WO2004113732A1 - 送風機 - Google Patents
送風機 Download PDFInfo
- Publication number
- WO2004113732A1 WO2004113732A1 PCT/JP2004/008839 JP2004008839W WO2004113732A1 WO 2004113732 A1 WO2004113732 A1 WO 2004113732A1 JP 2004008839 W JP2004008839 W JP 2004008839W WO 2004113732 A1 WO2004113732 A1 WO 2004113732A1
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- WO
- WIPO (PCT)
- Prior art keywords
- wing
- impeller
- bell mouth
- diameter
- boss
- Prior art date
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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
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/06—Helico-centrifugal pumps
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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
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/38—Blades
- F04D29/384—Blades characterised by form
- F04D29/386—Skewed blades
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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
Definitions
- the present invention relates to a blower used for ventilation, for example.
- the reference line of the wing is bent in the direction of rotation from the root to the middle at a predetermined inclination angle from the root to the middle, and the wing is bent from the middle to the tip.
- the reference line is bent at a predetermined inclination angle in the direction opposite to the rotation direction so that the outermost end of the reference line is located on the opposite side of the rotation direction from the line connecting the rotation center and the root. It is recorded.
- the conventional blower of the above configuration is basically a so-called axial blower in which air flows substantially along the axial direction. For this reason, there was a problem in that the mixed flow effect due to the blade shape was small in the outer periphery, and a sufficient increase in static pressure could not be obtained, the ventilation efficiency was poor, and noise increased. Disclosure of the invention
- An object of the present invention is to solve the above-described problems, and an object of the present invention is to obtain a blower capable of improving the blowing efficiency by increasing the static pressure and reducing the noise. It is.
- a blower includes: an impeller having a plurality of axial flow blades mounted on an outer peripheral surface of a boss at an interval in a circumferential direction; a case surrounding the impeller; and A bell mouth squeezed into a cylindrical shape to guide it to the case,
- the inner diameter of the mouse is smaller than the outer diameter of the impeller.
- an impeller having a plurality of blades mounted on the outer peripheral surface of the boss at an interval in the circumferential direction, a case surrounding the impeller, and a tube for guiding gas to the case.
- a bell mouth narrowed in a shape, wherein the inner diameter of the bell mouth is smaller than the outer diameter of the impeller, and a part of the wing portion located on the outer peripheral side from the inner diameter of the bell mouth is a part of the impeller.
- the bell mouth projects from the reduced-diameter end to the enlarged-diameter end in the direction along the rotation center axis.
- a boss and a plurality of blades attached to the outer peripheral surface of the boss at an interval in the circumferential direction are arranged, and when the wing is vertically projected on a plane perpendicular to the rotation center axis, A curve formed by connecting the concentric circles extending in the radial direction around the intersection with the rotation center axis and the center points of the arc lengths extending in the circumferential direction where the projected wing overlaps is formed in the circumferential direction.
- a straight line connecting the intersection and an end point on the boss side of the circumferential center curve of the wing, and a straight line connecting the intersection and any point of the circumferential center curve are defined as a center curve.
- the blade When the angle formed is a forward angle ⁇ ⁇ ⁇ with the rotation direction of the blade being positive, and the rate of change of this forward angle ⁇ ⁇ per unit length in the radial direction is defined as a forward ratio, the blade has a radially-advancing advance rate.
- FIG. 1 is a front view of a blower according to Embodiment 1 of the present invention.
- FIG. 2 is a front view of FIG. 1 excluding the bell mouth.
- FIG. 3 is a perspective view of the wing of FIG.
- FIG. 4 is a cross-sectional view taken along the line IV-IV in FIG. 1 when the blades are rotating, and is a diagram showing the flow of air when the air volume is large.
- FIG. 5 is a cross-sectional view taken along the line IV-IV in FIG. 1 when the blades are rotating, and is a diagram showing the flow of air when the air flow is small.
- FIG. 6 is a sectional view taken along the line VI-VI of FIG.
- Figure 7 shows the ratio (%) and the specific noise level (dBA) for the fan of the first embodiment.
- FIG. 8 is a relationship diagram between a forward movement rate of a swept wing portion and a specific noise level in the blower according to the first embodiment.
- FIG. 9 shows a blower according to Embodiment 2 of the present invention, and is a cross-sectional view along a rotation center axis when a blade is rotating.
- FIG. 10 shows a blower according to Embodiment 3 of the present invention, and is a cross-sectional view along a rotation center axis when a blade is rotating.
- FIG. 11 is a diagram showing the relationship between the ratio (%) and the relative value of the specific noise level in the blower according to the third embodiment.
- FIG. 12 is a diagram showing the relationship between the ratio (%) and the relative value of the static pressure difference in the blower according to the third embodiment.
- FIG. 13 shows a blower according to Embodiment 4 of the present invention, and is a cross-sectional view along the rotation center axis when the blades are rotating.
- FIG. 14 shows a blower according to Embodiment 4 of the present invention, and is a cross-sectional view along a rotation center axis when the blades are rotating.
- FIG. 15 is a view for explaining a stagger angle according to the first embodiment.
- FIG. 16 is a diagram for describing a radial center line according to the first embodiment.
- FIG. 1 is a front view of a blower according to Embodiment 1 of the present invention as viewed from a suction side,
- FIG. 2 is a front view without the bell mouth 8 in FIG. 1
- FIG. 3 is a perspective view of the wing 4 in FIG. 1
- FIG. 4 and 5 are cross-sectional views taken along line IV-IV when the wing 4 of FIG. 1 is rotating
- FIG. 6 is a cross-sectional view taken along line VI-VI of FIG.
- FIG. 2 shows a state in which the wing 4 is projected on a plane perpendicular to the rotation axis 30 which is the center axis of the boss 1, and is a view in which the plane perpendicular to the rotation axis 30 is viewed from the suction side. is there.
- This blower has a motor shaft 20, a cylindrical boss 1 directly connected concentrically with the motor shaft 20, and four bosses 1 attached at equal intervals in the circumferential direction to the outer peripheral surface of the boss 1. It has a wing 4, a cylindrical case 19 surrounding the periphery of the wing 4, and a bell mouse 8 attached to the suction side end of the case 19 to guide air into the case 19. I have.
- the boss 1 and the four blades 4 constitute an impeller, and the arrows in FIGS. 1 and 2 indicate the rotation direction of the impeller (boss 1).
- the rotation axis 30 which is the center axis of the boss 1 is the same as the rotation center axis of the impeller.
- an apparatus having a curved portion, which is disposed on the flow suction side and smoothly guides the airflow to the impeller, is called a bellmouth.
- Each wing 4 includes a forward wing portion 2 and a backward wing portion 3.
- the outermost end of the wing 4) connecting an arbitrary point of the curve 6 is defined as an advance angle ⁇ with the rotation direction of the wing 4 being positive, and the advance angle ⁇
- the rate of change per unit length in the radial direction is defined as the advance rate (° / mm).
- the advance angle 0 assumes that the clockwise rotation direction of the wing 4 from the first straight line toward the paper is positive, and the reverse rotation direction is negative. I do.
- the wing 4 rotates clockwise when viewed from a plane perpendicular to the rotation axis 30, and the suction direction is from the front to the back of the paper.
- the advance angle 0 of the wing 4 is a positive value when the second straight port is clockwise with respect to the first straight line, and the second straight port is When it is on the counterclockwise side, it is a negative value.
- the portion of the wing 4 having a positive forward value in the radial direction is the forward wing portion 2, and the portion of the wing 4 having a negative forward value is the retreating wing portion 3.
- the wing 4 composed of the forward wing portion 2 and the backward wing portion 3 has a larger arc length as going from the boss 1 side to the outer peripheral portion 7.
- the arc shape of the boundary portion 5 between the forward wing portion 2 and the retreat wing portion 3 substantially matches the arc shape at the wing radius position where the wing 4 is located.
- the advancing rate which is the variation of the advancing angle 0 of the wing 4 per unit length in the radial direction, is zero at the intersection C between the boundary 5 and the circumferential center curve 6, and the outer diameter ( On the (outer circumference) side, the forward wing portion 3 is a negative retreat wing portion 3, and on the inner diameter (boss) side of the intersection C, the forward wing portion 2 has a positive forward speed.
- the blade 4 described above is referred to as a composite blade, and the blade used for a general axial flow blower is referred to as an axial flow blade.
- the forward wing portion 2 mainly functions as an axial blower
- the backward wing portion 3 mainly functions as a centrifugal blower.
- the size of the diameter D1 of the opening 8A of the bell mouth 8 attached to the air suction side of the wing 4 approximately matches the size of the diameter D3 of the boundary 5 .
- the approximate agreement here means that there is a deviation of about 10% between the diameter D1 of the bell mouth 8 and the diameter D3 of the boundary 5 of the wing 4.
- the blade 4 As shown in FIG. 15, the blade 4 according to the present embodiment has a leading edge 4F, which is the front side in the rotation direction of each blade, and a rear edge in the rotation direction, in a cascade in which the blades 4 are developed in a cylindrical surface of each diameter.
- ⁇ the angle between the straight line L2 connecting the trailing edge 4B, which is the side, and the straight line L1 parallel to the direction of the rotation center axis, as viewed from the suction side (the stagger angle) is ⁇
- FIG. In the range from 0 ° to 90 ° in a counterclockwise direction toward the plane of paper 5.
- the center axis of rotation (rotation axis) at the portion of blade 4 in contact with boss 1 is a straight line that extends the center point of the height in the 0 direction perpendicular to the axis to the outer periphery of the blade.
- the line connecting the center points of the axial heights at each radius of the wing is defined as the radial center line g.
- a straight line that connects the center point of the axial height at the boss and any point on the radial center line G is defined as a straight line.
- the angle between the straight line and the straight line c is defined as ⁇ .
- the four blades 4 arranged on the outer peripheral surface of the boss 1 have an inclination ⁇ > 0 toward the suction side with respect to a plane perpendicular to the rotation axis 30.
- a straight line is It is inclined to the gas suction side.
- the curved surface on the pressure surface side of the impeller is inclined toward the discharge side and the outer peripheral side, so that a flow outward in the radial direction can be generated, and the static pressure can be increased.
- FIG. 16 shows the case where the radial center line G is a curve, it may be a straight line.
- FIG. 4 shows a case where the radial center line G is a straight line, and the straight line overlaps the radial center line G.
- the wing 4 has a circumferential cross-sectional shape (shape when the wing 4 is cut perpendicularly to the rotation axis 30) in the forward wing portion 2 in the area on the inner peripheral side of the diameter D 1 of the bell mouth 8.
- the swept wing portion 3 located on the outer diameter side from the diameter D 1 of the bell mouth 8 is similar to the wing of a centrifugal blower (referred to as a centrifugal wing in this specification), and has a radial direction as shown by an arrow in FIG. It becomes a meridional flow that spreads over the sea, creating a flow field similar to that of a centrifugal blower.
- Fig. 4 shows the blower with the above configuration when the air volume is large. That is, as shown by the arrow 2, the fluid flows substantially along the direction of the central axis 30 and the circumferential cross section of the blade 4 is equal to that of the axial blower, so that the fluid operates as an axial blower.
- the air volume when the air volume is small, it becomes as shown in Fig. 5. That is, the diameter of the opening 8A of the bell mouth 8 (D1 shown in Fig. 4) is smaller than the inner diameter of the case 19 (D2 shown in Fig. 4), and the meridional flow is a mixed flow as shown by arrow E.
- the component increases, and flows out of the swept wing section 3 with a negative advancing rate.
- the swept wing section 3 has a wing shape that roughly matches the meridional flow spreading in the centrifugal direction. As a result, the load on the wing 4 is reduced, and the blowing efficiency is increased.
- the wing 4 includes the forward wing portion 2 on the boss 1 side having a positive forward ratio in the radial direction and the retreat wing portion 3 on the outer peripheral side of the wing 4 having a negative forward value.
- the arc length of the wing 4 increases from the boss 1 side toward the outer peripheral side. Therefore, the arc length of the blade becomes longer toward the outer circumference in the radial direction. As the blade area increases and the effective radius of the blade flow increases, the static pressure rise due to centrifugal force increases, and it is possible to increase the blade work.
- the forward wing 2 has the same flow as the axial blower, and operates as the axial blower.
- the advancing rate retreats negatively so as to roughly match the flow, and the portion corresponding to the retreating wing 3 is similar to the wing of a centrifugal blower. Operate.
- the blower according to the present embodiment has both functions of an axial blower and a centrifugal blower, and has a flow field that expands in the radial direction similar to that of the centrifugal blower caused by the installation of the bellmouth, and a blower similar to the axial blower.
- the wing shape can be made to conform to the two flow fields, the flow field flowing in the direction parallel to the rotation center axis, and the increase in noise due to turbulence can be reduced.
- the tangent angle of the circumferential center curve 6 gradually inclines greatly toward the gas discharge side as the boss 1 moves from the boss 1 side to the boundary section 5 side.
- the tangent of the circumferential center curve 6 gradually inclines to the gas suction side, so the curved surface of the impeller is inclined to the outer periphery side, An outward flow can be generated, and a static pressure can be increased.
- the diameter of the blower on the suction side becomes equal to the diameter D1 of the bell mouth 8, and the suction area is reduced.
- the diameter of the suction side of the impeller is The diameter is equal to D1, and the flow becomes the same as that of the axial blower even when the air flow is large or small, and it operates as an axial blower.
- FIG. 7 is a diagram in which the inventor of the present application obtained an experiment of the performance of the blower having the above-described configuration.
- the ratio of the diameter D 3 of the boundary 5 to the inner diameter D 1 ′ of the bell mouth 8 D 3 ZD 1, (%) was plotted on the horizontal axis, and the bell mouth 8 was attached to the case 19 under almost the condition of the highest efficiency point.
- lower specific noise level than when Bellmouth 8 is not attached
- the inside diameter D 1 ′ of the bell mouth 8 is the diameter of the inner surface of the reduced diameter portion of the bell mouth 8 as shown in FIG.
- the diameter D 1 of the bell mouth 8 shown in FIG. 4 is the diameter of the central part of the thickness of the reduced diameter portion of the bell mouth 8, and the inner diameter D 1 ′ of the bell mouth 8 is substantially equal to the diameter D 1 .
- the highest efficiency point is defined as the outer diameter of the wing 4 (the outer diameter of the wing 4, ie, the boss 1), while the diameter D 1 (inner diameter D l,) of the opening 8 A of the bell mouth 8 is fixed. Is the outer diameter of the impeller composed of the four blades 4) and the highest point of the air blowing efficiency (static pressure X air flow / motor output) when changing.
- FIG. 8 is a diagram obtained by conducting experiments on the performance of the blower having the above-described configuration.
- the abscissa represents the advance rate of the swept wing 3 and the case 1 under the condition of the almost maximum efficiency point.
- FIG. 9 is a diagram in which the vertical axis represents the value of the specific noise level (dBA), which is lower when the bellmouth 8 is attached to 9 than when the bellmouth 8 is not attached. From this figure, it can be seen that within the range of the forward rate of 12.0 (° / mm) to 12.9 (°-/ mm), a remarkable effect was obtained in reducing the noise of the blower. It was found that the specific noise level was reduced by about 11.1 [dBA] at maximum in Fig. 2.
- a part 4 A of the wing part located on the outer peripheral side from the inner diameter of the bell mouth 8, that is, a part of the retreat wing part 3 in the present embodiment In the direction along the rotation axis 30, the bell mouth 8 protrudes from the reduced-diameter end 8 B toward the enlarged-diameter end 8 C. If the part 4 A of the wing part located on the outer peripheral side of the inner diameter of the bell mouth 8 is located at the reduced diameter end of the bell mouth 8 in the direction along the rotation center axis (rotation axis) 30 of the impeller.
- a part 4 A of the wing portion located on the outer peripheral side from the inner diameter of the bell mouth 8 is displaced along the rotation center axis (rotation axis) 30 of the impeller. Protruding from the reduced-diameter end 8B toward the enlarged-diameter end 8C reduces the leakage flow generated between the impeller and the reduced-diameter end 8B. And loss of air volume can be reduced. In addition, since the turbulence caused by leakage is reduced, noise can be reduced.
- the impeller having the composite wing described above but also a general axial flow wing or It has an impeller having centrifugal impellers, a case surrounding the impeller, and a bell mouth narrowed cylindrically to guide gas to the case, and the inside diameter of the bell mouth is smaller than the outside diameter of the impeller.
- a blower that is configured so that a part of the wing part located on the outer peripheral side from the inner diameter of the bell mouth expands from the reduced diameter end of the bell mouth in the direction along the rotation center axis of the impeller. By protruding toward the side end, the blowing efficiency can be improved and noise can be reduced as in the case of the composite wing.
- FIG. 9 is a view for explaining a configuration of a blower according to Embodiment 2 of the present invention, and is a cross-sectional view along a rotation axis (rotation center axis) 30 when blade 4 is rotating.
- the boundary portion 5 serving as the boundary between the forward wing portion 2 and the backward wing portion 3 is located on the outer peripheral side of the inner diameter of the bell mouth 8. That is, D1 'and D3.
- the wing shape of the wing 4 (impeller) on the inner peripheral side from the boundary 5 between the forward wing 2 and the retreat wing 3 is the forward wing 2 and the inner peripheral side of the inner diameter D 1 ′ of the bell mouth 8 In the area, it operates as an axial blower, so it has the characteristics of large air volume. Further, the wing shape of the wing 4 (impeller) on the inner peripheral side from the boundary part 5 is the forward wing part 2, and in the region on the outer peripheral side from the inner diameter D 1 ′ of the bell mouth 8, it is narrowed by the bell mouth 8. Therefore, the flow spreads radially outward, and the static pressure can be increased by centrifugal force.
- the shape of the wing on the outer peripheral side from the boundary portion 5 between the forward wing portion 2 and the backward wing portion 3 of the wing 4 (impeller) is the backward wing portion 3, and operates as a centrifugal blower.
- the flow almost coincides with the meridional flow spreading in the centrifugal direction, so that the load on is reduced and the air blowing efficiency is increased. Therefore, it is desirable that the boundary portion 5 between the forward wing portion 2 and the retreating wing portion 3 of the wing 4 (impeller) is located on the outer peripheral side of the inner diameter D 1 ′ of the bell mouth 8.
- the inner diameter D l, of the bellmouth 8 be closer to the boss 1 than the radial position of the boundary 5 between the forward wing portion 2 and the backward wing portion 3 of the wing 4 (impeller).
- the minimum noise point of the axial fan is on the open side, and the minimum noise point of the centrifugal fan is on the static pressure side.
- the area where the flow spreads radially outward increases, and the flow state simulates the flow on the ⁇ static pressure side of the impeller.
- the inner diameter D 1 ′ of the bell mouth 8 is increased, the flow area that spreads radially outward becomes smaller, and the area of the wing that operates as an axial blower on the boss 1 side is smaller than the inner diameter D 1 ′ of the bell mouth 8. The flow becomes larger and the flow simulates the flow on the low static pressure side.
- the boundary portion 5 serving as the boundary between the forward wing portion 2 and the retreat wing portion 3 is located on the outer peripheral side from the inner diameter of the bell mouth 8, the inner diameter D of the bell mouth 8 is By changing 1 ′, the three-dimensional flow field generated in the impeller (wing 4) is changed, and the flow difference depending on the operating point can be controlled by the inner diameter D1 ′ of the bell mouth 8.
- the relationship between the diameter D 3 of the boundary portion 5 which is the boundary between the forward wing portion 2 and the retreating wing portion 3 and the inner diameter D 1 ′ of the bell mouth 8 is D l. Not only when ⁇ D3, but also when the inner diameter D1 of the bellmouth is smaller than the outer diameter D4 of the wing, the flow can flow radially outward, and the flow spreads radially. As a result, the static pressure can be increased.
- FIG. 10 is a view for explaining a configuration of a blower according to Embodiment 3 of the present invention, and is a cross-sectional view along rotation axis 30 when blade 4 is rotating.
- the wing 4 has a forward wing portion 2 on the boss 1 side having a positive forward value in the radial direction, and an outer wing portion 2 having a negative value.
- the case has been described in which the swept wing portion 3 is provided on the circumferential side, and the arc length of the wing 4 is a compound wing that is longer from the boss 1 side toward the outer circumferential side.
- a blower including a bell mouth 8 narrowed in a shape and having a diameter smaller than the inner diameter D l of the bell mouth 8 and an outer diameter D 4 of a power impeller is also provided.
- the inside diameter D 1 ′ of the bell mouth 8 is smaller than the outside diameter D 4 of the axial impeller, the gas flow is constricted by the bell mouth when flowing into the blade ratio on the suction side of the impeller, Spreads radially outward from the mouse toward the discharge side.
- the region located inside the inner diameter D 1 ′ of the bell mouth 8 operates as an axial flow blower, and thus has a large air volume characteristic.
- the area outside the inner diameter D 1 ′ of the bell mouth 8 is constricted by the bell mouth, so that the flow spreads outward in the radial direction. It is possible to increase the static pressure.
- the inner diameter D 1 ′ of the bell mouth 8 is increased when the operating point is on the low static pressure side, and the inner diameter D 1 ′ is decreased when the operating point is on the high static pressure side.
- the operating point can be controlled, and the operating point aimed at the impeller can be used. Therefore, low noise and high efficiency can be achieved.
- the inner diameter of the bell mouth is smaller than the outer diameter of the axial flow impeller, it is possible to flow the flow radially outward.
- the static pressure can be increased by the flow spreading in the direction.
- the bell mouth that guides the air flow is located on the suction side of the axial blower (axial flow impeller), so that regardless of the mounting conditions of the axial flow impeller, the function of equalizing the distribution of the suction flow works. Turbulence flowing into the axial impeller can be reduced, and noise can be reduced.
- FIG. 11 is a diagram in which the inventor of the present invention has experimentally determined the performance of the blower having the above-described configuration.
- the outer diameter of the axial flow impeller constituted by the boss 1 and the four axial flow blades 40 is shown in FIG. (Shown as D4 in Fig. 10) and the ratio of D1 '/ D4 (%) when the inner diameter of bellmouth 8 (shown as D1' in Fig. 10) is changed
- FIG. 9 is a diagram in which the value of the specific noise level K s (d BA), which is reduced when the bell mouth 8 is attached to the case 1 9 compared to when the bell mouth 8 is not attached, is taken as the axis, and the horizontal axis is used as the axis. .
- FIG. 12 is a diagram in which the inventor of the present invention obtained an experiment of the performance of the blower having the above-described configuration.
- the outer diameter of the axial flow impeller constituted by the boss 1 and the four axial flow blades 40 is shown in FIG. (Shown as D4 in Fig. 10) and the ratio of D1 '/ D4 (%) when the inner diameter of bellmouth 8 (shown as D1' in Fig. 10) is changed
- D4 in Fig. 10 The ratio of D1 '/ D4 (%) when the inner diameter of bellmouth 8 (shown as D1' in Fig. 10) is changed
- It is a diagram when the relative value of the static pressure difference between the upstream side and the downstream side of the blower is set as the axis, and the vertical axis is set as the axis.
- the shaft Axial impellers can have high static pressure and low noise without relatively impairing the large air volume characteristics of the flow impeller.
- FIG. 13 is a view for explaining the configuration of the blower according to the fourth embodiment of the present invention.
- FIG. 14 is a cross-sectional view taken along the rotation axis 30 when the wing 4 is rotating.
- FIG. 21 is a diagram for explaining another configuration of the blower according to the fourth embodiment, and is a cross-sectional view along a rotation axis 30 when a blade 4 is rotating.
- the bold arrow Indicates the direction of gas inflow, the longer the speed is higher.
- the air path in which the impeller is arranged differs depending on the mounting conditions, and there may be a difference in the suction flow velocity in the circumferential direction of the rotation center axis 30 of the impeller on the impeller suction side.
- the inner surface of the constricted portion from the end on the enlarged diameter side to the end on the reduced diameter side of the bell mouth 8 has a curved surface shape in which the distance from the rotation center axis 30 of the impeller is not uniform in the circumferential direction.
- the distance from the rotation center axis 30 of the blade * at the reduced-diameter end of the bell mouth 8 on the left and right in FIG. Once equal on the left and right, that is, the left distance d1 and the right distance d2 are equal.
- the length (height) of the rotation center axis direction 30 (height) between the enlarged-diameter side end portion and the reduced-diameter side end portion is made longer on the right side, the inner surface of the throttle portion is rotated by the impeller.
- the distance from the central axis 30 is different between the right side and the left side in FIG. That is, the curvature of the inner surface of the throttle portion on the right side, which is the high-speed inflow side, is made larger than that on the left side.
- the length of the rotation center axis direction 30 between the enlarged-diameter side end and the reduced-diameter side end is equal on the left and right sides, and only the curvature is changed.
- the curvature of the inner surface of the narrow portion on the right side, which is the side, may be larger than that on the left side. .
- FIGS. 13 and 14 show a blower having the axial flow blade 40, a blower having the composite blade 4 can be similarly configured to obtain the same effect.
- this blower is not limited to a blower for ventilation, but can of course be applied to a blower for cooling a heat exchanger of an automobile, a refrigerator, or an air conditioner. What is blown is not limited to air, but may be any gas.
- the blower of the present invention since the inside diameter of the bell mouth is smaller than the outside diameter of the axial impeller, the flow is oblique, and the static pressure is increased by centrifugal force. In addition to creating a flow field that matches the flow near the wing surface to the wing, noise can be reduced.
- the inner diameter of the bellmouth is smaller than the outer diameter of the impeller, and a part of the wing portion located on the outer peripheral side of the inner diameter of the bellmouth is located on the reduced diameter side of the bellmouth in the direction along the rotation center axis of the impeller. Since it protrudes from the end toward the enlarged end, the circulation vortex generated by the rotation of the impeller between the reduced end and the enlarged end of the bellmouth, and the contraction of the bellmouth It is possible to control both the leakage flow from the radial end and the impeller, and it is possible to achieve high efficiency and low noise by enabling high static pressure and large air volume. .
- the wing has a forward wing portion on the boss side having a positive forward ratio in the radial direction and a retreating wing portion on the outer peripheral side having a negative value in the radial direction, and the arc length of the wing is from the boss side to the outer peripheral side. Therefore, the ventilation efficiency can be improved by increasing the static pressure, and the noise can be reduced.
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Abstract
Description
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Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
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JP2005507274A JP4610484B2 (ja) | 2003-06-18 | 2004-06-17 | 送風機 |
US10/521,787 US7331758B2 (en) | 2003-06-18 | 2004-06-17 | Blower |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003173867 | 2003-06-18 | ||
JP2003-173867 | 2003-06-18 |
Publications (1)
Publication Number | Publication Date |
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WO2004113732A1 true WO2004113732A1 (ja) | 2004-12-29 |
Family
ID=33534737
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2004/008839 WO2004113732A1 (ja) | 2003-06-18 | 2004-06-17 | 送風機 |
Country Status (5)
Country | Link |
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US (1) | US7331758B2 (ja) |
JP (2) | JP4610484B2 (ja) |
CN (3) | CN101144485B (ja) |
TW (1) | TWI274814B (ja) |
WO (1) | WO2004113732A1 (ja) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2011065039A1 (ja) * | 2009-11-26 | 2011-06-03 | 株式会社クボタ | 渦巻ポンプ |
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JPWO2008093390A1 (ja) * | 2007-01-29 | 2010-05-20 | 三菱電機株式会社 | 多翼遠心送風機 |
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- 2004-06-17 WO PCT/JP2004/008839 patent/WO2004113732A1/ja active Application Filing
- 2004-06-17 CN CN2008101781050A patent/CN101408196B/zh not_active Expired - Fee Related
- 2004-06-17 JP JP2005507274A patent/JP4610484B2/ja not_active Expired - Lifetime
- 2004-06-17 CN CNB2004800006801A patent/CN100491744C/zh not_active Expired - Fee Related
- 2004-06-17 US US10/521,787 patent/US7331758B2/en not_active Expired - Fee Related
- 2004-06-18 TW TW93117632A patent/TWI274814B/zh not_active IP Right Cessation
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JPH0968199A (ja) * | 1995-08-31 | 1997-03-11 | Mitsubishi Electric Corp | 軸流送風機、空気調和機 |
Cited By (6)
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WO2011065039A1 (ja) * | 2009-11-26 | 2011-06-03 | 株式会社クボタ | 渦巻ポンプ |
JP2011111956A (ja) * | 2009-11-26 | 2011-06-09 | Kubota Corp | 渦巻ポンプ |
CN102667176A (zh) * | 2009-11-26 | 2012-09-12 | 株式会社久保田 | 离心泵 |
JP2014231844A (ja) * | 2014-09-12 | 2014-12-11 | 株式会社クボタ | 渦巻ポンプ |
WO2017199444A1 (ja) * | 2016-05-20 | 2017-11-23 | 三菱電機株式会社 | 遠心送風機、空気調和装置および冷凍サイクル装置 |
JPWO2017199444A1 (ja) * | 2016-05-20 | 2019-02-21 | 三菱電機株式会社 | 遠心送風機、空気調和装置および冷凍サイクル装置 |
Also Published As
Publication number | Publication date |
---|---|
CN1697932A (zh) | 2005-11-16 |
US20050260075A1 (en) | 2005-11-24 |
CN101408196A (zh) | 2009-04-15 |
JP4610484B2 (ja) | 2011-01-12 |
JPWO2004113732A1 (ja) | 2006-08-03 |
CN101408196B (zh) | 2011-06-01 |
TW200508503A (en) | 2005-03-01 |
JP5059071B2 (ja) | 2012-10-24 |
CN100491744C (zh) | 2009-05-27 |
TWI274814B (en) | 2007-03-01 |
CN101144485B (zh) | 2011-10-12 |
US7331758B2 (en) | 2008-02-19 |
JP2009281392A (ja) | 2009-12-03 |
CN101144485A (zh) | 2008-03-19 |
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