Blower and air conditioning unit

Abstract

To provide an air blowing device in which surging can be suppressed.SOLUTION: An air glowing device (101) includes an impeller (30) and a casing (10). The casing includes a tongue portion (71). The tongue portion extends along a rotational axis direction of the impeller and partitions an inlet side (S1) and an outlet side (S2). The tongue portion includes a first end portion (71a) and a second end portion (71b) and a center portion (71c). The first end portion and the second end portion are positioned at both ends in the rotational axis direction. The center portion is positioned between the first end portion and the second end portion. A width dimension of the tongue portion is a length from an end edge on the inlet side of the tongue portion to an end edge on the outlet side. The width dimension at the first end portion is smaller than the width dimension at the center portion of the tongue portion.SELECTED DRAWING: Figure 3

Description

[Technical field]

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

[0002] Conventionally, indoor units of air conditioners (hereinafter referred to as air conditioning units) that are installed on the side walls of a room instead of on the ceiling, take in air from the front or top, and blow out the conditioned air from an outlet at the bottom have been widely used. For example, as shown in Patent Document 1 (JP Patent Publication No. 2016-50720), a heat exchanger that exchanges heat between the refrigerant and the air and a blower are housed inside the air conditioning unit. The blower in Patent Document 1 includes a crossflow fan. Summary of the Invention [Problem to be solved by the invention]

[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 instability in the blown air (so-called surging). [Means for solving the problem]

[0004] A blower device according to a first aspect includes an impeller and a casing. The casing includes a tongue portion. The tongue portion extends along the direction of the rotation axis 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 both ends in the direction of the rotation axis. The central portion is located between the first end portion and the second end portion. With respect to the width dimension of the tongue portion, which is the length from the edge of the tongue portion on the suction side to the edge of the tongue portion on the blowing side, 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 third aspect of the invention is a blower device according to the first or second aspect, wherein 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 width dimension of the first end and the second end is smaller than the width dimension of the central portion.

[0009] A fifth aspect of the invention is the blower device 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 a blower device according to any one of the first to fifth aspects, wherein at the first end, the width dimension of the tongue portion gradually decreases with increasing distance from the central portion.

[0011] A seventh aspect of the invention 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] The blower device of an eighth aspect is a blower device of any one of the first aspect to the seventh aspect, which satisfies formula (1) when the length dimension in the rotational axis direction of the first end is M and the outer diameter of the impeller is D. Formula (1): 0.10≦M / D≦1.35

[0013] A blower device of a ninth aspect is a blower device of any one of the first aspect to the eighth aspect, which satisfies formula (2) when the angle, as viewed in the direction of the rotational axis, made by 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 blowing side edge of the central portion is θa, and the angle, as viewed in the direction of the rotational axis, made by 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 blowing side edge of the first end is θb. Formula (2): 0.39≦θb / θa≦0.98

[0014] A blower device of a tenth aspect is a blower device of any of the first aspect to the ninth aspect, which satisfies equations (1) and (2) when the length dimension in the rotational axis direction of the first end 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 the suction side edge of the central portion and a second line extending from the rotational axis to the blowing side edge 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 suction side edge of the first end and a fourth line extending from the rotational 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

[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 aspect to the tenth aspect. The diameter of the impeller fan is 126 mm or more.

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

[0018] [Figure 1] 1 is a configuration diagram of an air conditioning device consisting of an air conditioning outdoor unit and an air conditioning unit. [Diagram 2] 2 is a longitudinal cross-sectional view of the air conditioning unit at the center (cross-sectional view taken along the line II-II of FIG. 1 ). [Diagram 3] FIG. [Figure 4] FIG. [Diagram 5] 1 is a graph showing the relationship between M / D and the increase in static pressure, where M is the length in the rotation axis direction and D is the outer diameter of the impeller. [Figure 6] 11 is another graph showing the relationship between M / D and the static pressure increase amount, where M is the length dimension in the rotation axis direction and D is the outer diameter of the impeller. [Figure 7] 13 is a graph showing the relationship between the angle range of the tongue with respect to the axis of rotation and the amount of static pressure increase. [Figure 8] FIG. 13 is a perspective view of a tongue portion in a modified example. [Figure 9] 13 is a graph showing the relationship between M / D and the static pressure increase amount when the length dimension in the rotation axis direction of the modified example is M and the outer diameter of the impeller is D. [Figure 10] FIG. 13 is a perspective view of a tongue in another modified example. [Figure 11] FIG. 13 is a perspective view of a tongue in another modified example. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[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. In addition, expressions indicating directions such as "up", "down", and "front" are used as appropriate, but these indicate 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. In addition, expressions such as "same" and "parallel" may be used, but these include not only cases where they are completely the same or parallel, but also cases where they are substantially the same or parallel.

[0020] (1) Overall structure 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 placed outside the room via refrigerant piping 93 to form an air conditioner 90. The air conditioning unit 100 performs cooling operation and heating operation in the room 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 crossflow fan including an impeller 30 and a casing 10 .

[0023] (2-1) Crossflow fan The crossflow fan includes a cylindrical impeller 30 that extends long in the horizontal direction, and a motor that rotates the impeller 30. The impeller 30 has a large number of fan blades 31 arranged along the 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 shown by a dotted line in FIG. 2; hereinafter, referred to as an imaginary circumscribing circle) connecting the outer ends of the multiple 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 dimension of the air conditioning unit 100 satisfy formula (3). Formula (3): (Diameter of impeller 30 fan / height of 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 a user's operation input 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 exhaust 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 exhaust port 10b is located lower than the rotation axis O. More specifically, the exhaust port 10b is formed in the front side portion of the bottom surface of the casing 10, and blows air forward and downward of 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 closer to the front than 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 air outlet 10b.

[0032] 3, tongue portion 71 extends along the rotation axis direction of impeller 30. In other words, the longitudinal direction of tongue portion 71 is parallel to the rotation axis direction of impeller 30. Tongue portion 71 separates an intake side S1 and an exhaust side S2 in the internal space of blower 101. Tongue portion 71 has a curved surface facing 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 both ends in the rotation axis direction. 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, and may be smaller on the blowing side S2 than on the blowing side S2.

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

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

[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 71c and the edge of the blowing side S2 of the first end portion 71a are at the same position. That is, 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. In detail, 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 rotation axis direction is M and the outer diameter of the impeller 30 is D, M / D satisfies formula (1). Formula (1): 0.10≦M / D≦1.35

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

[0042] As shown in Fig. 4, the angle 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 blowing side S2 of the central portion 71c is defined as θa when viewed in the direction of the rotation axis. The angle 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 blowing side S2 of the first end portion 71a is defined as θb when viewed in the direction of the rotation axis. 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 dimension of tongue portion 71 at second end portion 71b is smaller than the width dimension of tongue portion 71 at central portion 71c. The width dimension of tongue portion 71 at second end portion 71b is the same as the width dimension of tongue portion 71 at first end portion 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 71c and the edge of the blowing side S2 of the second end portion 71b are at the same position. That is, 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. In particular, 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 dimension of the second end 71b in the rotation axis direction is M' and the outer diameter of the impeller 30 is D, M' / D satisfies formula (1)'. Formula (1)´:0.10≦M´ / D≦1.35

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

[0051] The angle, as viewed in the direction of the rotation axis, made by 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 blowing side S2 of the central portion 71c is defined as θa. The angle, as viewed in the direction of the rotation axis, made by a fifth straight 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 straight line L6 extending from the rotation axis O to the edge of the blowing side S2 of the second end portion 71b is defined as θb'. θa is greater than θb'. Specifically, θb' / θa satisfies formula (2)'. Equation (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 exchangers and filters The heat exchanger 20 is a fin-and-tube type heat exchanger having a V-shape in a vertical 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 the air flowing from the suction port 10a side to the impeller 30 side and the refrigerant flowing through the tubes. The heat exchanger 20 is composed of a large number of aluminum heat transfer fins and a large number of tubes that pass through a large number of holes opened in the heat transfer fins. The tubes, which are copper heat transfer tubes, have an outer diameter of 5 mm or 4 mm.

[0054] The air flow upstream side of 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 collects dust contained in the air flowing from the suction port 10a to the heat exchanger 20.

[0055] (4) Features (4-1) Compared to the center, both ends of the crossflow fan in the direction of the rotation axis are affected by suction from the sides. This causes the air flow to separate at the sides. As a result, air is less easily sucked in at both ends of the crossflow fan, and the circulating vortex of the air inside the fan becomes larger. As a result, the wind speed decreases and surging occurs. At this time, the circulating vortex at both ends inside the crossflow fan becomes larger than the circulating vortex in the center, as shown by the dashed arc 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 blowing side S2 of the tongue 71, is smaller at the first end 71a than at the center 71c. As a result, the circulating vortex inside the crossflow fan becomes smaller at the first end 71a and the second end 71b, like the solid arc shown in FIG. 4. This makes it possible to increase the static pressure in the blowing flow path, and therefore the wind speed. As a result, the occurrence of surging can be suppressed.

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

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

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

[0060] Therefore, it is possible to increase the blowing speed at the end portion where the wind speed is originally slower.

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

[0062] Here, since the width dimension of the first end portion 71a and the second end portion 71b is smaller than the width dimension of the central portion 71c, the blowing speed can be made larger than if the width dimension of only one end were reduced.

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

[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 rotation axis direction is M and the outer diameter of the impeller 30 is D, formula (1) is satisfied. Formula (1): 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) Equation (2) is satisfied when the angle, as viewed in the direction of the rotational axis, made by 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-out side S2 of the central portion 71c is θa, and the angle, as viewed in the direction of the rotational axis, made by a third straight line L3 extending from the rotation axis O to the edge of the suction side S1 of the first end 71a and a fourth straight line L4 extending from the rotation axis O to the edge of the blow-out side S2 of the first end 71a is θb. Formula (2): 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 air blower 101. This allows the air conditioning unit 100 to suppress the occurrence of surging.

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

[0071] According to this configuration, since a cross-flow fan with a large fan diameter is used for the impeller 30, it is possible to reduce noise and power consumption during air-conditioning operation.

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

[0073] According to this configuration, since a crossflow 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 conditioning operation.

[0074] (5) Variations (5-1) Variation 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 can be made higher at the first end 71a, where the wind speed is originally slower, than at the second end 71b.

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

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

[0078] (5-3) Variation C In the above embodiment and modification 1A, both the width dimension of the first end 71a and the width dimension of the second end 71b are smaller than the width dimension of the central portion 71c. However, the width dimensions of the first end 71a and the width dimensions of the second end 71b are not particularly limited to this. For example, only the width dimension of the first end 71a may be smaller than the width dimension 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) Variation D In the above embodiment, the width of the first end 71a is constant in the rotation 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 as it moves away 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 unlikely to be lost, so that air blowing tends to be stable.

[0082] In the case of the modified example D, in 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) Variation E As shown in FIG. 11, at the first end 71a, the width dimension of the tongue 71 may decrease in a sloping manner 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 that air blowing is stable.

[0085] In the case of the modified example E, in 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) Variation F As shown in FIG. 11, the first end 71a and the second end 71b may have different shapes. EXAMPLES

[0087] Blower devices with impeller fan diameters of 115 mm, 126 mm, 135 mm, and 149 mm were prepared. The angle θa of each blower device as viewed in the direction of the rotation axis between a first line extending from the rotation axis to the edge of the suction side of the central part and a second line extending from the rotation axis to the edge of the blowing side of the central part, and the angle θb of each blower device as viewed in the direction of the rotation axis between a third line extending from the rotation axis to the edge of the suction side of the first end and a fourth line extending from the rotation axis to the edge of the blowing side of the first end were set to θb / θa = 0.85. In each blower device, only the width dimension of the tongue was changed in various ways at both the first end and the second end, and the static pressure increase was measured. The width dimension of the tongue was the same at the first end and the second end. The results are shown in Figure 5.

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

[0089] 5 and 6, the horizontal axis is M / D and the vertical axis is the static pressure increase. Test results showed that when M / D is 0.10 to 1.35, the static pressure increase is large. This means that the occurrence of surging is suppressed. EXAMPLES

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

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

[0092] Blower devices with impeller fan diameters of 115 mm, 126 mm, 135 mm, and 149 mm were prepared. For each blower, θb / θa=0.85 was used. For each blower, only the width dimension of the tongue at the first end was changed in various ways, and the static pressure increase was measured. The width dimension of the tongue at the second end was the same as the width dimension of the tongue at the center.

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

[0094] The results are shown in Figure 9.

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

[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 described in the claims. [Explanation of symbols]

[0097] 10 Casing 10a Intake port 10b Air outlet 10c Air outlet passage 17 Stabilizer 18 Rear Guide 20 Heat exchanger 30 Impeller 30a: Imaginary circle connecting the outer ends of the fan blades (imaginary circumscribing circle) 31 Fan wing 71 Stabilizer tongue 71a First end 71b Second end 71c central part 73 Stabilizer support 100 air conditioning units 101 Blower O Fan Rotation Shaft L1 1st straight line L2 2nd straight line L3 3rd straight line L4 4th Straight Line S1 Suction side S2 Outlet side [Prior art documents] [Patent documents]

[0098] [Patent Document 1] JP 2016-50720 A

Claims

1. A crossflow fan impeller (30) having a plurality of fan blades (31) arranged along a circumference and having a rotation axis (O) as a center of rotation; a casing (10) including a tongue portion (71) extending along a rotation axis direction of the impeller and separating an intake side (S1) from an exhaust side (S2); Equipped with The tongue portion has a first end portion (71a) and a second end portion (71b) located at both ends in the rotation axis direction, and a central portion (71c) located between the first end portion and the second end portion, The tongue portion has a curved surface facing the impeller when viewed in the rotation axis direction, The curved surface extends along an imaginary circumscribing surface (30a) connecting the outer ends of the fan blades, With respect to a width dimension of the tongue portion, which is a length from an end edge on the suction side to an end edge on the blowing side as viewed in the rotation axis direction, 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, When viewed in the rotation axis direction, an edge of the curved surface at the first end portion on the suction side (S1) is located closer to the blowing side (S2) than an edge of the curved surface at the central portion on the suction side (S1). Blower device (101).

2. 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. The blower device according to claim 1 .

3. The first end portion is an end portion 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 portion, and the second end portion. The blower device according to claim 1 .

4. The width dimension of the first end portion and the second end portion is smaller than the width dimension of the central portion. The blower device according to claim 1 .

5. The width dimension of the first end is smaller than the width dimension of the second end. The blower device according to claim 1 .

6. At the first end, a width dimension of the tongue portion gradually decreases with increasing distance from the central portion. The blower device according to claim 1 .

7. A gap dimension between the central portion and the impeller is equal to a gap dimension between the first end portion and the impeller. The blower device according to claim 1 .

8. When the length dimension of the first end in the rotation axis direction is M and the outer diameter of the impeller is D, formula (1) is satisfied. The blower device according to claim 1 . Formula (1): 0.10≦M / D≦1.35

9. Equation (2) is satisfied when the angle, as viewed in the direction of the rotation axis, made by a first straight line (L1) extending from the rotation axis (O) to the suction side edge of the central portion and a second straight line (L2) extending from the rotation axis to the blowing side edge of the central portion is θa, and the angle, as viewed in the direction of the rotation axis, made by a third straight line (L3) extending from the rotation axis to the suction side edge of the first end and a fourth straight line (L4) extending from the rotation axis to the blowing side edge of the first end is θb. The blower device according to claim 1 . Formula (2): 0.47≦θb / θa≦0.90

10. Formula (1) and Formula (2) are satisfied when a length dimension in the rotation axis direction of the first end is M, an outer diameter of the impeller is D, an angle as viewed in the rotation axis direction made by a first line extending from the rotation axis to an edge on the suction side of the central portion and a second line extending from the rotation axis to an edge on the blowing side of the central portion is θa, and an angle as viewed in the rotation axis direction made by a third line extending from the rotation axis to the edge on the suction side of the first end and a fourth line extending from the rotation axis to the edge on the blowing side of the first end is θb. The blower device according to claim 1 . Formula (1): 0.10≦M / D≦1.35 Formula (2): 0.47≦θb / θa≦0.90

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. Air conditioning unit.

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

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