KR100971855B1 - Air conditioner - Google Patents

Abstract

An inlet port 4 for introducing indoor air into the housing of the indoor unit 1, a blower port 5 provided in the lower part of the housing, a blower path 6 for communicating between the inlet port 4 and the blower outlet 5; The refrigerant heat pipes are arranged in a plurality of stages and in a plurality of rows, and are bent along the inner surface of the housing to be disposed opposite to the intake port 4, and the indoor heat exchanger 9 and the blower outlet 5 in the air passage 6. In the air conditioner provided with the cross flow fan (7) disposed between the), the blower path (6) has a front guide portion (6a) to guide the air forward and downward and the flow passage area is enlarged toward the downstream, The sum of the length of the upper wall 6b and the length of the lower wall 6c of the blowing path 6 on the downstream side of the flow fan 7 was made 3.5 times or more the diameter of the crossflow fan 7.

Cross Flow Fan, Heat Exchanger, Indoor Unit, Blowing Path, Air Conditioner

Description

Air conditioner {AIR CONDITIONER}

The present invention relates to an air conditioner that harmonizes air introduced from the room and delivers it to the room.

Conventional air conditioners are disclosed in Patent Documents 1 and 2. The air conditioner of patent document 1 improves the thickness distribution of the blade | wing of a blowing fan, and the pressure loss of a blowing fan is reduced. Thereby, energy saving of an air conditioner is aimed at. Moreover, the air conditioner of patent document 2 has the movable panel which closes the suction port provided in the housing front surface of the indoor unit. When the air conditioner is driven, indoor air is introduced by moving the movable panel to open the inlet wide. As a result, the pressure loss at the time of suction is reduced, and energy saving of the air conditioner is aimed at.

Patent Document 1: Japanese Patent Application Publication No. 2003-028089

Patent Document 2: Japanese Patent Application Laid-open No. 2000-111082

In recent years, the conservation of the global environment has been strongly insisted, and further energy saving of so-called white household appliances is strongly desired. However, according to the conventional air conditioner described above, the rough air is blown out from the jet port into the air in the room. At this time, the wall surface of the passageway existing until then disappears suddenly, the kinetic energy is lost to the surrounding air by the viscosity of the air, and becomes a static pressure equal to the atmospheric pressure. Since this phenomenon is performed at once as the air flow is discharged from the jet port, the air flow in the vicinity of the jet port is greatly disturbed, resulting in a pressure loss accompanying it. Therefore, there was a problem that energy saving of the air conditioner could not be sufficiently achieved.

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

In order to achieve the above object, the present invention provides a suction port for introducing indoor air into the housing of the indoor unit, a blowout port provided at the lower portion of the housing, a blowing path for communicating between the suction port and the blower port, and a refrigerant pipe in multiple stages. An air conditioner having a plurality of rows and an indoor heat exchanger which is bent along the inner surface of the housing and disposed to face the inlet in the blower path, and a crossflow fan disposed between the indoor heat exchanger and the blower outlet in the blower path; The air flow path has a front guide part which guides air downward and forwards and expands the flow path area toward the downstream, and the sum of the length of the upper wall and the length of the lower wall of the air blow path downstream from the cross flow fan. It is characterized in that more than 3.5 times the diameter of the cross flow fan have.

According to this configuration, the air in the room is introduced into the housing from the suction port by the drive of the cross flow fan to distribute the blowing path. The air is heat exchanged with an indoor heat exchanger having a large pressure loss arranged in a plurality of stages in a vertical direction and a plurality of rows in an inward direction by meandering the refrigerant pipe. The roughened air flows through the front guide part while expanding the flow path area along the upper wall and the lower wall of the blowing path from the exhaust side of the cross flow fan, and is discharged from the jet port. At this time, the airflow along the upper wall and the lower wall of the blowing path is gradually decelerated, and the kinetic energy is converted into the static pressure and recovered as the static pressure.

Moreover, this invention is equipped with the 1st wind direction plate which changes the wind direction of the said blower opening up and down in the air conditioner of the said structure, The front end of the said upper wall from the front upper direction at the time of operation of an air conditioner, a 1st wind direction plate And the front end of the lower wall, and the front end of the lower wall. According to this structure, the kinetic energy of the airflow which flows through a ventilation path | route is collect | recovered sequentially from the lower direction with a slow flow rate.

Moreover, this invention provides the 2nd wind direction plate below the 1st wind direction plate in the air conditioner of the said structure, and arrange | positioned the front end part of the 1st wind direction plate in front of the front end part of the 2nd wind direction plate, It is characterized by the above-mentioned. Doing.

In addition, the present invention includes a first and a second wind direction plate which is variable in the air conditioner of the above configuration up and down the blowing port, the upper wall is bent from the end of the upper surface of the front guide portion in the bent portion to the front upwards It has an inclined inclined surface, and the rear end part of a 1st wind direction plate is arrange | positioned ahead of the said bending part, and the rear end part of the 2nd wind direction plate lower than a 1st wind direction plate is arrange | positioned behind the said bending part, It is characterized by the above-mentioned. .

According to this configuration, the airflow flowing along the upper wall of the blowing path is bent by the second wind direction plate and flows upward along the inclined surface. The kinetic energy of the air stream of the lower part bent by the 2nd wind direction plate is converted into positive pressure by the flow path formed between the 2nd wind direction plate and the 1st wind direction plate, and is recovered. The kinetic energy of the upper air stream bent by the second wind direction plate is converted into a positive pressure by a flow path formed between the first wind direction plate and the inclined surface and recovered.

The present invention is also characterized in that 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 ° in the air conditioner having the above-described configuration. According to this structure, airflow flows smoothly along a wall surface, without peeling from the wall surface which consists of inclined surfaces of a 1st, 2nd wind direction plate, and a ventilation path.

The present invention is also characterized in that, in the air conditioner having the above-described configuration, a third wind direction plate is provided below the second wind direction plate, and the angle formed by the second and third wind direction plates is set to 10 ° to 15 °. According to this structure, airflow flows smoothly along a wall surface, without peeling from the wall surface which consists of 2nd, 3rd wind direction plates.

In addition, the present invention is characterized in that the angle formed by the tangent of the wind direction plate disposed at the bottom of the air conditioner having the above-described configuration and the end of the lower wall of the front guide portion is 10 ° to 15 °. According to this structure, airflow flows smoothly along a wall surface, without peeling from the wall surface which consists of a wind direction board of the lowest stage.

In addition, the present invention is characterized in that, in the air conditioner having the above configuration, the length of the upper wall is 1.5 times or more the diameter of the cross flow fan.

The present invention also provides a suction port for introducing indoor air into a housing of an indoor unit, a blower port provided at a lower portion of the housing, a blowing path for communicating between the suction port and the blower port, and a refrigerant pipe in multiple stages and in a plurality of rows. At the same time, the indoor heat exchanger is bent along the inner surface of the housing and disposed to face the inlet in the blower path, the cross flow fan disposed between the indoor heat exchanger and the blower in the blower path, and the wind direction of the blower outlet is vertically variable. In the air conditioner provided with the 1st, 2nd wind direction plate, The said air flow path has a front guide part which guides air downwardly from the said cross flow fan, and flow path area expands downstream, and is compared with the said cross flow fan. The length of the upper wall of the blowing path on the downstream side of the crossflow fan At least 1.5 times the diameter, the upper wall has an inclined surface that is bent from the end of the front guide portion at the bent portion and inclined forward upward, and the rear end of the first wind direction plate is disposed ahead of the bent portion, A rear end portion of the second wind direction plate below the first wind direction plate is disposed behind the bent portion.

According to this configuration, the air in the room is introduced into the housing from the suction port by the drive of the cross flow fan to distribute the blowing path. The air is harmonized by heat exchange with an indoor heat exchanger having a large pressure loss arranged in a plurality of stages and a plurality of rows in the vertical direction, meandering the refrigerant pipe. The rough air flows from the exhaust side of the cross flow fan to the front guide while expanding the flow path area along the upper wall and the lower wall of the blowing path. The airflow flowing along the upper wall of the blowing path is bent by the second wind direction changing plate and flows upward along the slope. The airflow in the lower part bent by the second wind direction changing plate is gradually decelerated by the flow path formed between the second wind direction changing plate and the first wind direction changing plate, and the kinetic energy is converted into the static pressure and recovered as the static pressure. The upper air flow bent by the second wind direction changing plate is gradually decelerated by the flow path formed between the first wind direction changing plate and the inclined surface, and the kinetic energy is converted into the static pressure and recovered as the static pressure.

The present invention is also characterized in that 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 ° in the air conditioner having the above-described configuration.

The present invention is also characterized in that, in the air conditioner having the above-described configuration, a third wind direction plate is provided below the second wind direction plate, and the angle formed by the second and third wind direction plates is set to 10 ° to 15 °.

The present invention is also characterized in that the angle formed by the tangent of the wind direction plate disposed at the bottom of the air conditioner having the above-described configuration and the end portion of the lower portion of the front guide part is set to 10 ° to 15 °.

Moreover, this invention is the front end of the said upper wall, the front end of a 1st wind direction plate, the front end of a 2nd wind direction plate, and the front of the said lower wall from the front upper direction at the time of operation of an air conditioner in the said air conditioner. It arrange | positioned in order of the edge part, It is characterized by the above-mentioned. According to this structure, the kinetic energy of the airflow which flows through a ventilation path | route is collect | recovered sequentially from the lower direction with a slow flow rate.

In another aspect, the present invention, the inlet for introducing the indoor air into the housing of the indoor unit, a blower is provided in the lower portion of the housing, a blower path for communicating between the inlet and the blower port, and is disposed opposite to the inlet in the blower path An indoor heat exchanger, and a cross flow fan disposed between the indoor heat exchanger and the blower port in the blower path, wherein the length of the upper wall of the blower path downstream of the crossflow fan is 1.5 times the diameter of the crossflow fan. It was characterized by having more than doubled.

According to this configuration, the air in the room is introduced into the housing from the suction port by the drive of the cross flow fan to distribute the blowing path. The air is heat-exchanged with the indoor heat exchanger, and the air is circulated along the upper wall and the lower wall of the blowing path from the exhaust side of the cross flow fan and discharged from the blower outlet. At this time, the airflow along the upper wall and the lower wall of the blowing path is gradually decelerated, and the kinetic energy is converted into the static pressure and recovered as the static pressure.

In another aspect, the present invention, the inlet for introducing the indoor air into the housing of the indoor unit, a blower is provided in the lower portion of the housing, a blower path for communicating between the inlet and the blower port, and is disposed opposite to the inlet in the blower path An indoor heat exchanger and a cross flow fan disposed between the indoor heat exchanger and the blower port in the blower path, wherein the sum of the length of the upper wall and the length of the lower wall of the blower path downstream from the crossflow fan; It is characterized by setting it as 3.5 times or more of the diameter of a crossflow fan.

According to this configuration, the air in the room is introduced into the housing from the suction port by the drive of the cross flow fan to distribute the blowing path. The air is heat-exchanged with the indoor heat exchanger, and the air is circulated along the upper wall and the lower wall of the blowing path from the exhaust side of the cross flow fan and discharged from the blower outlet. At this time, the airflow along the upper wall and the lower wall of the blowing path is gradually decelerated, and the kinetic energy is converted into the static pressure and recovered as the static pressure.

According to the present invention, since the sum of the length of the upper wall and the length of the lower wall of the blower path downstream of the crossflow fan is 3.5 times or more the diameter of the crossflow fan, the air is blown at the time of operation of the air conditioner. The long distance along the top and bottom walls of the smoothly flow. Thereby, the disturbance of the airflow in the vicinity of the jet port is small, and the pressure loss accompanying it becomes small. In addition, the kinetic energy is converted to static pressure by deceleration until the air along the long top and bottom walls is sufficiently slow. Therefore, a sufficient recovery of the kinetic energy of the airflow can reduce the rise of the static pressure by the crossflow fan, and energy saving of the air conditioner can be achieved.

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 part which guides air forward and downward and expands a flow path area as it goes downstream is provided, it is possible to collect | restore kinetic energy fully by decelerating air stream gradually.

In addition, according to the present invention, since the air conditioner is disposed in the order of the front end of the upper wall, the front end of the first wind direction plate, and the front end of the lower wall from the front upper side, the low flow rate of low density kinetic energy The kinetic energy of the air stream can be efficiently recovered by sequentially recovering from the.

Moreover, according to this invention, since the 2nd wind direction plate was provided below the 1st wind direction plate, and the front end part of the 1st wind direction plate was arrange | positioned ahead of the front end part of the 2nd wind direction plate, the low flow velocity of a slow downward flow velocity is carried out. By recovering energy sequentially, the kinetic energy of the air stream can be efficiently recovered.

According to the present invention, the rear end portion of the first wind direction plate is disposed in front of the bent portion between the front guide portion upper surface and the inclined surface, and the rear end portion of the second wind direction plate lower than the first wind direction plate is located behind the curved portion. Since it is arrange | positioned, it is possible to bend the airflow by a 2nd wind direction plate, and to follow a slope. Further, the kinetic energy of the air stream can be efficiently recovered by sequentially recovering from the low-density kinetic energy having a low flow rate below.

In addition, according to the present invention, since the angle between the inclined surface and the first wind direction plate and the angle between the first and second wind direction plates are 10 ° to 15 °, the flow path between the inclined surface and the first wind direction plate and the first and second wind direction plates are The flow path between them is enlarged continuously, and airflow flows smoothly along a wall surface, without peeling from a wall surface. As a result, the kinetic energy of the airflow can be smoothly converted into the static pressure, thereby efficiently recovering the kinetic energy.

According to the present invention, since the angle formed by the third wind direction plate below the second wind direction plate and the second wind direction plate is set to 10 ° to 15 °, the flow path between the second and third wind direction plates is continuously enlarged. Airflow flows along the wall smoothly without peeling from the wall surface. As a result, the kinetic energy of the airflow can be smoothly converted into the static pressure, thereby efficiently recovering the kinetic energy.

In addition, according to the present invention, since the angle formed by the tangent of the wind direction plate disposed at the lowermost part and the end of the lower wall is set to 10 ° to 15 °, the flow path between the lowermost wind direction plate and the lower wall of the ventilation path is continuously flow path. Is expanded so that the airflow flows smoothly along the wall without peeling from the wall. As a result, the kinetic energy of the airflow can be smoothly converted into the static pressure, thereby efficiently recovering the kinetic energy.

Further, according to the present invention, since the length of the upper wall of the blower path on the downstream side of the crossflow fan is 1.5 times or more of the diameter of the crossflow fan, the air is longer along the upper wall of the blower path during operation of the air conditioner. Distribute the streets smoothly. Thereby, the disturbance of the airflow in the vicinity of the jet port is small, and the pressure loss accompanying it becomes small. In addition, the kinetic energy is converted to static pressure by deceleration until the air along the long top and bottom walls is sufficiently slow. Therefore, a sufficient recovery of the kinetic energy of the airflow can reduce the rise of the static pressure by the crossflow fan, and energy saving of the air conditioner can be achieved.

In addition, it is possible to recover the kinetic energy and lengthen the reach of the airflow whose flow velocity is reduced. As a result, the air blown out from the jet port reaches the ceiling of the room and moves on the wall surface facing the air conditioner, the bottom surface, and the wall surface on the air conditioner side. Therefore, the airflow of the roughened air reaches all corners of the room, and the airflow stirs the entire room greatly. Therefore, the temperature distribution of the whole living area except a part of the upper part of the room is equalized, and a comfortable space with little direct wind can be obtained.

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 part which guides air forward and downward and expands a flow path area as it goes downstream is provided, it is possible to collect | restore kinetic energy fully by decelerating air stream gradually.

Further, since the rear end of the first wind direction plate is disposed in front of the bent portion between the front guide portion upper surface and the inclined surface, and the rear end of the second wind direction plate lower than the first wind direction plate is disposed behind the bend portion, We can bend airflow by 2 wind direction plates and let you follow slope. Further, the kinetic energy of the air stream can be efficiently recovered by sequentially recovering from the low-density kinetic energy having a low flow rate below.

Further, according to the present invention, since the air conditioner is disposed in order from the front upper side to the front end of the upper wall, the front end of the first wind direction plate, the front end of the second wind direction plate, and the front end of the lower wall. It is possible to efficiently recover the kinetic energy of the air stream by sequentially recovering the low-density kinetic energy having a slow flow rate.

1 is a side sectional view showing a state during operation of an indoor unit of an air conditioner according to a first embodiment of the present invention.

Fig. 2 is a side sectional view showing the details of the blowing path of the indoor unit of the air conditioner of the first embodiment of the present invention.

Fig. 3 is a side sectional view showing the details of the bent portion of the blowing path of the indoor unit of the air conditioner of the first embodiment of the present invention.

Fig. 4 is a side sectional view showing a state at the time of stopping operation of the indoor unit of the air conditioner of the first embodiment of the present invention.

Fig. 5 is a side sectional view showing the details of the vicinity of the jet port of the indoor unit of the air conditioner according to the first embodiment of the present invention.

Fig. 6 is a diagram showing the relationship between the air flow rate of the cross flow fan of the indoor unit of the air conditioner of the first embodiment of the present invention and the input of the fan drive motor.

Fig. 7 is a side sectional view showing a comparative example of an indoor unit of the air conditioner of the first embodiment of the present invention.

It is a figure explaining the change of the static pressure of the comparative example of the indoor unit of the air conditioner of 1st Embodiment of this invention.

Fig. 9 is a diagram showing the change of the static pressure of the comparative example of the indoor unit of the air conditioner of the first embodiment of the present invention.

It is a figure explaining the change of the static pressure of the indoor unit of the air conditioner of 1st Embodiment of this invention.

It is a figure which shows the change of the static pressure of the indoor unit of the air conditioner of 1st Embodiment of this invention.

It is a figure which shows the relationship of the length of the upper wall, the length of the lower wall, and the power consumption of a cross flow fan of the ventilation path of the indoor unit of the air conditioner of 1st Embodiment of this invention.

It is a figure which shows the relationship of the length of the upper wall of the ventilation path of the indoor unit of the air conditioner of the 1st embodiment of this invention, the length of a lower wall, and the arrival distance of the airflow of a crossflow fan.

Fig. 14 is a side sectional view showing a state when the indoor unit of the air conditioner of the second embodiment of the present invention is stopped operating.

Fig. 15 is a side sectional view showing a state during operation of the indoor unit of the air conditioner of the second embodiment of the present invention.

Fig. 16 is a side cross-sectional view showing a state when the indoor unit of the air conditioner of the third embodiment of the present invention is stopped operating.

Fig. 17 is a side sectional view showing a state during operation of the indoor unit of the air conditioner of the third embodiment of the present invention.

Fig. 18 is a side sectional view showing a state during operation of the indoor unit of the air conditioner of the fourth embodiment of the present invention.

Fig. 19 is a side sectional view showing a state during operation of an indoor unit of an air conditioner according to a fifth embodiment of the present invention.

[Description of the code]

DESCRIPTION OF SYMBOLS 1 Indoor unit, 2 cabinet, 3 front panel, 4 suction port, 5 blower outlet, 6 ventilation path, 6a front guide part, 6b upper wall, 6b5 inclined surface, 6c lower wall, 7 cross flow Fan, 8: air filter, 9: indoor heat exchanger, 10, 13: drain pan, 12: vertical louver, 21: movable panel, 22, 23: rotating shaft, 61: temperature sensor, 111, 112, 113: horizontal louver

<1st embodiment>

EMBODIMENT OF THE INVENTION Below, embodiment of this invention is described with reference to drawings. 1 is a side sectional view showing an indoor unit of an air conditioner of a first embodiment. The indoor unit 1 of the air conditioner is held by the cabinet 2, and the front panel 3 is detachably attached to the cabinet 2. The cabinet 2 and the front panel 3 constitute a housing of the indoor unit 1.

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

In the housing of the indoor unit 1, a blowing path 6 is formed to connect the suction port 4 and the jet port 5. The cross flow fan 7 which supplies air is arrange | positioned in the ventilation path 6. The blowing path 6 is surrounded by the upper wall 6b and the lower wall 6c on the downstream side of the cross flow fan 7. Moreover, the blowing path 6 has the front guide part 6a which guides the air discharged by the crossflow fan 7 to the front downward. The front guide part 6a is formed so that flow path area may enlarge as it goes downstream.

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

The upper surface 6b3 of the front guide portion 6a is inclined forward downward. An inclined surface 6b5 bent upward from the end of the upper surface 6b3 of the front guide portion 6a through the bent portion 6b4 and inclined upwardly is formed. The bent portion 6b4 is composed of a smooth and smooth surface.

The lower wall 6c of the blowing path 6 has a rear guide portion 6c5 along the circumferential surface of the crossflow fan 7. The rear guide portion 6c5 extends in the exhaust direction of the cross flow fan 7, and the lower wall 6c includes a lower surface 6c3 of the front guide portion 6a from the lower end of the rear guide portion 6c5. It is formed into a spiral curved surface.

The angle α formed between the upper surface 6b3 and the lower surface 6c3 of the front guide portion 6a is formed at about 20 °. The angle? Formed between the inclined surface 6b5 and the horizontal surface is formed at about 20 degrees. The angle γ formed between the upper surface 6b3 of the front guide portion 6a and the horizontal surface is formed at 5 °. Therefore, the angle β + γ formed by the upper surface 6b3 and the inclined surface 6b5 of the front guide portion 6a is formed at 25 degrees. Each of α, β, and γ is preferably formed at 15 ° to 20 °, 30 ° or less, and 0 ° to 10 °, respectively.

When angle (beta) + (gamma) is 17 degrees or less, the air along the wall surface of a flow path can flow smoothly with a small pressure loss, without peeling off from a wall surface. However, as will be described later, the angle β + γ is larger than 17 ° in order to divide the flow path into pluralities by the horizontal louvers 111, 112, and 113. For this reason, the horizontal louver 112 of the intermediate | middle stage is arrange | positioned facing the bend part 6b4, and peeling of airflow is suppressed.

As shown in Fig. 3, at least one plane 6f may be provided in the bent portion 6b4 to connect the ends of the plane 6f with the smooth curved surface 6e, respectively. In this case, the angle θ5 formed by the upper surface 6b3 and the plane 6f of the front guide portion 6a and the angle θ6 formed by the plane 6f and the inclined surface 6b5 are formed to be 17 degrees or less. In the case where there are a plurality of planes 6f, all of the angles formed by the planes are formed to be 17 degrees or less. Thereby, the air along the wall surface of the flow path can flow smoothly with small pressure loss without being peeled off from the wall surface. Therefore, energy saving can be improved.

In addition, the lengths of the upper wall 6b and the lower wall 6c of the airflow path 6 downstream of the crossflow fan 7 are 1.9D and 2.1D, respectively, with the diameter of the crossflow fan 7 as D. FIG. It is formed. The front end portions 6b1 and 6c1 of the stabilizer portion 6b7 and the rear guide portion 6c5 are provided in the vicinity of the radial direction perpendicular to the exhaust direction of the cross flow fan 7, and the upper wall 6b and the lower wall 6c. It is the viewpoint of. When the stabilizer portion 6b7 and the rear guide portion 6c5 are formed extending to the intake side of the crossflow fan 7, the front gap 6b2 and the rear of which the distance to the crossflow fan 7 is minimized. The gap 6c2 portion may be referred to as the top wall 6b and the bottom wall 6c.

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

In Fig. 1, the front louver 6a is provided with a vertical louver 12 which can change the ejection angle in the left and right directions. The ejection opening 5 is provided with a plurality of horizontal louvers 111, 112, 113 which can change the ejection angle in the vertical direction in the front upward, horizontal direction, front downward and immediately downward directions. The air filter 8 which collects and removes the dust contained in the air sucked from the intake port 4 is provided in the position which opposes the front panel 3. An air filter cleaning device (not shown) is provided in a space formed between the front panel 3 and the air filter 8. 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 a meandering refrigerant tube (not shown) which is arranged in multiple rows in the vertical direction and in the plurality of rows in the vertical direction, 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 a refrigeration cycle is driven by the compressor. In the cooling operation by the operation of the refrigeration cycle, the indoor heat exchanger 9 is cooled to a lower temperature than the ambient temperature. In the heating operation, the indoor heat exchanger 9 is heated to a higher temperature than the ambient temperature.

Between the indoor heat exchanger 9 and the air filter 8, an electrostatic precipitator (not shown) and a temperature sensor 61 for detecting the temperature of the sucked air are provided. The side part of the indoor unit 1 is provided with the control part (not shown) which controls the drive of an air conditioner. In the lower part before and after the indoor heat exchanger 9, the drain pans 10 and 13 which collect the dew condensation which fell from the indoor heat exchanger 9 at the time of cooling or dehumidification are provided.

In the air conditioner of the above configuration, in the stopped state of the air conditioner, as shown in Fig. 4, the horizontal louvers 111 and 112 are disposed at positions shielding the upper and lower portions of the ventilation path 6. The horizontal louver 113 is disposed inside the blowing path 6. As a result, the jet port 5 is closed. At this time, the horizontal louvers 111 and 112 are disposed along the front surface of the front panel 3. In addition, the horizontal louver 112 is disposed to connect the lower end of the horizontal louver 111 and the bottom surface of the cabinet 2. As a result, the beauty of the indoor unit 1 is not impaired.

The condensation prevention means is provided in the side which does not face the ventilation path 6 of the upper wall 6b. As the 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. Moreover, other condensation prevention means other than a heat insulating material may be sufficient. Also, even if condensation occurs on the side of the upper wall 6b that does not face the blowing path 6, the condensation water is introduced into the drain pan 10. As a result, a reliable air conditioner can be obtained without any problem due to condensation water.

When the air conditioner starts to operate and performs cooling operation, for example, as shown in FIG. 1, the horizontal louvers 111, 112, 113 are arrange | positioned by opening the blower outlet 5. As shown in FIG. The vertical louvers 12 face in a predetermined direction. The cross flow fan 7 is driven so that the coolant from the outdoor unit (not shown) flows into the indoor heat exchanger 9 to operate the refrigeration cycle. As a result, air is sucked into the indoor unit 1 from the intake port 4, and dust contained in the air is removed by the air filter 8. In addition, the air introduced into the indoor unit 1 is cooled by heat exchange with the indoor heat exchanger 9.

Conditioned air cooled in the indoor heat exchanger (9) is regulated in left and right directions and up and down directions by the vertical louvers (12) and the horizontal louvers (111, 112, 113), and is indicated by an arrow E along the inclined surface 6b5. As described above, it is sent out to the room toward the front upward. Thereby, the indoor unit 1 will be in the state of the front upper blowing which sends a rough air to the front upward.

Harmonic air sent from the jet port 5 to the room along the inclined surface 6b5 toward the front upward reaches the ceiling surface S of the room (see Fig. 2). Subsequently, the Coanda effect causes the side wall facing the indoor unit 1, the bottom surface, and the side wall W1 on the indoor unit 1 side to move to the indoor unit 1 from the ceiling surface S. Is inhaled.

By doing in this way, a cold wind or a warm wind does not always directly reach a user, and it can prevent a user's discomfort and can improve comfort. In addition, it is possible to improve the safety of health without cooling the user's body temperature locally at the time of cooling. In addition, since the airflow stirs the entire room greatly, the temperature distribution in the room becomes uniform near the set temperature. That is, the entire living area of the user except for a part of the upper part of the room roughly coincides with the set temperature, so that a comfortable space is obtained in which the temperature fluctuation is small and the direct wind hardly touches the user.

Fig. 5 is a side sectional view showing details near the jet port 5 at this time. The horizontal louver 111 at the uppermost end faces the inclined surface 6b5, and the rear end thereof is disposed in front of the bent portion 6b4. The horizontal louver 112 of the intermediate stage opposes the bent portion 6b4, and the rear end is disposed behind the bent portion 6b4. Then, the front end of the terminal 6b6 of the upper wall 6b, the front end of the uppermost horizontal louver 111, the front end of the intermediate louver 112, and the lowermost horizontal louver 113 from the front upper side. And the end 6c4 of the lower wall 6c.

Moreover, the horizontal louver 111 is arrange | positioned so that the angle (theta) 1 which the inclined surface 6b5 and the uppermost horizontal louver 111 makes may be 13 degrees. The horizontal louvers 112 are disposed such that an angle θ2 formed between the uppermost horizontal louver 111 and the intermediate horizontal horizontal louver 112 is 10 °. The horizontal louver 113 is disposed such that an angle θ3 formed between the horizontal louver 112 at the middle stage and the horizontal louver 113 at the bottom stage is 10 °. Moreover, the angle (theta) 4 which the lowest horizontal transverse louver 113 and the tangent 98 make is 12 degrees.

Since the horizontal louvers 111, 112, and 113 are arranged so that the angles θ1 to θ4 are 17 degrees or less, the air flow in the flow path divided by the horizontal louvers 111, 112, and 113 is at least separated from the wall surface of each flow path. Is suppressed. Therefore, the airflow flows smoothly and the energy saving property can be improved.

FIG. 6 shows the relationship between the airflow rate of the crossflow fan 7 and the input (power consumption) required by a fan drive motor (not shown) for driving the crossflow fan 7 when the airflow amount is transmitted. have. The vertical axis represents the input (unit: W) of the fan drive motor, and the horizontal axis represents the amount of air (unit: m 3 / minute) of the cross flow fan 7.

In the figure, K1 shows this embodiment and shows the case where the horizontal louvers 111, 112, 113 are arrange | positioned as shown in FIG. K2 shows the 4th Embodiment of FIG. 18 mentioned later in detail, and abbreviate | omits the horizontal louver 113 about this embodiment. K3 has shown the 5th Embodiment of FIG. 19 mentioned later in detail, In this embodiment, the horizontal louver 113 is abbreviate | omitted and the arrangement | positioning and shape of the horizontal louvers 111 and 112 are changed.

In addition, K4 has shown the 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 1D and 2.1D, respectively. This is the length of the upper wall 6b and the lower wall 6c which are usually formed in a conventional air conditioner. Moreover, the horizontal louvers 111 and 112 are arrange | positioned so that the flow path may be divided roughly equally, and the airflow will be introduced smoothly forward and upward.

By comparing K1 and K2, the effect by having arrange | positioned the horizontal louver 113 as shown in FIG. 5 can be grasped | ascertained. By comparing K2 and K3, the effect by the shape and arrangement | positioning of the horizontal louvers 111 and 112 can be grasped | ascertained. By comparing K1 and K4, the effect according to the length of the upper wall 6b and the lower wall 6c can be grasped.

According to Fig. 6, K1 to K3 can be driven with less input (power consumption) than the comparative example K4. Moreover, when the noise at the same air volume was compared with the case of K1 to K4, K1 became about 2 dB low noise for K4, K2 and K3 were equivalent to K1, and noise was larger than K1 at the error level.

8-11 is a figure explaining the difference of the power consumption of the crossflow fan 7 of this embodiment K1 and the comparative example K4. 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 of the airflow flowing through the inside of the indoor unit 1 at this time, with the vertical axis representing the static pressure of the airflow, and the horizontal axis representing the air flow direction.

When the cross flow fan 7 is driven, external air whose static pressure is equal to atmospheric pressure is sucked into the housing of the indoor unit 1 to generate airflow. The airflow flows through the intake port 4, the indoor heat exchanger 9, and the ventilation path 6, and when air flows through the indoor heat exchanger 9, the air is harmonized to become the harmonized air. At this time, pressure losses ΔPa, ΔPb, and ΔPc are generated by the air resistances of the intake port 4, the indoor heat exchanger 9, and the blowing path 6, respectively. As a result, the static pressure of the air flow decreases during the circulation of the air blowing path 6, resulting in atmospheric pressure-ΔPa-ΔPb-ΔPc. In addition, the pressure loss of the air filter 8 and other parts is abbreviate | omitted and demonstrated.

In addition, the air flow discharged from the blower outlet 5 generate | occur | produces the pressure loss (DELTA) Pd1 accompanying the airflow disturbance at the time of exiting the blower outlet 5. In other words, the airflows blown out from the jet port 5 suddenly disappear from the top, bottom, left and right wall surfaces of the blowing path 6 that existed until then, and are blown into the surrounding air. At that time, the kinetic energy is applied to the surrounding air by the viscosity of the air, causing the surrounding air to move slowly. Therefore, the airflow sent out from the jet port 5 loses kinetic energy to the surrounding air, and eventually reaches a static pressure equal to atmospheric pressure. Since this phenomenon takes place at once as the air flow is discharged from the jet port 5, the air flow in the vicinity of the jet port 5 is greatly disturbed and pressure loss accompanying it occurs.

For this reason, the crossflow fan 7 needs to raise the sum total ((DELTA) Pa + (DELTA) Pb + (DELTA) Pc + (DELTA) Pd1) of the static pressure drop by the said pressure loss at once. Therefore, the static pressure increase ΔP0 by the crossflow fan 7 should be equivalent to the sum of the static pressure decreases (ΔPa + ΔPb + ΔPc + ΔPd1).

The product (ΔP0 × Q) of the static pressure rise (ΔP0) and the amount of air flow (Q) passed through becomes the work of the crossflow fan (7). When the static pressure rise by the crossflow fan 7 is smaller than the sum of the static pressure drop (ΔP0 <ΔPa + ΔPb + ΔPc + ΔPd1), the crossflow fan 7 causes the desired airflow to flow to the indoor heat exchanger 9. Can't. Therefore, sufficient air conditioning cannot be performed.

On the other hand, the case of this embodiment K1 is shown to FIG. 10, FIG. 10 is a side 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 of the airflow flowing through the interior of the indoor unit 1 at this time, with the vertical axis representing the static pressure of the airflow, and the horizontal axis representing the blowing direction of the airflow. have.

When the cross flow fan 7 is driven, external air whose static pressure is equal to atmospheric pressure is sucked into the housing of the indoor unit 1 as described above, and airflow is generated. At this time, pressure losses ΔPa, ΔPb, and ΔPc are generated by the respective air resistances of the intake port 4, the indoor heat exchanger 9, and the blowing path 6. As a result, the static pressure of the air flow decreases during the circulation of the air blowing path 6, resulting in atmospheric pressure-ΔPa-ΔPb-ΔPc.

On the other hand, the pressure loss (DELTA) Pd2 of the air stream sent out from the blowing port 5 becomes smaller than the pressure loss (DELTA) Pd1 of the comparative example of FIG. That is, the airflow which passed the front guide part 6a smoothly follows the inclined surface 6b5 via the bend part 6b4. For this reason, like the comparative example, the quantity of kinetic energy deprived of the surrounding air is small without rapidly losing the kinetic energy to the surrounding air.

Moreover, since the whole airflow which flowed through the front guide part 6a follows the inclined surface 6b5 by the Coanda effect, the flowchart which follows the lower wall 6c of the ventilation path 6 is affected by this. For this reason, it spreads gradually into the surrounding air from the lower side of airflow, without spreading in one step, and becomes static pressure equal to atmospheric pressure. Therefore, the disturbance of the airflow in the vicinity of the jet port 5 is small, and the pressure loss ΔPd2 accompanying it is small.

Moreover, the flow path area is gradually enlarged by the front guide part 6a of the ventilation path 6, and the flow path area is gradually enlarged by the inclined surface 6b5 and the horizontal louver 113 after that. For this reason, the airflow flows smoothly along the inclined surface 6b5 even after passing through the front guide portion 6a while gradually expanding the basin area.

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 flowing through the lowermost horizontal louver 113 of the airflow sent out from the jet port 5 It gradually expands. Next, the flow path of the airflow which flows between the horizontal louvers 112 and 113 of the airflow sent out from the jet port 5 gradually expands. Next, the flow path of the airflow which flows between the horizontal louvers 111 and 112 of the airflow sent out from the blower outlet 5 gradually expands. Finally, the flow path of the airflow above the horizontal louver 111 which distributes the uppermost side of the airflow sent out from the jet port 5 gradually expands. Therefore, the airflow gradually and smoothly decreases the flow velocity from the lower side.

When the flow velocity of the airflow is smoothly lowered, the static pressure of the airflow increases by Bernoulli's equation known in the field of fluid mechanics. That is, the flow velocity (kinetic energy) of the air flow is converted into the static pressure (potential energy). Therefore, before the kinetic energy of the air stream sent out from the jet port 5 is taken into the surrounding air or disturbs the air stream, a part thereof is converted into a static pressure, thereby obtaining a positive pressure rise ΔP2.

Thereby, the crossflow fan 7 needs to raise the part which subtracted the static pressure rise (DELTA) P2 from the sum total ((DELTA) Pa + (DELTA) Pb + (DELTA) Pc + (DELTA) Pd2) of the static pressure drop by the said pressure loss at once. For this reason, the static pressure rise (DELTA) P1 by the crossflow fan 7 becomes (DELTA) Pa + (DELTA) Pb + (DELTA) Pc + (DELTA) Pd2-(DELTA) P2.

Therefore, compared with the static pressure rise (DELTA P0) required for the crossflow fan 7 in the comparative example (refer FIG. 8, FIG. 9), the required static pressure rise (DELTA) P1 becomes small by (DELTA) P2 + (DELTA) Pd1-(DELTA) Pd2. As a result, the work of the crossflow fan 7 becomes smaller by (ΔP2 + ΔPd1-ΔPd2) × Q, and thus the input (power consumption) of the fan drive motor can be reduced by this amount, and energy saving can be achieved.

That is, the pressure loss ΔPd2 in the vicinity of the jet port 5 can be made small, and at the same time, the air along the upper wall 6b and the lower wall 6c is decelerated to convert the kinetic energy into a static pressure, thereby increasing the static pressure ( The cross flow fan 7 is assisted by ΔP2. In other words, conventionally, the kinetic energy that has been deprived of the surrounding air is sufficiently recovered, converted into static pressure, and used for work for blowing air. Therefore, the static pressure rise by the crossflow fan 7 can be made small, and energy saving of an air conditioner can be aimed at.

Further, as described above, since the wind speed gradually decreases smoothly from the lower side of the air flow to the positive pressure, the loss in converting the flow rate (kinetic energy) of the air flow into the positive pressure (potential energy) is small. For this reason, the conversion efficiency which converts a flow velocity into a static pressure becomes very good, and it becomes possible to convert many kinetic energy into a static pressure.

Fig. 12 is a contour diagram showing the result 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 | shaft shows the length of the upper wall 6b, and it divides into the diameter D of the crossflow fan 7, and is dimensionless. The horizontal axis represents the length of the lower wall 6c, and is divided by the diameter D of the cross flow fan 7 to make it dimensionless. The air volume of the crossflow fan 7 is fixed at 16 m 3 / min. In the figure, K1 and K4 are the same conditions as the above-mentioned 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, since the length is extremely short and does not hold as a crossflow fan 7, measurement is abbreviate | omitted. In addition, since the measurement point of the figure of FIG. 12 is finite, the outline figure is completed using the interpolation and prediction of each measurement value.

As is apparent from Fig. 12, when the length of the upper wall 6b and the length of the lower wall 6c are increased, the power consumption of the cross flow fan 7 can be reduced. In addition, the value of power consumption suddenly changes 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 becomes 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, power consumption can be significantly reduced. As a result, the kinetic energy of the airflow continues to be converted to the static pressure until the speed of the airflow becomes sufficiently low, and the kinetic energy of the airflow can be sufficiently converted to the static pressure and recovered.

Fig. 13 is a contour diagram showing the result of examining the distance of arrival of the air flow (unit: m) along the ceiling surface by varying the lengths of the upper wall 6b and the lower wall 6c. Reach is made into the distance to the position where the average wind speed becomes 0.05 kPa for 30 seconds. As in Fig. 12, the vertical axis represents the length of the upper wall 6b, and is divided by the diameter D of the cross flow fan 7 to be dimensionless. The horizontal axis represents the length of the lower wall 6c, and is divided by the diameter D of the cross flow fan 7 to make it dimensionless. The air volume of the crossflow fan 7 is fixed at 16 m 3 / min. In the figure, K1 and K4 are the same conditions as the above-mentioned 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, since the length is extremely short and does not hold as a crossflow fan 7, measurement is abbreviate | omitted. In addition, since the measurement point of FIG. 13 is finite, the contour figure is completed using interpolation and prediction of each measurement value.

As is apparent from Fig. 13, the reach distance is less dependent on the length of the lower wall 6c and is greatly changed by the length of the upper wall 6b. That is, in order to extend the reach, it is effective to prevent the kinetic energy dissipating upward of the air flow and is greatly influenced by the length of the upper wall 6b.

Further, 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 jet port 5 induces the movement of the surrounding air by viscosity from immediately afterwards, and the kinetic energy of the airflow is gradually lost to the surrounding air. However, when the length of the upper wall 6b is 1.5D or more, since the upper wall 6b has a sufficient length, the movement of air in the upper direction of the airflow is abruptly reduced. As a result, the kinetic energy is not lost, and the airflow reaches far. In other words, even in the airflow after sufficiently recovering the kinetic energy, when the length of the upper wall 6b is 1.5D or more, the reach distance can be secured large.

When the airflow blown out from the crossflow fan 7 flows through the blowing path 6, the lower portion (near the lower wall 6c) is lower than the upper portion (near the upper wall 6b) near the ejection opening 5. . That is, in the vicinity of the jet port 5, the airflow which distribute | circulates the upper part of the blowing path 6 has a comparatively high density kinetic energy, and the airflow which distribute | circulates the lower part of the blowing path 6 has a comparatively low density kinetic energy. This phenomenon is a characteristic common to a normal crossflow fan.

If the kinetic energy is recovered from the air stream having a nonuniform energy density, only the kinetic energy recovery from the high velocity flow air stream having a relatively high density of kinetic energy proceeds. As a result, it becomes difficult to recover sufficient kinetic energy from the airflow having a slow flow rate having a relatively low density of kinetic energy.

That is, since the flow path of the airflow is gradually enlarged, the wind speed of the airflow is lowered and converted to static pressure. Therefore, when the flow path of the flow having a non-uniform wind speed distribution is enlarged, the airflow having the high wind speed first passes through the passage and is greatly reduced. As a result, the airflow with a slow wind speed becomes difficult to decelerate. As a result, the kinetic energy recovery efficiency from the entire air stream is lowered. For this reason, the kinetic energy may be recovered separately by dividing the air stream having a relatively high kinetic energy with a high flow velocity and the air stream having a relatively low density kinetic energy with a low flow velocity. As a result, the kinetic energy can be efficiently recovered from the entire air stream.

In addition, the slow-flowing airflow having a relatively low density of kinetic energy gradually loses kinetic energy in addition to the wall resistance, and the energy density gradually decreases. For this reason, it is necessary to recover the kinetic energy at the earliest possible stage. A slow-flowing air stream having a relatively low density of kinetic energy has a small amount of kinetic energy and thus can sufficiently recover kinetic energy at a relatively short distance. On the other hand, the air velocity having a high velocity of kinetic energy has a large kinetic energy and thus requires a relatively long distance 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, and the lower flow path may be relatively short, and the flow path may be sequentially lengthened toward the upper part. As a result, the kinetic energy can be efficiently recovered from the airflow having a nonuniform energy density peculiar to the crossflow fan 7. Therefore, in this embodiment, the ventilation paths 6 are divided into four vertically by the horizontal louvers 111, 112, and 113 at the time of the operation of the air conditioner 1. As shown in FIG.

That is, the uppermost flow path formed by the inclined portion 6b5 and the uppermost horizontal louver 111, the second-stage flow path formed by the uppermost horizontal louver 111 and the intermediate horizontal transverse louver 112, and the intermediate end The blowing path is formed by three flow paths formed by the horizontal louver 112 and the lowest horizontal louver 113 at the bottom, and the four flow paths at the lowest flow path formed by the lowest horizontal louver 113 and the lower wall 6c. Divided.

And as described above, the end 6b6 of the upper wall 6b from the front upward, the front end of the horizontal louver 111, the front end of the horizontal louver 112, the front end of the horizontal louver 113, the lower wall 6c ) Is arranged in the order of the end 6c4. Thereby, each divided flow path can be lengthened gradually as it goes upwards.

Further, it is more preferable that each of the angles θ1 to θ4 (see Fig. 5) representing the enlargement ratio of the flow path area of each flow path is in the range of 10 ° to 15 °. In other words, when the angles θ1 to θ4 are made larger than 15 °, the airflow flowing through each flow path is separated from the wall surface or rapidly decelerated, so that a loss is likely to occur when converting the kinetic energy into a static pressure. If the angles θ1 to θ4 are made smaller than 10 °, the path is unnecessarily extended, and the loss of kinetic energy due to friction between the air flow and the wall surface increases accordingly.

In addition, the magnitude of the kinetic energy of the air flow is proportional to the power of the flow rate. When the crossflow 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 flows through the lower part (near the lower wall 6c) of the blowing path 6. This is a multiple of the wind speed. For this reason, the kinetic energy of the airflow which flows through the upper part (near upper wall 6b) of the ventilation path 6 has the movement which the airflow which flows through the lower part (near the lower wall 6c) of the ventilation path 6 has. It can be tens of times more energy. The upper part of the blowing path 6 requires a sufficiently long flow path because the amount of kinetic energy to be recovered is very large.

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. If the angle α is more than that, the airflow flowing through the front guide portion 6a is separated from the wall surface or rapidly decelerates, resulting in energy loss. At this time, if the flow path is divided by the horizontal louvers and the flow path area is expanded in the range of 10 ° to 15 °, respectively, only two divisions are possible. As a result, it is very difficult to effectively recover the kinetic energy from the airflow in the energy state that is tens of times as different as described above.

For this reason, the horizontal end louver 112 of an intermediate | middle end is arrange | positioned behind back bend 6b4 opposite the bent part 6b4, and is arrange | positioned substantially parallel to the upper surface 6b3 of the front guide part 6a. Thereby, the flow path of the airflow which distributes the front guide part 6a is divided into two vertically. And the flow path below the horizontal louver 112 can be further divided into two by the horizontal louver 113 in the range of (theta) 3 and (theta) 4 from 10 degrees to 15 degrees.

In addition, the upper wall 6b is bent upward at the bent portion 6b4 opposite the horizontal louver 112. Thereby, the flow path of the airflow which distributes the upper direction of the horizontal louver 112 is expanded. And the gradually expanding flow path formed by the horizontal louver 112 and the inclined surface 6b5 is divided by the horizontal louver 111 of the uppermost stage. Since the rear end portion of the uppermost horizontal louver 111 faces the inclined surface 6b5 and is disposed ahead of the bent portion 6b4, the horizontal louvers 112 are positioned 10 ° by 10 ° by the horizontal louvers 111. It can be divided into two in the range of 15 °. In addition, it is not very efficient to bend the lower surface 6c3 of the front guide portion 6a downward so as to expand the same so that the wind speed is slow.

Further, when the rear end of the lowermost horizontal louver 113 and the lower surface 6c3 of the front guide portion 6a are disposed so as to overlap at a position close to the end portion 6c4 of the lower wall 6c in a direction perpendicular to the airflow More preferred. Thereby, kinetic energy can be collect | recovered more efficiently by the airflow which distribute | circulates the flow path below the horizontal louver 113. FIG.

In addition, since the horizontal louvers 111, 112, 113 are comprised so that rotation about the rotation axis (not shown) can be carried out, it can change a wind direction in another arrangement.

According to this embodiment, the sum of the length of the upper wall 6b and the length of the lower wall 6c of the blowing path 6 on the downstream side of the crossflow fan 7 is equal to the diameter D of the crossflow fan 7. Since it is set to 3.5 times or more, air flows smoothly through a long distance along the upper wall 6b and the lower wall 6c of the blowing path 6 during operation of the air conditioner. Thereby, the disturbance of the airflow in the vicinity of the jet port 5 is small, and the 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 it is sufficiently slow, and the kinetic energy is converted into a static pressure, and the positive pressure rise ΔP2 assists the cross flow fan 7. . In other words, conventionally, the kinetic energy that has been deprived of the surrounding air is sufficiently recovered, converted into static pressure, and used for work for blowing air. Therefore, the static pressure rise by the crossflow fan 7 can be made small, and energy saving of an air conditioner can be aimed at.

In addition, it is possible to recover the kinetic energy and lengthen the reach of the airflow whose flow velocity is reduced. As a result, the air blown out from the jet port 5 reaches the ceiling of the room, and moves on the wall surface facing the air conditioner, the bottom surface, and the wall surface on the air conditioner side in order. Therefore, the airflow of the roughened air reaches all corners of the room, and the airflow stirs the entire room greatly. Therefore, it is possible to obtain a comfortable space with almost no direct wind by uniformizing the temperature distribution of the entire living area except for a part of the upper part of the room.

In addition, the cross flow fan 7 generally causes surging when the pressure loss of the flow path becomes high. As a result, a case in which the desired air volume cannot be obtained or a noise greatly increases. When the indoor heat exchanger 9 is configured to bend with a plurality of stages and a plurality of rows of refrigerant tubes as in the present embodiment, very high pressure loss occurs. For this reason, it is necessary to prepare the countermeasure of surging by making the rotation speed of the crossflow fan 7 considerably large. Thereby, the noise of the crossflow fan 7 becomes large and energy saving property worsens.

For this reason, by converting the kinetic energy of airflow into static pressure and assisting the crossflow fan 7 by the static pressure rise, the crossflow fan 7 is less likely to cause surging and the noise can be made relatively low. In particular, when four or more rows of coolant tubes are provided in one direction, the pressure loss becomes very large, and according to the present embodiment, a greater effect can be obtained.

<2nd embodiment>

Next, Fig. 14 is a side end view showing the indoor unit of the air conditioner of the second embodiment. For convenience of explanation, the same reference numerals are given to the same parts as in the first embodiment shown in FIGS. 1 to 13 described above. In this embodiment, the front panel 3 is pivotally supported at the lower end by the rotation shaft 22. Moreover, the front panel 3 is bendable by the rotating shaft 23 arrange | positioned at the front surface. The other part is the same as that of 1st Embodiment.

When the air conditioner is stopped, the front panel 3 is disposed so that the upper end portion is in contact with the upper part of the housing, as shown in FIG. In addition, the jet port 5 is shielded by the horizontal louvers 111 and 112 similarly to the first embodiment.

When the air conditioner is driven, as shown in FIG. 15, the front panel 3 rotates on the rotation shafts 22 and 23, and the blowing path 6 is driven by the front panel 3 between the rotation shafts 22 and 23. As shown in FIG. Of the inclined surface 6b5 is formed. Thereby, the diameter of the crossflow fan 7 is set to D, and the length of the upper wall 6b of the air flow path 6 downstream from the crossflow fan 7 is 1.5D or more. In addition, the sum of the length of the upper wall 6b and the length of the lower wall 6c of the blowing path 6 downstream from the crossflow fan 7 is formed to be 3.5D or more. Therefore, the same effects as in the first embodiment can be obtained.

Third Embodiment

Next, Fig. 16 is a side sectional view showing the indoor unit of the air conditioner of the third embodiment. For convenience of explanation, the same reference numerals are given to the same parts as in the first embodiment shown in FIGS. 1 to 13 described above. In this embodiment, the lower part of the front panel 3 is opened, and the movable panel 21 which closes the said opening is pivotally supported by the lower end part by the rotating shaft 22. As shown in FIG. The other part is the same as that of 1st Embodiment.

When the air conditioner is stopped, the movable panel 21 is arranged to close the lower part of the front panel 3 as shown in FIG. In addition, the jet port 5 is shielded by the horizontal louvers 111 and 112 similarly to the first embodiment.

When the air conditioner is driven, as shown in Fig. 17, the movable panel 21 rotates on the rotary shaft 22, and the inclined surface 6b5 of the blowing path 6 is formed by the movable panel 21. As shown in FIG. Thereby, the diameter of the crossflow fan 7 is set to D, and the length of the upper wall 6b of the air flow path 6 downstream from the crossflow fan 7 is 1.5D or more. In addition, the sum of the length of the upper wall 6b and the length of the lower wall 6c of the blowing path 6 downstream from the crossflow fan 7 is formed to be 3.5D or more. Therefore, the same effects as in the first embodiment can be obtained.

&Lt; Fourth Embodiment &

Next, FIG. 18 is a side sectional view showing the indoor unit of the air conditioner of the fourth embodiment. The same reference numerals are attached to the same parts as the first embodiment shown in Figs. 1 to 13 described above. In this embodiment, the horizontal louver 113 of the first embodiment is omitted as described above. The other part including the lengths of the upper wall 6b and the lower wall 6c of the ventilation path 6 is the same as in the first embodiment.

According to the air conditioner of this embodiment, since the lowermost horizontal louver 113 is omitted compared with the air conditioner of the first embodiment, the efficiency of the recovery of the kinetic energy of the airflow flowing down the blowing path 6 slightly decreases. . However, as shown in K2 of FIG. 6 described above, power consumption can be made smaller than that of Comparative Example K4 of FIG. 7, and energy saving can be achieved compared with the prior art.

&Lt; Embodiment 5 >

Next, Fig. 19 is a side sectional view showing the indoor unit of the air conditioner of the fifth embodiment. The same reference numerals are attached to the same parts as the first embodiment shown in Figs. 1 to 13 described above. In the present embodiment, as described above, the horizontal louver 113 of the first embodiment is omitted, and the length and arrangement of the horizontal louvers 111 and 112 are changed. The other part including the lengths of the upper wall 6b and the lower wall 6c of the ventilation path 6 is the same as in the first embodiment.

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

According to the air conditioner of this embodiment, compared with the air conditioner of 1st, 2nd embodiment, the efficiency of collection | recovery of the kinetic energy of the airflow which flows through the inside of the ventilation path 6 falls. However, as shown in K3 of FIG. 6 mentioned above, power consumption can be made smaller than the comparative example K4 of FIG. 7, and energy saving can be aimed at compared with the former.

Although the air conditioner which concerns on this invention was demonstrated by 1st-5th embodiment, this invention is not limited to the said embodiment, It can implement by making a suitable change in the range which does not deviate from the meaning of this invention.

According to this invention, it can use for the air conditioner which introduces and harmonizes indoor air.

Claims (16)

An inlet for introducing indoor air into the housing of the indoor unit, a blower provided in the lower part of the housing, a blower path for communicating between the inlet and the blower, a plurality of stages and a plurality of coolant tubes, and an inner surface of the housing. An air conditioner having an indoor heat exchanger, which is bent along the suction port in the blower path, and a crossflow fan disposed between the indoor heat exchanger and the blower outlet in the blower path, A first wind direction plate provided to face the upper wall of said blowing path downstream from said cross flow fan, and varying the wind direction of said jet port up and down; It is provided below a 1st wind direction plate, and is provided with the 2nd wind direction plate which changes the wind direction of the said blower opening up and down, The blowing path has a front guide portion that guides the air downward in the forward direction to expand the flow path area toward the downstream, The sum of the length of the upper wall and the lower wall of the blowing path on the downstream side of the crossflow fan is not less than 3.5 times the diameter of the crossflow fan, and the length of the upper wall is the diameter of the crossflow fan. More than 1.5 times The upper wall has an inclined surface that is bent from the end portion of the upper surface of the front guide portion inclined forward downward and inclined upwardly, When the air is blown out upward from the blower port, the first wind direction plate has a front end behind the front end of the upper wall and is disposed ahead of the front end of the second wind direction plate, and the rear end is ahead of the curved portion. The second wind direction plate is disposed at the rear end portion of the second wind direction opposite to the curved portion, First and second wind direction plates are disposed such that the flow path of the air flows flowing between the upper wall and the first wind direction plate and the flow path of the air flows flowing between the first wind direction plate and the second wind direction plate gradually expand toward the downstream. Air conditioner, characterized in that. According to claim 1, At least one plane is provided in the bent portion and connecting the ends of the plane to each smooth surface, while the angle between the upper surface of the front guide portion and the plane and the angle between the plane and the inclined surface is An air conditioner, characterized in that formed below 17 °. The air conditioner according to claim 1, wherein 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 °. The third wind direction plate is provided below the second wind direction plate, and the rear end portion of the third wind direction plate is disposed in front of the rear end portion of the second wind direction plate, and the second and third wind direction plates are An air conditioner comprising an angle of 10 ° to 15 °. 4. The rear end of the wind direction plate disposed at the lowermost portion and the lower surface of the front guide portion are disposed so as to overlap at a position close to the end of the lower wall of the front guide portion in a direction perpendicular to the air flow. And an angle formed by a tangential line of the wind direction plate disposed in the end portion of the front wall of the front guide portion is 10 ° to 15 °. An inlet for introducing indoor air into the housing of the indoor unit, a blower provided in the lower part of the housing, a blower path for communicating between the inlet and the blower, a plurality of stages and a plurality of coolant tubes, and an inner surface of the housing. An air conditioner having an indoor heat exchanger, which is bent along the suction port in the blower path, and a crossflow fan disposed between the indoor heat exchanger and the blower outlet in the blower path, A first wind direction plate provided to face the upper wall of said blowing path downstream from said cross flow fan, and varying the wind direction of said jet port up and down; It is provided below a 1st wind direction plate, and is provided with the 2nd wind direction plate which changes the wind direction of the said blower opening up and down, The blowing path has a front guide portion that guides the air downward from the cross flow fan to the front and downwards, and the flow path area is enlarged toward the downstream. The length of the upper wall of the blowing path downstream of the cross flow fan is 1.5 times or more of the diameter of the cross flow fan, and the upper wall is bent from the end of the front guide portion at the bent portion to be tilted upward upward. Have a photographic slope, At least one plane is provided at the bent portion and the ends of the plane are connected to each other by a smooth curved surface, and the angle formed between the top surface of the front guide portion and the plane and the angle formed by the plane and the inclined surface are 17 ° or less. , When the air is blown out upward from the blower port, the first wind direction plate has a front end behind the front end of the upper wall and is disposed ahead of the front end of the second wind direction plate, and the rear end is ahead of the curved portion. The second wind direction plate is disposed at the rear end portion of the second wind direction opposite to the curved portion, First and second wind direction plates are disposed such that the flow path of the air flows flowing between the upper wall and the first wind direction plate and the flow path of the air flows flowing between the first wind direction plate and the second wind direction plate gradually expand toward the downstream. Air conditioner, characterized in that. The air conditioner according to claim 6, wherein 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 °. The 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, and the second and third wind direction plates are formed. An air conditioner comprising an angle of 10 ° to 15 °. 8. The rear end of the wind direction plate disposed at the lowermost portion and the lower surface of the front guide portion are arranged so as to overlap at a position close to the end of the lower wall of the front guide portion in a direction perpendicular to the airflow. And an angle formed by a tangential line of the wind direction plate disposed in the end portion of the front wall of the front guide portion is 10 ° to 15 °. delete delete delete delete delete delete delete

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