JPWO2012017480A1 - Air conditioner indoor unit and air conditioner - Google Patents

Abstract

An indoor unit of an air conditioner capable of improving airflow controllability over a conventional air conditioner, and an air conditioner including the indoor unit are obtained. The indoor unit 100 includes a casing 1 in which a suction port 2 is formed in an upper portion and a blower outlet 3 is formed in a lower portion of a front surface portion, and an axial flow type or a mixed flow type provided on the downstream side of the suction port 2 in the casing 1. , The heat exchanger 50 provided downstream of the fan 20 in the casing 1 and upstream of the air outlet 3 and for exchanging heat between the air blown out from the fan 20 and the refrigerant, and the air outlet 3 and an upper and lower vane 70 that controls the vertical direction of the airflow blown out from the outlet 3, and the vertical direction of the airflow that has passed through the heat exchanger is set upstream of the upper and lower vane 70. An auxiliary upper and lower vane 71 to be controlled is provided.

Description

  The present invention relates to an indoor unit in which a fan and a heat exchanger are housed in a casing, and an air conditioner including the indoor unit.

  Conventionally, there exists an air conditioner in which a fan and a heat exchanger are housed in a casing. As such, “an air conditioner comprising a main body casing having an air inlet and an air outlet, and a heat exchanger disposed in the main body casing, wherein the air outlet includes a plurality of small propellers. There has been proposed an “air conditioner in which a fan unit having a fan arranged in the width direction of the air outlet is disposed” (see, for example, Patent Document 1). This air conditioner is provided with a fan unit at the air outlet to facilitate airflow direction control, and a fan unit having the same configuration is also provided at the suction port to improve the heat exchanger performance due to an increase in the air volume. I am doing so.

Japanese Patent Laying-Open No. 2005-3244 (paragraphs 0012, 0013, 0018 to 0021, FIGS. 5 and 6)

  The air conditioner like patent document 1 is provided with the heat exchanger in the upstream of the fan unit (blower). That is, the movable fan unit is provided on the air outlet side. For this reason, the airflow blown out from the air outlet has a swirl speed component accompanying the rotation of the fan, and the airflow controllability for inducing the airflow to a desired position in the air-conditioning target space is impaired. was there.

  The present invention has been made to solve the above-described problems, and includes an indoor unit of an air conditioner that can improve air flow controllability compared to a conventional air conditioner, and the indoor unit. The purpose is to obtain an air conditioner.

  An indoor unit of an air conditioner according to the present invention includes a casing having a suction port formed in an upper portion thereof and a blower outlet formed in a lower side of a front surface portion, and an axial flow type or a slant provided on the downstream side of the suction port in the casing. A flow type fan, a heat exchanger that is provided downstream of the fan in the casing and upstream of the air outlet, exchanges heat between the air blown from the fan and the refrigerant, and provided in the air outlet. An upper and lower vane that controls the vertical direction of the airflow blown from the outlet, and an auxiliary upper and lower vane that controls the vertical direction of the airflow that has passed through the heat exchanger is provided upstream of the upper and lower vanes. It is what.

  Moreover, the air conditioner which concerns on this invention is equipped with said indoor unit.

  In the present invention, since the auxiliary upper and lower vanes are provided on the upstream side of the upper and lower vanes, the air flow blown out from the outlet is smoothly deflected. Therefore, it is possible to obtain an indoor unit of an air conditioner that can improve the airflow controllability compared to a conventional air conditioner, and the indoor unit.

It is a longitudinal cross-sectional view which shows the indoor unit of the air conditioner which concerns on Embodiment 1 of this invention. It is an external appearance perspective view which shows the indoor unit of the air conditioner which concerns on Embodiment 1 of this invention. It is the perspective view which looked at the indoor unit which concerns on Embodiment 1 of this invention from the front right side. It is the perspective view which looked at the indoor unit which concerns on Embodiment 1 of this invention from the back right side. It is the perspective view which looked at the indoor unit which concerns on Embodiment 1 of this invention from the front left side. It is a perspective view which shows the drain pan which concerns on Embodiment 1 of this invention. It is a longitudinal cross-sectional view which shows the dew condensation generation | occurrence | production position of the indoor unit which concerns on Embodiment 1 of this invention. It is a block diagram which shows the signal processing apparatus which concerns on Embodiment 1 of this invention. It is a longitudinal cross-sectional view which shows another example of the indoor unit of the air conditioner which concerns on Embodiment 1 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 2 of this invention. It is explanatory drawing (longitudinal sectional drawing) for demonstrating the airflow control operation | movement of the indoor unit which concerns on Embodiment 2 of this invention. It is explanatory drawing (longitudinal sectional drawing) for demonstrating the airflow control operation | movement of the indoor unit which concerns on Embodiment 2 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 3 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 3 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 4 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 4 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 5 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 5 of this invention. It is a refrigerant circuit figure which shows an example of the refrigerant circuit of the air conditioner provided with the indoor unit which concerns on Embodiment 5 of this invention. It is a refrigerant circuit figure which shows an example of the refrigerant circuit of the air conditioner provided with the indoor unit which concerns on Embodiment 5 of this invention. It is a refrigerant circuit figure which shows another example of the refrigerant circuit of the air conditioner provided with the indoor unit which concerns on Embodiment 5 of this invention. It is a refrigerant circuit figure which shows another example of the refrigerant circuit of the air conditioner provided with the indoor unit which concerns on Embodiment 5 of this invention. It is a perspective view which shows the indoor unit which concerns on Embodiment 6 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 7 of this invention. It is explanatory drawing (longitudinal sectional drawing) for demonstrating the airflow control operation | movement of the indoor unit which concerns on Embodiment 7 of this invention. It is explanatory drawing (longitudinal sectional drawing) for demonstrating the airflow control operation | movement of the indoor unit which concerns on Embodiment 7 of this invention. It is a principal part enlarged view which shows an example of the moving mechanism which moves the rotating shaft position of the auxiliary | assistant upper and lower vane 71 which concerns on Embodiment 4 of this invention. It is a principal part enlarged view which shows another example of the moving mechanism which moves the rotating shaft position of the auxiliary | assistant vertical vane 71 which concerns on Embodiment 4 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 8 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 9 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 10 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 11 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 12 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 13 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 14 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 15 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 16 of this invention. It is a longitudinal cross-sectional view which shows the indoor unit which concerns on Embodiment 17 of this invention. 3 is a schematic diagram for explaining a configuration example of a heat exchanger 50. FIG. It is explanatory drawing which shows an example of the wind speed distribution of the blower outlet in the indoor unit which concerns on Embodiment 18 of this invention. It is explanatory drawing which shows another example of the wind speed distribution of the blower outlet in the indoor unit concerning Embodiment 18 of this invention. It is a principal part enlarged view (front sectional drawing) which shows the blower outlet vicinity of the indoor unit which concerns on Embodiment 18 of this invention. It is explanatory drawing which shows the wind speed distribution of a blower outlet when the air volume of each fan is made the same in the indoor unit which concerns on Embodiment 19 of this invention. It is explanatory drawing which shows an example of the wind speed distribution of a blower outlet in case the indoor unit which concerns on Embodiment 19 of this invention drive | operates in low air volume mode. It is a characteristic view which shows the relationship between the air volume reduction rate of the center part fan and the noise reduction effect at the time of the same air volume in the indoor unit according to Embodiment 19 of the present invention. It is explanatory drawing which shows an example of the wind speed distribution of the blower outlet in the indoor unit concerning Embodiment 20 of this invention.

  Hereinafter, a specific embodiment of an air conditioner (more specifically, an indoor unit of an air conditioner) according to the present invention will be described. In the first embodiment, a basic configuration of each unit constituting the indoor unit of the air conditioner will be described. In the second and subsequent embodiments, the detailed configuration of each unit or another example will be described. In each of the following embodiments, the present invention will be described by taking a wall-mounted indoor unit as an example. In the drawings shown in each embodiment, the shape and size of each unit (or a constituent member of each unit) may be partially different.

Embodiment 1 FIG.
<Basic configuration>
FIG. 1 is a longitudinal sectional view showing an indoor unit (referred to as an indoor unit 100) of an air conditioner according to Embodiment 1 of the present invention. FIG. 2 is an external perspective view showing the indoor unit. In the first embodiment and the embodiments described later, the left side in FIG. 1 will be described as the front side of the indoor unit 100. Hereinafter, the configuration of the indoor unit 100 will be described with reference to FIGS. 1 and 2.

(overall structure)
The indoor unit 100 supplies conditioned air to an air-conditioning target area such as a room by using a refrigeration cycle that circulates a refrigerant. The indoor unit 100 is mainly accommodated in a casing 1 in which a suction port 2 for sucking indoor air into the interior and a blower outlet 3 for supplying conditioned air to an air-conditioning target area are formed. The fan 20 sucks room air from the suction port 2 and blows out the conditioned air from the blower outlet 3 and the air passage from the fan 20 to the blower outlet 3, and exchanges heat between the refrigerant and the room air for conditioned air. And a heat exchanger 50 for producing And the air path (arrow Z) is connected in the casing 1 by these components. The suction port 2 is formed in the upper part of the casing 1. The blower outlet 3 has an opening formed in the lower part of the casing 1 (more specifically, on the lower side of the front part of the casing 1). The fan 20 is disposed on the downstream side of the suction port 2 and on the upstream side of the heat exchanger 50, and is configured by, for example, an axial flow fan or a diagonal flow fan.

  Further, in the indoor unit 100, the rotation speed of the fan 20 and the orientations of the upper and lower vanes 70 and the left and right vanes 80 (including auxiliary upper and lower vanes 71 when the later described auxiliary upper and lower vanes 71 are provided) ( A control device 281 for controlling the angle) and the like. Note that the controller 281 may not be shown in the drawings shown in the first embodiment and each embodiment described later.

  In the indoor unit 100 configured as described above, the fan 20 is provided on the upstream side of the heat exchanger 50, so that it is compared with a conventional air conditioner indoor unit in which the fan 20 is provided at the outlet 3. The generation of the swirling flow of the air blown from the outlet 3 and the variation in the wind speed distribution can be suppressed. For this reason, comfortable ventilation to an air-conditioning object area is attained. Further, since there is no complicated structure such as a fan at the air outlet 3, it is easy to take measures against condensation that occurs at the boundary between warm air and cold air during cooling operation. Furthermore, since the fan motor 30 is not exposed to cold air or warm air that is air-conditioned air, a long operating life can be provided.

(fan)
In general, an indoor unit of an air conditioner has a limited installation space, and thus often cannot have a large fan. For this reason, in order to obtain a desired air volume, a plurality of fans having an appropriate size are arranged in parallel. As shown in FIG. 2, the indoor unit 100 according to Embodiment 1 includes three fans 20 arranged in parallel along the longitudinal direction of the casing 1 (in other words, the longitudinal direction of the air outlet 3). Yes. In order to obtain a desired heat exchanging capacity in the dimensions of a current general air conditioner indoor unit, approximately two to four fans 20 are preferable. In the indoor unit according to the first embodiment, all the fans 20 are configured in the same shape, and almost the same amount of air flow can be obtained by all the fans 20 by operating all the operation rotational speeds equally.

  By configuring in this way, the optimum fan design corresponding to the indoor unit 100 of various specifications can be achieved by combining the number, shape, size, and the like of the fans 20 according to the required air volume and the ventilation resistance inside the indoor unit 100. Is possible.

(Bellmouth)
In the indoor unit 100 according to the first embodiment, a bell mouth 5 on a duct is disposed around the fan 20. The bell mouth 5 is for smoothly guiding the intake and exhaust of air to the fan. As shown in FIG. 1, the bell mouth 5 according to the first embodiment has a substantially circular shape in plan view. In the longitudinal section, the bell mouth 5 according to the first embodiment has the following shape. The upper part 5a has a substantially arc shape whose end part widens upward. The central portion 5b is a straight portion where the diameter of the bell mouth is constant. The lower part 5c has a substantially arc shape whose end part extends downward. And the suction inlet 2 is formed in the edge part (arc part of the suction side) of the upper part 5a of the bellmouth 5. FIG.
The bell mouth 5 shown in FIG. 1 of the first embodiment has a duct shape configured higher than the height of the impeller of the fan 20, but is not limited thereto, and the height of the bell mouth 5 is not limited thereto. A semi-open bellmouth configured lower than the height of the impeller of the fan 20 may be used. Furthermore, the bell mouth 5 may not be provided with the straight portion 5b shown in FIG. 1 but may be constituted only by the end portions 5a and 5c.

  The bell mouth 5 may be formed integrally with the casing 1, for example, in order to reduce the number of parts and improve the strength. Further, for example, the bell mouth 5, the fan 20, the fan motor 30, and the like may be modularized, and the casing 1 may be attached and detached to improve maintenance.

  In the first embodiment, the end of the upper portion 5 a of the bell mouth 5 (arc portion on the suction side) is configured in a uniform shape with respect to the circumferential direction of the opening surface of the bell mouth 5. In other words, the bell mouth 5 has no structure such as a notch or a rib with respect to the rotation direction about the rotation axis 20a of the fan 20, and has a uniform shape having axial symmetry.

  By configuring the bell mouth 5 in this way, the end of the upper portion 5a of the bell mouth 5 (the arc portion on the suction side) has a uniform shape with respect to the rotation of the fan 20. A uniform flow is realized as a flow. For this reason, the noise which generate | occur | produces by the drift of the suction flow of the fan 20 can be reduced.

(Partition plate)
As shown in FIG. 2, in the indoor unit 100 according to the first embodiment, a partition plate 90 is provided between adjacent fans 20. These partition plates 90 are installed between the heat exchanger 50 and the fan 20. That is, the air path between the heat exchanger 50 and the fan 20 is divided into a plurality of air paths (three in the first embodiment). Since the partition plate 90 is installed between the heat exchanger 50 and the fan 20, the end on the side in contact with the heat exchanger 50 has a shape along the heat exchanger 50. More specifically, as shown in FIG. 1, the heat exchanger 50 includes a longitudinal section from the front side to the rear side of the indoor unit 100 (that is, a longitudinal section when the indoor unit 100 is viewed from the right side. Are arranged in a substantially Λ shape. For this reason, the heat exchanger 50 side end part of the partition plate 90 is also substantially [Lambda] type.

  In addition, what is necessary is just to determine the position of the fan 20 side edge part of the partition plate 90 as follows, for example. When the adjacent fans 20 are sufficiently separated from each other on the suction side so as not to affect each other, the end of the partition plate 90 on the fan 20 side may be extended to the outlet surface of the fan 20. However, when the adjacent fans 20 are close enough to influence each other on the suction side, and the shape of the end of the upper portion 5a of the bell mouth 5 (arc portion on the suction side) can be formed sufficiently large, The end of the plate 90 on the fan 20 side extends to the upstream side (suction side) of the fan 20 so as not to affect the adjacent air path (so that the adjacent fans 20 do not affect each other on the suction side). It may be extended.

  Further, the partition plate 90 can be formed of various materials. For example, the partition plate 90 may be formed of a metal such as steel or aluminum. For example, the partition plate 90 may be formed of resin or the like. However, since the heat exchanger 50 becomes a high temperature during the heating operation, when the partition plate 90 is formed of a low melting point material such as a resin, the heat exchanger 50 is slightly between the partition plate 90 and the heat exchanger 50. A good space should be formed. When the partition plate 90 is made of a material having a high melting point such as aluminum or steel, the partition plate 90 may be disposed in contact with the heat exchanger 50. When the heat exchanger 50 is, for example, a fin tube type heat exchanger, a partition plate 90 may be inserted between the fins of the heat exchanger 50.

  As described above, the air path between the heat exchanger 50 and the fan 20 is divided into a plurality of air paths (three in the first embodiment). A noise absorbing material can be provided in this air passage, that is, in the partition plate 90 and the casing 1 to reduce noise generated in the duct.

  Further, these divided air paths are formed in a substantially quadrangular shape with one side being L1 and L2 in plan view. That is, the width of the divided air path is L1 and L2. For this reason, for example, the amount of air generated by the fan 20 installed inside the substantially square shape formed by L1 and L2 is reliably transferred to the heat exchanger 50 in the region surrounded by L1 and L2 downstream of the fan 20. pass.

  Thus, by dividing the air passage in the casing 1 into a plurality of air passages, the air blown from each fan 20 is blown into the indoor unit 100 even if the flow field created downstream by the fan 20 has a swirling component. Cannot move freely in the longitudinal direction (the direction perpendicular to the plane of FIG. 1). For this reason, the air blown out by the fan 20 can be passed through the heat exchanger 50 in the region surrounded by L1 and L2 downstream of the fan 20. As a result, variation in the air volume distribution in the longitudinal direction of the indoor unit 100 flowing into the entire heat exchanger 50 (in the direction orthogonal to the plane of FIG. 1) can be suppressed, and high heat exchange performance can be achieved. Further, by dividing the inside of the casing 1 with the partition plate 90, interference between the adjacent fans 20 and the swirl flow generated by the adjacent fans 20 can be prevented. For this reason, the loss of fluid energy due to the interference between the swirling flows can be suppressed, and the pressure loss of the indoor unit 100 can be reduced together with the improvement of the wind speed distribution. In addition, each partition plate 90 does not need to be formed with a single plate, and may be formed with a plurality of plates. For example, the partition plate 90 may be divided into two parts on the front side heat exchanger 51 side and the back side heat exchanger 55 side. Needless to say, it is preferable that there is no gap at the joint between the plates constituting the partition plate 90. By dividing the partition plate 90 into a plurality of parts, the assembling property of the partition plate 90 is improved.

(fan motor)
The fan 20 is rotationally driven by a fan motor 30. The fan motor 30 used may be an inner rotor type or an outer rotor type. In the case of the outer rotor type fan motor 30, a structure in which the rotor is integrated with the boss 21 of the fan 20 (the boss 21 is provided with a rotor) is also used. Further, by making the size of the fan motor 30 smaller than the size of the boss 21 of the fan 20, it is possible to prevent loss of the airflow generated by the fan 20. Further, by arranging a motor inside the boss 21, the axial dimension can be reduced. By making the fan motor 30 and the fan 20 easy to attach and detach, the maintainability is also improved.

  The use of a relatively expensive DC brushless motor as the fan motor 30 can improve efficiency, extend the service life, and improve the controllability. However, even if other types of motors are used, air conditioning It goes without saying that the primary function of the machine is satisfied. The circuit for driving the fan motor 30 may be integrated with the fan motor 30 or may be configured externally to take dust and fire prevention measures.

  The fan motor 30 is attached to the casing 1 by a motor stay 16. Further, the fan motor 30 is a box type (fan 20, housing, fan motor 30, bell mouth 5, motor stay 16 and the like are integrated into a module) used for CPU cooling and the like, and is detachable from the casing 1. If the structure is possible, the maintainability is improved and the accuracy of the chip clearance of the fan 20 can be increased. In general, a narrow tip clearance is preferable because of high air blowing performance.

  Note that the drive circuit of the fan motor 30 may be configured inside the fan motor 30 or may be external.

(Motor stay)
The motor stay 16 includes a fixing member 17 and a support member 18. The fixing member 17 is to which the fan motor 30 is attached. The support member 18 is a member for fixing the fixing member 17 to the casing 1. The support member 18 is, for example, a rod-like member, and extends from the outer peripheral portion of the fixing member 17, for example, radially. As shown in FIG. 1, the support member 18 according to the first embodiment extends approximately in the horizontal direction. In addition, the support member 18 may provide a stationary blade effect as a blade shape or a plate shape.

(Heat exchanger)
The heat exchanger 50 of the indoor unit 100 according to Embodiment 1 is arranged on the leeward side of the fan 20. As the heat exchanger 50, for example, a fin tube heat exchanger or the like may be used. As shown in FIG. 1, the heat exchanger 50 is divided by a symmetry line 50a in the right vertical section. The symmetry line 50a divides the installation range of the heat exchanger 50 in this cross section in the left-right direction at a substantially central portion. That is, the front side heat exchanger 51 is on the front side (left side in FIG. 1) with respect to the symmetry line 50a, and the rear side heat exchanger 55 is on the back side (right side in FIG. 1) with respect to the symmetry line 50a. Each is arranged. The front-side heat exchanger 51 and the rear-side heat exchanger 55 are arranged so that the distance between the front-side heat exchanger 51 and the rear-side heat exchanger 55 widens with respect to the air flow direction, that is, the right-side longitudinal section. The heat exchanger 50 is arranged in the casing 1 so that the cross-sectional shape of the heat exchanger 50 is substantially Λ-shaped. That is, the front side heat exchanger 51 and the back side heat exchanger 55 are arranged so as to be inclined with respect to the flow direction of the air supplied from the fan 20.

  Further, the heat exchanger 50 is characterized in that the air passage area of the back surface side heat exchanger 55 is larger than the air passage area of the front surface side heat exchanger 51. That is, in the heat exchanger 50, the air volume of the back side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. In the first embodiment, the longitudinal length of the back side heat exchanger 55 is longer than the longitudinal length of the front side heat exchanger 51 in the right vertical section. Thereby, the air path area of the back surface side heat exchanger 55 is larger than the air path area of the front surface side heat exchanger 51. The other configurations (such as the length in the depth direction in FIG. 1) of the front side heat exchanger 51 and the back side heat exchanger 55 are the same. That is, the heat transfer area of the back side heat exchanger 55 is larger than the heat transfer area of the front side heat exchanger 51. Moreover, the rotating shaft 20a of the fan 20 is installed above the symmetry line 50a.

  By configuring the heat exchanger 50 in this manner, the generation of a swirling flow of the air blown from the blower outlet 3 and the distribution of the wind speed are compared with a conventional air conditioner indoor unit in which a fan is provided at the blower outlet. Occurrence can be suppressed. In addition, by configuring the heat exchanger 50 in this manner, the air volume of the back side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. And when the air which passed each of the front side heat exchanger 51 and the back side heat exchanger 55 merges by this air volume difference, this merged air will bend to the front side (blower outlet 3 side). For this reason, it is no longer necessary to bend the airflow rapidly in the vicinity of the outlet 3, and the pressure loss in the vicinity of the outlet 3 can be reduced.

  Moreover, in the indoor unit 100 according to the first embodiment, the flow direction of the air flowing out from the back side heat exchanger 55 is the flow from the back side to the front side. For this reason, the indoor unit 100 according to the first embodiment bends the flow of air after passing through the heat exchanger 50, as compared with the case where the heat exchanger 50 is arranged in a substantially v shape in the right vertical section. It becomes easy.

  Since the indoor unit 100 has a plurality of fans 20, the weight tends to increase. When the indoor unit 100 becomes heavy, the strength of the wall surface for installing the indoor unit 100 is required, which is a restriction on installation. For this reason, it is preferable to reduce the weight of the heat exchanger 50. Moreover, since the indoor unit 100 arrange | positions the fan 20 in the upstream of the heat exchanger 50, the height dimension of the indoor unit 100 becomes large and tends to become restrictions on installation. For this reason, it is preferable to reduce the weight of the heat exchanger 50. Moreover, it is preferable to reduce the size of the heat exchanger 50.

  Therefore, in the first embodiment, fin tube type heat exchangers are used as the heat exchangers 50 (the front side heat exchanger 51 and the back side heat exchanger 55), and the heat exchanger 50 is downsized. More specifically, the heat exchanger 50 according to the first embodiment includes a plurality of fins 56 stacked via a predetermined gap, and a plurality of heat transfer tubes 57 penetrating the fins 56. In the first embodiment, the fins 56 are stacked in the left-right direction of the casing 1 (the direction orthogonal to the plane of FIG. 1). That is, the heat transfer tube 57 passes through the fin 56 along the left-right direction of the casing 1 (the direction orthogonal to the plane of FIG. 1). In Embodiment 1, in order to improve the heat exchange efficiency of the heat exchanger 50, two rows of heat transfer tubes 57 are arranged in the ventilation direction of the heat exchanger 50 (the width direction of the fins 56). These heat transfer tubes 57 are arranged in a substantially zigzag shape in the right vertical section.

  Further, the heat transfer tube 57 is formed of a circular tube having a thin diameter (diameter of about 3 mm to 7 mm), and the refrigerant flowing through the heat transfer tube 57 (the refrigerant used in the indoor unit 100 and the air conditioner including the indoor unit 100) is R32. Thus, the heat exchanger 50 is reduced in size. That is, the heat exchanger 50 exchanges heat between the refrigerant flowing in the heat transfer tube 57 and the room air via the fins 56. For this reason, when the heat transfer tube 57 is made thin, the pressure loss of the refrigerant becomes large at the same refrigerant circulation amount as compared with a heat exchanger having a large heat transfer tube diameter. However, R32 has a larger latent heat of vaporization at the same temperature than R410A, and can exhibit the same ability with a smaller amount of refrigerant circulation. For this reason, by using R32, the amount of refrigerant to be used can be reduced, and the pressure loss in the heat exchanger 50 can be reduced. Therefore, the heat exchanger 50 can be reduced in size by configuring the heat transfer tube 57 as a thin circular tube and using R32 as the refrigerant.

  In the heat exchanger 50 according to the first embodiment, the heat exchanger 50 is reduced in weight by forming the fins 56 and the heat transfer tubes 57 from aluminum or an aluminum alloy. In addition, when the weight of the heat exchanger 50 does not become an installation-like restriction | limiting, of course, you may comprise the heat exchanger tube 57 with copper.

(Finger guard & filter)
In the indoor unit 100 according to the first embodiment, the finger guard 15 and the filter 10 are provided at the suction port 2. The finger guard 15 is installed for the purpose of preventing the rotating fan 20 from being touched. For this reason, the shape of the finger guard 15 is arbitrary as long as the hand cannot be touched to the fan 20. For example, the shape of the finger guard 15 may be a lattice shape, or may be a circular shape formed of a large number of different rings. In addition, the finger guard 15 may be made of a material such as a resin or a metal material. However, when strength is required, the finger guard 15 is preferably made of a metal. In addition, the finger guard 15 is preferably as thin and strong as possible from the viewpoint of lowering ventilation resistance and maintaining strength. The filter 10 is provided to prevent dust from flowing into the indoor unit 100. The filter 10 is detachably provided on the casing 1. Moreover, although not shown in figure, the indoor unit 100 which concerns on this Embodiment 1 may be provided with the automatic cleaning mechanism which cleans the filter 10 automatically.

(Wind direction control vane)
Moreover, the indoor unit 100 which concerns on this Embodiment 1 is provided in the blower outlet 3 with the up-and-down vane 70 and the right-and-left vane (not shown) which are mechanisms which control the blowing direction of airflow.

(Drain pan)
FIG. 3 is a perspective view of the indoor unit according to Embodiment 1 of the present invention as viewed from the front right side. FIG. 4 is a perspective view of the indoor unit as viewed from the rear right side. FIG. 5 is a perspective view of the indoor unit as viewed from the front left side. FIG. 6 is a perspective view showing the drain pan according to Embodiment 1 of the present invention. In order to facilitate understanding of the shape of the drain pan, in FIGS. 3 and 4, the right side of the indoor unit 100 is shown in cross section, and in FIG. 5, the left side of the indoor unit 100 is shown in cross section.

  A front side drain pan 110 is provided below a lower end portion of the front side heat exchanger 51 (a front side end portion of the front side heat exchanger 51). A back side drain pan 115 is provided below the lower end portion of the back side heat exchanger 55 (the back side end of the back side heat exchanger 55). In the first embodiment, the back side drain pan 115 and the back portion 1b of the casing 1 are integrally formed. The back side drain pan 115 is provided with connection ports 116 to which the drain hose 117 is connected at both the left end and the right end. In addition, it is not necessary to connect the drain hose 117 to both the connection ports 116, and the drain hose 117 may be connected to one of the connection ports 116. For example, when the drain hose 117 is to be pulled out to the right side of the indoor unit 100 during installation of the indoor unit 100, the drain hose 117 is connected to the connection port 116 provided at the right end of the back side drain pan 115, and the back side The connection port 116 provided at the left end of the drain pan 115 may be closed with a rubber cap or the like.

  The front side drain pan 110 is disposed at a position higher than the back side drain pan 115. Further, between the front side drain pan 110 and the back side drain pan 115, a drainage channel 111 serving as a drain moving path is provided at both the left end and the right end. The drainage channel 111 has a front end connected to the front drain pan 110 and is provided so as to incline downward from the front drain pan 110 toward the rear drain pan 115. In addition, a tongue portion 111 a is formed at the end of the drainage channel 111 on the back side. The rear end of the drainage channel 111 is disposed so as to cover the upper surface of the back side drain pan 115.

During the cooling operation, when the indoor air is cooled by the heat exchanger 50, condensation occurs in the heat exchanger 50. The dew adhering to the front side heat exchanger 51 is dropped from the lower end portion of the front side heat exchanger 51 and collected by the front side drain pan 110. The dew adhering to the back side heat exchanger 55 drops from the lower end of the back side heat exchanger 55 and is collected by the back side drain pan 115.
In the first embodiment, the front-side drain pan 110 is provided at a position higher than the back-side drain pan 115, so that the drain collected by the front-side drain pan 110 is directed toward the back-side drain pan 115 toward the drainage channel 111. Flowing. Then, the drain is dropped from the tongue 111 a of the drainage channel 111 to the back side drain pan 115 and collected by the back side drain pan 115. The drain collected by the back side drain pan 115 passes through the drain hose 117 and is discharged to the outside of the casing 1 (indoor unit 100).

  By providing the front-side drain pan 110 at a position higher than the back-side drain pan 115 as in the first embodiment, the drain collected by both drain pans is disposed on the back-side drain pan 115 (most rear side of the casing 1). Can be collected in the drain pan). For this reason, by providing the connection port 116 of the drain hose 117 in the back side drain pan 115, the drain collected by the front side drain pan 110 and the back side drain pan 115 can be discharged to the outside of the casing 1. Therefore, when performing maintenance (such as cleaning the heat exchanger 50) of the indoor unit 100 by opening the front surface of the casing 1, it is not necessary to attach or detach the drain pan to which the drain hose 117 is connected. Improves.

  Further, since the drainage channels 111 are provided at both the left end and the right end, even if the indoor unit 100 is installed in an inclined state, the drain collected by the front side drain pan 110 can be surely received from the back side drain pan. 115. In addition, since the connection ports for connecting the drain hose 117 are provided at both the left end and the right end, the hose pull-out direction can be selected according to the installation conditions of the indoor unit 100, and the indoor unit 100 The workability when installing is improved. In addition, since the drainage channel 111 is disposed so as to cover the backside drain pan 115 (that is, a connection mechanism is not required between the drainage channel 111 and the backside drain pan 115), the front side drain pan 110 is disposed. It becomes easy to attach and detach, and the maintainability is further improved.

  In addition, the drainage channel 111 may be arranged so that the rear side end of the drainage channel 111 is connected to the rear side drain pan 115 and the front side drain pan 110 covers the drainage channel 111. Even in such a configuration, it is possible to obtain the same effect as the configuration in which the drainage channel 111 is disposed so as to cover the back side drain pan 115. Further, the front-side drain pan 110 does not necessarily need to be higher than the rear-side drain pan 115. Even if the front-side drain pan 110 and the rear-side drain pan 115 have the same height, the drain collected by both drain pans is connected to the rear-side drain pan 115. The drainage hose can be discharged.

(nozzle)
Further, the indoor unit 100 according to Embodiment 1 has an opening length d1 on the entrance side of the nozzle 6 in the right vertical section (between the drain pans defined between the front-side drain pan 110 and the back-side drain pan 115 portion. The throttle length d1) is configured to be larger than the opening length d2 on the outlet side of the nozzle 6 (the length of the outlet 3). That is, the nozzle 6 of the indoor unit 100 satisfies d1> d2 (see FIG. 1).

  The reason why the nozzle 6 satisfies d1> d2 is as follows. In addition, since d2 affects the reachability of the airflow, which is one of the basic functions of the indoor unit, in the following, d2 of the indoor unit 100 according to the first embodiment is approximately the same as the air outlet of the conventional indoor unit. It will be described as being length.

  By making d1> d2 the shape of the nozzle 6 in the longitudinal section, the air passage becomes larger and the angle A of the heat exchanger 50 arranged on the upstream side (the front side heat on the downstream side of the heat exchanger 50). It is possible to increase the angle formed by the exchanger 51 and the back side heat exchanger 55. For this reason, the wind speed distribution generated in the heat exchanger 50 is relaxed, and the air path downstream of the heat exchanger 50 can be formed large, so that the pressure loss of the entire indoor unit 100 can be reduced. Furthermore, the deviation of the wind speed distribution that has occurred near the inlet of the nozzle 6 can be made uniform by the effect of contraction and guided to the outlet 3.

  For example, in the case of d1 = d2, the deviation of the wind speed distribution generated in the vicinity of the inlet of the nozzle 6 (for example, the flow biased to the back side) becomes the deviation of the wind speed distribution at the outlet 3 as it is. That is, in the case of d1 = d2, air is blown out from the outlet 3 in a state where the wind speed distribution is uneven. For example, in the case of d1 <d2, when the air that has passed through the front-side heat exchanger 51 and the rear-side heat exchanger 55 merges in the vicinity of the inlet of the nozzle 6, the contraction loss increases. For this reason, in the case of d1 <d2, if the diffusion effect of the outlet 3 is not obtained, a loss corresponding to the contraction loss occurs.

(ANC)
In addition, the indoor unit 100 according to Embodiment 1 is provided with an active silencing mechanism as shown in FIG.

  More specifically, the silencing mechanism of the indoor unit 100 according to the first embodiment includes a noise detection microphone 161, a control speaker 181, a silencing effect detection microphone 191, and a signal processing device 201. The noise detection microphone 161 is a noise detection device that detects the operation sound (noise) of the indoor unit 100 including the blowing sound of the fan 20. The noise detection microphone 161 is disposed between the fan 20 and the heat exchanger 50. In the first embodiment, it is provided on the front surface in the casing 1. The control speaker 181 is a control sound output device that outputs a control sound for noise. The control speaker 181 is disposed below the noise detection microphone 161 and above the heat exchanger 50. In this Embodiment 1, it is provided in the front part in the casing 1 so that it may face the center of an air path. The silencing effect detection microphone 191 is a silencing effect detection device that detects the silencing effect by the control sound. The muffler effect detection microphone 191 is provided in the vicinity of the air outlet 3 in order to detect noise coming from the air outlet 3. Further, the muffler effect detection microphone 191 is attached at a position avoiding the wind flow so as not to hit the blown air coming out of the blowout port 3. The signal processing device 201 is a control sound generation device that causes the control speaker 181 to output a control sound based on the detection results of the noise detection microphone 161 and the silencing effect detection microphone 191. The signal processing device 201 is accommodated in the control device 281, for example.

  FIG. 8 is a block diagram showing the signal processing apparatus according to Embodiment 1 of the present invention. Electric signals input from the noise detection microphone 161 and the muffler effect detection microphone 191 are amplified by the microphone amplifier 151 and converted from an analog signal to a digital signal by the A / D converter 152. The converted digital signal is input to the FIR filter 158 and the LMS algorithm 159. The FIR filter 158 generates a control signal that has been corrected so that the noise detected by the noise detection microphone 161 has the same amplitude and opposite phase as the noise when the noise reduction effect detection microphone 191 is installed. After being converted from a digital signal to an analog signal by the D / A converter 154, it is amplified by the amplifier 155 and emitted from the control speaker 181 as a control sound.

  As shown in FIG. 7, when the air conditioner is in a cooling operation, the temperature of the region B between the heat exchanger 50 and the outlet 3 is lowered by the cold air, so that water vapor in the air appears as water droplets. Condensation occurs. For this reason, the indoor unit 100 is provided with a water receptacle or the like (not shown) for preventing water droplets from coming out of the air outlet 3 in the vicinity of the air outlet 3. In addition, since the area | region where the noise detection microphone 161 and the control speaker 181 which are upstream of the heat exchanger 50 are arrange | positioned is upstream of the area | region cooled with cold air | atmosphere, dew condensation does not arise.

  Next, a method for suppressing the operation sound of the indoor unit 100 will be described. The operation sound (noise) including the blowing sound of the fan 20 in the indoor unit 100 is detected by the noise detection microphone 161 attached between the fan 20 and the heat exchanger 50, and the microphone amplifier 151 and the A / D converter 152 are detected. And is input to the FIR filter 158 and the LMS algorithm 159.

The tap coefficients of the FIR filter 158 are sequentially updated by the LMS algorithm 159. In the LMS algorithm 159, the tap coefficient is updated according to the equation 1 (h (n + 1) = h (n) + 2 · μ · e (n) · x (n)), and the optimum tap is set so that the error signal e approaches zero. The coefficient is updated.
Note that h is a filter tap coefficient, e is an error signal, x is a filter input signal, and μ is a step size parameter. The step size parameter μ controls a filter coefficient update amount for each sampling.

  Thus, the digital signal that has passed through the FIR filter 158 whose tap coefficient has been updated by the LMS algorithm 159 is converted to an analog signal by the D / A converter 154, amplified by the amplifier 155, and the fan 20 and heat exchanger. 50 is emitted as a control sound from the control speaker 181 attached between the indoor unit 100 and the air passage in the indoor unit 100.

  On the other hand, at the lower end of the indoor unit 100, the sound is transmitted from the fan 20 through the air path to the muffler effect detection microphone 191 attached in the direction of the outer wall of the air outlet 3 so that the wind emitted from the air outlet 3 does not hit. The sound after the control sound emitted from the control speaker 181 interferes with the noise coming out from the blow outlet 3 is detected. Since the sound detected by the muffling effect detection microphone 191 is input to the error signal of the LMS algorithm 159 described above, the tap coefficient of the FIR filter 158 is updated so that the sound after the interference approaches zero. become. As a result, noise in the vicinity of the air outlet 3 can be suppressed by the control sound that has passed through the FIR filter 158.

  As described above, in the indoor unit 100 to which the active silencing method is applied, the noise detection microphone 161 and the control speaker 181 are arranged between the fan 20 and the heat exchanger 50, and the silencing effect detection microphone 191 is connected to the blower outlet 3. It is installed in the place where the wind current does not hit. For this reason, since it is not necessary to attach a member that requires active silencing to the region B where condensation occurs, water droplets are prevented from adhering to the control speaker 181, the noise detecting microphone 161, and the silencing effect detecting microphone 191, and the silencing performance is deteriorated. The failure of the speaker and microphone can be prevented.

  Note that the attachment positions of the noise detection microphone 161, the control speaker 181, and the mute effect detection microphone 191 shown in the first embodiment are merely examples. For example, as shown in FIG. 9, the noise reduction effect detection microphone 191 may be disposed between the fan 20 and the heat exchanger 50 together with the noise detection microphone 161 and the control speaker 181. Further, although the microphone has been exemplified as a means for detecting the silencing effect after the noise is canceled by the noise or the control sound, it may be configured by an acceleration sensor or the like that detects the vibration of the casing. Alternatively, the sound may be regarded as air flow disturbance, and the noise reduction effect after the noise is canceled by noise or control sound may be detected as air flow disturbance. That is, a flow rate sensor, a hot wire probe, or the like that detects an air flow may be used as a means for detecting a silencing effect after noise is canceled by noise or control sound. It is also possible to detect the air flow by increasing the gain of the microphone.

  In the first embodiment, the FIR filter 158 and the LMS algorithm 159 are used in the signal processing device 201. However, any adaptive signal processing circuit that brings the sound detected by the mute effect detection microphone 191 close to zero may be active. Alternatively, a filtered-X algorithm that is generally used in the automatic mute method may be used. Further, the signal processing device 201 may be configured to generate the control sound by a fixed tap coefficient instead of the adaptive signal processing. Further, the signal processing device 201 may be an analog signal processing circuit instead of digital signal processing.

  Further, in the first embodiment, the case where the heat exchanger 50 that cools the air so that condensation occurs is described, but the present invention is applicable even when the heat exchanger 50 that does not cause condensation is disposed. Therefore, it is possible to prevent performance deterioration of the noise detection microphone 161, the control speaker 181, the silencing effect detection microphone 191, and the like without considering the presence or absence of dew condensation due to the heat exchanger 50.

Embodiment 2. FIG.
(Auxiliary upper and lower vanes)
The indoor unit 100 according to Embodiment 1 performs the vertical control of the airflow that has passed through the heat exchanger 50 using only the upper and lower vanes 70. By providing the following auxiliary upper and lower vanes on the upstream side of the upper and lower vanes 70, the air flow controllability of the indoor unit 100 can be improved. In the second embodiment, the same functions and configurations as those in the first embodiment will be described using the same reference numerals.

FIG. 10 is a longitudinal sectional view showing the indoor unit according to Embodiment 2 of the present invention.
In the indoor unit 100 according to the second embodiment, auxiliary upper and lower vanes 71 are provided between the heat exchanger 50 and the upper and lower vanes 70 (that is, upstream of the upper and lower vanes 70).

  A conventional indoor unit is provided with a heat exchanger so as to cover the upstream side of a fan (such as a crossflow fan). On the other hand, in the indoor unit 100 according to the second embodiment, the fan 20 is provided on the upstream side of the heat exchanger 50. For this reason, the indoor unit 100 according to the second embodiment can provide the auxiliary upper and lower vanes 71 in the region occupied by the fan in the conventional indoor unit. Therefore, in the vertical cross section on the right side, the auxiliary upper and lower vanes 71 are positioned so that the upstream end of the auxiliary upper and lower vanes 71 is located above the imaginary straight line (the two-dot chain line shown in FIG. 10) connecting the lower ends of the heat exchanger 50. 71 can also be provided. In the conventional indoor unit, even when only the upper and lower vanes 70 do not provide sufficient distance for bending the air flow, and the desired air flow controllability cannot be obtained, the indoor unit 100 according to the second embodiment is provided on the upstream side of the upper and lower vanes 70. Since the auxiliary upper and lower vanes 71 can be provided, the air flow controllability can be improved.

  The indoor unit 100 configured as described above controls the direction of the airflow that has passed through the heat exchanger 50 as follows.

FIG. 11 is an explanatory diagram (longitudinal sectional view) for explaining the airflow control operation of the indoor unit according to Embodiment 2 of the present invention.
For example, when the airflow that has passed through the heat exchanger 50 is to be bent downward during heating operation, the upper and lower vanes 70 and the auxiliary upper and lower vanes 71 are controlled so that the state shown in FIG. 10 is changed to the state shown in FIG. do it. That is, in the right vertical section, the upper and lower vanes 70 and the auxiliary upper and lower vanes 71 may be rotated counterclockwise so that the upper and lower vanes 70 and the auxiliary upper and lower vanes 71 are directed downward. At this time, the auxiliary upper and lower vanes 71 may be controlled so as to be higher than the upper and lower vanes 70. Thus, by making the angles of the upper and lower vanes 70 and the auxiliary upper and lower vanes 71 different, the airflow that has passed through the heat exchanger 50 can be bent smoothly, and airflow controllability is further improved.

FIG. 12 is an explanatory diagram (longitudinal sectional view) for explaining the airflow control operation of the indoor unit according to Embodiment 2 of the present invention.
For example, when the airflow that has passed through the heat exchanger 50 is to be bent upward during cooling operation, the upper and lower vanes 70 and the auxiliary upper and lower vanes 71 are controlled so that the state shown in FIG. 10 is changed to the state shown in FIG. do it. That is, in the right vertical section, the upper and lower vanes 70 and the auxiliary upper and lower vanes 71 may be rotated clockwise so that the upper and lower vanes 70 and the auxiliary upper and lower vanes 71 are directed upward. At this time, the auxiliary upper and lower vanes 71 may be controlled so as to face downward from the upper and lower vanes 70. Thus, by making the angles of the upper and lower vanes 70 and the auxiliary upper and lower vanes 71 different, the airflow that has passed through the heat exchanger 50 can be bent smoothly, and airflow controllability is further improved.

  As described above, in the indoor unit 100 configured as described above, the auxiliary upper and lower vanes 71 are provided on the upstream side of the upper and lower vanes 70, so that the heat exchanger 50 has passed through both the heating operation and the cooling operation. A sufficient distance can be obtained to bend the airflow. For this reason, the airflow controllability of the indoor unit 100 is improved.

Embodiment 3 FIG.
A plurality of auxiliary upper and lower vanes 71 may be installed. In the third embodiment, items that are not particularly described are the same as those in the second embodiment, and the same functions and configurations are described using the same reference numerals.

13 and 14 are longitudinal sectional views showing an indoor unit according to Embodiment 3 of the present invention.
In the indoor unit 100 according to Embodiment 3, two auxiliary upper and lower vanes (auxiliary upper and lower vanes 71a and 71b) are provided between the heat exchanger 50 and the upper and lower vanes 70 (that is, upstream of the upper and lower vanes 70). Is provided. More specifically, an auxiliary upper and lower vane 71 a is provided on the upstream side of the upper and lower vanes 70. An auxiliary upper and lower vane 71b is further provided upstream of the auxiliary upper and lower vane 71a. Of course, three or more auxiliary upper and lower vanes 71 may be provided.

  The indoor unit 100 configured as described above controls the direction of the airflow that has passed through the heat exchanger 50 as follows.

  For example, when the airflow that has passed through the heat exchanger 50 is to be bent upward during cooling operation, the upper and lower vanes 70, auxiliary upper and lower vanes 71a, and 71b are controlled so as to be in the state shown in FIG. That's fine. At this time, the auxiliary upper and lower vanes 71a may be controlled so as to face downward from the upper and lower vanes 70. Moreover, it is good to control the auxiliary | assistant upper / lower vane 71b so that it may become downward rather than the auxiliary | assistant upper / lower vane 71a. Thus, by making the angles of the upper and lower vanes 70, the auxiliary upper and lower vanes 71a, and the auxiliary upper and lower vanes 71b different, the airflow that has passed through the heat exchanger 50 can be bent more smoothly than in the second embodiment.

  For example, when it is desired to bend the airflow that has passed through the heat exchanger 50 downward during heating operation, the upper and lower vanes 70, the auxiliary upper and lower vanes 71a, and 71b are controlled so as to be in the state shown in FIG. That's fine. At this time, the auxiliary upper and lower vanes 71a may be controlled so as to be higher than the upper and lower vanes 70. Moreover, it is good to control the auxiliary | assistant upper / lower vane 71b so that it may become upward rather than the auxiliary | assistant upper / lower vane 71a. Thus, by making the angles of the upper and lower vanes 70, the auxiliary upper and lower vanes 71a, and the auxiliary upper and lower vanes 71b different, the airflow that has passed through the heat exchanger 50 can be bent more smoothly than in the second embodiment.

  As described above, the indoor unit 100 according to the third embodiment has a plurality of auxiliary upper and lower vanes 71 provided on the upstream side of the upper and lower vanes 70, and thus heats more smoothly than the indoor unit 100 according to the second embodiment. The airflow that has passed through the exchanger 50 can be bent. For this reason, the air flow controllability of the indoor unit 100 according to the third embodiment is further improved as compared with the indoor unit 100 according to the second embodiment.

Embodiment 4 FIG.
Further, the rotational axis positions of the upper and lower vanes 70 and the auxiliary upper and lower vanes 71 may be movable. In Embodiment 4, items that are not particularly described are the same as those in Embodiment 2 or Embodiment 3, and the same functions and configurations are described using the same reference numerals.

15 and 16 are longitudinal sectional views showing an indoor unit according to Embodiment 4 of the present invention.
In the indoor unit 100 according to Embodiment 4, the rotational axis position of the auxiliary upper and lower vanes 71 during the heating operation is different from the rotational axis position of the auxiliary upper and lower vanes 71 during the cooling operation.

That is, when it is desired to bend the airflow that has passed through the heat exchanger 50 downward, the rotation shaft of the auxiliary upper and lower vanes 71 moves to the rotation shaft position 71c as shown in FIG. Then, the auxiliary upper and lower vanes 71 rotate around the rotation shaft position 71c.
Further, when it is desired to bend the airflow that has passed through the heat exchanger 50 upward, the rotation shaft of the auxiliary upper and lower vanes 71 moves to the rotation shaft position 71d as shown in FIG. Then, the auxiliary upper and lower vanes 71 rotate around the rotation shaft position 71d.
The rotation axis position of the auxiliary upper and lower vanes 71 is not limited to the above two points (the rotation axis position 71c and the rotation axis position 71d). The rotational axis position of the auxiliary upper and lower vanes 71 may be moved between the two points according to the angles of the upper and lower vanes 70 and the auxiliary upper and lower vanes 71.

In this way, when the rotational axis position of the auxiliary upper and lower vanes 71 is variable, for example, the following moving mechanism may be provided.
FIG. 27 is an essential part enlarged view showing an example of a moving mechanism for moving the rotational axis position of the auxiliary upper and lower vanes 71 according to Embodiment 4 of the present invention.
The moving mechanism shown in FIG. 27 includes a linear actuator 72 and a motor 73 such as a stepping motor. A rotating shaft of auxiliary upper and lower vanes 71 is attached to the motor 73. More specifically, the rotating shaft of the auxiliary upper and lower vanes 71 is inserted into a slit 1 a formed in the side surface of the casing 1 and attached to the motor 73. The motor 73 is attached to the movable part of the direct acting actuator 72.
When the movable portion of the linear actuator 72 moves along the longitudinal direction of the slit 1a, the rotational axis position of the auxiliary upper and lower vanes 71 also moves. Further, by rotating the motor 73, the auxiliary upper and lower vanes 71 rotate about the rotation axis.

Further, when the rotational axis position of the auxiliary upper and lower vanes 71 is variable, for example, the following moving mechanism may be provided.
FIG. 28 is an essential part enlarged view showing another example of the moving mechanism for moving the rotational axis position of the auxiliary upper and lower vanes 71 according to Embodiment 4 of the present invention.
28 includes a motor 74 such as a stepping motor, for example, a motor 73 such as a stepping motor, and an arm 75 that connects the motor 73 and the motor 74. A rotating shaft of auxiliary upper and lower vanes 71 is attached to the motor 73. More specifically, the rotating shaft of the auxiliary upper and lower vanes 71 is inserted into a slit 1 a formed in the side surface of the casing 1 and attached to the motor 73. The motor 73 is attached to the motor 74 via the arm 75.
As the motor 74 rotates, the motor 73 moves along the slit 1a. As a result, the rotational axis position of the auxiliary upper and lower vanes 71 also moves along the slit 1a. Further, by rotating the motor 73, the auxiliary upper and lower vanes 71 rotate about the rotation axis.

  As described above, in the indoor unit 100 configured as described above, the rotational axis position of the auxiliary upper and lower vanes 71 can be adjusted in accordance with the direction of the airflow, so that the upper and lower vanes 70 are independent of the angles of the upper and lower vanes 70 and 71. The upstream end portion of the auxiliary upper and lower vanes 71 can be brought close to each other. For this reason, separation of the airflow in the auxiliary upper and lower vanes 71 can be suppressed. Therefore, it is possible to smoothly bend the airflow while suppressing a decrease in power efficiency of the indoor unit 100.

  Note that even if the rotational axis position of the upper and lower vanes 70 is movable, the effects shown in the fourth embodiment can be obtained. Of course, both the rotation axis position of the upper and lower vanes 70 and the rotation axis position of the auxiliary upper and lower vanes 71 may be movable.

Embodiment 5 FIG.
By providing the auxiliary upper and lower vanes 71, the airflow can be controlled from the vicinity of the heat exchanger as compared with the conventional case. For this reason, airflow controllability can be further improved by providing the front side heat exchanger 51 and the back side heat exchanger 55 with independent heat exchange actions. In Embodiment 5, items that are not particularly described are the same as those in Embodiments 2 to 4, and the same functions and configurations are described using the same reference numerals.

  17 and 18 are longitudinal sectional views showing an indoor unit according to Embodiment 5 of the present invention.

As shown in FIG. 17, during the heating operation, cool air (arrow C) is generated in the front side heat exchanger 51, and warm air (arrow H) is generated in the back side heat exchanger 55. By comprising in this way, since the rise of warm air can be suppressed with cold air, airflow controllability improves.
Further, as shown in FIG. 18, during the cooling operation, cool air is generated in the front side heat exchanger 51 and warm air is generated in the back side heat exchanger 55. By configuring in this way, it is possible to suppress cold dripping with warm air, and air flow controllability is improved.

  As described above, in order for the front-side heat exchanger 51 and the back-side heat exchanger 55 to have independent heat exchange functions, the refrigerant circuit of the air conditioner including the indoor unit 100 according to the fifth embodiment is changed to the following. What is necessary is just to comprise.

FIG. 19 is a refrigerant circuit diagram of an air conditioner including an indoor unit according to Embodiment 5 of the present invention.
In this refrigerant circuit, the compressor 401, the four-way valve 402, the outdoor heat exchanger 403, the expansion device 404, the flow path switching device 405, the rear surface side heat exchanger 55, the expansion device 406, and the front surface side heat exchanger 51 are refrigerant piping. Connected and configured. Further, the flow path switching device 405 includes check valves 405a to 405d.

  The compressor 401 sucks the refrigerant flowing through the refrigerant pipe and compresses the refrigerant to bring it into a high temperature / high pressure state. The four-way valve 402 switches the flow path of the refrigerant discharged from the compressor 401 during the heating operation and the cooling operation. The outdoor heat exchanger 403 functions as a condenser or an evaporator, and performs heat exchange between a refrigerant flowing through the refrigerant pipe and a fluid (air, water, refrigerant, etc.), and a heat exchanger 50 (front side heat exchanger). 51 and the back side heat exchanger 55). The expansion device 404 and the expansion device 406 are for decompressing and expanding the refrigerant flowing through the refrigerant pipe. The throttling device 404 and throttling device 406 may be composed of, for example, a capillary tube or a solenoid valve. The heat exchanger 50 (the front side heat exchanger 51 and the back side heat exchanger 55) functions as a condenser or an evaporator, and performs heat exchange between the refrigerant flowing in the refrigerant pipe and the fluid. The flow path switching device 405 regulates the flow direction of the refrigerant flowing through the refrigerant pipe in one direction.

  Here, the operation of such a refrigerant circuit will be briefly described.

[Cooling operation]
During the cooling operation, the refrigerant flow path of the four-way valve 402 is as shown in FIG.
The refrigerant that has been compressed by the compressor 401 and has become high temperature and high pressure flows into the outdoor heat exchanger 403. In the outdoor heat exchanger 403, the refrigerant is a low-temperature and high-pressure gas-liquid two-phase refrigerant. This refrigerant is decompressed in the expansion device 404 and becomes a low-temperature, low-pressure gas-liquid two-phase refrigerant. Since the flow direction of the refrigerant flowing out from the expansion device 404 is defined by the flow path switching device 405, the refrigerant flows into the back side heat exchanger 55. At this time, the indoor air is cooled and becomes cooling air. The refrigerant having exchanged heat with the back side heat exchanger 55 flows into the expansion device 406 and is depressurized, and then flows into the front side heat exchanger 51. At this time, by reducing the pressure reduction amount in the expansion device 404 and increasing the pressure reduction amount in the expansion device 406, the rear side heat exchanger 55 can generate conditioned air having a temperature higher than that of the front side heat exchanger 51. it can. Further, as shown in FIG. 21, the same effect can be obtained by using a four-way valve 407 instead of the flow path switching device 405.

[Heating operation]
During the heating operation, the refrigerant flow path of the four-way valve 402 is as shown in FIG.
The refrigerant that has been compressed by the compressor and has reached a high temperature and a high pressure flows into the back heat exchanger 55 because the flow direction is defined by the flow path switching device 405. At this time, the room air is heated to become heating air. The refrigerant that has exchanged heat with the back-side heat exchanger 55 flows into the expansion device 406. The refrigerant that has flowed into the expansion device 406 is depressurized to a low-temperature and low-pressure gas-liquid two-phase refrigerant and flows into the front-side heat exchanger 51. The refrigerant becomes a low-temperature and low-pressure liquid refrigerant in the front-side heat exchanger 51. The refrigerant that has flowed out of the front-side heat exchanger 51 is decompressed by the expansion device 404 and then flows into the outdoor heat exchanger 403 where it is heated to become a low-temperature / low-pressure gas refrigerant. By reducing the amount of decompression in the expansion device 404 and increasing the amount of decompression in the expansion device 406, the back side heat exchanger 55 can generate conditioned air having a temperature higher than that of the front side heat exchanger 51. Also, as shown in FIG. 22, the same effect can be obtained even if a four-way valve is used instead of the check valve.

Embodiment 6 FIG.
Further, the upper and lower vanes 70 and the auxiliary upper and lower vanes 71 may be divided into a plurality of parts in the longitudinal direction (left and right direction) of the casing 1 so that they can be controlled independently. In the sixth embodiment, items not particularly described are the same as those in the second to fifth embodiments, and the same functions and configurations are described using the same reference numerals.

FIG. 23 is a perspective view showing an indoor unit according to Embodiment 6 of the present invention.
In the indoor unit 100 according to Embodiment 6, the upper and lower vanes 70 are divided into a plurality of upper and lower vanes along the longitudinal direction of the casing 1. In FIG. 23, it is divided into three upper and lower vanes (upper and lower vanes 70a to 70c). The rotation angles of the upper and lower vanes 70a to 70c can be independently controlled. In the indoor unit 100 according to Embodiment 6, the auxiliary upper and lower vanes 71 are divided into a plurality of auxiliary upper and lower vanes along the longitudinal direction of the casing 1. In FIG. 23, it is divided into three auxiliary upper and lower vanes (auxiliary upper and lower vanes 71e to 71g). The auxiliary upper and lower vanes 71e are disposed on the upstream side of the upper and lower vanes 70a. The auxiliary upper and lower vanes 71f are disposed on the upstream side of the upper and lower vanes 70b. The auxiliary upper and lower vanes 71g are disposed on the upstream side of the upper and lower vanes 70c. The auxiliary upper and lower vanes 71e to 71g can independently control the rotation angles.

  In the indoor unit 100 configured as described above, it is possible to have a distribution of upward and downward airflow in the longitudinal direction of the casing. For this reason, when a plurality of persons are present in the air-conditioning target area, an air flow tailored to each person can be generated, so the comfort of air conditioning is improved.

Embodiment 7 FIG.
A drain pan may be provided in the air passage of the casing 1 in the case where a transmutation portion exists in the lower part of the heat exchanger 50 in the right vertical section (for example, a substantially M-type heat exchanger 50). In such a case, for example, the auxiliary upper and lower vanes 71 may be arranged at the following positions. In Embodiment 7, items that are not particularly described are the same as those in Embodiments 2 to 6, and the same functions and configurations are described using the same reference numerals.

FIG. 24 is a longitudinal sectional view showing an indoor unit according to Embodiment 7 of the present invention.
The indoor unit 100 according to the seventh embodiment is provided with a substantially M-type heat exchanger 50 in the right vertical section. An intermediate drain pan 118 for collecting the drain generated from the front side heat exchanger 51 and the back side heat exchanger 55 is provided below the connecting portion between the front side heat exchanger 51 and the back side heat exchanger 55. Yes. The auxiliary upper and lower vanes 71 are disposed below (for example, directly below) the intermediate drain pan 118. Since the lower part of the drain in the air passage is a dead water area of the blowing airflow, the auxiliary upper and lower vanes 71 are disposed in this dead water area.

  The indoor unit 100 configured as described above controls the direction of the airflow that has passed through the heat exchanger 50 as follows.

  For example, when the airflow that has passed through the heat exchanger 50 is to be bent downward during heating operation, the upper and lower vanes 70 and the auxiliary upper and lower vanes 71 are controlled downward so that the state shown in FIG. 25 is obtained. At this time, since the auxiliary upper and lower vanes 71 are disposed in the dead water area, it is possible to suppress the deterioration of the blowing performance due to the collision between the airflow that has passed through the heat exchanger 50 and the auxiliary upper and lower vanes 71.

  For example, when the airflow that has passed through the heat exchanger 50 is to be bent upward as in the cooling operation, the upper and lower vanes 70 and the auxiliary upper and lower vanes 71 are controlled upward so that the state shown in FIG. 26 is obtained. At this time, since the auxiliary upper and lower vanes 71 are disposed in the dead water area, it is possible to suppress the deterioration of the blowing performance due to the collision between the airflow that has passed through the heat exchanger 50 and the auxiliary upper and lower vanes 71.

As described above, in the indoor unit 100 configured as described above, the air flow controllability can be improved while suppressing the deterioration of the blowing performance due to the collision between the air flow that has passed through the heat exchanger 50 and the auxiliary upper and lower vanes 71. .
Further, by arranging the auxiliary upper and lower vanes 71 as in the seventh embodiment, the airflow that has passed through the front-side heat exchanger 51 and the airflow that has passed through the back-side heat exchanger 55 are reliably separated. Can do. For this reason, the air flow controllability when the front side heat exchanger 51 and the back side heat exchanger 55 have independent heat exchange actions is further improved.

Embodiment 8 FIG.
<Heat exchanger>
One of the features of the present invention is that the fan 20 is disposed on the upstream side of the heat exchanger 50. Thereby, generation | occurrence | production of the whirling flow of the air which blows off from the blower outlet 3, and generation | occurrence | production of a wind speed are suppressed compared with the indoor unit of the conventional air conditioner in which the fan is provided in the blower outlet. Therefore, the shape of the heat exchanger 50 is not limited to the shape shown in the first to seventh embodiments, and may be the following shape, for example. In the eighth embodiment, the same functions and configurations as those of the first to seventh embodiments will be described using the same reference numerals.

FIG. 29 is a longitudinal sectional view showing an indoor unit according to Embodiment 8 of the present invention.
In the indoor unit 100 according to Embodiment 8, the heat exchanger 50 that is not divided into the front-side heat exchanger 51 and the back-side heat exchanger 55 is provided on the downstream side of the fan 20.

  According to such a configuration, the air that has passed through the filter 10 flows into the fan 20. In other words, the air flowing into the fan 20 is less disturbed than the air flowing into the conventional indoor unit (passed through the heat exchanger). For this reason, compared with the conventional indoor unit, the air which passes the outer peripheral part of the blade | wing 23 of the fan 20 becomes a thing with little disturbance of a flow. Therefore, the indoor unit 100 according to Embodiment 8 can suppress noise as compared with the conventional indoor unit.

  Moreover, since the fan 20 is provided in the upstream of the heat exchanger 50, the indoor unit 100 is blown out from the blower outlet 3, compared with the indoor unit of the conventional air conditioner in which the fan is provided in the blower outlet. The generation of the swirling air flow and the generation of the wind speed distribution can be suppressed. In addition, since there is no complicated structure such as a fan at the air outlet 3, it is easy to take measures against dew condensation caused by backflow or the like.

Embodiment 9 FIG.
By configuring the heat exchanger 50 with the front side heat exchanger 51 and the back side heat exchanger 55, it becomes possible to further suppress noise than the indoor unit 100 according to the eighth embodiment. At this time, the shape is not limited to the shape of the heat exchanger 50 shown in the first embodiment, and for example, the shape can be as follows. In the ninth embodiment, differences from the above-described eighth embodiment will be mainly described, and the same parts as those in the eighth embodiment are denoted by the same reference numerals.

FIG. 30 is a longitudinal sectional view showing an indoor unit according to Embodiment 9 of the present invention.
As shown in FIG. 30, the front-side heat exchanger 51 and the back-side heat exchanger 55 constituting the heat exchanger 50 are divided by a symmetric line 50 a in the right vertical section. The symmetry line 50a divides the installation range of the heat exchanger 50 in this cross section in the left-right direction at a substantially central portion. That is, the front side heat exchanger 51 is arranged on the front side (left side of the drawing) with respect to the symmetry line 50a, and the rear side heat exchanger 55 is arranged on the back side (right side of the drawing) with respect to the symmetry line 50a. The front-side heat exchanger 51 and the rear-side heat exchanger 55 are arranged so that the distance between the front-side heat exchanger 51 and the rear-side heat exchanger 55 is narrow with respect to the air flow direction, that is, the right-side longitudinal section. It is arrange | positioned in the casing 1 so that the cross-sectional shape of the heat exchanger 50 may become a substantially V type in a surface.

  That is, the front side heat exchanger 51 and the back side heat exchanger 55 are arranged so as to be inclined with respect to the flow direction of the air supplied from the fan 20. Furthermore, the air path area of the back surface side heat exchanger 55 is characterized by being larger than the air path area of the front surface side heat exchanger 51. In the ninth embodiment, the length in the longitudinal direction of the back side heat exchanger 55 is longer than the length in the longitudinal direction of the front side heat exchanger 51 in the right vertical section. Thereby, the air path area of the back surface side heat exchanger 55 is larger than the air path area of the front surface side heat exchanger 51. The other configurations of the front side heat exchanger 51 and the back side heat exchanger 55 (the length in the depth direction in FIG. 30 and the like) are the same. That is, the heat transfer area of the back side heat exchanger 55 is larger than the heat transfer area of the front side heat exchanger 51. Moreover, the rotating shaft 20a of the fan 20 is installed above the symmetry line 50a.

According to such a configuration, since the fan 20 is provided on the upstream side of the heat exchanger 50, the same effect as in the eighth embodiment can be obtained.
Moreover, according to the indoor unit 100 which concerns on this Embodiment 9, the quantity of air according to an air path area passes through each of the front side heat exchanger 51 and the back side heat exchanger 55. FIG. That is, the air volume of the back side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. And when the air which passed each of the front side heat exchanger 51 and the back side heat exchanger 55 merges by this air volume difference, this merged air will bend to the front side (blower outlet 3 side). For this reason, it is no longer necessary to bend the airflow rapidly in the vicinity of the outlet 3, and the pressure loss in the vicinity of the outlet 3 can be reduced. Therefore, the indoor unit 100 according to the ninth embodiment can further suppress noise compared to the indoor unit 100 according to the eighth embodiment. Moreover, since the indoor unit 100 according to the ninth embodiment can reduce the pressure loss in the vicinity of the outlet 3, it can also reduce the power consumption.

  Further, an amount of air corresponding to the heat transfer area passes through each of the front side heat exchanger 51 and the back side heat exchanger 55. For this reason, the heat exchange performance of the heat exchanger 50 is improved.

  In addition, although the heat exchanger 50 shown in FIG. 30 is comprised by the substantially V shape by the front side heat exchanger 51 and the back side heat exchanger 55 which were formed separately, it is not limited to this structure. . For example, the front-side heat exchanger 51 and the back-side heat exchanger 55 may be configured as an integrated heat exchanger (see FIG. 39). Further, for example, each of the front-side heat exchanger 51 and the back-side heat exchanger 55 may be configured by a combination of a plurality of heat exchangers (see FIG. 39). In the case of the integrated heat exchanger, the front side becomes the front side heat exchanger 51 and the rear side becomes the back side heat exchanger 55 with respect to the symmetry line 50a. In other words, the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 50a may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 50a. Moreover, when each of the front side heat exchanger 51 and the back side heat exchanger 55 is configured by a combination of a plurality of heat exchangers, the longitudinal lengths of the plurality of heat exchangers constituting the front side heat exchanger 51 are each. Is the length of the front side heat exchanger 51 in the longitudinal direction. The sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 55 is the longitudinal length of the back side heat exchanger 55.

Further, it is not necessary to incline all the heat exchangers constituting the heat exchanger 50 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 50 may be arranged vertically in the right vertical section. (See FIG. 39).
Further, when the heat exchanger 50 is composed of a plurality of heat exchangers (for example, when the heat exchanger 50 is composed of the front side heat exchanger 51 and the back side heat exchanger 55), the location where the arrangement gradient of the heat exchanger 50 changes ( For example, the heat exchangers do not have to be in complete contact with each other at a substantial connection point between the front-side heat exchanger 51 and the back-side heat exchanger 55, and there may be some gaps.
Moreover, the shape of the heat exchanger 50 in the right-side vertical cross section may be partially or entirely curved (see FIG. 39).

FIG. 39 is a schematic diagram for explaining a configuration example of the heat exchanger 50. FIG. 39 shows the heat exchanger 50 as seen from the right vertical cross section. In addition, although the whole shape of the heat exchanger 50 shown in FIG. 39 is a substantially (LAMBDA) type, the whole shape of a heat exchanger is an example to the last.
As shown to Fig.39 (a), you may comprise the heat exchanger 50 by a some heat exchanger. As shown in FIG. 39 (b), the heat exchanger 50 may be configured as an integrated heat exchanger. As shown to 12 (c), you may comprise the heat exchanger which comprises the heat exchanger 50 by a some heat exchanger further. Moreover, as shown in FIG.39 (c), you may arrange | position a part of heat exchanger which comprises the heat exchanger 50 vertically. As shown in FIG. 39 (d), the shape of the heat exchanger 50 may be a curved shape.

Embodiment 10 FIG.
Moreover, the heat exchanger 50 may be configured as follows. In the tenth embodiment, differences from the above-described ninth embodiment will be mainly described, and the same parts as those in the ninth embodiment are denoted by the same reference numerals.

FIG. 31 is a longitudinal sectional view showing an indoor unit according to Embodiment 10 of the present invention.
The indoor unit 100 according to the tenth embodiment is different from the indoor unit 100 according to the ninth embodiment in the arrangement of the heat exchanger 50.

  The heat exchanger 50 according to the tenth embodiment is composed of three heat exchangers, and each of these heat exchangers has a different inclination with respect to the flow direction of the air supplied from the fan 20. Is arranged. And the heat exchanger 50 is a substantially N type in the right side longitudinal cross-section. Here, the heat exchanger 51a and the heat exchanger 51b arranged on the front side of the symmetry line 50a constitute the front side heat exchanger 51, and the heat exchanger 55a and the heat exchanger 55a arranged on the back side of the symmetry line 50a The heat exchanger 55b constitutes the back side heat exchanger 55. That is, in the tenth embodiment, the heat exchanger 51b and the heat exchanger 55b are configured as an integrated heat exchanger. The symmetry line 50a divides the installation range of the heat exchanger 50 in the right vertical section in the left-right direction at a substantially central portion.

  In the right vertical section, the length in the longitudinal direction of the back surface side heat exchanger 55 is longer than the length in the longitudinal direction of the front surface side heat exchanger 51. That is, the air volume of the back side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. Here, the comparison of the lengths is the sum of the lengths of the heat exchanger groups constituting the front-side heat exchanger 51 and the sum of the lengths of the heat exchanger groups constituting the back-side heat exchanger 55. Should be compared.

  According to such a configuration, the air volume of the rear side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. For this reason, when the air which passed each of the front side heat exchanger 51 and the back side heat exchanger 55 merges by air volume difference similarly to Embodiment 9, this merged air is the front side (air outlet 3 To the side). For this reason, it is no longer necessary to bend the airflow rapidly in the vicinity of the outlet 3, and the pressure loss in the vicinity of the outlet 3 can be reduced. Therefore, the indoor unit 100 according to the tenth embodiment can further suppress noise compared to the indoor unit 100 according to the eighth embodiment. Moreover, since the indoor unit 100 can reduce the pressure loss in the vicinity of the blower outlet 3, it also becomes possible to reduce power consumption.

  Further, by making the shape of the heat exchanger 50 substantially N-shaped in the right vertical section, it is possible to increase the area through which the front-side heat exchanger 51 and the back-side heat exchanger 55 pass. The wind speed can be made smaller than that in the ninth embodiment. For this reason, compared with Embodiment 9, the pressure loss in the front side heat exchanger 51 and the back side heat exchanger 55 can be reduced, and further reduction in power consumption and noise can be achieved.

  In addition, although the heat exchanger 50 shown in FIG. 31 is comprised by the substantially N type | mold by the three heat exchangers formed separately, it is not limited to this structure. For example, the three heat exchangers constituting the heat exchanger 50 may be configured as an integrated heat exchanger (see FIG. 39). Further, for example, each of the three heat exchangers constituting the heat exchanger 50 may be configured by a combination of a plurality of heat exchangers (see FIG. 39). In the case of the integrated heat exchanger, the front side becomes the front side heat exchanger 51 and the rear side becomes the back side heat exchanger 55 with respect to the symmetry line 50a. In other words, the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 50a may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 50a. Moreover, when each of the front side heat exchanger 51 and the back side heat exchanger 55 is configured by a combination of a plurality of heat exchangers, the longitudinal lengths of the plurality of heat exchangers constituting the front side heat exchanger 51 are each. Is the length of the front side heat exchanger 51 in the longitudinal direction. The sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 55 is the longitudinal length of the back side heat exchanger 55.

Further, it is not necessary to incline all the heat exchangers constituting the heat exchanger 50 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 50 may be arranged vertically in the right vertical section. (See FIG. 39).
Further, when the heat exchanger 50 is constituted by a plurality of heat exchangers, it is not necessary that the heat exchangers are completely in contact with each other at a place where the arrangement gradient of the heat exchanger 50 changes, and there is a slight gap. May be.
Moreover, the shape of the heat exchanger 50 in the right-side vertical cross section may be partially or entirely curved (see FIG. 39).

Embodiment 11 FIG.
Moreover, the heat exchanger 50 may be configured as follows. In the eleventh embodiment, differences from the above-described ninth and tenth embodiments will be mainly described, and the same parts as those in the ninth and tenth embodiments are denoted by the same reference numerals. doing. Moreover, the case where the indoor unit is a wall-mounted type attached to the wall surface of the air-conditioning target area is shown as an example.

FIG. 32 is a longitudinal sectional view showing the indoor unit according to Embodiment 11 of the present invention.
The indoor unit 100 of the eleventh embodiment is different from the indoor units shown in the ninth and tenth embodiments in the manner of arrangement of the heat exchanger 50.

  The heat exchanger 50 according to the eleventh embodiment includes four heat exchangers, and each of these heat exchangers is arranged with a different inclination with respect to the flow direction of the air supplied from the fan 20. Has been. The heat exchanger 50 is substantially W-shaped in the right vertical section. Here, the heat exchanger 51a and the heat exchanger 51b arranged on the front side of the symmetry line 50a constitute the front side heat exchanger 51, and the heat exchanger 55a and the heat exchanger 55a arranged on the back side of the symmetry line 50a The heat exchanger 55b constitutes the back side heat exchanger 55. The symmetry line 50a divides the installation range of the heat exchanger 50 in the right vertical section in the left-right direction at a substantially central portion.

  In the right vertical section, the length in the longitudinal direction of the back surface side heat exchanger 55 is longer than the length in the longitudinal direction of the front surface side heat exchanger 51. That is, the air volume of the back side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. Here, the comparison of the lengths is the sum of the lengths of the heat exchanger groups constituting the front-side heat exchanger 51 and the sum of the lengths of the heat exchanger groups constituting the back-side heat exchanger 55. Should be compared.

  According to such a configuration, the air volume of the rear side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. Therefore, as in the ninth and tenth embodiments, when the air that has passed through each of the front-side heat exchanger 51 and the rear-side heat exchanger 55 merges due to the difference in air volume, It will bend to the side (air outlet 3 side). For this reason, it is no longer necessary to bend the airflow rapidly in the vicinity of the outlet 3, and the pressure loss in the vicinity of the outlet 3 can be reduced. Therefore, the indoor unit 100 according to the eleventh embodiment can further suppress noise compared to the indoor unit 100 according to the eighth embodiment. Moreover, since the indoor unit 100 can reduce the pressure loss in the vicinity of the blower outlet 3, it also becomes possible to reduce power consumption.

  Moreover, since the area which passes the front side heat exchanger 51 and the back side heat exchanger 55 can be taken large by making the shape of the heat exchanger 50 into a substantially W type in the right vertical section, it passes through each. The wind speed can be made smaller than those in the ninth and tenth embodiments. For this reason, compared with Embodiment 9 and Embodiment 10, the pressure loss in the front side heat exchanger 51 and the back side heat exchanger 55 can be reduced, and further reduction in power consumption and noise is possible. It becomes.

  In addition, although the heat exchanger 50 shown in FIG. 32 is comprised by the substantially W shape by the four heat exchangers formed separately, it is not limited to this structure. For example, the four heat exchangers constituting the heat exchanger 50 may be configured as an integrated heat exchanger (see FIG. 39). Further, for example, each of the four heat exchangers constituting the heat exchanger 50 may be configured by a combination of a plurality of heat exchangers (see FIG. 39). In the case of the integrated heat exchanger, the front side becomes the front side heat exchanger 51 and the rear side becomes the back side heat exchanger 55 with respect to the symmetry line 50a. In other words, the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 50a may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 50a. Moreover, when each of the front side heat exchanger 51 and the back side heat exchanger 55 is configured by a combination of a plurality of heat exchangers, the longitudinal lengths of the plurality of heat exchangers constituting the front side heat exchanger 51 are each. Is the length of the front side heat exchanger 51 in the longitudinal direction. The sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 55 is the longitudinal length of the back side heat exchanger 55.

Further, it is not necessary to incline all the heat exchangers constituting the heat exchanger 50 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 50 may be arranged vertically in the right vertical section. (See FIG. 39).
Further, when the heat exchanger 50 is constituted by a plurality of heat exchangers, it is not necessary that the heat exchangers are completely in contact with each other at a place where the arrangement gradient of the heat exchanger 50 changes, and there is a slight gap. May be.
Moreover, the shape of the heat exchanger 50 in the right-side vertical cross section may be partially or entirely curved (see FIG. 39).

Embodiment 12 FIG.
Further, as shown in the first embodiment, the heat exchanger 50 may be configured as follows. In the twelfth embodiment, differences from the above-described ninth to eleventh embodiments are mainly described, and the same reference numerals are given to the same portions as those in the ninth to eleventh embodiments. doing. Moreover, the case where the indoor unit is a wall-mounted type attached to the wall surface of the air-conditioning target area is shown as an example.

FIG. 33 is a longitudinal sectional view showing an indoor unit according to Embodiment 12 of the present invention.
In the indoor unit 100 of the twelfth embodiment, the arrangement of the heat exchanger 50 is different from the indoor units shown in the ninth to eleventh embodiments.
More specifically, the indoor unit 100 according to the twelfth embodiment includes two heat exchangers (a front-side heat exchanger 51 and a rear-side heat exchanger 55) as in the ninth embodiment. However, the arrangement of the front side heat exchanger 51 and the back side heat exchanger 55 is different from the indoor unit 100 shown in the ninth embodiment.

That is, the front side heat exchanger 51 and the back side heat exchanger 55 are arranged with different inclinations with respect to the flow direction of the air supplied from the fan 20. In addition, a front side heat exchanger 51 is arranged on the front side of the symmetry line 50a, and a back side heat exchanger 55 is arranged on the back side of the symmetry line 50a. The heat exchanger 50 has a substantially Λ shape in the right vertical section.
The symmetry line 50a divides the installation range of the heat exchanger 50 in the right vertical section in the left-right direction at a substantially central portion.

  In the right vertical section, the length in the longitudinal direction of the back surface side heat exchanger 55 is longer than the length in the longitudinal direction of the front surface side heat exchanger 51. That is, the air volume of the back side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. Here, the comparison of the lengths is the sum of the lengths of the heat exchanger groups constituting the front-side heat exchanger 51 and the sum of the lengths of the heat exchanger groups constituting the back-side heat exchanger 55. Should be compared.

The indoor unit 100 configured as described above has the following air flow inside.
First, indoor air flows into the indoor unit 100 (casing 1) from the suction port 2 formed in the upper part of the casing 1 by the fan 20. At this time, dust contained in the air is removed by the filter 10. When this indoor air passes through the heat exchanger 50 (the front-side heat exchanger 51 and the back-side heat exchanger 55), it is heated or cooled by the refrigerant that is conducted through the heat exchanger 50 to become conditioned air. . At this time, the air passing through the front side heat exchanger 51 flows from the front side to the back side of the indoor unit 100. Further, the air passing through the back side heat exchanger 55 flows from the back side of the indoor unit 100 to the front side.
The conditioned air that has passed through the heat exchanger 50 (the front-side heat exchanger 51 and the back-side heat exchanger 55) passes from the outlet 3 formed in the lower part of the casing 1 to the outside of the indoor unit 100, that is, the air-conditioning target area. Blown out.

  According to such a configuration, the air volume of the rear side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. Therefore, as in the ninth to eleventh embodiments, when the air that has passed through each of the front-side heat exchanger 51 and the rear-side heat exchanger 55 merges due to the difference in air volume, It will bend to the side (air outlet 3 side). For this reason, it is no longer necessary to bend the airflow rapidly in the vicinity of the outlet 3, and the pressure loss in the vicinity of the outlet 3 can be reduced. Therefore, the indoor unit 100 according to the twelfth embodiment can further suppress noise compared to the indoor unit 100 according to the eighth embodiment. Moreover, since the indoor unit 100 can reduce the pressure loss in the vicinity of the blower outlet 3, it also becomes possible to reduce power consumption.

  Moreover, in the indoor unit 100 according to the twelfth embodiment, the flow direction of the air flowing out from the back side heat exchanger 55 is the flow from the back side to the front side. For this reason, the indoor unit 100 which concerns on this Embodiment 12 becomes easier to bend the flow of the air after passing the heat exchanger 50. FIG. That is, the indoor unit 100 according to the twelfth embodiment can more easily control the airflow of the air blown out from the outlet 3 than the indoor unit 100 according to the ninth embodiment. Therefore, in the indoor unit 100 according to the twelfth embodiment, compared with the indoor unit 100 according to the ninth embodiment, it is not necessary to bend the airflow in the vicinity of the air outlet 3 further, thereby further reducing power consumption and noise. Is possible.

  Note that the heat exchanger 50 shown in FIG. 33 is configured in a substantially Λ shape by the front side heat exchanger 51 and the back side heat exchanger 55 formed separately, but is not limited to this configuration. . For example, the front-side heat exchanger 51 and the back-side heat exchanger 55 may be configured as an integrated heat exchanger (see FIG. 39). Further, for example, each of the front-side heat exchanger 51 and the back-side heat exchanger 55 may be configured by a combination of a plurality of heat exchangers (see FIG. 39). In the case of the integrated heat exchanger, the front side becomes the front side heat exchanger 51 and the rear side becomes the back side heat exchanger 55 with respect to the symmetry line 50a. In other words, the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 50a may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 50a. Moreover, when each of the front side heat exchanger 51 and the back side heat exchanger 55 is configured by a combination of a plurality of heat exchangers, the longitudinal lengths of the plurality of heat exchangers constituting the front side heat exchanger 51 are each. Is the length of the front side heat exchanger 51 in the longitudinal direction. The sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 55 is the longitudinal length of the back side heat exchanger 55.

Further, it is not necessary to incline all the heat exchangers constituting the heat exchanger 50 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 50 may be arranged vertically in the right vertical section. (See FIG. 39).
Further, when the heat exchanger 50 is constituted by a plurality of heat exchangers, it is not necessary that the heat exchangers are completely in contact with each other at a place where the arrangement gradient of the heat exchanger 50 changes, and there is a slight gap. May be.
Moreover, the shape of the heat exchanger 50 in the right-side vertical cross section may be partially or entirely curved (see FIG. 39).

Embodiment 13 FIG.
Moreover, the heat exchanger 50 may be configured as follows. In the thirteenth embodiment, differences from the ninth to twelfth embodiments will be mainly described, and the same parts as those in the ninth to twelfth embodiments are denoted by the same reference numerals. ing.

FIG. 34 is a longitudinal sectional view showing an indoor unit according to Embodiment 13 of the present invention.
The indoor unit 100 of the thirteenth embodiment is different from the indoor units shown in the ninth to twelfth embodiments in the manner of arrangement of the heat exchanger 50.
More specifically, the indoor unit 100 of the thirteenth embodiment is composed of three heat exchangers as in the tenth embodiment. However, the arrangement of these three heat exchangers is different from the indoor unit 100 shown in the tenth embodiment.

  That is, each of the three heat exchangers constituting the heat exchanger 50 is arranged with a different inclination with respect to the flow direction of the air supplied from the fan 20. The heat exchanger 50 has a substantially И type in the right vertical section. Here, the heat exchanger 51a and the heat exchanger 51b arranged on the front side of the symmetry line 50a constitute the front side heat exchanger 51, and the heat exchanger 55a and the heat exchanger 55a arranged on the back side of the symmetry line 50a The heat exchanger 55b constitutes the back side heat exchanger 55. That is, in the thirteenth embodiment, the heat exchanger 51b and the heat exchanger 55b are configured as an integrated heat exchanger. The symmetry line 50a divides the installation range of the heat exchanger 50 in the right vertical section in the left-right direction at a substantially central portion.

  In the right vertical section, the length in the longitudinal direction of the back surface side heat exchanger 55 is longer than the length in the longitudinal direction of the front surface side heat exchanger 51. That is, the air volume of the back side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. Here, the comparison of the lengths is the sum of the lengths of the heat exchanger groups constituting the front-side heat exchanger 51 and the sum of the lengths of the heat exchanger groups constituting the back-side heat exchanger 55. Should be compared.

  According to such a configuration, the air volume of the rear side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. For this reason, as in the ninth to twelfth embodiments, when the air that has passed through each of the front-side heat exchanger 51 and the rear-side heat exchanger 55 merges due to the difference in air volume, It will bend to the side (air outlet 3 side). For this reason, it is no longer necessary to bend the airflow rapidly in the vicinity of the outlet 3, and the pressure loss in the vicinity of the outlet 3 can be reduced. Therefore, the indoor unit 100 according to the thirteenth embodiment can further suppress noise compared to the indoor unit 100 according to the eighth embodiment. Moreover, since the indoor unit 100 can reduce the pressure loss in the vicinity of the blower outlet 3, it also becomes possible to reduce power consumption.

  Further, in the indoor unit 100 according to Embodiment 13, the flow direction of the air flowing out from the back side heat exchanger 55 is the flow from the back side to the front side. For this reason, the indoor unit 100 according to the thirteenth embodiment makes it easier to bend the air flow after passing through the heat exchanger 50. That is, the indoor unit 100 according to the thirteenth embodiment can more easily control the airflow of the air blown out from the outlet 3 than the indoor unit 100 according to the tenth embodiment. Therefore, in the indoor unit 100 according to the thirteenth embodiment, compared with the indoor unit 100 according to the tenth embodiment, it is no longer necessary to bend the airflow in the vicinity of the air outlet 3 and further reduce power consumption and noise. Is possible.

  In addition, by making the shape of the heat exchanger 50 approximately И type in the vertical cross section on the right side, the area passing through the front side heat exchanger 51 and the back side heat exchanger 55 can be increased, so that each passes through. The wind speed can be made smaller than that in the twelfth embodiment. For this reason, compared with Embodiment 12, the pressure loss in the front side heat exchanger 51 and the back side heat exchanger 55 can be reduced, and further reduction in power consumption and noise can be achieved.

  In addition, although the heat exchanger 50 shown in FIG. 34 is comprised by the substantially И type | mold by the three heat exchangers formed separately, it is not limited to this structure. For example, the three heat exchangers constituting the heat exchanger 50 may be configured as an integrated heat exchanger (see FIG. 39). Further, for example, each of the three heat exchangers constituting the heat exchanger 50 may be configured by a combination of a plurality of heat exchangers (see FIG. 39). In the case of the integrated heat exchanger, the front side becomes the front side heat exchanger 51 and the rear side becomes the back side heat exchanger 55 with respect to the symmetry line 50a. In other words, the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 50a may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 50a. Moreover, when each of the front side heat exchanger 51 and the back side heat exchanger 55 is configured by a combination of a plurality of heat exchangers, the longitudinal lengths of the plurality of heat exchangers constituting the front side heat exchanger 51 are each. Is the length of the front side heat exchanger 51 in the longitudinal direction. The sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 55 is the longitudinal length of the back side heat exchanger 55.

Further, it is not necessary to incline all the heat exchangers constituting the heat exchanger 50 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 50 may be arranged vertically in the right vertical section. (See FIG. 39).
Further, when the heat exchanger 50 is constituted by a plurality of heat exchangers, it is not necessary that the heat exchangers are completely in contact with each other at a place where the arrangement gradient of the heat exchanger 50 changes, and there is a slight gap. May be.
Moreover, the shape of the heat exchanger 50 in the right-side vertical cross section may be partially or entirely curved (see FIG. 39).

Embodiment 14 FIG.
Moreover, the heat exchanger 50 may be configured as follows. In the fourteenth embodiment, differences from the ninth to thirteenth embodiments will be mainly described, and the same reference numerals are given to the same portions as those in the ninth to thirteenth embodiments. ing.

FIG. 35 is a longitudinal sectional view showing an indoor unit according to Embodiment 14 of the present invention.
The indoor unit 100 of the fourteenth embodiment is different from the indoor units shown in the ninth to thirteenth embodiments in the way of arranging the heat exchanger 50.
More specifically, the indoor unit 100 according to the fourteenth embodiment includes four heat exchangers as in the eleventh embodiment. However, the arrangement of these four heat exchangers is different from the indoor unit 100 shown in the eleventh embodiment.

  That is, each of the four heat exchangers constituting the heat exchanger 50 is arranged with a different inclination with respect to the flow direction of the air supplied from the fan 20. The heat exchanger 50 has a substantially M shape in the right vertical section. Here, the heat exchanger 51a and the heat exchanger 51b arranged on the front side of the symmetry line 50a constitute the front side heat exchanger 51, and the heat exchanger 55a and the heat exchanger 55a arranged on the back side of the symmetry line 50a The heat exchanger 55b constitutes the back side heat exchanger 55. The symmetry line 50a divides the installation range of the heat exchanger 50 in the right vertical section in the left-right direction at a substantially central portion.

  In the right vertical section, the length in the longitudinal direction of the back surface side heat exchanger 55 is longer than the length in the longitudinal direction of the front surface side heat exchanger 51. That is, the air volume of the back side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. Here, the comparison of the lengths is the sum of the lengths of the heat exchanger groups constituting the front-side heat exchanger 51 and the sum of the lengths of the heat exchanger groups constituting the back-side heat exchanger 55. Should be compared.

  According to such a configuration, the air volume of the rear side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. For this reason, as in the ninth to thirteenth embodiments, when the air that has passed through each of the front-side heat exchanger 51 and the rear-side heat exchanger 55 merges due to the difference in air volume, It will bend to the side (air outlet 3 side). For this reason, it is no longer necessary to bend the airflow rapidly in the vicinity of the outlet 3, and the pressure loss in the vicinity of the outlet 3 can be reduced. Therefore, the indoor unit 100 according to Embodiment 14 can further suppress noise compared to the indoor unit 100 according to Embodiment 8. Moreover, since the indoor unit 100 can reduce the pressure loss in the vicinity of the blower outlet 3, it also becomes possible to reduce power consumption.

  Further, in the indoor unit 100 according to Embodiment 14, the flow direction of the air flowing out from the back side heat exchanger 55 is the flow from the back side to the front side. For this reason, the indoor unit 100 which concerns on this Embodiment 14 becomes easier to bend the flow of the air after passing the heat exchanger 50. FIG. That is, the indoor unit 100 according to the fourteenth embodiment can more easily control the airflow of the air blown out from the outlet 3 than the indoor unit 100 according to the eleventh embodiment. Therefore, in the indoor unit 100 according to the fourteenth embodiment, compared with the indoor unit 100 according to the eleventh embodiment, there is no need to bend the airflow in the vicinity of the air outlet 3 further, thereby further reducing power consumption and noise. Is possible.

  Further, by making the shape of the heat exchanger 50 substantially M-shaped in the right vertical section, it is possible to increase the area that passes through the front-side heat exchanger 51 and the back-side heat exchanger 55. It becomes possible to make a wind speed smaller than Embodiment 12 and Embodiment 13. For this reason, compared with Embodiment 12 and Embodiment 13, the pressure loss in the front side heat exchanger 51 and the back side heat exchanger 55 can be reduced, and further reduction in power consumption and noise is possible. It becomes.

  In addition, although the heat exchanger 50 shown in FIG. 35 is comprised by the substantially M type | mold by the four heat exchangers formed separately, it is not limited to this structure. For example, the four heat exchangers constituting the heat exchanger 50 may be configured as an integrated heat exchanger (see FIG. 39). Further, for example, each of the four heat exchangers constituting the heat exchanger 50 may be configured by a combination of a plurality of heat exchangers (see FIG. 39). In the case of the integrated heat exchanger, the front side becomes the front side heat exchanger 51 and the rear side becomes the back side heat exchanger 55 with respect to the symmetry line 50a. In other words, the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 50a may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 50a. Moreover, when each of the front side heat exchanger 51 and the back side heat exchanger 55 is configured by a combination of a plurality of heat exchangers, the longitudinal lengths of the plurality of heat exchangers constituting the front side heat exchanger 51 are each. Is the length of the front side heat exchanger 51 in the longitudinal direction. The sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 55 is the longitudinal length of the back side heat exchanger 55.

Further, it is not necessary to incline all the heat exchangers constituting the heat exchanger 50 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 50 may be arranged vertically in the right vertical section. (See FIG. 39).
Further, when the heat exchanger 50 is constituted by a plurality of heat exchangers, it is not necessary that the heat exchangers are completely in contact with each other at a place where the arrangement gradient of the heat exchanger 50 changes, and there is a slight gap. May be.
Moreover, the shape of the heat exchanger 50 in the right-side vertical cross section may be partially or entirely curved (see FIG. 39).

Embodiment 15 FIG.
Moreover, the heat exchanger 50 may be configured as follows. In the fifteenth embodiment, differences from the ninth to fourteenth embodiments will be mainly described, and the same reference numerals are given to the same portions as the ninth to fourteenth embodiments. ing.

FIG. 36 is a longitudinal sectional view showing an indoor unit according to Embodiment 15 of the present invention.
The indoor unit 100 of the fifteenth embodiment is different from the indoor units shown in the ninth to fourteenth embodiments in the manner in which the heat exchanger 50 is arranged.
More specifically, the indoor unit 100 of the fifteenth embodiment is composed of two heat exchangers (a front-side heat exchanger 51 and a rear-side heat exchanger 55), as in the twelfth embodiment, and has a right vertical section. In FIG. However, in the fifteenth embodiment, by making the pressure loss of the front side heat exchanger 51 and the pressure loss of the back side heat exchanger 55 different, the air volume of the front side heat exchanger 51 and the back side heat exchanger 55 are changed. The air volume is different.

  That is, the front side heat exchanger 51 and the back side heat exchanger 55 are arranged with different inclinations with respect to the flow direction of the air supplied from the fan 20. A front-side heat exchanger 51 is disposed on the front side of the symmetry line 50a, and a back-side heat exchanger 55 is disposed on the back side of the symmetry line 50a. The heat exchanger 50 has a substantially Λ shape in the right vertical section.

In the right vertical section, the length in the longitudinal direction of the back side heat exchanger 55 and the length in the longitudinal direction of the front side heat exchanger 51 are the same. The specifications of the front-side heat exchanger 51 and the back-side heat exchanger 55 are determined so that the pressure loss of the back-side heat exchanger 55 is smaller than the pressure loss of the front-side heat exchanger 51. In the case of using a fin tube type heat exchanger as the front side heat exchanger 51 and the back side heat exchanger 55, for example, the short side length of the back side heat exchanger 55 in the right vertical section (of the back side heat exchanger 55). The width of the fins 56) may be smaller than the length in the short side direction of the front side heat exchanger 51 (the width of the fins 56 of the front side heat exchanger 51) in the right vertical section. For example, the distance between the fins 56 of the back surface side heat exchanger 55 may be larger than the distance between the fins 56 of the front surface side heat exchanger 51. For example, the diameter of the heat transfer tube 57 of the back surface side heat exchanger 55 may be smaller than the diameter of the heat transfer tube 57 of the front surface side heat exchanger 51. For example, the number of the heat transfer tubes 57 of the back surface side heat exchanger 55 may be smaller than the number of the heat transfer tubes 57 of the front surface side heat exchanger 51.
The symmetry line 50a divides the installation range of the heat exchanger 50 in the right vertical section in the left-right direction at a substantially central portion.

According to such a configuration, since the fan 20 is provided on the upstream side of the heat exchanger 50, the same effect as in the eighth embodiment can be obtained.
Further, according to the indoor unit 100 according to the fifteenth embodiment, an amount of air corresponding to the pressure loss passes through each of the front side heat exchanger 51 and the back side heat exchanger 55. That is, the air volume of the back side heat exchanger 55 is larger than the air volume of the front side heat exchanger 51. And when the air which passed each of the front side heat exchanger 51 and the back side heat exchanger 55 merges by this air volume difference, this merged air will bend to the front side (blower outlet 3 side). For this reason, it is no longer necessary to bend the airflow rapidly in the vicinity of the outlet 3, and the pressure loss in the vicinity of the outlet 3 can be reduced. Therefore, the indoor unit 100 according to the fifteenth embodiment suppresses noise further than the indoor unit 100 according to the eighth embodiment without increasing the length of the back side heat exchanger 55 in the right vertical section. Is possible. Moreover, since the indoor unit 100 can reduce the pressure loss in the vicinity of the blower outlet 3, it also becomes possible to reduce power consumption.

  In addition, although the heat exchanger 50 shown in FIG. 36 is comprised by the substantially (LAMBDA) type | mold by the front side heat exchanger 51 and the back side heat exchanger 55 which were formed separately, it is not limited to this structure. . For example, the shape of the heat exchanger 50 in the right vertical section may be configured to be approximately V-shaped, approximately N-shaped, approximately W-shaped, approximately И-shaped, approximately M-shaped, or the like. Further, for example, the front-side heat exchanger 51 and the back-side heat exchanger 55 may be configured as an integrated heat exchanger (see FIG. 39). Further, for example, each of the front-side heat exchanger 51 and the back-side heat exchanger 55 may be configured by a combination of a plurality of heat exchangers (see FIG. 39). In the case of the integrated heat exchanger, the front side becomes the front side heat exchanger 51 and the rear side becomes the back side heat exchanger 55 with respect to the symmetry line 50a. That is, the pressure loss of the heat exchanger arranged on the back side of the symmetry line 50a may be made smaller than the pressure loss of the heat exchanger arranged on the front side of the symmetry line 50a. Moreover, when each of the front side heat exchanger 51 and the back side heat exchanger 55 is configured by a combination of a plurality of heat exchangers, the sum of the pressure losses of the plurality of heat exchangers constituting the front side heat exchanger 51. However, it becomes the pressure loss of the front side heat exchanger 51. The sum of the pressure losses of the plurality of heat exchangers constituting the back side heat exchanger 55 becomes the pressure loss of the back side heat exchanger 55.

Further, it is not necessary to incline all the heat exchangers constituting the heat exchanger 50 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 50 may be arranged vertically in the right vertical section. (See FIG. 39).
Further, when the heat exchanger 50 is composed of a plurality of heat exchangers (for example, when the heat exchanger 50 is composed of the front side heat exchanger 51 and the back side heat exchanger 55), the location where the arrangement gradient of the heat exchanger 50 changes ( For example, the heat exchangers do not have to be in complete contact with each other at a substantial connection point between the front-side heat exchanger 51 and the back-side heat exchanger 55, and there may be some gaps.
Moreover, the shape of the heat exchanger 50 in the right-side vertical cross section may be partially or entirely curved (see FIG. 39).

Embodiment 16 FIG.
Further, in the ninth to fifteenth embodiments described above, the fan 20 may be arranged as follows. In the sixteenth embodiment, the difference from the ninth to fifteenth embodiments will be mainly described, and the same reference numerals are given to the same portions as those in the ninth to fifteenth embodiments. ing.

  FIG. 37 is a longitudinal sectional view showing the indoor unit according to Embodiment 16 of the present invention. Based on Fig.37 (a)-FIG.37 (c), the method of arrangement | positioning of the fan 20 in the indoor unit 100 is demonstrated.

The heat exchanger 50 of the indoor unit 100 according to Embodiment 16 has the same arrangement as the indoor unit 100 of Embodiment 12. However, the indoor unit 100 according to the sixteenth embodiment is different from the indoor unit 100 according to the twelfth embodiment in the manner in which the fan 20 is arranged.
That is, in the indoor unit 100 according to the sixteenth embodiment, the arrangement position of the fan 20 is determined according to the air volume and the heat transfer area of the front side heat exchanger 51 and the back side heat exchanger 55.

For example, in the state shown in FIG. 37A (in the right vertical section, the position of the rotation axis 20a of the fan 20 and the position of the symmetry line 50a substantially coincides), the heat transfer area is larger than that of the front heat exchanger 51. The air volume of the large rear side heat exchanger 55 may be insufficient. Thus, when the air volume of the back side heat exchanger 55 is insufficient, the heat exchanger 50 (the front side heat exchanger 51 and the back side heat exchanger 55) may not be able to exhibit desired heat exchange performance. In such a case, as shown in FIG. 37B, the arrangement position of the fan 20 may be moved in the back direction.
By configuring in this way, it becomes possible to distribute the air volume according to the heat transfer area of the front side heat exchanger 51 and the back side heat exchanger 55, and the heat exchanger 50 (the front side heat exchanger 51 and the back side heat exchanger 51). The heat exchange performance of the vessel 55) is improved.

  In addition, for example, in the state shown in FIG. 37A, the air volume of the back side heat exchanger 55 may be insufficient, such as when the pressure loss of the back side heat exchanger 55 is large. In addition, due to space limitations in the casing 1, only the air volume adjustment by the configuration of the front side heat exchanger 51 and the back side heat exchanger 55 passed through the front side heat exchanger 51 and the back side heat exchanger 55. There are cases where the air that has joined later cannot be adjusted to a desired angle. Thus, when the air volume of the back surface side heat exchanger 55 is insufficient, the air merged after passing through each of the front surface side heat exchanger 51 and the back surface side heat exchanger 55 may not bend more than a desired angle. In such a case, as shown in FIG. 37B, the arrangement position of the fan 20 may be moved in the back direction.

  By configuring in this way, it is possible to finely control the air volume of each of the front-side heat exchanger 51 and the back-side heat exchanger 55, and the airflow passes through each of the front-side heat exchanger 51 and the back-side heat exchanger 55. Later merged air can be bent to a desired angle. For this reason, according to the formation position of the blower outlet 3, the flow direction of the air merged after passing each of the front side heat exchanger 51 and the back side heat exchanger 55 can be adjusted to a suitable direction.

For example, the heat transfer area of the front side heat exchanger 51 may be larger than the heat transfer area of the back side heat exchanger 55. In such a case, as shown in FIG. 37C, the arrangement position of the fan 20 may be moved in the front direction.
By configuring in this way, it becomes possible to distribute the air volume according to the heat transfer area of the front side heat exchanger 51 and the back side heat exchanger 55, and the heat exchanger 50 (the front side heat exchanger 51 and the back side heat exchanger 51). The heat exchange performance of the vessel 55) is improved.

  Further, for example, in the state shown in FIG. 37A, the air volume of the back side heat exchanger 55 may become larger than necessary. In addition, due to space limitations in the casing 1, only the air volume adjustment by the configuration of the front side heat exchanger 51 and the back side heat exchanger 55 passed through the front side heat exchanger 51 and the back side heat exchanger 55. There are cases where the air that has joined later cannot be adjusted to a desired angle. For this reason, the air merged after passing through each of the front side heat exchanger 51 and the back side heat exchanger 55 may bend more than a desired angle. In such a case, the arrangement position of the fan 20 may be moved in the front direction as shown in FIG.

  By configuring in this way, it is possible to finely control the air volume of each of the front-side heat exchanger 51 and the back-side heat exchanger 55, and the airflow passes through each of the front-side heat exchanger 51 and the back-side heat exchanger 55. Later merged air can be bent to a desired angle. For this reason, according to the formation position of the blower outlet 3, the flow direction of the air merged after passing each of the front side heat exchanger 51 and the back side heat exchanger 55 can be adjusted to a suitable direction.

  In addition, although the heat exchanger 50 shown in FIG. 37 is comprised by the substantially (LAMBDA) type | mold by the front side heat exchanger 51 and the back side heat exchanger 55 which were formed separately, it is not limited to this structure. . For example, the shape of the heat exchanger 50 in the right vertical section may be configured to be approximately V-shaped, approximately N-shaped, approximately W-shaped, approximately И-shaped, approximately M-shaped, or the like. Further, for example, the front-side heat exchanger 51 and the back-side heat exchanger 55 may be configured as an integrated heat exchanger (see FIG. 39). Further, for example, each of the front-side heat exchanger 51 and the back-side heat exchanger 55 may be configured by a combination of a plurality of heat exchangers (see FIG. 39). In the case of the integrated heat exchanger, the front side becomes the front side heat exchanger 51 and the rear side becomes the back side heat exchanger 55 with respect to the symmetry line 50a. In other words, the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 50a may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 50a. Moreover, when each of the front side heat exchanger 51 and the back side heat exchanger 55 is configured by a combination of a plurality of heat exchangers, the longitudinal lengths of the plurality of heat exchangers constituting the front side heat exchanger 51 are each. Is the length of the front side heat exchanger 51 in the longitudinal direction. The sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 55 is the longitudinal length of the back side heat exchanger 55.

Further, it is not necessary to incline all the heat exchangers constituting the heat exchanger 50 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 50 may be arranged vertically in the right vertical section. (See FIG. 39).
Further, when the heat exchanger 50 is composed of a plurality of heat exchangers (for example, when the heat exchanger 50 is composed of the front side heat exchanger 51 and the back side heat exchanger 55), the location where the arrangement gradient of the heat exchanger 50 changes ( For example, the heat exchangers do not have to be in complete contact with each other at a substantial connection point between the front-side heat exchanger 51 and the back-side heat exchanger 55, and there may be some gaps.
Moreover, the shape of the heat exchanger 50 in the right-side vertical cross section may be partially or entirely curved (see FIG. 39).

Embodiment 17. FIG.
Further, in the ninth to fifteenth embodiments described above, the fan 20 may be arranged as follows. In the seventeenth embodiment, differences from the above-described ninth to sixteenth embodiments will be mainly described, and the same parts as those in the ninth to sixteenth embodiments are denoted by the same reference numerals. doing.

FIG. 38 is a longitudinal sectional view showing an indoor unit according to Embodiment 17 of the present invention.
The heat exchanger 50 of the indoor unit 100 according to the seventeenth embodiment has the same arrangement as the indoor unit 100 of the twelfth embodiment. However, the indoor unit 100 according to the sixteenth embodiment is different from the indoor unit 100 according to the twelfth embodiment in the manner in which the fan 20 is arranged.
That is, in the indoor unit 100 according to the seventeenth embodiment, the inclination of the fan 20 is determined according to the air volume and the heat transfer area of the front side heat exchanger 51 and the back side heat exchanger 55.

For example, the air volume of the back side heat exchanger 55 having a larger heat transfer area than the front side heat exchanger 51 may be insufficient. In addition, due to space limitations in the casing 1, the fan 20 may not be adjusted by moving the fan 20 in the front-rear direction. Thus, when the air volume of the back side heat exchanger 55 is insufficient, the heat exchanger 50 (the front side heat exchanger 51 and the back side heat exchanger 55) may not be able to exhibit desired heat exchange performance. In such a case, as shown in FIG. 38, the fan 20 may be inclined toward the back side heat exchanger 55 in the right vertical section.
With this configuration, even when the fan 20 cannot be moved in the front-rear direction, it is possible to distribute the air volume according to the heat transfer area of the front-side heat exchanger 51 and the rear-side heat exchanger 55, and the heat exchanger The heat exchange performance of 50 (the front side heat exchanger 51 and the back side heat exchanger 55) is improved.

  Further, for example, when the pressure loss of the back side heat exchanger 55 is large, the air volume of the back side heat exchanger 55 may be insufficient. In addition, due to space limitations in the casing 1, only the air volume adjustment by the configuration of the front side heat exchanger 51 and the back side heat exchanger 55 passed through the front side heat exchanger 51 and the back side heat exchanger 55. There are cases where the air that has joined later cannot be adjusted to a desired angle. Furthermore, due to space limitations in the casing 1, the fan 20 may not be adjusted by moving the fan 20 in the front-rear direction. Thus, when the air volume of the back surface side heat exchanger 55 is insufficient, the air merged after passing through each of the front surface side heat exchanger 51 and the back surface side heat exchanger 55 may not bend more than a desired angle. In such a case, as shown in FIG. 38, the fan 20 may be inclined toward the back side heat exchanger 55 in the right vertical section.

  With this configuration, even when the fan 20 cannot be moved in the front-rear direction, it is possible to finely control the respective air volumes of the front-side heat exchanger 51 and the rear-side heat exchanger 55, and the front-side heat exchanger The air merged after passing through each of 51 and the back side heat exchanger 55 can be bent to a desired angle. For this reason, according to the formation position of the blower outlet 3, the flow direction of the air merged after passing each of the front side heat exchanger 51 and the back side heat exchanger 55 can be adjusted to a suitable direction.

  In addition, although the heat exchanger 50 shown in FIG. 38 is comprised by the substantially (LAMBDA) type | mold by the front side heat exchanger 51 and the back side heat exchanger 55 which were formed separately, it is not limited to this structure. . For example, the shape of the heat exchanger 50 in the right vertical section may be configured to be approximately V-shaped, approximately N-shaped, approximately W-shaped, approximately И-shaped, approximately M-shaped, or the like. Further, for example, the front-side heat exchanger 51 and the back-side heat exchanger 55 may be configured as an integrated heat exchanger (see FIG. 39). Further, for example, each of the front-side heat exchanger 51 and the back-side heat exchanger 55 may be configured by a combination of a plurality of heat exchangers (see FIG. 39). In the case of the integrated heat exchanger, the front side becomes the front side heat exchanger 51 and the rear side becomes the back side heat exchanger 55 with respect to the symmetry line 50a. In other words, the length in the longitudinal direction of the heat exchanger disposed on the back side of the symmetry line 50a may be longer than the length of the heat exchanger disposed on the front side of the symmetry line 50a. Moreover, when each of the front side heat exchanger 51 and the back side heat exchanger 55 is configured by a combination of a plurality of heat exchangers, the longitudinal lengths of the plurality of heat exchangers constituting the front side heat exchanger 51 are each. Is the length of the front side heat exchanger 51 in the longitudinal direction. The sum of the longitudinal lengths of the plurality of heat exchangers constituting the back side heat exchanger 55 is the longitudinal length of the back side heat exchanger 55.

Further, it is not necessary to incline all the heat exchangers constituting the heat exchanger 50 in the right vertical section, and a part of the heat exchangers constituting the heat exchanger 50 may be arranged vertically in the right vertical section. (See FIG. 39).
Further, when the heat exchanger 50 is composed of a plurality of heat exchangers (for example, when the heat exchanger 50 is composed of the front side heat exchanger 51 and the back side heat exchanger 55), the location where the arrangement gradient of the heat exchanger 50 changes ( For example, the heat exchangers do not have to be in complete contact with each other at a substantial connection point between the front-side heat exchanger 51 and the back-side heat exchanger 55, and there may be some gaps.
Moreover, the shape of the heat exchanger 50 in the right-side vertical cross section may be partially or entirely curved (see FIG. 39).

Embodiment 18 FIG.
<Individual fan control>
As described above, the indoor unit 100 according to the present invention includes the plurality of fans 20. By controlling each of these fans 20 individually, the wind direction controllability of the indoor unit 100 can be improved. Further, by using the auxiliary vane shown in the second to seventh embodiments, the wind direction controllability can be further improved. In the eighteenth embodiment, an example of a specific embodiment for individually controlling the air volume of each fan 20 will be described. Here, in the eighteenth embodiment, an indoor unit 100 in which three fans 20 are arranged in parallel along the left-right direction (longitudinal direction) of the casing 1 will be described as an example. For convenience of description, when it is necessary to distinguish between the fans 20, the fans 20 </ b> A, 20 </ b> B, and 20 </ b> C are referred to in order from the left side of the casing 1. In the eighteenth embodiment, the same functions and configurations as those in the first to seventeenth embodiments will be described using the same reference numerals. Needless to say, the invention shown in the eighteenth embodiment is established even when the number of fans arranged in parallel in the indoor unit 100 is other than three.

FIG. 40 is an explanatory diagram showing an example of the wind speed distribution at the air outlet in the indoor unit according to Embodiment 18 of the present invention. FIG. 40 shows a front view of the indoor unit 100.
In indoor unit 100 according to Embodiment 18, three fans 20 are provided in the left-right direction (longitudinal direction) of casing 1. When the air volume of these fans 20 is increased in order from the fan 20 on the left side of FIG. 40, the wind speed distribution at the outlet 3 of the indoor unit 100 becomes as shown by the arrow in FIG. That is, assuming that the air volume of the fans 20A to 20C is fan 20A <fan 20B <fan 20C, the wind speed distribution at the outlet 3 of the indoor unit 100 is as shown by the arrow in FIG. In addition, the direction of the arrow shown in FIG. 40 shows the direction of airflow, and the magnitude | size of the arrow of FIG. 40 has shown the magnitude | size of the wind speed. That is, the arrow in FIG. 40 indicates that the longer the length, the faster the wind speed (in other words, the greater the air volume).

Moreover, FIG. 41 is explanatory drawing which shows another example of the wind speed distribution of the blower outlet in the indoor unit concerning Embodiment 18 of this invention. FIG. 41 shows a front view of the indoor unit 100.
When the air volume of each fan 20 is increased in order from the fan 20 on the right side of FIG. 40, the wind speed distribution at the outlet 3 of the indoor unit 100 is as shown by the arrow in FIG. That is, if the air volume of the fans 20A to 20C is fan 20A> fan 20B> fan 20C, the wind speed distribution at the outlet 3 of the indoor unit 100 is as shown by the arrow in FIG. In addition, the direction of the arrow shown in FIG. 41 shows the direction of airflow, and the magnitude | size of the arrow of FIG. 41 has shown the magnitude | size of the wind speed. That is, the arrow in FIG. 41 indicates that the longer the length, the faster the wind speed (in other words, the greater the air volume).

FIG. 42 is a principal part enlarged view (front sectional view) showing the vicinity of the air outlet of the indoor unit according to Embodiment 18 of the present invention. FIG. 42 shows the left and right vanes 80 in the case where the airflow blown from the outlet 3 is controlled in the right direction of FIG.
As shown in FIG. 42, the airflow bent by the left and right vanes 80 collides with the side wall portion of the casing 1 in the vicinity of the air outlet 3, resulting in ventilation loss. In such a case, as shown in FIG. 41, it is good to generate the air volume of each fan 20 so that the wind speed of the right end part of the blower outlet 3 becomes small (refer FIG. 41). When the total air volume of the air outlet 3 is set to the same air volume as that of a conventional indoor unit (an indoor unit in which only one fan is provided or an indoor unit in which each of the plurality of fans is not controlled), By individually controlling the air volume of each fan 20, it is possible to reduce a ventilation loss caused by an air current colliding with the side wall portion of the casing 1.

  In addition, when inventors investigated the influence which the wind speed distribution of the blower outlet 3 (difference of the air volume for each fan 20) has on the heat exchange performance, if the difference of the air volume of the adjacent fans 20 is about 20% or less. It was found that there is little influence on the heat exchange performance. Further, it was found that if the difference in the air volume between adjacent fans 20 is about 10% or less, the influence on the heat exchange performance is further reduced. For this reason, when the air volume is individually controlled for each fan 20, the difference in the air volume between adjacent fans 20 is preferably about 20% or less. Further, when the air volume is individually controlled for each fan 20, it is more preferable that the difference in air volume between adjacent fans 20 is about 10% or less.

  Moreover, the effect of individually controlling the air volume of each fan 20 is not limited to the above-described ventilation loss reduction effect. For example, when there is a place where air conditioning is to be intensively performed (when spot air conditioning is performed), the air volume of each fan 20 may be individually controlled so that the airflow reaching this place increases. Also, for example, if there is a place where you want to avoid air-conditioning airflow (when performing windbreak mild air-conditioning), make sure that the airflow reaching this place is small (or that airflow does not reach this place) What is necessary is just to control the air volume of the fan 20 separately.

  In the eighteenth embodiment, a plurality of fans 20 having the same shape (same specifications) are provided, and the air volume of each fan 20 is individually controlled by changing the rotation speed of each fan 20. In this case, “the product of the number of blades 23 of the fan 20 and the number of rotations of the impeller 25 of the fan 20” may be separated by about 10 Hz for each fan 20. By doing in this way, the effect which suppresses the beep sound (the beat sound which arises by interference of a blade passing frequency noise (BPF)) which generate | occur | produces from each fan 20 can also be anticipated.

Embodiment 19. FIG.
Further, the air volume of each fan 20 may be individually controlled as follows. In the nineteenth embodiment, items not specifically described are the same as those in the eighteenth embodiment, and the same functions and configurations are described using the same reference numerals.

FIG. 43 is an explanatory diagram showing the wind speed distribution at the outlet when the air volume of each fan 20 is the same in the indoor unit according to Embodiment 19 of the present invention. FIG. 43 shows a front view of the indoor unit 100. 43 indicates the direction of airflow, and the size of the arrow in FIG. 43 indicates the magnitude of the wind speed. That is, the arrow in FIG. 43 indicates that the longer the length, the faster the wind speed (in other words, the greater the air volume).
As shown in FIG. 43, it can be seen that when the airflow generated by each fan 20 is the same, the wind speed decreases in the vicinity of both ends of the air outlet 3. This is because the wind speed is reduced by the airflow friction generated at the side wall of the casing 1 constituting the air passage. For this reason, when the indoor unit 100 is operated in the low air volume (low capacity) mode, backflow may occur in this speed reduction region (near both ends of the outlet 3). This reverse flow may cause an abnormal sound such as a breathing sound. Further, during the cooling operation, this reverse flow causes problems such as the formation of condensation due to the mixing of warm air and cold air.

  Therefore, in the indoor unit 100 according to Embodiment 19, when the indoor unit 100 is operated in the low air volume (low capacity) mode, the air volume of each fan 20 is controlled as shown in FIG.

FIG. 44 is an explanatory diagram showing an example of the wind speed distribution at the outlet when the indoor unit according to Embodiment 19 of the present invention operates in the low air volume mode.
When operating in the low air volume (low capacity) mode, the indoor unit 100 according to the nineteenth embodiment has a fan 20A and a fan 20C arranged at both ends so that the wind speed in the vicinity of both ends of the air outlet 3 is increased. Is larger than the air volume of the fan 20B arranged in the center. The same air volume as the conventional indoor unit (an indoor unit in which only one fan is provided, or an indoor unit in which each of a plurality of fans is not controlled) in the low air volume (low capacity) mode. In this case, by controlling the air volume of each fan 20 in this way, the above-described problems that occur in the low air volume (low capacity) mode can be solved.

  In addition, when inventors investigated the influence which the wind speed distribution of the blower outlet 3 (difference of the air volume for each fan 20) has on the heat exchange performance, if the difference of the air volume of the adjacent fans 20 is about 20% or less. It was found that there is little influence on the heat exchange performance. Further, it was found that if the difference in the air volume between adjacent fans 20 is about 10% or less, the influence on the heat exchange performance is further reduced. For this reason, when the air volume is individually controlled for each fan 20, the difference in the air volume between adjacent fans 20 is preferably about 20% or less. Further, when the air volume is individually controlled for each fan 20, it is more preferable that the difference in air volume between adjacent fans 20 is about 10% or less.

  Similarly to the eighteenth embodiment, for example, when there is a place where air conditioning is to be intensively performed (when spot air conditioning is performed), the air volume of each fan 20 is further individually increased so that the airflow reaching this place is increased. You may control to. Also, for example, if there is a place where you want to avoid air-conditioning airflow (when performing windbreak mild air-conditioning), make sure that the airflow reaching this place is small (or that airflow does not reach this place) The air volume of the fan 20 may be further individually controlled.

  Further, when the indoor unit 100 is provided with the above-described silencing mechanism or the silencing mechanism described later (for example, the use of a sound absorbing material, the housing 26 of the fan 20 that functions as a Helmholtz silencer, and the active silencing mechanism), each fan 20 The silencing effect is further improved by combining the configuration for individually controlling the air volume with these silencing mechanisms. For example, when an active silencing mechanism is provided in the indoor unit 100, it is preferable to provide a silencing mechanism corresponding to the number of sound sources (the number of fans 20). However, there may be a case where a silencer mechanism corresponding to the number of sound sources (the number of fans 20) cannot be provided due to restrictions on dimensions and costs of the indoor unit 100. Even in such a case, a sufficient silencing effect can be obtained by combining the configurations for individually controlling the air volume of each fan 20.

  FIG. 45 is a characteristic diagram showing the relationship between the air volume reduction rate of the central fan and the noise reduction effect at the same air volume in the indoor unit according to Embodiment 19 of the present invention. FIG. 45 shows the amount of noise reduction when the air volume of the fan 20B disposed in the center portion is reduced by making the total air volume of the air outlet 3 the same. Further, -1 dB, -2 dB, -3 dB, -4 dB, and -5 dB shown in FIG. 45 are noise reduction effects with respect to the noise most relevant to the sound detected by the noise reduction detection device. The noise detection microphone 161 and the control speaker of the silencing mechanism used to obtain the result of FIG. 45 are machine boxes (control boards) provided on both the left and right side portions of the casing 1 so as not to affect the air flow in the air path. Etc. are installed in a box (not shown) in which etc. are stored. For this reason, −1 dB, −2 dB, −3 dB, −4 dB, and −5 dB shown in FIG. 45 indicate the silencing effect on the noise emitted by the fan 20A and the fan 20C.

  For example, when the silencing mechanism with a silencing effect of -5 dB is provided in the indoor unit 100, the noises radiated by the fan 20A and the fan 20B disposed in the vicinity of both ends are reduced by 5 dB, respectively. On the other hand, since the noise radiated from the fan 20B disposed in the central portion has no effect of the silencing mechanism, the entire indoor unit 100 can provide a silencing effect of 2.7 dB in total. At this time, assuming that the air volume of the central fan 20B is reduced by about 15% as shown in the nineteenth embodiment, in order to obtain the same air volume, the fan 20A and the fan 20B arranged near both ends are respectively Increase 7.5% airflow. When the air volume of each fan 20 is individually controlled in this way, the noise radiated by the fan 20A and the fan 20B disposed in the vicinity of both ends increases by 1.9 dB, and the noise radiated from the fan 20B disposed in the center is Reduced by 2 dB. As a result, the overall indoor unit 100 can obtain a noise reduction effect of 3.5 dB in total, and the noise reduction effect is improved as compared to before the air volume of each fan 20 is individually controlled.

  In the nineteenth embodiment, a plurality of fans 20 having the same shape (same specifications) are provided, and the air volume of each fan 20 is individually controlled by changing the rotation speed of each fan 20. In this case, “the product of the number of blades 23 of the fan 20 and the number of rotations of the impeller 25 of the fan 20” may be separated by about 10 Hz for each fan 20. By doing in this way, the effect which suppresses the beep sound (the beat sound which arises by interference of a blade passing frequency noise (BPF)) which generate | occur | produces from each fan 20 can also be anticipated.

Embodiment 20. FIG.
Further, the air volume of each fan 20 may be individually controlled as follows. Note that in this twentieth embodiment, items that are not particularly described are the same as those in the eighteenth embodiment or the nineteenth embodiment, and the same functions and configurations are described using the same reference numerals.

FIG. 46 is an explanatory diagram showing an example of the wind speed distribution at the air outlet in the indoor unit according to Embodiment 20 of the present invention. FIG. 46 shows a front view of the indoor unit 100. 46 indicates the direction of airflow, and the size of the arrow in FIG. 46 indicates the size of the wind speed. That is, the arrow in FIG. 46 indicates that the longer the length, the faster the wind speed (in other words, the greater the air volume).
In indoor unit 100 according to Embodiment 20, the air volume of fan 20B arranged at the center is arranged at both ends so that the wind speed at the center of blower outlet 3 is larger than the wind speed near both ends. It is larger than the air volume of the fan 20A and the fan 20C.

  The airflow blown out from the outlet 3 gradually loses velocity energy where it comes into contact with the low speed or stop air in the room, and finally the velocity at the center of the airflow is reduced. For this reason, the airflow blown out from the blowout port 3 is made as in the present embodiment 20, so that the flow velocity at the central portion of the airflow when the same airflow is generated is reduced to the conventional indoor unit (the room provided with only one fan). Or an indoor unit that does not control the air volume of each of the plurality of fans), and airflow reachability can be improved.

  In addition, when inventors investigated the influence which the wind speed distribution of the blower outlet 3 (difference of the air volume for each fan 20) has on the heat exchange performance, if the difference of the air volume of the adjacent fans 20 is about 20% or less. It was found that there is little influence on the heat exchange performance. Further, it was found that if the difference in the air volume between adjacent fans 20 is about 10% or less, the influence on the heat exchange performance is further reduced. For this reason, when the air volume is individually controlled for each fan 20, the difference in the air volume between adjacent fans 20 is preferably about 20% or less. Further, when the air volume is individually controlled for each fan 20, it is more preferable that the difference in air volume between adjacent fans 20 is about 10% or less.

  Similarly to the eighteenth embodiment, for example, when there is a place where air conditioning is to be intensively performed (when spot air conditioning is performed), the air volume of each fan 20 is further individually increased so that the airflow reaching this place is increased. You may control to. Also, for example, if there is a place where you want to avoid air-conditioning airflow (when performing windbreak mild air-conditioning), make sure that the airflow reaching this place is small (or that airflow does not reach this place) The air volume of the fan 20 may be further individually controlled.

  In the twentieth embodiment, a plurality of fans 20 having the same shape (same specifications) are provided, and the air volume of each fan 20 is individually controlled by changing the rotation speed of each fan 20. In this case, “the product of the number of blades 23 of the fan 20 and the number of rotations of the impeller 25 of the fan 20” may be separated by about 10 Hz for each fan 20. By doing in this way, the effect which suppresses the beep sound (the beat sound which arises by interference of a blade passing frequency noise (BPF)) which generate | occur | produces from each fan 20 can also be anticipated.

Embodiment 21. FIG.
In the eighteenth to twentieth embodiments, a plurality of fans 20 having the same shape (same specifications) are provided, and the air volume of each fan 20 is individually controlled by changing the rotation speed of each fan 20. The present invention is not limited to this, and the same effect as in the eighteenth to twentieth embodiments can be obtained by using a fan 20 having a different blowing capacity (for example, a fan 20 having a different fan diameter, boss ratio, blade attachment angle, etc.). . In the eighteenth to twentieth embodiments, the use of a plurality of fans 20 having different blowing capacities improves the mounting density of the fans 20 and allows more detailed control of the wind speed distribution inside the indoor unit 100 (casing 1). The effect which was not acquired can also be acquired further.

  It should be noted that the difference in air volume between adjacent fans 20 is about 20% or less (more preferably 10% or less) to prevent the heat exchange performance from deteriorating, and “the number of blades 23 of the fan 20 and the impeller of the fan 20 It is effective to use the fans 20 having different numbers of blades 23 in order to achieve both of preventing the beat noise by separating the product of the rotational speed of 25 by about 10 Hz in each fan 20.

  DESCRIPTION OF SYMBOLS 1 Casing, 1a Slit, 1b Back surface part, 2 Suction port, 3 Outlet, 5 Bell mouth, 5a Upper part, 5b Center part, 5c Lower part, 6 Nozzle, 10 Filter, 15 Finger guard, 16 Motor stay, 17 Fixing member, 18 Support member, 20 (20A to 20C) Fan, 20a Rotating shaft, 21 Boss, 23 Blade, 25 Impeller, 26 Housing, 30 Fan motor, 50 Heat exchanger, 50a Symmetric line, 51 Front heat exchanger, 51a, 51b heat exchanger, 55 back heat exchanger, 55a, 55b heat exchanger, 56 fins, 57 heat transfer tube, 70 upper and lower vanes, 70a to 70c upper and lower vanes, 71 auxiliary upper and lower vanes, 71a to 71g auxiliary upper and lower vanes, 72 linear actuator, 73 motor, 74 motor, 75 arm, 80 left and right , 90 partition plate, 100 indoor unit, 110 front side drain pan, 111 drainage channel, 111a tongue, 115 back side drain pan, 116 connection port, 117 drain hose, 118 intermediate drain pan, 151 microphone amplifier, 152 A / D conversion 154 D / A converter, 155 amplifier, 158 FIR filter, 159 LMS algorithm, 161 noise detection microphone, 181 control speaker, 191 mute effect detection microphone, 201 signal processing device, 281 control device, 401 compressor, 402 four-way Valve, 403 outdoor heat exchanger, 404 throttling device, 405 flow path switching device, 405a-405d check valve, 406 throttling device, 407 four-way valve.

An indoor unit of an air conditioner according to the present invention includes a casing having a suction port formed in an upper portion thereof and a blower outlet formed in a lower side of a front surface portion, and an axial flow type or a slant provided on the downstream side of the suction port in the casing. A flow type fan, a heat exchanger that is provided downstream of the fan in the casing and upstream of the air outlet, exchanges heat between the air blown from the fan and the refrigerant, and provided in the air outlet. The upper and lower vanes for controlling the vertical direction of the airflow blown from the outlet , and the auxiliary upper and lower vanes provided on the upstream side of the upper and lower vanes for controlling the vertical direction of the airflow that has passed through the heat exchanger. The heat exchanger has a front side heat exchanger arranged on the front side of the casing and a back side heat exchanger arranged on the rear side of the casing, and the upstream end of the auxiliary upper and lower vanes is on the front side. Lower end of heat exchanger and lower end of back side heat exchanger The virtual straight line connecting the bets are those located on the upstream side.

Claims (12)

A casing in which a suction port is formed in the upper part and a blower outlet is formed in the lower part of the front part,
An axial flow type or diagonal flow type fan provided on the downstream side of the suction port in the casing;
A heat exchanger that is provided on the downstream side of the fan in the casing and upstream of the outlet, and exchanges heat between the air blown out of the fan and the refrigerant;
An upper and lower vane that is provided at the outlet and controls the vertical direction of the airflow blown from the outlet;
With
An indoor unit of an air conditioner, wherein auxiliary upper and lower vanes for controlling the vertical direction of the airflow that has passed through the heat exchanger are provided upstream of the upper and lower vanes.   The indoor unit of the air conditioner according to claim 1, wherein a plurality of the auxiliary upper and lower vanes are provided.   The indoor unit of the air conditioner according to claim 1 or 2, wherein at least one of the rotation axis position of the upper and lower vanes and the rotation axis position of the auxiliary upper and lower vanes is variable. The heat exchanger includes a front side heat exchanger disposed on the front side of the casing, and a back side heat exchanger disposed on the back side of the casing,
The indoor unit of an air conditioner according to any one of claims 1 to 3, wherein the front-side heat exchanger and the back-side heat exchanger have independent heat exchange actions. The auxiliary vane is divided into a plurality along the left-right direction of the casing,
Each of these divided | segmented auxiliary vanes is an indoor unit of the air conditioner as described in any one of Claims 1-4 which can control the direction independently. When bending the airflow blown from the blowout port upward,
The indoor unit of the air conditioner according to any one of claims 1 to 5, wherein the upper and lower vanes and the auxiliary upper and lower vanes are controlled in an upward direction as a vane whose direction is arranged on the downstream side. . When bending the airflow blown out from the blowout port downward,
The interior of the air conditioner according to any one of claims 1 to 5, wherein directions of the upper and lower vanes and the auxiliary upper and lower vanes are controlled in a downward direction as the vanes are disposed on the downstream side. Machine.   The indoor unit of the air conditioner according to claim 4, wherein the temperature of the airflow passing through the front side heat exchanger is lower than the temperature of the airflow passing through the back side heat exchanger. In the heat exchanger, the longitudinal section cut from the front side to the back side of the casing, a transformation part is formed in the lower part,
The indoor unit of an air conditioner according to claim 1, wherein the auxiliary upper and lower vanes are disposed below the transformation portion. The heat exchanger is
A front-side heat exchanger disposed on the front side of the casing;
A back side heat exchanger disposed on the back side of the casing;
Have
In side view,
The indoor unit of the air conditioner according to any one of claims 1 to 9, wherein a length in the longitudinal direction of the front side heat exchanger is shorter than a length in the longitudinal direction of the back side heat exchanger. The heat exchanger is
A front-side heat exchanger disposed on the front side of the casing;
A back side heat exchanger disposed on the back side of the casing;
Have
The pressure loss of the said front side heat exchanger is an indoor unit of the air conditioner as described in any one of Claims 1-10 larger than the pressure loss of the said back side heat exchanger.   The air conditioner provided with the indoor unit as described in any one of Claims 1-11.

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