US20150192143A1 - Centrifugal multi-blade blower - Google Patents

Centrifugal multi-blade blower Download PDF

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Publication number
US20150192143A1
US20150192143A1 US14/410,796 US201314410796A US2015192143A1 US 20150192143 A1 US20150192143 A1 US 20150192143A1 US 201314410796 A US201314410796 A US 201314410796A US 2015192143 A1 US2015192143 A1 US 2015192143A1
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United States
Prior art keywords
impeller
plate
peripheral edge
vanes
inner peripheral
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.)
Abandoned
Application number
US14/410,796
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English (en)
Inventor
Masaharu Sakai
Shouichi Imahigashi
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Denso Corp
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Denso Corp
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Filing date
Publication date
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Assigned to DENSO CORPORATION reassignment DENSO CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: IMAHIGASHI, SHOUICHI, SAKAI, MASAHARU
Publication of US20150192143A1 publication Critical patent/US20150192143A1/en
Abandoned legal-status Critical Current

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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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression
    • F04D17/162—Double suction pumps
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • 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
    • F04D29/26—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
    • F04D29/283—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 rotors of the squirrel-cage type
    • 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
    • F04D29/30—Vanes

Definitions

  • the present disclosure relates to a centrifugal multi-blade blower that draws air from a direction of a rotation axis and blows out the air radially outward of the rotation axis.
  • An impeller of a conventional centrifugal multi-blade blower includes vanes arranged around the rotation axis, and blows out radially outward the air, which is drawn from the direction of the rotation axis.
  • a wind direction rapidly changes from the rotation axis direction to the radial direction at spaces between adjacent vanes (hereinafter referred to as an inter-vane space) near an air inlet. Accordingly, the air does not flow easily compared to on an opposite side from the inlet in the rotation axis direction.
  • an inner peripheral edge part 111 of a vane 110 on a side plate 130 -side is formed in a tapered shape so that an inner diameter of an impeller 100 on the side plate 130 -side (inlet side) is larger than on a main plate 120 -side (opposite side from the inlet). Accordingly, draft resistance on the inlet side of the impeller 100 is reduced to facilitate a flow of the air flowing from the rotation axis direction through the inter-vane space near the inlet.
  • FIG. 21 is a meridian plane diagram corresponding to the impeller 100 illustrated in FIG. 20 of Patent Document 1.
  • the meridian plane is a surface of section including the rotation axis of the impeller, onto which a shape of the vane is rotationally projected.
  • FIGS. 22 and 23 are diagrams illustrating the issue of the above conventional technology.
  • FIG. 22 is a cross-sectional view taken along a line XXII-XXII in FIG. 21 (sectional view of the vane 110 on the main plate 120 -side).
  • FIG. 23 is a cross-sectional view taken along a line XXIII-XXIII in FIG. 21 (sectional view of the vane 110 on the side plate 130 -side).
  • an inlet angle ⁇ of each vane 110 is an angle made between a tangent of an inscribed circle passing through the inner peripheral edge part 111 of each vane (alternate long and short dash line in FIGS. 22 and 23 ), and a tangent at an inner end part of the inner peripheral edge part 111 on a positive pressure surface 110 a -side (alternate long and two short dashes line in FIGS. 22 and 23 ).
  • a circumferential speed Us′ on the side plate 130 -side is faster than a circumferential speed Um′ on the main plate 120 -side (Us′>Um′).
  • a change of the flow direction of air flowing into the inter-vane space on the side plate 130 -side is greater than on the main plate 120 -side. Accordingly, as illustrated in FIGS. 22 and 23 , an absolute inflow speed Cs′ of the air flowing into the inner peripheral edge part 111 of the vane 110 on the side plate 130 -side is slower than an absolute inflow speed Cm′ of the air flowing into the inner peripheral edge part 111 of the vane 110 on the main plate 120 -side (Cs′ ⁇ Cm′).
  • an inflow angle ⁇ s′ on the side plate 130 -side is smaller than an inflow angle ⁇ m′ on the main plate 120 -side.
  • an inlet angle ⁇ s′ on the side plate 130 -side is made the same as an inlet angle ⁇ m′ on the main plate 120 -side as in the impeller 100 of the above conventional technology, a difference (incidence angle ⁇ s′) between the inlet angle ⁇ s′ and the inflow angle ⁇ s′ on the side plate 130 -side is larger than an incidence angle ⁇ m′ on the main plate 120 -side.
  • the incidence angle ⁇ s′ on the side plate 130 -side is still larger than the incidence angle ⁇ m′ on the main plate 120 -side, and it is difficult to sufficiently restrain the exfoliation of the air flow on the side plate 130 -side.
  • a flow speed on the side plate 130 -side of the impeller 100 on the air outlet side is reduced due to the exfoliation of the air flow on the side plate 130 -side.
  • the present disclosure addresses the above issues.
  • the impeller includes a main plate that is joined to a rotation shaft, vanes which are arranged around the axis of the rotation shaft and the other end sides of which in the rotation axis direction are connected to the main plate, and a side plate that connects together the vanes on their one end sides in the rotation axis direction.
  • the vanes are characterized in that the inlet angle on a cross-sectional surface crossing each inner peripheral edge part of the vanes on a meridian plane of the impeller in a predetermined direction is evenly made in the entire region from the side plate-side through the main plate-side, and that outer peripheral edge parts of the vanes are configured to be away from the axis of the rotation shaft from the main plate-side toward the side plate-side.
  • the outer peripheral diameter of the impeller is larger on the side plate side than on the main plate side. Accordingly, a flow rate on the air outlet side on the side plate side of the impeller can be increased. As a consequence, a flow speed on the air outlet side on the side plate side of the impeller can be increased compared to the impeller of the conventional technology.
  • a flow rate of air flowing into the inner peripheral edge part on the side plate side increases.
  • This increase of the flow rate of air flowing into the inner peripheral edge part on the side plate side makes faster a flow speed (absolute inflow speed) on the side plate side. Accordingly, an inflow angle on the side plate side can be brought close to the inlet angle.
  • the exfoliation of the air flow on the side plate side can be restricted as compared with the impeller of the conventional technology, and there can be mitigated a reduction of the flow speed on the air outlet side on the side plate side in association with the exfoliation of the air flow on the side plate side.
  • the centrifugal multi-blade blower of the present disclosure can sufficiently evenly make a flow speed distribution in the rotation axis direction on an air outlet side of the impeller, which becomes an issue in the impeller of the conventional technology.
  • the inlet angle is an intersecting angle between a tangent of a circle (inscribed circle) passing through each inner peripheral edge part of the vanes in a radial direction of the rotation axis, and the inner peripheral edge part of the vane.
  • FIG. 1 is a schematic view illustrating an air-conditioning system for a vehicle including a blower in accordance with a first embodiment
  • FIG. 2 is a perspective view illustrating an impeller of the blower of the first embodiment
  • FIG. 3 is a half sectional view illustrating the impeller of the blower of the first embodiment
  • FIG. 4 is a diagram illustrating a vane part viewed from an arrowed line IV in FIG. 3 ;
  • FIG. 5 is a diagram illustrating the vane part viewed from an arrowed line V in FIG. 3 ;
  • FIG. 6 is a diagram illustrating the vane part viewed from an arrowed line VI in FIG. 3 ;
  • FIG. 7 is a meridian plane diagram illustrating the entire impeller of the first embodiment
  • FIG. 8 is a meridian plane diagram illustrating an essential part of the impeller of the first embodiment
  • FIG. 9 is a cross-sectional view taken along a line IX-IX in FIG. 8 ;
  • FIG. 10 is a cross-sectional view taken along a line X-X in FIG. 8 ;
  • FIG. 11 is a perspective view illustrating an impeller of a blower in accordance with a second embodiment
  • FIG. 12 is a half sectional view illustrating the impeller of the blower of the second embodiment
  • FIG. 13 is a top view illustrating the impeller of the blower of the second embodiment
  • FIG. 14 is a meridian plane diagram illustrating the impeller of the blower of the second embodiment
  • FIG. 15 is a meridian plane diagram illustrating an impeller of a blower in accordance with a third embodiment
  • FIG. 16 is a meridian plane diagram illustrating an essential part of an impeller of a blower in accordance with a fourth embodiment
  • FIG. 17 is a meridian plane diagram illustrating an impeller of a blower in accordance with a modification
  • FIG. 18 is a meridian plane diagram illustrating an impeller of a blower in accordance with another modification
  • FIG. 19 is a perspective view illustrating an impeller of a blower in accordance with yet another modification
  • FIG. 20 is a half sectional view illustrating the impeller of the blower of the yet another modification
  • FIG. 21 is a meridian plane diagram illustrating an essential part of an impeller in accordance with a conventional technology
  • FIG. 22 is a cross-sectional view taken along a line XXII-XXII in FIG. 21 ;
  • FIG. 23 is a cross-sectional view taken along a line XXIII-XXIII in FIG. 21 .
  • a centrifugal multi-blade blower of the present disclosure is applied to an air-conditioning system 1 for a vehicle including a water-cooled engine.
  • the air-conditioning system 1 includes an air-conditioning casing 2 that defines an air passage for blown air which is blown into a vehicle interior.
  • an inside air introduction port 3 for introducing inside air (vehicle interior air)
  • an outside air introduction port 4 for introducing outside air (vehicle exterior air)
  • an inside-outside air switch door 5 for selectively opening or closing these introduction ports 3 , 4 .
  • a blower 7 is disposed on a downstream side of the inside-outside air switch door 5 in an air flow direction, and the air introduced through the introduction ports 3 , 4 is blown by this blower 7 toward air outlets 14 , 15 , 17 which will be described later.
  • the blower 7 is a centrifugal multi-blade blower that blows out radially outward the air which is drawn from the direction of the rotation axis.
  • a single-suction type blower that suctions air from its one end side in the rotation axis direction and blows out the air outward in the radial direction.
  • the blower 7 includes an impeller 7 a, a scroll casing (casing) 7 b, and an electric motor 7 c that drives the impeller 7 a.
  • the impeller 7 a rotates with a rotation shaft 70 as the center to blow out the air outward in the radial direction, and is configured from resin.
  • the scroll casing 7 b accommodates the impeller 7 a, and includes a vortical passage through which the air blown out of the impeller 7 a merges together.
  • the scroll casing 7 b includes an inlet port 74 that opens on one end side of the rotation shaft 70 . Details of the impeller 7 a of the blower 7 of the present embodiment will be described later.
  • An evaporator 9 is disposed on a downstream side of the blower 7 in the air flow direction, and all the air blown by the blower 7 passes through this evaporator 9 .
  • the evaporator 9 of the present embodiment is an air cooling means for exchanging heat between refrigerant flowing in the evaporator 9 and blown air which is blown by the blower 7 to cool the blown air.
  • this evaporator 9 constitutes a vapor-compression type refrigeration cycle.
  • a heater core 10 is disposed on a downstream side of the evaporator 9 in the air flow direction.
  • the heater core 10 is an air heating means for exchanging heat between engine coolant for cooling an engine 11 and air after having passed through the evaporator 9 to heat the air after having passed through the evaporator 9 .
  • the air-conditioning casing 2 includes a bypass passage 12 through which the air after having passed through the evaporator 9 flows to bypass the heater core 10 .
  • a bypass passage 12 through which the air after having passed through the evaporator 9 flows to bypass the heater core 10 .
  • an air mixing door 13 On an upstream side of the heater core 10 in the air flow direction, there is disposed an air mixing door 13 that adjusts an air volume ratio between the volume of air passing through the heater core 10 and the volume of air passing through the bypass passage 12 to adjust the temperature of air blown out into the vehicle interior.
  • the face air outlet 14 for blowing out the air toward an upper half of a body of an occupant of the vehicle
  • the foot air outlet 15 for blowing out the air toward a foot of the occupant
  • the defroster air outlet 17 for blowing out the air toward an inner surface of a window pane 16 .
  • Blowing-out mode switch doors 18 , 19 , and 20 are arranged respectively on an upstream side of these air outlets 14 , 15 , 17 in the air flow direction. These blowing-out mode switch doors 18 to 20 are switchingly opened or closed to switch between a face mode in which to blow out the air toward an upper body of the occupant, a foot mode in which to blow out the air toward a lower body of the occupant, and a defroster mode in which to blow out the air toward an inner surface of the window pane of the vehicle.
  • the impeller 7 a of the blower 7 of the present embodiment will be described below. As illustrated in a perspective view of FIG. 2 and a half sectional view of FIG. 3 , the impeller 7 a of the blower 7 includes vanes 71 , a side plate 72 , and a main plate 73 .
  • the main plate 73 is configured by a disc-like member that is joined to the rotation shaft 70 .
  • the main plate 73 of the present embodiment is connected to a part 71 b of each vane 71 on the other end side (lower side on a plane of paper) in the rotation axis direction, and is configured to overlap with the vanes 71 when viewed from the rotation axis direction.
  • the side plate 72 is connected to a part of each vane 71 radially outward of the rotation shaft 70 on one end side (upper side on a plane of paper) in the rotation axis direction.
  • the side plate 72 of the present embodiment is connected to cover an outer peripheral edge part (vane rear edge) 712 of each vane 71 on the one end side in the rotation axis direction, from a radially outward side of the rotation shaft 70 .
  • the side plate 72 of the present embodiment has an annular shape (shroud shape) which is bent such that its part on the one end side in the rotation axis direction is located inward of the part on the other end side in the radial direction of the rotation shaft 70 .
  • the side plate 72 of the present embodiment is configured such that its inner peripheral diameter Ds is larger than an outer peripheral diameter Dm of the main plate 73 , and has a shape that does not overlap with the main plate 73 when viewed from the rotation axis direction.
  • the vanes 71 are arranged around the axis Z of the rotation shaft 70 .
  • the vanes 71 , the side plate 72 , and the main plate 73 , which constitute the impeller 7 a, are integrally molded by resin molding or the like.
  • the impeller 7 a configured in this manner blows out by centrifugal force radially outward of the impeller 7 a the air, which has flowed from the inlet port 74 on the one end side in the rotation axis direction into inter-vane spaces (spaces between the vanes 71 ) in the impeller 7 a.
  • FIGS. 4 to 6 are diagrams viewed respectively from arrowed lines in FIG. 3 and illustrate the shape of the vane 71 of the present embodiment.
  • illustrations of the side plate 72 and the main plate 73 are omitted, and typical three vanes 71 in directions of the arrowed lines A to C in FIG. 3 are illustrated.
  • an inner peripheral edge part (vane front edge) 711 is provided for each vane 71 between parts 71 a, 71 b on both end sides of the vane 71 on an inner peripheral side of the impeller 7 a.
  • an outer peripheral edge part (vane rear edge) 712 is provided for each vane 71 between the parts 71 a, 71 b on both end sides of the vane 71 on an outer peripheral side of the impeller 7 a.
  • each vane 71 of the present embodiment when viewed from the rotation axis direction, a part 711 a of the inner peripheral edge part 711 on the one end side in the rotation axis direction is located further on a front side than a part 711 b of the inner peripheral edge part 711 on the other end side in the rotation axis direction, in a rotation direction R of the impeller 7 a.
  • the impeller 7 a of the present embodiment is configured to blow out radially outward the air which is drawn from the rotation axis direction. Accordingly, the part 711 a of the inner peripheral edge part 711 on the one end side in the rotation axis direction is located on a front side of the part 711 b of the inner peripheral edge part 711 on the other end side in the rotation axis direction, in the rotation direction R, so that the air is suctioned easily into the inter-vane spaces from the rotation axis direction on the side plate 72 -side. As a result, the flow rate of air flowing into the inter-vane spaces on the side plate 72 -side can be increased.
  • the part 711 a of the inner peripheral edge part 711 on the one end side in the rotation axis direction may be hereinafter referred to as a forward part 711 a
  • the part 711 b of the inner peripheral edge part 711 on the other end side in the rotation axis direction may be hereinafter referred to as a backward part 711 b.
  • the specific shapes of the inner peripheral edge part 711 and the outer peripheral edge part 712 of each vane 71 will be described with reference to the meridian plane diagrams in FIGS. 7 and 8 .
  • the “meridian plane” is a surface of section including the rotation shaft 70 of the impeller 7 a, onto which a shape of the vane 71 is rotationally projected.
  • the inner peripheral edge part 711 of the vane 71 of the present embodiment is configured to separate from the axis Z of the rotation shaft 70 from the main plate 73 -side toward the side plate 72 -side such that the inner peripheral diameter of the impeller 7 a on the side plate 72 -side is larger than the inner peripheral diameter on the main plate 73 -side.
  • the inner peripheral diameter of the impeller 7 a is a diameter of an inscribed circle passing through the inner peripheral edge parts 711 of the vanes 71 in the radial direction of the rotation shaft 70 .
  • the inlet angle ⁇ on each cross-sectional surface crossing the inner peripheral edge part 711 of the vane 71 that appears on the meridian plane of the impeller 7 a in a predetermined direction is set to be evenly made in the entire region from the side plate 72 -side through the main plate 73 -side.
  • “Evenly” means a state where the inlet angle ⁇ is not shifted or a state where there is only a minute difference within ⁇ 5 degrees in the entire region from the side plate 72 -side through the main plate 73 -side.
  • FIG. 9 is a cross-sectional view taken along a line IX-IX in FIG. 8
  • FIG. 10 is a cross-sectional view taken along a line X-X in FIG. 8
  • the cross-section surface along the line IX-IX is a surface of section obtained by cutting a part of the vane 71 on the main plate 73 -side in a direction perpendicular to the rotation axis direction.
  • the cross-section surface along the line X-X is a surface of section obtained by cutting a part of the vane 71 on the side plate 72 -side in a direction perpendicular to the rotation axis direction.
  • an inlet angle ⁇ m as at the inner peripheral edge part 711 of each vane 71 on each cross-section perpendicular to the rotation axis direction is set at an angle (e.g., angle ranging from 55 degrees to 76 degrees) that is even in the entire region from the side plate 72 -side through the main plate 73 -side.
  • the inlet angle ⁇ m as is an angle made between a tangent line (alternate long and short dash line in FIGS. 9 and 10 ) of the inscribed circle passing through the inner peripheral edge parts 711 of the vanes 71 , and a tangent line (alternate long and two short dashes line in FIGS. 9 and 10 ) at an inner end part 713 a of the vane 71 on a positive pressure surface 713 -side.
  • the outer peripheral edge parts 712 of the vanes 71 are shaped to be away from the axis Z of the rotation shaft 70 from the main plate 73 -side toward the side plate 72 -side such that the outer peripheral diameter of the impeller 7 a on the side plate 72 -side is larger than the outer peripheral diameter of the impeller 7 a on the main plate 73 -side.
  • the outer peripheral diameter of the impeller 7 a is a diameter of a circumscribed circle passing through the outer peripheral edge parts 712 of the vanes 71 in the radial direction of the rotation shaft 70 .
  • the vanes 71 of the present embodiment are configured to have the inner peripheral diameter increased from the main plate 73 -side toward the side plate 72 -side, and to have the outer peripheral diameter increased from the main plate 73 -side toward the side plate 72 -side (d 1 >d 2 , D 1 >D 2 ).
  • an outer configuration of the impeller 7 a of the present embodiment has a shape of an inverted trapezoid.
  • a side-plate side inner-outer diameter ratio is smaller than a main-plate side inner-outer diameter ratio.
  • the main-plate side inner-outer diameter ratio is a ratio of an outer peripheral diameter D 2 to an inner peripheral diameter d 2 (D 2 /d 2 ) of the impeller 7 a on the main plate 73 -side.
  • the air-conditioning system 1 of the present embodiment When the operation of the air-conditioning system 1 is started by operation by the occupant, for example, the air introduced into the air-conditioning casing 2 through the introduction ports 3 , 4 is blown toward the air outlets 14 , 15 , 17 by the blower 7 .
  • the blown air which is blown by the blower 7 is adjusted to have a desired temperature by the evaporator 9 , the heater core 10 , and the air mixing door 13 , and is blown out into the vehicle interior through any air outlet of the air outlets 14 , 15 , 17 .
  • the inner peripheral edge parts 711 of the vanes 71 are shaped to separate from the axis Z of the rotation shaft 70 from the main plate 73 -side toward the side plate 72 -side such that the inner peripheral diameter of the impeller 7 a becomes large from the main plate 73 -side toward the side plate 72 -side. Accordingly, draft resistance on the side plate 72 -side of the impeller 7 a can be reduced to make the air flowing from the rotation axis direction flow easily into the inter-vane spaces on the side plate 72 -side.
  • the inlet angle ⁇ m, as at the inner peripheral edge part 711 of each vane 71 on each cross-section perpendicular to the axis of the rotation shaft 70 is made evenly in the entire region from the side plate 72 -side through the main plate 73 -side. Accordingly, as compared to a normal centrifugal multi-blade blower, the exfoliation of the air flow on the side plate 72 -side can be limited to make the air flowing from the rotation axis direction flow easily into the inter-vane spaces near the inlet port 74 .
  • the outer peripheral edge parts 712 of the vanes 71 are shaped to be away from the axis Z of the rotation shaft 70 from the main plate 73 -side toward the side plate 72 -side. Accordingly, there is evenly made a flow speed distribution in the rotation axis direction on an air outlet side of the impeller 7 a, which comes to an issue when the inlet angle ⁇ m, as at the inner peripheral edge part 711 of each vane 71 is made evenly in the entire region from the side plate 72 -side through the main plate 73 -side.
  • the flow rate of the impeller 7 a on its air outlet side increases in proportion to the second power of the outer peripheral diameter of the impeller 7 a under conditions where rotating speed and draft resistance are constant. Accordingly, by increasing the outer peripheral diameter of the impeller 7 a on the side plate 72 -side compared with on the main plate 73 -side, the flow rate on the air outlet side of the impeller 7 a on its side plate 72 -side increases, whereupon the flow speed on the air outlet side of the impeller 7 a on its side plate 72 -side becomes fast. Thus, the flow speed on the side plate 72 -side of the impeller 7 a on its air outlet side can be brought close to the flow speed on the main plate 73 -side.
  • the flow rate of air flowing into the inner peripheral edge parts 711 on the side plate 72 -side increases in accordance with the increase of the flow rate on the air outlet side of the impeller 7 a on its side plate 72 -side.
  • This increase of the flow rate of air flowing into the inner peripheral edge parts 711 on the side plate 72 -side makes faster the flow speed on the side plate 72 -side. Accordingly, a difference between the inlet angle and the inflow angle on the side plate 72 -side can be reduced.
  • a circumferential speed Us on the side plate 72 -side is faster than a circumferential speed Um on the main plate 73 -side (Us>Um) as illustrated in FIGS. 9 and 10 .
  • an inflow angle ⁇ s on the side plate 72 -side is an angle that is close to an inflow angle ⁇ m on the main plate 73 -side.
  • the inlet angle ⁇ s on the side plate 72 -side is made (almost) the same as the inlet angle ⁇ m on the main plate 73 -side. Accordingly, a difference (incidence angle ⁇ s) between the inlet angle ⁇ s and the inflow angle ⁇ s on the side plate 72 -side is reduced.
  • the exfoliation of the air flow on the side plate 72 -side is sufficiently curbed, so that there can be alleviated a reduction of the flow speed on the air outlet side on the side plate 72 -side associated with the exfoliation of the air flow on the side plate 72 -side. Consequently, the flow speed on the side plate 72 -side of the impeller 7 a on its air outlet side can be brought even closer to the flow speed on the main plate 73 -side.
  • the flow speed distribution in the rotation axis direction on the air outlet side of the impeller 7 a can be sufficiently evenly made. Improvement in efficiency of the blower 7 and restraint of noise of the blower 7 can be promoted.
  • the part 711 a of the inner peripheral edge part 711 on the one end side in the rotation axis direction is positioned further on a front side in the rotation direction R than the part 711 b of the inner peripheral edge part 711 on the other end side in the rotation axis direction.
  • a second embodiment will be described below.
  • an example of modification of the shape of the main plate 73 to the first embodiment will be described.
  • explanation will be given with the description of a part similar or equivalent to the first embodiment omitted or simplified.
  • an outer peripheral diameter of a main plate 73 is made smaller than in the first embodiment as illustrated in a perspective view in FIG. 11 , a half sectional view in FIG. 12 , and a top view in FIG. 13 .
  • the outer peripheral diameter of the main plate 73 is made small such that the main plate 73 and a forward part 711 a of an inner peripheral edge part 711 do not overlap with each other when the impeller 7 a is viewed from the rotation axis direction.
  • a distance L 1 from an axis Z of a rotation shaft 70 to an outer peripheral end of the main plate 73 is smaller than a distance L 2 from the axis Z of the rotation shaft 70 to the forward part 711 a of the inner peripheral edge part 711 .
  • blower 7 of the present embodiment produces effects similar to the first embodiment.
  • the forward part 711 a of the inner peripheral edge part 711 is located on a front side of a backward part 711 b of the inner peripheral edge part 711 in the rotation direction R, when integrally molding vanes 71 , a side plate 72 , and the main plate 73 , the forward part 711 a may be undercut.
  • the impeller 7 a is shaped such that the main plate 73 and a forward part 711 a of an inner peripheral edge part 711 do not overlap with each other in the rotation axis direction by making small the outer peripheral diameter of the main plate 73 . Accordingly, when integrally-shaping at least the main plate 73 and the vanes 71 by molding, a molded article can be taken out from a mold by sliding the mold in the rotation axis direction. As a consequence, the impeller 7 a can easily be produced to reduce the costs.
  • a third embodiment will be described below.
  • an example of modification of the shape of the impeller 7 a to the first and second embodiments will be described.
  • explanation will be given with the description of a part similar or equivalent to the first and second embodiments omitted or simplified.
  • a ratio of an outer peripheral diameter D 1 to an inner peripheral diameter d 1 of an impeller 7 a on a side plate 72 -side is larger than a ratio of an outer peripheral diameter D 2 to an inner peripheral diameter d 2 of the impeller 7 a on a main plate 73 -side (main-plate side inner-outer diameter ratio) (D 1 /d 1 >D 2 /d 2 ).
  • outer peripheral edge parts 712 of vanes 71 are configured to be away from an axis Z of a rotation shaft 70 from the main plate 73 -side toward the side plate 72 -side, and inner peripheral edge parts 711 of the vanes 71 are configured to extend along the rotation axis direction.
  • the outer peripheral diameter of the impeller 7 a on the side plate 72 -side is larger than the outer peripheral diameter of the impeller 7 a on the main plate 73 -side
  • the inner peripheral diameter of the impeller 7 a on the side plate 72 -side and the inner peripheral diameter of the impeller 7 a on the main plate 73 -side are equal to each other.
  • blower 7 of the present embodiment produces effects similar to the effects of the first embodiment.
  • the inner peripheral diameter of the impeller 7 a on the side plate 72 -side is not too large, so that there can be limited the increase of the circumferential speed Us at the inner peripheral edge part 711 on the side plate 72 -side. Therefore, as a result of the configuration of the present embodiment, there can be restrained a the increase of the circumferential speed at the inner peripheral edge part 711 on the side plate 72 -side which influences the inflow angle at the inner peripheral edge part 711 on the side plate 72 -side in addition to the flow rate increase on the side plate 72 -side.
  • the inflow angle ⁇ s at the inner peripheral edge part 711 on the side plate 72 -side becomes large, so that the difference between the inlet angle ⁇ s and the inflow angle ⁇ s at the inner peripheral edge part 711 on the side plate 72 -side is reduced. As a result, the exfoliation on the side plate 72 -side can be effectively inhibited.
  • imaginary flow lines whereby flow directions of air flowing into inner peripheral edge parts 711 of vanes 71 are assumed, are set, and the inlet angles ⁇ on cross-sections on the imaginary flow lines are made evenly in the entire region from a side plate 72 -side through a main plate 73 -side (e.g., angle ranging from 55 degrees to 76 degrees).
  • first to sixth division lines Yd 1 to Yd 6 are set as the imaginary flow lines, and the inlet angles ⁇ on cross-sections on the imaginary flow lines Yd 1 to Yd 6 are made evenly over the entire range of the inner peripheral edge part 711 of the vane 71
  • the inner peripheral edge part 711 of the vane 71 is divided into a predetermined number of portions whose lengths along the inner peripheral edge part 711 are equal to set a division point Yin at the inner peripheral edge part 711 .
  • the division point Yin at the inner peripheral edge part 711 is set as a first inner peripheral division point Yi 1 , a second inner peripheral division point Yi 2 , . . . , and a sixth inner peripheral division point Yi 6 in order from one end side of the vane 71 in the rotation axis direction.
  • an outer peripheral edge part 712 of the vane 71 is divided into a predetermined number of portions whose lengths along the outer peripheral edge part 712 are equal to set a division point Yon at the outer peripheral edge part 712 .
  • the division point Yon at the outer peripheral edge part 712 is set as a first outer peripheral division point Yo 1 , a second outer peripheral division point Yo 2 , . . . , and a sixth outer peripheral division point Yo 6 in order from one end side of the vane 71 in the rotation axis direction.
  • a line (first to sixth division points Yd 1 to Yd 6 ) that connects together the division points having the same number out of the inner peripheral division point Yin and the outer peripheral division point Yon when counted in order from one end side of the vane 71 in the rotation axis direction is set as the imaginary flow line.
  • blower 7 of the present embodiment produces effects similar to the effects of the first embodiment. Furthermore, the blower 7 of the present embodiment has the advantage that design surfaces of the vanes 71 do not intersect with each other and the vanes 71 of an impeller 7 a are thereby easily designed.
  • the present embodiment there has been described an example of setting the six imaginary flow lines by dividing the inner peripheral edge part 711 and the outer peripheral edge part 712 of the vane 71 into six portions.
  • the present disclosure is not limited to this example, and the set number of imaginary flow lines may be specified at an arbitrary number (e.g., ten).
  • the present disclosure is not limited to this example.
  • the side plate 72 has an annular shape which is bent such that its part on the one end side in the rotation axis direction is located inward of the part on the other end side in the radial direction of the rotation shaft 70 .
  • the present disclosure is not limited to this example.
  • the side plate 72 is formed in a circular ring shape extending along the rotation axis direction, and may be connected to the outer peripheral edge parts 712 of the vanes 71 located radially outward on the one end side in the rotation axis direction.
  • the side plate 72 is connected to cover the outer peripheral edge parts 712 of the vanes 71 from a radially outward side of the rotation shaft 70 .
  • the present disclosure is not limited to this example.
  • the side plate 72 may be connected to the parts 71 a of the vanes 71 on the one end side in the rotation axis direction.
  • the main plate 73 and the side plate 72 do not overlap with each other as far as possible when viewed from the rotation axis direction so that undercutting is not caused when integrally molding the impeller 7 a.
  • the main plate 73 and the side plate 72 may overlap with each other when viewed from the rotation axis direction.
  • the inner peripheral edge parts 711 of the vanes 71 extend along the rotation axis direction.
  • the inner peripheral edge parts 711 of the vanes 71 may separate from the axis Z of the rotation shaft 70 from the main plate 73 -side toward the side plate 72 -side.
  • first and second impeller parts 7 aa, 7 ab that are configured similar to the impeller 7 a described in the above embodiments may be provided.
  • Main plates 73 a, 73 b of the impeller parts 7 aa, 7 ab may be connected together by a connecting member 75 .
  • Each vane 71 of the impeller parts 7 aa, 7 ab is configured such that the inlet angle ⁇ on each cross-sectional surface crossing the inner peripheral edge part 711 on the meridian plane of the impeller 7 a in a predetermined direction is made evenly in the entire region from a side plate 72 a, 72 b -side through a main plate 73 a, 73 b -side.
  • the outer peripheral edge parts 712 of the vanes 71 in the impeller parts 7 aa, 7 ab are configured to be away from the axis Z of the rotation shaft 70 from the main plates 73 a, 73 b -side toward the side plates 72 a, 72 b -side.
  • the inlet angle ⁇ on each cross-section perpendicular to the rotation axis direction on the meridian plane of the impeller 7 a is made evenly in the entire region from the side plate 72 -side through the main plate 73 -side.
  • the present disclosure is not limited to this example.
  • the inlet angle ⁇ on each cross-section perpendicular to the inner peripheral edge part 711 on the meridian plane of the impeller 7 a may be made evenly in the entire region from the side plate 72 -side through the main plate 73 -side.
  • blower 7 may be applied to another air-conditioning system as well as to the air-conditioning system 1 for a vehicle.
  • the present disclosure is not limited to a particular numeral for the component of the embodiment except, for example, when the numerical value of the component such as the number, value, amount, or range is referred to, when it is clearly shown to be particularly necessary, or when the component is obviously limited to its particular numeral in principle.
  • the component is not limited to this shape or positional relationship except, for example, in the case of its particularly explicit indication or in the case of the component limited to its particular shape, positional relationship or the like in principle.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US14/410,796 2012-06-26 2013-06-06 Centrifugal multi-blade blower Abandoned US20150192143A1 (en)

Applications Claiming Priority (5)

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JP2012-142803 2012-06-26
JP2012142803 2012-06-26
JP2013-100170 2013-05-10
JP2013100170A JP2014029149A (ja) 2012-06-26 2013-05-10 遠心式多翼送風機
PCT/JP2013/003549 WO2014002392A1 (ja) 2012-06-26 2013-06-06 遠心式多翼送風機

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US20150192143A1 true US20150192143A1 (en) 2015-07-09

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US (1) US20150192143A1 (enrdf_load_stackoverflow)
JP (1) JP2014029149A (enrdf_load_stackoverflow)
KR (1) KR101666923B1 (enrdf_load_stackoverflow)
CN (1) CN104411980B (enrdf_load_stackoverflow)
DE (1) DE112013003213T5 (enrdf_load_stackoverflow)
WO (1) WO2014002392A1 (enrdf_load_stackoverflow)

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US20150285261A1 (en) * 2014-04-07 2015-10-08 Halla Visteon Climate Control Corp. Blower with curved blades
US20160040683A1 (en) * 2013-03-15 2016-02-11 Regal Beloit America, Inc. Fan
US20170101993A1 (en) * 2015-10-07 2017-04-13 Samsung Electronics Co., Ltd. Turbofan for air conditioning apparatus
US9926832B2 (en) * 2015-04-24 2018-03-27 Briggs & Stratton Corporation Reverse fin cooling fan
US10167766B2 (en) 2015-04-24 2019-01-01 Briggs & Stratton Corporation Reverse fin cooling fan
EP3995698A1 (en) * 2020-11-05 2022-05-11 LG Electronics Inc. Centrifugal fan for refrigerator
GB2602987A (en) * 2021-01-22 2022-07-27 Cool T Ltd Fan apparatus and methods of use
US20240376908A1 (en) * 2021-08-04 2024-11-14 Gree Green Refrigeration Technology Center Co., Ltd. Of Zhuhai Centrifugal Fan Impeller, Fan and Air Conditioning System

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US10030667B2 (en) * 2016-02-17 2018-07-24 Regal Beloit America, Inc. Centrifugal blower wheel for HVACR applications
JP2018096323A (ja) * 2016-12-15 2018-06-21 株式会社ヴァレオジャパン 送風機
CN109083865B (zh) * 2018-08-16 2023-08-22 泛仕达机电股份有限公司 一种前向多翼离心风机及其叶轮
JP6973417B2 (ja) * 2019-01-07 2021-11-24 株式会社デンソー 遠心式送風機
EP3922860A4 (en) * 2019-02-07 2022-02-16 Mitsubishi Electric Corporation CENTRIFUGAL AIR BLOWER AND AIR CONDITIONER USING IT
JP7317235B2 (ja) * 2020-07-06 2023-07-28 三菱電機株式会社 多翼羽根車および遠心送風機
WO2025014112A1 (ko) * 2023-07-11 2025-01-16 한온시스템 주식회사 차량용 블로워 유닛
CN117267169B (zh) * 2023-11-23 2024-03-12 广东顺威精密塑料股份有限公司 一种变进口角的多翼离心叶轮及使用其的离心风机

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US20160040683A1 (en) * 2013-03-15 2016-02-11 Regal Beloit America, Inc. Fan
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US9926832B2 (en) * 2015-04-24 2018-03-27 Briggs & Stratton Corporation Reverse fin cooling fan
US10167766B2 (en) 2015-04-24 2019-01-01 Briggs & Stratton Corporation Reverse fin cooling fan
US20170101993A1 (en) * 2015-10-07 2017-04-13 Samsung Electronics Co., Ltd. Turbofan for air conditioning apparatus
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US10563657B2 (en) * 2015-10-07 2020-02-18 Samsung Electronics Co., Ltd. Turbofan for air conditioning apparatus
EP3995698A1 (en) * 2020-11-05 2022-05-11 LG Electronics Inc. Centrifugal fan for refrigerator
GB2602987A (en) * 2021-01-22 2022-07-27 Cool T Ltd Fan apparatus and methods of use
GB2602987B (en) * 2021-01-22 2023-01-11 Cool T Ltd Fan apparatus and method of use
US20240376908A1 (en) * 2021-08-04 2024-11-14 Gree Green Refrigeration Technology Center Co., Ltd. Of Zhuhai Centrifugal Fan Impeller, Fan and Air Conditioning System

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CN104411980B (zh) 2016-12-28
CN104411980A (zh) 2015-03-11
JP2014029149A (ja) 2014-02-13
DE112013003213T5 (de) 2015-04-02
KR20150031296A (ko) 2015-03-23
WO2014002392A1 (ja) 2014-01-03
KR101666923B1 (ko) 2016-10-17

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