Air supply device and air conditioning unit

Abstract

A blower device (101) is provided with an impeller (30) and a housing (10). The housing includes a tongue portion (71). The tongue portion extends in the direction of the rotation axis of the impeller and separates a suction side (S1) and a discharge side (S2). The tongue portion has a first end portion (71a), a second end portion (71b), and a central portion (71c). The first end portion and the second end portion are located at both ends in the rotation axis direction. The central portion is located between the first end portion and the second end portion. The width dimension of the tongue portion, which is the length from the end edge of the tongue portion on the suction side to the end edge of the tongue portion on the blow-out side, is smaller at the first end than at the center portion.

Description

Technical Field

[0001] This invention relates to air supply devices and air conditioning units. Background Technology

[0002] Previously, indoor units (hereinafter referred to as air conditioning units) of air conditioners were widely used in the following manner: they were installed on the side wall of the room, not on the ceiling, and drew in air from the front and upper surface, then conditioned the air and blew it out from the lower outlet. For example, as shown in Patent Document 1 (Japanese Patent Application Publication No. 2016-50720), the air conditioning unit contained a heat exchanger and an air supply device that carried out the heat exchange between the refrigerant and the air. The air supply device in Patent Document 1 included a cross-flow fan. Summary of the Invention

[0003] The problem that the invention aims to solve

[0004] In crossflow fans, due to factors such as filter blockage and frost buildup on the heat exchanger during cooling operation, ventilation resistance increases, leading to an unstable phenomenon in the outflow (so-called surge).

[0005] Methods for solving problems

[0006] The first-view air supply device includes an impeller and a housing. The housing includes a tongue. The tongue extends along the rotation axis of the impeller, separating an intake side and an exhaust side. The tongue has a first end, a second end, and a central portion. The first and second ends are located at opposite ends in the rotation axis direction. The central portion is located between the first and second ends. Regarding the length from the end edge of the tongue on the intake side to the end edge on the exhaust side, i.e., the width of the tongue, the width of the tongue at the first end is smaller than the width of the tongue at the central portion.

[0007] Here, since the width of the tongue at the first end is smaller than the width of the tongue at the center, it is possible to suppress surging.

[0008] In the second viewpoint of the air supply device, when viewed from the direction of the rotation axis, the end edge of the central part on the side of the air outlet and the end edge of the first end on the side of the air outlet are located at the same position.

[0009] In the third viewpoint air supply device, the first end is the end where the air velocity decreases when the width of the tongue is the same at the central part, the first end, and the second end.

[0010] In the air supply device of the fourth viewpoint, the width dimensions of the first end and the second end are smaller than the width dimension of the central part in any of the first to third viewpoints.

[0011] In the air supply device of the fifth viewpoint, the width dimension of the first end is smaller than the width dimension of the second end in any of the air supply devices of the first to fourth viewpoints.

[0012] In the air supply device of the sixth viewpoint, in any of the air supply devices of the first to fifth viewpoints, the width dimension of the tongue at the first end gradually decreases as it moves away from the portion closer to the center.

[0013] In the air supply device of the seventh viewpoint, the clearance between the central part and the impeller is equal to the clearance between the first end and the impeller in any of the air supply devices of the first to sixth viewpoints.

[0014] The air supply device of the eighth viewpoint satisfies equation (1) when the length dimension in the direction of the rotation axis of the first end is set as M and the outer diameter of the impeller is set as D. Equation (1): 0.10≤M / D≤1.35.

[0015] In the air supply device of the ninth viewpoint, in any of the air supply devices of the first to eighth viewpoints, when viewed from the direction of the rotation axis, the angle between the first straight line extending from the end edge near the suction side of the central part of the rotation axis and the second straight line extending from the end edge near the discharge side of the central part of the rotation axis is set as θa, and the angle between the third straight line extending from the end edge near the suction side of the first end of the rotation axis and the fourth straight line extending from the end edge near the discharge side of the first end of the rotation axis is set as θb, equation (2) is satisfied. Equation (2): 0.39≤θb / θa≤0.98.

[0016] In the air supply device of the tenth viewpoint, in any of the air supply devices of the first to ninth viewpoints, when the length dimension of the first end in the direction of rotation axis is set as M, the outer diameter of the impeller is set as D, the angle between the first straight line extending from the end edge near the suction side of the central part of the rotation axis when viewed from the direction of rotation axis and the second straight line extending from the end edge near the discharge side of the central part of the rotation axis is set as θa, and the angle between the third straight line extending from the end edge near the suction side of the first end of the rotation axis when viewed from the direction of rotation axis and the fourth straight line extending from the end edge near the discharge side of the first end of the rotation axis is θb, equations (1) and (2) are satisfied. Equation (1): 0.10 ≤ M / D ≤ 1.35, Equation (2): 0.39≤θb / θa≤0.98.

[0017] The air conditioning unit of the eleventh viewpoint has an air supply device for any one of the first to tenth viewpoints.

[0018] The air conditioning unit of the twelfth viewpoint has the air supply device of any one of the first to tenth viewpoints. The diameter of the impeller fan is 126 mm or more.

[0019] The air conditioning unit of the thirteenth viewpoint has an air supply device for any of the viewpoints from the first to the tenth viewpoint. The air conditioning unit satisfies equation (3). Equation (3): (Diameter of impeller fan / Height of air conditioning unit) ≥ (126 / 300). Attached Figure Description

[0020] Figure 1 This is a structural diagram of an air conditioning unit consisting of an outdoor unit and an air conditioning module.

[0021] Figure 2 This is a longitudinal sectional view of the air conditioning unit at the central part (along... Figure 1 (Cross-section view of arrow II-II).

[0022] Figure 3 It is a three-dimensional diagram of the tongue.

[0023] Figure 4 This is a magnified view of a section of the air conditioning unit.

[0024] Figure 5 This is a graph showing the relationship between M / D and the increase in static pressure when the length dimension in the direction of the rotation axis is set as M and the outer diameter of the impeller is set as D.

[0025] Figure 6 This is another graph showing the relationship between M / D and the increase in static pressure when the length dimension in the direction of the rotation axis is set as M and the outer diameter of the impeller is set as D.

[0026] Figure 7 It is a graph showing the relationship between the range of angles of the tongue relative to the axis of rotation and the increase in static pressure.

[0027] Figure 8 This is a three-dimensional view of the tongue in a modified example.

[0028] Figure 9 This is a graph showing the relationship between M / D and the increase in static pressure when the length dimension in the direction of the rotation axis of the modified example is set as M and the outer diameter of the impeller is set as D.

[0029] Figure 10 This is a three-dimensional view of the tongue in another variation.

[0030] Figure 11 This is a three-dimensional view of the tongue in another variation. Detailed Implementation

[0031] In the following description, the rotating shaft refers to the rotating shaft of the impeller 30. The direction of the rotating shaft refers to the direction in which the rotating shaft of the impeller 30 extends. Furthermore, terms such as "up," "down," and "front" are used appropriately to indicate direction, representing the various directions in which the air conditioning unit 100 is installed and normally used. For example, the up-down direction is the vertical direction. Also, terms such as "same" and "parallel" are sometimes used, but these include not only cases of being completely identical or parallel, but also cases of being substantially identical or parallel.

[0032] (1) Overall structure

[0033] like Figure 1 As shown, the air conditioning unit 100 is a wall-mounted indoor unit installed on the indoor wall. Furthermore, the air conditioning unit 100 is connected to the outdoor unit 91 of an air conditioner located outdoors via refrigerant piping 93, thus forming an air conditioning unit 90. The air conditioning unit 100 operates for indoor cooling and heating according to the operation of a remote control or the like.

[0034] like Figure 2 As shown, the air conditioning unit 100 includes an air supply device 101, a heat exchanger 20, and a filter 40.

[0035] (2) Air supply device

[0036] The air supply device 101 includes a crossflow fan with an impeller 30 and a housing 10.

[0037] (2-1) Crossflow fan

[0038] The crossflow fan has a cylindrical impeller 30 that extends horizontally and a motor that rotates the impeller 30. The impeller 30 has a plurality of fan blades 31 arranged along its circumference. The impeller 30 generates an airflow from the heat exchanger 20 side to the outlet 10b side by rotating.

[0039] As the impeller 30 rotates, air flows from the room through the filter 40 to the heat exchanger 20. The air that has passed through the heat exchanger 20 is then blown out of the room.

[0040] The diameter of the fan in impeller 30 is not particularly limited, but can be, for example, 126 mm or more. The diameter of the fan in impeller 30 is an imaginary circle formed by connecting the outer ends of multiple fan blades 31 when viewed from the axis of rotation (see reference). Figure 2 The diameter of the circle 30a (hereinafter referred to as the imaginary circumcircle) shown by the dashed line. The diameter of the fan of the impeller 30 is preferably 130 mm or more, and more preferably 135 mm or more.

[0041] The diameter of the fan of impeller 30 and the height of air conditioning unit 100 satisfy equation (3).

[0042] Equation (3): (Diameter of fan with impeller 30 / Height of air conditioning unit) ≥ (126 / 300)

[0043] Furthermore, the rotational speed of the impeller 30 motor is changed by a control device (not shown). The control device, built into the air conditioning unit 100, changes the motor speed based on user input via remote control or similar means.

[0044] (2-2) Outer shell

[0045] The housing 10 is an assembly of components that form the outline and frame of the air conditioning unit 100. The housing 10 supports and houses the filter 40, the heat exchanger 20, and the impeller 30.

[0046] An intake port 10a is formed on the upper part of the outer casing 10 to draw in indoor air. An outlet 10b is formed on the lower part of the outer casing 10 to deliver conditioned air into the room. The intake port 10a is located higher than the rotation axis O, which is the center of rotation of the impeller 30. More specifically, the intake port 10a is formed on the top surface (upper surface) of the outer casing 10, drawing in indoor air from the space above the air conditioning unit 100. The outlet 10b is located lower than the rotation axis O. More specifically, the outlet 10b is formed on the front side portion of the bottom surface of the outer casing 10, blowing air in front of and below the air conditioning unit 100.

[0047] The housing 10 includes a front panel 15, a rear guide 18, and a stabilizer 17. The stabilizer 17 and the rear guide 18 form a blowout airflow path 10c for vortex-shaped airflow from the impeller 30 to the outlet 10b. The upper part of the rear guide 18 is located higher than the rotation axis O. The front panel 15 is disposed on the front side of the filter 40. The stabilizer 17 is disposed on the front side of the rear guide 18. The stabilizer 17 has a tongue 71 and a support 73. The support 73 supports the tongue 71.

[0048] As the impeller 30 rotates, air flows from the room through the intake 10a and the filter 40 to the heat exchanger 20. The air flowing through the heat exchanger 20 flows through the exhaust air path 10c and is blown out of the room from the outlet 10b.

[0049] like Figure 3 As shown, the tongue 71 extends along the rotation axis of the impeller 30. That is, the length direction of the tongue 71 is parallel to the rotation axis of the impeller 30. The tongue 71 separates the intake side S1 and the exhaust side S2 within the internal space of the air supply device 101. The tongue 71 has a curved surface opposite to the impeller 30.

[0050] The tongue 71 has a first end portion 71a, a second end portion 71b, and a central portion 71c. The first end portion 71a and the second end portion 71b are located at opposite ends in the direction of the rotation axis. The first end portion 71a is the end of the tongue 71 where the wind speed decreases when the width dimension of the tongue 71 is the same at the central portion 71c, the first end portion 71a, and the second end portion 71b. The central portion 71c is located between the first end portions 71a and 71b.

[0051] The clearance between the tongue 71 and the impeller 30 remains constant from the suction side S1 to the discharge side S2 of the tongue 71. However, the clearance between the tongue 71 and the impeller 30 is not particularly limited to this, and can vary from the suction side S1 to the discharge side S2. Specifically, the clearance between the tongue 71 and the impeller 30 can be larger on the suction side S1 than on the discharge side S2, or smaller on the discharge side S2 than on the discharge side S2.

[0052] Regarding the width of the tongue 71, the width of the tongue 71 at the first end 71a is smaller than the width of the tongue 71 at the central portion 71c. The width of the tongue 71 is the length from the end edge of the tongue 71 on the inhalation side S1 to the end edge of the tongue 71 on the exhalation side S2.

[0053] The width dimension of the first end 71a does not change in the direction of rotation axis.

[0054] At the end edge of the inhalation side S1, there is a step between the first end 71a and the central portion 71c.

[0055] When viewed from the direction of the rotation axis, the end edge of the blow-out side S2 of the central portion 71c is located at the same position as the end edge of the blow-out side S2 of the first end portion 71a. That is, the shape of the end edge of the blow-out side S2 of the tongue portion 71 does not change in the direction of the rotation axis.

[0056] The clearance between the first end 71a and the impeller 30 is equal to the clearance between the central portion 71c and the impeller 30. In detail, the shortest distance from the end edge of the first end 71a on the blow-out side S2 to the imaginary circumcircle of the impeller 30 is equal to the shortest distance from the end edge of the central portion 71c on the blow-out side S2 to the imaginary circumcircle of the impeller 30.

[0057] When the length dimension in the direction of the rotation axis of the first end 71a is set as M and the outer diameter of the impeller 30 is set as D, M / D satisfies equation (1). Equation (1): 0.10≤M / D≤1.35.

[0058] The preferred range for M / D is 0.25 to 1.25, and more preferably 0.40 to 1.15.

[0059] like Figure 4As shown, when viewed from the direction of the rotation axis, the angle formed by the first straight line L1 extending from the rotation axis O towards the end edge of the central portion 71c near the suction side S1 and the second straight line L2 extending from the rotation axis O towards the end edge of the central portion 71c near the discharge side S2 is defined as θa. When viewed from the direction of the rotation axis, the angle formed by the third straight line L3 extending from the rotation axis O towards the end edge of the first end portion 71a near the suction side S1 and the fourth straight line L4 extending from the rotation axis O towards the end edge of the first end portion 71a near the discharge side S2 is defined as θb. θa is greater than θb. Specifically, θb / θa satisfies equation (2). Equation (2): 0.39≤θb / θa≤0.98.

[0060] The preferred range for θb / θa is 0.42 to 0.95, and more preferably 0.47 to 0.90.

[0061] The width of the tongue 71 at the second end 71b is smaller than the width of the tongue 71 at the central part 71c. The width of the tongue 71 at the second end 71b is the same as the width of the tongue 71 at the first end 71a.

[0062] The width dimension of the second end 71b remains unchanged in the direction of rotation. The length dimension M2 of the second end 71b in the direction of rotation is the same as the length dimension M of the first end 71a in the direction of rotation.

[0063] At the end edge of the inhalation side S1, there is a step between the second end 71b and the central portion 71c.

[0064] When viewed from the direction of the rotation axis, the end edge of the blow-out side S2 of the central portion 71c and the end edge of the blow-out side S2 of the second end portion 71b are located at the same position. That is, the shape of the end edge of the blow-out side S2 of the tongue portion 71 does not change in the length direction.

[0065] The clearance between the second end 71b and the impeller 30 is equal to the clearance between the central portion 71c and the impeller 30. Specifically, the shortest distance from the end edge of the second end 71b on the blow-out side S2 to the imaginary circumcircle of the impeller 30 is equal to the shortest distance from the end edge of the central portion 71c on the blow-out side S2 to the imaginary circumcircle of the impeller 30.

[0066] When the length dimension in the direction of the rotation axis of the second end 71b is set as M′ and the outer diameter of the impeller 30 is set as D, M′ / D satisfies equation (1)′. Equation (1)′: 0.10≤M′ / D≤1.35.

[0067] The preferred range for M′ / D is 0.25 to 1.25, and more preferably 0.40 to 1.15.

[0068] Viewed from the direction of the rotation axis, the angle formed by the first straight line L1 extending from the rotation axis O towards the end edge of the central portion 71c near the suction side S1 and the second straight line L2 extending from the rotation axis O towards the end edge of the central portion 71c near the discharge side S2 is denoted as θa. Viewed from the direction of the rotation axis, the angle formed by the fifth straight line L5 extending from the rotation axis O towards the end edge of the second end 71b near the suction side S1 and the sixth straight line L6 extending from the rotation axis O towards the end edge of the second end 71b near the discharge side S2 is denoted as θb′. θa is greater than θb′. Specifically, θb′ / θa satisfies equation (2)′. Equation (2): 0.39≤θb′ / θa≤0.98(2).

[0069] The preferred range for θb′ / θa is 0.42 to 0.95, and more preferably 0.47 to 0.90.

[0070] (3) Heat exchangers and filters

[0071] The heat exchanger 20 is a finned tube type heat exchanger with a "H" shape in longitudinal section. The shape of the heat exchanger 20 is not particularly limited. For example, the heat exchanger 20 can also be inverted V shape. The heat exchanger 20 facilitates heat exchange between air flowing from the suction port 10a to the impeller 30 and refrigerant flowing in the tubes. The heat exchanger 20 consists of multiple aluminum heat transfer fins and multiple tubes with multiple holes formed through these heat transfer fins. The outer diameter of the copper heat transfer tubes is 5 mm or 4 mm.

[0072] The upstream side of the airflow from the impeller 30 is covered by a filter 40. Specifically, the heat exchanger 20 located above and in front of the impeller 30 is covered by the filter 40. The filter 40 traps dust contained in the air flowing from the intake 10a to the heat exchanger 20.

[0073] (4) Characteristics

[0074] (4-1)

[0075] A crossflow fan experiences lateral intake at both ends compared to the central section along its rotational axis. This results in airflow stripping at the sides. Consequently, air is difficult to draw in at the ends of the crossflow fan, leading to increased air circulation turbulence inside the fan. As a result, the airflow speed decreases, causing surge. At this point, as... Figure 4 As shown by the dotted arc, the circulating vortex at both ends of the crossflow fan is larger than the circulating vortex at the center.

[0076] In a crossflow fan, regarding the length from the end edge of the tongue 71 near the intake side S1 to the end edge near the exhaust side S2, i.e., the width of the tongue 71, the width of the tongue 71 at the first end 71a is smaller than the width of the tongue 71 at the central part 71c. Therefore, at the first end 71a and the second end 71b, the circulating vortex inside the crossflow fan... Figure 4 The arc, as shown by the solid line, becomes smaller. This increases the static pressure in the blowout path, thus increasing the air velocity. As a result, surge is suppressed.

[0077] (4-2)

[0078] When viewed from the direction of the rotation axis, the end edge of the blow-out side S2 of the central portion 71c and the end edge of the blow-out side S2 of the first end portion 71a are located in the same position.

[0079] Here, when viewed from the direction of the rotation axis, the position of the end edge of the blow-out side S2 remains unchanged at the central portion 71c and the first end portion 71a. Therefore, the distance between the tongue 71 and the impeller 30 remains constant along the entire length of the tongue 71, and thus, the air delivery efficiency does not decrease.

[0080] (4-3)

[0081] The first end 71a is the end where the wind speed decreases when the width of the tongue 71 is the same at the central part 71c, the first end 71a, and the second end 71b.

[0082] Therefore, it is possible to increase the blowing speed at the end where the wind speed was originally lower.

[0083] (4-4)

[0084] The width of the first end portion 71a and the second end portion 71b is smaller than the width of the central portion 71c.

[0085] Here, since the width of the first end 71a and the second end 71b is smaller than the width of the central part 71c, the blowing speed can be increased compared to reducing the width of only one end.

[0086] (4-5)

[0087] The clearance between the central portion 71c and the impeller 30 is equal to the clearance between the first end portion 71a and the impeller 30.

[0088] Here, the distance between the tongue 71 and the impeller 30 remains constant along the entire length of the tongue 71. Therefore, the air supply efficiency does not decrease.

[0089] (4-6)

[0090] When the length dimension in the direction of the rotation axis of the first end 71a is set as M and the outer diameter of the impeller 30 is set as D, equation (1) is satisfied. Equation (1): 0.10≤M / D≤1.35.

[0091] like Figure 5 as well as Figure 6 As shown, surge is suppressed when M / D is 0.10~1.35.

[0092] (4-7)

[0093] When viewed from the direction of the rotation axis, the angle between the first straight line L1 extending from the rotation axis O to the end edge of the central part 71c near the suction side S1 and the second straight line L2 extending from the rotation axis O to the end edge of the central part 71c near the discharge side S2 is set as θa. When viewed from the direction of the rotation axis, the angle between the third straight line L3 extending from the rotation axis O to the end edge of the first end 71a near the suction side S1 and the fourth straight line L4 extending from the rotation axis O to the end edge of the first end 71a near the discharge side S2 is set as θb, then equation (2) is satisfied. Equation (2): 0.39≤θb / θa≤0.98.

[0094] like Figure 7 As shown, if θb / θa is 0.39~0.98, surge is suppressed.

[0095] (4-8)

[0096] The air conditioning unit 100 includes the aforementioned air supply device 101. As a result, the air conditioning unit 100 is able to suppress the generation of surge.

[0097] (4-9)

[0098] The diameter of the impeller 30 fan is 126mm or more.

[0099] According to this structure, since the cross-flow fan with a large diameter impeller 30 is used, it is possible to reduce noise and power consumption during air conditioning operation.

[0100] (4-10)

[0101] Air conditioning unit 100 satisfies formula (3). Equation (3): (Diameter of impeller fan / Height of air conditioning unit) ≥ (126 / 300).

[0102] According to this structure, since the cross-flow fan with a large diameter impeller 30 is used for the indoor unit body, it is possible to reduce noise and power consumption during air conditioner operation.

[0103] (5) Variations

[0104] (5-1) Variation A

[0105] In the above embodiment, the width of the first end 71a is the same as the width of the second end 71b. However, the width of the first end 71a and the width of the second end 71b are not particularly limited thereto. The width of the first end 71a and the width of the second end 71b may also be different. For example, the width of the first end 71a may be smaller than the width of the second end 71b.

[0106] In this case, at the first end 71a where the wind speed was originally lower, the wind speed can be made greater than at the second end 71b.

[0107] (5-2) Variation B

[0108] In the above embodiment, the length dimension M2 of the second end 71b in the direction of rotation axis is the same as the length dimension M of the first end 71a in the direction of rotation axis. However, the length dimension M2 of the second end 71b in the direction of rotation axis can also be different from the length dimension M of the first end 71a in the direction of rotation axis. For example, the length dimension M2 of the second end 71b in the direction of rotation axis can also be smaller than the length dimension M of the first end 71a in the direction of rotation axis.

[0109] In this case, at the first end 71a where the wind speed was originally lower, the wind speed can be made greater than at the second end 71b.

[0110] (5-3) Variation C

[0111] In the above-described embodiments and variations 1A, both the width of the first end 71a and the width of the second end 71b are smaller than the width of the central portion 71c. However, the width of the first end 71a and the width of the second end 71b are not particularly limited thereto. For example, it is also possible that only the width of the first end 71a is smaller than the width of the central portion 71c.

[0112] In this case, the wind speed can be increased at the first end 71a where the wind speed was originally lower.

[0113] (5-4) Variation D

[0114] In the above embodiment, the width of the first end 71a is constant in the direction of the rotation axis. However, it is not particularly limited to this. Alternatively, as... Figure 10 As shown, at the first end 71a, the width of the tongue 71 decreases in stages as it moves away from the portion closer to the center 71c.

[0115] In this case, the continuity of the circulating vortex generated inside the impeller 30 in the direction of rotation axis is not easily lost, so the air supply is easy to stabilize.

[0116] In the case of variant D, with respect to equation (2), the third straight line L3 is a straight line extending from the rotation axis O toward the end edge of the first end 71a near the suction side S1.

[0117] (5-5) Variation E

[0118] It can also be like Figure 11 As shown, at the first end 71a, the width of the tongue 71 decreases in a sloping manner as it moves away from the portion closer to the central portion 71c.

[0119] In this case, the continuity of the circulating vortex generated inside the impeller 30 in the direction of rotation axis is not lost, thus the air supply is stable.

[0120] In the case of variant E, with respect to equation (2), the third straight line L3 is a straight line extending from the rotation axis O toward the end edge of the first end 71a near the suction side S1.

[0121] (5-6) Variation F

[0122] It can also be like Figure 11 As shown, the first end 71a and the second end 71b are set with different shapes.

[0123] Example 1

[0124] Air supply devices with impeller diameters of 115mm, 126mm, 135mm, and 149mm were prepared. For each air supply device, the angle θa formed by a first straight line extending from the central end edge near the suction side of the rotation axis and a second straight line extending from the central end edge near the discharge side of the rotation axis, and the angle θb formed by a third straight line extending from the first end edge near the suction side of the rotation axis and a fourth straight line extending from the first end edge near the discharge side of the rotation axis, when viewed from the rotation axis direction, were set to θb / θa = 0.85. In each air supply device, only the width of the tongue was varied at the first and second ends, and the increase in static pressure was measured. At the first and second ends, the width of the tongue was set to be the same. Figure 5 This indicates the result.

[0125] Furthermore, air supply devices with θb / θa ratios of 0.98, 0.85, 0.68, and 0.39 were prepared. The fan diameter of each impeller was 135 mm. In each air supply device, only the width of the tongue was varied at the first and second ends, and the increase in static pressure was measured. Figure 6 This indicates the result.

[0126] exist Figure 5 and Figure 6 In the figure, the horizontal axis represents M / D, and the vertical axis represents the increase in static pressure. The experimental results show that the increase in static pressure increases when M / D is between 0.10 and 1.35. This means that surge is suppressed.

[0127] Example 2

[0128] A fan with a diameter of 135 mm was prepared for air delivery. M / D = 0.30. Various changes to θb / θa were made, and the increase in static pressure was measured. The increase in static pressure was measured for cases where θb / θa was changed at both the first and second ends, and for cases where θb / θa was changed only at the first end. When θb / θa was changed at both the first and second ends, the value of θb / θa at the first end was the same as the value of θb / θa at the second end. Figure 7 This indicates the result.

[0129] exist Figure 7 In the diagram, the horizontal axis represents θb / θa, and the vertical axis represents the increase in static pressure. The experimental results show that, with variations in θb / θa at both the first and second ends, the increase in static pressure increases when θb / θa is between 0.39 and 0.98. This indicates that surge is suppressed.

[0130] Example 3

[0131] Air supply devices with impeller diameters of 115mm, 126mm, 135mm, and 149mm were prepared. In each air supply device, θb / θa = 0.85. In each air supply device, at the first end, only the width of the tongue was varied, and the increase in static pressure was measured. The width of the tongue at the second end was set to be the same as the width of the tongue at the central part.

[0132] Furthermore, for an air supply device with a fan diameter of 135mm, the increase in static pressure was measured by changing the width of the tongue at the second end, where the original airflow speed was high. In this embodiment, the width of the tongue at the first end and the width of the tongue at the central part were set to be the same.

[0133] Figure 9 This indicates the result.

[0134] exist Figure 9 In the figure, the horizontal axis represents M / D, and the vertical axis represents the increase in static pressure. The test results show that the increase in static pressure increases when M / D is between 0.10 and 1.35. This means that at the first end, even if only the width of the tongue is changed, surge can be suppressed.

[0135] The embodiments of this disclosure have been described above, but it should be understood that various changes in manner and details can be made without departing from the spirit and scope of this disclosure as set forth in the claims.

[0136] Label Explanation

[0137] 10 casing

[0138] 10a Inlet

[0139] 10b blowout

[0140] 10c blows out airflow path

[0141] 17 stabilizer

[0142] 18-year-old guide

[0143] 20 heat exchangers

[0144] 30 impeller

[0145] 30a An imaginary circle (imaginary circumcircle) connecting the outer ends of the fan blades.

[0146] 31 fan blades

[0147] 71 stabilizer tongue

[0148] 71a First end

[0149] 71b Second end

[0150] 71c Central Department

[0151] 73 Stabilizer Support

[0152] 100 air conditioning units

[0153] 101 air supply device

[0154] O Fan rotating shaft

[0155] L1 First Straight Line

[0156] L2 Second Straight Line

[0157] L3 Third Straight Line

[0158] L4 Fourth Straight Line

[0159] S1 Inhalation Side

[0160] S2 blowout side

[0161] Existing technical documents

[0162] Patent documents

[0163] Patent Document 1: Japanese Patent Application Publication No. 2016-50720

Claims

1. An air supply device (101), comprising: Impeller (30); and The housing (10) includes a tongue (71) that extends along the rotation axis of the impeller and separates an intake side (S1) and an exhaust side (S2). The tongue has a first end portion (71a) and a second end portion (71b) located at both ends in the direction of rotation axis, and a central portion (71c) located between the first end portion and the second end portion. Regarding the length from the end edge of the tongue on the inhalation side to the end edge on the exhalation side, i.e., the width of the tongue, the width of the tongue at the first end is smaller than the width of the tongue at the central part.

2. The air supply device according to claim 1, wherein, When viewed from the direction of the rotation axis, the end edge of the central portion on the blow-out side and the end edge of the first end portion on the blow-out side are located at the same position.

3. The air supply device according to claim 1 or 2, wherein, The first end is the end where the wind speed decreases when the width of the tongue is the same at the central part, the first end, and the second end.

4. The air supply device according to any one of claims 1 to 3, wherein, The width of the first end and the second end is smaller than the width of the central portion.

5. The air supply device according to any one of claims 1 to 4, wherein, The width of the first end is smaller than the width of the second end.

6. The air supply device according to any one of claims 1 to 5, wherein, In the first end portion, the width of the tongue decreases in stages as it moves away from the portion closer to the central portion.

7. The air supply device according to any one of claims 1 to 6, wherein, The clearance between the central portion and the impeller is equal to the clearance between the first end portion and the impeller.

8. The air supply device according to any one of claims 1 to 7, wherein, When the length dimension in the direction of the rotation axis of the first end is set as M and the outer diameter of the impeller is set as D, equation (1) is satisfied. Equation (1): 0.10≤M / D≤1.

35.

9. The air supply device according to any one of claims 1 to 8, wherein, When the angle between the first straight line (L1) extending from the rotation axis (O) toward the central part near the suction side when viewed from the direction of the rotation axis and the second straight line (L2) extending from the rotation axis toward the central part near the discharge side when viewed from the direction of the rotation axis is set as θa, and the angle between the third straight line (L3) extending from the rotation axis toward the first end near the suction side when viewed from the direction of the rotation axis and the fourth straight line (L4) extending from the rotation axis toward the first end near the discharge side when viewed from the direction of the rotation axis is set as θb, equation (2) is satisfied. Equation (2): 0.39≤θb / θa≤0.

98.

10. The air supply device according to any one of claims 1 to 9, wherein, When the length dimension of the first end in the direction of rotation axis is set as M, the outer diameter of the impeller is set as D, the angle between the first straight line extending from the end edge near the suction side of the central part of the rotation axis when viewed from the direction of rotation axis and the second straight line extending from the end edge near the discharge side of the central part of the rotation axis is set as θa, and the angle between the third straight line extending from the end edge near the suction side of the first end of the rotation axis when viewed from the direction of rotation axis and the fourth straight line extending from the end edge near the discharge side of the first end of the rotation axis is set as θb, equations (1) and (2) are satisfied. Equation (1): 0.10 ≤ M / D ≤ 1.35, Equation (2): 0.39≤θb / θa≤0.

98.

11. An air conditioning unit (100) comprising an air supply device according to any one of claims 1 to 10.

12. An air conditioning unit comprising the air supply device according to any one of claims 1 to 10, wherein, The diameter of the impeller fan is 126 mm or more.

13. An air conditioning unit comprising the air supply device according to any one of claims 1 to 10, wherein, The air conditioning unit satisfies equation (3). Equation (3): (Diameter of impeller fan / Height of air conditioning unit) ≥ (126 / 300).

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