ES2589903T3 - Turbo fan and air conditioner - Google Patents

Abstract

A turbo fan (1) comprising: a disk-shaped main board (2); a projecting hub (2a) formed by projecting a central portion of the main plate (2) in a direction of the axis of rotation; and a plurality of blades (3) each of which is vertically provided in the projection direction of the hub (2a) by the use of a flat part on the outer periphery side of the main plate (2) as the base The turbo fan is characterized in that it further comprises: a plurality of engine cooling holes (5) that are formed in the hub (2a) in order to cool a motor (8) arranged in a space that has a projection shape surrounded by the bushing (2a); a plurality of bushing guide marks (9a) formed by solidifying the resin in the bushing guides, the bushing guides are provided radially in the bushing (2a) and by forming the bushing (2a) by means of the flow of a thermoplastic resin at the time of molding; and resin melting portions (A) each of which is formed by means of thermoplastic resin melting flowing out of the neighboring bushing guides at the time of molding, in which the engine cooling holes ( 5) are arranged in such a way that the resin melting portions (A) are avoided.

Description

DESCRIPTION

Turbo fan and air conditioner Background of the invention Field of the invention

The present invention relates to a turbo fan molded from a thermoplastic resin and an air conditioner in which the turbo fan is mounted.

Description of the related technique

There is a conventional turbo fan molded of a thermoplastic resin in which the rigidity of the turbo fan is ensured by means of ribs each constructed by means of a resin injected in order to carry out a lighter weight by means of reducing the thickness (see, for example, Japanese Patent Application No. 3,131,625 (p. 3 and 4 and FIGS. 1 and 3)).

There is also another turbo fan in which the material is reduced through the formation of a recess at an intersection of a vane and a main plate to carry out a cost reduction (see, for example, the Application for Utility Model Japanese Open to the Public Num. 4-116698 (page 1 and FIG. 1)).

In addition, there is another turbo fan including a plurality of vanes that have similar sectional shapes in which thickness gradually increases from a cover to a main plate, and the distance between neighboring vanes gradually narrows from the cover to the main board With the configuration, a time difference is created in the exhaust release vortices that flow from the cover to the main board in an exhaust port of the turbo fan, thereby preventing noise resonance and the like and reducing the noise (see, 20 for example, Japanese Patent Application No. 3,544,325 (pages 7 to 9, FIGS. 5 and 6)).

In addition, there is another turbo fan by the use of a thick hollow vane, which thereby shortens the cooling and hardening time at the time of molding, which prevents deformation at the time of cooling and hardening, and the reduction of plastic material (see, for example, the Japanese Utility Model Application Open to the Public 4-116699 (page 1 and FIG. 1)).

25 Description of the invention

Problem to be solved by the invention

The conventional turbo fan in Japanese Patent Application No. 3,131,625 (pages 3 and 4 and FIGS. 1 and 3) has reinforcement ribs to carry out a thinner main plate, the ribs also serve as a grna of a resin for improvement in molding capacity. However, the resistance of a fusion portion 30 of the resin, in which the resins flowing from the ribs fuse at the time of molding, is low. Specifically, the melting portion of the resin is placed almost the same distance from the neighboring ribs, and the strength of the portion is low. The conventional turbo fan has a front vane rib positioned near the front end of a vane and extending in the radial direction, a rear vane rib positioned near the rear end of the vane and extending in the direction 35 radial, a connection rib for the connection of the rib of the front vane and the rib of the rear vane, and a reinforcement rib of the vane. For the ribs, the resin is injected from the resin injection port.

When the resin injected from the resin injection port flows to the ribs, in each of the ribs of the front blade and the rib of the rear blade, the resin flows in two ways in the radial direction 40 next to the center of rotation and the side of the outer periphery. In the connection rib, the resin flows in a direction that has a component in the radial direction and a component in the circumferential direction. In the reinforcement rib of the vane, the resin flows in the opposite direction to the connection rib. That is, the resin injected from an injection port flows in the plurality of ribs that extend in the radial direction. Resins that flow out of the ribs fuse and the fusion portion of the resin is formed. The resin fusion portion is also formed between resins that flow out of neighboring resin injection ports. Consequently, a number of fusion portions of the resin are created in the entire turbo fan, and limits the improvement in the turbo fan resistance. Generally, a plurality of holes for cooling an engine is formed in a projected portion of a main plate near the axis of rotation. When the melting portion of the resin is formed in a cooling hole of the engine as an opening portion having a low resistance, the resistance becomes smaller. For example, when an impact is applied in a direction parallel to the axis of rotation for the turbo fan during transport or the like, a crack occurs in the fusion portion of the resin around the engine cooling hole. When the low resistance portions are connected, a problem occurs such that the crack extends. With the configuration of the cranes, the fusion portion of the resin can be extended to the outer peripheral end 55 of the fan. This causes a problem such that the crack that occurs in the fusion portion of the

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Resin extends to the outer peripheral end, the fan breaks easily, and the quality of the product deteriorates.

The configuration described in the Japanese Utility Model Application Open to Public No. 4-116698 (page 1 and FIG. 1) in which a recess is formed at the intersection of a pallet and a main board has the following problem. A flow along the surface of the main board is generated by rotating the turbo fan. The flow on the surface of the main board leaves a corner R at the upstream end of the recess and then collides with a corner R at the downstream end, whereby noise is generated by pressure fluctuations.

In the turbo fan described in Japanese Patent Application No. 3544325 (pages 7 to 9, FIGS. 5 and 6), the vane does not have a hollow structure and the thickness in portions of the vane is largely variable , so that there is a temperature difference in the portions of the blade at the time of molding. Consequently, a cavity is generated due to uneven flow of the resin and there is a reduction in local thickness (hereafter referred to as locally small thickness). This causes a problem in which the molding capacity deteriorates. Since the entire palette is made of a resin, compared to a pallet that has a hollow shape, a greater amount of resin is necessary. The fan becomes heavy and the cost of the fan becomes high. Consequently, an air conditioner in which the turbo fan is mounted becomes heavy. There is a problem in which the portability for the worker is low.

A centrifugal fan described in the Japanese Utility Model Application Application Open to Public No. 4-116699 (page 1 and FIG. 1) has a thick hollow vane. However, when the vane is too thick, the air passage area of the fan is reduced. Consequently, there is a possibility that noise may increase due to the increase in the air speed of the passage. The vane sections perpendicular to the axis of rotation are the same. When the pallet is released from a mold at the time of injection molding, there is no current. The fan has a problem in which the resin adheres to the mold and a breakage occurs.

US 2003/198556 describes a turbo fan and a mold used to make the turbo fan, which allows the turbo fan to be integrally molded by means of a single molding process. The turbo fan has a turntable coupled to an axis of a drive motor in its center, a plurality of vanes radially arranged in and integrally formed with a periphery of the turntable, and a ring-shaped cover formed integrally with the ends front of the vanes to face the turntable.

The present invention has been achieved to solve the problems as described above, and an objective of the invention is to obtain a reliable turbo fan that is prevented from breaking at the time of transport or the like by means of the implementation of an improvement in the molding capacity and resistance of the turbo fan made of a thermoplastic resin, and an air conditioner in which the turbo fan is mounted.

Another object of the invention is to obtain a turbo fan that performs a noise reduction and an air conditioner in which the turbo fan is mounted.

Means to solve the problem

In accordance with aspects of the present invention, a turbo fan and an air conditioner according to the appended claims are provided.

Effect of the invention

According to the invention, it is possible to prevent a fan from breaking due to an impact due to the configuration in which the resin fusion portion is not connected to the engine cooling hole. Consequently, resistance can be improved, and an effect can be obtained in which a reliable turbo fan is produced.

Brief description of the figures

FIGS. 1A and 1B are a plan view and a side view, respectively, of a turbo fan according to a first embodiment of the invention.

FIG. 2 is a perspective view of the turbo fan according to the first embodiment of the invention.

FIG. 3 is a view illustrating the turbo fan according to the first embodiment of the invention.

FIG. 4 is an enlarged view illustrating the turbo fan according to the first embodiment of the invention.

FIG. 5 is a view illustrating a cross section taken along line H1-H2 of FIG. 4, which shows the first embodiment of the invention.

FIG. 6 is an enlarged view illustrating a cross section taken along line O-O1-O2-O3 of FIG. 1A, which shows the first embodiment of the invention.

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FIG. 7 is a flow chart showing a fan molding process according to the first embodiment of the invention.

FIG. 8 is a graph showing the molding time (time from the injection of the resin until it is removed after cooling) with respect to the ratio t1 / t0 of the maximum thickness t1 of a bushing shaft 9a and the minimum thickness t0 of the other portion of a main board 2 in the first embodiment of the invention.

FIG. 9 is a graph showing the molding time (time from the injection of the resin until it is taken out after cooling) with respect to the ratio t2 / t0 of the maximum thickness t2 of a pallet blade 9b and the minimum thickness t0 of the other portion of the main board 2 in the first embodiment of the invention.

FIGS. 10A and 10B are views showing a palette according to the first embodiment of the invention. FIG. 10A is a side view showing a vane on the fan and FIG. 10B is a view showing a cross section taken along the Z-Z line of FIG. 10A.

FIG. 11 is an explanatory view showing the palette according to the first embodiment of the invention and showing a vertical section taken along the Y-Y line of FIG. 10B

FIG. 12 is a graph showing the molding time of the fan (sec.) And the noise value (dB) when the faces are standing on the outside of the blade and inside the hole are inclined at an angle of inclination 0 towards the inside of the gap with respect to the axis of rotation and the angle of inclination 0 is changed.

FIG. 13 is a bottom view showing a turbo molded fan with another configuration of grna according to the first embodiment of the invention.

FIG. 14 is a bottom view showing a turbo molded fan with another configuration of grna more in accordance with the first embodiment of the invention.

FIG. 15 is a perspective view showing the turbo fan that has another configuration, seen from below, according to the first embodiment of the invention.

FIG. 16 is a partially enlarged perspective view showing a part of the turbo fan according to the first embodiment of the invention.

FIGS. 17A and 17B are views illustrating a palette according to the first embodiment of the invention. FIG. 17A is a side view of a vane on a fan, and FIG. 17B is a view showing a cross section taken along the Z-Z line of FIG. 17A.

FIG. 18A and 18B are views illustrating a palette according to the first embodiment of the invention. FIG. 18A is a view showing a vertical section taken along the Y-Y line of FIG. 17B and FIG. 18B is a partially enlarged view of FIG. 18.

FIG. 19 is a view illustrating a part of the lower face of the turbo fan according to the first embodiment of the invention.

FIG. 20 is a graph showing the ratio between the maximum opening diameter F of an opening of the vane 3b having a hollow structure at the difference At between the height of a front grille of the vane 9ba and the height of a crane rear of the vane 9bb and the noise value with the same volume of air according to the first embodiment of the invention.

FIG. 21 is a perspective view showing a mounted air conditioner, seen from a room according to the first embodiment of the invention.

FIG. 22 is a view showing a vertical cross section of the air conditioner according to the first embodiment of the invention.

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

Description of the preferred embodiment

First Realization

A turbo fan (hereinafter, simply referred to as a fan) according to a first embodiment of the present invention will be described below with reference to the figures.

FIG. 1A is a plan view of a fan according to the embodiment seen from one side of the cover, and shows a vane by means of a partial cut of the cover outwards. FIG. 1B is a side view of the fan of FIG. 1A. The left half of FIG. 1B shows a side face, and the right half shows a longitudinal section taken along the line O-O1-O2-O3 of FIG. 1A. FIG. 2 is a perspective view

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which shows a lower face of the fan according to the embodiment, is dedr, seen from the side opposite the cover.

As shown in FIGS. 1A and 1B and FIG. 2, a fan 1 is constructed by means of a disk-shaped main plate 2. A central portion of the main plate 2 has a projected shape that projects in the direction of the rotation axis, and a motor (not shown) is arranged in the space surrounded by the projection. The projection will be called a bushing 2a. A protuberance 2c is formed in the center of the hub 2a, that is, in the center of the main plate 2, and the rod of an engine is fixed to the protuberance 2c. A portion on which the motor is mounted is called an outer fan of the main plate 2. On a flat plate portion on the outer peripheral side of the inner fan opposite the outer fan, a plurality of, for example, seven vanes is provided 3. In a portion connected to the boss 2c of the main plate 2, a thicker upper portion of bushing 2d is provided, which is thicker than a thickness t0 of an inclined face of bushing 2a.

The vane 3 uses, as a base portion, a flat portion on the outer peripheral side of the main plate 2 and has a hollow bag shape that is in an upright position from an opening of the vane 3b in the base portion in the direction of bushing projection 2a. In the base portion, an opening of the vane 3b is positioned between an end of the inner radius side of the vane 3a and an end of the outer radius side of the vane 3c. A central line 3a-3c of the opening of the vane 3b and the radius of the main plate 2 are arranged such that they intersect at a predetermined angle of, for example, about 45 °. As shown in FIG. 1A, a plurality of vanes 3 are arranged in variable steps such that at least part of the passage angles of the circumferential direction assembly 61, 62, 63, ..., and 67 with respect to the axis of rotation. In FIG. 1A, for example, 61 = 64 <63 = 66 = 67 <62 = 65.

The fan 1 is driven by the motor and rotates in the direction of the arrow D around a center of rotation O. A cover 4 is provided around the fan 1 in accordance with that shown in FIG. 1B and is fixed to each of the vanes 3 from above in FIG. 1 B.

An internal air duct of the fan 6 is formed when inserted between the cover 4 and the main plate 2 near the bushing 2a, and an external air duct of the fan 7 is constructed by the bushing 2a on the side where the motor is arranged . In the bushing 2a, the cooling holes of the motor 5 that are constituted by a plurality of openings are formed in almost equidistant positions from the center of rotation O around the center of rotation O, which thereby provides communication between the duct internal air fan 6 and the external air duct fan 7. In FIG. 1A, for example, seven engine cooling holes 5 are provided. Each of the engine cooling holes 5 is arranged in a straight line O-3a that connects one end of the inner radius side of the vane 3a and the center of rotation O. Like the vanes 3, the plurality of cooling holes of the motor 5 are also formed such that at least part of the passage angles of the circumferential steering assembly y1, y2, y3, ... , and y7 of the plurality of engine cooling holes 5 vain. In this case, the pass angles of the circumferential steering assembly y1, y2, Y3, ..., and y7 of the cooling holes of the motor 5 are set as, for example, y1 = Y4 <Y3 = y6 = Y7 < Y2 = Y5 in a manner similar to the passage angles of the circumferential steering assembly 6 of the vanes 3.

The main plate 2 and the vanes 3 are integrally molded by the use of a thermoplastic resin such as ABS or ASG (hereafter referred to simply as resin). In FIG. 2, the reference number 10 denotes a mark of a resin injection port used for the injection of the resin at the time of molding of the main plate 2 and the vanes 3. The mark 10 is positioned near a folding part between the bushing 2a and the flat part of the main plate 2 and near the end of the inner radius side of the vane 3a in the flat part and will be referred to as a resin injection port 10. The gmas 9 which serve as paths of The resin at the time of molding are formed in the fan. In a mold, the gm 9 corresponds to a portion that is a larger space in the direction of the thickness of the main parts of the main plate 2 so that the resin can pass easily. In the fan as a finished article, the resin in the grind 9 is solidified and maintained, and the thickness of the grind portion is greater than the minimum thickness t0 of the portion other than the crane in the main plate 2.

One of the ranges 9 is a bushing shaft 9a for the formation of the bushing at the time of molding. For example, seven gmas of bushing 9a are formed radially in bushing 2a and extend linearly in the radial direction of the fan from the resin injection ports 10 towards the center of rotation O without crossing other gmas to positions near the holes of engine cooling 5. Bushing 9a is thicker than the minimum thickness t0 on the inclined face of bushing 2a and has a predetermined thickness t1 (> t0). The cooling holes of the engine 5 are arranged near the ends on the central side of the fan of the bushing ranges 9a, and the ends of the inner radius side of the vane 3a of the vanes 3 are arranged near the other ends in the outer radius side of the fan of the bushing gmas 9a. In addition, a central line 11 in the direction of the width of each of the linear bushing ranges 9a is arranged such that it extends into the cooling hole of the engine 5. The end of the inner radius side of the vane 3a , the resin injection portion 10, the bushing gma 9a, and the engine cooling hole 5 are arranged such that they are positioned in an almost straight line that extends in the radial direction with the center of rotation O as the starting point In the embodiment, the passage angles of the assembly 6 in the circumferential direction of the vanes 3 are set as

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uneven passage angles, such that the cooling holes of the engine 5, the bushing ranges 9a, and the resin injection ports 10 are formed similarly in uneven steps with respect to the center of rotation O. When the angles of passage of the assembly 6 of the vanes 3 are identical angles of passage, the angles of passage of the assembly in the circumferential direction of the cooling holes of the motor 5, the gmas of bushing 9a, and the resin injection ports 10 are also identical angles of passage.

In the flat plate portion of the outer radius side of the main plate 2 as the base of the hollow vane 3, a vane gam 9b is formed around the opening of the vane 3b. Pallet gm 9b is a gma for the formation of pallet 3 when the resin is caused to flow at the time of molding. Like the bushing gma 9a, the vane gma 9b has a predetermined thickness t2 (> t0) greater than the thickness t0 of the flat plate portion of the outer radius side of the main board 2. A connecting gma 9c It is a GMA for connecting the bushing gma 9a and the paddle gma 9b. The connecting gam 9c is formed, for example, with the same thickness t1 as that of the bushing gma 9a and a width smaller than that of the bushing gma 9a and that of the vane gm 9b.

When the fan 1 rotates in the direction D, the ambient air is guided on the vanes 3 of the cover 4 and sucked into the interior of the cover 4, passes through an internal air duct of the fan 6, and blows out of the spaces between the vanes 3 on the periphery of the fan as shown by the arrows E1 in FIG. 2. At this time, the pressure in an internal air duct of the fan 6 is negative with respect to the pressure in an external air duct of the fan 7 in which the motor is connected. As shown in FIGS. 1B and 2, a part E2 of the air blowing out from the fan 1 passes through the cooling holes of the motor 5 that connect the internal air duct of the fan 6 to the external air duct of the fan 7 and flows into the external air duct of fan 7 while rotating due to friction with bushing 2a. The part E2 of the air flow passes through the cooling holes of the motor 5 and flows into the internal air duct of the fan 6 under negative pressure. A motor is mounted on the side of the external air duct of the fan 7 surrounded by the bushing 2a and fixed to the fan 1 in the boss 2c. With the air stream E2, the engine cools.

At the time of integrally molding the turbo fan with such a configuration by the use of a resin, the resin is injected from the plurality of resin injection ports 10 to a mold having a fan-shaped space. The resin injected from the resin injection ports 10 is carried to the gmas 9 as thick portions, flows throughout the fan, and the main plate 2 and the vanes 3 are integrally formed. FIG. 3 is a bottom view of the fan. The bushing ranges 9a are gmas each provided between one end of the center side 9a1 to one end of the outer radius side of the fan 9a2. The cooling holes of the motor 5 are arranged near the ends of the center side of the fan 9a1 and the ends of the inner radius side of the vane 3a are arranged near the ends of the outer radius side of the fan 9a2.

A part of the resin flows into the bushing ranges 9a and, after that, flows into the bushing 2a of the main plate and forms the portion. Another part flows from the connection ranges 9c to the vane ranges 9b, flows to the vanes 3 and the main plate 2 around the vanes 3, and forms the portions. The resin flow is shown by arrow B in FIG. 3. The resin flows through ranges 9 to the mold as shown by arrows B, and the resin flows from neighboring ranges 9, collides and merges into a fusion portion of the resin positioned such that be almost equidistant from neighboring gmas. The melting portion of the resin is indicated by a dashed line A.

The resin injected from the resin injection ports 10 and driven to the bushing ranges 9a flows smoothly in a direction towards the center of rotation O in the radial direction. In addition, the resin flowing in a bushing gma 9a flows to a neighboring bushing gma 9a, such that a fusion portion of the resin A is formed between the neighboring bushing glands 9a. Since the cooling holes of the motor 5 are arranged in such a way as to avoid the melting portions of the resin A, a melting portion of the resin A is formed near a cooling hole of the engine 5, not in relation to the cooling hole of the motor 5, but between the cooling holes of the motor 5 neighbors.

Since the fusion portion of the resin A is not coupled to the cooling hole of the motor 5 as an opening that has low impact resistance, the occurrence of a crack connected to the cooling hole of the motor 5 and the portion can be prevented of fusion of the resin A, and the resistance of the molded fan 1 can be improved. Therefore, even if an impact is applied in the direction of the rotation axis of the fan 1 at the time of transport or the like, for example, in the vertical direction of FIG. 1B and a crack occurs in the periphery of the cooling hole of the motor 5, the extension of the crack in the radial direction of the main plate 2 can be prevented. Consequently, the fan 1 can be prevented from breaking, and can improve reliability against impact on fan 1.

In particular, in the embodiment, by means of the formation of the cooling hole of the engine 5 on the extension line of the bushing range 9a, the formation of the fusion portion of the resin A near the cooling hole of the engine 5 It can certainly be avoided.

Gmas 9 are not complicated. A gma 9 forks to two gmas; the bushing gma 9a, and the connecting gma 9c in the resin injection port 10, and branches in the vane gma 9b in two directions

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in the connection part of the connection gma 9c and the vane gma 9b. Since the resistance is low in the fusion portion of the resin A in accordance with the above described, it is preferred to set the number and length of the fusion portions of the resin A as small as possible. In the configuration of ranges 9 according to the embodiment, the fusion portion of the resin A is not formed by the resin injected from the resin injection port 10, but is formed by the contact portion of the injected resin from the resin injection ports 10 neighbors. Consequently, the number of the fusion portions of resin A can be reduced as a whole. As described above, gmas 9 are constructed relatively simply, the resin flows along gmas 9 more easily, the occurrence of contractions is reduced, and the molding capacity can be improved.

Also, in the fan according to the embodiment, one end of the fusion portion of the resin A is in contact with the protuberance 2c. The fusion portion of the resin A extends in the radial direction between the cooling holes of the neighboring motor 5. The other end is in contact with the center of the vane 3. In the conventional configuration in which the fusion portion of the resin A extends directly to the outer periphery, in the event that a crack occurs along the fusion portion of the resin A, there is a possibility that the crack extends to the outer periphery of the fan 1 and the fan 1 is broken. In contrast, in the embodiment, the end of the outer radius side of the melting portion of the resin A formed on the main plate 2 is in contact with the vane range 9b. Consequently, the fusion portion of the resin A formed on the main plate 2 can be made shorter, that is, the portion can be shortened with low resistance. In this way, a fan 1 with high resistance reliability can be obtained. Even if a crack occurs near the fusion portion of resin A and extends along the fusion portion of resin A at the time of transport or the like, since the end of the outer radius side of the Fusion portion of the resin A is in contact with the thick vane 9b gma, the crack stops at this part. In addition, in the event that the crack does not stop at the vane gm 9b, the entire vane 3, which is connected to the vane gm 9b and is height in the axial direction, serves as a member of the resistance. Consequently, fan 1 can be prevented from being completely broken, and reliability against impact can be improved.

The configuration of the fusion portion of resin A and ranges 9 will be described in detail below. The number of pieces, the shape, and the angle with respect to the radius of the vanes 3, the shape and configuration of the gmas 9, the positions of the resin injection holes 10, the shape and position of the engine cooling hole 5, and the like are set as described above. That is, one end of the fusion portion of the resin A is in contact with the protuberance 2c, the fusion portion of the resin A extends in the radial direction between the cooling holes of the neighboring motor 5, and the other end it is in contact with the center of the vane 3. With the configuration, the fan 1 can be obtained which has reliability against an impact.

FIG. 4 is a partially enlarged view of FIG. 3. FIG. 5 is a view illustrating a cross section taken along line H1-H2 of FIG. 4. The resin injection port 10 is provided, for example, in the bushing gma 9a in a position close to the connecting gma 9c. Two neighboring resin injection ports 10m and 10n will be described as an example. The 10m resin injection port is connected to a 9am bushing gma, a 9bm vane gma, and a 9cm connection gma. The resin is injected from the resin injection port 10m to mold the 3m vane and the main plate 2 around the 3m vane. On the other hand, a resin injection port 10n is connected to a bushing gam 9an, a vane gma 9bn, and a connecting gma 9cn. The resin is injected from the resin injection port 10n to mold the vane 3n and the main plate 2 around the vane 3n. The vane 3 formed vertically on the main plate 2 has a predetermined thickness t3 (> t0) and the thickness on the vane 3 is almost uniform.

In the case where the vane 3m is positioned in front of the vanes 3n in the direction of rotation of the fan (the direction of the arrow D), to prevent the fusion portion of the resin A formed between the two vanes 3m and 3n are connected to the outer periphery of the fan, the area L must be formed with the resin injected from the resin injection port 10n. In particular, when the resin injected from the resin injection port 10n, not the resin injected from the resin injection port 10m, is used as the resin to form a flat part 3cmt from the end of the outer radius side of the blade of the 3m vane, the fusion portion of the resin A formed between the 9an and 9am bushing grommets certainly contacts the 3m vane. To accomplish this, the ranges 9 must be constructed in such a way that the distance from the resin injection port 10n is shorter than the distance from the resin injection port 10m with respect to the lengths of the flow paths of the resin that flows to the flat part 3cmt on the outer periphery of the vane.

Specifically, the number of parts and the shape of the vanes 3, the shape and configuration of the gmas 9, the positions of the resin injection holes 10, the shape and position of the engine cooling hole 5, the speed resin injection, and the like, are properly adjusted and, for example, a simulation is carried out. Thus, a part in which the melting portion of the resin A is to be formed in the fan at the time of molding can be examined. The configuration must be constructed in such a way that one end of the fusion portion of the resin A obtained by means of the simulation comes into contact with the protuberance 2c and extends into the bushing 2a between the cooling holes of the neighboring motor 5, and the other end comes into contact with the paddle gma 9b.

As described above, the turbo fan includes: the disk-shaped main board 2; the bushing

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projected 2a formed by having a central portion of the main plate 2 project in the direction of the axis of rotation; the plurality of vanes 3 each by the use of a flat part of the outer periphery side of the main plate 2 as the base and provided vertically in the projecting direction of the bushing 2a; the plurality of engine cooling holes 5 formed in the bushing 2a and for the cooling of an engine arranged in a space having a projection shape surrounded by the bushing 2a; the plurality of bushing cranes 9a that are radially provided in bushing 2a and in which a resin is flowed at the time of molding, to thereby form bushing 2a; and the fusion portion of the resin A formed by the fusion of the resin flowing out from the neighboring bushing cranes 9a at the time of molding. By means of the arrangement of the cooling holes of the engine 5 in order to avoid the melting portion of the resin A, there is an effect that a turbo fan can be obtained that has high reliability against an impact.

The plurality of cooling holes of the motor 5 provided in the bushing 2a is disposed in portions on the extended lines of the bushing cranes 9a to the center of rotation O such that the coupling between the cooling holes of the motor 5 having a low impact resistance and the melting portion of the resin A is undoubtedly prevented, and the fan having high reliability against an impact is obtained.

By forming the bushing cranes 9a radially around the center of rotation O, the resin flows to the boss 2c around the center of rotation more easily, and the molding capacity can be improved.

Each grind 9 as a path of the resin is formed in order to be separated to a bushing crane 9a and a vane wheel 9b. A connection crane 9c is provided for the connection of the rods 9a and 9b and, in addition, the resin is injected from the resin injection port 10 provided in any of the rods 9a, 9b, and 9c. In particular, either of the resin flowing in the bushing ring 9a and the resin flowing in the vane ring 9b necessarily flows through the connecting wire 9c. Accordingly, the balance between the amount of resin flowing in the bushing ring 9a and that of the resin flowing in the knife drawing 9b can be adjusted according to the configuration of the width and thickness of the connecting wire 9c . By properly adjusting the injection amounts of the resin flowing in the bushing crane 9a and the vane crane 9b, the occurrence of a cavity or locally small thickness due to irregular flow can be prevented, and the Resistance deterioration can be prevented.

While the resin injection port 10 is provided directly on the bushing crane 9a in the embodiment, the resin injection port 10 can be provided on the vane gland 9b or the connecting gland 9c. In the case of providing the resin injection port 10 in the connection gland 9c, by making the thickness and width of the gland between the resin injection port 10 and the bushing gland 9a and those of the gland between The resin injection port 10 and the blade vane 9b are different from each other according to the resin flow rate required, the balance of the resin quantities can be adjusted.

Since the vane 3 has the hollow shape and opening of the vane 9b is provided around the opening 3b, the weight can be reduced due to the hollow shape, and the resin extends to the entire mold more easily at the time of molding of the pallets 3. Accordingly, the pallet 3 can be made thinner and lighter. By reducing the weight, the weight in the peripheral portion of the fan is reduced with respect to the center of rotation. Therefore, the centrifugal resistance at the time of rotation is reduced and a voltage applied to the root of the main plate as the base of the vane 3 is reduced. As a result, the resistance of the fan 1 can be improved, and the resistance of the fan 1 can be improved. prevent breakage at the time of rotation. Since the portion of the vane wire 9b is maintained as the resin in a molded body, the thickness of the connected part of the vane 3 and the main plate 2 on which the tension is concentrated can be increased by the vane wire 9b As described above, the resin flow capacity is improved by the vane grille 9b, the molding capacity can be improved, and the turbo fan resistance can be improved.

As described above, by supplying the plurality of bushing cranes 9a that are radially provided in the bushing 2a and in which a resin is flowed at the time of molding, the bushing is thus formed 2nd; the plurality of pallet grains 9b that are provided, respectively, around the bases of the vanes 13 and in which the resin is flowed at the time of molding, thereby forming the vane 3; and the connection cranes 9c to connect respectively the bushing glands 9a and the vane grids 9b positioned close to the respective bushing cranes 9a, each of the rods 9 is continuously formed in the radial direction from the center of rotation side a the outer periphery of the main plate 2. Accordingly, the resin injected from the resin injection port 10 forks to the resin flowing to the center of rotation and the resin flowing to the side of the outer periphery in the main flow directions After that, the resin does not flow backwards but instead flows to the main plate 2 at the periphery while it flows through the rods 9.

As described above, the flow directions of the resin are relatively simple, such that a portion in which the melting portion of the resin A is formed can be clearly predicted. There are also effects that the resin can flow smoothly, the molding capacity can be improved, and the fan 1 can be obtained very reliable. In addition, the distance of the fusion portion of resin A can be shortened, and deterioration of the turbo fan resistance can be prevented.

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Compared to the conventional configuration in which the resin fusion portions are formed by the resin injected from a single resin injection port, in the embodiment, the number of resin fusion portions A can be decreased, simplify the design of the mold, and the occurrence of a locally small cavity and thickness due to irregular flow can be prevented.

FIG. 6 is a partially enlarged view of FIG. 1 B. As shown in the figure, in the fan according to the embodiment, the bushing gma 9a having the thickness t1 projects from the bushing 2a having the thickness t0 next to the external air duct of the fan 7 only by the difference in thickness (t1-t0) on the face of the wall that builds the bushing 2a of the external air duct of the fan 7. The cooling hole of the motor 5 is positioned in the extension line of the bushing gma 9a on the side of the center of rotation. Consequently, the bushing gma 9a functions as an air guiding plate and induces the air flow G towards the cooling hole of the engine 5. The bushing gma 9a serves as an air guiding plate to the air flow G, thereby increasing the current of air flowing on the surface of a motor mounted on the portion surrounded by bushing 2a and accelerates the cooling of the engine. In general, the temperature protection control is carried out in such a way that the power supply to the motor stops when the temperature rises to a certain temperature in the temperature increase of the motor. However, by accelerating the engine cooling, the engine can be operated efficiently without executing the temperature protection control. In addition, engine breakage caused by high engine temperature can also be prevented.

As described above, by projecting the bushing gma 9a from the face of the main plate 2 of the bushing 2a to the external air duct of the fan 7 as the motor mounting side, the current is increased From air to the surface of the engine, engine cooling can be accelerated, and there is an effect that a very reliable turbo fan can be obtained.

With respect to the shape of the fan according to the embodiment, a plurality of assemblies each constructed by the vane 3, the vane gma 9b, the bushing gma 9a, the connecting gma 9c, and the engine cooling hole 5 are provided radially around the axis of rotation O as a center. Specifically, all vanes 3 that build the fan 1 have almost the same arrangement as the resin injection port 10, the bushing gma 9a, the vane gma 9b, the connecting gma 9c, and the cooling hole of the Engine 5 prepare for the paddle. Therefore, by injecting almost the same amount of resin into the plurality of resin injection ports 10, the resin flows in similar directions throughout the disk-shaped fan 1, and vanes 3 can be formed under similar molding conditions. Consequently, there is an effect such that, in a fan completed by molding, the occurrence of a cavity and a locally small thickness caused by uneven flow can be prevented as a whole, and a turbo fan is obtained which has a high reliability in the resistance.

For example, when the amount of resin required is different between the assemblies each constructed by vane 3, vane gam 9b, bushing gma 9a, connection gma 9c, and the cooling hole of the motor 5 due to , for example, variations in the passages in the circumferential direction, by changing the amount of resin injected from the resin injection port 10, according to the necessary amount, molding can be carried out under conditions of similar molding, and an effect similar to the previous one occurs.

By supplying the same number of cooling holes of the engine 5 and the bushing ranges 9a, the removal rate of the vane 3 in the cooling hole of the engine 5 can be made almost similar to the cooling holes of the engine 5 which construct the fan 1. Accordingly, the turbulent air flow E2 from the external air duct of the fan 7 to the internal air duct of the fan 6 through the engine cooling hole 5 passes to the rear side of the vane 3 formed by vane gma 9b connected to bushing gma 9a closest to the engine cooling hole 5. Turbulent air flows E2 from the engine cooling holes 5 flowing between vanes 3 and 3, respectively, and which do not collide directly with each other Therefore, without being subjected to large pressure fluctuations, a turbo fan can be obtained that performs a noise reduction.

Although an equal number of engine cooling holes 5 and bushing 9a are provided in this case, the number of engine cooling holes 5 may be smaller than that of bushing ranges 9a. For example, the cooling holes of the engine 5 may not be provided on the side of the center of rotation O of all bushing ranges 9a. By supplying the cooling holes of the motor 5 in positions avoiding the resin fusion portions A of the bushing 2a and in uniform positions with respect to the center of rotation O, a turbo fan is obtained which has a high reliability in the resistance , which can be molded under substantially uniform molding conditions and in which the occurrence of a cavity and the thickness locally due to uneven flow can be prevented as a whole. Obviously, by supplying an equal number of cooling holes of the engine 5 and bushing 9a, the turbo fan can be molded

under more uniform molding conditions, and a very reliable turbo fan is obtained.

The fan shape is thus constructed in accordance with that shown in FIG. 1 that a plurality of assemblies each made of vane 3, vane gma 9b, bushing gma 9a, connecting gma 9c, and the cooling hole of the motor 5 are provided radially around the axis of rotation O as a center, and so

minus one of the angles formed each between the neighboring sets is different from the other angles. With the

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configuration, the air flow E2 released to the outside from the cooling hole of the motor 5 and the air flow E1 blowing from the vane 3 are prevented from having periodicity. Therefore, noise can be prevented due to the number of fan revolutions and silence is maintained in the direction of the ofdo.

As described above, by supplying a plurality of assemblies each constructed by the vane 3, the vane crane 9b, the bushing crane 9a, the connecting crane 9c, and the engine cooling hole 5 arranged radially around the axis of rotation as a center, each of the vanes 3 has almost the same arrangement with respect to the resin injection port 10, the bushing crane 9a, the bushing

of vane 9b, and the engine cooling hole 5. Therefore, molding conditions can be made almost

likewise, the occurrence of a cavity and a locally small thickness caused by the flow can be prevented

irregular, and you get a turbo fan that has high reliability in resistance.

In the assemblies each constructed by the vane 3, the vane crane 9b, the bushing crane 9a, the connecting crane 9c, and the cooling hole of the motor 5, when making at least one of the angles formed each between neighboring sets different from the other angles, an effect is obtained that the noise can be reduced.

By supplying the cooling holes of the engine 5 of the same number as that of the bushing cranes 9a, the positional relationships between the cooling hole of the engine 5 and the vanes 3 can be made equal, the air flow E2 flowing from the external air duct of the fan 7 to the internal air duct of the fan 6 can pass smoothly between the vanes and outside. The effects of noise reduction can occur and, in addition, the molding capacity is high.

A fan molding process will now be described with reference to FIG. 7. FIG. 7 is a flow chart showing the fan molding process. A mold for molding the fan 1 having the shape shown in FIGS. 1 to 6 is fixed (ST1), and the thermoplastic resin is injected from the resin injection ports 10 (ST2). The injected resin flows through the bushing cranes 9a, the connecting cranes 9c, and the vane cranes 9b and, in addition, extends from the cranes 9 to the main plate 2 and the vanes 3. The entire fan is filled with the resin in a few milliseconds. Next, the fan cools to harden the thermoplastic resin (ST3). After the thermoplastic resin is completely hardened, the molded fan 1 is released and removed from the mold (ST4). After that, the cover 4 is fixed to the suction side of the fan 1 (ST5). In addition, the program advances to a process such as the union of the rod of an engine.

Next, the thicknesses of the parts of the resin formed by the fan 1 will be described.

As shown in FIGS. 5 and 6, the minimum thickness of the part other than the cranes 9 of the main plate 2 is t0, the thickness of the bushing crane 9a is t1, the thickness of the pallet crane 9b formed around the vane opening 3b that has a hollow shape is t2, and the thickness of the vane 3 that has a hollow shape is t3. At least the thicknesses t1, t2, and t3 are adjusted so that they are greater than the thickness t0. While there is a case in which the rods 9 have an error at the time of molding or their corner portion has an R-shape, a portion that has the maximum thickness is established as the thickness of the grind 9. Agree As shown in the diagrams, the thicknesses of the grids 9 include the thickness of the main plate 2 and the thickness of the projected portion from the face of the main plate.

FIG. 8 is a graph showing the molding time with respect to the ratio t1 / t0 of the thickness t1 of the bushing crane 9a to the thickness mmimo t0 of the portion other than the bushing in the main plate 2. The abscissa axis shows t1 / t0, and the ordinate axis indicates the molding time (sec.), The molding time denotes the time required for ST2 to ST4 in the flowchart shown in FIG. 7, which is the time from the injection of the resin to the extraction of the mold after cooling.

As shown in the graph of FIG. 8, in the case where t1 / t0 is 1.0 or less, that is, the thickness t1 of the bushing crane 9a is equal to or less than the minimum thickness t0 of the portion other than the cranes on the main board 2, lane 9a is thinner, the resin flow is not good, it takes time for the resin to flow throughout the mold, and the molding time increases. In the case where t1 / t0 is greater than 2.0, that is, the thickness t1 of the bushing crane 9a is larger than twice as large as the minimum thickness t0 of the portion other than the cranes on the main board 2, it takes time to cool the resin, and the time until the extraction increases. As a consequence, when the ratio t1 / t0 is set in the range of 1.1 <t1 / t0 <2, the molding time can be shortened by at least more than the case in which the thicknesses t1 and t0 are equal ( t1 / t0 = 1.0). By shortening the molding time, the amount of production can be increased. In addition, the electricity used by a molding machine can also be reduced so that energy can be saved.

FIG. 9 is a graph showing the molding time with respect to the proportion t2 / t0 of the thickness t2 of the pallet crane 9b to the thickness mmimo t0 of the portion other than the cranes in the main plate 2. The axis of abscissa shows t2 / t0, and the ordinate axis indicates the molding time (sec.). The molding time denotes the time required for ST2 to ST4 in the flowchart shown in FIG. 7, which is the time since the injection of the resin for extraction after cooling.

As shown in the graph of FIG. 9, in the case where t2 / t0 is 1.0 or less, that is, the thickness

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t2 of the pallet gma 9b is equal to or less than the minimum thickness t0 of the portion other than the gmas on the main board 2, the gma 9b is thinner, the resin flow is not good, it takes time for The resin flows throughout the mold, and the molding time increases. In the case where t2 / t0 is greater than 2.0, that is, the thickness t2 of the pallet gma 9b is greater than twice as large as the minimum thickness t0 of the portion other than the gmas on the main board 2 , it takes time to cool the resin, and the time until extraction is increased. As a result, when the ratio t2 / t0 is set in the range of 1.1 <t2 / t0 <2, the molding time can be shortened by at least more than the case in which the thickness t2 and t0 are equal ( t2 / t0 = 1.0). By shortening the molding time, the amount of production can be increased. In addition, the electricity used by a molding machine can also be reduced so that energy can be saved.

Therefore, by setting the ratio t1 / t0 between the thickness t1 of the bushing gma 9a and the mm thickness t0 of the portion other than the gmas 9 on the main board 2 in the range of 1.1 < t1 / t0 <2, the molding time can be shortened compared to the case in which the thicknesses t1 and t0 are equal (t1 / t0 = 1.0). Similarly, by setting the ratio t2 / t0 between the thickness t2 of the pallet range 9b and the minimum thickness t0 of the portion other than the ranges 9 on the main board 2 in the range of 1.1 < t2 / t0 <: 2, the molding time can be shortened compared to the case in which the thickness of t2 and t0 are equal (t2 / t0 = 1.0). In particular, by setting the upper limit of the thicknesses t1 and t2 of the ranges 9 to twice the minimum thickness t0 of the main plate 2, the molding time can be shortened, the amount of the resin can be reduced, and a reduction in the weight and cost of the fan 1 can also be achieved.

Although the thickness t1 of the bushing gma 9a and the thickness t2 of the pallet gma 9b have been described separately, it is also possible to satisfy one of the thicknesses or both. In the configuration in which both of the thicknesses t1 and t2 are satisfied, the molding time can be shortened even more efficiently.

As described above, when at least one of the thickness of the bushing gma 9a and the thickness of the paddle gma 9b is set to "t" and the thickness of the portion other than the gmas 9 in the main plate 2 is t0, by setting the ratio t / t0 to be in the range of 1.1 <t / t0 <2, the molding time can be shortened compared to the case in which the thicknesses ty t0 are equal (t / t0 = 1.0).

The shape of palette 3 will be described below.

FIGS. 10A and 10B and FIG. 11 show the configuration of a palette 3. FIGS. 10A and 10B and FIG. 11 are diagrams illustrating palette 3 according to the embodiment. FIG. 10A is a side view of a vane. FIG. 10B is a view illustrating a cross section taken along the Z-Z line of FIG. 10A. FIG. 11 is an explanatory view illustrating the vertical section taken along line A-A of FIG. 10B.

As shown in FIG. 10A, a hollow on the side of the inner vane radius 3dc and a hollow on the side of the outer radius of the vane 3dd of a pallet hollow 3d inclines towards the inside of the hollow shape with respect to a linear X line parallel to the axis rotating at arbitrary angles 01 and 02, respectively, that is, the vane gap 3d narrows from the opening of the vane 3b, as a base, formed in the main plate 2 for the end of the vane suction side 3e towards The inside of the hollow shape. Since the vane 3 has an almost uniform thickness, the end of the inner radius side of the vane 3a and the end of the outer radius side of the vane 3c also inclines towards the inside of the hollow shape, with respect to the line Linear X parallel with the axis of rotation at arbitrary angles 01 and 02, respectively, that is, the vane ends 3a, 3c are tapered from the opening of the vane 3b towards the end of the suction side of the vane 3e towards the inside the hollow shape.

As shown in FIG. 11, a front recess of the vane 3da in the direction of rotation D of the vane 3 and a rear recess of the vane 3b as a side face in the direction of reverse rotation of the vane 3 inclines inwardly of the hollow shape with respect to the linear line X parallel to the axis of rotation at arbitrary angles 03 and 04, respectively, that is, the lateral surfaces 3da, 3db of the recess of the vane 3d narrow from the opening of the vane 3b at the end from the suction side of the paddle 3e towards the inside of the hollow shape. Since the vane 3 has an almost uniform thickness, the surface of the inner radius side of the vane 3f and the surface of the outer radius side of the vane 3g also slope with respect to the linear line X parallel to the axis of rotation , at arbitrary angles 03 and 04, respectively, that is to say the hollow of the vane 3d narrows from the opening of the vane 3b towards the end of the suction side of the vane 3e towards the inside of the hollow shape.

In synthesis, the vane 3 and the recess of the pallet 3d have a conical shape from the main plate 2 to the cover 4 and are inclined towards the inside of the recess in the predetermined angles 01 and 02, and the predetermined angles 03 and 04. Consequently, at the time of releasing the mold from the mold body of the fan in the direction of the axis of rotation, the resin and the mold can be gently separated from each other due to the inclination. It is possible to prevent the vane 3 from adhering to the mold and breaking, such that the molding capacity can be improved. At the end of the cooling and hardening of the resin, the mold is in close contact with the standing faces 3a, 3c, 3f and 3g of the fan mold body on the outside of the vane 3 which has the hollow shape, and also with the 3dc, 3dd, 3rd, and 3db standing faces of the fan mold body inside or on the hollow side of the vane 3. The standing faces on both the outside and inside of the gap narrow from the base in the

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vertical direction Consequently, the mold can be easily released on both the outside of the vane 3 and the inside of the recess of the vane 3.

In addition, the weight of the pallet 3 that has the hollow shape can be reduced compared to that of the pallet 3 that does not have a hollow shape. In the case where the thickness of the pallet 3 is not uniform, poor molding occurs due to variations in the cooling time and hardening of the resin, and there is a problem of low molding capacity. However, the thickness of the vane 3 becomes almost uniform, such that the cooling and hardening time of the resin can be made almost uniform, poor molding can be avoided, and the molding capacity can be improved.

As described above, the turbo fan includes: the disk-shaped main board 2; the projected bushing 2a formed by making the central portion of the main plate 2 project in the direction of the rotation axis; and the plurality of vanes 3 each of which has the hollow shape, and is provided in order to be in the flat part of the side of the outer periphery of the main plate 2 as a base in the projecting direction of the bushing 2a , the base has the opening 3b. The standing faces 3a, 3g, 3c, and 3f on the outside of the pallet 3 having the hollow shape and the standing faces 3da, 3db, 3dc, and 3dd on the inside or on the hollow side of the palette 3 are they tip inside the hollow, and the outside of the vane 3 and the hollow inside narrow from the base. With the configuration, the mold can be released easily, and damage to the pallet 3 caused by the adhesion of the pallet 3 to the mold can be prevented.

In addition, by making the thickness of the vane 3 almost uniform, the cooling and hardening time of the resin can be made uniform, and a turbo fan can be obtained that has excellent molding capacity.

In addition, by means of the formation of the vane 3 hollowly, the entire fan 1 can be made lighter.

FIG. 12 is a graph showing the molding time of the fan (sec.) And the noise value (dB) when the entire angle 01 of the end of the inner radius side of the vane 3a with respect to the axis of rotation, the angle 02 from the end of the outer radius side of the vane 3c with respect to the axis of rotation, the angle of inclination 03 of the front recess of the vane 3da with respect to the axis of rotation, and the angle of inclination 04 of the rear recess of the vane 3db with respect to the axis of rotation they are set at the same angle of inclination 0, and the angle of inclination 0 is changed. The abscissa axis indicates the inclination angle 0 and the ordinate axis indicates the molding time (sec.) And the noise value (dB). The noise value (dB) was measured at a point just below the fan and separated from the fan by 2 m. The molding time is the time corresponding to ST2 to ST4 in the flow chart showing the molding process shown in FIG. 7.

The molding time will be described on the basis of the graph shown in FIG. 12.

In the case where the angle of inclination 0 <0 °, the vane 3 has a widened shape from the side of the main plate 2 towards the side of the cover 4, such that the mold cannot be released, and the configuration it is impossible. In the case where 0 = 0 °, that is, in the case where the vane 3 is not inclined with respect to the axis of rotation, the friction between the vane 3 and the mold is large. If the mold is not released slowly, the vane 3 breaks due to the adhesion to the mold, so that a long time of molding is necessary. On the contrary, by means of the use of the inclination angles 0, the mold release is facilitated, and the mold release time can be shortened. In addition, the surface area of the vane 3 is increased, and the cooling area also increases, such that the cooling time is shortened. Consequently, by using the inclination angles 0, the molding time can be shortened. When the angle of inclination 0 is 1 °, the molding time becomes approximately half that in the case in which the angle of inclination 0 is 0 °. Therefore, when the angle of inclination 0 is 1 ° or larger, the molding time is shortened, and the molding capacity is high.

The noise value will now be described on the basis of the graph shown in FIG. 12.

When the angle of inclination 0 is too large in the proportion between the angle of inclination 0 and the noise value, the flow path between neighboring vanes 3 and 3 narrows, the air velocity passing in the path increases, And increase the noise. According to the measurement result in FIG. 12, when the angle of inclination 0 is greater than 3 °, the noise increases. Consequently, when the inclination angle 0 is set in the range of 1 ° <0 <3 °, a preferred noise value can be maintained.

As a result, by setting the angle of inclination 0 in the range of 1 ° <0 <3 °, a turbo fan is obtained which has a change with small noise and a high molding capacity.

As described above, by making the foot faces 3a, 3g, 3c, and 3f on the outside of the palette 3 having the hollow shape and the faces standing 3da, 3db, 3dc, and 3dd on the inside or on the hollow side of the vane are inclined towards the inside of the recess, each of the predetermined inclination angles 0 is set in the range of 1 ° <0 <3 °. It produces an effect that a turbo fan is obtained that has a change with small noise and a high molding capacity.

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In the foregoing, the entire hollow of the inner radius side of the vane 3dc, the hollow of the outer radius side of the vane 3dd, the front recess of the vane 3da, and the rear recess of the vane 3db of the vane are inclined towards the interior of the hole at the same angle of inclination 0 with respect to the axis of rotation. However, even when they are tilted at different angles from each other, a similar effect occurs.

The end of the inner radius side of the vane 3a, the end of the outer radius side of the vane 3c, the end of the suction side of the vane 3e, the front side of the vane 3f on the front side in the direction of Rotation of the vane, and the rear side of the vane 3g on the rear side of the vane 3 have an almost uniform thickness. However, the invention is not limited to the configuration, and may be slightly different from each other due to a molding error and the like. At the end of the inner radius side of the vane 3a and the end of the outer radius side of the vane 3c, since the width in the direction of rotation is small, and it is difficult to make the thicknesses uniform in this part. It is sufficient to cause the thickness of the pallet 3 to be almost uniform with the fluctuation to some extent. By making the thickness uniform, the resin is injected uniformly and cools uniformly. Therefore, a preferred mold body can be obtained.

In the embodiment, by making the central portion of the vane 3 in an upright position in the direction of projection of the bushing 2a from the base of the main plate 2 and the inclination of the standing faces on the outside of the vane 3 and inside or on the hollow side inside the hole, the above effects are obtained. In the configuration, the mold is released in the direction of the axis of rotation and in parallel with the axis of rotation. For example, the mold can also be released in the direction of the axis of rotation while the mold rotates slightly around the axis of rotation as the center. In the case of mold release while rotating, the configuration in which the central portion of the vane 3 is in an upright position in the direction of projection of the bushing 2a from the base of the main plate 2 is not used, but rather a way is used in which the central portion of the vane 3 tilts from the base of the main plate 2 to the end of the suction side of the vane 3e in the direction of rotation of release by a predetermined angle. Also in the case of using the configuration in which the vane 3 tilts, by means of the inclination of the standing faces on the outside of the vane 3 and the inside or the hollow side towards the inside of the recess, the release of the Mold can be carried out easily, and effects similar to the above occur.

The turbo fan 1 will be described in which the cranes 9 are formed with another configuration. FIG. 13 is a bottom view of the turbo fan 1 molded with another configuration of grna. In FIG. 13, the same reference numbers as those in FIG. 3 express the same or corresponding parts.

In FIG. 13, the cooling hole 9d grains are provided, each formed in such a way that it surrounds the cooling hole of the engine 5. By means of the connection of the crane 9d and the bushing crane 9a, an integral crane is formed.

In the turbo fan constructed in accordance with what has been described above, part of the resin injected from the resin injection port 10 at the time of molding flows from the bushing crane 9a to the grinding wheel 9d for a cooling hole and also flows to bushing 2a and boss 2c. At this time, the resin flowing in the bushing shaft 9a branches to two directions in the cooling hole 9d, and flows into the cooling hole 9d provided around the engine cooling hole 5. After that the resin flows throughout the cooling hole of the motor 5, the resin reliably melts again on the side of the boss 2c of the cooling hole of the engine 5, and flows into the boss 2c. As described above, by means of the supply of the cooling crane 9d, the flow capacity of the resin around the cooling hole of the motor 5 improves, so that the molding capacity can be improved.

By supplying the cooling hole 9d around the cooling hole of the motor 5, the resin in the cooling hole 9d hardens to remain around the cooling hole of the engine 5 as an opening, and the periphery of the cooling hole of the motor 5 becomes thick. Consequently, the resistance around the cooling hole of the motor 5, which tends to decrease due to the opening, can be improved. Therefore, a turbo fan is obtained that has durability against breakage even with an applied impact.

FIG. 14 is a bottom view of the turbo fan 1 molded with another additional crane configuration. In FIG. 14, the same reference numbers as those in FIG. 3 express the same or corresponding parts.

In FIG. 14, the linear bushing 9a is connected to the cooling hole 9d around the cooling hole of the motor 5 and is also connected to a thicker upper portion of bushing 2d. The center of rotation side of the cooling hole of the engine 5 is the thicker upper portion of bushing 2d which is thicker than the other portion of the cranes in the main plate 2.

In the turbo fan constructed in accordance with what has been described above, part of the resin injected from the resin injection port 10 at the time of molding flows from the bushing crane 9a to the grinding wheel 9d for a cooling hole and flows in additional form to the upper thick portion of bushing 2d, which thus forms the portion. In a manner similar to the configuration of FIG. 13, the resin flowing in the bushing shaft 9a branches in two directions in the cooling hole 9d, and flows in the cooling hole 9d

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provided around the engine cooling hole 5. After the resin flows around the engine cooling hole 5, the resin flows to the thick top portion of bushing 2d connected to the periphery of the engine cooling hole 5, which in this way it forms the upper thick portion of bushing 2d.

Like the configuration of FIG. 13, by supplying the gma of the cooling hole 9d around the cooling hole of the motor 5, the resin in the gma of the cooling hole 9d hardens to remain around the cooling hole of the engine 5 as an opening, and the periphery of the cooling hole of the motor 5 becomes thick. Consequently, the resistance around the cooling hole of the motor 5, which tends to decrease due to the opening, can be improved. By supplying the gmas of the cooling hole 9d, the molding capacity and resistance can be improved by an improvement in the flow capacity of the resin around the engine cooling hole 5. A turbo fan is obtained It has durability against breakage even with an applied impact.

In addition, in configuration, the cooling hole 9d is directly connected with the upper thick portion of bushing 2d around the boss, which is thicker than the bushing tilt face. Consequently, the resin flows smoothly to the upper thick portion of bushing 2d, and the resin flowing in the gma of the reliable cooling hole 9d melts again on the front side in the direction of resin flow of the cooling hole of the engine 5, that is, on the side of the boss 2c of the cooling hole of the engine 5, and the resin resulting from the fusion flows to the upper thick portion of bushing 2d. Therefore, the resin can be reliably injected into the periphery of the cooling hole of the motor 5 as an opening in an amount of thickness of the cooling hole 9d. Therefore, the resistance around the cooling hole of the motor 5, which tends to decrease due to the opening, can be improved.

As described above, by supplying the gma of the cooling hole 9d connected to the gma of bushing 9a and formed in such a way that it surrounds the cooling hole of the engine 5, a turbo fan can be obtained which carries Improved molding capacity and strength through improved resin flowability around the engine cooling hole 5.

Next, the pallet size 9b will be described in detail. FIG. 15 is a perspective view of the turbo fan according to the embodiment and having another configuration, seen from below. FIG. 16 is a partially enlarged perspective view showing a part of FIG. 15. FIGS. 17A and 17B and FIGS. 18A and 18B are explanatory views illustrating a palette 3. FIG. 17A is a side view of vane 3 and FIG. 17B is a cross section taken along line Z-Z of FIG. 17A. FIG. 18A is a cross section taken along line Y-Y of FIG. 17B. FIG. 18B is an enlarged view of the portion of a circle M in FIG. 18. FIG. 19 is an explanatory view illustrating a part of the lower face of the turbo fan 1.

The configuration of the turbo fan shown in this case is another configuration of the vane range 9b provided around the opening of the vane 3b formed at the base of the vane 3.

For example, as shown in FIGS. 15 to 18B, the vane gma 9b is provided around the opening in the vane 3 which has a hollow shape, and the vane gma 9b on the front side in the direction of rotation of the vane which is referred to as a frontal gma of the vane 9ba, and the vane gma 9b on the rear side in the direction of rotation of the vane is called a rear gma of the vane 9bb. The height of the projection from the face of the main plate 2 of the front gma of the vane 9ba and that from the face of the main plate 2 of the rear gma of the vane 9bb are made different from each other. The height of the projection in the direction of the axis of rotation of the front gma of the vane 9ba is adjusted to be greater than that of the rear gma of the vane 9bb by a predetermined height, and the front gma of the vane 9ba is It projects outside the fan.

A stream of air C near the main plate 2 in the opening of the vane 3b generated at the moment in which the fan 1 rotates in the direction D collides with the frontal gma of the vane 9ba, bends outward, draws a parabola, and flows in order to approach the main plate 2 again on the side of the rear gma of the vane 9b. FIG. 16 is an enlarged view showing this status. If the front gma of the vane 9ba and the rear gma of the vane 9bb have the same height, at the time of rotation of the fan, the flow around the main plate 2 is separated from the front gma of the vane 9ba and collides with the corner of the rear gma of the vane 9bb, such that a pressure fluctuation occurs, which causes such a problem that noise in the narrow band occurs.

On the contrary, when the front gma of the vane 9ba is set to be higher than the rear gma of the vane 9bb by means of a predetermined height, in accordance with that shown in FIG. 18B, the flow near the opening of the vane 3b is in accordance with that shown by arrow C in FIG. 18. Specifically, the flow after leaving the front gma of the vane 9ba draws a parabola that curves outwardly from the main plate 2 and flows in order to approach the main plate 2 again on the rear side in the direction of rotation of the rear gma of the palette 9bb. If the front gma of the vane 9ba is arranged to be higher, the air flow C curves outwardly from the surface of the main board 2, such that the distance from the main board 2 increases. As a result, a point of re-attachment of the air current changes C to the rear side of the rear opening of the vane 3b. By causing the air stream C to be gently reattached to the rear side of the rear opening of the vane 3b, the air stream C can be prevented from colliding with the

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corner of the rear gma of the palette 9bb, and noise can be reduced.

As the frontal gma of the vane 9ba becomes thicker, the resin flows to the vane 3 more smoothly. As a result, contraction can be avoided, and on the other hand, the resistance in the frontal gma of the vane 9ba improves, so that the fan resistance also improves.

As described above, by making the front gma of the vane 9ba higher than the rear gma of the vane 9bb by means of a predetermined height such that it protrudes outward from the fan, a turbo is achieved Lightweight, strong, highly reliable and low noise fan, which can be prevented from breaking at the time of rotation and transport.

Next, the difference At (shown in FIG. 18B) will be described between the height of the front gma of the vane 9ba and the height of the rear gma of the vane 9bb of the gma of vane 9b formed such that surround the vane 3, with respect to the maximum aperture diameter F of the vane opening 3b of the vane having a hollow structure is shown in FIG. 19. The maximum opening width F is the diameter of a circle that inscribes from the opening in the face of the main plate 2, and At denotes the difference between the height of the front gma of the vane 9ba and the height of the gma rear of palette 9bb.

When the difference in height At is small, the flow from the front gma of the vane 9ba does not draw a parabola having a sufficient height, but collides with the corner of the rear gma of the vane 9bb. Consequently, the noise is produced due to pressure fluctuations in the opening of the vane 3b. On the contrary, when the frontal gma of the vane 9ba is too high, that is, the difference At is too large, the flow is separated by the frontal gma of the vane 9ba, and a peak sound is generated due to the rotation speed. . As described above, there is a desirable range of the difference At between the height of the front gma of the vane 9ba and the height of the rear gma of the vane 9bb.

The flow that crosses the opening of the vane 3b refers not only to the difference At between the height of the front gma of the vane 9ba and the rear gma of the vane 9bb but also the maximum opening diameter F of the opening of the palette 3b. Accordingly, the ratio (At / F) of the difference At between the height of the front gma of the vane 9ba and the height of the rear gma of the vane 9bb is calculated with the maximum opening diameter F of the opening of the palette 3b. FIG. 20 is a graph showing the ratio between the ratio (At / F)% and the noise value (dB) with the same volume of air. The abscissa axis indicates the At / F (%) and the ordinate axis indicates the noise value (dB). The noise value was measured just below the fan and 2m away from it.

By means of the construction of the turbo fan so that the proportion is at least in the range of 4% <At / F <22% based on the measurement result shown in FIG. 20, the turbo fan with the lowest noise in the case where the height of the projection of the face of the main plate 2 of the front gma of the vane 9ba and that of the rear gma of the vane 9bb are equal , that is, At = 0 (At / F = 0) is obtained.

In the case where At / F <4%, the difference At of the gmas is small with respect to the maximum opening diameter F. Therefore, the possibility that the flow that deviates from the frontal gma of the vane 9ba collides with the corner of the rear gma of the vane 9bb it becomes high, and a pressure fluctuation occurs so that the noise is generated in the narrow band. On the other hand, in the case where 22% At / F, the difference At of the projection heights of the gmas is large with respect to the maximum aperture diameter F. Therefore, the flow that deviates from the gma Front of the vane 9ba separates, and increases the noise by a peak sound due to the speed of rotation.

As described above, by means of the formation of the turbo fan in such a way that the difference between the projection height of the front gma of the vane 9ba and the projection height of the rear gma of the vane 9bb with respect to at the maximum opening diameter F of the opening of the vane 3b is set in the range of 4% <At / F <22%, the noise can be suppressed, which is generated in the narrow band at the time of rotation of the fan and that the flow around the main plate 2 is separated from the front gma of the vane 9ba, collides with the corner of the rear gma of the vane 9bb so that a pressure fluctuation occurs. A point of re-attachment of the air stream after leaving the front gma of the vane 9ba to the rear side in the direction of rotation of the rear gma of the vane 9bb moves to the rear side of the rear opening of the vane 3g, so that the air stream C is gently reattached to the rear side of the rear opening of the vane 3g. Since the projection height of the front gma of the vane 9ba is not too high, such that the flow is not separated by the front gma of the vane 9ba, the occurrence of the generation of a peak sound is suppressed due to the rotation speed, and noise deterioration can be prevented. Consequently, noise reduction can be achieved.

Therefore, by means of the formation of the turbo fan in such a way that the At / F ratio of the difference At of the projection heights of the front gma of the vane 9ba and the rear gma of the vane 9bb with the diameter of Maximum opening F of the vane opening 3b of the vane having the hollow structure is set in the range of 4% <At / F <22%, noise can be reduced.

By supplying the configuration described above of the fan, in addition to the settings

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from the opening of the vane 3b and the gma of vane 9b, other effects can be obtained.

For example, by supplying the cooling holes of the engine 5 in order to avoid the melting portions of the resin, the turbo fan is obtained which has a high reliability in the resistance. By supplying the bushing gma 9a, the resin flows easily to the protuberance 2c near the top of the main plate 2, and the resin flow capacity in the entire main plate can be improved. Since the vane 3 has the hollow structure, the weight of the turbo fan as a whole can be reduced. In addition, the recess of the palette 3d has the conical shape that has an angle of inclination of molding, which is inclined at the predetermined angle 0 of the main plate 2 towards the cover 4, such that the mold can be released easily , pallet breakage can be prevented due to the adhesion of pallet 3 to the mold, and the molding capacity is high. Since the thickness of the vane 3 is almost uniform, the cooling and hardening time can be made uniform. Therefore, to a certain extent the occurrence of a poor molding caused by irregularities due to variations in the cooling and hardening time can be avoided.

In the embodiment, a fan has been described in which the plurality of vanes 3 are constructed by seven vanes and, consequently, seven grids 9 and seven engine cooling holes 5 are provided. However, the number of vanes 3, The number of grains 9, and the number of the cooling holes of the motor 5 are not limited to the foregoing but may be arbitrary.

Although the number of the cooling holes of the engine 5 is the same as that of the bushing cranes 9a, as described above, the number of cooling holes of the engine 5 can be set to be smaller than the number of bushing grains 9a. When the cooling hole of the engine 5 is arranged in the extension line of the bushing gma 9a, the cooling hole of the engine 5 and the melting portion of the resin are not between each other, so that the resistance is high. Therefore, even in the case where the number of. engine cooling holes 5 is set to be smaller than that of bushing cranes 9a, it is preferred to arrange the engine cooling hole 5 on the extension line of bushing gma 9a. By decreasing the number of the cooling holes of the engine 5, although the function of cooling the engine decreases, the resistance of the fan hub 2a can be increased.

FIGS. 21 to 23 show an example of the configuration in which the turbo fan 1 described in the embodiment is mounted in an air conditioner. FIG. 21 is a perspective view showing a state in which an air conditioner is mounted on the ceiling, seen from a room. FIG. 22 is a vertical cross section of the air conditioner. FIG. 23 is a horizontal cross section of the air conditioner. An example of mounting the turbo fan 1 in a ceiling-mounted air conditioner will be described.

The air conditioner shown in FIG. 21 is a ceiling-mounted air conditioner apparatus and faces a room 19 through a decorative panel 13 that has an almost square shape. In a central portion of the decorative panel 13, a suction grill 13a is arranged as an air intake port to the air conditioner body, and a filter 20 to remove air dust that passes through the suction grill 13a . The decorative panel 13 also has ejection ports of the panel 13b formed along the sides of the decorative panel 13. Each of the ejection ports of the panel 13b has a wind vane in the direction of the wind 13c.

As shown in FIG. 22, a body of the air conditioner 12 is arranged with an upper plate 12c facing upwards through room 19, side plates 12d are attached to the sides of the upper plate 12c, and is mounted such that the lower side is opened to room 19. An aspiration port of the body 12a in the central portion of the lower face of the body of the air conditioner 12 is arranged in such a way that it communicates with the aspiration grid 13a of the decorative panel 13. The ejection ports of the body 12b arranged around the suction port of body 12a are arranged so that they communicate with the ejection ports of panel 13b. The body of the air conditioner 12 has therein the fan 1, a bell mouth 14 that forms a suction air path of the turbo fan, and a motor 8 to rotate the fan 1.

A heat exchanger 15 is disposed in a discharge air path that extends from a part between the vanes as a blow part of the air flow in the fan 1 to the ejection ports of the panel 13b. The heat exchanger 15 has aluminum fins 15a and heat transfer tubes 15b. The heat exchanger 15 has a configuration that the plurality of aluminum fins 15a each have a rectangular shape, which extends in the height direction of the body of the air conditioner 12, that is, in the vertical direction they are stacked at predetermined intervals and heat transfer tubes 15b in a plurality of stages penetrate the fins in the direction of the stack.

As shown in FIG. 23, the heat exchanger 15 is formed almost C-shaped so that it surrounds the side of the periphery of the turbo fan 1. For the heat transfer tubes 15b at one of the two ends of the heat exchanger 15 which have almost a C-shape, a header 16 to adjust an amount of refrigerant to each of the heat transfer tubes 15b, a distributor 17, and connection tubes 18 that connect the distributor 17 with the outdoor unit are attached. A refrigerant, such as

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Carbon is circulated in heat transfer tubes 15b.

By means of the air conditioner constructed in accordance with that described above, when the turbo fan 1 rotates in the direction of rotation D, the air in room 19 passes through the suction grill 13a of the decorative panel 13 and the filter 20 and the dust is removed from the air. The resulting air passes through the suction port of the body 12a and the bell mouth 14 and is sucked into the turbo fan 1. The air passes between the vanes 3 of the turbo fan 1 and is discharged to the heat exchanger 15. The Indoor air is the heat exchanged with the refrigerant that flows in the heat transfer tubes 15b at the time of passing through the heat exchanger 15, which thus carries out the heat exchange for heating, cooling , or the like, or dehumidification. After that, when the air blows towards the ejection port of the body 12b and the ejection ports of the panel 13b in room 19, the air direction is controlled by the wind vanes in the wind direction 13c.

At the time of transporting the air conditioner, generally, the air conditioner is maintained such that the direction of the rotation axis of the turbo fan 1 is perpendicular, that is, the rotating rod of the fan motor 8 is perpendicular . Specifically, the body of the air conditioner 12 is loaded into a truck or the like, and is carried in a state where the upper plate of the body 12c becomes a lower face

0 the side of the bell mouth 14 of the body of the air conditioner 12 becomes the underside.

By mounting the turbo fan 1 according to the embodiment of the built-in air conditioner shown in FIGS. 21 to 23, the following effects occur.

By improving the molding capacity of the turbo fan 1, the turbo fan 1 can be made thinner and lighter, and the weight of the entire product can be reduced. Since resistance reliability has been improved, the turbo fan 1 can be prevented from being damaged by an impact such as vibration at the time of transport. The product reliability of the air conditioner can also be improved.

In the turbo fan 1 in which the cooling holes of the engine 5 and the vanes 3 are arranged in uneven steps, the turbulent flow released from the cooling holes of the engine 5 outside the turbo fan

1 and the blowing flow of the vanes 3 have no periodicity. Therefore, noise can be reduced due to fan rotation speed, and noise reduction can be achieved. By mounting the fan 1 in the air conditioner, the turbulent flow flowing outward from the fan 1 to the ejection port of the panel 13b is also reduced. Consequently, the noise in the fan 1 is reduced and, in addition, the noise in the air conditioner can be further reduced, whereby a silent air conditioner is obtained. Since the heat exchange is carried out with the refrigerant in the heat exchanger 15 in a state where turbulent flow is reduced, an efficient air conditioner is obtained.

The present invention is not limited to the built-in air conditioner shown in FIGS. 21-23. Although the air conditioner having ejection ports of the panel 13b in the four directions on the ceiling has been described in this case, two ejection ports of the panel 13b can be provided in two directions such that face each other The air conditioner may not be fully mounted in a recess in the ceiling, but may be mounted in a state in which it projects downward from the ceiling surface. The air conditioner is not limited to a type of ceiling mount, but it can also be a type of wall mount. By applying the turbo fan according to the realization of an air conditioner that has another configuration in which the turbo fan is mounted, in a manner similar to the previous one, it is possible to prevent the breakage of a fan during transport of the product, and you get a quiet and light air conditioner with low noise, high product quality, and it is also very easy to carry.

As described above, by means of the configuration that includes at least any one of the turbo fans described in the embodiment and a heat exchanger, in which the air drawn from a suction port by the turbo fan is heat exchanges with a refrigerant in the heat exchanger, and by blowing the resulting air from an ejection port, a light air conditioner is obtained with high resistance reliability and also achieves noise reduction .

The invention is not limited to the air conditioner, but can also be applied to a ventilation fan and an air filter that each includes a turbo fan, and effects similar to the above can be obtained.

In accordance with the present invention, the following effects can be obtained.

The plurality of bushing grains 9a, which are connected to the resin injection ports 10 and extend linearly in the radial direction of the fan with a thickness greater than that of the inclined face of the bushing 2a of the main plate, are provided in predetermined intervals of the side face on the motor side of the main board 2. When the resin flows from the bushing cranes 9a to the thicker upper portion of bushing 2d near the thicker boss than the inclined face of the bushing at the moment of the molding, the fusion portion of the resin A is not connected to the cooling hole of the motor 5 as an opening that has a low resistance against impact, but is formed between the cooling holes of the engine 5. Accordingly, the resin flows easily to the extrusion 2c to improve the molding capacity, and the fusion portion of the resin formed

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on the main board 2 it can be shortened. Therefore, even if an impact is applied in the axial direction (vertical direction in FIG. 1B) of the turbo fan 1 at the time of transport or the like so that a crack occurs in the worst case, the Turbo fan is resistant to breakage. Improved molding capacity and high reliability can be achieved against an impact of the turbo fan.

The cooling holes of the engine 5 are arranged near the ends of the center side of the fan 9a1 of the bushing cranes 9a, and at least the number of the cooling holes of the engine 5 and the number of the bushing cranes 9a They are equal. In addition, the ends of the inner radius side of the vane 3a are disposed near the ends of the outer radius side of the fan 9a2 of the bushing cranes 9a. The bushing cranes 9a and vane cranes 9b formed in such a way as to surround the openings 3b of the vanes 3 are connected to each other through the connecting rods 9c, such that the melting portion of the resin A made of the resin flowing from the bushing cranes 9a is formed between the cooling holes of the motor 5 with reliability. As a result, even if an impact is applied in the axial direction (vertical direction in FIG. 1B) of the fan turbo 1 at the time of transport or the like so that a crack occurs in the worst case, the turbo fan is resistant to breakage. Improved molding capacity and high reliability against an impact of the turbo fan can be achieved. Since the bushing crane 9a and the vane crane 9b are not integrally formed, the amount of injection of the resin injected from the resin injection port 10 between the bushing crane 9a and the vane grille 9b can be adjusted. Therefore, the occurrence of a locally small cavity and thickness due to uneven flow can be avoided, and therefore resistance deterioration can be prevented. Since the resin flows more easily due to the vane grains 9b, the thickness of the vane 3 can be reduced, and the thickness of the connecting part of the vane 3 and the main plate 2 in which it can be increased Concentrate stress. In this way, both an improvement in the molding capacity and an improvement in the resistance of the turbo fan can be carried out by means of the improvement in the flow capacity of the resin.

Since the neighboring linear bushing cranes 9a are formed in such a way that they do not overlap each other, the main direction of the resin stream is the radial direction such that the direction of the flow is less complicated compared to the case. conventional in which the ribs that form the cranes for a resin injection port 10 are numerous, the fusion portion of the resin A can be made clearer, the number of fusion portions of the resin A can be reduced, it can simplify the design of the mold, the occurrence of a cavity and the thickness locally small can be avoided due to uneven flow, and the deterioration of the turbo fan resistance can be prevented.

Since the bushing crane 9a projects towards the side of the external air duct of the fan 7 of the main plate, the bushing crane 9a can also serve as an air winch to induce the flow G towards the engine cooling hole 5. With the configuration, the air flowing on the surface of the fan motor 8, which is mounted on the side of the external air duct of the fan 7 of the bushing 2a and fixed to the turbo fan 1 by means of the boss 2c, increases , in order to cool the engine more easily. Therefore, temperature protection control to cope with the increase in engine temperature becomes unnecessary and, in addition, engine breakage due to high temperature can also be prevented.

The resin injection port provided near the end of the inner radius side of the vane and the vane grout formed so as to surround the opening of the side of the main plate of the vane having the hollow shape are connected to each other. through the connection wire. The hollow of the inner radius side of the blade, the hollow of the outer radius side of the blade, the hollow front surface of the blade, and the hollow rear surface of the blade of the blade gap are inclined faces at an arbitrary angle 0 with respect to the axis of rotation. The end of the inner radius side of the blade, the end of the outer radius side of the blade, the end of the suction side of the blade, and the end of the front side of the blade on the front side and the end of the side Rear of the vane on the rear side in the direction of rotation of the vane are formed such that they have almost the same thickness throughout the entire vane. The vane and the vane gap are formed in such a way that it narrows from the main plate towards the cover. Since the pallet has a hollow structure, the weight of the pallet can be reduced. Due to the almost uniform thickness, the occurrence of a poor molding caused by variations in the cooling and hardening time of the resin due to a non-uniform thickness of the pallet is suppressed, so that the molding capacity is high. In addition, since each of the vane and the recess of the vane has a conical shape in an angle of molding inclination, which is inclined at the predetermined angle from the main plate towards the cover, the mold can be released easily The pallet breakage can be prevented due to the adhesion of the pallet to the mold and the molding capacity is high.

In a turbo fan made of a thermoplastic resin that includes: a disk-shaped main plate having a projected bushing formed by making a central portion such that it covers a motor, a plurality of engine cooling holes formed in the bushing , for the communication of the motor and the interior of the fan, and a protuberance as a part of attachment to a rotating rod of an engine, which is provided in the central portion of the hub; a plurality of pallets; and a cover for coupling the plurality of vanes to form an air inlet wall, a plurality of bushing grains, each of which is connected to a resin injection port formed in a flat part of the main plate near the end of the inner radius side of the vane, made thicker than the inclined face of the main plate, and linearly extended in the radial direction of the fan, is provided at predetermined intervals on the side face of the motor side of the plate principal. The bushing cranes are formed in this way in which a fusion portion of the resin formed

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between the neighboring bushing cranes it is not connected at least to the engine cooling holes. The hollow of the inner radius side of the blade, the hollow of the outer radius side of the blade, the hollow front surface of the blade, and the hollow rear surface of the blade of the blade gap are inclined faces at an arbitrary angle 0 with respect to the axis of rotation. The end of the inner radius side of the blade, the end of the outer radius side of the blade, the end of the suction side of the blade, and the end of the front side of the blade on the front side and the end of the side Rear of the vane on the rear side of the direction of rotation of the vane are formed such that they are almost the same thickness throughout the entire vane. The vane and the vane hole are formed in such a way that they narrow from the main plate towards the cover. Given the bushing cranes, the flow capacity of the resin in the bushing and the main plate is high, and the molding capacity is high. Since the bushing cranes are formed in such a way that the melting portion of the resin does not communicate with at least the engine cooling holes, the breakage of the fan caused by an impact at the time of transport or the like is avoided. . Since the vane has a hollow structure, the weight of the turbo fan as a whole can be reduced. Due to the almost uniform thickness, the occurrence of a poor molding caused by variations in the cooling and hardening time of the resin due to a non-uniform thickness of the pallet is suppressed, so that the molding capacity is high. In addition, since each of the vane and the recess of the vane has a conical shape at an angle of molding inclination, which is inclined at the predetermined angle from the main plate towards the cover, the mold can be released easily, The pallet breakage can be avoided due to the adhesion of the pallet to the mold, and the molding capacity is high.

In addition, due to the reduction in the weight of the vanes, the weight of the outer peripheral portion of the turbo fan is reduced relative to the center of rotation of the turbo fan. Accordingly, the centrifugal resistance is reduced at the time of rotation, the tension applied on the root of the vane on the main plate is reduced, and the resistance can be improved. Therefore, breakage of the turbo fan can be prevented at the time of rotation. As a result, a light weight and high reliability of the turbo fan having high molding capacity and strength is obtained.

The hollow of the inner radius side of the vane, the hollow of the outer radius side of the vane, the hollow front surface of the vane, and the hollow rear surface of the vane of the vane of the vane are faces inclined at an angle of inclination 0 from 1 ° to 3 ° with respect to the axis of rotation. The end of the inner radius side of the blade, the end of the outer radius side of the blade, the end of the suction side of the blade, and the end of the front side of the blade on the front side and the end of the side Rear of the vane on the rear side in the direction of rotation of the vane are formed such that they have almost the same thickness throughout the entire vane. The vane and the vane hole are formed in such a way that they narrow from the main plate towards the cover. Since the pallet has a hollow structure, the weight can be reduced. Due to the almost uniform thickness, the occurrence of a poor molding caused by variations in the cooling and hardening time of the resin due to a non-uniform thickness of the pallet is suppressed, so that the molding capacity is high. In addition, since each of the vane and the recess of the vane has a conical shape at an angle of molding inclination, which is inclined at the predetermined angle from the main plate towards the cover, the mold can be released with ease, the pallet breakage can be avoided due to the adhesion of the pallet to the mold, and the molding capacity is high. A noise change is at least small and does not deteriorate. As a result, when at least the angle of inclination 0 is from 1 ° to 3 °, a turbo fan with a small noise change and high molding capacity is obtained.

The angles of passage of the assembly 6 in the circumferential direction of the vanes 3 are established as unequal angles of passage and, simultaneously, the angles of passage and in the circumferential direction of the cooling holes of the motor 5 are unequal angles of passage in correspondence with the vanes 3. The bushing cranes 9a that extend linearly in the radial direction from the center of rotation of the fan Or are also arranged in uneven steps in correspondence with the vanes 3 and the engine cooling holes 5. A resin injection port 10, bushing crane 9a, vane crane 9b, and the cooling hole of the motor 5 are arranged in almost the same arrangement. Consequently, the molding conditions almost do not change, the occurrence of a cavity and the locally small thickness can be prevented due to uneven flow, and deterioration of the turbo fan resistance can be prevented. Since the cooling holes of the motor 5 and the vanes 3 are arranged in the same arrangement, the turbulent flow E2 from the external air duct of the fan 7 to the internal air duct of the fan 6 through the cooling hole of the motor 5 does not collide directly with the vane 3, the turbo fan is not subjected to pressure fluctuations in such a way that the noise can be reduced.

The resin flowing out from the resin injection port 10 flows from the bushing crane 9a to the cooling hole 9d and flows to the boss 2c. Since the cooling hole 9d is located around the cooling hole of the motor 5, after the resin flows inside, the resin is fused back on the back side in the direction of flow of the cooling hole resin from the engine, and the fused resin flows to the 2c protuberance. Consequently, unlike the conventional technique in which there is no cooling hole around the cooling hole and the resin does not easily re-merge on the back side in the direction of flow of the cooling hole resin , the resistance around the cooling hole of the motor 5, which tends to decrease due to the opening, can be improved. As a result, an improvement is achieved both in the molding capacity and in the resistance by means of the improvement in the flow capacity of the resin around the engine cooling hole, and a turbo fan is obtained which

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It is resistant to breakage even when an impact is applied.

When the ratio of t1 / t2 is in the range of 1.1 to 2, and the ratio of t2 / t0 is in the range of 1.1 to 2, in which t1 denotes the maximum thickness of the range of bushing 9a, t2 denotes the maximum thickness of the pallet gma 9b, and t0 denotes the minimum thickness of the other portion of the main plate 2, the molding time can be shortened compared to the case in which the thicknesses are equal (t1 / t0, t2 / t0 =). The amount of production can be increased at the same time, the electricity needed for a molding machine can also be reduced, and energy can be saved.

The frontal gma of the vane corresponding to the lateral face in the direction of rotation of the vane of the pallet gma formed such that it surrounds the opening on the outer side of the main plate of the vane having a hollow structure has a height greater than the rear gma of the blade corresponding to the side face on the opposite side in the direction of rotation of the blade and is formed such that it protrudes outside the fan. Consequently, the noise, which is generated in the narrow band at the time of rotation can be suppressed since the flow around the main plate is separated from the front range of the vane, collides with the corner of the rear range of the paddle, so there is a pressure fluctuation. A reattachment point of the air stream after moving away from the front vane of the vane to the rear side in the direction of rotation of the rear vane of the vane moves to the rear side of the vane opening in such a way that the air stream is gently reattached. Therefore, noise can be reduced.

In a turbo fan made of a thermoplastic resin that includes: a disk-shaped main plate having a projected bushing formed by making a central portion such that it covers a motor, a plurality of engine cooling holes formed in the bushing for the communication between the motor and the interior of the fan, and a protuberance as a fixing part fixed to an axis of rotation of an engine, which is provided in the central portion of the hub; a plurality of pallets; and a cover for coupling the plurality of vanes to form an air inlet wall, a plurality of bushing ranges, each of which is connected to a resin injection port formed in a flat portion of the main plate near the end of the side of the inner radius of the vane, made thicker than the inclined face of the main plate, and extends linearly in the radial direction of the fan, is provided at predetermined intervals on the side face of the motor side of the main board The bushing ranges are formed in this way that a portion of the fusion of the resin formed between the neighboring bushing shafts is not connected at least to the engine cooling holes. The hollow of the inner radius side of the blade, the hollow of the outer radius side of the blade, the hollow front surface of the blade, and the hollow rear surface of the blade of the blade gap are inclined faces at an arbitrary angle 0 with respect to the axis of rotation. The end of the inner radius side of the blade, the end of the outer radius side of the blade, the end of the suction side of the blade, and the end of the front side of the blade on the front side and the end of the side Rear of the vane on the rear side in the direction of rotation of the vane are formed such that they have almost the same thickness throughout the entire vane. The vane and the vane gap are formed in such a way that they narrow from the main plate towards the cover. The vane gma formed in such a way that it surrounds the opening outside the main plate of the vane having the hollow structure is connected through the connecting gma. The front gma of the pallet corresponding to the side face in the direction of rotation of the pallet of the pallet gma has a height greater than that of the rear gma of the pallet corresponding to the side face on the opposite side in the direction of rotation of the vane and is formed in such a way that it protrudes outside the fan. Due to the bushing gmas, the resin flow capacity in the bushing and main plate is high, and the molding capacity is high. Since the bushing ranges are formed in such a way that the melting portion of the resin is not connected to at least the engine cooling holes, the breakage of the fan caused due to an impact at the time of transport or Similar. Since the vane has a hollow structure, the weight of the turbo fan as a whole can be reduced. Due to almost uniform thickness, the occurrence of a poor molding caused by variations in the cooling and hardening time of the resin due to a non-uniform thickness of the blade is suppressed, so that the molding capacity is high. In addition, since each of the vane and the recess of the vane has a conical shape at an angle of molding inclination, which is inclined at the predetermined angle from the main plate towards the cover, the mold can be released with Ease, pallet breakage can be avoided due to adhesion of the pallet to the mold, and the molding capacity is high. The noise can be suppressed, which is generated in the narrow band at the time of rotation, since the flow around the main plate is separated from the front gma of the vane, collides with the corner of the rear gma of the vane, in such a way that what produces a pressure fluctuation. A point of re-attachment of the air flow after departing from the front vane of the vane to the rear side in the direction of rotation of the rear vane of the vane moves to the rear side of the vane opening so that the air stream is gently reattached. Therefore, noise can be reduced. Since the front gma of the blade becomes thicker, the resin flows smoothly to the blade at the time of molding, and contraction can be prevented. On the other hand, the resistance in the frontal gma of the vane is improved, so that the resistance of the turbo fan is also improved. As a result, a lightweight, strong, and low noise turbo fan can be obtained that can be prevented from breaking at the time of rotation and transport.

The turbo fan is formed in such a way that the At / F ratio of the difference At between the height of the front gma of the vane 9ba and the height of the rear gma of the vane 9bb with respect to the maximum opening diameter F of the vane opening 3b is in the range of 4% to 22%. At the time of rotation, the noise is

5

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twenty

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35

it can be suppressed, which is generated in the narrow band since the flow around the main plate is separated from the front gma of the vane, collides with the corner of the rear gma of the vane so that a pressure fluctuation occurs . An air flow re-attachment point after departing from the front vane of the vane to the rear side in the direction of rotation of the rear vane of the vane moves to the rear side of the vane opening, such that the air flow is gently reattached to the rear side of the rear opening of the vane, so that noise can be reduced. A peak sound is suppressed due to the speed of rotation, which is generated by separating the flow in the front gma of the blade with a thickness that is too large, and noise deterioration can be prevented. Consequently, noise reduction can be achieved.

An air conditioner that includes: the turbo fan 1 having any of the configurations described in the first embodiment; and the heat exchanger arranged on the suction side or on the ejection side of the turbo fan can be tuned thanks to the improvement in the molding capacity of the turbo fan 1 and, consequently, the weight can be reduced. In addition, the air conditioner has high reliability in terms of resistance. Consequently, at the time of assembly after transport, the turbo fan 1 is not broken due to an impact, such as vibrations at the time of transport, such that the reliability of the product is high. The weight of the product can also be reduced only by the reduced weight of the turbo fan 1.

The present invention also provides a built-in ceiling air conditioner, which has the following configuration. The side plates and the upper plate of the air conditioner body are formed by plate members. The interior of the body of the air conditioner that includes the side plates and at least part of the roof serves as a wall of the air path by the use of a heat insulating material. An engine and the turbo fan 1 having at least one of the configurations described in the first embodiment are mounted around the center of the air conditioner body. A bell mouth that constitutes a suction port of the turbo fan and a port of aspiration of the body is arranged in the central portion of the lower face of the body of the air conditioner. A heat exchanger is arranged vertically in order to surround the turbo fan. A drain pan made of foam is arranged under the heat exchanger. An ejection port of a body is provided in a position around the aspiration port of the body and almost along the side plate of the body of the air conditioner. A decorative panel that has the suction port of the panel and the ejection port of the panel that communicates with the aspiration port of the body and the ejection port of the body, respectively, is attached to the lower face of the body. With the configuration, the air conditioner can be refined thanks to the improvement in the molding capacity of the turbo fan 1 and, consequently, the weight can be reduced. In addition, the air conditioner has high reliability in terms of resistance. Consequently, at the time of assembly after transport, the turbo fan 1 is not broken due to an impact, such as vibrations at the time of transport, such that the reliability of the product is high. The weight of the product can also be reduced only by the reduced weight of the turbo fan 1.

Claims (10)

1. A turbo fan (1) comprising: a disk-shaped main board (2); 5 a projected bushing (2a) formed by projecting a central portion of the main plate (2) in a direction of the axis of rotation; Y a plurality of vanes (3) each of which is provided vertically in the direction of projection of the bushing (2a) by the use of a flat part of the side of the outer periphery of the main plate (2) as a base The turbo fan is characterized by also comprising: a plurality of engine cooling holes (5) that are formed in the hub (2a) in order to cool a motor (8) arranged in a space that has a projection shape surrounded by the hub (2a); a plurality of bushing crane marks (9a) formed by solidifying the resin in the bushing cranes, the bushing cranes are provided radially in the bushing (2a) and by means of bushing formation (2a) by means of the flow of a thermoplastic resin at the time of molding; Y twenty resin fusion portions (A) each of which is formed by the fusion of thermoplastic resin flowing out of the neighboring bushing cranes at the time of molding, wherein the engine cooling holes (5) are arranged in such a way as to avoid the resin fusion portions (A). 2. The turbo fan (1) according to claim 1, wherein each of the vanes (3) has a hollow shape that has an opening in the base, the turbo fan includes a plurality of pallet-shaped marks (9b) formed by solidifying the resin in the rods. of pallet, the pallet cranes are provided around the bases of the pallets (3) in order to form the 30 pallets (3), and a plurality of marks of connecting grains (9c) formed by means of solidification of the resin in the connection cranes, each of the connection cranes connect one of the bushing cranes (9a) to one of the vane cranes positioned near the bushing cradle, and The thermoplastic resin is injected from the injection ports (10) formed in the bushing cranes, the connecting cranes, or the paddle cranes and they are allowed to flow in all the cranes, which thus performs the molding . 3. The turbo fan according to claim 1 or 2, wherein the plurality of engine cooling holes (5) formed in the hub (2a) are arranged in parts at the extension lines of the crane marks of bushing (9a) next to center of rotation. 4. The turbo fan (1) according to claim 3, wherein an equal number of engine cooling holes 40 (5) and bushing crane marks (9a) are provided. 5. The turbo fan according to any one of claims 1 to 4, wherein the marks of the bushing cranes (9a) project from the face of the main plate (2) of the bushing (2a) on the side of engine layout 6. The turbo fan (1) according to any one of claims 2 to 5, wherein a plurality of assemblies each made of the vane (3), the mark of the vane ring (9b), the mark of the bushing shaft (9a), the 45 mark of the connecting wire (9c) and the engine cooling hole (5) are provided radially around the center of rotation axis. 7. The turbo fan (1) according to claim 6, wherein at least one of the angles (61 to 6 7) each formed between neighboring assemblies is different from the other angles. 8. The turbo fan (1) according to any one of claims 1 to 7, which further comprises a plurality of markings of cooling hole grains (9d) formed by solidifying the resin into the cooling hole cranes, the cooling hole cranes are connected respectively to the bushing cranes and formed in such a way that they surround the engine cooling holes (5) 9. The turbo fan (1) according to any of claims 2 to 8, wherein when at least one of the thickness of the marks of the bushing cranes (9a) or the thickness of the marks of the bushing grains palette (9b) se 55 is set as "t" and the minimum thickness of a portion other than the marks of the cranes on the main board (2) is set as t0, the ratio t / t0 is set in the range of 1.1 <t / t0 <2. 10. An air conditioner comprising: the turbo fan (1) according to any one of claims 1 to 9; Y a heat exchanger (15), 5 wherein the air drawn from an aspiration port by the turbo fan (1) is exchanged for heat with a refrigerant in the heat exchanger (15), and the resulting air is allowed to blow out from an ejection port.