JP4559472B2 - Turbo fan, air conditioner - Google Patents

Description

  The present invention relates to a turbo fan molded from a thermoplastic resin and an air conditioner equipped with the turbo fan.

Some conventional turbofans molded from thermoplastic resin are designed to reduce the thickness and weight by securing the rigidity of the turbofan with ribs made of injected resin runners. (For example, refer to Patent Document 1).
Moreover, there existed some which reduced material by providing a recess in the intersection part of a wing | blade and a main plate, and aimed at cost reduction (for example, refer patent document 2).
In addition, the cross-sectional shape of multiple blades is a similar shape that gradually increases in thickness from the shroud to the main plate, and the adjacent distance of each blade is gradually narrowed from the shroud to the main plate, so that the blower outlet of the turbofan In some cases, a time difference is generated in the discharge vortex of the blown flow from the shroud to the main plate to prevent noise resonance and the like (for example, see Patent Document 3).
In addition, there are some blades that are hollow and have a large blade thickness to shorten the cooling and hardening time during molding, prevent deformation distortion during cooling and hardening, and reduce plastic materials (for example, Patent Document 4). reference).

Japanese Patent No. 3131625 (3rd, 4th page, FIG. 1, FIG. 3) Japanese Utility Model Publication No. 4-116698 (first page, FIG. 1) Japanese Patent No. 3544325 (7th to 9th pages, FIGS. 5 and 6) Japanese Utility Model Publication No. 4-116699 (first page, FIG. 1)

In the conventional turbofan according to Patent Document 1, ribs that improve the moldability by providing reinforcement for thinning the main plate and the runner of the resin are provided, but the resin that flows out from the ribs at the time of molding merges. The strength of the resin junction is weakened. That is, the resin joining portion is located at substantially the same distance from adjacent ribs, and the strength is weak at this portion. In this conventional apparatus, a blade front end rib that extends in the radial direction through the vicinity of the blade front end, a blade rear end rib that extends in the radial direction through the vicinity of the rear end of the blade, a blade front end rib, and a blade rear A connection rib for connecting the end ribs and a blade reinforcing rib are provided, and resin is injected into these ribs from one resin injection port.
When the resin injected from the resin injection port flows to each rib, the blade leading end rib and the blade trailing end rib flow in two directions in the radial direction on the rotation center side and the outer peripheral side, and the connecting rib has a radial component and a circumferential direction. The blade reinforcing rib flows in the direction opposite to the connecting rib. That is, the resin injected from one injection port flows through a plurality of ribs extending in the radial direction, and the resins flowing out from the ribs come into contact with each other to form a resin joining portion. Since the resin merging portion is also formed between the resin flowing out from the adjacent resin inlet, a large number of resin merging portions are formed in the entire turbofan, and there is a limit to improving the strength of the turbofan. Usually, a plurality of motor cooling holes are provided in the convex portion of the main plate near the rotating shaft. However, when the resin confluence portion passes through the motor cooling hole, which is an opening having a low strength, the strength is further increased. It will be lower. For example, if an impact in the direction parallel to the rotation axis is applied to the turbo fan during transportation, etc., cracks will occur in the motor cooling hole and the resin junction around it, and this low strength part is connected There was a problem that the cracks that occurred were spread. In addition, in this runner configuration, there is a part where the resin merge part extends to the outer peripheral edge of the fan, and cracks generated at the resin merge part easily extend to the outer peripheral edge and break, resulting in a problem that the product quality deteriorates. there were.

  Further, in the configuration shown in Patent Document 2 in which a recess is provided at the intersection of the blade and the main plate, a flow along the main plate surface is generated when the turbofan rotates, and the flow on the main plate surface is upstream of the recess. After leaving the corner R at the side end, it collided with the corner R at the downstream end, and abnormal noise was generated due to pressure fluctuation.

  Further, in the turbofan disclosed in Patent Document 3, since the blades are not hollow, and there are significant differences in thickness at each part of the blades, a temperature difference occurs at each part of the blades during molding. For this reason, there has been a problem that the occurrence of cavities or local thinning of the wall thickness (hereinafter referred to as sink) occurs due to unevenness of the hot water, and the moldability deteriorates. In addition, since the entire blade is formed of resin, a larger amount of resin is required as compared with a hollow blade, which increases the fan weight and cost. Furthermore, the air conditioner mounted becomes heavier along with this, and there is a problem that the transportability of workers is poor.

  The centrifugal fan described in Patent Document 4 is a hollow blade having a large blade thickness. However, if the blade thickness is too thick, the air passage area of the fan is reduced, so that noise may increase due to an increase in the passing wind speed. There is sex. In addition, the blade cross-sections perpendicular to the rotating shaft are all the same, there is no draft when the blade is pulled out from the mold during injection molding, and there is a possibility that the resin may come into the mold and break. there were.

This invention was made to solve the above problems, and by improving the moldability and strength of the turbofan molded with thermoplastic resin, it can prevent breakage during transportation, The purpose is to obtain a highly reliable turbo fan and an air conditioner equipped with the turbo fan.
It is another object of the present invention to provide a turbo fan capable of reducing noise and an air conditioner equipped with the turbo fan.

  A turbofan according to the present invention includes a disc-shaped main plate, a convex hub formed by projecting a central portion of the main plate in the direction of the rotation axis, and a base plate portion on the outer peripheral side of the main plate in the protruding direction of the hub. A plurality of wings standing upright, a plurality of wings provided on the hub, motor cooling holes for cooling a motor disposed in a convex space surrounded by the hub, and a thermoplastic resin radially provided in the hub and injecting thermoplastic resin during molding And a plurality of hub runners that form the hub, and a resin merging portion formed by contacting the thermoplastic resin that has flowed out of the adjacent runner for the hub during the molding, and the motor The cooling hole is arranged so as to avoid the resin joining portion.

  According to this invention, since the resin joining portion is not connected to the motor cooling hole, it is possible to prevent the fan from breaking against an impact. As a result, the strength can be improved, and a highly reliable turbofan can be obtained.

It is the top view (Drawing 1 (a)) which shows the turbo fan concerning Embodiment 1 of this invention, and the explanatory view (Drawing 1 (b)) seen from the side. It is a perspective view which shows the turbo fan which concerns on Embodiment 1 of this invention. It is explanatory drawing which shows the turbo fan which concerns on Embodiment 1 of this invention. It is explanatory drawing which expands and shows the turbo fan which concerns on Embodiment 1 of this invention. FIG. 5 is an explanatory diagram showing a cross section taken along line H1-H2 of FIG. 4 according to the first embodiment of the present invention. It is explanatory drawing which expands and shows the cross section in O-O1-O2-O3 of FIG.1 (b) regarding Embodiment 1 of this invention. 6 is a flowchart illustrating a fan forming process according to the first embodiment of the present invention. According to the first embodiment of the present invention, the molding time (from resin injection to cooling to removal) with respect to the ratio t1 / t0 between the maximum thickness t1 of the runner 9a for the hub and the minimum thickness t0 of the other part of the main plate 2 is determined. It is a graph which shows (time). According to the first embodiment of the present invention, the molding time (from resin injection to cooling to removal) with respect to the ratio t2 / t0 between the maximum wall thickness t2 of the blade runner 9b and the minimum wall thickness t0 of the other part of the main plate 2 is concerned. It is a graph which shows (time). It is explanatory drawing which shows the wing | blade which concerns on Embodiment 1 of this invention, the side surface (FIG. 10 (a)) which shows one wing | blade of a fan, and the cross section in the ZZ line of FIG. b)). It is explanatory drawing which shows the wing | blade which concerns on Embodiment 1 of this invention, and shows the longitudinal cross-section in the YY line of FIG.10 (b). The fan forming time (sec) and noise value (dB) when the standing surface of the outer side of the blade and the inner side of the wing are inclined to the inner side of the wing at the inclination angle θ with respect to the rotation axis and the inclination angle θ is changed are shown. It is a graph. It is a bottom view which shows the turbo fan which concerns on the turbo fan by Embodiment 1 of this invention, and was shape | molded by the other runner structure. It is a bottom view which shows the turbo fan by which it was related with the turbo fan by Embodiment 1 of this invention, and was shape | molded by still another runner structure. It is the perspective view which looked at the turbo fan of another structural example from the lower surface according to Embodiment 1 of this invention. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a partial perspective view showing an enlarged part of a turbofan according to Embodiment 1 of the present invention. It is explanatory drawing which shows the blade | wing which concerns on Embodiment 1 of this invention, and is the side surface (FIG. 17 (a)) which shows one blade of a fan, and the cross section in the ZZ line of FIG. b)). It is explanatory drawing which shows the wing | blade which concerns on Embodiment 1 of this invention, and expands the longitudinal cross-section (FIG. 18 (a)) and the part of FIG. 18 (a) in the YY line of FIG. It is explanatory drawing shown (FIG.18 (b)). It is explanatory drawing which concerns on Embodiment 1 of this invention and shows a part of lower surface of a turbofan. According to the first embodiment of the present invention, the ratio of the height difference Δt between the blade front runner 9ba and the blade rear runner 9bb to the maximum opening width diameter F of the hollow blade opening 3b and the noise at the same air flow It is the graph which showed the relationship of the value. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of an air conditioner viewed from an installed room according to Embodiment 1 of the present invention. 1 is a longitudinal sectional view showing an air conditioner according to Embodiment 1 of the present invention. 1 is a horizontal sectional view showing an air conditioner according to Embodiment 1 of the present invention.

Explanation of symbols

  1 turbo fan, 2 main plate, 2a hub, 2b fan inner peripheral side surface, 2c boss, 2d hub upper thick wall part, 3 blade, 5 motor cooling hole, 8 motor, 9 runner, 9a runner for hub, 9b blade Runway, 9ba Wing forward runner, 9bb Wing rear runner, 9c Connecting runner, 9d Cooling hole runner, 10 Resin inlet, 12 Air conditioner body, 15 Heat exchanger, A Resin junction, B Resin flow direction during molding, C airflow near blade opening, D fan rotation direction, E1, E2 airflow, F maximum opening width of blade opening 3b (diameter of inscribed circle of opening on main plate surface), G hub The airflow that is guided to the motor cooling hole by the runner, O rotation center.

Embodiment 1 FIG.
Hereinafter, a turbofan (hereinafter simply referred to as a fan) according to Embodiment 1 of the present invention will be described with reference to the drawings.
FIG. 1A is a plan view of the fan according to this embodiment as viewed from the shroud side, and shows a blade with a part of the shroud cut away. FIG. 1B is an explanatory diagram viewed from the side of FIG. 1A, where the left half is a side surface and the right half is a longitudinal section taken along O-O1-O2-O3 of FIG. Show. FIG. 2 is a perspective view of the fan according to this embodiment as viewed from the lower surface, that is, the side opposite to the shroud.

  As shown in FIGS. 1 and 2, the fan 1 is composed of a disk-shaped main plate 2, the central portion of the main plate 2 has a convex shape protruding in the direction of the rotation axis, and a motor ( (Not shown). This convex portion is referred to as a hub 2a. A boss 2c is formed at the center of the hub 2a, that is, at the center of the main plate 2, and the motor shaft is fixed to this portion. The portion where the motor is installed is referred to as the fan outer side of the main plate 2, and a plurality of, for example, seven blades 3 are provided on the outer peripheral side flat plate portion on the opposite side of the fan inside. The portion connected to the boss 2c of the main plate 2 is provided with a hub upper thick portion 2d in order to ensure strength, and is thicker than the thickness t0 of the inclined surface of the hub 2a.

  The wing 3 has a bag-like hollow shape in which the outer peripheral side flat plate portion of the main plate 2 is used as a base, and is erected in the protruding direction of the hub 2a from the wing opening 3b of the base. At the base, the blade opening 3b is located between the blade inner circumferential end 3a and the blade outer circumferential end 3c, and the center line 3a-3c of the blade opening 3b and the radius of the main plate 2 are at a predetermined angle, for example 45 It is arranged to intersect at an angle of about °. Then, as shown in FIG. 1A, the plurality of blades 3 are arranged such that the circumferential mounting pitch angles σ1, σ2, σ3,. In FIG. 1A, for example, σ1 = σ4 <σ3 = σ6 = σ7 <σ2 = σ5.

  The fan 1 is driven by a motor and rotates around the rotation center O in the direction of arrow D. The shroud 4 is provided on the outer periphery of the fan 1 as shown in FIG. 1 (b), and is fixed to each blade 3 from above in FIG. 1 (b).

  A fan internal air passage 6 is formed in the vicinity of the hub 2a between the shroud 4 and the main plate 2, and a fan external air passage 7 is formed in the hub 2a on the side where the motor is disposed. The hub 2a has a motor cooling hole 5 formed of a plurality of openings around the rotation center O at a position substantially equidistant from the rotation center O, and the fan internal air passage 6 and the fan external side air passage 7 communicate with each other. In FIG. 1A, for example, seven motor cooling holes 5 are provided, and each is arranged on a straight line O-3a connecting one blade inner circumferential end 3a and the rotation center O. Here, the circumferential mounting pitch angles γ 1, γ 2, γ 3,... Γ 7 of the plurality of motor cooling holes 5 are also formed to be at least partially different unequal pitches, similarly to the blade 3. Here, the circumferential mounting pitch angles γ1, γ2, γ3,... Γ7 of the motor cooling holes 5 are set to, for example, γ1 = γ4 <γ3 = γ6 = γ7 <γ2 = γ5, similarly to the circumferential mounting pitch angle σ of the blade 3. .

  The main plate 2 and the blades 3 are integrally formed of a thermoplastic resin (hereinafter simply referred to as resin) such as ABS or ASG. In FIG. 2, 10 is a mark of a resin injection port used for injecting resin when the main plate 2 and the blade 3 are molded, in the vicinity of a bent portion between the hub 2a and the flat portion of the main plate 2, and In the vicinity of the blade inner peripheral end 3a of the flat portion, it is referred to as a resin injection port 10 here. The fan is formed with a runner 9 that becomes a passage for resin during molding, and the mold has a space that is larger in the thickness direction than the main portion of the main plate 2 so that the resin can easily pass therethrough. In the finished fan, the resin in the runner 9 is solidified and remains thicker than the minimum thickness t0 of the main plate 2 other than the runner.

  One of the runners 9 is a hub runner 9a that forms a hub during molding. The hub runners 9a are provided, for example, in a radial manner on the hub 2a. The hub runners 9a extend from the resin injection port 10 toward the rotation center O and intersect with other runners in the fan radial direction to the vicinity of the motor cooling hole 5. It extends straight without doing. The hub runner 9a is made thicker than the minimum wall thickness t0 on the inclined surface of the hub 2a to a predetermined wall thickness t1 (> t0). Further, the motor cooling hole 5 is disposed in the vicinity of the fan center side end of the hub runner 9a, and the blade inner peripheral end 3a of the blade 3 is provided in the vicinity of the fan outer peripheral end of the other hub runner 9a. Is configured to be arranged. Further, the center line 11 in the width direction of the straight hub runner 9a is disposed so as to pass over the motor cooling hole 5, and the inner peripheral end 3a of the blade, the resin injection portion 10, the hub runner 9a, The motor cooling holes 5 are disposed so as to be positioned on substantially straight lines extending in the radial direction starting from the rotation center O. In this embodiment, since the mounting pitch angle σ in the circumferential direction of the blades 3 is an unequal pitch, the motor cooling hole 5, the hub runner 9a, and the resin injection port 10 are also unequal with respect to the rotation center O. Composed of pitch. When the mounting pitch angle σ of the blades 3 is equal, the circumferential mounting pitch angles of the motor cooling hole 5, the hub runner 9a, and the resin inlet 10 are also equal.

  Further, a blade runner 9b is formed around the blade opening 3b on the outer peripheral side flat plate portion of the main plate 2 which is the base of the hollow blade 3. The blade runner 9b is a runner that forms the blade 3 by injecting resin during molding. Like the hub runner 9a, the blade runner 9b is thicker than the wall thickness t0 of the outer peripheral side plate portion of the main plate 2, and has a predetermined thickness. The thickness is t2 (> t0). The connecting runner 9c is a runner that connects the hub runner 9a and the blade runner 9b. The connecting runner 9c has a wall thickness t1 similar to that of the hub runner 9a, for example, and is smaller than the hub runner 9a and the blade runner 9b.

  When the fan 1 rotates in the direction D, the surrounding air is guided to the blades 3 by the shroud 4 and sucked into the shroud 4, passes through the fan internal air passage 6, and as shown by the arrow E 1 in FIG. Blow out from between wings 3. At this time, the fan internal air passage 6 has a negative pressure compared to the fan external air passage 7 to which the motor is attached. Therefore, as shown in FIGS. 1B and 2, a part E2 of the flow blown out from the fan 1 passes through the motor cooling hole 5 communicating between the fan internal air passage 6 and the fan external air passage 7. It flows into the fan external air passage 7 while turning due to friction with the hub 2a. Then, the air flows through the motor cooling hole 5 to the negative pressure fan internal air passage 6. A motor is disposed on the fan external air passage 7 side surrounded by the hub 2a and is fixed to the fan 1 by a boss 2c. The motor is cooled by the airflow E2.

When the turbo fan having such a configuration is integrally formed of resin, resin is injected from a plurality of resin injection ports 10 into a mold having a fan-shaped space. The resin injected from the resin injection port 10 is guided to the runner 9 which is a thick part and flows to the entire fan, so that the main plate 2 and the blade 3 are integrally formed. FIG. 3 is an explanatory view of the fan as seen from below. The hub runner 9a is a runner provided between the central end 9a1 and the fan outer peripheral end 9a2. The motor cooling hole 5 is disposed in the vicinity of the fan central end 9a1, and the blade inner peripheral end. The portion 3a is disposed in the vicinity of the fan outer peripheral side end portion 9a2.
Part of the resin flows through the hub runner 9a and then flows to the hub 2a of the main plate to form this part. The other part flows from the connecting runner 9c to the blade runner 9b, and then flows to the blade 3 and the main plate 2 around the blade 3 to form this portion. The flow of the resin at this time is shown by an arrow B in FIG. The resin flows into the mold as indicated by arrow B through each runner 9, and the resin that has flowed out from the adjacent runners 9 abuts at the resin junction at an approximately equal distance from the runner 9. This resin joining portion is indicated by a dotted line A.

The resin injected from the resin injection port 10 and guided to the hub runner 9a smoothly flows in one direction toward the rotation center O in the radial direction. Further, the resin flowing through the hub runner 9a flows toward the adjacent hub runner 9a, and a resin junction A is formed between the adjacent hub runners 9a. Since the motor cooling hole 5 is arranged so as to avoid the resin merging portion A, the resin merging portion A formed in the vicinity of the motor cooling hole 5 is not formed by being connected to the motor cooling hole 5, but is adjacent. It is formed between the motor cooling holes 5.
Since the resin merging portion A is not connected to the motor cooling hole 5 which is an opening having low strength against impact, it is possible to prevent a crack connected to the motor cooling hole 5 and the resin merging portion A, and the molded fan 1 The strength of can be improved. Therefore, even if an impact is applied in the direction of the rotation axis of the fan 1 during transportation, for example, in the vertical direction of FIG. 1B and a crack is generated around the motor cooling hole 5, the generated crack is the diameter of the main plate 2. It can be prevented from extending in the direction. As a result, the fan 1 can be prevented from being broken, and the reliability of the fan 1 against the impact can be improved.
In particular, in this embodiment, by providing the motor cooling hole 5 on the extension line of the hub runner 9a, it is possible to reliably prevent the resin junction A from being formed near the motor cooling hole 5.

  In addition, the runner 9 is not configured to branch in a complicated manner, but is branched in two directions of the hub runner 9a and the connecting runner 9c at the resin inlet 10, and at the connection portion between the runner 9c and the blade runner 9b. It branches to the two-way wing runner 9b. As described above, since the strength at the resin joining portion A is weak, it is preferable to reduce the number and length of the resin joining portions A to be formed as much as possible. In the configuration of the runner 9 according to this embodiment, the resin merging portion A is not formed by the resins injected from one resin injection port 10, and abuts on the resin injected from the adjacent resin injection port 10. The resin joining portion A is formed at the portion. For this reason, the number of the resin joining part A can be decreased as a whole. In this manner, the runner 9 is relatively simple, and the resin can easily flow along the runner 9, reducing the occurrence of sink marks and improving moldability.

  Furthermore, in the fan according to this embodiment, as shown by the dotted line, the resin joining portion A has one end abutting against the boss 2c, extending between the adjacent motor cooling holes 5 in the radial direction, and the other end being a blade. 3 is in contact with the center. In the configuration in which the resin joining portion A extends as it is to the outer peripheral end as in the conventional case, when a crack occurs along the resin joining portion A, the crack may extend to the outer peripheral end of the fan 1 and may be divided and cut. . On the other hand, in this embodiment, the outer peripheral side end portion of the resin joining portion A formed on the main plate 2 is configured to abut on the blade runner 9b. For this reason, the resin joining part A formed in the main plate 2 can be shortened, and the weak portion can be shortened, whereby the fan 1 having high strength and reliability can be obtained. Further, even when a crack is generated in the vicinity of the resin confluence portion A during transportation and the crack expands along the resin confluence portion A, the outer peripheral side end of the resin confluence portion A is thick. Since it is in contact with the road 9b, the crack stops at this portion. Further, when the crack does not stop in the blade runner 9b, the entire blade 3 connected to the blade runner 9b and having a height in the axial direction becomes a strength member. For this reason, it is possible to prevent the fan 1 from being completely divided and cut, and to improve the reliability with respect to impact.

The configuration of the resin junction A and the runway 9 will be described in more detail below. The angle of the blade 3 with respect to the number, shape and radius, the shape and configuration of the runner 9, the position of the resin inlet 10, the shape and position of the motor cooling hole 5, etc. If it is configured to abut against 2c, extend radially between adjacent motor cooling holes 5, and abut the other end to the center of blade 3, fan 1 having high reliability against impact can be obtained. .
4 is an explanatory view showing a part of FIG. 3 in an enlarged manner, and FIG. 5 is an explanatory view showing a cross-sectional view taken along line H1-H2 of FIG. The resin injection port 10 is provided, for example, at a position near the connecting runner 9c of the hub runner 9a. Here, for example, two adjacent resin injection ports 10m and 10n will be described. The resin injection port 10m is connected to a hub runner 9am, a blade runner 9bm, and a connecting runner 9cm, from which resin is injected to mold the blade 3m and the main plate 2 around it. On the other hand, the resin injection port 10n is connected to the hub runner 9an, the blade runner 9bn, and the connecting runner 9cn, and resin is injected therefrom to form the blade 3n and the main plate 2 around this. The thickness of the wing 3 standing on the main plate 2 is set to a predetermined thickness t3 (> t0), and the entire wing 3 is substantially uniform.

  When the blade 3m is positioned in front of the blade 3n in the fan rotation direction (arrow D direction), in order to prevent the resin joining portion A formed between the two blades 3m and 3n from being connected to the fan outer peripheral end, What is necessary is just to comprise so that resin which forms the part of the area | region L may be shape | molded with the resin inject | poured from the resin injection port 10n. In particular, if the resin forming the vicinity of the flat plate portion 3 cmt at the blade outer peripheral side end of the blade 3 m is not the resin injected at the resin injection port 10 m but the resin injected at the resin injection port 10 n, the hub runner 9an, The resin joining portion A formed between 9 am surely contacts the blade 3m. For this purpose, the length of the resin flow path flowing to the flat plate portion 3 cmt at the blade outer peripheral end is such that the distance from the resin injection port 10 n is shorter than the distance from the resin injection port 10 m. A road 9 may be configured.

  Specifically, the number and shape of the blades 3, the shape and configuration of the runner 9, the position of the resin injection port 10, the shape and position of the motor cooling hole 5, the resin injection speed, etc. are set and simulated, for example, It is possible to examine which part of the fan the resin joining part A is formed when molding. If the resin joining portion A obtained by the simulation is configured so that one end contacts the boss 2c, passes through the hub 2a between the adjacent motor cooling holes 5, and the other end contacts the blade runner 9b. Good.

  As described above, the disc-shaped main plate 2, the convex hub 2 a formed by projecting the central portion of the main plate 2 in the direction of the rotation axis, and the outer peripheral side flat plate portion of the main plate 2 as the base stand in the protruding direction of the hub 2 a. A plurality of blades 3 to be provided, a plurality of blades 3 provided in the hub 2a, motor cooling holes 5 for cooling a motor disposed in a convex space surrounded by the hub 2a, and a radially provided hole in the hub 2a for injecting resin during molding Thus, the motor cooling hole 5 is provided with a plurality of hub runners 9a forming the hub 2a and a resin joining portion A formed by abutting the resin flowing out from the adjacent hub runner 9a during molding. By arranging so as to avoid the resin joining portion A, there is an effect that a turbo fan having high reliability with respect to impact can be obtained.

  The plurality of motor cooling holes 5 provided in the hub 2a are disposed in a portion where the runner 9a for the hub is extended to the rotation center O side, so that the motor cooling hole 5 and the resin joining portion A having low strength against impact are provided. And a fan with high reliability against impact can be obtained.

  In addition, since the hub runner 9a is formed linearly around the rotation center O, the resin can easily flow to the boss 2c around the rotation center, and the moldability can be improved.

Further, the runner 9 serving as a resin passage is formed by separating the runner 9a for the hub and the runner 9b for the blade, and a connecting runner 9c for connecting the runners 9a, 9b is provided. , 9b, 9c, the resin is injected from the resin injection port 10 provided at any one position. That is, at least one of the resins flowing into the hub runner 9a and the blade runner 9b flows through the connecting runner 9c. For this reason, the balance between the amount of resin flowing in the hub runner 9a and the amount of resin flowing in the blade runner 9b can be adjusted according to the setting of the width and thickness of the connecting runner 9c. By properly adjusting the injection amount of the resin flowing into the hub runner 9a and the blade runner 9b, it is possible to prevent the occurrence of cavities and local thinning of the wall thickness due to unevenness of the hot water runoff, and to prevent deterioration in strength. .
In this embodiment, the resin inlet 10 is directly provided in the hub runner 9a. However, the resin inlet 10 may be provided in the blade runner 9b. Moreover, you may provide in the connection runway 9c. When the resin inlet 10 is provided in the connecting runner 9c, the thickness and width of the runner between the resin inlet 10 and the hub runner 9a, and the gap between the resin inlet 10 and the blade runner 9b. The balance of the amount of resin can be adjusted by making a difference according to the flow rate of the resin that requires the thickness and width of the runner.

  Further, since the blade 3 has a hollow shape and the blade runner 9b is provided around the opening 3b, the weight can be reduced by the hollow shape, and the resin can easily flow around the entire mold when the blade 3 is molded. Thinning of the wing 3 is also possible, further reducing the weight. The weight reduction reduces the weight at the outer periphery of the fan 1 relative to the rotation center of the fan 1, so that the centrifugal force during rotation is reduced and the stress applied to the base of the main plate that is the base of the blade 3 is reduced. As a result, the strength of the fan 1 can be improved and damage during rotation can be prevented. Further, since the portion of the blade runner 9b remains as a resin in the molded body, the thickness of the joint portion between the blade 3 and the main plate 2 where stress concentrates can be increased by the blade runner 9b. In this manner, the resin fluidity can be improved by the blade runner 9b to improve the moldability, and the strength of the turbofan can be improved.

Further, as described above, a plurality of radials are provided in the hub 2a, and are provided around the bases of the hub runners 9a for forming the hub 2a by flowing in the resin at the time of molding and the wings 3, and the resin at the time of molding. The runner 9b includes a runner 9b for forming a blade 3 by flowing in, and a connecting runner 9c for connecting each of the runners 9a for a hub and the runner 9b for a blade located in the vicinity thereof. Is formed by being connected from the rotation center side to the outer periphery of the main plate 2 in the radial direction. For this reason, in the main flow direction of the resin injected from the resin injection port 10, the resin flows toward the rotation center and the resin toward the outer peripheral side, and then flows through the runner 9 without flowing in the opposite direction. It flows to the surrounding main plate 2.
Thus, since the flow direction of resin becomes comparatively simple, the part where the resin confluence | merging part A is formed can be estimated clearly. In addition, there is an effect that the resin can flow smoothly, the moldability can be improved, and the highly reliable fan 1 can be obtained. Furthermore, the distance of the resin joining part A can be shortened and the strength deterioration of the turbofan can be prevented.

  In addition, as compared with the configuration in which the resin merge portion is formed by the resin injected from one resin injection port as in the prior art, in this embodiment, the number of the resin merge portions A can be reduced and the mold design can be simplified. It is possible to prevent the generation of cavities and local thinning of the wall thickness due to unevenness in the hot water.

  FIG. 6 is an explanatory view showing a part of FIG. As shown in the figure, in the fan according to this embodiment, the hub runner 9a having the wall thickness t1 is provided on the wall surface constituting the hub 2a of the fan external air passage 7 from the hub 2a having the wall thickness t0. It projects by a thickness difference (t1-t0) toward the fan external air passage 7 side. And the motor cooling hole 5 is arrange | positioned on the extension line | wire by the side of the rotation center of the runner 9a for hubs. For this reason, the runner 9a for the hub functions as an air guide plate and induces an airflow G toward the motor cooling hole 5. Since the hub runner 9a serves as a wind guide plate for the airflow G, the airflow flowing on the surface of the motor disposed in the portion surrounded by the hub 2a is increased and the cooling of the motor is promoted. Normally, temperature protection control is performed to stop energization of the motor when the temperature rises above a certain temperature with respect to the temperature rise of the motor. However, by promoting motor cooling, the temperature protection control is efficiently executed. I can drive. Further, the motor can be prevented from being damaged due to the high temperature of the motor.

  Thus, the runner 9a for the hub protrudes from the surface of the main plate 2 of the hub 2a to the fan external air passage 7 side which is the motor arrangement side, thereby increasing the air flow flowing on the surface of the motor. Cooling can be promoted, and a highly reliable turbo fan can be obtained.

Further, the fan according to this embodiment is configured such that a set including the blade 3, the blade runner 9b, the hub runner 9a, the connecting runner 9c, and the motor cooling hole 5 is radially formed around the rotation axis O. Several sets are provided. That is, the arrangement of the resin inlet 10, the runner 9 a for the hub, the runner 9 b for the blade, the connecting runner 9 c, and the motor cooling hole 5 with respect to one blade 3 is provided in all the blades 3 constituting the fan 1. It is almost equivalent. Therefore, if substantially the same amount of resin is injected from the plurality of resin injection ports 10, the resin flows in the same direction throughout the disk-shaped fan 1 and can be molded under the same molding conditions. For this reason, the fan completed by molding can prevent the occurrence of cavities and local thinning of the wall thickness due to unevenness of hot water as a whole, and has an effect of obtaining a highly reliable turbo fan.
Further, for example, by changing the circumferential pitch, the amount of resin required for each set constituted by the blade 3, the blade runner 9b, the hub runner 9a, the connecting runner 9c, and the motor cooling hole 5 is reduced. If they are different, if the amount of resin injected from the resin injection port 10 is changed according to the amount, it can be molded under the same molding conditions, and the same effect as described above can be obtained.

Further, by providing the same number of motor cooling holes 5 and hub runners 9 a, the positional relationship of the blades 3 with respect to the motor cooling holes 5 can be made substantially the same as that of the motor cooling holes 5 constituting the fan 1. For this reason, the turbulent flow E2 flowing out from the fan external air passage 7 to the fan internal air passage 6 through the motor cooling hole 5 is connected to the hub runner 9a closest to the motor cooling hole 5. It flows behind the wing 3 formed by the road 9b. In other words, each of the turbulent flows E2 flowing out from the motor cooling hole 5 flows between the blades 3 and 3 and does not directly collide with each other. A fan is obtained.
Although the same number of motor cooling holes 5 and hub runners 9a are provided here, the number of motor cooling holes 5 may be smaller than that of hub runners 9a. For example, the motor cooling holes 5 may not be provided on the rotation center O side of all the hub runners 9a. By providing the motor cooling hole 5 at a position that avoids the resin joining portion A of the hub 2a and at an equal position with respect to the rotation center O, it is highly reliable in strength and can be molded under uniform molding conditions to some extent. As a whole, it is possible to obtain a turbofan capable of preventing the occurrence of cavities due to unevenness of hot water and local thinning of the wall thickness. Of course, by providing the same number of motor cooling holes 5 and runners 9a for the hub, a highly reliable turbo fan can be obtained because molding can be performed under even molding conditions.

  Further, as shown in FIG. 1, the shape of the fan is a group composed of the blade 3, the blade runner 9b, the hub runner 9a, the connecting runner 9c, and the motor cooling hole 5, with the rotation axis O as the center. A plurality of sets are provided radially, and at least one of the angles formed by the adjacent sets is configured to be different from the other angles. This prevents the turbulence E2 discharged to the outside from the motor cooling hole 5 and the flow E1 blown from the blade 3 from having periodicity. For this reason, noise caused by the rotational speed of the fan can be prevented, and quietness is maintained in terms of hearing.

Thus, by providing a plurality of sets each including the blade 3, the blade runner 9 b, the hub runner 9 a, the connecting runner 9 c, and the motor cooling hole 5 radially about the rotation axis, one blade 3, the resin injection port 10, the runner 9 a for hub, the runner 9 b for blades, and the motor cooling hole 5 are almost the same, so that the molding conditions can be made equivalent, and the occurrence of cavities and meat due to unevenness in the runner It is possible to prevent the thickness from being thinned locally, and to obtain a turbo fan with high strength and reliability.
Further, in the group constituted by the blade 3, the blade runner 9 b, the hub runner 9 a, the connecting runner 9 c, and the motor cooling hole 5, at least one of the angles formed by adjacent groups is set as another angle. By configuring differently, an effect of reducing noise can be obtained.

  If the same number of motor cooling holes 5 as the runners 9a for the hub are provided, the arrangement relationship between the motor cooling holes 5 and the blades 3 can be made equal, and the motor cooling holes from the fan external air passage 7 to the fan internal air passage 6 can be obtained. The flow E2 flowing out through 5 can smoothly flow between the blades to the outside, noise can be reduced, and the moldability is good.

  Here, the fan forming step will be described with reference to FIG. FIG. 7 is a flowchart showing a fan molding process. A molding die for molding the fan 1 having the shape shown in FIGS. 1 to 6 is fixed (ST1), and a thermoplastic resin is injected from the resin injection port 10 (ST2). The injected resin flows through the hub runner 9 a, the connecting runner 9 c, and the blade runner 9 b, and further flows from the runner 9 to the main plate 2 and the blade 3. The resin fills the entire fan in approximately several milliseconds. Next, the thermoplastic resin is cured by cooling (ST3), and after completely cured, the fan 1 molded by mold release is taken out (ST4). Thereafter, the shroud 4 is fixed to the suction side of the fan 1 (ST5). Furthermore, it progresses to processes, such as attaching the shaft of a motor after this.

Next, the thickness of each part of the resin constituting the fan 1 will be described.
As shown in FIGS. 5 and 6, the minimum thickness of the portion excluding the runner 9 of the main plate 2 is t0, the thickness of the hub runner 9a is t1, and the blade formed around the hollow blade opening 3b. The wall thickness of the runner 9b is t2, and the wall thickness of the hollow blade 3 is t3. At least the thicknesses t1, t2, and t3 are made thicker than the thickness t0. The runner 9 may have a shape with an error at the time of molding or a corner portion having R, but the portion with the largest wall thickness is the thickness of the runner 9. The thickness of the runner 9 is a portion including the thickness of the main plate 2 and a portion protruding from the main plate surface as shown in the figure.
FIG. 8 is a graph showing the molding time with respect to the ratio t1 / t0 of the thickness t1 of the hub runner 9a and the minimum thickness t0 of the main plate 2 other than the runner, where the horizontal axis is t1 / t0 and the vertical axis is The molding time (sec) is shown. Here, the formation time indicates the time taken from ST2 to ST4 in the flowchart shown in FIG. 7, and is the time from resin injection to cooling to removal.

  As shown in the graph of FIG. 8, when t1 / t0 is 1.0 or less, that is, the thickness t1 of the hub runner 9a is equal to or less than the minimum thickness t0 of the portion other than the runner of the main plate 2, The runner 9a is thinner and the resin is less rotated, and it takes time for the resin to travel to the entire mold, and the molding time increases. When t1 / t0 is greater than 2.0, that is, when the thickness t1 of the hub runner 9a is greater than twice the minimum thickness t0 of the portion other than the runner of the main plate 2, the resin cooling is performed. It takes time to take out and the time to take out becomes long. As a result, in the range of 1.1 ≦ t1 / t0 ≦ 2, the molding time can be shortened compared to at least the same thickness (t1 / t0 = 1.0). By shortening the molding time, the production amount can be increased, and further, the electricity cost required by the molding machine can be reduced, and energy saving can be achieved.

FIG. 9 is a graph showing the molding time with respect to the ratio t2 / t0 of the wall thickness t2 of the blade runner 9b and the minimum thickness t0 of the portion other than the runner of the main plate 2, where the horizontal axis is t2 / t0 and the vertical axis is The molding time (sec) is shown. Here, the formation time indicates the time taken from ST2 to ST4 in the flowchart shown in FIG. 7, and is the time from resin injection to cooling to removal.
As shown in the graph of FIG. 9, when t2 / t0 is 1.0 or less, that is, when the thickness t2 of the blade runner 9b is equal to or less than the minimum thickness t0 of the portion other than the runner of the main plate 2, The runner 9b is thinner and the resin does not rotate well, and it takes time for the resin to travel to the entire mold, and the molding time increases. When t2 / t0 is larger than 2.0, that is, when the thickness t2 of the blade runner 9b is larger than twice the minimum thickness t0 of the portion other than the runner of the main plate 2, the cooling of the resin is performed. Takes a long time and takes a long time to take out. As a result, in the range of 1.1 ≦ t2 / t0 ≦ 2, the molding time can be shortened compared to at least the same thickness (t2 / t0 = 1.0). By shortening the molding time, the production amount can be increased, and further, the electricity cost required by the molding machine can be reduced, and energy saving can be achieved.

Therefore, if the ratio t1 / t0 between the thickness t1 of the hub runner 9a and the minimum thickness t0 of the portion excluding the runner 9 of the main plate 2 is in the range of 1.1 ≦ t1 / t0 ≦ 2, the same thickness Compared to the case where the thickness (t1 / t0 = 1) is used, the molding time can be shortened. Further, if the ratio t2 / t0 between the wall thickness t2 of the wing runner 9b and the minimum thickness t0 of the main plate 2 excluding the runner 9 is in the range of 1.1 ≦ t2 / t0 ≦ 2, the same thickness Compared to the case where the thickness (t2 / t0 = 1) is used, the molding time can be shortened. In particular, by setting the thicknesses t1 and t2 of the runner 9 to be not more than twice the minimum thickness t0 of the main plate 2 and providing an upper limit on the thickness of the runner 9, the molding time can be shortened and the amount of resin can be reduced. The fan 1 can be reduced in weight and cost.
Here, the thickness t1 of the hub runner 9a and the thickness t2 of the blade runner 9b are separately described. However, either one may be configured to satisfy either, or both may be satisfied. Good. If both are satisfied, the molding time can be shortened and it is effective.

  Thus, t is the thickness of at least one of the thickness of the runner 9a for the hub and the thickness of the runner 9b for the blades, and the minimum thickness of the portion excluding the runner 9 of the main plate 2 is t0. When the ratio t / t0 is in the range of 1.1 ≦ t / t0 ≦ 2, there is an effect that the molding time can be shortened as compared with the case where the ratio is configured with the same thickness (t / t0 = 1).

Hereinafter, the shape of the blade 3 will be described.
The configuration of one blade 3 is shown in FIGS. FIG.10 and FIG.11 is explanatory drawing which shows the wing | blade 3 which concerns on this embodiment, FIG.10 (a) is the side surface of one wing | blade, FIG.10 (b) is in the ZZ line of Fig.10 (a). A cross section is shown, and FIG. 11 shows the vertical cross section in the YY line of FIG.10 (b).
As shown in FIG. 10A, the blade inner peripheral hollow portion 3dc and the blade outer peripheral hollow portion 3dd of the blade hollow portion 3d are provided on the main plate 2 at arbitrary angles θ1 and θ2 with respect to the straight line X parallel to the rotation axis. The blade opening 3b is used as a base and is inclined inward toward the blade suction side end 3e toward the inside of the hollow shape. Since the thickness of the blade 3 is substantially uniform, the blade inner circumferential end 3a and the blade outer circumferential end 3c are also sucked from the blade opening 3b at arbitrary angles θ1 and θ2 with respect to the straight line X parallel to the rotation axis. It inclines inside the hollow shape toward the side end 3e.
Further, as shown in FIG. 11, the blade front hollow portion 3da and the blade rear hollow portion 3db on the side opposite to the rotation direction of the blade 3 are at an arbitrary angle with respect to the straight line X parallel to the rotation axis. It is the structure which inclines inside hollow shape toward the blade | wing suction side edge part 3e from the blade opening part 3b by (theta) 3 and (theta) 4. Since the thickness of the blade 3 is substantially uniform, the blade front side portion 3f and the blade rear side portion 3g are also at arbitrary angles θ3 and θ4 with respect to the straight line X parallel to the rotation axis from the blade opening 3b to the blade suction side end portion. It inclines inside hollow shape toward 3e.

That is, the blade 3 and the blade hollow portion 3d are formed in a tapered shape having a gradient inclined toward the hollow inside at a predetermined angle θ1, θ2, θ3, θ4 from the main plate 2 toward the shroud 4. For this reason, when the mold is removed from the fan molded body in the direction of the rotation axis, the resin and the mold can be smoothly released by the inclination, and the blade 3 adheres to the mold and the blade 3 is damaged. Can be prevented, and moldability can be improved. At the end of the cooling and curing of the resin, the mold is in close contact with the fan molded body at the standing surfaces 3a, 3c, 3f, and 3g on the outer side of the hollow blade 3, and the standing surfaces 3dc, 3dd, and 3da on the hollow side. It is in close contact with the fan molded body at 3 db. Here, both of the standing surfaces on the outer side and the hollow side are tapered from the base toward the standing direction. For this reason, it can be easily released from the outside of the blade 3 and can be easily released from the inside of the hollow of the blade 3.
In addition, since the blade 3 has a hollow shape, the weight can be reduced as compared with a hollow shape. Further, when the thickness of the blade 3 is uneven, there is a problem that molding failure due to uneven cooling and hardening time of the resin occurs and the moldability is poor, but the thickness of the blade 3 is made substantially uniform. The cooling and curing time of the resin can be made almost uniform, molding defects can be prevented, and moldability can be improved.

In this way, the disc-shaped main plate 2, the convex hub 2a formed by projecting the central portion of the main plate 2 in the direction of the rotation axis, and the outer peripheral side flat plate portion of the main plate 2 as the base portion are erected in the projecting direction of the hub 2a. A plurality of hollow wings 3 having openings 3b at the base, and outer standing surfaces 3a, 3g, 3c, 3f and hollow inner standing surfaces 3da, 3db, 3dc of the hollow wing 3 3dd is inclined to the inside of the hollow, and the outer side and the inner side of the blade 3 are tapered from the base so that the molding die can be easily released, and damage to the blade 3 due to the attachment of the blade 3 to the molding die. Can be prevented.
Furthermore, by making the thickness of the blades 3 substantially uniform, the cooling and hardening time of the resin can be made uniform, and a turbofan with good moldability can be obtained.
Furthermore, since the blade 3 has a hollow shape, the entire fan 1 can be reduced in weight.

  FIG. 12 shows an angle θ1 with respect to the rotation axis of the blade inner circumferential end 3a, an angle θ2 with respect to the rotation axis of the blade outer circumferential end 3c, an inclination angle θ3 with respect to the rotation axis of the blade blade front hollow portion 3da, and the blade rear hollow 6 is a graph showing the fan forming time (sec) and noise value (dB) when the inclination angle θ is changed by inclining all the inclination angles θ4 with respect to the rotation axis of the part 3db, and the horizontal axis Represents the tilt angle θ, and the vertical axis represents the molding time (sec) and the noise value (dB). This noise value (dB) was measured at a point 2 m below the fan. Further, the molding time is ST2 to ST4 in the flowchart showing the molding process shown in FIG.

The molding time will be described based on the graph shown in FIG.
In the case of the inclination angle θ <0 °, the blade 3 has a shape that expands from the main plate 2 side toward the shroud 4 side. When θ = 0 °, that is, when it is not inclined with respect to the rotation axis, the friction between the blade 3 and the mold is large, and if the mold is not released slowly, the blade 3 adheres to the mold and breaks. Therefore, a long molding time is required. On the other hand, by providing the inclination angle θ, it is easy to release the mold, and the release time can be shortened. Further, since the surface area of the blade 3 is increased and the cooling area is increased, the cooling time is shortened. For this reason, forming time can be shortened by giving inclination-angle (theta). If the inclination angle θ is 1 °, the molding time is about ½ compared to the case of the inclination angle 0 °. Therefore, if the inclination angle θ is at least 1 ° or more, the molding time is shortened and the moldability is high.

Next, a noise value is demonstrated based on the graph shown in FIG.
In the relationship between the inclination angle θ and the noise value, if the inclination angle θ is too large, the flow path between the adjacent blades 3 and the blades 3 becomes narrow, and the passing wind speed increases, resulting in an increase in noise. According to the measurement result of FIG. 12, when the tilt angle θ is tilted larger than 3 °, the noise is increased. For this reason, if the inclination angle θ is configured in the range of 1 ° ≦ θ ≦ 3 °, a good noise value can be maintained.
From the above results, by setting the inclination angle θ in the range of 1 ° ≦ θ ≦ 3 °, a turbo fan with small noise change and high moldability can be obtained.

  In this way, the outer standing surfaces 3a, 3g, 3c, and 3f and the hollow inner standing surfaces 3da, 3db, 3dc, and 3dd of the hollow wing 3 are inclined toward the hollow inner side, and predetermined inclination angles θ are respectively set. Is in the range of 1 ° ≦ θ ≦ 3 °, there is an effect of obtaining a turbo fan with small noise change and high moldability.

Here, all of the blade inner peripheral hollow portion 3dc, the blade outer peripheral hollow portion 3dd, the blade front hollow portion 3da, and the blade rear hollow portion 3db are inclined inwardly at the same inclination angle θ with respect to the rotation axis. However, the same effect can be obtained even if each is inclined at a different angle.
Further, the thicknesses of the blade inner peripheral side end 3a, the blade outer peripheral side end 3c, the blade suction side end 3e, the front blade front side portion 3f, and the rear blade rear side portion 3g with respect to the rotation direction of the blade are as follows: Although the thickness of the blade 3 is almost uniform, it is not limited to this, and may be slightly different depending on a molding error. In the blade inner peripheral end 3a and the blade outer peripheral end 3c, the width in the rotational direction is small, and it is difficult to configure the same thickness in this portion. What is necessary is just to make the thickness of the wing | blade 3 substantially uniform in the range which has a certain amount of fluctuation | variation. By configuring the wall thickness uniformly, the resin is uniformly injected and cooled uniformly, so that a good molded body can be obtained.

  Further, in this embodiment, the central portion of the wing 3 is erected vertically from the base portion of the main plate 2 in the protruding direction of the hub 2a, and the erected surfaces of the wing 3 and the hollow inner side are inclined toward the hollow inner side. Thus, the effects as described above are obtained. In this configuration, the mold is released by separating in the direction of the rotation axis and parallel to the rotation axis. On the other hand, for example, the mold may be configured to be released by rotating in the direction of the rotation axis and releasing it while rotating a little around the rotation axis. In the case of rotating and separating, the central part of the blade 3 is not configured to stand vertically from the base part of the main plate 2 in the protruding direction of the hub 2a, but the central part of the blade 3 is from the base part of the main plate 2 to the blade suction side. The shape is inclined at a predetermined angle in the rotational release direction toward the end 3e. Even in the case where the blade 3 is inclined as described above, it is possible to easily release the mold by inclining the standing surface on the outer side and the hollow inner side of the blade 3 toward the hollow inner side, and the same effect as described above can be obtained.

Next, the turbo fan 1 formed with the runway 9 as another configuration will be described. FIG. 13 is a bottom view showing a turbofan 1 molded with another runner configuration. In the figure, the same reference numerals as those in FIG. 3 denote the same or corresponding parts.
In the figure, a cooling hole runner 9d formed so as to surround the motor cooling hole 5 is provided, and the cooling hole runner 9d and the hub runner 9a are connected to form an integrated runner. ing.

In the turbofan configured as described above, a part of the resin injected from the resin injection port 10 during molding flows from the hub runner 9a toward the cooling hole runner 9d, and further to the hub 2a and the boss 2c. It flows toward. At this time, the resin flowing through the hub runner 9 a is divided into two directions by the cooling hole runner 9 d and flows through the cooling hole runner 9 d provided around the motor cooling hole 5. Then, after flowing around the motor cooling hole 5, that is, at the boss 2 c side of the motor cooling hole 5, it reliably rejoins and flows toward the boss 2 c. Thus, by providing the cooling hole runner 9d, the moldability can be improved by improving the resin fluidity around the motor cooling hole 5.
Further, by providing the cooling hole runner 9d on the outer periphery of the motor cooling hole 5, the cooling hole runner 9d remains solid around the motor cooling hole 5 which is an opening, and is configured to be thick. Therefore, it is possible to improve the strength around the motor cooling hole 5 where the strength is likely to decrease at the opening, and a turbofan having durability against breakage can be obtained even when an impact is applied.

FIG. 14 is a bottom view showing a turbofan 1 molded with still another runner configuration. In the figure, the same reference numerals as those in FIG. 3 denote the same or corresponding parts.
In the figure, the straight hub runner 9a is connected to the cooling hole runner 9d around the motor cooling hole 5 and further connected to the hub upper thick portion 2d. The rotation center side of the motor cooling hole 5 is a hub upper thick portion 2d, which is a portion thicker than the main portion of the main plate 2 other than the runner.

  In the turbofan configured as described above, a part of the resin flowing from the resin inlet 10 at the time of molding flows from the hub runner 9a toward the cooling hole runner 9d, and further passes through the hub upper thick portion 2d. Flow to form this part. Similar to the configuration shown in FIG. 13, the resin flowing through the hub runner 9 a is divided into two directions by the cooling hole runner 9 d and flows through the cooling hole runner 9 d provided around the motor cooling hole 5. Then, after flowing around the motor cooling hole 5, it flows toward the hub upper thick portion 2d connected to the motor cooling hole 5, and this portion is molded.

As in the configuration of FIG. 13, by providing the cooling hole runner 9d on the outer periphery of the motor cooling hole 5, the cooling hole runner 9d remains solid around the motor cooling hole 5 which is an opening, and the wall thickness is increased. Thus, the strength around the motor cooling hole 5 can be improved. Thus, by providing the cooling hole runner 9d, it is possible to improve moldability and strength by improving the resin fluidity around the motor cooling hole 5, and it is durable against breakage even when an impact is applied. A turbofan having characteristics can be obtained.
Further, in this configuration, the cooling hole runner 9d is directly connected to the hub upper thick portion 2d in the vicinity of the boss that is thicker than the thickness of the hub inclined surface. For this reason, the resin flows smoothly to the hub upper thick portion 2d, and the resin flowing through the cooling hole runner 9d is more reliably forward of the motor cooling hole 5 in the resin flow direction, that is, on the boss 2c side of the motor cooling hole 5. It rejoins and flows to the hub upper thick part 2d. Accordingly, the resin can be reliably injected around the motor cooling hole 5 that is the opening with the thickness of the cooling hole runner 9d, and the strength around the motor cooling hole 5 where the strength is likely to decrease at the opening can be improved.

  Thus, by providing the cooling hole runner 9d connected to the hub runner 9a and surrounding the motor cooling hole 5, the resin fluidity around the motor cooling hole 5 is improved. A turbofan that can improve moldability and strength can be obtained.

  Next, the wing runner 9b will be described in detail. FIG. 15 is a perspective view of a turbo fan according to another configuration example as seen from below, FIG. 16 is a partial perspective view showing a part of FIG. 15 in an enlarged manner, and FIGS. FIG. 17A shows a side surface of the blade 3, and FIG. 17B shows a cross section taken along the line ZZ of FIG. 17A. FIG. 18A shows a cross section taken along line YY of FIG. 17B, and FIG. 18B shows an enlarged portion of a circle M in FIG. FIG. 19 is an explanatory view showing a part of the lower surface of the turbofan 1.

The configuration of the turbofan shown here shows another configuration example related to the blade runner 9b provided around the blade opening 3b formed at the base of the blade 3.
For example, as shown in FIGS. 15 to 18, a blade runner 9 b is provided around the opening of the hollow blade 3, and the blade runner 9 b on the front side in the blade rotation direction is used as the blade front runner 9 ba and the blade rotation direction. The wing runner 9b on the rear side is referred to as a wing rear runner 9bb. Then, a difference is made between the protrusion height of the blade front runner 9ba from the surface of the main plate 2 and the protrusion height of the blade rear runner 9bb from the surface of the main plate 2, and the protrusion height of the blade front runner 9ba in the rotation axis direction. Is made higher than the protruding height of the blade rear runner 9bb by a predetermined height, and protrudes to the outside of the fan.

  In the vicinity of the main plate 2 in the blade opening 3b, the airflow C generated when the fan 1 rotates in the direction D hits the blade front runner 9ba and curves outward, draws a parabola, and again on the blade rear runner 9b side. It flows so as to approach the main plate 2. This is shown in an enlarged manner in FIG. Here, when the blade front runner 9ba and the blade rear runner 9bb are at the same height, the flow in the vicinity of the main plate 2 collides with the corner of the blade rear runner 9bb after the blade front runner 9ba leaves when the fan rotates. However, there is a problem that noise is generated in a narrow band due to pressure fluctuation.

On the other hand, when the blade front runner 9ba is made higher than the blade rear runner 9bb by a predetermined height as shown in FIG. 18 (b), the flow in the vicinity of the blade opening 3b is indicated by the arrow C in FIG. 18 (a). It flows like. That is, the flow after leaving the blade front runner 9ba draws a parabola that curves outward from the main plate 2, and approaches the main plate 2 again at the rear in the rotational direction of the blade rear runner 9bb. When the blade front runner 9ba is increased, the distance from the main plate 2 when the airflow C curves outward from the surface of the main plate 2 increases. As a result, the reattachment point of the airflow C moves to the rear of the blade rear opening 3b. By smoothly reattaching the airflow C to the rear of the blade rear opening 3b in this manner, the airflow C can be prevented from colliding with the corner of the blade rear runner 9bb, and noise can be reduced.
Further, since the thickness of the front runner 9ba for the blade is increased, the resin can more easily flow to the blade 3 to prevent the sink, and the strength at the front runner 9ba of the blade is improved, and the strength of the fan is also improved. improves.

  In this way, the blade front runner 9ba is configured to be higher by a predetermined height than the blade rear runner 9bb and protrudes to the outside of the fan, so that it is lightweight and strong and can be rotated and transported. The fan can be prevented from being damaged, and a highly reliable and low noise turbo fan can be obtained.

Here, the blade front runner 9ba and the blade rear runner 9bb of the blade runner 9b formed so as to surround the periphery of the blade 3 with respect to the maximum opening diameter F of the blade opening portion 3b having a hollow structure shown in FIG. The height difference Δt (shown in FIG. 18B) will be further described. Here, the maximum opening width F is the diameter of the inscribed circle on the surface of the main plate 2 of the opening, and Δt is the difference between the height of the blade front runner 9ba and the height of the blade rear runner 9bb.
When the height difference Δt is small, the flow leaving the blade front runner 9ba does not become a sufficiently high parabola, but collides with the corner of the blade rear runner 9bb. For this reason, noise is generated due to pressure fluctuations at the blade opening 3b. On the other hand, if the blade front runner 9ba is too high, that is, if the difference Δt is too large, the flow is separated in the blade front runner 9ba, and a peak sound due to the rotational speed is generated. Thus, there is a desirable range in the height difference Δt between the blade front runner 9ba and the blade rear runner 9bb.

  However, the flow across the blade opening 3b is related not only to the height difference Δt between the blade front runner 9ba and the blade rear runner 9bb but also to the maximum opening diameter F of the blade opening 3b. Therefore, the ratio (Δt / F) of the height difference Δt between the blade front runner 9ba and the blade rear runner 9bb with respect to the maximum opening diameter F of the blade opening 3b is calculated. FIG. 20 is a graph showing the relationship between the ratio (Δt / F)% and the noise value (dB) at the same air volume, with the horizontal axis indicating the ratio Δt / F (%) and the vertical axis indicating the noise value (dB). The noise level was measured at a position directly under the fan and about 2 m away from the fan.

From the measurement result shown in FIG. 20, the projecting height from the surface of the main plate 2 of the blade front runner 9ba and the blade rear runner 9bb is configured to be at least 4% ≦ Δt / F ≦ 22%. Therefore, a turbo fan with lower noise than that when Δt = 0 (Δt / F = 0) can be obtained.
When Δt / F <4%, the difference Δt of the runner with respect to the maximum opening diameter F is small, and there is a high possibility that the flow leaving the blade front runner 9ba collides with the corner of the blade rear runner 9bb. Thus, pressure fluctuation occurs and noise is generated in a narrow band. On the other hand, in the case of 22% <Δt / F, the difference Δt in the protrusion height of the runner with respect to the maximum opening diameter F is large, and the flow away from the blade front runner 9ba is separated, resulting in the rotational speed. Noise increases due to peak sound.

  In this way, the difference in protrusion height between the blade front runner 9ba and the blade rear runner 9bb with respect to the maximum opening diameter F of the blade opening 3b is set to a range of 4% ≦ Δt / F ≦ 22%. If configured, it is possible to suppress the flow in the vicinity of the main plate 2 from colliding at the corner of the blade rear runner 9bb, causing pressure fluctuations, and generating noise in a narrow band during fan rotation. Then, the flow after the blade front runner 9ba is detached can be reattached smoothly by moving the reattachment point of the blade rear runner 9bb to the rear in the rotation direction to the rear of the blade rear opening 3g. In addition, since the protrusion height of the blade front runner 9ba is too high, the flow does not separate in the blade front runner 9ba, and the generation of peak sound due to the rotational speed can be suppressed and noise deterioration can be prevented. For these reasons, noise can be reduced.

  Therefore, the turbofan has a ratio Δt / F of the difference Δt / F in the protrusion height between the blade front runner 9ba and the blade rear runner 9bb with respect to the maximum opening diameter F of the blade opening 3b having a hollow structure. By configuring so that t / F ≦ 22%, the noise can be reduced.

Of course, in addition to the configuration of the blade opening 3b and the blade runner 9b, by combining the above-described fan configuration, further effects can be obtained.
For example, by providing the motor cooling hole 5 while avoiding the resin joining portion, a highly reliable turbo fan can be obtained. Further, by providing the hub runner 9a, the resin can easily flow to the boss 2c near the top of the main plate 2, and the resin fluidity in the entire main plate can be improved. Further, since the blades 3 are hollow, the entire turbofan can be reduced in weight. Further, since the blade hollow portion 3d has a tapering shape having a forming draft angle inclined from the main plate 2 toward the shroud 4 at a predetermined angle θ, the blade 3 is easily attached to the mold to prevent the blade from being damaged. High moldability. Further, since the thickness of the blades 3 is made substantially uniform, the cooling and hardening time can be made uniform, so that it is possible to prevent the occurrence of molding defects due to unevenness caused by the non-uniform cooling and hardening time.

In this embodiment, a fan having seven blades 3 and seven motor cooling holes 5 corresponding to the number of blades 3 is described. The number of 9 and the number of motor cooling holes 5 are not limited to this, and may be any number.
The number of motor cooling holes 5 is the same as the number of hub runners 9a. However, as described above, the number of motor cooling holes 5 may be smaller than the number of hub runners 9a. However, if the motor cooling hole 5 is arranged on the extension line of the hub runner 9a, the motor cooling hole 5 and the resin merging portion are not connected, and a high strength can be obtained. For this reason, even when the number of motor cooling holes 5 is smaller than the number of hub runners 9a, it is preferable to arrange the motor cooling holes 5 on the extension line of the hub runner 9a. If the number of motor cooling holes 5 is reduced, the function of cooling the motor is reduced, but the strength of the fan hub 2a can be increased.

  FIG. 21 to FIG. 23 show a configuration example in which any one of the turbofans 1 described in this embodiment is mounted on an air conditioner. FIG. 21 shows a state in which the air conditioner is installed on the ceiling, FIG. 22 is a longitudinal sectional view showing the air conditioner, and FIG. 23 is a horizontal sectional view showing the air conditioner. Here, an example in which the turbo fan 1 is mounted on, for example, a ceiling-embedded air conditioner is shown.

  The air conditioner shown in FIG. 21 is embedded on the upper side of the ceiling and faces the room 19 with a substantially rectangular decorative panel 13. Near the center of the decorative panel 13, a suction grill 13a, which is an air suction port for the air conditioner main body, and a filter 20 for removing dust after passing through the suction grill 13a are disposed. Moreover, it has the panel blower outlet 13b formed along each edge | side of the decorative panel 13, and is further provided with the wind direction vane 13c in each panel blower outlet 13b.

  In addition, as shown in FIG. 22, the air conditioner main body 12 is installed in a direction to be a top plate 12 c upward with respect to the room 19, and a side plate 12 d is attached around the top plate 12 c and the lower side toward the room 19 is Installed to open. The main body suction port 12 a disposed at the center of the lower surface of the air conditioner main body 12 is disposed so as to communicate with the suction grille 13 a of the decorative panel 13. Moreover, the main body outlet 12b arrange | positioned around the main body inlet 12a is arrange | positioned so that it may connect with the panel outlet 13b. The air conditioner main body 12 includes a fan 1, a bell mouth 14 that forms a suction air passage for the turbo fan, and a motor 8 that rotationally drives the fan 1.

Moreover, the heat exchanger 15 is arrange | positioned in the blowing air path from between the blade | wings which are the airflow blowing parts of the fan 1 to the panel blower outlet 13b. The heat exchanger 15 has aluminum fins 15a and heat transfer tubes 15b, and a plurality of rectangular aluminum fins 15a extending in the height direction, that is, the vertical direction of the air conditioner main body 12 are laminated at a predetermined interval, and laminated on this. It is the structure which penetrated the heat exchanger tube 15b in multiple steps from the direction.
And as shown in FIG. 23, the heat exchanger 15 is formed in a substantially C shape so that the outer peripheral side of the turbofan 1 may be enclosed. A header 16 for adjusting the amount of refrigerant to each heat transfer tube 15b and a connection pipe 18 for connecting the outdoor unit to the distributor 17 are attached to one heat transfer tube 15b at two ends of the substantially C-shaped heat exchanger 15. It has been. A refrigerant such as carbon dioxide is circulated in the heat transfer tube 15b.

  When the turbo fan 1 rotates in the rotation direction D by the air conditioner configured as described above, the air in the room 19 passes through the suction grill 13a and the filter 20 of the decorative panel 13 and is removed, and the main body suction port 12a and the bell mouth are removed. After passing through 14, it is sucked into the turbofan 1. Then, it passes between the blades 3 of the turbofan 1 and blows out toward the heat exchanger 15. The indoor air is heat-exchanged and dehumidified, such as heating and cooling, by exchanging heat with the refrigerant flowing in the heat transfer tube 15b when passing through the heat exchanger 15. Then, when it blows out toward the room 19 from the main body blower outlet 12b and the panel blower outlet 13b, wind direction control is carried out by the wind direction vane 13c.

  When the air conditioner is transported, the turbo fan 1 is usually held so that the rotation axis direction of the turbo fan 1 is vertical, that is, the rotation axis of the fan motor 8 is vertical. That is, the air conditioner main body 12 is loaded and transported on a truck or the like with the main body top plate 12c being the lower surface or the bell mouth 14 side of the air conditioner main body 12 being the lower surface.

By mounting the turbo fan 1 according to this embodiment on the ceiling-embedded air conditioner shown in FIGS. 21 to 23, the following effects can be obtained.
That is, by improving the moldability of the turbofan 1, the thickness can be reduced and the weight of the entire product can be reduced. Further, since the strength reliability can be improved, the turbo fan 1 can be prevented from being broken by an impact such as vibration during transportation, and the product reliability can be improved as an air conditioner.
Further, in the turbo fan 1 in which the motor cooling holes 5 and the blades 3 are unequal pitches, the turbulence of the air flow discharged from the motor cooling holes 5 to the outside of the turbo fan 1 and the air flow blown from the blades 3 have periodicity. As a result, the noise caused by the rotation speed of the fan could be reduced and the noise could be reduced. Since the fan 1 is mounted on the air conditioner, the turbulence of the airflow flowing out of the fan 1 and flowing to the panel outlet 13b is also reduced. Therefore, in addition to the noise reduction of the fan 1, the noise is further reduced as an air conditioner. A quiet air conditioner can be obtained. Further, since heat exchange with the refrigerant is performed by the heat exchanger 15 in a state where the turbulence of the airflow is reduced, an efficient air conditioner can be obtained.

  The ceiling-embedded air conditioner shown in FIGS. 21 to 23 is not limited. Here, the panel outlets 13b are shown in the four directions on the ceiling, but the two panel outlets 13b may be provided in two directions so as to face each other. Moreover, it is not the structure which embeds all the air conditioner main bodies in a ceiling, You may install in the state which protruded from the ceiling. Moreover, it is not restricted to what is installed in a ceiling, What is installed in a wall surface may be used. By applying the turbo fan according to this embodiment to the air conditioner with other configurations equipped with a turbo fan, it is possible to prevent fan breakage during product transport, low noise, high product quality, quietness and light weight as above. And an air conditioner with high transportability can be obtained.

As described above, the turbo fan configured by at least one of the embodiments described in this embodiment and a heat exchanger are provided, and the air sucked from the suction port by the turbo fan is used as the refrigerant and heat by the heat exchanger. By exchanging and configuring to blow out from the outlet, an air conditioner that is highly reliable in strength, lightweight, and capable of reducing noise can be obtained.
Moreover, it is not restricted to an air conditioner, It can apply also to the ventilation fan and air cleaner which mounted the turbo fan, and can obtain the effect similar to the above.

Moreover, according to this invention, the following effects are acquired.
That is, a plurality of hub runners 9a that are continuous with the resin injection port 10 and that are thicker than the thickness of the obliquely inclined surface of the hub 2a of the main plate and extend linearly in the fan radial direction are formed at predetermined intervals on the side surface of the main plate 2 on the motor side. When the resin flows from the hub runner 9a toward the hub upper thick part 2d near the boss that is thicker than the thickness of the hub inclined surface at the time of molding, the resin joining part A is an opening having low strength against impact. Since it is formed between the motor cooling holes 5 without being connected to a certain motor cooling hole 5, it is easy to flow up to the boss 2c and the moldability is improved, and the resin joining portion generated in the main plate 2 can be shortened. Even if an impact is applied in the axial direction of the turbo fan 1 (vertical direction in FIG. 1B) and a crack occurs, the turbo fan is difficult to break, improving the moldability and increasing the reliability of the turbo fan against the impact. it can.

  Further, motor cooling holes 5 are provided in the vicinity of the fan center side end portion 9a1 of the hub runner 9a, and at least the number of the motor cooling holes 5 and the hub runners 9a is the same. In the vicinity of the fan outer peripheral end portion 9a2, a blade inner peripheral end portion 3a is disposed, and a blade runner 9b formed so as to surround the hub runner 9a and the opening 3b of the blade 3 is provided. Are connected by the connecting runner 9c, the resin junction A of the resin flowing out from the hub runner 9a is reliably generated between the motor cooling holes 5. As a result, an impact is applied in the axial direction of the turbo fan 1 during transportation (vertical direction in FIG. 1 (b)), and even if a crack occurs, the turbo fan is difficult to break, improving moldability and impact of the turbo fan. Can be highly reliable. Further, since the hub runner 9a and the blade runner 9b are not integrally formed, the injection amount of the resin injected from the resin inlet 10 between the hub runner 9a and the blade runner 9b can be adjusted, Generation of cavities and local thinning of the wall thickness due to unevenness of hot water can be prevented, and deterioration of strength can be prevented. Furthermore, the wing runner 9b makes it easier to surround the resin, so that the wing 3 can be made thinner, and the thickness of the joint between the stress-concentrated wing 3 and the main plate 2 can be increased. It is possible to improve both the improvement and the strength of the turbofan.

  Also, since the adjacent straight runners 9a for the hub are formed so as not to overlap each other, compared to the case where the ribs forming the runners for one resin inlet 10 are diverse as in the prior art, The main flow direction of the resin is the radial direction, the flow direction is not complicated, the resin merge part A can be clarified, the number of the resin merge parts A can be reduced, the mold design can be simplified, and the occurrence of cavities and Local thickness reduction of the thickness can be prevented, and deterioration of the strength of the turbofan can be prevented.

  Further, since the hub runner 9a is formed so as to protrude toward the fan external air passage 7 side of the main plate, it can also serve as a wind guide plate for inducing a flow G toward the motor cooling hole 5 by the hub runner 9a. . As a result, the air flowing on the surface of the fan motor 8 that is disposed on the fan external air passage 7 side of the hub 2a and is fixed to the turbo fan 1 by the boss 2c increases, and the motor can be easily cooled. Therefore, the temperature protection control can be performed independently because the motor temperature rises, and further, the motor can be prevented from being damaged due to a high temperature.

  In addition, the resin inlet provided near the blade inner peripheral end and the blade runner formed so as to surround the periphery of the opening on the main plate outer side of the blade having a hollow structure are connected by a connecting runner, and the blade hollow The blade inner peripheral hollow part, the blade outer peripheral hollow part, the blade front hollow part surface, and the blade rear hollow part surface are inclined at an arbitrary angle θ with respect to the rotation axis, the blade inner peripheral end part, and the blade outer peripheral side. The thickness of the end, the blade suction side end, the front blade front side and the rear blade rear side with respect to the blade rotation direction are formed so that the thickness of the entire blade is substantially the same. Since the wing and the wing hollow section toward the side are formed to have a tapered shape, the wing has a hollow structure, so the wing can be reduced in weight and the thickness is almost uniform, so the wing thickness is not uniform Molding defects due to unevenness of the cooling and curing time of the resin that can occur are difficult to occur and the moldability is good. In addition, since the blade and the blade hollow part have a tapering shape with a forming draft inclined at a predetermined angle from the main plate toward the shroud, the mold can be easily released from the mold, and the blade can be prevented from being damaged and the moldability is high. .

In addition, a convex hub formed so as to cover the motor at the center has a plurality of motor cooling holes for communicating the motor and the fan, and a fixing portion for the motor rotation shaft is provided at the center of the hub. In a turbofan formed of a thermoplastic resin having a disk-shaped main plate having a certain boss, a plurality of blades and a shroud connecting the plurality of blades to form a suction air guide wall, an end portion on the blade inner peripheral side A plurality of hub runners that are continuous with the resin inlet provided in the flat part of the main plate in the vicinity and that are thicker than the thickness of the obliquely inclined surface of the main plate and extend linearly in the fan radial direction on the motor side surface of the main plate at a predetermined interval The resin confluence formed between adjacent runners for the hub is formed with a runner so that it is not connected to at least the motor cooling hole, and the blade inner peripheral hollow portion and the blade outer peripheral hollow portion of the blade hollow portion are formed. Front and blade front hollow surface, blade rear hollow surface The blades are inclined at an arbitrary angle θ with respect to the rotation axis, the blade inner peripheral end, the blade outer peripheral end, the blade suction side end, the front blade front side with respect to the blade rotation direction, and the rear blade rear side. The thickness of each part is formed so that the entire wing has almost the same thickness, and the wing and the wing hollow part are tapered from the main plate toward the shroud side. The hub and main plate have high resin flowability and high moldability, and the hub junction is formed so that the resin junction does not communicate with at least the motor cooling hole, preventing damage to the fan due to impact during transportation. However, because the blades have a hollow structure, the entire turbofan can be reduced in weight, and since the thickness is almost uniform, molding defects due to uneven cooling and hardening time of the resin that can occur when the blade thickness is uneven are difficult to form. Is good. In addition, since the blade and the blade hollow part have a tapering shape with a forming draft inclined at a predetermined angle from the main plate toward the shroud, the mold can be easily released from the mold, and the blade can be prevented from being damaged and the moldability is high. .
Furthermore, the weight of the blades reduces the weight at the outer periphery of the turbofan relative to the center of rotation of the turbofan, reducing the centrifugal force during rotation and reducing the stress applied to the root of the main plate of the blade, improving the strength. It is possible to prevent damage to the turbofan during rotation. As a result, it is possible to obtain a highly reliable turbo fan that is lightweight, has high moldability and high strength.

  In addition, the blade inner hollow portion, the blade outer peripheral hollow portion, the blade front hollow portion surface, and the blade rear hollow portion surface are inclined surfaces with an inclination angle θ = 1-3 ° with respect to the rotation axis. The thickness of the blade inner peripheral end, the blade outer peripheral end, the blade suction side end, the front blade front side, and the rear blade rear side with respect to the rotational direction of the blade are substantially the same for the entire blade. Since the wing and the wing hollow part are formed in a tapered shape from the main plate to the shroud side, the wing can be reduced in weight and the wall thickness is almost uniform. Molding defects due to uneven cooling and curing time of the resin that can occur when the blade thickness is uneven are less likely to occur and the moldability is good. In addition, since the blade and the blade hollow part have a tapering shape with a forming draft inclined at a predetermined angle from the main plate toward the shroud, the mold can be easily released from the mold, and the blade can be prevented from being damaged and the moldability is high. . In addition, at least the noise change is small and does not deteriorate. From the above results, if the inclination angle θ is at least 1 ° to 3 °, a change in noise is small, and a turbofan with high moldability can be obtained.

  Further, the circumferential mounting pitch angle σ of the blade 3 is arranged at an unequal pitch, and at the same time, the circumferential pitch angle γ of the motor cooling hole 5 is an unequal pitch angle relative to the blade 3 and the fan rotation center O The hub runner 9a that extends linearly in a radial direction from the blade 3 and the motor cooling hole 5 is also unequal to one resin injection port 10, the hub runner 9a, the blade runner 9b, and the motor cooling. Since the arrangement of the holes 5 is almost the same, it is difficult to change the molding conditions, and it is possible to prevent the occurrence of cavities and local thinning of the wall thickness due to unevenness of the hot water run, and the strength deterioration of the turbofan can be prevented. Since the arrangement relationship between the motor cooling hole 5 and the blade 3 is the same, the turbulent flow E2 flowing out from the fan external air passage 7 to the fan internal air passage 6 through the motor cooling hole 5 does not directly collide with the blade 3, so that the pressure fluctuation is reduced. A turbo fan capable of reducing noise without being greatly affected can be obtained.

  Further, the resin flowing out from the resin injection port 10 flows from the hub runner 9a toward the cooling hole runner 9d toward the boss 2c. At this time, there is a cooling hole runner 9d on the outer periphery of the motor cooling hole 5, and after the resin flows in, the reflow of the motor cooling hole is ensured to rejoin and flow toward the boss 2c. There is no runner for the cooling hole, and it is unlikely that it will be difficult to rejoin the cooling hole in the resin flow direction, and the strength around the motor cooling hole 5 that tends to decrease the strength at the opening can be improved. As a result, it is possible to improve the moldability and strength by improving the resin fluidity around the motor cooling hole, and to obtain a turbofan that is not easily broken even when an impact is applied.

  Further, the ratio of the maximum thickness t1, t2 of the hub runner 9a and the blade runner 9b to the minimum thickness t0 of the other portion of the main plate 2 t1 / t2 = 1.1-2, t2 / t0 = In the range of 1.1 to 2, the molding time can be shortened compared to the case of at least the same wall thickness (t1 / t0, t2 / t0 =), the production amount can be increased in the same time, and the electric cost of the molding machine can be increased. Reduction is also possible and energy saving.

  Further, the blade front runner corresponding to the blade rotation direction side surface of the blade runner formed so as to surround the opening on the outer side of the main plate of the hollow blade is the blade rear runway corresponding to the blade rotation direction opposite side surface. Since it is formed so as to protrude outside the fan, the flow near the main plate during rotation collides at the corner of the runner after the blade forward runway, causing pressure fluctuations in a narrow band. Generation of noise is suppressed, and the reattachment point of the flow after the blade front runner detachment to the rear in the rotational direction of the blade rear runner is moved to the rear of the blade opening so that the noise can be reduced.

  In addition, a convex hub formed so as to cover the motor at the center has a plurality of motor cooling holes for communicating the motor and the fan, and a fixing portion for the motor rotation shaft is provided at the center of the hub. In a turbofan formed of a thermoplastic resin having a disk-shaped main plate having a certain boss, a plurality of blades and a shroud connecting the plurality of blades to form a suction air guide wall, an end portion on the blade inner peripheral side A plurality of hub runners that are continuous with the resin inlet provided in the flat part of the main plate in the vicinity and that are thicker than the thickness of the obliquely inclined surface of the main plate and extend linearly in the fan radial direction on the motor side surface of the main plate at a predetermined interval The resin confluence formed between adjacent runners for the hub is formed with a runner so that it is not connected to at least the motor cooling hole, and the blade inner peripheral hollow portion and the blade outer peripheral hollow portion of the blade hollow portion are formed. Front and blade front hollow surface, blade rear hollow surface The blades are inclined at an arbitrary angle θ with respect to the rotation axis, the blade inner peripheral end, the blade outer peripheral end, the blade suction side end, the front blade front side with respect to the blade rotation direction, and the rear blade rear side. The thickness of each part of the wing is formed so that the entire wing has almost the same thickness, and the wing and the wing hollow part are tapered from the main plate toward the shroud side. The blade runner is connected to the blade runner formed so as to surround the periphery of the opening, and the blade front runner of the blade rotation direction side portion of the blade runner is the blade rotation direction opposite side equivalent portion. Since it is higher than the runner behind the blade and protrudes to the outside of the fan, the hub runner has high resin flowability at the hub and main plate, high moldability, and at least the motor junction is at the motor cooling hole. Since the hub runway is formed so as not to communicate with the fan, the fan breaks due to impact during transportation. Loss can be prevented. In addition, since the blades have a hollow structure, the entire turbofan can be reduced in weight, and since the wall thickness is approximately uniform, molding defects due to uneven cooling and hardening time of the resin that can occur when the blade thickness is uneven are less likely to occur. good. In addition, since the blade and the blade hollow part have a tapering shape with a forming draft inclined at a predetermined angle from the main plate toward the shroud, the mold can be easily released from the mold, and the blade can be prevented from being damaged and the moldability is high. . In addition, the flow near the main plate during rotation is prevented from colliding at the corner of the runner behind the blade and causing pressure fluctuations to generate noise in a narrow band. Since the reattachment point to the rear of the rear runner in the rotational direction is moved to the rear of the blade rear opening and smoothly reattached, the noise can be reduced. In addition, since the thickness of the front runner for the wing is increased, the resin can flow more easily into the wing during molding, and it is possible to prevent sink marks. In addition, the strength at the front runner is improved, and the strength of the turbo fan is improved To do. From the above results, it is possible to obtain a low-noise turbofan that is light and strong, can prevent damage to the fan even during rotation and transportation.

  Further, the turbofan has a ratio Δt / F = 4 to 22% of a difference Δt between the maximum opening diameter F of the blade opening 3b having a hollow structure and the height of the blade front runner 9ba and the blade rear runner 9bb. In this way, the flow near the main plate during rotation collides at the corner of the runner after the blade forward runoff, causing pressure fluctuations and noise generation in a narrow band. Noise can be reduced because the reattachment point of the flow after leaving the road is reattached smoothly by moving the reattachment point to the rear of the blade rear runner in the rotational direction. In addition, the thickness of the runner front runner is too high, and the flow is separated in the runner front runner to suppress the generation of peak sound due to the rotational speed, thereby preventing noise deterioration and reducing noise.

  Further, the turbo fan 1 having any one of the configurations described in the first embodiment is mounted, and the heat exchanger is disposed on the suction side or the discharge side of the turbo fan. Since the thickness can be reduced, the weight can be reduced and the strength reliability is high. Therefore, when installed after transportation, the turbo fan 1 is not broken by an impact such as vibration during transportation, and the product reliability is high. In addition, the weight of the product can be reduced as the turbo fan 1 becomes lighter.

  Further, the side plate and the top plate of the air conditioner main body are formed of a sheet metal member, and the side plate and at least a part of the air conditioner main body inside the top plate constitute an air passage wall surface with a heat insulating material, A motor and the turbo fan 1 having any one of the configurations described in the first embodiment are mounted near the center of the interior, and a suction port of the turbo fan and a main body suction port are provided at the center of the lower surface of the air conditioner body. A bell mouth is disposed, and a heat exchanger is erected so as to surround the outer periphery of the turbofan, and a drain pan formed of a foam material is disposed at a lower portion of the heat exchanger, and the main body suction port A decorative panel having a main body outlet and a panel inlet and a panel outlet that communicate with the main body outlet and the main body outlet, respectively, is attached to the lower surface of the main body. Buried ceiling By adopting a type air conditioner, it is possible to reduce the thickness by improving the moldability of the turbofan 1 and to reduce the weight. Furthermore, since the strength reliability is high, the turbofan 1 is subjected to shocks such as vibration during transportation after installation. The product reliability is high because there is no destruction. In addition, the weight of the product can be reduced as the turbo fan 1 becomes lighter.

Claims (13)

  A disc-shaped main plate, a convex hub formed by projecting the central portion of the main plate in the direction of the rotation axis, and a plurality of wings erected in the projecting direction of the hub using the outer peripheral side flat plate portion of the main plate as a base, The hub is formed by a plurality of motor cooling holes provided in the hub and cooling motors arranged in a convex space surrounded by the hub, and a thermoplastic resin that is provided radially in the hub and injects a thermoplastic resin during molding. A plurality of hub runners, and a resin joining portion formed by contacting the thermoplastic resin flowing out from the adjacent hub runner at the time of molding, and the motor cooling hole includes the resin joining portion. A turbofan characterized by being arranged to avoid.   The wing has a hollow shape having an opening in the base, and is provided around the base of each of the wings. The wing runner that forms the wing, each of the hub runners, and the wing A connecting runner connecting the runners, and injecting the thermoplastic resin from an inlet provided in any one of the runner for the hub, the connecting runner, and the runner for the wing, The turbofan according to claim 1, wherein the turbofan is formed by flowing into all of the runners.   A disk-shaped main plate, a convex hub formed by projecting the central portion of the main plate in the direction of the rotation axis, and an outer side flat plate portion of the main plate as a base portion and standing in the projecting direction of the hub and open to the base portion A plurality of hollow wings, a plurality of wings provided radially to the hub, and a hub runner for forming the hub by injecting a thermoplastic resin during molding, and provided around the base of each of the wings. A blade runner that flows the thermoplastic resin during the molding to form the blade, and a connecting runner that connects each of the hub runners and the blade runner located in the vicinity thereof. A turbofan characterized by that.   4. The turbo fan according to claim 1, wherein a plurality of motor cooling holes provided in the hub are arranged in a portion extending the runner for the hub toward the rotation center.   The turbo fan according to claim 4, wherein the same number of motor cooling holes and hub runners are provided.   The turbofan according to claim 1, wherein the runner for the hub protrudes from the surface of the main plate of the hub toward the motor arrangement side.   3. A plurality of sets each including the blade, the blade runner, the hub runner, the connecting runner, and the motor cooling hole are provided radially around the rotation axis. The turbofan according to any one of claims 4 to 6.   8. The turbo fan according to claim 7, wherein at least one of the angles formed by the adjacent groups is different from the other angles.   9. A cooling hole runner connected to the hub runner and formed so as to surround the motor cooling hole is provided, and the cooling hole runner is provided. The turbo fan according to any one of the above.   When the thickness of at least one of the thickness of the runner for the hub and the thickness of the runner for the wing is t, and the minimum thickness of the portion excluding the runner of the main plate is t0, the ratio 10. The turbo fan according to claim 2, wherein t / t 0 is in a range of 1.1 ≦ t / t 0 ≦ 2.   A disk-shaped main plate, a convex hub formed by projecting the central portion of the main plate in the direction of the rotation axis, and an outer side flat plate portion of the main plate as a base portion and standing in the projecting direction of the hub and open to the base portion A plurality of hollow wings having wings, and wing runners provided around the openings so as to protrude from the main plate in a direction opposite to the erection direction of the wings. A turbofan characterized in that a protrusion height of the blade runner positioned around the blade is higher than a protrusion height of the blade runner positioned around the rear of the opening in the rotation direction.   The diameter of the inscribed circle on the surface of the main plate of the opening is defined as a maximum opening width F, and Δt is the protrusion height of the runner for the blades located around the front of the opening in the rotation direction and the rear of the opening in the rotation direction. The Δt / F is in a range of 0.04 ≦ Δt / F ≦ 0.22 when the difference from the protruding height of the wing runner positioned around is set to be 0.04 ≦ Δt / F ≦ 0.22. Turbo fan. The turbofan according to any one of claims 1 to 12, and a heat exchanger, wherein the air sucked from the suction port by the turbofan is heat-exchanged with the refrigerant by the heat exchanger, and the blowout port An air conditioner characterized by being configured to blow out from the air.

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