JP4014617B2 - Air conditioner - Google Patents

Description

  The present invention relates to an air conditioner that harmonizes and sends out air taken in from a room.

Conventional air conditioners are disclosed in Patent Documents 1 and 2. The air conditioner of Patent Literature 1 improves the thickness distribution of the blades of the blower fan to reduce the pressure loss of the blower fan. Thereby, energy saving of the air conditioner is achieved. Moreover, the air conditioner of patent document 2 has a movable panel which block | closes the suction inlet provided in the housing | casing front surface of the indoor unit. When the air conditioner is driven, the movable panel is moved, and the air is taken in by opening the suction port widely. Thereby, the pressure loss at the time of suction is reduced, and energy saving of the air conditioner is achieved.
JP 2003-028089 A JP 2000-1111082 A

  In recent years, preservation of the global environment has been screamed, and further energy saving of so-called white goods is strongly desired. However, according to the conventional air conditioner described above, the conditioned air is vigorously sent from the air outlet into the indoor air. At this time, the wall surface of the passage that has existed until then suddenly disappears, and the kinetic energy is deprived by the surrounding air due to the viscosity of the air, resulting in the same static pressure as the atmospheric pressure. This phenomenon occurs immediately when the airflow is sent out from the outlet, so that the airflow in the vicinity of the outlet is greatly disturbed, resulting in a pressure loss. Therefore, there is a problem that energy saving of the air conditioner cannot be sufficiently achieved.

  An object of this invention is to provide the air conditioner which can aim at energy saving more.

In order to achieve the above object, the present invention provides a suction port for taking indoor air into a housing of an indoor unit, an air outlet provided at a lower portion of the housing, and an air flow for communicating between the air inlet and the air outlet. A path, an indoor heat exchanger in which refrigerant pipes are arranged in a plurality of stages and in a plurality of rows, bent along the inner surface of the housing, and disposed opposite to the suction port in the ventilation path, In an air conditioner comprising a cross flow fan disposed between the indoor heat exchanger and the outlet,
A front panel that forms the front surface of the housing of the indoor unit;
An air filter that is provided between the front panel and the indoor heat exchanger and collects and removes dust contained in the air sucked from the suction port;
An air filter cleaning device provided between the front panel and the indoor heat exchanger for removing dust accumulated in the air filter;
A first wind direction plate provided opposite to the upper wall of the air flow path on the downstream side of the cross flow fan, and capable of vertically changing the air direction of the air outlet;
A second wind direction plate provided below the first wind direction plate and configured to vary the wind direction of the air outlet up and down;
The air flow path has a front guide portion that expands the flow path area as it goes downstream by guiding air forward and downward,
The sum of the length of the upper wall and the length of the lower wall of the air flow path on the downstream side of the cross flow fan is at least 3.5 times the diameter of the cross flow fan, and the length of the upper wall is Make it more than 1.5 times the diameter of the cross flow fan ,
The upper wall has an inclined surface that is bent at the bent portion from the end of the upper surface of the front guide portion that is inclined forward and downward, and is inclined upward and forward.
When the air is sent forward and upward from the air outlet, the front end of the first wind direction plate is rearward of the front end of the upper wall and forward of the front end of the second wind direction plate. The second wind direction plate is disposed in front of the bent portion, the rear end of the second wind direction plate is opposed to the bent portion, and rearward of the bent portion.
The air flow path flowing between the upper wall and the first wind direction plate and the air flow path flowing between the first wind direction plate and the second wind direction plate are gradually enlarged toward the downstream. The first and second wind direction plates are arranged .

  According to this structure, indoor air is taken in into a housing | casing from a suction inlet by the drive of a crossflow fan, and distribute | circulates a ventilation path | route. The air is harmonized by exchanging heat with an indoor heat exchanger having a large pressure loss arranged in a plurality of rows in the vertical direction and in a plurality of rows in the depth direction by meandering the refrigerant pipe. The conditioned air circulates from the exhaust side of the cross flow fan along the upper and lower walls of the air flow path through the front guide portion while expanding the flow passage area, and is sent out from the blowout port. At this time, the air flow along the upper wall and the lower wall of the air blowing path is gradually decelerated, and the kinetic energy is converted into static pressure and recovered as static pressure.

Further , the airflow flowing along the upper wall of the air flow path is bent by the second wind direction plate and flows forward and upward along the inclined surface. The kinetic energy of the lower airflow bent by the second wind direction plate is recovered by being converted into static pressure by a flow path formed between the second wind direction plate and the first wind direction plate. The kinetic energy of the upper airflow bent by the second wind direction plate is recovered by being converted into static pressure by a flow path formed between the first wind direction plate and the inclined surface.

  According to the present invention, in the air conditioner configured as described above, an angle formed by the inclined surface and the first wind direction plate and an angle formed by the first and second wind direction plates are set to 10 ° to 15 °. According to this configuration, the airflow smoothly flows along the wall surface without being separated from the wall surface formed by the first and second airflow direction plates and the inclined surface of the air blowing path.

According to the present invention, in the air conditioner configured as described above, a third wind direction plate is provided below the second wind direction plate, and the rear end of the third wind direction plate is disposed in front of the rear end of the second wind direction plate . 2. The angle formed by the third wind direction plate is 10 ° to 15 °. According to this configuration, the airflow smoothly flows along the wall surface without being separated from the wall surface formed of the second and third wind direction plates.

In the air conditioner having the above-described configuration, the rear end of the wind direction plate disposed at the lowermost position and the lower surface of the front guide portion are close to the end of the lower wall of the front guide portion in a direction perpendicular to the airflow. Further, the angle between the wind direction plate disposed at the lowest position and the tangent at the end of the lower wall of the front guide portion is set to 10 ° to 15 °. According to this configuration, the airflow smoothly flows along the wall surface without being separated from the wall surface formed by the lowermost wind direction plate.

According to the present invention, the sum of the length of the upper wall and the length of the lower wall of the air flow path on the downstream side of the cross flow fan is set to 3.5 times or more the diameter of the cross flow fan. Air smoothly circulates a long distance along the upper and lower walls of the blowing path. Thereby, there is little disturbance of the airflow in the vicinity of a blower outlet, and the pressure loss accompanying it becomes small. In addition, the kinetic energy is converted into static pressure by decelerating until the air along the long upper and lower walls is sufficiently slow. Therefore, the kinetic energy of the airflow can be sufficiently recovered to reduce the static pressure increase due to the cross flow fan, and energy saving of the air conditioner can be achieved.
In addition, since the length of the upper wall of the air flow path on the downstream side of the cross flow fan is 1.5 times or more the diameter of the cross flow fan, the kinetic energy is recovered to increase the reach of the air flow with a reduced flow velocity. can do. Thereby, the air sent out from the blower outlet reaches the ceiling of the room, and sequentially travels through the wall surface facing the air conditioner, the floor surface, and the wall surface on the air conditioner side. Therefore, the airflow of conditioned air reaches every corner of the room, and the airflow greatly stirs the entire room. Therefore, it is possible to obtain a comfortable space with almost no direct wind by uniformizing the temperature distribution of the entire living area excluding a part of the indoor upper part.

  In addition, since the indoor heat exchanger is composed of a plurality of rows and a plurality of stages, even when an indoor heat exchanger having a large pressure loss is used, the kinetic energy of the airflow can be sufficiently recovered to save energy in the air conditioner. In addition, since the front guide portion is provided in which the flow path area is increased as the air is guided forward and downward, the kinetic energy can be sufficiently recovered by gradually decelerating the airflow.

  Further, according to the present invention, when the air conditioner is operated, since the front end of the upper wall, the front end of the first wind direction plate, and the front end of the lower wall are arranged in this order from the front upper side, the lower density kinetic energy with the lower flow velocity is recovered in order. Thus, the kinetic energy of the airflow can be recovered efficiently.

  Further, according to the present invention, the second wind direction plate is provided below the first wind direction plate, and the front end of the first wind direction plate is disposed in front of the front end of the second wind direction plate. It is possible to recover the kinetic energy of the airflow efficiently by recovering in order from the energy.

  According to the invention, the rear end of the first wind direction plate is disposed in front of the bent portion between the upper surface of the front guide portion and the inclined surface, and the second wind direction plate below the first wind direction plate. Since the end is disposed behind the bent portion, the airflow can be bent along the inclined surface by the second wind direction plate. Further, the kinetic energy of the airflow can be efficiently recovered by sequentially recovering from the low-density kinetic energy having a low flow velocity below.

  According to the present invention, the angle formed between the inclined surface and the first wind direction plate and the angle formed between the first and second wind direction plates are set to 10 ° to 15 °. And the flow path between the 1st, 2nd wind direction board is expanded continuously, and airflow distribute | circulates along a wall surface smoothly, without peeling from a wall surface. Thereby, the kinetic energy of the airflow can be smoothly converted into static pressure, and the kinetic energy can be efficiently recovered.

  According to the present invention, the angle formed by the second wind direction plate and the third wind direction plate below the second wind direction plate is set to 10 ° to 15 °, so that the flow path between the second and third wind direction plates is continuous. Thus, the flow path is enlarged, and the airflow smoothly flows along the wall surface without being separated from the wall surface. Thereby, the kinetic energy of the airflow can be smoothly converted into static pressure, and the kinetic energy can be efficiently recovered.

  Further, according to the present invention, the angle formed by the lowermost wind direction plate and the tangent at the end of the lower wall is set to 10 ° to 15 °, so that there is a gap between the lowermost wind direction plate and the lower wall of the air flow path. The flow path is continuously expanded, and the airflow smoothly flows along the wall surface without being separated from the wall surface. Thereby, the kinetic energy of the airflow can be smoothly converted into static pressure, and the kinetic energy can be efficiently recovered.

<First Embodiment>
Embodiments of the present invention will be described below with reference to the drawings. Drawing 1 is a side sectional view showing the indoor unit of the air harmony machine of a 1st embodiment. The indoor unit 1 of the air conditioner has a main body held by a cabinet 2, and a front panel 3 is detachably attached to the cabinet 2. A cabinet of the indoor unit 1 is configured by the cabinet 2 and the front panel 3.

  The cabinet 2 is provided with a claw portion (not shown) on the rear side surface, and is supported by engaging the claw portion with a mounting plate (not shown) attached to the side wall W1 of the room. An air outlet 5 is provided in the gap between the lower end portion of the front panel 3 and the lower end portion of the cabinet 2. The air outlet 5 is formed in a substantially rectangular shape extending in the width direction of the indoor unit 1 and is provided facing the front lower side. A lattice-shaped suction port 4 is provided on the upper surface of the front panel 3.

  Inside the housing of the indoor unit 1, an air blowing path 6 that connects the suction port 4 and the air outlet 5 is formed. A cross flow fan 7 for sending air is arranged in the air blowing path 6. The ventilation path 6 is surrounded by the upper wall 6b and the lower wall 6c on the downstream side of the cross flow fan 7. Further, the air blowing path 6 has a front guide portion 6a for guiding the air sent out by the cross flow fan 7 forward and downward. The front guide portion 6a is formed such that the flow path area is enlarged toward the downstream.

  FIG. 2 is a side sectional view showing details of the air flow path 6 on the downstream side of the cross flow fan 7. The upper wall 6 b of the air blowing path 6 has a stabilizer portion 6 b 7 along the peripheral surface of the cross flow fan 7. The stabilizer portion 6b7 is formed to extend in the exhaust direction of the cross flow fan 7, and is continuous with the upper surface 6b3 of the front guide portion 6a at the lower end.

  The upper surface 6b3 of the front guide portion 6a is inclined forward and downward. An inclined surface 6b5 that is bent upward from the end of the upper surface 6b3 of the front guide portion 6a via the bent portion 6b4 and inclined forward and upward is formed. The bent portion 6b4 is a gentle and smooth curved surface.

  The lower wall 6 c of the air blowing path 6 has a rear guider portion 6 c 5 along the peripheral surface of the cross flow fan 7. The rear guider portion 6c5 is formed extending in the exhaust direction of the cross flow fan 7, and the lower wall 6c is formed in a spiral curved surface including the lower surface 6c3 of the front guide portion 6a from the lower end of the rear guider portion 6c5.

  An angle α formed by the upper surface 6b3 and the lower surface 6c3 of the front guide portion 6a is formed to be about 20 °. The angle β formed by the inclined surface 6b5 and the horizontal plane is formed at about 20 °. An angle γ formed by the upper surface 6b3 of the front guide portion 6a and the horizontal plane is 5 °. Accordingly, the angle (β + γ) formed by the upper surface 6b3 of the front guide portion 6a and the inclined surface 6b5 is formed at 25 °. The angles α, β, and γ are preferably formed to be about 15 ° to 20 °, 30 ° or less, and about 0 ° to 10 °, respectively.

  When the angle (β + γ) is 17 ° or less, the air along the wall surface of the flow path can be smoothly circulated with a small pressure loss without being separated from the wall surface. However, as will be described later, the angle (β + γ) is larger than 17 ° in order to divide the flow path into a plurality of parts by the horizontal louvers 111, 112, 113. For this reason, the middle horizontal louver 112 is disposed opposite to the bent portion 6b4 to suppress separation of the airflow.

  As shown in FIG. 3, at least one flat surface 6f may be provided in the bent portion 6b4, and the end portions of the flat surface 6f may be connected by a smooth curved surface 6e. In this case, an angle θ5 formed by the upper surface 6b3 of the front guide portion 6a and the flat surface 6f and an angle θ6 formed by the flat surface 6f and the inclined surface 6b5 are formed to be 17 ° or less. When there are a plurality of planes 6f, the angles formed by the planes are all formed at 17 ° or less. Thereby, the air along the wall surface of the flow path can be smoothly circulated with a small pressure loss without being separated from the wall surface. Therefore, energy saving can be improved.

  The lengths of the upper wall 6b and the lower wall 6c of the air flow path 6 on the downstream side of the cross flow fan 7 are respectively 1.9D and 2.1D, where D is the diameter of the cross flow fan 7. The ends 6b1 and 6c1 of the stabilizer portion 6b7 and the rear guider portion 6c5 are provided in the vicinity of the diameter direction perpendicular to the exhaust direction of the cross flow fan 7, and are the starting points of the upper wall 6b and the lower wall 6c. When the stabilizer portion 6b7 and the rear guider portion 6c5 are formed to extend to the intake side of the cross flow fan 7, the front gap 6b2 and the rear gap 6c2 portions where the distance from the cross flow fan 7 is minimized are the upper wall 6b and the lower wall. It is good also as a starting point of 6c.

  The front end of the inclined surface 6b5 is in contact with the lower end of the front panel 3 to form the end 6b6 of the upper wall 6b. The lower front end of the cabinet 2 is formed with a small radius of curvature where the end 6c4 of the lower surface 6c3 of the front guide portion 6a becomes an inflection point. The end 6c4 is the end point of the lower wall 6c (hereinafter, 6c4 may be referred to as the end of the lower wall 6c). Reference numeral 98 denotes a tangent at the end 6b4 of the lower surface 6c3 of the front guide portion 6a.

  In FIG. 1, the front guide 6a is provided with a vertical louver 12 capable of changing the blowing angle in the left-right direction. The blower outlet 5 is provided with a plurality of lateral louvers 111, 112, 113 that can change the vertical blow angle in the front upper direction, the horizontal direction, the front lower direction, and the direct lower direction. An air filter 8 that collects and removes dust contained in the air sucked from the suction port 4 is provided at a position facing the front panel 3. In a space formed between the front panel 3 and the air filter 8, an air filter cleaning device (not shown) is provided. The dust accumulated in the air filter 8 is removed by the air filter cleaning device.

  An indoor heat exchanger 9 is disposed between the cross flow fan 7 and the air filter 8 in the air blowing path 6. The indoor heat exchanger 9 has meandering refrigerant pipes (not shown) arranged in a plurality of stages in the vertical direction and in a plurality of lines in the front and rear directions, and is bent in multiple stages along the front panel 3. The indoor heat exchanger 9 is connected to a compressor (not shown) arranged outdoors, and the refrigeration cycle is operated by driving the compressor. The indoor heat exchanger 9 is cooled to a temperature lower than the ambient temperature during the cooling operation by the operation of the refrigeration cycle. Further, during the heating operation, the indoor heat exchanger 9 is heated to a temperature higher than the ambient temperature.

  Between the indoor heat exchanger 9 and the air filter 8, an electric dust collector (not shown) and a temperature sensor 61 for detecting the temperature of the sucked air are provided. A controller (not shown) that controls the driving of the air conditioner is provided on the side of the indoor unit 1. Drain pans 10 and 13 that collect condensation that has fallen from the indoor heat exchanger 9 during cooling or dehumidification are provided in the lower part of the front and rear of the indoor heat exchanger 9.

  In the air conditioner having the above-described configuration, when the air conditioner is stopped, the lateral louvers 111 and 112 are disposed at positions that shield the upper and lower portions of the blower path 6 as shown in FIG. The lateral louver 113 is arranged inside the air blowing path 6. Thereby, the blower outlet 5 is obstruct | occluded. At this time, the horizontal louvers 111 and 112 are arranged along the front surface of the front panel 3. Further, the horizontal louver 112 is disposed so as to connect the lower end of the horizontal louver 111 and the bottom surface of the cabinet 2. Thereby, the beauty of the indoor unit 1 is not impaired.

  Condensation prevention means is applied to the side of the upper wall 6b that does not face the air flow path 6. As the dew condensation preventing means, the upper wall 6b may be formed of a heat insulating material, or a heat insulating material may be provided on the upper surface of the upper wall. Further, other dew condensation prevention means other than the heat insulating material may be used. Even if dew condensation occurs on the side of the upper wall 6 b that does not face the air flow path 6, the dew condensation water is guided to the drain pan 10. For this reason, a highly reliable air conditioner can be obtained without any problem due to condensed water.

  When the air conditioner is started and a cooling operation is performed, for example, the horizontal louvers 111, 112, and 113 are arranged with the air outlet 5 opened as shown in FIG. The vertical louver 12 is directed in a predetermined direction. The cross flow fan 7 is driven, the refrigerant from the outdoor unit (not shown) flows to the indoor heat exchanger 9, and the refrigeration cycle is operated. Thus, air is sucked into the indoor unit 1 from the suction port 4, and dust contained in the air is removed by the air filter 8. The air taken into the indoor unit 1 is cooled by exchanging heat with the indoor heat exchanger 9.

  The conditioned air cooled by the indoor heat exchanger 9 is regulated in the left-right direction and the up-down direction by the vertical louver 12 and the horizontal louvers 111, 112, 113, and forwardly upward as indicated by an arrow E along the inclined surface 6b5. Sent to the room. Thereby, the indoor unit 1 will be in the state of the front upper blowing which sends out conditioned air to the front upper direction.

  The conditioned air sent into the room from the blowout port 5 toward the front upper direction along the inclined surface 6b5 reaches the ceiling surface S (see FIG. 2) of the room. Thereafter, the air is sucked into the indoor unit 1 along the side wall, the floor surface facing the indoor unit 1 and the side wall W1 on the indoor unit 1 side from the ceiling surface S by the Coanda effect.

  By doing so, the user is not always exposed to the cold wind or the warm wind, and the user's discomfort can be prevented and the comfort can be improved. Furthermore, health safety can be improved without locally lowering the user's body temperature during cooling. Further, since the air flow greatly agitates the entire room, the temperature distribution in the room becomes uniform near the set temperature. That is, a comfortable space can be obtained in which the entire living area of the user substantially matches the set temperature except for a part above the room, the temperature variation is small, and the direct wind hardly hits the user.

  FIG. 5 is a side sectional view showing details of the vicinity of the air outlet 5 at this time. The uppermost horizontal louver 111 faces the inclined surface 6b5, and the rear end thereof is disposed in front of the bent portion 6b4. The middle horizontal louver 112 faces the bent portion 6b4, and the rear end thereof is disposed behind the bent portion 6b4. From the upper front, the end 6b6 of the upper wall 6b, the front end of the uppermost horizontal louver 111, the front end of the middle horizontal louver 112, the front end of the lowermost horizontal louver 113, and the end 6c4 of the lower wall 6c are arranged in this order. .

  Further, the horizontal louver 111 is arranged so that the angle θ1 formed by the inclined surface 6b5 and the uppermost horizontal louver 111 is 13 °. The horizontal louver 112 is arranged so that the angle θ2 formed by the uppermost horizontal louver 111 and the middle horizontal louver 112 is 10 °. The horizontal louver 113 is arranged so that an angle θ3 formed by the middle horizontal louver 112 and the lowermost horizontal louver 113 is 10 °. Further, the angle θ4 formed by the lowermost horizontal louver 113 and the tangent line 98 is 12 °.

  Since the horizontal louvers 111, 112, and 113 are arranged so that the angles θ1 to θ4 are 17 ° or less, the airflow in the flow path divided by the horizontal louvers 111, 112, and 113 is separated from the flow path wall surface. Minimized. Therefore, the airflow can smoothly flow and energy saving can be improved.

FIG. 6 shows the relationship between the airflow of the crossflow fan 7 and the input (power consumption) required by a fan drive motor (not shown) that drives the crossflow fan 7 when the airflow is sent out. The vertical axis represents the fan drive motor input (unit: W), and the horizontal axis represents the airflow (unit: m ³ / min) of the cross flow fan 7.

  In the figure, K1 indicates the present embodiment, and the horizontal louvers 111, 112, and 113 are disposed as shown in FIG. K2 shows the fourth embodiment of FIG. 18 whose details will be described later, and the lateral louver 113 is omitted from this embodiment. K3 shows the fifth embodiment shown in FIG. 19 whose details will be described later, and the arrangement and shape of the horizontal louvers 111, 112 are changed by omitting the horizontal louver 113 from this embodiment.

  K4 represents a comparative example of FIG. In the comparative example, the horizontal louver 113 is omitted, and the lengths of the upper wall 6b and the lower wall 6c are set to 1D and 2.1D, respectively. This is the length of the upper wall 6b and the lower wall 6c normally formed in the conventional air conditioner. The lateral louvers 111 and 112 are arranged so as to divide the flow path substantially equally, and smoothly guide the airflow upward and forward.

  By comparing K1 and K2, the effect of arranging the horizontal louver 113 as shown in FIG. 5 can be grasped. By comparing K2 and K3, the effect of the shape and arrangement of the horizontal louvers 111 and 112 can be grasped. By comparing K1 and K4, the effect of the length of the upper wall 6b and the lower wall 6c can be grasped.

  According to the figure, in the case of K1-K3, it can drive with less input (power consumption) compared with a comparative example (K4). When the noise at the same air volume was compared for the cases of K1 to K4, K1 was about 2 dB lower than K4, and K2 and K3 were equivalent to K1 and the noise level was larger than K1.

  8-11 is a figure explaining the difference in the power consumption of the crossflow fan 7 of this embodiment (K1) and a comparative example (K4). FIG. 8 is a side sectional view of the indoor unit 1 schematically showing the state of K4. FIG. 9 is a diagram schematically showing the transition of the static pressure state of the airflow flowing through the interior of the indoor unit 1 at this time. The vertical axis indicates the static pressure of the airflow, and the horizontal axis indicates the airflow direction of the airflow. Show.

  When the cross flow fan 7 is driven, external air whose static pressure is equal to the atmospheric pressure is sucked into the housing of the indoor unit 1 to generate an air flow. The airflow flows through the suction port 4, the indoor heat exchanger 9, and the air blowing path 6, and the air is harmonized into conditioned air when flowing through the indoor heat exchanger 9. At this time, pressure losses ΔPa, ΔPb, and ΔPc are generated by the air resistances of the suction port 4, the indoor heat exchanger 9, and the blower path 6. As a result, the static pressure of the airflow decreases while flowing through the air blowing path 6 and becomes atmospheric pressure−ΔPa−ΔPb−ΔPc. Note that the pressure loss of the air filter 8 and other parts will be omitted.

  Furthermore, when the air flow sent out from the air outlet 5 exits the air outlet 5, a pressure loss ΔPd1 associated with the disturbance of the air current occurs. That is, the air flow sent out from the blower outlet 5 is ejected into the surrounding air suddenly without the upper, lower, left and right wall surfaces of the air blowing path 6 existing so far. At that time, the surrounding air is moved slowly by giving kinetic energy to the surrounding air due to the viscosity of the air. Therefore, the airflow sent from the blower outlet 5 is deprived of kinetic energy by the surrounding air and eventually becomes the same static pressure as the atmospheric pressure. Since this phenomenon is performed at once as soon as the airflow is sent out from the blowout port 5, the airflow in the vicinity of the blowout port 5 is greatly disturbed, resulting in a pressure loss.

  For this reason, the cross flow fan 7 needs to raise the sum (ΔPa + ΔPb + ΔPc + ΔPd1) of the static pressure drop due to the pressure loss at once. Therefore, the static pressure increase ΔP0 by the cross flow fan 7 must be equivalent to the total static pressure decrease (ΔPa + ΔPb + ΔPc + ΔPd1).

  The product (ΔP0 × Q) of the static pressure increase ΔP0 and the air flow rate Q to be circulated is the work of the cross flow fan 7. When the static pressure increase by the cross flow fan 7 is smaller than the total static pressure decrease (ΔP0 <ΔPa + ΔPb + ΔPc + ΔPd1), the cross flow fan 7 cannot circulate the desired air volume to the indoor heat exchanger 9. Therefore, sufficient air conditioning cannot be performed.

  On the other hand, the case of this embodiment (K1) is shown in FIGS. FIG. 10 is a side cross-sectional view of the indoor unit 1 schematically showing the state of K1. FIG. 11 is a diagram schematically showing the transition of the static pressure state of the airflow flowing through the interior of the indoor unit 1 at this time, as in FIG. 9. The vertical axis indicates the static pressure of the airflow, and the horizontal axis Indicates the direction of air flow.

  When the cross flow fan 7 is driven, external air whose static pressure is equal to the atmospheric pressure is sucked into the housing of the indoor unit 1 and airflow is generated as described above. At this time, pressure losses ΔPa, ΔPb, and ΔPc are generated by the air resistances of the suction port 4, the indoor heat exchanger 9, and the blower path 6. As a result, the static pressure of the airflow decreases while flowing through the air blowing path 6 and becomes atmospheric pressure−ΔPa−ΔPb−ΔPc.

  On the other hand, the pressure loss ΔPd2 of the air flow sent out from the outlet 5 is smaller than the pressure loss ΔPd1 of the comparative example of FIG. That is, the airflow flowing through the front guide portion 6a smoothly follows the inclined surface 6b5 via the bent portion 6b4. For this reason, unlike the comparative example, the kinetic energy is not rapidly taken away by the surrounding air, and the amount of kinetic energy taken by the surrounding air is small.

  Moreover, since the whole airflow which distribute | circulated the front guide part 6a follows the inclined surface 6b5 by the Coanda effect, the flow along the lower wall 6c of the ventilation path 6 is also influenced by this. For this reason, without diffusing at a stretch, it is gradually diffused into the surrounding air from the lower side of the air flow and becomes the same static pressure as the atmospheric pressure. Therefore, the disturbance of the airflow in the vicinity of the outlet 5 is small, and the pressure loss ΔPd2 associated therewith is small.

  Further, the flow passage area is gradually enlarged by the front guide portion 6 a of the air blowing path 6, and then the flow passage area is gradually enlarged by the inclined surface 6 b 5 and the lateral louver 113. For this reason, the airflow circulates while gradually expanding the basin area while smoothly following the inclined surface 6b5 even after passing through the front guide portion 6a.

  At this time, since the horizontal louvers 111, 112, and 113 are arranged as shown in FIG. 5 described above, the flow path of the airflow that flows under the lowermost horizontal louver 113 of the airflow sent from the blowout port 5 is provided. It is gradually enlarged. Next, the flow path of the airflow flowing between the horizontal louvers 112 and 113 of the airflow sent out from the blower outlet 5 is gradually enlarged. Next, the flow path of the airflow flowing between the horizontal louvers 111 and 112 of the airflow sent out from the blower outlet 5 is gradually enlarged. Finally, the flow path of the airflow above the lateral louver 111 that circulates on the uppermost side of the airflow sent from the outlet 5 is gradually enlarged. Accordingly, the flow velocity of the airflow decreases gradually and smoothly from the lower side.

  When the flow velocity of the airflow decreases smoothly, the static pressure of the airflow increases according to Bernoulli's equation known in the field of hydrodynamics. That is, the flow velocity (kinetic energy) of the airflow is converted into static pressure (potential energy). Accordingly, before the kinetic energy of the airflow sent from the outlet 5 is taken away by the surrounding air or the airflow is disturbed, a part thereof is converted into a static pressure to obtain a static pressure increase ΔP2.

  Accordingly, the cross flow fan 7 needs to increase at a stretch the amount obtained by subtracting the static pressure increase ΔP2 from the total static pressure decrease due to the pressure loss (ΔPa + ΔPb + ΔPc + ΔPd2). Therefore, the static pressure increase ΔP1 caused by the cross flow fan 7 is ΔPa + ΔPb + ΔPc + ΔPd2−ΔP2.

  Accordingly, the required static pressure increase ΔP1 is smaller by ΔP2 + ΔPd1−ΔPd2 than the static pressure increase ΔP0 required for the cross flow fan 7 in the comparative example (see FIGS. 8 and 9). As a result, the work of the cross flow fan 7 is reduced by (ΔP2 + ΔPd1−ΔPd2) × Q, and therefore, the input (power consumption) of the fan drive motor can be reduced by this amount to save energy.

  That is, the pressure loss ΔPd2 in the vicinity of the outlet 5 can be reduced, the air along the upper wall 6b and the lower wall 6c is decelerated to convert the kinetic energy into static pressure, and the crossflow fan 7 is driven by the static pressure increase ΔP2. Assist. In other words, the kinetic energy previously taken by the surrounding air can be sufficiently recovered and converted to static pressure, and used for work for blowing air. Therefore, an increase in static pressure due to the cross flow fan 7 can be reduced, and energy saving of the air conditioner can be achieved.

  As described above, since the wind speed is gradually and gradually reduced from the lower side of the airflow to convert it to static pressure, there is a loss in converting the airflow velocity (kinetic energy) to static pressure (positional energy). small. For this reason, the conversion efficiency for converting the flow velocity into the static pressure is extremely improved, and a large amount of kinetic energy can be converted into the static pressure.

FIG. 12 is a contour diagram showing the results of examining the input (power consumption, unit: W) of the fan drive motor of the cross flow fan 7 by varying the lengths of the upper wall 6b and the lower wall 6c. The vertical axis indicates the length of the upper wall 6b and is dimensionless by dividing by the diameter D of the cross flow fan 7. The horizontal axis indicates the length of the lower wall 6 c and is dimensionless by dividing by the diameter D of the cross flow fan 7. The airflow of the cross flow fan 7 is fixed at 16 m ³ / min. In the figure, K1 and K4 are the same conditions as in FIG.

  Note that when the length of the upper wall 6b and the lower wall 6c is less than 0.5D and less than 1.5D, respectively, the length is extremely short and the cross flow fan 7 is not formed. Further, since the measurement points in the figure are finite, the contour diagram is completed using interpolation and prediction of each measurement value.

  As is clear from the figure, the power consumption of the cross flow fan 7 can be reduced by increasing the length of the upper wall 6b and the length of the lower wall 6c. Further, the power consumption value changes abruptly in the vicinity of the line L1 where the sum of the length of the upper wall 6b and the length of the lower wall 6c is 3.5D. Therefore, when the sum of the length of the upper wall 6b and the length of the lower wall 6c is 3.5D or more, the power consumption can be significantly reduced. Thereby, the kinetic energy of the airflow continues to be converted into static pressure until the speed of the airflow becomes sufficiently low, and the kinetic energy of the airflow can be converted into sufficient static pressure and recovered.

FIG. 13 is a contour diagram showing the result of examining the reach distance (unit: m) of the air flow along the ceiling surface by changing the length of the upper wall 6b and the lower wall 6c. The reach distance is a distance to a position where the average wind speed for 30 seconds is 0.05 m / s. Similarly to FIG. 12, the vertical axis indicates the length of the upper wall 6b, and is made dimensionless by dividing by the diameter D of the crossflow fan 7. The horizontal axis indicates the length of the lower wall 6 c and is dimensionless by dividing by the diameter D of the cross flow fan 7. The airflow of the cross flow fan 7 is fixed at 16 m ³ / min. In the figure, K1 and K4 are the same conditions as in FIG.

  In addition, when the length of the upper wall 6b and the lower wall 6c is less than 0.5D and less than 1.5D, respectively, the length is extremely short and the cross flow fan 7 is not formed, so measurement is omitted. Further, since the measurement points in the figure are finite, the contour diagram is completed using interpolation and prediction of each measurement value.

  As is apparent from the figure, the reach distance has a small dependence on the length of the lower wall 6c, and varies greatly depending on the length of the upper wall 6b. That is, in order to extend the reach distance, it is effective to prevent the kinetic energy from being dissipated upward, and the length of the upper wall 6b is greatly affected.

  In addition, the reach distance suddenly changes in the vicinity of the line L2 where the length of the upper wall 6b is 1.5D. That is, the airflow blown out from the outlet 5 immediately induces the movement of the surrounding air due to the viscosity, and the kinetic energy of the airflow is gradually lost to the surrounding air. However, if the length of the upper wall 6b is 1.5D or more, the upper wall 6b has a sufficient length, so that the upward movement of the airflow is rapidly reduced. Thereby, the kinetic energy for that amount is not impaired, and the airflow reaches far. That is, even in the airflow after sufficiently recovering the kinetic energy, it is possible to ensure a large reach distance if the length of the upper wall 6b is 1.5D or more.

  When the airflow blown out from the cross flow fan 7 flows through the blower path 6, the lower part (near the lower wall 6c) becomes lower in the vicinity of the outlet 5 than the upper part (near the upper wall 6b). That is, in the vicinity of the air outlet 5, the airflow flowing through the upper part of the blowing path 6 has a relatively high density kinetic energy, and the airflow flowing through the lower part of the blowing path 6 has a relatively low density kinetic energy. This phenomenon is a characteristic common to ordinary cross flow fans.

  If kinetic energy is simultaneously recovered from an airflow having a non-uniform energy density, only kinetic energy recovery from an airflow having a relatively high density and a high flow velocity proceeds. This makes it difficult to recover sufficient kinetic energy from an airflow having a relatively low density and a slow flow velocity.

  In other words, since the flow path of the airflow is gradually expanded to reduce the wind speed of the airflow and converted to static pressure, if the flow path of the flow having a non-uniform wind speed distribution is expanded, It is greatly decelerated through the passage. This makes it difficult for the airflow with a low wind speed to be decelerated. As a result, the kinetic energy recovery efficiency from the entire airflow is reduced. For this reason, it is advisable to separate the kinetic energy separately by dividing the air flow having a relatively high density kinetic energy and the high flow velocity and the air flow having a relatively low density kinetic energy and the low flow velocity. Thereby, kinetic energy can be efficiently recovered from the entire airflow.

  In addition, as the air flow having a relatively low density of kinetic energy and having a low flow velocity flows, the kinetic energy is gradually lost due to wall resistance and the like, and the energy density is gradually lowered. For this reason, it is necessary to collect kinetic energy as early as possible. An airflow having a relatively low density and a slow flow velocity has a small amount of kinetic energy, so that the kinetic energy can be sufficiently recovered at a relatively short distance. On the other hand, since a high-speed airflow having a relatively high density of kinetic energy has a lot of kinetic energy, a relatively long distance is required to recover sufficient kinetic energy.

  For this reason, the air flow path 6 may be divided into a plurality of flow paths in the vertical direction, the lower flow path may be relatively short, and the flow paths may be lengthened sequentially toward the top. Thereby, the kinetic energy can be efficiently recovered from the airflow having the non-uniform energy density unique to the cross flow fan 7. Therefore, in this embodiment, the air flow path 6 is divided into four vertically by the horizontal louvers 111, 112, 113 during the operation of the air conditioner 1.

  That is, the uppermost flow path formed by the inclined portion 6b5 and the uppermost horizontal louver 111, the second flow path formed by the uppermost horizontal louver 111 and the middle horizontal louver 112, and the middle The four channels of the third channel formed by the horizontal louver 112 and the lowermost horizontal louver 113, and the lowermost channel formed by the lowermost horizontal louver 113 and the lower wall 6c. The ventilation path is divided into two.

  As described above, the upper end 6b6 of the upper wall 6b, the front end of the lateral louver 111, the front end of the lateral louver 112, the front end of the lateral louver 113, and the end 6c4 of the lower wall 6c are arranged in this order from the front upper side. Thereby, each divided flow path can be sequentially lengthened as it goes upward.

  It is more preferable that the angles θ1 to θ4 (see FIG. 5) representing the enlargement ratio of the flow passage area of each flow passage are in the range of 10 ° to 15 °. That is, if the angles θ1 to θ4 are larger than 15 °, the airflow flowing through each flow path is separated from the wall surface or rapidly decelerated, and there is a high possibility that a loss will occur when converting kinetic energy into static pressure. Become. If the angles θ1 to θ4 are smaller than 10 °, the path is unnecessarily extended, and the loss of kinetic energy due to the friction between the airflow and the wall surface increases accordingly.

  The magnitude of the kinetic energy of the airflow is proportional to the square of the flow velocity. When the cross flow fan 7 is used, the wind speed of the airflow flowing through the upper part (near the upper wall 6b) of the blowing path 6 is several times the wind speed of the airflow flowing through the lower part (near the lower wall 6c) of the blowing path 6. For this reason, the kinetic energy which the airflow which distribute | circulates the upper part (near the upper wall 6b) of the ventilation path 6 becomes tens of times the kinetic energy which the airflow which distribute | circulates the lower part (near the lower wall 6c) of the ventilation path 6 becomes. There is. Since the amount of kinetic energy to be recovered is very large in the upper part of the air blowing path 6, a sufficiently long flow path is required.

  On the other hand, the angle α (see FIG. 2) representing the enlargement ratio of the flow path area of the front guide portion 6a of the blowing path 6 is preferably about 20 ° as described above. When the angle α is more than that, the airflow flowing through the front guide portion 6a is peeled off from the wall surface or is rapidly decelerated, resulting in energy loss. At this time, if a flow path whose flow area is expanded in a range of 10 ° to 15 ° by dividing each horizontal louver is formed, only about two divisions are possible. As a result, as described above, it is extremely difficult to effectively recover kinetic energy from an airflow having an energy state that is several tens of times as wide as described above.

  For this reason, the middle horizontal louver 112 faces the bent portion 6b4, the rear end thereof is arranged behind the bent portion 6b4, and is arranged substantially parallel to the upper surface 6b3 of the front guide portion 6a. Thereby, the flow path of the airflow which circulates through the front guide part 6a is divided into two vertically. The flow path below the lateral louver 112 can be further divided into two by the lateral louver 113 in the range of θ3 and θ4 of 10 ° to 15 °.

  Further, the upper wall 6b bends upward at the bent portion 6b4 facing the lateral louver 112. Thereby, the flow path of the airflow that flows above the lateral louver 112 is enlarged. The gradually expanding flow path formed by the horizontal louver 112 and the inclined surface 6b5 is divided by the uppermost horizontal louver 111. Since the uppermost horizontal louver 111 is opposed to the inclined surface 6b5 and the rear end is disposed forward of the bent portion 6b4, the horizontal louver 111 is positioned above the horizontal louver 112 so that θ1 and θ2 are in the range of 10 ° to 15 °. Can be divided into two. Note that it is not very efficient to bend the lower surface 6c3 of the front guide portion 6a downward and enlarge it in the same manner because the wind speed is slow.

  It is more desirable to arrange the rear end of the lowermost horizontal louver 113 and the lower surface 6c3 of the front guide portion 6a so as to overlap at a position close to the end 6c4 of the lower wall 6c in the direction perpendicular to the airflow. Thereby, kinetic energy can be more efficiently recovered from the airflow flowing through the flow path below the horizontal louver 113.

  In addition, since the horizontal louvers 111, 112, and 113 are configured to be rotatable around a rotation axis (not shown), the wind direction can be changed in another arrangement.

  According to the present embodiment, the sum of the length of the upper wall 6b and the length of the lower wall 6c of the air flow path 6 on the downstream side of the cross flow fan 7 is 3.5 times or more the diameter D of the cross flow fan 7. During the operation of the air conditioner, air smoothly circulates over a long distance along the upper wall 6b and the lower wall 6c of the air blowing path 6. Thereby, there is little disturbance of the airflow in the blower outlet 5 vicinity, and pressure loss (DELTA) Pd2 accompanying it becomes small.

  In addition, the air along the upper wall 6b and the lower wall 6c is decelerated until the speed becomes sufficiently low, and the kinetic energy is converted into static pressure, and the crossflow fan 7 is assisted by the static pressure increase ΔP2. In other words, the kinetic energy previously taken by the surrounding air is sufficiently recovered and converted to static pressure, and can be used for work for blowing air. Therefore, an increase in static pressure due to the cross flow fan 7 can be reduced, and energy saving of the air conditioner can be achieved.

  The cross flow fan 7 generally causes surging when the pressure loss in the flow path increases. As a result, there are cases where a desired air volume cannot be obtained or the noise is greatly increased. When the indoor heat exchanger 9 has a plurality of stages and a plurality of rows of refrigerant tubes and is bent as in the present embodiment, a very high pressure loss occurs. For this reason, it is necessary to take a countermeasure against surging by increasing the rotational speed of the cross flow fan 7 considerably. Thereby, the noise of the cross flow fan 7 becomes large and energy saving property worsens.

  For this reason, by converting the kinetic energy of the airflow into a static pressure and assisting the cross flow fan 7 by the increase in the static pressure, the cross flow fan 7 hardly causes surging and the noise can be relatively reduced. In particular, when four or more rows of refrigerant pipes are juxtaposed in the depth direction, the pressure loss becomes very large, so that a greater effect can be achieved by this embodiment.

Second Embodiment
Next, FIG. 14 is a side sectional view showing the indoor unit of the air conditioner of the second embodiment. For convenience of explanation, the same reference numerals are assigned to the same parts as those in the first embodiment shown in FIGS. In the present embodiment, the front panel 3 is pivotally supported by the rotation shaft 22 at the lower end. Further, the front panel 3 can be bent by a rotating shaft 23 arranged on the front surface. Other parts are the same as those in the first embodiment.

  When the air conditioner is stopped, as shown in FIG. 14, the front panel 3 is arranged so that the upper end is in contact with the upper part of the casing. Moreover, the blower outlet 5 is shielded by the horizontal louvers 111 and 112 as in the first embodiment.

  As shown in FIG. 15, when the air conditioner is driven, the front panel 3 is rotated by the rotating shafts 22 and 23, and the inclined surface 6 b 5 of the air blowing path 6 is formed by the front panel 3 between the rotating shafts 22 and 23. The Accordingly, the length of the upper wall 6b of the air flow path 6 on the downstream side of the cross flow fan 7 is formed to be 1.5D or more with the diameter of the cross flow fan 7 being D. In addition, the sum of the length of the upper wall 6b and the length of the lower wall 6c on the downstream side of the cross flow fan 7 is formed to be 3.5D or more. Therefore, the same effect as the first embodiment can be obtained.

<Third Embodiment>
Next, FIG. 16 is a side sectional view showing the indoor unit of the air conditioner according to the third embodiment. For convenience of explanation, the same reference numerals are assigned to the same parts as those in the first embodiment shown in FIGS. In the present embodiment, the lower portion of the front panel 3 is opened, and the movable panel 21 that closes the opening is pivotally supported by the rotating shaft 22 at the lower end. Other parts are the same as those in the first embodiment.

  When the air conditioner is stopped, the movable panel 21 is disposed so as to block the lower portion of the front panel 3 as shown in FIG. Moreover, the blower outlet 5 is shielded by the horizontal louvers 111 and 112 as in the first embodiment.

  As shown in FIG. 17, when the air conditioner is driven, the movable panel 21 is rotated by the rotation shaft 22, and the inclined surface 6 b 5 of the blower path 6 is formed by the movable panel 21. Accordingly, the length of the upper wall 6b of the air flow path 6 on the downstream side of the cross flow fan 7 is formed to be 1.5D or more with the diameter of the cross flow fan 7 being D. In addition, the sum of the length of the upper wall 6b and the length of the lower wall 6c on the downstream side of the cross flow fan 7 is formed to be 3.5D or more. Therefore, the same effect as the first embodiment can be obtained.

<Fourth embodiment>
Next, FIG. 18 is a side sectional view showing the indoor unit of the air conditioner of the fourth embodiment. The same parts as those in the first embodiment shown in FIGS. 1 to 13 are denoted by the same reference numerals. This embodiment omits the lateral louver 113 of the first embodiment as described above. Other portions including the lengths of the upper wall 6b and the lower wall 6c of the air blowing path 6 are the same as those in the first embodiment.

  According to the air conditioner of the present embodiment, the lowermost horizontal louver 113 is omitted as compared with the air conditioner of the first embodiment, so that the efficiency of recovering the kinetic energy of the airflow flowing under the air blowing path 6 is slightly reduced. To do. However, as indicated by K2 in FIG. 6 described above, the power consumption can be made smaller than in the comparative example K4 in FIG. 7, and energy saving can be achieved as compared with the conventional example.

<Fifth Embodiment>
Next, FIG. 19 is a side sectional view showing the indoor unit of the air conditioner of the fifth embodiment. The same parts as those in the first embodiment shown in FIGS. 1 to 13 are denoted by the same reference numerals. In the present embodiment, as described above, the lateral louver 113 of the first embodiment is omitted, and the length and arrangement of the lateral louvers 111 and 112 are changed. Other portions including the lengths of the upper wall 6b and the lower wall 6c of the air blowing path 6 are the same as those in the first embodiment.

  The horizontal louvers 111 and 112 arranged above and below face the bent portion 6b4, and the rear ends thereof are arranged behind the bent portion 6b4. The front ends of the horizontal louvers 111 and 112 are disposed at substantially the same position in the front-rear direction in front of the bent portion 6b4. Moreover, the flow path which divided | segmented the front guide part 6a of the ventilation path 6 at substantially equal intervals by the horizontal louvers 111 and 112 is formed.

  According to the air conditioner of this embodiment, the efficiency of recovering the kinetic energy of the airflow flowing through the air flow path 6 is lower than that of the air conditioner of the first and second embodiments. However, as indicated by K3 in FIG. 6 described above, the power consumption can be made smaller than in the comparative example K4 in FIG. 7, and energy saving can be achieved as compared with the conventional example.

  Although the air conditioner according to the present invention has been described with reference to the first to fifth embodiments, the present invention is not limited to the above-described embodiments, and may be implemented with appropriate modifications without departing from the spirit of the present invention. can do.

  ADVANTAGE OF THE INVENTION According to this invention, it can utilize for the air conditioner which takes in indoor air and harmonizes.

Side surface sectional drawing which shows the state at the time of the operation | movement of the indoor unit of the air conditioner of 1st Embodiment of this invention. Side surface sectional drawing which shows the detail of the ventilation path | route of the indoor unit of the air conditioner of 1st Embodiment of this invention Side surface sectional drawing which shows the detail of the bending part of the ventilation path | route of the indoor unit of the air conditioner of 1st Embodiment of this invention Side surface sectional drawing which shows the state at the time of the operation stop of the indoor unit of the air conditioner of 1st Embodiment of this invention Side surface sectional drawing which shows the detail of the blower outlet vicinity of the indoor unit of the air conditioner of 1st Embodiment of this invention The figure which shows the relationship between the air volume of the cross flow fan of the indoor unit of the air conditioner of 1st Embodiment of this invention, and the input of a fan drive motor. Side surface sectional drawing which shows the comparative example of the indoor unit of the air conditioner of 1st Embodiment of this invention The figure explaining the transition of the static pressure of the comparative example of the indoor unit of the air conditioner of 1st Embodiment of this invention. The figure which shows transition of the static pressure of the comparative example of the indoor unit of the air conditioner of 1st Embodiment of this invention. The figure explaining transition of the static pressure of the indoor unit of the air conditioner of a 1st embodiment of the present invention. The figure which shows transition of the static pressure of the indoor unit of the air conditioner of 1st Embodiment of this invention. The figure which shows the relationship of the length of the upper wall of the ventilation path | route of the indoor unit of the air conditioner of 1st Embodiment of this invention, the length of a lower wall, and the power consumption of a crossflow fan. The figure which shows the relationship between the length of the upper wall of the ventilation path | route of the indoor unit of the air conditioner of 1st Embodiment of this invention, the length of a lower wall, and the arrival distance of the airflow of a crossflow fan. Side surface sectional drawing which shows the state at the time of the operation stop of the indoor unit of the air conditioner of 2nd Embodiment of this invention Side surface sectional drawing which shows the state at the time of the operation | movement of the indoor unit of the air conditioner of 2nd Embodiment of this invention. Side surface sectional drawing which shows the state at the time of the operation stop of the indoor unit of the air conditioner of 3rd Embodiment of this invention Side surface sectional drawing which shows the state at the time of the operation | movement of the indoor unit of the air conditioner of 3rd Embodiment of this invention. Side surface sectional drawing which shows the state at the time of the operation | movement of the indoor unit of the air conditioner of 4th Embodiment of this invention. Side surface sectional drawing which shows the state at the time of the operation | movement of the indoor unit of the air conditioner of 5th Embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Indoor unit 2 Cabinet 3 Front panel 4 Suction port 5 Air outlet 6 Air flow path 6a Front guide part 6b Upper wall 6b5 Inclined surface 6c Lower wall 7 Cross flow fan 8 Air filter 9 Indoor heat exchangers 10, 13 Drain pans 111, 112, 113 Horizontal louver 12 Vertical louver 21 Movable panel 22, 23 Rotating shaft 61 Temperature sensor

Claims (5)

A suction port for taking indoor air into the housing of the indoor unit, and an air outlet provided at the bottom of the housing;
A ventilation path that allows communication between the suction port and the outlet, and a plurality of refrigerant pipes arranged side by side in a plurality of rows and bent along the inner surface of the housing, facing the suction port in the ventilation path In an air conditioner comprising: an indoor heat exchanger disposed; and a cross flow fan disposed between the indoor heat exchanger in the air blowing path and the outlet.
A front panel that forms the front surface of the housing of the indoor unit;
An air filter that is provided between the front panel and the indoor heat exchanger and collects and removes dust contained in the air sucked from the suction port;
An air filter cleaning device provided between the front panel and the indoor heat exchanger for removing dust accumulated in the air filter;
A first wind direction plate provided opposite to the upper wall of the air flow path on the downstream side of the cross flow fan, and capable of vertically changing the air direction of the air outlet;
A second wind direction plate provided below the first wind direction plate and configured to vary the wind direction of the air outlet up and down;
The air flow path has a front guide portion that expands the flow path area as it goes downstream by guiding air forward and downward,
The sum of the length of the upper wall and the length of the lower wall of the air flow path on the downstream side of the cross flow fan is at least 3.5 times the diameter of the cross flow fan, and the length of the upper wall is Make it more than 1.5 times the diameter of the cross flow fan ,
The upper wall has an inclined surface that is bent at the bent portion from the end of the upper surface of the front guide portion that is inclined forward and downward, and is inclined upward and forward.
When the air is sent forward and upward from the air outlet, the front end of the first wind direction plate is rearward of the front end of the upper wall and forward of the front end of the second wind direction plate. The second wind direction plate is disposed in front of the bent portion, the rear end of the second wind direction plate is opposed to the bent portion, and rearward of the bent portion.
The air flow path flowing between the upper wall and the first wind direction plate and the air flow path flowing between the first wind direction plate and the second wind direction plate are gradually enlarged toward the downstream. An air conditioner in which first and second wind direction plates are arranged . The bent portion is provided with at least one flat surface, and ends of the flat surfaces are connected with smooth curved surfaces, and the angle formed by the upper surface of the front guide portion and the flat surface and the angle formed by the flat surface and the inclined surface are as follows: The air conditioner according to claim 1, wherein the air conditioner is formed at 17 ° or less . The angle between the inclined surface and the first wind direction plate and the angle between the first and second wind direction plates are set to 10 ° to 15 °.
The air conditioner according to claim 1 or claim 2, characterized in that the. A third wind direction plate is provided below the second wind direction plate, the rear end of the third wind direction plate is disposed in front of the rear end of the second wind direction plate, and the angle formed by the second and third wind direction plates is 10 ° to the air conditioner according to claim 3, characterized in that the 15 °. The rear end of the wind direction plate disposed at the lowest position and the lower surface of the front guide section are arranged so as to overlap each other in the direction perpendicular to the airflow at a position close to the end of the lower wall of the front guide section, and at the lowest position. The air conditioner according to claim 3 or 4 , wherein an angle formed by the wind direction plate disposed and a tangent line at the end of the lower wall is 10 ° to 15 ° .

Images