WO2007083501A1

WO2007083501A1 - Air conditioner

Info

Publication number: WO2007083501A1
Application number: PCT/JP2006/326032
Authority: WO
Inventors: Masaki Ohtsuka
Original assignee: Sharp Kabushiki Kaisha
Priority date: 2006-01-20
Filing date: 2006-12-27
Publication date: 2007-07-26
Also published as: EP1975522B1; EP1975522A1; KR20080077699A; EP1975522A4; KR100971855B1

Abstract

An air conditioner comprises an air intake port (4) for introducing the air in a room into the casing of an indoor machine (1), an air discharge port (5) formed at the lower part of the casing, an air flow path (6) for communicating the air intake port (4) with the air discharge port (5), an indoor heat exchanger (9) having refrigerant tubes arranged in a plurality of stages and rows parallel with each other and disposed curvedly along the inner surface of the casing so as to face the air intake port (4), and a cross flow fan (7) disposed between the indoor heat exchanger (9) in the air flow path (6) and the air discharge port (5). The air flow path (6) includes a forward guide part (6a) which guides the air to the forward lower side and is gradually increased in its flow passage area toward the downstream side. The sum of the lengths of the upper wall (6b) and the lower wall (6c) of the air flow path (6) closer to the downstream side than the cross flow fan (7) is set to 3.5 times the diameter of the cross flow fan (7) or more.

Description

Specification

Air conditioner

Technical field

TECHNICAL FIELD [0001] The present invention relates to an air conditioner that harmonizes air taken from a room and sends the air into the room.

Background art

Conventional air conditioners are disclosed in Patent Documents 1 and 2. The air conditioner of Patent Document 1 improves the thickness distribution of the blades of the air supply fan and reduces the pressure loss of the blower fan. As a result, energy conservation of the air conditioner is achieved. The air conditioner of Patent Document 2 has a movable panel that closes the suction port provided on the front surface of the casing 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. As a result, the pressure loss at the time of suction is reduced, and energy saving of the air conditioner is achieved.

Patent Document 1: Japanese Patent Laid-Open No. 2003-028089

Patent Document 2: Japanese Patent Laid-Open No. 2000-111082

Disclosure of the invention

Problems to be solved by the invention

[0003] In recent years, the preservation of the global environment has been screamed, and further energy saving of so-called white goods is strongly desired. However, according to the above-described conventional air conditioner, the conditioned air is vigorously sent from the air outlet into the indoor air. At this time, the wall surface of the existing passage 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 as soon as the air flow is sent out, and the air flow near the air outlet is greatly disturbed, resulting in a pressure loss. Therefore, there has been a problem that energy saving of the air conditioner cannot be sufficiently achieved.

[0004] An object of the present invention is to provide an air conditioner that can further save energy.

Means for solving the problem 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 a space between the air inlet and the air outlet. A ventilation path to be communicated; an indoor heat exchanger in which refrigerant tubes 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 including a cross flow fan disposed between the indoor heat exchanger and the air outlet in the path, the air flow path guides the air forward and downward and flows toward the downstream. It has a front guide that enlarges the road area, and the sum of the length of the upper and lower walls of the air flow path downstream of the cross flow fan is 3.5 times the diameter of the cross flow fan. It is characterized by the above.

[0006] According to this configuration, the air in the suction loca chamber is taken into the housing by the drive of the cross flow fan and flows through the air blowing path. The air is harmonized by heat exchange with indoor heat exchange with 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 through the front guide part along the upper and lower walls of the air flow path on the exhaust side of the cross-flow fan through the front guide, and is sent out from the outlet. At this time, the airflow along the upper and lower walls of the ventilation path is gradually decelerated, and the kinetic energy is converted to static pressure and recovered as static pressure.

[0007] Further, the present invention provides the air conditioner configured as described above, further comprising a first wind direction plate that can change a wind direction of the air outlet up and down, and a front end of the upper wall from the front upper side during operation of the air conditioner. 1 It is characterized by arrange | positioning in order of the front end of the wind direction board, and the front end of the said lower wall. According to this configuration, the kinetic energy of the airflow flowing through the air blowing path is collected sequentially from the lower side of the flow velocity.

[0008] Further, according to the present invention, in the air conditioner configured as described above, a second wind direction plate is provided below the first wind direction plate, and a front end of the first wind direction plate is disposed forward of a front end of the second wind direction plate. It features.

[0009] In the air conditioner having the above-described configuration, the present invention further includes first and second wind direction plates that are variable above and below the air outlet, and the upper wall is bent at a bent portion from an end of the upper surface of the front guide portion. And the rear end of the first wind direction plate is disposed in front of the bent portion, and the rear end of the second wind direction plate below the first wind direction plate is the front end. Than the bent part It is characterized by being arranged at the rear.

[0010] 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 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 to static pressure by the flow path formed between the second wind direction plate and the first wind direction plate. The kinetic energy of the upper air stream bent by the second wind direction plate is recovered by being converted into static pressure by the flow path formed between the first wind direction plate and the inclined surface.

[0011] In the air conditioner having the above-described configuration, the present invention is characterized in that 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 °. Yes. According to this configuration, the airflow smoothly flows along the wall surface without being separated from the wall surface formed by the inclined surfaces of the first and second wind direction plates and the air flow path.

[0012] Further, 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 an angle formed by the second and third wind direction plates is set to 10 ° to 15 °. It is a feature. According to this configuration, the air flow smoothly flows along the wall surface without peeling off the wall force that is also the second and third wind direction plate force.

[0013] Further, according to the present invention, in the air conditioner having the above-described configuration, an angle formed between the wind direction plate disposed at the lowermost position and the tangent at the end of the lower wall of the front guide portion is set to 10 ° to 15 °. It features. According to this configuration, the airflow smoothly flows along the wall surface without peeling off the wall surface force, which is the lowest wind direction plate force.

[0014] In the air conditioner configured as described above, the present invention is characterized in that the length of the upper wall is 1.5 times or more the diameter of the cross-flow fan.

[0015] Further, the present invention is a suction port for taking indoor air into the housing of the indoor unit, a blowout port provided in the lower portion of the housing, a ventilation path that communicates between the suction port and the blowout port, An indoor heat exchanger in which refrigerant tubes are arranged in a plurality of rows and in a plurality of rows and bent along the inner surface of the housing and disposed opposite to the suction port in the air supply path, and the indoors in the air supply path In an air conditioner including a cross-flow fan disposed between a heat exchanger ^^ and the air outlet, and first and second air direction plates that change the air direction of the air outlet up and down, The path is a flow path surface as it guides air forward and downward from the cross flow fan and goes downstream. A front guide portion having an enlarged product, and 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 wall has an inclined surface that is bent at the terminal force bending portion of the front guide portion and is inclined forward and upward, and the rear end of the first wind direction plate is disposed in front of the bent portion, and the first wind direction plate Further, the rear end of the second wind direction plate below is arranged behind the bent portion.

[0016] According to this configuration, the air in the suction loca chamber is taken into the housing by the driving of the cross flow fan and flows through the air blowing path. The air is harmonized by heat exchange with indoor heat exchange with a large pressure loss arranged in a plurality of rows in the vertical direction and in a plurality of rows in the front and rear by meandering the refrigerant pipe. The conditioned air circulates in the front guide section while expanding the flow path area along the upper and lower walls of the air flow path of the cross flow fan. The airflow flowing along the upper wall of the ventilation path is bent by the second wind direction changing plate and flows forward and upward along the inclined surface. The lower airflow bent by the second wind direction change plate is gradually decelerated by the flow path formed between the second wind direction change plate and the first wind direction change plate, and the kinetic energy is converted to static pressure and Recovered as pressure. The upper airflow bent by the second wind direction change plate is gradually decelerated by the flow path formed between the first wind direction change plate and the inclined surface, and the kinetic energy is converted to static pressure and recovered as static pressure. Is done.

[0017] Further, in the air conditioner having the above-described configuration, the present invention is characterized in that 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 10 ° to 15 °. Yes.

[0018] Further, in the air conditioner having the above-described configuration, the present invention includes a third wind direction plate provided below the second wind direction plate, and an angle formed by the second and third wind direction plates is set to 10 ° to 15 °. It is a feature.

[0019] Further, according to the present invention, in the air conditioner having the above-described configuration, an angle formed between the wind direction plate disposed at the lowermost position and the tangent at the end of the lower wall of the front guide portion is set to 10 ° to 15 °. It features.

[0020] In the air conditioner having the above-described configuration, the present invention provides a front end of the upper wall, a front end of the first wind direction plate, a front end of the second wind direction plate, and a front end of the lower wall when the air conditioner is operated. They are arranged in the order of the front edge. According to this configuration, the kinetic energy of the airflow flowing through the blower path is sequentially recovered in the downward force with the slow flow rate. [0021] Further, the present invention is a suction port for taking indoor air into the housing of the indoor unit, a blower outlet provided in the lower part of the housing, a blower path that communicates between the suction port and the blower outlet, An indoor heat exchanger disposed opposite to the suction port in the air passage, and a cross flow fan disposed between the indoor heat exchanger ^^ in the air passage and the outlet. It is characterized in that 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.

[0022] According to this configuration, the air inside the suction loca is also taken into the housing by the driving of the cross flow fan, and flows through the ventilation path. The air is harmonized by heat exchange with the indoor heat exchange, and the conditioned air flows from the exhaust side of the cross flow fan along the upper and lower walls of the air flow path and is sent out from the outlet. At this time, the airflow along the upper and lower walls of the air flow path is gradually decelerated, and the kinetic energy is converted to static pressure and recovered as static pressure.

[0023] Further, the present invention provides a suction port for taking indoor air into the housing of the indoor unit, a blowout port provided in a lower portion of the housing, a blower path communicating between the suction port and the blowout port, An indoor heat exchanger disposed opposite to the suction port in the air passage, and a cross flow fan disposed between the indoor heat exchanger ^^ in the air passage and the outlet. It is characterized in that the sum of the length of the upper wall and 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.

[0024] According to this configuration, the air inside the suction loci chamber is taken into the housing by the driving of the cross flow fan and flows through the air blowing path. The air is harmonized by heat exchange with the indoor heat exchange, and the conditioned air flows from the exhaust side of the cross flow fan along the upper and lower walls of the air flow path and is sent out from the outlet. At this time, the airflow along the upper and lower walls of the air flow path is gradually decelerated, and the kinetic energy is converted to static pressure and recovered as static pressure.

The invention's effect

[0025] According to the present invention, since 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 3.5 times or more the diameter of the cross flow fan, the air conditioner During operation, air flows smoothly along the upper and lower walls of the air flow path over a long distance. As a result, there is less air flow disturbance near the outlet, and the pressure loss associated with it is reduced. The kinetic energy is reduced by decelerating until the air along the long upper and lower walls is sufficiently slow. Converted to pressure. Therefore, the kinetic energy of the airflow can be sufficiently recovered to reduce the static pressure rise by the cross flow fan, and the energy saving of the air conditioner can be achieved.

[0026] In addition, because the indoor heat exchangers ^ are arranged in multiple rows and multiple stages, even when using an indoor heat exchanger with large pressure loss, the kinetic energy of the airflow is sufficiently recovered to save energy in the air conditioner. Can be planned. Since the front guide portion is provided in which the flow area is increased as the air is guided to the lower front side and goes downstream, the airflow can be gradually decelerated to sufficiently recover the motion energy.

[0027] Further, according to the present invention, 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 during operation of the air conditioner, the low-density motion energy having a low lower flow velocity is arranged. The rugged force can be recovered in order to efficiently recover the kinetic energy of the airflow.

[0028] 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 the power of density kinetic energy in order.

[0029] According to the present 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 below the first wind direction plate. Since the rear end of the plate is disposed behind the bent portion, the airflow can be bent along the inclined surface by the second wind direction plate. In addition, the kinetic energy of the air flow can be efficiently recovered by recovering in order from the low-density kinetic energy having a low downward flow velocity.

[0030] 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 °. The flow path between the first and second wind direction plates is continuously expanded, and the air flow smoothly flows along the wall surface without peeling off the wall force. As a result, the kinetic energy of the airflow can be smoothly converted to static pressure, and the kinetic energy can be recovered efficiently.

[0031] Further, according to the present invention, since the angle formed by the second wind direction plate and the third wind direction plate below the second wind direction plate is 10 ° to 15 °, the flow between the second and third wind direction plates is The channel is continuously expanded, and the airflow smoothly flows along the wall without peeling off the wall. This allows the kinetic energy to be efficiently recovered by converting the kinetic energy of the airflow into static pressure smoothly. wear.

[0032] Further, according to the present invention, since the angle formed between the wind direction plate disposed at the lowermost position and the tangent at the end of the lower wall is set to 10 ° to 15 °, the lowermost wind direction plate and the lower wall of the air flow path The channel between the two is continuously expanded, and the airflow smoothly flows along the wall without peeling off the wall force. As a result, the kinetic energy of the airflow can be smoothly converted to static pressure, and the kinetic energy can be efficiently recovered.

[0033] Further, according to the present invention, 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. It smoothly circulates a long distance along the upper wall of the ventilation path. As a result, there is less air flow disturbance in the vicinity of the air outlet, and the associated pressure loss is reduced. The kinetic energy is converted into static pressure by decelerating until the air along the long upper and lower walls becomes sufficiently slow, with a force tl. Accordingly, the kinetic energy of the airflow can be sufficiently recovered to reduce the static pressure rise by the cross flow fan, and the energy saving of the air conditioner can be achieved.

[0034] Further, the kinetic energy can be recovered to increase the reach distance of the airflow with a reduced flow velocity. As a result, the air sent out from the outlet also reaches the ceiling of the room and sequentially travels through the wall facing the air conditioner, the floor, and the wall on the air conditioner side. Therefore, the conditioned air stream reaches every corner of the room, and the air stream greatly stirs the entire room. Therefore, it is possible to obtain a comfortable space with almost no direct wind by equalizing the temperature distribution of the entire living area except for a part above the room.

[0035] In addition, since the indoor heat exchanger is composed of a plurality of rows and stages, even when an indoor heat exchanger with a large pressure loss is used, the kinetic energy of the airflow is sufficiently recovered to save energy of the air conditioner. Can be planned. Since the front guide portion is provided in which the flow area is increased as the air is guided to the lower front side and goes downstream, the airflow can be gradually decelerated to sufficiently recover the motion energy.

[0036] Further, 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 rear end of the second wind direction plate below the first wind direction plate. Is disposed behind the bent portion, the airflow can be bent along the inclined surface by the second wind direction plate. In addition, the kinetic energy of the airflow is recovered by recovering in order from the lower flow velocity! Lugie can be collected efficiently.

[0037] According to the present invention, since 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 are arranged in this order from the front upper side during operation of the air conditioner, the lower flow velocity The kinetic energy of the airflow can be efficiently recovered by recovering in order of slow kinetic energy power.

Brief Description of Drawings

FIG. 1 is a side cross-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 cross-sectional view showing details of a ventilation path of the indoor unit of the air conditioner according to the first embodiment of the present invention.

FIG. 3 is a side cross-sectional view showing details of a bent portion of a ventilation path of the indoor unit of the air conditioner according to the first embodiment of the present invention.

FIG. 4 is a side cross-sectional view showing a state when the operation of the indoor unit of the air conditioner according to the first embodiment of the present invention is stopped.

FIG. 5 is a side sectional view showing details of the vicinity of the air outlet 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 volume of the cross flow fan of the indoor unit of the air conditioner according to 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 the indoor unit of the air conditioner of the first embodiment of the present invention. FIG. 8 is a static pressure of the comparative example of the indoor unit of the air conditioner of the first embodiment of the present invention. Figure explaining the transition of

FIG. 9 is a graph showing changes in static pressure of a comparative example of the indoor unit of the air conditioner according to the first embodiment of the present invention.

FIG. 10 is a diagram for explaining the transition of the static pressure of the air conditioner indoor unit according to the first embodiment of the present invention. FIG. 11 is the transition of the static pressure of the air conditioner indoor unit of the first embodiment of the present invention. Figure showing

FIG. 12 is a diagram showing the relationship between the length of the upper wall, the length of the lower wall, and the power consumption of the cross flow fan of the indoor unit of the air conditioner according to the first embodiment of the present invention.

FIG. 13 shows the length of the upper wall of the air flow path of the indoor unit of the air conditioner according to the first embodiment of the present invention. Diagram showing the relationship between wall length and crossflow fan airflow reach

FIG. 14 is a side cross-sectional view showing a state when the operation of the indoor unit of the air conditioner of the second embodiment of the present invention is stopped.

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

FIG. 16 is a side cross-sectional view showing a state when the operation of the indoor unit of the air conditioner according to the third embodiment of the present invention is stopped.

FIG. 17 is a side sectional view showing a state during operation of the indoor unit of the air conditioner according to 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 according to the fourth embodiment of the present invention.

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

Explanation of symbols

1 Indoor unit

2 Cabinet

3 Front panel

4 Suction port

5 Air outlet

6 Air flow path

6a Front guide

6b upper wall

6b 5 inclined surface

6c lower wall

7 Cross flow fan

8 Airfinoleta

9 Indoor heat exchanger

10, 13 Drain pan 111, 112, 113 Horizontal Luno

12 Vertical louver

21 Movable panel

22, 23 Rotating shaft

61 Temperature sensor

BEST MODE FOR CARRYING OUT THE INVENTION

[0040] <First embodiment>

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a side sectional view showing the indoor unit of the air conditioner of the first 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. The cabinet of indoor unit 1 is composed of cabinet 2 and front panel 3.

[0041] 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 of the front panel 3 and the lower end 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.

[0042] Inside the casing of the indoor unit 1, a blower path 6 that connects the suction port 4 and the blowout port 5 is formed. A cross flow fan 7 for sending air is disposed in the air blowing path 6. The air 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. 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 increases as it goes 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 6b of the air flow path 6 has a stabilizer portion 6b7 along the peripheral surface of the cross flow fan 7. The stabilizer portion 6b7 is formed extending 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.

[0044] The upper surface 6b3 of the front guide portion 6a is inclined forward and downward. End of upper surface 6b3 of front guide 6a An inclined surface 6b5 that is bent upward through the bent portion 6b4 and inclined forward and upward is formed. The bend 6b4 is a gentle and smooth curved surface.

The lower wall 6c of the air flow path 6 has a rear guider part 6c5 along the peripheral surface of the cross flow fan 7. The rear guider portion 6c5 is formed to extend 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 end force of the rear guider portion 6c5 and the lower surface 6c3 of the front guide portion 6a.

[0046] The 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 between the slope 6b5 and the horizontal plane is about 20 °. An angle γ formed by the upper surface 6b3 of the front guide portion 6a and the horizontal plane is 5 °. Therefore, the angle (β + y) formed by the upper surface 6 b3 of the front guide portion 6a and the inclined surface 6b5 is 25 °. It is desirable to form the squares j8 and γ at about 15 ° to 20 °, 30 ° or less, and about 0 ° to 10 °, respectively.

[0047] When the angle (j8 + γ) is 17 ° or less, the air along the wall surface of the flow path can be circulated with a small pressure loss to the sliding force without peeling off the wall surface force. However, the angle (+ γ) is larger than 17 ° in order to divide the flow path into a plurality of parts by the horizontal louvers 111, 112, 113 as described later. For this reason, the middle horizontal louver 112 is disposed opposite to the bent portion 6b4 to suppress separation of the airflow.

[0048] 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 05 formed by the upper surface 6b3 of the front guide portion 6a and the plane 6f and an angle 06 formed by the plane 6f and the inclined surface 6b5 are formed to be 17 ° or less. If there are multiple planes 6f, the angles formed by the planes are all less than 17 °. Thereby, the air along the wall surface of the flow path can be smoothly circulated with a small pressure loss without peeling off the wall surface force. Therefore, energy saving can be improved.

[0049] 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 formed to be 1.9D and 2.1D, where the diameter of the cross flow fan 7 is D, respectively. Has been. The ends 6b 1 and 6c 1 of the stabilizer part 6b7 and the rear guider part 6c5 are provided in the vicinity of the diameter direction perpendicular to the exhaust direction of the cross flow fan 7, and V is the starting point of the upper wall 6b and the lower wall 6c. . When the stabilizer 6b7 and the rear guider part 6c5 are formed to extend to the intake side of the crossflow fan 7, the front gear that minimizes the distance to the crossflow fan 7 is used. The part 6b2 and the rear gap 6c2 may be the starting points of the upper wall 6b and the lower wall 6c.

[0050] The front end of the inclined surface 6b5 abuts on the lower end of the front panel 3 to form the end 6b6 of the upper wall 6b. The front end of the lower surface 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, 6c 4 may be referred to as the end of the lower wall 6c.) ₀ Note that 98 indicates the tangent at the end 6b4 of the lower surface 6c3 of the front guide portion 6a. And

In FIG. 1, the front guide portion 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 blowout angle in the vertical direction to the upper front, the horizontal direction, the lower front, and the right lower direction. An air filter 8 is provided at a position opposite to the front panel 3 to collect and remove dust contained in the air sucked from the suction port 4! /. 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.

[0052] Between the crossflow fan 7 and the air filter 8 in the air passage 6, an indoor heat exchanger 9 is disposed. The indoor heat exchanger 9 has meandering refrigerant pipes (not shown) arranged in a plurality of rows in the vertical direction and in a plurality of rows 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. During the cooling operation, the indoor heat exchanger 9 is cooled to a temperature lower than the ambient temperature 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.

[0053] 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 control unit (not shown) for controlling 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 at the bottom before and after indoor heat exchange.

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 blowing 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. This 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. As a result, the aesthetics of the indoor unit 1 are not impaired.

[0055] Condensation preventing means is provided on the side of the upper wall 6b that does not face the air passage 6. As a means for preventing condensation, the upper wall 6b may be formed of a heat insulating material, and 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 condensation occurs on the side of the upper wall 6b that does not face the air supply path 6, the condensed water is guided to the drain pan 10. Therefore, it is possible to obtain a highly reliable air conditioner without problems caused by condensed water.

[0056] 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, refrigerant from the outdoor unit (not shown) flows into the indoor heat exchanger 9, and the refrigeration cycle is operated. As a result, 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. In addition, the air taken into the indoor unit 1 is cooled by exchanging heat with the indoor heat exchanger 9.

[0057] 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, as shown by an arrow E along the inclined surface 6b5. Are sent out indoors toward the upper front. As a result, the indoor unit 1 is in a state of blowing forward and upward, which sends conditioned air upward and upward.

The conditioned air sent from the outlet 5 along the inclined surface 6b5 forward and upward into the room reaches the ceiling surface S (see FIG. 2) of the room. Thereafter, the coanda effect causes the indoor unit 1 to be sucked from the ceiling surface S through the side wall facing the indoor unit 1, the floor, and the side wall W1 on the indoor unit 1 side.

[0059] By doing so, the user is not always exposed to the cold wind or the warm wind directly. 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. Also, since the air flow greatly stirs the entire room, the temperature distribution in the room is uniform around the set temperature. That is, except for the upper part of the room, the entire living area of the user Therefore, it is possible to obtain a comfortable space where 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. Be placed.

[0061] Further, the horizontal louver 111 is arranged so that the angle 01 between the inclined surface 6b5 and the uppermost horizontal louver 111 is 13 °. The horizontal louver 112 is arranged so that an angle Θ 2 formed by the uppermost horizontal louver 111 and the middle horizontal louver 112 is 10 °. The horizontal louver 113 is arranged so that the angle Θ 3 formed by the middle horizontal louver 112 and the lowermost horizontal louver 113 is 10 °. In addition, the angle 04 between the lowermost horizontal louver 113 and the tangent line 98 is 12 °.

[0062] Since the horizontal louvers 111, 112, and 113 are arranged so that the angles 0 1 to 0 4 are equal to or less than 17 °, the airflow in the flow path divided by the horizontal louvers 111, 112, and 113 Separation of wall force is minimized. Therefore, it is possible to improve the energy saving property by smoothly flowing the airflow.

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

[0064] In the drawing, K1 represents the present embodiment, and shows a case where horizontal lateral Lunos 111, 112, and 113 are arranged as shown in FIG. K2 shows a fourth embodiment shown in FIG. 18 whose details will be described later, and the lateral louver 113 is omitted from this embodiment. K3 shows a fifth embodiment of 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.

[0065] K4 represents a comparative example of FIG. In the comparative example, the lateral louver 113 is omitted, and the lengths of the upper wall 6b and the lower wall 6c are set to 1D and 2. ID, respectively. This is a conventional air conditioner The lengths of the upper wall 6b and the lower wall 6c that are usually formed are as follows. The horizontal louvers 111 and 112 are arranged so as to divide the flow path substantially equally, and smoothly guide the air flow forward and upward.

[0066] 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.

[0067] According to the figure, K1 to K3 can be driven with less input (power consumption) than the comparative example (K4). When the noise at the same air volume was compared between Κ1 and Κ4, K1 was about 2dB lower than Κ4, and K2 and Κ3 were equivalent to K1 and the noise level was higher than K1.

FIGS. 8 to 11 are diagrams for explaining the difference in power consumption of the crossflow fan 7 between the present embodiment (K1) and the comparative example (Κ4). FIG. 8 is a side sectional view of the indoor unit 1 schematically showing the state of Κ4. Fig. 9 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. The vertical axis shows the static pressure of the airflow, and the horizontal axis shows the direction of the airflow. It shows.

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 blower path 6, and the air is harmonized into conditioned air when flowing through the indoor heat exchanger 9. At this time, pressure losses A Pa, A Pb, and A Pc are generated by the air resistances of the suction port 4, the indoor heat exchanger 9, and the air blowing path 6, respectively. As a result, the static pressure of the airflow decreases while flowing through the air blowing path 6, and becomes atmospheric pressure A Pa—A Pb—A Pc. Note that the pressure loss in the air filter 8 and other parts will be omitted.

[0070] Further, when the air flow sent out from the outlet 5 exits the outlet 5, a pressure loss A Pdl is generated due to the disturbance of the air current. In other words, the air flow sent out from the outlet 5 is ejected into the surrounding air suddenly disappearing from the upper, lower, left and right wall surfaces of the air passage 6 that has existed until then. 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 outlet 5 takes kinetic energy to the surrounding air. Over time, the static pressure will be the same as the atmospheric pressure. This phenomenon occurs immediately when the airflow is sent out from the outlet 5, so that the airflow in the vicinity of the outlet 5 is greatly disturbed, resulting in a pressure loss.

For this reason, the cross flow fan 7 has a total static pressure drop due to the pressure loss (Δ Pa +

(A Pb + A Pc + A Pdl) needs to be increased 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 + ΔPdl).

The product (ΔPO X Q) of this static pressure rise ΔPO and the flow rate Q of flow (ΔPO X Q) is the work of the cross flow fan 7. If the increase in static pressure by the cross flow fan 7 is smaller than the total decrease in static pressure (Δ ΡΟ A Pa + A Pb + A Pc + A Pdl), the cross flow fan 7 Cannot be distributed. Therefore, sufficient air conditioning cannot be performed.

In contrast, the case of the present embodiment (K1) is shown in FIGS. 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, as in Fig. 9. The vertical axis shows 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 Δ Ρ & and Δ Ρ Δ Ρο are generated by the air resistances of the suction port 4, the indoor heat exchanger 9, and the air blowing 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 airflow sent from the outlet 5 is the pressure loss of the comparative example of FIG.

It becomes smaller than ΔPdl. 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.

[0076] In addition, since the entire airflow flowing through the front guide portion 6a is along the inclined surface 6b5 due to the Coanda effect, the flow along the lower wall 6c of the blower path 6 is also affected by this. For this reason, it is gradually diffused into the surrounding air from the lower side of the air flow that does not diffuse at a stretch, and the static pressure is the same as the atmospheric pressure. The Therefore, the air flow disturbance near the outlet 5 is small, and the pressure loss A Pd2 associated therewith is small.

[0077] Further, the flow path area is gradually enlarged by the front guide portion 6a of the blower path 6, and then the flow path area is gradually enlarged by the inclined surface 6b5 and the lateral louver 113. For this reason, the airflow flows along the inclined surface 6b5 smoothly after passing through the front guide portion 6a while gradually expanding the basin area.

[0078] At this time, since the horizontal louvers 111, 112, 113 are arranged as shown in FIG. 5 described above, the flow of the airflow flowing below the lowermost horizontal louver 113 of the airflow sent from the outlet 5 is reduced. The flow path 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 outlet 5 is gradually expanded. Next, the flow path of the airflow flowing between the horizontal louvers 111 and 112 of the airflow sent from the blowout port 5 is gradually expanded. Finally, the flow path of the airflow above the horizontal louver 111 that circulates on the uppermost side of the airflow sent from the outlet 5 is gradually expanded. Therefore, the air flow gradually decreases smoothly and gradually with the lower force.

[0079] 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 to static pressure (positional energy 1). Accordingly, before the kinetic energy of the air flow sent out from the outlet 5 is taken away by the surrounding air or the air flow is disturbed, a part of it is converted to static pressure to obtain a static pressure increase ΔP2.

[0080] Thereby, the cross flow fan 7 is the sum of the static pressure drop due to the pressure loss (A Pa +

A Pb + A Pc + A Pd2) must be increased at once by subtracting the static pressure increase Δ Ρ2. For this reason, the static pressure increase Δ Ρ1 by the cross flow fan 7 becomes A Pa + A Pb + A Pc + ΔΡd2—ΔΡ2.

Therefore, the required static pressure increase Δ Ρ1 is only Δ Ρ2 + A Pdl— A Pd2 compared to the static pressure increase Δ PO required for the cross flow fan 7 in the comparative example (see FIGS. 8 and 9) Get smaller. As a result, the work force A Pdl—A Pd2) X Q of the cross flow fan 7 is reduced, and thus the fan drive motor input (power consumption) can be reduced by this amount to save energy.

That is, the pressure loss A Pd2 in the vicinity of the outlet 5 can be reduced, and the upper wall 6b and the lower wall can be reduced. The air along 6c is decelerated, the kinetic energy is converted to static pressure, and the crossflow fan 7 is assisted by the static pressure rise ΔP2. In other words, the kinetic energy previously taken away by the surrounding air can be fully recovered and converted to static pressure, which can be used for work for blowing air. Therefore, the increase in static pressure due to the cross flow fan 7 can be reduced, and energy saving of the air conditioner can be achieved.

[0083] As described above, the flow velocity (kinetic energy) of the airflow is converted to static pressure (potential energy) in order to gradually and smoothly reduce the wind speed from the lower side of the airflow and convert it to static pressure. The loss at the time is small. For this reason, the conversion efficiency for converting the flow velocity into static pressure is extremely improved, and it is possible to convert a large amount of kinetic energy into 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 while varying the lengths of the upper wall 6b and the lower wall 6c. The vertical axis indicates the length of the upper wall 6 b and is dimensionless by dividing by the diameter D of the cross flow fan 7. The horizontal axis shows the length of the lower wall 6c, which is made dimensionless by dividing by the diameter D of the crossflow fan 7. The airflow of the crossflow fan 7 is 16m ³ / min—constant. In the figure, Kl and Κ4 are the same conditions as in Figure 6 above.

[0085] 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 measurement is omitted because the length is not an extremely short cross flow fan 7. . In addition, since the measurement points in the figure are finite, the contour diagram is completed using interpolation and prediction of each measurement value.

[0086] 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. In addition, 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, if 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 static pressure until the velocity of the airflow becomes sufficiently low, and the kinetic energy of the airflow can be sufficiently converted to static pressure and recovered.

FIG. 13 is a contour diagram showing the results of examining the reach distance (unit: m) of the airflow along the ceiling surface while varying the lengths of the upper wall 6b and the lower wall 6c. The reach is the distance to the position where the average wind speed over 30 seconds is 0.05 mZs. As in Fig. 12, the vertical axis shows the length of the upper wall 6b. However, it is made dimensionless by dividing by the diameter D of the crossflow fan 7. The horizontal axis shows the length of the lower wall 6c, which is made dimensionless by dividing by the diameter D of the crossflow fan 7. The airflow of the cross flow fan 7 is 16m ³ / min—constant. In the figure, Kl and Κ4 are the same conditions as in Figure 6 above.

[0088] 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. . Also, since the measurement points in the figure are finite, the contour diagram is completed using interpolation and prediction of each measurement value.

[0089] As is apparent from the figure, the reach distance varies greatly depending on the length of the upper wall 6b, which is less dependent on the length of the lower wall 6c. In other words, in order to extend the reach distance, it is effective to prevent the kinetic energy from dissipating in the upward direction of the air current, which is greatly affected by the length of the upper wall 6b.

[0090] In addition, the reach distance rapidly 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 viscosity, and the kinetic energy of the airflow is gradually taken away by the surrounding air. However, if the length of the upper wall 6b is set to 1.5D or more, the upper wall 6b has a sufficient length, so that the air movement in the upward direction of the airflow is drastically reduced. As a result, the kinetic energy is not lost and the airflow reaches far. In other words, even in the airflow after sufficient kinetic energy has been recovered, a large reachable distance can be secured by making the length of the upper wall 6b 1.5D or more.

[0091] When the airflow blown out from the cross flow fan 7 flows through the air flow path 6, the lower part (near the lower wall 6c) becomes slower than the upper part (near the upper wall 6b) near the outlet 5. That is, in the vicinity of the air outlet 5, the airflow flowing through the upper part of the blower path 6 has a relatively high density of kinetic energy, and the airflow flowing through the lower part of the blower path 6 has a relatively low density of kinetic energy. This phenomenon is a common characteristic of ordinary crossflow fans.

[0092] When kinetic energy is simultaneously recovered from an airflow having a non-uniform energy density, the force is increased if the kinetic energy is recovered from an airflow having a relatively high density and a high flow velocity. This makes it difficult to recover sufficient kinetic energy from a low-velocity airflow with a relatively low density of kinetic energy. [0093] That is, gradually increase the flow path of the airflow to reduce the wind speed of the airflow and convert it to static pressure! Therefore, if the flow path with a non-uniform wind speed distribution is expanded, the air stream with a high wind speed passes through the passage first and is greatly decelerated. This makes it difficult for the slow airflow to be decelerated. As a result, the kinetic energy recovery efficiency from the entire airflow is reduced. For this reason, it is better to collect the kinetic energy separately by dividing the flow velocity and airflow with relatively high kinetic energy and the low velocity airflow with relatively low density kinetic energy. This makes it possible to efficiently recover the kinetic energy of the entire airflow.

[0094] Further, 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 gradually decreases. For this reason, it is necessary to collect kinetic energy as early as possible. Since the kinetic energy is relatively low, the kinetic energy is relatively low, and the kinetic energy can be sufficiently recovered at a relatively short distance. On the other hand, since the velocity of the flow velocity with relatively high density kinetic energy and the air current has much kinetic energy, a relatively long distance is required to recover sufficient kinetic energy.

For this reason, it is preferable that the air flow path 6 is divided into a plurality of flow paths in the vertical direction, and the flow paths are made longer in order as the lower flow paths are relatively short and go upward. As a result, the aerodynamic kinetic energy having the non-uniform energy density unique to the cross flow fan 7 can be efficiently recovered. Therefore, in the present embodiment, the air passage 1 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, and the second flow path formed by the uppermost horizontal louver 111 and the middle horizontal louver 112. And a third-stage flow path formed by the middle horizontal louver 112 and the lowermost horizontal louver 113, and a lowermost flow path formed by the lowermost horizontal louver 113 and the lower wall 6c. The air flow path is divided into two flow paths.

Then, as described above, the front end 6b6 of the upper wall 6b, the front end of the horizontal louver 111, the front end of the horizontal louver 112, the front end of the horizontal 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. [0098] It should be noted that it is more desirable that the angles θ 1 to Θ 4 (see FIG. 5) representing the enlargement ratio of the channel area of each channel be in the range of 10 ° to 15 °. In other words, if the angles 0 1 to 04 are larger than 15 °, the airflow flowing through each flow path is separated from the wall surface or rapidly decelerated, and loss occurs when the kinetic energy is converted to static pressure. The possibility increases. If the angles 0 1 to 0 4 are smaller than 10 °, the path is unnecessarily extended, and the amount of kinetic energy due to the friction between the airflow and the wall increases accordingly.

[0099] 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 that flows through the upper part of the airflow path 6 (near the upper wall 6b) is several times the wind speed of the airflow that flows through the lower part of the airflow path 6 (near the lower wall 6c). . For this reason, the kinetic energy of the airflow that flows through the upper part of the ventilation path 6 (near the upper wall 6b) is several tens of times the kinetic energy of the airflow that flows through the lower part of the ventilation path 6 (near the lower wall 6c) There is. Since the amount of kinetic energy to be recovered is very large in the upper part of the ventilation path 6, a sufficiently long flow path is required.

On the other hand, the angle oc (see FIG. 2) representing the enlargement ratio of the flow path area of the front guide portion 6a of the air blowing path 6 is preferably about 20 ° as described above. When the angle α is larger than that, the airflow passing through the front guide 6a is separated from the wall surface or decelerated abruptly, resulting in energy loss. At this time, if the channel is divided by the horizontal louver and the channel area is expanded in the range of 10 ° to 15 °, it can only be divided into two. As a result, it is extremely difficult to effectively recover kinetic energy from an air current that is several tens of times wide as described above.

[0101] 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. As a result, the flow path of the airflow flowing through the front guide portion 6a is divided into two vertically. Then, the lower flow path of the horizontal louver 112 can be further divided into two by the horizontal louver 113 so that 0 3 and 04 are in the range of 10 ° to 15 °.

[0102] Furthermore, the upper wall 6b is bent upward at the bent portion 6b4 facing the lateral louver 112. As a result, the flow path of the airflow flowing above the lateral louver 112 is expanded. The gradually expanding flow path formed by the horizontal louver 112 and the inclined surface 6b5 is formed by the uppermost horizontal louver 111. Divided. Since the uppermost horizontal louver 111 faces the inclined surface 6b5 and the rear end is arranged in front of the bent portion 6b4, the horizontal louver 111 is positioned above the horizontal louver 112 by 0 °, 0 2 from 10 ° to 15 °. It can be divided into two in the range of. Note that it is not very efficient to bend the lower surface 6c3 of the front guide portion 6a downward and expand it in the same way because the wind speed is slow.

[0103] It should be noted that it is more desirable that the rear end of the lowermost horizontal louver 113 and the lower surface 6c3 of the front guide portion 6a are arranged so as to be close to the terminal end 6c4 of the lower wall 6c in the direction perpendicular to the airflow, . As a result, the kinetic energy can be recovered more efficiently by the aerodynamic force flowing through the flow path below the lateral louver 113.

[0104] 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 other arrangements.

[0105] 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 the diameter D of the cross flow fan 7 or more. Therefore, during the operation of the air conditioner, air smoothly flows over a long distance along the upper wall 6b and the lower wall 6c of the air blowing path 6. As a result, the air flow disturbance near the outlet 5 is reduced and the pressure loss A Pd2 is reduced accordingly.

[0106] Power! Then, 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 cross flow fan 7 is assisted by the static pressure increase ΔP2. In other words, the kinetic energy that was previously taken away by the surrounding air is fully recovered and converted to static pressure, which can be used for work for blowing air. Therefore, the increase in static pressure due to the crossflow fan 7 can be reduced, and energy saving of the air conditioner can be achieved.

[0107] Further, the kinetic energy can be recovered to increase the reach distance of the airflow with a reduced flow velocity. As a result, the air sent out from the outlet 5 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 conditioned air stream reaches every corner of the room, and the air stream greatly stirs the entire room. Therefore, it is possible to obtain a comfortable space with almost no direct wind by equalizing the temperature distribution of the entire living area except a part of the upper part of the room.

[0108] Note that the cross flow fan 7 generally causes surging when the pressure loss in the flow path increases. Rub. As a result, the desired air volume cannot be obtained or the noise may increase significantly. When the indoor heat exchanger 9 is bent and configured with a plurality of stages and a plurality of rows of refrigerant tubes 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 number of revolutions of the cross flow fan 7 considerably. As a result, the noise of the cross flow fan 7 increases and the energy saving performance deteriorates.

[0109] Therefore, by converting the kinetic energy of the airflow into static pressure and assisting the cross fan 7 with the increase in static pressure, the cross flow fan 7 is less prone to surging and the noise is relatively small. be able to. In particular, when four or more rows of refrigerant pipes are juxtaposed in the depth direction, the pressure loss becomes very large, and this embodiment can provide a greater effect.

[0110] <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 parts as those in the first embodiment shown in FIGS. 1 to 13 are denoted by the same reference numerals. In the present embodiment, the front panel 3 is pivotally supported by the rotating 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 in the first embodiment.

[0111] When the air conditioner is stopped, the front panel 3 is arranged so that the upper end is in contact with the upper part of the casing, as shown in FIG. Further, the outlet 5 is shielded by the horizontal louvers 111 and 112 as in the first embodiment.

When the air conditioner is driven, as shown in FIG. 15, the front panel 3 is rotated by the rotating shafts 22 and 23, and the front panel 3 between the rotating shafts 22 and 23 is inclined surface 6b5 of the air flow path 6 Is formed. Thus, 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, where D is the diameter of the cross flow fan 7. Further, 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 formed to be 3.5D or more. Therefore, the same effect as the first embodiment can be obtained.

[0113] <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 used for the same parts as those in the first embodiment shown in FIGS. Is attached. In the present embodiment, the lower portion of the front panel 3 is opened, and a movable panel 21 that closes the opening is pivotally supported at the lower end by a rotating shaft 22. Other parts are the same as in the first embodiment.

[0114] When the air conditioner is stopped, the movable panel 21 is arranged so as to block the lower part of the front panel 3 as shown in FIG. Further, the outlet 5 is shielded by the horizontal louvers 111 and 112 as in the first embodiment.

When the air conditioner is driven, as shown in FIG. 17, the movable panel 21 is rotated by the rotation shaft 22, and the inclined surface 6 b 5 of the blowing path 6 is formed by the movable panel 21. As a result, the length of the upper wall 6b of the blower passage 6 on the downstream side of the cross flow fan 7 is formed to be 1.5D or more, where D is the diameter of the single fan 7 of the cross fan. Further, 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 formed to be 3.5D or more. Therefore, the same effect as that of the first embodiment can be obtained.

[0116] <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 given the same reference numerals. In the present embodiment, the lateral louver 113 of the first embodiment is omitted as described above. Other parts 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.

[0117] 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 the recovery of the kinetic energy of the airflow flowing under the air flow path 6 is eliminated. Slightly decreases. However, as indicated by K2 in FIG. 6 described above, the power consumption can be made smaller than in Comparative Example K4 in FIG. 7, and energy saving can be achieved compared to the conventional example.

[0118] <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 given 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, 112 are changed. Other parts 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. [0119] The horizontal louvers 111, 112 arranged above and below are opposed to the bent portion 6b4, and the rear ends thereof are arranged behind the bent portion 6b4. The front ends of the horizontal louvers 111, 112 are arranged at substantially the same position in front of the bent portion 6b4 and in the front-rear direction. Further, the lateral louvers 111 and 112 form a flow path in which the front guide portion 6a of the air blowing path 6 is divided at substantially equal intervals.

[0120] According to the air conditioner of the present embodiment, the efficiency of recovering the kinetic energy of the airflow flowing in the air supply 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 compared to the conventional example.

[0121] 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 appropriate modifications are made without departing from the spirit of the present invention. Can be implemented.

Industrial applicability

[0122] According to the present invention, it can be used for an air conditioner that takes in indoor air and harmonizes it.

Claims

The scope of the claims

[1] A suction port for taking indoor air into the housing of the indoor unit, a blow-off port provided at a lower portion of the housing, a ventilation path for communicating between the suction port and the blow-out port, and a plurality of refrigerant pipes An indoor heat exchanger that is arranged in parallel in a plurality of rows and is bent along the inner surface of the housing and disposed opposite to the suction port in the air blowing path; and the indoor heat exchanger in the air blowing path; In the air conditioner provided with a cross flow fan disposed between the air outlet and the air flow path, the air flow path has a front guide portion in which the flow path area is expanded toward the downstream by guiding the air forward and downward. An air conditioner characterized in that the sum of the length of the upper wall and the length of the lower wall of the air flow path downstream of the cross flow fan is 3.5 times or more the diameter of the cross flow fan. .

[2] Provided with a first wind direction plate that varies the wind direction of the air outlet up and down, and is arranged from the front upper side to the front end of the upper wall, the front end of the first wind direction plate, and the front end of the lower wall during operation of the air conditioner The air conditioner according to claim 1, wherein the air conditioner is provided.

[3] The air conditioner according to claim 2, wherein a second wind direction plate is provided below the first wind direction plate, and a front end of the first wind direction plate is disposed in front of a front end of the second wind direction plate. .

[4] The upper wall has a terminal force on the upper surface of the front guide portion that is inclined forward and downward, and has an inclined surface that is bent at the bent portion and inclined forward and upward, and the rear end of the first wind direction plate is more than the bent portion. 4. The air conditioner according to claim 3, wherein the air conditioner is disposed forward and a rear end of the second wind direction plate is disposed rearward of the bent portion.

[5] Provided with first and second wind direction plates that are variable up and down the blower outlet, the upper wall has an inclined surface that is bent at a terminal force bending portion of the upper surface of the front guide portion and inclined forward and upward, The rear end of the first wind direction plate is arranged in front of the bent portion, and the rear end of the second wind direction plate below the first wind direction plate is arranged in rear of the bent portion. The air conditioner according to claim 1.

[6] The air conditioner according to claim 4 or 5, 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 10 ° to 15 °. Machine.

7. The air conditioner according to claim 6, wherein a third wind direction plate is provided below the second wind direction plate, and an angle formed by the second and third wind direction plates is 10 ° to 15 °.

[8] The air conditioner according to [6], wherein an angle formed by a wind direction plate disposed at a lowermost position and a tangent at the end of the lower wall is set to 10 ° to 15 °.

[9] The air conditioner according to [1], wherein a length of the upper wall is 1.5 times or more a diameter of the cross flow fan.

[10] A suction port for taking indoor air into the housing of the indoor unit, a blow-off port provided at a lower portion of the housing, a ventilation path communicating between the suction port and the blow-out port, and a plurality of refrigerant pipes An indoor heat exchanger that is arranged in parallel in a plurality of rows and is bent along the inner surface of the housing and disposed opposite to the suction port in the air blowing path; and the indoor heat exchanger in the air blowing path; In the air conditioner including a cross flow fan disposed between the air outlet and first and second air direction plates that change the air direction of the air outlet vertically, the air flow path is the cross flow fan. Force The air flow area is increased as the air is guided forward and downward, and the flow path area is enlarged. The cross flow fan has a front guide portion, and the length of the upper wall of the air flow path downstream of the cross flow fan 1.5 times the diameter of the upper wall and the upper wall End force of the front guide portion has an inclined surface that is bent at the bent portion and inclined forward and upward, the rear end of the first wind direction plate is disposed in front of the bent portion, and more than the first wind direction plate. An air conditioner characterized in that the rear end of the lower second wind direction plate is arranged behind the bent portion.

11. The air conditioner according to claim 10, 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 10 ° to 15 °.

12. The air conditioner according to claim 11, wherein a third wind direction plate is provided below the second wind direction plate, and an angle formed by the second and third wind direction plates is 10 ° to 15 °.

[13] The angle formed by the wind direction plate arranged at the lowermost position and the tangent at the end of the lower wall of the front guide portion is 1

12. The air conditioner according to claim 11, wherein the air conditioner is set to 0 ° to 15 °.

14. The air conditioner is arranged in the order of 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 from the front upper side during operation of the air conditioner. The air conditioner described in 1.

[15] A suction port for taking indoor air into the housing of the indoor unit, a blow-off port provided at a lower portion of the housing, a blower path that communicates between the suction port and the blower outlet, An indoor heat exchanger disposed opposite to the suction port, and the indoor heat exchange in the air blowing path And a cross flow fan disposed between the air outlet and the outlet, and the length of the upper wall of the air flow path on the downstream side of the cross flow fan is 1.5 times the diameter of the cross flow fan or more An air conditioner characterized by that.

A suction port for taking indoor air into the housing of the indoor unit, a blow-off port provided at a lower portion of the housing, a blower path communicating between the suction port and the blower outlet, and the suction port in the blower path And a cross flow fan disposed between the indoor heat exchanger in the air passage and the outlet, and the air blower on the downstream side of the cross flow fan. An air conditioner characterized in that the sum of the length of the upper wall and the length of the lower wall of the path is at least 3.5 times the diameter of the cross flow fan.