WO2013051297A1

WO2013051297A1 - Air conditioner

Info

Publication number: WO2013051297A1
Application number: PCT/JP2012/053629
Authority: WO
Inventors: 健一矢萩; 悟己時田
Original assignee: 日立アプライアンス株式会社
Priority date: 2011-10-05
Filing date: 2012-02-16
Publication date: 2013-04-11
Also published as: JP2013079617A

Abstract

This air conditioner is provided with: a housing body (21) having air suction openings (27, 27') and an air discharge opening (29); a heat exchanger (33) for subjecting interior air, which is sucked from the air suction openings (27, 27'), to heat exchange; a cross-flow fan (311) located downstream of the heat exchanger (33) and discharging, from the air discharge opening (29), the interior air having been subjected to heat exchange with the heat exchanger (33); and a drive device (313) disposed on one end side of the cross-flow fan (311) and driving the cross-flow fan (311). The cross-flow fan has blades which are arranged in the circumferential direction and air gaps which are formed by the blades. The air gaps have a connection air gap for connecting the cross-flow fan (311) to the drive device (313). The connection air gap (321) is formed to be greater than the remaining air gaps. The chord length of blades (314c, 314d) which form the connection air gap (321) is formed to be greater than the chord length of the remaining blades (314b).

Description

Air conditioner

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

In general, in a home air conditioner, a cross-flow fan is used as a blower fan in order to place a low-blowing wind in a uniform flow and deliver it to a distant place of the air-conditioned space. A fan motor for rotating the cross flow fan is disposed adjacent to the cross flow fan in the axial direction.

In Patent Document 1, the boss and the drive motor are rotated by reducing the axial length of several blades facing the fixing screw of the boss and arranging the auxiliary support plate at the contracted end of the blade. An air gap is formed to insert a fastening jig (driver or the like) of a fixing screw that fixes the shaft and the fixing screw.

In Patent Document 1, although the air volume is increased as compared with the outer boss type of cross-flow fan, local backflow occurs at the position where the wing is omitted. Therefore, wind speed fluctuation becomes large near this gap, resulting in 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 air blown out from the notch to the outside of the support plate may turn around to cause an exposure during cooling or the like.

JP 2000-205178 A

The present invention provides an air conditioner having an improved wind velocity distribution in an air conditioner provided with a cross-flow fan having an air gap for inserting a fastening jig for fixing screws for fixing a boss portion and a drive motor rotary shaft. To be a task.

The air conditioner according to the present invention comprises a housing having an air suction port and an air blowout port, a heat exchanger for exchanging heat with room air taken in from the air suction port, and a heat exchanger located downstream of the heat exchanger. A cross-flow fan for blowing out the heat-exchanged indoor air from the air outlet, and a drive device disposed at one end side of the cross-flow fan to drive the cross-flow fan, the cross-flow fan includes a plurality of circumferentially arranged blades and a plurality of blades And a plurality of air gaps formed by the wings of the plurality of air gaps, wherein the plurality of air gaps have connection air gaps for connecting the cross-flow fan to the drive device, and the connection air gaps are formed wider than the other air gaps to form connection air gaps. The chord length of each wing is longer than the chord length of the other wings.

According to the present invention, in an air conditioner provided with a cross-flow fan having an air gap for inserting a fastening jig for fixing screws for fixing the boss portion and the drive motor rotary shaft, a chord of a wing forming the air gap. Since the length is longer than the chord length of the other wings, the wind velocity distribution near this gap can be improved, thus providing an air conditioner having an improved wind velocity distribution throughout the cross flow fan.

(A) And (b) is a front view and AA sectional drawing of a cross-flow fan, respectively. It is a block diagram of a cross flow fan. It is the disassembled perspective view seen from the spindle side of the cross flow fan. 4 (a) is an enlarged view of the boss of the cross-flow fan, and FIG. 4 (b) is a view of a gap where the support disc on the boss side is broken. It is a BB cross section of FIG. 4 (a). It is a gap enlarged view for a boss fixed tool. It is a CC cross section of FIG. It is a DD cross section of FIG. FIG. 6 is an enlarged view of a blade C of a cross-flow fan and a tip of a blade D. It is the disassembled perspective view seen from the boss | hub side of the cross flow fan. FIG. 2 is a perspective view of a cross flow fan and a blower motor incorporated in an air conditioner. It is sectional drawing which integrated the cross-flow fan in the air conditioner. It is a figure which shows the improvement effect of wind speed distribution. It is a figure which shows the improvement effect of the static pressure characteristic of the cross-flow fan at the time of throttling air volume by rotation speed constant (1106 / min). It is a figure which shows the improvement effect of the static pressure characteristic of the cross-flow fan at the time of throttling air volume by constant rotation speed (700 / min). It is a figure which shows the improvement effect of the ventilation motor power consumption of the cross-flow fan when the amount of winds is throttled with rotation speed constant (1106 / min).

Hereinafter, embodiments of the present invention will be described 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 6 to 11. FIGS. 1A and 1B are a front view and a cross-sectional view of a cross flow fan, respectively. FIG. 2 is a block diagram of a cross flow fan. In FIGS. 1 (a) and 1 (b) and FIG. 2, in order to make the description easy to understand, illustration of a part of the wing around the boss is omitted, and the inner boss is illustrated. FIG. 3 is an exploded perspective view of the cross flow fan as viewed from the support shaft side. FIG. 4 (a) is an enlarged view of a boss of a cross flow fan, and FIG. 4 (b) is a view of a gap in which a support disk on the boss side is broken. FIG. 6 is an enlarged view of a gap for a boss fixing tool. FIG. 7 is a cross section taken along the line CC in FIG. FIG. 8 is a cross section taken along the line DD of FIG. FIG. 9 is an enlarged view of a blade C and a blade D of a cross-flow 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 a cross flow fan and a blower motor incorporated in the air conditioner.

In FIGS. 1 (a) and 1 (b), a circular bossed support disk 316b and a support shaft supported disk 316c are located at both ends of the cross-flow fan 311. A plurality of circular hollow support disks 316a are spaced apart between the

support disks

316b and 316c. These

support disks

316 a, 316 b, 316 c are arranged parallel to one another such that their centers are located on the fan central axis L.

A plurality of wings 314 arranged in the circumferential direction of the support disc 316 are disposed between the support discs 316. As shown in FIG. 3, these wings 314 have a so-called wing-like shape in which the surface in the rotational direction of the cross flow fan 311 is concavely curved and the surface opposite to the rotational direction of the cross flow fan 311 is convexly curved. . Further, the wings 314 are formed substantially parallel to the fan central axis L.

317a of FIG. 2 is a single-wing vehicle without a boss (a boss-less single-wing vehicle 317a). A boss A single wheel 317a has a wing A 314a disposed on one side of a hollow support disk 316a, and a connection hole 318a in which the tip of a wing A 314a of the bossless single wheel 317a adjacent to the other face fits (FIG. See). The hollow support disk 316a holds the wing 314a and enhances the strength of the entire cross-flow fan 311 in which a plurality of single-wheeled vehicles are connected.

As shown in FIG. 2, a support shaft 326 extends outward from the center of the outer side surface of the support disk with support shaft 316c, and this support shaft 326 has a housing 231 for an air conditioner as shown in FIG. Supported by 20. Similar to the hollow support disk 316a, the inner surface of the support disk with support shaft 316c has a connection hole 318c (see FIG. 10) in which the tip of the wing A 314a of the adjacent single bossless single wheel 317a is fitted.

As shown in FIGS. 3 and 4 (a) and (b), the inner surface of the bossed support disk 316b (the surface on which the wings B 314 b, wings C 314 c, wings D 314 d, etc. stand) is the motor shaft 313 a of the blower motor 313. And a boss 322 for fixing the cross flow fan 311. A screw 323 for fixing the motor shaft 313a and the boss 322 is provided on the boss 322 perpendicularly to the fan central 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 a wind.

As shown in FIGS. 4A and 4B, the boss 322 of the cross flow fan 311 is provided inside the bossed support disc 316b on the side of the blower motor 313. Therefore, between the bossed support disc 316b and the hollow support disc 316a adjacent to the bossed support disc 316b to form a fixed tool space 321 for fastening the screw 323 for fixing the boss 322 and the motor shaft 313a. The fixed tool air gap 321 is formed by omitting one or two wings 314 of the plurality of wings 314 passed. The fixed tool air gap 321 is wider than the other air gaps formed by the blades 314 of the cross-flow fan 311 (the wings of the blades 314 arranged opposite to the fixed tool air gap 321 form another air gap 314 Than the wings of the

However, as described above, when making the air gap 321 for fixing tools for tightening the screw 323 of the boss 322 wider than other air gaps or simply omitting the wing 314 to be there, the cross-flow fan 311 Wind speed distribution decreases.

In order to suppress the reduction of the wind speed distribution due to the air gap 321 for such a stationary tool, as shown in FIG. 6, an air gap 321 for the stationary tool is formed, and the wings C 314 c facing each other across the air gap 321 for the stationary tool The chord length of D314d was made larger than the chord length of other wings B314b. As an example, the wing C 314 c and the wing D 314 d opposed to each other with the air gap 321 for the fixed tool are protruded inward relative to the other wing B 314 b. Further, the distances from the axial center of the cross-flow fan to the outer peripheral end of all the blades including the blade C314c and the blade D314d are equal.

The portion outside the inner diameter circle Rb of the wing B 314 b (the circle formed by the line connecting the inner ends of the other wings B 314 b) of the wing C 314 c and the wing D 314 d can have the same shape as the wing B 314 b. In an air conditioner provided with a cross-flow fan 311 having a space 321 for a fixed tool for inserting a fastening jig for fixing screws for fixing a boss portion and a drive motor rotary shaft, the space 321 for the fixed tool is formed Since the chord length of the wing C314c and the wing D314d is larger than the chord length of the other wings B314b, the reduction of the air blowing performance by the air gap 321 for the fixed tool can be suppressed, so the wind speed distribution of the air gap 321 for the fixed tool Thus, an air conditioner having an improved wind speed distribution throughout the cross flow fan 311 can be provided. By improving the wind speed distribution, the number of revolutions of the compressor required to obtain the same air volume is reduced, and the noise in the cross flow fan 311 is also reduced. In addition, the imbalance of the cross flow fan is increased by the amount of the removed wing mass, but by increasing the chord length, the amount of imbalance is reduced and the imbalance is suppressed.

Wing C314c, wing D314d, the part outside the inner diameter circle Rb of wing B314b (the circle formed by the line connecting the inner ends of other wings B314b) has the same shape as wing B314b, and the center of the inward projecting part The curvature of the line is made larger than the curvature at the position of the inner diameter circle Rb of the wing B 314 b so as to gently extend toward the boss 322. The arrangement position of the wing C 314 c of the boss single-wheeled wheel 317 b and the portions excluding the extensions 314 c ′ and 314 d ′ of the wing D 314 d is the same as the arrangement position of the wings A 314 a of the boss-less single-wheeled wheel 317 a (that is, In the cross-flow fan, a bossed single wheel 317b not provided with a connection gap is disposed on one end side of the cross-flow fan 311, and a connection gap is provided from the bossed single wheel 317b from one end side to the other end of the cross-flow fan The wings that are configured by sequentially connecting the plurality of non-bossless single-wing wheels 317a and that form the connecting air gap are arranged similarly to the wings of the corresponding non-bossless single-wing wheels 317a. The wings of the bossless single winged vehicle are arranged similarly to the wings of any other corresponding bossless single winged wheel 317a.). As described above, by forming the wing C 314 c and the wing D 314 d opposite to each other with the space 321 for the fixed tool interposed therebetween, the local wind flow at the connecting portion of the boss single-wheeled wheel 317 b and the bossless single-wheeled wheel 317 a However, except for the vicinity of the air gap 321, it becomes almost the same as the local wind flow at the connection between the bossless single wheels 317a, and the air flow characteristics when the bossless single wheels 317a are connected, connection Most of the structural study results can be used. For this reason, the parts that need to be examined in the boss single-wheeled vehicle 317b are only the shapes including the lengths of the wings C314c and the extensions 314c 'and 314d' of the wing D314d sandwiching the air gap 321, and the matters to be discussed are largely omitted. Development period can be shortened.

The portion in contact with the hollow support disc 316a of the boss-less single-wing wheel 317a adjacent to the wing C314c and the wing D314d has the same shape as the wing A314a, and as shown in FIG. 7 and FIG. The portion extending the chord length at C314c and wing D314d is from the root of the wing C314c and wing D314d to the front of the wing tip step f '.

As shown in FIG. 8, the hollow support disc 316a of the bossless single wheel 317a has a depth f, as shown in FIG. 8, since the tip of the wing A 314a of the adjacent bossless single wheel 317a fits in as described above. It has a connecting hole 318a matched to the wing shape of the wing A 314a. The length e of the connection hole 318a along the wing center line is e ≧ e ', where e' is the length of the wing center line at the tip of the wing A 314a. The wing B 314 b has the same shape as the wing A 314 a, and the wing B 314 b is fitted into the connection hole 318 a of the hollow support disc 316 a as shown in FIG. 8 like the wing A 314 a. Further, the portions other than the wings C and the extensions 314c 'and 314d' of the wings D have the same wing shape as the wings B, and the length e 'along the wing centerline at the step portion is the same as the wings B314b, As shown in FIG. 7, e ≧ e ′.

When connecting the wing A 314 a to the adjacent bossless single wheel 317 a with the wing C 314 c and the wing tip step f ′ of the wing D 314 d (a surface opposite to the wing A 314 a of the hollow support disk 316 a of the bossless single wheel 317 a When the tip of the wing C314c and the tip of the wing D314d is fitted into the connection hole 318a, the wings C314c and the extensions 314c 'and 314d' of the wing D314d do not get in the way. The wing tip step f 'of the wing C314c and the wing D314d is f' ≧ f.

With this configuration, single-wing vehicles 317 other than the boss single-wheeled vehicles 317b can be unified into the single-wheeled vehicles 317a other than the single-wheeled vehicles 317b including single-wing vehicles adjacent to the single-wheeled vehicles 317b with bosses. Since the types of molding dies of the car 317 can be two types of the molding die of the bossless single winged wheel 317a and the molding die of the bossed single winged wheel 317b, an increase in the number of kinds of molding dies can be suppressed.

The axial dimension of the boss single-wheeled wheel 317b may be different from the axial dimension of the boss-less single-wheeled wheel 317a. Even when the width of the heat exchanger 33 is changed, a cross flow fan 311 of an appropriate length is configured only by preparing a forming die of a bossed single-wing wheel 317b whose axial dimension is increased or decreased. can do.

Further, in the cross flow fan of the embodiment, a plurality of single impellers formed by arranging a large number of blades in the circumferential direction are connected and connected in the axial direction on one surface near the outer periphery of the support disk. The single-wheeled vehicle constituting one end of the cross-flow fan has a boss for fixing the cross-flow fan to the shaft of the cross-flow fan drive, and the single-wheeled vehicle constituting the other end of the cross-flow fan has a support shaft The single wheeled vehicle of the present invention is used as the cross flow fan according to any one of claims 1 to 3.

As a result, since a plurality of single-wing vehicles with short wingspans are stacked to form a cross-flow fan of a required length, the wing widths of individual single-wing vehicles can be made small and cost-effective plastics are made be able to. In this case, even in the case of injection molding using plastics, the difference in chord length between the base and the tip of the wing to be erected on the support disk, which is caused by the draft of the mold, is due to the shortened wing width. It becomes smaller and the adverse effect on the blowing performance is reduced.

In addition, the performance difference between the bossed single-wing vehicle 317b and the adjacent bossless single-wing vehicle 317a is reduced, the wind speed at the air outlet of the bossed single-wheeled vehicle portion 317b is increased, and the wind speed distribution is improved. Can ease their dissatisfaction. In addition, the use of plastic makes it possible to improve air blowing performance such as noise by adopting a thick airfoil at the center of the wing.

Further, in the cross flow fan 311 of the embodiment, between the wings of the single-wheeled wheeled boss 317b is made the same except for the portions between adjacent single-wheeled wheels and the space for the boss fixing tool. In the plastic cross-flow fan 311, the types of forming dies can be reduced and the initial cost can be suppressed by making the single-bladed wheel in the central part excluding both ends into a single-bladed wheel having exactly the same shape. At this time, a concave portion conforming to the wing shape is supported on the connecting portion between adjacent single-wing wheels, and the position is determined only by overlapping. Since the cascade pitch angle of the bossed single-wheeled vehicle 317b is the same except for the cascade pitch angle of the adjacent single-wheeled vehicle and the portion corresponding to the air gap for the boss fixing tool, the adjacent bossless single-wing By providing a recess in the support disk of car 317a according to the wing shape used for connecting bosses without a single winged wheel 317a, the position is determined only by stacking the bossed single winged wheel 317b on the adjacent single winged wheel can do.

In this manner, a single-wing vehicle identical to the other non-boss single-wheeled vehicle 317a can be used as the non-boss-free single-wheeled vehicle 317a adjacent to the bossed single-wing vehicle 317b, and the connection recess different from the other non-bossed single-wing vehicle 317a There is no need to make a single-wing vehicle with a separate. Therefore, the initial cost of manufacture can be reduced without increasing the types of molds, and since the types of parts do not increase, the management cost at the time of manufacture can also be reduced.

Further, the shape of the connecting portion of the wings constituting the largest wing of the bossed single-wing vehicle 317b with the adjacent bossless single-wheeled wheel 317a is made the same as the corresponding portion of the adjacent bossless single-wheeled wheel 317a. As a result, the support disk of the adjacent bossless single-wing vehicle 317a is provided with a recess adapted to the wing shape used for connecting the bossless single-wheeled vehicles 317a, and the wing of the bossed single-wheeled carriage 317b is contained therein. A boss single-wheeled wheel 317 b is stacked on the recess and connected by a method such as fusion or adhesion. At this time, the portion where the chord length is extended approaches only the support disc of the adjacent bossless single wheel 317a with a slight gap, but the connection strength with the adjacent single wheel is the above connection portion. There is no need to fuse or bond this part as it can be secured sufficiently. As described above, since only one type of bossless single-wing wheel 317a is required, the initial cost of manufacturing can be reduced without increasing the types of molds. In addition, since the types of parts do not increase, the management cost at the time of manufacture can be reduced.

Next, the extensions of the wing C and the wing D will be described with reference to FIGS. 5 to 7 and 9. FIG. 5 is a cross section taken along the line B-B in FIG.

In general, when operating a cross flow fan, it is necessary to pay attention to the unbalance of the cross flow fan. Unbalance is caused by various things in construction and manufacturing, and a large unbalance leads to an increase in vibration and noise and impairs the quality of a product incorporating a cross flow fan. For this reason, balance weights are attached to the cross-flow fan blades to reduce unbalance. In this case, when the amount of unbalance originally is large, the number of balance weights to be attached increases, and the amount of work of the unbalance removing operation increases. For this reason, it is important to reduce the original amount of unbalance.

Change the length of the extension 314c 'of the wing C 314c to 5 mm, 10 mm, 20 mm, and install it in the air conditioner of FIG. 11, and blow out the air passing through the bossed single wheel 317b (speed comparison position F: The wind speed in (refer FIG. 11) was compared. As a result, the improvement of the wind speed was favorable in the case of 10 mm of extended length.

As shown in FIG. 5, by providing the extension portions 314c 'and 314d' on the wing C and the wing D, the chord lengths Gc and Gd of the wing C and the wing D become larger than the chord length Gb of the wing B 314b. At this time, the unbalance amount is improved by the moment due to the mass of the extension portions 314c 'and 314d'. The cross flow fan of this embodiment (outside diameter (distance from the center axis of the cross flow fan to the outside diameter end of the blade x 2) Do = 110 mm, inside diameter (from the center axis of the cross flow fan to the inside diameter end of the wing In order to provide the gap 321 for the boss fixing tool, the distance is calculated by calculation of distance x 2) Db = 83.5 mm, inner and outer diameter difference Do-Db = 26.5, chord length gb = 15.7 mm, and 34 blades. The wings C and the extensions D of the wings D can cancel 80% of the amount of imbalance when only one wing is removed. At this time, the inside diameters Dc and Dd of the wing C and the

wings D

314 c and 314 d are 63.5 mm, and the inside and outside diameter difference Do-Dc is 46.5 mm, which is 1.8 times the initial inside and outside diameter difference. According to further calculations, if the extension is extended to twice the initial inner and outer diameter difference (blade C, inner diameter Dc of blade D, Dd = 57 mm, inner and outer diameter difference = 53 mm), the above unbalance amount is approximately 100 It turned out that it can cancel%.

Generally, the shape of the cross-flow fan for air conditioners is determined by the analogy from similarity rules to determine the main specifications such as the outer diameter and the length, in accordance with the characteristics of the load and the required performance. Accordingly, the outer diameter side blade angle, the inner diameter side blade angle, the inner and outer diameter ratio, and the like are similar. For this reason, the relationship between the length of the above-mentioned extension parts 314c 'and 314d' and the inner and outer diameter difference is also the same.

In the embodiment, the wing C of the wing C, and the wing C of the center line of the extensions 314c 'and 314d' of the wing D, and the inner diameter circles Rc and Rd of the

wings D

314c and 314d are straight lines, and the inner diameter circle Rb of the wing B 314b It connects smoothly with the center line of the wing. Further, the straight line on the side of the inner diameter circles Rc and Rd is a straight line directed to the axial center of the cross flow fan 311. This is because the air flow comes in and out from the inner diameter end of the blade, so the air flow in both directions is considered.

By doing this, it is also possible to secure a fixed tool air gap 321 for fixing the boss of the cross flow fan 311. In the case of a blade C 314 c which has a convex surface directed to the fixed tool air gap 321, the width of the fixed tool air gap 321 is such that the direction of this straight line intersects at a distance from the axial center of the cross flow fan 311 or does not intersect at all. Can be secured more reliably.

Further, the thickness of the wings C and the extensions 314c 'and 314d' of the wings D are combined with a constant portion and a uniformly decreasing portion toward the axial center of the cross-flow fan 311. Thus, by reducing the wall thickness monotonously, the wing C and

wings D

314 c, 314 d have the maximum wing thickness in the middle which is the basis of the wing shape, and keep the shape monotonously decreasing forward and backward can do. In this way, flat flat portions are created in the wings C and the extensions 314c 'and 314d' of the wings D, and the fabrication of the mold is simplified as compared to the one formed by continuous curved surfaces.

Furthermore, the extension dimensions of the wings C and D extensions 314c 'and 314d' are maximized at the root of the wing, minimized at the tip step position S of the wings C and D, and monotonously reduced in the middle Do. As a result, the dimension of the extension portion is reduced at the portion approaching the wing of the adjacent single-wing wheel 317, and the difference in size with the wing of the adjacent single-wing wheel 317 is reduced. The disturbance is alleviated and the generation of noise and the like is suppressed.

Thus, the inner diameter of the wing C forming the largest wing between the wings and the

wings D

314c, 314d are smaller than the inner diameter of the other wings to increase the chord length, and the inner and outer diameter differences of the wings forming the largest wing are other No more than twice the inner and outer diameter difference of the wing (that is, {(the distance from the central axis of the cross flow fan to the outer end of the wing that forms the connecting gap))-(connective gap from the central axis of the cross flow fan Distance from the inner end of the wing) 2 2 × {(distance from the central axis of the cross flow fan to the outer end of the other wing)-(distance from the central axis of the cross flow fan to the inner end of the other wing) A) relationship. Thus, the outer diameter of the cross flow fan is maintained, and the enlargement of the electric device incorporating the cross flow fan can be avoided. A smaller inner diameter improves the fan characteristics. On the other hand, if the inner and outer diameter difference of the blade exceeds twice the inner and outer diameter differences of the other blades, the increase in the rotational moment due to the smaller inner diameter will be equal to the rotational moment of the removed blade, but the inner diameter is reduced. As a result, the internal vortex of the cross-flow fan becomes unstable and adverse effects occur. Therefore, it is preferable to make the inner and outer diameter difference 2 times or less. Even when the difference between the inner and outer diameters is not more than twice, about 80% of the amount of unbalance due to the removal of the wing to secure the gap can be improved.

Further, the wing C forming the connection gap 321 and the

wings D

314 c and 314 d are not located on the line connecting the connection gap 321 and the central axis of the cross flow fan 311. Specifically, the extension line of the extension center line directed to the inner diameter of the wing that is convex on the air gap and constitutes the air gap is configured not to cross between the air gap and the rotation center. As a result, the inlet angle on the inner peripheral side is set to about 90 ° to suppress the deterioration of the characteristics of the cross flow fan 311, and the extension of the wing hinders the insertion and removal of the boss fixing tool from the gap. I have not.

In addition, a flat wing surface is provided at a portion of the wing C that forms the largest wing between the wings and the inner diameters of the

wings D

314 c and 314 d smaller than the inner diameters of the other wings. This simplifies the manufacture of molds when making the impeller of plastics and reduces mold costs. In particular, if the thickness of this portion is equal to or less than the maximum thickness of a portion larger than the inner diameter of the other wings of the wings forming the largest wing and 50% or more of the maximum thickness, molding is easy and the strength of the wings is also A 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 made approximately 90 degrees, and the basic structure as the cross flow fan is not broken, so that stable performance can be obtained.

Further, the chord length of the wing C constituting the largest wing and the

wings D

314 c and 314 d are monotonously decreased from the boss side toward the adjacent single-wing vehicle. As a result, the presence of the boss portion can improve the fan characteristics of the base portion of the wing of the bossed single-wheeled vehicle which is significantly deteriorated, and a drastic change of the inner diameter of the wing occurring at the boundary portion with the adjacent single-wheeled vehicle. It is possible to alleviate the disturbance of the air flow in the fan.

Here, the case where the cross flow fan of the present invention is used for a domestic air conditioner will be described with reference to FIGS. 11 to 12. FIG. FIG. 12 is a cross-sectional view of a cross-flow fan incorporated in an air conditioner.

The indoor unit 2 of the air conditioner includes the indoor heat exchanger 33 located at the central portion of the housing body 21, the cross-flow fan 311 located downstream of the heat exchanger 33, and the lower end of the indoor heat exchanger 33. It has a dew tray 35 and the like positioned, and has a decorative panel 25 facing the air-conditioned space of the casing 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 whose temperature and humidity are adjusted. The suction panel 251 is pivoted by driving the open / close arm with an arm drive device with a pivot shaft provided on the decorative panel 25 as a fulcrum, and opens the air suction port 27 'at the time of operation of the air conditioner. As a result, room air is drawn into the indoor unit 2 from the air inlets 27 and 27 'during operation. On the other hand, the vertical air flow direction plate 291 is rotated by a drive motor at a required angle at the time of operation of the air conditioner with a rotation shaft provided at both ends as a fulcrum to open the air outlet 29 and held in that state . The air flow from the cross flow fan 311 is caused to flow to the blow air passage 290 having a width substantially equal to the length of the cross flow fan 311, and the air flow is deflected in the vertical direction by the up and down wind direction plate 291 disposed at the blowout port 29 Blow air out into the room.

The results of operation by incorporating the cross-flow fan of the present invention into the indoor unit of the air conditioner of FIG. 12 will be described using FIGS. 11 and 13 to 16. FIG. FIG. 13 shows the improvement effect of the wind speed distribution. FIG. 14 is a view showing the improvement effect 1 of the static pressure characteristic. FIG. 15 shows the improvement effect 2 of the static pressure characteristic. FIG. 16 is a view showing the improvement effect of the blower motor power consumption.

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 shown in 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 wings sandwiching the largest wings of the bossed single-wheeled vehicle are extended by 10 mm to the inner diameter side, and the other parts are the same.

Focusing on the wind speed at the position of the single-bladed boss, as shown in FIG. 13, the air flow blown out from the cross flow fan at the rightmost comparison position G flows in the blow air path 290 approximately equal to the length of the cross flow fan. Since the air flow path is largely expanded in the axial direction outside of the cross flow fan in the middle, the air flow is expanded in the lateral direction, so there is almost no difference in the air flow speed between the cross flow fan of the present invention and the conventional cross flow fan. On the other hand, at the comparison position F, which is the approximate center in the axial direction of the boss single-wheeled vehicle, there is almost no difference at large wind speeds (black and white circles in Fig. 13), but the air flow resistance is large and the wind speed is In the smaller area (black triangle and white triangle in Fig. 13), the wind speed of the extended 10 mm fan of the embodiment is significantly improved to 2.2 m / s against the wind speed of 1.8 m / s of the conventional non-long fan It was done.

In general, in order to achieve both comfort and energy saving, it is important to operate the compressor continuously at a low capacity close to the set temperature and at a low temperature corresponding to the heat load. At present, continuous operation with low capacity is performed by inverter control. In this case, since the operation time with low capacity and low power consumption is extended, low power consumption at low capacity greatly contributes to energy saving. According to the result of FIG. 13, the wind speed distribution of the air outlet 29 is improved particularly at a small wind speed. This leads to a reduction in the power consumption of the blower motor when operating with a low air volume that is compatible with low capacity. Therefore, the effect of direct connection to energy saving and noise reduction can be expected.

Next, the improvement effect of the static pressure characteristic of the cross flow fan of the embodiment of the cross flow fan when the air flow rate is reduced at a constant rotational speed will be described using FIGS. 14 and 15. The static pressure of the cross flow fan when the air flow rate is reduced with the number of revolutions fixed at 1106 / min is compared and the result is shown in FIG. The volume of air exhibiting 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 into the air conditioner). This means that, in other words, the cross flow fan 311 of the present invention can reduce the rotational speed of the cross flow fan necessary to obtain the same air volume and static pressure. As the rotational speed of the cross flow fan is reduced, the power consumption is reduced, resulting in energy saving. Also, noise can be reduced.

FIG. 15 shows the measurement results of the static pressure of the cross flow fan when the air flow rate is reduced with the number of rotations reduced and the number of rotations kept constant at 700 / min. In this case, the operating point when incorporated in the air conditioner is considered to be 5 m ³ / min and around 3 Pa, estimated from the data of the above-mentioned rotational speed 1106 / min. The air volume which shows the same static pressure increased like the above-mentioned above near this value. As a result, when the cross flow fan of the present invention is used in an air conditioner, the number of rotations of the blower motor for obtaining the same air volume and static pressure can be reduced to achieve energy saving and noise reduction.

Next, the improvement effect of the power consumption of the blower motor of an Example is demonstrated using FIG. A comparison result of the power consumption of the blower motor of the cross flow fan when the air flow rate is reduced at a constant rotational speed (1106 / min) is shown in FIG. In this case, although there is no difference in power consumption at high air volume, a difference in power consumption of approximately 0.1 W is observed at low air volume. Even if the power consumption is reduced by about 0.1 W, as described above, since the operation time with a low capacity and a low air volume is long, a great energy saving effect can be obtained. As described above, when the cross-flow fan of the present invention is used for an air conditioner, the wind speed distribution of the air outlet can be improved, which contributes to energy saving.

231 Bearing 311 Cross-flow fan 313 Blower motor 313 a Motor shaft 314 Wing 314 a Wing A
314b Wing B
314c Wing C
314c ′ Wing C extension 314d Wing D
314d ′ Wing D extension 316 Support disk 316a Hollow support disk 316b Support disk with boss 316c Support disk with support shaft 317 Single-wing vehicle 317a No boss Single-wheel vehicle 317b Boss single-wheel vehicle 318a Hollow support disk Connection hole 318c Support hole with support shaft Connection hole 321 Fixed tool air gap (connection air gap)
322 boss 323 screw 326 spindle A to G speed comparison position Da to Dd inner diameter Do of wing A to wing D outer diameter Ga to Gd of wing A to wing D chord length L of wing A to wing D fan central axis R rotation Direction Ra ~ Rd Inner diameter circle of wing A ~ wing D Tip step position e Support disc connection hole Wing centerline length e 'Wing type centerline length f at wing tip step position Support disc connection hole depth f 'wing tip step

Claims

A housing having an air inlet and an air outlet;
A heat exchanger that exchanges heat with room air drawn in from the air suction port;
A cross flow fan located downstream of the heat exchanger and blowing out room air heat-exchanged with the heat exchanger from the air outlet;
And a driving device disposed at one end of the cross flow fan and driving the cross flow fan.
The cross-flow fan has a plurality of wings arranged in a circumferential direction, and a plurality of air gaps formed by the plurality of wings.
The plurality of air gaps include connection air gaps for connecting the cross flow fan to the driver,
The connection gap is formed wider than the plurality of other gaps,
An air conditioner, wherein a chord length of the wing forming the connection gap is formed longer than a chord length of the plurality of other wings.
The air conditioner according to claim 1, wherein the wing forming the connection gap projects more inward than the other wings.
The air conditioner according to claim 2, wherein distances from an axial center of the cross flow fan to outer peripheral ends of the blades forming the connection gap and the plurality of blades are equal.
4. The air conditioner according to claim 3, wherein {(the distance from the central axis of said cross flow fan to the outer end of said wing forming said connection space)-(from the central axis of said cross flow fan to form said connection space Distance to the inner end of the wing)} ≦ 2 × {(distance from the central axis of the cross-flow fan to the outer end of the other wing) — (relative to the central axis of the cross-flow fan) An air conditioner satisfying the condition of distance to the inner end).
The air conditioner according to claim 3, wherein the wing forming the connection gap is not located on a line connecting the connection gap and a central axis of the cross flow fan.
The air conditioner according to claim 3, wherein a portion of the wings forming the connection gap that protrudes to the inner peripheral side relative to the other wings has a flat wing surface.
The air conditioner according to claim 3, wherein the cross flow fan has a boss-equipped single-wheeled vehicle not having the connection space at one end side of the cross flow fan, and the one end side to the other end side of the cross flow fan A plurality of boss-free single-wing vehicles not having the connection space from the single-wheeled vehicle with bosses sequentially connected, and from the one end side of the cross-flow fan where the drive unit is disposed, the other end of the cross-flow fan Head to the side,
An air conditioner in which a chord length of the wing forming the connection gap is formed short.
The air conditioner according to claim 3, wherein the cross flow fan has a boss-equipped single-wheeled vehicle not having the connection space at one end side of the cross flow fan, and the one end side to the other end side of the cross flow fan And a plurality of boss-less single-wing vehicles not having the connection space sequentially connected from the boss-equipped single-wing vehicle, and the blades constituting the boss-equipped single-fly vehicles other than the wings forming the connection gap. Are arranged in the same manner as the corresponding unbossed monowing wing of the wing,
An air conditioner wherein the wings of the bossless single winged vehicle are arranged in the same manner as the wings of any other corresponding bossless single winged wheels.