CN114364921B

CN114364921B - Air conditioner indoor unit and air conditioner

Info

Publication number: CN114364921B
Application number: CN202080064049.7A
Authority: CN
Inventors: 堤智彦; 鹈饲康史; 藤田浩辉; 村上智哉
Original assignee: Daikin Industries Ltd
Current assignee: Daikin Industries Ltd
Priority date: 2019-09-17
Filing date: 2020-09-07
Publication date: 2023-10-24
Anticipated expiration: 2040-09-07
Also published as: JP2021046958A; EP4015930A4; AU2020350294A1; CN114364921A; EP4015930B1; EP4015930A1; AU2020350294B2; WO2021054180A1; JP6897735B2

Abstract

An air conditioning indoor unit (1) is provided with a control device (100). When the operation in the first airflow control mode is to be performed, the control device (100) shifts to the operation in the first airflow control mode after the operation in the second airflow control mode, wherein in the first airflow control mode, the interval between the first horizontal blade (41) and the second horizontal blade (51) on the downstream side of the flow of the blown air is wider than the interval between the first horizontal blade (41) and the second horizontal blade (51) on the upstream side, a part of the blown air is made to flow along the lower airfoil surface of the first horizontal blade (41), and the other part of the blown air is made to flow along the upper airfoil surface of the second horizontal blade (51), and in the second airflow control mode, the separation angle between the first horizontal blade (41) and the second horizontal blade (51) is made to be narrower than the predetermined separation angle between the first horizontal blade (41) and the second horizontal blade (51) in the first airflow control mode, and the blown air is blown.

Description

Air conditioner indoor unit and air conditioner

Technical Field

The present disclosure relates to an air conditioning indoor unit and an air conditioner provided with the same.

Background

Conventionally, as an air conditioning indoor unit, there are the following air conditioning indoor units: the air conditioner includes a housing provided with an air outlet, a first horizontal blade attached to a front edge portion of the air outlet, and a second horizontal blade attached to a rear edge portion of the air outlet (see, for example, patent document 1 (japanese patent application laid-open No. 2017-125678)). The first horizontal blade and the second horizontal blade adjust the vertical direction of the blown air flowing from the outlet of the casing to the indoor space.

Prior art literature

Patent literature

Patent document 1: japanese patent laid-open No. 2017-125678

Disclosure of Invention

Problems to be solved by the invention

In the above-described conventional air conditioning indoor unit, even if the blown air is supplied to a wide range in order to control the first horizontal blade and the second horizontal blade, it is impossible to cause the airflow to follow the respective airfoils of the first horizontal blade and the second horizontal blade. Therefore, the conventional air conditioning indoor unit has a problem that the blown air cannot be supplied over a wide range.

The present disclosure addresses the problem of providing an air conditioning indoor unit that can stably supply blown air over a wide range.

Means for solving the problems

An air conditioner indoor unit according to an embodiment of the present disclosure includes:

a housing having an air outlet through which air from the air blower fan is blown out;

a first horizontal blade that controls a vertical direction of the blown air from the outlet;

a first driving part for driving the first horizontal blade;

a second horizontal blade disposed at a rear side of the first horizontal blade and configured to control a vertical direction of the blown air;

a second driving part for driving the second horizontal blade; and

A control device for controlling the blower fan, the first driving unit and the second driving unit,

when the control device is to perform the operation in the first airflow control mode, the control device is to perform the operation in the second airflow control mode, and then to switch to the operation in the first airflow control mode in which the interval between the first horizontal blade and the second horizontal blade on the downstream side of the flow of the blown air is made larger than the interval on the upstream side, a part of the blown air is made to flow along the lower surface of the first horizontal blade, and another part of the blown air is made to flow along the upper surface of the second horizontal blade, and in the second airflow control mode in which the separation angle between the first horizontal blade and the second horizontal blade is made to be smaller than the predetermined separation angle between the first horizontal blade and the second horizontal blade in the first airflow control mode, and the blown air is blown.

According to the above configuration, when the operation in the first airflow control mode is to be performed, the operation in the second airflow control mode is performed, and then the operation in the second airflow control mode is performed, in which the separation angle between the first horizontal blade and the second horizontal blade is made narrower than the predetermined separation angle between the first horizontal blade and the second horizontal blade in the first airflow control mode, and the blown air is blown out. Thereby, the transition from the second airflow control mode to the first airflow control mode is made while maintaining the coanda effect at the lower airfoil surface of the first horizontal blade and the upper airfoil surface of the second horizontal blade. As a result, after the transition to the first airflow control mode, a part of the blown air is caused to flow along the lower airfoil surface of the first horizontal blade, and another part of the blown air is caused to flow along the upper airfoil surface of the second horizontal blade. Therefore, stable supply of the blown air to a wide range can be realized.

In one embodiment, in the operation in the second airflow control mode, the rotation speed of the blower fan is set to be higher than that in the first airflow control mode.

According to the above aspect, in the operation in the second airflow control mode, the rotational speed of the blower fan is made higher than that in the first airflow control mode, and therefore, the coanda effect at the lower airfoil surface of the first horizontal blade and the upper airfoil surface of the second horizontal blade can be improved.

In one embodiment, in the operation in the second airflow control mode performed before the operation in the first airflow control mode, one of the first horizontal blade and the second horizontal blade is driven to narrow a separation angle between the first horizontal blade and the second horizontal blade.

According to the above aspect, since the separation angle between the first horizontal blade and the second horizontal blade is narrowed by driving one of the first horizontal blade and the second horizontal blade, the driving control of the first horizontal blade and the second horizontal blade for narrowing the separation angle is simplified as compared with the case of driving both the first horizontal blade and the second horizontal blade.

In the air conditioning indoor unit according to one aspect, in the second airflow control mode, one of the first horizontal blade and the second horizontal blade having a larger angle with respect to the direction of the air blown out during the operation in the first airflow control mode is driven so as to narrow the separation angle between the first horizontal blade and the second horizontal blade.

According to the above aspect, in the second airflow control mode, the larger one of the first horizontal blade and the second horizontal blade is driven to narrow the separation angle of the first horizontal blade and the second horizontal blade with respect to the wind direction of the blown air in the operation in the first airflow control mode, and therefore, the airflow along the larger one of the angles is easily obtained.

In one embodiment, the first horizontal vane and/or the second horizontal vane rotates faster during the operation in the second airflow control mode than during the transition from the operation in the second airflow control mode to the operation in the first airflow control mode.

According to the above aspect, the rotation of the first horizontal blade and/or the second horizontal blade is relatively slow when the operation in the second airflow control mode is shifted to the operation in the first airflow control mode, and therefore, the peeling of the airflow at the first horizontal blade and/or the second horizontal blade can be suppressed because the rotation is faster than the rotation.

any one of the plurality of air conditioning indoor units; and

an air conditioner outdoor unit connected to the air conditioner indoor unit via a refrigerant pipe.

According to the above configuration, by providing the air conditioning indoor unit, stable supply of the blown air to a wide range can be realized.

Drawings

Fig. 1 is a refrigerant circuit diagram of an air conditioner according to a first embodiment of the present disclosure.

Fig. 2 is a schematic cross-sectional view of the indoor unit in the operation stopped state according to the first embodiment of the present disclosure.

Fig. 3 is a structural diagram of the inside of the indoor unit.

Fig. 4 is a control block diagram of the air conditioner.

Fig. 5 is a schematic cross-sectional view of the indoor unit in the first inclined airflow control mode.

Fig. 6 is a schematic cross-sectional view of the indoor unit in the ceiling airflow control mode.

Fig. 7 is a schematic cross-sectional view of the indoor unit in the vertical airflow control mode.

Fig. 8 is a schematic cross-sectional view of the indoor unit in the second inclined airflow control mode.

Fig. 9 is a perspective view of a first horizontal baffle of a first embodiment of the present disclosure.

Fig. 10 is a top view of the first horizontal barrier.

Fig. 11 is a bottom view of the first horizontal barrier.

Fig. 12 is a cross-sectional view taken along line XII-XII of fig. 11 in the direction of the arrow.

Fig. 13 is a cross-sectional view taken along line XIII-XIII of fig. 11 in the direction of the arrow.

Fig. 14 is a perspective view of a second horizontal baffle of a first embodiment of the present disclosure.

Fig. 15 is a plan view of the second horizontal barrier.

Fig. 16 is a bottom view of the second horizontal barrier.

Fig. 17 is a sectional view taken along the arrow direction of the line XVII-XVII in fig. 13.

Fig. 18 is a sectional view taken along the arrow direction of line XVIII-XVIII of fig. 13.

Fig. 19 is a simulation result diagram of the blown air of the indoor unit according to the first embodiment.

Fig. 20 is another simulation result diagram of the blown air of the indoor unit according to the first embodiment.

Fig. 21 is a simulation result diagram of the blown air of the indoor unit of the comparative example.

Fig. 22 is a simulation result diagram of the blown air of the indoor unit of the comparative example.

Fig. 23 is an image of the blown air of the indoor unit according to the first embodiment.

Fig. 24 is a view for explaining the wind speed of the blown air of the indoor unit according to the first embodiment.

Fig. 25 is a schematic cross-sectional view of the indoor unit in the pre-tilt airflow control mode.

Fig. 26 is a flowchart for explaining a transition from the operation in the pre-tilt airflow control mode to the operation in the first tilt airflow control mode.

Fig. 27 is a schematic cross-sectional view of the indoor unit in another pre-tilt airflow control mode.

Fig. 28 is a schematic cross-sectional view of the indoor unit in another pre-tilt airflow control mode.

Fig. 29 is a control block diagram of an air conditioner according to a second embodiment of the present disclosure.

Detailed Description

Hereinafter, the air conditioning indoor unit and the air conditioner of the present disclosure will be described in detail with reference to the illustrated embodiments. Common parts in the drawings are denoted by the same reference numerals, and repetitive description thereof will be omitted.

First embodiment

Fig. 1 shows a refrigerant circuit RC provided in an air conditioner according to a first embodiment of the present disclosure. The air conditioner is a pair-to-pair type air conditioner in which an indoor unit 1 and an outdoor unit 2 are connected one to one. The indoor unit 1 is an example of an air conditioning indoor unit. The outdoor unit 2 is an example of an air conditioning outdoor unit. The communication pipes L1 and L2 are examples of refrigerant pipes.

The air conditioner includes: a compressor 11; a four-way switching valve 12 having one end connected to the discharge side of the compressor 11; an outdoor heat exchanger 13, one end of which is connected to the other end of the four-way switching valve 12; an electric expansion valve 14 having one end connected to the other end of the outdoor heat exchanger 13; an indoor heat exchanger 15, one end of which is connected to the other end of the motor-operated expansion valve 14 via a shutoff valve 21 and a communication pipe L1; and a gas-liquid separator 16, one end of which is connected to the other end of the indoor heat exchanger 15 via a communication pipe L2, a shutoff valve 22, and a four-way switching valve 12, and the other end of which is connected to the suction side of the compressor 11. Here, the compressor 11, the four-way switching valve 12, the outdoor heat exchanger 13, the motor-operated expansion valve 14, the indoor heat exchanger 15, the gas-liquid separator 16, and the like constitute a refrigerant circuit RC of the air conditioner. The indoor heat exchanger 15, the indoor fan 10, and the like constitute the indoor unit 1. On the other hand, the compressor 11, the four-way switching valve 12, the outdoor heat exchanger 13, the motor-operated expansion valve 14, the gas-liquid separator 16, the outdoor fan 20, and the like constitute the outdoor unit 2. The indoor fan 10 is an example of a blower fan. The electric expansion valve 14 is an example of a pressure reducing mechanism.

The indoor unit 1 includes: an indoor heat exchanger temperature sensor T4 that detects the temperature of the indoor heat exchanger 15; an indoor temperature sensor T5 that detects an indoor temperature; and a floor temperature sensor T6 that detects a temperature of the floor facing the indoor space R (shown in fig. 2, 5 to 8). An indoor fan 10 that circulates indoor air through an indoor heat exchanger 15 is provided in the indoor unit 1. In addition, as the indoor heat exchanger temperature sensor T4 and the indoor temperature sensor T5, for example, a thermistor or the like is used. As the floor temperature sensor T6, for example, an infrared temperature sensor or the like is used. The indoor space R is an example of an air-conditioning target space.

The outdoor unit 2 includes an outdoor heat exchanger temperature sensor T1 that detects the temperature of the outdoor heat exchanger 13, an outside air temperature sensor T2 that detects the outside air temperature, and an evaporation temperature sensor T3 that detects the evaporation temperature of the motor-operated expansion valve 14. The outdoor unit 2 is provided with an outdoor fan 20 for supplying outside air to the outdoor heat exchanger 13. As the outdoor heat exchanger temperature sensor T1, the outside air temperature sensor T2, and the evaporation temperature sensor T3, for example, thermistors or the like are used.

The air conditioner includes a remote controller (hereinafter, referred to as a "remote controller"), which is not shown. By operating the remote controller, 1 operation such as cooling operation, dehumidifying operation, heating operation, etc. can be started or stopped, or other operations can be switched. Further, by operating the remote controller, the set temperature of the indoor temperature can be changed, or the air volume of the air blown out by the indoor unit 1 can be adjusted.

When the cooling operation or the dehumidifying operation is selected by the remote controller and the four-way switching valve 12 is switched to the solid line state of fig. 1, the refrigerant from the compressor 11 flows through the refrigerant circuit RC in the order of the four-way switching valve 12, the outdoor heat exchanger 13, the motor-operated expansion valve 14, the indoor heat exchanger 15, the four-way switching valve 12, and the gas-liquid separator 16 as indicated by solid line arrows. On the other hand, when the heating operation is selected and the four-way switching valve 12 is switched to the state of the broken line in fig. 1, the refrigerant from the compressor 11 flows through the refrigerant circuit RC in the order of the four-way switching valve 12, the indoor heat exchanger 15, the electric expansion valve 14, the outdoor heat exchanger 13, the four-way switching valve 12, and the gas-liquid separator 16, as indicated by the broken line arrow.

Fig. 2 schematically illustrates a longitudinal section of the indoor unit 1 in an operation stopped state. The indoor unit 1 is a wall-mounted type.

The indoor unit 1 includes a casing 30 including a casing main body 31 and a front panel 32. The casing 30 is attached to a wall surface W facing the indoor space R, and accommodates the indoor fan 10, the indoor heat exchanger 15, the drain pan 33, and the like. The indoor space R is an example of an air-conditioning target space.

The housing main body 31 is composed of a plurality of members, and has a front surface portion 31a, an upper surface portion 31b, a rear surface portion 31c, and a lower surface portion 31d. A front panel 32 is openably and closably attached to the front surface 31 a. Further, a suction port (not shown) is provided from the front surface portion 31a to the upper surface portion 31 b.

The front panel 32 forms a front surface 31a of the indoor unit 1, and has a flat shape without a suction port, for example. The upper end portion of the front panel 32 is rotatably supported by the upper surface portion 31b of the housing main body 31, and can be operated by a hinge.

The indoor fan 10 and the indoor heat exchanger 15 are mounted to the casing main body 31. The indoor heat exchanger 15 exchanges heat with indoor air sucked into the casing 30 through the suction port. The indoor heat exchanger 15 has an inverted V-shape with both ends facing downward and a bent portion located on the upper side when viewed from the side. The indoor fan 10 is located below the curved portion of the indoor heat exchanger 15. The indoor fan 10 is, for example, a cross-flow fan, and sends the indoor air having passed through the indoor heat exchanger 15 to the outlet 34 of the lower surface 31d of the casing main body 31.

The housing main body 31 is provided with a first partition wall 35 and a second partition wall 36. The space sandwiched between the first partition wall 35 and the second partition wall 36 serves as a blowout flow path 37 connecting the indoor fan 10 and the blowout port 34.

The drain pan 33 is disposed below the front portion of the indoor heat exchanger 15, and receives dew condensation water from the front portion. The dew condensation water is discharged outdoors through a drain hose (not shown).

The indoor unit 1 further includes a first horizontal baffle 41 and a second horizontal baffle 51 disposed on the rear side (wall surface W side) of the first horizontal baffle 41. The first horizontal baffle 41 and the second horizontal baffle 51 adjust the vertical direction of the blown air flowing through the blow-out flow path 37 and blown out from the blow-out port 34. The first horizontal barrier 41 is an example of a first horizontal blade. The second horizontal barrier 51 is an example of a second horizontal blade.

The first horizontal barrier 41 has: a first end 41a disposed upstream with respect to the flow of the blown air during operation of the indoor unit 1; and a second end 41b disposed downstream of the flow of the blown air. The first horizontal barrier 41 is rotatably attached to the lower surface 31d of the housing main body 31.

To describe in more detail, the first horizontal barrier 41 has a piece 41g (shown in fig. 9 to 13) connected to the second end 41 b. The piece 41g is attached to the attachment portion 38 of the housing main body 31, and the first horizontal barrier 41 is rotatable about the attachment portion 38. When the operation of the indoor unit 1 is stopped, the first horizontal barrier 41 assumes a posture along the front side portion of the lower surface portion 31d of the casing main body 31. When the operation of the indoor unit 1 is started, the first horizontal barrier 41 is rotated by driving the first horizontal barrier motor 73 (shown in fig. 3 and 4), and the interval between the front side portion of the lower surface portion 31d of the casing main body 31 and the second end portion 41b of the first horizontal barrier 41 is enlarged. At this time, the first horizontal barrier 41 can take a plurality of inclined postures with respect to the horizontal plane. As the first horizontal barrier motor 73, for example, a 4-phase winding stepping motor is used.

The second horizontal barrier 51 has, like the first horizontal barrier 41: a first end 51a disposed upstream with respect to the flow of the blown air; and a second end 51b disposed downstream of the flow of the blown air. The first end 51a of the second horizontal barrier 51 is rotatably attached to the lower surface 31d of the housing main body 31.

To describe in more detail, when the operation of the indoor unit 1 is stopped, the second horizontal barrier 51 assumes a posture of closing the outlet 34. When the operation of the indoor unit 1 is started, the second horizontal barrier motor 74 (shown in fig. 3 and 4) drives the second horizontal barrier 51. Thereby, the second horizontal baffle plate 51 rotates about the first end 51a, and the second end 51b is separated from the mounting portion 38, so that the air outlet 34 is opened. At this time, the second horizontal barrier 51 can take a plurality of inclined postures with respect to the horizontal plane. As the second horizontal barrier motor 74, for example, a 4-phase winding stepping motor is used.

The indoor unit 1 further includes a plurality of vertical flaps 61 (shown in fig. 3) for adjusting the direction of the air flow in the left-right direction of the blown air. The plurality of vertical baffles 61 are arranged in the air outlet channel 37 at predetermined intervals along the longitudinal direction of the air outlet 34 (the direction perpendicular to the paper surface of fig. 2). The vertical barrier 61 is an example of a vertical blade.

Fig. 3 schematically shows the internal structure of the indoor unit 1.

The first and second horizontal shutters 41 and 51 are supported by the first and second rotation shafts 71 and 72 so as to be rotatable in the up-down direction. The first and second rotation shafts 71 and 72 are driven to rotate by the first and second horizontal barrier motors 73 and 74, and the first and second horizontal barriers 41 and 51 are rotated in the vertical direction. The first horizontal barrier motor 73 is an example of a first driving unit. The second horizontal barrier motor 74 is an example of a second driving unit.

The plurality of vertical barriers 61 are divided into a first vertical barrier group G1 and a second vertical barrier group G2. The vertical barrier 61 constituting the first vertical barrier group G1 is an example of one vertical blade among the plurality of vertical blades. The vertical barrier 61 constituting the second vertical barrier group G2 is an example of the other vertical blade among the plurality of vertical blades.

The first vertical barrier group G1 is constituted by a plurality of vertical barriers 61 facing the opening area on the left side of the center in the left-right direction of the air outlet 34. The vertical barriers 61 belonging to the first vertical barrier group G1 are coupled to each other by a first coupling rod 81. The first link 81 is driven in the left-right direction by the first vertical barrier group motor 83, and the plurality of vertical barriers 61 are rotated in the left-right direction about respective rotation shafts (not shown).

The second vertical barrier group G2 is constituted by a plurality of vertical barriers 61 facing the opening area on the right side of the center in the left-right direction of the air outlet 34. The vertical barrier 61 belonging to the second vertical barrier group G2 is connected to the second connecting rod 82 in the same manner as the vertical barrier 61 belonging to the first vertical barrier group G1, and can be rotated by the second vertical barrier group motor 84.

Fig. 4 is a control block diagram of the air conditioner.

The air conditioner includes a control device 100 including a microcomputer, an input/output circuit, and the like. The control device 100 includes an indoor control unit (not shown) provided on the indoor unit 1 side and an outdoor control unit (not shown) provided on the outdoor unit 2 side.

The control device 100 controls the compressor 11, the four-way switching valve 12, the indoor fan motor 85, the outdoor fan motor 86, the display unit 50, the first horizontal barrier motor 73, the second horizontal barrier motor 74, the first vertical barrier motor 83, the second vertical barrier motor 84, and the like based on signals from the outdoor heat exchanger temperature sensor T1, the outside air temperature sensor T2, the evaporation temperature sensor T3, the indoor heat exchanger temperature sensor T4, the indoor temperature sensor T5, and the like. The display unit 50 is provided in the indoor unit 1, and is an LED or the like for displaying at least the operation state. In addition, the indoor fan motor 85 drives the indoor fan 10. In addition, the outdoor fan motor 86 drives the outdoor fan 20.

The indoor unit 1 can perform operations (for example, cooling operation, heating operation, and the like) in the first diagonal airflow control mode, the ceiling airflow control mode, the vertical airflow control mode, and the second diagonal airflow control mode. Based on the above signals or the like, 1 airflow control mode is automatically selected from a first oblique airflow control mode, a ceiling airflow control mode, a vertical airflow control mode, and a second oblique airflow control mode, which will be described later, or is switched to another airflow control mode. In addition, by operating the remote controller, 1 mode out of the first oblique air flow control mode, the ceiling air flow control mode, the vertical air flow control mode, and the second oblique air flow control mode can be selected. The first diagonal airflow control mode is an example of the first airflow control mode.

< first inclined airflow control mode >

Fig. 5 schematically shows a longitudinal section of the indoor unit 1 in which transition to the first inclined airflow control mode is completed.

In the first inclined airflow control mode, the interval between the first horizontal baffle 41 and the second horizontal baffle 51 is wider on the downstream side than on the upstream side of the flow of the blown air, and the blown air flowing from the air outlet 34 to the indoor space R flows obliquely downward toward the front side (the side opposite to the wall surface W side).

More specifically, when the virtual plane V1 passing through the center of the first end portion 41a of the first horizontal baffle 41 in the thickness direction and the center of the second end portion 41b of the first horizontal baffle 41 in the thickness direction is defined, the inclination angle θ1 of the virtual plane V1 with respect to the horizontal plane H in the first inclined airflow control mode is, for example, +10°. On the other hand, if the virtual plane V2 passing through the center in the thickness direction of the first end portion 51a and the center in the thickness direction of the second end portion 41b of the second horizontal baffle plate 51 is defined, the inclination angle θ2 of the virtual plane V2 with respect to the horizontal plane H in the first inclined airflow control mode is, for example, +70°. At this time, the separation angle of the first horizontal barrier 41 and the second horizontal barrier 51 is, for example, 60 °. When the inclination angles θ1 and θ2 are positive (+) angles, the front sides of the virtual planes V1 and V2 are positioned below the rear sides of the virtual planes V1 and V2. The separation angle corresponds to an angle obtained by subtracting the inclination angle θ1 from the inclination angle θ2. Further, 60 ° is an example of a predetermined separation angle.

In other words, the first horizontal baffle 41 assumes the posture in the first inclined airflow control mode when rotated 25 ° from the state when the operation of the indoor unit 1 is stopped. On the other hand, when the second horizontal baffle 51 is rotated 70 ° from the state when the operation of the indoor unit 1 is stopped, the second horizontal baffle is in the posture when in the first inclined airflow control mode. Here, the angle obtained by subtracting the rotation angle of the first horizontal barrier 41 from the rotation angle of the second horizontal barrier 51 becomes the separation angle of the first horizontal barrier 41 and the second horizontal barrier 51 in the first inclined airflow control mode.

In the first airflow control mode, the vertical barriers 61 of the first vertical barrier group G1 take the following postures: the downstream end of the flow of the blown air is inclined to the left of the housing 30 than the upstream end of the flow of the blown air. In addition, in the first airflow control mode, each vertical barrier 61 of the second vertical barrier group G1 takes the following posture: the downstream end of the flow of the blown air is inclined to the right of the housing 30 than the upstream end of the flow of the blown air.

More specifically, the interval between the vertical baffles 61 of the first vertical baffle group G1 and the vertical baffles 61 of the second vertical baffle group G2 is wider on the downstream side than on the upstream side of the flow of the blown air. In other words, each vertical barrier 61 of the first vertical barrier group G1 rotates such that an end portion located on the downstream side of the flow of the blown air is closer to the left side surface portion of the casing main body 31 and an end portion located on the upstream side of the flow of the blown air is farther from the left side surface portion of the casing main body 31. On the other hand, each vertical barrier 61 of the second vertical barrier group G2 rotates such that an end portion located on the downstream side of the flow of the blown air is closer to the right side surface portion of the casing main body 31 and an end portion located on the upstream side of the flow of the blown air is farther from the right side surface portion of the casing main body 31.

< ceiling airflow control pattern >

Fig. 6 schematically shows a longitudinal section of the indoor unit 1 in which the transition to the ceiling airflow control mode is completed.

In the ceiling airflow control mode, the blown-out air flowing from the air outlet 34 to the indoor space R flows in the horizontal direction.

More specifically, in the ceiling airflow control mode, the inclination angle θ1 of the virtual plane V1 with respect to the horizontal plane H is, for example, -5 °. On the other hand, in the ceiling airflow control mode, the inclination angle θ2 of the virtual plane V2 with respect to the horizontal plane H is, for example, +15°. At this time, the inclination angles θ1, θ2 are smaller than those in the first inclination airflow control mode. Conversely, the tilt angles θ1, θ2 in the first tilt airflow control mode are larger than the tilt angles θ1, θ2 in the ceiling airflow control mode. When the inclination angle θ1 is negative (-), the front side of the virtual plane V1 is located above the rear side of the virtual plane V1.

In other words, the first horizontal baffle 41 is turned 10 ° from the state when the operation of the indoor unit 1 is stopped, and assumes a posture when in the ceiling airflow control mode. On the other hand, when the second horizontal baffle 51 is rotated 15 ° from the state when the operation of the indoor unit 1 is stopped, the second horizontal baffle is in the ceiling airflow control mode.

< vertical airflow control mode >

Fig. 7 schematically shows a longitudinal section of the indoor unit 1 in which transition to the vertical airflow control mode is completed.

In the vertical airflow control mode, the blown-out air flowing from the air outlet 34 to the indoor space R flows downward along the wall surface W.

More specifically, in the vertical airflow control mode, the inclination angle θ1 of the virtual plane V1 with respect to the horizontal plane H is, for example, +105°. On the other hand, in the vertical airflow control mode, the inclination angle θ2 of the virtual plane V2 with respect to the horizontal plane H is, for example, +100°.

In other words, the first horizontal barrier 41 assumes a posture when in the vertical airflow control mode when rotated by 125 ° from the state when the operation of the indoor unit 1 is stopped. On the other hand, when the second horizontal barrier 51 is rotated 100 ° from the state when the operation of the indoor unit 1 is stopped, the second horizontal barrier is in the posture when in the vertical airflow control mode.

< second inclined airflow control mode >

Fig. 8 schematically shows a longitudinal section of the indoor unit 1 in which transition to the second inclined airflow control mode is completed.

In the second inclined airflow control mode, the interval between the first horizontal baffle 41 and the second horizontal baffle 51 is wider on the downstream side than on the upstream side of the flow of the blown air, and the blown air flowing from the air outlet 34 to the indoor space R flows obliquely downward toward the front side. In this case, the width of the blown air in the up-down direction is smaller than in the first tilt airflow control mode.

More specifically, in the second inclined airflow control mode, the inclination angle θ1 of the virtual plane V1 with respect to the horizontal plane H is, for example, -5 °. On the other hand, in the second inclined airflow control mode, the inclination angle θ2 of the virtual plane V2 with respect to the horizontal plane H is, for example, +45°. At this time, the separation angle of the first horizontal barrier 41 and the second horizontal barrier 51 is, for example, 50 °. The separation angle corresponds to an angle obtained by subtracting the inclination angle θ1 from the inclination angle θ2.

In other words, when the first horizontal baffle 41 is rotated 15 ° from the state when the operation of the indoor unit 1 is stopped, the posture is set in the second inclined airflow control mode. On the other hand, when the second horizontal baffle 51 is rotated 52.5 ° from the state when the operation of the indoor unit 1 is stopped, the second inclined airflow control mode is set to the second inclined airflow control mode. Here, the angle obtained by subtracting the rotation angle of the first horizontal barrier 41 from the rotation angle of the second horizontal barrier 51 is the separation angle of the first horizontal barrier 41 and the second horizontal barrier 51 in the second inclined airflow control mode.

< Structure of first horizontal baffle 41 >

Fig. 9 is a view of the upper wing surface 41c of the first horizontal barrier 41 as seen obliquely. Fig. 10 is a view of the upper wing surface 41c of the first horizontal barrier 41 from the front. Fig. 11 is a view of the lower wing surface 41d of the first horizontal barrier 41 from the front. Fig. 12 is a cross-sectional view as seen from line XII-XII of fig. 11. Fig. 13 is a sectional view as seen from line XIII-XIII of fig. 11. The cross-sectional view taken along line XII '-XII' in fig. 11 is the same as that in fig. 12, and therefore is not shown.

As shown in fig. 9 to 13, the first horizontal barrier 41 has the following shape: the thickness becomes thinner as approaching the second end 41b side from the first end 41a side, except for a part of the first end 41a side. The first horizontal baffle 41 has an upper airfoil surface 41c facing the casing main body 31 when the operation of the indoor unit 1 is stopped, and a lower airfoil surface 41d facing the indoor space when the operation of the indoor unit 1 is stopped.

The upper airfoil surface 41c includes a curved surface 41e that is curved to be concave in the short-side direction of the first horizontal barrier 41. In other words, when the first horizontal barrier 41 is cut along the above-described short side direction, the line indicating the cross section of the upper airfoil surface 41c includes a curved line protruding toward the lower airfoil surface 41d side. Here, the short side direction of the first horizontal barrier 41 corresponds to a direction orthogonal to the long side direction of the first horizontal barrier 41 and the thickness direction of the first horizontal barrier 41.

The lower wing surface 41d includes a curved surface 41f that is curved and swelled in the short side direction of the first horizontal barrier 41. In other words, when the first horizontal barrier 41 is cut along the above-described short side direction, the line indicating the cross section of the lower airfoil surface 41d includes a curved line that bulges to the opposite side from the upper airfoil surface 41 c.

In addition, the radius of curvature of the curved surface 41e of the upper airfoil surface 41c is set smaller than the radius of curvature of the curved surface 41f of the lower airfoil surface 41d of the first horizontal baffle plate 41.

The curved surfaces 41e and 41f are provided from one end in the longitudinal direction of the first horizontal barrier 41 to the other end in the longitudinal direction of the first horizontal barrier 41.

< Structure of second horizontal baffle plate 51 >

Fig. 14 is a view of the upper wing surface 51c of the second horizontal barrier 51 as seen obliquely. Fig. 15 is a view of the upper wing surface 51c of the second horizontal barrier 51 from the front. Fig. 16 is a view of the lower wing surface 51d of the second horizontal barrier 51 from the front. Fig. 17 is a sectional view as seen from the line XVII-XVII of fig. 16. Fig. 18 is a cross-sectional view taken along line XVIII-XVIII of fig. 16. The cross-sectional view taken along the line XV '-XV' in fig. 16 is the same as the cross-sectional view taken along the line XV '-XV' in fig. 17, and thus illustration thereof is omitted.

As shown in fig. 14 to 18, the second horizontal baffle 51 has an upper airfoil surface 51c facing the blowout flow path 37 when the operation of the indoor unit 1 is stopped, and a lower airfoil surface 51d facing the indoor space when the operation of the indoor unit 1 is stopped. In the second horizontal baffle 51, the thickness of the central portion between the first end portion 51a and the second end portion 51b is thicker than the thicknesses of the first end portion 51a and the second end portion 51 b.

The upper wing surface 51c includes a curved surface 51e that is curved and swelled in the short side direction of the second horizontal barrier 51. In other words, when the second horizontal barrier 51 is cut along the above-described short side direction, the line indicating the cross section of the upper airfoil surface 51c includes a curved line that bulges to the opposite side from the lower airfoil surface 51d. Here, the short side direction of the second horizontal barrier 51 corresponds to a direction orthogonal to the long side direction of the second horizontal barrier 51 and the thickness direction of the second horizontal barrier 51.

Further, a concave portion 51h is provided on the upper airfoil surface 51c on the second end 51b side. When the operation of the indoor unit 1 is stopped, a part of the mounting portion 38 enters the recess 51h, and the second horizontal baffle 51 does not interfere with the mounting portion 38.

The lower wing surface 51d includes a first curved surface 51f curved to be concave in the short side direction of the second horizontal baffle 51 and a second curved surface 51g curved to be convex in the short side direction of the second horizontal baffle 51. In other words, when the second horizontal baffle 51 is cut along the above-described short side direction, the line indicating the cross section of the lower airfoil surface 51d includes a bending line that bulges toward the upper airfoil surface 51c side and a bending line that bulges toward the opposite side from the upper airfoil surface 51 c.

The first curved surface 51f is provided on the second end 51b side of the lower wing surface 51d, and overlaps the curved surface 51e in the thickness direction of the second horizontal baffle 51.

The second curved surface 51g is provided on the first end 51a side of the lower airfoil surface 51d, and is connected to the first curved surface 51 f.

The radius of curvature (for example, 396mm or more) of the curved surface 51e of the upper airfoil surface 51c is set smaller than the radius of curvature (for example, 1800mm or more) of the first curved surface 51f of the lower airfoil surface 51 d. In other words, the radius of curvature of the first curved surface 51f of the lower airfoil surface 51d of the second horizontal baffle plate 51 is set in the range of 4 to 5 times the radius of curvature of the curved surface 51e of the upper airfoil surface 51c of the second horizontal baffle plate 51.

The second horizontal barrier 51 is formed so that the cross section along the short side direction is identical in shape except for both ends in the long side direction. Conversely, both ends of the second horizontal barrier 51 in the longitudinal direction have a cross-sectional shape different from the other parts of the second horizontal barrier 51.

To describe in more detail, the upper wing surface 51c at both ends in the longitudinal direction of the second horizontal barrier 51 does not include the curved surface 51e. The lower wing surface 51d at both ends in the longitudinal direction of the second horizontal baffle 51 does not include the first curved surface 51f and the second curved surface 51g. In fig. 14, a region where the curved surface 51e is formed is indicated by a broken line.

According to the air conditioner having the above configuration, when the operation (for example, the heating operation) in the first airflow control mode is performed, the interval between the first horizontal baffle 41 and the second horizontal baffle 51 is wider on the downstream side than on the upstream side of the flow of the blown air, and the blown air flows obliquely downward on the side opposite to the wall surface W side. At this time, a part of the blown air flows along the lower wing surface 41d of the first horizontal baffle 41. Since the lower airfoil surface 41d of the first horizontal baffle 41 includes the curved surface 41f that becomes convex, the coanda effect at the lower airfoil surface 41d of the first horizontal baffle 41 is improved. As a result, a part of the blown air is strongly drawn to the lower wing surface 41d of the first horizontal baffle 41, and flows along the lower wing surface 41d of the first horizontal baffle 41. On the other hand, since the upper airfoil surface 51c of the second horizontal baffle plate 51 includes the curved surface 51e that becomes convex, the coanda effect at the upper airfoil surface 51c of the second horizontal baffle plate 51 is improved. As a result, the other part of the blown air is strongly pulled up to the upper surface 51c of the second horizontal baffle 51.

In this way, a part of the blown air is strongly pulled up to the lower wing surface 41d of the first horizontal baffle 41, while another part of the blown air is strongly pulled up to the lower wing surface 51d of the second horizontal baffle 51, so that the air flow can be suppressed from being peeled off from the first and second horizontal baffles 41, 51.

When the operation in the first airflow control mode is performed, the distance between the first horizontal baffle 41 and the downstream side of the second horizontal baffle 51 is wider than the distance between the first horizontal baffle 41 and the upstream side of the second horizontal baffle 51, and the blown air flows obliquely downward on the front side, so that the blown air can be blown over a wide area, for example, the ground surface facing the indoor space R.

In a state in which the distance between the first horizontal baffle 41 and the second horizontal baffle 51 on the downstream side of the flow of the blown air is greatly increased compared to the distance between the first horizontal baffle 41 and the second horizontal baffle 51 on the upstream side of the flow of the blown air, the separation of the air flow from the first horizontal baffle 41 and the second horizontal baffle 51 can be suppressed, and therefore, the blown air can be greatly increased in the up-down direction.

In addition, a part of the air from the air outlet channel 37 flows between the housing main body 31 and the upper surface 41c of the first horizontal baffle 41 through between the front edge of the air outlet 34 and the first end 41a of the first horizontal baffle 41. At this time, since the upper airfoil surface 41c of the first horizontal baffle 41 includes the curved surface 41e that becomes a concave surface, the coanda effect at the upper airfoil surface 41c of the first horizontal baffle 41 is improved. As a result, a part of the air is drawn to the upper wing surface 41c of the first horizontal baffle 41, and flows along the upper wing surface 41c of the first horizontal baffle 41. Therefore, for example, when the air from the blowout flow path 37 is cool air, the upper airfoil surface 41c of the first horizontal baffle 41 can be covered with cool air, and dew condensation at the upper airfoil surface 41c of the first horizontal baffle 41 can be suppressed.

The other part of the air from the air outlet passage 37 flows between the wall surface W and the lower surface 51d of the second horizontal baffle 51 through between the rear edge of the air outlet 34 and the first end 51a of the second horizontal baffle 51. At this time, since the lower wing surface 51d of the second horizontal baffle plate 51 includes the curved surface 51e which becomes a concave surface, the coanda effect at the lower wing surface 51d of the second horizontal baffle plate 51 is improved. As a result, the other part of the air is drawn to the lower wing surface 51d of the second horizontal barrier 51, and flows along the lower wing surface 51d of the second horizontal barrier 51. Therefore, for example, when the air from the blowout flow path 37 is cool air, the lower airfoil surface 51d of the second horizontal baffle 51 can be covered with cool air, and dew condensation at the lower airfoil surface 51d of the second horizontal baffle 51 can be suppressed.

In the first inclined airflow control mode, the separation angle between the first horizontal baffle 41 and the second horizontal baffle 51 is set to 60 °, for example, so that the blown air can be reliably spread in the up-down direction.

In the first inclined airflow control mode, the inclination angles θ1, θ2 of the virtual planes V1, V2 with respect to the horizontal plane H become larger than in the ceiling airflow control mode, and therefore, the blown air can be reliably caused to flow obliquely downward on the front side.

In the first inclined airflow control mode, the vertical baffles 61 of the first vertical baffle group G1 are rotated so that the downstream end of the flow of the blown air approaches the left side, while the vertical baffles 61 of the second vertical baffle group G2 are rotated so that the downstream end of the flow of the blown air approaches the right side. Thus, the substantial shape of the air flow path formed by the plurality of vertical baffles 61 of the first vertical baffle group G1 and the second vertical baffle group G2 is a shape that gradually expands from the upstream side toward the downstream side of the flow of the blown air. As a result, the blown air can be expanded in the left-right direction.

In addition, since the air conditioner includes the indoor unit 1, the air flow can be prevented from being peeled off from the first horizontal baffle 41 and the second horizontal baffle 51, and thus the blown air can be expanded in the up-down direction, and the air-conditioning unevenness can be reduced.

Fig. 19 shows the results of simulation of the expansion of the blown air of the indoor unit 1 in the up-down direction in the first tilt airflow control mode.

The blown air from the indoor unit 1 expands in the vertical direction, and is blown from the upper body to the lower body of the user. Therefore, when the indoor unit 1 performs the heating operation, as shown in fig. 20, the area (the area with the deepest color in fig. 20) of the surface on the indoor unit 1 side of the user can be increased.

Fig. 21 shows the results of simulation of the expansion of the blown air of the indoor unit 1001 of the comparative example in the up-down direction.

The indoor unit 1001 of the comparative example differs from the indoor unit 1 only in that it includes a conventional first horizontal baffle and second horizontal baffle. The tilt angles of the conventional first horizontal baffle and second horizontal baffle with respect to the horizontal plane were set in the same manner as in the simulation of fig. 19. In addition, the lower wing surface and the upper wing surface of the conventional first horizontal baffle plate and the conventional second horizontal baffle plate respectively do not include a curved surface, but a flat surface.

Such air blown out from the indoor unit 1001 does not expand in the vertical direction and can be blown only to the lower body of the user. Therefore, when the indoor unit 1001 performs the heating operation, as shown in fig. 22, the area (the area with the deepest color in fig. 22) of the surface of the user on the indoor unit 1001 side is not large.

Fig. 23 is a top-bottom-left-right expanded image of the blown air of the indoor unit 1.

In a place 1m in front of the indoor unit 1, the blown air passes through a region of, for example, 1.4m in the vertical direction and 1.2m in the horizontal direction. In this case, when a person sits on a chair placed in the above-described place, as shown by the solid line in fig. 24, the variation in the wind speed of the blown air blown to each part of the person can be reduced. The wind speed of the blown air blown to each part of the person can be set to 1m/s or less. On the other hand, when the indoor unit 1001 of the comparative example is operated, as shown by the broken line in fig. 24, the variation in the wind speed of the blown air blown to each part of the person increases. In addition, even if the wind speed of the blown air blown under the knee of the person is about 1m/s, the wind speed of the blown air blown to the chest of the person exceeds 2m/s.

In this way, the indoor unit 1 can deliver gentle wind to each part of the user substantially uniformly as compared with the indoor unit 1001 of the comparative example.

Fig. 25 schematically shows a longitudinal section of the indoor unit 1 in which transition to the pre-tilt airflow control mode is completed. In addition, the pre-tilt airflow control mode is an example of the second airflow control mode.

After the operation in the pre-tilt airflow control mode is performed, the operation in the first tilt airflow control mode is performed.

More specifically, the operation (for example, the heating operation, the cooling operation, and the like) in the pre-tilt airflow control mode is performed such that the separation angle between the first horizontal baffle plate 41 and the second horizontal baffle plate 51 in the pre-tilt airflow control mode is smaller than the predetermined separation angle (for example, 60 °) between the first horizontal baffle plate 41 and the second horizontal baffle plate 51 in the first tilt airflow control mode, and the blown-out air is blown out from the air outlet 34 to the indoor space R. After the operation in the pre-tilt airflow control mode, the operation is then shifted to the first tilt airflow control mode.

When the transition to the operation in the pre-tilt airflow control mode is completed, the separation angle of the first horizontal barrier 41 and the second horizontal barrier 51 is, for example, 30 °.

In addition, in the operation of the pre-tilt airflow control mode, the rotational speed of the indoor fan 10 is higher than that in the first tilt airflow control mode. For example, when the rotational speed of the indoor fan 10 in the first diagonal air flow control mode corresponds to the intermediate air volume (the air volume that is larger than the weak air volume and smaller than the strong air volume), the rotational speed of the indoor fan 10 in the pre-diagonal air flow control mode is set to correspond to the strong air volume.

In addition, after the operation of narrowing the separation angle between the first horizontal barrier 41 and the second horizontal barrier 51 is completed from the start of the operation in the pre-tilt airflow control mode to the completion of the transition to the operation in the first tilt airflow control mode, the rotation speed of the blower fan is reduced to the rotation speed at the time of the operation in the first tilt airflow control mode.

When the first and second horizontal shutters 41 and 51 are set to the posture of fig. 25, both the first and second horizontal shutters 41 and 51 are rotated.

The first and second horizontal shutters 41 and 51 in the operation in the pre-tilt airflow control mode are rotated at a faster speed than the first and second horizontal shutters 41 and 51 in the transition from the operation in the pre-tilt airflow control mode to the operation in the first tilt airflow control mode.

In addition, the two-dot chain line in fig. 25 shows the posture of the second horizontal barrier 51 when the transition to the first inclined airflow control mode is completed.

< transition to first inclined airflow control mode >

The following describes a transition from the operation in the pre-tilt airflow control mode to the operation in the first tilt airflow control mode, with reference to the flowchart of fig. 26. The transfer is controlled by the control device 100.

For example, when the user operates the remote control to select the heating operation in the first diagonal flow control mode while the indoor unit 1 is in the operation stop state of fig. 2, the above-described process for transfer is started, and in step S1, the heating operation in the pre-diagonal flow control mode is started.

More specifically, when the heating operation in the pre-tilt airflow control mode is started, the hot blown air is blown out from the air outlet 34 into the indoor space R, and therefore the compressor 11, the indoor fan 10, and the like are operated.

Next, in step S2, the rotational speed of the indoor fan 10 is set to a high rotational speed. The high rotation speed is higher than the set rotation speed of the indoor fan 10 at the time of heating operation in the first diagonal flow control mode.

Next, in step S3, the first horizontal barrier 41 is rotated counterclockwise by 25 ° from the operation stop state of the indoor unit 1, and the second horizontal barrier 51 is rotated counterclockwise by 55 ° from the operation stop state of the indoor unit 1. Thereby, the separation angle of the first horizontal baffle 41 and the second horizontal baffle 51 is made narrower than in the first inclined airflow control mode. In short, the first and second horizontal shutters 41 and 51 are moved from the posture of fig. 5 to the posture of fig. 25.

When the first and second horizontal shutters 41 and 51 are rotated, the rotational speeds of the first and second horizontal shutters 41 and 51 are faster than the rotational speeds of the first and second horizontal shutters 41 and 51 when the operation is shifted from the heating operation in the pre-tilt airflow control mode to the operation in the first tilt airflow control mode.

Next, in step S4, it is determined whether or not a predetermined time (for example, 1 second) has elapsed since the first and second horizontal shutters 41 and 51 were in the posture of fig. 5. This step S4 is repeated until it is determined that the first horizontal barrier 41 and the second horizontal barrier 51 have elapsed a predetermined time from the posture of fig. 5.

Next, in step S5, the rotational speed of the indoor fan 10 is reduced to the set rotational speed.

Next, in step S6, the heating operation in the first diagonal flow control mode is started.

Finally, in step S7, the second horizontal barrier 51 is rotated 15 ° counterclockwise from the posture of fig. 25 while maintaining the posture of the first horizontal barrier 41. Thus, the first and second horizontal shutters 41 and 51 assume the posture of fig. 25.

In this way, when the heating operation in the first diagonal flow control mode is to be performed, the heating operation in the pre-diagonal flow control mode is performed, and then the heating operation in the pre-diagonal flow control mode is performed, and the heating operation in the first diagonal flow control mode is shifted to the heating operation in the first diagonal flow control mode, in which the separation angle between the first horizontal baffle plate 41 and the second horizontal baffle plate 51 is made narrower than the predetermined separation angle between the first horizontal baffle plate 41 and the second horizontal baffle plate 51 in the first diagonal flow control mode, and the blown air is blown out. Thereby, the transition from the pre-tilt airflow control mode to the first tilt airflow control mode is made while maintaining the coanda effect at the lower airfoil surface 41d of the first horizontal baffle 41 and the upper airfoil surface 51c of the second horizontal baffle 51. As a result, after the transition to the first inclined airflow control mode, a part of the blown-out air is caused to flow along the lower airfoil surface 41d of the first horizontal baffle plate 41, and another part of the blown-out air is caused to flow along the upper airfoil surface 51c of the second horizontal baffle plate 51. Therefore, the difference in wind speed becomes small in each portion of the blown air flowing between the lower airfoil surface 41d of the first horizontal baffle 41 and the upper airfoil surface 51c of the second horizontal baffle 51. Therefore, when the blown air is blown out to a wide area, for example, stable supply of the blown air to a wide area can be realized.

In short, by switching the heating operation in the pre-tilt airflow control mode to the heating operation in the first tilt airflow control mode, stable coanda wind can be formed in the first tilt airflow control mode.

If the heating operation in the pre-tilt airflow control mode is then shifted to the heating operation in the first tilt airflow control mode, the supply of the blown air to a wide range can be similarly reproduced.

In addition, in the heating operation in the pre-tilt airflow control mode, the rotation speed of the indoor fan 10 is made higher than that in the first tilt airflow control mode, and therefore, the coanda effect of the lower airfoil surface 41d of the first horizontal barrier 41 and the upper airfoil surface 51c of the second horizontal barrier 51 can be improved.

Further, since the rotation speed of the second horizontal barrier 51 for changing from the posture of fig. 2 to the posture of fig. 25 is faster than the rotation speed of the second horizontal barrier 51 for changing from the posture of fig. 25 to the posture of fig. 5, the separation of the air flow at the second horizontal barrier 51 can be suppressed when changing from the posture of fig. 25 to the posture of fig. 5.

Further, the air conditioning indoor unit is provided with the indoor unit 1, whereby stable supply of the blown air to a wide area can be realized.

In the first embodiment described above, the operation is shifted from the operation stop state of the indoor unit 1 to the heating operation in the first diagonal air flow control mode through the heating operation in the pre-diagonal air flow control mode, but for example, the operation may be shifted from the heating operation in the ceiling air flow control mode to the heating operation in the first diagonal air flow control mode through the heating operation in the pre-diagonal air flow control mode.

In summary, in the embodiment of the present disclosure, the transition to the first diagonal airflow control mode is performed immediately after the start of the operation of the indoor unit 1, but may be performed after passing through another airflow control mode.

In the first embodiment, the first tilt airflow control mode is selected by the user using, for example, a remote controller, but even if there is no selection by the user, for example, the control device may select the heating operation of the first tilt airflow control mode based on the detection signal of the floor temperature sensor T6 or the like. In this case, the heating operation in the first diagonal airflow control mode is automatically selected, and therefore, the convenience of the indoor unit 1 is improved.

In the first embodiment, the operation in the pre-tilt airflow control mode is the heating operation, but may be a cooling operation, a blowing operation, or the like.

In the first embodiment, the operation in the first diagonal flow control mode is the heating operation, but may be the cooling operation, the air blowing operation, or the like. In this case, the operation in the first oblique air flow control mode may be the same as the operation in the immediately preceding pre-oblique air flow control mode.

In the first embodiment, the operation in the pre-tilt airflow control mode is performed immediately before the heating operation in the first tilt airflow control mode, but the operation in the pre-tilt airflow control mode similar to the pre-tilt airflow control mode may be performed immediately before the heating operation in the first tilt airflow control mode.

In the first embodiment, the first and second horizontal shutters 41 and 51 are in the posture of fig. 25 when the transition to the operation in the pre-tilt airflow control mode is completed, but may be in a posture other than fig. 25 as long as the separation angle is narrower than that in the first tilt airflow control mode.

For example, the first horizontal barrier 41 and the second horizontal barrier 51 may be in the posture of fig. 27 when the operation to the pre-tilt airflow control mode is completed. In this case, the rotational speeds of the first and second horizontal shutters 41 and 51 for changing from the other posture to the posture of fig. 27 may be faster than the rotational speeds of the first and second horizontal shutters 41 and 51 for changing from the posture of fig. 27 to the posture of fig. 5.

The two-dot chain line in fig. 27 shows the postures of the first and second horizontal shutters 41 and 51 when the transition to the first oblique air flow control mode is completed.

For example, the first horizontal barrier 41 and the second horizontal barrier 51 may be in the posture of fig. 28 when the operation to the pre-tilt airflow control mode is completed. In this case, the rotation speed of the first horizontal barrier 41 for changing from the other posture to the posture of fig. 28 may be faster than the rotation speed of the first horizontal barrier 41 for changing from the posture of fig. 28 to the posture of fig. 5.

In addition, the two-dot chain line in fig. 28 shows the posture of the first horizontal barrier 41 when the transition to the first inclined airflow control mode is completed.

In the first embodiment, the rotation speed of the indoor fan 10 is reduced when the operation of narrowing the separation angle between the first horizontal barrier 41 and the second horizontal barrier 51 is completed from the start of the operation in the pre-tilt airflow control mode to the completion of the transition to the operation in the first tilt airflow control mode, but the rotation speed of the indoor fan 10 may be maintained without being reduced.

In the first embodiment, when the first and second horizontal shutters 41 and 51 are set to the posture of fig. 25, both the first and second horizontal shutters 41 and 51 are rotated, but only one of the first and second horizontal shutters 41 and 51 may be rotated as long as the posture immediately before the first and second horizontal shutters 41 and 51 satisfies the predetermined condition. In this case, the rotation control of the first and second horizontal shutters 41 and 51 for making the posture of fig. 25 becomes simple.

Here, when the predetermined condition is satisfied, for example, one of the first horizontal barrier 41 and the second horizontal barrier 51 may take the posture of fig. 25.

In addition, when only one of the first and second horizontal flaps 41 and 51 is rotated to reduce the separation angle of the first and second horizontal flaps 41 and 51, the one of the first and second horizontal flaps 41 and 51 may have a larger angle with respect to the wind direction of the blown air in the operation in the first oblique air flow control mode. In this case, the air flow along the larger angle is easily obtained.

Here, the wind direction is a direction parallel to a tangential line of the lower end of the inner peripheral surface of the second partition wall 36 (a direction of 45 ° with respect to the horizontal plane), and is a direction obliquely downward from the indoor unit 1.

In the first embodiment, the air conditioner is of a paired type including 1 indoor unit 1 and 1 outdoor unit 2, but may be of a multiple type including a plurality of indoor units 1 and 1 outdoor unit 2.

In the first embodiment, for example, at the time of cooling operation, dehumidifying operation, or heating operation, the control device 100 may appropriately select one of the first diagonal air flow control mode, the ceiling air flow control mode, the vertical air flow control mode, and the second diagonal air flow control mode, or may switch between these modes, based on a signal from the indoor temperature sensor T5 or the like.

In the first embodiment, for example, the user may select a desired mode from among the first diagonal air flow control mode, the ceiling air flow control mode, the vertical air flow control mode, and the second diagonal air flow control mode, for example, by a remote controller during cooling operation, dehumidifying operation, or heating operation.

In the first embodiment, the separation angle between the first horizontal baffle 41 and the second horizontal baffle 51 in the first inclined airflow control mode is set to 60 °, but may be set to other than 60 °. In this case, the separation angle is, for example, in the range of 53 ° to 60 °.

In the first embodiment, in the first diagonal flow control mode, the vertical baffle 61 disposed at the left end of the plurality of vertical baffles 61 and the vertical baffle 61 disposed at the right end of the plurality of vertical baffles 61 are spaced apart at a wider interval on the downstream side than on the upstream side, but may be spaced apart at substantially the same interval. In other words, in the first diagonal flow control mode, the control for expanding the blown air in the left-right direction may be performed, or the control for expanding the blown air in the left-right direction may not be performed.

Second embodiment

The indoor unit of the air conditioner includes a human sensor 91 that detects a distance from a human in the indoor space R. The control device 200 controls the first and second horizontal barrier motors 73, 74 based on the detection result of the human sensor 91.

More specifically, in the vertical airflow control mode, when the distance detected by the human sensor 91 is equal to or less than a predetermined distance (for example, 1 m), the control device 200 switches the vertical airflow control mode to the first airflow control mode. The distance is, for example, a distance in the front-rear direction between the indoor unit and the person.

In the air conditioner having the above configuration, in addition to the same operational effects as those of the first embodiment, when the distance detected by the human sensor 91 is equal to or less than the predetermined distance, the vertical airflow control mode is switched to the first airflow control mode, so that the air blown out from the indoor unit can be blown out directly to the person in the indoor space R at an appropriate timing.

The specific embodiments of the present disclosure have been described, but the present disclosure is not limited to the first and second embodiments and the modifications thereof, and can be implemented with various modifications within the scope of the present disclosure. For example, a part of the contents described in the first and second embodiments may be deleted or replaced as an embodiment of the present disclosure. Alternatively, the content obtained by combining the modification of the first embodiment and the second embodiment may be an embodiment of the present disclosure.

Description of the reference numerals

1 indoor unit

2 outdoor unit

10 indoor fan

11 compressor

12 four-way switching valve

13 outdoor heat exchanger

14 electric expansion valve

15 indoor heat exchanger

16 gas-liquid separator

20 outdoor fan

30 outer casing

34 air outlet

41 first horizontal baffle

41c, 51c upper airfoil surface

41d, 51d lower airfoil

41e, 41f, 51e curved surfaces

51 second horizontal baffle

51f first curved surface

51g second curved surface

61 vertical baffle

73 first horizontal baffle motor

74 second horizontal baffle motor

83 first vertical baffle group motor

84 second vertical baffle group motor

91 people sensor

100. 200 control device

G1 first vertical baffle group

G2 second vertical baffle group

L1, L2 communication piping

RC refrigerant circuit

T1 outdoor heat exchanger temperature sensor

T2 outside air temperature sensor

T3 evaporation temperature sensor

T4 indoor heat exchanger temperature sensor

T5 indoor temperature sensor

T6 ground temperature sensor

Tilt angle of theta 1 and theta 2

Claims

1. An air conditioner indoor unit (1) is characterized in that,

the air conditioning indoor unit (1) is provided with:

a housing (30) which is provided with a blow-out port (34) for blowing out air from the blower fan (10);

a first horizontal blade (41) that controls the vertical direction of the air blown out from the air outlet (34);

A first driving unit (73) for driving the first horizontal blade (41);

a second horizontal blade (51) which is disposed on the rear side of the first horizontal blade (41) and controls the vertical direction of the blown air;

a second driving unit (74) for driving the second horizontal blade (51); and

control devices (100, 200) for controlling the blower fan (10), the first driving unit (73), and the second driving unit (74),

when the control device (100, 200) is to perform an operation in a first airflow control mode, the control device is to perform an operation in a second airflow control mode, and then to transition to the operation in the first airflow control mode, wherein in the first airflow control mode, a downstream side distance between the first horizontal blade (41) and the second horizontal blade (51) is made larger than an upstream side distance, a part of the blown air is made to flow along a lower surface of the first horizontal blade (41), and another part of the blown air is made to flow along an upper surface of the second horizontal blade (51), and in the second airflow control mode, a separation angle between the first horizontal blade (41) and the second horizontal blade (51) is made to be smaller than a predetermined separation angle between the first horizontal blade (41) and the second horizontal blade (51) in the first airflow control mode,

In the operation in the second airflow control mode, the rotation speed of the blower fan (10) is made higher than that in the first airflow control mode, whereby the coanda effect at the lower airfoil surface of the first horizontal blade and the upper airfoil surface of the second horizontal blade in the second airflow control mode can be increased as compared with that in the first airflow control mode, and the second airflow control mode can be shifted to the first airflow control mode while maintaining the coanda effect at the lower airfoil surface of the first horizontal blade and the upper airfoil surface of the second horizontal blade.

2. An air conditioning indoor unit (1) according to claim 1, characterized in that,

in the operation in the second airflow control mode performed before the operation in the first airflow control mode, one of the first horizontal blade (41) and the second horizontal blade (51) is driven to narrow a separation angle between the first horizontal blade (41) and the second horizontal blade (51).

3. An air conditioning indoor unit (1) according to claim 1 or 2, characterized in that,

in the second airflow control mode, one of the first horizontal blade (41) and the second horizontal blade (51) having a larger angle with respect to the wind direction of the blown air is driven during the operation in the first airflow control mode, and the separation angle between the first horizontal blade (41) and the second horizontal blade (51) is narrowed.

4. An air conditioning indoor unit (1) according to claim 1 or 2, characterized in that,

the rotation of the first horizontal blade (41) and/or the second horizontal blade (51) during the operation in the second airflow control mode is faster than the rotation of the first horizontal blade (41) and/or the second horizontal blade (51) during the transition from the operation in the second airflow control mode to the operation in the first airflow control mode.

5. An air conditioner, characterized in that the air conditioner comprises:

an air conditioning indoor unit (1) according to any one of claims 1 to 4; and

an air conditioning outdoor unit (2) connected to the air conditioning indoor unit (1) via refrigerant pipes (L1, L2).