JP2013079617A - Air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an air conditioner improved in wind speed distribution, in the air conditioner with a circulating fan having a clearance for inserting therein a fixing screw fastening jig which fixes a boss and a drive motor rotating shaft.SOLUTION: This air conditioner comprises: a box having an air inlet and an air outlet; a heat exchanger which heat-exchanges in-room air sucked from the air inlet; the circulating fan which is positioned at the downstream side of the heat exchanger, and blows out the in-room air which is heat-exchanged by the heat exchanger from the air outlet; and a drive unit which is arranged at the one-end side of the circulating fan, and drives the circulating fan. The circulating fan has a plurality of wings aligned in the circumferential direction and a plurality of clearances formed of the plurality of wings, the plurality of clearances have connecting clearances for connecting the circulating fan to the drive unit, the connecting clearances are formed wider than other clearances, and wing chord lengths of the wings forming the connecting clearances are formed longer than wing cord lengths of the other wings.

Description

  The present invention relates to an air conditioner provided with a cross-flow fan.

  Generally, a once-through fan is used as a blower fan in a domestic air conditioner in order to carry the wind blown out with low noise on a uniform flow and deliver it to a distant place in an air-conditioned space. A fan motor for rotating the cross-flow fan is disposed adjacent to the axial direction of the cross-flow fan.

  In Patent Document 1, the axial length of several blades facing the fixing screw of the boss portion is shortened, and an auxiliary support plate is disposed at the contracted end portion of the wing, thereby rotating the boss portion and the drive motor. A gap is formed to insert a fastening tool (such as a screwdriver) for fastening a fixing screw for fixing the shaft.

  In Patent Document 1, the air volume is increased as compared with the outer boss type cross-flow fan, but a reverse flow is locally generated at a position where the blade is omitted. Accordingly, wind speed fluctuations increase in the vicinity of the gap, leading to an increase in noise and a decrease in efficiency. In addition, since a large notch is formed in the support plate, a part of the blown air circulates from the notch to the outside of the support plate, which may cause dew condensation during cooling.

JP 2000-205178 A

  The present invention provides an air conditioner having an improved wind speed distribution in an air conditioner having a cross-flow fan having a gap for inserting a fixing screw fastening jig for fixing a boss portion and a drive motor rotating shaft. The task is to do.

  The air conditioner of the present invention includes a housing having an air inlet and an air outlet, a heat exchanger that exchanges heat between indoor air sucked from the air inlet, a heat exchanger that is located downstream of the heat exchanger, A cross-flow fan that blows out indoor air that has undergone heat exchange from an air outlet, and a driving device that is disposed on one end side of the cross-flow fan and drives the cross-flow fan, and the cross-flow fan includes a plurality of blades arranged in the circumferential direction and a plurality of blades The plurality of air gaps have a connection air gap for connecting the cross-flow fan to the driving device, and the connection air gap is formed wider than other air gaps to form a connection air gap. The chord length of the wing is longer than the chord length of the other wings.

  According to the present invention, in an air conditioner including a cross-flow fan having a gap for inserting a fixing screw fastening jig for fixing a boss portion and a drive motor rotating shaft, a chord of a blade forming the gap is provided. Since the length is formed larger than the chord length of the other blades, the air velocity distribution in the vicinity of the air gap is improved, so that an air conditioner with improved wind velocity distribution in the entire cross-flow fan can be provided.

The front view of a once-through fan. The block diagram of a once-through fan. The exploded perspective view seen from the spindle side of the once-through fan. The boss part enlarged view of a once-through fan. BB cross section of FIG. The space | gap part enlarged view for boss fixing tools. CC cross section of FIG. The DD cross section of FIG. The enlarged view of the wing | blade C and the wing | blade D tip of a once-through fan. The exploded perspective view seen from the boss side of the once-through fan. The perspective view of a once-through fan and a blower motor incorporated in an air conditioner. Sectional drawing which incorporated a once-through fan in an air conditioner. The figure which shows the improvement effect of wind speed distribution. The figure which shows the improvement effect of a static pressure characteristic. The figure which shows the improvement effect of a static pressure characteristic. The figure which shows the improvement effect of ventilation motor power consumption.

  Embodiments of the present invention will be described below with reference to the drawings. First, the cross-flow fan of the present invention will be described with reference to FIGS. 1 to 4 and FIGS. 6 to 11. FIG. 1 is a front view of the cross-flow fan. FIG. 2 is a configuration diagram of the cross-flow fan. In FIG. 1 and FIG. 2, illustration of a part of the wings around the boss portion is omitted, and the internal boss portion is illustrated for easy understanding. FIG. 3 is an exploded perspective view as seen from the support shaft side of the cross-flow fan. FIG. 4A is an enlarged view of the boss portion of the cross-flow fan, and FIG. 4B is a view of the gap portion in which the support disk on the boss side is broken. FIG. 6 is an enlarged view of the gap for the boss fixing tool. FIG. 7 is a cross-sectional view taken along the line CC in FIG. FIG. 8 is a DD cross section of FIG. FIG. 9 is an enlarged view of the tips of the blades C and D of the once-through fan. FIG. 10 is an exploded perspective view seen from the boss side of the cross-flow fan. FIG. 11 is a perspective view of the cross-flow fan and the blower motor incorporated in the air conditioner.

  In FIG. 1, circular support disks 316b with bosses and support disks 316c with support shafts are positioned at both ends of the cross-flow fan 311. Between the support disks 316b and 316c, a plurality of circular hollow support disks 316a are positioned with a space therebetween. These support disks 316a, 316b, 316c are arranged in parallel to each other so that their centers are located on the fan center axis L.

  A plurality of wings 314 arranged in the circumferential direction of the support disk 316 are arranged between the support disks 316. As shown in FIG. 3, these blades 314 have a so-called airfoil shape in which a surface in the rotation direction of the cross-flow fan is curved in a concave shape and a surface opposite to the rotation direction of the cross-flow fan is curved in a convex shape. The blade 314 is formed substantially parallel to the fan central axis L.

  317a in FIG. 2 is a single vane wheel without a boss portion (a single vane wheel 317a without a boss). In the bossless single vane wheel 317a, a blade A314a is disposed on one surface of the hollow support disc 316a, and a connecting hole 318a (FIG. 10) into which the tip of the blade A314a of the bossless single vane wheel 317a adjacent to the other surface is fitted. See). The hollow support disk 316a holds the blades 314a and increases the strength of the entire cross-flow fan 311 in which a plurality of single blade wheels are connected.

  As shown in FIG. 2, a support shaft 326 extends outwardly from the center of the outer surface of the support disk 316c with support shaft, and this support shaft 326 is supported by a housing 231 as shown in FIG. 20 is supported. Similar to the hollow support disc 316a, the inner surface of the support disc 316c with a support shaft has a connecting hole 318c (see FIG. 10) into which the tip of the blade A314a of the adjacent single vane wheel 317a without boss fits.

  As shown in FIGS. 3 and 4, the inner surface of the bossed support disk 316 b (the surface on which the blades B 314 b, C 314 c, and D 314 d are erected) fixes the cross-flow fan 311 to the motor shaft 313 a of the blower motor 313. A boss 322 is provided. The boss 322 is provided with a screw 323 for fixing the motor shaft 313 a and the boss 322 perpendicular to the fan center axis L. When the cross-flow fan 311 is rotationally driven by the blower motor 313 (see FIG. 11) via the boss 322, the cross-flow fan 311 rotates to generate wind.

  As shown in FIG. 4, the boss 322 of the cross-flow fan 311 is provided inside a support disc 316b with a boss on the blower motor 313 side. Therefore, in order to form the fixing tool gap 321 for tightening the screw 323 for fixing the boss 322 and the motor shaft 313a, the boss-equipped support disk 316b and the adjacent hollow support disk 316a are formed between them. The fixed tool gap 321 is formed by, for example, omitting one or two of the blades 314 to be delivered. The fixed tool gap 321 is wider than other gaps formed by the cross-flow fan blades 314 (between the blades of the blades 314 arranged opposite to the fixed tool gap 321, the blades 314 forming the other gaps Wider than between wings.)

  However, if the gap 321 for the fixed tool for tightening the screw 323 of the boss 322 is formed to be wider than the other gaps or the blades 314 that should be there are simply omitted, the cross-flow fan 311 is removed. The wind speed distribution is reduced.

  In order to suppress such a decrease in the wind speed distribution due to the fixed tool gap 321, as shown in FIG. 6, the fixed tool gap 321 is formed, and the blade C 314 c and the blade are opposed to each other with the fixed tool gap 321 interposed therebetween. The chord length of D314d was made larger than the chord length of the other wing B314b. As an example, the wing C314c and the wing D314d that face each other across the fixed tool gap 321 are protruded inward from the other wing B314b. Further, the distance from the axial center of the once-through fan to the outer peripheral side ends of the blades C314c and D314d and all the blades including the other blades B314b and the like is equal.

  The wing C314c and the wing D314d may have the same shape as the wing B on the outer side of the inner diameter circle Rb of the wing B (a circle formed by a line connecting the inner ends of the other wings B314b). A blade forming a fixed tool gap 321 in an air conditioner having a cross-flow fan having a fixed tool gap 321 for inserting a fixing screw fastening jig for fixing a boss portion and a drive motor rotating shaft. Since the chord length of each of the wings is formed larger than the chord length of the other wings, it is possible to suppress the reduction of the air blowing performance due to the gap 321 for the fixed tool. An air conditioner that improves the wind speed distribution of the entire fan can be provided. By improving the wind speed distribution, the number of rotations of the compressor necessary for obtaining the same air volume is reduced, and noise in the cross-flow fan is also reduced. Further, the unbalance of the cross-flow fan increases by the amount of the removed blade, but by increasing the chord length, the amount of unbalance is reduced and the unbalance is suppressed.

  The wing C314c and the wing D314d have the same shape as the wing B on the outer side of the inner diameter circle Rb of the wing B (a circle formed by the line connecting the inner ends of the other wings B314b), and the center of the portion protruding inward The curvature of the line is made larger than the curvature at the position of the inner diameter circle Rb of the wing B, and it is formed so as to gently extend toward the boss 322. The arrangement position of the bossed single vane wheel 317b excluding the blades C314c and the extension portions 314c ′ and 314d ′ of the vane D314d is the same as the arrangement position of the vane A314a of the bossless single vane wheel 317a (that is, The cross-flow fan has a bossed single vane wheel that does not have a connection gap on one end side of the cross-flow fan, and extends from one end side to the other end side of the cross-flow fan. The wings of a single wing vehicle with bosses other than the wings that are formed by sequentially connecting bossless single wing vehicles are arranged in the same manner as the corresponding wingless single wing vehicles. The car wings are arranged in the same way as the wings of any other corresponding bossless single wing car.) Thus, by forming the wing C314c and the wing D314d that are opposed to each other with the fixed tool gap 321 interposed therebetween, the local wind flow at the connecting portion between the boss-equipped single vane wheel 317b and the boss-less single vane wheel 317a. However, except for the vicinity of the gap 321, the flow of air is almost the same as the local wind flow at the connecting portion between the bossless single vanes 317 a, and the air blowing characteristics when the bossless single vanes 317 a are connected, Most of the structural results can be used. For this reason, only the shape including the lengths of the extension portions 314c ′ and 314d ′ of the wing C314c and the wing D314d sandwiching the gap 321 is necessary for the bossed single vane wheel 317b, and the matters to be studied are largely omitted. Development period can be shortened.

  The part of the single bladed wheel 317a adjacent to the blade C314c and blade D314d that contacts the hollow support disk 316a has the same shape as the blade A314a, and is provided with a blade tip step f 'as shown in FIGS. 7 and 9, and the blade C314c, The portion of the blade D314d that extends the chord length is from the root of the blade C314c and the blade D314d to the front of the blade tip step f ′.

  As described above, the hollow supporting disc 316a of the bossless single vane wheel 317a is fitted with the tip of the blade A314a of the adjacent bossless single vane wheel 317a, and therefore, as shown in FIG. It has a connecting hole 318a that matches the airfoil shape of the wing A314a. The length e along the airfoil center line of the connecting hole 318a is e ≧ e ′, where e ′ is the length of the airfoil center line at the tip of the airfoil A314a. The wing B 314b has the same shape as the wing A 314a, and the wing B 314b fits into the connection hole 318a of the hollow support disk 316a as shown in FIG. 8, as with the wing A 314a. Further, the portions of the wing C and the wing D excluding the extension portions 314c ′ and 314d ′ are the same wing shape as the wing B, and the length e ′ along the wing shape center line at the step portion is the same as the wing B 314b. As shown in FIG. 7, e ≧ e ′.

  The blade tip step f ′ of the blade C314c and the blade D314d is connected to the surface of the hollow support disc 316a opposite to the blade A314a of the hollow support disk 316a of the bossless single blade wheel 317a when the blade A314a is connected to the adjacent bossless single blade wheel 317a. The extension portions 314c ′ and 314d ′ of the blades C314c and D314d are provided so as not to obstruct the connection holes 318a provided in the blades C314c and D314d. The blade tip difference f ′ of the blade C314c and the blade D314d is f ′ ≧ f.

  By configuring in this way, it is possible to unify single blade vehicles other than the bossed single blade vehicle 317b including the single blade vehicle adjacent to the bossed single blade vehicle 317b into the bossless single blade vehicle 317a. Since there are only two types of molds, that is, the mold for the bossless single vane wheel 317a and the mold for the single vane vehicle with the boss, an increase in the types of molds can be suppressed.

  The axial dimension of the bossed single vane wheel 317b may be different from the axial dimension of the bossless single vane wheel 317a. Even when the lateral width of the heat exchanger 33 is changed, the cross-flow fan 311 having an appropriate length can be configured only by preparing a mold for the bossed single vane wheel 317b whose axial dimension is increased or decreased. can do.

  In addition, the cross-flow fan of the embodiment is configured by connecting and connecting a plurality of single vane wheels in the axial direction on one surface near the outer periphery of the support disc in the circumferential direction. The single vane wheel constituting one end of the cross-flow fan is provided with a boss for fixing the cross-flow fan to the shaft of the cross-flow fan drive device, and the single vane wheel constituting the other end of the cross-flow fan is provided with a support shaft. The single vane wheel at the end is the cross-flow fan according to claims 1 to 3.

  As a result, a plurality of single vanes with a short blade width are stacked to form a cross-flow fan of a required length, so that the blade width of each single vane can be small, and cost-effective plastics are made. be able to. In this case, even in the injection molding using plastics, the difference in the chord length between the root of the blade and the tip of the blade that stands on the support disk caused by the draft angle of the mold is due to the shortened blade width. The negative effect on the air blowing performance is reduced.

  In addition, the performance difference between the single vane with boss and the adjacent single vane without boss is reduced, the wind speed at the air outlet of the single vane with boss is increased, the wind speed distribution is improved, and the user is dissatisfied. Can be tempered. In addition, the use of plastics increases the air blowing performance such as noise by adopting an airfoil with a thickness at the center of the blade.

  Moreover, the cross-flow fan of an Example makes the space | interval of the wing | blade of a single vane wheel the same except for the space | interval corresponding to the space | gap part for boss | hub part fixing tools between the blades of an adjacent single vane wheel. In the cross-flow fan made of plastics, the type of the mold can be reduced and the initial cost can be suppressed by making the single vane in the central part excluding both ends into the single vane having the same shape. At this time, a position corresponding to the wing shape is supported on a connecting portion between adjacent single vanes by forming it on a disk, for example, so that the position is determined only by overlapping. The blade row pitch angle of the single vane with boss is the same as the blade row pitch angle of the adjacent single vane except for the portion corresponding to the gap for the boss fixing tool. By providing the support disk with a recess that matches the blade shape used to connect the bossless single vanes, the position can be determined simply by overlapping the single vane with boss on the adjacent single vane. .

  In this way, the same single-wing vehicle as other bossless single-wing vehicles can be used as a bossless single-wing vehicle adjacent to a bossed single-wing vehicle, and a single wing vehicle having a connecting recess different from other bossless single-wing vehicles. There is no need to make a separate impeller. Therefore, it is possible to reduce the initial cost of production without increasing the types of molds, and also to reduce the management cost during production because the types of parts do not increase.

  In addition, the shape of the connecting portion of the blades constituting the largest blade of the bossed single vane with the adjacent bossless single vane is the same as the corresponding portion of the adjacent bossless single vane. As a result, the support disc of the adjacent bossless single vane is provided with a recess that matches the shape of the blade used to connect the bossless single vane, and the boss is inserted into the recess where the wing of the bossed single vane is contained. The attached single vans are stacked and connected by a method such as fusion or adhesion. At this time, the portion where the chord length is extended is only close to the support disk of the adjacent single vane without boss with a slight gap, but the connection strength with the adjacent single vane is sufficient with the above-mentioned connecting portion. Since this can be ensured, it is not necessary to fuse or bond this part. Thus, since only one type of bossless single vane is required, it is not necessary to increase the types of molds, and the initial cost of production can be reduced. In addition, since the types of parts do not increase, the management cost during production can be reduced.

  Next, the extension part of the wing | blade C and the wing | blade D is demonstrated using FIGS. 5-7 and FIG. FIG. 5 is a BB cross section of FIG.

  In general, when operating a cross-flow fan, attention must be paid to the imbalance of the cross-flow fan. Unbalance occurs due to various structural and manufacturing reasons, and large unbalance leads to increased vibration and noise, which impairs the quality of products incorporating cross-flow fans. For this reason, a balance weight is attached to the blades of the cross-flow fan to reduce the unbalance. In this case, if the amount of original unbalance is large, the number of balance weights to be attached increases, and the amount of unbalance removal work increases. For this reason, it is important to keep the original unbalance amount small.

  The extension length of the blade C314c is changed to 5 mm, 10 mm, and 20 mm, and is incorporated into the air conditioner of FIG. 11, and the position where the air passes through the bossed single vane wheel 317b (wind speed comparison position F: see FIG. 11) The wind speed at was compared. As a result, the improvement of the wind speed was good when the extension length was 10 mm.

  As shown in FIG. 5, the extension portions 314c ′ and 314d ′ are provided on the blades C and D, so that the chord lengths gc and gd of the blades C and D are larger than the chord length gb of the blade B. At this time, the amount of unbalance due to the moment due to the mass of the extension portions 314c ′ and 314d ′ is improved. This is the cross-flow fan of the embodiment (outer diameter (distance from the central axis of the cross-flow fan to the outer diameter side end of the blade × 2) Do = 110 mm, inner diameter (from the central axis of the cross-flow fan to the inner diameter side end of the blade) Distance x 2) Db = 83.5 mm, inner / outer diameter difference Do−Db = 26.5, chord length gb = 15.7 mm, number of blades 34), to provide the boss fixing tool gap 321, 80% of the amount of imbalance when only one blade is removed can be canceled by the extensions 314c 'and 314d' of the blade C and blade D. The inner diameters Dc and Dd of the blades C and D at this time are 63.5 mm, and the inner / outer diameter difference Do-Dc is 46.5 mm, which is 1.8 times the initial inner / outer diameter difference. According to further calculations, if the extension is extended to twice the initial inner / outer diameter difference (blade C, inner diameter Dc of blade D, Dd = 57 mm, inner / outer diameter difference = 53 mm), the above-mentioned unbalance amount is almost 100%. % Can be canceled.

  Generally, as for the shape of the once-through fan for an air conditioner, main specifications such as the outer diameter and the length are determined by analogy with the similarity law according to the characteristics of the load and the required performance. Therefore, the outer diameter side blade angle, the inner diameter side blade angle, the inner / outer diameter ratio, and the like are similar. For this reason, the relationship between the lengths of the extension portions 314c ′ and 314d ′ and the difference between the inner and outer diameters is the same.

  In the embodiment, the wing C of the blade B and the wing C of the wing B have a straight line on the inner side circle Rc and Rd side of the wing C of the center line of the extension parts 314c ′ and 314d ′ of the wing D and the wing D. Connected smoothly with the center line. In addition, the straight lines on the inner diameter circles Rc and Rd side are straight lines toward the axial center of the cross-flow fan 311. This is because the airflow enters and exits from the blade inner diameter end, so that bidirectional airflow is taken into consideration.

  By doing in this way, the fixing tool gap for fixing the boss of the once-through fan can be secured. Note that in the blade C314c having a convex surface facing the fixed tool gap, the width of the fixed tool gap can be ensured by making the direction of this straight line intersect at a position farther from the axial center of the once-through fan or not at all. Can be secured.

  In addition, the thicknesses of the extension portions 314c 'and 314d' of the blade C and the blade D are combined with a constant portion and a portion that uniformly decreases toward the axial center of the cross-flow fan. In this way, by reducing the wall thickness monotonously, the wing C, wings D 314c and 314d have the maximum blade thickness in the middle of the wing shape, and maintain a shape that monotonously decreases forward and backward. can do. By doing so, flat flat portions are created in the extended portions 314c 'and 314d' of the wing C and wing D, and the fabrication of the mold is simplified as compared with the case where the wing C and the wing D are formed of continuous curved surfaces. Is done.

  Further, the extension dimensions of the extension portions 314c 'and 314d' of the blade C and blade D are maximized at the root of the blade, minimized at the tip step position S of the blade, and monotonously decreasing in the middle. As a result, the dimension of the extension is reduced in the part approaching the blade of the adjacent single vane wheel, the dimensional difference with the blade of the adjacent single vane wheel is reduced, and the turbulence of the air flow in the impeller of the cross-flow fan is reduced. The generation of noise is suppressed.

  In this way, the inner diameter of the blades forming the largest blade is made smaller than the inner diameter of the other blades to increase the chord length. (That is, {(distance from the central axis of the cross-flow fan to the outer edge of the blade forming the connection gap) − (from the central axis of the cross-flow fan to the inner edge of the blade forming the connection gap) Distance)} ≦ 2 × {(distance from the central axis of the cross-flow fan to the outer edge of the other blade) − (distance from the central axis of the cross-flow fan to the inner edge of the other blade)}. .) Thereby, the outer diameter of a cross-flow fan is maintained and the enlargement of the electric equipment incorporating a cross-flow fan can be avoided. When the inner diameter is reduced, the fan characteristics are improved. On the other hand, if the difference between the inner and outer diameters of the blade exceeds twice the difference between the inner and outer diameters of the other blades, the increase in rotational moment due to the smaller inner diameter is equivalent to the rotational moment of the removed blade, but the smaller inner diameter As a result, the internal vortex of the cross-flow fan becomes unstable and adverse effects occur. Therefore, it is preferable to make the difference between the inner and outer diameters twice or less. Even when the difference between the inner and outer diameters is twice or less, about 80% of the amount of unbalance obtained by removing the blades to secure the air gap can be improved.

  Further, the blades forming the connection gap are not located on the line connecting the connection gap and the central axis of the cross-flow fan. Specifically, the extension line of the extension center line that faces the inner diameter of the blade that forms the gap with the convex surface facing the gap is configured not to cross between the gap and the rotation center. As a result, the inlet angle on the inner peripheral side is set to around 90 ° to suppress the deterioration of the characteristics of the cross-flow fan, and the blade extension part prevents the insertion and removal of the boss fixing tool from the gap. There is no.

  Moreover, it has a flat blade surface in the part made smaller than the internal diameter of the other blade | wing which forms the largest blade | wing. This simplifies the production of the mold when the impeller is made of plastics, and can reduce mold costs. In particular, if the thickness of this portion is less than the maximum thickness of the portion larger than the inner diameter of the other blades forming the gap between the maximum blades and 50% or more of the maximum wall thickness, forming is easy and the strength of the blades is also increased. Sufficient cross-flow fan can be obtained. Further, by providing the flat portion, the blade angle on the inner diameter side of the blade can be approximately 90 degrees, and the basic structure as a cross-flow fan is not destroyed, so that stable performance can be obtained.

  Also, the chord length of the wings that make up the largest wing is monotonously decreased from the boss side toward the adjacent single wing wheel. This makes it possible to improve the fan characteristics at the base of the blades of a single vane with a boss that is significantly deteriorated due to the presence of the bosses, and to drastically change the inner diameter of the blade at the boundary between adjacent single vanes. It can alleviate and suppress the turbulence of the air flow in the fan.

  Here, the case where the cross-flow fan of this invention is used for a domestic air conditioner will be described with reference to FIGS. FIG. 12 is a perspective view of the cross-flow fan incorporated in the air conditioner. FIG. 12 is a perspective view of the cross-flow fan and the blower motor incorporated in the air conditioner.

  The indoor unit 2 of the air conditioner includes an indoor heat exchanger 33 located at the center of the housing body 21, a cross-flow fan 311 located downstream of the heat exchanger 33, and a lower end of the indoor heat exchanger 33. A dew tray 35 and the like are provided, and a decorative panel 25 is provided facing the air-conditioned space of the housing body 21. The decorative panel 25 has air inlets 27 and 27 ′ for sucking room air and an air outlet 29 for blowing out air in which temperature and humidity are harmonized. The suction panel 251 is rotated by driving an open / close arm with an arm driving device using a rotation shaft provided on the decorative panel 25 as a fulcrum, and opens the air suction port 27 ′ during operation of the air conditioner. Thereby, during operation, room air is sucked into the indoor unit 2 from the air suction ports 27 and 27 '. On the other hand, the vertical wind direction plate 291 is pivoted at a required angle during operation of the air conditioner by the drive motor with the pivot shafts provided at both ends as a fulcrum, and the air outlet 29 is opened and held in that state. The blown airflow from the crossflow fan 311 is passed through a blowout air passage 290 having a width substantially equal to the length of the crossflow fan 311, and the vertical airflow direction plate 291 disposed at the blowout port 29 deflects the vertical direction of the airflow to exchange heat. Blow out the air into the room.

  The result of operating the once-through fan of the present invention incorporated in the indoor unit of the air conditioner of FIG. 12 will be described with reference to FIGS. 11 and 13 to 16. FIG. 13 shows the effect of improving the wind speed distribution. FIG. 14 is a diagram showing the improvement effect 1 of the static pressure characteristics. FIG. 15 is a diagram showing the improvement effect 2 of the static pressure characteristics. FIG. 16 is a diagram showing the effect of improving the power consumption of the blower motor.

  The cross-flow fan 311 of the present invention and the conventional cross-flow fan were incorporated into the indoor unit of the air conditioner of FIGS. 11 and 12, and the wind speeds were compared at the wind speed comparison positions A to G (see FIG. 11) of the air outlet 29. The difference between the cross-flow fan of the present invention and the conventional cross-flow fan is that the blades sandwiching the largest blades of the bossed single vane are extended to the inner diameter side by 10 mm, and the other parts are the same.

  Focusing on the wind speed at the position of the bossed single vane vehicle, as shown in FIG. 13, the airflow blown from the cross-flow fan at the rightmost comparison position G flows through the blowout air passage 290 that is substantially equal to the length of the cross-flow fan. In the middle, the blowout air passage is large and spreads outward in the axial direction of the cross-flow fan, so that there is almost no difference in the blown-out air speed between the cross-flow fan of the present invention and the conventional cross-flow fan due to the effect of the airflow expanding laterally. On the other hand, at the comparative position F, which is substantially the center in the axial direction of the bossed single vane, there is almost no difference between the places where the wind speed is large (black circle and white circle in FIG. 13), but the resistance to the airflow increases and the wind speed increases. In the small area (black triangle and white triangle in FIG. 13), the wind speed of the extended 10 mm fan of the embodiment is greatly improved to 2.2 m / s, compared to the wind speed of the conventional non-extension fan of 1.8 m / s. It was done.

  In general, in order to achieve both comfort and energy saving, it is important to continuously operate the compressor at a low capacity corresponding to the heat load in the vicinity of the set temperature. Currently, continuous operation with low capacity is performed by inverter control. In this case, since the operation time with low capacity and low power consumption becomes long, low power consumption at low capacity greatly contributes to energy saving. According to the results of FIG. 13, the wind speed distribution at the air outlet 29 was improved particularly at a low wind speed. This leads to a reduction in power consumption of the blower motor when operating with a low air volume corresponding to low capacity. Therefore, it is possible to expect an effect that directly leads to energy saving and noise reduction.

  Next, the effect of improving the static pressure characteristics of the cross-flow fan of the embodiment will be described with reference to FIGS. The result of comparing the static pressure is shown in FIG. The amount of air showing the same static pressure increased in a portion close to the point where the wind speeds were compared (that is, a portion close to the operating point when incorporated in an air conditioner). In other words, this means that the rotational speed of the once-through fan required to obtain the same air volume and static pressure can be reduced. Power consumption is reduced by reducing the number of rotations of the once-through fan, saving energy. In addition, noise can be reduced.

  FIG. 15 shows the results when the rotational speed is lowered. In this case, the operating point when incorporated in the air conditioner is estimated to be about 5 m3 / min and about 3 Pa, estimated from the data of the rotation speed 1106 / min. Near this value, the air volume showing the same static pressure increased as described above. Thereby, the rotation speed of the blower motor for obtaining the same air volume and static pressure can be lowered, and energy saving and noise reduction can be achieved.

  Next, the improvement effect of the power consumption of the air blower motor of an Example is demonstrated using FIG. The result of comparing the power consumption of the blower motor is shown in FIG. In this case, a difference in power consumption is not observed where the air volume is large, but a difference in power consumption of about 0.1 W is recognized where the air volume is small. Even if the power consumption is reduced by about 0.1 W, as described above, the operation time with a low capacity and a low air volume is long, so that a great energy saving effect is obtained. Thus, when the cross-flow fan of this invention is used for an air-conditioning apparatus, the wind speed distribution of a blower outlet can be improved and it can contribute to energy saving.

231 Bearing 311 Cross-flow fan 313 Blower motor 313a Motor shaft 314 Blade 314a Blade A
314b Wing B
314c Wing C
314c ′ Extension part of wing C 314d wing D
314d 'Extension portion 316 of wing D Support disc 316a Hollow support disc 316b Support disc 316 with boss Support disc 317 with support shaft Single van 317a Single van 317 without boss Single van 318a Hollow support disc Connecting hole 318c Connecting hole 321 of supporting disk with support shaft Fixed tool gap 322 Boss 323 Screw 326 Support shaft A to G Wind speed comparison position Da to Dd Inner diameter of blade A to blade D Do Outer diameter of blade A to blade D Ga to Gd Blade length L of blade A to blade D Fan central axis R Direction of rotation Ra to Rd Inner diameter circle S of blade A to blade D Tip step position e Support disk connecting hole Airfoil centerline length e 'Blade tip Airfoil centerline length f at step position f Support disk connecting hole depth f 'Blade tip step

Claims (8)

A housing having an air inlet and an air outlet;
A heat exchanger that exchanges heat between indoor air sucked from the air suction port;
A cross-flow fan that is located downstream of the heat exchanger and blows out indoor air that has exchanged heat with the heat exchanger from the air outlet;
A drive device disposed on one end side of the cross-flow fan and driving the cross-flow fan,
The cross-flow fan has a plurality of blades arranged in a circumferential direction, and a plurality of gaps formed by the plurality of blades.
The plurality of gaps have connection gaps for connecting the cross-flow fan to the driving device,
The connection gap is formed wider than the other gaps,
An air conditioner in which a chord length of the wing forming the connection gap is formed longer than a chord length of the other wing.   The air conditioner according to claim 1, wherein the blades forming the connection gap protrude more toward the inner periphery than the other blades.   The air conditioner according to claim 2, wherein the distance from the axial center of the cross-flow fan to the outer peripheral side ends of the blades and the plurality of blades forming the connection gap is equal.   In Claim 3, {(Distance from the center axis of the cross-flow fan to the outer end of the blade forming the connection gap)-(Inner end of the blade forming the connection gap from the center axis of the cross-flow fan) Distance to the part)} ≦ 2 × {(distance from the central axis of the cross-flow fan to the outer end of the other blade) − (distance from the central axis of the cross-flow fan to the inner end of the other blade) )} Air conditioner.   4. The air conditioner according to claim 3, wherein the blades forming the connection gap are not located on a line connecting the connection gap and a central axis of the cross-flow fan.   4. The air conditioner according to claim 3, wherein a portion of the blades forming the connection gap that protrudes toward the inner peripheral side of the other blades has a flat blade surface. 4. The cross flow fan according to claim 3, wherein a single vane wheel with a boss not provided with the connection gap is disposed on one end side of the cross flow fan, and the single unit with the boss is arranged from one end side to the other end side of the cross flow fan. It is configured by sequentially connecting a plurality of bossless single impellers that do not have the connection space from the impeller,
An air conditioner in which a chord length of the blade that forms the connection gap is shortened from one end side of the cross-flow fan on which the driving device is disposed toward the other end side of the cross-flow fan. 4. The cross flow fan according to claim 3, wherein a single vane wheel with a boss not provided with the connection gap is disposed on one end side of the cross flow fan, and the single unit with the boss is arranged from one end side to the other end side of the cross flow fan. It is configured by sequentially connecting a plurality of bossless single impellers that do not have the connection space from the impeller,
The wings constituting the bossed single impeller other than the wings forming the connection gap are arranged in the same manner as the corresponding bossless single impeller wings,
An air conditioner in which the wings of the bossless single vane are arranged in the same manner as the blades of any other corresponding bossless single vane.