WO2020230563A1 - 遠心送風機 - Google Patents

遠心送風機 Download PDF

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Publication number
WO2020230563A1
WO2020230563A1 PCT/JP2020/017395 JP2020017395W WO2020230563A1 WO 2020230563 A1 WO2020230563 A1 WO 2020230563A1 JP 2020017395 W JP2020017395 W JP 2020017395W WO 2020230563 A1 WO2020230563 A1 WO 2020230563A1
Authority
WO
WIPO (PCT)
Prior art keywords
air
outer peripheral
peripheral wall
impeller
ventilation passage
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.)
Ceased
Application number
PCT/JP2020/017395
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
翔 小坂
修三 小田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Denso Corp
Original Assignee
Denso Corp
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 Denso Corp filed Critical Denso Corp
Priority to CN202080026725.1A priority Critical patent/CN113677897A/zh
Publication of WO2020230563A1 publication Critical patent/WO2020230563A1/ja
Priority to US17/454,332 priority patent/US20220065263A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • 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
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • F04D29/424—Double entry casings
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • F04D29/4246—Fan casings comprising more than one outlet
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid 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
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • F04D25/166—Combinations of two or more pumps ; Producing two or more separate gas flows using fans
    • 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
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • F04D29/286—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors multi-stage rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet

Definitions

  • the present disclosure relates to a centrifugal blower capable of distinguishing between the air inside the vehicle and the air outside the vehicle and simultaneously inhaling the air.
  • a one-sided suction type centrifugal blower capable of distinguishing between vehicle interior air (hereinafter, also referred to as inside air) and vehicle interior outside air (hereinafter, also referred to as outside air) and simultaneously sucking is known (for example, a patent).
  • the centrifugal blower described in Patent Document 1 is configured such that air taken in from the outside is sucked into the inside of the impeller via a filter and blown out to the outer ventilation path in the radial direction of the impeller. ..
  • the radial outer ventilator of the impeller is partitioned by a partition wall into one axial upper ventilator and one axial lower ventilator of the impeller.
  • a separation cylinder is provided inside the impeller in the radial direction to separate the air taken in from the outside into the upper ventilation passage and the lower ventilation passage.
  • the separation cylinder is a tubular portion having a shape that extends from the air introduction portion provided between the impeller and the filter and the air inlet formed in the air introduction portion through the radial inside of the impeller and outward in the radial direction. Has. With this configuration, a part of the air taken in from the outside passes from the air inlet of the air introduction portion to the inside of the tubular portion, and flows to the lower ventilation passage through the impeller.
  • the centrifugal blower described in Patent Document 1 is configured to separately blow out the air sucked from one of the axial directions of the impeller into the upper and lower ventilation passages.
  • An object of the present disclosure is to provide a centrifugal blower capable of improving ventilation efficiency while suppressing an increase in physique.
  • the centrifugal blower is: It is possible to distinguish between the air inside the vehicle and the air outside the vehicle and inhale at the same time.
  • An inside / outside air box with an outside air inlet for introducing vehicle interior air and an inside / outside air inlet for introducing vehicle interior air,
  • An impeller that draws in the air introduced into the inside and outside air box from one side of the axis of rotation by rotating around the axis of rotation and blows it out in the direction away from the axis of rotation.
  • a scroll casing having a spiral outer wall (51) surrounding the radial outer side of the impeller and forming a ventilation path in which the flow path area expands along the rotation direction of the impeller.
  • a bell mouth portion provided on one side of the scroll casing in the axial direction and forming an air suction port to the impeller, and a bell mouth portion.
  • An air introduction part arranged between the bell mouth part and the inside / outside air box so as to overlap the suction port in the axial direction, and a tubular part connected to the air introduction part and at least partly arranged inside the impeller.
  • a separation cylinder that separates the air that passes through the suction port into the inner air that passes through the inside of the tubular portion and the outer air that passes through the outside of the tubular portion. It is arranged inside the scroll casing and has a partition portion that divides the ventilation passage into a first ventilation passage through which the outside air passes and a second ventilation passage through which the inside air passes.
  • the scroll casing has a nose portion that minimizes the scroll diameter, which is the distance from the rotation axis to the outer peripheral wall, and a winding end portion that maximizes the scroll diameter.
  • the suction port is divided into a first half region that guides air upstream of the ventilation passage and a second half region that guides air downstream of the ventilation passage by a reference line passing through the rotation axis and the nose.
  • the air introduction portion is arranged so that the area overlapping the first half region in the axial direction is larger than the area overlapping the second half region.
  • At least a part of the outer peripheral wall has a widening angle from the nose portion to the intermediate portion set between the nose portion and the winding end portion, which is larger than the expanding angle from the intermediate portion to the winding end portion.
  • the scroll casing has a larger flow path area of the ventilation passage when the outer wall has a large expansion angle than when the expansion angle is small. Therefore, when the divergence angle of the outer peripheral wall is large, the air pressure loss is reduced as compared with the case where the divergence angle is small.
  • the spread angle from the nose portion to the middle portion on the outer peripheral wall is larger than the spread angle from the middle portion to the winding end portion. Therefore, the pressure loss of the air flowing upstream of the ventilation path is reduced. According to this, since air easily flows from the flow path on the back side of the separation cylinder to the upstream of the ventilation path, it is possible to sufficiently secure the flow rate of the air flowing through the ventilation path.
  • the divergence angle from the intermediate portion to the winding end portion of the outer peripheral wall is smaller than the divergence angle of the outer peripheral wall from the nose portion to the intermediate portion. The increase in size is suppressed.
  • centrifugal blower of the present disclosure it is possible to improve the blowing efficiency while suppressing the increase in size of the physique.
  • FIG. 2 is a sectional view taken along line II-II of FIG.
  • FIG. 3 is a sectional view taken along line III-III of FIG. It is explanatory drawing for demonstrating the spread angle of the scroll casing of the centrifugal blower which concerns on 1st Embodiment.
  • FIG. 2 is a sectional view taken along line II-II of FIG.
  • FIG. 3 is a sectional view taken along line III-III of FIG. It is explanatory drawing for demonstrating the spread angle of the scroll casing of the centrifugal blower which concerns on 1st Embodiment.
  • FIG. 2 is a
  • FIG. 7 is a sectional view taken along line VIII-VIII of FIG. It is explanatory drawing for demonstrating the spread angle of the scroll casing of the centrifugal blower which concerns on 2nd Embodiment. It is explanatory drawing for demonstrating the flow of air in the centrifugal blower which concerns on 2nd Embodiment.
  • Centrifugal blower 1 is arranged inside the instrument panel at the front of the vehicle interior.
  • the centrifugal blower 1 includes an inner / outer air box 10, a filter 20, an impeller 30, an electric motor 40, a scroll casing 50, a bell mouth portion 60, a partition portion 57, and a separation cylinder 70.
  • the arrows indicating up / down, front / back, left / right in each drawing indicate the up / down direction DR1, the front / rear direction DR2, and the left / right direction DR3 when the centrifugal blower 1 is mounted on the vehicle.
  • the inner / outer air box 10 is arranged on the upper side of the centrifugal blower 1.
  • an outside air introduction port 11 for introducing outside air On the upper surface of the inside / outside air box 10, in order from the front side of the DR2 in the front-rear direction, an outside air introduction port 11 for introducing outside air, a first inside air introduction port 12 for introducing inside air, and a second inside air introduction port for introducing inside air. 13 is formed.
  • the outside air from the outside air introduction port 11 or the inside air from the first inside air introduction port 12 is introduced into the first introduction space 101, and the inside air from the second inside air introduction port 13 is introduced.
  • the introduction space 102 is formed.
  • the first introduction space 101 and the second introduction space 102 communicate with each other via the communication passage 103.
  • a first inside / outside air door 14 and a second inside / outside air door 15 are provided inside the inside / outside air box 10.
  • the first inside / outside air door 14 is a door that selectively opens and closes the outside air introduction port 11 and the first inside / outside air introduction port 12.
  • the second inside / outside air door 15 is a door that selectively opens / closes the second inside / outside air introduction port 13 and the communication passage 103.
  • the first inside / outside air door 14 and the second inside / outside air door 15 are composed of rotary doors.
  • the first inside / outside air door 14 and the second inside / outside air door 15 may be composed of doors other than the rotary door.
  • the filter 20 is arranged below the inside / outside air box 10.
  • the filter 20 collects foreign matter contained in the air introduced into the inside / outside air box 10.
  • the inner / outer air box 10 and the filter 20 have a rectangular shape when viewed from above.
  • the impeller 30 is a centrifugal fan that sucks in from one side of the fan axis CL in the axial direction and blows out the sucked air in a direction away from the fan axis CL, which is the rotation axis.
  • the impeller 30 is composed of a sirocco fan.
  • the impeller 30 is not limited to a sirocco fan, and may be composed of a radial fan, a turbo fan, or the like.
  • the axial direction of the impeller 30 is a direction extending along the fan axis CL.
  • the radial direction of the impeller 30 is orthogonal to the fan axis CL and extends radially around the fan axis CL.
  • the impeller 30 has a plurality of first blades 31, a plurality of second blades 32, a main plate 33, a side plate 34, and a separation plate 35.
  • the plurality of first blades 31 are arranged side by side around the fan axis CL.
  • a first wing passage 310 through which air flows is formed between the plurality of first blades 31.
  • the plurality of second blades 32 are arranged side by side around the fan axis CL.
  • the plurality of second blades 32 are positioned on the other side in the axial direction with respect to the plurality of first blades 31.
  • a second wing passage 320 through which air flows is formed between the plurality of second blades 32.
  • the main plate 33 is composed of a disk-shaped member centered on the fan axis CL.
  • the main plate 33 is provided with a boss portion 331 in which the shaft 42 of the electric motor 40 is connected so as not to rotate relative to the central portion thereof.
  • the lower ends of the plurality of second blades 32 are fixed to the radial outer portion of the impeller 30 of the main plate 33.
  • the side plate 34 is a member that reinforces the impeller 30.
  • the side plate 34 is formed in a ring shape centered on the fan axis CL.
  • the side plate 34 supports a portion of the plurality of first blades 31 located on one side in the axial direction.
  • the separation plate 35 is a member that connects the plurality of first blades 31 and the plurality of second blades 32.
  • the separation plate 35 includes air flowing through the first wing passage 310 formed between the plurality of first blades 31 and air flowing through the second wing passage 320 formed between the plurality of second blades 32. It is also a member that suppresses the mixing of air.
  • the separation plate 35 has a ring shape centered on the fan axis CL, and is composed of a plate-shaped member whose plate surface expands so as to intersect the fan axis CL.
  • the lower end portions of the plurality of first blades 31 are fixed to the plate surface on one side in the axial direction of the impeller 30, and the upper end portions of the plurality of second blades 32 are fixed to the plate surface on the other side in the axial direction. Is fixed.
  • a plurality of first blades 31, a plurality of second blades 32, a main plate 33, a side plate 34, and a separation plate 35 are integrally molded by a molding technique such as injection molding. It is configured as an integrally molded product.
  • the electric motor 40 is an electric motor that rotates the impeller 30.
  • the electric motor 40 has a main body 41 that generates power for rotating the impeller 30, and a shaft 42 that is rotated by the power of the main body 41.
  • the shaft 42 extends from the main body 41 toward one side in the axial direction of the impeller 30.
  • the shaft 42 is fixed to the main plate 33 of the impeller 30 by the motor cap 43. As a result, when the shaft 42 rotates, the impeller 30 rotates.
  • the scroll casing 50 is a housing that houses the impeller 30 inside.
  • the scroll casing 50 functions to rectify the airflow radiating from the impeller 30 into a flow in the circumferential direction of the impeller 30.
  • the scroll casing 50 has a spiral outer peripheral wall 51 surrounding the impeller 30 in the radial direction and a discharge wall 52 connected to the outer peripheral wall 51.
  • the scroll casing 50 forms a ventilation passage 53 and a discharge passage 54 in which the flow path area expands along the rotation direction R of the impeller 30.
  • the scroll casing 50 has a nose portion Ps having a minimum scroll diameter rs, which is the distance from the fan axis CL to the outer peripheral wall 51, and a winding end portion Pe having a maximum scroll diameter rs.
  • the nose portion Ps is a portion that is the starting point of the ventilation passage 53, and is a portion that minimizes the flow path area in the ventilation passage 53.
  • the radius line passing through the fan axis CL and the nose portion Ps is set as the reference line Lb.
  • the reference line Lb is set as the reference angle (that is, 0 °) of the winding angle ⁇ .
  • the winding angle ⁇ is an angle in the circumferential direction centered on the fan axis CL.
  • the winding end portion Pe is a portion that is the end point of the ventilation passage 53, and is a portion that has the maximum flow path area in the ventilation passage 53.
  • a discharge wall 52 is connected to the winding end portion Pe. Unlike the outer peripheral wall 51, the discharge wall 52 extends linearly along the left-right direction DR3. The discharge wall 52 forms a discharge path 54 that blows air toward an air conditioning unit of a vehicle air conditioner (not shown). As a result, the air flowing inside the scroll casing 50 is introduced into the air conditioning unit.
  • the air conditioning unit adjusts the air introduced from the centrifugal blower 1 to a desired temperature and blows it into the vehicle interior.
  • the air conditioning unit is configured to adjust the air introduced from the centrifugal blower 1 to a desired temperature by a heat exchanger such as an evaporator or a heater core.
  • the scroll casing 50 is provided with a bell mouth portion 60 that forms an air suction port 61 for the impeller 30 on the upper end surface portion 55 on one side of the impeller 30 in the axial direction.
  • the bell mouth portion 60 constitutes a peripheral portion of the suction port 61.
  • the bell mouth portion 60 has an arcuate cross-sectional shape so that air can flow smoothly through the suction port 61. As a result, the air that has passed through the filter 20 is sucked into the impeller 30 from the bell mouth portion 60.
  • the region of the suction port 61 that guides the air upstream of the air passage 53 is the first half region 62, and the region that guides the air downstream of the air passage 53 is the second half region 63.
  • the first half region 62 is a region closer to the upstream than the downstream of the ventilation passage 53 when the suction port 61 is divided into two regions by the reference line Lb.
  • the latter half region 63 is a region closer to the downstream side than the upstream side of the ventilation passage 53 when the suction port 61 is divided into two regions by the reference line Lb.
  • the upper end surface portion 55 of the scroll casing 50 is provided with a mounting frame 56 for mounting the above-mentioned inner / outer air box 10 and the filter 20.
  • the inside / outside air box 10 and the filter 20 are attached to the attachment frame 56.
  • a partition portion 57 for partitioning the ventilation passage 53 and the discharge passage 54 into the first ventilation passage 531 and the second ventilation passage 532 is provided inside the scroll casing 50.
  • the partition portion 57 is provided at a position corresponding to the separating plate 35 of the impeller 30.
  • the partition portion 57 is provided so as to overlap the separating plate 35 in the radial direction of the impeller 30, for example.
  • the first ventilation passage 531 is formed by the first outer peripheral wall portion 511 of the outer peripheral wall 51.
  • the first outer peripheral wall portion 511 is an upper portion of the outer peripheral wall 51 that overlaps with the first blade 31 in the radial direction.
  • the second ventilation passage 532 is formed by the second outer peripheral wall portion 512 on the outer peripheral wall 51.
  • the second outer peripheral wall portion 512 is a lower portion of the outer peripheral wall 51 that overlaps with the second blade 32 in the radial direction.
  • the separation cylinder 70 is a tubular member extending in the axial direction of the impeller 30.
  • the separation cylinder 70 has openings located at both ends in the axial direction.
  • the air passing through the suction port 61 is separated by the separation cylinder 70 into inner air passing through the inside of the separation cylinder 70 and outer air passing through the outside of the separation cylinder 70.
  • the separation cylinder 70 is connected to the air introduction portion 71 and the air introduction portion 71 arranged between the bell mouth portion 60 and the inside / outside air box 10, and at least a part of the separation cylinder 70 is arranged inside the impeller 30. Has 72.
  • the air introduction portion 71 is formed with an air inlet 710 for introducing air inside the tubular portion 72.
  • the air inlet 710 opens below the second introduction space 102 of the inner / outer air box 10 so that the air introduced into the second introduction space 102 of the inner / outer air box 10 flows into the air inlet 710.
  • the air introduction portion 71 has a substantially rectangular outer shape when viewed from one side in the axial direction.
  • the air introduction portion 71 covers substantially half of the suction port 61 and the bell mouth portion 60.
  • the air introduction portion 71 is arranged so that the area overlapping the first half region 62 of the suction port 61 in the axial direction is larger than the area overlapping the second half region 63 of the suction port 61. Specifically, the air introduction portion 71 covers a portion of the suction port 61 and the bell mouth portion 60 that overlaps with the second introduction space 102 in the vertical DR1.
  • the air introduction portion 71 has three edge portions 711, 712, 713 in contact with the mounting frame 56 of the scroll casing 50, and an outer edge portion 714 that overlaps with the suction port 61 in the axial direction.
  • the outer edge portion 714 is not in contact with the mounting frame 56 of the scroll casing 50.
  • a tubular portion 72 is connected to the air introduction portion 71.
  • the upper portion 721 connected to the air introduction portion 71 is inclined in the axial direction, and the lower portion 722 located inside the scroll casing 50 extends vertically along the fan axis CL.
  • the tubular portion 72 is inclined in the axial direction so that the center at the lower end of the upper portion 721 connected to the air introduction portion 71 intersects the fan axis CL. Further, the lower portion 722 of the tubular portion 72 has a shape that expands in the radial direction toward the other side in the axial direction.
  • the lower end of the lower portion 722 is provided at a position corresponding to the separating plate 35 of the impeller 30.
  • the lower end of the lower portion 722 is provided so as to overlap the separating plate 35 in the radial direction of the impeller 30, for example.
  • the first outer peripheral wall portion 511 and the second outer peripheral wall portion 512 will be described with reference to FIGS. 3, 4, and 5.
  • the first outer peripheral wall portion 511 and the second outer peripheral wall portion 512 are formed by a scroll curve having a predetermined spread angle starting from the nose portion Ps.
  • the expansion angle ⁇ 1 from the nose portion Ps to the intermediate portion Pm set between the nose portion Ps and the winding end portion Pe is set, and the expansion angle ⁇ 1 from the intermediate portion Pm to the winding end portion Pe is 2 Is bigger than.
  • the first outer peripheral wall portion 511 is composed of a scroll curve in which the range R ⁇ 1 from the nose portion Ps to the intermediate portion Pm is formed by a constant expansion angle ⁇ 1. Further, the first outer peripheral wall portion 511 is composed of a scroll curve in which the range R ⁇ 2 from the intermediate portion Pm to the winding end portion Pe is formed by a constant expansion angle ⁇ 2. The spread angle ⁇ 1 is larger than the spread angle ⁇ 2.
  • the scroll diameter rs of the first outer peripheral wall portion 511 increases as the winding angle ⁇ increases.
  • the scroll diameter rs of the first outer peripheral wall portion 511 changes in a logarithmic spiral in the range R ⁇ 1 from the nose portion Ps to the intermediate portion Pm as shown by the following mathematical formula F1, from the intermediate portion Pm to the winding end portion Pe.
  • the range R ⁇ 2 of it changes in a logarithmic spiral as shown by the following mathematical formula F2.
  • the setting range of the intermediate portion Pm which is a change point for changing the spread angle in the first outer peripheral wall portion 511, will be described with reference to FIG.
  • the virtual line extending along the outer edge portion 714 of the air introduction portion 71 is shown as the first virtual line L1
  • the virtual line extending in the direction orthogonal to the outer edge portion 714 while passing through the fan axis CL is the second virtual line. It is shown as L2.
  • the first outer peripheral wall portion 511 intersects the second virtual line L2 at the rearmost position.
  • the position of the first outer peripheral wall portion 511 that intersects with the second virtual line L2 is referred to as an intersection position Pc.
  • the intersection position Pc is a position in the first ventilation passage 531 that equally divides the region where air flows from the flow path between the air introduction portion 71 and the bell mouth portion 60 into an upstream region and a downstream region. Therefore, if the intermediate portion Pm is set at a position advanced in the rotation direction R of the impeller 30 from the intersection position Pc or the intersection position Pc on the first outer peripheral wall portion 511, a wide range from the nose portion Ps to the intermediate portion Pm can be obtained.
  • the expansion angle ⁇ 1 of the first outer peripheral wall portion 511 becomes large. As a result, the flow rate of air flowing upstream of the first ventilation passage 531 increases.
  • first outer peripheral wall portion 511 intersects the first virtual line L1 at the rightmost position and the leftmost position.
  • the position advanced from the intersection position Pc in the rotation direction R of the impeller 30 is referred to as an extension position Px.
  • the extension position Px is the most downstream position of the first ventilation passage 531 in the region where air flows from the flow path between the air introduction portion 71 and the bell mouth portion 60. Therefore, even if the intermediate portion Pm is set to a position advanced in the rotation direction R of the impeller 30 from the extension position Px, the air flow between the air introduction portion 71 and the bell mouth portion 60 is hardly affected. Conceivable.
  • the intermediate portion Pm is set to the range ST from the intersection position Pc to the extension position Px. Specifically, the intermediate portion Pm is set at a position substantially intermediate between the intersection position Pc and the extension position Px on the first outer peripheral wall portion 511.
  • the second outer peripheral wall portion 512 has a constant spreading angle ⁇ 3 from the nose portion Ps to the winding end portion Pe.
  • the constant spread angle does not mean a state in which the spread angle does not change in a strict sense, but also includes a state in which the spread angle slightly changes due to a manufacturing error or the like.
  • the second outer peripheral wall portion 512 is composed of a scroll curve in which the range R ⁇ 3 from the nose portion Ps to the winding end portion Pe is formed by a constant expansion angle ⁇ 3.
  • the scroll diameter rs of the second outer peripheral wall portion 512 increases as the winding angle ⁇ increases.
  • the scroll diameter rs of the second outer peripheral wall portion 512 changes in a logarithmic spiral as shown by the following mathematical formula F3 in the range R ⁇ 3 from the nose portion Ps to the winding end portion Pe.
  • the expansion angle ⁇ 1 of the first outer peripheral wall portion 511 is set to a value obtained by adding a predetermined angle ⁇ to the expansion angle ⁇ 3 of the second outer peripheral wall portion 512.
  • the expansion angle ⁇ 2 of the first outer peripheral wall portion 511 is set to a value obtained by subtracting a predetermined angle ⁇ from the expansion angle ⁇ 3 of the second outer peripheral wall portion 512.
  • the spread angle ⁇ 1 of the first outer peripheral wall portion 511 is 4.5 [deg]
  • the spread angle ⁇ 2 of the first outer peripheral wall portion 511 is 2.5 [deg]
  • ⁇ 3 is set to 3.5 [deg].
  • the centrifugal blower 1 can be set as an air suction mode to an outside air mode for sucking outside air, an inside air mode for sucking inside air, and an inside / outside air mode for separately sucking outside air and inside air at the same time.
  • the outside air mode is a mode in which only the outside air is introduced inside the inside / outside air box 10.
  • the centrifugal blower 1 is configured such that the first inside / outside air door 14 is displaced at a position where the outside air introduction port 11 is opened and the second inside / outside air door 15 is displaced at a position where the communication passage 103 is opened in the outside air mode. There is.
  • the inside air mode is a mode in which only the inside air is introduced inside the inside / outside air box 10.
  • the first inside / outside air door 14 is displaced to a position where the first inside air introduction port 12 is opened, and the second inside / outside air door 15 is displaced to a position where the second inside air introduction port 13 is opened. It is configured as follows.
  • the inside / outside air mode is a mode for introducing outside air and inside air inside the inside / outside air box 10.
  • the first inside / outside air door 14 is displaced to a position where the outside air introduction port 11 is opened
  • the second inside / outside air door 15 is displaced to a position where the second inside / outside air introduction port 13 is opened in the inside / outside air mode. It is configured in.
  • the outside air introduced into the first introduction space 101 is sucked into the first wing passage 310 of the impeller 30 via the outside of the separation cylinder 70, as shown by the solid arrow Fao in FIG.
  • the outside air sucked into the first wing passage 310 is blown out to the first ventilation passage 531.
  • the spreading angle ⁇ 1 from the nose portion Ps to the intermediate portion Pm in the first outer peripheral wall portion 511 is larger than the spreading angle ⁇ 2 from the intermediate portion Pm to the winding end portion Pe. ing. Therefore, the ventilation resistance upstream of the first ventilation passage 531 is reduced, and the pressure loss of the air flowing upstream of the first ventilation passage 531 is reduced. According to this, air easily flows from the flow path on the back side of the separation cylinder 70 to the upstream of the first ventilation passage 531. Therefore, it is possible to sufficiently secure the flow rate of the air flowing through the first ventilation passage 531.
  • the inside air introduced into the second introduction space 102 is sucked into the second wing passage 320 of the impeller 30 via the inside of the separation cylinder 70, as shown by the alternate long and short dash arrow Fai in FIG.
  • the inside air sucked into the second wing passage 320 is blown out to the second ventilation passage 532.
  • the outside air flowing through the first ventilation passage 531 and the inside air flowing through the second ventilation passage 532 are introduced into the air conditioning unit from the scroll casing 50, adjusted to a desired temperature inside the air conditioning unit, and then different outlets. Is blown into the passenger compartment.
  • the spread angle ⁇ 1 from the nose portion Ps to the intermediate portion Pm in the first outer peripheral wall portion 511 of the scroll casing 50 is larger than the spread angle ⁇ 2 from the intermediate portion Pm to the winding end portion Pe. ing.
  • the pressure loss of the air flowing upstream of the first ventilation passage 531 is reduced. Therefore, air easily flows from the flow path on the back side of the separation cylinder 70 to the upstream of the first ventilation passage 531, and it is possible to sufficiently secure the flow rate of the air flowing through the first ventilation passage 531.
  • the divergence angle ⁇ 2 from the intermediate portion Pm to the winding end portion Pe in the first outer peripheral wall portion 511 is smaller than the divergence angle ⁇ 1 of the first outer peripheral wall portion 511 from the nose portion Ps to the intermediate portion Pm. , The increase in the physique of the scroll casing 50 is suppressed.
  • centrifugal blower 1 of the present embodiment it is possible to improve the blowing efficiency while suppressing the increase in size of the physique.
  • the air passing through the inside of the separation cylinder 70 flows through the second ventilation passage 532. Therefore, the pressure loss of air upstream of the second ventilation passage 532 is unlikely to occur. Despite this, if the second outer peripheral wall portion 512 is changed in the spread angle in the same manner as the first outer peripheral wall portion 511, the air flow downstream of the second ventilation passage 532 may be unnecessarily restricted. There is.
  • the second outer peripheral wall portion 512 has a constant spreading angle ⁇ 3 from the nose portion Ps to the intermediate portion Pm. According to this, since the air flow downstream of the second ventilation passage 532 is not unnecessarily restricted, it is possible to sufficiently secure the flow rate of the air flowing through the second ventilation passage 532. ..
  • the centrifugal blower 1 is set at a position where the intermediate portion Pm is ahead of the intersection position Pc or the intersection position Pc in the first outer peripheral wall portion 511 in the rotation direction R of the impeller 30. According to this, the spread angle becomes large in a wide range from the nose portion Ps to the intermediate portion Pm, and the pressure loss of the air flowing upstream of the first ventilation passage 531 is sufficiently reduced. As a result, air easily flows from the flow path on the back side of the separation cylinder 70 to the upstream of the first ventilation passage 531.
  • the intermediate portion Pm is set in the range from the intersection position Pc to the extension position Px.
  • the centrifugal blower 1 of the present embodiment is configured such that most of the tubular portion 72 of the separation cylinder 70 overlaps with the air introduction portion 71 in the axial direction in the vicinity of the suction port 61.
  • the upper portion 721 and the lower portion 722 each have an axis so that the center at the lower end portion of the lower portion 722 of the tubular portion 72 intersects the fan axis CL. It is tilted in the direction.
  • the center CLm of the tubular portion 72 near the suction port 61 is located on the rear side of the fan axis CL.
  • the area of the region outside the tubular portion 72 of the suction port 61 that is covered by the air introduction portion 71 is smaller than the area of the region that is not covered by the air introduction portion 71. Therefore, the pressure loss of the air flowing through the region covered by the air introduction portion 71 becomes large, and there is a concern that the flow rate of the air flowing from the flow path on the back side of the separation cylinder 70 to the upstream of the first ventilation passage 531 decreases.
  • a third virtual line of the first outer peripheral wall portion 511 is parallel to the outer edge portion 714 of the air introduction portion 71 and extends so as to equally divide the outer region of the tubular portion 72 at the suction port 61. It is shown as a virtual line L3.
  • the first outer peripheral wall portion 511 intersects the first virtual line L1 at the leftmost extension position Px, and intersects the third virtual line L3 at a position slightly ahead of the extension position Px. ing.
  • the position of the first outer peripheral wall portion 511 that intersects with the third virtual line L3 is referred to as an equally divided position Py.
  • the equally divided position Py is a position advanced in the rotation direction R of the impeller 30 from the intersection position Pc and the extension position Px. Therefore, if the equally divided position Py is set as the upper limit of the set position of the intermediate portion Pm, even if the pressure loss of the air flowing through the region covered by the air introduction portion 71 becomes large, the flow path on the back side of the separation cylinder 70 becomes the first. 1 It is possible to facilitate the flow of air upstream of the ventilation passage 531.
  • outside air is introduced from the outside air introduction port 11 into the first introduction space 101 and from the second inside air introduction port 13 as shown in FIG. 10 in the inside / outside air mode.
  • Inside air is introduced into the second introduction space 102.
  • the outside air introduced into the first introduction space 101 is sucked into the first wing passage 310 of the impeller 30 via the outside of the separation cylinder 70, as shown by the solid arrow Fao in FIG.
  • the outside air sucked into the first wing passage 310 is blown out to the first ventilation passage 531.
  • the spreading angle ⁇ 1 from the nose portion Ps to the intermediate portion Pm in the first outer peripheral wall portion 511 is larger than the spreading angle ⁇ 2 from the intermediate portion Pm to the winding end portion Pe. ing. Therefore, the ventilation resistance upstream of the first ventilation passage 531 is reduced, and the pressure loss of the air flowing upstream of the first ventilation passage 531 is reduced. According to this, air easily flows from the flow path on the back side of the separation cylinder 70 to the upstream of the first ventilation passage 531. Therefore, it is possible to sufficiently secure the flow rate of the air flowing through the first ventilation passage 531.
  • the upper limit of the set position of the intermediate portion Pm is not the extension position Px but the equally divided position Py. That is, in the first outer peripheral wall portion 511 of the present embodiment, the intermediate portion Pm is set to the range ST from the intersection position Pc to the equally divided position Py. According to this, the intermediate portion Pm can be set at an appropriate position in consideration of the pressure loss on the suction port 61 side.
  • the inside air introduced into the second introduction space 102 is sucked into the second wing passage 320 of the impeller 30 via the inside of the separation cylinder 70, as shown by the alternate long and short dash arrow Fai in FIG.
  • the inside air sucked into the second wing passage 320 is blown out to the second ventilation passage 532.
  • the centrifugal blower 1 described above has the same configuration as that of the first embodiment. Therefore, the centrifugal blower 1 of the present embodiment can obtain the same effect as that of the first embodiment from the same configuration as that of the first embodiment.
  • the equally divided position Py is the upper limit of the set position of the intermediate portion Pm, so that the intermediate portion Pm can be set to an appropriate position in consideration of the pressure loss on the suction port 61 side. It will be possible. For example, when the pressure loss of the air flowing through the region covered by the air introduction portion 71 at the suction port 61 becomes large, the flow on the back side of the separation cylinder 70 is made by moving the intermediate portion Pm closer to the equally divided position Py than the extension position Px. It is possible to facilitate the flow of air from the road to the upstream of the first ventilation passage 531.
  • the lower limit of the setting range of the intermediate portion Pm may be the intersection position Pc.
  • the intermediate portion Pm may be set at a position between the nose portion Ps and the intersection position Pc.
  • the upper limit of the setting range of the intermediate portion Pm is desirable, but not limited to, the upper limit of the setting range of the intermediate portion Pm to be the extension position Px or the equally divided position Py.
  • the intermediate portion Pm may be set at a position between the equally divided position Py and the winding end portion Pe.
  • the upper limit of the setting range of the intermediate portion Pm is desirable, but not limited to, the upper limit of the setting range of the intermediate portion Pm to be the extension position Px or the equally divided position Py.
  • the intermediate portion Pm may be set at a position between the equally divided position Py and the winding end portion Pe.
  • the second outer peripheral wall portion 512 has a constant spread angle ⁇ 3 from the nose portion Ps to the winding end portion Pe.
  • the expansion angle from the nose portion Ps to the intermediate portion Pm is larger than the expansion angle from the intermediate portion Pm to the winding end portion Pe. You may.
  • the centrifugal blower includes an inner / outer air box, an impeller, a scroll casing, a bell mouth portion, a separation cylinder, and a partition portion. , Equipped with.
  • the outer peripheral wall of the scroll casing has a widening angle from the nose portion to the intermediate portion set between the nose portion and the winding end portion, which is larger than the expanding angle from the intermediate portion to the winding end portion.
  • the air introduction portion has an outer edge portion that overlaps with the suction port in the axial direction.
  • the intermediate portion is set at an intersection position or a position advanced in the rotation direction of the impeller from the intersection position. However, it is a position of the outer peripheral wall that intersects the virtual line that passes through the rotation axis and extends in the direction orthogonal to the outer edge portion.
  • the intersection position on the outer wall is the position that divides the area where air flows from the flow path between the air introduction part and the bell mouth into the upstream area and the downstream area in the ventilation path. Therefore, if the intermediate portion is set at an intersection position on the outer peripheral wall or a position ahead of the intersection position in the rotation direction of the impeller, the spread angle becomes large in a wide range from the nose portion to the intermediate portion. According to this, the pressure loss of the air flowing upstream of the ventilation path is sufficiently reduced. As a result, air can easily flow from the flow path on the back side of the separation cylinder to the upstream of the ventilation path.
  • the intermediate portion is set in the range from the intersection position to the extension position.
  • the position is ahead of the intersection position in the direction of rotation of the impeller.
  • the extension position on the outer peripheral wall is the most downstream position of the ventilation path where air flows from the flow path between the air introduction part and the bell mouth. Therefore, if the intermediate portion is set in the range from the intersection position to the extension position, the expansion angle of the outer peripheral wall becomes large in a wide range from the nose portion to the intermediate portion. According to this, the pressure loss of the air flowing upstream of the ventilation passage is sufficiently reduced, so that the air easily flows from the flow path on the back side of the separation cylinder to the upstream of the ventilation passage. In particular, since the intermediate portion is limited to the range up to the extension position, it is possible to suppress the increase in the size of the scroll casing while ensuring the flow rate of the air flowing through the ventilation passage.
  • the intermediate portion is set in the range from the intersection position to the equally divided position.
  • the equally divided position is the position that intersects the virtual line that is parallel to the outer edge of the outer peripheral wall and extends so as to equally divide the outer region of the tubular portion at the suction port, and the blade is more than the intersection position. It is a position advanced in the direction of rotation of the car.
  • the area outside the tubular portion at the suction port is covered with the air introduction portion.
  • the area of the area to be covered is smaller than the area of the area not covered by the air introduction. In this case, the pressure loss of the air flowing through the region covered by the air introduction portion becomes large, and there is a concern that the flow rate of the air flowing from the flow path on the back side of the separation cylinder to the upstream of the ventilation path decreases.
  • the position intersecting the virtual line extending so as to equally divide the outer region of the tubular portion at the suction port is set as the equally divided position, and the equally divided position is set as the upper limit of the set position of the intermediate portion. It is possible to facilitate the flow of air from the flow path on the back side of the separation cylinder to the upstream of the ventilation passage.
  • the outer peripheral wall has a first outer peripheral wall portion forming the first ventilation passage and a second outer peripheral wall portion forming the second ventilation passage.
  • the divergence angle from the nose portion to the intermediate portion of the first outer peripheral wall portion is larger than the divergence angle from the intermediate portion to the winding end portion.
  • the second outer peripheral wall portion has a constant spread angle from the nose portion to the winding end portion.
  • the divergence angle from the nose portion to the intermediate portion in the first outer peripheral wall portion is larger than the divergence angle from the intermediate portion to the winding end portion, so that the pressure of the air flowing upstream of the first ventilation passage is increased. Loss is reduced. As a result, air can easily flow from the flow path on the back side of the separation cylinder to the upstream of the first ventilation passage, so that a sufficient flow rate of air flowing through the first ventilation passage can be secured.
  • the air passing through the inside of the separation cylinder flows in the second ventilation passage, so that the pressure loss of the air upstream of the second ventilation passage is unlikely to occur.
  • the second outer peripheral wall is expanded in the same manner as the first outer peripheral wall and the expansion angle is changed, there is a possibility that the air flow downstream of the second ventilation path is unnecessarily restricted.
  • the second outer peripheral wall portion has a constant divergence angle from the nose portion to the intermediate portion. According to this, since the air flow downstream of the second ventilation passage is not unnecessarily restricted, it is possible to sufficiently secure the flow rate of the air flowing through the second ventilation passage.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air-Conditioning For Vehicles (AREA)
PCT/JP2020/017395 2019-05-15 2020-04-22 遠心送風機 Ceased WO2020230563A1 (ja)

Priority Applications (2)

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CN202080026725.1A CN113677897A (zh) 2019-05-15 2020-04-22 离心送风机
US17/454,332 US20220065263A1 (en) 2019-05-15 2021-11-10 Centrifugal blower

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JP2019-092293 2019-05-15
JP2019092293A JP7200824B2 (ja) 2019-05-15 2019-05-15 遠心送風機

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US17/454,332 Continuation US20220065263A1 (en) 2019-05-15 2021-11-10 Centrifugal blower

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JP (1) JP7200824B2 (enExample)
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JP7003902B2 (ja) * 2018-12-14 2022-02-04 株式会社デンソー 遠心ファン、遠心送風機
JP7310578B2 (ja) * 2019-12-06 2023-07-19 株式会社デンソー 遠心送風機
US11473593B2 (en) * 2020-03-04 2022-10-18 Lg Electronics Inc. Blower comprising a fan installed in an inner space of a lower body having a first and second upper body positioned above and a space formed between the bodies wherein the bodies have a first and second openings formed through respective boundary surfaces which are opened and closed by a door assembly
EP4184014B1 (en) 2020-03-04 2025-05-07 LG Electronics, Inc. Blower
JP7374344B2 (ja) * 2020-11-27 2023-11-06 三菱電機株式会社 空気調和装置

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JP2018091274A (ja) * 2016-12-06 2018-06-14 株式会社ヴァレオジャパン 遠心送風機
JP2019011694A (ja) * 2017-06-29 2019-01-24 株式会社ヴァレオジャパン 車両用空調装置のための遠心送風機

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CN109863311B (zh) * 2016-10-18 2021-09-14 法雷奥日本株式会社 离心式送风机
JP2018155151A (ja) * 2017-03-16 2018-10-04 株式会社ヴァレオジャパン 車両用空調装置のための遠心送風機
CN109469645B (zh) * 2017-05-23 2023-12-15 宁波方太厨具有限公司 一种离心风机蜗壳
JP7310578B2 (ja) * 2019-12-06 2023-07-19 株式会社デンソー 遠心送風機

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JPS61229999A (ja) * 1985-04-03 1986-10-14 Matsushita Refrig Co 送風装置
JPH1137096A (ja) * 1997-07-17 1999-02-09 Zexel Corp ブロワユニット
JP2018091274A (ja) * 2016-12-06 2018-06-14 株式会社ヴァレオジャパン 遠心送風機
JP2019011694A (ja) * 2017-06-29 2019-01-24 株式会社ヴァレオジャパン 車両用空調装置のための遠心送風機

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JP2020186692A (ja) 2020-11-19
CN113677897A (zh) 2021-11-19
US20220065263A1 (en) 2022-03-03

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