+

WO2006006668A1 - Ventilateur centrifuge et climatiseur équipé d'un ventilateur centrifuge - Google Patents

Ventilateur centrifuge et climatiseur équipé d'un ventilateur centrifuge Download PDF

Info

Publication number
WO2006006668A1
WO2006006668A1 PCT/JP2005/013039 JP2005013039W WO2006006668A1 WO 2006006668 A1 WO2006006668 A1 WO 2006006668A1 JP 2005013039 W JP2005013039 W JP 2005013039W WO 2006006668 A1 WO2006006668 A1 WO 2006006668A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
blade
centrifugal blower
centrifugal
blades
Prior art date
Application number
PCT/JP2005/013039
Other languages
English (en)
Japanese (ja)
Inventor
Kanjirou Kinoshita
Original Assignee
Daikin Industries, Ltd.
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Daikin Industries, Ltd. filed Critical Daikin Industries, Ltd.
Priority to CN200580023831XA priority Critical patent/CN1985092B/zh
Priority to AU2005260828A priority patent/AU2005260828B8/en
Priority to US11/632,160 priority patent/US20070251680A1/en
Priority to EP05765682A priority patent/EP1783374A4/fr
Publication of WO2006006668A1 publication Critical patent/WO2006006668A1/fr

Links

Classifications

    • 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 equipped with the centrifugal blower.
  • a well-known centrifugal blower includes a hub connected to a rotating shaft of a motor, a shroud disposed to face the outer peripheral portion of the hub at a predetermined interval, and the shroud and the hub.
  • Some have an impeller composed of a plurality of blades arranged at a predetermined interval along the circumferential direction between the outer peripheral portion (see Patent Document 1).
  • a hub in which a rotating shaft of a motor is connected to an axial center portion, and an outer peripheral portion of the hub are erected at predetermined intervals along the circumferential direction.
  • an impeller comprising a plurality of blades, and a bell mouth having an air suction port is provided on the air suction side of the impeller (see Patent Document 2).
  • Patent Document 1 JP-A-11-101194.
  • Patent Document 2 JP-A-10-185238.
  • the present invention has been made in view of the above points, and is excellent in mass productivity and capable of cost reduction, and is a low-noise and high-efficiency centrifugal fan and an air conditioner including the centrifugal fan Is intended to provide.
  • a hub 2 in which a rotating shaft 4a of a motor 4 is connected to an axial center portion, and an outer peripheral portion of the hub 2 along a circumferential direction.
  • An impeller 1 comprising a plurality of blades 3 standing up at a predetermined interval and having a leading edge 3a inclined forward in the rotation direction is provided, and an air suction port 6 is provided on the air suction side of the impeller 1.
  • the wind speed distribution at the exit portion of the blade 3 is improved, and aerodynamic performance can be improved and operation noise can be reduced.
  • the impeller 1 can be integrally formed, cost can be reduced, and mass productivity is excellent.
  • a hub 2 in which the rotating shaft 4a of the motor 4 is coupled to the shaft center portion, and a large number of the hub 2 are set up at predetermined intervals in the circumferential direction.
  • the impeller 1 is composed of a blade 3 that has a leading edge 3a that is not inclined even if the front edge 3a is directed in either the forward or backward direction of rotation.
  • a centrifugal blower in which a bell mouth 5 having a suction port 6 is disposed, and is sucked into the impeller 1 again from the blowing side of the impeller 1 through the back side of the air suction port 6 in the bell mouth 5. Circulated flow f
  • a blade represented by a radial plate fan In the impeller 1 provided with a circulating flow f that is sucked into the impeller 1 again from the blowout side of the impeller 1 through the back side of the air suction port 6 in the bell mouth 5 is formed.
  • the impeller 1 can be integrally formed, cost can be reduced, and mass productivity can be improved.
  • each blade 3 sucks the circulating flow f formed by the ring body 20.
  • the entire blade 3 in the impeller 1 can be inclined in the counter-rotating direction, that is, inclined in the opposite direction with respect to the rotating direction.
  • the blade 3 sucks the circulating flow f formed by the ring body 20.
  • the blade tip of the blade 3 in the impeller 1 can be inclined along the rotation direction.
  • the blade 3 sucks the circulating flow f formed by the ring body 20.
  • each blade 3 absorbs the circulating flow f formed by the ring body 20.
  • the inner diameter of the air suction port 6 in the bell mouth 5 is D, and the impeller 1
  • the inner diameter of the air suction port 6 in the bell mouth 5 is D, and the impeller 1
  • the leading edge of the leading edge cannot effectively work, hindering the improvement of aerodynamic performance.
  • ring bodies 9 and 20 having a predetermined width in the centrifugal direction can be attached to the tip end in the axial direction of the blade 3 in the impeller 1.
  • the ring bodies 9 and 20 that rotate together with the impeller 1 act as a rotating disk, and the rotational flow is induced in the outlet flow of the blade 3 by the viscous action of the rotating disk.
  • fan performance can be improved and noise can be reduced by rectifying the blowout flow and rectifying the circulation flow.
  • the centrifugal body width of the ring body 20 is H, and the outer diameter of the blade 3 in the impeller 1 is D.
  • the minimum specific noise Ks can be kept low, and it is possible to further improve the aerodynamic performance and reduce the operating noise.
  • a mixed flow diffuser 23 for guiding the air flow from the impeller 1 to the oblique rear side may be provided on the outlet side of the impeller 1.
  • a mixed flow centrifugal diffuser 23 for guiding the flow of air blown from the impeller 1 in the centrifugal direction from the oblique rear side may be provided on the blow side of the impeller 1.
  • a through space S can also be formed. It becomes fruit.
  • the stream line f of the air flow fluctuates greatly, and finally the circulating flow f passes through the flow path between the blades 3.
  • the outer diameter of the hub 2 constituting the impeller 1 is smaller than the outer diameter D of each blade 3.
  • the opening 22 is formed in the outer peripheral portion of each blade 3 on the hub side, and particularly when the above-described mixed flow diffuser 23 or mixed flow centrifugal diffuser 23 is provided, the blade 3 The blowout resistance of the air flow blown out from the fan becomes small.
  • the number of the blades 3, 3, ... in the impeller 1 is 5 to 15.
  • the minimum specific noise Ks can be kept low, effectively improving aerodynamic performance and reducing operating noise. Can make noise.
  • the number of blades 3 in the impeller 1 may be 20 to 50.
  • the maximum static pressure efficiency ratio can be made high, while the minimum specific noise level can be kept low. It is possible to improve performance and reduce driving noise.
  • the number of blades 3 in the impeller 1 is desirably 30 to 72 U.
  • the centrifugal blower of the above aspect is adopted as the blower X. You can also.
  • Such a configuration greatly contributes to the improvement of performance and cost reduction as an air conditioner because the effective working effect possessed by the centrifugal fan can be exhibited.
  • FIG. 1 is a longitudinal sectional view of a centrifugal blower X that works on the first embodiment of the present invention.
  • FIG. 2 is a front view of an impeller in a centrifugal blower X that is effective in the first embodiment.
  • FIG. 3 ( ⁇ ), ( ⁇ ), and (C) are three types of modifications of the centrifugal blower X that is useful for the first embodiment.
  • FIG. 6 is a characteristic diagram showing a change in minimum specific noise Ks with respect to D).
  • FIG. 5 (A) is a cross-sectional view of the main part showing the case of k ⁇ 0, and (B) is a cross-sectional view of the main part showing the case of k ⁇ 0.6.
  • FIG. 6 Vertical view of air conditioner Z incorporating centrifugal blower X, which is powerful in the first embodiment
  • 1 1 is a cross-sectional view.
  • FIG. 7 is a longitudinal sectional view of a centrifugal blower X that works on the second embodiment.
  • FIG. 8 (A) to (L) are modified examples of the centrifugal blower X that is useful for the second embodiment of the present invention.
  • 2 2 is a characteristic diagram showing changes in low specific noise ks.
  • FIG. 13 is a front view of an impeller in a centrifugal blower X that works on the third embodiment.
  • FIG. 6 is a characteristic diagram showing a change in minimum specific noise Ks with respect to D).
  • FIG. 1 A first figure.
  • FIG. 18 Vertical of air conditioner Z incorporating centrifugal blower X, which is powerful in the third embodiment
  • 3 3 is a sectional view.
  • ⁇ 24] A semi-longitudinal sectional view showing a modified example I of the centrifugal blower X that works on the fourth embodiment.
  • 5 ⁇ 31] is a semi-longitudinal sectional view showing a modified example II of the centrifugal blower X that works on the fifth embodiment.
  • FIG. 1 A first figure.
  • FIG.33 Modified example of centrifugal blower X that is useful for the fifth embodiment.
  • FIG. 1 A first figure.
  • Centrifugal blower powering the fifth embodiment is another contrast with modification III of X
  • FIG. 37 is a longitudinal sectional view showing a configuration of a centrifugal blower that works on the sixth embodiment.
  • FIG. 39 is a longitudinal sectional view showing a configuration of a centrifugal blower that works on the seventh embodiment.
  • ⁇ 40 It is a horizontal sectional view showing a configuration of a centrifugal blower that works on the eighth embodiment.
  • ⁇ 41 It is a longitudinal sectional view showing a configuration of a centrifugal blower that works on the eighth embodiment.
  • FIG. 42 is a horizontal sectional view showing a configuration of a main part of a test example of a centrifugal blower useful for the eighth embodiment.
  • FIG. 43 is a graph showing the relationship between the performance of the test example of the centrifugal blower according to the eighth embodiment and the number of blades.
  • FIG. 44 is a semi-longitudinal sectional view of a test example showing the configuration of a centrifugal blower according to an eighth embodiment.
  • FIG. 45 is a horizontal sectional view showing a configuration of a centrifugal blower that works on the ninth embodiment.
  • FIG. 46 is a longitudinal sectional view showing a configuration of a centrifugal blower that works on the ninth embodiment.
  • FIG. 47 is a horizontal sectional view showing a configuration of a centrifugal blower that is effective in the tenth embodiment.
  • FIG. 48 is a longitudinal sectional view showing a configuration of a centrifugal fan that is useful for the tenth embodiment.
  • FIG. 49 is a horizontal sectional view showing a configuration of a main part of a test example of a centrifugal blower useful for the tenth embodiment.
  • FIG. 50 is a graph showing the performance of a test example of the centrifugal fan according to the tenth embodiment in relation to the number of blades.
  • FIG. 51 is a horizontal sectional view showing the structure of a centrifugal blower that works in the eleventh embodiment.
  • FIG. 52 is a longitudinal sectional view showing the structure of a centrifugal blower that works in an eleventh embodiment.
  • FIG. 53 is a horizontal sectional view showing the structure of a centrifugal blower that is powerful in the twelfth embodiment.
  • FIG. 54 is a longitudinal sectional view showing the structure of a centrifugal blower that is powerful in the twelfth embodiment.
  • FIG. 55 is a semi-longitudinal sectional view showing the structure of a centrifugal blower that works in the thirteenth embodiment.
  • FIG. 56 is a semi-longitudinal sectional view showing a configuration of a main part of a centrifugal blower working on a thirteenth embodiment.
  • FIG. 57 is a horizontal sectional view showing the structure and operation of the main part of the centrifugal blower working on the thirteenth embodiment.
  • FIG. 58 is a horizontal sectional view showing the structure and operation of the main part of the centrifugal blower working on the thirteenth embodiment.
  • FIG. 59 is a semi-longitudinal sectional view showing the configuration of a centrifugal fan that is useful for the fourteenth embodiment.
  • FIG. 60 is a horizontal sectional view showing the structure and operation of the essential parts of a centrifugal blower useful for a fourteenth embodiment.
  • (First embodiment) 1 to 6 show the centrifugal fan X and the centrifugal fan X according to the first embodiment of the present invention.
  • Air conditioner z is shown.
  • the centrifugal blower X has a rotating shaft 4a of the motor 4 at the shaft center.
  • a disk-shaped hub 2 is connected to a disk-shaped hub 2 and a plurality of blades 3 erected at predetermined intervals in the circumferential direction on the outer periphery of the hub 2.
  • a bell mouth 5 having an air suction port 6 is disposed on the air suction side of 1, and
  • the impeller 1 has its leading edge inclined forward in the rotational direction, and the outer diameter side end portion 3b of each blade 3 is located closer to the impeller 1 than the inner diameter side end portion 3a. It is a swept-blade type (that is, a turbofan type) located on the rear side of the rotational direction M. In this way, since the ratio of the static pressure increase to the total pressure increase of the impeller 1 is large, the spiral scroll becomes unnecessary.
  • a concave portion 2 a for accommodating the motor 4 is formed in the axial center portion of the hub 2.
  • the motor fixing part 7 fixes the motor 4.
  • the bearing boss 8 pivots the rotating shaft 4a of the motor 4! /.
  • the reinforcing ring 9 connects the tip ends of each blade 3 in the axial direction.
  • the inner diameter D of the air suction port 6 of the bell mouth 5 is the same as that of the impeller 1.
  • a distribution space S is formed on the outer peripheral side), and is sucked into the impeller 1 again from the blowout side of the impeller 1 through the back side of the air suction port 6 in the bell mouth 5.
  • the shape of the air suction port 6 in the bell mouth 5 may be a straight shape as shown in FIG. 3 (A) or a wedge shape as shown in FIG. 3 (B). As shown in Fig. 3 (C), a flare shape may be used.
  • the inner diameter of the air inlet 6 in the bell mouth 5 is D
  • the reinforcing rib 9 is the center, and the outer periphery of the reinforcing rib 9 is bent from the outlet side of the impeller 1.
  • a circulating flow f is formed which is sucked into the impeller 1 again through the back side of the air inlet 6 in the lumouth 5. Therefore, the air passing through the blade 3 after being sucked in from the air suction port 6
  • the main flow f is attracted to the tip side of the blade 3 by the circulating flow f, and the outlet portion of the blade 3
  • the wind speed distribution in minutes can be improved, and aerodynamic performance can be improved and driving noise can be reduced. Since the shroud does not require a shroud, the impeller 1 can be integrally formed, and the cost can be reduced and the mass productivity is excellent.
  • the minimum specific noise Ks can be kept low, and it is possible to further improve the aerodynamic performance and lower the operating noise.
  • the inner diameter of the blade 3 in the centrifugal blower X that is useful for the present embodiment is D, the blade
  • the outer diameter of 3 is D
  • the inner diameter of the air inlet 6 is D
  • the suction side center Q force of the air inlet 6 is diagonal.
  • FIG. 6 shows a ceiling-embedded air incorporating a centrifugal blower X that can be used in the present embodiment.
  • a harmony device z is shown.
  • the heat exchanger 15 and the centrifugal fan X are disposed in the air flow path 14 of the air flow W formed in the casing 13, and the motor fixing portion 7 that fixes the motor 4 is provided on the casing 13.
  • the optimum diameter of the suction port 6 can be made larger than that of the conventional one, and the pressure loss in the air filter 17 or the like can be kept small.
  • FIGS. 7 and 11 show the centrifugal fan X and the centrifugal fan X according to the second embodiment of the present invention.
  • Air conditioner Z is shown.
  • the impeller 1 in the centrifugal blower X is provided with the reinforcing belt in the first embodiment.
  • a ring body 20 having a predetermined width H in the centrifugal direction is attached.
  • Other configurations, functions, and effects are the same as those in the first embodiment, and a description thereof will be omitted.
  • the ring body 20 can have various shapes as shown in FIGS. 8 (A) to (L).
  • the following is just an example, and it should be noted that shapes other than those shown in the figures can be used! ⁇ .
  • the ring body 20 may be joined to the axial end face of the blade 3, and as shown in FIG. 8 (B), the ring body 20 is anti-hub.
  • the ring body 20 may be installed in a state inclined to the hub side as shown in Fig. 8 (D).
  • the end of the ring body 20 in the centrifugal direction may be an arcuate surface 20a, and the end of the ring body 20 in the centrifugal direction may be an arcuate surface 20a. It may be attached in a state of being curved and inclined toward the opposite hub side. In this case, the formation of the circulation flow f is promoted by the Coanda effect.
  • the surface of the ring body 20 on the side opposite to the hub may be a recess 20b.
  • the formation of the circulation flow f is promoted because a negative pressure is generated in the recess 20b.
  • the surface of the ring body 20 on the side opposite to the hub may be a recess 20b and attached to the hub in an inclined state. Also in this case, the formation of the circulation flow f is promoted as in the case shown in FIG. In addition, as shown in FIG.
  • the surface on the side of the hub may be a recess 20c. In this case, since a negative pressure is generated in the recess 20c, the formation of the circulating flow f is promoted.
  • the hub side surface of the ring body 20 is formed as a recess 20c and the hub side It may be attached in an inclined state. Also in this case, the formation of the circulating flow f is promoted as in the case shown in FIG. Also, as shown in Fig. 8 (I), the hub side surface of the ring body 20 is formed as a recess 20c and the hub side It may be attached in an inclined state. Also in this case, the formation of the circulating flow f is promoted as in the case shown in FIG. Also, as shown in Fig. 8
  • It may be formed of a member having a comparatively thick thickness, and the arc surfaces 20d and 20e may be formed on the attachment portion side and the centrifugal end portion side, respectively. In this case, a smooth circulation flow f is formed.
  • an inclined surface 2b inclined to the anti-wing root side is formed at a portion where the blade 3 is erected, while the ring body 20 is relatively formed.
  • the outer diameter of the blade 3 in the centrifugal blower X that is useful for this embodiment is D, the ring
  • the distance between the ring body 20 and the bell mouth 5 is L, and the minimum specific noise with respect to the variable LZD.
  • FIG. 11 shows a ceiling-embedded air incorporating a centrifugal blower X that can be used in the present embodiment. Harmonic device Z is shown. In this case, the flow of the air flow W formed in the casing 13
  • a heat exchanger and a centrifugal blower X are arranged in the air passage 14 to fix the motor 4 that fixes the motor 4.
  • the fixed portion 7 is integrated with the top plate 13 a of the casing 13.
  • Air conditioner Z Air conditioner Z
  • the air conditioner Z can be used because the effective effects of the centrifugal fan X can be exhibited.
  • the diameter can be made larger than the conventional one, and the pressure loss in the air filter 17 can be kept small.
  • the present invention is applied to one having a small number of blades 3 (that is, 5 to 15).
  • FIGS. 12 to 16 show the centrifugal fan X and the third preferred embodiment of the present invention.
  • the centrifugal blower X has a rotating shaft of the motor 4 at the shaft center.
  • a bell mouth 5 having an air suction port 6 is disposed on the air suction side of the impeller 1.
  • the impeller 1 has its leading edge inclined forward in the rotational direction, and the outer diameter side end 3b of each blade 3 is closer to the impeller 1 than the inner diameter side end 3a.
  • a swept wing type ie, turbofan type located on the rear side of the rotational direction M.
  • the spiral scroll can be dispensed with.
  • the number of blades 3 is the first and the second.
  • a concave portion 2a for accommodating the motor 4 is formed in the axial center portion of the hub 2.
  • the motor fixing part 7 fixes the motor 4.
  • the bearing boss 8 pivotally supports the rotating shaft 4 a of the motor 4.
  • the centrifugal method is the same as in the second embodiment.
  • a ring body 20 having a predetermined width H is attached in the direction.
  • the ring body 20 has a shape that inclines toward the hub 2 as it applies force in the centrifugal direction.
  • a circulation space S is formed on the back side of the bell mouth 5 (in other words, on the outer peripheral side), and the back side of the air inlet 6 in the bell mouth 5 from the blowing side of the impeller 1 The circulating flow sucked into the impeller 1 again through
  • the shape of the air suction port 6 in the bell mouth 5 may be a wedge shape or a flare shape, which may be a straight shape.
  • the inner diameter of the air suction port 6 in the bell mouth 5 is D
  • the number is 40.
  • the wind speed distribution is improved, and aerodynamic performance can be improved and driving noise can be reduced.
  • the shroud is unnecessary, the impeller 1 can be integrally formed, which can reduce the cost and is excellent in mass productivity.
  • the minimum specific noise Ks can be kept low, further improving the aerodynamic performance and lowering the operating noise.
  • —0. 3 ⁇ k (D -D) / (D-
  • the inner diameter of the blade 3 in the centrifugal blower X that is useful in the present embodiment is D, and the blade
  • the outer diameter of 3 is D
  • the inner diameter of the air inlet 6 is D
  • the suction side central force of the air inlet 6 is diagonal 4
  • centrifugal blower X In centrifugal blower X
  • Figure 15 shows the relationship between the outer diameter D of the blade 3 and the distance L between the ring body 20 and the bell mouth 5
  • the minimum specific noise Ks can be kept low in the range of LZD ⁇ 0.07.
  • BZD ⁇ 0.113 is set.
  • FIG. 18 shows a ceiling-embedded air incorporating a centrifugal blower X that is useful for the present embodiment.
  • Harmonic device Z is shown.
  • the flow of the air flow W formed in the casing 13 A heat exchanger and a centrifugal blower X are arranged in the air passage 14 to fix the motor 4 that fixes the motor 4.
  • the fixed portion 7 is integrated with the top plate 13 a of the casing 13.
  • Air conditioner Z is suction drip
  • the appropriate aperture can be made larger than that of the conventional one, and the pressure loss in the air filter 17 can be suppressed to a small extent.
  • each blade 3 in the impeller 1 may be inclined at substantially the same inclination angle as the inclination angle of the ring body 20. Even in this case, D, D,
  • each blade 3 in the impeller 1 is inclined at an inclination angle substantially the same as the inclination angle of the ring body 20, and the inlet side end portion of each blade 3 is connected to the hub. Try to tilt the impeller 1 so that it approaches the centripetal direction of the impeller 1 as you move to the side. Even in this case, the relationship between D, D, D, H, L, and B is the same as described above.
  • each blade 3 in the impeller 1 is inclined at an inclination angle substantially the same as the inclination angle of the ring body 20, and the inlet side end portion of each blade 3 is connected to the hub. It may be inclined to approach the centripetal direction of the impeller 1 as it is directed toward the side, and a selection 21 may be formed at the inlet side end. In this way, the blowing sound is reduced because the formation of the boundary layer on the blade surface is suppressed.
  • FIG. 22 shows a centrifugal blower X that can be used in the fourth embodiment of the present invention.
  • the outer diameter D of the hub 2 constituting the impeller 1 is set smaller than the outer diameter D of each blade 3.
  • BZD ⁇ 0.08 is set.
  • each blade 3 in the impeller 1 may be inclined at substantially the same inclination angle as the inclination angle of the ring body 20. Even in this case, D, D,
  • each blade 3 in the impeller 1 is inclined at substantially the same inclination angle as the inclination angle of the ring body 20, and the inlet side end portion of each blade 3 is connected to the hub.
  • the relationship between D, D, D, H, L, and B is the same as described above.
  • each blade 3 in the impeller 1 is inclined at substantially the same inclination angle as the inclination angle of the ring body 20, and the inlet side end portion of each blade 3 is connected to the hub. It may be inclined to approach the centripetal direction of the impeller 1 as it is directed toward the side, and a selection 21 may be formed at the inlet side end. In this way, the blowing sound is reduced because the formation of the boundary layer on the blade surface is suppressed.
  • the impeller 1 may be a mixed flow fan type in which the outer peripheral side of the hub 2 (that is, the portion where the blade 3 is provided) is inclined. Even in this case, D, D, D
  • the impeller 1 is a mixed flow fan type in which the outer peripheral side of the hub 2 (that is, the portion where the blade 3 is provided) is inclined, and the inlet side end of each blade 3 is connected to the hub side. Try to tilt it so that it approaches the centripetal direction of the impeller 1 as you go. Even in this case, the relationship between D, D, D, H, L, and B is the same as described above.
  • centrifugal blower X that is useful for the present embodiment can also be incorporated into the air conditioner.
  • FIG. 29 shows a centrifugal blower X that can be used in the fifth embodiment of the present invention.
  • the outer diameter D of the hub 2 constituting the impeller 1 is set smaller than the outer diameter D of each blade 3.
  • a mixed flow centrifugal diffuser 23 is provided on the blowout side of the impeller 1 to guide the blown air flow from the impeller 1 from the obliquely rear side to the centrifugal direction.
  • an opening 22 is formed in the outer peripheral portion of each blade 3 on the hub side, and the blowing resistance force S of the air flow blown from the blade 3 is reduced, and the air blown from the impeller 1 is reduced. It is possible to efficiently recover the static pressure of the dynamic pressure in the flow and improve the performance (that is High efficiency, low noise).
  • Other configurations and operational effects are the same as those in the third embodiment, and thus description thereof is omitted.
  • each blade 3 in the impeller 1 may be inclined at substantially the same inclination angle as the inclination angle of the ring body 20. Even in this case, D
  • each blade 3 in the impeller 1 is inclined at substantially the same inclination angle as the inclination angle of the ring body 20, and the inlet side end portion of each blade 3 is connected to the hub. Try to tilt the impeller 1 so that it approaches the centripetal direction of the impeller 1 as you move to the side. Even in this case, the relationship between D, D, D, H, L, and B is the same as described above.
  • the present invention is applied to one having a large number of blades 3, 3, ... (ie, 30 to 50).
  • the centrifugal blower X in FIG. 32 is a blade of the centrifugal blower X according to the third embodiment described above.
  • a mixed-flow centrifugal diffuser 23 similar to that shown in FIGS. 29 to 31 is provided for the structure of the car and the bell mouth.
  • centrifugal fan X according to the modified example I of the third embodiment shown in Fig. 19 (Fig. 33) and the conventional centrifugal fan with a shroud are mixed with a centrifugal flow centrifugal separator.
  • the ring body 20 is provided on the outer periphery of the tip end in the axial direction of the blade 3 as described above, and the main flow is generated by the circulating flow f formed by the ring body 20 as described above.
  • the noise reduction effect is shown in Fig. 34 because the air velocity distribution of the air flow finally blown out becomes uniform throughout the whole as shown in Fig. 35. It is much larger than the conventional centrifugal blower with shroud.
  • FIG. 36 and FIG. 37 show an impeller of a centrifugal blower that can be used in the sixth embodiment of the present invention.
  • the impeller 1 of this centrifugal blower includes a disk-shaped hub 2 in which the rotating shaft 4a of the motor 4 is connected to the shaft center, and the hub 2 And a plurality of blades 3 erected at predetermined intervals along the circumferential direction.
  • Each blade 3 of the impeller 1 has an inner diameter side end 3a that is a front edge thereof inclined forward in the rotation direction, and an outer diameter side end 3b that is a rear edge is an inner diameter side end 3a. It is located behind the impeller 1 in the rotational direction M, and the camber line is regarded as a swept wing type (so-called turbofan type) convex in the rotational direction!
  • the number of blades 3 of the impeller 1 is set to 20 to 50, for example, and a ring body 20 having a predetermined width H in the centrifugal direction is attached to the outer periphery of the bell mouth side end. It has been.
  • the bell mouth side end portions of the ring body 20 and the blades 3 are each configured to incline toward the hub 2 according to the directional force in the centrifugal direction, as in FIG.
  • Other configurations are basically the same as those of the above-described embodiments.
  • Such an impeller 1 is configured in combination with a bell mouth 5 similar to those of the above-described embodiments without providing a shroud. Even if the centrifugal blower of this embodiment is used, the following beneficial effects similar to those of the above embodiments can be obtained.
  • the presence of the ring body 20 forms a circulating flow f that is sucked into the impeller 1 again from the blowout side of the impeller 1 through the back side of the air suction port 6 in the bell mouth 5.
  • the impeller 1 can be integrally formed, the structure can be simplified, the cost can be reduced, and the mass productivity can be improved.
  • FIG. 38 and FIG. 39 show an impeller of a centrifugal blower that is effective in the seventh embodiment of the present invention.
  • the impeller 1 of the centrifugal blower includes a disk-shaped hub 2 in which a rotating shaft 4a of a motor 4 is connected to an axial center portion, and an outer peripheral portion of the hub 2. Consists of a plurality of blades 3 standing at predetermined intervals in the circumferential direction
  • Each blade 3 of the impeller 1 has an inner diameter side end portion 3a that is a front edge thereof inclined forward in the rotation direction, and an outer diameter side end portion 3b that is a rear edge is an inner diameter side end portion 3a. It is located behind the impeller 1 in the rotational direction M, and the camber line is recessed in the rotational direction. Untyped).
  • the number of blades 3 of the impeller 1 is set to 20 to 50, for example, and a ring body 20 having a predetermined width H in the centrifugal direction is attached to the outer periphery of the bell mouth side end. It has been.
  • the bell mouth side end portions of the ring body 20 and the blades 3 are each configured to incline toward the hub 2 according to the directional force in the centrifugal direction, as in FIG.
  • Other configurations are basically the same as those of the above-described embodiments.
  • Such an impeller 1 is configured in combination with a bell mouth 5 similar to those of the above-described embodiments without providing a shroud. Even if the centrifugal blower of this embodiment is used, the following beneficial effects similar to those of the above embodiments can be obtained.
  • the presence of the ring body 20 forms a circulating flow f that is sucked into the impeller 1 again from the outlet side of the impeller 1 through the back side of the air inlet 6 in the bell mouth 5.
  • the impeller 1 can be integrally formed, the structure can be simplified, the cost can be reduced, and the mass productivity can be improved.
  • FIG. 40 and FIG. 41 show an impeller of a centrifugal blower that can be used in the eighth embodiment of the present invention.
  • the impeller 1 of the centrifugal blower includes a disc-shaped hub 2 having a shaft 4 connected to the rotating shaft 4a of the motor 4, and an outer peripheral portion of the hub 2. It consists of a plurality of blades 3 erected at predetermined intervals along the circumferential direction.
  • Each blade 3 of the impeller 1 has an inner diameter side end portion 3a that is a front edge thereof inclined forward in the rotation direction, and an outer diameter side end portion 3b that is a rear edge is an inner diameter side end portion 3a. It is positioned behind the impeller 1 in the rotational direction M, and the camber line is a receding blade type (so-called turbofan type) with a straight line.
  • the number of blades 3 of the impeller 1 is set to a large number of, for example, 20 to 50, and a ring body having a predetermined width H in the centrifugal direction on the outer periphery of the bell mouth side end portion thereof With 20 It is installed.
  • the bell mouth side end portions of the ring body 20 and the blade 3 are configured to incline toward the hub 2 side as they are directed in the centrifugal direction, respectively, as in FIG. .
  • Other configurations are basically the same as those of the above-described embodiments.
  • the presence of the ring body 20 forms a circulating flow f that is sucked into the impeller 1 again from the blowout side of the impeller 1 through the back side of the air suction port 6 in the bell mouth 5.
  • the wind speed distribution at the exit of the blades 3 is improved evenly, improving aerodynamic performance and lowering operating noise.
  • the impeller 1 can be integrally formed, the structure can be simplified and the cost can be reduced, and the mass productivity can be improved.
  • each blade 3 As described above is positioned behind the rotational direction M of the impeller 1 with respect to the inner diameter side end 3a, and the camber line is a receding blade having a linear shape.
  • the centrifugal blower used for the measurement has the impeller configuration shown in FIGS. 40 and 41.
  • FIG. 45 and FIG. 46 show a centrifugal blower that can be used in the ninth embodiment of the present invention.
  • the impeller 1 of this centrifugal blower includes a disc-shaped hub 2 in which the rotating shaft 4a of the motor 4 is coupled to the shaft center, and a circle on the outer periphery of the hub 2. It is composed of a plurality of blades 3 erected at predetermined intervals along the circumferential direction.
  • Each blade 3 of the impeller 1 has an inner diameter side end portion 3a which is a leading edge thereof, which is not inclined in any direction forward or backward in the rotational direction M, and the camber line is in the radial direction. It is a radial wing type (so-called radial plate fan type) that extends in a straight line.
  • the number of blades 3 of the impeller 1 is set to a large number of, for example, 30 to 72, and a ring body having a predetermined width H in the centrifugal direction on the outer periphery of the bell mouth side end. 20 is attached.
  • the bell mouth side end portions of the ring body 20 and the blades 3 are configured to incline toward the hub 2 side as they are directed in the centrifugal direction, respectively, as in FIG. 44 described above. Yes.
  • Other configurations are basically the same as those of the above-described embodiments.
  • the presence of the ring body 20 forms a circulating flow f that is sucked into the impeller 1 again from the blowout side of the impeller 1 through the back side of the air suction port 6 in the bell mouth 5.
  • the wind speed distribution at the exit part of blade 3 is improved evenly and aerodynamics It is possible to improve performance and reduce driving noise.
  • the impeller 1 can be integrally formed, and the cost can be greatly reduced by simplifying the structure and improving mass production.
  • FIGS. 47 and 48 show a centrifugal fan blade wheel that can be used in the tenth embodiment of the present invention.
  • the impeller 1 of this centrifugal blower includes a disk-shaped hub 2 in which the rotating shaft 4a of the motor 4 is connected to the shaft center portion, and an outer peripheral portion of the hub 2. It consists of a plurality of blades 3 erected at predetermined intervals along the circumferential direction.
  • Each blade 3 of the impeller 1 has an inner diameter side end portion 3a that is a leading edge thereof that is not inclined in the forward or backward direction of the rotational direction M, and the camber line is in the rotational direction M. It is a radial blade type that is slightly inclined backward (the first variation of the radial plate fan).
  • the number of blades 3 of the impeller 1 is set to a large number of, for example, 30 to 72, and a ring body having a predetermined width H in the centrifugal direction on the outer periphery of the bell mouth side end portion thereof 20 is attached.
  • the ring mouth side end portions of the ring body 20 and the blades 3 are formed so as to incline toward the hub 2 side in the centrifugal direction as in the case of FIG.
  • Other configurations are basically the same as those of the above-described embodiments.
  • the presence of the ring body 20 forms a circulating flow f that is sucked into the impeller 1 again from the blowout side of the impeller 1 through the back side of the air suction port 6 in the bell mouth 5.
  • the wind speed distribution at the exit of the blades 3 is improved evenly, improving aerodynamic performance and lowering operating noise. Since no shroud is required, the impeller 1 can be integrally molded, and the simplification of the structure and the improvement of mass productivity The cost can be reduced and the mass productivity is excellent.
  • FIG. 51 and FIG. 52 show a centrifugal fan blade wheel that can be used in the eleventh embodiment of the present invention.
  • the impeller 1 of this centrifugal blower includes a disc-shaped hub 2 having a shaft 4 connected to a rotating shaft 4a of a motor 4, and an outer peripheral portion of the hub 2. It consists of a plurality of blades 3 erected at predetermined intervals along the circumferential direction.
  • Each blade 3 of the impeller 1 has an inner diameter side end portion 3a which is a front edge thereof, which is not inclined in any direction forward or backward in the rotational direction M, and the camber line is forward in the rotational direction M. It is regarded as a radial wing type (second variation of the radial plate fan) The
  • the number of blades 3 of the impeller 1 is set to a large number of, for example, 30 to 72 as described above, and a predetermined width H in the centrifugal direction is provided on the outer periphery of the bell mouth side end portion.
  • a ring body 20 is provided.
  • the end portions on the bell mouth side of the ring body 20 and the blades 3 are formed so as to be inclined toward the hub 2 side in the centrifugal direction as in the case of FIG.
  • Other configurations are basically the same as those of the above-described embodiments.
  • the presence of the ring body 20 forms a circulating flow f that is sucked into the impeller 1 again from the blowout side of the impeller 1 through the back side of the air suction port 6 in the bell mouth 5.
  • the impeller 1 can be integrally formed, and the cost can be greatly reduced by simplifying the structure and improving mass productivity.
  • FIG. 53 and FIG. 54 show a centrifugal fan blade wheel that can be used in the twelfth embodiment of the present invention.
  • the impeller 1 of this centrifugal blower includes a disk-shaped hub 2 in which the rotating shaft 4a of the motor 4 is connected to the shaft center, and the hub 2 And a plurality of blades 3 erected along the circumferential direction along the circumferential direction at a predetermined interval.
  • Each blade 3 of the impeller 1 is of a radial blade type (radial tip fan type with an exit angle 0 of about 90 °) in which the camber line has a concave curve in the rotational direction.
  • the number of blades 3 of the impeller 1 is set to, for example, 20 to 50, as in the sixth, seventh, and eighth embodiments.
  • a ring body 20 having a predetermined width H is attached.
  • the ring body 20 Similarly to the case of FIG. 44 described above, the end portions of the blade 3 on the bell mouth side are each configured to incline toward the hub 2 side toward the centrifugal direction.
  • Other configurations are basically the same as those of the above-described embodiments.
  • the presence of the ring body 20 forms a circulating flow f that is sucked into the impeller 1 again from the blowout side of the impeller 1 through the back side of the air suction port 6 in the bell mouth 5.
  • the wind speed distribution at the exit of the blades 3 is evenly improved, and aerodynamic performance can be improved and operation noise can be reduced.
  • the impeller 1 can be integrally formed, and the cost can be greatly reduced by simplifying the structure and improving mass productivity.
  • FIGS. 55 to 58 show the configuration of the main part of a centrifugal blower that is useful for the thirteenth embodiment of the present invention.
  • the impeller 1 of this centrifugal blower is a disk-shaped hub in which the rotating shaft of the motor is connected to the shaft center portion as in the above embodiments. 2 and a plurality of blades 3 erected on the outer peripheral portion of the hub 2 along the circumferential direction at a predetermined interval.
  • Each blade 3 of this impeller 1 is of a forward inclined blade type 3A (Fig. 57) whose whole is inclined at a predetermined angle forward in the rotational direction M, or a reverse inclined blade type 3B ( Figure 58).
  • the number of blades 3 of the impeller 1 is set to a large number of 30 to 72, for example, on the outer periphery of the bell mouth side end. Is provided with a ring body 20 having a predetermined width H in the centrifugal direction. In the case of the present embodiment, the ring mouth side end portions of the ring body 20 and the blades 3 are formed so as to incline toward the hub 2 side in the centrifugal direction, as is apparent from FIG. Other configurations are described above. It is the same as that of each embodiment
  • the ring body 20 forms a circulation flow f in which the blowing side force of the impeller 1 is again sucked into the impeller 1 through the back side of the air suction port 6 in the bell mouth 5.
  • the main air flow f passing through the root 3 is attracted to the tip side of the blade 3 by the circulating flow f.
  • the wind speed distribution at the exit part of the blade 3 is improved, so that aerodynamic performance can be improved and the noise of operation can be reduced.
  • the impeller 1 can be integrally formed, the structure can be simplified, the cost can be reduced, and the mass productivity can be improved.
  • the blade 3 (3B) acts in a direction in which it is difficult to suck the circulating flow f formed by the ring body 20.
  • the blade 3 (3B) acts in a direction in which it is difficult to suck the circulating flow f formed by the ring body 20.
  • FIG. 59 and FIG. 60 show a centrifugal blower useful for the fourteenth embodiment of the present invention. The structure of the main part of the is shown.
  • the impeller 1 of this centrifugal blower is a disc-shaped hub in which the rotating shaft of the motor is connected to the shaft center as in the above embodiments. 2 and a plurality of blades 3 erected on the outer peripheral portion of the hub 2 along the circumferential direction at a predetermined interval.
  • Each blade 3 of the impeller 1 has a forward-tilt type 3A in which only its blade tip 3C is inclined at a predetermined angle forward in the rotational direction M, or a reverse-tilt type 3B of the opposite side. (Folding line L).
  • the number of blades 3 of the impeller 1 is set to a large number of 30 to 72, for example, on the outer periphery of the bell mouth side end. Is provided with a ring body 20 having a predetermined width H in the centrifugal direction. In the case of the present embodiment, the ring mouth side end portions of the ring body 20 and the blades 3 are formed so as to incline toward the hub 2 side toward the centrifugal direction, as is apparent from FIG. Other configurations are basically the same as those of the above-described embodiments.
  • the ring body 20 forms a circulating flow f in which the blowing side force of the impeller 1 is again sucked into the impeller 1 through the back side of the air suction port 6 in the bell mouth 5.
  • the main air flow f passing through the root 3 is attracted to the tip side of the blade 3 by the circulating flow f.
  • the shroud does not require a shroud
  • the impeller 1 can be integrally formed, the structure can be simplified and the cost can be reduced, and the mass productivity can be improved.

Landscapes

  • 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)

Abstract

Ventilateur centrifuge ayant un moyeu (2), une section d'axe à laquelle un arbre rotatif (4a) d'un moteur (4) est connecté, une roue à pales (1) munie de pales (3) qui sont montées le long du pourtour extérieur du moyeu (2) avec un espacement prédéfini dans une direction circonférentielle et dont le bord antérieur (3a) est incliné vers l'avant dans une direction de rotation. Ledit ventilateur centrifuge est muni d'un pavillon d'entrée (5) ayant une ouverture pour l'aspiration de l'air (6) et qui est placé du côté de l'aspiration de l'air de la roue à pales (1). Un flux de circulation f2 est formé, dans lequel le flux circule depuis le côté de soufflement de la roue à pales (1), à travers le côté postérieur de l'ouverture pour aspiration de l'air (6) dans le pavillon d'entrée (5), jusqu'à la roue à pales (1) dans laquelle le flux est à nouveau aspiré.
PCT/JP2005/013039 2004-07-14 2005-07-14 Ventilateur centrifuge et climatiseur équipé d'un ventilateur centrifuge WO2006006668A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
CN200580023831XA CN1985092B (zh) 2004-07-14 2005-07-14 离心式鼓风机及具有离心式鼓风机的空调装置
AU2005260828A AU2005260828B8 (en) 2004-07-14 2005-07-14 Centrifugal blower and air conditioner with centrifugal blower
US11/632,160 US20070251680A1 (en) 2004-07-14 2005-07-14 Centrifugal Blower and Air Conditioner with Centrifugal Blower
EP05765682A EP1783374A4 (fr) 2004-07-14 2005-07-14 Ventilateur centrifuge et climatiseur équipé d'un ventilateur centrifuge

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP2004-207288 2004-07-14
JP2004207288 2004-07-14
JP2004-366076 2004-12-17
JP2004366076 2004-12-17
JP2005195654A JP3879764B2 (ja) 2004-07-14 2005-07-05 遠心送風機
JP2005-195654 2005-07-05

Publications (1)

Publication Number Publication Date
WO2006006668A1 true WO2006006668A1 (fr) 2006-01-19

Family

ID=35784004

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2005/013039 WO2006006668A1 (fr) 2004-07-14 2005-07-14 Ventilateur centrifuge et climatiseur équipé d'un ventilateur centrifuge

Country Status (6)

Country Link
US (1) US20070251680A1 (fr)
EP (1) EP1783374A4 (fr)
JP (1) JP3879764B2 (fr)
CN (1) CN1985092B (fr)
AU (1) AU2005260828B8 (fr)
WO (1) WO2006006668A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7967557B2 (en) 2007-01-29 2011-06-28 Mitsubishi Electric Corporation Multiblade centrifugal blower
JP2020063683A (ja) * 2018-10-15 2020-04-23 日立建機株式会社 建設機械

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4895955B2 (ja) * 2007-09-25 2012-03-14 日立アプライアンス株式会社 乾燥機及び洗濯乾燥機
JP4872997B2 (ja) * 2008-02-28 2012-02-08 ダイキン工業株式会社 送風機及び該送風機を備えた空気調和機
KR101486550B1 (ko) * 2010-11-16 2015-01-23 삼성전자 주식회사 송풍용 원심팬 및 이를 갖는 냉장고
WO2013005596A1 (fr) * 2011-07-01 2013-01-10 シャープ株式会社 Dispositif de refroidissement, et dispositif d'éclairage mettant en œuvre celui-ci
JP5213999B2 (ja) * 2011-07-01 2013-06-19 シャープ株式会社 冷却装置
JP5097847B1 (ja) * 2011-07-01 2012-12-12 シャープ株式会社 照明装置
US8776394B2 (en) * 2011-10-04 2014-07-15 Whirlpool Corporation Blower for a laundry treating appliance
KR101400665B1 (ko) * 2012-06-12 2014-05-27 선문대학교 산학협력단 원심형 송풍장치
CN102748816A (zh) * 2012-08-08 2012-10-24 南昌航空大学 环流式节能空调器
CN102954041B (zh) * 2012-11-20 2015-09-02 石狮市通达电机有限公司 离心式鼓风机及包含该种离心式鼓风机的空调机
JP6142285B2 (ja) * 2013-03-21 2017-06-07 パナソニックＩｐマネジメント株式会社 片吸込み型遠心送風機
JP6288516B2 (ja) * 2014-12-03 2018-03-07 三菱重工業株式会社 インペラ、及び回転機械
CN107615566B (zh) * 2015-09-14 2021-02-05 松下知识产权经营株式会社 温度调节单元、温度调节系统、车辆
EP3219992B1 (fr) * 2016-03-14 2020-09-30 Soler & Palau Research, S.L. Unité de ventilateur
JP6844526B2 (ja) * 2017-12-26 2021-03-17 パナソニックＩｐマネジメント株式会社 多翼遠心ファン
CN108240355B (zh) * 2018-02-08 2024-08-13 浙江帅康电气股份有限公司 一种带有缓冲仓的蜗壳及包含该蜗壳的油烟机
JP6673385B2 (ja) * 2018-02-22 2020-03-25 ダイキン工業株式会社 ターボファン、及び空気調和機の室内機
CN112262286A (zh) * 2018-04-06 2021-01-22 Lg电子株式会社 风扇组件和空调器
CN111845995A (zh) * 2020-08-28 2020-10-30 广东省智能制造研究所 一种低噪声负压爬壁机器人
US11778757B2 (en) * 2020-10-23 2023-10-03 Manufacturing Resources International, Inc. Display assemblies incorporating electric vehicle charging equipment
GB2615971B (en) * 2020-12-23 2025-01-01 Mitsubishi Electric Corp Fan

Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1528797A (fr) 1967-04-17 1968-06-14 Lyonnaise Ventilation Perfectionnements aux ventilateurs centrifuges
JPS5049711A (fr) * 1973-09-05 1975-05-02
FR2317620A1 (fr) 1975-07-10 1977-02-04 Sueddeutsche Kuehler Behr Installation de refroidissement peu bruyante, en particulier pour vehicules automobiles
US4202296A (en) 1976-12-21 1980-05-13 Suddeutsche Kuhlerfabrik Julius Fr. Behr GmbH & Co. K.G. Cooling system for internal combustion engines
JPH09126189A (ja) * 1995-10-30 1997-05-13 Zexel Corp 送風ファン
JP2715839B2 (ja) * 1992-02-28 1998-02-18 株式会社デンソー 遠心式送風機
JPH10185238A (ja) 1996-12-20 1998-07-14 Fujitsu General Ltd 送風装置
JPH11101194A (ja) 1997-09-30 1999-04-13 Daikin Ind Ltd 遠心送風機及び該遠心送風機を備えた空気調和機
DE19903359A1 (de) 1998-02-02 1999-08-05 Denso Corp Zentrifugal-Gebläseeinheit
JP2000320490A (ja) * 1999-05-07 2000-11-21 Mitsubishi Heavy Ind Ltd 多翼送風機
JP3131598B2 (ja) * 1997-07-17 2001-02-05 株式会社ゼクセルヴァレオクライメートコントロール ブロワユニット
JP2001173596A (ja) 1999-12-21 2001-06-26 Mitsubishi Heavy Ind Ltd 多翼送風機
JP2002156128A (ja) * 2000-09-05 2002-05-31 Lg Electronics Inc 空気調和機用ターボファン
JP2002357196A (ja) * 2001-05-30 2002-12-13 Matsushita Seiko Co Ltd 遠心ファン
JP3404858B2 (ja) * 1994-02-07 2003-05-12 株式会社デンソー 遠心多翼送風機
JP2003172297A (ja) * 2001-12-07 2003-06-20 Calsonic Kansei Corp シロッコファン
JP2004360670A (ja) * 2003-05-09 2004-12-24 Daikin Ind Ltd 遠心送風機

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1049976A (en) * 1964-11-18 1966-11-30 Davidson & Co Ltd Improvements in or relating to fans
SE443408B (sv) * 1979-09-28 1986-02-24 Sueddeutsche Kuehler Behr Radialflekt for verme- eller luftkonditioneringsanleggningar i fordon
DE2940773C2 (de) * 1979-10-08 1986-08-14 Punker GmbH, 2330 Eckernförde Hochleistungs-Radialventilator
FR2564531B1 (fr) * 1984-05-15 1992-04-30 Solyvent Ventec Ste Lyonn Vent Ventilateur centrifuge
US4884946A (en) * 1987-05-04 1989-12-05 Belanger, Inc. Blower housing construction
US4747275A (en) * 1987-09-18 1988-05-31 Carrier Corporation Apparatus for controlling flow through a centrifugal impeller
US5352089A (en) * 1992-02-19 1994-10-04 Nippondenso Co., Ltd. Multi-blades fan device
DE4335686B4 (de) * 1993-10-20 2006-07-27 Robert Bosch Gmbh Gebläse
US5988979A (en) * 1996-06-04 1999-11-23 Honeywell Consumer Products, Inc. Centrifugal blower wheel with an upwardly extending, smoothly contoured hub
US5855469A (en) * 1997-07-17 1999-01-05 Iowa State University Research Foundation, Inc. End seal design for blower
JP3268279B2 (ja) * 1999-01-18 2002-03-25 三菱電機株式会社 空気調和機
KR100413177B1 (ko) * 2001-10-17 2003-12-31 학교법인 선문학원 원심 다익 팬

Patent Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1528797A (fr) 1967-04-17 1968-06-14 Lyonnaise Ventilation Perfectionnements aux ventilateurs centrifuges
JPS5049711A (fr) * 1973-09-05 1975-05-02
FR2317620A1 (fr) 1975-07-10 1977-02-04 Sueddeutsche Kuehler Behr Installation de refroidissement peu bruyante, en particulier pour vehicules automobiles
US4202296A (en) 1976-12-21 1980-05-13 Suddeutsche Kuhlerfabrik Julius Fr. Behr GmbH & Co. K.G. Cooling system for internal combustion engines
JP2715839B2 (ja) * 1992-02-28 1998-02-18 株式会社デンソー 遠心式送風機
JP3404858B2 (ja) * 1994-02-07 2003-05-12 株式会社デンソー 遠心多翼送風機
JPH09126189A (ja) * 1995-10-30 1997-05-13 Zexel Corp 送風ファン
JPH10185238A (ja) 1996-12-20 1998-07-14 Fujitsu General Ltd 送風装置
JP3131598B2 (ja) * 1997-07-17 2001-02-05 株式会社ゼクセルヴァレオクライメートコントロール ブロワユニット
JPH11101194A (ja) 1997-09-30 1999-04-13 Daikin Ind Ltd 遠心送風機及び該遠心送風機を備えた空気調和機
DE19903359A1 (de) 1998-02-02 1999-08-05 Denso Corp Zentrifugal-Gebläseeinheit
JP2000320490A (ja) * 1999-05-07 2000-11-21 Mitsubishi Heavy Ind Ltd 多翼送風機
JP2001173596A (ja) 1999-12-21 2001-06-26 Mitsubishi Heavy Ind Ltd 多翼送風機
JP2002156128A (ja) * 2000-09-05 2002-05-31 Lg Electronics Inc 空気調和機用ターボファン
JP2002357196A (ja) * 2001-05-30 2002-12-13 Matsushita Seiko Co Ltd 遠心ファン
JP2003172297A (ja) * 2001-12-07 2003-06-20 Calsonic Kansei Corp シロッコファン
JP2004360670A (ja) * 2003-05-09 2004-12-24 Daikin Ind Ltd 遠心送風機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP1783374A4

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7967557B2 (en) 2007-01-29 2011-06-28 Mitsubishi Electric Corporation Multiblade centrifugal blower
EP2108845A4 (fr) * 2007-01-29 2011-10-26 Mitsubishi Electric Corp Ventilateur centrifuge multi-pales
JP2020063683A (ja) * 2018-10-15 2020-04-23 日立建機株式会社 建設機械
WO2020080260A1 (fr) * 2018-10-15 2020-04-23 日立建機株式会社 Engin de chantier
JP7207933B2 (ja) 2018-10-15 2023-01-18 日立建機株式会社 建設機械
US11680583B2 (en) 2018-10-15 2023-06-20 Hitachi Construction Machinery Co., Ltd. Construction machine

Also Published As

Publication number Publication date
CN1985092B (zh) 2011-09-07
JP3879764B2 (ja) 2007-02-14
AU2005260828A1 (en) 2006-01-19
JP2006194235A (ja) 2006-07-27
EP1783374A1 (fr) 2007-05-09
EP1783374A4 (fr) 2010-02-24
CN1985092A (zh) 2007-06-20
US20070251680A1 (en) 2007-11-01
AU2005260828B8 (en) 2009-01-29
AU2005260828B2 (en) 2009-01-15

Similar Documents

Publication Publication Date Title
WO2006006668A1 (fr) Ventilateur centrifuge et climatiseur équipé d'un ventilateur centrifuge
JP4035237B2 (ja) 軸流送風機
JP4358965B2 (ja) 遠心型羽根車および空気清浄装置
US8870541B2 (en) Centrifugal multiblade fan
JP5832804B2 (ja) 遠心式ファン
JP4426776B2 (ja) 送風用遠心羽根車
WO2012008238A1 (fr) Ventilateur centrifuge à pales multiples et installation de climatisation utilisant ce ventilateur
JP4779627B2 (ja) 多翼送風機
JP4581992B2 (ja) 遠心送風機および該遠心送風機を備えた空気調和装置
JP2003232295A (ja) 遠心ファンおよびその遠心ファンを備えた加熱調理器
JP2018132012A (ja) 電動送風機および電動掃除機、ならびにインペラの製造方法
JP2715839B2 (ja) 遠心式送風機
JP6844526B2 (ja) 多翼遠心ファン
JPH09195988A (ja) 多翼送風機
JP2023015577A (ja) 軸流ファン
JP4269092B2 (ja) 多翼遠心ファン
JP2001159396A (ja) 遠心ファン及び該遠心ファンを備えた空気調和機
JP3130089U (ja) 遠心送風機
JP2000303992A (ja) 斜流送風機
JP3902193B2 (ja) 多翼遠心送風機
CN116249838A (zh) 螺旋桨式风扇
JPH07279891A (ja) 多翼送風機
JP3476085B2 (ja) 多翼送風ファン
KR100824149B1 (ko) 원심 송풍기 및 원심 송풍기를 구비한 공기 조화 장치
JP7317235B2 (ja) 多翼羽根車および遠心送風機

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BW BY BZ CA CH CN CO CR CU CZ DE DK DM DZ EC EE EG ES FI GB GD GE GH GM HR HU ID IL IN IS KE KG KM KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NA NG NI NO NZ OM PG PH PL PT RO RU SC SD SE SG SK SL SM SY TJ TM TN TR TT TZ UA UG US UZ VC VN YU ZA ZM ZW

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): BW GH GM KE LS MW MZ NA SD SL SZ TZ UG ZM ZW AM AZ BY KG KZ MD RU TJ TM AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LT LU LV MC NL PL PT RO SE SI SK TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG

121 Ep: the epo has been informed by wipo that ep was designated in this application
WWE Wipo information: entry into national phase

Ref document number: 11632160

Country of ref document: US

WWE Wipo information: entry into national phase

Ref document number: 200580023831.X

Country of ref document: CN

Ref document number: 1020077000947

Country of ref document: KR

NENP Non-entry into the national phase

Ref country code: DE

WWW Wipo information: withdrawn in national office

Country of ref document: DE

WWE Wipo information: entry into national phase

Ref document number: 2005765682

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2005260828

Country of ref document: AU

ENP Entry into the national phase

Ref document number: 2005260828

Country of ref document: AU

Date of ref document: 20050714

Kind code of ref document: A

WWP Wipo information: published in national office

Ref document number: 2005260828

Country of ref document: AU

WWP Wipo information: published in national office

Ref document number: 1020077000947

Country of ref document: KR

WWP Wipo information: published in national office

Ref document number: 2005765682

Country of ref document: EP

WWP Wipo information: published in national office

Ref document number: 11632160

Country of ref document: US

点击 这是indexloc提供的php浏览器服务，不要输入任何密码和下载