JP5716766B2 - Air conditioner - Google Patents

Description

  The present invention relates to an air conditioner including a cross flow fan.

  The cross flow fan is a blower having a plurality of blades extending in the axial direction and arranged in the rotation direction. As the cross flow fan applied to the air conditioner, a plurality of impellers having a plurality of blades are arranged in the axial direction and connected. In an air conditioner including a cross flow fan, a stabilizer and a rear guider are disposed on both sides of the outer peripheral portion of the fan. The stabilizer is called the front tongue, and the fan closest part from the front end of the rear guider is called the rear tongue. These tongue portions constitute a ventilation path on the blowing side of the fan. In addition, a vortex airflow is generated between the tongue and the fan, and when the fan blades pass through the vortex airflow, a wind noise (NZ sound) is generated by the interference between the vortex airflow and the blades. To do.

  In order to reduce this wind noise, conventionally, the timing of generating wind noise is dispersed by shifting the position of the blades between adjacent impellers in the circumferential direction or changing the shape of the tongue.

  As an example of reducing the wind noise by changing the shape of the tongue portion, for example, in Patent Document 1, the position closest to the fan in the front tongue portion and the rear tongue portion is shifted in the rotation axis direction for each impeller. . That is, the front tongue portion and the rear tongue portion have a step portion at a position facing the connecting portion between the impellers. With this configuration, the timing at which the blade passes through the front tongue portion or the tip of the rear tongue portion is shifted for each impeller, so the timing at which the wind noise is generated is dispersed and the wind noise is reduced.

JP-A-62-118094

  However, in the air conditioner of Patent Document 1, since the timing at which the blades pass through the front tongue portion or the tip of the rear tongue portion is shifted for each impeller, wind noise can be reduced to some extent, but one blade wheel can be reduced. Since the timing at which the blades pass through the front tongue part or the rear tongue part is the same, the noise reduction effect was not sufficient.

  Then, an object of this invention is to provide the air conditioner which can reduce a wind noise more.

An air conditioner according to a first aspect of the present invention is a crossflow fan in which a plurality of impellers each having a plurality of blades arranged at unequal pitches in the circumferential direction are arranged in an axial direction, and the crossflow fan A stabilizer and a rear guider that are arranged on both sides of the outer peripheral portion, and at least one tip portion of the stabilizer and the rear guider is a plurality of step portions that are shifted in the circumferential direction of the crossflow fan. The plurality of stepped portions include at least one first stepped portion that faces an intermediate portion in the axial direction of the impeller, and the impeller that faces the first stepped portion. when viewed corresponding blades of the adjacent impeller thereto, blades of the other axial end of the impeller relative to the blades of the axial end of the impeller is the cross flow fan of times Are arranged to be shifted a predetermined angle in the direction, the circumferential direction of the displacement direction of the first step portion in the direction toward the other end from the one axial end is adjacent thereto and the impeller opposite to the first stepped portion The impeller is in a direction opposite to a circumferential shift direction between the blades of the impeller.

  In this air conditioner, the tip of at least one of the stabilizer and the rear guider has a first step portion that is shifted in the circumferential direction at a position facing an intermediate portion in the axial direction of the impeller. The timing of passing the front end of the rear guider can be shifted from the first step portion. Therefore, the wind noise can be generated by shifting without generating the wind noise with one blade at the same time. Therefore, wind noise can be reduced.

  The air conditioner according to a second invention is characterized in that, in the first invention, the plurality of stepped portions include a second stepped portion facing a connecting portion between the impellers.

  In this air conditioner, the tip of the stabilizer or the rear guider has a second step portion that is shifted in the circumferential direction at a position facing the connecting portion of the impellers, so that the timing of generating wind noise for each impeller is generated. The wind noise can be further reduced.

  An air conditioner according to a third invention is characterized in that, in the first or second invention, the height of a portion between two adjacent step portions is constant in the axial direction.

  In this air conditioner, the stabilizer or the rear guider has a tip portion between two adjacent stepped portions extending linearly in the axial direction, so that it is easy to produce the stabilizer or the rear guider.

  The air conditioner according to a fourth aspect of the present invention is the air conditioner according to the third aspect of the present invention, wherein the plurality of stepped portions are two or more first stepped portions that respectively face the middle portions in the axial direction of the two adjacent impellers, A second stepped portion facing the connecting portion between the two impellers, and in a direction from one axial end to the other end, the displacement direction of the first stepped portion in the circumferential direction is the second stepped portion. The shape and the height of a range opposite to the circumferential direction of the portion and opposite to the two adjacent impellers in the tip portion are the same.

  In this air conditioner, the tip portion of the stabilizer or the rear guider has a first step portion in a range facing two adjacent impellers, and the shape and height of the range facing the two impellers are different. They are the same as each other. Therefore, it is easy to produce a stabilizer or a rear guider. Further, the height of the tip of the stabilizer or the rear guider can be made substantially the same as a whole.

The air conditioner according to a fifth aspect of the present invention is the air conditioner according to the third aspect, wherein the plurality of stepped portions are opposed to a connecting portion between the impeller facing the first stepped portion and the impellers on both sides thereof. In the direction from one axial end to the other end, the displacement direction of the first step portion in the circumferential direction is opposite to the circumferential displacement direction of the second step portion. Te, before Symbol circumferential direction of the deviation angle of the second step portion, and wherein the go smaller than the predetermined angle.

  In this air conditioner, the shift direction of the first step portion and the second step portion is the reverse direction, and the shift direction of the blades arranged with a predetermined angle shift is the reverse direction of the shift direction of the first step portion. Since the deviation angle of the second step portion is smaller than the predetermined angle, the time difference between the two wind noises that occur at the first step portion and the second step portion are generated at the boundary. The time shift direction of the two wind noises can be made the same. Therefore, it is possible to generate the wind noise by sequentially shifting from one axial end to the other end of the crossflow fan. Thereby, the directivity due to the interference of wind noise generated between the step portions can be suppressed, and the sound can be effectively silenced throughout the room.

  The air conditioner according to a sixth aspect of the present invention is the air conditioner according to the fifth aspect of the present invention, wherein the circumferential deviation angle of the first stepped portion is the predetermined angle, and the axial range of the impeller that faces the first stepped portion. The first stepped portion is equal to a value obtained by dividing the number of the first stepped portions by one, and a circumferential shift angle of the second stepped portion is equal to that of the first stepped portion in the axial range. It is the same as the total value of the deviation angles in the circumferential direction.

In this air conditioner, the two wind cuts that occur with the first stepped portion deviated from the boundary are defined as the deviation angle of the first stepped portion (the deviation angle between the blades (predetermined angle)) within the axial range of the impeller. The two wind noises generated by shifting by the number of the first step portions divided by the value obtained by adding 1 to the number of the first step portions and the two wind noises generated by shifting the second step portion as a boundary The angle is shifted by the angle obtained by subtracting the shift angle of the second step portion from the angle). Therefore, the deviation time of the two wind noises generated at the boundary of the first step portion and the deviation time of the two wind noises generated at the boundary of the second step portion can be made the same. Therefore, the present invention provides a silent effect similar to that obtained when the number of impellers is increased so that the connecting portion of the impeller faces the position corresponding to the first stepped portion of the present invention without providing the first stepped portion. Can be obtained. In other words, the present invention can reduce the number of impellers by increasing the impeller blade length while maintaining silent performance. Moreover, since the number of the connection parts of the impeller used as ventilation resistance can be reduced, ventilation characteristics can be improved.
An air conditioner according to a seventh aspect of the present invention is a cross flow fan in which a plurality of impellers each having a plurality of blades arranged in the circumferential direction are arranged in the axial direction, and the outer periphery of the cross flow fan A stabilizer and a rear guider that are arranged on both sides of the unit to form a ventilation path, and at least one tip of the stabilizer and the rear guider has a plurality of stepped portions that are shifted in the circumferential direction of the crossflow fan. The multi-step shape, wherein the plurality of stepped portions include at least one first stepped portion facing an axial middle portion of the impeller, and a height of a portion between two adjacent stepped portions. Are constant in the axial direction, and the plurality of stepped portions are two second steps facing the connecting portions of the impeller facing the first stepped portion and the impellers on both sides thereof. In the direction from one end to the other end in the axial direction, the circumferential shift direction of the first stepped portion is opposite to the circumferential shift direction of the second stepped portion and is adjacent to 2 The blades of the two impellers are arranged so as to be shifted by a predetermined angle in the circumferential direction, and a circumferential shift angle of the second stepped portion is smaller than the predetermined angle, and is directed from one axial end to the other. In the direction, a circumferential shift direction of the first step portion is opposite to a circumferential shift direction between the blades of the two adjacent impellers.
An air conditioner according to an eighth aspect of the present invention is the air conditioner according to the seventh aspect of the present invention, wherein a circumferential shift angle of the first step portion is opposite to the first step portion with the predetermined angle. It is the same as the value obtained by dividing the number of the first stepped portions in the axial range of the impeller by 1 and the circumferential deviation angle of the second stepped portion is in the axial range. It is the same as the total value of the circumferential shift angles of a certain first stepped portion.

  As described above, according to the present invention, the following effects can be obtained.

  In the first invention, since at least one tip portion of the stabilizer and the rear guider has a first step portion shifted in the circumferential direction at a position facing the middle portion in the axial direction of the impeller, one blade is the stabilizer or The timing of passing the front end of the rear guider can be shifted from the first step portion. Therefore, the wind noise can be generated by shifting without generating the wind noise with one blade at the same time. Therefore, wind noise can be reduced.

  In the second invention, the tip of the stabilizer or the rear guider has the second step portion that is shifted in the circumferential direction at a position facing the connecting portion of the impellers, so that the timing of generating wind noise for each impeller is generated. The wind noise can be further reduced.

  In 3rd invention, since the part between two adjacent level | step-difference parts has extended in the axial direction at the front-end | tip part of a stabilizer or a rear guider, it is easy to produce a stabilizer or a rear guider.

  In 4th invention, the front-end | tip part of a stabilizer or a rear guider has a 1st level | step-difference part in the range which opposes two adjacent impellers, respectively, and the shape and height of the range which opposes the said 2 impellers are the same. They are the same as each other. Therefore, it is easy to produce a stabilizer or a rear guider. Further, the height of the tip of the stabilizer or the rear guider can be made substantially the same as a whole.

  In the fifth aspect of the invention, the displacement direction of the first step portion and the second step portion is the reverse direction, and the displacement direction of the blades arranged at a predetermined angle is opposite to the displacement direction of the first step portion. Since the deviation angle of the second step portion is smaller than the predetermined angle, the time difference between the two wind noises that occur at the first step portion and the second step portion are generated at the boundary. The time shift direction of the two wind noises can be made the same. Therefore, it is possible to generate the wind noise by sequentially shifting from one axial end to the other end of the crossflow fan. Thereby, the directivity due to the interference of wind noise generated between the step portions can be suppressed, and the sound can be effectively silenced throughout the room.

  In the sixth aspect of the invention, the two wind cuts that occur with the first stepped portion deviated from the boundary are defined as a deviation angle of the first stepped portion (a deviation angle between the blades (predetermined angle)) within an axial range of the impeller. The two wind noises generated by shifting by the number of the first step portions divided by the value obtained by adding 1 to the number of the first step portions and the two wind noises generated by shifting the second step portion as a boundary The angle is shifted by the angle obtained by subtracting the shift angle of the second step portion from the angle). Therefore, the deviation time of the two wind noises generated at the boundary of the first step portion and the deviation time of the two wind noises generated at the boundary of the second step portion can be made the same. Therefore, the present invention provides a silent effect similar to that obtained when the number of impellers is increased so that the connecting portion of the impeller faces the position corresponding to the first stepped portion of the present invention without providing the first stepped portion. Can be obtained. In other words, the present invention can reduce the number of impellers by increasing the impeller blade length while maintaining silent performance. Moreover, since the number of the connection parts of the impeller used as ventilation resistance can be reduced, ventilation characteristics can be improved.

It is an external appearance perspective view of the indoor unit of the air conditioner which concerns on embodiment of this invention. It is sectional drawing of an indoor unit. It is a perspective view of a cross flow fan. It is a partial expansion perspective view near the cross flow fan in the indoor unit. It is the figure which looked at the cross flow fan vicinity in an indoor unit from the front. It is the figure which looked at the cross flow fan vicinity in an indoor unit from upper direction. FIG. 7 is a partially enlarged view of the vicinity of a rear guider in a cross-sectional view taken along line AA in FIGS. 5 and 6. It is a perspective view of the front end side part of a rear guider. It is the elements on larger scale near the stabilizer of sectional drawing along the AA line of Drawing 5 and Drawing 6. It is a perspective view of a front guider. It is the elements on larger scale of FIG. It is the elements on larger scale when the rear guider and crossflow fan which concern on other embodiment of this invention are seen from upper direction. It is a perspective view of the rear guider which concerns on other embodiment of this invention. It is a perspective view of the front guider which concerns on other embodiment of this invention.

Embodiments of the present invention will be described below.
As shown in FIG. 1, the indoor unit 1 of the air conditioner of this embodiment has an elongated shape in one direction as a whole, and is installed on the wall surface of the room so that the longitudinal direction is horizontal. The indoor unit 1 constitutes an air conditioner together with an outdoor unit (not shown), and performs indoor air conditioning.
In the following description, the direction protruding from the wall to which the indoor unit 1 is attached is referred to as “front”, and the opposite direction is referred to as “rear”. Further, the left-right direction shown in FIG. 1 is simply referred to as “left-right direction”.

  As shown in FIG. 2, the indoor unit 1 includes a casing 2 and internal devices such as a heat exchanger 3, a cross flow fan 10, a filter 4, and an electrical component box (not shown) housed in the casing 2. Yes. A suction port 2 a is formed on the upper surface of the casing 2, and an air outlet 2 b is formed on the lower surface of the casing 2. In the vicinity of the air outlet 2b, a horizontal flap 5 for adjusting the wind direction in the vertical direction and opening and closing the air outlet 2b is disposed.

  The cross flow fan 10 (hereinafter simply referred to as the fan 10) is disposed such that its axial direction is along the left-right direction, and rotates in the direction indicated by the arrow in FIG. A front guider 30 and a rear guider (rear tongue) 20 that form a ventilation path are disposed on both front and rear sides of the fan 10. The upper half of the front guider 30 is composed of a stabilizer (front tongue) 32. By arranging the stabilizer 32 and the rear guider 20 on both sides of the fan 10, the fan 10 sucks air from the upper front and blows out the lower rear. Further, the heat exchanger 3 is disposed so as to surround the front and the upper side of the fan 10. During the air-conditioning operation, the indoor air is sucked from the suction port 2a by driving the fan 10, and the sucked air is heated or cooled in the heat exchanger 3 and then blown out from the air outlet 2b.

Hereinafter, the fan 10, the rear guider 20, and the front guider 30 will be described in detail.
[fan]
As shown in FIG. 3, the fan 10 includes a plurality (six in this embodiment) of impellers 12 arranged in the axial direction (left and right direction) and an end plate 11.

  The end plate 11 constitutes the right end portion of the fan 10, and a boss portion 11 a connected to a rotating shaft of a motor (not shown) that drives the fan 10 projects from the center portion of the right surface of the end plate 11. Has been.

  The right five impellers 12A among the six impellers 12 include a plurality of blades 15 arranged in the circumferential direction and a substantially annular support plate 13 connected to the left ends of the plurality of blades 15. 15 and the support plate 13 are integrally formed. The right end of the blade 15 of the impeller 12A is joined to the adjacent end plate 11 or the support plate 13 of the impeller 12A by welding or the like.

  Of the six impellers 12, the leftmost impeller 12B is composed of a plurality of blades 15 arranged in the circumferential direction and a substantially disc-shaped end plate 14 connected to the left end of the plurality of blades 15. The blade 15 and the end plate 14 are integrally formed. The right end of the blade 15 of the impeller 12B is joined to the support plate 13 of the adjacent impeller 12A by welding or the like. A shaft (not shown) that is rotatably supported by a bearing (not shown) provided on the casing 2 projects from the center of the left surface of the end plate 14.

  The plurality of blades 15 of the impeller 12 extend along the axial direction (left-right direction), and are arranged in a forward blade structure with a predetermined blade angle. The axial lengths of the blades 15 of the five impellers 12A are all the same, and are almost twice the axial length of the blades 15 of the impeller 12B. In the present embodiment, the plurality of blades 15 of the impeller 12 are arranged at unequal pitches in the circumferential direction. The arrangement pitch of the blades 15 of the six impellers 12 is the same. The plurality of blades 15 may be arranged at an equal pitch.

  As shown in FIG. 4, the plurality of blades 15 of the two adjacent impellers 12 are arranged so as to be shifted in the circumferential direction. Specifically, the blade 15 is shifted from the blade 15 of the impeller 12 adjacent to the left side of the blade 15 by an angle θ in the rotation direction (the arrow direction in FIG. 4). That is, each of the plurality of blades 15 of the six impellers 12 is shifted by an angle θ in the rotation direction as it goes to the right.

[Rear guider]
The rear guider 20 is disposed behind the fan 10, and the lower end of the rear guider 20 is connected to the air outlet 2b (see FIG. 2). As shown in FIGS. 5 and 6, the length of the rear guider 20 in the left-right direction is substantially the same as the length of the fan 10 in the left-right direction, and the rear guider 20 faces the fan 10 over substantially the entire left-right direction of the fan 10. ing. The upper end of the rear guider 20 is located slightly higher than the upper end of the fan 10 (see FIGS. 2 and 6).

  As shown in FIG. 2, of the surface facing the fan 10 of the rear guider 20, the portion excluding the upper and lower ends is configured with a substantially arc-shaped curved surface 21. The separation distance (shortest distance) between the curved surface 21 and the outer peripheral portion of the fan 10 becomes smaller toward the upper side.

  Further, the rear guider 20 has a protruding portion 22 above (front end side) from the curved surface 21. The projecting portion 22 is formed in a substantially arc shape whose cross-sectional shape perpendicular to the left-right direction swells on the opposite side to the fan 10. The separation distance (shortest distance) between the protrusion 22 and the outer peripheral portion of the fan 10 increases as it goes upward. As described above, since the separation distance (shortest distance) between the curved surface 21 and the outer peripheral portion of the fan 10 decreases toward the upper side, the rear guider 20 has a lower end of the protrusion 22 and an upper end of the curved surface 21. At the boundary 20a (hereinafter referred to as the closest position 20a).

  As shown in FIG. 8, the protrusion 22 is composed of divided pieces 23 and 24 that are alternately arranged in the left-right direction. The protrusion 22 is formed by six divided pieces 23 and five divided pieces 24.

  Each of the divided pieces 23 and 24 extends linearly along the left-right direction, and the divided piece 23 and the divided piece 24 are shifted by an angle α1 in the circumferential direction of the fan 10 (see FIG. 7). The cross-sectional shape orthogonal to the left-right direction of the divided piece 23 is substantially the same as the cross-sectional shape orthogonal to the left-right direction of the divided piece 24. The heights of the upper ends of the six divided pieces 23 are all the same. Further, the heights of the upper ends of the five divided pieces 24 are all the same.

  Of the six divided pieces 23, the right and left five divided pieces 23 have the same length in the left-right direction, and are substantially half the length in the left-right direction of the blade 15 of the impeller 12A. The left-right length of the leftmost segment 23 is substantially the same as the left-right length of the blade 15 of the impeller 12B. The lengths of the five divided pieces 24 in the left-right direction are all the same, and are substantially half the length of the blade 15 of the impeller 12A in the left-right direction.

  A step formed at the boundary between the tip (upper end) of the split piece 24 and the tip of the split piece 23 on the left side thereof is defined as a step portion (second step portion) 25, and the tip of the split piece 24 and the split piece 23 on the right side thereof are provided. A step formed at the boundary with the tip of the step is referred to as a step portion (first step portion) 26. The deviation direction in the circumferential direction of the step portion 25 is opposite to the deviation direction in the circumferential direction of the step portion 26. The step portion 25 faces the connecting portion (support plate 13) between the impellers 12, and the step portion 26 faces the substantially central portion in the left-right direction of the impeller 12.

  As shown in FIG. 11, the divided piece 23 is shifted from the left divided piece 24 by an angle α1 in the direction opposite to the rotation direction of the fan 10 (the arrow direction in FIG. 11). That is, the stepped portion 26 is shifted by an angle α1 in the direction opposite to the rotation direction of the fan 10 when viewed from the left to the right, and the stepped portion 25 is rotated by the fan 10 when viewed from the left to the right. The direction is shifted by an angle α1. Therefore, the displacement direction of the two blades 15 shifted by the angle θ of the two adjacent impellers 12 is the same as the displacement direction in the circumferential direction of the step portion 25 and the displacement direction in the circumferential direction of the step portion 26. The reverse direction. Further, in the present embodiment, the angle α1 is a value that is approximately half of the deviation angle θ between the blades 15 of the two adjacent impellers 12.

[Front guider]
The front guider 30 is disposed in front of the fan 10, and the lower end of the front guider 30 is connected to the air outlet 2b (see FIG. 2). The front guider 30 includes a stabilizer 32 that is disposed to face the fan 10 and a front wall portion 31 that extends from the lower end of the stabilizer 32 to the air outlet 2b.

  As shown in FIGS. 5 and 6, the length of the stabilizer 32 in the left-right direction is substantially the same as the length of the fan 10 in the left-right direction, and the stabilizer 32 faces the fan 10 over almost the entire area in the left-right direction of the fan 10. ing. Moreover, the upper end of the stabilizer 32 exists in the position lower than the center of the fan 10 (refer FIG.2 and FIG.5).

  As shown in FIG. 9, of the surface of the stabilizer 32 that faces the fan 10, the portion excluding the upper and lower end portions is configured by a substantially arc-shaped curved surface 33. The separation distance (shortest distance) between the curved surface 33 and the outer peripheral portion of the fan 10 becomes smaller toward the upper side. The stabilizer 32 has a bent surface 34 that bends substantially forward from the lower end of the curved surface 33. The lower end of the bent surface 34 is connected to the front wall portion 31.

  The stabilizer 32 has a flat end surface 35 that extends downward and forward from the upper end of the curved surface 33, and a convex portion 36 that is disposed in front of the end surface 35 and projects upward from the end surface 35. The convex portion 36 and the end surface 35 constitute the upper end portion of the rear guider 20. The stabilizer 32 is closest to the outer peripheral portion of the fan 10 at the upper end 32a of the curved surface 33 (hereinafter referred to as the closest position 32a).

  As shown in FIG. 10, the stabilizer 32 (the convex portion 36, the end surface 35, the curved surface 33, and the bent surface 34) is composed of divided pieces 37 and 38 that are alternately arranged in the left-right direction. The stabilizer 32 is formed by six divided pieces 37 and five divided pieces 38.

  Each of the divided pieces 37 and 38 extends linearly along the left-right direction, and the divided piece 37 and the divided piece 38 are shifted by an angle β1 in the circumferential direction of the fan 10 (see FIG. 9). The cross-sectional shape orthogonal to the left-right direction of the divided piece 37 is substantially the same as the cross-sectional shape orthogonal to the left-right direction of the divided piece 38. The heights of the upper ends of the six divided pieces 37 are all the same. Further, the heights of the upper ends of the five divided pieces 38 are all the same.

  Of the six divided pieces 37, the right and left five divided pieces 37 have the same length in the left-right direction, and are substantially half the length in the left-right direction of the blade 15 of the impeller 12A. Moreover, the left-right direction length of the leftmost division piece 37 is substantially the same as the left-right direction length of the blade 15 of the impeller 12B. The lengths in the left-right direction of the five divided pieces 38 are all the same, and are approximately half the length in the left-right direction of the blade 15 of the impeller 12A.

  The step formed at the boundary between the divided piece 38 and the left divided piece 37 is defined as a stepped portion (second stepped portion) 39, and the step formed at the boundary between the divided piece 38 and the right divided piece 37 is defined as a step. , A step portion (first step portion) 40. The deviation direction of the stepped portion 39 in the circumferential direction is opposite to the deviation direction of the stepped portion 40 in the circumferential direction. The stepped portion 39 faces the connecting portion (support plate 13) between the impellers 12, and the stepped portion 40 faces the substantially central portion in the left-right direction of the impeller 12.

  As shown in FIG. 5, the split piece 37 is shifted from the left split piece 38 by an angle β1 in the direction opposite to the rotation direction of the fan 10. That is, the stepped portion 40 is shifted by an angle β1 in the direction opposite to the rotation direction of the fan 10 when viewed from the left to the right, and the stepped portion 39 is rotated by the fan 10 when viewed from the left to the right. The direction is shifted by an angle β1. Therefore, the shift direction of the two blades 15 shifted by the angle θ of the two adjacent impellers 12 is the same as the shift direction of the stepped portion 39 in the circumferential direction, and is the same as the shift direction of the stepped portion 40 in the circumferential direction. The reverse direction. In the present embodiment, the angle β1 is approximately half the deviation angle θ between the blades 15 of the two adjacent impellers 12.

  Next, wind noise generated between the rear guider 20 and the fan 10 will be described with reference to FIG. In FIG. 11, only the right three impellers 12 among the six impellers 12 are displayed. Of the blades of the three impellers 12, only the three blades 15 that are shifted by an angle θ in the rotational direction toward the right are displayed.

  When the fan 10 is rotated, the right half of the rightmost blade 15 out of the six blades 15 shifted by an angle θ first passes through the divided piece 23 first, and then the left half of the blade 15 , Passing through the divided piece 24. An eddy current (indicated by an arrow in FIG. 7) is generated between the front end portion of the rear guider 20 and the fan 10, and wind noise is generated by the interference between the vortex and the blades. Therefore, in this embodiment, the wind noise generated when one blade 15 passes through the rear guider 20 can be generated by being dispersed twice.

  In addition, after the rightmost blade 15 passes through the divided piece 24, the right half of the second blade 15 from the right passes through the divided piece 23. Therefore, in this embodiment, it is possible to generate wind noise generated when the two blades 15 arranged so as to be shifted by the angle θ pass through the rear guider 20 while shifting the timing. Thereafter, approximately the left half of the second blade from the right passes through the divided piece 24, and then the remaining four blades 15 pass through the divided pieces 23 and 24 in the same manner.

  Further, a vortex airflow (indicated by an arrow in FIG. 9) is also generated between the curved surface 33 of the stabilizer 32 and the fan 10, and when the blade 15 passes through the curved surface 33 of the stabilizer 32, the vortex airflow and the blade Wind noise is generated by the interference of 15. Since the stabilizer 32 is provided with the step portions 39 and 40, the wind noise generated when one blade 15 passes through the stabilizer 32 is generated twice in the same manner as the rear guider 20. In addition, wind noise generated when the two blades 15 arranged with a shift of the angle θ pass through the stabilizer 32 can be generated with a shifted timing.

  As described above, in the air conditioner of the present embodiment, the front end portions of the rear guider 20 and the stabilizer 32 are stepped portions (first stepped portions) that are shifted in the circumferential direction at positions facing the middle portion in the axial direction of the impeller 12A. Part) 26 and 40, the timing at which one blade 15 passes through the stabilizer 32 and the tip of the rear guider 20 can be shifted from the first stepped portions 26 and 40 as boundaries. Accordingly, the wind noise can be generated by shifting the wind noise without simultaneously generating the wind noise by the single blade 15. Therefore, wind noise can be reduced.

  Further, in the present embodiment, the front end portions of the rear guider 20 and the stabilizer 32 have step portions (second step portions) 25 and 39 that are shifted in the circumferential direction at positions facing the connecting portions between the impellers 12. The timing at which wind noise is generated for each impeller 12 can be shifted, and wind noise can be further reduced.

  Moreover, in this embodiment, since the part between two adjacent level | step-difference parts has extended in the axial direction at the front-end | tip part of the rear guider 20 and the stabilizer 32, the stabilizer 32 or the rear guider 20 is easy to produce.

  In the present embodiment, the rear guider 20 and the tip of the stabilizer 32 have the same shape and height in a range facing the five impellers 12A. Therefore, the rear guider 20 and the stabilizer 32 are easy to produce. Further, the heights of the tip portions of the rear guider 20 and the stabilizer 32 can be made substantially the same as a whole.

  In the present embodiment, the first stepped portions 26 and 40 and the second stepped portions 25 and 39 are displaced in the opposite direction, and the displacement direction between the blades 15 arranged with the angle θ shifted is the first stepped portion. 26 and 40 are opposite to each other, and the second stepped portions 25 and 39 have a smaller shift angle than the angle θ, so that two wind noises generated by shifting the first stepped portions 26 and 40 from each other. The time shift direction can be made the same as the time shift direction of the two wind noises generated with the second step portions 25 and 39 as the boundary. Therefore, it is possible to generate the wind noise by shifting from one end of the fan 10 in the axial direction toward the other end. Thereby, the directivity due to the interference of wind noise generated in each divided piece (between each stepped portion) can be suppressed, and the sound can be effectively silenced throughout the room.

  Further, in the present embodiment, the two wind cuts that occur with the first stepped portions 26 and 40 deviated from the boundary are generated with a shift by the shift angle (α1, β1) of the first stepped portions 26 and 40, and The two wind noises that occur when the two stepped portions 25 and 39 deviate from the boundary are the angle obtained by subtracting the shift angle (α1, β1) of the second stepped portions 25 and 39 from the shift angle θ between the blades 15. Generated out of position. Therefore, the deviation time of the two wind noises generated at the boundary between the first step portions 26 and 0 and the deviation time of the two wind noises generated at the boundary between the second step portions 25 and 39 are the same. it can. Therefore, this embodiment has the same silent effect as the case where the number of impellers 12 is increased so that the connecting portion of the impeller 12 faces the position corresponding to the first stepped portion without providing the first stepped portion. Can be obtained. In other words, this embodiment can increase the blade length of the impeller 12 and reduce the number of impellers while maintaining silent performance. Moreover, since the number of the connection parts of the impeller used as ventilation resistance can be reduced, ventilation characteristics can be improved.

  As mentioned above, although embodiment of this invention was described, it should be thought that the specific structure of this invention is not limited to the said embodiment. The scope of the present invention is shown not only by the description of the above-described embodiment but also by the scope of claims for patent, and further includes meanings equivalent to the scope of claims for patent and all modifications within the scope. Note that the following modifications can be implemented in combination as appropriate.

  In the above embodiment, the deviation angle α1 of the stepped portions 25 and 26 and the deviation angle β1 of the stepped portions 39 and 40 are substantially half of the deviation angle θ between the blades 15, but may be smaller or larger than that. Good. However, when it is larger than θ / 2, it is preferable that the angle be less than θ.

  In the above embodiment, the displacement direction of the first step portions 26 and 40 is opposite to the displacement direction of the blades 15, and the displacement direction of the second step portions 25 and 39 is the same as the displacement direction of the blades 15. However, on the contrary, the displacement direction of the first step portions 26 and 40 is the same as the displacement direction of the blades 15 and the displacement direction of the second step portions 25 and 39 is the displacement direction of the blades 15. It may be in the opposite direction.

In the above embodiment, the rear guider 20 has only one first stepped portion 26, 40 in the axial range of one impeller 12A. However, for example, a single impeller like the rear guider 120 shown in FIG. Two or more first step portions 126 and 127 may be provided in the axial range of 12A.
In the case of this modification, the deviation angle α2 of the second stepped portion 125 should be the same as the total value of the deviation angles α3 and α4 of the first stepped portions 126 and 127 within the axial range of one impeller 12A. preferable. Further, the shift angles α3 and α4 of the first stepped portions 126 and 127 are obtained by dividing the shift angle θ between the blades 15 by the value obtained by adding 1 to the number of the first stepped portions in the axial range of the impeller 12A. Preferably the value is the same. With this configuration, it is possible to make the deviation time of wind noise generated by shifting the first stepped portions 126 and 127 the same as the shift time of wind noise generated by shifting the second stepped portion 125 as the boundary.
Further, the shift angle between the two or more first step portions provided in the axial range of one impeller may be a value other than the above-described value. In this case, the shift angles of the two or more first step portions may all be the same or different from each other.
Similarly, the stabilizer 32 may be provided with two or more first step portions in the axial range of one impeller 12A.

In the above-described embodiment, the tip portion of the rear guider 20 has the same shape and height in the range facing the five impellers 12A, but may be different.
For example, the number of first stepped portions, the shift angle, or the shift direction may be different for each impeller 12A. Moreover, the 1st level | step-difference part may be provided only in the position facing the axial direction middle part of some impellers 12A among five impellers 12A. Moreover, the 2nd level | step-difference part may be provided only in the position facing the one part connection part of the connection parts of the six impellers 12. FIG.
Similarly, the stabilizer 32 may have different shapes and heights in a range facing the five impellers 12A.

In the above embodiment, in the rear guider 20, the height of each of the divided pieces 23 and 24 (the height of the portion between the adjacent stepped portions) is constant with respect to the axial direction. For example, like the rear guider 220 shown in FIG. In addition, the height of each divided piece 228 may be continuously changed in the axial direction. The cross-sectional shape orthogonal to the axial direction of each divided piece 228 is substantially constant. With this configuration, wind noise generated when the blades 15 pass through one divided piece 228 can be generated by continuously shifting. In FIG. 13, the stepped portions 229 on both sides of the split piece 228 are opposed to the axially central portion of the impeller 12 </ b> A (or the end portion of the impeller 12) and the connecting portion between the impellers 12.
Similarly, for the stabilizer 32, for example, like the stabilizer 232 of the front guider 230 shown in FIG. 14, the height of each divided piece 241 may be continuously changed in the axial direction. In FIG. 14, the step portions 242 on both sides of the split piece 241 are opposed to the axially central portion of the impeller 12 </ b> A (or the end portion of the impeller 12) and the connecting portion between the impellers 12.

  In the above embodiment, the rear guider 20 is formed in a shape shifted in the circumferential direction from the tip to the boundary between the projection 22 and the curved surface 21, but shifted in the circumferential direction from the tip to the middle of the curved surface 21. It may be formed in a shape. That is, the lower ends of the divided pieces 23 and 24 may be above the boundary between the protrusion 22 and the curved surface 21.

  In the embodiment described above, the stabilizer 32 is formed in a shape in which the entire vertical direction is shifted in the circumferential direction, but only a part on the tip side may be formed in a shape shifted in the circumferential direction. That is, the lower ends of the divided pieces 37 and 38 may be above the lower end of the stabilizer 32. For example, only the end surface 35 and the convex portion 36 may be formed in a shape shifted in the circumferential direction, or the tip from the stabilizer 32 to the middle of the curved surface 33 may be formed in a shape shifted in the circumferential direction.

  In the above embodiment, both the rear guider 20 and the stabilizer 32 are formed in a multi-stage shape having a first step portion that faces the middle portion in the axial direction of the impeller 12A, but only one of the rear guider 20 and the stabilizer 32 is The multistage shape having a first step portion facing the middle portion in the axial direction of the impeller 12A, and the other has a shape without the first step portion (that is, a shape having no step portion at all, or the impeller 12 It may be a multi-stage shape having only a second step portion facing the connecting portion between each other.

  In the above embodiment, the rear guider 20 has a cross-sectional shape orthogonal to the left-right direction having the protrusion 22 having a substantially arc-shaped cross section above the arcuate curved surface 21. It is not limited to. For example, the curved surface 21 may have a cross-sectional shape in which only the surface on the fan 10 side has a substantially arc shape and the surface on the opposite side to the fan 10 has a substantially flat protrusion. When the cross-sectional shape of the rear guider 20 is different from the shape of the above-described embodiment, at least a portion including the portion from the nearest position closest to the fan 10 to the tip in the rear guider 20 is shifted in the circumferential direction (divided piece). To do.

  In the above embodiment, the stabilizer 32 has a cross-sectional shape orthogonal to the left-right direction having a flat end surface 35 and a convex portion 36 having a substantially triangular cross section on the upper side of the curved surface 33. The cross-sectional shape of 32 is not limited to this. For example, it may have a cross-sectional shape in which the convex portion 36 is connected to the upper end of the curved surface 33 without providing the end surface 35. When the cross-sectional shape of the stabilizer 32 is different from the shape of the above-described embodiment, a portion including the portion from the nearest position closest to the fan 10 to the tip in the stabilizer 32 is a shape shifted in the circumferential direction (divided piece).

  In the above embodiment, an example in which the present invention is applied to a wall-mounted indoor unit configured to suck indoor air from the upper part of the indoor unit and blow out air from the lower part of the indoor unit has been described. It is not limited to this. For example, the present invention can be applied to a floor-standing indoor unit configured to suck indoor air from the lower part of the indoor unit and blow out air from the upper part of the indoor unit.

  By using the present invention, wind noise can be further reduced.

DESCRIPTION OF SYMBOLS 1 Indoor unit 10 of air conditioner Cross flow fan 12 (12A, 12B) Impeller 15 Blade 20, 120, 220 Rear guider 25, 125 Step part (second step part)
26, 126, 127 Stepped portion (first stepped portion)
30, 230 Front guider 32, 232 Stabilizer 39 Step part (second step part)
40 Step part (first step part)
229 Stepped portion (first stepped portion, second stepped portion)
242 Stepped portion (first stepped portion, second stepped portion)

Claims (8)

A cross flow fan in which a plurality of impellers each having a plurality of blades arranged at unequal pitches in the circumferential direction are arranged side by side in the axial direction;
It is provided with a stabilizer and a rear guider that are arranged on both sides of the outer periphery of the cross flow fan to form a ventilation path,
At least one tip portion of the stabilizer and the rear guider has a multi-stage shape having a plurality of step portions shifted in the circumferential direction of the cross flow fan,
The plurality of stepped portions include at least one first stepped portion facing an axial middle portion of the impeller,
When the corresponding impellers of the impeller and the impeller adjacent to the first stepped portion are viewed, the impeller blades on the other axial end side with respect to the impeller blades on the one axial end side Is arranged to deviate by a predetermined angle in the rotational direction of the cross flow fan,
In the direction from one end to the other in the axial direction, the circumferential shift direction of the first stepped portion is the circumferential shift between the blades of the impeller facing the first stepped portion and the impeller adjacent thereto. An air conditioner characterized by being in a direction opposite to the direction.   The air conditioner according to claim 1, wherein the plurality of stepped portions include a second stepped portion that faces a connecting portion between the impellers.   The air conditioner according to claim 1 or 2, wherein a height of a portion between two adjacent stepped portions is constant in the axial direction. The plurality of stepped portions are two or more first stepped portions facing axially intermediate portions of the two adjacent impellers, and a second stepped portion facing the connecting portion between the two impellers. Contains
In a direction from one axial end to the other end, a circumferential shift direction of the first stepped portion is opposite to a circumferential shift direction of the second stepped portion,
4. The air conditioner according to claim 3, wherein a shape and a height of a range facing the two adjacent impellers in the front end portion are the same. 5. The plurality of stepped portions include two second stepped portions facing the connecting portions of the impeller facing the first stepped portion and the impellers on both sides thereof,
In a direction from one axial end to the other end, a circumferential shift direction of the first stepped portion is opposite to a circumferential shift direction of the second stepped portion,
The air conditioner according to claim 3, wherein a circumferential shift angle of the second step portion is smaller than the predetermined angle. The circumferential deviation angle of the first step portion divides the predetermined angle by a value obtained by adding 1 to the number of the first step portions in the axial range of the impeller facing the first step portion. Is the same as
6. The air conditioner according to claim 5, wherein a circumferential shift angle of the second step portion is the same as a total value of circumferential shift angles of the first step portion in the axial range. Machine. A cross flow fan in which a plurality of impellers each having a plurality of blades arranged in the circumferential direction are arranged side by side in the axial direction;
It is provided with a stabilizer and a rear guider that are arranged on both sides of the outer periphery of the cross flow fan to form a ventilation path,
At least one tip portion of the stabilizer and the rear guider has a multi-stage shape having a plurality of step portions shifted in the circumferential direction of the cross flow fan,
The plurality of stepped portions include at least one first stepped portion facing an axial middle portion of the impeller,
The height of the portion between the two adjacent step portions is constant with respect to the axial direction,
The plurality of stepped portions include two second stepped portions facing the connecting portions of the impeller facing the first stepped portion and the impellers on both sides thereof,
In a direction from one axial end to the other end, a circumferential shift direction of the first stepped portion is opposite to a circumferential shift direction of the second stepped portion,
The blades of two adjacent impellers are arranged with a predetermined angle shift in the circumferential direction,
A circumferential shift angle of the second step portion is smaller than the predetermined angle;
In a direction from one axial end to the other end, a circumferential shift direction of the first stepped portion is opposite to a circumferential shift direction between the blades of the two adjacent impellers. Air conditioner to do. The circumferential deviation angle of the first step portion divides the predetermined angle by a value obtained by adding 1 to the number of the first step portions in the axial range of the impeller facing the first step portion. Is the same as
The air conditioning according to claim 7, wherein a circumferential shift angle of the second stepped portion is the same as a total value of circumferential shift angles of the first stepped portion in the axial range. Machine.

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