JP2014163606A - Indoor unit of air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an indoor unit of an air conditioner capable of achieving high heat exchanging performance by combining a substantially square heat exchanger and a substantially rectangular air outlet, and reducing ventilation resistance.SOLUTION: A substantially rectangular air outlet arranged in parallel with a linear region of a heat exchanger is disposed on a position closer to a rotational inlet side of a fan in the linear region. Since the air outlet having a length determined to obtain a prescribed wind velocity, is positioned closer to the rotational inlet side of the fan having high wind velocity, the air can be blown out from the air outlet with high efficiency while reducing ventilation resistance. As a result, an indoor unit can contribute to energy saving of an air conditioner.

Description

  The present invention relates to an indoor unit of an air conditioner, and more particularly to an indoor unit of an air conditioner that is used by being embedded in a ceiling so that cold air or hot air blows out from the ceiling of the room.

  In general, as an indoor unit of an air conditioner, a wall-mounted indoor unit installed so as to be hung on an upper portion of an indoor wall surface and an embedded indoor unit installed by being embedded in a ceiling are known. An indoor unit embedded in a ceiling is suitable for air conditioning in a large room, and the present invention is directed to an indoor unit of an air conditioner that is used by being embedded in the ceiling.

  An indoor unit of an air conditioner having such a configuration is described in, for example, Japanese Patent Application Laid-Open No. 2005-241069 (Patent Document 1).

  FIG. 8 shows a configuration of a four-direction blowout type indoor unit installed in a general ceiling as disclosed in Patent Document 1. The indoor unit is provided with, for example, a centrifugal type or turbo type blower fan 1 (hereinafter abbreviated as “fan”) as a blower inside a frame, and a heat exchanger (here, pipe 2). It is a structure provided with. The frame body is composed of a box-shaped casing 3 whose lower surface (surface to be installed on the ceiling) is substantially rectangular, and a decorative panel 20 attached to the lower surface of the casing 3. Four elongate outlets 11 are provided so as to be along. The blower outlet 11 is generally configured such that the blower outlet 11 provided in the decorative panel 20 is overlapped with the blower outlet 11 provided in the casing 3. In addition, a drainage pump 4 that discharges moisture accumulated in a water receiver that receives moisture condensed on the heat exchanger 2 is attached to a corner portion of the casing 3. Further, a gas side pipe connection port 5, a liquid side pipe connection port 6, a gas header 7, a distributor 8, and an expansion valve 9 are installed at the corner of the other casing 3, and these are surrounded by a baffle plate 12. ing. And as shown in FIG. 8, the center point of the length direction of each blower outlet 11 which opposes the rotation center of a fan is located on the same line. That is, as shown in FIG. 8, the A and B dimensions of the air outlet 11 are substantially the same length with a center line Ce extending from the center point of the fan 1 to the air outlet 11 as a boundary.

JP 2005-241069 A

And in this kind of air conditioning apparatus, in order to suppress global warming, it is calculated | required to air-condition a room | chamber interior to predetermined | prescribed preset temperature with as little electric power energy as possible. For this purpose, improvement of components and improvement of the air path structure are performed from various viewpoints. In such an improvement, in order to efficiently blow out the air heat-exchanged by the heat exchanger from the blowout port, the shape of the heat exchanger is bent so that the straight region and the adjacent straight region are connected to each other. It is understood that it is desirable to combine a blower outlet formed in a substantially rectangular shape so as to correspond to the linear region of this substantially square heat exchanger, while forming so as to have a substantially square shape composed of regions. It was.
However, it has been found that if such a combination is simply used and the configuration shown in FIG. 8 is adopted, air cannot be blown out from the air outlet with high efficiency. The reason is that there is a bias in the wind speed distribution in the linear region of the heat exchanger to which the air outlet is connected.

  As shown in FIG. 9, the air flow blown out from the fan 1 flows into the heat exchanger 2 substantially vertically in the bent region and inclines in the linear region. And the wind speed is relatively large in the curved region flowing in substantially vertically. The reason is that, in addition to the structure in which the air flow is blocked in the bending region, the static pressure is restored near the bending region of the heat exchanger by increasing the distance between the fan 1 and the heat exchanger 2. And since the static pressure difference before and behind the heat exchanger 2 becomes large, it is because it becomes easy to flow a lot of air fundamentally. For this reason, the wind speed in the linear region existing between the bent region of the heat exchanger 2 and the next bent region tends to become slower according to the rotational traveling direction of the fan 1.

  Thus, the fact that the wind speed distribution in the linear region of the heat exchanger is biased means that the ventilation resistance is biased. Therefore, if a region where the wind speed is high is used, the ventilation resistance can be reduced. For this purpose, it is conceivable to increase the length of the air outlet to a region where the wind speed is large. However, as a practical problem, a method of increasing the length of the air outlet to obtain a predetermined wind speed should be adopted. There is a restriction that it is not possible.

  In such a background, it is important how to reduce the draft resistance efficiently and blow out the air efficiently without changing the length of the air outlet determined to obtain a predetermined wind speed. It is what comes.

  An object of the present invention is to combine a heat exchanger formed in a substantially square shape with a blowout port formed in a substantially rectangular shape, and reduce the ventilation resistance to efficiently blow out air from the blowout port. Is to provide a machine.

  A feature of the present invention is that a substantially rectangular air outlet is arranged in parallel to the linear area of the heat exchanger, and the air outlet is arranged at a position close to the rotation entry side of the fan between the linear areas. is there.

  According to the present invention, the air outlet having a length determined so as to obtain a predetermined wind speed is arranged close to the rotational approach side of the fan having a large wind speed blown out from the heat exchanger. The air can be efficiently blown out from the blowout port by reducing the size. As a result, it becomes possible to contribute to energy saving of the air conditioner.

It is a block diagram which shows the internal structure of the indoor unit which becomes the 1st Embodiment (Example 1) of this invention. It is sectional drawing which shows the structure of the cross section of the indoor unit shown in FIG. It is a block diagram which shows the structure by the side of the ceiling of the indoor unit shown in FIG. It is a block diagram which shows the structure of the fin of the heat exchanger used for the indoor unit shown in FIG. It is a block diagram which shows the internal structure of the indoor unit which becomes the 2nd Embodiment (Example 2) of this invention. It is a block diagram which shows the internal structure of the indoor unit which becomes the 3rd Embodiment (Example 3) of this invention. It is a block diagram which shows the structure by the side of the ceiling of the indoor unit shown in FIG. It is a block diagram which shows the internal structure of the conventional indoor unit. It is explanatory drawing which shows the velocity distribution of the air which blows off from the heat exchanger of the indoor unit shown in FIG.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. However, the present invention is not limited to the following embodiments, and various modifications and application examples are included in the technical concept of the present invention. Is also included in the range.

  First, a first embodiment of the present invention will be described in detail with reference to FIGS. 1 and 2, the main configuration of the indoor unit of the ceiling-embedded air conditioner is that the heat exchanger 14 including the fan 1, the heat exchanger pipe 2, and the fin 10, the expansion valve 9, and the drainage pump 4 are used. A control board (not shown) for controlling the number of rotations of the fan and the like, and a box-shaped casing 3 which accommodates these boards and has a substantially rectangular bottom surface are formed. These are installed embedded in the ceiling plate 19. A rectangular decorative panel 20 is interposed between the casing 3 of the indoor unit and the ceiling plate 19 so that the design looks good.

  The fan 1 generally uses what is called a centrifugal fan or a turbo fan. When the fan 1 is driven to rotate by a fan motor 13, the fan 1 sucks air from the rotation center side and blows out air from the circumference side in the rotation radius direction. Has been. Inside the casing 3, the fan 1 is arrange | positioned in the center, and the heat exchanger 14 is arrange | positioned along the rectangular casing so that the outer peripheral side of the fan 1 may be covered. Further, a grill 16 having a square suction port formed at the lower center of the casing 3 is fixed, and indoor air is sucked into the rotation center side of the fan from this suction port.

  The lower portion of the casing 3 is provided with a substantially rectangular air outlet 11 formed along the four sides of the suction port on the outer peripheral side of the grill 16 where the suction port is formed. A flow path is formed so that the air blown in the radial direction from the outer periphery of the fan 1 is blown into the room through the heat exchanger 14 and from the blowout port 11. The air outlet 11 includes an air outlet formed in the decorative panel 20. Therefore, hereinafter, the air outlets formed in the decorative panel 20 and the casing 3 are collectively referred to as the air outlet 11.

  A filter 17 for preventing dust and the like from entering the casing 3 is attached to the suction port formed in the grill 16. Further, a flap (blade) 18 that adjusts the air blowing direction in the vertical direction or the horizontal direction is provided in the vicinity of the air outlet 11 of the decorative panel 20.

  The room air sucked from the suction port by the rotation of the fan 1 is heated or cooled by the heat exchanger 14 and is blown out from the air outlet 11 as harmonized air. At this time, the condensed water condensed on the surface of the heat exchanger 14 is discharged out of the indoor unit by the drainage pump 4 through the drainage groove 15 below the heat exchanger 14. Generally, a flexible pipe is used to be discharged outdoors.

  As shown in FIG. 4, the heat exchanger 14 has a structure in which the refrigerant flows inside the heat exchanger pipe 2 and the air flows outside thereof. A fin 10 is attached to the surface of the heat exchanger pipe 2, and heat (hot or cold) on the surface of the heat exchanger pipe 2 is diffused by heat conduction to the fin 10, and air flowing around the surface of the fin 10 It is designed to exchange heat.

  The heat exchanger 14 is generally provided with a plurality of heat exchanger pipes 2. At both ends of the heat exchanger pipe 2, a distributor 8 is attached to one side in parallel with a plurality of pipe paths and generally to allow liquid refrigerant to flow evenly, and the other side distributes or collects gas refrigerant. A gas header 7 is attached.

  Further, the heat exchanger 14 is provided with an outdoor unit on which a compressor is mounted and a gas side pipe connection part 5 and a liquid side pipe connection part 6 for sending and receiving refrigerant. These pipe connection parts 5 and 6 are outside the casing 3 so that the pipes can be connected after the indoor unit is installed on the ceiling.

  Furthermore, in general, a gas pipe through which a refrigerant with a high gas ratio always flows and a liquid pipe through which a refrigerant with a high liquid ratio always flow are uniquely determined. For this reason, an expansion valve 9 is provided between the distributor 8 and the liquid side pipe connection portion 6 inside the casing 3.

  The heat exchanger 14 of the present embodiment has a shape that surrounds the fan 1 in a substantially square shape in accordance with the shape of the rectangular casing 3 in order to increase the heat exchange area as much as possible. Therefore, this heat exchanger 14 is connected to the four-sided linear region St, the three bent regions Co connecting the adjacent linear regions among the four corners, and the outdoor unit formed at the remaining corners. Piping and other components, and a piping connection region in which a distribution block, an expansion valve 9 and the like are arranged. In addition, the heat exchanger piping 2 is also provided with the linear area | region St and the bending area | region Co according to this.

  In the upper right corner area of the casing 3 in FIG. 1, the above-described pipe connection area is located. In this corner area, a gas side pipe connection port 5 and a liquid side pipe connection port 6 are exposed to the outside of the casing 3, and a refrigerant pipe connected to the outdoor unit is connected thereto. The gas side pipe connection port 5 is connected to a gas header 7 of the heat exchanger by piping, and the liquid side pipe connection port 6 is connected to the distributor 8 via an expansion valve 9. The distributor 8 distributes the refrigerant to a plurality of refrigerant pipes, and the distributor 8 and the heat exchanger 14 are connected by a plurality of pipes.

  In addition, a pipe connection region where the gas side pipe connection port 5, the liquid side pipe connection port 6, the gas header 7, the distributor 8, and the expansion valve 9 are installed is surrounded by a baffle plate 12. This is because the gas side pipe connection port 5 and the liquid side pipe connection port 6 are drawn out from the opening of the casing 3 to the outside, and there is a gap, and the air pressurized by the fan 1 through the gap is outside. This is to prevent it from flowing into. Further, since the gas header 7, the distributor 8, and the expansion valve 9 are considered to have ventilation resistance, it is also for isolating from the air flow by the fan 1.

  FIG. 2 shows a cross-sectional structure of the indoor unit of FIG. The indoor unit is installed inside the ceiling plate 19 in the room, and the lower side from the ceiling plate 19 is the indoor side, and the upper side from the ceiling plate 19 is the inside of the ceiling. The arrows in FIG. 2 indicate the flow of air, and the indoor air passes through the grill 16 and the filter 17 and flows to the center of the fan 1 by the bell mouth 22.

  The fan 1 is rotationally driven by a fan motor 13 at the top thereof, and the air sucked from the center of the fan 1 is discharged to the left and right in FIG. A heat exchanger 14 is disposed outside the fan 1, and the air passes through the heat exchanger 14 and is adjusted to a predetermined temperature according to the cooling operation or the heating operation. Moreover, the air which passed the heat exchanger 14 flows along the ventilation flow path formed in the casing 3, and is blown out indoors from the blower outlet 11. FIG. Further, a flap 18 for adjusting the blowing direction is attached to the outlet 11.

  FIG. 3 shows a top view of the decorative panel viewed from the indoor side, and a substantially square decorative panel 20 is attached to the ceiling side. The grille 16, the filter 17 and the flap 18 are provided on the makeup panel 20. Moreover, the square surface of the decorative panel 20 is made large so that the casing 3 cannot be seen when looking up from the indoor side.

  FIG. 4 shows the configuration of the fin 10 attached to the heat exchanger pipe 2 of the heat exchanger 14, and the fin 10 is attached vertically so as to be orthogonal to the heat exchanger pipe 2. In FIG. 4, the air flow generated by the fan 1 is schematically indicated by arrows.

  Next, the operation of the indoor unit according to the present embodiment in the above configuration will be described. As shown in FIG. 4, the sucked air is blown out of the fan 1 by being inclined in the rotation direction 21 of the fan 1 rather than the radial direction of the fan 1 by the rotation of the fan 1.

  For this reason, in the linear region St of the heat exchanger 14, the air flows easily because the flow of the air blown out from the fan 1 and the direction of the fin 10 approximately coincide with each other on the rotation approach side of the fan 1. Of course, when the distance between the fan 1 and the heat exchanger 14 is increased, the static pressure in the vicinity of the bending region Co is recovered, and the difference in static pressure before and after the heat exchanger in this portion is increased, so that a large amount of air flows easily. Has also contributed. On the other hand, on the rotation exit side of the fan 1 in the straight line region St, the flow of air blown out from the fan 1 and the direction of the fins 10 do not match, making it difficult for the air to flow.

  That is, as viewed from the rotation direction 21 of the fan 1, the ease of air flow decreases as the straight region St is advanced from the vicinity where the curved region Co is connected to the straight region St. For this reason, in this straight line region St, when viewed from the rotation direction 21 of the fan 1, from the vicinity connected to the straight region St from the curved region Co to the vicinity connected to the next curved region Co. In the meantime, as shown in FIG. 9, it has a wind speed distribution in which the wind speed decreases.

  Therefore, when a substantially square heat exchanger having a curved region Co and a straight region St is used, the amount of air after passing through the heat exchanger 14 is 21 in the rotational direction 21 of the fan 1 as shown in FIG. In view of this, the behavior gradually decreases as the straight region St is advanced from the vicinity where the curved region Co is connected to the straight region St. That is, the ease of air flow deteriorates as the straight region St is advanced.

  However, in the conventional indoor unit as shown in FIG. 8, the A and B dimensions of the air outlet 11 are substantially the same length with a center line Ce extending from the center of the fan 1 to the air outlet 11 as a boundary. . In addition, it is not possible to adopt a method of increasing the length of the air outlet 11 in order to obtain a predetermined wind speed. For this reason, the arrangement | positioning position of the blower outlet 11 is not necessarily what was arrange | positioned in the area | region where the wind speed of 14 linear area | region St of a heat exchanger is quick.

  Therefore, in this embodiment, when such a wind speed distribution is taken into consideration, the influence of pressure loss is dominant on the side where the wind speed is large, in other words, the side where the air volume is large, so the flow path on the side where the air volume is small The following configuration is adopted from the technical knowledge that the overall pressure loss can be reduced by adopting the configuration in which the pressure loss on the side with the larger air volume is reduced even if the pressure loss is slightly increased.

  Here, as described above, the length of the air outlet 11 is a practical problem, and there is a restriction that a method of increasing the length of the air outlet in order to obtain a predetermined wind speed cannot be adopted. For this reason, it is assumed that the length of the air outlet 11 is not so long.

  In the present embodiment, as shown in FIG. 1, the air outlet 11 is arranged close to the rotation approaching side of the fan 1 when viewed from the rotation direction 21 of the fan 1 in the range of the linear region St. . Specifically, with respect to the center line Ce extending from the rotation center of the fan 1 so as to be orthogonal to the respective outlets, the center point in the length direction of the outlet 11 does not coincide with the center line Ce. The center point of the blower outlet 11 in the length direction is close to the bent region Co side on the rotation approach side of the fan 1. For this reason, A dimension which is the length of the blower outlet 11 on the rotation approach side of the fan 1 is longer than the B dimension which is the length of the blower outlet 11 on the rotation exit side of the fan 1 with the center line Ce as a boundary. It will be. Therefore, the blower outlet 11 is arranged between the straight regions St of the heat exchanger 14 so as to approach the side where the wind speed is fast, in other words, the side where the air volume is large.

  As a result, when viewed from the rotational exit side of the fan 1 where the air volume in the straight region St is small, the distance to the air outlet 11 is long and the passage area of the fin 10 is apparently narrowed, but the pressure loss increases. When viewed from the rotation entry side of the fan 1 with a large air volume, the distance to the blowout port 11 is short, and the passage area of the fin 10 is larger than that on the rotation exit side of the fan 1, so that the pressure loss is reduced.

  And, as described above, the larger air volume side is considered to be dominant as the overall pressure loss, so the arrangement can reduce the overall ventilation resistance as a result. This will lead to an increase in airflow. Further, if the ventilation resistance is reduced, the amount of air increases at the same rotation speed of the fan 1 and the heat exchange performance is improved. Therefore, it can be expected that the compressor load of the outdoor unit is reduced and it contributes to energy saving. Furthermore, if the draft resistance is reduced, the same air volume can be obtained, so that the number of rotations of the fan 1 can be lowered. Therefore, the electric power of the fan motor 13 that rotationally drives the fan 1 can be reduced, which also contributes to energy saving. Can be expected.

  Further, in this embodiment, it is easy to secure the space for the pipe connection region by bringing the air outlet 11 closer to the rotation approach side of the fan 1 of the heat exchanger 14. That is, by moving the air outlet 11 toward the rotation approach side of the fan 1, it becomes easier to secure a space where the pipe connection region is located, and the side surface of the baffle plate 12 facing the fan 1 as shown in FIG. The heat exchanger 14 can be arranged so as to be parallel to the linear region St of the heat exchanger 14 and substantially coincide with the inner surface of the heat exchanger 14, that is, so-called flush. For this reason, the end of the heat exchanger 14 connected to the distributor 8 can be disposed in this portion, and the expansion valve 9, the gas header 7 and the like can be further disposed. That is, it is possible to adopt a configuration in which components such as the distributor 8, the expansion valve 9, and the gas header 7 are arranged close to one side surface. If it does in this way, it will become possible to utilize the heat exchanger 14 effectively. The reason is as follows.

  In the conventional indoor unit shown in FIG. 8, the outlet 11 is substantially symmetric with respect to the center line Ce passing through the rotation center of the fan 1. That is, the A dimension and the B dimension were almost the same. For this reason, when the components such as the distributor 8, the expansion valve 9, and the gas header 7 are arranged close to one side surface, the straight region St on the rotation exit side of the fan of the heat exchanger 14 is greatly reduced. Will be. For this reason, since the heat exchanger part which should be originally disappeared, the subject that the heat exchanger of this part cannot be utilized occurred.

  Therefore, by adopting a configuration in which the air outlet 11 is arranged close to the rotation approach side of the fan 1 as in this embodiment, even if the baffle plate 12 is brought to the same surface as the inside of the heat exchanger 14, A sufficient linear area St of the exchanger 14 can be secured. As a result, in the conventional indoor unit shown in FIG. 8, the straight region St of the heat exchanger 14 that has been shaved can be utilized to the maximum extent. In particular, when viewed from the rotation direction 21 of the fan 1, the portion from the pipe connection region to the next straight region St is a portion where the air volume is large because it is on the rotation approach side of the fan 1 within the range of the straight region St. By adopting a configuration in which components such as the distributor 8, the expansion valve 9, and the gas header 7 are arranged close to one side surface of the casing 3, the blower outlet 11 is provided on the rotation entry side of the fan 1, that is, on the portion where the air volume is large. Can contribute to the improvement of the air volume. In addition, since components such as the distributor 8, the expansion valve 9, and the gas header 7 can be arranged close to one side surface of the casing 3, there is an effect that the configuration can be made compact.

  As shown in FIG. 2, a drainage groove 15 is formed by the casing 3 below the heat exchanger 14, and the water condensed in the heat exchanger 14 at the time of cooling or the like passes through the fins of the heat exchanger 14. Then, it falls into the drainage groove 15. Then, the water accumulated in the drain groove 15 is discharged to the outside of the casing 3 by the drain pump 4. In the conventional indoor unit, the drainage pump 4 is arranged at the corner of the indoor unit as shown in FIG. When the drainage pump is arranged at such a position, there arises a problem that the outlet 11 cannot be brought close to the rotation approach side of the fan with the drainage pump 4 as a reference.

  In contrast, in this embodiment, as shown in FIG. 1, the drainage pump 4 is arranged on the rotation exit side of the fan 1 in the linear region St of the heat exchanger 14. That is, with the drainage pump 4 as a reference, the air outlet 11 is arranged close to the rotational entry side of the fan 1 in the linear region St of the heat exchanger 14, so that the space is vacant, and the drainage pump 4 is placed in this vacant space. Can be arranged. Then, by disposing the drainage pump 4, the space where the drainage pump 4 has been located so far is further vacant. Therefore, the outlet 11 is arranged close to the vacant space with the drainage pump 4 as a reference. Will be able to. Thus, in the conventional indoor unit, it is difficult to move the air outlet 11 because the drainage pump 4 is arranged. However, by adopting the described configuration, the air outlet 11 is connected to the heat exchanger 14. The straight region St can be extended to the rotation approach side of the fan 1.

  Although not shown, the decorative panel 20 is equipped with a motor for driving the flap 18. By disposing this motor on the fan rotation exit side of the air outlet 11, it is possible to further extend the air outlet 11 to the rotation entrance side of the fan 1.

  As described above, according to the present embodiment, the substantially rectangular air outlet that is fluidly connected to the straight region existing between the bent region of the heat exchanger and the next bent region, and arranged in parallel therewith. Are arranged at a position close to the rotation approach side of the fan between the linear regions. According to this, since the air outlet having a length determined so as to obtain a predetermined wind speed is arranged close to the rotational approach side of the fan having a high wind speed, the airflow resistance is reduced and the airflow resistance is efficiently reduced. Air can be blown out from the air outlet. As a result, it becomes possible to contribute to energy saving of the air conditioner.

  Next, a second embodiment of the present invention will be described in detail with reference to FIG. In FIG. 5, the drainage pump 4 is located inside the casing 3 and outside the heat exchanger 14, and when viewed from the drainage pump 4, the linear region St of the heat exchanger 14 on the rotation exit side of the fan 1. It is set as the structure arrange | positioned in the rotation approach side of the fan 1 rather than the surface U of the fan side.

  Of course, the arrangement position of the drainage pump 4 is the rotational exit of the fan 1 with respect to the center line Ce of the linear region st of the heat exchanger 14 on the rotational approach side of the fan 1 when viewed from the drainage pump 4. In this embodiment, the air outlet 11 is disposed at a position that does not overlap the projection portion.

  In the conventional indoor unit shown in FIG. 8, the drainage pump 4 is configured to be disposed at a connection portion that connects adjacent linear regions. Moreover, this connecting portion is a region where the wind speed is high as shown in FIG. However, this connection portion is an obstacle to ventilation because the drainage pump 4 is located.

  On the other hand, in the present embodiment, as described above, the fan 1 is disposed closer to the rotation entry side of the fan 1 than the fan-side extension surface U of the linear region St of the heat exchanger 14 on the rotation exit side of the fan 1 when viewed from the drain pump 4. Therefore, since the drainage pump 4 does not exist in the bent region Co on the rotation and withdrawal side of the fan 1 with respect to the drainage pump 4, the bent region Co of the heat exchanger can be effectively used, and the ventilation resistance is reduced. Reduction and increase in air volume can be expected.

  Further, in FIG. 5, the position of the drainage pump 4 is arranged symmetrically with respect to the pipe connection region surrounded by the baffle plate 12 and the rotational rotation center of the fan. In the conventional configuration shown in FIG. 8, since the drainage pump 4 and the pipe connection region are located at both ends of one linear region St of the heat exchanger 14, it is difficult to ensure the necessary dimensions of the air outlet 11 existing between them. There was a problem. On the other hand, in the present embodiment, the arrangement position of the drainage pump 4 is arranged at a position symmetrical to the rotational rotation center of the fan 1 with respect to the pipe connection region surrounded by the baffle plate 12. Therefore, the drainage pump 4 is disposed in a portion of the linear region St that is different from the linear region St of the heat exchanger 14 where the piping region is located. For this reason, it becomes possible to ensure the required dimension of the blower outlet 11 enough.

  Further, by bending the rotation exit side of the fan 1 in the linear region St of the heat exchanger 14 where the drainage pump 4 is located to the fan 1 side, the linear region St continues linearly on the rotation exit side of the fan 1. By suppressing and making air flow more easily, the uniformity of the wind speed distribution which comes out from the blower outlet 11 can be improved.

  As shown in the first embodiment and the second embodiment, in an indoor unit having a plurality of outlets 11, at least one outlet 11 among the plurality of outlets 11 is within the range of the linear region St of the heat exchanger 14. If the fan 1 is moved toward the rotation approach side, the effect of reducing the ventilation resistance and increasing the air volume can be obtained.

  However, desirably, if the outlets 11 are in four directions as in both embodiments, it is more likely that all the outlets 11 are brought closer to the rotational approach side of the fan 1 within the range of the straight region St of the heat exchanger 14. An effect is obtained. The reason for this is that if there is at least one air outlet 11 similar to the conventional arrangement position, the adjacent portion between the air outlet 11 at the conventional arrangement position and the air outlet 11 at the arrangement position as in this embodiment. In this case, the distance between them is greatly separated.

  Therefore, in this adjacent portion, the flow of the bent region Co of the heat exchanger 14 having a relatively large air volume cannot be used in the region where the air flowing through the conventional air outlet 11 flows in the conventional manner and the wind speed is high. In the case where the arrangement as in the example is performed, the air outlet 11 on the front side is separated from the bent region Co in terms of distance, so the ventilation resistance is increased, which is not preferable.

  On the other hand, if all the air outlets 11 are brought closer to the rotational approach side of the fan 1 having a large wind speed in the range of the linear region St of the heat exchanger 14, the distance from the air outlet 11 on the slow wind speed side is increased. However, since the distance of the blower outlet 11 on the side where the wind speed is large is close, the ventilation resistance can be reduced.

  Next, a third embodiment of the present invention will be described in detail with reference to FIGS. FIGS. 6 and 7 show a case where the air outlet 11 is applied to the one in two directions, and the basic configuration is substantially the same as the embodiment shown in FIG. As shown in the figure, a heat exchanger 14 having a fan 1 at the center of the casing 3 and having a substantially square shape is disposed outside the fan 1. As in the first embodiment, the heat exchanger 14 includes a straight region St and a bending region Co that connects them. Further, a substantially rectangular air outlet 11 is disposed outside thereof in parallel with the straight region of the heat exchanger 14. And the blower outlet 11 is comprised so that the blower outlet 11 may be put near the rotation approach side of the fan 1 seeing from the rotation direction of the fan 1 in the range of the linear area | region St.

  The relationship between the air flow generated by the fan 1 and the direction of the fins 10 of the heat exchanger 14 is the same as that shown in FIG. 4, and as described above, the rotation entry side of the fan 1 in the linear region St of the heat exchanger 14. In this case, the amount of air passing through the heat exchanger 14 is larger than that on the rotation exit side.

  Therefore, by bringing the air outlet 11 closer to the rotation approaching side of the fan 1 when viewed from the rotation direction of the fan 1, the ventilation resistance can be reduced and the air volume can be increased as compared with the conventional air outlet. Further, in the same manner as in the first embodiment, a motor for the flap 18 is installed in a space generated by placing the air outlet 11 close to the rotation approaching side of the fan 1 when viewed from the rotation direction of the fan 1 or pipe connection. It becomes easy to install the region, and the degree of freedom in design can be increased.

  As described above, according to the present invention, the substantially rectangular air outlet that is fluidly connected to the linear region existing between the bent region of the heat exchanger and the next bent region is arranged in parallel therewith. In the straight line area, the fan is arranged at a position close to the rotational approach side of the fan. According to this, since the air outlet having a length determined so as to obtain a predetermined wind speed is arranged close to the rotational approach side of the fan having a high wind speed, the airflow resistance is reduced and the airflow resistance is efficiently reduced. Air can be blown out from the air outlet. As a result, it becomes possible to contribute to energy saving of the air conditioner.

  DESCRIPTION OF SYMBOLS 1 ... Blower fan, 2 ... Heat exchanger piping, 3 ... Casing, 4 ... Drain pump, 5 ... Gas side piping connection port, 6 ... Liquid side piping connection port, 7 ... Gas header, 8 ... Distributor, 9 ... Expansion Valves, 10 ... fins, 11 ... outlets, 12 ... baffle plates, 13 ... fan motors, 14 ... heat exchangers, 15 ... drains, 16 ... grills, 17 ... filters, 18 ... flaps, 19 ... ceiling boards, 20 ... decorative panel, R ... rotation direction of the fan, Ce ... center line extending from the center of the fan to the outlet, St ... linear area of the heat exchanger, Co ... bending area of the heat exchanger.

Claims (6)

A box-shaped casing having a substantially rectangular bottom surface, a decorative panel attached to the bottom surface of the casing, a blower fan provided in the casing, and a linear region surrounding the blower fan in the casing And a substantially rectangular heat exchanger having a curved region connecting the linear regions, and at least one substantially rectangular shape formed in the casing and the decorative panel and blowing out the air heat-exchanged by the heat exchanger into the room An air conditioner indoor unit in which air generated by the blower fan is blown out from the air outlet after heat exchange in the heat exchanger,
The substantially rectangular air outlet is arranged in parallel with the linear region of the heat exchanger, and is arranged at a position close to the rotational entry side of the blower fan between the front linear regions. An air conditioner indoor unit that is characterized. A box-shaped casing having a substantially rectangular bottom surface, a decorative panel attached to the bottom surface of the casing, a blower fan provided in the casing, and a linear region surrounding the blower fan in the casing And a substantially rectangular heat exchanger having a curved region connecting the straight regions, and a substantially rectangular air outlet that is formed in the casing and the decorative panel and blows out the air heat-exchanged by the heat exchanger into the room. In the indoor unit of the air conditioner that is provided, and the air flow generated by the blower fan is blown out from the air outlet after heat exchange in the heat exchanger,
The substantially rectangular air outlet is disposed in parallel with the linear region of the heat exchanger, and with respect to a center line Ce extending from the rotation center of the blower fan in a direction perpendicular to the air outlet, The center point of the blower outlet in the lengthwise direction is located between the straight line regions and on the rotation approaching side of the fan and closer to the bending region Co side, and the blower on the rotation approaching side of the blower fan is bordered on the centerline Ce. The indoor unit of the air conditioner characterized in that the length of the outlet is set longer than the length of the air outlet on the side of rotation of the blower fan 1. In the indoor unit of the air conditioning apparatus according to claim 1 or 2,
The substantially rectangular air outlets are four air outlets corresponding to the linear regions of the heat exchanger, or two air outlets corresponding to the opposing linear regions of the heat exchanger. An air conditioner indoor unit. In the indoor unit of the air conditioning apparatus according to any one of claims 1 to 3,
In one corner region of the casing, at least components such as a gas header, a distributor, an expansion valve, and a pipe connection portion connected to the heat exchanger pipe are arranged close to one side surface of the casing. The component is surrounded by a baffle plate arranged so as to be substantially flush with a surface of the linear region of the heat exchanger located on the one side surface of the blower fan side. An air conditioner indoor unit. In the indoor unit of the air conditioning apparatus according to any one of claims 1 to 4,
An indoor unit of an air conditioner, wherein a drainage pump for draining condensed water generated in the heat exchanger is disposed between the casing and a linear region of the heat exchanger. In the indoor unit of the air conditioning apparatus according to any one of claims 1 to 4,
The drainage pump for draining the condensed water generated in the heat exchanger is between the casing and the linear region of the heat exchanger, and with respect to the drainage pump, the extended surface of the next linear region. An indoor unit of an air conditioner, wherein the indoor unit is arranged on a fan rotation approach side of the blower fan.

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