JP7490492B2 - Air conditioning outlet unit - Google Patents

Description

The present invention relates to an air conditioning outlet unit.

Patent Document 1 discloses an air outlet unit used in air conditioning equipment for heating and cooling the interior of a building. This air outlet unit is attached to the ceiling of a room and includes two louvers that are inclined outward from the outside of the room toward the inside of the room, and an airflow diffusion member that extends along the ceiling. As a result, the air outlet of the air outlet unit is defined as a first air outlet section located between the airflow diffusion member and the first louver, a second air outlet section located between the two louvers, and a third air outlet section located between the second louver and the outer peripheral wall.

In Patent Document 1, the narrowing ratios on the inlet and outlet sides of the louvers are further adjusted so that the conditioned air is blown out along the ceiling. The narrowing ratios that are adjusted are a first narrowing ratio, which is the ratio of the opening area of the first blowing section to the opening area of the outdoor end of the first louver, a second narrowing ratio, which is the ratio of the opening area of the second blowing section to the opening area between the outdoor ends of the two louvers, and a third narrowing ratio, which is the ratio of the opening area of the third blowing section to the opening area between the outdoor end of the second louver and the outer wall. By adjusting these narrowing ratios, the conditioned air blown out into the room prevents indoor air from coming into contact with the airflow diffusion member and the louvers, and suppresses condensation on the airflow diffusion member and the louvers during cooling.

Patent No. 4726404

The air conditioning outlet unit of Patent Document 1 can only blow out conditioned air in a direction along the ceiling due to the arrangement of the airflow diffusion member. Therefore, during heating, when conditioned air (warm air) tends to accumulate on the ceiling, it takes time to heat the area near the floor of the room. In other words, the air conditioning outlet unit of Cited Document 1 can suppress the occurrence of condensation at the outlet during cooling, but has poor air conditioning efficiency for heating the area near the floor during heating.

The objective of the present invention is to provide an air conditioning air outlet unit that can suppress the occurrence of condensation at the air outlet during cooling and can heat the area near the floor surface with good air conditioning efficiency during heating.

One aspect of the present invention includes a cylindrical duct having an air outlet at one end, through which an air current of conditioned air flows toward the air outlet, a first louver provided at the one end of the duct and consisting of a cylindrical body that spreads outward from the upstream side to the downstream side of the air current, a first air outlet section defined inside the first louver of the air outlet, a second air outlet section defined outside the first louver of the air outlet, and a first flow dividing plate provided within the duct so as to be spaced apart upstream of the air current from the first louver, consisting of a cylindrical body that spreads outward from the upstream side to the downstream side of the air current, and dividing the air current into a first branch flow directed toward the first blowing portion and a second branch flow directed toward the second blowing portion, and an expansion section which is a space provided between the first and second diverted flows and is located at a distance upstream of the airflow from the air outlet and has an opening area smaller than the opening area of the air outlet, and which is provided between the first and second diverted flows and has an opening area gradually increasing from the first and second diverted flows toward the air outlet, wherein a first conditioned air including the first diverted flow is blown out from the first air outlet in a direction along the axis of the duct, and a second conditioned air including the second diverted flow is blown out from the second air outlet at a first blowing angle inclined to the axis of the duct that depends on the inclination of the first louver, and the wind speed of the first conditioned air is faster than the wind speed of the second conditioned air.

In this embodiment, the first conditioned air is blown out from the first blowing section in a direction along the axis of the duct, so that the vicinity of the floor surface of the room can be quickly heated during heating, and the vicinity of the floor surface of the room can be quickly cooled during cooling. In addition, since the first diverting plate is cylindrical and expands outward from the upstream side to the downstream side of the airflow, the wind speed of the second diverted flow in the duct becomes slower than the wind speed of the first diverted flow due to the resistance when the airflow collides. Furthermore, since the first louver is cylindrical and expands outward from the upstream side to the downstream side of the airflow, the wind speed of the second conditioned air including the second diverted flow at the blowing outlet becomes slower than the wind speed of the first conditioned air including the first diverted flow due to the resistance when the second diverted flow collides. Due to this speed difference, the first conditioned air attracts the second conditioned air, and the downstream end of the first louver can be covered by the second conditioned air. As a result, indoor air containing a large amount of moisture can be prevented from coming into contact with the first louver, which can prevent condensation from occurring when indoor air comes into contact with the first louver and drops in temperature during cooling.

The air conditioning outlet unit of the present invention can suppress the occurrence of condensation at the outlet during cooling, and can warm the area near the floor surface with good air conditioning efficiency during heating.

1 is a cross-sectional view of an air conditioning air outlet unit according to an embodiment of the present invention. FIG. 1B is an enlarged cross-sectional view of part B of FIG. FIG. 2 is an exploded perspective view of the air conditioning outlet unit as viewed from above. FIG. 4 is an exploded perspective view of the air conditioning outlet unit as viewed from below. FIG. 1B is a plan view of FIG. 1B is a bottom view of FIG. 1A. Schematic diagram showing the experimental method.

The following describes an embodiment of the present invention with reference to the drawings.

Figure 1A shows an air conditioning air outlet unit 10 according to an embodiment of the present invention. This air outlet unit 10 is attached to the ceiling 1 of a room in a building and is connected to a main duct 5 (see Figure 5) of an air conditioning system that cools and heats the room.

The air outlet unit 10 comprises a duct 12 connected to the main duct 5, a louver set 20 attached to the air outlet 17 at one end of the duct 12, and a diffusion member 30 attached inside the duct 12. The airflow Af of the conditioned air Ca supplied from the main duct 5 into the duct 12 is diffused by the diffusion member 30 and flows toward the air outlet 17, and is blown out into the room by the louver set 20 at a predetermined air outlet angle θ1 to θ3.

As shown in Figures 1A, 2A, and 2B, the duct 12 includes a connection portion 13, an extension portion 14, and a cover 16, and is generally cylindrical with an axis A that extends linearly. The connection portion 13 and the extension portion 14 are integral resin parts, and the cover 16 is a separate resin part from the connection portion 13 and the extension portion 14.

The connection part 13 is cylindrical with a diameter that allows connection to the main duct 5. A diverter part 13a is provided at the end of the connection part 13 on the extension part 14 side, that is, at the downstream end of the connection part 13 in the direction in which the conditioned air Ca flows (airflow Af). The diverter part 13a is provided with mounting holes 13b for mounting the diffusion member 30. The mounting holes 13b are non-penetrating recesses recessed radially outward, and multiple mounting holes (four in this embodiment) are provided at intervals in the circumferential direction.

The expansion section 14 is formed between the diverter section 13a and the air outlet 17, and is a quadrangular pyramid cylinder whose opening area gradually increases from the diverter section 13a toward the air outlet 17. More specifically, the expansion section 14 is connected to the circular diverter section 13a, and the opening 14a located at the downstream end of the airflow Af of the harmonious air Ca expands to form a quadrangle. The total length D1 of the lower edge of the four walls 14b that define the opening 14a is longer than the inner diameter R1 of the diverter section 13a, and the opening area of the opening 14a is larger than the opening area of the diverter section 13a.

The center of curvature of each wall 14b constituting the expansion section 14 is located inside the duct 12 and below the lower end of the wall 14b (on the air outlet 17 side), and is curved with a set radius of curvature. Referring to FIG. 1A, the inclination angle of the wall 14b with respect to the axis A of the duct 12 is α. The inclination angle α of the wall 14b is defined as the angle between the axis A and a straight line L1 passing through the upper and lower ends of the inner surface of the wall 14b located on the axis A side. The wall 14b may be flat without being curved. The inclination angle α will be described in detail later.

The downstream end of the expansion section 14 is provided with an attachment section 15 for attaching the cover 16. Referring to FIG. 3, the attachment section 15 is square-shaped when viewed in the direction in which the axis A extends, and protrudes radially outward from the expansion section 14. A positioning recess 15a is provided at the center of each of the four outer surfaces of the attachment section 15. On both sides of the positioning recess 15a, a pressure contact section 15b that bulges in an arc shape and a slit 15c consisting of an arc-shaped groove are provided. The slit 15c allows the pressure contact section 15b to be elastically deformed. Referring to FIG. 1B, the outer surface of the attachment section 15 is provided with a locking section 15d for locking the cover 16.

As shown in Figures 1A and 1B, the cover 16 is provided to removably attach the louver set 20 to the duct 12. The cover 16 includes a rectangular cylindrical outer frame portion 16a that surrounds the outer periphery of the attachment portion 15, a rectangular end wall portion 16g that is connected to the lower end of the outer frame portion 16a, and an air outlet 17 formed in the end wall portion 16g.

The outer frame 16a is made up of four walls 16b. Each wall 16b has a first portion 16c extending along the axis A and a second portion 16d inclined inward (towards the axis A) from the first portion 16c toward the interior of the room. When the cover 16 is attached to the duct 12, the pressure contact portion 15b of the attachment portion 15 is pressure-contacted to the first portion 16c. Two of the four walls 16b facing each other are formed with positioning protrusions 16e that fit into the positioning recesses 15a. In addition, each wall 16b is provided with a locking claw 16f that locks into the locking portion 15d.

The end wall portion 16g is connected to the lower end of the outer frame portion 16a (second portion 16d) and extends perpendicular to the axis A when the cover 16 is attached to the duct 12. The end wall portion 16g is positioned with a gap between it and the attachment portion 15, and a seal member 18 is disposed between the end wall portion 16g and the attachment portion 15 to prevent leakage of the conditioned air Ca.

The air outlet 17 is a rectangular hole with a dimension D2 larger than the opening 14a. In other words, the opening area of the air outlet 17 is larger than both the opening area of the opening 14a and the opening area of the diverter 13a. When the cover 16 is attached to the duct 12, the center of the air outlet 17 is located on the axis A. A locking frame 16h for attaching the louver set 20 is provided inside the air outlet 17. The locking frame 16h protrudes from the end wall 16g toward the axis A. The inner edge of the locking frame 16h and the inner edge of the opening 14a are generally aligned in the vertical direction along which the axis A extends.

As shown in Figures 1A and 4, the louver set 20 is attached to the air outlet 17 of the cover 16 located at one end of the duct 12. The louver set 20 has two louvers 21 and 22 of different sizes, and guides the conditioned air Ca1 to Ca3 to be blown out in a specified direction in the room.

The louver set 20 defines the air outlet 17 into a first air outlet section 17a located inside the first louver 21, a second air outlet section 17b located between the two louvers 21 and 22, and a third air outlet section 17c located outside the second louver 22. The louver set 20 is configured so that the first conditioned air Ca1 is blown out from the first air outlet section 17a in a direction along the axis A (blowout angle θ1). The second air outlet section 17b is configured to blow out the second conditioned air Ca2 at a blowout angle (first blowout angle) θ2 that depends on the inclination of the first louver 21, at an inclination with respect to the axis A. The third air outlet section 17c is configured to blow out the third conditioned air Ca3 at a blowout angle (second blowout angle) θ3 that depends on the inclination of the second louver 22, at an inclination with respect to the axis A. The blowing angle θ3 of the third conditioned air Ca3 is greater than the blowing angle θ2 of the second conditioned air Ca2. Specifically, it is as follows.

The first louver 21 is a pyramidal cylindrical body that spreads outward from the upstream side to the downstream side of the airflow Af, and is composed of four inclined plates 21a. The louver set 20 is attached to the duct 12 via the cover 16, so that the center of the first louver 21 is located on the axis A.

Each inclined plate 21a is curved with a set radius of curvature, with the center of curvature located on the upper outside opposite the axis A. Referring to FIG. 1A, the inclination angle of the inclined plate 21a (first louver 21) with respect to the axis A is β1. The inclination angle β1 of the inclined plate 21a is the angle between the axis A and a straight line L2 passing through the upper and lower ends of the inner surface of the first louver 21 located on the axis A side, and is defined as the acute angle. The inclined plate 21a may be flat without being curved. The inclination angle β1 will be described in detail later.

A plurality of partition plates 23a, 23b are provided inside the first louver 21 to form a lattice pattern. The partition plates 23a are generally flat, extend in a first direction (direction perpendicular to the paper surface in FIG. 1A) perpendicular to the axis A, and are provided at intervals in a second direction (left-right direction in FIG. 1A) perpendicular to the axis A and the first direction. The partition plates 23b are generally flat, extend in the second direction, and are provided at intervals in the first direction. The thickness of the partition plates 23a, 23b is approximately 2 mm, and the interval between adjacent partition plates 23a and the interval between adjacent partition plates 23b are approximately 7.5 mm.

Continuing to refer to Figures 1A and 4, the second louvers 22 are arranged to surround the first louvers 21, and are made of a quadrangular pyramidal cylindrical body that spreads outward from the upstream side to the downstream side of the airflow Af, and are composed of four inclined plates 22a. The louver set 20 is attached to the duct 12 via the cover 16, so that the center of the second louvers 22 is located on the axis A. The second louvers 22 are connected to the first louvers 21 via the ribs 24. The upper end of the second louvers 22 is provided with a locking claw portion 25 that locks into the locking frame 16h of the cover 16.

Each inclined plate 22a is located at the upper outside with the center of curvature on the opposite side to the axis A, and is curved with a set radius of curvature. Referring to FIG. 1A, the inclination angle of the inclined plate 22a (second louver 22) with respect to the axis A is β2. The inclination angle β2 of the inclined plate 22a is defined as the acute angle between the axis A and a straight line L3 passing through the upper and lower ends of the inner surface of the second louver 22 located on the axis A side. The inclination angle β2 of the second louver 22 is larger than the inclination angle β1 of the first louver 21. The inclined plate 22a may be flat without being curved. The inclination angle β2 will be described in detail later.

As shown in Figures 1A, 2A and 2B, the diffusion member 30 is disposed in the diverting section 13a in the duct 12, and divides the airflow Af of the conditioned air Ca and diffuses it in the expansion section 14. The diffusion member 30 includes two diverting plates 31 and 32 of different sizes and four ribs 33 that unite these plates. The airflow Af in the connection section 13 is divided by the first diverting plate 31 into a first diverting flow Af1 directed toward the first blowing section 17a and a second diverting flow Af2 directed toward the second blowing section 17b, and by the second diverting plate 32 into a second diverting flow Af2 directed toward the second blowing section 17b and a third diverting flow Af3 directed toward the third blowing section 17c.

The first diverting plate 31 is a conical cylinder that spreads outward from the upstream side to the downstream side of the airflow Af. Referring to FIG. 1A, the inclination angle of the first diverting plate 31 with respect to the axis A is γ1. The inclination angle γ1 of the first diverting plate 31 is the angle between the axis A and a straight line L4 that passes through the upper and lower ends of the outer surface of the first diverting plate 31 that is located opposite the axis A, and is defined as the acute angle. Note that the first diverting plate 31 is not limited to being flat, and may be curved like the louvers 21 and 22.

The second flow dividing plate 32 is provided so as to surround the first flow dividing plate 31, and is connected to the first flow dividing plate 31 via the ribs 33. The second flow dividing plate 32 is a conical cylindrical body that spreads outward from the upstream side to the downstream side of the air flow Af. Referring to FIG. 1A, the inclination angle of the second flow dividing plate 32 with respect to the axis A is γ2. The inclination angle γ2 of the second flow dividing plate 32 is defined as the acute angle formed by the axis A and a straight line L5 passing through the upper and lower ends of the outer surface of the second flow dividing plate 32 located opposite the axis A. Note that the second flow dividing plate 32 is not limited to being flat, and may be curved like the louvers 21 and 22.

The inclination angle γ1 of the first flow dividing plate 31 and the inclination angle γ2 of the second flow dividing plate 32 are set so that the first louver 21 is located between the extension line (straight line L4) of the first flow dividing plate 31 and the extension line (straight line L5) of the second flow dividing plate 32, and the second louver 22 is located on the extension line of the second flow dividing plate 32. This allows the second flow dividing plate Af2 divided by the first flow dividing plate 31 to flow toward the second blowing section 17b, and the third flow dividing plate Af3 divided by the second flow dividing plate 32 to flow toward the third blowing section 17c.

The ribs 33 protrude radially from the outer peripheral surface of the first diverting plate 31, and further protrude radially outward through the second diverting plate 32. The diameter of a virtual circle (not shown) passing through the outer ends 33a of all the ribs 33 is larger than the inner diameter of the diverting section 13a and smaller than the outer diameter of the diverting section 13a. The outer ends 33a of the ribs 33 are inclined outward from the upstream side to the downstream side of the airflow Af. The diffusion member 30 is inserted from the opening 14a and pressed into the diverting section 13a, so that the outer ends 33a are attached to the mounting holes 13b. The first diverting plate 31 protrudes toward the upstream and downstream sides of the airflow Af relative to the ribs 33. The second diverting plate 32 protrudes toward the downstream side of the airflow Af relative to the ribs 33.

Next, we will explain the airflow Af of the conditioned air Ca supplied to the air outlet unit 10.

As shown in FIG. 1A, the airflow Af of the conditioned air Ca collides with the diffusion member 30 within the connection portion 13, and is diffused outward around the axis A due to the inclination of the flow dividers 31 and 32.

Specifically, a portion of the airflow Af is divided into a first divided flow Af1 that passes through the first flow dividing plate 31, and a second divided flow Af2 that collides with the first flow dividing plate 31 and passes outside the first flow dividing plate 31. The remaining portion of the airflow Af is divided into the aforementioned second divided flow Af2 that passes through the second flow dividing plate 32, and a third divided flow Af3 that collides with the second flow dividing plate 32 and passes outside the second flow dividing plate 32.

The first diversion flow Af1 does not collide with either of the diversion plates 31, 32, so the wind speed is hardly reduced. The second diversion flow Af2 is decelerated by the resistance when it collides with the inclined first diversion plate 31, so its wind speed is slower than that of the first diversion flow Af1. The third diversion flow Af3 is decelerated by the resistance when it collides with the inclined second diversion plate 32, so its wind speed is slower than that of the first diversion flow Af1. The reduction rate of the second diversion flow Af2 and the third diversion flow Af3 depends on the inclination angles γ1 and γ2 of the diversion plates 31 and 32.

Then, the first to third branches Af1 to Af3 pass through the expansion section 14 and collide with the louver set 20 at the air outlet 17, and are blown out in a predetermined direction in the room due to the inclination of the louvers 21 and 22.

Specifically, the first diverted flow Af1 is blown into the room from the first blowing section 17a. Due to the inclination of the first diverting plate 31, a portion of the second diverted flow Af2 is blown into the room from the first blowing section 17a, and the remaining majority of the second diverted flow Af2 is blown into the room from the second blowing section 17b. Due to the inclination of the second diverting plate 32, the third diverted flow Af3 is blown into the room from the third blowing section 17c.

The first conditioned air Ca1, including the first diverted flow Af1, is blown out from the first blowing section 17a in a direction along the axis A (blowout angle θ1). At this time, the first conditioned air Ca1 collides with the partition plates 23a and 23b of the first blowing section 17a, but because these extend along the axis A, the wind speed of the first diverted flow Af1 (first conditioned air Ca1) hardly decreases.

The second conditioned air Ca2, which includes the second diverted flow Af2, is blown out from the second blowing section 17b at a blowing angle θ2 that is greater than the blowing angle θ1 of the first conditioned air Ca1 due to the inclination of the first louver 21. At this time, the second conditioned air Ca2 is decelerated by the resistance when it collides with the inclined first louver 21, so its wind speed becomes slower than the wind speed of the first conditioned air Ca1. In other words, the second diverted flow Af2, which is slower than the first diverted flow Af1, is further decelerated by the first louver 21 and blown out as the second conditioned air Ca2.

The third conditioned air Ca3 including the third diverted flow Af3 is blown out from the third blowing section 17c at a blowing angle θ3 that is greater than the blowing angle θ2 of the second conditioned air Ca2 due to the inclination of the second louver 22. At this time, the third conditioned air Ca3 is decelerated by the resistance when it collides with the second louver 22. Because the inclination angle β2 of the second louver 22 is greater than the inclination angle β1 of the first louver 21, the wind speed of the third conditioned air Ca3 is slower than the wind speed of the second conditioned air Ca2. In other words, the third diverted flow Af3, which is slower than the first diverted flow Af1, is further decelerated by the second louver 22 and blown out as the third conditioned air Ca3.

In this way, the diffusion member 30 and the louver set 20 cause the wind speeds V1 to V3 of the conditioned air Ca1 to Ca3 blown out from the individual blowing sections 17a to 17c to be such that the wind speed V1 of the first conditioned air Ca1 is the fastest and the wind speed V3 of the third conditioned air Ca3 is the slowest. The inventors of the present application conducted extensive experiments to prevent condensation on the louvers 21 and 22, and found the optimal effective range for the wind speed ratio of the wind speeds V1 to V3 of the conditioned air Ca1 to Ca3.

Specifically, as shown in FIG. 1B, the first conditioned air Ca1 attracts the second conditioned air Ca2, which covers the downstream end of the first louver 21, thereby preventing condensation caused by the indoor air coming into contact with the first louver 21 and dropping in temperature. To achieve this, the wind speed ratio V2/V1 between the wind speed V1 of the first conditioned air Ca1 and the wind speed V2 of the second conditioned air Ca2 is set to satisfy the following formula.

[Equation 1]
0.20≦V2/V1≦0.60
V1: Wind speed of the first conditioned air V2: Wind speed of the second conditioned air

The second conditioned air Ca2 attracts the third conditioned air Ca3, which covers the downstream end of the second louver 22, preventing condensation caused by the indoor air coming into contact with the second louver 22 and dropping in temperature. To achieve this, the wind speed ratio V3/V2 between the wind speed V2 of the second conditioned air Ca2 and the wind speed V3 of the third conditioned air Ca3 is set to satisfy the following formula.

[Equation 2]
0.15≦V3/V2≦0.75
V2: Wind speed of the second conditioned air V3: Wind speed of the third conditioned air

By setting the wind speeds V1 to V3 of the conditioned air Ca1 to Ca3 within the effective range described above, it is possible to prevent the indoor air from coming into contact with the louvers 21 and 22 due to the airflow of the conditioned air Ca1 to Ca3. This makes it possible to prevent condensation from occurring when the indoor air comes into contact with the louvers 21 and 22 during cooling and drops in temperature.

In order to set the wind speeds V1 to V3 of the conditioned air Ca1 to Ca3 within the effective range described above, the flow dividing section 13a, the air outlet 17, the louvers 21 and 22, and the flow dividing plates 31 and 32 are configured as follows.

Referring to Figure 1A, the dimension D2 of one side of the air outlet 17 is larger than the inner diameter R1 of the diverter section 13a, and an extension section 14 is formed between them. The inclination angle α of the wall 14b of the extension section 14 is preferably set to 15 degrees or more and 20 degrees or less, and is set to 15 degrees in this embodiment. If the inclination angle α is made too large, the diverters Af2 and Af3 will diffuse too much, so that the wind speeds V2 and V3 and the air volumes of the second and third conditioned air Ca2 and Ca3 blown out from the second and third blowing sections 17b and 17c will become too small, and the wind speed ratios V2/V1 and V3/V2 will be outside the effective range. If the inclination angle α is made too small, the diffusion of the divided flows Af2 and Af3 will be too small, so the wind speeds V2 and V3 and the air volume of the second conditioned air Ca2 and the third conditioned air Ca3 blown out from the second blowing section 17b and the third blowing section 17c will be too large, and the wind speed ratios V2/V1 and V3/V2 will be outside the effective range. Therefore, it is preferable to set the inclination angle α of the wall 14b of the extension section 14 within the above-mentioned specified range.

The inclination angle β1 of the first louver 21 relative to the axis A of the duct 12 is preferably set to 20 degrees or more and 30 degrees or less, and is set to 30 degrees in this embodiment. If the inclination angle β1 is made too small, the angle difference between the blowing angle θ2 of the second conditioned air Ca2 and the blowing angle θ3 of the third conditioned air Ca3 becomes large, making it difficult for the second conditioned air Ca2 to attract the third conditioned air Ca3, and there is a risk of condensation occurring on the second louver 22. If the inclination angle β1 is made too large, the angle difference between the blowing angle θ1 of the first conditioned air Ca1 and the blowing angle θ2 of the second conditioned air Ca2 becomes large, making it difficult for the first conditioned air Ca1 to attract the second conditioned air Ca2, and there is a risk of condensation occurring on the first louver 21. Therefore, it is preferable to set the inclination angle β1 of the first louver 21 within the above-mentioned specified range.

The inclination angle β2 of the second louver 22 relative to the axis A of the duct 12 is preferably set to 65 degrees or more and 70 degrees or less, and is set to 68 degrees in this embodiment. If the inclination angle β2 is made too small, the third conditioned air Ca3 cannot be blown out along the cover 16, and there is a risk that the indoor air will come into contact with the cover 16 and condensation will occur on the cover 16. If the inclination angle β2 is made too large, the angle difference between the blowing angle θ2 of the second conditioned air Ca2 and the blowing angle θ3 of the third conditioned air Ca3 will become large, making it difficult for the second conditioned air Ca2 to attract the third conditioned air Ca3, and there is a risk that condensation will occur on the second louver 22. Therefore, it is preferable to set the inclination angle β2 of the second louver 22 within the above-mentioned specified range.

The inclination angle γ1 of the first flow dividing plate 31 with respect to the axis A of the duct 12 is preferably set to 25 degrees or more and 40 degrees or less, and is set to 30 degrees in this embodiment. The inclination angle γ2 of the second flow dividing plate 32 with respect to the axis A of the duct 12 is preferably set to 25 degrees or more and 40 degrees or less, and is set to 30 degrees in this embodiment. If the inclination angles γ1 and γ2 are made too small, the deceleration and diffusion of the divided flows Af2 and Af3 will be insufficient, and the wind speed ratios V2/V1 and V3/V2 will be outside the effective range. If the inclination angles γ1 and γ2 are made too large, the deceleration and diffusion of the divided flows Af2 and Af3 will be excessive, and the wind speed ratios V2/V1 and V3/V2 will also be outside the effective range. Therefore, it is preferable to set the inclination angle γ1 of the first flow dividing plate 31 and the inclination angle γ2 of the second flow dividing plate 32 within the above-mentioned ranges.

In the air outlet unit 10 of this embodiment, the inner diameter R1 of the diverter 13a is set to 93 mm, and the dimension D2 of the air outlet 17 is set to 133.2 mm. In addition, the total length D1 of the lower edge of the wall 14b that defines the opening 14a is set to 115.5 mm.

In this case, the total length D3 of the expansion section 14, which is the dimension in the direction in which the axis A extends, is preferably set in the range of 35 mm to 50 mm, and is set to 42 mm in this embodiment. If the total length D3 of the expansion section 14 is made too small, the diffusion of the divided flows Af2 and Af3 will be insufficient, and the wind speed ratios V2/V1 and V3/V2 of the conditioned air Ca1 to Ca3 will be outside the effective range. If the total length D3 of the expansion section 14 is made too large, the diffusion of the divided flows Af2 and Af3 will be excessive, and the wind speed ratios V2/V1 and V3/V2 of the conditioned air Ca1 to Ca3 will also be outside the effective range. Therefore, it is preferable to set the total length D3 of the expansion section 14 within the above-specified range.

As described above, the dimension of one side of the square-shaped air outlet 17 is D2. In contrast, the dimension of one side of the first air outlet 17a is D4, the dimension of one side of the second air outlet 17b is D5, and the dimension of one side of the third air outlet 17c is D6. The dimension D4 of the first air outlet 17a is defined as the distance between the inner edges of the upstream ends of the opposing first louvers 21. The dimension D5 of the second air outlet 17b is defined as the distance between the outer edge of the first louver 21 and the inner edge of the second louver 22 at the upstream ends of the louvers 21 and 22. The dimension D5 of the third air outlet 17c is defined as the distance between the outer edge of the second louver 22 and the inner edge of the air outlet 17 at the upstream end of the second louver 22.

The ratio of the opening area of the first blowing section 17a based on the dimension D4 to the opening area of the blowing outlet 17 based on the dimension D2 is 45% or more and 55% or less. The ratio of the opening area of the second blowing section 17b based on the dimension D5 to the opening area of the blowing outlet 17 is 20% or more and 25% or less. The ratio of the opening area of the third blowing section 17c based on the dimension D6 to the opening area of the blowing outlet 17 is 5% or more and 10% or less. The opening area of the blowing outlet 17 includes the opening areas of the first blowing section 17a, the second blowing section 17b, and the third blowing section 17c, as well as the occupied areas of the two louvers 21 and 22 (ratio of approximately 20%). However, the occupied areas of the lattice-shaped partition plates 23a and 23b are not included.

If the ratio of the opening area of the first blowing section 17a is made too small, the wind speed ratio V2/V1 of the conditioned air Ca1, Ca2 will be outside the effective range, and the air volume required for temperature control near the floor surface of the room will not be obtained. If the ratio of the opening area of the first blowing section 17a is made too large, the air volume cannot be secured at the second blowing section 17b and the third blowing section 17c, and condensation may occur at the louvers 21, 22. Therefore, it is preferable that the ratio of the opening area of the first blowing section 17a to the opening area of the blowing port 17 is set within the above-mentioned specified range.

If the proportion of the opening area of the second blowing section 17b is made too small, the air volume at the second blowing section 17b cannot be secured, and the wind speed ratios V2/V1 and V3/V2 of the conditioned air Ca1 to Ca3 fall outside the effective range. If the proportion of the opening area of the second blowing section 17b is made too large, the wind speed ratios V2/V1 and V3/V2 of the conditioned air Ca1 to Ca3 also fall outside the effective range. Therefore, it is preferable that the proportion of the opening area of the second blowing section 17b to the opening area of the blowing port 17 is set within the above-mentioned specified range.

If the proportion of the opening area of the third blowing section 17c is made too small, the air volume at the third blowing section 17c cannot be secured, and condensation may occur on the cover 16. If the proportion of the opening area of the third blowing section 17c is made too large, the wind speed ratio V3/V2 of the conditioned air Ca2, Ca3 falls outside the effective range. Therefore, it is preferable that the proportion of the opening area of the third blowing section 17c to the opening area of the blowing port 17 is set within the above-mentioned specified range.

As described above, in the air outlet unit 10 of this embodiment, the inner diameter R1 of the diverter section 13a, the total length D3 of the expansion section 14, the dimension D2 of the air outlet 17, and the opening ratio of each of the air outlet sections 17a to 17c are set within the appropriate ranges described above, and the inclination angles γ1 and γ2 of the louvers 21 and 22 are set within the appropriate ranges described above. In this air outlet unit 10, the inner diameter of the upstream end of the first diverter plate 31 is R2, and the inner diameter of the upstream end of the second diverter plate 32 is R3. The inner diameter of the downstream end of the first diverter plate 31 is R4, and the inner diameter of the downstream end of the second diverter plate 32 is R5.

The ratio of the opening area of the upstream end of the first flow dividing plate 31 based on the inner diameter R2 to the opening area of the flow dividing section 13a based on the inner diameter R1 is 0.5% to 2.5%. The ratio of the opening area between the upstream ends of the two flow dividing plates 31 and 32 based on the inner diameters R2 and R3 and the thickness (2 mm) of the first flow dividing plate 31 to the opening area of the flow dividing section 13a is 25% to 30%. The ratio of the opening area of the outer side of the upstream end of the second flow dividing plate 32 based on the inner diameter R3 and the thickness (2 mm) of the second flow dividing plate 32 to the opening area of the flow dividing section 13a is 53% to 61%. The opening area of the flow dividing section 13a includes the occupied areas of the two flow dividing plates 31 and 32 and the rib 33 (ratio is approximately 15%).

The ratio of the opening area of the downstream end of the first flow dividing plate 31 based on the inner diameter R4 to the opening area of the flow dividing section 13a based on the inner diameter R1 is 6% to 11%. The ratio of the opening area between the downstream ends of the two flow dividing plates 31, 32 based on the inner diameters R4, R5 and the thickness (2 mm) of the first flow dividing plate 31 to the opening area of the flow dividing section 13a is 35% to 39%. The ratio of the opening area of the outer downstream end of the second flow dividing plate 32 based on the inner diameter R4 and the thickness (2 mm) of the second flow dividing plate 32 to the opening area of the flow dividing section 13a is 39% to 45%. The opening area of the flow dividing section 13a includes the occupied areas of the two flow dividing plates 31, 32 and the rib 33 (ratio is approximately 15%).

If the opening area on the upstream side of the flow dividing plates 31, 32 is made excessively small and the opening area on the downstream side of the flow dividing plates 31, 32 is made excessively large, the inclination angles γ1, γ2 of the first flow dividing plate 31 become large, and the deceleration and diffusion of the diverted flows Af2, Af3 become excessive. If the opening area on the upstream side of the flow dividing plates 31, 32 is made excessively large and the opening area on the downstream side of the flow dividing plates 31, 32 is made excessively small, the inclination angles γ1, γ2 of the first flow dividing plate 31 become small, and the deceleration and diffusion of the diverted flows Af2, Af3 become insufficient. Therefore, it is preferable to set the ratio of the opening area of each part partitioned by the flow dividing plates 31, 32 to the opening area of the flow dividing section 13a to the above-mentioned specified range.

As shown in FIG. 1B, in the air outlet unit 10 configured in this manner, the first conditioned air Ca1 including the first diverted flow Af1 is blown out from the first blowing section 17a along the axis A of the duct 12. The third conditioned air Ca2 including the second diverted flow Af2 is blown out from the second blowing section 17b at a blowing angle θ2 inclined relative to the axis A of the duct 12. The third conditioned air Ca3 including the third diverted flow Af3 is blown out from the third blowing section 17c at a blowing angle θ3 further inclined relative to the axis A of the duct 12.

Of the wind speeds V1 to V3 of the individual conditioned air Ca1 to Ca3, the wind speed V1 of the first conditioned air Ca1 is the fastest, and the wind speed V3 of the third conditioned air Ca3 is the slowest. Moreover, the wind speed ratio between the wind speed V1 of the first conditioned air Ca1 blown out from the first blowing section 17a and the wind speed V2 of the second conditioned air Ca2 satisfies 0.20≦V2/V1≦0.60. Moreover, the wind speed ratio between the wind speed V2 of the second conditioned air Ca2 blown out from the second blowing section 17b and the wind speed V3 of the third conditioned air Ca3 satisfies 0.15≦V3/V2≦0.75.

Therefore, the first conditioned air Ca1 can attract a part of the second conditioned air Ca2, which can cover the downstream end of the first louver 21. Also, the second conditioned air Ca2 can attract a part of the third conditioned air Ca3, which can cover the downstream end of the second louver 22. Therefore, the conditioned air Ca1 to Ca3 can prevent the indoor air from coming into contact with the air outlet unit 10. As a result, during cooling, it is possible to prevent condensation from occurring as the indoor air comes into contact with the air outlet unit 10 and drops in temperature.

The air outlet unit 10 configured in this manner has the following features:

The first conditioned air Ca1 is blown out from the first blowing section 17a along the axis A of the duct 12, so that the area near the floor of the room can be quickly heated during heating, and the area near the floor of the room can be quickly cooled during cooling.

Because the first diverter plate 31 provided in the duct 12 is inclined, the wind speed of the second diverter Af2 in the duct 12 becomes slower than the wind speed of the first diverter Af1 due to the resistance when the airflow Af collides. Also, because the first louver 21 is inclined, the wind speed V2 of the second conditioned air Ca2 including the second diverter Af2 at the air outlet 17 becomes slower than the wind speed V1 of the first conditioned air Ca1 including the first diverter Af1 due to the resistance when the second diverter Af2 collides. Due to the speed difference between the first conditioned air Ca1 and the second conditioned air Ca, the first conditioned air Ca1 attracts the second conditioned air Ca2, and the second conditioned air Ca2 can cover the downstream end of the first louver 21. As a result, indoor air containing a lot of moisture can be prevented from coming into contact with the first louver 21, and condensation caused by the indoor air coming into contact with the first louver 21 and dropping in temperature during cooling can be prevented.

Between the diverter section 13a and the air outlet 17, an expansion section 14 with a gradually expanding opening area is formed, so that the diverters Af1 and Af2 separated by the first diverter plate 31 can be effectively diffused in the expansion section 14 with an expanded opening area. In addition, the wind speed of the second diverter Af2 inclined with respect to the axis A of the duct 12 can be reliably made slower than the wind speed of the first diverter Af1 along the axis A of the duct 12.

The wind speed ratio between the wind speed V1 of the first conditioned air Ca1 and the wind speed V2 of the second conditioned air Ca2 satisfies 0.20≦V2/V1≦0.60, so the first conditioned air Ca1 can reliably attract the second conditioned air Ca2, and the second conditioned air Ca2 can reliably cover the downstream end of the first louver 21.

Since the inclination angle γ1 of the first diversion plate 31 is between 25 degrees and 40 degrees, the airflow Af can be reliably diffused so that the wind speed of the second diversion Af2 is slower than the wind speed of the first diversion Af1.

Since the inclination angle β1 of the first louver 21 is between 20 degrees and 30 degrees, the wind speed ratio V2/V1 can be reliably obtained, which allows the first conditioned air Ca1 to attract the second conditioned air Ca2 and prevent condensation.

The second louver 22 is inclined so that the third conditioned air Ca3 is blown out from the third blowing section 17c at a blowing angle θ3 that is larger than the blowing angle θ2 at the second blowing section 17b. Therefore, due to the resistance when the third branch flow Af3 collides, the wind speed V3 of the third conditioned air Ca3 becomes slower than the wind speed V2 of the second conditioned air Ca2. Therefore, due to the speed difference between the second conditioned air Ca2 and the third conditioned air Ca3, the second conditioned air Ca2 attracts the third conditioned air Ca3, and the third conditioned air Ca3 can cover the downstream end of the second louver 22. As a result, indoor air can be prevented from coming into contact with the second louver 22, and condensation caused by the indoor air coming into contact with the second louver 22 and dropping in temperature during cooling can be prevented.

The wind speed ratio between the wind speed V2 of the second conditioned air Ca2 and the wind speed V3 of the third conditioned air Ca3 satisfies 0.15≦V3/V2≦0.75, so the second conditioned air Ca2 can reliably attract the third conditioned air Ca3, and the third conditioned air Ca3 can reliably cover the downstream end of the second louver 22.

Since the inclination angle γ2 of the second diversion plate 32 is between 25 degrees and 40 degrees, the airflow Af can be reliably diffused so that the wind speed V3 of the third diversion Af3 is slower than the wind speed V1 of the first diversion Af1.

Since the inclination angle β2 of the second louver 22 is between 65 degrees and 70 degrees, the second conditioned air Ca2 can attract the third conditioned air Ca3, ensuring the wind speed ratio V3/V2 that prevents condensation.

The ratio of the opening area of the first blowing section 17a to the opening area of the blowing outlet 17 is set to the appropriate range described above, so that the area near the floor surface of the room can be quickly cooled or heated. Also, the ratio of the opening area of the second blowing section 17b to the opening area of the blowing outlet 17 and the ratio of the opening area of the third blowing section 17c are set to the appropriate range described above, so that in addition to the wind speed ratios V2/V1 and V3/V2, the first blowing section 17a has the highest air volume ratio and the third blowing section 17c has the lowest air volume ratio. As a result, the first conditioned air Ca1 can reliably attract the second conditioned air Ca2, and the second conditioned air Ca2 can reliably attract the third conditioned air Ca3.

In addition, the ratio of the opening area of the inside of the first flow dividing plate 31, the ratio of the opening area between the two flow dividing plates 31 and 32, and the ratio of the opening area of the outside of the second flow dividing plate 32 to the opening area of the flow dividing section 13a are set within the appropriate ranges described above, so that the divided flows Af1 to Af3 adjusted to a predetermined wind speed can be guided to the blowing sections 17a to 17c, respectively. Therefore, the wind speed ratios V2/V1 and V3/V2 of the conditioned air Ca1 to Ca3 can be set within the effective range.

As described above, the air outlet unit 10 of this embodiment blows out the first conditioned air Ca1 along the axis A of the duct 12, so that the temperature near the floor surface can be cooled or heated quickly. In addition, the speed difference is set for the conditioned air Ca1 to Ca3 blown out from the blowing sections 17a to 17c, and in particular, the wind speed ratio is set to 0.20≦V2/V1≦0.60, 0.15≦V3/V2≦0.75, so that condensation during cooling can be prevented. In order to confirm the effect on condensation, the inventors conducted an experiment with reference to the description in the book "Planning and Design of Low-Temperature Air-Blowing Air-Conditioning Systems" published on December 25, 2003, by the Society of Heating, Air-Conditioning and Sanitary Engineers of Japan.

(Experimental Example)
As shown in Fig. 5, a two-chamber air-conditioned room was used, which was divided into a first test room 2 and a second test room 3, and a main duct 5 was inserted through a wall 4 separating the test rooms 2 and 3, so that the test rooms 2 and 3 were connected to each other via the main duct 5. A blower (Suiden SJF-300L-3) 6 was installed in the first test room 2 so as to be located at one end of the main duct 5, so that air in the first test room 2 could be supplied to the second test room 3 through the main duct 5. A wooden frame 7 was installed in the second test room 3, and the other end of the main duct 5 was connected to an air outlet unit 10 attached to the ceiling 1 of the wooden frame 7.

Anemometers (Testo hot wire anemometer testo425 manufactured by Testo) 8a-8c were attached to the first blowing section 17a to the third blowing section 17c of the blowing outlet unit 10 to measure the wind speeds V1-V3 of the conditioned air Ca1-Ca3. In addition, to check whether the second conditioned air Ca2 was being drawn in by the first conditioned air Ca1, and whether the third conditioned air Ca3 was being drawn in by the second conditioned air Ca2, a smoke generator 9 (ANTARI Z-1000II) was installed at the intake of the blower 6, and a super slow motion camera (SONY FDR-AX700) was installed in the second test room 3 to film the movement of the smoke blowing out of the blowing outlet unit 10.

After adjusting the temperature of the first test room 2 to 10°C and the temperature of the second test room 3 to 30°C and 65% humidity, the blower 6 was driven to blow the air from the first test room 2 through the main duct 5 and out of the air outlet unit 10 of the second test room 3, and this state was maintained for six hours. Then, the wind speed ratios V2/V1 and V3/V2 were calculated from the wind speeds V1-V3 measured by the anemometers 8a-8c, and the presence or absence of entrainment of conditioned air Ca2 and Ca3 and the presence or absence of dripping of condensation water onto the floor surface of the second test room 3 after six hours were evaluated. The results are shown in Table 1 below.

In Table 1, invention products 1 to 5 are air outlet units 10 in which both the wind speed ratios V2/V1 and V3/V2 are within the effective range described above. Comparison products 1 to 3 are air outlet units 10 in which the wind speed ratio V2/V1 is outside the effective range described above. In the case of invention products 1 to 5, the entrainment of conditioned air Ca2 and Ca3 was confirmed in the airflow visualization test using smoke, and no dripping of condensation water was observed on the floor surface of the wooden frame 7 in the condensation test. In the case of comparison products 1 to 3, the entrainment of conditioned air Ca2 and Ca3 was not confirmed in the airflow visualization test using smoke, and dripping of condensation water was observed on the floor surface of the wooden frame 7 in the condensation test.

From the results of this experiment, it was confirmed that, of the wind speeds V1 to V3 of the conditioned air Ca1 to Ca3 blown out from the air outlet unit 10, it is preferable that wind speed V1 is the fastest and wind speed V3 is the slowest, and it is more preferable that the wind speed ratios V2/V1 and V3/V2 satisfy 0.20≦V2/V1≦0.60 and 0.15≦V3/V2≦0.75. It was also confirmed that setting the wind speed ratio V2/V1 within the aforementioned effective range is effective in preventing condensation. It was also confirmed that by doing so, it is possible to suppress the occurrence of condensation at the air outlet 17 during cooling, and to heat the area near the floor surface with good air conditioning efficiency during heating.

The air conditioning outlet unit 10 of the present invention is not limited to the configuration of the above embodiment, and various modifications are possible.

For example, the air outlet 17 and the louvers 21, 22 are not limited to a square shape, but may be circular or a polygonal shape other than a square shape. Also, the connection portion 13 (flow dividing portion 13a) and the flow dividing plates 31, 32 are not limited to a circle shape, but may be rectangular or a polygonal shape other than a square shape.

The louver set 20 may be formed of the first louvers 21 and the partition plates 23a and 23b, without providing the second louvers 22. A third louver may be provided to surround the second louvers 22, and the number of louvers can be changed as required. The diffusion member 30 may be formed of the first flow dividing plate 31 and ribs 33, without providing the second flow dividing plate 32. A third flow dividing plate may be provided to surround the second flow dividing plate 32, and the number of flow dividing plates can be changed as required.

REFERENCE SIGNS LIST 1 ceiling 2 first test chamber 3 second test chamber 4 wall 5 main duct 6 blower 7 wooden frame 8a-8c anemometer 9 smoke generator 10 air conditioning outlet unit 12 duct 13 connection section 13a diverter section 13b mounting hole 14 extension section 14a opening 14b wall 15 mounting section 15a positioning recess 15b pressure contact section 15c slit 15d locking section 16 cover 16a outer frame section 16b wall section 16c first section 16d second section 16e positioning protrusion 16f locking claw 16g end wall section 16h locking frame 17 outlet 17a first blowing section 17b second blowing section 17c third blowing section 20 louver set 21 First louver 21a Inclined plate 22 Second louver 22a Inclined plate 23a, 23b Partition plate 24 Rib 25 Locking claw portion 30 Diffusion member 31 First flow dividing plate 32 Second flow dividing plate 33 Rib 33a Outer end α Incline angle of duct wall β1 Incline angle of first louver β2 Incline angle of second louver γ1 Incline angle of first flow dividing plate γ2 Incline angle of second flow dividing plate Ca Conditioned air Ca1 First conditioned air Ca2 Second conditioned air Ca3 Third conditioned air Af Air flow Af1 First branch Af2 Second branch Af3 Third branch θ1: Blowing angle of first conditioned air θ2: Blowing angle of second conditioned air (first blowing angle)
θ3: Third conditioned air blowing angle (second blowing angle)

Claims (13)

a cylindrical duct having an air outlet at one end, through which an airflow of conditioned air flows toward the air outlet;
a first louver provided at the one end of the duct and made of a cylindrical body expanding outward from the upstream side toward the downstream side of the airflow;
A first air outlet portion defined inside the first louver of the air outlet;
A second blowing section defined outside the first louver of the blowing port;
a first flow dividing plate that is provided in the duct so as to be located on the upstream side of the airflow with a gap therebetween relative to the first louver, the first flow dividing plate being a cylindrical body that spreads outward from the upstream side toward the downstream side of the airflow, and that divides the airflow into a first flow dividing portion directed toward the first blowing portion and a second flow dividing portion directed toward the second blowing portion,
The duct is
a flow dividing portion in which the first flow dividing plate is provided, the flow dividing portion being located on the upstream side of the airflow with a gap with respect to the air outlet and having an opening area smaller than an opening area of the air outlet;
an expansion section that is provided between the diverter section and the air outlet, the opening area of which gradually increases from the diverter section toward the air outlet, and which is a space that diffuses the first diverted flow and the second diverted flow;
having
The first conditioned air including the first branched flow is blown out from the first blowing portion in a direction along an axis of the duct,
The second conditioned air including the second branched flow is blown out from the second blowing portion at a first blowing angle depending on an inclination of the first louver, and is inclined with respect to an axis of the duct;
The air conditioning outlet unit, wherein the wind speed of the first conditioned air is faster than the wind speed of the second conditioned air. The air-conditioning air outlet unit according to claim 1 , wherein a wind speed ratio between a wind speed of the first conditioned air and a wind speed of the second conditioned air satisfies the following:
0.20≦V2/V1≦0.60
V1: Wind speed of the first conditioned air V2: Wind speed of the second conditioned air 3. The air-conditioning outlet unit according to claim 1 , wherein an inclination angle of the first flow dividing plate with respect to an axis of the duct is equal to or greater than 25 degrees and is equal to or smaller than 40 degrees. The air-conditioning outlet unit according to claim 1 , wherein an inclination angle of the first louver with respect to an axis of the duct is equal to or greater than 20 degrees and equal to or less than 30 degrees. a second louver that is provided at the one end of the duct so as to surround the first louver, that is made of a cylindrical body that spreads outward from the upstream side toward the downstream side of the airflow, and that defines the second blowing section together with the first louver;
A third blowing section defined outside the second louver of the air outlet;
a second flow dividing plate that is provided in the duct so as to surround the first flow dividing plate, that is made of a cylindrical body that spreads outward from the upstream side toward the downstream side of the airflow, and that divides the airflow into the second flow dividing plate and a third flow dividing plate directed toward the third blowing portion,
the third conditioned air including the third branch is blown out from the third blowing portion at a second blowing angle that depends on an inclination of the second louver and is greater than the first blowing angle, and is inclined with respect to the axis of the duct;
The air conditioning air outlet unit according to claim 1 , wherein a wind speed of the third conditioned air is slower than a wind speed of the second conditioned air. a cylindrical duct having an air outlet at one end, through which an airflow of conditioned air flows toward the air outlet;
a first louver provided at the one end of the duct and made of a cylindrical body expanding outward from the upstream side toward the downstream side of the airflow;
a second louver provided at the one end of the duct so as to surround the first louver and made of a cylindrical body expanding outward from the upstream side toward the downstream side of the airflow;
A first air outlet portion defined inside the first louver of the air outlet;
A second blowing section defined outside the first louver of the blowing port;
A third blowing section defined outside the second louver of the air outlet;
a first flow dividing plate that is provided in the duct so as to be located upstream of the airflow relative to the first louver, the first flow dividing plate being a cylindrical body that spreads outward from the upstream side toward the downstream side of the airflow, and that divides the airflow into a first flow dividing portion directed toward the first blowing portion and a second flow dividing portion directed toward the second blowing portion;
Equipped with
In a direction in which the airflow flows, a downstream end of the second louver protrudes further than a downstream end of the first louver,

The wind speed of the first conditioned air blown out from the first blowing portion is faster than the wind speed of the second conditioned air blown out from the second blowing portion,
The air speed of the third conditioned air blown out from the third blowing portion is slower than that of the second conditioned air. 7. The air conditioning air outlet unit according to claim 6, further comprising a second air diversion plate arranged in the duct to surround the first air diversion plate, the second air diversion plate being a cylindrical body that widens outward from the upstream side to the downstream side of the air flow, and dividing the air flow into the second diversion plate and a third diversion plate directed toward the third blowing section. The air conditioning air outlet unit according to claim 5 , wherein a wind speed ratio between a wind speed of the second conditioned air and a wind speed of the third conditioned air satisfies the following:
0.15≦V3/V2≦0.75
V2: Wind speed of the second conditioned air V3: Wind speed of the third conditioned air The air-conditioning outlet unit according to claim 5 or 7, wherein an inclination angle of the second flow dividing plate with respect to an axis of the duct is equal to or greater than 25 degrees and equal to or less than 40 degrees. The air-conditioning outlet unit according to claim 5 , wherein an inclination angle of the second louver with respect to an axis of the duct is equal to or greater than 65 degrees and equal to or less than 70 degrees. A ratio of an opening area of the first blowing section to an opening area of the blowing port is 45% or more and 55% or less,
The ratio of the opening area of the second blowing section to the opening area of the blowing port is 20% or more and 25% or less,
A ratio of an opening area of the third blowing section to an opening area of the blowing port is 5% or more and 10% or less.
The air-conditioning outlet unit according to any one of claims 5 to 10 . A ratio of an opening area of the inside of the upstream end of the first flow dividing plate to an opening area of the flow dividing portion of the duct provided with the first flow dividing plate and the second flow dividing plate is 0.5% or more and 2.5% or less,
The ratio of an opening area between the upstream end of the first flow dividing plate and the upstream end of the second flow dividing plate to an opening area of the flow dividing portion of the duct is 25% or more and 30% or less,
The ratio of the opening area of the upstream end outer side of the second flow dividing plate to the opening area of the flow dividing portion of the duct is 53% or more and 61% or less.
10. The air-conditioning outlet unit according to claim 5, 7 or 9. The ratio of the opening area of the downstream end inner side of the first flow dividing plate to the opening area of the flow dividing portion of the duct is 6% or more and 11% or less,
The ratio of the opening area between the downstream end of the first flow dividing plate and the downstream end of the second flow dividing plate to the opening area of the flow dividing portion of the duct is 35% or more and 39% or less,
The ratio of the opening area of the downstream end outer side of the second flow dividing plate to the opening area of the flow dividing portion of the duct is 39% or more and 45% or less.
The air-conditioning outlet unit according to claim 12 .

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