Centrifugal Blower and Air Conditioner with Centrifugal Blower
A centrifugal blower having a hub (2), to an axis section of which a rotating shaft (4a) of a motor (4) is connected, and a blade wheel (1) provided with blades (3) that are stood on the outer periphery of the hub (2) at predetermined spacings in a circumferential direction and whose front edge (3a) is inclined forward in a rotation direction, wherein a bellmouth (5) having an air suction opening (6) is provided on the air suction side of the blade wheel (1). A circulation flow f2 is formed, in which the flow flows from the blowout side of the blade wheel (1) through the rear side of the air suction opening (6) in the bellmouth (5) to the blade wheel (1) into which the flow is sucked again.
The present invention relates to a centrifugal blower and an air conditioner having a centrifugal blower.
BACKGROUND ARTA typical well known centrifugal blower includes an impeller having a hub connected to a rotation shaft of a motor, a shroud arranged to face the peripheral portion thereof in a state spaced from the peripheral portion by a predetermined distance, and a plurality of vanes arranged at predetermined intervals in the circumferential direction between the shroud and the peripheral portion of the hub (see Patent Publication 1).
A centrifugal blower having no shroud includes an impeller having a hub with a central portion to which a rotation shaft of a motor is connected, a plurality of vanes arranged on the peripheral portion of the hub at predetermined intervals in the circumferential direction, and a bellmouth having an air intake port located at an air intake side of the impeller (see Patent Publication 2).
- Patent Publication 1: Japanese Laid-Open Patent Publication No. 11-101194
- Patent Publication 2: Japanese Laid-Open Patent Publication No. 10-185238
The centrifugal blower described in Patent Publication 1 is often used as a sweep back vane type centrifugal blower (i.e., a turbo fan) that has a complicated structure in which the outer diameter end of a vane end is located rearward from the inner diameter end of the vane with respect to the rotational direction of the impeller. Further, a large number of vanes are arranged between the shroud and the peripheral portion of the hub. Thus, in order to produce such an impeller, the hub and vanes must be integrally molded and a shroud, which is produced separately, must be joined with the molded body. This is problematic from the aspects of mass production and cost.
The centrifugal blower described in Patent Publication 2 is often used as a sweep forward vane type centrifugal blower (i.e., a sirocco fan) that has a simple structure in which the outer diameter end of a vane is located frontward from the inner diameter end of the vane with respect to the rotational direction of the impeller. However, the aerodynamic performance and operational noise characteristics will deteriorate unless a spiral casing is used. This is problematic from the aspects of mass production and cost.
DISCLOSURE OF THE INVENTIONAccordingly, it is an object of the present invention to provide a quiet and highly efficient centrifugal blower having superior mass productivity and enabling cost reduction and an air conditioner having such a centrifugal blower.
A first aspect of the present invention for solving the above problems is a centrifugal blower including an impeller 1 having a hub 2 with a central portion connected to a rotation shaft 4a of a motor 4 and a plurality of vanes 3 arranged on a peripheral portion of the hub 2 at predetermined intervals in a circumferential direction. The vanes are provided with front rims 3a inclined toward the front in a rotational direction. A bellmouth 5 is provided with an air intake port 6 arranged at an air intake side of the impeller. The centrifugal blower is formed so that a circulating flow f2 is generated to flow out from an outlet side of the impeller 1, flow back into the impeller 1, and pass through the rear side of the air intake port 6 of the bellmouth 5.
This structure makes it possible for an impeller 1 having sweep back type vanes represented, for example, by a turbo fan to form a circulating flow f2 which flows out from the outlet side of the impeller 1 and is drawn back into the impeller 1, passing through the rear side of the air intake port 6 of the bellmouth 5.
As a result, main air flow f, passing across the vanes 3 is drawn to the distal end side of the vanes 3 by the circulating flow f2, which improves the air speed distribution in the exit portions of the vanes 3, enabling improvement of aerodynamic performance and reduction of operational noise.
Moreover, since no shroud is required, the impeller 1 can be molded integrally, which makes it possible to simplify the structure and reduce the cost, resulting in improvement in mass productivity.
A second aspect of the present invention for solving the above problems is a centrifugal blower including an impeller 1 having a hub 2 with a central portion connected to a rotation shaft 4a of a motor 4 and a plurality of vanes 3 arranged on a peripheral portion of the hub 2 at predetermined intervals in a circumferential direction. The vanes provided with front rims 3a are neither inclined toward the front nor the rear in a rotational direction. A bellmouth 5 is provided with an air intake port 6 arranged at an air intake side of the impeller. The centrifugal blower is formed so that a circulating flow f2 is generated to flow out from an outlet side of the impeller 1, flow back into the impeller 1, and pass through the rear side of the air intake port 6 of the bellmouth 5.
This structure makes it possible for an impeller 1 having sweep back type vanes represented, for example, by a radial plate fan to form a circulating flow f2 which flows out from the outlet side of the impeller 1 and is drawn back into the impeller 1, passing through the rear side of the air intake port 6 of the bellmouth 5.
As a result, main air flow f1 passing across the vanes 3 is drawn to the distal end side of the vanes 3 by the circulating flow f2, which improves the air speed distribution in the exit portions of the vanes 3, enabling improvement of aerodynamic performance and reduction of operational noise.
Moreover, since no shroud is required, the impeller 1 can be molded integrally, which makes it possible to simplify the structure and reduce the cost, resulting in improvement in mass productivity.
It is preferred that the vanes 3 in the impeller 1 are entirely inclined in the rotational direction.
In this structure, the vanes 3 function to draw in the circulating flow f2 generated by the ring body 20. This generates a strong circulating flow f2.
Even if the inner diameter D0 of the air intake port 6 of the bellmouth 5 is enlarged, the strong circulating flow f2 will smoothly circulate near the ring body 20 without deeply entering the inner side of the vanes 3. This obtains satisfactory fan performance.
Further, the vanes 3 in the impeller 1 may entirely be inclined opposite the rotational direction.
In this structure, the vanes 3 function in the direction that makes it difficult to draw in the circulating flow f2 generated by the ring body 20.
Even if the inner diameter D0 of the air intake port 6 of the bellmouth 5 is reduced, the circulating flow f2 will smoothly circulate near the ring body 20 without deeply entering the inner side of the vanes 3. This obtains satisfactory fan performance.
Further, the vanes 3 in the impeller 1 may include vane tips inclined in the rotational direction.
In this structure, the vanes 3 function to draw in the circulating flow f2 generated by the ring body 20. This generates a strong circulating flow f2.
Even if the inner diameter D0 of the air intake port 6 of the bellmouth 5 is enlarged, the strong circulating flow f2 will smoothly circulate near the ring body 20 without deeply entering the inner side of the vanes 3. This obtains satisfactory fan performance.
Further, the vanes 3 in the impeller 1 may include vane tips inclined opposite the rotational direction.
In this structure, the vanes 3 function in the direction making it difficult to draw in the circulating flow f2 generated by the ring body 20.
Even if the inner diameter D0 of the air intake port 6 of the bellmouth 5 is reduced, the circulating flow f2 will smoothly circulate near the ring body 20 without deeply entering the inner side of the vanes 3. This obtains satisfactory fan performance.
Further, when an inner diameter of the air intake port 6 of the bellmouth 5 is represented by D0, an inner diameter of the vanes 3 in the impellers 1 is represented by D1, and an outer diameter of the vanes 3 is represented by D2, 0<(D0-D1)/(D2-D1)<0.6 may be satisfied.
In this structure, the minimum specific noise Ks may be lowered, as shown in
If (D0-D1)/(D2-D1)≧0.6 is satisfied when the number of vanes 3 is small, reversed flow f′ generated at the front rims of the vanes 3 will become strong, as shown in
If 0≧(D0-D1)/(D2-D1) is satisfied when the number of the vanes 3 is small, the front rims of the vanes 3 will not function effectively, as shown in
When an inner diameter of the air intake port 6 of the bellmouth 5 is represented by D0, the inner diameter of the vanes 3 in the impeller 1 is represented by D1, and the outer diameter of the vanes 3 is represented by D2, -0.3<(D0-D1)/(D2-D1)<0.3 may be satisfied.
In this structure; the minimum specific noise Ks may be lowered, as shown in
If (D0-D1)/(D2-D1)≧0.3 is satisfied when the number of vanes 3 is large, a reversed flow f′ generated at the front rims of the vanes 3 will become strong, as shown in
If −3≧(D0-D1)/(D2-D1) is satisfied when the number of the vanes 3 is large, the front rims of the vanes 3 will not function effectively. This inhibits the improvement of the aerodynamic performance.
A ring body 9, 20 having a predetermined width in a centrifugal direction may be attached to axial distal ends of the vanes 3 in the impeller 1. In this structure, the ring body 9, 20 rotating together with the impeller 1 functions as a rotary disk, and the viscosity action of the rotary disk induces a rotational direction flow in the outlet flow from the vanes 3. This rectifies the discharge flow and circulating flow and improves the fan performance and reduces noise.
When a width in the centrifugal direction of the ring body 20 is represented by H, and the outer diameter of the vanes 3 of the impeller 1 is represented by D2, 0.05<ki=H/D2<0.225 may be satisfied. In this structure, as shown in
It is further desirable that 0.1≦ki=H/D2≦0.15 be satisfied to reduce noise.
If ki=H/D2≦0.05 is satisfied, the effect will be reduced. If ki=H/D2≧0.225 is satisfied, the formation of circulating flow will be affected adversely to weaken the circulating flow at the rear distal portions of the vanes 3. This inhibits improvement of the aerodynamic performance.
A diagonal diffuser 23 may be arranged at the outlet side of the impeller 1 to guide air that is blown out of the impeller 1 diagonally rearward. In this structure, the dynamic pressure in the air flow blown out from the impeller 1 efficiently returns to the static pressure. This greatly contributes to improvement of the performance (that is, high efficiency and low noise).
Further, a diagonal centrifugal diffuser 23 may be arranged at the outlet side of the impeller 1 to guide air blown out of the impeller 1 in a centrifugal direction from a diagonal rear side. In this structure, the air flow blown out from the impeller 1 efficiently returns to static pressure from dynamic pressure. This equalizes the air speed distribution and greatly contributes to improvement of the performance (that is, high efficiency and low noise).
A circulation space S may be formed at a peripheral side of the air intake port 6 of the bellmouth 5 to allow passage of the circulating flow f2. In this structure, the generation of the circulating flow f2 is facilitated and ensured.
When an exit side height of the vanes 3 in the impeller 1 is represented by B and an outer diameter of the vanes 3 is represented by D2, B/D2≧0.113 is satisfied. This structure eliminates the problem of fluctuation in the air flow line f1 at the exit side of the impeller 1 and obtains stable performance.
If B/D2<0.113 is satisfied, the air flow line f1 at the exit side of the impeller 1 will fluctuate more as the air flow increases and the circulating flow f2 will eventually obstruct the flow passages between the vane 3. This would result in a sharp drop of the performance.
The hub 2 of the impeller 1 has an outer diameter D3 that is smaller than the outer diameter D2 of the vanes 3. In this structure, an opening 22 is formed in a peripheral portion at the hub side of the vanes 3. When the diagonal diffuser 23 or the diagonal centrifugal diffuser 23 is provided, the discharge resistance of the air flow blown out from the vanes 3 is reduced.
When the exit side height of the vanes 3 of the impeller 1 is represented by B and the outer diameter of the vanes 3 is represented by D2, B/D2≧0.08 is satisfied. This structure eliminates the problem of fluctuation in the air flow line f1 at the exit side of the impeller 1 even if the exit side height B of the vane 3 of the impeller 1 is decreased. Thus, stable performance is obtained.
If B/D2<0.08 is satisfied, the air flow line f1 at the exit side of the impeller 1 will fluctuate greatly and the circulating flow f2 will eventually obstruct the flow passages between the vanes 3. Thus causes a sharp drop in the performance.
It is preferred that the number of the vanes 3 in the impeller 1 be 5 to 15. In this case, in the present invention, as shown in
It is preferred that the number of the vanes 3 in the impeller 1 be 20 to 50. As shown in
It is preferred that the number of the vanes 3 in the impeller 1 be 30 to 72.
As shown in
In an air conditioner including a heat exchanger 15 and a blower X arranged in an air duct 14 formed in a casing 13, the above centrifugal blower may be employed as the blower X. In this structure, the centrifugal blower effectively exhibits its operations and advantages. This greatly contributes to improvement of performance and cost reduction of the air conditioner.
BRIEF DESCRIPTION OF THE DRAWINGS
FIGS. 3(A), 3(B) and 3(C) are cross-sectional views respectively showing main parts of three different modifications of the centrifugal blower X1 of the first embodiment;
FIGS. 8(A) to 8(L) are cross-sectional views respectively showing main parts of modifications of the centrifugal blower X2 of the second embodiment of the present invention;
Several preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.
First Embodiment FIGS. 1 to 6 illustrate a centrifugal blower X1 and an air conditioner Z1 according to a first embodiment of the present invention. As shown in
As shown in
A recess 2a is formed in the central portion of the hub 2 to house the motor 4. A motor fixing portion 7 is used to fix the motor 4. A bearing boss 8 rotatably supports the rotation shaft 4a of the motor 4. A reinforcing ring 9 connects axial distal ends of the vanes 3.
The air intake port 6 of the bellmouth 5 has an inner diameter D0 that is set to be greater than an inner diameter D1 of the vanes 3 of the impeller 1. A circulation space S is formed at the rear side (i.e., the peripheral side) of the bellmouth 5 to ensure that a circulating flow f2 is easily generated in a manner that it flows out of the outlet side of the impeller 1 and is then drawn back into the impeller 1 through the rear side of the air intake port 6 in the bellmouth 5.
The air intake port 6 of the bellmouth 5 may have a straight shape as shown in
In the present embodiment, when the inner diameter of the air intake port 6 of the bellmouth 5 is represented by D0, the inner diameter of the vanes 3 of the impeller 1 is represented by D1, and the outer diameter of the vanes 3 is represented by D2, these dimensions are set to satisfy O<(D0-D1)/(D2-D1)<0.6. There are ten vanes 3.
The operation and advantages of the above centrifugal blower will now be described. In the above structure, circulating flow f2 is generated around the reinforcing rib 9 so as to flow out of the outlet side of the impeller 1 and then be drawn back into the impeller 1 through the rear side of the air intake port 6 in the bellmouth 5. Accordingly, a main air flow f1 passing across the vanes 3 after being drawn into from the air intake port 6 is drawn towards the distal ends of the vanes 3 by the circulating flow f2. This improves the air speed distribution in the exit portions of the vanes 3, enhances the aerodynamic performance, and lowers the operational noise. Moreover, since no shroud is required, the integral molding of the impeller 1 is enabled. This lowers costs and provides high mass productivity.
Further, in the present embodiment, when the inner diameter of the air intake port 6 of the bellmouth 5 is represented by D0, the inner diameter of the vanes 3 of the impeller 1 is represented by D1, and the outer diameter of the vanes 3 is represented by D2, the dimensions are set to satisfy 0<k=(D0-D1)/(D2-D1)<0.6. This lowers the minimum specific noise Ks low as shown in
When 0≧k=(D0-D1)/(D2-D1) is satisfied, as shown in
With D1 representing the inner diameter of the vanes 3, D2 representing the outer diameter of the vanes 3, and D0 representing the inner diameter of the air intake port 6A in the centrifugal blower X1 of this embodiment, a microphone 12 located 45 degrees to the front and one meter away from the intake center Q of the air intake port 6 was used to check changes in the minimum specific noise Ks with respect to a variable k=(D0-D1)/(D2-D1).
In this case, a heat exchanger 15 and the centrifugal blower X1 are arranged in an air duct 14 for air flow W that is formed in a casing 13. The motor fixing portion 7 for fixing the motor 4 is formed integrally with a top plate 13a of the casing 13. This air conditioner Z1 includes an intake grille 16, an air filter 17,.a drain pan 18, and an air outlet port 19.
This structure allows the centrifugal blower X1 to effectively exhibit its advantageous effects. This greatly contributes to enhancement in the performance of the air conditioner Z1 and reduction in costs. Additionally, the. optimum diameter for the air intake port 6 may be set to be greater than that of a conventional one. This suppresses pressure loss in the air filter 17 or the like.
Second Embodiment
In this case, the impeller 1 in the centrifugal blower X2 includes a ring body 20, which has a predetermined width H in the centrifugal direction, in lieu of the reinforcing ring 9 of the first embodiment. In other respects, the structure and effects of the second embodiment are the same as those of the first embodiment. Thus, such parts will not be described.
The ring body 20 may take various shapes as shown in FIGS. 8(A) to 8(L). The following descriptions are only examples, and it is obvious that the ring body 20 may take other shapes that are not shown in the drawings.
As shown in
As shown in
As shown in
As shown in
As shown in
With D2 representing the outer diameter of the vanes 3 and H representing the width of the ring body 20 in the centrifugal direction in the centrifugal blower X2 of this embodiment, a microphone 12 located 45 degrees to the front and one meter away from the intake center Q of the air intake port 6 was used to check changes in the minimum specific noise Ks with respect to a variable ki=H/D2.
It can be seen from the above results that satisfactory operational noise characteristics were obtained in the range 0.05<ki<0.225. The range 0.1<ki<0.15 is more preferable. When ki=H/D≦0.05 is satisfied, the effect will be reduced. When ki=H/D≧0.225 is satisfied, the formation of circulating flow will be adversely affected and weaken the circulating flow at the rear distal portions of the vanes 3. This inhibits enhancement of the aerodynamic performance.
With L representing the distance between the ring body 20 and the bellmouth 5, changes in the minimum specific noise Ks with respect to a variable L/D2 were checked.
The centrifugal blower of the above embodiments is applied when the number of the vanes 3 is small (i.e., 5 to 15 vanes).
Third EmbodimentFIGS. 12 to 16 show a centrifugal blower X3 and an air conditioner Z3 according to a third embodiment of the present invention.
As shown in
As shown in
A recess 2a is formed in the central portion of the hub 2 for housing the motor 4. A motor fixing portion 7 is used to fix the motor 4. A bearing boss 8 rotatably supports the rotation shaft 4a of the motor 4.
Like the second embodiment, the impeller 1 of the third embodiment is provided with a ring body 20 having a predetermined width H in the centrifugal direction. In the third embodiment, the ring body 20 is inclined toward the hub 2 in the centrifugal direction.
A circulation space S is formed at the rear side (i.e., the peripheral side) of the bellmouth 5 to ensure that a circulating flow f2 is easily generated in a manner that it flows out of the outlet side of the impeller 1 and is then drawn back into the impeller 1 through the rear side of the air intake port 6 in the bellmouth 5. Like the first embodiment, the air intake port 6 of the bellmouth 5 may take any of a straight shape, a wedge shape, and a flared shape.
In this embodiment, when the inner diameter of the air intake port 6 of the bellmouth 5 is represented by D0, the inner diameter of the vanes 3 of the impeller 1 is represented by D1, and the outer diameter of the vanes 3 is represented by D2, the dimensions are set to satisfy −0.3<(D0-D1)/(D2-D1)<0.3. The number of the vanes 3 is 40.
The operation and advantages of the above centrifugal blower will now be described.
Circulating flow f2 is generated to flow out of the outlet side of the impeller 1 and then be drawn back into the impeller 1 through the rear side of the air intake port 6 in the bellmouth 5. Accordingly, a main air flow f1 passing across the vanes 3 after being drawn into from the air intake port 6 is drawn towards the distal ends of the vanes 3 by the circulating flow f2. This improves the air speed distribution in the exit portions of the vanes 3, enhances the aerodynamic performance, and lowers the operational noise. Moreover, since no shroud is required, the integral molding of the impeller 1 is enabled. This lowers costs and provides high mass productivity.
In this third embodiment, when the inner diameter of the air intake port 6 of the bellmouth 5 is represented by D0, the inner diameter of the vanes 3 of the impeller 1 is represented by D1, and the outer diameter of the vanes 3 is represented by D2, the dimensions are set such that −0.3<k=(D0-D1)/(D2-D1)<0.3 is satisfied. As shown in
With D1 representing the inner diameter of the vanes 3, D2 representing the outer diameter of the vanes 3, and D0 representing the inner diameter of the air intake port 6 in the centrifugal blower X2 of this embodiment, a microphone 12 located 45 degrees to the front and one meter away from the intake center Q of the air intake port 6 was used to check changes in the minimum specific noise Ks with respect to a variable k=(D0-D1)/(D2-D1).
The relationship between the outer diameter D2 of the vanes 3 and the width H in the centrifugal direction of the ring body 20 in the centrifugal blower X3 is the same as that in the second embodiment. The relationship between the outer diameter D2 of the vanes 3 and the distance L between the ring body 20 and the bellmouth 5 in the centrifugal blower X3 is shown in
When the exit side height B of the vanes 3 in the impeller 1 decreases, fluctuation in the air flow line f, increases at the exit side of the impeller 1. This eventually causes the circulating flow f2 to obstruct the flow passage between the vanes 3. In such a case, the aerodynamic performance falls sharply as shown by the solid line in
Therefore, this embodiment is set to satisfy B/D2≧0.113. This setting solves the problem of fluctuation in the air flow line f1 at the exit side of the impeller 1, and provides stable performance as shown by the double-dotted line in
In the centrifugal blower X3 of the third embodiment, changes in the maximum flow rate coefficient φmax (the coefficient when there is no deterioration is defined as reference value=1) with respect to B/D2 was checked.
Modifications of the centrifugal blower X3 of the third embodiment will be described.
Modification I As shown in
As shown in
As shown in
In the fourth embodiment as well as in the third embodiment, when the exit side height B of the vanes 3 in the impeller 1 decreases, fluctuation in the air flow line f1 increases at the exit side of the impeller 1. This eventually causes the circulating flow f2 to obstruct the flow passage between the vanes 3. In such a case, the aerodynamic performance falls sharply as shown by the solid line in
Therefore, this embodiment is set to satisfy B/D2≧0.08. The reason the upper limit of B/D2 is less than that in the third embodiment is in that the opening 22 is formed in the peripheral portion of the hub-side of the vanes 3. This setting solves the problem of fluctuation in the air flow line f1 at the exit side of the impeller 1, and provides stable performance as shown by the double-dotted line in
In the centrifugal blower X3 of this embodiment, changes in the maximum flow rate coefficient (φmax (the coefficient when there is no deterioration is defined as reference value=1) with respect to B/D2 was checked.
Modifications of the centrifugal blower X4 of the fourth embodiment will now be described.
Modification I As shown in
As shown in
As shown in
As shown in
As shown in
It is obvious that the centrifugal blower X4 of the fourth embodiment may be incorporated in an air conditioner.
Fifth Embodiment
Modifications of the centrifugal blower X5 of the fifth embodiment will now be described.
Modification I As shown in
As shown in
The centrifugal blowers of the third to the fifth embodiments employ a large number of the vanes 3 (i.e., 30 to 50 vanes).
It is obvious that the centrifugal blower X4 of to this embodiment may be incorporated in an air conditioner. It is also obvious that similar effects may be obtained by using a spiral casing.
Modification III The centrifugal blower X5 shown in
In this case, as shown in
In order to check this effect, for example, the centrifugal blower X3 of modification I of the third embodiment shown in
In the conventional shrouded centrifugal blower shown in
Moreover, the air flow deflected toward the hub 2 is further deflected rearward by passing through the diagonal passage in the diagonal centrifugal diffuser 23 and being directly blown out in the centrifugal direction. Thus, the air speed distribution of the ultimately blown out air flow is greatly deflected toward the rear side.
In contrast, the centrifugal blower X3 of the modification I of the third embodiment shown in
In contrast, in the case of the centrifugal blower X5 of the modification III of the fifth embodiment, which has the diagonal centrifugal diffuser 23 of which passage shape changes in the radial direction, the air speed distribution of the air ultimately blown out from the outlet port in the centrifugal direction becomes uniform over the entirety as shown in
As shown in
Each vane 3 of the impeller 1 has an inner diameter end 3a, or front rim, inclined forward in the rotational direction, and a outer diameter end 3b, or rear rim, located rearward from the inner diameter end 3a in the rotational direction M of the impeller 1. Thus, the impeller 1 is of a sweep back vane type (so called turbo fan type) in which a camber line protrudes in the rotational direction.
The number of vanes 3 of the impeller 1 is set to, for example, 20 to 50. A ring body 20 having a predetermined width H in the centrifugal direction is attached to the peripheral portion of the vane ends on the side of a bellmouth. In this embodiment, the end of the ring body 20 and the end of each vane 3 on the side of the bellmouth are inclined toward the hub 2 in the centrifugal direction like in
The centrifugal blower of this embodiment, which has the impeller 1 as described above formed in combination with a bellmouth 5 like those of the above embodiments without a shroud, also has the advantages described below that are similar to those of the above embodiments.
Specifically, the presence of the ring body 20 causes the generation of the circulating flow f2 that flows out from the outlet side of the impeller 1, flows back into the impeller 1, and passes the rear side of the air intake port 6 of the bellmouth 5. Therefore, main air flow f1 passing across the vanes 3 is effectively drawn toward the distal ends of the vanes 3 by the circulating flow f2. As a result, the air speed distribution in the exit portion of the vanes 3 is improved uniformly. This enhances the aerodynamic performance and reduces operational noise.
Moreover, since no shroud is required, the impeller 1 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity.
Seventh Embodiment
Each vane 3 of the impeller 1 has an inner diameter end 3a, or a front rim, inclined forward in the rotational direction and an outer diameter end 3b, or rear rim located rearward from the inner diameter end 3a in the rotational direction M of the impeller 1. Thus, the impeller 1 is of a sweep back vane type (so called turbo fan type) in which a camber line protrudes in the rotational direction.
The number of vanes 3 of the impeller 1 is set, for example, to 20 to 50. A ring body 20 having a predetermined width H in the centrifugal direction is attached to the peripheral portion of the vane ends on the side of a bellmouth. In this embodiment, the end of the ring body 20 and the end of each vane 3 on the side of the bellmouth are inclined toward the hub 2 along the centrifugal direction, like in
The centrifugal blower of this embodiment, which has the impeller 1 as described above formed in combination with a bellmouth 5 like those of the above embodiments without a shroud, also has the advantages described below that are similar to thoseof the above embodiments.
Specifically, the presence of the ring body 20 causes the generation of the circulating flow f2 that flows out from the outlet side of the impeller 1, flows back into the impeller 1, and passes the rear side of the air intake port 6 of the bellmouth 5. Therefore, main air flow f1 passing across the vanes 3 is effectively drawn toward the distal ends of the vanes 3 by the circulating flow f2. As a result, the air speed distribution in the exit portion of the vanes 3 is improved uniformly. This enhances the aerodynamic performance and reduces operational noise.
Moreover, since no shroud is required, the impeller 1 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity.
Eighth Embodiment
Each vane 3 of the impeller 1 has an inner diameter end 3a, or a front rim, inclined forward in the rotational direction, and an outer diameter end 3b, or a rear rim, located rearward from the inner diameter end 3a in the rotational direction M of the impeller 1. Thus, the impeller 1 is of a sweep back vane type (so called turbo fan type) in which a camber line protrudes in the rotational direction.
The number of vanes 3 of the impeller 1 is set to, for, example, a large value from 20 to 50. A ring body 20 having a predetermined width H in the centrifugal direction is attached to the peripheral portion of the vane ends at the side of a bellmouth. In this embodiment, the end of the ring body 20 and the ends of the vanes 3 at the side of the bellmouth are inclined toward the hub 2 along the centrifugal direction like those in
The centrifugal blower of this embodiment, which has the impeller 1 as described above formed in combination with a bellmouth 5 like those of the above embodiments without a shroud, also has the advantages described below that are similar to those of the above embodiments.
Specifically, the presence of the ring body 20 causes the generation of the circulating flow f2 that flows out from the outlet side of the impeller 1, flows back into the impeller 1, and passes the rear side of the air intake port 6 of the bellmouth 5. Therefore, the main air flow f1 passing across the vanes 3 is effectively drawn toward the distal ends of the vanes 3 by the circulating flow f2. As a result, the air speed distribution in the exit portion of the vanes 3 is improved uniformly. This enhances the aerodynamic performance and reduces operational noise. Moreover, since no shroud is required, the impeller 1 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity.
In a centrifugal blower having an impeller as described above employing sweep back vanes having a straight camber line and including outer diameter ends 3b located rearward from inner diameter ends 3a in the rotational direction M of the impeller 1, the maximum static pressure efficiency ratio (reference value of 1.0) and minimum specific noise level ratio (reference value level of ±0) were measured using the number of vanes as parameters. The measurement results obtained are shown in the graph of
The centrifugal blower used for the measurement has an impeller formed as shown
From the measurement results shown in
In contrast, the problems as described above seldom occur when the number of vanes 3 is 20 to 50. Further, the static pressure efficiency ratio is high, and the specific noise level ratio is minimized. Thus, it is apparent that the noise reduction performance is effectively improved while the fan efficiency is increased.
Similar improvements in performance related to the number of vanes can be expected for the above sixth and seventh embodiments and for a twelfth embodiment described later.
Ninth Embodiment
The impeller 1 is of a radial vane type (so called a radial plate fan type) in which each vane 3 has an inner diameter end 3a, or a front rim, that is neither inclined toward the front nor the rear in the rotational direction M and has a straight camber line extending in the radial direction.
The number of vanes 3 of the impeller 1 is set to a large value, for example, 30 to 72, and a ring body 20 having a predetermined width H in the centrifugal direction is arranged on the peripheral portion of the ends of the vanes at the bellmouth side. In this embodiment, the end of the ring body 20 and the ends of the vanes 3 at the side of the bellmouth are inclined toward the hub 2 in the centrifugal direction, like those shown in
The centrifugal blower of this embodiment, which has the impeller 1 as described above formed in combination with a bellmouth 5 like those of the above embodiments without a shroud, also has the advantages described below that are similar to those of the above embodiments.
Specifically, the presence of the ring body 20 causes the generation of the circulating flow f2 that flows out from the outlet side of the impeller 1, flows back into the impeller 1, and passes the rear side of the air intake port 6 of the bellmouth 5. Therefore, main air flow fhd 1 passing across the vanes 3 is effectively drawn toward the distal ends of the vanes 3 by the circulating flow f2. As a result, the air speed distribution in the exit portion of the vanes 3 is improved uniformly. This enhances the aerodynamic performance and reduces operational noise.
Moreover, since no shroud is required, the impeller 1 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity.
Tenth Embodiment
The impeller 1 is of a radial vane type (first modification of the radial plate fan type described above) in which each vane 3 has an inner diameter end 3a, or a front rim, that is neither inclined toward the front nor the rear in the rotational direction M and has a camber line slightly inclined toward the rear in the rotational direction M.
The number of vanes 3 of the impeller 1 is set to a large value of for example, 30 to 72, and a ring body 20 having a predetermined width H in the centrifugal direction is arranged on the peripheral portion of the ends of the vanes at the bellmouth side. In this embodiment, the end of the ring body 20 and the ends of the vanes 3 at the side of the bellmouth are inclined toward the hub 2 in the centrifugal direction like in
The centrifugal blower of this embodiment, which has the impeller 1 as described above formed in combination with a bellmouth 5 like those of the above embodiments without a shroud, also has the advantages described below that are similar to those of the above embodiments.
Specifically, the presence of the ring body 20 causes the generation of the circulating flow f2 that flows out from the outlet side of the impeller 1, flows back into the impeller 1, and passes the rear side of the air intake port 6 of the bellmouth 5. Therefore, main air flow f1 passing across the vanes 3 is effectively drawn toward the distal ends of the vanes 3 by the circulating flow f2. As a result, the air speed distribution in the exit portion of the vanes 3 is improved uniformly. This enhances the aerodynamic performance and reduces operational noise. Moreover, since no shroud is required, the impeller 1 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity.
For the centrifugal blower of the tenth embodiment, the maximum static pressure efficiency ratio (reference value of 1.0) and minimum specific noise level ratio (reference value level of ±0) were measured by using the numbers of the vanes as a parameter. The measurement results obtained are shown in the graph of
The centrifugal blower used for the measurement has an impeller formed as shown
From the measurement results shown in
In contrast, the problems as described above seldom occur when the number of vanes 3 is 30 to 72. Further, the static pressure efficiency ratio is high, and the specific noise level ratio is minimized. Thus, it is apparent that the noise reduction performance is effectively improved while the fan efficiency is increased.
Similar improvements in performance related to the number of vanes can be expected for the ninth embodiment described above and eleventh embodiment described below.
Eleventh Embodiment
The impeller 1 is of a radial vane type (second modification of the radial plate fan type described above) in which each vane 3 has an inner diameter end 3a, or a front rim that is neither inclined toward the front nor the rear in the rotational direction M and a camber line slightly inclined toward the front in the rotational direction M.
The number of vanes 3 of the impeller 1 is set to a large value of, for example, 30 to 72 like in the above embodiments, and a ring body 20 having a predetermined width H in the centrifugal direction is arranged on the peripheral portion of the ends of the vanes at the bellmouth side. In this embodiment, the end of the ring body 20 and the ends of the vanes 3 on the side of the bellmouth are inclined toward the hub 2 in the centrifugal direction like in
The centrifugal blower of this embodiment, which has the impeller 1 as described above formed in combination with a bellmouth 5 like those of the above embodiments without a shroud, also has the advantages described below that are similar to those of the above embodiments.
Specifically, the presence of the ring body 20 causes the generation of the circulating flow f2 that flows out from the outlet side of the impeller 1, flows back into the impeller 1, and passes the rear side of the air intake port 6 of the bellmouth 5. Therefore, the main air flow f1 passing across the vanes 3 is effectively drawn toward the distal ends of the vanes 3 by the circulating flow f2. As a result, the air speed distribution in the exit portion of the vanes 3 is improved uniformly. This enhances the aerodynamic performance and reduces operational noise.
Moreover, since no shroud is required, the impeller 1 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity.
Twelfth Embodiment
As shown in
The impeller 1 is of a radial vane type (radial tip fan type with an outlet angle θ2 of about 90 degrees) in which each vane 3 has a curved camber line recessed in the rotational direction.
The number of the vanes 3 of the impeller 1 is set to, for example, 20 to 50 like in the sixth, seventh, and eighth embodiments, and a ring body 20 having a predetermined width H in the centrifugal direction is arranged on the peripheral portion of the ends of the vanes at the bellmouth side. In this embodiment, the end of the ring body 20 and the ends of the vanes 3 on the side of the bellmouth are inclined toward the hub 2 in the centrifugal direction like in
The centrifugal blower of this embodiment, which has the impeller 1 as described above formed in combination with a bellmouth 5 like those of the above embodiments without a shroud, also has the advantages described below that are similar to those of the above embodiments.
Specifically, the presence of the ring body 20 causes the generation of the circulating flow f2 that flows out from the outlet side of the impeller 1, flows back into the impeller 1, and passes the rear side of the air intake port 6 of the bellmouth 5. Therefore, main air flow f1 passing across the vanes 3 is effectively drawn toward the distal ends of the vanes 3 by the circulating flow f2. As a result, the air speed distribution in the exit portion of the vanes 3 is improved uniformly. This enhances the aerodynamic performance and reduces operational noise.
Moreover, since no shroud is required, the impeller 1 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity.
Thirteenth EmbodimentFIGS. 55 to 58 show the structure of main parts of a centrifugal blower according to a thirteenth embodiment of the present invention.
As shown in FIGS. 55 to 58, this centrifugal blower impeller 1 includes, for example, a disk-shaped hub 2 having central portion to which a rotation shaft 4a of a motor 4 is connected and a plurality of vanes 3 arranged on the peripheral portion of the hub 2 at predetermined intervals in the circumferential direction.
The vanes 3 of this impeller 1 are either forward inclined type vanes 3A (
Regardless of the type, the number of vanes 3 of the impeller 1 is set to a large value of, for example, 30 to 72, and a ring body 20 having a predetermined width H in the centrifugal direction is arranged on the peripheral portion of the ends of the vanes at the bellmouth side. In this embodiment, the end of the ring body 20 and the ends of the vanes 3 on the side of the bellmouth are inclined toward the hub 2 along the centrifugal direction, as viewed from
The centrifugal blower of this embodiment, which has the impeller 1 as described above formed in combination with a bellmouth 5 like those of the above embodiments without a shroud, also has the advantages described below that are similar to those of the above embodiments.
Specifically, the presence of the ring body 20 causes the generation of the circulating flow f2 that flows out from the outlet side of the impeller 1, flows back into the impeller 1, and passes the rear side of the air intake port 6 of the bellmouth 5. Therefore, main air flow f1 passing across the vanes 3 is effectively drawn toward the distal ends of the vanes 3 by the circulating flow f2. As a result, the air speed distribution in the exit portion of the vanes 3 is improved uniformly. This enhances the aerodynamic performance and reduces operational noise. Moreover, since no shroud is required, the impeller 1 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity.
The centrifugal blower has unique advantages as described below in relation to the inner diameter D0 of the air intake port 6 in the bellmouth 5.
(A) When the vanes 3 are forward inclined vanes 3A
In this case, for example, as shown in
Even if the inner diameter D0 of the air intake port 6 of the bellmouth 5 is enlarged as shown by reference numeral 6A in
(B) When the vanes 3 are rearward inclined vanes 3B
In this case, for example, as shown in
As shown in
The vanes 3 of this impeller 1 are either forward inclined type vanes 3A in which only the vane tips 3C are inclined forward at a predetermined angle in the rotational direction M or rearward inclined type vanes 3B inclined opposite the forward inclined type vanes 3A (fold line L).
Regardless of the type, the number of vanes 3 of the impeller 1 is set to a large value of, for example, 30 to 72, and a ring body 20 having a predetermined width H in the centrifugal direction is arranged on the peripheral portion of the ends of the vanes at the bellmouth side. In this embodiment, the end of the ring body 20 and the ends of the vanes 3 on the side of the bellmouth are inclined toward the hub 2 in the centrifugal direction, as viewed from
The centrifugal blower of this embodiment shown in
Specifically, the presence of the ring body 20 causes the generation of the circulating flow f2 that flows out from the outlet side of the impeller 1, flows back into the impeller 1, and passes the rear side of the air intake port 6 of the bellmouth 5. Therefore, the main air flow f1 passing across the vanes 3 is effectively drawn toward the distal ends of the vanes 3 by the circulating flow f2. As a result, the air speed distribution in the exit portion of the vanes 3 is improved uniformly. This enhances the aerodynamic performance and reduces operational noise. Moreover, since no shroud is required, the impeller 1 can be molded integrally. This simplifies the structure, reduces costs, and improves mass productivity.
The centrifugal blower described above has unique advantages as described below in relation to the inner diameter D0 of the air intake port 6 in the bellmouth 5.
(A) When the vanes 3 are forward inclined vanes 3A having vane tips 3C inclined forward in the rotational direction
In this case, for example, as shown in
Even if the inner diameter D0 of the air intake port 6 of the bellmouth 5 is enlarged as shown by reference numeral 6A in
(B) When the vanes 3 are rearward inclined vanes 3B having vane tips 3C inclined rearward in the rotational direction
In this case, for example, as shown in
Even if the inner diameter D0 of the air intake port 6 of the bellmouth 5 is reduced as shown by reference numeral 6B in
Claims
1. A centrifugal blower including an impeller (1) having a hub (2) with a central portion connected to a rotation shaft (4a) of a motor (4), a plurality of vanes (3) arranged on a peripheral portion of the hub (2) at predetermined intervals in a circumferential direction, the vanes provided with front rims (3a) inclined toward the front in a rotational direction, and a bellmouth (5) provided with an air intake port (6) arranged at an air intake side of the impeller, the centrifugal blower being characterized in that:
- a circulating flow (f2) is generated to flow out from an outlet side of the impeller (1), flow back into the impeller (1), and pass through a rear side of the air intake port (6) of the bellmouth (5).
2. A centrifugal blower including an impeller (1) having a hub (2) with a central portion connected to a rotation shaft (4a) of a motor (4), a plurality of vanes (3) arranged on a peripheral portion of the hub (2) at predetermined intervals in a circumferential direction, the vanes provided with front rims (3a) neither inclined toward the front nor the rear in a rotational direction, and a bellmouth (5) provided with an air intake port (6) arranged at an air intake side of the impeller, the centrifugal blower being characterized in that:
- a circulating flow (f2) is generated to flow out from an outlet side of the impeller (1), flow back into the impeller (1), and pass through the rear side of the air intake port (6) of the bellmouth (5).
3. The centrifugal blower according to claim 2, characterized in that the vanes (3) in the impeller (1) are entirely inclined in the rotational direction.
4. The centrifugal blower according to claim 2, characterized in that the vanes (3) in the impeller (1) are entirely inclined opposite the rotational direction.
5. The centrifugal blower according to claim 1 or 2, characterized in that the vanes (3) in the impeller (1) include vane tips inclined in the rotational direction.
6. The centrifugal blower according to claim 1 or 2, characterized in that the vanes (3) in the impeller (1) include vane tips inclined opposite the rotational direction.
7. The centrifugal blower according to claim 1, characterized in that when an inner diameter of the air intake port (6) of the bellmouth (5) is represented by D0, an inner diameter of the vanes (3) in the impellers (1) is represented by D1, and an outer diameter of the vanes (3) is represented by D2, 0<(D0-D1)/(D2-D1)<0.6 is satisfied.
8. The centrifugal blower according to claim 1, characterized in that when an inner diameter of the air intake port (6) of the bellmouth (5) is represented by D0, the inner diameter of the vanes (3) in the impeller (1) is represented by D1, and the outer diameter of the vanes (3) is represented by D2, −0.3<(D0-D1)/(D2-D1)<0.3 is satisfied.
9. The centrifugal blower according to claim 1, characterized in that a ring body (9), (20) having a predetermined width in a centrifugal direction is attached to axial distal ends of the vanes (3) in the impeller (1).
10. The centrifugal blower according to claim 9, characterized in that when a width in the centrifugal direction of the ring body (20) is represented by H, and the outer diameter of the vanes (3) of the impeller (1) is represented by D2, 0.05<ki=H/D2<0.225 is satisfied.
11. The centrifugal blower according to claim 1, characterized in that a diagonal diffuser (23) is arranged at the outlet side of the impeller (1) to guide air that is blown out of the impeller (1) diagonally rearward.
12. The centrifugal blower according to claim 1, characterized in that a diagonal centrifugal diffuser (23) is arranged at the outlet side of the impeller (1) to guide air blown out of the impeller (1) in a centrifugal direction from a diagonal rear side.
13. The centrifugal blower according to claim 1, characterized in that a circulation space (S) is formed at a peripheral side of the air intake port (6) of the bellmouth (5) to allow passage of the circulating flow (f2).
14. The centrifugal blower according to claim 1, characterized in that when an exit side height of the vanes (3) in the impeller (1) is represented by B and an outer diameter of the vanes (3) is represented by D2, B/D2≧0.113 is satisfied.
15. The centrifugal blower according to claim 1, characterized in that the hub (2) of the impeller (1) has an outer diameter D3 that is smaller than the outer diameter D2 of the vanes (3).
16. The centrifugal blower according to claim 15, characterized in that when an exit side height of the vanes (3) of the impeller (1) is represented by B and an outer diameter of the vanes (3) is represented by D2, B/D2≧0.08 is satisfied.
17. The centrifugal blower according to claim 1, characterized in that the number of the vanes (3) in the impeller (1) is 5 to 15.
18. The centrifugal blower according to claim 1, characterized in that the number of the vanes (3) in the impeller (1) is 20 to 50.
19. The centrifugal blower according to claim 2 characterized in the number of the vanes (3) in the impeller (1) is 30 to 72.
20. An air conditioner including a heat exchanger (15) and a blower (X) arrange in an air duct (14) formed in a casing (13), the air conditioner being characterized in that the centrifugal blower according to claim 1 is employed as the blower (X).
Type: Application
Filed: Jul 14, 2005
Publication Date: Nov 1, 2007
Inventor: Kanjirou Kinoshita (Sakai-shi)
Application Number: 11/632,160
International Classification: F28F 9/22 (20060101); F01D 1/02 (20060101);