Blower device and air conditioning unit

Abstract

A blower device (101) comprises an impeller (30) and a casing (10). The casing includes a tongue part (71). The tongue part extends along the rotary shaft direction of the impeller and partitions an intake side (S1) off from a blowout side (S2). The tongue part has a first end part (71a), a second end part (71b), and a center part (71c). The first end part and the second end part are positioned at respective ends in the rotary shaft direction. The center part is positioned between the first end part and the second end part. Regarding the width dimension of the tongue part, which is the length from the edge on the intake side to the edge on the blowout side of the tongue part, the width dimension of the tongue part at the first end part is smaller than the width dimension of the tongue part at the center part.

Description

Blower and air conditioning unit

[0001] The present invention relates to a blower and an air conditioning unit.

[0002] Conventionally, indoor units of air conditioners (hereinafter referred to as air conditioning units) that are installed on the side walls of a room rather than on the ceiling, draw in air from the front or top, and blow out conditioned air from outlets at the bottom have become widespread. For example, as shown in Patent Document 1 (JP 2016-50720 A), the air conditioning unit houses a heat exchanger that exchanges heat between a refrigerant and air, and a blower. The blower in Patent Document 1 includes a crossflow fan.

[0003] Cross-flow fans have the problem that ventilation resistance increases due to clogged filters and frost on the heat exchanger during cooling operation, causing unstable blown airflow (so-called surging).

[0004] A first aspect of the blower device includes an impeller and a casing. The casing includes a tongue portion. The tongue portion extends along the rotational axis direction of the impeller and separates the suction side from the blowing side. The tongue portion has a first end portion, a second end portion, and a central portion. The first end portion and the second end portion are located at opposite ends in the rotational axis direction. The central portion is located between the first end portion and the second end portion. With regard to the width dimension of the tongue portion, which is the length from the suction side edge of the tongue portion to the blowing side edge of the tongue portion, the width dimension of the tongue portion at the first end portion is smaller than the width dimension of the tongue portion at the central portion.

[0005] Here, since the width dimension of the tongue portion at the first end portion is smaller than the width dimension of the tongue portion at the central portion, surging can be suppressed.

[0006] A blower device according to a second aspect is the blower device according to the first aspect, wherein the blowing side edge of the central portion and the blowing side edge of the first end portion are at the same position when viewed in the rotation axis direction.

[0007] A blower device of a third aspect is a blower device of the first or second aspect, in which the first end is the end at which the wind speed is smaller when the width dimension of the tongue portion is the same at the central portion, the first end, and the second end.

[0008] A fourth aspect of the invention is the air blower according to any one of the first to third aspects, wherein the widths of the first and second ends are smaller than the width of the central portion.

[0009] A fifth aspect of the invention is the air blower according to any one of the first to fourth aspects, wherein the width dimension of the first end is smaller than the width dimension of the second end.

[0010] A sixth aspect of the invention is the blower device according to any one of the first to fifth aspects, wherein the width of the tongue at the first end decreases in stages with increasing distance from the central portion.

[0011] A seventh aspect of the blower device is a blower device according to any one of the first to sixth aspects, wherein the gap dimension between the central portion and the impeller is equal to the gap dimension between the first end portion and the impeller.

[0012] An eighth aspect of the present invention is a blower device according to any one of the first to seventh aspects, wherein when the length of the first end in the rotational axis direction is M and the outer diameter of the impeller is D, the following formula (1) is satisfied: 0.10≦M / D≦1.35.

[0013] A ninth aspect of the present invention relates to the air blower of any one of the first to eighth aspects, wherein when the angle, as viewed in the direction of the rotational axis, between a first line extending from the rotational axis to an edge on the suction side of the central portion and a second line extending from the rotational axis to an edge on the blowing side of the central portion is θa, and the angle, as viewed in the direction of the rotational axis, between a third line extending from the rotational axis to an edge on the suction side of a first end portion and a fourth line extending from the rotational axis to an edge on the blowing side of the first end portion is θb, the following equation (2) is satisfied: 0.39≦θb / θa≦0.98.

[0014] A blower device of a tenth aspect is the blower device of any of the first to ninth aspects, wherein when the length dimension of the first end in the rotational axis direction is M, the outer diameter of the impeller is D, the angle as viewed in the rotational axis direction made by a first line extending from the rotational axis to an edge on the suction side of the central portion and a second line extending from the rotational axis to an edge on the blowing side of the central portion is θa, and the angle as viewed in the rotational axis direction made by a third line extending from the rotational axis to the edge on the suction side of the first end and a fourth line extending from the rotational axis to the edge on the blowing side of the first end is θb, the following formulas are satisfied: Formula (1): 0.10≦M / D≦1.35 Formula (2): 0.39≦θb / θa≦0.98

[0015] An air conditioning unit according to an eleventh aspect includes the air blower according to any one of the first to tenth aspects.

[0016] An air conditioning unit according to a twelfth aspect includes the blower device according to any one of the first to tenth aspects. The diameter of the impeller fan is 126 mm or more.

[0017] An air conditioning unit according to a thirteenth aspect includes the blower device according to any one of the first to tenth aspects. The air conditioning unit satisfies formula (3): (diameter of impeller fan / height dimension of air conditioning unit)≧(126 / 300).

[0018] 1 is a configuration diagram of an air conditioner consisting of an air conditioning outdoor unit and an air conditioning unit. FIG. 2 is a longitudinal cross-sectional view of the air conditioning unit at the center (cross-sectional view of the arrows II-II in FIG. 1). FIG. 3 is a perspective view of a tongue. FIG. 4 is a partially enlarged cross-sectional view of the air conditioning unit. FIG. 5 is a graph showing the relationship between M / D and the static pressure increase when the length dimension in the rotational axis direction is M and the outer diameter of the impeller is D. FIG. 6 is another graph showing the relationship between M / D and the static pressure increase when the length dimension in the rotational axis direction is M and the outer diameter of the impeller is D. FIG. 7 is a graph showing the relationship between the angular range of the tongue with respect to the rotational axis and the static pressure increase. FIG. 8 is a perspective view of a tongue in a modified example. FIG. 9 is a graph showing the relationship between M / D and the static pressure increase when the length dimension in the rotational axis direction of a modified example is M and the outer diameter of the impeller is D. FIG. 10 is a perspective view of a tongue in another modified example. FIG. 11 is a perspective view of a tongue in another modified example.

[0019] In the following description, the rotation axis refers to the rotation axis of the impeller 30. The rotation axis direction refers to the direction in which the rotation axis of the impeller 30 extends. Furthermore, expressions indicating directions such as "up," "down," and "front" are used as appropriate, but these refer to the respective directions when the air conditioning unit 100 is installed and in normal use. For example, the up-down direction is the vertical direction. Furthermore, expressions such as "same" and "parallel" may be used, but these include not only cases where the expressions are completely the same or parallel, but also cases where the expressions are substantially the same or parallel.

[0020] (1) Overall Configuration As shown in Fig. 1, the air conditioning unit 100 is a wall-mounted indoor unit that is attached to a wall surface inside a room. The air conditioning unit 100 is also connected to an outdoor air conditioning unit 91 located outside the room via refrigerant piping 93 to form an air conditioner 90. The air conditioning unit 100 performs indoor cooling and heating operations in response to operation using a remote control or the like.

[0021] As shown in FIG. 2 , the air conditioning unit 100 includes a blower 101 , a heat exchanger 20 , and a filter 40 .

[0022] (2) Blower The blower 101 includes a cross-flow fan including an impeller 30 and a casing 10 .

[0023] (2-1) Crossflow Fan The crossflow fan includes a cylindrical impeller 30 that extends horizontally and a motor that rotates the impeller 30. The impeller 30 has a large number of fan blades 31 arranged along its circumference. By rotating, the impeller 30 generates an air flow that flows from the heat exchanger 20 side to the air outlet 10b side.

[0024] When 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 blown out into the room.

[0025] The diameter of the fan of the impeller 30 is not particularly limited, but is, for example, 126 mm or more. The diameter of the fan of the impeller 30 is the diameter of an imaginary circle (see circle 30a indicated by a dotted line in FIG. 2; hereinafter referred to as an imaginary circumscribing circle) connecting the outer ends of the numerous fan blades 31 when viewed in the direction of the rotation axis. The diameter of the fan of the impeller 30 is preferably 130 mm or more, and more preferably 135 mm or more.

[0026] The diameter of the fan of the impeller 30 and the height of the air conditioning unit 100 satisfy the following formula (3): (Diameter of the fan of the impeller 30 / Height of the air conditioning unit)≧(126 / 300).

[0027] The rotation speed of the motor of the impeller 30 is changed by a control device (not shown). The control device built into the air conditioning unit 100 changes the rotation speed of the motor based on an operation input by a user via a remote control or the like.

[0028] (2-2) Casing The casing 10 is an assembly of members that form the outer shell and frame of the air conditioning unit 100. The casing 10 supports and houses the filter 40, the heat exchanger 20, and the impeller 30.

[0029] An intake port 10a is formed in the upper part of the casing 10 to take in indoor air. An outlet port 10b is formed in the lower part of the casing 10 to send 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 in the top surface (upper surface) of the casing 10 and draws in indoor air from the space above the air conditioning unit 100. The outlet port 10b is located lower than the rotation axis O. More specifically, the outlet port 10b is formed in the front portion of the bottom surface of the casing 10 and blows air forward and downward from the air conditioning unit 100.

[0030] The casing 10 includes a front panel 15, a rear guider 18, and a stabilizer 17. The stabilizer 17 and the rear guider 18 form an outlet air flow path 10c for scroll-shaped air flowing from the impeller 30 to the air outlet 10b. The upper part of the rear guider 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 further in front of the rear guider 18. The stabilizer 17 has a tongue portion 71 and a support portion 73. The support portion 73 supports the tongue portion 71.

[0031] When the impeller 30 rotates, air flows from the room through the air inlet 10a and the filter 40 to the heat exchanger 20. The air that has passed through the heat exchanger 20 flows into the outlet air flow path 10c and is blown out into the room from the outlet 10b.

[0032] 3, the tongue portion 71 extends along the direction of the rotational axis of the impeller 30. In other words, the longitudinal direction of the tongue portion 71 is parallel to the direction of the rotational axis of the impeller 30. The tongue portion 71 separates the suction side S1 and the blowing side S2 in the internal space of the blower 101. The tongue portion 71 has a curved surface that faces the impeller 30.

[0033] The tongue portion 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 portion where the wind speed is smaller when the width dimension of the tongue portion 71 is the same for 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.

[0034] The gap dimension between the tongue portion 71 and the impeller 30 does not change from the suction side S1 to the blowing side S2 of the tongue portion 71. However, the gap dimension between the tongue portion 71 and the impeller 30 is not particularly limited to this and may change from the suction side S1 to the blowing side S2. Specifically, the gap dimension between the tongue portion 71 and the impeller 30 may be larger on the suction side S1 than on the blowing side S2, or may be smaller on the blowing side S2 than on the blowing side S2.

[0035] The width of the tongue portion 71 at the first end 71a is smaller than the width of the tongue portion 71 at the central portion 71c. The width of the tongue portion 71 is the length from the edge of the suction side S1 of the tongue portion 71 to the edge of the blowing side S2.

[0036] The width of the first end 71a does not change in the direction of the rotation axis.

[0037] At the edge of the suction side S1, there is a step between the first end 71a and the central portion 71c.

[0038] When viewed in the rotation axis direction, the edge of the blowing side S2 of the central portion 71 c and the edge of the blowing side S2 of the first end portion 71 a are at the same position. In other words, the shape of the edge of the blowing side S2 of the tongue portion 71 does not change in the rotation axis direction.

[0039] The gap dimension between the first end 71a and the impeller 30 is equal to the gap dimension between the central portion 71c and the impeller 30. Specifically, the shortest distance from the edge of the blowing side S2 of the first end 71a to the imaginary circumscribing circle of the impeller 30 is equal to the shortest distance from the edge of the blowing side S2 of the central portion 71c to the imaginary circumscribing circle of the impeller 30.

[0040] When the length of the first end 71a in the rotational axis direction is M and the outer diameter of the impeller 30 is D, M / D satisfies formula (1): 0.10≦M / D≦1.35.

[0041] The preferred range of M / D is 0.25 to 1.25, and more preferably 0.40 to 1.15.

[0042] As shown in Figure 4, the angle between a first line L1 extending from the rotation axis O to the edge of the suction side S1 of the central portion 71c and a second line L2 extending from the rotation axis O to the edge of the blow-off side S2 of the central portion 71c is defined as θa. The angle between a third line L3 extending from the rotation axis O to the edge of the suction side S1 of the first end 71a and a fourth line L4 extending from the rotation axis O to the edge of the blow-off side S2 of the first end 71a is defined as θb. θa is greater than θb. Specifically, θb / θa satisfies formula (2). Formula (2): 0.39 ≤ θb / θa ≤ 0.98

[0043] The preferred range of θb / θa is 0.42 to 0.95, and more preferably 0.47 to 0.90.

[0044] The width of the tongue portion 71 at the second end 71b is smaller than the width of the tongue portion 71 at the central portion 71c. The width of the tongue portion 71 at the second end 71b is the same as the width of the tongue portion 71 at the first end 71a.

[0045] The width of the second end 71b does not change in the rotational axis direction. The length M2 of the second end 71b in the rotational axis direction is the same as the length M of the first end 71a in the rotational axis direction.

[0046] At the edge of the suction side S1, there is a step between the second end 71b and the central portion 71c.

[0047] When viewed in the rotation axis direction, the edge of the blowing side S2 of the central portion 71 c and the edge of the blowing side S2 of the second end portion 71 b are located at the same position. In other words, the shape of the edge of the blowing side S2 of the tongue portion 71 does not change in the longitudinal direction.

[0048] The gap dimension between the second end 71b and the impeller 30 is equal to the gap dimension between the central portion 71c and the impeller 30. Specifically, the shortest distance from the edge of the blowing side S2 of the second end 71b to the imaginary circumscribing circle of the impeller 30 is equal to the shortest distance from the edge of the blowing side S2 of the central portion 71c to the imaginary circumscribing circle of the impeller 30.

[0049] When the length of the second end portion 71b in the rotational axis direction is M' and the outer diameter of the impeller 30 is D, M' / D satisfies the formula (1)'. Formula (1)': 0.10≦M' / D≦1.35

[0050] The preferred range of M' / D is 0.25 to 1.25, and more preferably 0.40 to 1.15.

[0051] The angle between a first line L1 extending from the rotation axis O to the edge of the suction side S1 of the central portion 71c and a second line L2 extending from the rotation axis O to the edge of the blow-off side S2 of the central portion 71c is defined as θa. The angle between a fifth line L5 extending from the rotation axis O to the edge of the suction side S1 of the second end portion 71b and a sixth line L6 extending from the rotation axis O to the edge of the blow-off side S2 of the second end portion 71b is defined as θb'. θa is greater than θb'. Specifically, θb' / θa satisfies formula (2)'. Formula (2)': 0.39≦θb' / θa≦0.98 (2)

[0052] The preferred range of θb' / θa is 0.42 to 0.95, and more preferably 0.47 to 0.90.

[0053] (3) Heat Exchanger and Filter The heat exchanger 20 is a fin-and-tube heat exchanger having a V-shaped cross section. The shape of the heat exchanger 20 is not particularly limited. The heat exchanger 20 may have, for example, an inverted V-shape. The heat exchanger 20 exchanges heat between air flowing from the suction port 10a side to the impeller 30 side and refrigerant flowing through the tubes. The heat exchanger 20 is composed of a number of aluminum heat transfer fins and a number of tubes that pass through a number of holes drilled in the heat transfer fins. The copper heat transfer tubes have an outer diameter of 5 mm or 4 mm.

[0054] The upstream side of the air flow of the impeller 30 is covered by a filter 40. Specifically, the heat exchanger 20, which is located above and in front of the impeller 30, is covered by the filter 40. The filter 40 collects dust contained in the air flowing from the suction port 10a to the heat exchanger 20.

[0055] (4) Features (4-1) The ends of a crossflow fan in the direction of its rotational axis are more susceptible to lateral suction than the central portion. This causes the airflow to separate at the sides. As a result, air is less easily drawn into the ends of the crossflow fan, causing the circulating vortex of air inside the fan to become larger. As a result, the air speed decreases, causing surging. In this case, the circulating vortex at both ends inside the crossflow fan becomes larger than the circulating vortex in the central portion, as shown by the dashed arcs in Figure 4.

[0056] In the crossflow fan, the width of the tongue 71, which is the length from the edge of the suction side S1 to the edge of the outlet side S2, is such that the width of the tongue 71 at the first end 71a is smaller than the width of the tongue 71 at the center 71c. As a result, the circulating vortex inside the crossflow fan becomes smaller at the first and second ends 71a and 71b, like the solid arcs shown in Figure 4. This increases the static pressure in the outlet flow path, thereby increasing the wind speed. As a result, the occurrence of surging can be suppressed.

[0057] (4-2) The edge of the central portion 71c on the blowing side S2 and the edge of the first end portion 71a on the blowing side S2 are located at the same position when viewed in the rotation axis direction.

[0058] Here, when viewed in the direction of the rotation axis, the position of the edge of the blowing side S2 is the same between the central portion 71c and the first end portion 71a, so the distance between the tongue portion 71 and the impeller 30 is kept constant over the entire length of the tongue portion 71, and therefore the air blowing efficiency does not decrease.

[0059] (4-3) The first end 71a is the end where the wind speed is smaller when the width dimension of the tongue 71 is the same at the center 71c, the first end 71a, and the second end 71b.

[0060] Therefore, the blowing speed at the end portion where the wind speed is originally slower can be increased.

[0061] (4-4) The width of the first end portion 71a and the second end portion 71b is smaller than the width of the central portion 71c.

[0062] Here, since the width dimension of the first end and second end 71a, 71b is smaller than the width dimension of the central portion 71c, the blowing speed can be increased compared to when the width dimension of only one end is reduced.

[0063] (4-5) The gap dimension between the central portion 71c and the impeller 30 is equal to the gap dimension between the first end portion 71a and the impeller 30.

[0064] Here, the distance between the tongue portion 71 and the impeller 30 is kept constant over the entire length of the tongue portion 71. Therefore, the air blowing efficiency does not decrease.

[0065] (4-6) When the length of the first end 71a in the rotational axis direction is M and the outer diameter of the impeller 30 is D, the following formula (1) is satisfied: 0.10≦M / D≦1.35.

[0066] As shown in FIGS. 5 and 6, when M / D is between 0.10 and 1.35, the occurrence of surging is suppressed.

[0067] (4-7) When the angle, as viewed in the direction of the rotation axis, between a first straight line L1 extending from the rotation axis O to the edge of the suction side S1 of the central portion 71c and a second straight line L2 extending from the rotation axis O to the edge of the blow-off side S2 of the central portion 71c is defined as θa, and the angle, as viewed in the direction of the rotation axis, between a third straight line L3 extending from the rotation axis O to the edge of the suction side S1 of the first end portion 71a and a fourth straight line L4 extending from the rotation axis O to the edge of the blow-off side S2 of the first end portion 71a is defined as θb, the following equation (2) is satisfied: 0.39≦θb / θa≦0.98.

[0068] As shown in FIG. 7, if θb / θa is between 0.39 and 0.98, the occurrence of surging is suppressed.

[0069] (4-8) The air conditioning unit 100 includes the above-described blower 101. This allows the air conditioning unit 100 to suppress the occurrence of surging.

[0070] (4-9) The diameter of the fan of the impeller 30 is 126 mm or more.

[0071] According to this configuration, a cross-flow fan with a large fan diameter is used for the impeller 30, so noise and power consumption can be reduced during air conditioning operation.

[0072] (4-10) The air conditioning unit 100 satisfies formula (3): (diameter of impeller fan / height dimension of air conditioning unit)≧(126 / 300).

[0073] According to this configuration, a cross-flow fan with a large diameter impeller 30 is used for the indoor unit body, so noise and power consumption can be reduced during air conditioning operation.

[0074] (5) Modifications (5-1) Modification A In the above embodiment, the width dimension of the first end 71a is the same as the width dimension of the second end 71b. However, the width dimensions of the first end 71a and the second end 71b are not particularly limited to this. The width dimensions of the first end 71a and the second end 71b may be different. For example, the width dimension of the first end 71a may be smaller than the width dimension of the second end 71b.

[0075] In this case, the wind speed at the first end 71a, which is originally slower, can be made higher than that at the second end 71b.

[0076] (5-2) Modification Example B In the above embodiment, the length M2 of the second end 71b in the rotational axis direction is the same as the length M of the first end 71a in the rotational axis direction. However, the length M2 of the second end 71b in the rotational axis direction may be different from the length M of the first end 71a in the rotational axis direction. For example, the length M2 of the second end 71b in the rotational axis direction may be smaller than the length M of the first end 71a in the rotational axis direction.

[0077] In this case, the wind speed at the first end 71a, which is originally slower, can be made higher than that at the second end 71b.

[0078] (5-3) Modification C In the above embodiment and Modification 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 widths of the first end 71a and the second end 71b are not particularly limited to this. For example, only the width of the first end 71a may be smaller than the width of the central portion 71c.

[0079] In this case, the wind speed can be increased at the first end 71a, where the wind speed is originally slower.

[0080] (5-4) Modification D In the above embodiment, the width of the first end 71a is constant in the rotational axis direction. However, this is not particularly limited. As shown in Fig. 10, the width of the tongue 71 at the first end 71a may be gradually reduced with increasing distance from the central portion 71c.

[0081] In this case, the continuity of the circulating vortex generated inside the impeller 30 in the direction of the rotation axis is less likely to be lost, so air blowing is more likely to be stable.

[0082] In the case of the modified example D, in the formula (2), the third straight line L3 is a straight line extending from the rotation axis O to the edge of the suction side S1 at the center of the first end 71a.

[0083] (5-5) Modification E As shown in FIG. 11, at the first end 71a, the width dimension of the tongue portion 71 may decrease in a slope shape with increasing distance from the central portion 71c.

[0084] In this case, the continuity of the circulating vortex generated inside the impeller 30 in the direction of the rotation axis is not lost, so air blowing is stable.

[0085] In the case of the modified example E, in the formula (2), the third straight line L3 is a straight line extending from the rotation axis O to the edge of the suction side S1 at the center of the first end 71a.

[0086] (5-6) Modification F As shown in FIG. 11, the first end 71a and the second end 71b may have different shapes.

[0087] Blower devices with impeller fan diameters of 115 mm, 126 mm, 135 mm, and 149 mm were prepared. For each blower, the angle θa, as viewed in the direction of the rotational axis, between a first line extending from the rotational axis to the suction-side edge of the central portion and a second line extending from the rotational axis to the blow-side edge of the central portion was defined as θa. The angle θb, as viewed in the direction of the rotational axis, between a third line extending from the rotational axis to the suction-side edge of the first end and a fourth line extending from the rotational axis to the blow-side edge of the first end was defined as θb / θa = 0.85. For each blower, the width of the tongue portion was varied at both the first and second ends, and the static pressure increase was measured. The width of the tongue portion was the same at both the first and second ends. The results are shown in Figure 5.

[0088] Furthermore, blowers with θb / θa ratios of 0.98, 0.85, 0.68, and 0.39 were prepared. The diameter of the impeller fan for each was 135 mm. For each blower, the width of the tongue portion was varied at both the first end and the second end, and the increase in static pressure was measured. The results are shown in Figure 6.

[0089] 5 and 6, the horizontal axis represents M / D and the vertical axis represents static pressure increase. Test results showed that the static pressure increase was large when the M / D was between 0.10 and 1.35. This means that surging was suppressed.

[0090] A blower with an impeller fan diameter of 135 mm was prepared. M / D = 0.30 was used. The increase in static pressure was measured by varying θb / θa. The increase in static pressure was measured when θb / θa was varied at both the first and second ends, and when θb / θa was varied only at the first end. When θb / θa was varied at both the first and second ends, the value of θb / θa at the first end and the value of θb / θa at the second end were kept the same. The results are shown in Figure 7.

[0091] In Figure 7, the horizontal axis is θb / θa, and the vertical axis is the static pressure increase. As a result of the test, when θb / θa was changed at both the first end and the second end, the static pressure increase was large when θb / θa was 0.39 to 0.98. This means that the occurrence of surging was suppressed.

[0092] Blower devices with impeller fan diameters of 115 mm, 126 mm, 135 mm, and 149 mm were prepared. For each blower, θb / θa was set to 0.85. For each blower, the width of the tongue portion at the first end was varied, and the static pressure increase was measured. The width of the tongue portion at the second end was the same as the width of the tongue portion at the center.

[0093] Furthermore, for a blower with an impeller fan diameter of 135 mm, the width of the tongue was changed at the second end, where the wind speed was originally high, and the static pressure increase was measured. In this example, the width of the tongue at the first end was the same as that at the center.

[0094] The results are shown in FIG.

[0095] In Figure 9, the horizontal axis represents M / D and the vertical axis represents static pressure increase. Test results showed that the static pressure increase was large when M / D was between 0.10 and 1.35. This means that surging was suppressed at the first end even when only the width dimension of the tongue portion was changed.

[0096] Although the embodiments of the present disclosure have been described above, it will be understood that various changes in form and details can be made without departing from the spirit and scope of the present disclosure as defined in the claims.

[0097] DESCRIPTION OF SYMBOLS 10 Casing 10a Intake port 10b Outlet port 10c Outlet air flow path 17 Stabilizer 18 Rear guider 20 Heat exchanger 30 Impeller 30a Imaginary circle (imaginary circumscribed circle) connecting outer ends of fan blades 31 Fan blade 71 Tongue portion of stabilizer 71a First end 71b Second end 71c Central portion 73 Support portion of stabilizer 100 Air conditioning unit 101 Blower device O Fan rotation axis L1 First straight line L2 Second straight line L3 Third straight line L4 Fourth straight line S1 Intake side S2 Outlet side

[0098] JP 2016-50720 A

Claims

1. A blower (101) comprising: an impeller (30); and a casing (10) including a tongue portion (71) extending along the rotational axis direction of the impeller and separating an intake side (S1) and an exhaust side (S2), wherein the tongue portion has a first end (71a) and a second end (71b) located at both ends in the rotational axis direction, and a central portion (71c) located between the first end and the second end, and with respect to a width dimension of the tongue portion, which is the length from the suction side edge of the tongue portion to the exhaust side edge of the tongue portion, the width dimension of the tongue portion at the first end is smaller than the width dimension of the tongue portion at the central portion.

2. The blower device according to claim 1, wherein the blowing side edge of the central portion and the blowing side edge of the first end portion are at the same position when viewed in the direction of the rotation axis.

3. A blower device as described in claim 1 or claim 2, wherein the first end is the end at which the wind speed is slower when the width dimension of the tongue portion is the same at the central portion, the first end, and the second end.

4. A blower device according to any one of claims 1 to 3, wherein the width dimensions of the first end and the second end are smaller than the width dimension of the central portion.

5. A blower device according to any one of claims 1 to 4, wherein the width dimension of the first end is smaller than the width dimension of the second end.

6. The air blower device according to any one of claims 1 to 5, wherein at said first end, the width dimension of said tongue portion gradually decreases with increasing distance from said central portion.

7. The blower device according to any one of claims 1 to 6, wherein a gap dimension between the central portion and the impeller is equal to a gap dimension between the first end portion and the impeller.

8. The blower according to any one of claims 1 to 7, wherein when the length dimension of the first end in the rotational axis direction is M and the outer diameter of the impeller is D, formula (1) is satisfied. Formula (1): 0.10≦M / D≦1.

35.

9. The blower according to any one of claims 1 to 8, wherein when the angle, as viewed in the direction of the rotation axis, made by a first line (L1) extending from a rotation axis (O) to an edge on the suction side of the central portion and a second line (L2) extending from the rotation axis to an edge on the blowing side of the central portion is θa, and the angle, as viewed in the direction of the rotation axis, made by a third line (L3) extending from the rotation axis to the edge on the suction side of the first end and a fourth line (L4) extending from the rotation axis to the edge on the blowing side of the first end is θb, the formula (2) is satisfied. Formula (2): 0.39≦θb / θa≦0.98 10. The blower according to any one of claims 1 to 9, wherein formulas (1) and (2) are satisfied when the length dimension in the rotation axis direction of the first end is M, the outer diameter of the impeller is D, the angle as viewed in the rotation axis direction made by a first line extending from the rotation axis to the suction side edge of the central portion and a second line extending from the rotation axis to the blowing side edge of the central portion is θa, and the angle as viewed in the rotation axis direction made by a third line extending from the rotation axis to the suction side edge of the first end and a fourth line extending from the rotation axis to the blowing side edge of the first end is θb. Formula (1): 0.10≦M / D≦1.35 Formula (2): 0.39≦θb / θa≦0.98 11. An air conditioning unit (100) comprising a blower device according to any one of claims 1 to 10.

12. An air conditioning unit comprising the blower 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 equipped with the blower device according to any one of claims 1 to 10, which satisfies formula (3): (diameter of impeller fan / height dimension of air conditioning unit) ≧ (126 / 300).

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