US20030012649A1 - Centrifugal blower - Google Patents
Centrifugal blower Download PDFInfo
- Publication number
- US20030012649A1 US20030012649A1 US10/192,131 US19213102A US2003012649A1 US 20030012649 A1 US20030012649 A1 US 20030012649A1 US 19213102 A US19213102 A US 19213102A US 2003012649 A1 US2003012649 A1 US 2003012649A1
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- United States
- Prior art keywords
- fan
- rotational shaft
- blade
- centrifugal
- airflow
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
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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
- F04D29/4233—Fan casings with volutes extending mainly in axial or radially inward direction
Definitions
- centrifugal fans use a centrifugal force to take in air in an axial direction, and to blow the air outward in a radial direction.
- the air blown out from the centrifugal fan has an airflow of an axial direction component directed from an intake side to a counter-intake side.
- L/D should be set to 0.12 and over (0.15 in the present embodiment)
- the fan inlet opening angle ⁇ 1 should be set to from 55° to 85° (65° in the present embodiment)
- the fan-outlet-opening angle ⁇ 2 should be set from 15° to 45° (35° in the present embodiment)
- the fan advancing angle ⁇ should be set from 4° to 10° (7° in the present embodiment).
Abstract
A centrifugal multi-blade fan has multiple blades about a rotational shaft and draws in air along the rotational shaft and then blows the air approximately perpendicular to the rotational shaft to reduce wind noise. A scroll casing encloses the multi-blade fan and defines a scroll-shaped airflow passage for directing the air blown from the multi-blade fan. The scroll casing has an intake opening and an outlet opening at a scroll end, in a downstream scroll casing portion. The scroll casing expands such that a flow passage cross-sectional area on the airflow downstream side is larger than that on an airflow upstream side. A ratio of a blade length to a diameter of the multi-blade fan is greater than or equal to 0.12, and an outer scroll casing radius, relative to the rotational axis, increases as a logarithmic spiral, its expansion angle being from 3.3° to 4.80°.
Description
- This application is based upon, claims the benefit of priority of, and incorporates by reference the contents of prior Japanese Patent Applications No. 2001-215649 filed Jul. 16, 2001, and No. 2001-322201 filed Oct. 19, 2001.
- 1. Field of the Invention
- The present invention relates to a centrifugal blower having a centrifugal multiblade fan (abbreviated as a centrifugal fan hereafter) applied to a vehicular air-conditioning apparatus.
- 2. Description of the Related Art
- Generally, centrifugal fans use a centrifugal force to take in air in an axial direction, and to blow the air outward in a radial direction. The air blown out from the centrifugal fan has an airflow of an axial direction component directed from an intake side to a counter-intake side.
- In the invention disclosed in Japanese Patent Laid-Open Publication No. Hei. 5-195995, an expanded part for expanding an airflow passage on the counter-intake side is formed in the airflow passage outside a centrifugal fan, and a side wall on a side of the centrifugal fan is tilted as a tilted surface in the expanded part (See FIGS. 20A and 20B). FIG. 20B is an enlargement of the area noted by the circular portion XXB of FIG. 20A. With this construction, the air blown out from the centrifugal fan flows smoothly along the tilted surface as shown as a solid line in FIG. 20B, and generation of airflow flowing toward the inlet opening along the inner wall surface on the outer peripheral side is restrained. As a result, interference (collision) of air directly flowing from the centrifugal fan toward the inner wall surface on the outer peripheral side of the scroll casing, air blown outward in the radial direction, and the air flowing toward the inlet opening along the inner wall surface on the outer periphery side is prevented from reducing wind noise.
- The inventors produced and examined the blower described in the publication above, investigated the flow of the air in detail, and found the following points.
- When the quantity of the airflow blown out from the centrifugal fan is relatively large, the air flows as described above (the solid line in FIG. 20B) and a stable swirling flow is generated. When the quantity of the airflow blown out from the centrifugal fan is relatively small, the quantity of the airflow is not enough for air which has collided with a
wall surface 74 f to flow along awall surface 74 g and atilted surface 74 h. Therefore, the flow does not extend over the entire expanded part, and a stable swirling flow is not generated. As a result, the flow becomes unstable, the airflow tends to be disturbed, and wind noise becomes worse. - In view of the foregoing problems, an object of the present invention is to provide a centrifugal blower which can sufficiently reduce the wind noise even when the airflow quantity is small.
- To attain the above object, a centrifugal blower according to a first aspect of the present invention comprises a centrifugal multiblade fan provided with multiple blades about a rotational shaft for taking in air in an axial direction of the rotational shaft and blowing the air outward in a radial direction with respect to the rotational shaft. A scroll casing is used for storing the centrifugal multiblade fan, the scroll casing constituting a scroll-shaped airflow passage for channeling the air blown out from the centrifugal multiblade fan, and having an intake opening on one end in the axial direction of the rotational shaft, and an outlet opening on an airflow downstream side of a scroll end.
- The centrifugal blower is characterized in that expanded parts, expanded in a direction parallel with the rotational shaft, are provided in the airflow passage such that a flow passage cross-sectional area on the airflow downstream side is larger than that on the airflow upstream side. Additionally, a ratio of a blade length of the blades to a diameter of the centrifugal multiblade fan is 0.12 and over, an outer peripheral radius of the scroll casing extends as a logarithmic spiral, and its expansion angle n is from 3.3° to 4.80°.
- With this construction, noise is sufficiently reduced even when the airflow quantity is small as shown in FIGS. 8 and 9 as described below.
- A centrifugal blower according to a second aspect of the present invention comprises a centrifugal multiblade fan provided with multiple blades about a rotational shaft for taking in air along an axial direction of the rotational shaft, and blowing the air outward in a radial direction. Additional components include a scroll casing for storing the centrifugal multi-blade fan, the casing constituting a scroll-shaped airflow passage for the air blown out from the centrifugal multiblade fan. Also evident are an intake opening on one end in the axial direction of the rotational shaft, and an outlet opening on the airflow downstream side of the scroll end. This centrifugal blower is characterized in that expanded parts, expanded in a direction parallel with the rotational shaft, are provided in the airflow passage such that a flow passage cross-sectional area on the airflow downstream side is larger than that on the airflow upstream side, a ratio of a blade length of the blades to a diameter of the centrifugal multiblade fan is 0.12 or above, an outer peripheral radius of the scroll casing extends as a logarithmic spiral, and its expansion angle is from 3.5° to 4.5°.
- With this construction, airflow noise is sufficiently reduced even when the airflow quantity is small as shown in FIGS. 8 and 9 described below.
- A dimension of the winding-end portion in the direction parallel with the rotational shaft is 1.1 times to 2.3 times a dimension of a nose in the scroll casing in the direction parallel with the rotational shaft in a third aspect of the invention. With this constitution, noise is sufficiently reduced even when the airflow quantity is small as shown in FIGS. 8 and 10 described below.
- The dimension of the winding-end portion in the direction parallel with the rotational shaft is from 1.3 times to 2.1 times of the dimension of a nose in the scroll casing in the direction parallel with the rotational shaft in a fourth aspect of the invention. With this constitution, noise is sufficiently reduced even when the airflow quantity is small as shown in FIGS. 8 and 10 described below.
- The airflow passage may be constituted so as to have an approximately rectangular cross-section in a fifth aspect of the invention. The airflow passage is constituted so as to have an approximately rectangular cross-section whose corners are formed as an arc (rounded internal corners) in a sixth aspect of the invention. With this constitution, since an unstable swirling flow is prevented from being generated at the corners in the airflow passage, and simultaneously, a generated swirling flow is circulated smoothly, the swirling flow is stabilized, and the noise is reduced.
- A protrusion protruding toward the centrifugal multiblade fan is provided on the inner wall on the outer periphery of the scroll casing, and has an approximately triangular shape protruding toward the centrifugal multi-blade fan as seen from a primary flow direction of the air flowing through the airflow passage in a seventh aspect of the invention.
- When the protrusion is provided at a part with which air with the highest flow rate of the air blown out from the centrifugal multiblade fan collides, the air blown out from the centrifugal multiblade fan is easily split into the inlet opening side and the outlet opening side. As a result, generation of a swirling flow is promoted, and wind noise is reduced.
- A centrifugal blower according to an eighth aspect of the present invention comprises a centrifugal multiblade fan provided with multiple blades about a rotational shaft for taking in air along an axial direction of the rotational shaft, and for blowing the air outward in a radial direction. The blower also exhibits a scroll casing for storing the centrifugal multi-blade fan, constituting a scroll-shaped airflow passage for channeling and directing the air blown away from the centrifugal multi-blade fan. The blower has an intake opening on one end in the axial direction of the rotational shaft, and an outlet opening on an airflow downstream side of a scroll end. The centrifugal blower is characterized in that a ratio of a blade length of the blades to a diameter of the centrifugal multi-blade fan is 0.12 and over, a fan inlet opening angle of the centrifugal multi-blade fan is from 55° to 85°, a fan outlet opening angle of the centrifugal multi-blade fan is from 15° to 45°, and a fan advancing angle, which is an angle between a line connecting an inlet-opening-side end of the blade with the rotational center of the multiblade fan, and a line connecting an outlet opening end of the blade with the rotational center of the multi-blade fan, ranges from 4° to 10°. With this construction, noise is sufficiently reduced even when the airflow quantity is small as shown in FIGS.16 to 19 described below.
- It is preferable that a curvature radius of the blade on the inlet opening side is equal to or less than a curvature radius of the blade on the outlet opening side in a ninth aspect of the invention.
- It is preferable that the blades have a shape for smoothly connecting curved surfaces having two or more curvature radii with one another in a tenth aspect of the invention.
- An outer peripheral side radius of the scroll casing extends as a logarithmic spiral, and its expansion angle n is from 3.3° to 4.8° in an eleventh aspect of the invention.
- With this constitution, noise is sufficiently reduced even when the airflow quantity is small as shown in FIG. 8, FIG. 9, and FIGS.16 to 19 described below.
- The outer peripheral radius of the scroll casing extends as a logarithmic spiral, and its expansion angle n is from 3.5° to 4.5° in a twelfth aspect of the invention.
- With this constitution, noise is sufficiently reduced even when the airflow quantity is small as shown in FIG. 8, FIG. 9, and FIGS.16 to 19 described below.
- It is preferable that expanded parts, expanded in a direction parallel with the rotational shaft, are provided in the airflow passage such that a flow passage cross-sectional area on the airflow downstream side is larger than that on the airflow upstream side in a thirteenth aspect of the invention.
- Further areas of applicability of the present invention will become apparent from the detailed description provided hereinafter. It should be understood that the detailed description and specific examples, while indicating the preferred embodiment of the invention, are intended for purposes of illustration only and are not intended to limit the scope of the invention.
- FIG. 1 is a schematic drawing of an air-conditioning apparatus according to embodiments of the present invention;
- FIG. 2 is a sectional view of a blower according to a first embodiment of the present invention;
- FIG. 3 is a descriptive drawing for an outlet-opening angle β2;
- FIG. 4 is a view seen from a direction indicated by an arrow A in FIG. 2;
- FIG. 5 is a view seen from a direction indicated by an arrow B in FIG. 2;
- FIG. 6A is a descriptive drawing for describing an air flowing effect of the present invention;
- FIG. 6B is a descriptive drawing for describing an air flowing effect of the present invention;
- FIG. 7 is a schematic drawing showing airflow in an airflow passage of a scroll casing;
- FIG. 8 is a graph showing a relationship between specific noise level and blade length divided by fan diameter (L/D);
- FIG. 9 is a graph showing a relationship between the specific noise level and an expansion angle;
- FIG. 10 is a graph showing a relationship between the specific noise level and an expansion ratio in an axial direction;
- FIG. 11 is a schematic drawing showing a sectional shape of an airflow passage according to a second embodiment of the present invention;
- FIG. 12 is a schematic drawing showing a sectional shape of an airflow passage according to a third embodiment of the present invention;
- FIG. 13 is a descriptive drawing showing an inlet-opening angle β1, an outlet-opening angle β2, and an advancing angle γ;
- FIG. 14A is a descriptive drawing showing a relationship between the inlet-opening angle β1, the outlet-opening angle β2, the advancing angle γ, and airflow;
- FIG. 14B is a descriptive drawing showing a relationship between the inlet-opening angle β1, the outlet-opening angle β2, the advancing angle γ, and airflow;
- FIG. 15A is a descriptive drawing showing a relationship between the inlet-opening angle β1, the outlet-opening angle β2, the advancing angle γ, and the airflow;
- FIG. 15B is a descriptive drawing showing a relationship between a large blade length and airflow;
- FIG. 16 is a chart showing a relationship between the minimum specific noise level, the ratio of blade length to fan diameter L/D, and the airflow rate;
- FIG. 17 is a chart showing a relationship between the fan inlet-opening angle β1, the specific noise level, and the airflow rate;
- FIG. 18 is a chart showing a relationship between the fan outlet-opening angle β2, and the specific noise level; and a relationship between the fan-outlet-opening angle β2 and the airflow quantity;
- FIG. 19 is a chart showing a relationship between the advancing angle γ and the specific noise level; and a relationship between the advancing angle γ and the airflow quantity; and
- FIG. 20A is a perspective view of a blower according to the prior art; and
- FIG. 20B is an enlarged view of encircled area XXB in FIG. 20A according to the prior art.
- First Embodiment
- A centrifugal blower is applied to a blower in a vehicle air-conditioning apparatus according to a first embodiment of the present invention. FIG. 1 is a schematic drawing of a vehicle air-
conditioning apparatus 1 for a vehicle equipped with a water-cooled engine, and the centrifugal blower (abbreviated as a blower hereafter) according to the present invention. - An internal
air intake opening 3 for taking in cabin air, and an externalair intake opening 4 for taking in outside air are formed on an airflow upstream side of anair conditioner casing 2 forming an airflow passage. An intake-openingswitching door 5 is provided for selectively opening and closing theintake openings switching door 5. - A filter (not shown) for removing dust in the air, and a
blower 7 according to the present invention are provided on the airflow downstream side of the intake-openingswitching door 5. Theblower 7 blows air drawn from both of theintake openings individual outlet openings - An
evaporator 9 for cooling the air blown out into a cabin is provided on the airflow downstream side of theblower 7, and the entire volume of air blown by theblower 7 passes through theevaporator 9. Aheater core 10 for heating the air blown out into the cabin is provided on the airflow downstream side of theevaporator 9, and thisheater core 10 uses the coolant for theengine 11 as a heat source to heat the air. The blower shown in FIG. 1 is a schematic drawing, and its detail will be described later. - A
bypass passage 12 for bypassing theheater core 10 is formed in theair conditioner casing 2. Anair mix door 13 for adjusting an airflow quantity ratio between an airflow quantity passing through theheater core 10, and an airflow quantity passing through thebypass passage 12 to adjust the temperature of the air blown into the cabin, is provided on the airflow upstream side of theheater core 10. - A
face aperture 14 for blowing out the air-conditioned air to the upper body of passengers in the cabin, afoot aperture 15 for blowing out the air to the feet of the passengers in the cabin, and adefroster aperture 17 for blowing out the air on the inner surface of awindshield 16 are formed on an extreme airflow downstream side of theair conditioner casing 2. - Blow
mode switching doors individual apertures mode switching doors - Generally, since a large airflow is required in a face mode where the air is blown out from the
face aperture 14 for the vehicle air-conditioning apparatus, a draft resistance (a pressure loss) for the face mode is smaller than that for the other blow modes (a foot mode for blowing out the air from thefoot aperture 15, and a defroster mode for blowing out the air from the defroster aperture 17). - The
blower 7 is a centrifugal blower which draws in air parallel to the direction of a rotational shaft and blows it away from the shaft in a radial direction (perpendicular to the rotational shaft). A centrifugal multi-blade fan 72 (abbreviated as a fan hereafter) is made of resin (polypropylene in the present embodiment) or other plastic or metal, and has a large number ofblades 71 about a rotational shaft. Aboss 71 a is present for holding themultiple blades 71. - In the present embodiment, the
fan 72 is a radial fan where a fan outlet opening angle (β2) of theblade 71 is more than 60°, and less than 120°, and the specification of thefan 72 is set such that the ratio of the blade length L of the blade 71 (see FIG. 3) to the diameter D of the fan 72 (see FIG. 2) (L/D) is 0.12 and higher (L/D=0.14 in the present embodiment). - The fan outlet opening angle β2 is an angle between the tangent line of the
blade 71 and the tangent line of an outside edge of thefan 72, and is measured on a forward side of the rotational direction of thefan 72 as shown in FIG. 3. The blade length L of theblade 71 is a difference between the outside radius and the inside radius of thefan 72. - An
electric motor 73 is driven to rotate thefan 72 in FIG. 2. A scroll casing 74 (abbreviated as a casing hereafter) stores thefan 72, and constitutes anairflow passage 74 a for circulating the air blown out from thefan 72. - As shown in FIGS. 4 and 5, the
casing 74 is made of resin (polypropylene in the present embodiment), and is made in a scroll shape about the rotational shaft of thefan 72 such that an outer peripheral radius r3 increases as a logarithmic spiral function of a scroll angle θ. An outlet opening 74 b is formed in a part on the airflow downstream of a scroll end in thecasing 74 for connecting with theair conditioner casing 2. - The logarithmic spiral is represented as
Equation 1 described below, and an expansion angle n is from 3.5° to 4.5° or from 3.3° to 4.8° (4° in the present embodiment). -
r 3=r 0·(π/180)·n·θ (Equation 1) - In this equation, θ is an angle in radians measured from a base line connecting the center of the curvature radius of a
nose 74 c with the rotational center of thefan 72 in the rotational direction of the fan, and ro is the outer peripheral inner radius on the base line (θ=0). - The
nose 74 c is a part where a scroll start side and a scroll end side overlap in thecasing 74. A part of the airflow downstream side, and a part of the airflow upstream side communicate with each other through a slight gap (not shown) in thenose 74 c. - An inlet opening75 for introducing the air into the
casing 74 opens on the opposite side of themotor 73 in the rotational axial direction on thecasing 74 as shown in FIG. 2. Abellmouth 76 is formed on an opening-outer edge 75 a of theinlet opening 75. - In a section including the rotational shaft, a
circular shroud 77 has a shape along the airflow which changes direction from the inlet opening 75 toward the outside in the radial direction (perpendicular to the shaft), and is formed on an end of theblades 71 on the side of theinlet opening 75. An opposingbent wall 78 is formed on thecasing 74 near thebellmouth 76, opposite to theshroud 77 with apredetermined gap 77 a, and smoothly bends from thebellmouth 76 toward the outside in the radial direction along the shape of theshroud 77. - In the
airflow passage 74 a of thecasing 74, the inner radius of the outer periphery r3 increases as a logarithmic spiral such that the flow passage cross-sectional area in the airflow downstream side (the side of the outlet opening 74) is larger than that in the airflow upstream side (the side of thenose 74 c in the casing 74). Simultaneously, expandedparts - A dimension H1 of the winding-end portion parallel with the rotational shaft is from 1.3 times to 2.1 times, or from 1.1 times to 2.3 times (1.5 times in the present embodiment) a dimension H0 of the
nose 74 c (at scroll angle θ=0) parallel with the rotational shaft. An expanded dimension Hup on the side of theinlet opening 75 is less than 0.4 times an expanded dimension HLR on the opposite side of the inlet opening 75 (0<Hup/HLR<0.4) in the expandedparts - The expanded dimension Hup on the side of the
inlet opening 75 is a dimension from the inner wall on the side of the inlet opening 75 to an inner wall of an upper side expanded part in thecasing 74 measured parallel with the rotational shaft as shown in FIG. 2. The upper side expanded part is a part of thecasing 74 on the scroll end side shifted by the outer diameter dimension D of thefan 72 from a part corresponding to the rotational center (the rotation shaft) of thefan 72 toward the outlet opening 74 b as shown in FIG. 4. - The expanded dimension HLR on the opposite side of the
inlet opening 75 is a dimension from the inner wall on the opposite side of the inlet opening 75 to an inner wall of a lower (far) side expanded part in thecasing 74 measured parallel to (along) the rotational shaft. The lower side expanded part is a part of thecasing 74 on the scroll end side shifted by the outer diameter dimension D of thefan 72 from the part corresponding to the rotation center (the rotation shaft) of thefan 72 to the outlet opening 74 b. - The expanded
part 74 d out of the expandedparts inlet opening 75, and is formed proximate the scroll end toward the outlet opening 74 b of thecasing 74. The expandedpart 74 e out of the expandedparts inlet opening 75, and is formed from a range of a part up to about 60° from a neighborhood of thenose 74 c in the rotational direction of thefan 72 toward the outlet opening 74 b of thecasing 74. - The following section describes characteristics (actions and effects) of the present embodiment. As described above in the summary of the invention, when the quantity of the airflow blown out from the
fan 72 is relatively small, the quantity of the airflow is not enough for air which has collided with awall surface 74 f to flow along awall surface 74 g, and the tiltedsurface 74 h. Particularly, the flow does not move across or over the entire expandedpart 74 e, and a stable swirling flow is not generated. - The air taken into the
fan 72 flows into gaps betweenblades 71 from a direction tilted with respect to the height direction (the direction parallel with the rotational shaft) of theblades 71, and is blown out from thefan 72 as shown in FIGS. 6A and 6B. - Since the
blade 71 does not add momentum to the airflow parallel to the rotational shaft between theblades 71, the air between theblades 71 has a constant velocity component in the rotational shaft direction. When the blade length L of theblade 71 increases (L1>L2), because a time required for air flowing out from the gap between theblades 71 after flowing thereinto increases, a travel distance of the air between theblades 71 in the rotational shaft direction increases (h1>h0). - When it is assumed that the airflow quantity blown out from the
fan 72 is constant regardless of the blade length L, the flow rate of the air blown out from thefan 72 increases as the blade length L of theblade 71 increases. Thus, increasing the blade length L prevents a decrease of the flow rate of the air blown out from thefan 72 when the blown air quantity is small. As a result, the flow extends over the expandedpart 74 e, a stable swirling flow is generated, and wind noise is reduced. - Since the
airflow passage 74 a curves in a scroll shape, when the air flows along theairflow passage 74 a, a secondary flow (a swirling flow) is generated as shown in FIG. 7. Since the swirling flow of the air blown out from thefan 72 matches this secondary flow (the swirling flow), the swirling flow is more stably generated, and wind noise is reduced. - When the inventors measured the specific noise level using the ratio of the blade length L of the
blade 71 to the diameter D of the fan 72 (L/D), the expansion angle n of the scroll and the expanding ratio in the axial direction (winding end portion with respect to the dimension H0 parallel to the rotational axis andnose portion 74 c withincasing 74, and the dimension HI (ratio H1/H0) which is parallel to the rotational axis) as parameters, the results as shown in FIG. 8 and FIG. 9 have been obtained. - FIG. 8 and FIG. 9 respectively show results when the cross-sectional area of the scroll air passage with respect to the winding direction angle e are set as equal, but the expansion angle n and the expanding ratio in the axial direction are varied. Therefore, when the expansion angle n is large and the expansion ratio in the axial direction is 1.0, the cross-sectional shape of the
air passage 74 a becomes oblong in the horizontal direction (perpendicular to the rotational shaft). To the contrary, when the expansion angle n is small, the expansion ratio in the axial direction becomes larger and the cross-sectional shape of theair passage 74 a becomes oblong in the vertical direction (parallel to the rotational shaft). - As clearly shown by the test results, when L/D is set to 0.12 and over, the expansion angle n is set to 3.3° and over and 4.8° and below, so the wind noise can be reduced.
- As in the first embodiment, when the expansion angle n=4° and the expansion ratio in the axial direction is 1.5, the ratio of cross-section of
air passage 74 a in length and breadth becomes approximately 2:1, which is a favorable shape in terms of a pair of swirling movement of the air flow situated above and below each other. Therefore, the airflow becomes stable and the wind noise can be greatly reduced. - On the other hand, when the expansion angle n is larger (n>4.8°), the distance from the
fan 72 to the wall surface 74 g (the outer peripheral side inner wall of the casing 74) becomes larger. Therefore, when the airflow amount is small, as in the foot mode, the momentum of air blown out from thefan 72 becomes small when it collides with the wall surface 74 g. As a result, swirling airflow is hardly generated. Also, when the expansion angle n is larger, the momentum of air blown out from thefan 72 becomes larger and swirling airflow is generated by making the blade length longer. However, since the cross-sectional shape of the air passage becomes oblong in the horizontal direction, there is not enough space for swirling movement. As a result, airflow becomes unstable and the noise cannot be reduced so much. - To the contrary, when the expansion angle n is smaller (n<3.3°), the cross-sectional shape of the
airflow passage 74 a becomes oblong in the vertical direction. Therefore, when the airflow amount is small, as in the foot mode, the airflow does not reach the wall surface 74 g and stable swirling airflow is not generated. Also, even though the expansion angle n is small, the air reaches the wall surface 74 g by lengthening the blade length. However, the swirling airflow becomes oblong in the vertical direction and the airflow becomes unstable. - FIG. 10 shows a test result with a ratio of the dimension H1 to the dimension H0 (H1/H0) as a parameter, where H1 is the dimension of the winding-end portion parallel with the rotational shaft, and H0 is the dimension of the
nose 74 c parallel with the rotational shaft in thecasing 74. As the test results clearly show, when H1/H0 is 1.3 to 2.1, the specific noise level can be reduced. Here, FIG. 10 shows the test result when L/D=0.14 and the expansion angle n=4.0°. - The definition of the specific noise level follows JIS B 0132, and the test method is based on JIS B 8340.
- In the present embodiment, L/D is set to 0.12 and over, the expansion angle n is set to from 3.5° to 4.5°, and H1/H0 is set from 1.3 to 2.1. However, the present embodiment is not limited to these conditions. It is only necessary to set L/D to 0.12 and over and to set the expansion angle n from 3.5° to 4.5°, or to set L/D to 0.12 and over, and to set H1/H0 from 1.3 to 2.1.
- Second Embodiment
- The cross-section of the
flow passage 74 a can be set as an approximately rectangular shape whose corners are arcs in a second embodiment as shown in FIG. 11. With this structure, since an unstable swirling flow is prevented from being generated at the corners of theairflow passage 74 a, and simultaneously, a generated swirling flow is smoothly circulated, the swirling flow is stabilized, and wind noise is reduced. It is preferable that the curvature radius of the arcs is properly set according to the radius of the swirling flow generated in theairflow passage 74 a. - Third Embodiment
- FIG. 12 shows a third embodiment of the present invention. A
protrusion 74 j protruding toward thefan 72 is formed along almost theentire airflow passage 74 a on the inner wall of the outer peripheral portion of thecasing 74, and the cross-section of theprotrusion 74 j is approximately triangular (wedge-shaped) and protrudes toward thefan 72 when theprotrusion 74 j is seen from a primary flow direction of the air flowing through theairflow passage 74 a. - With this structure, since the
protrusion 74 j is provided at a part with which air with the highest flow rate of the air blown out from thefan 72 collides, the air blown out from thefan 72 is easily divided into the side of theinlet opening 75 and the opposite side. This promotes the generation of swirling flow to reduce wind noise generation. - Fourth Embodiment
- In the present embodiment, the blade length L is extended to shift the air blown out from the
fan 72 toward the opposite side of the inlet opening 75 for increasing the flow rate. Also, the air blown out from thefan 72 collides with thewall surface 74 f to generate a stable swirling flow as described above. In a fourth embodiment, L/D is set to 0.12 and over, a fan inlet opening angle β1 is set from 55° to 85°, a fan outlet opening angle β2 is set from 15° to 45°, and a fan advancing angle γ is set to 4° to 10°. With these settings, the air is prevented from separating from theblades 71 and from between theblades 71. Also, air counter-flow is prevented from forming between theblades 71 at the outlet opening side of the fan, and wind noise is reduced. - With reference to FIG. 13, the fan inlet opening angle β1 is an angle between the tangent line of the
blade 71 and the tangent line of an inside edge of thefan 72, and is measured on the forward-facing side of the blade in the rotational direction of thefan 72 as shown in FIG. 13. The fan advancing angle γ is an angle between a line L1 connecting an end of theblade 71 closest to an inlet opening side with the rotational center of thefan 72 and a line L2 connecting an end of theblade 71 near an outlet opening side with the rotation center of thefan 72. That is, line L1 is drawn from the rotational center of thefan 72 tangent to a first end of theblade 71 that is closest to the rotational center. This first point of tangency is on the front side of the blade that leads during the rotation of theblade 71. The line L2 is drawn from the rotational center of thefan 72 tangent to a second end of theblade 71 farthest from the rotational center. This second point of tangency is on the front side of theblade 71 that leads during the rotation of theblade 71. - The following section describes characteristics (actions and effects) of the present embodiment.
- FIG. 14A shows a state of the air flowing between the
blades 71 when the fan inlet opening angle β1 is large (about 90°). When the fan inlet opening angle β1 is larger than an angle at which the air flows into the fan 72 (theoretical flow-in angle is about 30°), the air between theblades 71 is separated from theblade 71 on the forward side in the rotational direction. Thus, a flow rate distribution on the fan outlet opening side becomes uneven, and noise tends to be generated. - FIG. 14B shows a state of the air flowing between the
blades 71 when the fan inlet opening angle β1 is set to the theoretical flow-in angle. In this state, though, the separation of the air from theblade 71 on the forward side in the rotation direction is prevented on the inlet opening side. However, when the fan advancing angle γ is small, the air separated from theblade 71 on the forward side in the rotation direction is blown out without being attached to theblade 71 again on the outlet opening side. As a result, a counter-flow is generated on the forward side in the rotation direction, and new noise may be generated. - In the present embodiment, L/D, the fan inlet opening angle β1, the fan outlet opening angle β2, and the fan advancing angle γ are set to proper values, and the separation on the inlet opening side is restrained, and simultaneously, the air separated from the
blade 71 on the forward side in the rotational direction is attached again as shown in FIGS. 15A and 15B. As a result, the airflow between theblades 71 is optimized, a stable swirling flow is generated, and noise is reduced. - FIG. 16 represents a test result showing a relationship between L/D and the minimum specific noise level, and a relationship between L/D and the airflow rate. FIG. 17 represents a test result showing a relationship between the fan inlet opening angle β1 and the specific noise level, and a relationship between the fan inlet opening angle β1 and the airflow rate. FIG. 18 represents a test result showing a relationship between the fan outlet opening angle β2 and the specific noise level, and a relationship between the fan outlet opening angle β2 and the airflow rate. FIG. 19 represents a test result showing a relationship between the advancing angle γ and the specific noise level, and a relationship between the advancing angle γ and the airflow rate. The test conditions and the definitions of the technical terms are the same as those in the embodiments described above.
- As these test results clearly show, L/D should be set to 0.12 and over (0.15 in the present embodiment), the fan inlet opening angle β1 should be set to from 55° to 85° (65° in the present embodiment), the fan-outlet-opening angle β2 should be set from 15° to 45° (35° in the present embodiment), and the fan advancing angle γ should be set from 4° to 10° (7° in the present embodiment).
- In the present embodiment, the curvature radius r1 on the inlet opening side of the
blade 71 is equal to or less than the curvature radius r2 on the outlet opening side of theblade 71, and curved surfaces having more than two curvature radii r1 and r2 are smoothly connected to form theblade 71 such that the fan inlet opening angle β1, the fan outlet opening angle β2, and the fan advancing angle γ satisfy the advantageous conditions described above. However, the present embodiment is not limited to this construction, and the curvature radius may increase gradually from the inlet opening side to the outlet opening side, or may be constant as long as the conditions above are satisfied. - The present embodiment may be combined with the embodiments described above. As shown in FIGS. 8 and 9, and FIGS.16 to 19, L/D is set to 0.12 and over, the fan inlet opening angle β1 is set from 55° to 85°, the fan outlet opening angle β2 is set from 15° to 45°, the fan advancing angle γ is set from 4° to 10°, and the expansion angle n is set from 3.3° to 4.8°. Alternatively, L/D is set to 0.12 and over, the fan inlet opening angle β1 is set from 55° to 85°, the fan outlet opening angle β2 is set from 15° to 45°, the fan advancing angle γ is set from 4° to 10°, and the expansion angle n is set from 3.5° to 4.5°.
- The present embodiment may be applied to a casing not including the expanded
parts airflow passage 74 a parallel with the rotational shaft is constant). - Other Embodiments
- While the tilted
surface 74 h is provided in the expandedpart 74 e in the first embodiment, the present invention is not limited to this construction, and the airflow passage may have other shapes such as a simple rectangle, a circle, and an ellipse.
Claims (19)
1. A centrifugal blower comprising:
a centrifugal multi-blade fan having multiple blades about a rotational shaft, wherein said centrifugal fan takes in air along an axial direction of said rotational shaft and blows said air outward in a radial direction with respect to said rotational shaft; and
a scroll casing for storing said centrifugal multi-blade fan, said scroll casing defining a scroll-shaped airflow passage for directing said air blown out from said centrifugal multi-blade fan, said scroll casing having an intake opening at a first end of said rotational shaft and an outlet opening at a scroll end at an airflow downstream portion, wherein
a first expanded part and a second expanded part are expanded in a direction parallel with said rotational shaft and are provided in said airflow passage such that a flow passage cross-sectional area on the airflow downstream side is larger than that on an airflow upstream side,
a ratio of a blade length of said blades to a diameter of the centrifugal multi-blade fan is equal to or over 0.12, and
an outer peripheral radius of said scroll casing expands as a logarithmic spiral, and its expansion angle is from 3.3° to 4.8°.
2. A centrifugal blower comprising:
a centrifugal multi-blade fan provided with multiple blades about a rotational shaft for drawing in air along said rotational shaft and blowing said air outward in a radial direction, perpendicular to said rotational shaft; and
a scroll casing for storing said centrifugal multi-blade fan, said scroll casing defining a scroll-shaped airflow passage for directing said air blown out from said centrifugal multi-blade fan, and said scroll casing defines an intake opening on a first end in the axial direction of said rotational shaft, and an outlet opening at an airflow downstream side of a scroll end, wherein
a plurality of expanded parts extending in a direction parallel to said rotational shaft are provided in said airflow passage such that a flow passage cross-sectional area on the airflow downstream side is larger than that on an airflow upstream side,
a ratio of a blade length (L) of said blades to a diameter of the centrifugal multi-blade fan is equal to or over 0.12,
an outer peripheral radius of said scroll casing extends as a logarithmic spiral, wherein its expansion angle is from 3.5° to 4.5°.
3. The centrifugal blower according to claim 1 , wherein a dimension of said winding-end portion in a direction parallel with said rotational shaft is from 1.1 times to 2.3 times a dimension of a nose in said scroll casing in a direction parallel with said rotational shaft.
4. The centrifugal blower according to claim 2 , wherein a dimension of said winding-end portion in a direction parallel with said rotational shaft is from 1.1 times to 2.3 times a dimension of a nose in said scroll casing in a direction parallel with said rotational shaft.
5. The centrifugal blower according to claim 1 , wherein a dimension of said winding-end portion in a direction parallel with said rotational shaft is from 1.3 times to 2.1 times of a dimension of a nose in said scroll casing in a direction parallel with said rotational shaft.
6. The centrifugal blower according to claim 2 , wherein a dimension of said winding-end portion in a direction parallel with said rotational shaft is from 1.3 times to 2.1 times of a dimension of a nose in said scroll casing in a direction parallel with said rotational shaft.
7. The centrifugal blower according to claim 1 , wherein said airflow passage has an approximately rectangular cross-section.
8. The centrifugal blower according to claim 1 , wherein said airflow passage has an approximately rectangular cross-section with rounded interior passage corners.
9. The centrifugal blower according to claim 1 , wherein a protrusion protruding toward said centrifugal multi-blade fan is provided on an inner wall on an outer peripheral side of said scroll casing, and has an approximately triangular shape protruding toward said centrifugal multi-blade fan when viewed from a primary flow direction of the air flowing through said airflow passage.
10. A centrifugal blower comprising:
a centrifugal multi-blade fan provided with multiple blades about a rotational shaft for taking in air in an axial direction of said rotational shaft, and blowing the air outward in a radial direction; and
a scroll casing for storing said centrifugal multi-blade fan, constituting a scroll-shaped airflow passage for directing the air blown out from said centrifugal multi-blade fan, and having an intake opening proximate to a first end of said rotational shaft along the axial direction of said rotational shaft, and an outlet opening at an airflow downstream side of a scroll end of said scroll casing, wherein
a ratio of a blade length of said blades to a diameter of said centrifugal multi-blade fan is 0.12 and over,
a fan inlet opening angle of said centrifugal multi-blade fan ranges from 55° to 85°,
a fan outlet opening angle of said centrifugal multi-blade fan ranges from 15° to 45°, and
a fan advancing angle, which is an angle between a line connecting an inlet opening side end of said blade with a rotational center of said multi-blade fan, and a line connecting an outlet opening side end of said blade with the rotational center of said multi-blade fan, from 4° to 10°.
11. The centrifugal blower according to claim 10 , wherein a curvature radius of said blade on an inlet opening side is equal to or less than a curvature radius of said blade on the outlet opening side.
12. The centrifugal blower according to claim 11 , wherein said blades have a shape for smoothly blending curved surfaces having two or more curvature radii.
13. The centrifugal blower according to claim 10 , wherein an outer peripheral side radius of said scroll casing extends as a logarithmic spiral, and its expansion angle is from 3.3° to 4.8°.
14. The centrifugal blower according to claim 10 , wherein an outer peripheral side radius of said scroll casing extends as a logarithmic spiral, and its expansion angle is from 3.5° to 4.5°.
15. The centrifugal blower according to claim 10 , wherein expanded parts expanded in a direction parallel with said rotational shaft are provided in said airflow passage such that a flow passage cross-sectional area on an airflow downstream side is larger than that on an airflow upstream side.
16. A centrifugal multi-blade fan for an automobile air blower comprising:
a rotational shaft to which a plurality of air-forcing blades are equidistantly attached in a radial arrangement;
a scroll casing for encompassing said rotational shaft and said plurality of blades, wherein said scroll casing is constructed as a scroll-shaped airflow passage for directing air blown out from said air-forcing blades, said scroll casing further defining an intake opening around a first end of said rotational shaft along the axial direction of said rotational shaft and an outlet opening at a scroll end portion of said scroll casing; and
a fan advancing angle, which is an angle between a first line tangent to a first end of said blade on a forward facing side of said blade and a second line tangent to a second end of said blade on a forward facing side of said blade, both of said lines passing through a rotational center of said rotational shaft, wherein said fan advancing angle is from 4° to 10°.
17. A centrifugal multi-blade fan for an automobile air blower according to claim 16 , wherein a ratio of a blade length of said plurality of blades to a diameter of said centrifugal multi-blade fan is equal to or greater than 0.12.
18. A centrifugal multi-blade fan for an automobile air blower according to claim 17 , wherein a fan inlet opening angle of said centrifugal multi-blade fan ranges from 55° to 85°.
19. A centrifugal multi-blade fan for an automobile air blower according to claim 18 , wherein a fan outlet opening angle of said centrifugal multi-blade fan ranges from 15° to 45°.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
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US11/888,080 US20070274833A1 (en) | 2001-07-16 | 2007-07-31 | Centrifugal blower |
US12/653,665 US20100098535A1 (en) | 2001-07-16 | 2009-12-16 | Centrifugal blower |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2001-215649 | 2001-07-16 | ||
JP2001215649 | 2001-07-16 | ||
JP2001322201 | 2001-10-19 | ||
JP2001-322201 | 2001-10-19 |
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US11/888,080 Division US20070274833A1 (en) | 2001-07-16 | 2007-07-31 | Centrifugal blower |
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US20030012649A1 true US20030012649A1 (en) | 2003-01-16 |
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Application Number | Title | Priority Date | Filing Date |
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US11/888,080 Abandoned US20070274833A1 (en) | 2001-07-16 | 2007-07-31 | Centrifugal blower |
US12/653,665 Abandoned US20100098535A1 (en) | 2001-07-16 | 2009-12-16 | Centrifugal blower |
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US11/888,080 Abandoned US20070274833A1 (en) | 2001-07-16 | 2007-07-31 | Centrifugal blower |
US12/653,665 Abandoned US20100098535A1 (en) | 2001-07-16 | 2009-12-16 | Centrifugal blower |
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Cited By (33)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20040244853A1 (en) * | 2002-01-03 | 2004-12-09 | Harman Jayden David | Fluid flow controller |
WO2005073561A1 (en) * | 2004-01-30 | 2005-08-11 | Pax Scientific, Inc | Housing for a centrifugal fan, pump or turbine |
US20050269458A1 (en) * | 2002-01-03 | 2005-12-08 | Harman Jayden D | Vortex ring generator |
US20060102239A1 (en) * | 2003-07-02 | 2006-05-18 | Pax Scientific, Inc. | Fluid flow control device |
US20060263201A1 (en) * | 2003-11-04 | 2006-11-23 | Harman Jayden D | Fluid circulation system |
US20060275123A1 (en) * | 2005-06-02 | 2006-12-07 | Honda Motor Co., Ltd. | Multi-blade fan for air-cooled engine |
US20070025846A1 (en) * | 2004-01-30 | 2007-02-01 | Pax Scientific, Inc. | Vortical flow rotor |
CN100334359C (en) * | 2005-02-08 | 2007-08-29 | 宁波方太厨具有限公司 | Fan Volute structure of ceiling fume exhaustor |
US20070212218A1 (en) * | 2006-03-07 | 2007-09-13 | Denso Corporation | Centrifugal blower |
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US20090114205A1 (en) * | 2007-11-06 | 2009-05-07 | Rbc Horizon, Inc. | High Efficiency Furnace Having a Blower Housing with an Enlarged Air Outlet Opening |
US20090114206A1 (en) * | 2007-11-06 | 2009-05-07 | Rbc Horizon, Inc. | Furnace Air Handler Blower Housing with an Enlarged Air Outlet Opening |
US20090123285A1 (en) * | 2006-08-24 | 2009-05-14 | Panasonic Corporation | Double suction type centrifugal fan |
US20090308472A1 (en) * | 2008-06-15 | 2009-12-17 | Jayden David Harman | Swirl Inducer |
US20100078007A1 (en) * | 2007-11-06 | 2010-04-01 | Rbc Horizon, Inc. | High Efficiency Furnace/Air Handler Blower Housing with a Side Wall Having an Exponentially Increasing Expansion Angle |
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US20110189005A1 (en) * | 2010-08-11 | 2011-08-04 | Rbc Horizon, Inc. | Low Profile, High Efficiency Blower Assembly |
US20110217188A1 (en) * | 2007-06-14 | 2011-09-08 | Rbc Horizon, Inc. | Extended Length Cutoff Blower |
US20120057971A1 (en) * | 2010-08-31 | 2012-03-08 | Denso Corporation | Centrifugal blower |
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US20120211205A1 (en) * | 2009-11-09 | 2012-08-23 | Mitsubishi Heavy Industries, Ltd. | Multi-blade centrifugal fan and air conditioner employing the same |
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US9017011B2 (en) | 2011-12-29 | 2015-04-28 | Regal Beloit America, Inc. | Furnace air handler blower with enlarged backward curved impeller and associated method of use |
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Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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DE202005004180U1 (en) | 2005-03-14 | 2006-07-27 | Ebm-Papst Landshut Gmbh | centrifugal blower |
JP5287772B2 (en) * | 2010-03-16 | 2013-09-11 | 株式会社デンソー | Centrifugal multi-blade fan |
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CN109759326A (en) * | 2019-03-28 | 2019-05-17 | 北京化工大学 | Turbo air classifier logarithmic spiral curve wind blade |
Citations (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1053154A (en) * | 1912-02-20 | 1913-02-18 | Creamery Package Mfg Co | Centrifugal fan. |
US1163778A (en) * | 1913-09-23 | 1915-12-14 | Walter P Scheurmann | Centrifugal pump. |
US3140042A (en) * | 1961-08-15 | 1964-07-07 | Fujii Noriyoshi | Wheels for centrifugal fans of the forward curved multiblade type |
US3246834A (en) * | 1963-12-18 | 1966-04-19 | Space Conditioning Inc | Blower housing |
US3394876A (en) * | 1959-07-24 | 1968-07-30 | Bruno Eck | Drum motor blade construction |
US3856431A (en) * | 1973-10-24 | 1974-12-24 | Singer Co | Side expansion scroll-type blowers |
US4182596A (en) * | 1978-02-16 | 1980-01-08 | Carrier Corporation | Discharge housing assembly for a vane axial fan |
US4917572A (en) * | 1988-05-23 | 1990-04-17 | Airflow Research And Manufacturing Corporation | Centrifugal blower with axial clearance |
US4919592A (en) * | 1989-01-18 | 1990-04-24 | Superstill Technology, Inc. | Radially compact fluid compressor |
US5352089A (en) * | 1992-02-19 | 1994-10-04 | Nippondenso Co., Ltd. | Multi-blades fan device |
US5813831A (en) * | 1996-03-11 | 1998-09-29 | Denso Corporation | Centrifugal blower having a bell-mouth ring for reducing noise |
US5997246A (en) * | 1998-04-02 | 1999-12-07 | Ford Motor Company | Housing for a centrifugal blower |
US6050772A (en) * | 1995-08-28 | 2000-04-18 | Toto Ltd. | Method for designing a multiblade radial fan and a multiblade radial fan |
US6142732A (en) * | 1998-05-26 | 2000-11-07 | Carrier Corporation | Fan scroll |
US6299409B1 (en) * | 1998-04-10 | 2001-10-09 | Denso Corporation | Centrifugal type blower unit |
US6439839B1 (en) * | 1999-08-10 | 2002-08-27 | Lg Electronics Inc. | Blower |
US6575701B2 (en) * | 2001-04-24 | 2003-06-10 | Denso Corporation | Blower for vehicle |
US6604906B2 (en) * | 2000-08-04 | 2003-08-12 | Calsonic Kansei Corporation | Centrifugal multiblade blower |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1197653A (en) * | 1913-08-27 | 1916-09-12 | Gen Electric | Compressor. |
US1261807A (en) * | 1916-11-08 | 1918-04-09 | John E Greenawalt | Fan-blower. |
US3407993A (en) * | 1966-10-14 | 1968-10-29 | Molon Motor & Coil Corp | Blower |
US3824028A (en) * | 1968-11-07 | 1974-07-16 | Punker Gmbh | Radial blower, especially for oil burners |
US5573369A (en) * | 1995-11-08 | 1996-11-12 | The Scott Fetzer Company | Impeller for vacuum cleaner with tapered blades |
KR100337287B1 (en) * | 1999-07-28 | 2002-05-17 | 윤종용 | centrifugal fan |
-
2002
- 2002-07-10 US US10/192,131 patent/US20030012649A1/en not_active Abandoned
- 2002-07-15 DE DE10231983A patent/DE10231983A1/en not_active Withdrawn
-
2007
- 2007-07-31 US US11/888,080 patent/US20070274833A1/en not_active Abandoned
-
2009
- 2009-12-16 US US12/653,665 patent/US20100098535A1/en not_active Abandoned
Patent Citations (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1053154A (en) * | 1912-02-20 | 1913-02-18 | Creamery Package Mfg Co | Centrifugal fan. |
US1163778A (en) * | 1913-09-23 | 1915-12-14 | Walter P Scheurmann | Centrifugal pump. |
US3394876A (en) * | 1959-07-24 | 1968-07-30 | Bruno Eck | Drum motor blade construction |
US3140042A (en) * | 1961-08-15 | 1964-07-07 | Fujii Noriyoshi | Wheels for centrifugal fans of the forward curved multiblade type |
US3246834A (en) * | 1963-12-18 | 1966-04-19 | Space Conditioning Inc | Blower housing |
US3856431A (en) * | 1973-10-24 | 1974-12-24 | Singer Co | Side expansion scroll-type blowers |
US4182596A (en) * | 1978-02-16 | 1980-01-08 | Carrier Corporation | Discharge housing assembly for a vane axial fan |
US4917572A (en) * | 1988-05-23 | 1990-04-17 | Airflow Research And Manufacturing Corporation | Centrifugal blower with axial clearance |
US4919592A (en) * | 1989-01-18 | 1990-04-24 | Superstill Technology, Inc. | Radially compact fluid compressor |
US5352089A (en) * | 1992-02-19 | 1994-10-04 | Nippondenso Co., Ltd. | Multi-blades fan device |
US6050772A (en) * | 1995-08-28 | 2000-04-18 | Toto Ltd. | Method for designing a multiblade radial fan and a multiblade radial fan |
US5813831A (en) * | 1996-03-11 | 1998-09-29 | Denso Corporation | Centrifugal blower having a bell-mouth ring for reducing noise |
US5997246A (en) * | 1998-04-02 | 1999-12-07 | Ford Motor Company | Housing for a centrifugal blower |
US6299409B1 (en) * | 1998-04-10 | 2001-10-09 | Denso Corporation | Centrifugal type blower unit |
US6142732A (en) * | 1998-05-26 | 2000-11-07 | Carrier Corporation | Fan scroll |
US6439839B1 (en) * | 1999-08-10 | 2002-08-27 | Lg Electronics Inc. | Blower |
US6604906B2 (en) * | 2000-08-04 | 2003-08-12 | Calsonic Kansei Corporation | Centrifugal multiblade blower |
US6575701B2 (en) * | 2001-04-24 | 2003-06-10 | Denso Corporation | Blower for vehicle |
Cited By (64)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8733497B2 (en) | 2002-01-03 | 2014-05-27 | Pax Scientific, Inc. | Fluid flow controller |
US7980271B2 (en) | 2002-01-03 | 2011-07-19 | Caitin, Inc. | Fluid flow controller |
US20050269458A1 (en) * | 2002-01-03 | 2005-12-08 | Harman Jayden D | Vortex ring generator |
US20040244853A1 (en) * | 2002-01-03 | 2004-12-09 | Harman Jayden David | Fluid flow controller |
US7673834B2 (en) | 2002-01-03 | 2010-03-09 | Pax Streamline, Inc. | Vortex ring generator |
US8381870B2 (en) | 2002-01-03 | 2013-02-26 | Pax Scientific, Inc. | Fluid flow controller |
US20060102239A1 (en) * | 2003-07-02 | 2006-05-18 | Pax Scientific, Inc. | Fluid flow control device |
US7802583B2 (en) | 2003-07-02 | 2010-09-28 | New Pax, Inc. | Fluid flow control device |
US8631827B2 (en) | 2003-07-02 | 2014-01-21 | Pax Scientific, Inc. | Fluid flow control device |
US20060263201A1 (en) * | 2003-11-04 | 2006-11-23 | Harman Jayden D | Fluid circulation system |
US7862302B2 (en) | 2003-11-04 | 2011-01-04 | Pax Scientific, Inc. | Fluid circulation system |
US20070025846A1 (en) * | 2004-01-30 | 2007-02-01 | Pax Scientific, Inc. | Vortical flow rotor |
US20090035132A1 (en) * | 2004-01-30 | 2009-02-05 | Pax Streamline, Inc. | Housing for a centrifugal fan, pump, or turbine |
US7488151B2 (en) | 2004-01-30 | 2009-02-10 | Pax Streamline, Inc. | Vortical flow rotor |
US7416385B2 (en) | 2004-01-30 | 2008-08-26 | Pax Streamline, Inc. | Housing for a centrifugal fan, pump, or turbine |
EA009581B1 (en) * | 2004-01-30 | 2008-02-28 | Пакс Сайентифик, Инк. | Housing for a centrifugal fan, pump or turbine |
WO2005073561A1 (en) * | 2004-01-30 | 2005-08-11 | Pax Scientific, Inc | Housing for a centrifugal fan, pump or turbine |
US7832984B2 (en) | 2004-01-30 | 2010-11-16 | Caitin, Inc. | Housing for a centrifugal fan, pump, or turbine |
CN100334359C (en) * | 2005-02-08 | 2007-08-29 | 宁波方太厨具有限公司 | Fan Volute structure of ceiling fume exhaustor |
US7618239B2 (en) * | 2005-06-02 | 2009-11-17 | Honda Motor Co., Ltd. | Multi-blade fan for air-cooled engine |
US20060275123A1 (en) * | 2005-06-02 | 2006-12-07 | Honda Motor Co., Ltd. | Multi-blade fan for air-cooled engine |
US20070212218A1 (en) * | 2006-03-07 | 2007-09-13 | Denso Corporation | Centrifugal blower |
US7972110B2 (en) * | 2006-03-07 | 2011-07-05 | Denso Corporation | Centrifugal blower |
DE102006019177A1 (en) * | 2006-04-21 | 2007-10-25 | Behr Gmbh & Co. Kg | Tumbler radial fan, in particular for a motor vehicle air conditioning system |
US8100637B2 (en) * | 2006-08-24 | 2012-01-24 | Panasonic Corporation | Double suction type centrifugal fan |
US20090123285A1 (en) * | 2006-08-24 | 2009-05-14 | Panasonic Corporation | Double suction type centrifugal fan |
US20110217188A1 (en) * | 2007-06-14 | 2011-09-08 | Rbc Horizon, Inc. | Extended Length Cutoff Blower |
US9546668B2 (en) | 2007-06-14 | 2017-01-17 | Regal Beloit America, Inc. | Extended length cutoff blower |
US8591183B2 (en) | 2007-06-14 | 2013-11-26 | Regal Beloit America, Inc. | Extended length cutoff blower |
US20100078007A1 (en) * | 2007-11-06 | 2010-04-01 | Rbc Horizon, Inc. | High Efficiency Furnace/Air Handler Blower Housing with a Side Wall Having an Exponentially Increasing Expansion Angle |
US8001958B2 (en) * | 2007-11-06 | 2011-08-23 | Rbc Horizon, Inc. | Furnace air handler blower housing with an enlarged air outlet opening |
US20100263653A2 (en) * | 2007-11-06 | 2010-10-21 | Rbc Horizon, Inc. | High Efficiency Furnace/Air Handler Blower Housing with a Side Wall Having an Exponentially Increasing Expansion Angle |
US8025049B2 (en) * | 2007-11-06 | 2011-09-27 | Rbc Horizon, Inc. | High efficiency furnace having a blower housing with an enlarged air outlet opening |
US8550066B2 (en) | 2007-11-06 | 2013-10-08 | Regal Beloit America, Inc. | High efficiency furnace/air handler blower housing with a side wall having an exponentially increasing expansion angle |
US9513029B2 (en) | 2007-11-06 | 2016-12-06 | Regal Beloit America, Inc. | High efficiency furnace/air handler blower housing with a side wall having an exponentially increasing expansion angle |
US20110114073A2 (en) * | 2007-11-06 | 2011-05-19 | Rbc Horizon, Inc. | Furnace Air Handler Blower Housing with an Enlarged Air Outlet Opening |
US20090114205A1 (en) * | 2007-11-06 | 2009-05-07 | Rbc Horizon, Inc. | High Efficiency Furnace Having a Blower Housing with an Enlarged Air Outlet Opening |
US20090114206A1 (en) * | 2007-11-06 | 2009-05-07 | Rbc Horizon, Inc. | Furnace Air Handler Blower Housing with an Enlarged Air Outlet Opening |
US20090308472A1 (en) * | 2008-06-15 | 2009-12-17 | Jayden David Harman | Swirl Inducer |
ITAN20090083A1 (en) * | 2009-11-04 | 2011-05-05 | Nello Animobono | FAN PERFECTED WITH LOW SOUND EMISSION AND WARMING DEVICE USING THE FAN. |
US9011092B2 (en) * | 2009-11-09 | 2015-04-21 | Mitsubishi Heavy Industries, Ltd. | Multi-blade centrifugal fan and air conditioner employing the same |
US20120211205A1 (en) * | 2009-11-09 | 2012-08-23 | Mitsubishi Heavy Industries, Ltd. | Multi-blade centrifugal fan and air conditioner employing the same |
US9644631B2 (en) | 2009-11-09 | 2017-05-09 | Mitsubishi Heavy Industries, Ltd. | Multi-blade centrifugal fan and air conditioner employing the same |
US20110189005A1 (en) * | 2010-08-11 | 2011-08-04 | Rbc Horizon, Inc. | Low Profile, High Efficiency Blower Assembly |
US20120057971A1 (en) * | 2010-08-31 | 2012-03-08 | Denso Corporation | Centrifugal blower |
US9206817B2 (en) * | 2010-08-31 | 2015-12-08 | Nippon Soken, Inc. | Centrifugal blower |
US9447792B2 (en) | 2010-08-31 | 2016-09-20 | Denso Corporation | Centrifugal blower |
US8427827B2 (en) * | 2010-11-05 | 2013-04-23 | Lenovo (Singapore) Pte. Ltd. | Flow rectifying cooling apparatus and a method for rectifying flow in a cooling apparatus |
US20120113588A1 (en) * | 2010-11-05 | 2012-05-10 | Lenovo (Singapore) Pte. Ltd. | Flow rectifying cooling apparatus and a method for rectifying flow in a cooling apparatus |
CN103270315A (en) * | 2010-12-21 | 2013-08-28 | 依必安-派特穆尔芬根股份有限两合公司 | Fan diffuser having a circular inlet and a rotationally asymmetrical outlet |
US9017011B2 (en) | 2011-12-29 | 2015-04-28 | Regal Beloit America, Inc. | Furnace air handler blower with enlarged backward curved impeller and associated method of use |
US9574565B2 (en) | 2012-03-12 | 2017-02-21 | Nidec Corporation | Centrifugal fan having main blade with axially upper end projecting upward |
CN103307023A (en) * | 2012-03-12 | 2013-09-18 | 日本电产株式会社 | Centrifugal fan |
US10662969B2 (en) | 2012-03-12 | 2020-05-26 | Nidec Corporation | Centrifugal fan |
US9885361B2 (en) * | 2013-12-30 | 2018-02-06 | Dongbu Daewoo Electronics Corporation | Centrifugal fan for devices including refrigerators |
US20150184663A1 (en) * | 2013-12-30 | 2015-07-02 | Dongbu Daewoo Electronics Corporation | Centrifugal fan for devices including refrigerators |
US10913324B2 (en) * | 2014-02-03 | 2021-02-09 | Denso Corporation | Blower |
US10288085B2 (en) | 2015-04-22 | 2019-05-14 | Mitsubishi Heavy Industries Thermal Systems, Ltd. | Centrifugal blower |
CN109519416A (en) * | 2017-09-19 | 2019-03-26 | 宁波方太厨具有限公司 | A kind of centrifugal blower |
CN107975493A (en) * | 2017-12-29 | 2018-05-01 | 豫新汽车空调股份有限公司 | A kind of fan for air conditioner on vehicle impeller mechanism |
US11333367B2 (en) | 2018-05-09 | 2022-05-17 | Trane International Inc. | HVACR system including multi-positional and multi-use plenum fans |
CN109291760A (en) * | 2018-09-12 | 2019-02-01 | 珠海格力电器股份有限公司 | Air exhausting structure and air-conditioning |
CN109505782A (en) * | 2018-12-24 | 2019-03-22 | 佛山市南海九洲普惠风机有限公司 | A kind of spherical kuppe impeller |
CN110552910A (en) * | 2019-09-12 | 2019-12-10 | 佛山市南海九洲普惠风机有限公司 | Wind wheel and centrifugal fan |
Also Published As
Publication number | Publication date |
---|---|
US20070274833A1 (en) | 2007-11-29 |
US20100098535A1 (en) | 2010-04-22 |
DE10231983A1 (en) | 2003-02-06 |
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