WO2007040236A1

WO2007040236A1 - Turbo fan and air conditioner

Info

Publication number: WO2007040236A1
Application number: PCT/JP2006/319832
Authority: WO
Inventors: Takashi Ikeda; Atsushi Edayoshi; Kazutaka Suzuki; Katsumi Shibayama; Hiroshi Nakashima
Original assignee: Mitsubishi Electric Corporation
Priority date: 2005-10-06
Filing date: 2006-10-04
Publication date: 2007-04-12
Also published as: JP4559472B2; JPWO2007040236A1; EP1933040A4; CN101099044A; EP2980414B1; ES2589903T3; EP2980414A1; JP2010216486A; JP5121887B2; EP1933040A1; EP1933040B1; CN100559031C; ES2800055T3

Abstract

A turbo fan comprising a main shroud and blades which are integrally formed by use of a thermosetting resin. The turbo fan having high reliability in strength and capable of reducing noise includes the disk-like main shroud (2), a hub (2a) for installing a motor in a space formed by projecting the center part of the main shroud (2) in the direction of a rotating axis, the plurality of blades (3) having a base part formed of the outer peripheral side flat plate part of the main shroud (2) and vertically installed in the projected direction of the hub (2a), and a plurality of motor cooling holes (5) formed in the hub (2a) and communicating with the space in which the motor is disposed. To form the hub (2a), the thermosetting resin is poured into a plurality of hub runners (9a) radially formed in the hub (2a). The motor cooling holes (5) are so disposed as to avoid resin converging parts (A) formed between the adjacent hub runners (9a).

Description

Specification

Turbo fan, air conditioner

Technical field

TECHNICAL FIELD [0001] The present invention relates to a turbo fan molded from thermoplastic resin and an air conditioner equipped with the turbo fan.

Background art

[0002] A conventional turbofan molded with a thermoplastic resin has a reduced thickness by reducing the thickness of the turbofan by ensuring the rigidity of the turbofan by means of ribs made up of injected resin runners. (For example, see Patent Document 1).

In addition, there are some which reduce the material by providing a recess at the intersection of the wing and the main plate to reduce the cost (for example, see Patent Document 2).

In addition, the cross-sectional shape of multiple blades has a similar shape that gradually increases in thickness from the shroud to the main plate, and the adjacent distance between each blade gradually decreases from the shroud to the main plate, so that In some cases, a time difference is caused 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). Some blades have hollow blades with 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, patents). (Ref. 4).

[0003] Patent Document 1: Japanese Patent No. 3131625 (Pages 3, 4 and 1 and 3)

Patent Document 2: Japanese Utility Model Publication No. 4 116698 (Page 1, Figure 1)

Patent Document 3: Japanese Patent No. 3544325 (Pages 7-9, Fig. 5, Fig. 6)

Patent Document 4: Japanese Utility Model Publication No. 4 116699 (1st page, Fig. 1)

Disclosure of the invention

Problems to be solved by the invention

[0004] The conventional turbofan according to Patent Document 1 is provided with ribs that improve the moldability by combining the reinforcement for reducing the thickness of the main plate and the hot water of the resin, but the rib force also flows out during molding. The strength of the cocoon resin confluence where the cocoa oil merges is weakened. That is, approximately the same distance from adjacent ribs The part of separation becomes the cocoon resin confluence, where the strength is weak. In this conventional apparatus, the blade front end side rib that extends in the radial direction passing through the vicinity of the blade front end portion, the blade rear end side rib that extends in the radial direction through the vicinity of the rear end portion of the blade, the blade front end side rib, and the blade Connecting ribs that connect the rear end side ribs and blade reinforcing ribs are provided, and the power of one resin injection port is injected into these ribs.

When the resin injected from the resin injection port flows into each rib, the blade tip side rib and the blade rear end side rib flow in two directions in the radial direction on the rotation center side and the outer peripheral side. It flows in a direction having a radial component and a circumferential component, and flows in a direction opposite to the connecting rib in the blade reinforcing rib. That is, the resin injected from one injection port flows through a plurality of ribs extending in the radial direction, and the resin released from this rib force abuts with each other to form a resin confluence portion. Since the resin merging section is also formed between the effluents flowing out from the adjacent resin injection loca, many turbo merging sections are formed in the entire turbofan, which limits the improvement of the turbo fan strength. was there. Usually, a plurality of holes for cooling the motor are provided in the convex part of the main plate near the rotating shaft. However, if the resin confluence part passes through the motor cooling hole, which is a low-strength opening, the strength is further increased. Becomes low. For example, when an impact in the direction parallel to the rotation axis is applied to the turbo fan during transportation, cracks occur in the motor cooling hole and the surrounding resin joint, and these low strength parts are connected. And there was a problem that the crack that occurred was spread. In addition, in this runner configuration, there is a part where the resin-filled joint extends to the outer peripheral edge of the fan, and cracks generated at the resin-filled joint extend to the outer peripheral edge and break, and product quality deteriorates immediately. There was a point.

[0005] In the configuration shown in Patent Document 2 in which a recess is provided at the intersection between 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 concave. After leaving the corner R at the upstream end of the plant, it collided with the corner R at the downstream end, and an abnormal noise was generated due to pressure fluctuation.

[0006] In addition, in the turbofan disclosed in Patent Document 3, since the blade has a hollow structure and there is a significant difference in thickness at each part of the blade, a temperature difference occurs at each part of the blade during molding. For this reason, there is a problem in that moldability is deteriorated due to generation of cavities and local thin wall thickness (hereinafter referred to as sink) due to unevenness of the hot water. Also, the entire wing is made of greaves In comparison with a hollow blade, a large amount of grease is required, which increases the fan weight and cost. In addition, the air conditioner that is installed becomes heavier and the transportability of workers is poor.

[0007] In addition, the centrifugal fan described in Patent Document 4 is a hollow blade having a large blade thickness, but if the blade thickness is too thick, the air passage area of the fan is reduced. It can grow. In addition, the blade cross-sections perpendicular to the rotating shaft are all the same, and there is a problem that when the blade is pulled out from the mold during injection molding, the resin with a low draft may reach the mold and break. It was.

[0008] The present invention has been made to solve the above-described problems, and by improving the moldability and strength of a turbofan molded from a thermoplastic resin, it can be broken during transportation. The purpose is to obtain a turbo fan and an air conditioner equipped with a turbo fan.

Another object of the present invention is to obtain a turbo fan capable of reducing noise and an air conditioner equipped with the turbo fan.

Means for solving the problem

[0009] 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 an outer peripheral flat plate portion of the main plate as a base. A plurality of blades standing in the projecting direction, a plurality of blades provided in the hub, and motor cooling holes for cooling a motor disposed in a convex space surrounded by the hub, and provided radially in the hub during molding. A plurality of hub runners that form the hub by injecting thermoplastic resin, and a resin joint formed by the thermoplastic resin flowing out from the adjacent hub runners at the time of molding. And the motor cooling hole is disposed so as to avoid the resin merging portion.

The invention's effect

[0010] According to this invention, since the resin confluence 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.

Brief Description of Drawings FIG. 1 is a plan view (FIG. 1 (a)) showing a turbofan according to Embodiment 1 of the present invention, and an explanatory view seen from the side (FIG. 1 (b)).

圆 2] A perspective view showing a turbofan according to Embodiment 1 of the present invention.

圆 3] An explanatory view showing a turbofan according to Embodiment 1 of the present invention.

圆 4] An enlarged explanatory view of the turbo fan according to the first embodiment of the present invention. [5] FIG. 5 is an explanatory diagram showing a cross section taken along line HI-H2 of FIG. 4 according to the first embodiment of the present invention.

FIG. 6 is an explanatory view showing, in an enlarged manner, a cross section taken along O-Ol-02-03 in FIG. 1 (b) according to the first embodiment of the present invention.

FIG. 7 is a flowchart showing a fan forming process according to the first embodiment of the present invention.

[Fig. 8] A ratio between the maximum wall thickness tl of the hub runner 9a and the minimum wall thickness to the other part of the main plate 2 according to Embodiment 1 of the present invention. Molding time for tlZtO (oil injection input cooling It is a graph showing the time taken out.

[Fig. 9] According to Embodiment 1 of the present invention, the ratio of the maximum wall thickness t2 of the blade runner 9b to the minimum wall thickness tO of the other part of the main plate 2 t2 ZtO molding time (resin injection input cooling It is a graph showing the time taken out.

[10] FIG. 10 is an explanatory view showing a blade according to Embodiment 1 of the present invention, a side view showing one fan blade (FIG. 10 (a)), and a cross section taken along the line Z-Z in FIG. 10 (a) ( Figure 10 (b)) is shown.

圆 11] An explanatory view showing the wing according to Embodiment 1 of the present invention, showing a longitudinal section taken along line Y—Y of FIG. 10 (b).

[Fig.12] Fan forming time (sec) and noise value when the outside surface of the blade and the standing surface on the inside of the hollow are inclined to the inside of the blade at an inclination angle Θ with respect to the rotation axis, and the inclination angle Θ is changed It is a graph which shows (dB).

FIG. 13 is a bottom view showing a turbo fan according to Embodiment 1 of the present invention and formed with another runner configuration.

FIG. 14 is a bottom view showing a turbo fan according to Embodiment 1 of the present invention, which is formed with still another runner configuration.

15] According to Embodiment 1 of the present invention, an oblique view of a turbo fan of another configuration example viewed from below. FIG.

FIG. 16 is a partial perspective view showing, in an enlarged manner, a part of the turbo fan according to the first embodiment of the present invention.

FIG. 17 is an explanatory view showing a blade according to Embodiment 1 of the present invention, and is a side view showing one fan blade (FIG. 17 (a)), and a cross section taken along the line ZZ in FIG. 17 (a). (Fig. 17 (b)) is shown.

FIG. 18 is an explanatory view showing a wing according to Embodiment 1 of the present invention, and is a longitudinal section taken along line Y—Y in FIG. 17 (b) (FIG. 18 (a)) and FIG. 18 (a). FIG. 18 is an enlarged explanatory view (FIG. 18 (b)).

FIG. 19 is an explanatory view showing a part of the lower surface of the turbofan according to the first embodiment of the present invention.

FIG. 20 relates to Embodiment 1 of the present invention, and is the same as the ratio of the height difference At between the blade front runner 9ba and the blade rear runner 9bb with respect to the maximum opening width diameter F of the blade opening 3b having a hollow structure. It is the graph which showed the relation of the noise value in the air volume.

FIG. 21 is a perspective view of the air conditioner according to the first embodiment of the present invention and viewed from the installed room power.

FIG. 22 is a longitudinal sectional view showing an air conditioner according to Embodiment 1 of the present invention.

FIG. 23 is a horizontal sectional view showing the air conditioner according to the first embodiment of the present invention.

Explanation of symbols

[0012] 1 turbo fan, 2 main plate, 2a hub, 2b fan inner peripheral side, 2c boss, 2d hub upper thick part, 3 blades, 5 motor cooling hole, 8 motor, 9 runners, 9a runner for hub 9b wing runner, 9ba wing forward runner, 9bb wing rear runner, 9c articulated runner, 9d cooling hole runner, 10 oil filler inlet, 12 air conditioner body, 15 heat exchanger, A A The oil flow direction during B formation, the air flow in the vicinity of the C blade opening, the D fan rotation direction, the El, E2 air flow, the maximum opening width of the F blade opening 3b (inscribed inside the opening on the main plate surface) The diameter of the circle), the airflow that is directed toward the motor cooling hole by the runway for the G hub, and the center of rotation.

BEST MODE FOR CARRYING OUT THE INVENTION

Embodiment 1.

Hereinafter, a turbo fan (hereinafter simply referred to as a fan) according to Embodiment 1 of the present invention will be described. Based on

FIG. 1 (a) 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. 1 (b) is an explanatory diagram showing the lateral force of Fig. 1 (a). The left half is the side and the right half is the vertical cross section at O-Ol-02-03 in Fig. 1 (a). Show. FIG. 2 is a perspective view showing the lower surface of the fan according to this embodiment, that is, the force opposite to the shroud.

As shown in FIGS. 1 and 2, the fan 1 is composed of a disk-shaped main plate 2, and the central portion of the main plate 2 has a convex shape protruding in the rotation axis direction, and is a space surrounded by the convex portions. A motor (not shown) is arranged in This convex portion is referred to as a knob 2a. A boss 2c is formed at the center of the hub 2a, that is, 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 of the main plate 2 connected to the boss 2c is provided with a hub upper thick portion 2d to ensure strength and is thicker than the thickness tO of the inclined surface of the hub 2a.

[0015] The wing 3 has a bag-like hollow shape with the outer peripheral side flat plate portion of the main plate 2 as a base portion and standing from the blade opening portion 3b of the base portion in the protruding direction of the hub 2a. At the base, the blade opening 3b is located between the blade inner peripheral end 3a and the blade outer peripheral end 3c, and the centerline 3a-3c of the blade opening 3b and the radius of the main plate 2 are at a predetermined angle, for example 45 ° Arranged to intersect at an angle of about. Then, as shown in FIG. 1 (a), the plurality of blades 3 are arranged so that the circumferential mounting pitch angles σ 1, σ 2, σ 3,. Deploy. In Fig. 1 (a), for example, σ 1 = σ 4 ^ σ d = σ 6 = σ 7 ^ σ 2 = σ 5 and so on.

[0016] The fan 1 is driven by a motor and rotates in the direction of arrow D around the rotation center Ο.

The shroud 4 is provided on the outer periphery of the fan 1 as shown in FIG. 1 (b), and is fixed to the upper force blades 3 in FIG. 1 (b).

[0017] A fan internal air passage 6 is formed in the vicinity of the hub 2a by being sandwiched 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 having a plurality of opening forces around the rotation center O and at a position substantially equidistant from the rotation center O, and communicates the fan internal air passage 6 and the fan external air passage 7. . In Fig. 1 (a) For example, seven motor cooling holes 5 are provided, and each is arranged on a straight line O-3a that connects 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, as in the blade 3. Here, the circumferential mounting pitch angle γ 1, y 2, γ 3,... Γ 7 of the motor cooling hole 5 is the same as the circumferential mounting pitch angle σ of the blade 3, for example, γ 1 = γ 4 <γ 3 = γ 6 = γ 7 <γ 2 = γ 5

[0018] The main plate 2 and the blades 3 are integrally formed of, for example, a thermoplastic resin such as ABS or ASG (hereinafter simply referred to as resin). In FIG. 2, 10 is the trace of the oil injection port used to inject the resin when forming the main plate 2 and the blade 3, and the bent portion between the hub 2a of the main plate 2 and the flat portion. It is in the vicinity and in the vicinity of the blade inner peripheral end 3a of the flat portion, and is here referred to as a resin injection port 10. Also, the fan has a runner 9 that becomes a passage for the resin during molding, and the mold can easily pass the grease so that the space is larger in the thickness direction than the main part of the main plate 2. In the fan, which is a finished product, the fat in the runner 9 is solidified and remains thicker than the minimum thickness of the part other than the runner in the main plate 2.

[0019] 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 nozzle 2a. The hub runners 9a extend from the resin inlet 10 toward the rotation center O, and run into other fan runners in the fan radial direction to the vicinity of the motor cooling hole 5. It extends straight without crossing. The hub runner 9a is thicker than the minimum wall thickness tO on the inclined surface of the hub 2a, and has a predetermined wall thickness tl (> tO). In addition, a motor cooling hole 5 is arranged near the fan center side end of the hub runner 9a, and the blade 3 inner end of the blade 3 is near the fan outer end of the other hub runner 9a. 3a is arranged. Furthermore, the center line 11 in the width direction of the straight hub runner 9a is arranged so as to pass over the motor cooling hole 5, and the inner peripheral end 3a of the blade, the grease injection part 10, the hub runner 9a , And the motor cooling hole 5 are disposed so as to be positioned on a substantially straight line 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 blade 3 is an unequal pitch, the motor cooling hole 5, the hub runner 9a, and the oil filler inlet 10 are also not Consists of equal pitch. When the mounting pitch angle σ of the blades 3 is an equal pitch, the circumferential mounting pitch angles of the motor cooling hole 5, the hub runner 9a, and the resin inlet 10 are also the same pitch. [0020] In addition, a blade runner 9b is formed around the blade opening 3b in 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 grease during molding. Similar to the hub runner 9a, the blade runner 9b is thicker than the wall thickness tO of the outer plate on the outer side of the main plate 2. The wall thickness is t2 (> t0). The connecting runner 9c is a runner connecting the runner 9a for the hub and the runner 9b for the wing. The connecting runner 9c is made of, for example, the same wall thickness tl as the nove runner 9a, and the width is smaller than that of the hub runner 9a and the blade runner 9b.

[0021] When the fan 1 rotates in the direction D, the surrounding air is guided to the blade 3 by the shroud 4 and sucked into the shroud 4 and passes through the fan internal air passage 6 as shown by an arrow E1 in FIG. It blows out from between the wings 3 on the fan periphery. 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 Fig. 1 (b) and Fig. 2, part of the flow blown out from fan 1 through motor cooling hole 5 communicating between fan internal air passage 6 and fan external air passage 7 E2 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 fan internal air passage 6. On the side of the fan external air passage 7 surrounded by the hub 2a, a motor is disposed by being fixed to the fan 1 by a boss 2c, and the motor is cooled by the airflow E2.

[0022] When the turbo fan having such a configuration is integrally formed with a resin, the 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 runway 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 runner 9a for the hub is a runner provided between the center end 9al and the fan outer end 9a2, and the motor cooling hole 5 is arranged near the fan center end 9al, and the blade inner end The part 3a is arranged in the vicinity of the fan outer peripheral side end part 9a2.

A part of the resin flows through the hub runner 9a and then flows into 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 flows to the blade 3 and the main plate 2 around the blade 3 to form this portion. The flow of resin at this time is shown by arrow B in FIG. As each arrow 9 passes through each runner 9, the resin flows into the mold, and the adjacent runner 9 also flows out from the runway 9 at the joint where the resin is almost equidistant. To do. This merging area is indicated by dotted line A. [0023] The resin injected from the resin injection port 10 and guided to the runner 9a for the hub flows smoothly in one direction against the rotation center O in the radial direction. Further, the resin flowing through the hub runner 9a flows toward the adjacent hub runner 9a, so that a resin joining portion A is formed between the adjacent hub runners 9a. Since the motor cooling hole 5 is arranged so as to avoid the resin cooling hole A, the resin cooling hole A formed near the motor cooling hole 5 is not formed by being connected to the motor cooling hole 5. It is formed between adjacent motor cooling holes 5.

Since the resin confluence A is connected to the motor cooling hole 5, which is an opening with low strength against impact, it is possible to prevent cracks connected to the motor cooling hole 5 and the resin confluence A from forming. The strength of the fan 1 can be improved. Therefore, even when a shock is applied in the direction of the rotation axis of the fan 1 during transportation, for example, in the vertical direction in FIG. 1 (b) and a crack occurs around the motor cooling hole 5, the generated crack is still in 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 breaking, and the reliability of the fan 1 against 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 formation of the resin confluence portion A near the motor cooling hole 5. .

[0024] Further, in the configuration in which the runner 9 is complicatedly branched, the nozzle inlet 10 branches in two directions, the nove runner 9a and the connecting runner 9c, and the connected runner 9c and the wing runner Branches to the wing runner 9b in two directions at the connection part 9b. As described above, since the strength is low at the resin joining portion A, it is preferable to reduce the number and the length of the resin joining portion A to be formed as much as possible. In the configuration of the runner 9 according to this embodiment, the coconut resin injected from one cocoon injection port 10 does not form the cocoon resin merging portion A, but the A resin merging portion A is formed at the portion in contact with the oil. For this reason, as a whole, the number of cocoon resin confluences A can be reduced. In this way, the runner 9 is relatively simple, so that the resin can easily flow along the runner 9, and the occurrence of sink marks can be reduced and the moldability can be improved.

[0025] Further, in the fan according to this embodiment, as shown by the dotted line, the resin joining portion A is in contact with the boss 2c and extends in the radial direction through between the adjacent motor cooling holes 5, The other end is in contact with the center of the wing 3. In the conventional configuration in which the resin joint A extends directly to the outer peripheral edge, when a crack occurs along the resin joint A, the crack extends to the outer peripheral edge of the fan 1. In addition, there was a possibility of being divided and cut. On the other hand, in this embodiment, the outer peripheral side end portion of the resin confluence portion A formed on the main plate 2 is configured to abut against the blade runner 9b. For this reason, the resin joining portion A formed on 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. In addition, even if a crack occurs near the resin confluence A during transportation and the crack expands along the resin confluence A, the outer peripheral end of the resin confluence A is thick. Since it is in contact with the wing runner 9b, the crack stops at this point. Further, when a crack that does not stop in the blade runner 9b is connected, 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 to improve the reliability with respect to impact.

[0026] The configurations of the resin-filling junction A and the runway 9 will be described in more detail below. The number of blades 3 'shape' angle to radius, runner 9 shape 'configuration, position of filler inlet 10, position of motor cooling hole 5' position, etc. A fan that is highly reliable against impacts can be configured by abutting one end against the boss 2c, extending radially between adjacent motor cooling holes 5 and the other end abutting against the center of the blade 3. 1 is 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 the line HI-H2 of FIG. The resin injection port 10 is provided, for example, at a position close to the connecting runner 9c of the water runner 9a. Here, for example, two adjacent resin injection ports 10m and 10η will be described. The oil injection port 10m is connected to the hub runner 9am, the blade runner 9bm, and the connecting runner 9cm, and the power is injected to form the blade 3m and the main plate 2 around it. On the other hand, the oil injection port 10η is connected to the hub runner 9an, the runner runner 9bn, and the connecting runner 9cn, and the power is poured to form the blade 3n and the main plate 2 around it. . The blade 3 standing on the main plate 2 has a predetermined wall thickness t3 (> t0), and the entire blade 3 is substantially uniform.

[0027] When the blade 3m is positioned in front of the blade 3n in the fan rotation direction (arrow D direction), the resin confluence A formed between the two blades 3m and 3n is not connected to the outer peripheral edge of the fan. In order to do so, the resin forming the region L may be formed with the resin injected from the resin injection port 10η. In particular, if the resin that forms the vicinity of the flat plate part 3cmt at the blade outer peripheral end of the blade 3m is not the resin injected at the resin injection port 10m but the resin injected at the resin injection port 10η, the hub The ligation junction A formed between the 9an and 9am runways is surely 3m on the wing. Abut. For that purpose, the distance from the resin inlet 10η is shorter than the distance from the resin inlet 10m in the flow path length of the resin flowing to the flat plate part 3cmt at the outer peripheral edge of the blade. In addition, the runway 9 may be configured.

[0028] Specifically, the number of blades 3 'shape, runner 9 shape' configuration, the position of the oil filler inlet 10, the shape of the motor cooling hole 5 'position, the oil injection speed, etc. are set. For example, by simulating, it is possible to examine which part of the fan can form the resin merging portion A during molding. Then, the resin confluence portion A obtained in the simulation has one end abutting against the boss 2c, passing through the hub 2a between the adjacent motor cooling holes 5, and the other end abutting against the blade runner 9b. Just configure

[0029] As described above, the disc-shaped main plate 2, the convex hub 2a formed by projecting the central portion of the main plate 2 in the rotation axis direction, and the outer peripheral side flat plate portion of the main plate 2 as the base, A plurality of blades 3 standing in the projecting direction of the motor, a plurality of blades 3 provided in the hub 2a, and a motor cooling hole 5 for cooling the motor arranged in the convex space surrounded by the hub 2a, and provided in a radial pattern in the hub 2a. A plurality of hub runners 9a that form the hub 2a by injecting the resin during molding and a resin junction A formed by the contact of the resin flowing out from the adjacent hub runner 9a during molding A And the motor cooling hole 5 is arranged so as to avoid the resin joining portion A, so that it is possible to obtain a turbo fan with high reliability against impact.

[0030] In addition, a 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. A fan can be obtained that can be configured so as to be surely connected to the oil confluence section A and has high reliability with respect to impact.

[0031] Further, by forming the hub runner 9a in a straight line radially around the rotation center O, it is easy to flow the grease to the boss 2c around the rotation center, and the moldability can be improved.

[0032] In addition, the runner 9 serving as a passage for the oil and fat is formed separately from the runner 9a for the hub and the runner 9b for the wing, and a connecting runner 9c that connects the runners 9a and 9b is provided. Furthermore, it is the structure which inject | pours the resin from the resin injection port 10 provided in any one place of the runners 9a, 9b, 9c. That is, at least one of the oils flowing into the hub runner 9a and the blade runner 9b flows through the connecting runner 9c. For this reason, depending on the width and thickness settings of the connecting runner 9c, It is possible to adjust the balance between the amount of fat and the amount of sallow flowing through the wing runner 9b. By properly adjusting the injection amount of the oil flowing into the hub runner 9a and the wing runner 9b, it is possible to prevent the occurrence of cavities and local thinning of the wall thickness due to unevenness of the runner, and the strength is reduced. Can be prevented.

In this embodiment, the grease injection port 10 may be provided in the power blade runner 9b in which the resin injection port 10 is directly provided in the nozzle runner 9a. Further, it may be provided on the connecting runway 9c. When the oil filler inlet 10 is provided in the connecting runner 9c, the thickness and width of the runner between the oil filler inlet 10 and the hub runner 9a, and the oil filler inlet 10 and the blade runner 9b By making a difference depending on the flow rate of the fat that requires the wall thickness and width of the runner, the amount of the fat can be adjusted.

[0033] Further, since the blade 3 has a hollow shape and the blade runner 9b is provided around the opening 3b, the hollow shape can reduce the weight, and the resin can easily flow around the entire mold when the blade 3 is formed. As a result, the wing 3 can be made thinner and lighter. The light weight reduces the weight at the outer periphery of the fan 1 with respect to the rotation center of the fan 1, thereby reducing the centrifugal force during rotation and reducing the stress applied to the base of the main plate that is the base of the blade 3. The 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 between the blade 3 and the main plate 2 where the stress is concentrated can be increased by the blade runner 9b. As described above, the fluidity of the resin can be improved by the blade runner 9b to improve the formability, and the strength of the turbofan can be improved.

[0034] Further, as described above, a plurality of radials are provided in the hub 2a, and the hub runner 9a is formed around the base of each of the blades 3 and the hub 3a is formed by injecting the grease during molding to form the hub 2a. , A blade runner 9b that forms a blade 3 by injecting the resin during molding, and a hub runner 9c that connects each of the hub runner 9a and the blade runner 9b located in the vicinity thereof. Thus, the runner 9 is formed to be 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, it flows in the opposite direction after it is divided into the directional grease at the center of rotation and the directional grease at the outer peripheral side. As it flows through Nagu Yudo 9, it flows to the main plate 2 around it.

As described above, the flow direction of the resin becomes relatively simple, so that the part where the resin-bound joint part A is formed can be clearly predicted. In addition, the resin can flow smoothly, and the moldability can be improved and the highly reliable fan 1 can be obtained. In addition, shorten the distance of Therefore, the strength of the turbo fan can be prevented.

[0035] In addition, in this embodiment, the number of the resin merging portions A is smaller than that in the conventional configuration in which the resin merging portions are also formed by the resin injected from one resin injection port. The mold design can be reduced and the mold design can be simplified, and the generation of cavities and local thinning of the wall thickness due to unevenness of the hot water can be prevented.

FIG. 6 is an explanatory view showing a part of FIG. 1 (b) in an enlarged manner. As shown in the figure, in the fan according to this embodiment, on the wall surface constituting the hub 2a of the fan external air passage 7, the hub runner 9a having a wall thickness tl extends from the hub 2a having a wall thickness tO. , Projecting to the fan external air passage 7 side by a wall thickness difference (tl tO). The motor cooling hole 5 is disposed on the extension line on the rotation center side of the hub runner 9a. For this reason, the runner 9a for the hub functions as a wind guide plate, and induces a directional airflow G to the motor cooling hole 5. The hub runway 9a serves as a wind guide plate for the airflow G, thereby increasing the airflow flowing on the surface of the motor disposed in the portion surrounded by the hub 2a and promoting the cooling of the motor. Normally, temperature protection control is performed to stop energization of the motor when the motor temperature rises above a certain temperature, but the efficiency of the temperature protection control is not executed by promoting motor cooling. I can drive well. Furthermore, it can prevent the motor from getting damaged due to high temperature.

[0037] In this manner, the runner 9a for the hub increases the air flow flowing on the surface of the motor because the surface force of the main plate 2 of the hub 2a protrudes toward the fan external air passage 7 on the motor arrangement side. The cooling of the motor can be promoted, the reliability is high, and the turbo fan can be obtained.

[0038] The shape of the fan according to this embodiment is such that a set composed of the blade 3, the blade runner 9b, the hub runner 9a, the connecting runner 9c, and the motor cooling hole 5 is centered on the rotation axis O. A plurality of sets are provided radially. That is, for one blade 3, the arrangement power of the oil 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 All the blades 3 constituting the fan 1 Is almost the same. Therefore, if substantially the same amount of the 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 generation of cavities and local thinning of the wall thickness due to unevenness of the hot water as a whole, and has the effect of obtaining a highly reliable turbo fan. In addition, for example, by changing the circumferential pitch, the amount of grease required for each set consisting of the blade 3, the blade runner 9b, the hub runner 9a, the connecting runner 9c, and the motor cooling hole 5 is increased. If they are different, by changing the amount of the resin injected from the resin injection port 10 according to the amount, it can be molded under the same molding conditions, and the same effect as described above can be obtained.

[0039] Further, by providing the same number of motor cooling holes 5 and runners 9a for the hub, the arrangement relationship of the blades 3 with respect to the motor cooling holes 5 is substantially the same as that of the motor cooling holes 5 constituting the fan 1. Can be. For this reason, the turbulent flow E2 flowing 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 runner 9b. In other words, each of the turbulent flows E2 flowing out of the motor cooling hole 5 flows between the blades 3 and 3, and does not directly collide with each other. A fan is obtained. Here, the number of the motor cooling holes 5 and the hub runners 9a is the same. The number of the motor cooling holes 5 may be smaller than that of the hub runners 9a. For example, it is not necessary to provide the motor cooling hole 5 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 joint A of the knob 2a and at an equal position with respect to the rotation center O, the strength is highly reliable and the molding conditions are uniform to some extent. As a whole, it is possible to obtain a turbofan that can prevent 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 hub runners 9a, a more reliable turbo fan can be obtained because molding can be performed under even molding conditions.

In addition, as shown in FIG. 1, the shape of this fan is a combination of a blade 3, a blade runner 9 b, a hub runner 9 a, a connecting runner 9 c, and a motor cooling hole 5. A plurality of sets are provided radially around the center, 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 discharged from the blade 3 from having periodicity. For this reason, noise caused by the rotation speed of the fan can be prevented, and quietness is maintained for hearing.

[0041] In this way, by providing a plurality of sets each including the blade 3, the blade runner 9b, the hub runner 9a, the connecting runner 9c, and the motor cooling hole 5 radially about the rotation axis, The arrangement of the oil filler inlet 10, the hub runner 9a, the vane runner 9b, and the motor cooling hole 5 is almost the same for one blade 3. Therefore, the molding conditions can be made equal, the generation of cavities due to unevenness in hot water and the local thinning of the wall thickness can be prevented, and a highly reliable turbo fan can be obtained.

In addition, in the group composed of the blade 3, the blade runner 9b, the hub runner 9a, the connecting runner 9c, and the motor cooling hole 5, at least one of the angles formed by the adjacent pairs is set as another angle. By configuring differently, the effect of reducing noise can be obtained.

[0042] Further, if the same number of motor cooling holes 5 as the nozzle runner 9a are provided, the arrangement relationship between the motor cooling holes 5 and the blades 3 can be made equal. The flow E2 that flows out through the motor cooling hole 5 can smoothly flow between the blades to the outside, and noise can be reduced.

Here, the fan forming step will be described with reference to FIG. FIG. 7 is a flowchart showing the fan forming process. A mold for forming the fan 1 having the shape shown in FIGS. 1 to 6 is fixed (ST1), and thermoplastic resin is injected from the resin injection port 10 (ST2). The injected resin flows through the hub runner 9a, the connecting runner 9c, and the blade runner 9b, and further spreads from the runner 9 to the main plate 2 and the blade 3. Grease fills the entire fan in approximately a few milliseconds. Next, it is cooled to cure the thermoplastic resin (ST3), and after it is 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). Further, the process proceeds to a process such as attaching a motor shaft.

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 main plate 2 except for the runner 9 is tO, the thickness of the hub runner 9a is tl, and the blade is 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. Make at least the wall thicknesses tl, t2, and t3 thicker than the wall thickness tO. The runner 9 may have a molding error or a corner having a rounded corner. However, the runner 9 has the largest wall thickness. As shown in the figure, the wall thickness of the runner 9 includes the thickness of the main plate 2 and the portion where the main plate surface force protrudes.

Fig. 8 is a graph showing the ratio of the wall thickness tl of the hub runner 9a and the minimum wall thickness tO of the main plate 2 other than the runner tO to tl ZtO. The horizontal axis represents tlZtO and the vertical axis represents the molding time ( sec). Here, the formation time indicates the time from ST2 to ST4 in the flowchart shown in FIG. 7, and is the time from injection of the resin to cooling and removal. [0045] As shown in the graph of FIG. 8, when tlZtO is 1.0 or less, that is, when the thickness tl of the hub runner 9a is equal to or less than the minimum thickness tO of the portion other than the runner of the main plate 2. However, the runner 9a is thinner and the resin is poorer around the resin, so it takes time for the resin to move around the entire mold, increasing the molding time. In addition, when tl / tO is larger than 2.0, that is, when the wall thickness tl of the hub runner 9a is larger than twice the minimum thickness tO of the main plate 2 other than the runner, It takes time to cool down and the time to take out becomes longer. As a result, if the range is 1. l≤tlZtO≤2, the molding time can be shortened compared to the case of at least the same wall thickness (tlZtO = l. 0). By shortening the molding time, the amount of production can be increased, and further, the electricity bill that can be consumed by the molding machine can be reduced, thereby saving energy.

FIG. 9 is a graph showing the molding time with respect to the ratio t2Z tO of the thickness t2 of the wing runner 9b and the minimum thickness tO of the main plate 2 other than the runner, where t2ZtO is on the horizontal axis and t2ZtO is on the vertical axis. Indicates molding time (sec). Here, the formation time is the time from ST2 to ST4 in the flowchart shown in FIG. 7, and is the time from injection of the resin to cooling and removal.

As shown in the graph of Fig. 9, when t2ZtO 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 tO of the portion other than the runner of the main plate 2, the runner 9b is thinner and the resin is not good around the resin. It takes time for the resin to move around the entire mold, which increases the molding time. In addition, if t2ZtO is greater than 2.0, that is, if the thickness t2 of the blade runner 9b is greater than twice the minimum thickness tO of the portion other than the runner of the main plate 2, the cooling of the grease will be reduced. Time takes a long time to take out. As a result, if the range is 1. l≤t2ZtO≤2, the molding time can be shortened compared to at least the same thickness (t2ZtO = l. 0). By shortening the molding time, it is possible to increase the production volume, and further reduce the electricity cost that is required by the molding machine, thereby saving energy.

[0047] Therefore, the ratio between the thickness tl of the runner 9a for the hub and the minimum thickness tO of the portion excluding the runner 9 of the main plate 2 If the ratio tlZtO is 1. l≤tlZtO≤2, the same meat Compared to the case of a thickness (tlZtO = l), there is an effect that the molding time can be shortened. Also, the ratio of the thickness t2 of the wing runner 9b and the minimum thickness tO of the portion excluding the runner 9 of the main plate 2 If t2ZtO is in the range of l≤t2ZtO≤2, the same thickness (t2ZtO = Compared with the case of l), there is an effect that the molding time can be shortened. In particular, the wall thickness tl, t2 of runner 9 should be less than twice the minimum wall thickness tO of main plate 2, and By setting an upper limit on the wall thickness, the molding time can be shortened, the amount of the resin can be reduced, and the weight of the fan 1 can be reduced and the cost can be reduced.

Here, the wall thickness tl of the hub runner 9a and the wall thickness t2 of the blade runner 9b are described separately. However, either one may be configured to satisfy either, or both may be satisfied. Also good. If both are satisfied, the molding time can be shortened and it is effective.

[0048] In this way, the thickness of at least one of the thickness of the hub runner 9a and the thickness of the blade runner 9b is t, and the minimum thickness of the portion excluding the runner 9 of the main plate 2 is t. If t is tO, the ratio tZtO is 1

If it is in the range of i≤tZto≤2, the forming time can be shortened compared to the case of the same wall thickness (tZto = i).

[0049] Hereinafter, the shape of the blade 3 will be described.

The configuration of one blade 3 is shown in FIGS. 10 and 11 are explanatory views showing the blade 3 according to this embodiment. FIG. 10 (a) is a side view of one blade, and FIG. 10 (b) is a Z-Z line in FIG. 10 (a). Fig. 11 shows a vertical cross section taken along line YY in Fig. 10 (b). As shown in Fig. 10 (a), the blade inner hollow portion 3dc and the blade outer hollow portion 3dd of the blade hollow portion 3d are the main plate 2 at arbitrary angles Θ 1 and Θ 2 with respect to the straight line X parallel to the rotation axis. The blade opening 3b provided at the base is inclined toward the inside of the hollow shape by directing the blade suction side end 3e. Since the thickness of the blade 3 is almost uniform, the blade inner peripheral end 3a and the blade outer peripheral end 3c are also at an arbitrary angle 0 1 and Θ 2 from the blade opening 3b with respect to the straight line X parallel to the rotation axis. The blade suction side end 3e is inclined toward the inner side of the hollow shape by force.

In addition, 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 with respect to the rotation direction D of the blade 3. In this configuration, Θ3 and Θ4 are inclined from the blade opening 3b to the blade suction side end 3e to incline inside the hollow shape. Since the thickness of blade 3 is almost equal, blade front side 3f and blade rear side 3g are also at arbitrary angles Θ 3 and Θ 4 with respect to straight line X parallel to the rotation axis, from blade opening 3b to blade suction side The end 3e is inclined toward the inner side of the hollow shape.

That is, the blade 3 and the blade hollow portion 3d are directed from the main plate 2 toward the shroud 4 at a predetermined angle 0 1, 0 2,

It has a tapered shape with a gradient inclined inside the hollow at Θ 3 and Θ 4. For this reason, when the mold is removed from the fan molded body in the direction of the rotation axis, the resin can be smoothly lubricated by the inclination. The mold can be released from the mold, the blade 3 can be prevented from adhering to the mold and the blade 3 can be damaged, and the 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 by the outer standing surfaces 3a, 3c, 3f, 3g of the hollow blade 3, and the standing surfaces 3dc, 3dd, It is in close contact with the fan molded body at 3da and 3db. Here, both the outer and inner surfaces of the hollow are tapered from the base toward the standing direction. Therefore, the mold can be easily released outside the blade 3 and can be easily released inside the hollow of the blade 3.

In addition to this, by making the wing 3 hollow, the weight can be reduced compared to a non-hollow shape. In addition, when the blade 3 thickness is uneven, there is a problem that molding failure occurs due to uneven cooling and hardening time of the resin and the moldability is poor, but the thickness of the blade 3 is approximately equal. As a result, the cooling and curing time of the resin can be made almost uniform, molding defects can be prevented, and moldability can be improved.

[0051] In this way, the disk-shaped main plate 2, the convex hub 2a formed by projecting the central portion of the main plate 2 in the rotation axis direction, and the protrusion of the knob 2a with the outer peripheral side flat plate portion of the main plate 2 as the base. A plurality of hollow-shaped blades 3 having an opening 3b at the base and standing up in the direction, the outer standing surfaces 3a, 3g, 3c, 3f of the hollow-shaped blade 3 and the hollow inner standing surfaces By tilting 3da, 3db, 3dc, and 3dd to the inside of the hollow and forming the base force taper on the outside and inside of the blade 3, the mold can be easily released, and the blade 3 adheres to the mold. It is possible to prevent the blade 3 from being damaged.

Further, by making the blades 3 substantially uniform in thickness, 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.

[0052] FIG. 12 shows an angle θ1 with respect to the rotation axis of the blade inner peripheral end 3a, an angle Θ2 with respect to the rotation axis of the blade outer peripheral end 3c, and an inclination angle Θ with respect to the rotation axis of the blade front hollow portion 3da 3 and the blade rear hollow part 3db tilt angle with respect to the rotation axis Θ 4 is tilted at the same angle Θ, and the fan forming time (sec) and noise value (dB) when the tilt angle Θ is changed The horizontal axis shows the tilt angle Θ, and the vertical axis shows the molding time (sec) and noise level (dB). This noise level (dB) was measured at a point 2m below the fan. Further, the molding time is ST2 to ST4 in the flowchart showing the molding process shown in FIG.

[0053] The molding time will be described based on the graph shown in FIG. When the inclination angle θ <0 °, the blade 3 has a shape that expands toward the main plate 2 side force shroud 4 side, so that the mold cannot be released and is impossible. When 0 = 0 °, that is, when it is not tilted with respect to the rotation axis, the friction between the blade 3 and the mold is so great that the blade 3 will adhere to the mold and break if it is not released slowly. Therefore, a long molding time is required. On the other hand, by providing the inclination angle Θ, the mold release becomes easy and the mold release time can be shortened. Furthermore, the cooling area is increased as the surface area of the blade 3 is increased, so that 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 1Z2 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, the noise value will be described 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 3 becomes narrow and the passing wind speed increases, resulting in increased noise. According to the measurement results in Fig. 12, when the tilt angle Θ is tilted more than 3 °, the noise increases. For this reason, if the tilt angle 0 is configured in the range of 1 ° ≤ Θ ≤ 3 °, good noise values can be maintained.

From the above results, a turbo fan with small noise change and high formability can be obtained by setting the tilt angle 0 to the range of 1 ° ≤ Θ ≤ 3 °.

[0055] In this way, the outer standing surfaces 3a, 3g, 3c, 3f and the hollow inner standing surfaces 3da, 3db, 3dc, 3dd of the hollow wing 3 are inclined toward the hollow inner side to obtain a predetermined inclination. By setting each angle Θ within the range of 1 ° ≤ Θ ≤ 3 °, it is possible to obtain a highly formable turbofan with small noise change.

[0056] 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 of the blade have the same inclination angle with respect to the rotation axis. Although they are tilted inside the hollow at Θ, the same effect can be achieved by tilting them at different angles.

Also, each thickness of the blade inner end 3a, the blade outer end 3c, the blade suction end 3e, the front blade front side 3f, and the rear blade rear side 3g with respect to the rotation direction of the blade. Is a force that makes the blades 3 almost uniform wall thickness. . The blade inner peripheral end 3a and the blade outer peripheral end 3c have a small width in the rotational direction, and it is difficult to configure the same thickness at this portion. The thickness of the blade 3 should be made almost uniform within a certain range of fluctuation. By configuring the wall thickness uniformly, when the resin is evenly injected, it is cooled evenly, so that a good molded body can be obtained.

[0057] In this embodiment, the central portion of the wing 3 is constructed so that the base force of the main plate 2 is also erected perpendicularly to the protruding direction of the hub 2a, and the erection surfaces on the outer side and the hollow inner side of the wing 3 are arranged in the hollow inner By inclining to, the above effects can be obtained. In this configuration, the mold is released by separating the mold in the direction of the rotation axis and parallel to the rotation axis. On the other hand, for example, the mold may be released by releasing it while rotating it about the rotation axis in the direction of the rotation axis. When rotating and releasing, the center of the blade 3 is the base force of the main plate 2 and the base force of the main plate 2 is not perpendicular to the projecting direction of the hub 2a. The portion 3e has a shape inclined at a predetermined angle in the direction of rotational release by force. Even when the blade 3 is tilted in this way, it is possible to easily release the mold by inclining the standing surfaces 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.

[0058] Next, a turbofan 1 formed with the runner 9 as another structure will be described. FIG. 13 is a bottom view showing a turbofan 1 formed 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 integral hot water. Constructed as a road.

[0059] A part of the resin injected from the resin injection port 10 at the time of molding to the turbofan configured as described above is directed from the hub runner 9a to the cooling hole runner 9d. The current flows further toward the hub 2a and boss 2c. At this time, the oil 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 surely rejoins and flows toward the boss 2 c. Thus, by providing the cooling hole runner 9d, the moldability can be improved by improving the fluidity of the grease around the motor cooling hole 5.

In addition, by providing a cooling hole runner 9d on the outer periphery of the motor cooling hole 5, a motor that is an opening is provided. Around the cooling hole 5, the cooling hole runner 9 d remains solid, 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 if an impact is applied.

FIG. 14 is a bottom view showing a turbofan 1 formed 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 part 2d, which is a part thicker than the main part 2 except for the runner.

[0061] A part of the oil that flows into the turbofan configured in this way from the oil injection port 10 during molding flows from the hub runner 9a to the cooling hole runner 9d. Furthermore, it flows through the thick part 2d on the upper part of the hub to form this part. Similar to the configuration shown in FIG. 13, the oil flowing through the hub runner 9a is divided into two directions by the cooling hole runner 9d and flows through the cooling hole runner 9d provided around the motor cooling hole 5. . Then, after flowing around the motor cooling hole 5, it flows to the hub upper wall thickness portion 2d connected thereto, and this portion is molded.

[0062] Similar to 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 that is the opening. The thickness of the motor cooling hole 5 around the motor cooling hole 5 that is configured to be thick and easily reduced in strength can be improved. In this way, by providing the cooling hole runner 9d, it is possible to improve the formability and strength by improving the fluidity of the resin around the motor cooling hole 5, and against breakage even if the impact is strong. And a durable turbo fan.

Further, in this configuration, the cooling hole runner 9d is directly connected to the hub upper thick part 2d in the vicinity of the boss which is thicker than the thickness of the knob inclined surface. For this reason, the resin flows smoothly up to the hub upper thick part 2d, and the resin flowing through the cooling hole runner 9d is in front of the motor cooling hole 5 in the direction of the resin flow, that is, the boss 2c of the motor cooling hole 5. Re-merge on the side more securely and flow to the hub upper thick part 2d. Accordingly, it is possible to reliably inject the resin around the motor cooling hole 5 which is the opening with the thickness of the cooling hole runner 9d, and to improve the strength around the motor cooling hole 5 where the strength tends to decrease at the opening. . [0063] In this way, by providing the cooling hole runner 9d that is connected to the hub runner 9a and is formed so as to surround the motor cooling hole 5, the periphery of the motor cooling hole 5 is removed. A turbofan capable of improving moldability and improving strength by improving oil fluidity is obtained.

[0064] Next, the blade runner 9b will be described in detail. FIG. 15 relates to this embodiment, and is a perspective view of a turbo fan according to another configuration example as seen from the bottom surface, FIG. 16 is a partial perspective view showing a part of FIG. 15 in an enlarged manner, FIG. 17 and FIG. FIG. 17 (a) shows a side surface of the blade 3, and FIG. 17 (b) shows a cross section taken along line Z-Z in FIG. 17 (a). FIG. 18 (a) shows a cross section taken along line Y—Y of FIG. 17 (b), and FIG. 18 (b) shows an enlarged view of a circle M in FIG. 18 (a). 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 9b is provided around the opening of the hollow blade 3, and the blade runner 9b on the front side of the blade rotation direction is the blade forward runner 9ba, the blade rotation direction. The wing runner 9b on the rear side is called the wing rear runner 9bb. Then, the difference between the protruding height of the main runner 9ba on the main plate 2 and the protruding height of the main plate 2 on the main runner 9b on the rear side of the blade is different from that of the main runner 9ba. Raise the blade by a predetermined height above the protruding height of the rear runner 9bb and project it to the outside of the fan.

[0066] In the vicinity of the main plate 2 in the blade opening 3b, the air flow C generated when the fan 1 rotates in the direction D is curved outward by hitting the blade front runner 9ba, drawing a parabola, and forming a parabola. It flows to approach the main plate 2 again on the 9b side. This situation is shown enlarged in FIG. Here, when the blade front runner 9ba and the blade rear runner 9bb are at the same height, the flow near the main plate 2 collides with the corner of the blade rear runner 9bb after the blade front runner 9ba is detached when the fan rotates. However, there was a problem that noise was generated in a narrow band due to pressure fluctuation.

[0067] On the other hand, as shown in Fig. 18 (b), when the blade front runner 9ba is raised by a predetermined height compared to the blade rear runner 9bb, the flow in the vicinity of the blade opening 3b is shown in Fig. 18 (a). Flows as indicated by arrow C in. That is, the flow after leaving the blade front runner 9ba draws a parabola that curves outside the main plate 2, and approaches the main plate 2 again in the rotational direction of the blade rear runner 9bb. Increasing the wing front runner 9ba increases the distance from the main plate 2 when the airflow C also curves outwardly on the surface force of the main plate 2. The 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 way, the airflow C can be prevented from colliding with the corner of the blade rear runner 9bb, and noise can be reduced.

In addition, since the thickness of the front runner 9ba for the wings is increased, it is easier for the grease to flow into the wing 3 and it is possible to prevent sink marks, and the strength at the front runner 9ba is also improved. Will also improve.

[0068] In this way, the blade front runner 9ba is configured to be higher than the blade rear runner 9bb by a predetermined height so that it protrudes to the outside of the fan. The fan can be prevented from being damaged during transportation, and a highly reliable and low noise turbo fan can be obtained.

[0069] Here, with respect to the maximum opening diameter F of the blade opening 3b of the hollow structure shown in FIG. 19, the blade front runner 9ba and the blade rear of the blade runner 9b formed so as to surround the periphery of the blade 3 The height difference Δt from the runway 9bb (shown in Fig. 18 (b)) will be further explained. 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 At is the difference between the height of the blade front runner 9ba and the height of the blade rear runner 9bb.

If 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 At is too large, the flow separates in the blade front runner 9ba and a peak sound is generated due to the rotational speed. Thus, there is a desirable range in the height difference At between the blade front runner 9ba and the blade rear runner 9bb.

[0070] However, the flow across the blade opening 3b is also related to the maximum opening diameter F of the blade opening 3b, which is not only the difference in height At between the blade front runner 9ba and the blade rear runner 9bb. Therefore, the ratio (AtZF) 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 (AtZF)% and the noise value (dB) at the same air volume. The horizontal axis shows the ratio AtZF (%) and the vertical axis shows the noise value (dB). This noise level was measured just under the fan and about 2m away from the fan.

[0071] Based on the measurement results shown in Fig. 20, the blade front runner 9ba and the blade rear runner 9bb protrude from the surface of the main plate 2 by configuring so that at least 4% ≤ AtZF ≤ 22%. The same height That is, a turbo fan with lower noise than that at At = 0 (At / F = 0) can be obtained.

When AtZF <4%, the difference between the runners with respect to the maximum opening diameter F Att is small and the flow away from the front runner 9ba is likely to collide with the corner of the rear runner 9bb. As a result, pressure fluctuations occur and noise is generated in a narrow band. On the other hand, in the case of 22% AtZF, the difference in the protrusion height of the runner with respect to the maximum opening diameter F is large. Noise increases due to peak sound.

[0072] 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 in the range of 4% ≤AtZF≤22%. If configured, the flow in the vicinity of the main plate 2 during fan rotation can be prevented from colliding at the corner of the blade runner 9bb after the blade front runner 9ba is separated, causing pressure fluctuations and generating noise in a narrow band. Then, the flow after the blade front runner 9ba detaches can be reattached smoothly by moving the reattachment point of the blade rear runner 9bb to the rear in the rotational direction of the blade rear opening 3g. In addition, since the protruding height of the blade front runner 9ba is too high, the generation of peak sound due to the rotational speed at which the flow is separated in the blade front runner 9ba can be suppressed, and noise noise can be prevented. For these reasons, noise can be reduced.

[0073] Therefore, the turbofan has a difference between the protrusion height of the front runner 9ba and the rear runner 9bb relative to the maximum opening diameter F of the blade opening 3b having a hollow structure. The ratio of At is AtZF, 4% ≤ AtZF≤ By configuring so as to be in the range of 22%, noise can be reduced.

[0074] 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 turbo fan with high strength and reliability can be obtained. In addition, by providing the hub runner 9a, the resin can flow to the boss 2c near the top of the main plate 2 and immediately improve the resin fluidity in the entire main plate. In addition, since the blades 3 are hollow, the entire turbofan can be reduced in weight. Furthermore, since the blade hollow portion 3d has a tapering shape having a forming draft inclined at a predetermined angle Θ from the main plate 2 toward the shroud 4, the blade 3 is attached to the mold and the blade is damaged. Can be prevented and formability is high. In addition, since the thickness of the blade 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 unevenness of the cooling and hardening time. [0075] In this embodiment, the plurality of blades 3 is composed of seven blades, and the number of power blades 3 described for the fan in which seven runners 9 and seven motor cooling holes 5 are provided accordingly. The number of runners 9 and the number of motor cooling holes 5 are not limited to this.

Further, the force in which the number of motor cooling holes 5 is configured to be the same as the number of nozzle runners 9a. As described above, the number of motor cooling holes 5 may be smaller than the number of nozzle runners 9a. However, if the motor cooling hole 5 is arranged on the extended line of the nozzle runner 9a, a high strength can be obtained without connecting the motor cooling hole 5 and the resin joining portion. 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 extended line of the nozzle runner 9a. If the number of motor cooling holes 5 is reduced, the function of cooling the motor is reduced. The strength of the fan hub 2a can be increased.

FIG. 21 to FIG. 23 show a configuration example in which 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 perspective view showing the air conditioner viewed from the room, 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 is shown in which the turbo fan 1 is mounted on, for example, a ceiling-embedded air conditioner.

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 body, and a filter 20 for removing air 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 each panel blower outlet 13b is provided with the wind direction vane 13c.

In addition, as shown in FIG. 22, the air conditioner main body 12 is installed in a direction to be a top plate 12c above the room 19, and a side plate 12d is attached around the top plate 12c. It is installed so that the lower side is open. The main body suction port 12a disposed at the center of the lower surface of the air conditioner main body 12 is disposed so as to communicate with the suction grill 13a of the decorative panel 13. Further, the main body outlet 12b arranged around the main body inlet 12a is arranged to communicate with the panel outlet 13b. The air conditioner 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.

[0079] In addition, the blowout air path from between the blades, which is the airflow blowing portion of the fan 1, to the panel blower outlet 13b The heat exchange ^^ 15 is arranged. 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 body 12 are laminated at predetermined intervals. In this configuration, the heat transfer tubes 15b are penetrated in multiple stages from the stacking direction.

As shown in FIG. 23, the heat exchanger 15 is formed in a substantially C shape so as to surround the outer peripheral side of the turbofan 1. The heat transfer tube 15b at one of the two ends of the substantially C-shaped heat exchanger 15 has a header 16 for adjusting the amount of refrigerant to each heat transfer tube 15b, a connection pipe 18 between the distributor 17 and the outdoor unit. It is attached. For example, a refrigerant such as carbon dioxide and carbon dioxide is circulated in the heat transfer tube 15b.

[0080] With the air conditioner configured as described above, when the turbofan 1 rotates in the rotation direction D, the air in the room 19 passes through the suction grille 13a and the filter 20 of the decorative panel 13 and is removed, and the main body inlet 12a After passing through the bell mouth 14, it is sucked into the turbo fan 1. After that, it passes between the blades 3 of the turbo fan 1 and blows out toward the heat exchanger. 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. Thereafter, when the air is blown out from the main body outlet 12b and the panel outlet 13b toward the room 19, the wind direction is controlled by the wind direction vane 13c.

When the air conditioner is transported, the turbo fan 1 is normally 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.

[0082] By installing the turbofan 1 according to this embodiment in 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, it can be made thinner and lighter, and the weight of the entire product can be reduced. In addition, 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.

In addition, in the turbo fan 1 in which the motor cooling holes 5 and the blades 3 are unequal pitches, the turbulence of the airflow discharged to the outside of the motor cooling holes 5 force turbofan 1 and the airflow blown out from the blades 3 are Since it has no periodicity, it was possible to reduce the noise caused by the rotation speed of the fan and to reduce the noise. By installing this fan 1 in the air conditioner, the turbulence of the airflow that flows out of the fan 1 and flows to the panel outlet 13b is also reduced, so that the noise of the fan 1 can be reduced and used as an air conditioner. Furthermore, noise can be lowered and a quiet air conditioner can be obtained. In addition, since heat exchange with the refrigerant is performed with heat exchange 15 in a state where the turbulence of the airflow is reduced, an efficient air conditioner can be obtained.

[0083] Note that the present invention is not limited to the ceiling-embedded air conditioner shown in Figs. Here, the force showing the panel outlet 13b in the four directions on the ceiling may be provided in two directions so that the two panel outlets 13b face each other. Further, in a configuration in which the air conditioner main body is completely embedded in the ceiling, it may be installed in a state where the ceiling force protrudes. Moreover, it is not limited to being installed on the ceiling, and may be installed on a wall surface. By applying the turbo fan according to this embodiment to other air conditioners equipped with a turbo fan, it is possible to prevent fan breakage during product transportation, as described above, and with low noise, high product quality and quietness. This makes it possible to obtain an air conditioner that is light and transportable.

[0084] As described above, the turbo fan configured by at least one of the forces described in this embodiment and the heat exchange ^^ are provided, and the air sucked from the suction port by the turbo fan is converted into the heat exchanger. By constructing the heat exchange with the refrigerant at ^^ so that the outlet force is also blown out, an air conditioner that is highly reliable and lightweight and can reduce noise can be obtained.

Further, the present invention can be applied not only to an air conditioner but also to a ventilation fan or an air purifier equipped with a turbo fan, and the same effect as described above can be obtained.

Further, according to the present invention, the following effects can be obtained.

That is, a plurality of hub runners 9a that are continuous with the resin injection port 10 and are thicker than the thickness of the obliquely inclined surface of the main plate hub 2a and linearly extend in the fan radial direction are predetermined on the motor side surface of the main plate 2. When the resin flows from the hub runner 9a to the hub upper wall thickness portion 2d near the boss from the hub runner 9a, the resin junction A is impacted. However, it is formed between the motor cooling holes 5 without being connected to the motor cooling holes 5 which are openings, so that it easily flows up to the boss 2c and the moldability is improved. Because the part can be shortened, impact is applied to the axial direction of the turbofan 1 (vertical direction in Fig. 1 (b)) during transportation. Even if cracks occur, it is possible to improve the formability of the turbofan that is difficult to break and to improve the reliability against the impact of the turbofan.

[0086] Further, motor cooling holes 5 are arranged in the vicinity of the fan center side end 9al of the runner 9a for the hub, and at least the number of the motor cooling holes 5 and the runner 9a for the hub is the same. In the vicinity of the fan outer peripheral end 9a2 of the runner 9a, a blade inner peripheral end 3a is disposed, and the blade hot water is formed so as to surround the hub runner 9a and the opening 3b of the blade 3. Since the road 9b is connected by the connecting runner 9c, the resin joining portion A of the resin flowing out from the hub runner 9a is surely generated between the motor cooling holes 5. As a result, the turbo fan 1 is less likely to break even if an impact is applied in the axial direction of the turbo fan 1 during transportation (vertical direction in Fig. 1 (b)) and a crack occurs. High reliability against impact can be achieved. Also, since the hub runner 9a and the blade runner 9b are integrally formed, injection of the grease flowing from the filler inlet 10 between the hub runner 9a and the blade runner 9b is injected. The amount can be adjusted, and the generation of cavities and local thinning of the wall thickness due to unevenness in hot water can be prevented, and the strength can be prevented. In addition, the wing runner 9b makes it easier for the grease to go around, making it possible to reduce the thickness of the wing 3 and increase the thickness of the joint between the wing 3 and the main plate 2 where stress is concentrated. It is possible to improve both the formability by improving the strength of the turbofan.

[0087] Further, since the adjacent linear hub runners 9a are formed so as not to overlap each other, there are a wide variety of ribs that form a runner with respect to a single resin inlet 10 as in the prior art. Compared to the case of waving, 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, and the number of the resin merge parts A can be reduced and the die design can be simplified. At the same time, the generation of cavities and local thinning of the wall thickness due to uneven hot water can be prevented, and deterioration of the strength of the turbofan can be prevented.

[0088] Further, since the runner 9a for the hub is formed so as to protrude toward the fan external air passage 7 of the main plate, the wind guide plate for inducing a flow G directed toward the motor cooling hole 5 by the runner 9a for the hub. Can also be used. As a result, the air flowing on the surface of the fan motor 8 disposed on the fan external air passage 7 side of the hub 2a and fixed to the turbo fan 1 by the boss 2c is increased, and the motor cooling is interrupted. Therefore, the temperature protection control is not affected because the motor temperature rises, and further, the motor can be prevented from being damaged due to the high temperature. [0089] In addition, the filler inlet provided in the vicinity of the end on the inner peripheral side of the blade and the blade runner formed so as to surround the periphery of the opening on the outer side of the main plate of the blade having a hollow structure are connected by a connecting runner The blade inner hollow portion, the blade outer hollow portion, the blade front hollow portion surface, and the blade front hollow portion surface of the blade hollow portion are inclined at an arbitrary angle Θ with respect to the rotation axis, and the blade inner peripheral end The thickness of the blade, the blade outer edge, the blade suction side edge, and the blade front side and the rear blade rear side with respect to the blade rotation direction are almost the same. The main blade force toward the shroud side The wing and the blade hollow part are formed to have a tapered shape, so that the wing can be made lightweight because the wing is hollow, and the thickness of the wing is almost uniform. Molding failure due to uneven cooling and curing time of the resin that can occur when the thickness is uneven is less likely to occur and the moldability is good. In addition, since the blade and blade hollow part has a tapered shape with a forming draft inclined at a predetermined angle toward the main plate force shroud, the blade is attached to the mold by the mold release and the blade can be prevented from being damaged. Is expensive.

[0090] Further, a convex hub formed so as to cover the motor in the central portion has a plurality of motor cooling holes for communicating the motor and the inside of the fan, and a rotation shaft of the motor is provided in the central portion of the hub. A turbofan formed of a thermoplastic resin having a disk-shaped main plate having a boss as a fixed portion of the wing, a plurality of blades, and a shroud that connects the plurality of blades to form a suction air guide wall. In this case, a plurality of hot water for the hub that is continuous with the filler inlet provided in the flat portion of the main plate near the blade inner peripheral end and is linearly extended in the fan radial direction and is thicker than the thickness of the inclined surface of the main plate. There is a passage on the motor side surface of the main plate at a predetermined interval, and the resin joint formed between adjacent hub runners is not connected to at least the motor cooling hole so that a runner is formed and the blade hollow Blade inner peripheral hollow part, blade outer peripheral hollow part, blade front hollow part surface, blade rear The surface of the hollow part is an inclined surface with 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 blade front side forward of the blade rotation direction, Each thickness of the rear side of the rear wing is formed so that the entire wing has almost the same thickness, and the wing and the wing hollow part from the main plate to the shroud side are formed to have a tapered shape. The hub runner is formed so that the hub and main plate have high grease fluidity and high moldability, and the resin junction is at least in communication with the motor cooling hole. Prevents damage to the fan due to impact, etc., and because the blades are hollow, the entire turbofan can be made lighter and the wall thickness is almost uniform Therefore, 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, the blade and blade hollow part has a tapering shape with a forming draft inclined by a predetermined angle toward the shroud, so that the blade adheres to the mold release and the blade can be prevented from being damaged. high.

In addition, the light 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 blades. Strength can be improved, and damage to the turbofan during rotation can be prevented. As a result, it is possible to obtain a highly reliable turbo fan that is lightweight, has high moldability and high strength.

[0091] Further, the blade inner hollow surface, the blade outer hollow surface, the blade front hollow surface, and the blade rear hollow surface of the blade hollow portion are inclined at an angle of inclination Θ = 1 to 3 ° with respect to the rotation axis. The thicknesses of the blade inner circumferential edge, blade outer circumferential edge, blade suction suction edge, front blade front side and rear blade rear side with respect to the blade rotation direction It is formed so that it has almost the same thickness as a whole, and the wing and the wing hollow part are tapered toward the main plate force shroud side. Since the thickness is almost uniform, molding defects due to uneven cooling and curing time of the resin, which can occur when the blade thickness is uneven, are less likely to occur. In addition, the blade and blade hollow part has a tapering shape with a forming draft inclined at a predetermined angle from the main plate to the shroud, so that the blade is attached to the mold by the mold release and the blade is prevented from being damaged, and the moldability is high. . Also, at least the noise change is small and not bad. From the above results, it is possible to obtain a high-performance turbofan with a small noise change if the inclination angle is at least 1 ° to 3 °.

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 Rotating center of the fan The runner 9a for the hub that extends linearly from the flange in the radial direction is also the blade 3, the single coolant inlet 10 at an unequal pitch relative to the motor cooling hole 5, the runner 9a for the hub, Since the arrangement of runner 9b and motor cooling hole 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. Can be prevented. Also, since the arrangement relationship between the motor cooling hole 5 and the blade 3 is the same, the turbulent flow E2 that flows 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 the pressure It is possible to obtain a turbo fan that is not subject to large fluctuations and can reduce noise.

[0093] In addition, 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 that time, there is a cooling hole runner 9d on the outer periphery of the motor cooling hole 5, and after refilling the resin, it will surely recombine at the rear of the motor cooling hole in the direction of oil flow and flow toward the boss 2c. There is no runner for the cooling hole in the periphery of the cooling hole, and it is less likely that it will be difficult to rejoin the cooling hole in the flow direction of the cooling hole. As a result, it is possible to improve the moldability and strength by improving the fluidity of the oil around the motor cooling hole, and to obtain a turbofan that is not easily broken even when an impact is applied.

[0094] Also, the ratio of the maximum wall thickness tl, t2 of the hub runner 9a and the blade runner 9b to the minimum wall thickness tO of the other part of the main plate 2 tlZt2 = l. 1-2, t2 / t0 = l. If it is in the range of 1 to 2, the molding time can be shortened compared to the case of at least the same wall thickness (tlZtO, t2ZtO =). It is also possible and energy saving.

[0095] The blade front runner of the blade rotation direction side portion 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 corresponding to the blade rotation direction opposite side surface portion. Since it is formed so that it protrudes to the outside of the fan, which is higher than the rear runner, the flow near the main plate during rotation collides with the corner of the runner behind the blade and causes pressure fluctuations. The noise generated in the narrow band is suppressed, and the flow direction after the runner is separated from the runner back runner. Can be achieved.

[0096] Further, 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 inside of the fan, and a rotation shaft of the motor is provided at the center of the hub. A turbofan formed of a thermoplastic resin having a disk-shaped main plate having a boss as a fixed portion of the wing, a plurality of blades, and a shroud that connects the plurality of blades to form a suction air guide wall. In this case, a plurality of hot water for the hub that is continuous with the filler inlet provided in the flat portion of the main plate near the blade inner peripheral end and is linearly extended in the fan radial direction and is thicker than the thickness of the inclined surface of the main plate. There is a passage on the motor side surface of the main plate at a predetermined interval, and the resin joint formed between adjacent hub runners is not connected to at least the motor cooling hole so that a runner is formed and the blade hollow Inside the wing The peripheral hollow part, the blade outer hollow part, the blade front hollow part surface, and the blade front hollow part surface are inclined at an arbitrary angle Θ with respect to the rotation axis, and the blade inner peripheral edge, blade outer peripheral edge, blade The suction side edge, front blade front side, and rear blade rear side relative to the blade rotation direction are formed to have the same thickness throughout the blade, and from the main plate toward the shroud. The blade and the blade hollow portion are formed to have a tapered shape, and are connected to a blade runner formed so as to surround the periphery of the opening on the main plate outer side of the blade having the hollow structure by a connecting runner. The runner front runner on the side corresponding to the blade rotation direction of the runner is formed so as to protrude to the outside of the fan which is higher than the runner rear runner on the side opposite to the blade rotation direction. Depending on the road, the lubrication fluidity at the hub and main plate is high and the moldability is high. Do communicated, as to form a runner hub, Ru since damage to the fan caused by an impact or the like during transportation Dekiru prevented. In addition, because the blades have a hollow structure, the entire turbofan can be made lighter, and because the 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 difficult to form. Is good. In addition, since the blade and the blade hollow part have a tapered shape with a forming draft inclined at a predetermined angle toward the main plate force shroud, the blade adheres to the mold and the blade is prevented from being damaged. high. Then, the flow near the main plate during rotation collides at the corner of the runner at the back of the blade and causes pressure fluctuations to generate noise in a narrow band. Noise can be reduced by moving the reattachment point on the rear of the runner rear runner to the rear of the blade rear opening and reattaching it smoothly. In addition, since the thickness of the front runner for the blades is increased, it is easier for the resin to flow into the blades during molding, and it is possible to prevent sink marks. Will also improve. From the above results, it is possible to obtain a low-noise turbo fan that is light and strong, can prevent damage to the fan during rotation and transportation.

The turbofan is formed so that the maximum opening diameter F of the blade opening 3b of the hollow structure and the height difference between the blade front runner 9ba and the blade rear runner 9bb At ratio AtZF = 4-22% Therefore, the flow in the vicinity of the main plate during rotation collides at the corner of the runner behind the blade and causes pressure fluctuations to generate noise in a narrow band. Noise can be reduced by moving the reattachment point of the runner rear runner to the rear in the direction of rotation and moving it to the rear of the rear opening and smoothly reattaching it. Also, the thickness of the runway ahead is too high The flow is separated in the hot water runway, and the generation of peak sound due to the rotation speed is suppressed, so that noise can be prevented and noise can be reduced.

[0098] In addition, an air conditioner in which the turbo fan 1 having any one of the configurations described in the first embodiment is mounted and a heat exchanger is disposed on the suction side or the outlet side of the turbo fan. Since it can be thinned by improving moldability, it can be made lighter and has high strength reliability. Therefore, when installed after transportation, the turbo fan 1 is not damaged by shocks such as vibration during transportation. High nature. In addition, the weight of the product can be reduced as the turbofan 1 becomes lighter.

[0099] Further, the side plate and the top plate of the air conditioner main body are formed of a sheet metal member, and at least a part of the air conditioner main body inside the side plate and the top plate constitutes an air passage wall surface with a heat insulating material, A motor and the turbo fan 1 having one of the configurations described in the first embodiment are mounted near the center of the interior of the air conditioner main body, and the suction port of the turbo fan is provided at the center of the lower surface of the air conditioner main body. A bell mouth that constitutes the main body suction port is disposed, 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 below the heat exchanger. And has a main body outlet at a position substantially along the air conditioner main body side plate around the main body inlet, and has a panel inlet and a panel outlet that respectively communicate with the main body inlet and the main body outlet. The panel is attached to the bottom of the main unit The use of a ceiling-embedded air conditioner makes it possible to reduce the thickness by improving the moldability of the turbofan 1, so that it can be made lighter and has high strength reliability. Product reliability is high with no damage caused by vibration or other shocks. In addition, the weight of the product can be reduced as the turbofan 1 becomes lighter.

Claims

The scope of the claims

[1] A disc-shaped main plate, and a convex hub formed by projecting the central portion of the main plate in the rotation axis direction;

A plurality of blades erected in the protruding direction of the hub with the outer peripheral side flat plate portion of the main plate as a base, and a motor cooling that cools a motor provided in the convex space surrounded by the hub. Holes, a plurality of hub runners that are provided radially in the hub and allow the thermoplastic resin to flow in at the time of molding, and the hub runner that flows out from the adjacent hub runner at the time of molding. A turbofan comprising: a resin merging portion formed by abutting a thermoplastic resin, wherein the motor cooling hole is disposed so as to avoid the resin merging portion.

[2] The blade is a hollow shape having an opening in the base, and is provided around the base of each of the blades, and is located near each of the blade runners forming the blades and each of the hub runners. A connecting runner that couples the runner for the wing, and the thermoplasticity from the injection loca provided in any one of the runner for the hub, the connected runner, and the runner for the wing 2. The turbofan according to claim 1, wherein sallow is injected and flown into all of the runners.

[3] A disk-shaped main plate, a convex hub formed by projecting a 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 A plurality of hollow wings having openings in the base, a plurality of radial wings provided in the hub, and a hub runner for forming the hub by injecting thermoplastic resin during molding; and the base of each of the wings Connected hot water that is provided around and connects the blade runners that flow into the thermoplastic resin during the molding to form the blades, and each of the hub runners and the blade runners located in the vicinity thereof. A turbofan characterized by comprising a road.

[4] The plurality of motor cooling holes provided in the hub are arranged in a portion where the runner for the hub is extended to the rotation center side. Turbo fan.

5. The turbofan according to claim 4, wherein the same number of motor cooling holes and hub runners are provided.

[6] The runner for the hub projects to the motor arrangement side of the surface force of the main plate of the hub The turbofan according to any one of claims 1 to 5, wherein the turbofan is characterized by the above.

[7] The present invention is characterized in that 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 about the rotation axis. The turbo fan according to any one of claims 2 and 6, wherein the force is any one of claims 4 to 6.

8. The turbofan according to claim 7, wherein at least one of the angles formed by the adjacent groups is different from the other angles.

[9] The cooling hole runner connected to the runner for the hub and formed so as to surround the periphery of the motor cooling hole. The turbo fan according to claim 8!

[10] 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 defined as t, and the minimum thickness of the main plate excluding the runner is defined as to. When the ratio tZtO is 1.

The turbofan according to any one of claims 2 to 9, wherein the range is 1≤tZtO≤2.

[11] A disk-shaped main plate, a convex hub formed by projecting a 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 A plurality of hollow blades having an opening at the base, and a blade runner provided around the opening so as to protrude from the main plate in a direction opposite to the standing direction of the blade. The height of the protrusion of the blade runner positioned around the front in the rotational direction is set higher than the height of the protrusion of the blade runner located around the rear of the opening in the rotational direction. Robot fan.

[12] The diameter of the inscribed circle on the surface of the main plate of the opening is defined as the maximum opening width F, and At is the protrusion height of the blade runner positioned around the front of the opening in the rotation direction and the rotation of the opening. 12. The AtZF is set to a range of 0.04≤At / F≤0.22 when the difference from the protruding height of the runner for the wing located in the rearward direction of the direction is set. Turbo fan

[13] A disk-shaped main plate, a convex hub formed by projecting a 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 A plurality of hollow wings having an opening at the base, and an outer side and a middle of the hollow wings A turbofan characterized in that a standing surface on the air inner side is inclined toward the hollow inner side, and the base force is also tapered at the outer side of the blade and the inner side of the hollow.

14. The turbofan according to claim 13, wherein the thickness of the blades is substantially uniform.

[15] Assume that the standing surfaces on the outer side and the inner side of the hollow wing are inclined toward the hollow inner side at a predetermined inclination angle Θ with respect to the rotation axis, and each of the predetermined inclination angles Θ is 1 ° ≤ Θ≤3 The turbofan according to claim 13 or claim 14, wherein the turbofan is in a range of ° C.

[16] The turbofan according to any one of claims 1 to 15 and a heat exchanger ^^, and air sucked from the suction port by the turbofan is transferred to the refrigerant and heat by the heat exchanger ^. An air conditioner characterized in that the air conditioner is configured to be replaced and blown out from a blow-out port.