EP3404270A1 - Fan with vaned diffuser and cleaner provided with same - Google Patents
Fan with vaned diffuser and cleaner provided with same Download PDFInfo
- Publication number
- EP3404270A1 EP3404270A1 EP18173039.1A EP18173039A EP3404270A1 EP 3404270 A1 EP3404270 A1 EP 3404270A1 EP 18173039 A EP18173039 A EP 18173039A EP 3404270 A1 EP3404270 A1 EP 3404270A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- stationary blade
- stationary
- fan
- stationary blades
- impeller
- 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.)
- Withdrawn
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—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
- F04D29/4253—Fan casings with axial entry and discharge
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D23/00—Other rotary non-positive-displacement pumps
- F04D23/008—Regenerative 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
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
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- A—HUMAN NECESSITIES
- A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
- A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
- A47L5/00—Structural features of suction cleaners
- A47L5/12—Structural features of suction cleaners with power-driven air-pumps or air-compressors, e.g. driven by motor vehicle engine vacuum
- A47L5/22—Structural features of suction cleaners with power-driven air-pumps or air-compressors, e.g. driven by motor vehicle engine vacuum with rotary fans
- A47L5/24—Hand-supported suction cleaners
-
- A—HUMAN NECESSITIES
- A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
- A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
- A47L5/00—Structural features of suction cleaners
- A47L5/12—Structural features of suction cleaners with power-driven air-pumps or air-compressors, e.g. driven by motor vehicle engine vacuum
- A47L5/22—Structural features of suction cleaners with power-driven air-pumps or air-compressors, e.g. driven by motor vehicle engine vacuum with rotary fans
- A47L5/38—Built-in suction cleaner installations, i.e. with fixed tube system to which, at different stations, hoses can be connected
-
- 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
- F04D29/444—Bladed diffusers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D5/00—Pumps with circumferential or transverse flow
- F04D5/002—Regenerative pumps
-
- A—HUMAN NECESSITIES
- A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
- A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
- A47L5/00—Structural features of suction cleaners
- A47L5/12—Structural features of suction cleaners with power-driven air-pumps or air-compressors, e.g. driven by motor vehicle engine vacuum
- A47L5/22—Structural features of suction cleaners with power-driven air-pumps or air-compressors, e.g. driven by motor vehicle engine vacuum with rotary fans
- A47L5/36—Suction cleaners with hose between nozzle and casing; Suction cleaners for fixing on staircases; Suction cleaners for carrying on the back
- A47L5/365—Suction cleaners with hose between nozzle and casing; Suction cleaners for fixing on staircases; Suction cleaners for carrying on the back of the vertical type, e.g. tank or bucket 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
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
-
- 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
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/5806—Cooling the drive system
-
- 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
-
- 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
- F05D2250/70—Shape
Definitions
- the present disclosure relates to a fan and a cleaner.
- Japanese Unexamined Patent Application Publication No. 2010-196705 discloses a related-art centrifugal compressor.
- the centrifugal compressor of Japanese Unexamined Patent Application Publication No. 2010-196705 includes a rotor, a diffuser, and a shroud.
- the rotor has a shaft to which an impeller and a bearing cartridge are attached.
- the diffuser includes a hub, a circumstantial wall, a plurality of radial vanes and a plurality of axial vanes.
- the radial vanes are two-dimensional blades spaced apart from one another in the circumferential direction on an upper surface of the hub.
- the circumferential wall surrounds the hub with a gap therebetween.
- the axial vanes are two-dimensional blades extending between the circumferential wall and the hub.
- the rotor is rotatably attached to the diffuser by using the bearing cartridge.
- the shroud is attached to the diffuser so as to cover the impeller and the diffuser.
- the radial vanes and the axial vanes are provided in respective different regions where air flows due to rotation of the impeller. This leads to reduction of the number of vanes in each of the regions, and accordingly, the gap between the adjacent vanes cannot be reduced in the circumferential direction. Thus, there is a possibility of reducing blowing efficiency.
- a fan includes an impeller rotated about the vertically extending central axis, a motor that rotates the impeller, a motor housing that houses the motor, and a fan casing disposed radially outside the motor housing so as to form a flow passage in a gap therebetween.
- a plurality of first stationary blades and a second stationary blade are disposed radially outside the motor housing.
- the first stationary blades are arranged in a circumferential direction and extend in an axial direction.
- the second stationary blade is disposed between the first stationary blades adjacent to each other in the circumferential direction, and the second stationary blade extends in the axial direction.
- An upper end of the second stationary blade is disposed further to a lower side than upper ends of the first stationary blades and further to an upper side than lower ends of the first stationary blades.
- axial direction a direction in which the central axis of a fan extends
- radial direction a direction perpendicular to the central axis of the fan
- circumferential direction a direction along the arc centered at the central axis of the fan
- suction side relative to an impeller is referred to as an "upper” side in description of the shapes and the positional relationships of components.
- a "lower” direction refers to a direction toward the floor and an “upper” direction refers to a direction separating from the floor in description of the shapes and the positional relationships herein. These directions are designations merely used for description, and these directions do not limit the actual positional relationships and the directions.
- upstream and downstream are referred to as those in the flowing direction of air sucked through an inlet when the fan is driven.
- FIG. 1 is a perspective view of the cleaner according to an embodiment of the present disclosure.
- a cleaner 100 illustrated in Fig. 1 is a so-called stick-type electrical cleaner and includes a casing 102.
- the casing 102 has an inlet 103 and an outlet 104 formed in a lower surface and an upper surface thereof, respectively.
- a power cord (not illustrated) extends from a rear surface of the casing 102.
- the power cord is connected to a power outlet (not illustrated) provided in a side wall of a room, thereby the power is supplied to the cleaner 100.
- the cleaner 100 may be of a so-called robot type, a canister type, or a handheld type electrical cleaner.
- An air passage (not illustrated) that connects the inlet 103 and the outlet 104 to each other is formed in the casing 102.
- a dust collector (not illustrated), a filter (not illustrated), and a fan 1 are arranged in this order from the upstream side toward the downstream side in the air passage. Foreign matter such as dust contained in the air flowing through the air passage is blocked by the filter and collected in the dust collector having a container shape.
- the dust collector and the filter are removably mounted in the casing 102. Thus, a floor F can be cleaned.
- a grip portion 105 and an operating portion 106 are provided in an upper portion of the casing 102.
- a user can move the cleaner 100 by holding the grip portion 105.
- the operating portion 106 includes a plurality of buttons 106a. Operations of the cleaner 100 are set by operating the buttons 106a. For example, the start and stop of drive, changes in rotational speed, and so forth of the fan 1 are instructed by operating the buttons 106a.
- a downstream end (upper end in Fig. 1 ) of a rod-shaped suction pipe 107 is connected to the inlet 103.
- a suction nozzle 110 is detachably attached to an upstream end of the suction pipe 107.
- Fig. 2 is a perspective view of the fan 1 according to the embodiment of the present disclosure.
- Fig. 3 is a perspective view of the fan 1 with a fan casing 2 removed.
- Fig. 4 is a longitudinal sectional view of the fan 1.
- the fan 1 includes the fan casing 2, an impeller 3, a motor housing 4, a motor 5, an upper bearing 6, a lower bearing 7, and a board 8.
- the impeller 3 is rotated in a rotational direction R about a central axis C by the motor 5, the air is sucked into the fan casing 2 from the upper side and exhausted from the fan casing 2 toward the lower side.
- the fan 1 includes the fan casing 2 having a cylindrical shape.
- the shape of the fan casing 2 is circular in the section in plan view.
- the fan casing 2 houses the impeller 3 and the motor housing 4.
- the fan casing 2 has an upper case portion 2A and a lower case portion 2B.
- the upper case portion 2A covers the impeller 3.
- the lower case portion 2B covers the motor housing 4.
- the upper case portion 2A and the lower case portion 2B may be an integrally formed single member or separately formed different members.
- a bell mouth 21 is provided in an upper portion of the upper case portion 2A.
- the bell mouth 21 extends upward from an upper end and is bent inward.
- An inlet 211 that is an opening in the vertical direction is provided at the upper end of the bell mouth 21.
- the inlet 211 is positioned further to the upper side than an upper end of the impeller 3.
- An outlet 22 that is an opening in the vertical direction is provided at a lower end of the lower case portion 2B.
- the fan 1 is disposed such that the inlet 211 faces the lower side ( Fig. 1 ).
- the impeller 3 includes molded resin components.
- the impeller 3 includes a base 31 and a plurality of blades 32.
- the diameter of the base 31 increases downward.
- the base 31 has a boss portion 311 projecting downward.
- the boss portion 311 is connected to an upper portion of a shaft 53, which will be described later, by press fitting.
- the impeller 3 is rotated in the rotational direction R about the central axis C by the motor 5.
- the plurality of blades 32 are arranged in the circumferential direction on an outer circumferential surface of the base 31.
- the blades 32 are integrally formed with the base 31.
- an upper portion is disposed on a leading side relative to a lower portion in the rotational direction R.
- the motor housing 4 has an upper housing 41 and a lower housing 42.
- the upper housing 41 is disposed further to the upper side than the lower housing 42.
- the motor housing 4 houses therein the motor 5.
- the upper housing 41 has a cup-shaped base portion 411.
- the base portion 411 has a cylindrical portion 4111 that is open at its lower portion and an upper lid portion 4112 positioned further to the upper side than the cylindrical portion 4111.
- the upper lid portion 4112 has a hole 4112A at the center thereof.
- the hole 4112A vertically penetrates through the upper lid portion 4112.
- the upper bearing 6 is secured to the upper lid portion 4112 at a lower portion of the hole 4112A.
- the upper bearing 6 includes a ball bearing, the upper bearing 6 may alternatively include another type of bearing such as a sleeve bearing.
- annular groove portion 4112B recessed downward is provided in an upper surface of the upper lid portion 4112.
- annular impeller projection 31A is provided on a lower surface of the base 31 of the impeller 3. At least part of the impeller projection 31A is accommodated in the groove portion 4112B.
- the cylindrical portion 4111 has a plurality of rod-shaped projections (not illustrated) on its inner circumferential surface.
- the rod-shaped projections radially inwardly project from the inner circumferential surface of the cylindrical portion 4111 and vertically extend.
- the rod-shaped projections have screw holes (not illustrated) that extend upward from lower ends thereof.
- a plurality of first stationary blades 412 are arranged in the circumferential direction on an outer circumferential surface of the cylindrical portion 4111.
- the first stationary blades 412 extend in the axial direction.
- a plurality of second stationary blades 413 are arranged in the circumferential direction on the outer circumferential surface of the cylindrical portion 4111.
- the second stationary blades 413 are each disposed between the first stationary blades 412 adjacent to each other in the circumferential direction. The structure of the stationary blades will be described in detail later.
- the lower housing 42 has a cup shape that is open at the upper side thereof.
- a bearing holding portion 421 is provided at the center of a bottom portion of the lower housing 42.
- the lower bearing 7 is held by the bearing holding portion 421.
- the lower bearing 7 may alternatively include another type of bearing such as a ball bearing.
- outlets 42A that are open in the vertical direction are disposed radially outside the bearing holding portion 421 at the bottom portion of the lower housing 42.
- the outlets 42A are arranged in the circumferential direction. As will be described later, the outlets 42A are openings through which the air having cooled a stator 51 is exhausted.
- a plurality of base stage portions are provided on an inner circumferential surface side of the lower housing 42.
- the base stage portions project radially inward.
- the base stage portions have screw holes (not illustrated) that vertically penetrate therethrough. The relationship between the base stage portions and the above-described rod-shaped projections will be described later.
- the motor 5 housed in the motor housing 4 is disposed further to the lower side than the impeller 3.
- the motor 5 includes the stator 51, a rotor 52, and a shaft 53.
- the stator 51 includes the stator core 511, a plurality of coils, and insulators.
- the stator core 511 is formed by vertically laminating electromagnetic steel plates.
- the stator core 511 includes an annular core back 5111 and a plurality of teeth (not illustrated).
- the plurality of teeth extend radially inward from an inner circumferential surface of the core back 5111, thereby forming a radial shape.
- the teeth have a substantially T-shape in plan view.
- the coils are wound around the teeth with the insulative insulators interposed therebetween.
- an inner circumferential surface and an outer circumferential surface of the core back 5111 are flat. This can prevent winding collapse of the coils. Furthermore, in portions other than the portions near the bottoms of the teeth, the inner circumferential surface and the outer circumferential surface of the core back 5111 are curved.
- Inner surfaces of the above-described rod-shaped projections of the upper housing 41 include flat surfaces that are in contact with the flat portions of the outer circumferential surface of the core back 5111, and the upper housing 41 is placed on the lower housing 42.
- the rod-shaped projections of the upper housing 41 are placed on the base stage portions of the lower housing 42.
- the screw holes of the rod-shaped projections and the screw holes of the base stage portions are disposed in the vertical direction in a continuous manner. Bolts are screwed into these screw holes from the lower side.
- the upper housing 41 is secured to the lower housing 42 by the bolts.
- vent holes 411A that penetrate through the upper housing 41 in the radial direction are formed at positions that are adjacent to and on both sides of the rod-shaped projections of the cylindrical portion 4111 in the circumferential direction and that are further to the lower side than the first stationary blades 412 ( Fig. 3 ). Effects of the vent holes 411A will be described later.
- the curved portions of the outer circumferential surface of the core back 5111 are in contact with the curved inner circumferential surface of the cylindrical portion 4111 along the inner circumferential surface of the cylindrical portion 4111. That is, the stator core 511 is in direct contact with the upper housing 41.
- the rotor 52 is disposed radially inside the stator 51. That is, the motor 5 is of a so-called inner-rotor type.
- the rotor 52 includes a plurality of magnets.
- the shaft 53 that vertically extends is secured to the rotor 52.
- the shaft 53 is rotatably held by the upper bearing 6 and the lower bearing 7.
- An upper end portion of the shaft 53 is secured to the boss portion 311 of the impeller 3.
- the discoidal board 8 is disposed further to the lower side than the lower housing 42.
- the board 8 includes a rigid board or a flexible board. Leads (not illustrated) extending from the coils of the motor 5 are electrically connected to a drive circuit (not illustrated) implemented on the board 8. Thus, the power can be supplied to the coils.
- the flow passage FL includes a space interposed between the outer circumferential surface of the upper housing 41 and an inner circumferential surface of the fan casing 2 and a space interposed between an outer circumferential surface of the lower housing 42 and the inner circumferential surface of the fan casing 2.
- the first stationary blades 412 and the second stationary blades 413 are disposed in the flow passage FL.
- Fig. 5 illustrates the fan 1 with part of the fan casing 2 removed so as to illustrate a section in which the stationary blades are visible.
- the first stationary blades 412 extending in the axial direction are arranged in the circumferential direction.
- the second stationary blades 413 extending in the axial direction are each disposed between the first stationary blades 412 adjacent to each other in the circumferential direction. Upper ends of the second stationary blades 413 are disposed further to the lower side than upper ends of the first stationary blades 412 and further to the upper side than lower ends of the first stationary blades 412.
- the air sucked through the inlet 211 due to the rotation of the impeller 3 flows into the flow passage FL from an upper end of the flow passage FL and is sent to the first stationary blades 412.
- the air flowing toward spaces between the first stationary blades 412 adjacent to one another in the circumferential direction is guided through the spaces between the first stationary blades 412.
- part of this air is guided through spaces between pressure surfaces PS1 of the first stationary blades 412 and suction surfaces MS2 of the second stationary blades 413
- the other part of this air is guided through spaces between suction surfaces MS1 of the first stationary blades 412 and pressure surfaces PS2 of the second stationary blades 413.
- the pressure surfaces refer to surfaces on trailing sides of the stationary blades in the rotational direction R of the impeller 3
- the suction surfaces refer to surfaces on leading sides of the stationary blades in the rotational direction R of the impeller 3.
- the air guided through the stationary blades is discharged to the outside through the outlet 22 at a lower portion.
- arrows illustrated in Fig. 4 indicate flows of the air.
- the fan 1 includes the impeller 3 rotated about the vertically extending central axis C, the motor 5 that rotates the impeller 3, the motor housing 4 that houses the motor 5, and the fan casing 2 that is disposed radially outside the motor housing 4 so as to form the flow passage FL in the gap therebetween.
- the plurality of first stationary blades 412 and the second stationary blades 413 are disposed radially outside the motor housing 4.
- the first stationary blades 412 are arranged in the circumferential direction and extend in the axial direction.
- the second stationary blades 413 are each disposed between the first stationary blades 412 adjacent to each other in the circumferential direction, and the second stationary blades 413 extend in the axial direction.
- the upper ends of the second stationary blades 413 are disposed further to the lower side than the upper ends of the first stationary blades 412 and further to the upper side than the lower ends of the first stationary blades 412.
- a large number of the stationary blades can be disposed in a particular region of the flow passage FL, and accordingly, the spacing between the stationary blades in the circumferential direction can be reduced. Accordingly, efficiency of blowing due to the airflow caused by the rotation of the impeller 3 can be improved.
- Fig. 6 illustrates an example of the relationship between the number of the stationary blades and the blowing efficiency.
- 13 of the first stationary blades 412 and 13 of the second stationary blades 413 are provided, that is, a total of 26 of the stationary blades are provided. It can be understood that, as the number of the stationary blades increases, the blowing efficiency improves as illustrated in Fig. 6 .
- lower ends of the second stationary blades 413 are disposed at a lower position than the lower ends of the first stationary blades 412. This allows the second stationary blades 413 to guide the air also at regions further to the lower side than the lower ends of the first stationary blades 412. Accordingly, compared to the case where only the first stationary blades 412 are disposed, the blowing efficiency can be improved.
- first stationary blades 412 at least partially superpose on the second stationary blades 413 when seen in the axial direction. This allows the first stationary blades 412 and the second stationary blades 413 to be disposed in particular regions of the flow passage FL in the circumferential direction. Thus, more stationary blades can be disposed, and accordingly, the blowing efficiency can be improved.
- the stator core 511 is in direct contact with the upper housing 41.
- the upper housing 41 is formed of, for example, metal
- the first stationary blades 412 and the second stationary blades 413 are formed of metal. That is, at least part of the motor 5 is in direct contact with the motor housing 4, and the first stationary blades 412 and the second stationary blades 413 are metal members.
- the rigidity of the stationary blades which are metal members
- heat is conducted from the motor 5 to the stationary blades due to thermal conduction and dissipated from the stationary blades into the air due to thermal transfer.
- the stationary blades are metal members
- the thermal conductivity of the stationary blades is improved. This can improve the cooling characteristics of the motor 5.
- the stator core 511 and the motor housing 4 may be in contact with each other with, for example, another member interposed therebetween. That is, the at least part of the motor 5 may be in indirect contact with the motor housing 4.
- the other member described above is preferably formed of a material having high thermal conductivity.
- the number of the first stationary blades 412 is 13, and the number of the second stationary blades 413 is 13. That is, the number of the first stationary blades 412 is equal to the number of the second stationary blades 413.
- the stationary blades can be equally distributed in the circumferential direction, and accordingly, generation of turbulent flow can be suppressed and blowing efficiency can be improved.
- the thickness of the second stationary blades 413 is smaller than the thickness of the first stationary blades 412.
- the width of parts of the flow passage FL defined by the first stationary blades 412 and the second stationary blades 413 adjacent to one another in the circumferential direction can be increased in a region of the flow passage FL where the second stationary blades 413 are disposed.
- a first lower curved surface CS1 which is curved toward the leading side in the rotational direction R of the impeller 3 as it extends downward, is formed in a lower end portion of the pressure surface PS1 of each of the first stationary blades 412
- a second lower curved surface CS2 which is curved toward the leading side in the rotational direction R of the impeller 3 as it extends downward, is formed in a lower end portion of the pressure surface PS2 of each of the second stationary blades 413.
- the radius of curvature of the second lower curved surface CS2 is larger than the radius of curvature of the first lower curved surface CS1.
- the lower end portion of the first stationary blade 412 having a large thickness in the circumferential direction is curved more. This can suppress separation of the air flowing downward along the first lower curved surface CS1 at a position immediately below the first stationary blade 412. Accordingly, generation of turbulent flow immediately below the first stationary blade 412 can be suppressed.
- the radius of curvature of the second lower curved surface CS2 is 1.8 to 2.5 times the radius of curvature of the first lower curved surface CS1.
- This can suppress the occurrence of a situation in which the air flowing along the pressure surface PS1 of the first stationary blade 412 strikes the pressure surface PS2 of the second stationary blade 413 when this air is guided along the first lower curved surface CS1 from the lower end of the first stationary blades 412 toward the leading side in the rotational direction R.
- generation of turbulent flow at a region further to the lower side than the first stationary blade 412 and the second stationary blade 413 can be suppressed, and accordingly, the airflow can be uniformed as much as possible.
- the first stationary blade 412 includes a first stationary blade upper portion 4121 and a first stationary blade lower portion 4122.
- the first stationary blade upper portion 4121 is inclined toward the circumferential direction toward a trailing side in the rotational direction R of the impeller 3 as it extends from the lower side toward the upper side.
- the first stationary blade lower portion 4122 is positioned further to the lower side than the first stationary blade upper portion 4121 in the axial direction.
- the second stationary blade 413 includes a second stationary blade upper portion 4131 and a second stationary blade lower portion 4132.
- the second stationary blade upper portion 4131 is inclined toward the circumferential direction toward the trailing side in the rotational direction R of the impeller 3 as it extends from the lower side toward the upper side.
- the second stationary blade lower portion 4132 is positioned further to the lower side than the second stationary blade upper portion 4131 in the axial direction.
- the air exhausted toward the leading side of the rotational direction R of the impeller 3 can be smoothly guided downward in the axial direction along the first stationary blade upper portion 4121 and the second stationary blade upper portion 4131. Accordingly, the blowing efficiency can be improved.
- the first stationary blade upper portion 4121 has a first pressure curved surface 4121A curved on the pressure surface PS 1 side and a first suction curved surface 4121B curved on the suction surface MS1 side. Furthermore, the second stationary blade upper portion 4131 has a second pressure curved surface 4131A curved on the pressure surface PS2 side and a second suction curved surface 4131B curved on the suction surface MS2 side.
- first stationary blade upper portion 4121 has first curved surfaces (4121A and 4121B) curved further toward the trailing side than the first stationary blade lower portion 4122 in the rotational direction R of the impeller 3
- second stationary blade upper portion 4131 has second curved surfaces (4131A and 4131B) curved further toward the trailing side than the second stationary blade lower portion 4132 in the rotational direction R of the impeller 3.
- the air can be smoothly guided by the first curved surfaces and the second curved surfaces. Accordingly, the blowing efficiency can be improved.
- the curved surface be formed on at least one of the pressure surface side and the suction surface side.
- an inclined surface as a not-curved flat surface may be formed on either of the pressure surface side and the suction surface side.
- L1 is a length in the circumferential direction between a trailing end of the first stationary blade 412 in the rotational direction R of the impeller 3 and a leading end of the first stationary blade upper portion 4121 on the pressure surface PS1 in the rotational direction R of the impeller 3
- L2 is a length in the circumferential direction between a trailing end of the second stationary blade 413 in the rotational direction R of the impeller 3 and a leading end of the second stationary blade upper portion 4131 on the pressure surface PS2 in the rotational direction R of the impeller 3
- L1 is larger than L2.
- the curved surface 4121A of the pressure surface PS1 of the first stationary blade upper portion 4121 is largely curved. Accordingly, the airflow can be guided downward by the first stationary blade 412, and the airflow having been guided by the first stationary blade 412 can be further guided downward by the second stationary blade 413.
- the radius of curvature of the pressure surface in one of the first curved surfaces (4121A) is smaller than the radius of curvature of the pressure surface in one of the second curved surface (4131A).
- the air having a rotating component toward the leading side in the rotational direction R of the impeller 3 can be guided downward in the axial direction by the first stationary blade upper portion 4121. Accordingly, the blowing efficiency can be improved.
- the radius of curvature of the pressure surface in the second curved surface be 1.8 to 2.2 times the radius of curvature of the pressure surface in the first curved surface.
- the second stationary blade lower portion 4132 has an extended surface S21.
- the extended surface S21 extends in the axial direction at a position further to the lower side than the lower end of the first stationary blade 412 on the pressure surface PS2 side.
- the air guided by and separated from the first stationary blade 412 is smoothly guided downward along the extended surface S21. This can suppress separation of the air having been separated from the first stationary blade 412 from the second stationary blade 413. Accordingly, the blowing efficiency can be improved.
- the first stationary blade lower portion 4122 has a first surface S1 that extends in the axial direction on the pressure surface PS1 side
- the second stationary blade lower portion 4132 has a second surface S2 that extends in the axial direction on the pressure surface PS2 side.
- the axial length of the first surface S1 is smaller than the axial length of the second surface S2.
- the extended surface S21 is included in the second surface S2.
- the axial length of the second surface S2 be 0.2 to 0.65 times the axial length of the second stationary blade lower portion 4132.
- the axial length of the second stationary blade upper portion 4131 is preferably 0.2 to 0.5 times the axial length of the second stationary blade 413.
- the airflow is guided downward in the axial direction by the second stationary blade upper portion 4131. Accordingly, the blowing efficiency can be improved.
- a width W1 between the first stationary blade 412 disposed on the trailing side in the rotational direction R of the impeller 3 out of the first stationary blades 412 adjacent to each other and the second stationary blade 413 disposed between the first stationary blades 412 adjacent to each other is preferably 1.1 to 1.3 times a width W2 between the first stationary blade 412 disposed on the leading side in the rotational direction R of the impeller 3 out of the first stationary blades 412 adjacent to each other and the second stationary blade 413 disposed between the first stationary blades 412 adjacent to each other.
- This can increase the likelihood of the airflow being guided to parts of the flow passage between the stationary blades positioned on the trailing side in the rotational direction R of the impeller 3. Accordingly, the blowing efficiency can be improved.
- the center of each of the second stationary blades 413 is disposed at the center of the width between the first stationary blades 412 adjacent to each other. This allows parts of the flow passage between the stationary blades to be uniform as much as possible. Accordingly, the blowing efficiency can be improved.
- the axial length between the upper ends of the first stationary blades 412 and the upper ends of the second stationary blades 413 is smaller than the length of the gap in the circumferential direction between the upper ends of the first stationary blades 412 adjacent to each other in the circumferential direction.
- the gaps between the upper ends of the first stationary blades 412 are increased in the circumferential direction. This increases the sectional area of parts of the flow passage between the first stationary blades 412. Accordingly, more air can be guided to the parts of the flow passage between the first stationary blades 412.
- the axial length of the region where the first stationary blades 412 and the second stationary blades 413 are superposed on one another in the circumferential direction is preferably 0.5 to 0.8 times the axial length of the first stationary blades 412. Accordingly, the blowing efficiency can be improved.
- the axial length of the second stationary blades 413 is larger than the axial length of the first stationary blades 412.
- the air is smoothly guided along the second stationary blades 413 also on the lower side of the flow passage. This can reduce the likelihood of generation of turbulent flow, and accordingly, the blowing efficiency can be improved.
- vent holes 411A are provided in the upper housing 41.
- the vent holes 411A penetrate through the upper housing 41 in the radial direction so as to allow communication between the flow passage FL and the inside of the upper housing 41.
- the vent holes 411A are disposed immediately below the specified first stationary blades 412.
- the motor housing 4 has the vent holes 411A, which penetrate through the upper housing 41 in the radial direction so as to allow communication between the flow passage FL and the inside of the motor housing 4. Accordingly, efficiency for cooling the motor 5 can be improved.
- the cleaner 100 includes the above-described fan 1. This allows the cleaner exhibiting improved blowing efficiency can be realized.
- Devices in which the fan is mounted are not limited to cleaners.
- the fan may be mounted in any of a variety of, for example, office automation devices, medical devices, transport devices, and home appliances other than the cleaners.
- the present disclosure can be utilized for, for example, a fan for a cleaner.
Abstract
Description
- The present disclosure relates to a fan and a cleaner.
- Japanese Unexamined Patent Application Publication No.
2010-196705 2010-196705 - The rotor has a shaft to which an impeller and a bearing cartridge are attached. The diffuser includes a hub, a circumstantial wall, a plurality of radial vanes and a plurality of axial vanes. The radial vanes are two-dimensional blades spaced apart from one another in the circumferential direction on an upper surface of the hub. The circumferential wall surrounds the hub with a gap therebetween. The axial vanes are two-dimensional blades extending between the circumferential wall and the hub. The rotor is rotatably attached to the diffuser by using the bearing cartridge. The shroud is attached to the diffuser so as to cover the impeller and the diffuser.
- According to Japanese Unexamined Patent Application Publication No.
2010-196705 - According to an exemplary embodiment of the present disclosure, a fan includes an impeller rotated about the vertically extending central axis, a motor that rotates the impeller, a motor housing that houses the motor, and a fan casing disposed radially outside the motor housing so as to form a flow passage in a gap therebetween. A plurality of first stationary blades and a second stationary blade are disposed radially outside the motor housing. The first stationary blades are arranged in a circumferential direction and extend in an axial direction. The second stationary blade is disposed between the first stationary blades adjacent to each other in the circumferential direction, and the second stationary blade extends in the axial direction. An upper end of the second stationary blade is disposed further to a lower side than upper ends of the first stationary blades and further to an upper side than lower ends of the first stationary blades.
- The above and other elements, features, steps, characteristics and advantages of the present disclosure will become more apparent from the following detailed description of the preferred embodiments with reference to the attached drawings.
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Fig. 1 is a perspective view of a cleaner according to an embodiment of the present disclosure; -
Fig. 2 is a perspective view of a fan according to the embodiment of the present disclosure; -
Fig. 3 is a perspective view of the fan according to the embodiment of the present disclosure with a fan casing removed; -
Fig. 4 is a longitudinal sectional view of the fan according to the embodiment of the present disclosure; -
Fig. 5 is a sectional view of the fan according to the embodiment of the present disclosure with part of the fan casing cut off; and -
Fig. 6 is a graph illustrating an example of the relationship between the number of stationary blades and blowing efficiency in the fan according to the embodiment of the present disclosure. - An exemplary embodiment of the present disclosure will be described below with reference to the drawings. Herein, a direction in which the central axis of a fan extends is referred to as "axial direction", a direction perpendicular to the central axis of the fan is referred to as "radial direction", and a direction along the arc centered at the central axis of the fan is referred to as "circumferential direction". Furthermore, the above-described central axis is defined as an axis that extends in "vertical direction", and herein, the suction side relative to an impeller is referred to as an "upper" side in description of the shapes and the positional relationships of components. However, the above-described "vertical direction" does not limit the positional relationships and directions when assembled in an actual apparatus. Furthermore, "upstream" and "downstream" referred to as those in the flowing direction of air sucked through an inlet when the impeller is rotated.
- Furthermore, in a cleaner, a "lower" direction refers to a direction toward the floor and an "upper" direction refers to a direction separating from the floor in description of the shapes and the positional relationships herein. These directions are designations merely used for description, and these directions do not limit the actual positional relationships and the directions. Furthermore, "upstream" and "downstream" are referred to as those in the flowing direction of air sucked through an inlet when the fan is driven.
- Herein, a cleaner according to the exemplary embodiment of the present disclosure is described.
Fig. 1 is a perspective view of the cleaner according to an embodiment of the present disclosure. Acleaner 100 illustrated inFig. 1 is a so-called stick-type electrical cleaner and includes acasing 102. Thecasing 102 has aninlet 103 and anoutlet 104 formed in a lower surface and an upper surface thereof, respectively. A power cord (not illustrated) extends from a rear surface of thecasing 102. The power cord is connected to a power outlet (not illustrated) provided in a side wall of a room, thereby the power is supplied to thecleaner 100. Thecleaner 100 may be of a so-called robot type, a canister type, or a handheld type electrical cleaner. - An air passage (not illustrated) that connects the
inlet 103 and theoutlet 104 to each other is formed in thecasing 102. A dust collector (not illustrated), a filter (not illustrated), and afan 1 are arranged in this order from the upstream side toward the downstream side in the air passage. Foreign matter such as dust contained in the air flowing through the air passage is blocked by the filter and collected in the dust collector having a container shape. The dust collector and the filter are removably mounted in thecasing 102. Thus, a floor F can be cleaned. - A
grip portion 105 and anoperating portion 106 are provided in an upper portion of thecasing 102. A user can move thecleaner 100 by holding thegrip portion 105. Theoperating portion 106 includes a plurality ofbuttons 106a. Operations of thecleaner 100 are set by operating thebuttons 106a. For example, the start and stop of drive, changes in rotational speed, and so forth of thefan 1 are instructed by operating thebuttons 106a. A downstream end (upper end inFig. 1 ) of a rod-shaped suction pipe 107 is connected to theinlet 103. Asuction nozzle 110 is detachably attached to an upstream end of thesuction pipe 107. - Next, an overall structure of the
fan 1 is described.Fig. 2 is a perspective view of thefan 1 according to the embodiment of the present disclosure.Fig. 3 is a perspective view of thefan 1 with afan casing 2 removed.Fig. 4 is a longitudinal sectional view of thefan 1. - Roughly classified, the
fan 1 includes thefan casing 2, an impeller 3, a motor housing 4, amotor 5, an upper bearing 6, alower bearing 7, and aboard 8. When the impeller 3 is rotated in a rotational direction R about a central axis C by themotor 5, the air is sucked into thefan casing 2 from the upper side and exhausted from thefan casing 2 toward the lower side. - The
fan 1 includes thefan casing 2 having a cylindrical shape. The shape of thefan casing 2 is circular in the section in plan view. Thefan casing 2 houses the impeller 3 and the motor housing 4. Thefan casing 2 has anupper case portion 2A and alower case portion 2B. Theupper case portion 2A covers the impeller 3. Thelower case portion 2B covers the motor housing 4. Theupper case portion 2A and thelower case portion 2B may be an integrally formed single member or separately formed different members. - A
bell mouth 21 is provided in an upper portion of theupper case portion 2A. Thebell mouth 21 extends upward from an upper end and is bent inward. Aninlet 211 that is an opening in the vertical direction is provided at the upper end of thebell mouth 21. Theinlet 211 is positioned further to the upper side than an upper end of the impeller 3. Anoutlet 22 that is an opening in the vertical direction is provided at a lower end of thelower case portion 2B. In the cleaner 100, thefan 1 is disposed such that theinlet 211 faces the lower side (Fig. 1 ). - The impeller 3 includes molded resin components. The impeller 3 includes a
base 31 and a plurality ofblades 32. The diameter of the base 31 increases downward. - The
base 31 has aboss portion 311 projecting downward. Theboss portion 311 is connected to an upper portion of ashaft 53, which will be described later, by press fitting. The impeller 3 is rotated in the rotational direction R about the central axis C by themotor 5. - The plurality of
blades 32 are arranged in the circumferential direction on an outer circumferential surface of thebase 31. Theblades 32 are integrally formed with thebase 31. In each of theblades 32, an upper portion is disposed on a leading side relative to a lower portion in the rotational direction R. Thus, when the impeller 3 is rotated, the air sucked through theinlet 211 is guided in a direction directed toward the lower side and toward the leading side in the rotational direction R to a flow passage FL positioned further to the lower side than the impeller 3. The flow passage FL will be described later. - The motor housing 4 has an
upper housing 41 and alower housing 42. Theupper housing 41 is disposed further to the upper side than thelower housing 42. The motor housing 4 houses therein themotor 5. - The
upper housing 41 has a cup-shapedbase portion 411. Thebase portion 411 has acylindrical portion 4111 that is open at its lower portion and anupper lid portion 4112 positioned further to the upper side than thecylindrical portion 4111. Theupper lid portion 4112 has ahole 4112A at the center thereof. Thehole 4112A vertically penetrates through theupper lid portion 4112. Theupper bearing 6 is secured to theupper lid portion 4112 at a lower portion of thehole 4112A. Although theupper bearing 6 includes a ball bearing, theupper bearing 6 may alternatively include another type of bearing such as a sleeve bearing. - An
annular groove portion 4112B recessed downward is provided in an upper surface of theupper lid portion 4112. Here, anannular impeller projection 31A is provided on a lower surface of thebase 31 of the impeller 3. At least part of theimpeller projection 31A is accommodated in thegroove portion 4112B. Thus, flowing of an airflow generated by the rotation of the impeller 3 to the inside of the impeller 3 (space SP) can be suppressed. That is, a labyrinth effect is produced so as to allow blowing efficiency of thefan 1 to be improved. - The
cylindrical portion 4111 has a plurality of rod-shaped projections (not illustrated) on its inner circumferential surface. The rod-shaped projections radially inwardly project from the inner circumferential surface of thecylindrical portion 4111 and vertically extend. The rod-shaped projections have screw holes (not illustrated) that extend upward from lower ends thereof. - A plurality of first
stationary blades 412 are arranged in the circumferential direction on an outer circumferential surface of thecylindrical portion 4111. The firststationary blades 412 extend in the axial direction. Furthermore, a plurality of secondstationary blades 413 are arranged in the circumferential direction on the outer circumferential surface of thecylindrical portion 4111. The secondstationary blades 413 are each disposed between the firststationary blades 412 adjacent to each other in the circumferential direction. The structure of the stationary blades will be described in detail later. - The
lower housing 42 has a cup shape that is open at the upper side thereof. Abearing holding portion 421 is provided at the center of a bottom portion of thelower housing 42. Thelower bearing 7 is held by thebearing holding portion 421. Although thelower bearing 7 includes a sleeve bearing, thelower bearing 7 may alternatively include another type of bearing such as a ball bearing. - A plurality of
outlets 42A that are open in the vertical direction are disposed radially outside thebearing holding portion 421 at the bottom portion of thelower housing 42. Theoutlets 42A are arranged in the circumferential direction. As will be described later, theoutlets 42A are openings through which the air having cooled astator 51 is exhausted. - A plurality of base stage portions (not illustrated) are provided on an inner circumferential surface side of the
lower housing 42. The base stage portions project radially inward. The base stage portions have screw holes (not illustrated) that vertically penetrate therethrough. The relationship between the base stage portions and the above-described rod-shaped projections will be described later. - The
motor 5 housed in the motor housing 4 is disposed further to the lower side than the impeller 3. Themotor 5 includes thestator 51, arotor 52, and ashaft 53. Thestator 51 includes thestator core 511, a plurality of coils, and insulators. - The
stator core 511 is formed by vertically laminating electromagnetic steel plates. Thestator core 511 includes an annular core back 5111 and a plurality of teeth (not illustrated). The plurality of teeth extend radially inward from an inner circumferential surface of the core back 5111, thereby forming a radial shape. The teeth have a substantially T-shape in plan view. The coils are wound around the teeth with the insulative insulators interposed therebetween. - In portions near the bottoms of the teeth, an inner circumferential surface and an outer circumferential surface of the core back 5111 are flat. This can prevent winding collapse of the coils. Furthermore, in portions other than the portions near the bottoms of the teeth, the inner circumferential surface and the outer circumferential surface of the core back 5111 are curved.
- Inner surfaces of the above-described rod-shaped projections of the
upper housing 41 include flat surfaces that are in contact with the flat portions of the outer circumferential surface of the core back 5111, and theupper housing 41 is placed on thelower housing 42. The rod-shaped projections of theupper housing 41 are placed on the base stage portions of thelower housing 42. The screw holes of the rod-shaped projections and the screw holes of the base stage portions are disposed in the vertical direction in a continuous manner. Bolts are screwed into these screw holes from the lower side. Thus, theupper housing 41 is secured to thelower housing 42 by the bolts. - In a state in which the
upper housing 41 is secured to thelower housing 42,vent holes 411A that penetrate through theupper housing 41 in the radial direction are formed at positions that are adjacent to and on both sides of the rod-shaped projections of thecylindrical portion 4111 in the circumferential direction and that are further to the lower side than the first stationary blades 412 (Fig. 3 ). Effects of the vent holes 411A will be described later. - Furthermore, the curved portions of the outer circumferential surface of the core back 5111 are in contact with the curved inner circumferential surface of the
cylindrical portion 4111 along the inner circumferential surface of thecylindrical portion 4111. That is, thestator core 511 is in direct contact with theupper housing 41. - The
rotor 52 is disposed radially inside thestator 51. That is, themotor 5 is of a so-called inner-rotor type. Therotor 52 includes a plurality of magnets. - The
shaft 53 that vertically extends is secured to therotor 52. Theshaft 53 is rotatably held by theupper bearing 6 and thelower bearing 7. An upper end portion of theshaft 53 is secured to theboss portion 311 of the impeller 3. - The
discoidal board 8 is disposed further to the lower side than thelower housing 42. Theboard 8 includes a rigid board or a flexible board. Leads (not illustrated) extending from the coils of themotor 5 are electrically connected to a drive circuit (not illustrated) implemented on theboard 8. Thus, the power can be supplied to the coils. - As illustrated in
Fig. 4 , the flow passage FL includes a space interposed between the outer circumferential surface of theupper housing 41 and an inner circumferential surface of thefan casing 2 and a space interposed between an outer circumferential surface of thelower housing 42 and the inner circumferential surface of thefan casing 2. The firststationary blades 412 and the secondstationary blades 413 are disposed in the flow passage FL. - Here, for description of the structure of the stationary blades,
Fig. 5 illustrates thefan 1 with part of thefan casing 2 removed so as to illustrate a section in which the stationary blades are visible. The firststationary blades 412 extending in the axial direction are arranged in the circumferential direction. The secondstationary blades 413 extending in the axial direction are each disposed between the firststationary blades 412 adjacent to each other in the circumferential direction. Upper ends of the secondstationary blades 413 are disposed further to the lower side than upper ends of the firststationary blades 412 and further to the upper side than lower ends of the firststationary blades 412. - With this structure, the air sucked through the
inlet 211 due to the rotation of the impeller 3 flows into the flow passage FL from an upper end of the flow passage FL and is sent to the firststationary blades 412. The air flowing toward spaces between the firststationary blades 412 adjacent to one another in the circumferential direction is guided through the spaces between the firststationary blades 412. Then, part of this air is guided through spaces between pressure surfaces PS1 of the firststationary blades 412 and suction surfaces MS2 of the secondstationary blades 413, and the other part of this air is guided through spaces between suction surfaces MS1 of the firststationary blades 412 and pressure surfaces PS2 of the secondstationary blades 413. Here, the pressure surfaces refer to surfaces on trailing sides of the stationary blades in the rotational direction R of the impeller 3, and the suction surfaces refer to surfaces on leading sides of the stationary blades in the rotational direction R of the impeller 3. - The air guided through the stationary blades is discharged to the outside through the
outlet 22 at a lower portion. Here, arrows illustrated inFig. 4 indicate flows of the air. As described above, since the airflow is regulated by the firststationary blades 412 and the secondstationary blades 413 so as to blow the air, the blowing efficiency can be improved. - That is, the
fan 1 according to the present embodiment includes the impeller 3 rotated about the vertically extending central axis C, themotor 5 that rotates the impeller 3, the motor housing 4 that houses themotor 5, and thefan casing 2 that is disposed radially outside the motor housing 4 so as to form the flow passage FL in the gap therebetween. The plurality of firststationary blades 412 and the secondstationary blades 413 are disposed radially outside the motor housing 4. The firststationary blades 412 are arranged in the circumferential direction and extend in the axial direction. The secondstationary blades 413 are each disposed between the firststationary blades 412 adjacent to each other in the circumferential direction, and the secondstationary blades 413 extend in the axial direction. The upper ends of the secondstationary blades 413 are disposed further to the lower side than the upper ends of the firststationary blades 412 and further to the upper side than the lower ends of the firststationary blades 412. - Thus, a large number of the stationary blades can be disposed in a particular region of the flow passage FL, and accordingly, the spacing between the stationary blades in the circumferential direction can be reduced. Accordingly, efficiency of blowing due to the airflow caused by the rotation of the impeller 3 can be improved.
Fig. 6 illustrates an example of the relationship between the number of the stationary blades and the blowing efficiency. According to the present embodiment, 13 of the firststationary blades 412 and 13 of the secondstationary blades 413 are provided, that is, a total of 26 of the stationary blades are provided. It can be understood that, as the number of the stationary blades increases, the blowing efficiency improves as illustrated inFig. 6 . - Furthermore, as illustrated in
Fig. 5 , lower ends of the secondstationary blades 413 are disposed at a lower position than the lower ends of the firststationary blades 412. This allows the secondstationary blades 413 to guide the air also at regions further to the lower side than the lower ends of the firststationary blades 412. Accordingly, compared to the case where only the firststationary blades 412 are disposed, the blowing efficiency can be improved. - Furthermore, the first
stationary blades 412 at least partially superpose on the secondstationary blades 413 when seen in the axial direction. This allows the firststationary blades 412 and the secondstationary blades 413 to be disposed in particular regions of the flow passage FL in the circumferential direction. Thus, more stationary blades can be disposed, and accordingly, the blowing efficiency can be improved. - Furthermore, as has been described, the
stator core 511 is in direct contact with theupper housing 41. Here, when theupper housing 41 is formed of, for example, metal, the firststationary blades 412 and the secondstationary blades 413 are formed of metal. That is, at least part of themotor 5 is in direct contact with the motor housing 4, and the firststationary blades 412 and the secondstationary blades 413 are metal members. - Thus, the rigidity of the stationary blades, which are metal members, can be improved. Furthermore, heat is conducted from the
motor 5 to the stationary blades due to thermal conduction and dissipated from the stationary blades into the air due to thermal transfer. When the stationary blades are metal members, the thermal conductivity of the stationary blades is improved. This can improve the cooling characteristics of themotor 5. Thestator core 511 and the motor housing 4 may be in contact with each other with, for example, another member interposed therebetween. That is, the at least part of themotor 5 may be in indirect contact with the motor housing 4. In this case, the other member described above is preferably formed of a material having high thermal conductivity. - Furthermore, as has been described, for example, the number of the first
stationary blades 412 is 13, and the number of the secondstationary blades 413 is 13. That is, the number of the firststationary blades 412 is equal to the number of the secondstationary blades 413. Thus, the stationary blades can be equally distributed in the circumferential direction, and accordingly, generation of turbulent flow can be suppressed and blowing efficiency can be improved. - Furthermore, in the circumferential direction, the thickness of the second
stationary blades 413 is smaller than the thickness of the firststationary blades 412. Thus, compared to the case where the thickness of the secondstationary blades 413 is large, the width of parts of the flow passage FL defined by the firststationary blades 412 and the secondstationary blades 413 adjacent to one another in the circumferential direction can be increased in a region of the flow passage FL where the secondstationary blades 413 are disposed. This allows the sectional area of the flow passage to be increased in a region where the firststationary blades 412 and the secondstationary blades 413 are disposed in the flow passage FL. Accordingly, the blowing efficiency can be improved. - Furthermore, a first lower curved surface CS1, which is curved toward the leading side in the rotational direction R of the impeller 3 as it extends downward, is formed in a lower end portion of the pressure surface PS1 of each of the first
stationary blades 412, and a second lower curved surface CS2, which is curved toward the leading side in the rotational direction R of the impeller 3 as it extends downward, is formed in a lower end portion of the pressure surface PS2 of each of the secondstationary blades 413. The radius of curvature of the second lower curved surface CS2 is larger than the radius of curvature of the first lower curved surface CS1. - Thus, the lower end portion of the first
stationary blade 412 having a large thickness in the circumferential direction is curved more. This can suppress separation of the air flowing downward along the first lower curved surface CS1 at a position immediately below the firststationary blade 412. Accordingly, generation of turbulent flow immediately below the firststationary blade 412 can be suppressed. - Preferably, the radius of curvature of the second lower curved surface CS2 is 1.8 to 2.5 times the radius of curvature of the first lower curved surface CS1. This can suppress the occurrence of a situation in which the air flowing along the pressure surface PS1 of the first
stationary blade 412 strikes the pressure surface PS2 of the secondstationary blade 413 when this air is guided along the first lower curved surface CS1 from the lower end of the firststationary blades 412 toward the leading side in the rotational direction R. Thus, generation of turbulent flow at a region further to the lower side than the firststationary blade 412 and the secondstationary blade 413 can be suppressed, and accordingly, the airflow can be uniformed as much as possible. - Furthermore, the first
stationary blade 412 includes a first stationary bladeupper portion 4121 and a first stationary bladelower portion 4122. The first stationary bladeupper portion 4121 is inclined toward the circumferential direction toward a trailing side in the rotational direction R of the impeller 3 as it extends from the lower side toward the upper side. The first stationary bladelower portion 4122 is positioned further to the lower side than the first stationary bladeupper portion 4121 in the axial direction. The secondstationary blade 413 includes a second stationary bladeupper portion 4131 and a second stationary bladelower portion 4132. The second stationary bladeupper portion 4131 is inclined toward the circumferential direction toward the trailing side in the rotational direction R of the impeller 3 as it extends from the lower side toward the upper side. The second stationary bladelower portion 4132 is positioned further to the lower side than the second stationary bladeupper portion 4131 in the axial direction. - Thus, the air exhausted toward the leading side of the rotational direction R of the impeller 3 can be smoothly guided downward in the axial direction along the first stationary blade
upper portion 4121 and the second stationary bladeupper portion 4131. Accordingly, the blowing efficiency can be improved. - The first stationary blade
upper portion 4121 has a first pressure curvedsurface 4121A curved on thepressure surface PS 1 side and a first suction curvedsurface 4121B curved on the suction surface MS1 side. Furthermore, the second stationary bladeupper portion 4131 has a second pressure curvedsurface 4131A curved on the pressure surface PS2 side and a second suction curvedsurface 4131B curved on the suction surface MS2 side. - That is, the first stationary blade
upper portion 4121 has first curved surfaces (4121A and 4121B) curved further toward the trailing side than the first stationary bladelower portion 4122 in the rotational direction R of the impeller 3, and the second stationary bladeupper portion 4131 has second curved surfaces (4131A and 4131B) curved further toward the trailing side than the second stationary bladelower portion 4132 in the rotational direction R of the impeller 3. - Thus, the air can be smoothly guided by the first curved surfaces and the second curved surfaces. Accordingly, the blowing efficiency can be improved. In the upper portion of each of the stationary blades, it is sufficient that the curved surface be formed on at least one of the pressure surface side and the suction surface side. For example, an inclined surface as a not-curved flat surface may be formed on either of the pressure surface side and the suction surface side.
- Furthermore, when L1 is a length in the circumferential direction between a trailing end of the first
stationary blade 412 in the rotational direction R of the impeller 3 and a leading end of the first stationary bladeupper portion 4121 on the pressure surface PS1 in the rotational direction R of the impeller 3, and L2 is a length in the circumferential direction between a trailing end of the secondstationary blade 413 in the rotational direction R of the impeller 3 and a leading end of the second stationary bladeupper portion 4131 on the pressure surface PS2 in the rotational direction R of the impeller 3, L1 is larger than L2. - Thus, the
curved surface 4121A of the pressure surface PS1 of the first stationary bladeupper portion 4121 is largely curved. Accordingly, the airflow can be guided downward by the firststationary blade 412, and the airflow having been guided by the firststationary blade 412 can be further guided downward by the secondstationary blade 413. - Furthermore, the radius of curvature of the pressure surface in one of the first curved surfaces (4121A) is smaller than the radius of curvature of the pressure surface in one of the second curved surface (4131A). Thus, the air having a rotating component toward the leading side in the rotational direction R of the impeller 3 can be guided downward in the axial direction by the first stationary blade
upper portion 4121. Accordingly, the blowing efficiency can be improved. It is particularly preferable that the radius of curvature of the pressure surface in the second curved surface be 1.8 to 2.2 times the radius of curvature of the pressure surface in the first curved surface. - Furthermore, the second stationary blade
lower portion 4132 has an extended surface S21. The extended surface S21 extends in the axial direction at a position further to the lower side than the lower end of the firststationary blade 412 on the pressure surface PS2 side. Thus, the air guided by and separated from the firststationary blade 412 is smoothly guided downward along the extended surface S21. This can suppress separation of the air having been separated from the firststationary blade 412 from the secondstationary blade 413. Accordingly, the blowing efficiency can be improved. - Furthermore, the first stationary blade
lower portion 4122 has a first surface S1 that extends in the axial direction on the pressure surface PS1 side, and the second stationary bladelower portion 4132 has a second surface S2 that extends in the axial direction on the pressure surface PS2 side. The axial length of the first surface S1 is smaller than the axial length of the second surface S2. The extended surface S21 is included in the second surface S2. Thus, since the length of the second surface S2 is large in the axial direction, separation of the airflow that has been redirected by the firststationary blade 412 to flow in the axial direction from the secondstationary blade 413 can be suppressed. Accordingly, the blowing efficiency can be improved. It is particularly preferable that the axial length of the second surface S2 be 0.2 to 0.65 times the axial length of the second stationary bladelower portion 4132. - Furthermore, the axial length of the second stationary blade
upper portion 4131 is preferably 0.2 to 0.5 times the axial length of the secondstationary blade 413. Thus, the airflow is guided downward in the axial direction by the second stationary bladeupper portion 4131. Accordingly, the blowing efficiency can be improved. - Furthermore, in the circumferential direction, in a region where the first stationary blade
lower portions 4122 and the second stationary bladelower portions 4132 are superposed on one another, a width W1 between the firststationary blade 412 disposed on the trailing side in the rotational direction R of the impeller 3 out of the firststationary blades 412 adjacent to each other and the secondstationary blade 413 disposed between the firststationary blades 412 adjacent to each other is preferably 1.1 to 1.3 times a width W2 between the firststationary blade 412 disposed on the leading side in the rotational direction R of the impeller 3 out of the firststationary blades 412 adjacent to each other and the secondstationary blade 413 disposed between the firststationary blades 412 adjacent to each other. This can increase the likelihood of the airflow being guided to parts of the flow passage between the stationary blades positioned on the trailing side in the rotational direction R of the impeller 3. Accordingly, the blowing efficiency can be improved. - Furthermore, in the circumferential direction, in a region where the first
stationary blade 412 and the secondstationary blade 413 are superposed on one another, the center of each of the secondstationary blades 413 is disposed at the center of the width between the firststationary blades 412 adjacent to each other. This allows parts of the flow passage between the stationary blades to be uniform as much as possible. Accordingly, the blowing efficiency can be improved. - Furthermore, the axial length between the upper ends of the first
stationary blades 412 and the upper ends of the secondstationary blades 413 is smaller than the length of the gap in the circumferential direction between the upper ends of the firststationary blades 412 adjacent to each other in the circumferential direction. Thus, the gaps between the upper ends of the firststationary blades 412 are increased in the circumferential direction. This increases the sectional area of parts of the flow passage between the firststationary blades 412. Accordingly, more air can be guided to the parts of the flow passage between the firststationary blades 412. - Furthermore, the axial length of the region where the first
stationary blades 412 and the secondstationary blades 413 are superposed on one another in the circumferential direction is preferably 0.5 to 0.8 times the axial length of the firststationary blades 412. Accordingly, the blowing efficiency can be improved. - Furthermore, the axial length of the second
stationary blades 413 is larger than the axial length of the firststationary blades 412. Thus, with the secondstationary blades 413 having a large length, the air is smoothly guided along the secondstationary blades 413 also on the lower side of the flow passage. This can reduce the likelihood of generation of turbulent flow, and accordingly, the blowing efficiency can be improved. - As has been described, the vent holes 411A are provided in the
upper housing 41. The vent holes 411A penetrate through theupper housing 41 in the radial direction so as to allow communication between the flow passage FL and the inside of theupper housing 41. As illustrated inFig. 5 , the vent holes 411A are disposed immediately below the specified firststationary blades 412. - Part of the air having flowed through the flow passage FL and been regulated by the first
stationary blades 412 and the secondstationary blades 413 passes through the vent holes 411A and flows into the motor housing 4 (Fig. 4 ). The air having flowed into the motor housing 4 flows upward into a space disposed further to the upper side than thestator 51. The air having flowed into this space flows downward and passes through the gaps formed in thestator 51 such as gaps between the teeth so as to be exhausted through theoutlets 42A of thelower housing 42. This reduces likelihood of heat of thestator 51 being stored in the motor housing 4. Accordingly, efficiency for cooling thestator 51 can be improved. - That is, the motor housing 4 has the vent holes 411A, which penetrate through the
upper housing 41 in the radial direction so as to allow communication between the flow passage FL and the inside of the motor housing 4. Accordingly, efficiency for cooling themotor 5 can be improved. - As has been described, the cleaner 100 according to the present embodiment includes the above-described
fan 1. This allows the cleaner exhibiting improved blowing efficiency can be realized. Devices in which the fan is mounted are not limited to cleaners. The fan may be mounted in any of a variety of, for example, office automation devices, medical devices, transport devices, and home appliances other than the cleaners. - The above-described embodiment can be modified in various manners without departing from the gist of the present disclosure.
- The present disclosure can be utilized for, for example, a fan for a cleaner.
- Features of the above-described preferred embodiments and the modifications thereof may be combined appropriately as long as no conflict arises.
- While preferred embodiments of the present disclosure have been described above, it is to be understood that variations and modifications will be apparent to those skilled in the art without departing from the scope and spirit of the present disclosure. The scope of the present disclosure, therefore, is to be determined solely by the following claims.
Claims (15)
- A fan (1) comprising:an impeller (3) rotated about a vertically extending central axis (C);a motor (5) rotating the impeller (3);a motor housing (4) housing the motor (5);a fan casing (2) disposed radially outside the motor housing (4) so as to form a flow passage (FL) in a gap therebetween;a plurality of first stationary blades (412) disposed radially outside the motor housing (4), the plurality of first stationary blades (412) arranged in a circumferential direction, the plurality of first stationary blades (412) extending in an axial direction; andat least one second stationary blade (413) disposed radially outside the motor housing (4), the at least one second stationary blade (413) disposed between the first stationary blades (412) adjacent to each other in the circumferential direction out of the plurality of first stationary blades (412), the at least one second stationary blade (413) extending in the axial direction, the plurality of first stationary blades (412) and the at least one second stationary blade (413) being disposed such that an upper end of the at least one second stationary blade (413) is disposed further to a lower side than upper ends of the plurality of first stationary blades (412) and further to an upper side than lower ends of the plurality of first stationary blades (412).
- The fan (1) according to Claim 1,
wherein a lower end of the at least one second stationary blade (413) is disposed further to the lower side than the lower ends of the plurality of first stationary blades (412). - The fan (1) according to Claim 1 or 2,
wherein, when seen in the axial direction, at least one of the plurality of first stationary blades (412) is partially superposed on the at least one second stationary blade (413). - The fan (1) according to any one of Claims 1 to 3,
wherein, in the circumferential direction, a thickness of the at least one second stationary blade (413) is smaller than a thickness of the plurality of first stationary blades (412) . - The fan (1) according to any one of Claims 1 to 4,
wherein the plurality of first stationary blades (412) each include
a first stationary blade upper portion (4121) inclined toward the circumferential direction toward a trailing side in a rotational direction of the impeller (3) as the first stationary blade upper portion (4121) extends from a lower side toward an upper side, and
a first stationary blade lower portion (4122) positioned further to the lower side than the first stationary blade upper portion (4121) in the axial direction, and
wherein the at least one second stationary blade (413) includes
a second stationary blade upper portion (4131) inclined toward the circumferential direction toward the trailing side in the rotational direction of the impeller (3) as the second stationary blade upper portion (4131) extends from the lower side toward the upper side, and
a second stationary blade lower portion (4132) positioned further to the lower side than the second stationary blade upper portion (4131) in the axial direction. - The fan (1) according to Claim 5,
wherein the first stationary blade upper portion (4121) has a first curved surface (4121A, 4121B) curved further toward the trailing side than the first stationary blade lower portion (4122) in the rotational direction of the impeller (3), and
the second stationary blade upper portion (4131) has a second curved surface (4131A, 4131B) curved further toward the trailing side than the second stationary blade lower portion (4132) in the rotational direction of the impeller (3) . - The fan (1) according to Claim 6,
wherein a length (L1) in the circumferential direction between a trailing end of the first stationary blade (412) in the rotational direction of the impeller (3) and a leading end of a first pressure surface in the first stationary blade upper portion (4121) in the rotational direction of the impeller (3) is larger than a length (L2) in the circumferential direction between a trailing end of the at least one second stationary blade (413) in the rotational direction of the impeller (3) and a leading end of a second pressure surface in the second stationary blade upper portion (4131) in the rotational direction of the impeller (3). - The fan (1) according to Claim 6 or 7,
wherein a radius of curvature of the first pressure surface in the first curved surface (4121A, 4121B) is smaller than a radius of curvature of the second pressure surface in the second curved surface (4131A, 4131B). - The fan (1) according to any one of Claims 5 to 8,
wherein the second stationary blade lower portion (4132) has an extended surface (S21) extending in the axial direction on a second pressure surface side at a position further to the lower side than the lower end of the first stationary blade (412). - The fan (1) according to Claim 9,
wherein the first stationary blade lower portion (4122) has a first surface (S1) that extends in the axial direction on a first pressure surface side,
wherein the second stationary blade lower portion (4132) has a second surface (S2) that extends in the axial direction on the second pressure surface side, and
wherein, an axial length of the first surface (S1) is smaller than an axial length of the second surface (S2). - The fan (1) according to any one of Claims 1 to 10,
wherein, in the circumferential direction, in a region where the plurality of first stationary blades (412) and the at least one second stationary blade (413) are superposed on one another, a center of the at least one second stationary blade (413) is disposed at a center of a width between the first stationary blades (412) adjacent to each other. - The fan (1) according to any one of Claims 1 to 11,
wherein, an axial length between the upper ends of the plurality of first stationary blades (412) and the upper end of the at least one second stationary blade (413) is smaller than a length of a gap in the circumferential direction between the upper ends of the first stationary blades (412) adjacent to each other in the circumferential direction. - The fan (1) according to any one of Claims 1 to 12,
wherein an axial length of the at least one second stationary blade (413) is larger than an axial length of the plurality of first stationary blades (412). - The fan (1) according to any one of Claims 1 to 13,
wherein the motor housing (4) has a vent hole (411A) that penetrates therethrough in the radial direction so as to allow communication between the flow passage (FL) and an inside of the motor housing (4). - A cleaner (100) comprising:
the fan (1) according to any one of Claims 1 to 14.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2017099248A JP2018193940A (en) | 2017-05-18 | 2017-05-18 | Blower and cleaner |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3404270A1 true EP3404270A1 (en) | 2018-11-21 |
Family
ID=62200325
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP18173039.1A Withdrawn EP3404270A1 (en) | 2017-05-18 | 2018-05-17 | Fan with vaned diffuser and cleaner provided with same |
Country Status (4)
Country | Link |
---|---|
US (1) | US20180335039A1 (en) |
EP (1) | EP3404270A1 (en) |
JP (1) | JP2018193940A (en) |
CN (1) | CN108953229B (en) |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11421708B2 (en) * | 2018-03-16 | 2022-08-23 | Carrier Corporation | Refrigeration system mixed-flow compressor |
JP7044083B2 (en) * | 2019-03-01 | 2022-03-30 | 三菱電機株式会社 | An electric blower and a vacuum cleaner equipped with the electric blower |
WO2021027079A1 (en) | 2019-08-09 | 2021-02-18 | 美的威灵电机技术(上海)有限公司 | Fan and electric appliance |
EP4050222A4 (en) * | 2020-01-06 | 2022-12-21 | Guangdong Welling Motor Manufacturing Co., Ltd. | Diffuser, air supply apparatus, and dust collection equipment |
CN113074140B (en) * | 2020-01-06 | 2022-10-18 | 广东威灵电机制造有限公司 | Diffuser, air supply device and dust collector |
CN113074127B (en) * | 2020-01-06 | 2023-02-03 | 广东威灵电机制造有限公司 | Air supply device and dust collector |
CN113074138B (en) * | 2020-01-06 | 2022-05-17 | 广东威灵电机制造有限公司 | Diffusion device, fan and dust catcher |
CN113074144B (en) * | 2020-01-06 | 2023-01-20 | 广东威灵电机制造有限公司 | Diffuser, axial air supply device and dust collector |
KR20220006918A (en) * | 2020-07-09 | 2022-01-18 | 엘지전자 주식회사 | Fan motor |
CN114109863B (en) * | 2020-08-27 | 2024-01-26 | 威灵(芜湖)电机制造有限公司 | Casing assembly, electric fan and electric appliance |
WO2023143015A1 (en) * | 2022-01-30 | 2023-08-03 | 苏州简单有为科技有限公司 | Fan and vacuum cleaning robot |
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DE3807277A1 (en) * | 1988-03-05 | 1989-09-14 | Kloeckner Humboldt Deutz Ag | Blower |
US6565315B1 (en) * | 1998-07-28 | 2003-05-20 | Willy Vogel Ag | Rotation device |
JP2010196705A (en) | 2009-02-24 | 2010-09-09 | Dyson Technology Ltd | Centrifugal compressor |
CN104343734A (en) * | 2014-09-05 | 2015-02-11 | 北京动力机械研究所 | Centrifugal compressor |
US20150173577A1 (en) * | 2013-12-24 | 2015-06-25 | Samsung Electronics Co., Ltd. | Cleaning device |
US20150267546A1 (en) * | 2014-03-20 | 2015-09-24 | Rolls-Royce Deutschland Ltd. & Co Kg | Group of blade rows |
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US6629332B2 (en) * | 2001-09-18 | 2003-10-07 | The Hoover Company | Floor cleaning device with a recovery tank |
US8943645B2 (en) * | 2010-10-08 | 2015-02-03 | Husqvarna Ab | Hand-held blower devices with vacuum function |
-
2017
- 2017-05-18 JP JP2017099248A patent/JP2018193940A/en active Pending
-
2018
- 2018-05-14 US US15/978,227 patent/US20180335039A1/en not_active Abandoned
- 2018-05-17 EP EP18173039.1A patent/EP3404270A1/en not_active Withdrawn
- 2018-05-17 CN CN201810474835.9A patent/CN108953229B/en active Active
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
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DE3807277A1 (en) * | 1988-03-05 | 1989-09-14 | Kloeckner Humboldt Deutz Ag | Blower |
US6565315B1 (en) * | 1998-07-28 | 2003-05-20 | Willy Vogel Ag | Rotation device |
JP2010196705A (en) | 2009-02-24 | 2010-09-09 | Dyson Technology Ltd | Centrifugal compressor |
US20150173577A1 (en) * | 2013-12-24 | 2015-06-25 | Samsung Electronics Co., Ltd. | Cleaning device |
US20150267546A1 (en) * | 2014-03-20 | 2015-09-24 | Rolls-Royce Deutschland Ltd. & Co Kg | Group of blade rows |
CN104343734A (en) * | 2014-09-05 | 2015-02-11 | 北京动力机械研究所 | Centrifugal compressor |
Also Published As
Publication number | Publication date |
---|---|
CN108953229A (en) | 2018-12-07 |
JP2018193940A (en) | 2018-12-06 |
US20180335039A1 (en) | 2018-11-22 |
CN108953229B (en) | 2020-12-15 |
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