AU2005260828A1 - Centrifugal blower and air conditioner with centrifugal blower - Google Patents

Description

DECLARATION I, Akira Yamada, a citizen of Japan, residing at Nagara, Gifu-shi, Gifu-ken, Japan, hereby declare that I am the translator of the attached document and certify that, to the best of my knowledge and belief, it is a true and accurate translation of International Patent Application No. PCT/JP2005/013039, filed on July 14, 2005. I further declare that all statements made herein of my own knowledge are true and that all statements made on information and belief are believed to be true, kira Yamada Translator Dated this 22nd date of December, 2006 DESCRIPTION CENTRIFUGAL BLOWER AND AIR CONDITIONER WITH CENTRIFUGAL BLOWER 5 TECHNICAL FIELD The present invention relates to a centrifugal blower and an air conditioner having a centrifugal blower. 10 BACKGROUND ART A typical well known centrifugal blower includes an impeller having a hub connected to a rotation shaft of a 15 motor, a shroud arranged to face the peripheral portion thereof in a state spaced from the peripheral portion by a predetermined distance, and a plurality of vanes arranged at predetermined intervals in the circumferential direction between the shroud and the peripheral portion of the hub 20 (see Patent Publication 1). A centrifugal blower having no shroud includes an impeller having a hub with a central portion to which a rotation shaft of a motor is connected, a plurality of vanes 25 arranged on the peripheral portion of the hub at predetermined intervals in the circumferential direction, and a bellmouth having an air intake port located at an air intake side of the impeller (see Patent Publication 2). 30 Patent Publication 1: Japanese Laid-Open Patent Publication No. 11-101194 Patent Publication 2: Japanese Laid-Open Patent Publication No. 10-185238 1 The centrifugal blower described in Patent Publication 1 is often used as a sweep back vane type centrifugal blower (i.e., a turbo fan) that has a complicated structure in 5 which the outer diameter end of a vane end is located rearward from the inner diameter end of the vane with respect to the rotational direction of the impeller. Further, a large number of vanes are arranged between the shroud and the peripheral portion of the hub. Thus, in order to produce 10 such an impeller, the hub and vanes must be integrally molded and a shroud, which is produced separately, must be joined with the molded body. This is problematic from the aspects of mass production and cost. 15 The centrifugal blower described in Patent Publication 2 is often used as a sweep forward vane type centrifugal blower (i.e., a sirocco fan) that has a simple structure in which the outer diameter end of a vane is located frontward from the inner diameter end of the vane with respect to the 20 rotational direction of the impeller. However, the aerodynamic performance and operational noise characteristics will deteriorate unless a spiral casing is used. This is problematic from the aspects of mass production and cost. 25 DISCLOSURE OF THE INVENTION Accordingly, it is an object of the present invention to provide a quiet and highly efficient centrifugal blower 30 having superior mass productivity and enabling cost reduction and an air conditioner having such a centrifugal blower. 2 A first aspect of the present invention for solving the above problems is a centrifugal blower including an impeller 1 having a hub 2 with a central portion connected to a rotation shaft 4a of a motor 4 and a plurality of vanes 5 3 arranged on a peripheral portion of the hub 2 at predetermined intervals in a circumferential direction. The vanes are provided with front rims 3a inclined toward the front in a rotational direction. A bellmouth 5 is provided with an air intake port 6 arranged at an air intake side of 10 the impeller. The centrifugal blower is formed so that a circulating flow f 2 is generated to flow out from an outlet side of the impeller 1, flow back into the impeller 1, and pass through the rear side of the air intake port 6 of the bellmouth 5. 15 This structure makes it possible for an impeller 1 having sweep back type vanes represented, for example, by a turbo fan to form a circulating flow f 2 which flows out from the outlet side of the impeller 1 and is drawn back into the 20 impeller 1, passing through the rear side of the air intake port 6 of the bellmouth 5. As a result, main air flow fi passing across the vanes 3 is drawn to the distal end side of the vanes 3 by the 25 circulating flow f 2 , which improves the air speed distribution in the exit portions of the vanes 3, enabling improvement of aerodynamic performance and reduction of operational noise. 30 Moreover, since no shroud is required, the impeller 1 can be molded integrally, which makes it possible to simplify the structure and reduce the cost, resulting in improvement in mass productivity. 3 A second aspect of the present invention for solving the above problems is a centrifugal blower including an impeller 1 having a hub 2 with a central portion connected 5 to a rotation shaft 4a of a motor 4 and a plurality of vanes 3 arranged on a peripheral portion of the hub 2 at predetermined intervals in a circumferential direction. The vanes provided with front rims 3a are neither inclined toward the front nor the rear in a rotational direction. A 10 bellmouth 5 is provided with an air intake port 6 arranged at an air intake side of the impeller. The centrifugal blower is formed so that a circulating flow f 2 is generated to flow out from an outlet side of the impeller 1, flow back into the impeller 1, and pass through the rear side of the 15 air intake port 6 of the bellmouth 5. This structure makes it possible for an impeller 1 having sweep back type vanes represented, for example, by a radial plate fan to form a circulating flow f 2 which flows 20 out from the outlet side of the impeller 1 and is drawn back into the impeller 1, passing through the rear side of the air intake port 6 of the bellmouth 5. As a result, main air flow fi passing across the vanes 25 3 is drawn to the distal end side of the vanes 3 by the circulating flow f 2 , which improves the air speed distribution in the exit portions of the vanes 3, enabling improvement of aerodynamic performance and reduction of operational noise. 30 Moreover, since no shroud is required, the impeller 1 can be molded integrally, which makes it possible to simplify the structure and reduce the cost, resulting in 4 improvement in mass productivity. It is preferred that the vanes 3 in the impeller 1 are entirely inclined in the rotational direction. 5 In this structure, the vanes 3 function to draw in the circulating flow f 2 generated by the ring body 20. This generates a strong circulating flow f 2 . 10 Even if the inner diameter Do of the air intake port 6 of the bellmouth 5 is enlarged, the strong circulating flow f 2 will smoothly circulate near the ring body 20 without deeply entering the inner side of the vanes 3. This obtains satisfactory fan performance. 15 Further, the vanes 3 in the impeller 1 may entirely be inclined opposite the rotational direction. In this structure, the vanes 3 function in the 20 direction that makes it difficult to draw in the circulating flow f 2 generated by the ring body 20. Even if the inner diameter Do of the air intake port 6 of the bellmouth 5 is reduced, the circulating flow f 2 Will 25 smoothly circulate near the ring body 20 without deeply entering the inner side of the vanes 3. This obtains satisfactory fan performance. Further, the vanes 3 in the impeller 1 may include 30 vane tips inclined in the rotational direction. In this structure, the vanes 3 function to draw in the circulating flow f 2 generated by the ring body 20. This 5 generates a strong circulating flow f 2 . Even if the inner diameter Do of the air intake port 6 of the bellmouth 5 is enlarged, the strong circulating flow 5 f 2 will smoothly circulate near the ring body 20 without deeply entering the inner side of the vanes 3. This obtains satisfactory fan performance. Further, the vanes 3 in the impeller 1 may include 10 vane tips inclined opposite the rotational direction. In this structure, the vanes 3 function in the direction making it difficult to draw in the circulating flow f 2 generated by the ring body 20. 15 Even if the inner diameter Do of the air intake port 6 of the bellmouth 5 is reduced, the circulating flow f 2 Will smoothly circulate near the ring body 20 without deeply entering the inner side of the vanes 3. This obtains 20 satisfactory fan performance. Further, when an inner diameter of the air intake port 6 of the bellmouth 5 is represented by Do, an inner diameter of the vanes 3 in the impellers 1 is represented by D 1 , and 25 an outer diameter of the vanes 3 is represented by D 2 , 0<(Do Di)/(D 2

-D

1 )<0.6 may be satisfied. In this structure, the minimum specific noise Ks may be lowered, as shown in Fig. 4, when the number of the vanes 30 3 is small (for example, 5 to 15). This further improves aerodynamic performance and reduces operational noise. If (Do-Di)/(D 2 -Dj) 0.6 is satisfied when the number of 6 vanes 3 is small, reversed flow f' generated at the front rims of the vanes 3 will become strong, as shown in Fig. 5(B), and the circulating flow f 2 at the rear rims of the vanes 3 will become weak. This inhibits the improvement of 5 aerodynamic performance. If 0 (Do-Di)/(D 2 -Di) is satisfied when the number of the vanes 3 is small, the front rims of the vanes 3 will not function effectively, as shown in Fig. 5(A). This inhibits 10 the improvement of aerodynamic performance. When an inner diameter of the air intake port 6 of the bellmouth 5 is represented by Do, the inner diameter of the vanes 3 in the impeller 1 is represented by D 1 , and the outer 15 diameter of the vanes 3 is represented by D 2 , -0.3<(Do Di)/(D 2

-D

1 )<0.3 may be satisfied. In this structure, the minimum specific noise Ks may be lowered, as shown in Fig. 14, when the number of the 20 vanes 3 is large (for example, 30 to 50). This further improves the aerodynamic performance and reduces operational noise. If (Do-Dj)/(D 2 -Di) 0.3 is satisfied when the number of 25 vanes 3 is large, a reversed flow f' generated at the front rims of the vanes 3 will become strong, as shown in Fig. 5(B), and the circulating flow f2 at the rear rims of the vanes 3 will become weak. This inhibits the improvement of the aerodynamic performance. 30 If -3 (Do-D 1

)/(D

2 -Di) is satisfied when the number of the vanes 3 is large, the front rims of the vanes 3 will not function effectively. This inhibits the improvement of the 7 aerodynamic performance. A ring body 9, 20 having a predetermined width in a centrifugal direction may be attached to axial distal ends 5 of the vanes 3 in the impeller 1. In this structure, the ring body 9, 20 rotating together with the impeller 1 functions as a rotary disk, and the viscosity action of the rotary disk induces a rotational direction flow in the outlet flow from the vanes 3. This rectifies the discharge 10 flow and circulating flow and improves the fan performance and reduces noise. When a width in the centrifugal direction of the ring body 20 is represented by H, and the outer diameter of the 15 vanes 3 of the impeller 1 is represented by D 2 , 0.05<ki=H/D 2 <0.225 may be satisfied. In this structure, as shown in Fig. 9, the minimum specific noise Ks is lowered. This further improves the aerodynamic performance and reduces operational noise. 20 It is further desirable that 0.lki=H/D 2 0.15 be satisfied to reduce noise. If ki=H/D 2 0.05 is satisfied, the effect will be 25 reduced. If ki=H/D 2 0.225 is satisfied, the formation of circulating flow will be affected adversely to weaken the circulating flow at the rear distal portions of the vanes 3. This inhibits improvement of the aerodynamic performance. 30 A diagonal diffuser 23 may be arranged at the outlet side of the impeller 1 to guide air that is blown out of the impeller 1 diagonally rearward. In this structure, the dynamic pressure in the air flow blown out from the impeller 8 1 efficiently returns to the static pressure. This greatly contributes to improvement of the performance (that is, high efficiency and low noise). 5 Further, a diagonal centrifugal diffuser 23 may be arranged at the outlet side of the impeller 1 to guide air blown out of the impeller 1 in a centrifugal direction from a diagonal rear side. In this structure, the air flow blown out from the impeller 1 efficiently returns to static 10 pressure from dynamic pressure. This equalizes the air speed distribution and greatly contributes to improvement of the performance (that is, high efficiency and low noise). A circulation space S may be formed at a peripheral 15 side of the air intake port 6 of the bellmouth 5 to allow passage of the circulating flow f 2 . In this structure, the generation of the circulating flow f 2 is facilitated and ensured. 20 When an exit side height of the vanes 3 in the impeller 1 is represented by B and an outer diameter of the vanes 3 is represented by D 2 , B/D 2 0.113 is satisfied. This structure eliminates the problem of fluctuation in the air flow line fi at the exit side of the impeller 1 and obtains 25 stable performance. If B/D 2 <0.113 is satisfied, the air flow line fi at the exit side of the impeller 1 will fluctuate more as the air flow increases and the circulating flow f2 will eventually 30 obstruct the flow passages between the vane 3. This would result in a sharp drop of the performance. The hub 2 of the impeller 1 has an outer diameter D 3 9 that is smaller than the outer diameter D 2 of the vanes 3. In this structure, an opening 22 is formed in a peripheral portion at the hub side of the vanes 3. When the diagonal diffuser 23 or the diagonal centrifugal diffuser 23 is 5 provided, the discharge resistance of the air flow blown out from the vanes 3 is reduced. When the exit side height of the vanes 3 of the impeller 1 is represented by B and the outer diameter of the 10 vanes 3 is represented by D 2 , B/D 2 0.08 is satisfied. This structure eliminates the problem of fluctuation in the air flow line fi at the exit side of the impeller 1 even if the exit side height B of the vane 3 of the impeller 1 is decreased. Thus, stable performance is obtained. 15 If B/D 2 <0.08 is satisfied, the air flow line fi at the exit side of the impeller 1 will fluctuate greatly and the circulating flow f 2 will eventually obstruct the flow passages between the vanes 3. Thus causes a sharp drop in 20 the performance. It is preferred that the number of the vanes 3 in the impeller 1 be 5 to 15. In this case, in the present invention, as shown in Fig. 4, the minimum specific noise Ks 25 may be lowered even when the number of vanes 3 is small. This effectively improves the aerodynamic performance and reduces operational noise. It is preferred that the number of the vanes 3 in the 30 impeller 1 be 20 to 50. As shown in Figs. 14 and 43, for example, when the number of the vanes 3 is large, the maximum static pressure efficiency ratio may especially be increased, and the minimum specific noise may be lowered. 10 This further effectively improves the aerodynamic performance and reduces operational noise. It is preferred that the number of the vanes 3 in the 5 impeller 1 be 30 to 72. As shown in Figs. 14 and 50, when the number of the vanes 3 is large and about 30 to 72, the maximum static pressure efficiency ratio may especially be effectively 10 increased, and the minimum specific noise may be minimized. This further improves the aerodynamic performance and reduces operational noise. In an air conditioner including a heat exchanger 15 15 and a blower X arranged in an air duct 14 formed in a casing 13, the above centrifugal blower may be employed as the blower X. In this structure, the centrifugal blower effectively exhibits its operations and advantages. This greatly contributes to improvement of performance and cost 20 reduction of the air conditioner. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a vertical cross-sectional view showing a 25 centrifugal blower Xi according to a first embodiment of the present invention; Fig. 2 is a front view showing an impeller of the centrifugal blower X 1 of the first embodiment; Figs. 3(A), 3(B) and 3(C) are cross-sectional views 30 respectively showing main parts of three different modifications of the centrifugal blower Xi of the first embodiment; Fig. 4 is a characteristic diagram showing changes in 11 the minimum specific noise Ks relative to a variable k=(Do

D

1

)/(D

2

-D

1 ) in the centrifugal blower Xi of the first embodiment; Fig. 5(A) is a cross-sectional view of a main part 5 when k 0 is satisfied, and Fig. 5(B) is a cross-sectional view of the main part when k 0.6 is satisfied; Fig. 6 is a vertical cross-sectional view showing an air conditioner Zi incorporating the centrifugal blower Xi of the first embodiment; 10 Fig. 7 is a vertical cross-sectional view showing a centrifugal blower X 2 according to a second embodiment; Figs. 8 (A) to 8(L) are cross-sectional views respectively showing main parts of modifications of the centrifugal blower X 2 of the second embodiment of the present 15 invention; Fig. 9 is a characteristic diagram showing changes in the minimum specific noise ks relative to a variable ki=H/D 2 in the centrifugal blower X 2 of the second embodiment; Fig. 10 is a characteristic diagram showing changes in 20 the minimum specific noise ks relative to a variable L/D 2 in the centrifugal blower X 2 of the second embodiment; Fig. 11 is a vertical cross-sectional view showing an air conditioner Z 2 incorporating the centrifugal blower X 2 of the second embodiment; 25 Fig. 12 is a vertical cross-sectional view showing a centrifugal blower X 3 according to a third embodiment; Fig. 13 is a front view of an impeller of the centrifugal blower X 3 of the third embodiment; Fig. 14 is a characteristic diagram showing changes in 30 the minimum specific noise Ks relative to a variable k=(Do

D

1

)/(D

2 -Di) in the centrifugal blower X 3 of the third embodiment; Fig. 15 is a characteristic diagram showing changes in 12 the maximum specific noise Ks relative to L/D 2 in the centrifugal blower X 3 of the third embodiment; Fig. 16 is a characteristic diagram showing changes in the static pressure relative to the air flow in the 5 centrifugal blower X 3 of the third embodiment; Fig. 17 is a characteristic diagram showing changes in the maximum flow rate coefficient pmax (the maximum flow rate coefficient when there is no deterioration being reference value=1) relative to B/D 2 in the centrifugal blower 10 X 3 of the third embodiment; Fig. 18 is a vertical cross-sectional view showing an air conditioner Z 3 incorporating the centrifugal blower X 3 of the third embodiment; Fig. 19 is a vertical half-sectional view showing 15 modification I of the centrifugal blower X 3 of the third embodiment; Fig. 20 is a vertical half-sectional view showing modification II of the centrifugal blower X 3 of the third embodiment; 20 Fig. 21 is a vertical half-sectional view showing modification III of the centrifugal blower X 3 of the third embodiment; Fig. 22 is a vertical half-sectional view showing a centrifugal blower X 4 according to a fourth embodiment; 25 Fig. 23 is a characteristic diagram showing changes in the maximum flow rate coefficient cpmax (the maximum flow rate coefficient when there is no deterioration is defined as reference value=1) relative to B/D 2 in the centrifugal blower X 4 of the fourth embodiment; 30 Fig. 24 is a vertical half-sectional view showing modification I of the centrifugal blower X 4 of the fourth embodiment; Fig. 25 is a vertical half-sectional view showing 13 modification II of the centrifugal blower X 4 of the fourth embodiment; Fig. 26 is a vertical half-sectional view showing modification III of the centrifugal blower X 4 of the fourth 5 embodiment; Fig. 27 is a vertical half-sectional view showing modification IV of the centrifugal blower X 4 of the fourth embodiment; Fig. 28 is a vertical half-sectional view showing 10 modification V of the centrifugal blower X 4 of the fourth embodiment; Fig. 29 is a vertical half-sectional view showing a centrifugal blower X 5 according to a fifth embodiment; Fig. 30 is a vertical half-sectional view showing 15 modification I of the centrifugal blower X 5 of the fifth embodiment; Fig. 31 is a vertical half-sectional view showing modification II of the centrifugal blower X 5 of the fifth embodiment; 20 Fig. 32 is a vertical half-sectional view showing modification III of the centrifugal blower Xs of the fifth embodiment; Fig. 33 is a vertical half-sectional view showing the structure and operation of a comparison example 25 (corresponding to the blower shown in Fig. 19) in comparison with modification III of the centrifugal blower X 5 of the fifth embodiment; Fig. 34 is a vertical half-sectional view showing the structure of a conventional centrifugal blower having a 30 shroud as another comparison example for modification III of the centrifugal blower X 5 of the fifth embodiment; Fig. 35 is a graph showing the noise reduction effect of modification III of the centrifugal blower X 5 of the fifth 14 embodiment in comparison with the comparison example; Fig. 36 is a horizontal cross-sectional view showing the structure of a centrifugal blower according to a sixth embodiment; 5 Fig. 37 is a vertical cross-sectional view showing the structure of the centrifugal blower of the sixth embodiment; Fig. 38 is a horizontal cross-sectional view showing the structure of a centrifugal blower according to a seventh embodiment; 10 Fig. 39 is a vertical cross-sectional view showing the structure of the centrifugal blower of the seventh embodiment; Fig. 40 is a horizontal cross-sectional view showing a centrifugal blower according to an eighth embodiment; 15 Fig. 41 is a vertical cross-sectional view showing the structure of the centrifugal blower of the eighth embodiment; Fig. 42 is a horizontal cross-sectional view showing the structure of a main part of a testing example of the 20 centrifugal blower of the eighth embodiment; Fig. 43 is a graph showing the relationship between the performance and the number of vanes in the testing example of the centrifugal blower of the eighth embodiment; Fig. 44 is a vertical half-sectional view of a testing 25 example showing the structure of the centrifugal blower of the eighth embodiment; Fig. 45 is a horizontal cross-sectional view showing the structure of a centrifugal blower according to a ninth embodiment; 30 Fig. 46 is a vertical cross-sectional view showing the structure of the centrifugal blower of the ninth embodiment; Fig. 47 is a horizontal cross-sectional view showing the structure of a centrifugal blower according to a tenth 15 embodiment; Fig. 48 is a vertical cross-sectional view showing the structure of the centrifugal blower of the tenth embodiment; Fig. 49 is a horizontal cross-sectional view showing 5 the structure of a main part in a testing example of the centrifugal blower of the tenth embodiment; Fig. 50 is a graph showing the relationship between the performance and the number of vanes in the testing example of the centrifugal blower of the tenth embodiment; 10 Fig. 51 is a horizontal cross-sectional view showing the structure of a centrifugal blower according to an eleventh embodiment; Fig. 52 is a vertical cross-sectional view showing the structure of the centrifugal blower of the eleventh 15 embodiment; Fig. 53 is a horizontal cross-sectional view showing the structure of a centrifugal blower according to a twelfth embodiment; Fig. 54 is a vertical cross-sectional view showing the 20 structure of the centrifugal blower of the twelfth embodiment; Fig. 55 is a vertical half-sectional view showing the structure of a centrifugal blower according to a thirteenth embodiment; 25 Fig. 56 is a vertical half-sectional view showing the structure of a main part in the centrifugal blower of the thirteenth embodiment; Fig. 57 is a horizontal cross-sectional view showing the structure and operation of the main part in the 30 centrifugal blower of the thirteenth embodiment; Fig. 58 is horizontal cross-sectional view showing the structure and operation of the main part in the centrifugal blower of the thirteenth embodiment; 16 Fig. 59 is a vertical half-sectional view showing the structure of a centrifugal blower according to a fourteenth embodiment; and Fig. 60 is a horizontal cross-sectional view showing 5 the structure and operation of a main part in the centrifugal blower of the fourteenth embodiment. BEST MODE FOR CARRYING OUT THE INVENTION 10 Several preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. (First Embodiment) 15 Figs. 1 to 6 illustrate a centrifugal blower X 1 and an air conditioner Zi according to a first embodiment of the present invention. 20 As shown in Figs. 1 and 2, the centrifugal blower Xi is provided with an impeller 1 including a disk-shaped hub 2 with a central portion to which a rotation shaft 4a of a motor 4 is connected and a plurality of vanes 3 arranged on the peripheral portion of the hub 2 at predetermined 25 intervals in the circumferential direction. A bellmouth 5 having an air intake port 6 is located at the air intake side of the impeller 1. As shown in Fig. 2, the impeller 1 is of a sweep back 30 vane type (i.e., a turbo fan type) in which the front rim of each vane is inclined toward the front in the rotational direction, that is, an outer diameter end 3b of each vane 3 is located rearward from an inner diameter end 3a of the 17 vane 3 relative to the rotational direction M of the impeller 1. With this structure, the ratio of static pressure increase occupies a large proportion in the total pressure increase of the impeller. This eliminates the need 5 for a spiral scroll. A recess 2a is formed in the central portion of the hub 2 to house the motor 4. A motor fixing portion 7 is used to fix the motor 4. A bearing boss 8 rotatably supports the 10 rotation shaft 4a of the motor 4. A reinforcing ring 9 connects axial distal ends of the vanes 3. The air intake port 6 of the bellmouth 5 has an inner diameter Do that is set to be greater than an inner diameter 15 Di of the vanes 3 of the impeller 1. A circulation space S is formed at the rear side (i.e., the peripheral side) of the bellmouth 5 to ensure that a circulating flow f 2 is easily generated in a manner that it flows out of the outlet side of the impeller 1 and is then drawn back into the 20 impeller 1 through the rear side of the air intake port 6 in the bellmouth 5. The air intake port 6 of the bellmouth 5 may have a straight shape as shown in Fig. 3(A), a wedge shape as shown 25 in Fig. 3(B), or a flared shape as shown in Fig. 3(C). In the present embodiment, when the inner diameter of the air intake port 6 of the bellmouth 5 is represented by Do, the inner diameter of the vanes 3 of the impeller 1 is 30 represented by D 1 , and the outer diameter of the vanes 3 is represented by D 2 , these dimensions are set to satisfy O<(Do Di)/(D 2 -D1)<0.6. There are ten vanes 3. 18 The operation and advantages of the above centrifugal blower will now be described. In the above structure, circulating flow f 2 is generated around the reinforcing rib 9 so as to flow out of the outlet side of the impeller 1 and 5 then be drawn back into the impeller 1 through the rear side of the air intake port 6 in the bellmouth 5. Accordingly, a main air flow fi passing across the vanes 3 after being drawn into from the air intake port 6 is drawn towards the distal ends of the vanes 3 by the circulating flow f 2 . This 10 improves the air speed distribution in the exit portions of the vanes 3, enhances the aerodynamic performance, and lowers the operational noise. Moreover, since no shroud is required, the integral molding of the impeller 1 is enabled. This lowers costs and provides high mass productivity. 15 Further, in the present embodiment, when the inner diameter of the air intake port 6 of the bellmouth 5 is represented by Do, the inner diameter of the vanes 3 of the impeller 1 is represented by D 1 , and the outer diameter of 20 the vanes 3 is represented by D 2 , the dimensions are set to satisfy 0<k=(Do-Di)/(D 2

-D

1 )<0.6. This lowers the minimum specific noise Ks low as shown in Fig. 4, enhances the aerodynamic performance, and lowers the operational noise. 25 When 0 k=(Do-D 1

)/(D

2 -Di) is satisfied, as shown in Fig. 5(A), the front distal portions of the vanes 3 do not function effectively and inhibits the enhancement of the aerodynamic performance. When k=(Do-D1)/(D 2 -Dj 1 ) 0.6 is satisfied, as shown in Fig. 5(B), a reversed flow f' 30 generated at the front distal portions of the vanes 3 will becomes strong, while the circulating flow f 2 at the rear distal portions of the vanes 3 will become weak. This also inhibits the enhancement of the aerodynamic performance. 19 With Di representing the inner diameter of the vanes 3,

D

2 representing the outer diameter of the vanes 3, and Do representing the inner diameter of the air intake port 6A in 5 the centrifugal blower Xi of this embodiment, a microphone 12 located 45 degrees to the front and one meter away from the intake center Q of the air intake port 6 was used to check changes in the minimum specific noise Ks with respect to a variable k= (Do-D 1

)/(D

2

-D

1 ) . Fig. 4 shows the results obtained. 10 It can be seen from the results that satisfactory operational noise characteristics were obtained in the range 0<k<0.6. Fig. 6 shows a ceiling-embedded air conditioner Zi 15 incorporating the centrifugal blower Xi of this embodiment. In this case, a heat exchanger 15 and the centrifugal blower Xi are arranged in an air duct 14 for air flow W that is formed in a casing 13. The motor fixing portion 7 for 20 fixing the motor 4 is formed integrally with a top plate 13a of the casing 13. This air conditioner Zi includes an intake grille 16, an air filter 17, a drain pan 18, and an air outlet port 19. 25 This structure allows the centrifugal blower Xi to effectively exhibit its advantageous effects. This greatly contributes to enhancement in the performance of the air conditioner Zi and reduction in costs. Additionally, the optimum diameter for the air intake port 6 may be set to be 30 greater than that of a conventional one. This suppresses pressure loss in the air filter 17 or the like. (Second Embodiment) 20 Figs. 7 and 11 respectively show a centrifugal blower

X

2 and an air conditioner Z 2 according to a second embodiment of the present invention. 5 In this case, the impeller 1 in the centrifugal blower

X

2 includes a ring body 20, which has a predetermined width H in the centrifugal direction, in lieu of the reinforcing ring 9 of the first embodiment. In other respects, the 10 structure and effects of the second embodiment are the same as those of the first embodiment. Thus, such parts will not be described. The ring body 20 may take various shapes as shown in 15 Figs. 8 (A) to 8 (L). The following descriptions are only examples, and it is obvious that the ring body 20 may take other shapes that are not shown in the drawings. As shown in Fig. 8(A), the ring body 20 may be joined 20 to the axial end surfaces of the vanes 3. As shown in Fig. 8(B), the ring body 20 may be attached to be inclined away from the hub. As shown in Fig. 8 (C), the ring body 20 may be attached to be inclined toward the hub. As shown in Fig. 8(D), the centrifugal end of the ring body 20 may be an 25 arcuate surface 20a. As shown in Fig. 8(E), the ring body 20 may have a centrifugal end formed by an arcuate surface 20a and the entire ring body 20 may be curved away from the hub. In this case, the Coanda effect enhances the generation of the circulating flow f 2 . 30 As shown in Fig. 8(F), the surface of the ring body 20 opposite the hub has a recess 20b. In this case, negative pressure is generated within the recess 20b to enhance 21 generation of the circulating flow f 2 . As shown in Fig. 8(G), the surface of the ring body 20 opposite the hub may have a recess 20b, and the ring body 20 may be inclined toward the hub. In this case as well as in the case shown in Fig. 8(F), 5 the generation of the circulating flow f 2 is enhanced. As shown in Fig. 8(H), the surface of the ring body 20 on the side facing toward the hub may have a recess 20c. In this case, negative pressure is generated within the recess 20c to enhance generation of the circulating flow f 2 . 10 As shown in Fig. 8(I), the surface of the ring body 20 on the side facing toward the hub may have a recess 20c, and the ring body 20 may be inclined toward the hub. In this case as well as in the case shown in Fig. 8(H), the 15 generation of the circulating flow f 2 is enhanced. As shown in Fig. 8(J), the ring body 20 may be formed of a relatively thick member having arcuate surfaces 20d and 20e formed on its attachment end and centrifugal end, respectively. This generates a smooth circulating flow f 2 . 20 As shown in Fig. 8(K), the ring body 20 may be formed of a relatively thick member having arcuate surfaces 20d and 20e formed on its attachment end and on its centrifugal end, respectively, and the ring body 20 may be inclined toward 25 the hub. In this case as well as in the case shown in Fig. 8(J), a smooth circulating flow f 2 is generated. As shown in Fig. 8(L), the hub 2 may include an inclined surface 2b at the region where the vanes 3 are 30 arranged such that the inclined surface 2b is inclined toward the side opposite the vanes, while the ring body 20 may be formed of a relatively thick member having arcuate surfaces 20d and 20e formed on its attachment end and 22 centrifugal end, respectively, and the ring body 20 may be attached to an inclined surface 3c (inclined at a same angle as the inclined surface 2b of the hub 2) formed at the distal end of each vane 3. In this case, during molding, the 5 ring body 20 may be removed from the peripheral side. With D 2 representing the outer diameter of the vanes 3 and H representing the width of the ring body 20 in the centrifugal direction in the centrifugal blower X 2 of this 10 embodiment, a microphone 12 located 45 degrees to the front and one meter away from the intake center Q of the air intake port 6 was used to check changes in the minimum specific noise Ks with respect to a variable ki=H/D 2 . Fig. 9 shows the results obtained. 15 It can be seen from the above results that satisfactory operational noise characteristics were obtained in the range 0.05<ki<0.225. The range 0.l<ki<0.15 is more preferable. When ki=H/D 0.05 is satisfied, the effect will 20 be reduced. When ki=H/D 0.225 is satisfied, the formation of circulating flow will be adversely affected and weaken the circulating flow at the rear distal portions of the vanes 3. This inhibits enhancement of the aerodynamic performance. 25 With L representing the distance between the ring body 20 and the bellmouth 5, changes in the minimum specific noise Ks with respect to a variable L/D 2 were checked. Fig. 10 shows the results obtained. As seen from the above results, satisfactory operational noise characteristics were 30 obtained in the range L/D 2 0.169. Fig. 11 shows a ceiling-embedded air conditioner Z 2 incorporating the centrifugal blower X 2 of the second 23 embodiment. In this case, a heat exchanger 15 and the centrifugal blower X 2 are arranged in an air duct 14 for air flow W that is formed within a casing 13. A motor fixing portion 7 for fixing a motor 4 is formed integrally with a 5 top plate 13a of the casing 13. The air conditioner Z 2 has an intake grille 16, an air filter 17, a drain pan 18, and an air outlet port 19. This structure enables the centrifugal blower X 2 to effectively exhibit its advantageous effects. This greatly contributes to enhancement in 10 performance of the air conditioner Z 2 and reduction in costs. Additionally, the optimum diameter of the air intake port 6 may be greater than that of a conventional one. This lowers pressure loss in the air filter 17. 15 The centrifugal blower of the above embodiments is applied when the number of the vanes 3 is small (i.e., 5 to 15 vanes). (Third Embodiment) 20 Figs. 12 to 16 show a centrifugal blower X 3 and an air conditioner Z 3 according to a third embodiment of the present invention. 25 As shown in Figs. 12 and 13, the centrifugal blower X3 is provided with an impeller 1 including a disk-shaped hub 2 having a central portion to which a rotation shaft 4a of a motor 4 is connected and a plurality of vanes 3 arranged on the peripheral portion of the hub 2 at predetermined 30 intervals in the circumferential direction. A bellmouth 5 having an air intake port 6 is arranged on the air intake side of the impeller 1. 24 As shown in Fig. 13, the impeller 1 is of a sweep back vane type (i.e., a turbo fan type) in which the front rim of each vane is inclined toward the front in the rotational direction, that is, an outer diameter end 3b of each vane 3 5 is located rearward from an inner diameter end 3a of the vane 3 relative to the rotational direction M of the impeller 1. With this structure, the ratio of static pressure increase occupies a large proportion in the total pressure increase of the impeller. This eliminates the need 10 of a spiral scroll. In the centrifugal blower X 3 of this embodiment, the number of vanes 3 is greater (for example, 30 to 50 vanes) than the numbers of vanes in the centrifugal blowers Xi and X 2 of the first and second embodiments. 15 A recess 2a is formed in the central portion of the hub 2 for housing the motor 4. A motor fixing portion 7 is used to fix the motor 4. A bearing boss 8 rotatably supports the rotation shaft 4a of the motor 4. 20 Like the second embodiment, the impeller 1 of the third embodiment is provided with a ring body 20 having a predetermined width H in the centrifugal direction. In the third embodiment, the ring body 20 is inclined toward the hub 2 in the centrifugal direction. 25 A circulation space S is formed at the rear side (i.e., the peripheral side) of the bellmouth 5 to ensure that a circulating flow f 2 is easily generated in a manner that it flows out of the outlet side of the impeller 1 and is then 30 drawn back into the impeller 1 through the rear side of the air intake port 6 in the bellmouth 5. Like the first embodiment, the air intake port 6 of the bellmouth 5 may take any of a straight shape, a wedge shape, and a flared 25 shape. In this embodiment, when the inner diameter of the air intake port 6 of the bellmouth 5 is represented by Do, the 5 inner diameter of the vanes 3 of the impeller 1 is represented by D 1 , and the outer diameter of the vanes 3 is represented by D 2 , the dimensions are set to satisfy -0.3<(Do-Di)/ (D 2

-D

1 )<0.3. The number of the vanes 3 is 40. 10 The operation and advantages of the above centrifugal blower will now be described. Circulating flow f 2 is generated to flow out of the outlet side of the impeller 1 and then be drawn back into 15 the impeller 1 through the rear side of the air intake port 6 in the bellmouth 5. Accordingly, a main air flow fi passing across the vanes 3 after being drawn into from the air intake port 6 is drawn towards the distal ends of the vanes 3 by the circulating flow f 2 . This improves the air 20 speed distribution in the exit portions of the vanes 3, enhances the aerodynamic performance, and lowers the operational noise. Moreover, since no shroud is required, the integral molding of the impeller 1 is enabled. This lowers costs and provides high mass productivity. 25 In this third embodiment, when the inner diameter of the air intake port 6 of the bellmouth 5 is represented by Do, the inner diameter of the vanes 3 of the impeller 1 is represented by D 1 , and the outer diameter of the vanes 3 is 30 represented by D 2 , the dimensions are set such that -0.3<k=(Do-Di)/(D 2

-D

1 )<0.3 is satisfied. As shown in Fig. 14, this lowers the minimum specific noise Ks low, which further enhances the aerodynamic performance, and reduces the 26 operational noise. When -0.3 k= (DO-Di)/ (D 2 -Di) is satisfied, the front distal portions of the vanes 3 will not function effectively and inhibit the enhancement of the aerodynamic performance. When k=(D 0 -Di)/(D 2 -Di)f0.3 is satisfied, the 5 reversed flow f' generated at the front distal portions of the vanes 3 becomes strong, and the circulating flow f 2 at the rear distal portions of the vanes 3 become weak. This inhibits enhancement in the aerodynamic performance. 10 With Di representing the inner diameter of the vanes 3,

D

2 representing the outer diameter of the vanes 3, and Do representing the inner diameter of the air intake port 6 in the centrifugal blower X 2 of this embodiment, a microphone 12 located 45 degrees to the front and one meter away from the 15 intake center Q of the air intake port 6 was used to check changes in the minimum specific noise Ks with respect to a variable k=(Do-Di)/(D 2 -Di). Fig. 14 shows the results obtained. It can be seen from the results that satisfactory operational noise characteristics were obtained in the range 20 -0.3<k<0.3. The relationship between the outer diameter D 2 of the vanes 3 and the width H in the centrifugal direction of the ring body 20 in the centrifugal blower X 3 is the same as that 25 in the second embodiment. The relationship between the outer diameter D 2 of the vanes 3 and the distance L between the ring body 20 and the bellmouth 5 in the centrifugal blower X 3 is shown in Fig. 15. The minimum specific noise Ks is lowered and suppressed in the range L/D 2 0.07. When 30 L/D 2 <0.07 is satisfied, the minimum specific noise Ks increases drastically. When the exit side height B of the vanes 3 in the 27 impeller 1 decreases, fluctuation in the air flow line fi increases at the exit side of the impeller 1. This eventually causes the circulating flow f 2 to obstruct the flow passage between the vanes 3. In such a case, the 5 aerodynamic performance falls sharply as shown by the solid line in Fig. 16, and a hysteresis will occur as shown by the broken line in Fig. 16. This is not irrelevant to the number of the vanes. 10 Therefore, this embodiment is set to satisfy B/D 2 0.113. This setting solves the problem of fluctuation in the air flow line fi at the exit side of the impeller 1, and provides stable performance as shown by the double-dotted line in Fig. 16. If B/D 2 <0.113 is satisfied, the air flow line at the 15 exit side of the impeller 1 will greatly fluctuate, and the circulating flow f 2 will eventually obstruct the flow passage between the vanes 3 and cause the performance to fall sharply. 20 In the centrifugal blower X 3 of the third embodiment, changes in the maximum flow rate coefficient max (the coefficient when there is no deterioration is defined as reference value=1) with respect to B/D 2 was checked. Fig. 17 shows the results obtained. Here, cpmax=Qmax/60(rD 2 B)u 2 is 25 satisfied, where u 2 =rD 2 N, Qmax represents the fully open air flow (m 3 /min), and N represents the rotation speed (rpm). It can be seen from the results shown in Fig. 17 that the maximum flow rate coefficient pmax is equal to the reference value of one when B/D 2 20.113 is satisfied. 30 Fig. 18 shows a ceiling-embedded air conditioner Z 3 incorporating the centrifugal blower X 3 of this embodiment. In this case, a heat exchanger 15 and the centrifugal blower 28

X

3 are arranged in an air duct 14 for air flow W that is formed within a casing 13. A motor fixing portion 7 is used for fixing a motor 4 is integral with a top plate 13a of the casing 13. The air conditioner Z 3 has an intake grille 16, 5 an air filter 17, a drain pan 18, and an air outlet port 19. This structure enables the centrifugal blower X3 to effectively exhibit its advantageous effects. This greatly contributes to enhancement in performance of the air conditioner Z 2 and reduction in costs. Additionally, the 10 optimum diameter of the air intake port 6 may be greater than that of a conventional one. This lowers pressure loss in the air filter 17. Modifications of the centrifugal blower X 3 of the third 15 embodiment will be described. (Modification I) As shown in Fig. 19, the tip side end of each vane 3 in the impeller 1 may be inclined at substantially the same 20 inclination angle as that of the ring body 20. In this case as well, the relationship among Do, Di, D 2 , H, L, and B is the same as described above. (Modification II) 25 As shown in Fig. 20, the tip side end of each vane 3 in the impeller 1 may be inclined at substantially the same inclination angle as that of the ring body 20, with the inlet side end of each vane 3 inclined in the centripetal direction of the impeller 1 toward the hub. In this case as 30 well, the relationship among Do, Di, D 2 , H, L, and B is the same as described before. (Modification III) 29 As shown in Fig. 21, the tip side end of each vane 3 in the impeller 1 may be inclined at substantially same inclination angle as an inclination angle of the ring body 20, with the inlet side end of each vane 3 inclined in the 5 centripetal direction of the impeller 1 toward the hub with serrations 21 formed in the inlet side end. This structure prevents the formation of a boundary layer on the vane surfaces. Thus, the air flow noise is reduced. In this case as well, the relationship among Do, D 1 , D 2 , H, L, and B is 10 the same as described before. (Fourth Embodiment) Fig. 22 shows a centrifugal blower X 4 according to a 15 fourth embodiment of the present invention. In this embodiment, the outer diameter D 3 of a hub 2 forming an impeller 1 is set to be smaller than the outer diameter D 2 of vanes 3. Accordingly, an opening 22 is formed in the hub side of the peripheral portion on the vanes 3. This reduces 20 the flow resistance of the air blown out of the vanes 3 when using a diagonal diffuser 23, which will be described later (see Fig. 29). In other respects, the structure and effects of the fourth embodiment are the same as those of the third embodiment and therefore will not be described. 25 In the fourth embodiment as well as in the third embodiment, when the exit side height B of the vanes 3 in the impeller 1 decreases, fluctuation in the air flow line f, increases at the exit side of the impeller 1. This 30 eventually causes the circulating flow f 2 to obstruct the flow passage between the vanes 3. In such a case, the aerodynamic performance falls sharply as shown by the solid line in Fig. 16, and a hysteresis will occur as shown by the 30 broken line in Fig. 16. This is not irrelevant to the number of the vanes. Therefore, this embodiment is set to satisfy B/D 2 0.08. 5 The reason the upper limit of B/D 2 is less than that in the third embodiment is in that the opening 22 is formed in the peripheral portion of the hub-side of the vanes 3. This setting solves the problem of fluctuation in the air flow line fi at the exit side of the impeller 1, and provides 10 stable performance as shown by the double-dotted line in Fig. 15. If B/D 2 <0.08 is satisfied, the air flow line at the exit side of the impeller 1 will greatly fluctuate, and the circulating flow f 2 will eventually obstruct the flow passage between the vanes 3 and cause the performance to fall 15 sharply. In the centrifugal blower X 3 of this embodiment, changes in the maximum flow rate coefficient cpmax (the coefficient when there is no deterioration is.defined as 20 reference value=1) with respect to B/D 2 was checked. Fig. 23 shows the results obtained. Here, cpmax=Qmax/60(rD 2 B)u 2 is satisfied, where u 2 =rD 2 N, Qmax represents the fully open air flow (m 3 /min), and N represents the rotation speed (rpm). It can be seen from the results shown in Fig. 23 that the 25 maximum flow rate coefficient cpmax is equal to the reference value of one when B/D 2 0.08 is satisfied. Modifications of the centrifugal blower X 4 of the fourth embodiment will now be described. 30 (Modification I) As shown in Fig. 24, the tip side end of each vane 3 of the impeller 1 may be inclined at substantially the same 31 inclination angle as that of the ring body 20. In this case as well, the relationship among Do, D 1 , D 2 , H, L, and B is the same as described before. 5 (Modification II) As shown in Fig. 25, the tip side end of each vane 3 in the impeller 1 may be inclined at substantially the same inclination angle as that of the ring body 20, with the inlet side end of each vane 3 inclined in the centripetal 10 direction of the impeller 1 toward the hub. In this case as well, the relationship among Do, D 1 , D 2 , H, L, and B is the same as described before. (Modification III) 15 As shown in Fig. 26, the tip side end of each vane 3 in the impeller 1 may be inclined at a substantially same inclination angle as an inclination angle of the ring body 20, and the inlet side end of each vane 3 is inclined in the centripetal direction of the impeller 1 toward the hub with 20 serrations 21 is formed in the inlet side end. This structure prevents the formation of a boundary layer on the vane surfaces. Thus, the air flow noise is reduced. In this case as well, the relationship among Do, D 1 , D 2 , H, L, and B is the same as described before. 25 (Modification IV) As shown in Fig. 27, the impeller 1 may be of a diagonal flow fan type in which the peripheral portion of the hub 2 (that is, the region where the vanes 3 are 30 arranged) is inclined. In this case as well, the relationship among Do, D 1 , D 2 , H, L, and B is the same as described before. 32 (Modification V) As shown in Fig. 28, the impeller 1 may be of a diagonal flow fan type in which the peripheral portion of the hub 2 (that is, the region where the vanes 3 are 5 arranged) is inclined, and the inlet side end of each vane 3 is inclined in the centripetal direction of the impeller 1 towards the hub. In this case as well, the relationship among Do, D 1 , D 2 , H, L, and B is the same as described before. 10 It is obvious that the centrifugal blower X 4 of the fourth embodiment may be incorporated in an air conditioner. (Fifth Embodiment) 15 Fig. 29 shows a centrifugal blower X 5 according to a fifth embodiment of the present invention. In this embodiment, the outer diameter D 3 of a hub 2 forming an impeller 1 is set to be smaller than the outer diameter D 2 of vanes 3, and a diagonal centrifugal diffuser 23 is arranged 20 on the outlet side of the impeller 1 so that an air flow from the impeller 1 is guided from the obliquely rear side in the centrifugal direction. In this structure, an opening 22 is formed in the hub side of the peripheral portion of the vanes 3. This reduces the air flow resistance of the air 25 blown out from the vanes 3, enables the dynamic pressure of the air blown out from the impeller 1 to efficiently return to the static pressure, and greatly contributes to the enhancement of the performance (i.e., high efficiency and low noise). In other respects, the structure and effects of 30 the fifth embodiment are the same as those of the third embodiment and therefore will not be described. Modifications of the centrifugal blower X 5 of the fifth 33 embodiment will now be described. (Modification I) As shown in Fig. 30, the tip side end of each vane 3 5 in the impeller 1 may be inclined at substantially the same inclination angle as that of the ring body 20. In this case as well, the relationship among Do, D 1 , D 2 , H, L, and B is the same as described before. 10 (Modification II) As shown in Fig. 31, the tip side end of each vane 3 in the impeller 1 may be inclined at substantially the same inclination angle as that of the ring body 20, with the inlet side end of each vane 3 inclined in the centripetal 15 direction of the impeller 1 towards the hub. In this case as well, the relationship among Do, D 1 , D 2 , H, L, and B is the same as described before. The centrifugal blowers of the third to the fifth 20 embodiments employ a large number of the vanes 3 (i.e., 30 to 50 vanes). It is obvious that the centrifugal blower X 4 of to this embodiment may be incorporated in an air conditioner. It is 25 also obvious that similar effects may be obtained by using a spiral casing. (Modification III) The centrifugal blower Xs shown in Fig. 32 is 30 characterized in that a diagonal centrifugal diffuser 23 similar to those shown in Figs. 29 to 31 is provided in the structure of the impeller and the bellmouth of the centrifugal blower X 3 of the third embodiment described above. 34 In this case, as shown in Fig. 32, the air speed distribution at the exit portion of the vanes 3 of the impeller 1 becomes greater at the intake side due to the 5 guiding function of the ring body 20, and relatively small at the side of the hub 2. However, afterwards, the speed of the air blown out from the side of the hub 2 is increased in the diagonal direction by the air flow passing through the diagonal diffuser passage that is deflected toward the side 10 of the hub 2 and ultimately blown out from the outlet port in the centrifugal direction. Thus, the speed of the air blown out from the outlet port in the centrifugal direction becomes uniform throughout. This improves the fan efficiency and effectively improves the noise reduction performance. 15 In order to check this effect, for example, the centrifugal blower X 3 of modification I of the third embodiment shown in Fig. 19 (Fig. 33) is compared with a conventional shrouded centrifugal blower provided with the 20 diagonal centrifugal diffuser 23 (Fig. 34) with regard to the air speed distribution. The comparison result is as described below. In the conventional shrouded centrifugal blower shown 25 in Fig. 34, the air flow drawn into the air intake port 6 of the bellmouth 5 is deflected toward the hub 2. This results in the air speed distribution at the exit portion of the vanes 3 being decreased at the air intake port 6 and increased at the side of the hub 2. Thus, the air flow is 30 greatly deflected toward the hub 2. Moreover, the air flow deflected toward the hub 2 is further deflected rearward by passing through the diagonal 35 passage in the diagonal centrifugal diffuser 23 and being directly blown out in the centrifugal direction. Thus, the air speed distribution of the ultimately blown out air flow is greatly deflected toward the rear side. 5 In contrast, the centrifugal blower X 3 of the modification I of the third embodiment shown in Fig. 33 is shroudless and has the ring body 20 provided on the peripheral portion of the axial distal ends of the vanes 3. 10 The main air flow fi is drawn toward the distal end side of the vanes 3 by the circulating flow f 2 formed by the ring body 20. This significantly improves the air speed distribution in the exit portion of the vanes 3. However, the air speed distribution of the blown out air in the ring 15 body 20 is great, and the air speed distribution is not necessarily uniform when the outlet port is viewed as a whole. In contrast, in the case of the centrifugal blower X5 20 of the modification III of the fifth embodiment, which has the diagonal centrifugal diffuser 23 of which passage shape changes in the radial direction, the air speed distribution of the air ultimately blown out from the outlet port in the centrifugal direction becomes uniform over the entirety as 25 shown in Fig. 32. Accordingly, as shown in Fig. 35, the noise reduction effect is much greater than that of the conventional shrouded centrifugal blower shown in Fig. 34. (Sixth Embodiment) 30 Figs. 36 and 37 show an impeller of a centrifugal blower according to a sixth embodiment of the present invention. 36 As shown in Figs. 36 and 37, this centrifugal blower impeller 1 includes, for example, a disk-shaped hub 2 having a central portion to which a rotation shaft 4a of a motor 4 5 is connected and a plurality of vanes 3 arranged on the peripheral portion of the hub 2 at predetermined intervals in the circumferential direction. Each vane 3 of the impeller 1 has an inner diameter 10 end 3a, or front rim, inclined forward in the rotational direction, and a outer diameter end 3b, or rear rim, located rearward from the inner diameter end 3a in the rotational direction M of the impeller 1. Thus, the impeller 1 is of a sweep back vane type (so called turbo fan type) in which a 15 camber line protrudes in the rotational direction. The number of vanes 3 of the impeller 1 is set to, for example, 20 to 50. A ring body 20 having a predetermined width H in the centrifugal direction is attached to the 20 peripheral portion of the vane ends on the side of a bellmouth. In this embodiment, the end of the ring body 20 and the end of each vane 3 on the side of the bellmouth are inclined toward the hub 2 in the centrifugal direction like in Fig. 24. In other respects, the structure of the sixth 25 embodiment is basically the same as the above embodiments. The centrifugal blower of this embodiment, which has the impeller 1 as described above formed in combination with a bellmouth 5 like those of the above embodiments without a 30 shroud, also has the advantages described below that are similar to those of the above embodiments. Specifically, the presence of the ring body 20 causes 37 the generation of the circulating flow f 2 that flows out from the outlet side of the impeller 1, flows back into the impeller 1, and passes the rear side of the air intake port 6 of the bellmouth 5. Therefore, main air flow fi passing 5 across the vanes 3 is effectively drawn toward the distal ends of the vanes 3 by the circulating flow f 2 . As a result, the air speed distribution in the exit portion of the vanes 3 is improved uniformly. This enhances the aerodynamic performance and reduces operational noise. 10 Moreover, since no shroud is required, the impeller 1 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity. 15 (Seventh Embodiment) Figs. 38 and 39 show an impeller of a centrifugal blower according TO a seventh embodiment of the present invention. As shown in Figs. 38 and 39, this centrifugal 20 blower impeller 1 includes, for example, a disk-shaped hub 2 having central portion to which a rotation shaft 4a of a motor 4 is connected and a plurality of vanes 3 arranged on the peripheral portion of the hub 2 at predetermined intervals in the circumferential direction. 25 Each vane 3 of the impeller 1 has an inner diameter end 3a, or a front rim, inclined forward in the rotational direction and an outer diameter end 3b, or rear rim located rearward from the inner diameter end 3a in the rotational 30 direction M of the impeller 1. Thus, the impeller 1 is of a sweep back vane type (so called turbo fan type) in which a camber line protrudes in the rotational direction. 38 The number of vanes 3 of the impeller 1 is set, for example, to 20 to 50. A ring body 20 having a predetermined width H in the centrifugal direction is attached to the peripheral portion of the vane ends on the side of a 5 bellmouth. In this embodiment, the end of the ring body 20 and the end of each vane 3 on the side of the bellmouth are inclined toward the hub 2 along the centrifugal direction, like in Fig. 24. In other respects, the structure of the seventh embodiment is basically the same as the above 10 embodiments. The centrifugal blower of this embodiment, which has the impeller 1 as described above formed in combination with a bellmouth 5 like those of the above embodiments without a 15 shroud, also has the advantages described below that are similar to those of the above embodiments. Specifically, the presence of the ring body 20 causes the generation of the circulating flow f 2 that flows out from 20 the outlet side of the impeller 1, flows back into the impeller 1, and passes the rear side of the air intake port 6 of the bellmouth 5. Therefore, main air flow fi passing across the vanes 3 is effectively drawn toward the distal ends of the vanes 3 by the circulating flow f 2 . As a result, 25 the air speed distribution in the exit portion of the vanes 3 is improved uniformly. This enhances the aerodynamic performance and reduces operational noise. Moreover, since no shroud is required, the impeller 1 30 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity. (Eighth Embodiment) 39 Figs. 40 and 41 show an impeller of a centrifugal blower according to a seventh embodiment of the present invention. As shown in Figs. 40 and 41, this centrifugal 5 blower impeller 1 includes, for example, a disk-shaped hub 2 having a central portion to which a rotation shaft 4a of a motor 4 is connected and a plurality of vanes 3 arranged on the peripheral portion of the hub 2 at predetermined intervals in the circumferential direction. 10 Each vane 3 of the impeller 1 has an inner diameter end 3a, or a front rim, inclined forward in the rotational direction, and an outer diameter end 3b, or a rear rim, located rearward from the inner diameter end 3a in the 15 rotational direction M of the impeller 1. Thus, the impeller 1 is of a sweep back vane type (so called turbo fan type) in which a camber line protrudes in the rotational direction. The number of vanes 3 of the impeller 1 is set to, for 20 example, a large value from 20 to 50. A ring body 20 having a predetermined width H in the centrifugal direction is attached to the peripheral portion of the vane ends at the side of a bellmouth. In this embodiment, the end of the ring body 20 and the ends of the vanes 3 at the side of the 25 bellmouth are inclined toward the hub 2 along the centrifugal direction like those in Fig. 24. In other respects, the structure of the eighth embodiment is basically the same as the above embodiments. 30 The centrifugal blower of this embodiment, which has the impeller 1 as described above formed in combination with a bellmouth 5 like those of the above embodiments without a shroud, also has the advantages described below that are 40 similar to those of the above embodiments. Specifically, the presence of the ring body 20 causes the generation of the circulating flow f 2 that flows out from 5 the outlet side of the impeller 1, flows back into the impeller 1, and passes the rear side of the air intake port 6 of the bellmouth 5. Therefore, the main air flow fi passing across the vanes 3 is effectively drawn toward the distal ends of the vanes 3 by the circulating flow f 2 . As a 10 result, the air speed distribution in the exit portion of the vanes 3 is improved uniformly. This enhances the aerodynamic performance and reduces operational noise. Moreover, since no shroud is required, the impeller 1 can be molded integrally. This simplifies the structure, reduces 15 costs, and improves mass productivity. In a centrifugal blower having an impeller as described above employing sweep back vanes having a straight camber line and including outer diameter ends 3b located 20 rearward from inner diameter ends 3a in the rotational direction M of the impeller 1, the maximum static pressure efficiency ratio (reference value of 1.0) and minimum specific noise level ratio (reference value level of ±0) were measured using the number of vanes as parameters. The 25 measurement results obtained are shown in the graph of Fig. 43. The centrifugal blower used for the measurement has an impeller formed as shown Figs. 40 and 41. Each vane 3 has an 30 inlet angle E 1 of 25 degrees and an outlet angle E 2 of 50 degrees as shown in Fig. 42. An inlet height Bi and an outlet height B 2 of each vane 3 are 35 mm and 30 mm, respectively. An inner diameter Do of the air intake port 6 41 of the bellmouth 25 is 130 mm, and an inner diameter Di and an outer diameter D 2 of the vane 3 are 110 mm and 160 mm, respectively. 5 From the measurement results shown in Fig. 43, it can be determined that the performance deteriorates when the number of the vanes 3 is less than 20 because the circulating flow f 2 enters deeply into the vanes 3 as shown by f 2 ' in Fig. 44. On the other hand, when the number of 10 vanes is greater than 50, the performance also deteriorates because the intervals P between the front distal portions of the vanes 3 become too narrow. In contrast, the problems as described above seldom 15 occur when the number of vanes 3 is 20 to 50. Further, the static pressure efficiency ratio is high, and the specific noise level ratio is minimized. Thus, it is apparent that the noise reduction performance is effectively improved while the fan efficiency is increased. 20 Similar improvements in performance related to the number of vanes can be expected for the above sixth and seventh embodiments and for a twelfth embodiment described later. 25 (Ninth Embodiment) Figs. 45 and 46 show a centrifugal blower according to a ninth embodiment of the present invention. As shown in 30 Figs. 45 and 46, this centrifugal blower has an impeller 1 which includes, for example, a disk-shaped hub 2 having a central portion to which a rotation shaft 4a of a motor 4 is connected and a plurality of vanes 3 arranged on the 42 peripheral portion of the hub 2 at predetermined intervals in the circumferential direction. The impeller 1 is of a radial vane type (so called a S radial plate fan type) in which each vane 3 has an inner diameter end 3a, or a front rim, that is neither inclined toward the front nor the rear in the rotational direction M and has a straight camber line extending in the radial direction. 10 The number of vanes 3 of the impeller 1 is set to a large value, for example, 30 to 72, and a ring body 20 having a predetermined width H in the centrifugal direction is arranged on the peripheral portion of the ends of the 15 vanes at the bellmouth side. In this embodiment, the end of the ring body 20 and the ends of the vanes 3 at the side of the bellmouth are inclined toward the hub 2 in the centrifugal direction, like those shown in Fig. 44. In other respects, the structure of the ninth embodiment is basically 20 the same as the above embodiments. The centrifugal blower of this embodiment, which has the impeller 1 as described above formed in combination with a bellmouth 5 like those of the above embodiments without a 25 shroud, also has the advantages described below that are similar to those of the above embodiments. Specifically, the presence of the ring body 20 causes the generation of the circulating flow f 2 that flows out from 30 the outlet side of the impeller 1, flows back into the impeller 1, and passes the rear side of the air intake port 6 of the bellmouth 5. Therefore, main air flow fi passing across the vanes 3 is effectively drawn toward the distal 43 ends of the vanes 3 by the circulating flow f 2 . As a result, the air speed distribution in the exit portion of the vanes 3 is improved uniformly. This enhances the aerodynamic performance and reduces operational noise. 5 Moreover, since no shroud is required, the impeller 1 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity. 10 (Tenth Embodiment) Figs. 47 and 48 show an impeller of a centrifugal blower according to a tenth embodiment of the present invention. As shown in Figs. 47 and 48, this centrifugal 15 blower impeller 1 includes, for example, a disk-shaped hub 2 having a central portion to which a rotation shaft 4a of a motor 4 is connected and a plurality of vanes 3 arranged on the peripheral portion of the hub 2 at predetermined intervals in the circumferential direction. 20 The impeller 1 is of a radial vane type (first modification of the radial plate fan type described above) in which each vane 3 has an inner diameter end 3a, or a front rim, that is neither inclined toward the front nor the 25 rear in the rotational direction M and has a camber.line slightly inclined toward the rear in the rotational direction M. The number of vanes 3 of the impeller 1 is set to a 30 large value of, for example, 30 to 72, and a ring body 20 having a predetermined width H in the centrifugal direction is arranged on the peripheral portion of the ends of the vanes at the bellmouth side. In this embodiment, the end of 44 the ring body 20 and the ends of the vanes 3 at the side of the bellmouth are inclined toward the hub 2 in the centrifugal direction like in Fig. 44. In other respects, the structure of the tenth embodiment is basically the same 5 as the above embodiments. The centrifugal blower of this embodiment, which has the impeller 1 as described above formed in combination with a bellmouth 5 like those of the above embodiments without a 10 shroud, also has the advantages described below that are similar to those of the above embodiments. Specifically, the presence of the ring body 20 causes the generation of the circulating flow f 2 that flows out from 15 the outlet side of the impeller 1, flows back into the impeller 1, and passes the rear side of the air intake port 6 of the bellmouth 5. Therefore, main air flow fi passing across the vanes 3 is effectively drawn toward the distal ends of the vanes 3 by the circulating flow f 2 . As a result, 20 the air speed distribution in the exit portion of the vanes 3 is improved uniformly. This enhances the aerodynamic performance and reduces operational noise. Moreover, since no shroud is required, the impeller 1 can be molded integrally. This simplifies the structure, reduces costs, 25 and improves mass productivity. For the centrifugal blower of the tenth embodiment, the maximum static pressure efficiency ratio (reference value of 1.0) and minimum specific noise level ratio 30 (reference value level of ±0) were measured by using the numbers of the vanes as a parameter. The measurement results obtained are shown in the graph of Fig. 50. 45 The centrifugal blower used for the measurement has an impeller formed as shown Figs. 47 and 48. Each vane 3 has an inlet angle 0 1 of 90 degrees and an outlet angle 0 2 of 75 degrees as shown in Fig. 49. An inlet height B 1 and an 5 outlet height B 2 of each vane 3 are 25 mm and 20 mm, respectively. An inner diameter Do of the air intake port 6 of the bellmouth 25 is 130 mm, and an inner diameter D 1 and an outer diameter D 2 of the vanes 3 are 130 mm and 150 mm, respectively. 10 From the measurement results shown in Fig. 53, it can be determined that the performance deteriorates when the number of the vanes 3 is less than 30 because the circulating flow f 2 enters deeply into the vanes 3 as shown 15 by f 2 ' in Fig. 44. On the other hand, when the number of vanes is greater than 72, the performance also deteriorates because the intervals P between the front distal portions of the vanes 3 become too narrow. 20 In contrast, the problems as described above seldom occur when the number of vanes 3 is 30 to 72. Further, the static pressure efficiency ratio is high, and the specific noise level ratio is minimized. Thus, it is apparent that the noise reduction performance is effectively improved 25 while the fan efficiency is increased. Similar improvements in performance related to the number of vanes can be expected for the ninth embodiment described above and eleventh embodiment described below. 30 (Eleventh Embodiment) Figs. 51 and 52 show an impeller of a centrifugal 46 blower according to a tenth embodiment of the present invention. As shown in Figs. 51 and 52, this centrifugal blower impeller 1 includes, for example, a disk-shaped hub 2 having a central portion to which a rotation shaft 4a of a 5 motor 4 is connected and a plurality of vanes 3 arranged on the peripheral portion of the hub 2 at predetermined intervals in the circumferential direction. The impeller 1 is of a radial vane type (second 10 modification of the radial plate fan type described above) in which each vane 3 has an inner diameter end 3a, or a front rim that is neither inclined toward the front nor the rear in the rotational direction M and a camber line slightly inclined toward the front in the rotational 15 direction M. The number of vanes 3 of the impeller 1 is set to a large value of, for example, 30 to 72 like in the above embodiments, and a ring body 20 having a predetermined width 20 H in the centrifugal direction is arranged on the peripheral portion of the ends of the vanes at the bellmouth side. In this embodiment, the end of the ring body 20 and the ends of the vanes 3 on the side of the bellmouth are inclined toward the hub 2 in the centrifugal direction like in Fig. 44. In 25 other respects, the structure of the eleventh embodiment is basically the same as the above embodiments. The centrifugal blower of this embodiment, which has the impeller 1 as described above formed in combination with 30 a bellmouth 5 like those of the above embodiments without a shroud, also has the advantages described below that are similar to those of the above embodiments. 47 Specifically, the presence of the ring body 20 causes the generation of the circulating flow f 2 that flows out from the outlet side of the impeller 1, flows back into the impeller 1, and passes the rear side of the air intake port 5 6 of the bellmouth 5. Therefore, the main air flow fi passing across the vanes 3 is effectively drawn toward the distal ends of the vanes 3 by the circulating flow f 2 . As a result, the air speed distribution in the exit portion of the vanes 3 is improved uniformly. This enhances the 10 aerodynamic performance and reduces operational noise. Moreover, since no shroud is required, the impeller 1 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity. 15 (Twelfth Embodiment) Figs. 53 and 54 show an impeller of a centrifugal blower according to a twelfth embodiment of the present 20 invention. As shown in Figs. 53 and 54, this centrifugal blower impeller 1 includes, for example, a disk-shaped hub 2 having a central portion to which a rotation shaft 4a of a motor 4 25 is connected and a plurality of vanes 3 arranged on the peripheral portion of the hub 2 at predetermined intervals in the circumferential direction. The impeller 1 is of a radial vane type (radial tip 30 fan type with an outlet angle G 2 of about 90 degrees) in which each vane 3 has a curved camber line recessed in the rotational direction. 48 The number of the vanes 3 of the impeller 1 is set to, for example, 20 to 50 like in the sixth, seventh, and eighth embodiments, and a ring body 20 having a predetermined width H in the centrifugal direction is arranged on the peripheral 5 portion of the ends of the vanes at the bellmouth side. In this embodiment, the end of the ring body 20 and the ends of the vanes 3 on the side of the bellmouth are inclined toward the hub 2 in the centrifugal direction like in Fig. 44. In other respects, the structure of the twelfth embodiment is 10 basically the same as the above embodiments. The centrifugal blower of this embodiment, which has the impeller 1 as described above formed in combination with a bellmouth 5 like those of the above embodiments without a 15 shroud, also has the advantages described below that are similar to those of the above embodiments. Specifically, the presence of the ring body 20 causes the generation of the circulating flow f 2 that flows out from 20 the outlet side of the impeller 1, flows back into the impeller 1, and passes the rear side of the air intake port 6 of the bellmouth 5. Therefore, main air flow fi passing across the vanes 3 is effectively drawn toward the distal ends of the vanes 3 by the circulating flow f 2 . As a result, 25 the air speed distribution in the exit portion of the vanes 3 is improved uniformly. This enhances the aerodynamic performance and reduces operational noise. Moreover, since no shroud is required, the impeller 1 30 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity. (Thirteenth Embodiment) 49 Figs. 55 to 58 show the structure of main parts of a centrifugal blower according to a thirteenth embodiment of the present invention. 5 As shown in Figs. 55 to 58, this centrifugal blower impeller 1 includes, for example, a disk-shaped hub 2 having central portion to which a rotation shaft 4a of a motor 4 is connected and a plurality of vanes 3 arranged on the 10 peripheral portion of the hub 2 at predetermined intervals in the circumferential direction. The vanes 3 of this impeller 1 are either forward inclined type vanes 3A (Fig. 57) in which the vane 3 is 15 entirely inclined toward the front at a predetermined angle in the rotational direction M or rearward inclined type vanes 3B (Fig. 58) inclined opposite the forward inclined type vanes. 20 Regardless of the type, the number of vanes 3 of the impeller 1 is set to a large value of, for example, 30 to 72, and a ring body 20 having a predetermined width H in the centrifugal direction is arranged on the peripheral portion of the ends of the vanes at the bellmouth side. In this 25 embodiment, the end of the ring body 20 and the ends of the vanes 3 on the side of the bellmouth are inclined toward the hub 2 along the centrifugal direction, as viewed from Fig. 55. In other respects, the structure of the thirteenth embodiment is basically the same as the above embodiments. 30 The centrifugal blower of this embodiment, which has the impeller 1 as described above formed in combination with a bellmouth 5 like those of the above embodiments without a 50 shroud, also has the advantages described below that are similar to those of the above embodiments. Specifically, the presence of the ring body 20 causes 5 the generation of the circulating flow f 2 that flows out from the outlet side of the impeller 1, flows back into the impeller 1, and passes the rear side of the air intake port 6 of the bellmouth 5. Therefore, main air flow fi passing across the vanes 3 is effectively drawn toward the distal 10 ends of the vanes 3 by the circulating flow f 2 . As a result, the air speed distribution in the exit portion of the vanes 3 is improved uniformly. This enhances the aerodynamic performance and reduces operational noise. Moreover, since no shroud is required, the impeller 1 can be molded 15 integrally. This simplifies the structure, reduces costs, and improves mass productivity. The centrifugal blower has unique advantages as described below in relation to the inner diameter Do of the 20 air intake port 6 in the bellmouth 5. (A) When the vanes 3 are forward inclined vanes 3A In this case, for example, as shown in Fig. 57, the 25 vanes 3 (3A) function to draw in circulating flow f 2 formed by the ring body 20. This generates a strong circulating flow f 2 . Even if the inner diameter Do of the air intake port 6 30 of the bellmouth 5 is enlarged as shown by reference numeral 6A in Fig. 55, the strong circulating flow f 2 will smoothly circulate near the ring body 20 without deeply entering the inner side of the vanes 3 (3A) . This achieves satisfactory 51 fan performance. (B) When the vanes 3 are rearward inclined vanes 3B 5 In this case, for example, as shown in Fig. 58, the vanes 3 (3B) function in a direction making it difficult to draw in the circulating flow f 2 formed by the ring body 20. Even if the inner diameter Do of the air intake port 6 of the bellmouth 5 is reduced as shown by reference numeral 6B in 10 Fig. 55, the circulating flow f 2 will smoothly circulate near the ring body 20 without deeply entering the inner side of the vanes 3 (3B). As a result, desirable blowing performance can be obtained. This achieves satisfactory fan performance. 15 (Fourteenth Embodiment) Figs. 59 and 60 show the structure of main parts of a centrifugal blower according to a fourteenth embodiment of the present invention. 20 As shown in Figs. 59 and 60, this centrifugal blower impeller 1 includes, for example, a disk-shaped hub 2 having a central portion to which a rotation shaft 4a of a motor 4 is connected and a plurality of vanes 3 arranged on the 25 peripheral portion of the hub 2 at predetermined intervals in the circumferential direction. The vanes 3 of this impeller 1 are either forward inclined type vanes 3A in which only the vane tips 3C are 30 inclined forward at a predetermined angle in the rotational direction M or rearward inclined type vanes 3B inclined opposite the forward inclined type vanes 3A (fold line L). 52 Regardless of the type, the number of vanes 3 of the impeller 1 is set to a large value of, for example, 30 to 72, and a ring body 20 having a predetermined width H in the centrifugal direction is arranged on the peripheral portion 5 of the ends of the vanes at the bellmouth side. In this embodiment, the end of the ring body 20 and the ends of the vanes 3 on the side of the bellmouth are inclined toward the hub 2 in the centrifugal direction, as viewed from Fig. 59. In other respects, the structure of the fourteenth 10 embodiment is basically the same as the above embodiments. The centrifugal blower of this embodiment shown in Fig. 59, which has the impeller 1 as described above formed in combination with a bellmouth 5 like those of the above 15 embodiments without a shroud, also has the advantages described below that are similar to those of the above embodiments. Specifically, the presence of the ring body 20 causes 20 the generation of the circulating flow f 2 that flows out from the outlet side of the impeller 1, flows back into the impeller 1, and passes the rear side of the air intake port 6 of the bellmouth 5. Therefore, the main air flow fi passing across the vanes 3 is effectively drawn toward the 25 distal ends of the vanes 3 by the circulating flow f 2 . As a result, the air speed distribution in the exit portion of the vanes 3 is improved uniformly. This enhances the aerodynamic performance and reduces operational noise. Moreover, since no shroud is required, the impeller 1 can be 30 molded integrally. This simplifies the structure, reduces costs, and improves mass productivity. The centrifugal blower described above has unique 53 advantages as described below in relation to the inner diameter Do of the air intake port 6 in the bellmouth 5. (A) When the vanes 3 are forward inclined vanes 3A 5 having vane tips 3C inclined forward in the rotational direction In this case, for example, as shown in Fig. 60, the vanes 3 (3A) function to draw in circulating flow f2 10 generated by the ring body 20. This forms a relatively strong circulating flow f 2 . Even if the inner diameter Do of the air intake port 6 of the bellmouth 5 is enlarged as shown by reference numeral 15 6A in Fig. 59, the strong circulating flow f 2 will smoothly circulate near the ring body 20 without deeply entering the inner side of the vanes 3 (3A). This achieves satisfactory fan performance. 20 (B) When the vanes 3 are rearward inclined vanes 3B having vane tips 3C inclined rearward in the rotational direction In this case, for example, as shown in Fig. 60, the 25 vanes 3 (3B) function in a direction making it difficult to draw in the circulating flow f 2 formed by the ring body 20. Even if the inner diameter Do of the air intake port 6 of the bellmouth 5 is reduced as shown by reference numeral 30 6B in Fig. 59, the circulating flow f 2 will smoothly circulate near the ring body 20 without deeply entering the inner side of the vanes 3 (3B). This achieves satisfactory fan performance. 54

Claims (20)

1. A centrifugal blower including an impeller (1) having a hub (2) with a central portion connected to a 5 rotation shaft (4a) of a motor (4), a plurality of vanes (3) arranged on a peripheral portion of the hub (2) at predetermined intervals in a circumferential direction, the vanes provided with front rims (3a) inclined toward the front in a rotational direction, and a bellmouth (5) 10 provided with an air intake port (6) arranged at an air intake side of the impeller, the centrifugal blower being characterized in that: a circulating flow (f 2 ) is generated to flow out from an outlet side of the impeller (1), flow back into the 15 impeller (1), and pass through a rear side of the air intake port (6) of the bellmouth (5).

2. A centrifugal blower including an impeller (1) having a hub (2) with a central portion connected to a 20 rotation shaft (4a) of a motor (4), a plurality of vanes (3) arranged on a peripheral portion of the hub (2) at predetermined intervals in a circumferential direction, the vanes provided with front rims (3a) neither inclined toward the front nor the rear in a rotational direction, and a 25 bellmouth (5) provided with an air intake port (6) arranged at an air intake side of the impeller, the centrifugal blower being characterized in that: a circulating flow (f 2 ) is generated to flow out from an outlet side of the impeller (1), flow back into the 30 impeller (1), and pass through the rear side of the air intake port (6) of the bellmouth (5).

3. The centrifugal blower according to claim 2, 55 characterized in that the vanes (3) in the impeller (1) are entirely inclined in the rotational direction.

4. The centrifugal blower according to claim 2, 5 characterized in that the vanes (3) in the impeller (1) are entirely inclined opposite the rotational direction.

5. - The centrifugal blower according to claim 1 or 2, characterized in that the vanes (3) in the impeller (1) 10 include vane tips inclined in the rotational direction.

6. The centrifugal blower according to claim 1 or 2, characterized in that the vanes (3) in the impeller (1) include vane tips inclined opposite the rotational direction. 15

7. The centrifugal blower according to any one of claims 1 to 6, characterized in that when an inner diameter of the air intake port (6) of the bellmouth (5) is represented by Do, an inner diameter of the vanes (3) in the 20 impellers (1) is represented by Di, and an outer diameter of the vanes (3) is represented by D 2 , 0<(Do-Di)/ (D 2 -Di)<0.6 is satisfied.

8. The centrifugal blower according to any one of 25 claims 1 to 6, characterized in that when an inner diameter of the air intake port (6) of the bellmouth (5) is represented by Do, the inner diameter of the vanes (3) in the impeller (1) is represented by D 1 , and the outer diameter of the vanes (3) is represented by D 2 , -0.3<(Do-D.)/(D 2 -Di)<0.3 30 is satisfied.

9. The centrifugal blower according to any one of claims 1 to 8, characterized in that a ring body (9), (20) 56 having a predetermined width in a centrifugal direction is attached to axial distal ends of the vanes (3) in the impeller (1). 5 10. The centrifugal blower according to claim 9, characterized in that when a width in the centrifugal direction of the ring body (20) is represented by H, and the outer diameter of the vanes (3) of the impeller (1) is represented by D 2 , 0.05<ki=H/D 2 <0.225 is satisfied.

10

11. The centrifugal blower according to any one of claims 1 to 10, characterized in that a diagonal diffuser (23) is arranged at the outlet side of the impeller (1) to guide air that is blown out of the impeller (1) diagonally 15 rearward.

12. The centrifugal blower according to any one of claims 1 to 10, characterized in that a diagonal centrifugal diffuser (23) is arranged at the outlet side of the impeller 20 (1) to guide air blown out of the impeller (1) in a centrifugal direction from a diagonal rear side.

13. The centrifugal blower according to any one of claims 1 to 12, characterized in that a circulation space 25 (S) is formed at a peripheral side of the air intake port (6) of the bellmouth (5) to allow passage of the circulating flow (f 2

) 14. The centrifugal blower according to any one of 30 claims 1 to 13, characterized in that when an exit side height of the vanes (3) in the impeller (1) is represented by B and an outer diameter of the vanes (3) is represented by D 2 , B/D 2 0.113 is satisfied. 57

15. The centrifugal blower according to any one of claims 1 to 13, characterized in that the hub (2) of the impeller (1) has an outer diameter D 3 that is smaller than 5 the outer diameter D 2 of the vanes (3).

16. The centrifugal blower according to claim 15, characterized in that when an exit side height of the vanes (3) of the impeller (1) is represented by B and an outer 10 diameter of the vanes (3) is represented by D 2 , B/D 2 0.08 is satisfied.

17. The centrifugal blower according to any one of claims 1 to 16, characterized in that the number of the 15 vanes (3) in the impeller (1) is 5 to 15.

18. The centrifugal blower according to any one of claims 1 to 16, characterized in that the number of the vanes (3) in the impeller (1) is 20 to 50. 20

19. The centrifugal blower according to any one of claims 2 to 16, characterized in that the number of the vanes (3) in the impeller (1) is 30 to 72. 25

20. An air conditioner including a heat exchanger (15) and a blower (X) arranged in an air duct (14) formed in a casing (13), the air conditioner being characterized in that the centrifugal blower according to any one of claims 1 to 19 is employed as the blower (X). 58