JPH06272690A - Vaned multilayer disc fan and design method therefor - Google Patents

Abstract

PURPOSE:To provide a design method for a vaned multilayer disc fan allowing the systematic determination of such dimensions as ensuring the highest static sound performance under a given condition, regarding an impeller, a drive means and a casing. CONSTITUTION:Regarding a design method for vaned multilayer disc fan having an impeller with a plurality of annular plates stacked on top of each other via a gap, and a plurality of vanes fixed to an annular plate laid between adjacent annular plates, a drive means for driving the impeller to rotate, and a scroll casing for housing the impeller, the dimensions of the impeller, drive means and the casing are determined, so that a discharge coefficient for a fan and the dimensionless discharge opening area of the casing can satisfy the predetermined relationship.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bladed multi-layer disk fan.

[0002]

2. Description of the Related Art An impeller having a plurality of annular plates laminated at intervals and a plurality of blades arranged between adjacent annular plates and fixed to the annular plate, and an impeller rotatingly driven. A multi-layer disk fan with blades including a drive means for driving and a scroll-type casing for storing an impeller has a quietness which is an advantage of the multi-layer disk fan, and has a small air volume which is a disadvantage of the multi-layer disk fan. As a silent fan that overcomes this difficulty by making the wings installed between the adjacent annular plates work.
He is a fan expected to have a wide range of applications. The effect of the specifications of the impeller, driving means, and casing of the bladeless multi-layer disk fan on the efficiency of the fan has been reported by Fukutomi et al.
No. 125-130).

[0003]

[Problems to be solved by the invention]
It relates to the effect of the specifications of the impeller, drive means and casing of a bladeless multilayer disc fan on the efficiency of the fan, and the specifications of the impeller, drive means and casing of the bladed multilayer disc fan are the noise of the fan. No research report has been published on the effect on performance. For this reason, conventionally, when designing a bladed multilayer disc fan, the specifications of the impeller, the drive means, and the casing that provide the best silent performance under given conditions have been determined by trial and error. As a result of earnest research, the inventor of the present invention has found that there is a certain correlation among the specifications of the impeller, the driving means, the casing of the bladed multilayer disc fan and the silent performance of the fan. It was The present invention has been made on the basis of such findings, and under the given conditions, the specifications of the impeller, the driving means, and the casing that give the most excellent silent performance are determined based on the certain correlation. It is an object of the present invention to provide a method of designing a multi-layered disk fan with blades that systematically determines.

[0004]

According to the present invention, there are provided a plurality of annular plates which are laminated at a distance from each other and a plurality of blades which are arranged between the adjacent annular plates and are fixed to the annular plates. In a method for designing a multi-layer disk fan with blades, which comprises an impeller, a driving means for rotating the impeller, and a scroll-shaped casing for storing the impeller, a flow coefficient of the fan and a dimensionless discharge port area of the casing. To determine the specifications of the impeller, the drive means, and the casing so that and satisfy a predetermined relationship. In a preferred embodiment of the present invention, the dimensionless discharge port area σ of the casing is
If it is less than 0.15, the fan flow coefficient Φ and σ are
= {0.391 σ + 0.006} ± 0.010 so that the fan flow coefficient Φ is Φ = 0.065 ± 0.010 when the dimensionless discharge port area σ of the casing is 0.15 or more. A method is provided for determining the specifications of the impeller and casing. Further, in the present invention, an impeller having a plurality of annular plates stacked with a space between each other and a plurality of blades arranged between the adjacent annular plates and fixed to the annular plate,
In a method for designing a multi-layer disk fan with blades, comprising a driving means for rotationally driving an impeller and a scroll-shaped casing for storing the impeller, in the case where the dimensionless discharge port area σ of the casing is less than 0.15, When the dimensionless discharge area σ of the casing is 0.15 or more, the fan flow coefficient Φ is such that the fan flow coefficient Φ and σ satisfy the relationship of Φ = {0.391 σ + 0.006} ± 0.010. , Φ = 0.065 ± 0.01
A method is provided which comprises determining the specifications of the impeller, the drive means and the casing so that they are zero, and then determining the blade geometry and mounting conditions. Further, according to the present invention, an impeller having a plurality of annular plates laminated at a distance from each other and a plurality of blades arranged between the adjacent annular plates and fixed to the annular plate, and the impeller are rotated. It comprises a driving means for driving and a scroll type casing for accommodating the impeller, the casing has a dimensionless discharge outlet area σ of less than 0.15, and the fan flow coefficient Φ and σ are Φ = {0.391 σ + 0.
Provided is a multilayer disk fan with blades, which satisfies the relationship of 006} ± 0.010. Further, according to the present invention, an impeller having a plurality of annular plates laminated at a distance from each other and a plurality of blades arranged between the adjacent annular plates and fixed to the annular plate, and the impeller are rotated. It is equipped with a driving means for driving and a scroll type casing for storing the impeller, and the dimensionless discharge outlet area σ of the casing is 0.15 or more, and the flow coefficient Φ of the fan is Φ = 0.065 ± 0.010. A characteristic multi-layer disk fan with blades is provided.

[0005]

When the flow coefficient of the fan and the dimensionless discharge port area of the casing satisfy a predetermined relationship, the specific noise of the fan becomes the lowest. Therefore, by determining the specifications of the impeller, the drive means, and the casing so that the flow coefficient of the fan and the dimensionless discharge port area of the casing satisfy a predetermined relationship, the best performance is obtained under the given conditions. It is possible to systematically determine the specifications of the impeller, the drive means, and the casing of the multi-layer disk fan with blades that provide silent performance, without repeating trial and error. When the casing dimensionless discharge outlet area σ is less than 0.15, the fan flow coefficient Φ and σ
And Φ = {0.391 σ + 0.006} ± 0.010, the fan flow coefficient Φ is Φ = 0.065 ± 0.0 when the casing dimensionless discharge outlet area σ is 0.15 or more.
By determining the specifications of the impeller, the driving means, and the casing so that the value becomes 010, it is possible to optimize the silent performance of the bladed multilayer disc fan under given conditions. When the dimensionless discharge port area σ of the casing is less than 0.15, the flow rate coefficients Φ and σ of the fan are Φ = {0.391 σ + 0.
006} ± 0.010, the impeller and the driving means are adjusted so that the flow coefficient Φ of the fan becomes Φ = 0.065 ± 0.010 when the dimensionless discharge outlet area σ of the casing is 0.15 or more. By determining the specifications of the casing and casing, and then determining the shape of the blade and the mounting conditions, the specific noise of the multi-layer disk fan with blade is 10 dB higher than that of the sirocco fan.
It can be reduced to some extent.

[0006]

EXAMPLES Examples of the present invention will be described below. Experiments were conducted to measure the air flow rate, the static pressure at the fan outlet, and the fan noise value of the multi-layer disk fan with blades. 1. Experimental conditions (1) Experimental device Experimental device for measuring air volume and static pressure Fig. 1 shows the experimental device. A suction nozzle is installed on the suction side of a fan body that includes an impeller 1, a scroll-shaped casing 2 that houses the impeller 1, and a motor 3, and a double-chamber type air flow measuring device (manufactured by Rika Seiki, model F-401) was installed. The air flow measuring device was provided with a flow rate adjusting damper and an auxiliary fan to control the static pressure at the fan outlet. The air flow discharged from the fan was rectified by a rectifying grid. The flow rate of the fan discharge air was measured by an orifice attached according to the AMCA standard, and the static pressure at the fan outlet was measured by a static pressure hole arranged near the fan outlet.

Experimental apparatus for noise measurement The experimental apparatus is shown in FIG. A suction nozzle was installed on the suction side of the fan body, and a static pressure adjustment box of the same size and shape as the air volume measuring device was provided on the discharge side of the fan body. In the static pressure adjustment box,
Lined with sound absorbing material. The static pressure adjusting box was equipped with a damper for adjusting the flow rate to control the static pressure at the fan outlet. The static pressure at the fan outlet was measured through a static pressure hole arranged near the fan outlet, and the noise at a predetermined static pressure at the fan outlet was measured. The noise of the motor was shut off by storing the motor in a soundproof box lined with sound absorbing material. The noise measurement was performed at a point 1 m upstream from the upper surface of the impeller on the axial center line of the fan in the anechoic chamber, and the noise level of the A characteristic was measured.

(2) Sample Impeller, Sample Casing Sample Impeller The sample impeller 1 has a large number of annular plates each having an outer diameter (diameter) of 100 mm and an inner diameter (diameter) of 58 mm, and blades are provided between adjacent annular plates. It was constructed by inserting and fixing with an adhesive. As the blades, a rearward-facing blade in which a USA35B airfoil is conformally mapped to a cylindrical blade row and a radial blade having a symmetrical cross-sectional shape with an appropriate roundness at the blade tip are adopted. Nine types of impellers 1 having different blade shapes, attachment states, the number of disks, etc. were tested. The specifications of the sample impeller 1 are shown in Table 1 and FIG.

[Table 1] In this embodiment, the impeller was manufactured by inserting the blades between the adjacent circular plates and fixing them with an adhesive, but a laminated body composed of the circular plates and the blades may be integrally molded at once. The one-step annular plate and the one-step blade may be integrally formed and then laminated and bonded and fixed to each other, or the blades may be inserted between adjacent annular plates and the rings and blades may be connected and fixed using bolts. You may.

Sample casing The height of the casing 2 was fixed at 27 mm. The spreading shape of the casing 2 is a logarithmic spiral shape given by the following equation, and the spreading angle θ _c is 2.39 °, 3.76 °, 4.50.
There are 3 types of °. r = r ₂ · exp (θtan θ _c ) r: radius of the casing side wall measured from the center of the impeller 1 r ₂ : outer diameter (radius) of the impeller 1 θ: angle from the reference line 0 ≦ θ ≦ 360 ° θ _c : divergence angle The degree of exposure e of the impeller 1, that is, the amount of radial projection of the impeller 1 from the inner side wall of the casing 2 corresponds to each divergence angle θ _c , and the outer diameter (diameter) of the impeller 1 is 1. 2%, 10.0%,
Three kinds of 30.0% were used. The sample casing 2 is shown in FIG. Rotational speed of the impeller 1 The rotational speeds of the impeller 1 are 4000 rpm and 7000 rpm.
There are two types.

2. Experiment, data processing (1) Experiment Experiment 1 Nine types of impellers 1 (0A01 to 0A09) shown in Table 1
And the spread angle θ _c (2.39 of the two types of casing 2).
°, 4.50 °) and the exposure degree e of one type of impeller 1
(1.2%) and the number of rotations of the two types of impellers 1 (4000
rpm, 7000 rpm) and the flow rate of the fan discharge air, the static pressure at the fan outlet, and the noise were measured. Experiment 2 0A04 (backward wing) selected in consideration of the result of Experiment 1
And 0A05 (radial blades), two types of impellers 1 and three types of casings 2 spread angles θ _c (2.39 °, 3.76).
°, 4.50 °) and the degree of exposure e of the three types of impellers 1
(1.2%, 10.0%, 30.0%) and the number of rotations of the two types of impellers 1 (4000 rpm, 7000 rpm) for each combination, the flow rate of the fan discharge air and the static of the fan outlet. The pressure and noise were measured.

(2) Data processing From the measured values of the flow rate of the fan discharge air, the static pressure at the fan outlet, and the noise, the flow coefficient Φ and the specific noise k _s based on the following equations.
Was calculated. Φ = Q / (πr ₂ Bu ₂ ) Q: Flow rate of fan discharge air m ³ / s r ₂ : Outer diameter (radius) of impeller 1 m B: Height of impeller 1 m u ₂ : Ring plate the outer peripheral speed _{m / s k s = SPL (} a) -10log 10 Q (P t) 2 SPL (a): noise level dB Q of a-: fan discharge air flow rate m ³ / s P _t: the fan exit all Pressure mmAq

3. Experimental Results (1) Experimental Results 1 The relationship between the flow coefficient Φ and the specific noise k _s obtained by the experiment 1 is shown in FIGS. The relationship between the flow rate coefficient Φ and the specific noise k _s shown in FIGS. 5 to 8 is that the flow rate coefficient and the static pressure at the fan outlet obtained by air volume / static pressure measurement are Φ ₁ and p ₁ , respectively, and noise measurement When the specific noise and the static pressure at the fan outlet obtained by the above are k _s1 and p ₁ , respectively, the flow coefficient Φ
Between the specific noise k _s and the specific noise k _s , it is determined that the relationship that the specific noise is k _s1 is established when the coefficient of flow rate is Φ ₁ . Since the air volume measuring device used for air volume / static pressure measurement and the static pressure adjustment box used for noise measurement have almost the same size and shape, the above relationship is considered to be established.

Consideration 1 From FIG. 5 and FIG. 6 showing the experimental results when the spread angle θ _c of the casing 2 is 2.39 ° and the exposure degree e of the impeller 1 is 1.2%, FIG. Regardless of the shape or the rotational speed of the impeller 1, the flow coefficient Φ is 0.
It can be seen that the specific noise k _s is almost the lowest when it is in the region of 035 ± 0.010. That is, it is understood that the silent performance of the fan can be optimized by determining the specifications of the fan so that the flow coefficient Φ becomes 0.035 ± 0.010. Consideration 2 From FIGS. 7 and 8 showing the experimental results when the spread angle θ _c of the casing 2 is 4.50 ° and the exposure degree e of the impeller 1 is 1.2%, the shape of the impeller 1 is determined. Irrespective of the rotation speed of the impeller 1, the flow coefficient Φ is 0.
It can be seen that the specific noise k _s is almost the lowest when it is in the region of 065 ± 0.010. That is, it is understood that the silent performance of the fan can be optimized by determining the specifications of the fan so that the flow coefficient Φ becomes 0.065 ± 0.010.

(2) Experimental Result 2 The relationship between the flow coefficient Φ and the specific noise k _s obtained in Experiment 2 is shown in FIGS. 9 to 17. Flow coefficient Φ shown in FIGS.
The relationship between the specific noise k _s and the specific noise k _s is obtained in the same manner as in the experimental result 1. Consideration 1 From FIGS. 9 to 17, regardless of the shape of the impeller 1,
Further, it can be seen that the specific noise k _s is almost the lowest when the flow coefficient Φ is in a certain specific region, regardless of the rotation speed of the impeller 1. Further, it can be seen that the specific region of the flow coefficient Φ is different for each combination of the spread angle of the casing 2 and the exposure degree e of the impeller 1. Table 2 shows the relationship between each combination of the spread angle of the casing 2 and the exposure degree e of the impeller 1 and the specific region of the flow coefficient Φ. Table 2 also shows the fan outlet area S corresponding to the combination of the divergence angle of the casing 2 and the exposure degree e of the impeller 1, and the fan dimensionless outlet area σ given by the following equation. . σ = S / (2πr ₂ B) S: Area of outlet of fan m ² r ₂ : Outer diameter (radius) of impeller 1 m B: Height of impeller 1 m

[Table 2]

Consideration 2 FIG. 18 shows the relationship between the specific region of the flow coefficient Φ described in Consideration 1 and the dimensionless discharge port area σ of the fan. From FIG.
Regardless of the shape of the impeller 1 or the rotational speed of the impeller 1, when the dimensionless discharge outlet area σ of the casing 2 is less than 0.15, the fan flow coefficient Φ is Φ =
When it is in the range of {0.391 σ + 0.006} ± 0.010, the specific noise k _s becomes almost the minimum, and when the dimensionless discharge port area σ of the casing 2 is 0.15 or more, the fan flow coefficient Φ is
It can be seen that the specific noise k _s is almost the lowest in the range of 0.065 ± 0.010. From the above, regardless of the shape of the impeller 1 or the rotation speed of the impeller 1, when the dimensionless discharge outlet area σ of the casing 2 is less than 0.15, the fan flow coefficient Φ Is Φ = {0.391 σ + 0.00
6} ± 0.010 By determining the specifications of the fan so that the dimensionless discharge port area σ of the casing 2 is 0.15 or more, the fan flow coefficient Φ is 0.065.
It can be seen that the noise reduction performance of the fan can be optimized by determining the specifications of the fan so that the range is ± 0.010.

Consideration 3 The specific noise of the sirocco fan, which is widely used for blowers, is 40.
~ 45dB ("Fluid Machine"<< Morishita Publishing >>
279). From FIGS. 9 to 17, the specific noise of the multi-layer disk fan with blades is compared with the specific noise of the sirocco fan by performing the optimization described in the consideration and further optimizing the shape of the blades and the mounting conditions. It can be seen that it can be reduced by about 10 dB.

The measurement experiments and the results of the air flow rate of the multi-layer disk fan with blades, the static pressure at the fan outlet, and the fan noise value have been described above. From the above measurement experiment, the following was clarified. The specific noise of the fan is lowest when the flow coefficient Φ of the fan and the dimensionless discharge port area σ of the casing 2 satisfy a predetermined relationship. Therefore, by determining the specifications of the fan so that the flow coefficient Φ of the fan and the dimensionless discharge port area σ of the casing 2 satisfy a predetermined relationship, the best silent performance can be obtained under the given conditions. The bladed multi-layer disk fan can be systematically designed without repeating trial and error. When the dimensionless discharge outlet area σ of the casing 2 is less than 0.15, the fan flow coefficient Φ and σ are Φ = {0.391
When the dimensionless discharge port area σ of the casing 2 is 0.15 or more so that the relationship of σ + 0.006} ± 0.010 is satisfied, the flow coefficient Φ of the fan becomes Φ = 0.065 ± 0.010. By determining the specifications, the silent performance of the fan can be optimized. By further optimizing the blade shape and mounting conditions, the specific noise of the multi-layer disk fan with blades can be reduced by about 10 dB with respect to the specific noise of the sirocco fan.

[0018]

As described above, in the present invention, the specifications of the impeller, the driving means, and the casing are determined so that the flow coefficient of the fan and the dimensionless discharge port area of the casing satisfy a predetermined relationship. It is possible to systematically determine the specifications of the impeller, the driving means, and the casing of the bladed multilayer disk fan that gives the best silent performance under given conditions, without repeating trial and error. In the present invention, the dimensionless discharge port area σ of the casing is 0.
When less than 15, the fan flow coefficient Φ and σ are Φ =
To satisfy the relationship of {0.391 σ + 0.006} ± 0.010,
When the dimensionless discharge port area σ of the casing is 0.15 or more, the specifications of the impeller, the driving means, and the casing are determined so that the flow coefficient Φ of the fan is Φ = 0.065 ± 0.010. It is possible to optimize the silent performance of the bladed multilayer disc fan under the specified conditions. When the dimensionless discharge outlet area σ of the casing is less than 0.15, the dimensionless discharge of the casing is adjusted so that the flow coefficient Φ and σ of the fan satisfy the relationship of Φ = {0.391 σ + 0.006} ± 0.010. Exit area σ
Is 0.15 or more, the fan flow coefficient Φ is Φ = 0.
The specific noise is reduced by about 10 dB from the specific noise of the sirocco fan by determining the specifications of the impeller, the driving means, and the casing so as to be 065 ± 0.010, and then determining the shape of the blade and the mounting conditions. be able to.

[Brief description of drawings]

FIG. 1 is a diagram showing an outline of an experimental device for measuring air volume and static pressure.

FIG. 2 is a diagram showing an outline of a noise measuring experimental device.

FIG. 3 is a diagram showing a configuration of a sample impeller. 3a is 0
Fig. 3 is a plan view of the A-04 impeller, Fig. 3b is a plan view of the 0A-05 impeller, and Fig. 3c is a schematic side view of the impeller.

FIG. 4 is a plan view of a sample casing.

FIG. 5: Flow coefficient Φ and specific noise k _s obtained in Experiment 1
It is a figure which shows the relationship with.

FIG. 6 is a flow coefficient Φ and specific noise k _s obtained in Experiment 1.
It is a figure which shows the relationship with.

FIG. 7: Flow coefficient Φ and specific noise k _s obtained in Experiment 1
It is a figure which shows the relationship with.

FIG. 8: Flow coefficient Φ and specific noise k _s obtained in Experiment 1
It is a figure which shows the relationship with.

FIG. 9: Flow coefficient Φ and specific noise k _s obtained in Experiment 2
It is a figure which shows the relationship with.

FIG. 10: Flow coefficient Φ and specific noise k obtained in Experiment 2
It is a figure which shows the relationship with _s .

FIG. 11: Flow coefficient Φ and specific noise k obtained in Experiment 2
It is a figure which shows the relationship with _s .

FIG. 12: Flow coefficient Φ and specific noise k obtained in Experiment 2
It is a figure which shows the relationship with _s .

FIG. 13: Flow coefficient Φ and specific noise k obtained in Experiment 2
It is a figure which shows the relationship with _s .

FIG. 14: Flow coefficient Φ and specific noise k obtained in Experiment 2
It is a figure which shows the relationship with _s .

FIG. 15: Flow coefficient Φ and specific noise k obtained in Experiment 2
It is a figure which shows the relationship with _s .

FIG. 16: Flow coefficient Φ and specific noise k obtained in Experiment 2
It is a figure which shows the relationship with _s .

FIG. 17: Flow coefficient Φ and specific noise k obtained in Experiment 2
It is a figure which shows the relationship with _s .

FIG. 18 is a region of the flow coefficient Φ that minimizes the specific noise k _s and the dimensionless discharge port area σ of the fan obtained in Experiment 2;
It is a figure which shows the relationship with.

[Explanation of symbols]

 1 Impeller 2 Scroll type casing 3 Motor

Claims (9)

[Claims] 1. An impeller having a plurality of annular plates laminated at a distance from each other and a plurality of blades fixed between the annular plates, the impeller being rotationally driven. In the method for designing a multi-layer disk fan with blades, comprising:
A method of determining the specifications of an impeller, a drive unit, and a casing so that a flow coefficient of a fan and a dimensionless discharge port area of a casing satisfy a predetermined relationship. 2. The dimensionless discharge port area σ of the casing is 0.
When less than 15, the fan flow coefficient Φ and σ are Φ =
To satisfy the relationship of {0.391 σ + 0.006} ± 0.010,
When the dimensionless discharge outlet area σ of the casing is 0.15 or more, the specifications of the impeller, the driving means, and the casing are determined so that the flow coefficient Φ of the fan is Φ = 0.065 ± 0.010. The method according to claim 1. 3. A method according to claim 1 or 2, characterized in that the blades arranged between adjacent annular plates are rearward-facing blades. 4. The method according to claim 1, wherein the blades arranged between the adjacent annular plates are radial blades. 5. An impeller having a plurality of annular plates laminated at a distance from each other and a plurality of blades fixed between the annular plates, the impeller being rotationally driven. In the method for designing a multi-layer disk fan with blades, comprising:
When the dimensionless discharge port area σ of the casing is less than 0.15, the flow rate coefficients Φ and σ of the fan are Φ = {0.391 σ + 0.
006} ± 0.010, the impeller and the driving means are adjusted so that the flow coefficient Φ of the fan becomes Φ = 0.065 ± 0.010 when the dimensionless discharge outlet area σ of the casing is 0.15 or more. And the specifications of the casing, and then determine the shape of the blade and the mounting conditions. 6. An impeller having a plurality of annular plates laminated at a distance from each other and a plurality of blades arranged between the adjacent annular plates and fixed to the annular plate, and the impeller is rotationally driven. And a scroll-type casing for storing the impeller, and the casing has a dimensionless discharge outlet area σ of 0.15.
And the fan flow coefficient Φ and σ are Φ = {0.39
A multi-layer disk fan with blades, which satisfies the relationship of 1 σ + 0.006} ± 0.010. 7. An impeller having a plurality of annular plates laminated at a distance from each other and a plurality of blades arranged between adjacent annular plates and fixed to the annular plate, and the impeller is rotationally driven. And a scroll-type casing for storing the impeller, and the casing has a dimensionless discharge outlet area σ of 0.15.
Above, the flow coefficient Φ of the fan is Φ = 0.065 ± 0.01
A multi-layer disk fan with blades, which is characterized by being 0. 8. The multi-layer disk fan with blades according to claim 6, wherein the blades disposed between the adjacent annular plates are rearward facing blades. 9. The multi-layer disk fan with blades according to claim 6, wherein the blades arranged between the adjacent annular plates are radial blades.