WO2004099625A1 - 遠心送風機 - Google Patents
遠心送風機 Download PDFInfo
- Publication number
- WO2004099625A1 WO2004099625A1 PCT/JP2004/005661 JP2004005661W WO2004099625A1 WO 2004099625 A1 WO2004099625 A1 WO 2004099625A1 JP 2004005661 W JP2004005661 W JP 2004005661W WO 2004099625 A1 WO2004099625 A1 WO 2004099625A1
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- WO
- WIPO (PCT)
- Prior art keywords
- impeller
- centrifugal blower
- concave portion
- suction port
- rotation axis
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/08—Sealings
- F04D29/16—Sealings between pressure and suction sides
- F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
- F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/002—Details, component parts, or accessories especially adapted for elastic fluid pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
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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
- F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
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- 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
- F05D2210/00—Working fluids
- F05D2210/10—Kind or type
- F05D2210/12—Kind or type gaseous, i.e. compressible
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S415/00—Rotary kinetic fluid motors or pumps
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
Definitions
- the present invention relates to a centrifugal blower, and more particularly, to a centrifugal blower that sucks gas from a rotation axis direction and blows out gas in a direction intersecting the rotation axis.
- FIGS. 1 and 2 show an example of a centrifugal blower called a multi-blade blower.
- FIG. 1 is a side view of a conventional multi-blade fan (specifically, a cross-sectional view taken along line AA in FIG. 2)
- FIG. 2 is a plan view of the conventional multi-blade fan. I have.
- the multi-blade blower 10 includes an impeller 13, a housing 11 for storing the impeller 13, a motor 14 for rotating the impeller 13, and the like.
- the axis OO in FIGS. 1 and 2 is the rotation axis of the impeller 13 and the motor 14.
- the impeller 13 has one end of a number of blades 33 (only a part of the number of blades 33 is shown in FIG. 2) fixed to the outer peripheral edge of the disk-shaped main plate 31, and the other end of the blades 33. Are connected by an annular side plate 32.
- the housing 11 is a scroll-shaped box in plan view, and has an opening 11a and a gas outlet lib.
- the bell mouth 12 is disposed so as to cover the opening 11a of the housing 11, and has an inlet 12a for guiding the gas to be sucked into the impeller 13.
- the suction port 12a is arranged to face the side plate 32 of the impeller 13.
- the bell mouth 12 has a curved portion 12b extending toward the impeller 13 on the inner peripheral edge of the suction port 12a, and a direction intersecting a rotation axis 0_0 formed to cover the opening 11a on the radially outer peripheral side of the curved portion 12b. And a flat portion 12c extending to the right side.
- each wing 33 of the impeller 13 pressurizes and blows out the gas from the inner space to the outer space, and the impeller 13 Gas is sucked into the space on the inner peripheral side of the impeller 13, and the air blown out to the outer peripheral side of the impeller 13 is collected at the outlet lib and is blown out. That is, the multi-blade blower 10 sucks gas mainly from the direction of the rotation axis ⁇ _ ⁇ , and blows gas from the outlet l ib, as indicated by an arrow W shown in FIGS.
- Patent Document 1 Japanese Patent Application Laid-Open No. 9-209994
- turbulence in the flow of gas near the intake port 12a causes an increase in noise and a decrease in blow performance.
- Such turbulence of the gas flow near the inlet 12a is as follows.
- the wall flow X and the swirling flow Y are forces that merge within the impeller 13. At this time, the flow is disturbed by the merge. Furthermore, if the flow disturbance occurs in the wall flow X and the swirl flow Y, the flow disturbance at the time of merging increases.
- the streamline of the wall flow X is generally orthogonal to the mainstream streamline (see arrow W) flowing into the inlet 12a from the rotation axis direction.
- a turbulence occurs.
- An object of the present invention is to provide a centrifugal blower capable of preventing flow disturbance near a suction port.
- a centrifugal blower is a centrifugal blower that sucks gas from a rotation axis direction and blows gas in a direction crossing the rotation axis, and includes an impeller and a bell mouth.
- the impeller rotates about a rotation axis.
- the bell mouth has a suction port arranged to face the impeller, and a recess around the suction port toward the impeller to form a negative pressure space. invite.
- a recess is provided around the suction mouth of the bell mouth to form a negative pressure space, and the flow of gas (wall flow) flowing into the suction mouth along the bell mouth passes near the recess.
- the water flows so as to be drawn into the space, and as a result, the wall flow flows along the bell mouth without separating.
- the turbulence of the flow near the suction port can be reduced, and the noise can be reduced and the blowing performance can be improved.
- a centrifugal blower according to a second invention is the centrifugal blower according to the first invention, wherein the bell mouth has a flat portion and a curved portion.
- the flat portion extends in a direction intersecting the rotation axis on the radially outer peripheral side of the concave portion.
- the curved portion extends toward the impeller on the radially inner peripheral side of the concave portion, and forms a suction port.
- the portion of the recess that is recessed most toward the impeller is located closer to the impeller than the connection between the flat portion and the recess, and is located closer to the impeller than the connection between the curved portion and the recess. I have.
- the recessed portion of the concave portion closest to the impeller is located closer to the impeller than the connecting portion between the flat portion and the concave portion, and is closer to the impeller than the connecting portion between the curved portion and the concave portion. Therefore, the negative pressure space formed by providing the concave portion can be reliably brought into a negative pressure state.
- a centrifugal blower according to a third aspect of the present invention is the centrifugal blower according to the second aspect, wherein the length from the center of the rotation axis to the connecting portion between the flat portion and the concave portion with respect to the outer radius of the impeller. 3.
- the length ratio is smaller than 0.8, the radial distance between the recess and the suction port is small. Surface flow reaches the inlet.
- the above length ratio is greater than 1.4 times, the radial distance between the recess and the suction port is large, so that the wall flow once suppressed separation has started to separate again. It reaches the inlet.
- a centrifugal blower according to a fourth aspect of the present invention is the centrifugal blower according to the second or third aspect, wherein the flat portion is virtually extended to the inner peripheral side and the flat surface formed on the anti-impeller side.
- the angle formed between the flat portion and the connecting portion between the flat portion and the concave portion from the portion of the concave portion closest to the impeller side to the connecting portion between the flat portion and the concave portion is 90 ° or less, which is larger than 60 °. .
- the above angle when the above angle is set to 60 ° or less, a sudden pressure change is less likely to occur when the wall flow flows from the flat portion toward the concave portion, and the effect of suppressing the separation of the wall flow is sufficiently obtained.
- the above angle is larger than 90 °, the space that hardly contributes as the negative pressure space increases, but the contribution to the improvement of the effect of suppressing the separation of the wall flow decreases. When molding with resin, etc., it is difficult to remove the mold.
- a centrifugal blower is the centrifugal blower according to any one of the twenty-fourth aspects, wherein the connecting portion between the flat portion and the concave portion and the connecting portion between the curved portion and the concave portion are virtually connected. Accordingly, the plane formed on the side opposite to the impeller is substantially orthogonal to the rotation axis. In this centrifugal blower, the plane formed on the anti-impeller side is substantially perpendicular to the rotation axis by virtually connecting the connection between the flat portion and the recess and the connection between the curved portion and the recess. Therefore, the gas flow when passing through the vicinity of the concave portion is not disturbed.
- a centrifugal blower according to a sixth invention is the centrifugal blower according to any one of the twenty-fifth inventions, wherein the bell mouth is arranged at a connection portion between the curved portion and the recess at an interval in a circumferential direction of the suction port. And further includes a plurality of protrusions protruding from the connection portion between the curved portion and the recess toward the side opposite to the impeller.
- a plurality of convex portions are formed at the connection portion between the curved portion of the bell mouth and the concave portion, that is, downstream of the flow of the concave portion.
- a centrifugal blower according to a seventh aspect of the present invention is the centrifugal blower according to the sixth aspect, wherein the most protruding portion of the convex portion on the anti-impeller side is located closer to the anti-impeller side than the connection portion between the flat portion and the concave portion. are doing.
- the portion of the projection that protrudes farthest away from the impeller is located closer to the impeller than the connection between the flat portion and the recess, so that a portion of the wall flow can be reliably formed in the projection. Can be guided to the side.
- a centrifugal blower according to an eighth aspect of the present invention is the centrifugal blower according to any one of the seventeenth aspects, wherein the recess is formed in an annular shape so as to surround the suction port.
- the concave portion is formed in an annular shape so as to surround the suction port, it has the effect of flowing along the bell mouth against the wall flow from the entire circumference of the suction port. It can reduce the turbulence of the flow near the inlet to reduce noise and improve the ventilation performance.
- a centrifugal blower is the centrifugal blower according to any one of the eighteenth aspects, wherein the impeller has a main plate, a plurality of blades, and an annular side plate.
- the main plate rotates around the rotation axis.
- the wings are arranged in a ring around the rotation axis, and the ends on the side opposite to the suction port are fixed to the main plate.
- the side plate connects the ends of the plurality of wings on the suction port side.
- the surface of the concave portion on the impeller side has a shape along the side plate.
- a centrifugal blower is the centrifugal blower according to the ninth aspect, wherein the end of the curved portion on the impeller side is arranged radially inward of the end of the side plate on the suction port side. It is arranged so as to overlap with the end of the side plate on the suction port side in the direction of the rotation axis.
- the end of the curved portion on the impeller side and the end of the side plate on the suction port side are arranged so as to overlap at a position on the radially inner peripheral side of the side plate. Merging with them becomes smooth, and noise can be further reduced.
- a centrifugal blower according to an eleventh aspect of the present invention is the centrifugal blower according to any one of the eighteenth to eighteenth aspects, comprising: an opening formed to face the impeller; and an outlet formed on the outer peripheral side. And a scroll-shaped housing for storing the impeller.
- the bell mouse is provided so that the suction port corresponds to the opening of the housing.
- the portion where the axial dimension of the housing is reduced is limited to only the portion provided with the concave portion, so that the space volume in the housing is secured.
- a centrifugal blower is the centrifugal blower according to the ninth or tenth aspect, wherein the centrifugal blower has an opening formed to face the impeller and a gas outlet formed on the outer peripheral side. And a scroll-shaped housing for storing the impeller. The bell mouth is provided so that the suction port corresponds to the opening of the housing.
- the inter-blade portion located between the plurality of wings of the main plate is notched at least at the front in the rotation direction of the wing.
- at least the inter-blade portion located between the plurality of blades of the main plate of the impeller is cut off at the front in the rotational direction of the blades. Gas flows through the gap. This makes it possible to make full use of the space volume of the housing.
- FIG. 1 is a side view (sectional view taken along line AA of FIG. 2) of a conventional multi-blade blower.
- FIG. 2 is a plan view of a conventional multi-blade blower.
- FIG. 3 is a side view (A-A cross-sectional view of FIG. 4) of the multi-blade blower according to the first embodiment of the present invention.
- FIG. 4 is a plan view of a multi-blade blower according to a first embodiment of the present invention.
- FIG. 5 is an enlarged view of FIG. 3, showing a vicinity of a concave portion of a bell mouth of the multi-blade blower.
- FIG. 6 is an enlarged view of FIG. 3, illustrating a wall flow and a swirling flow near a concave portion of a bell mouth.
- FIG. 7 is a side view of a multi-blade blower for performance comparison, corresponding to FIG. 3.
- FIG. 8 is an air volume-noise characteristic diagram comparing the performance of a multi-blade fan having a concave portion in a bell mouth and a multi-blade fan having no concave portion in a bell mouth.
- FIG. 9 is a cross-sectional view taken along line HH of FIGS. 3, 11, and 15.
- FIG. 10 is a diagram illustrating the flow of gas in the space between the blades of the impeller.
- FIG. 11 is a side view (sectional view taken along line AA of FIG. 12) of a multi-blade blower according to a second embodiment of the present invention.
- FIG. 12 is a plan view of a multi-blade blower according to a second embodiment of the present invention.
- FIG. 13 is an enlarged view of FIG. 11, showing a vicinity of a concave portion of a bell mouth of the multi-blade blower.
- FIG. 14 is an enlarged view of FIG. 11, illustrating a wall flow and a swirling flow near a concave portion of the bellmouth.
- FIG. 15 is a side view of a multi-blade blower according to a third embodiment of the present invention, corresponding to FIG. 3.
- FIG. 3 shows a multi-blade blower 110 according to the first embodiment of the present invention.
- FIG. 3 is a side view of the multi-blade blower 110 according to the first embodiment of the present invention (specifically, a cross-sectional view taken along line AA in FIG. 4), and
- FIG. FIG. 2 shows a plan view of the blower 110.
- the multi-blade blower 110 includes an impeller 113, a housing 111 for storing the impeller 113, a motor 114 for rotating the impeller 113, and the like, similarly to the conventional multi-blade blower 10 (see FIGS. 1 and 2). It is composed of Here, the axis 0-0 in FIGS. 3 and 4 is the rotation axis of the impeller 113 and the motor 114.
- the impeller 113 has one end of a number of blades 133 (only a part of the number of blades 133 is shown in FIG. 4) fixed to the outer peripheral edge of the disk-shaped main plate 131, and the other end of the blades 133.
- the side plate 132 has a different shape from the side plate 32 of the conventional multi-blade fan 10.
- the side plate 132 is an annular member that inclines toward the opposite main plate 131 side (that is, a suction port 112a side described later) with a force from the outer peripheral edge toward the inner peripheral edge.
- the housing 111 is a scroll-shaped box in plan view, and has an opening 111a and a gas outlet 111b. Further, in the present embodiment, the motor 114 is disposed in a space on the inner peripheral side of the impeller 113, and is supported by the housing 111 via a support member (not shown).
- the bell mouth 112 is disposed so as to cover the opening 11 la of the housing 111, and has a suction port 112 a for guiding the gas to be sucked to the impeller 113.
- the suction port 112 a is arranged so as to face the side plate 132 of the impeller 113.
- the Venore mouth 112 has a different shape from the bell mouth 12 of the conventional multi-blade blower 10, and has a concave portion 112d recessed toward the impeller 113 side around the inlet 112a. Yes.
- the Venore mouth 112 has a curved portion 112b extending toward the impeller 113 side on the inner peripheral edge of the suction port 112a, and a concave portion 112d formed on the radially outer peripheral side of the curved portion 112b. And a flat portion 112c formed on the radially outer peripheral side of the concave portion 112d so as to cover the opening 111a and extending in a direction intersecting the rotation axis OO.
- the recess 112d is formed in a ring shape so as to surround the suction port 112a.
- FIG. 5 is an enlarged view of FIG. 3, and is a view showing the vicinity of the concave portion 112d of the bell mouth 112 of the multi-blade blower 110.
- the connecting portion between the curved portion 112b and the concave portion 112d (specifically, the side of the anti-impeller 113) is point B, and the concave portion 112d of the concave portion 112d is most concave toward the impeller 113 (in detail, If the side of the anti-impeller 113 of this portion) is point C, and the connection between the flat portion 112c and the recess 112d (specifically, the side of the anti-impeller 113 of this portion) is point D, then point C becomes point B It is located closer to the impeller 113 than point D.
- the flat surface 115 formed by virtually connecting the point ⁇ and the point D is substantially orthogonal to the rotation axis ⁇ _ ⁇ , and the anti-impeller 113 of the flat portion 112c. Located on the same plane as the side surface. For this reason, the flow (wall flow) of the gas when passing through the vicinity of the concave portion 112d is not disturbed.
- a plane formed on the anti-impeller 113 side by virtually extending the flat portion 112c to the inner peripheral side (the same plane as the plane 115 in the present embodiment) and a point extending from the point C to the point D
- the angle ⁇ that the plane makes at point D is less than 90 °, which is greater than 60 °.
- a surface of the concave portion 112d of the bell mouth 112 on the impeller 113 side has a shape along the shape of the side plate 132. That is, by forming the concave portion 112d in the bellmouth 112, a shape along the side plate 132 is formed in the bellmouth 112.
- end of the curved portion 112b of the bell mouth 112 on the impeller 113 side is disposed radially inward of the end of the side plate 132 on the side of the inlet 112a, and the end of the side plate 132 on the side of the inlet 112a. It is arranged so that it overlaps the end in the direction of the rotation axis ⁇ _ ⁇ (see E in Fig. 5).
- the axial dimension F of the housing 111 Is limited only to the portion provided with the concave portion 112d (see f in FIG. 3), and the portion where the space volume in the housing 111 is narrowed is reduced as much as possible.
- FIG. 6 is an enlarged view of FIG. 3, and is a view for explaining the wall flow and the swirling flow near the concave portion 112d of the bell mouth 112.
- the impeller 113 rotates in the rotation direction R of FIG. Thereby, each wing 133 of the impeller 113 pressurizes and blows out the gas from the inner space to the outer space, and the gas is sucked into the inner space of the impeller 113 from the suction port 112a. At the same time, the gas blown to the outer peripheral side of the impeller 113 is collected at the outlet 111b and blown out. That is, the multi-blade blower 110 is the same as the conventional multi-blade blower 10, as indicated by the arrow W shown in FIGS. 3 and 4.
- the wall flow indicates that when the gas passes near the concave portion 112d, the space formed by providing the concave portion 112d (symbol S in FIG. 6) becomes a negative pressure, and this space S As a result, the fluid flows along the bell mouth 112 without causing flow separation like a conventional wall flow (arrow X in a two-dot chain line in the figure). Thereby, the turbulence of the flow near the suction port 112a is reduced, so that the noise is reduced and the blowing performance is improved.
- the power is 0.8 times or more and 1.4 times or less.
- the length ratio (KZ (i) R is smaller than 0.8 times, the radial distance between the concave portion 112d and the suction port 112a becomes small, Before the effect of suppressing the separation of the wall flow is sufficiently obtained, the wall flow reaches the inlet 112a.
- the concave portion 112d is arranged at an appropriate radial position according to the outer diameter size of the impeller 113, thereby forming the concave portion 112d to suppress the separation of the wall flow. Can be surely exerted as an effect of reducing the turbulence of the flow near the suction port 112a.
- the angle ⁇ is set to 60 ° or less, when the wall flow flows from the flat portion 112c toward the concave portion 112d, a sudden pressure change is unlikely to occur, and the operation of suppressing the separation of the wall flow is sufficiently performed. It's very good.
- the angle ⁇ is larger than 90 °, the space that hardly contributes as a negative pressure space increases, but the contribution to the improvement of the effect of suppressing the separation of the wall flow decreases.
- this multi-blade blower 110 by setting the angle ⁇ between the flat portion 112c and the surface facing the concave portion 112d in an appropriate angle range, the separation of the wall flow is suppressed by forming the concave portion 112d.
- the operation can be reliably exerted as an effect of reducing the turbulence of the flow near the suction port 112a.
- the concave portion 112d is formed in an annular shape so as to surround the suction port 112a, an effect of flowing along the bell mouth 112 with respect to the wall flow from the entire circumference of the suction port 112a can be exhibited. It has become.
- the gas blown to the outer periphery of the impeller 113 passes through the flow path between the bell mouse 112 and the side plate 132 in the axial direction and is sucked into the inner periphery of the impeller 113 again.
- the swirling flow (arrow Y in the figure) has a concave 112d in the bell mouth 112, and the surface of the concave 112d on the side of the impeller 113 has a shape along the side plate 132. So that it can flow smoothly toward the inner circumference side. this Thereby, the turbulence of the wall flow is reduced, and the turbulence of the swirling flow in the vicinity of the side plate 132 is also reduced, thereby reducing noise caused by the turbulence of the swirling flow.
- Both the flow Y and the axial flow of the impeller 113 can flow toward the main plate 131 side, so that the wall flow X and the swirl flow Y can be smoothly merged.
- the following experiment was performed on how the presence or absence of the concave portion 112d of the bell mouse 112 in the multi-blade blower 110 of the present embodiment affects the noise performance and the blowing performance.
- a multi-blade fan having the same impeller 213 as the impeller 113 and a bell mouth 212 without the concave portion 112d as a multi-blade blower for comparing the performance of the multi-blade blower 110 of the present embodiment.
- the blower 210 was prepared.
- the size of the impeller used in the experiment was 260 mm for the outer diameter of the impeller and 70 mm for the width of the impeller for both the impeller 113 and the impeller 213.
- FIG. 8 When airflow and noise value data were measured for these two multi-blade blowers 110 and 210, the results shown in FIG. 8 were obtained.
- the circle plot and the chain line in FIG. 8 show the experimental data of the multi-blade blower 210 for performance comparison (that is, without the bell mouth concave portion), and the square plot and the solid line show the multi-blade fan of this embodiment.
- Experimental data for blower 110 ie, with bellmouth recess
- the multi-blade fan 110 of the present embodiment is more effective than the multi-blade fan 210 for performance comparison under the same air volume condition (for example, the air volume is 7 m 3 / min).
- the noise value is reduced by about 1 dB (the same applies to other airflow conditions), indicating that the noise performance is excellent. It is considered that this is because, as described above, the turbulence of the flow near the inlet was reduced by providing the bell mouth with the concave portion.
- the rotational speed of the impeller in the same air volume condition for example, when the air volume of 7m 3 / min, multi-in-blade fan 110 is 754Min- 1, a multi-blade fan 210 in 783Min- 1, multi The blade blower 110 is smaller (the same applies to other airflow conditions). For this reason, the multi-blade fan 110 having a concave portion in the bell mouse requires less motor power to obtain the same air volume as the multi-blade blower 210 having no concave portion in the bell mouth. It has excellent performance, and it is powerful.
- the noise performance and the blowing performance can be improved.
- the gas also flows into the gap I between the main plate 131 and the housing 111 through the inter-blade portion 134.
- the space volume of the housing 111 can be fully utilized.
- the multi-blade blower 110 by providing the bell mouth 112 with the concave portion 112d, the flow of the gas (wall flow) flowing into the suction port 112a along the bell mouth 112 is prevented, and the flow is disturbed. In addition to this, it is desirable to reduce the turbulence of the flow that occurs when the wall flow merges with the main flow.
- a plurality of convex portions 312e are provided at the connection portion between the curved portion 312b of the bell mouth and the concave portion 312d, i.e. Provided.
- the multi-blade blower 310 of the present embodiment will be described with reference to the drawings.
- FIG. 11 shows a side view (specifically, a cross-sectional view taken along the line A-A in FIG. 12) of the multi-blade blower 310 according to the second embodiment
- FIG. 12 shows a plan view of the multi-blade blower 310. I have.
- the multi-blade blower 310 like the multi-blade blower 110 of the first embodiment, includes an impeller 313, a nosing 311 for enclosing the impeller 313, a motor 314 for rotating the impeller 313, and the like. I have.
- the shaft ⁇ _ ⁇ in FIGS. 11 and 12 is the impeller 313 and the motor 31 4 is the rotation axis.
- the impeller 313 has a number of blades 333 (only a part of the number of blades 333 is shown in FIG. 12) on the outer peripheral edge of the disk-shaped main plate 331. One end is fixed, and the other ends of the wings 333 are connected by an annular side plate 332.
- the housing 311 is a scroll-shaped box in a plan view, and has an opening 31 la and a gas outlet 31 lb.
- the bellows mouse 312 is disposed so as to cover the opening 311a of the housing 311 similarly to the bell mouth 112 of the first embodiment, and has a suction port 312a for guiding the gas to be sucked to the impeller 313. ing.
- the suction port 312a is arranged to face the side plate 332 of the impeller 313.
- the bell mouth 312 has a different shape from the bell mouth 112 of the multi-blade blower 110 of the first embodiment, and has a plurality of convex portions 312e in addition to the concave portions 312d. Specifically, as shown in FIGS.
- the plurality of convex portions 312e are arranged side by side at intervals in the circumferential direction of the suction port 312a at the connection portion between the curved portion 312b and the concave portion 312d. It is formed so as to protrude further from the impeller 313 side than the connection between the curved portion 312b and the concave portion 312d. Further, the plurality of convex portions 312e are radially arranged so as to correspond to the concave portion 312d provided annularly around the inlet 312a (in FIG. 12, only a part of the plurality of convex portions 312e is provided). Illustrated).
- FIG. 13 is an enlarged view of FIG. 11, and is a view showing the vicinity of the concave portion 312d of the bell mouth 312 of the multi-blade blower 310.
- connection portion between the curved portion 312b and the concave portion 312d (specifically, the side surface of the anti-impeller 313 of this portion) is point B ′, and the most The portion recessed toward the impeller 313 side (specifically, the side of the anti-impeller 313 of this portion) is designated as a point C ′, and the connection portion between the flat portion 312c and the recess 312d (specifically, the anti-impeller Assuming that the point 313 is the point D ′, the point C ′ is located closer to the impeller 313 than the points B ′ and D ′.
- the length ratio ⁇ ⁇ ′ from the rotation axis 0-0 to the point D ′ with respect to the outer radius ⁇ ) of the impeller 313 is ⁇ ⁇ ⁇ ⁇ .
- ⁇ ' is 0.8 times or more and 1.4 times or less.
- the plane 315 formed by virtually connecting the point B ′ and the point D ′ is substantially orthogonal to the rotation axis ⁇ _ ⁇ . And is located on the same plane as the surface of the flat portion 312c on the side opposite to the impeller 313.
- the angle ⁇ , formed at the point of force D 'with the plane to reach is greater than 60 ° 90. It is as follows.
- the surface of the concave portion 312d of the bell mouth 312 on the impeller 313 side (particularly, the surface corresponding to a point between the points B ′ and C ′) has a shape following the shape of the side plate 332 as in the first embodiment. have . That is, by forming the concave portion 312d in the bell mouth 312, a shape along the side plate 332 is formed in the Venore mouth 312.
- the end of the curved portion 312b of the bell mouth 312 on the impeller 313 side is disposed radially inward of the end of the side plate 332 on the suction port 312a side, as in the first embodiment, and
- the side plate 332 is disposed so as to overlap the end on the suction port 312a side in the rotation axis ⁇ - ⁇ direction.
- the projection 312e has a portion (point G ') most protruding from the impeller 313 side, which is located closer to the impeller 313 than point D'.
- the convex portion 312e is provided so as to smoothly connect the curved portion 312b and the concave portion 312d.
- the portion where the axial dimension of the housing 311 is reduced is limited to only the portion provided with the concave portion 312d, and the space inside the housing 311 is reduced.
- the part where the volume is reduced is reduced as much as possible.
- FIG. 14 is an enlarged view of FIG. 11, and is a diagram illustrating the flow of the wall surface and the swirling flow in the vicinity of the concave portion 312d of the Venore mouse 312.
- each blade 333 of the impeller 313 pressurizes and blows out the gas from the inner space to the outer space, and the gas is sucked into the inner space of the impeller 313 from the inlet 312a.
- the gas blown to the outer peripheral side of the impeller 313 is collected at the blowout port 31 lb and blown out. That is, similarly to the multi-blade blower 110 of the first embodiment, the multi-blade blower 310 sucks gas from the rotation axis 0-0 direction as indicated by an arrow W shown in FIGS. blow out gas from lb
- FIG. 11 the wall flow and the swirling flow of the gas near the suction port 312a of the Venore mouth 312 are as shown in FIG. 11 and FIG.
- the wall flow (arrow X in the figure) passes near the concave portion 312d as in the first embodiment.
- the gas Z flowing along 2b is the main stream W where the gas Z flowing along the projection 312e is merged.
- the gas Z flows more as compared with the case where the projection 312e is not formed as in the first embodiment.
- the gas also flows through the inter-blade portion 334 to the gap I ′ between the main plate 331 and the housing 311.
- the space volume of the housing 311 can be fully utilized.
- an annular side plate 132 inclined toward the anti-main plate 131 side that is, a suction port 112a side described later
- a multi-blade blower 410 having an impeller 413 using a side plate 432 having the same shape as the side plate 32 of the conventional multi-blade blower 10 (see FIG. 1) is also used.
- the multi-blade blower 410 is mainly the same as the impeller 413 having the same shape as the impeller 13 of the conventional multi-blade blower 10 and the bell mouth 112 of the multi-blade blower 110 of the first embodiment.
- a bell mouth 412 having a shape is provided.
- the housing 411 is a scroll-shaped box in a plan view, and has an opening 411a and a gas outlet 411b.
- the bellmouth 412 has the same shape as the noremouth 112 of the multi-blade blower 110 of the first embodiment, a concave portion formed in an annular shape so as to surround the sucker 412a, the curved hole 412b, and the suction port 412a.
- the connecting portion between the curved portion 412b and the concave portion 412d is a point B ", and the concave portion 412d is concaved most toward the impeller 413.
- the portion is a point C ", the connecting portion between the flat portion 412c and the concave portion 412d is a point D", and the plane formed by virtually connecting the points B "and D" is a plane 415.
- the space S can be made to have a negative pressure by providing the concave portion 412d, the flow near the suction port 412a can be reduced.
- Turbulence is reduced, and noise can be reduced and air blowing performance can be improved.
- a protrusion similar to the protrusion 312e of the bell mouth 312 of the second embodiment is provided to further reduce noise.
- the air blowing performance may be improved.
- at least a portion between the blades 433 of the main plate 431 of the impeller 413 is cut off at least in front of the blades in the rotation direction, as in the first and second embodiments.
- the space volume of the housing 411 can be fully utilized.
- the present invention is applied to a multi-blade blower having a forward-inclined blade impeller.
- gas is supplied from a rotating shaft direction such as a radial blower or a turbo blower. It can be applied to a centrifugal blower that inhales and blows out gas in a direction crossing the rotation axis.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP04729981A EP1624194A4 (en) | 2003-05-09 | 2004-04-28 | CENTRIFUGAL FAN |
US10/517,143 US7163371B2 (en) | 2003-05-09 | 2004-04-28 | Centrifugal fan |
AU2004236508A AU2004236508B2 (en) | 2003-05-09 | 2004-04-28 | Centrifugal Fan |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003-131719 | 2003-05-09 | ||
JP2003131719 | 2003-05-09 | ||
JP2003299857A JP3698150B2 (ja) | 2003-05-09 | 2003-08-25 | 遠心送風機 |
JP2003-299857 | 2003-08-25 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004099625A1 true WO2004099625A1 (ja) | 2004-11-18 |
Family
ID=33436429
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2004/005661 WO2004099625A1 (ja) | 2003-05-09 | 2004-04-28 | 遠心送風機 |
Country Status (7)
Country | Link |
---|---|
US (1) | US7163371B2 (ja) |
EP (1) | EP1624194A4 (ja) |
JP (1) | JP3698150B2 (ja) |
KR (1) | KR100625416B1 (ja) |
CN (2) | CN2723747Y (ja) |
AU (1) | AU2004236508B2 (ja) |
WO (1) | WO2004099625A1 (ja) |
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CN104295531A (zh) * | 2014-09-19 | 2015-01-21 | 珠海格力电器股份有限公司 | 离心风机以及空调器 |
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CN108713101B (zh) * | 2016-02-24 | 2019-10-18 | 株式会社电装 | 离心送风机 |
JP2018053863A (ja) * | 2016-09-30 | 2018-04-05 | 日本電産株式会社 | インペラ、遠心ファン、および送風機 |
US20180142693A1 (en) * | 2016-11-22 | 2018-05-24 | Ford Global Technologies, Llc | Blower assembly for a vehicle |
CN110073147B (zh) * | 2016-12-19 | 2021-07-02 | 三菱电机株式会社 | 空调装置 |
JP6635077B2 (ja) * | 2017-03-13 | 2020-01-22 | 株式会社デンソー | 遠心送風機 |
JP6997615B2 (ja) * | 2017-06-12 | 2022-01-17 | サンデン・オートモーティブクライメイトシステム株式会社 | 送風機 |
KR20210031183A (ko) * | 2019-09-11 | 2021-03-19 | 한온시스템 주식회사 | 차량용 블로워 유닛 및 이를 포함하는 공조장치 |
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- 2003-08-25 JP JP2003299857A patent/JP3698150B2/ja not_active Expired - Fee Related
- 2003-11-14 CN CN2003201006661U patent/CN2723747Y/zh not_active Expired - Lifetime
- 2003-11-14 CN CNB2003101163826A patent/CN1274964C/zh not_active Expired - Lifetime
-
2004
- 2004-04-28 WO PCT/JP2004/005661 patent/WO2004099625A1/ja active IP Right Grant
- 2004-04-28 US US10/517,143 patent/US7163371B2/en active Active
- 2004-04-28 EP EP04729981A patent/EP1624194A4/en not_active Withdrawn
- 2004-04-28 KR KR1020057001983A patent/KR100625416B1/ko not_active IP Right Cessation
- 2004-04-28 AU AU2004236508A patent/AU2004236508B2/en not_active Ceased
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Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN104204339A (zh) * | 2012-03-21 | 2014-12-10 | 株式会社东芝 | 衣物烘干机 |
CN104204339B (zh) * | 2012-03-21 | 2016-09-07 | 株式会社东芝 | 衣物烘干机 |
CN114930034A (zh) * | 2020-01-17 | 2022-08-19 | 三菱电机株式会社 | 离心送风机及空气调节装置 |
Also Published As
Publication number | Publication date |
---|---|
CN2723747Y (zh) | 2005-09-07 |
AU2004236508B2 (en) | 2007-07-12 |
JP3698150B2 (ja) | 2005-09-21 |
CN1548775A (zh) | 2004-11-24 |
JP2004360670A (ja) | 2004-12-24 |
EP1624194A4 (en) | 2011-08-10 |
EP1624194A1 (en) | 2006-02-08 |
KR20050028054A (ko) | 2005-03-21 |
US7163371B2 (en) | 2007-01-16 |
CN1274964C (zh) | 2006-09-13 |
AU2004236508A1 (en) | 2004-11-18 |
US20050226721A1 (en) | 2005-10-13 |
KR100625416B1 (ko) | 2006-09-15 |
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