JP4423919B2 - Centrifugal blower and air conditioner using the same - Google Patents

Description

  The present invention relates to a centrifugal blower having a compact configuration and an air conditioner configured using the centrifugal blower.

  In the indoor unit of an air conditioner in which a centrifugal blower and a heat exchanger are arranged in series in the airflow direction, the outer diameter of the centrifugal blower is required to prevent pressure loss of the intake air and to increase the ventilation area (heat exchange area). In general, a centrifugal impeller having a relatively large inner diameter ratio is used (see, for example, Patent Document 1). In this case, from the viewpoint of reducing the height of the centrifugal impeller, the central portion of the centrifugal impeller hub may be raised to the suction side (shroud side), and the motor may be disposed in the recess on the hub side. It is customary (see, for example, Patent Document 1).

  By the way, in the centrifugal blower provided with the centrifugal impeller having such a configuration, as shown in FIG. 10, when the centrifugal impeller 50 having a relatively large inner diameter ratio with respect to the outer diameter of the centrifugal blower is used, the suction port 54 is used. The wind speed of the suction air into the outer peripheral portion is larger than the center portion of the suction port 54, and the suction wind speed is uneven or the rotational speed of the centrifugal impeller for obtaining the required air volume is increased. There were problems such as increased noise.

  As a means for solving such a problem, a technique has been proposed in which an axial flow impeller is arranged coaxially with the upstream side of a centrifugal impeller and integrated with the centrifugal impeller (for example, Patent Documents). 2, see Patent Document 3).

JP 2003-74492 A (FIGS. 1 and 2)

JP-A-9-32796 (paragraphs “0017” to “0020”, FIG. 1) Japanese Patent Laid-Open No. 6-129396 (paragraph “0009”, FIG. 1)

  However, as shown in FIG. 11, the axial flow impeller 61 is arranged coaxially with the upstream side of the centrifugal impeller, and this is integrated with the centrifugal impeller, so that it is necessary to suppress the height of the blower. For example, when the central portion of the hub 51 is raised to the suction side, or as shown in FIG. When arranged on the upstream side of the impeller 61, the presence of the raised portion or the presence of the motor 56 makes it difficult for air to occur in the central portion of the blower in any of these, and as a result, in the vicinity of the outer periphery of the hub 51 The flow Aa is generated, resulting in an increase in noise and a decrease in blowing efficiency.

  As shown in FIG. 13, when the hub 51 of the centrifugal impeller 50 is a flat surface and the motor 56 is arranged on the lower surface side of the hub 51, the air flow at the center of the blower can be improved, but the motor 56 The problem that the height of the blower is increased due to the presence of the fan.

  Accordingly, in any of the structures shown in FIGS. 10 to 13, the axial flow impeller 61 is arranged coaxially with the upstream side of the centrifugal impeller 50, and this is integrated with the centrifugal impeller to adjust the suction wind speed. There was a problem that the effect that was originally aimed at equalization could not be expected so much.

  Therefore, in the present invention, a centrifugal fan capable of improving the air blowing performance without incurring an increase in operating noise or an increase in height, and the like, and a high heat exchange performance realized by including the centrifugal fan. It was made for the purpose of providing an air conditioner.

  In the present invention, the following configuration is adopted as a specific means for solving such a problem.

  In the first invention of the present application, the shroud of the centrifugal impeller 1 in which a plurality of blades 4 are disposed between a disk-shaped hub 2 and a ring-shaped shroud 3 which are coaxially spaced apart from each other. The axial flow impeller 30 provided with a plurality of blades 31 is arranged substantially coaxially and integrated on the inner peripheral side of the ring 3, while the centrifugal impeller 1 has a ring-shaped base portion 11a and the base portion. A steel plate rotor 11 having a plurality of protrusions 11b radially extending from 11a and having a ring-shaped magnet 15 attached to the base portion 11a is attached, and each of the rotors 11 is attached to a base 14. A coil body 12 formed by printing a plurality of coils 13 so as to correspond to each of the protrusions 11b is disposed so that the coils 13 face the protrusions 11b of the rotor 11, and the rotor It is characterized by being configured the motor 10 that drives integrally rotated 1 and the centrifugal impeller 1 and the axial flow impeller 30 in the coil body 12.

  The second invention of the present application is characterized in that, in the centrifugal blower according to the first invention, the rotor 11 is mounted on the upstream side surface 3a of the shroud 3.

  The third invention of the present application is characterized in that, in the centrifugal blower according to the first invention, the rotor 11 is mounted on the downstream side surface 2 a of the hub 2.

  In the fourth invention of the present application, the shroud of the centrifugal impeller 1 in which a plurality of blades 4 are disposed between a disk-shaped hub 2 and a ring-shaped shroud 3 which are coaxially spaced apart from each other. 3, an axial flow impeller 30 having a plurality of blades 31 is arranged on the same axis and integrated, while a part of the hub 2 of the centrifugal impeller 1 is attached to a ring. And a plurality of protrusions 11b extending radially from the base 11a in a radial direction, and a base member 14 on each of the protrusions 11b of the rotor 11. Coil bodies 12 formed by printing a plurality of coils 13 so as to correspond to the respective coils 13 are arranged so that the coils 13 face the projections 11b of the rotor 11, and the rotor 11 and the coils are arranged. The centrifugal blade in the body 12 1 and the axial flow impeller 30 is characterized by being configured the motor 10 that drives integrally rotate.

  In the fifth invention of the present application, the shroud 3 of the centrifugal impeller 1 in which a plurality of blades 4 are disposed between a disk-shaped hub and a ring-shaped shroud 3 that are coaxially spaced apart from each other. An axial flow impeller 30 provided with a plurality of blades 31 is arranged on the inner circumference side of the same and coaxially integrated with each other, and a part of the shroud 3 of the centrifugal impeller 1 is formed in a ring shape. The base 11a and a plurality of protrusions 11b extending radially from the base 11a in a radial manner, and a rotor 11 made of a magnet material, and a base 15 on each of the protrusions 11b of the rotor 11 The coil body 12 formed by printing a plurality of coils 13 so as to correspond to the above is disposed so that the respective coils 13 face the respective protrusions 11b of the rotor 11, and the rotor 11 and the coil body are arranged. 12 at the above centrifuge Roots wheel 1 and the axial flow impeller 30 is characterized by being configured the motor 10 that drives integrally rotate.

  According to a sixth invention of the present application, in the centrifugal blower according to the fourth or fifth invention, the rotor 11 is integrally formed with a magnet material, and insert molding is integrally performed with the hub 2 or the shroud 3 during resin molding. It is characterized by that.

  According to a seventh invention of the present application, in the centrifugal blower according to the fourth or fifth invention, the rotor 11 is mixed with a resin mixed with a magnet material at the time of resin molding of the hub 2 or the shroud 3. It is characterized by two-color molding integrally with these.

  In the eighth invention of the present application, in the centrifugal blower according to the first, second, third, fourth, fifth, sixth or seventh invention, the upstream tip of the blade 31 of the axial flow impeller 30 The part 31b is characterized in that it is positioned on the downstream side or flush with the upstream side wall surface 7a of the bell mouth 7 disposed on the upstream side of the shroud 3 of the centrifugal impeller 1.

  In the ninth invention of the present application, a heat exchanger 21 is added to the centrifugal blower according to the first, second, third, fourth, fifth, sixth, seventh or eighth invention. The air conditioner is characterized in that the heat exchanger 21 is arranged on the radially inner side and the radially outer side of the blade row in the impeller 1.

  In the tenth invention of the present application, the centrifugal blower according to the first, second, third, fourth, fifth, sixth, seventh or eighth invention is provided with a heat exchanger 21. The air conditioner is characterized in that the heat exchanger 21 is disposed radially inward of the blade row in the impeller 1.

  In the eleventh aspect of the present invention, the heat exchanger 21 is added to the centrifugal blower according to the first, second, third, fourth, fifth, sixth, seventh or eighth aspect of the invention. In the air conditioner, the heat exchanger 21 is arranged on the upstream side of the intake air in the impeller 1 so that at least one surface thereof is substantially perpendicular to the rotary shaft 8 of the centrifugal blower. It is said.

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

  (A) According to the centrifugal blower according to the first invention of the present application, a plurality of blades 4 are disposed between the disc-shaped hub 2 and the ring-shaped shroud 3 which are coaxially spaced apart and opposed to each other. On the inner peripheral side of the shroud 3 of the centrifugal impeller 1, an axial flow impeller 30 having a plurality of blades 31 is arranged substantially coaxially and integrated with the centrifugal impeller 1. A steel plate rotor 11 having a ring-shaped base portion 11a and a plurality of protrusions 11b extending radially from the base portion 11a in a radial direction and having a ring-shaped magnet 15 attached to the base portion 11a; A coil body 12 having a plurality of coils 13 printed on the base 14 so as to correspond to the protrusions 11 b of the rotor 11 is connected to the protrusions 11 b of the rotor 11. Against Place in the constitute a motor 10 which drives integrally rotating the centrifugal impeller 1 and the axial flow impeller 30 by the rotor 11 and the coil body 12.

  Therefore, according to the centrifugal blower of this invention, the said hub 2 in the said centrifugal impeller 1 is made into a disk shape, and the center part of the hub protrudes to the suction side like the centrifugal impeller in the conventional centrifugal blower. The resistance to the suction flow is less than in the case of the above, and the motor 10 does not exist on the suction side of the axial flow impeller 30, and the suction flow by the motor 10 as in the conventional centrifugal impeller 1 does not exist. Due to the absence of resistance and a synergistic effect thereof, the effect of uniforming the wind speed distribution of the suction flow toward the centrifugal impeller 1 by the axial flow impeller 30 is maximized. As a result, for example, the centrifugal impeller 1 Even when the ratio of the inner diameter to the outer diameter is relatively large, the suction wind speed is made as uniform as possible, the required rotational speed of the centrifugal impeller to obtain the required air volume is reduced, and the blowing noise is reduced. Energy resistance and centrifugal fan excellent in quietness drivability can be obtained.

  Further, since the motor 10 has a flat form composed of the rotor 11 and the coil body 12 facing each other in the axial direction of the centrifugal blower, the height dimension thereof is suppressed low. As a result, the motor 10 is provided. In the centrifugal blower configured as described above, the height can be kept small, and the size reduction can be achieved.

  Further, the motor 10 is disposed near the outer periphery of the centrifugal impeller 1, and is separated greatly from the rotary shaft portion located in the central portion of the centrifugal impeller 1 in the radial direction so that both of them can have different structures. Further, the influence of the heat on the motor 10 side on the rotating shaft portion is suppressed as much as possible, the deterioration of the lubrication performance due to the heat hardly occurs, and the durability and reliability of the bearing are improved accordingly. .

  (B) According to the centrifugal blower according to the second invention of the present application, in addition to the effect described in the above (a), the following specific effect is obtained. That is, in the present invention, since the rotor 11 is mounted on the upstream side surface 3a of the shroud 3, the motor 10 is disposed in a gap between the shroud 3 and the bell mouth 7 disposed on the upstream side. Thus, the idle space in the entire centrifugal fan can be effectively utilized. For example, as compared with the case where the motor 10 is disposed on the hub 2 side, the height reduction of the centrifugal fan is further promoted. Will be.

  (C) According to the centrifugal blower according to the third invention of the present application, in addition to the effect described in the above (a), the following specific effect is obtained. In other words, in the present invention, since the rotor 11 is mounted on the downstream side surface 2a of the hub 2, the hub 2 side has a higher rigidity than the shroud 3 side. This facilitates the stable operation of the motor 10 and improves its reliability.

  (D) In the centrifugal blower according to the fourth invention of the present application, a plurality of blades 4 are arranged between a disk-shaped hub 2 and a ring-shaped shroud 3 which are coaxially spaced apart and opposed to each other. On the inner peripheral side of the shroud 3 of the centrifugal impeller 1, an axial flow impeller 30 having a plurality of blades 31 is arranged substantially coaxially and integrated, while the hub of the centrifugal impeller 1 is integrated. 2 includes a ring-shaped base portion 11a and a rotor 11 made of a magnet material having a plurality of protrusions 11b radially extending from the base portion 11a in the radial direction. A coil body 12 formed by printing a plurality of coils 13 so as to correspond to each of the protrusions 11b is disposed so that the coils 13 face the protrusions 11b of the rotor 11. , The rotor 11 and the carp The centrifugal impeller 1 and the axial flow impeller 30 in the body 12 constitute a motor 10 which drives integrally rotate.

  Therefore, according to the centrifugal blower of this invention, the said hub 2 in the said centrifugal impeller 1 is made into a disk shape, and the center part of the hub protrudes to the suction side like the centrifugal impeller in the conventional centrifugal blower. The resistance to the suction flow is less than in the case of the above, and the motor 10 does not exist on the suction side of the axial flow impeller 30, and the suction flow by the motor 10 as in the conventional centrifugal impeller 1 does not exist. Due to the absence of resistance and a synergistic effect thereof, the effect of uniforming the wind speed distribution of the suction flow toward the centrifugal impeller 1 by the axial flow impeller 30 is maximized. As a result, for example, the centrifugal impeller 1 Even when the ratio of the inner diameter to the outer diameter is relatively large, the suction wind speed is made as uniform as possible, the required rotational speed of the centrifugal impeller to obtain the required air volume is reduced, and the blowing noise is reduced. Energy resistance and centrifugal fan excellent in quietness drivability can be obtained.

  Further, since the motor 10 has a flat form composed of the rotor 11 and the coil body 12 facing each other in the axial direction of the centrifugal blower, the height dimension thereof is suppressed low. As a result, the motor 10 is provided. In the centrifugal blower configured as described above, the height can be kept small, and the size reduction can be achieved.

  Further, the motor 10 is disposed near the outer periphery of the centrifugal impeller 1, and is separated greatly from the rotary shaft portion located in the central portion of the centrifugal impeller 1 in the radial direction so that both of them can have different structures. Further, the influence of the heat on the motor 10 side on the rotating shaft portion is suppressed as much as possible, the deterioration of the lubrication performance due to the heat hardly occurs, and the durability and reliability of the bearing are improved accordingly. .

  A part of the hub 2 of the centrifugal impeller 1 is a rotor 11 made of a magnet material having a ring-shaped base 11a and a plurality of protrusions 11b extending radially from the base 11a. For example, the structure of the hub 2 can be simplified and the cost of the centrifugal blower can be reduced as compared with the case where the rotor 11 is configured separately from the hub 2. .

  (E) In the centrifugal blower according to the fifth invention of the present application, a plurality of blades 4 are arranged between a disc-shaped hub (coaxially spaced and opposed) and a ring-shaped shroud 3. On the inner peripheral side of the shroud 3 of the centrifugal impeller 1, an axial flow impeller 30 having a plurality of blades 31 is arranged substantially coaxially and integrated, while the shroud of the centrifugal impeller 1 is integrated. 3 is constituted by a rotor 11 made of a magnet material having a ring-shaped base portion 11a and a plurality of protrusions 11b extending radially from the base portion 11a in the radial direction. The coil body 12 formed by printing a plurality of coils 13 so as to correspond to each of the protrusions 11b is arranged so that the coils 13 face the protrusions 11b of the rotor 11). And the rotor 11 It is characterized in that in serial coil body 12 to constitute a motor 10 which drives integrally rotating the centrifugal impeller 1 and the axial flow impeller 30.

  Therefore, according to the centrifugal blower of this invention, the said hub 2 in the said centrifugal impeller 1 is made into a disk shape, and the center part of the hub protrudes to the suction side like the centrifugal impeller in the conventional centrifugal blower. The resistance to the suction flow is less than in the case of the above, and the motor 10 does not exist on the suction side of the axial flow impeller 30, and the suction flow by the motor 10 as in the conventional centrifugal impeller 1 does not exist. Due to the absence of resistance and a synergistic effect thereof, the effect of uniforming the wind speed distribution of the suction flow toward the centrifugal impeller 1 by the axial flow impeller 30 is maximized. As a result, for example, the centrifugal impeller 1 Even when the ratio of the inner diameter to the outer diameter is relatively large, the suction wind speed is made as uniform as possible, the required rotational speed of the centrifugal impeller to obtain the required air volume is reduced, and the blowing noise is reduced. Energy resistance and centrifugal fan excellent in quietness drivability can be obtained.

  Further, since the motor 10 has a flat form composed of the rotor 11 and the coil body 12 facing each other in the axial direction of the centrifugal blower, the height dimension thereof is suppressed low. As a result, the motor 10 is provided. In the centrifugal blower configured as described above, the height can be kept small, and the size reduction can be achieved.

  Further, the motor 10 is disposed near the outer periphery of the centrifugal impeller 1, and is separated greatly from the rotary shaft portion located in the central portion of the centrifugal impeller 1 in the radial direction so that both of them can have different structures. Further, the influence of the heat on the motor 10 side on the rotating shaft portion is suppressed as much as possible, the deterioration of the lubrication performance due to the heat hardly occurs, and the durability and reliability of the bearing are improved accordingly. .

  Further, a part of the shroud 3 of the centrifugal impeller 1 is a rotor 11 made of a magnet material having a ring-shaped base portion 11a and a plurality of protrusions 11b extending radially from the base portion 11a. Since it is configured, for example, the structure of the shroud 3 portion can be simplified and the cost of the centrifugal blower can be reduced as compared with the case where the rotor 11 is configured separately from the shroud 3. .

  (F) According to the centrifugal blower according to the sixth invention of the present application, in addition to the effect described in (d) or (e) above, the following specific effect is obtained. That is, in the present invention, the rotor 11 is integrally formed of a magnet material, and insert molding is integrally performed with the hub 2 or the shroud 3 when the hub 2 or the shroud 3 is resin-molded. And the attachment work of the rotor 11 to these can be performed simultaneously, and the cost reduction of the centrifugal fan is promoted accordingly.

  (G) According to the centrifugal blower according to the seventh invention of the present application, in addition to the effects described in (d) and (e) above, the following specific effects can be obtained. That is, in the present invention, in the centrifugal blower according to the fourth or fifth invention, the rotor 11 is mixed with a resin mixed with a magnet material during resin molding of the hub 2 or the shroud 3. Since the two-color molding is integrally performed with them, the molding of the hub 2 or the shroud 3 and the molding of the rotor 11 can be completed in one process, and the cost of the centrifugal blower can be reduced by reducing the work man-hours. Is promoted.

  (H) According to the centrifugal blower according to the eighth invention of the present application, the effect described in (a), (b), (c), (d), (e), (f) or (g) is achieved. In addition, the following specific effects can be obtained. In other words, in the present invention, the upstream tip 31b of the blade 31 of the axial flow impeller 30 is located downstream of the upstream side wall surface 7a of the bell mouth 7 disposed on the upstream side of the shroud 3 of the centrifugal impeller 1. Since the centrifugal blower is used in an air conditioner and a heat exchanger is disposed on the upstream side of the centrifugal blower, the centrifugal blower and the heat exchanger It is possible to avoid this interference and to increase the capacity of the heat exchanger, which can contribute to increasing the capacity of the air conditioner.

  (I) According to the air conditioner pertaining to the ninth invention of the present application, heat is applied to the centrifugal blower pertaining to the first, second, third, fourth, fifth, sixth, seventh or eighth invention. In the air conditioner configured with the exchanger 21, the heat exchanger 21 is disposed on the radially inner side and the radially outer side of the blade row in the centrifugal impeller 1. The inside of the direction, that is, the portion that could not be used as the arrangement space for the heat exchanger 21 in the case of an air conditioner having a conventional structure, is also used as the arrangement space for the heat exchanger 21, and the outer dimensions of the air conditioner The heat exchange area can be increased without being enlarged, and as a result, it is possible to provide an air conditioner having a high heat exchange capability with a compact configuration.

  In addition, since the centrifugal blower is configured to include the thin centrifugal impeller 1 including the rotor 11 and the coil body 12, the centrifugal blower is configured to include the centrifugal blower as much as it is thin. The air conditioner that is used can also be made thin to make it compact, particularly in the height direction.

  (J) According to the air conditioner pertaining to the tenth invention of the present application, the centrifugal blower pertaining to the first, second, third, fourth, fifth, sixth, seventh or eighth invention is heated. In an air conditioner configured with an exchanger 21, the heat exchanger 21 may be a radially inner side of a blade row in the centrifugal impeller 1, that is, an air conditioner having a conventional structure. Since the portion that could not be used as the arrangement space of the heat exchanger 21 is used as the arrangement space of the heat exchanger 21, the heat exchange area can be secured without increasing the external dimensions of the air conditioner, and as a result It is possible to provide an air conditioner having a high heat exchange capacity with a compact configuration.

  In addition, since the centrifugal blower is configured to include the thin centrifugal impeller 1 including the rotor 11 and the coil body 12, the centrifugal blower is configured to include the centrifugal blower as much as it is thin. The air conditioner that is used can also be made thin to make it compact, particularly in the height direction.

  (K) According to the air conditioner pertaining to the eleventh invention of the present application, heat is applied to the centrifugal blower pertaining to the first, second, third, fourth, fifth, sixth, seventh or eighth invention. In the air conditioner configured with the exchanger 21, the heat exchanger 21 is arranged on the upstream side of the intake air in the impeller 1, and at least one surface thereof is substantially perpendicular to the rotary shaft 8 of the centrifugal blower. Even if the heat exchanger 21 is formed and arranged so as to surround the suction port 5 on the suction side of the centrifugal impeller 1, at least the rotary shaft 8 is arranged. Therefore, a necessary heat exchange area can be ensured in a portion substantially perpendicular to the air conditioner, and an air conditioner having a stable air conditioning capability that is less affected by the shape of the heat exchanger 21 can be provided.

  Hereinafter, the present invention will be specifically described based on preferred embodiments.

I: First Embodiment FIG. 1 shows a centrifugal blower X1 according to a first embodiment of the present invention. The centrifugal blower X1 is used, for example, as a blower of an air conditioner, and includes a centrifugal impeller 1, an axial flow impeller 30, and a motor 10 described below.

"Centrifuge impeller 1"
The centrifugal impeller 1 is a resin molded product, and has a hub 2 made of a resin disk, and has a suction port 5 having a substantially same outer diameter as that of the hub 2 and having a predetermined diameter at the center thereof. A plurality of resin-made ring-shaped shrouds 3 and a plurality of the hub 2 and the shroud 3 that are concentrically opposed to each other at predetermined intervals in a circumferential direction across the two. It comprises a single blade 4, and its outer peripheral portion serves as a blower outlet 6.

  Further, a resin fixing plate 9 is disposed on the lower side of the hub 2 of the centrifugal impeller 1 so as to be close to and opposed thereto. A steel rotating shaft 8 is fixed to the shaft center portion of the fixed plate 9 by insert molding at the time of resin molding of the fixed plate 9, and the tip protrudes outward from the upstream end of the shroud 3. ing.

  In this embodiment, when the centrifugal impeller 1 is manufactured, the hub 2 and the blades 4 are integrally molded with resin, and the tip portion of the blade 4 of the integrally molded product is separately provided. The above-mentioned shroud 3 molded with resin is abutted and these are bonded and fixed.

"Axial flow impeller 30"
As shown in FIGS. 1 and 2, the axial flow impeller 30 is configured by attaching a plurality of blades 31 around the boss 32 at a predetermined interval, and is a resin molded product. The outer diameter of the axial flow impeller 30, that is, the diameter of the outer peripheral edge of the blade 31 is set to be substantially the same as the inner peripheral diameter of the shroud 3, that is, the inner diameter of the suction port 5. The axial flow impeller 30 is fitted and arranged at the suction port 5 portion of the shroud 3 of the centrifugal impeller 1 and a part of the outer peripheral edge 31a of each blade 31 (specifically, The downstream edge of the outer peripheral edge 31 a is joined and fixed to the upstream end 3 b of the shroud 3 near the suction port 5 and integrated with the centrifugal impeller 1. Furthermore, in this case, the upstream tip 31b of the blade 31 of the axial flow impeller 30 is located downstream of the upstream side wall surface 7a of the bell mouth 7 disposed on the upstream side of the shroud 3 of the centrifugal impeller 1. It is located on the side or flush with it.

  In this way, the centrifugal impeller 1 in which the axial flow impeller 30 is integrally attached to the suction port 5 portion is provided with the rotation provided on the boss 32 of the axial flow impeller 30 on the fixed plate 9 side. By supporting the tip end portion of the shaft 8 on a bearing (not shown) disposed in the boss 32, the shaft 8 is rotatable relative to the fixed plate 9. Further, in a state where the centrifugal impeller 1 is attached to the fixed plate 9 side, the fixed plate 22 is disposed to face the upstream side surface 3 a of the shroud 3. The fixing plate 22 has a resin ring shape and is disposed so as to face the fixing plate 9 with the outer peripheral portion of the centrifugal impeller 1 sandwiched in the axial direction via a plurality of support members 23. ing.

"Motor 10"
The motor 10 is mounted on the upstream side surface 3 a of the shroud 3 of the centrifugal impeller 1, and the rotor 11 described below is disposed on the fixed plate 22 side so as to face the rotor 11. A coil body 12 is provided.

  As shown in FIG. 6, the rotor 11 is a sheet-like member formed by punching a thin steel plate, and extends radially from the outer periphery of the ring-shaped base portion 11 a and the base portion 11 a toward the radially outer side. A plurality of protrusions 11b are provided, and a ring-shaped magnet 15 that substantially matches the shape of the base portion 11a is attached to the upper surface of the base portion 11a. As shown in FIG. 1, the rotor 11 is fixed to a portion near the outer periphery of the upstream side surface 3 a of the shroud 3 in the centrifugal impeller 1 in a stuck state.

  As shown in FIG. 6, the coil body 12 has a sheet-like form configured by printing a plurality of coils 13 on the ring-shaped base 14 at predetermined intervals in the circumferential direction. In addition, the radial position of each coil 13 on the base 14 is set so as to substantially match the radial position of each protrusion 11 b in the rotor 11. As shown in FIG. 1, the coil body 12 is fixed to the lower surface side of the fixing plate 22 in a stuck state. In the attached state, the coils 13 of the coil body 12 are The relative positions of the two are set so that they can face each of the protrusions 11b of the rotor 11 attached to the shroud 3 side of the centrifugal impeller 1 in a close state.

  When the AC voltage is applied to each coil 13 on the coil body 12 side and the polarity of each coil 13 is alternately changed between the N pole and the S pole, the motor 10 is driven by the coil 13 and the magnet 15. A magnetic attractive force and a magnetic repulsive force are alternately applied between the protrusions 11b of the rotor 11 excited to the N pole or the S pole, and the magnetic attractive force and the magnetic repulsive force acting alternately are received. A relative rotational force is generated between the rotor 11 and the coil body 12, whereby the centrifugal impeller 1 and the embodiment axial flow impeller 30 integrated with the centrifugal impeller 1 rotate integrally around the rotating shaft 8. Driven, the air blowing action is performed by the 30 and the centrifugal impeller 1.

  A bell mouth 7 is disposed on the suction port 5 side of the centrifugal impeller 1. In this case, the bell mouth 7 has a shape that increases in diameter toward the upstream side, and the upstream shroud 3. Has a shape that expands toward the downstream side, so that an idle space is created between them. By arranging the coil body 12 together with the fixed plate 22 in the idle space, for example, As compared with the case where the motor 10 is disposed on the hub 2 side, the centrifugal fan can be further downsized in the height direction.

(Effects of centrifugal blower, etc.)
Thus, in the centrifugal blower X1 of this embodiment, the hub 2 in the centrifugal impeller 1 has a disk shape, and the central portion of the hub rises to the suction side like the centrifugal impeller of the conventional centrifugal blower. The resistance to the suction flow is less than in the case of the configuration, and the motor 10 does not exist on the suction side of the axial flow impeller 30, and the motor 10 is different from the conventional centrifugal impeller 1. Due to the absence of resistance to the suction flow and the synergistic effect thereof, the effect of uniforming the wind velocity distribution of the suction flow toward the centrifugal impeller 1 by the axial flow impeller 30 is maximized. Even when the ratio of the inner diameter to the outer diameter of the impeller 1 is relatively large, the suction wind speed is made as uniform as possible, and the necessary rotational speed of the centrifugal impeller for obtaining the required air volume is reduced and the blowing noise is reduced. And Re can be obtained centrifugal blower X1 excellent in energy-saving and quiet operation of only.

  In addition, since the motor 10 has a flat configuration including the rotor 11 and the coil body 12 that face each other in the axial direction of the centrifugal blower X1, the height dimension thereof can be kept low. As a result, in the centrifugal blower X1 configured to include the motor 10, the height dimension can be suppressed to be small and the size thereof can be reduced.

  Further, since the motor 10 has a flat configuration, the hub of the impeller is swelled to the shroud side, that is, the ventilation path side as in a conventional centrifugal blower, and a part of the motor enters here. As in the case of reducing the overall height of the centrifugal blower, the ventilation path is narrowed with the arrangement of the motor, and the suction flow flowing therethrough is not hindered. Therefore, since the required air volume can be ensured without increasing the rotational speed, the operation noise can be reduced, and the diameter of the centrifugal impeller 1 does not need to be excessively enlarged. As a result, it is possible to expect further downsizing of the centrifugal blower X1 in combination with downsizing in the height direction.

  Further, the motor 10 is disposed near the outer periphery of the centrifugal impeller 1 and is largely separated in the radial direction from the rotary shaft 8 located in the central portion of the centrifugal impeller 1 so that both of them can have different structures. . As a result, the influence of the heat on the motor 10 side on the bearing portion of the rotating shaft 8 is suppressed as much as possible, and the deterioration of the lubrication performance due to heat in the bearing portion is less likely to occur. Reliability is improved.

  Furthermore, in this case, the upstream tip 31b of the blade 31 of the axial flow impeller 30 is located downstream of the upstream side wall surface 7a of the bell mouth 7 disposed on the upstream side of the shroud 3 of the centrifugal impeller 1. Since the centrifugal blower X1 is used for an air conditioner and a heat exchanger is disposed on the upstream side of the centrifugal blower X1, the centrifugal blower X1 and the heat are disposed. Interference with the exchanger can be avoided and the capacity of the heat exchanger can be increased, which can contribute to increasing the capacity of the air conditioner.

II: Second Embodiment FIG. 3 shows a centrifugal blower X2 according to a second embodiment of the present invention. The centrifugal blower X2 has the same basic configuration as the centrifugal blower X1 according to the first embodiment, and is different from this in the arrangement structure of the motor 10. Therefore, here, this difference will be mainly described, and other structures and functions and effects will be given the same reference numerals corresponding to the members in FIGS. 1 and 2 and the members in FIG. The description here is omitted by using the corresponding description in the first embodiment.

  In this embodiment, of the rotor 11 and the coil body 12 constituting the motor 10, the rotor 11 is attached to the outer peripheral portion of the downstream side surface 2a of the hub 2 in the centrifugal impeller 1, while the coil body 12 is attached to the outer peripheral portion of the upper surface 9a of the fixed plate 9 so that each coil 13 thereof faces each projection 11b of the rotor 11 in a close proximity.

  In the centrifugal blower X2 configured as described above, the following specific effects can be obtained instead of or in addition to the effects of the centrifugal blower X1 according to the first embodiment.

  That is, in the centrifugal blower X2 of this embodiment, the hub 2 of the centrifugal impeller 1 in the centrifugal blower X1 has a disk shape, and the central portion of the hub is on the suction side like the centrifugal impeller in the conventional centrifugal blower. The resistance to the suction flow is less than in the case of the configuration protruding to the upper side, and the motor 10 does not exist on the suction side of the axial flow impeller 30, and the motor 10 does not exist like the conventional centrifugal impeller 1. Due to the absence of resistance to the suction flow by the motor 10 and their synergistic effect, the effect of uniforming the wind speed distribution of the suction flow toward the centrifugal impeller 1 by the axial flow impeller 30 is exhibited to the maximum. Even if the ratio of the inner diameter to the outer diameter of the centrifugal impeller 1 is relatively large, the suction air speed becomes as uniform as possible, and the required rotational speed of the centrifugal impeller to obtain the required air volume is reduced. Wind noise is reduced, it is possible to obtain a centrifugal blower X2 excellent in energy-saving and quiet operation of correspondingly.

  In addition, since the motor 10 has a flat configuration including the rotor 11 and the coil body 12 that face each other in the axial direction of the centrifugal blower X2, the height dimension thereof can be kept low. As a result, in the centrifugal blower X2 configured to include the motor 10, the height dimension can be suppressed to be small and the size thereof can be reduced.

  Further, since the motor 10 has a flat configuration, the hub of the impeller is swelled to the shroud side, that is, the ventilation path side as in a conventional centrifugal blower, and a part of the motor enters here. As in the case of reducing the overall height of the centrifugal blower, the ventilation path is narrowed with the arrangement of the motor, and the suction flow flowing therethrough is not hindered. Therefore, since the required air volume can be ensured without increasing the rotational speed, the operation noise can be reduced, and the diameter of the centrifugal impeller 1 does not need to be excessively enlarged. As a result, it is possible to expect further downsizing of the centrifugal blower X2 in combination with downsizing in the height direction.

  Further, the motor 10 is disposed near the outer periphery of the centrifugal impeller 1 and is largely separated in the radial direction from the rotary shaft 8 located in the central portion of the centrifugal impeller 1 so that both of them can have different structures. . As a result, the influence of the heat on the motor 10 side on the bearing portion of the rotating shaft 8 is suppressed as much as possible, and the deterioration of the lubrication performance due to heat in the bearing portion is less likely to occur. Reliability is improved.

  Furthermore, in this case, the upstream tip 31b of the blade 31 of the axial flow impeller 30 is located downstream of the upstream side wall surface 7a of the bell mouth 7 disposed on the upstream side of the shroud 3 of the centrifugal impeller 1. Since the centrifugal blower X2 is used for an air conditioner and a heat exchanger is disposed on the upstream side of the centrifugal blower X2, the centrifugal blower X2 and the heat Interference with the exchanger can be avoided and the capacity of the heat exchanger can be increased, which can contribute to increasing the capacity of the air conditioner.

III: Third Embodiment FIG. 4 shows a centrifugal blower X3 according to a third embodiment of the present invention. The centrifugal blower X3 has the same basic configuration as the centrifugal blower X1 according to the first embodiment, and is different from the centrifugal blower X3 in the configuration of the motor 10. Therefore, here, this difference will be mainly described, and the other structures and operational effects will be assigned the same reference numerals corresponding to the respective members in FIG. 1 and the respective members in FIG. The description here is omitted by using the corresponding description in the embodiment.

  In the centrifugal blower X3 of this embodiment, the shroud 3 is not a resin-integrated molded product as in the centrifugal blower X1 of the first embodiment, but a part of the shroud 3 is configured by the rotor 11. It is.

  That is, as shown in FIG. 7, the rotor 11 has a basic shape provided with a ring-shaped base portion 11a and a plurality of protrusions 11b extending radially outward from the outer periphery of the base portion 11a. This point is the same as in the case of the first embodiment. The difference from this is that the magnet 15 is not retrofitted as in the first embodiment, but the rotor 11 itself is made of a magnet material, which is a single structure. .

  The rotor 11 thus configured is not attached afterwards to the shroud 3 formed separately from the rotor 11 as in the first embodiment, but as shown in FIG. When the resin shroud 3 is formed, insert molding is performed integrally with the shroud 3 so that the rotor 11 is used as a part of the shroud 3.

  The configuration on the coil body 12 side and the arrangement structure thereof, and the support structure for the centrifugal impeller 1 on the fixed plate 9 side are the same as those in the first embodiment.

  In the centrifugal blower X3 configured as described above, the following specific effects can be obtained instead of or in addition to the effects of the centrifugal blower X1 according to the first embodiment.

  That is, in the centrifugal blower X3 of this embodiment, the hub 2 of the centrifugal impeller 1 has a disk shape, and the central portion of the hub is raised to the suction side like the centrifugal impeller in the conventional centrifugal blower. Compared to the case of the configuration, the resistance to the suction flow is small, and the motor 10 does not exist on the suction side of the axial impeller 30, and the suction flow by the motor 10 is different from the conventional centrifugal impeller 1. As a result of the synergistic effect, the effect of uniforming the wind speed distribution of the suction flow toward the centrifugal impeller 1 by the axial flow impeller 30 is maximized. As a result, for example, the centrifugal impeller Even when the ratio of the inner diameter to the outer diameter of 1 is relatively large, the suction wind speed is made as uniform as possible, the required rotational speed of the centrifugal impeller to obtain the required air volume is reduced, and the blowing noise is reduced. That's it It is possible to obtain a centrifugal blower X3 excellent in energy saving property and quietness drivability.

  In addition, since the motor 10 has a flat configuration including the rotor 11 and the coil body 12 that face each other in the axial direction of the centrifugal blower X3, the height dimension thereof can be kept low. As a result, in the centrifugal blower X3 configured to include the motor 10, the height dimension can be suppressed to be small and the size thereof can be reduced.

  Further, since the motor 10 has a flat configuration, the hub of the impeller is swelled to the shroud side, that is, the ventilation path side as in a conventional centrifugal blower, and a part of the motor enters here. As in the case of reducing the overall height of the centrifugal blower, the ventilation path is narrowed with the arrangement of the motor, and the suction flow flowing therethrough is not hindered. Therefore, since the required air volume can be ensured without increasing the rotational speed, the operation noise can be reduced, and the diameter of the centrifugal impeller 1 does not need to be excessively enlarged, so that the centrifugal blower X3 is enlarged in the radial direction. As a result, it is possible to expect further downsizing of the centrifugal blower X3 in combination with downsizing in the height direction.

  Further, in this embodiment, the rotor 11 is integrally formed with a magnet material, and insert molding is integrally performed with the shroud 3 at the time of resin molding of the shroud 3, so that the resin molding operation of the shroud 3 and the rotor 11 with respect to these are molded. The attachment work can be performed at the same time, and the cost reduction of the centrifugal blower X3 is promoted accordingly.

  In this embodiment, as described above, the rotor 11 is integrally formed with a magnet material, and insert molding is integrally performed with the rotor 11 during resin molding. For example, by using a resin mixed with a magnet material and a normal resin not mixed with this, and by two-color molding of the resin, the portion corresponding to the rotor 11 is made of the resin mixed with the magnet material and The shroud 3 other than the above can also be molded by a normal resin. By doing in this way, shaping | molding of the said shroud 3 and shaping | molding of the said rotor 11 can be completed in 1 process, and cost reduction of the centrifugal blower X3 can be achieved by reduction of an operation man-hour.

  Furthermore, in this case, the upstream tip 31b of the blade 31 of the axial flow impeller 30 is located downstream of the upstream side wall surface 7a of the bell mouth 7 disposed on the upstream side of the shroud 3 of the centrifugal impeller 1. Since the centrifugal blower X3 is used for an air conditioner and a heat exchanger is disposed on the upstream side of the centrifugal blower X3, the centrifugal blower X3 and the heat Interference with the exchanger can be avoided and the capacity of the heat exchanger can be increased, which can contribute to increasing the capacity of the air conditioner.

IV: Fourth Embodiment FIG. 5 shows a centrifugal blower X4 according to a fourth embodiment of the present invention. The centrifugal blower X4 has the same basic configuration as the centrifugal blower X2 according to the second embodiment, and is different from the centrifugal impeller 1 and the motor 10 in this configuration. Therefore, here, these differences will be mainly described, and the other structures and operational effects will be assigned the same reference numerals corresponding to the respective members in FIG. 3 and the respective members in FIG. The corresponding description in the second embodiment (that is, the first embodiment) is incorporated, and the description here is omitted.

  In the centrifugal blower X4 of this embodiment, the hub 2 is not a resin-integrated molded product like the centrifugal blower X2 of the second embodiment, but a part of the hub 2 is configured by the rotor 11. It is.

  That is, as shown in FIG. 7, the rotor 11 has a basic shape provided with a ring-shaped base portion 11a and a plurality of protrusions 11b extending radially outward from the outer periphery of the base portion 11a. This point is the same as in the case of the second embodiment. The difference from this is that the magnet 15 is not retrofitted as in the second embodiment, but the rotor 11 itself is made of a magnet material, which is a single structure. .

  The rotor 11 configured as described above is not attached to the hub 2 side formed separately from the hub 2 that is molded separately from the second embodiment, but instead of the hub 2 made of resin. Insert molding is performed integrally with the rotor 11 at the time of molding, and the rotor 11 is used as a part of the hub 2.

  The structure on the coil body 12 side and the arrangement structure thereof, and the support structure for the centrifugal impeller 1 on the fixed plate 9 side are the same as in the case of the second embodiment.

  In the centrifugal blower X4 configured as described above, the following specific effects can be obtained instead of or in addition to the effects of the centrifugal blower X2 according to the second embodiment.

  That is, in the centrifugal blower X4 of this embodiment, the hub 2 of the centrifugal impeller 1 has a disk shape, and the central portion of the hub is raised to the suction side like the centrifugal impeller in the conventional centrifugal blower. Compared to the case of the configuration, the resistance to the suction flow is small, and the motor 10 does not exist on the suction side of the axial impeller 30, and the suction flow by the motor 10 is different from the conventional centrifugal impeller 1. As a result of the synergistic effect, the effect of uniforming the wind speed distribution of the suction flow toward the centrifugal impeller 1 by the axial flow impeller 30 is maximized. As a result, for example, the centrifugal impeller Even when the ratio of the inner diameter to the outer diameter of 1 is relatively large, the suction wind speed is made as uniform as possible, the required rotational speed of the centrifugal impeller to obtain the required air volume is reduced, and the blowing noise is reduced. That's it It is possible to obtain a centrifugal blower X4 excellent in energy saving property and quietness drivability.

  In addition, since the motor 10 has a flat configuration including the rotor 11 and the coil body 12 that face each other in the axial direction of the centrifugal blower X4, the height dimension thereof is kept low. As a result, in the centrifugal blower X4 configured to include the motor 10, the height dimension can be suppressed to be small and the size thereof can be reduced.

  Further, since the motor 10 has a flat configuration, the hub of the impeller is swelled to the shroud side, that is, the ventilation path side as in a conventional centrifugal blower, and a part of the motor enters here. As in the case of reducing the overall height of the centrifugal blower, the ventilation path is narrowed with the arrangement of the motor, and the suction flow flowing therethrough is not hindered. Therefore, since the required air volume can be ensured without increasing the rotational speed, the operation noise can be reduced, and the diameter of the centrifugal impeller 1 does not need to be excessively enlarged. As a result, it is possible to expect further downsizing of the centrifugal blower X4 in combination with downsizing in the height direction.

  In this embodiment, as described above, the rotor 11 is integrally formed of a magnet material, and insert molding is integrally performed with the hub 2 during resin molding. In other embodiments, however, For example, by using a resin mixed with a magnet material and a normal resin not mixed with this, and by two-color molding of the resin, the portion corresponding to the rotor 11 is made of the resin mixed with the magnet material and The parts of the hub 2 other than the above can also be molded with ordinary resin. By doing in this way, shaping | molding of the said hub 2 and shaping | molding of the said rotor 11 can be completed in one process, and the cost reduction of a centrifugal blower can be achieved by reduction of an operation man-hour.

  Furthermore, in this case, the upstream tip 31b of the blade 31 of the axial flow impeller 30 is located downstream of the upstream side wall surface 7a of the bell mouth 7 disposed on the upstream side of the shroud 3 of the centrifugal impeller 1. Since the centrifugal blower X4 is used in an air conditioner and a heat exchanger is disposed on the upstream side of the centrifugal blower X4, the centrifugal blower X4 and the heat Interference with the exchanger can be avoided and the capacity of the heat exchanger can be increased, which can contribute to increasing the capacity of the air conditioner.

V: Fifth Embodiment FIG. 8 shows an air conditioner Z1 according to a fifth embodiment of the present invention. This air conditioner Z1 is configured by using a centrifugal blower X5 having the same configuration as the centrifugal blower X2 according to the second embodiment, and is particularly provided at the suction port 5 portion of the centrifugal impeller 1. This configuration is suitable when there is a relatively large space on the upper side of the axial flow impeller 30. That is, in the air conditioner Z1, a thin heat exchange is arranged on the upstream side of the bell mouth 7 which is disposed on the upstream side of the shroud 3 of the centrifugal impeller 1 and surrounds the axial impeller 30 together with the shroud 3. The heat exchanger 21 is arranged so that its heat transfer surface direction is orthogonal to the axial direction of the centrifugal blower X5.

  Thus, in the structure which arrange | positions the said heat exchanger 21 in the upstream of the said bellmouth 7, from the space margin, the said heat exchanger 21 is expanded in the plane direction, and the heat-transfer area is taken larger. As a result, it is possible to provide a high-performance air conditioner Z1 that achieves both compactness in the height direction and high heat exchange performance.

  Further, since the axial flow impeller 30 is provided inside the suction port 5 of the centrifugal impeller 1, the wind velocity distribution of the suction flow toward the centrifugal impeller 1 by the axial flow impeller 30 is uniform. Even if the ratio of the inner diameter to the outer diameter of the centrifugal impeller 1 is relatively large, the suction air speed becomes as uniform as possible, and as a result, the heat exchanger 21 The air flow A flows in as uniformly as possible from the entire area, the heat exchange action in the heat exchanger 21 is further promoted, and the heat transfer surface of the axial heat exchanger 21 is As a synergistic effect with being arranged so as to be orthogonal to the axial direction, further improvement in the heat exchange capability of the air conditioner Z1 can be expected.

  Further, in the centrifugal blower X5 in which the centrifugal impeller 1 and the axial flow impeller 30 are integrated, the hub 2 has a disk shape and has little resistance to the suction flow in the central portion of the hub 2, and the above Since the motor 10 serving as a ventilation resistance does not exist on the suction side of the axial impeller 30, the effect of uniformizing the wind speed distribution of the suction flow toward the centrifugal impeller 1 by the axial flow impeller 30 is maximized. As a result, even if the ratio of the inner diameter to the outer diameter of the centrifugal impeller 1 is relatively large, the centrifugal impeller 1 for obtaining the required air volume is made as uniform as possible. Therefore, the air conditioner Z1 excellent in energy saving and quiet operation can be obtained.

VI: Sixth Embodiment FIG. 9 shows an air conditioner Z2 according to a sixth embodiment of the present invention. This air conditioner Z2 is configured using a centrifugal blower X6 obtained by partially changing the structure of the centrifugal blower X1 according to the first embodiment, and is required to have higher heat exchange performance. In this case, the air conditioner is suitable.

  That is, the air conditioner Z2 includes a centrifugal blower X6 using the centrifugal impeller 1 in which the hub 2 is removed from the centrifugal impeller 1 used in the centrifugal blower X1 according to the first embodiment. On the other hand, for example, the centrifugal impeller 1 is disposed to face the casing wall 16 so that the casing wall 16 of the air conditioner functions as the hub 2. In the space surrounded by the shroud 3 and the casing wall 16 of the centrifugal impeller 1, the heat exchanger 21 is disposed across from the inside to the outside of the blade row of the centrifugal impeller 1. .

  In the air conditioner Z2 configured in this way, the heat exchanger 21 is arranged from the inner side to the outer side of the blade row of the centrifugal impeller 1 so that the heat transfer area of the heat exchanger 21 is increased. And the heat exchanger 21 enters the inside of the centrifugal impeller 1 so that an air flow flows as uniformly as possible throughout the heat exchanger 21. A high-performance air conditioner Z2 that achieves both compactness in direction and high heat exchange performance can be obtained.

  Further, in the centrifugal blower X6 in which the centrifugal impeller 1 and the axial flow impeller 30 are integrated, the hub 2 has a disk shape and has a low resistance to the suction flow at the central portion of the hub 2, and the above Since the motor 10 serving as a ventilation resistance does not exist on the suction side of the axial impeller 30, the effect of uniformizing the wind speed distribution of the suction flow toward the centrifugal impeller 1 by the axial flow impeller 30 is maximized. As a result, even if the ratio of the inner diameter to the outer diameter of the centrifugal impeller 1 is relatively large, the centrifugal impeller 1 for obtaining the required air volume is made as uniform as possible. Therefore, the air conditioner Z2 excellent in energy saving and quiet operation can be obtained.

  In this embodiment, the heat exchanger 21 is arranged across from the inner side to the outer side of the blade row of the centrifugal impeller 1, but in other embodiments of the present invention, A configuration in which the heat exchanger 21 is provided only inside the blade row of the centrifugal impeller 1 can also be adopted, and the above-described operation and effect can be obtained even in such a configuration.

It is sectional drawing of the centrifugal blower which concerns on 1st Embodiment of this invention. It is an II-II arrow line view of FIG. It is sectional drawing of the centrifugal blower which concerns on 2nd Embodiment of this invention. It is sectional drawing of the centrifugal blower which concerns on 3rd Embodiment of this invention. It is sectional drawing of the centrifugal blower which concerns on 4th Embodiment of this invention. It is a perspective view of the rotor and coil body with which the centrifugal blower of this invention was equipped. It is a perspective view which shows the state which shape | molded the rotor integrally with the shroud. It is sectional drawing of the air conditioner provided with the centrifugal blower which concerns on 5th Embodiment of this invention. It is sectional drawing of the air conditioner provided with the centrifugal blower which concerns on 6th Embodiment of this invention. It is sectional drawing which shows the 1st structural example of the conventional centrifugal blower. It is sectional drawing which shows the 2nd structural example of the conventional centrifugal blower. It is sectional drawing which shows the 3rd structural example of the conventional centrifugal blower. It is sectional drawing which shows the 4th structural example of the conventional centrifugal blower.

Explanation of symbols

1 ·· Impeller 2 ·· Hub 3 ·· Shroud 4 ·· Vane 5 ·· Suction port 6 ·· Air outlet 7 ·· Bellmouth 8 ·· Rotating shaft 9 ·· Fixing plate 10 ·· Motor 11 ·· Rotor 12 .. Coil body 13 .. Coil 14 .. Base 15 .. Magnet 16 .. Casing wall 17 .. Fixing plate 20 .. Rod-shaped member 21 .. Heat exchanger 22 .. Fixing plate 23.・ Axial impeller 31 ・ ・ Wings 32 ・ ・ Boss A ・ ・ Air flow

Claims (11)

The above-mentioned shroud of the centrifugal impeller (1) in which a plurality of blades (4) are disposed between a disc-shaped hub (2) and a ring-shaped shroud (3) which are arranged opposite to each other on the same axis. On the inner peripheral side of (3), an axial-flow impeller (30) provided with a plurality of blades (31) is arranged substantially coaxially and integrated with them,
The centrifugal impeller (1) is provided with a ring-shaped base (11a) and a plurality of protrusions (11b) extending radially from the base (11a) and ring-shaped on the base (11a). A steel plate rotor (11) with a magnet (15) attached thereto is attached,
A coil body (12) in which a plurality of coils (13) are printed on a base (14) so as to correspond to each of the protrusions (11b) of the rotor (11) is connected to the coils (13). Are arranged so as to face each of the protrusions (11b) of the rotor (11),
A centrifugal blower characterized in that the rotor (11) and the coil body (12) constitute a motor (10) that integrally rotates the centrifugal impeller (1) and the axial flow impeller (30). . In claim 1,
Centrifugal blower characterized in that the rotor (11) is mounted on the upstream side surface (3a) of the shroud (3). In claim 1,
Centrifugal blower characterized in that the rotor (11) is mounted on the downstream side surface (2a) of the hub (2). The above-mentioned shroud of the centrifugal impeller (1) in which a plurality of blades (4) are disposed between a disc-shaped hub (2) and a ring-shaped shroud (3) which are arranged opposite to each other on the same axis. On the inner peripheral side of (3), an axial-flow impeller (30) provided with a plurality of blades (31) is arranged substantially coaxially and integrated with them,
A part of the hub (2) of the centrifugal impeller (1) is provided with a ring-shaped base (11a) and a plurality of protrusions (11b) extending radially from the base (11a). And a rotor (11) made of magnet material,
A coil body (12) in which a plurality of coils (13) are printed on a base (14) so as to correspond to each of the protrusions (11b) of the rotor (11) is connected to the coils (13). Are arranged so as to face each of the protrusions (11b) of the rotor (11),
A centrifugal blower characterized in that the rotor (11) and the coil body (12) constitute a motor (10) that integrally rotates the centrifugal impeller (1) and the axial flow impeller (30). . The above-mentioned shroud of the centrifugal impeller (1) in which a plurality of blades (4) are disposed between a disc-shaped hub (2) and a ring-shaped shroud (3) which are arranged opposite to each other on the same axis. On the inner peripheral side of (3), an axial-flow impeller (30) provided with a plurality of blades (31) is arranged substantially coaxially and integrated with them,
A part of the shroud (3) of the centrifugal impeller (1) includes a ring-shaped base (11a) and a plurality of protrusions (11b) extending radially from the base (11a). And a rotor (11) made of magnet material,
A coil body (12) in which a plurality of coils (13) are printed on a base (15) so as to correspond to each of the protrusions (11b) of the rotor (11) is connected to the coils (13). Are arranged so as to face each of the protrusions (11b) of the rotor (11),
A centrifugal blower characterized in that the rotor (11) and the coil body (12) constitute a motor (10) that integrally rotates the centrifugal impeller (1) and the axial flow impeller (30). . In claim 4 or 5,
The centrifugal blower characterized in that the rotor (11) is integrally formed of a magnet material and is insert-molded integrally with the hub (2) or the shroud (3) during resin molding. In claim 4 or 5,
Centrifugation characterized in that the rotor (11) is molded in two colors integrally with the hub (2) or the shroud (3) using resin mixed with magnet material. Blower. In claim 1, 2, 3, 4, 5, 6 or 7,
The upstream tip (31b) of the blade (31) of the axial impeller (30) is upstream of the bell mouth (7) disposed on the upstream side of the shroud (3) of the centrifugal impeller (1). A centrifugal blower characterized in that it is positioned downstream of or flush with the side wall surface (7a). An air conditioner configured by adding a heat exchanger (21) to the centrifugal blower according to claim 1, 2, 3, 4, 5, 6, 7 or 8,
The air conditioner characterized in that the heat exchanger (21) is arranged radially inside and radially outside a blade row in the impeller (1). An air conditioner configured by adding a heat exchanger (21) to the centrifugal blower according to claim 1, 2, 3, 4, 5, 6, 7 or 8,
The air conditioner characterized in that the heat exchanger (21) is arranged radially inside the blade row in the impeller (1). An air conditioner configured by adding a heat exchanger (21) to the centrifugal blower according to claim 1, 2, 3, 4, 5, 6, 7 or 8,
The heat exchanger (21) is arranged on the upstream side of the intake air in the impeller (1) so that at least one surface thereof is substantially perpendicular to the rotary shaft (8) of the centrifugal blower. An air conditioner characterized by that.

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