EP1783374A1 - Zentrifugalgebläse und klimaanlage mit zentrifugalgebläse - Google Patents

Zentrifugalgebläse und klimaanlage mit zentrifugalgebläse Download PDF

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Publication number
EP1783374A1
EP1783374A1 EP05765682A EP05765682A EP1783374A1 EP 1783374 A1 EP1783374 A1 EP 1783374A1 EP 05765682 A EP05765682 A EP 05765682A EP 05765682 A EP05765682 A EP 05765682A EP 1783374 A1 EP1783374 A1 EP 1783374A1
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EP
European Patent Office
Prior art keywords
vanes
impeller
centrifugal blower
bellmouth
centrifugal
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Application number
EP05765682A
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English (en)
French (fr)
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EP1783374A4 (de
Inventor
Kanjirou c/o DAIKIN INDUSTRIES LTD. KINOSHITA
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Daikin Industries Ltd
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Daikin Industries Ltd
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Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of EP1783374A1 publication Critical patent/EP1783374A1/de
Publication of EP1783374A4 publication Critical patent/EP1783374A4/de
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps

Definitions

  • the present invention relates to a centrifugal blower and an air conditioner having a centrifugal blower.
  • a typical well known centrifugal blower includes an impeller having a hub connected to a rotation shaft of a 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 (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 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).
  • Patent Publication 1 Japanese Laid-Open Patent Publication No. 11-101194
  • Patent Publication 2 Japanese Laid-Open Patent Publication No. 10-185238
  • 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 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 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.
  • 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 rotational direction of the impeller.
  • a sweep forward vane type centrifugal blower i.e., a sirocco fan
  • 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 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 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.
  • 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 impeller 1, passing through the rear side of the air intake port 6 of the bellmouth 5.
  • 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.
  • 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 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 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 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 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.
  • 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.
  • vanes 3 in the impeller 1 are entirely inclined in the rotational direction.
  • 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 .
  • vanes 3 in the impeller 1 may entirely be inclined opposite the rotational direction.
  • the vanes 3 function in the direction that makes it difficult to draw in the circulating flow f 2 generated by the ring body 20.
  • vanes 3 in the impeller 1 may include vane tips inclined in the rotational direction.
  • 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 .
  • vanes 3 in the impeller 1 may include vane tips inclined opposite the rotational direction.
  • the vanes 3 function in the direction making it difficult to draw in the circulating flow f 2 generated by the ring body 20.
  • an inner diameter of the air intake port 6 of the bellmouth 5 is represented by D 0
  • an inner diameter of the vanes 3 in the impellers 1 is represented by D 1
  • an outer diameter of the vanes 3 is represented by D 2 , 0 ⁇ (D 0 -D 1 )/(D 2 -D 1 ) ⁇ 0.6 may be satisfied.
  • the minimum specific noise Ks may be lowered, as shown in Fig. 4, when the number of the vanes 3 is small (for example, 5 to 15). This further improves aerodynamic performance and reduces operational noise.
  • the minimum specific noise Ks may be lowered, as shown in Fig. 14, when the number of the vanes 3 is large (for example, 30 to 50). This further improves the aerodynamic performance and reduces operational noise.
  • a ring body 9, 20 having a predetermined width in a centrifugal direction may be attached to axial distal ends of the vanes 3 in the impeller 1.
  • 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 flow and circulating flow and improves the fan performance and reduces noise.
  • 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.
  • the dynamic pressure in the air flow blown out from the impeller 1 efficiently returns to the static pressure. This greatly contributes to improvement of the performance (that is, high efficiency and low noise).
  • 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.
  • the air flow blown out from the impeller 1 efficiently returns to static 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 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.
  • the hub 2 of the impeller 1 has an outer diameter D 3 that is smaller than the outer diameter D 2 of the vanes 3.
  • an opening 22 is formed in a peripheral portion at the hub side of the vanes 3.
  • the number of the vanes 3 in the impeller 1 be 5 to 15.
  • the minimum specific noise Ks may be lowered even when the number of vanes 3 is small. This effectively improves the aerodynamic performance and reduces operational noise.
  • the number of the vanes 3 in the 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. This further effectively improves the aerodynamic performance and reduces operational noise.
  • the number of the vanes 3 in the impeller 1 be 30 to 72.
  • the maximum static pressure efficiency ratio may especially be effectively increased, and the minimum specific noise may be minimized. This further improves the aerodynamic performance and reduces operational noise.
  • the above centrifugal blower may be employed as the blower X.
  • the centrifugal blower effectively exhibits its operations and advantages. This greatly contributes to improvement of performance and cost reduction of the air conditioner.
  • Figs. 1 to 6 illustrate a centrifugal blower X 1 and an air conditioner Z 1 according to a first embodiment of the present invention.
  • the centrifugal blower X 1 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 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.
  • 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 is located rearward from an inner diameter end 3a of the vane 3 relative to the rotational direction M of the impeller 1.
  • a sweep back vane type i.e., a turbo fan type
  • the ratio of static pressure increase occupies a large proportion in the total pressure increase of the impeller. This eliminates the need 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 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 D 0 that is set to be greater than an inner diameter D 1 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 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 in Fig. 3(B), or a flared shape as shown in Fig. 3(C).
  • 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 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 f 1 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 speed distribution in the exit portions of the vanes 3, enhances the aerodynamic performance, and lowers the operational noise.
  • the integral molding of the impeller 1 is enabled. This lowers costs and provides high mass productivity.
  • Fig. 4 shows the results obtained. 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 Z 1 incorporating the centrifugal blower X 1 of this embodiment.
  • a heat exchanger 15 and the centrifugal blower X 1 are arranged in an air duct 14 for air flow W that is formed in a casing 13.
  • the motor fixing portion 7 for fixing the motor 4 is formed integrally with a top plate 13a of the casing 13.
  • This air conditioner Z 1 includes an intake grille 16, an air filter 17, a drain pan 18, and an air outlet port 19.
  • the centrifugal blower X 1 allows the centrifugal blower X 1 to effectively exhibit its advantageous effects. This greatly contributes to enhancement in the performance of the air conditioner Z 1 and reduction in costs. Additionally, the optimum diameter for the air intake port 6 may be set to be greater than that of a conventional one. This suppresses pressure loss in the air filter 17 or the like.
  • 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.
  • 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.
  • the 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 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.
  • the ring body 20 may be joined 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 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 .
  • 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 generation of the circulating flow f 2 .
  • 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), the generation of the circulating flow f 2 is enhanced.
  • 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 .
  • 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.
  • the generation of the circulating flow f 2 is enhanced.
  • 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 .
  • 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 the hub. In this case as well as in the case shown in Fig. 8(J), a smooth circulating flow f 2 is generated.
  • the hub 2 may include an inclined surface 2b at the region where the vanes 3 are 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 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 ring body 20 may be removed from the peripheral side.
  • Fig. 9 shows the results obtained.
  • Fig. 11 shows a ceiling-embedded air conditioner Z 2 incorporating the centrifugal blower X 2 of the second embodiment.
  • 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 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 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.
  • the centrifugal blower of the above embodiments is applied when the number of the vanes 3 is small (i.e., 5 to 15 vanes).
  • 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.
  • the centrifugal blower X 3 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 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.
  • 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 is located rearward from an inner diameter end 3a of the vane 3 relative to the rotational direction M of the impeller 1.
  • the ratio of static pressure increase occupies a large proportion in the total pressure increase of the impeller. This eliminates the need of a spiral scroll.
  • the number of vanes 3 is greater (for example, 30 to 50 vanes) than the numbers of vanes in the centrifugal blowers X 1 and X 2 of the first and second embodiments.
  • 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.
  • the impeller 1 of the third embodiment is provided with a ring body 20 having a predetermined width H in the centrifugal direction.
  • the ring body 20 is inclined toward the hub 2 in the centrifugal direction.
  • 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 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 take any of a straight shape, a wedge shape, and a flared shape.
  • the dimensions are set to satisfy -0.3 ⁇ (D 0 -D 1 )/(D 2 -D 1 ) ⁇ 0.3.
  • the number of the vanes 3 is 40.
  • Circulating flow f 2 is generated to flow out of the outlet side of the impeller 1 and 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 f 1 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 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.
  • Fig. 14 shows the results obtained. It can be seen from the results that satisfactory operational noise characteristics were obtained in the range -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 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 L/D 2 ⁇ 0.07 is satisfied, the minimum specific noise Ks increases drastically.
  • this embodiment is set to satisfy B/D 2 ⁇ 0.113.
  • This setting solves the problem of fluctuation in the air flow line f 1 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 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.
  • Fig. 18 shows a ceiling-embedded air conditioner Z 3 incorporating the centrifugal blower X 3 of this embodiment.
  • a heat exchanger 15 and the centrifugal blower 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, an air filter 17, a drain pan 18, and an air outlet port 19. This structure enables the centrifugal blower X 3 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 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.
  • each vane 3 in the impeller 1 may be inclined at substantially the same inclination angle as that of the ring body 20.
  • the relationship among D 0 , D 1 , D 2 , H, L, and B is the same as described above.
  • 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.
  • the relationship among D 0 , D 1 , D 2 , H, L, and B is the same as described before.
  • 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 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.
  • the air flow noise is reduced.
  • the relationship among D 0 , D 1 , D 2 , H, L, and B is the same as described before.
  • Fig. 22 shows a centrifugal blower X 4 according to a fourth embodiment of the present invention.
  • 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 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).
  • the structure and effects of the fourth embodiment are the same as those of the third embodiment and therefore will not be described.
  • this embodiment is set to satisfy B/D 2 ⁇ 0.08.
  • 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 f 1 at the exit side of the impeller 1, and provides 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 sharply.
  • each vane 3 of the impeller 1 may be inclined at substantially the same inclination angle as that of the ring body 20.
  • the relationship among D 0 , D 1 , D 2 , H, L, and B is the same as described before.
  • 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.
  • the relationship among D 0 , D 1 , D 2 , H, L, and B is the same as described before.
  • 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 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.
  • the relationship among D 0 , D 1 , D 2 , H, L, and B is the same as described before.
  • 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 arranged) is inclined.
  • the relationship among D 0 , D 1 , D 2 , H, L, and B is the same as described before.
  • 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 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.
  • the relationship among D 0 , D 1 , D 2 , H, L, and B is the same as described before.
  • centrifugal blower X 4 of the fourth embodiment may be incorporated in an air conditioner.
  • Fig. 29 shows a centrifugal blower X 5 according to a fifth embodiment of the present invention.
  • 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 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.
  • an opening 22 is formed in the hub side of the peripheral portion of the vanes 3.
  • each vane 3 in the impeller 1 may be inclined at substantially the same inclination angle as that of the ring body 20.
  • the relationship among D 0 , D 1 , D 2 , H, L, and B is the same as described before.
  • 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 towards the hub.
  • the relationship among D 0 , D 1 , D 2 , H, L, and B is the same as described before.
  • the centrifugal blowers of the third to the fifth embodiments employ a large number of the vanes 3 (i.e., 30 to 50 vanes).
  • centrifugal blower X 4 of to this embodiment may be incorporated in an air conditioner. It is also obvious that similar effects may be obtained by using a spiral casing.
  • the centrifugal blower X 5 shown in Fig. 32 is 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.
  • 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 guiding function of the ring body 20, and relatively small at the side of the hub 2.
  • 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 of the hub 2 and ultimately blown out from the outlet port in the centrifugal direction.
  • 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.
  • 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 diagonal centrifugal diffuser 23 (Fig. 34) with regard to the air speed distribution.
  • the comparison result is as described below.
  • the air flow deflected toward the hub 2 is further deflected rearward by passing through the diagonal passage in the diagonal centrifugal diffuser 23 and being directly blown out in the centrifugal direction.
  • the air speed distribution of the ultimately blown out air flow is greatly deflected toward the rear side.
  • 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.
  • the main air flow f 1 is drawn toward the distal end side of the vanes 3 by the circulating flow f 2 formed by the ring body 20.
  • the air speed distribution of the blown out air in the ring body 20 is great, and the air speed distribution is not necessarily uniform when the outlet port is viewed as a whole.
  • Figs. 36 and 37 show an impeller of a centrifugal blower according to a sixth embodiment of the present invention.
  • 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 peripheral portion of the hub 2 at predetermined intervals in the circumferential direction.
  • Each vane 3 of the impeller 1 has an inner diameter 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.
  • 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 example, 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 bellmouth.
  • 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.
  • the structure of the sixth embodiment is basically the same as the above embodiments.
  • 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 similar to those of the above embodiments.
  • 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 6 of the bellmouth 5. Therefore, main air flow f 1 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 aerodynamic performance and reduces operational noise.
  • the impeller 1 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity.
  • Figs. 38 and 39 show an impeller of a centrifugal blower according TO a seventh embodiment of the present invention.
  • 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 peripheral portion of the hub 2 at predetermined intervals in the circumferential direction.
  • 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 direction M of the impeller 1.
  • 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, 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 bellmouth.
  • 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.
  • the structure of the seventh embodiment is basically the same as the above embodiments.
  • 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 similar to those of the above embodiments.
  • 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 6 of the bellmouth 5. Therefore, main air flow f 1 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 aerodynamic performance and reduces operational noise.
  • the impeller 1 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity.
  • Figs. 40 and 41 show an impeller of a centrifugal blower according to a seventh embodiment of the present invention.
  • 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 peripheral portion of the hub 2 at predetermined intervals in the circumferential direction.
  • 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 rotational direction M of the impeller 1.
  • 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 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.
  • 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 along the centrifugal direction like those in Fig. 24.
  • the structure of the eighth embodiment is basically the same as the above embodiments.
  • 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 similar to those of the above embodiments.
  • 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 6 of the bellmouth 5. Therefore, the main air flow f 1 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 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.
  • the centrifugal blower used for the measurement has an impeller formed as shown Figs. 40 and 41.
  • Each vane 3 has an inlet angle ⁇ 1 of 25 degrees and an outlet angle ⁇ 2 of 50 degrees as shown in Fig. 42.
  • An inlet height B 1 and an outlet height B 2 of each vane 3 are 35 mm and 30 mm, respectively.
  • An inner diameter D 0 of the air intake port 6 of the bellmouth 25 is 130 mm
  • an inner diameter D 1 and an outer diameter D 2 of the vane 3 are 110 mm and 160 mm, respectively.
  • Figs. 45 and 46 show a centrifugal blower according to a ninth embodiment of the present invention.
  • 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 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 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.
  • 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 vanes at the bellmouth side.
  • 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.
  • the structure of the ninth embodiment is basically the same as the above embodiments.
  • 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 similar to those of the above embodiments.
  • 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 6 of the bellmouth 5. Therefore, main air flow f 1 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 aerodynamic performance and reduces operational noise.
  • the impeller 1 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity.
  • Figs. 47 and 48 show an impeller of a centrifugal blower according to a tenth embodiment of the present invention.
  • 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 peripheral portion of the hub 2 at predetermined intervals in the circumferential direction.
  • 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 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 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.
  • 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 in Fig. 44.
  • the structure of the tenth embodiment is basically the same as the above embodiments.
  • 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 similar to those of the above embodiments.
  • 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 6 of the bellmouth 5. Therefore, main air flow f 1 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 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.
  • the maximum static pressure efficiency ratio (reference value of 1.0) and minimum specific noise level ratio (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.
  • the centrifugal blower used for the measurement has an impeller formed as shown Figs. 47 and 48.
  • Each vane 3 has an inlet angle ⁇ 1 of 90 degrees and an outlet angle ⁇ 2 of 75 degrees as shown in Fig. 49.
  • An inlet height B 1 and an outlet height B 2 of each vane 3 are 25 mm and 20 mm, respectively.
  • An inner diameter D 0 of the air intake port 6 of the bellmouth 25 is 130 mm
  • an inner diameter D 1 and an outer diameter D 2 of the vanes 3 are 130 mm and 150 mm, respectively.
  • Figs. 51 and 52 show an impeller of a centrifugal blower according to a tenth embodiment of the present invention.
  • 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 peripheral portion of the hub 2 at predetermined intervals in the circumferential direction.
  • the impeller 1 is of a radial vane type (second 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 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 H in the centrifugal direction is arranged on the peripheral portion of the ends of the vanes at the bellmouth side.
  • 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.
  • the structure of the eleventh embodiment is basically the same as the above embodiments.
  • 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 similar to those of the above embodiments.
  • 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 6 of the bellmouth 5. Therefore, the main air flow f 1 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 aerodynamic performance and reduces operational noise.
  • the impeller 1 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity.
  • Figs. 53 and 54 show an impeller of a centrifugal blower according to a twelfth embodiment of the present invention.
  • 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 peripheral portion of the hub 2 at predetermined intervals in the circumferential direction.
  • the impeller 1 is of a radial vane type (radial tip fan type with an outlet angle ⁇ 2 of about 90 degrees) in which each vane 3 has a curved camber line recessed in the rotational direction.
  • 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 portion of the ends of the vanes at the bellmouth side.
  • 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.
  • the structure of the twelfth embodiment is basically the same as the above embodiments.
  • 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 similar to those of the above embodiments.
  • 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 6 of the bellmouth 5. Therefore, main air flow f 1 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 aerodynamic performance and reduces operational noise.
  • the impeller 1 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity.
  • Figs. 55 to 58 show the structure of main parts of a centrifugal blower according to a thirteenth embodiment of the present invention.
  • 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 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 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.
  • 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.
  • 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.
  • the structure of the thirteenth embodiment is basically the same as the above embodiments.
  • 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 similar to those of the above embodiments.
  • 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 6 of the bellmouth 5. Therefore, main air flow f 1 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 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.
  • the centrifugal blower has unique advantages as described below in relation to the inner diameter D 0 of the air intake port 6 in the bellmouth 5.
  • the 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 .
  • 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 D 0 of the air intake port 6 of the bellmouth 5 is reduced as shown by reference numeral 6B in 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.
  • Figs. 59 and 60 show the structure of main parts of a centrifugal blower according to a fourteenth embodiment of the present invention.
  • 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 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 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).
  • 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.
  • 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.
  • the structure of the fourteenth embodiment is basically the same as the above embodiments.
  • 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 embodiments without a shroud, also has the advantages described below that are similar to those of the above embodiments.
  • 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 6 of the bellmouth 5. Therefore, the main air flow f 1 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 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.
  • centrifugal blower described above has unique advantages as described below in relation to the inner diameter D 0 of the air intake port 6 in the bellmouth 5.
  • the vanes 3 (3A) function to draw in circulating flow f 2 generated by the ring body 20. This forms a relatively strong circulating flow f 2 .
  • 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
EP05765682A 2004-07-14 2005-07-14 Zentrifugalgebläse und klimaanlage mit zentrifugalgebläse Withdrawn EP1783374A4 (de)

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JP2004207288 2004-07-14
JP2004366076 2004-12-17
JP2005195654A JP3879764B2 (ja) 2004-07-14 2005-07-05 遠心送風機
PCT/JP2005/013039 WO2006006668A1 (ja) 2004-07-14 2005-07-14 遠心送風機および遠心送風機を備えた空気調和装置

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EP1783374A4 EP1783374A4 (de) 2010-02-24

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CN109958633B (zh) * 2017-12-26 2022-02-18 松下知识产权经营株式会社 多叶片离心风机

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JP2006194235A (ja) 2006-07-27
AU2005260828A1 (en) 2006-01-19
CN1985092B (zh) 2011-09-07
EP1783374A4 (de) 2010-02-24
US20070251680A1 (en) 2007-11-01
WO2006006668A1 (ja) 2006-01-19
CN1985092A (zh) 2007-06-20
JP3879764B2 (ja) 2007-02-14
AU2005260828B8 (en) 2009-01-29

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