JPH09222095A - Blower - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a blower to improve fan efficiency and reduce the generation of noise. SOLUTION: When an impeller 11 is started to rotate counterclockwise as shown in Fig, external air is sucked in a casing through the suction port of the casing. The air flows obliquely downward through a central opening 11a. A part of the air flow flows to a base plate 13 as it is and flows in the lower portion of each gap partitioned by a partition plate 15. The air flow flows through a port right below the gap or a portion, opening obliquely, to the surrounding wall of the casing and flows in a peripheral direction along the surrounding wall and flows out to the outside of the casing through a delivery port. A remaining air flow containing an air flow flowing in the gap through a portion where the upper part of the gap is opened is guided upward by the partition plate 15 and guided to the upper portion of the gap partitioned by the partition plate 15. The air flow flows out to the outside of the casing through a delivery port through a similar route described above.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improved blower.

[0002]

2. Description of the Related Art Conventionally, a circular base plate,
An impeller having an annular top plate arranged coaxially with the base plate and parallel to the base plate, and a large number of radially oriented blade plates arranged between the base plate and the top plate. Blowers provided are known.

[0003]

In the conventional blower having the above structure, however, the fan efficiency is low and the noise is high due to the structure of the impeller and the characteristics of the centrifugal fan. There was a point.

Therefore, an object of the present invention is to provide a blower having high fan efficiency and low noise.

[0005]

A blower according to the present invention comprises:
A rotatable circular substrate, a plurality of blade plates fixed to the substrate along the circumferential direction of the substrate, and a gap formed by each blade plate into a gap close to the substrate and a gap separated from the substrate. A partition plate is provided from the inner peripheral side end of each blade to the outer peripheral side for partitioning. By rotating, the air is taken into the space on the inner peripheral side of each blade from the tip side, and the air is sent out to the outer peripheral side of each blade through the gap.

According to this structure, the gap formed by each vane plate by the partition plate disposed from the inner peripheral side end of each vane plate to the outer peripheral side is divided into a gap close to the substrate and a gap separated from the substrate. It is divided into Therefore, the difference between the air inflow speed into the gap on the side close to the substrate and the air inflow speed to the gap on the side distant from the substrate is smaller than that of the conventional blower. As a result, in the blower according to the present invention, the separation of the airflow in the gap on the side separated from the substrate is suppressed, and the fan efficiency is improved and the noise is reduced as compared with the conventional blower.

In the blower according to the preferred embodiment of the present invention, the partition plate is provided parallel to the substrate. In the blower according to the modified example of this embodiment, the partition plate is provided with a slope so that the inner peripheral side end is closer to the substrate than the outer peripheral side end.

Therefore, according to the blower according to the present modification, the air flow flowing into each of the gaps is separated not only from the gap close to the substrate but also from the substrate into which the air flow hardly flows in the conventional blower. Since the partition plate can guide the gap to the side more efficiently, it is possible to increase the air volume.

In the partition plate described above, in order to reduce the resistance to the inflowing air flow, the thickness of the inner peripheral side end portion can be made as thin as possible. The partition plate may be provided in a plurality of stages from the substrate side of each gap to the tip side. In that case, the inflowing air flow is divided in a state of being evenly distributed by the gaps of the respective stages formed by these partition plates.

The partition plates are preferably arranged at equal intervals.

In a blower according to another modification of the above-mentioned embodiment, a partition plate configured to partition only the inner peripheral portion of each gap is used.

It is also possible to provide an annular plate which covers each gap on the tip side of each vane plate facing the substrate.

Each of the gaps farthest from the substrate may be opened on the tip side.

The tip end side of each blade is provided with a reinforcing member for covering only the portion not overlapping the installation position of the partition plate, and a ring member for fixing each blade from the outer peripheral side end thereof. It may be that.

Each of the gaps near the substrate can be opened on the rear end side. For each blade, a flat plate-shaped one or an arcuately curved one is used.

In the blower having the above construction, since the upper, lower, and side portions of each vane are open, each of the above portions can be integrally molded with resin by using a mold.

[0017]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described in detail below with reference to the drawings.

FIG. 1 is a sectional view showing a side shape of a blower according to an embodiment of the present invention, and FIG. 2 is a sectional view showing a shape of the blower as seen from the line AA 'in FIG.

As shown in the drawing, this blower comprises a casing 7, an impeller 6, and a motor 8.

The casing 7 has a side surface having a shape as shown in FIG. 1 and a cross section taken along the line AA 'in FIG. 1 having a scroll shape as shown in FIG. A mouth 7a, a discharge port 7b, and a tongue portion 7c are provided.

The suction port 7a is provided in a substantially central portion of one of the two surfaces (upper surface in FIG. 1) which are in a mutually facing relationship, and the discharge port 7b is provided in the casing 7 main body as shown in FIG. It is formed so as to extend in the tangential direction of the outer peripheral portion. Further, the tongue portion 7c is provided at the connecting portion between the discharge port 7b and the casing 7 main body.

The impeller 6 is manufactured by integrally molding a resin and is housed in a casing 7.
Base plate 1, partition plate 2, top plate 3
And a vane plate 4, and a central opening 6a corresponding to the suction port 7a as shown in FIGS.

The base plate 1 has a disk shape, and is provided at a portion of the casing 7 near the lower surface shown in FIG. 1 so as to be axially supported by the output shaft of the motor 8. As shown in FIG. 2, a plurality of blade plates 4 are arranged on the upper surface of the base plate 1 shown in FIG. 1 at predetermined intervals in the circumferential direction. The partition plate 2 and the top plate 3 are both annular plates having the same size. The partition plate 2 is attached to each vane plate 4 parallel to the base plate 1 and concentrically with the base plate 1 at a position apart from the base plate 1 by an upward distance α in FIG. 1. Similarly, the top plate 3 also has blades so that it is parallel to the partition plate 2 and the base plate 1 at a position separated by a distance α from the partition plate 2 in the upward direction and is concentric with the base plate 1 and the partition plate 2. It is attached to the plate 4.

That is, the base plate 1, the partition plate 2,
With each vane plate 4, a plurality of inter-blade flow paths 5 are radially formed in which the inner peripheral side opening is relatively narrower than the outer peripheral side opening. Similarly, the partition plate 2, the top plate 3, and the vane plates 4 provide a plurality of blades having the same shape and the same size as the inter-blade passages 5 above the plurality of inter-blade passages 5. The inter-channels 5 are radially formed (see FIG. 2 for both). Therefore, the impeller 6 has two layers of inter-blade passages 5 in the vertical direction of FIG.

The motor 8 is fixed to a substantially central portion of the bottom surface of the casing 7 shown in FIG. 1, and the output shaft of the motor 8 is
As described above, it penetrates the bottom surface to support the base plate 1 and reaches the inside of the casing 7.

Next, the operation of the blower having the above structure will be described with reference to FIGS. 1 and 2.

When the impeller 6 starts to rotate counterclockwise in FIG. 2 by starting the motor 8, the air outside the casing 7 is sucked into the casing 7 through the suction port 7a.
The air sucked into the casing 7 flows into each inter-blade passage 5 through the central opening 6a. The air that has flowed into the inter-blade passages 5 passes through the inter-blade passages 5 in the radial outward direction, and is rotated from the rotating vane plates 4 as shown by arrows in FIG. It receives a force in the direction, is accelerated in the circumferential direction, and is given a centrifugal force.

The air that has passed through the blade-to-blade flow paths 5 in this manner is ejected radially outward from the outer edges of the blade-to-blade flow paths 5,
It flows in the circumferential direction (counterclockwise) along the surrounding wall of the casing 7 and flows out of the casing 7 through the discharge port 7b.

In the blower according to the present embodiment, the impeller 6 has the partition plate 2 to form the upper and lower two-layer blade-to-blade passages 5 in the height direction (vertical direction in FIG. 1).

Therefore, the air inflow velocity v1 of the lower inter-blade passage 5 near the base plate 1, the air inflow velocity v2 of the upper inter-blade passage 5 near the partition plate 2, and the partition plate of the lower inter-blade passage 5 2 Air inflow velocity v3 closer to 2 and upper inter-blade passage 5
Between the air inflow velocity v4 near the top plate and the air inflow velocity v1 to the region near the base plate 1 and the air inflow to the separated region in the inter-blade passage of the blower having no partition plate 2. It can be small compared to the difference with the speed v4. As a result, in the blower according to the present embodiment, since the separation of the air flow in the region β separated from the base plate 1, that is, the upper inter-blade passage 5 is suppressed, the fan efficiency is improved as compared with the conventional blower. It can be improved and noise can be reduced.

Since the partition plate 2 is arranged so that the distance between the base plate 1 and the partition plate 2 and the distance between the top plate 3 and the partition plate 2 are both α, the impeller 6
When the resin is integrally molded, the number of types of slide cores used for forming the inter-blade passage 5 can be one, and the cost of the mold can be reduced.

[Measurement of Noise of Blower] Noise was measured using the blower according to the present embodiment and the blower other than the present embodiment.

In this noise measurement, the blower according to the present embodiment has a height (= height of a space for accommodating the impeller) having a planar shape of a logarithmic spiral with a divergence angle of 4.5 °.
A scroll casing of mm is provided, and any one of the following structures as an impeller is selectively used. An impeller in which three inter-blade flow passages are vertically divided into four by arranging three partition plates having an outer diameter x inner diameter x plate thickness of 100 mm x 58 mm x 0.5 mm between the base plate and the top plate at equal intervals. 7 partitions between the base plate and the top plate
An impeller in which the inter-blade passages are divided into 8 parts by arranging them at equal intervals.

On the other hand, in this noise measurement, the blower other than this embodiment does not have a partition plate provided between the scroll casing and the base plate and the top plate, and does not divide the inter-blade flow passage into upper and lower parts. It is configured with and.

However, the base plate of each of these impellers has a diameter × plate thickness of 100 mm × 2 mm, and the top plate has an outer diameter × inner diameter × plate thickness of 100 mm × 58 mm ×
2 mm, blade plate pitch × plate thickness 3 ° × 0.5 mm
Are set respectively. The height of the impeller including the base plate and the top plate is set to 44 mm.

FIG. 3 is a schematic diagram showing an apparatus used for measuring the air volume of the blower described above.

The above-mentioned device is called a double chamber type air flow measuring device (manufactured by Rika Seiki, model F-401), which is provided with a rectifying grid and a plurality of orifices in the chamber, and a static pressure hole on the outer wall of the chamber. And a damper for adjusting the air volume and an auxiliary fan are attached.
As shown in FIG. 3, this device is provided with an impeller 6, a scroll type casing 7 and a motor 8, and is installed on the discharge side of a blower body having a suction nozzle installed on the suction side to measure the air volume. went. That is, in the above device,
By controlling the static pressure at the fan outlet with an air volume adjusting damper and an auxiliary fan, and rectifying the air flow discharged from the fan with a rectifying grid, the air volume of the fan discharge air is measured with an orifice mounted according to the AMCA standard, The static pressure at the fan outlet was measured through a static pressure hole arranged near the fan outlet.

FIG. 4 is a schematic diagram showing an apparatus used for measuring the specific noise of the blower described above.

As shown in FIG. 4, the above-mentioned apparatus comprises a static pressure adjusting box having a structure in which a sound absorbing material is lined, a damper for adjusting the air volume is provided inside, and static pressure holes are provided on the outer wall, and a motor for a blower. 8 and a soundproof box lined with a sound absorbing material. The static pressure adjustment box is set to have the same size and shape as the air volume measuring device described above.

In the above apparatus, as shown in FIG. 4, the static pressure adjusting box is provided on the discharge side of the blower main body having the suction nozzle installed on the suction side, and the motor 8 is housed in the soundproof box. Cut off the noise. And
While controlling the static pressure at the fan outlet with a damper for adjusting the air flow, the static pressure at the fan outlet was measured through static pressure holes, and the noise at a predetermined static pressure at the fan outlet was measured. The noise measurement was performed at a point 1 m upstream from the upper surface of the impeller 6 on the axial center line of the fan in an anechoic chamber, and the noise level of the A characteristic was measured.

Further, the impeller 6 was rotated at 500 rpm, and the air volume was variously changed by the air volume adjusting damper, and the air volume of the fan discharge air, the static pressure at the fan outlet, and the noise were measured. The specific noise ks was calculated based on the following equation from the measured values of the air volume of the fan discharge air, the static pressure at the fan outlet, and the noise.

[Equation 1]

Based on the measurement results thus obtained, the relationship between the specific noise ks and the air volume was obtained. The relationship between the specific noise ks and the air volume is calculated by measuring the air volume and static pressure,
The static pressure at the fan outlet is Q1 and P1, respectively, and the specific noise obtained by noise measurement and the static pressure at the fan outlet are ks, respectively.
If the air volume Q and the specific noise Ks are 1 and P1,
It was calculated assuming that the relation that the specific noise becomes Ks1 is established when the air volume is Q1. Since the size and shape of the air flow measuring device used to measure air flow and static pressure (see Fig. 3) and the static pressure adjustment box used to measure noise (see Fig. 4) are almost the same, it is considered that the above relationship holds. .

FIG. 5 shows the relationship between the fan specific noise Ks obtained by the above noise measurement and the flow coefficient φ of the impeller 6 given by the following equation.

[Equation 2]

From FIG. 5, in the impeller 6, when the partition plate 2 is disposed between the base plate 1 and the top plate 3 so that the partition plate 2 is not disposed between the base plate 1 and the top plate 3. It can be seen that the specific noise Ks decreases as compared with the above, and that the specific noise Ks decreases when the number of partition plates 2 provided increases.

[Measurement of Hydrodynamic Characteristic of Impeller Single Unit] The impeller 6 was taken out from the casing 7 and the hydrodynamic characteristic of the impeller 6 alone was measured.

As shown in FIG. 6, the impeller 6 is housed in a double chamber type air flow rate measuring device (manufactured by Rika Seiki, model F-401) having the same structure as in FIG. 3, and the impeller 6 is driven to rotate. 8 was placed on a stand installed outside the air flow measuring device. Then, the bell mouth was installed facing the impeller 6 to the air volume measuring device.

In the above apparatus, the air flow discharged from the impeller 6 was rectified by the rectifying grid while controlling the static pressure in the vicinity of the impeller 6 with the air volume adjusting damper and the auxiliary fan. The impeller 6 is rotated at 3240 rpm by the motor 8, the air volume of the discharge air of the impeller 6 is measured by the above-mentioned orifice mounted according to the AMCA standard, and the static pressure in the vicinity of the impeller 6 is determined by the static pressure in the vicinity of the impeller 6. It was measured with a hole.

From the respective measured values of the flow rate of the discharge air of the impeller 6 and the static pressure at the outlet of the impeller 6, the total pressure efficiency η of the impeller 6 alone was calculated based on the following equation.

(Equation 3)

FIG. 7 shows the relationship between the total pressure effect η of the impeller 6 alone obtained by the above measurement and the flow coefficient φ of the impeller 6.

From FIG. 7, by providing the partition plate 2 between the base plate 1 and the top plate 3, the total pressure is higher than that when the partition plate 2 is not provided between the base plate 1 and the top plate 3. It can be seen that the maximum value of the efficiency η increases and that the maximum value of the total pressure efficiency η increases as the number of the partition plates 2 arranged increases.

Further, the maximum value of the total pressure efficiency η is equal to the total pressure efficiency obtained when the impeller 6 is arranged in the scroll casing 7 of the optimum shape, but the impeller 6 is naturally the scroll of the optimum shape. It is arranged in the casing 7. Therefore, as shown in FIG. 7, the total pressure efficiency η of the blower increases when the partition plate 2 is arranged between the base plate 1 and the top plate 3, and the partition plate 2 is arranged. It can be seen that the total pressure efficiency η of the blower increases as the number of sheets increases.

As described above, according to one embodiment of the present invention, the impeller has a plurality of annular plates and has a plurality of blade-to-blade passages in the height direction of the impeller. The difference between the air inflow velocity into the region of the inter-blade flow passage close to the disc and the air inflow velocity into the region of the inter-blade flow passage separated from the disc is smaller than that of the conventional blower. As a result, in the blower according to the embodiment of the present invention, the separation of the airflow in the area separated from the disc of the inter-blade passage is suppressed, and compared with the conventional blower,
Fan efficiency is improved and noise is reduced. Further, by disposing the disc and the plurality of annular plates at equal intervals, it is possible to set the type of the slide core to 1 when the impeller is integrally molded with resin, and The cost can be reduced.

By the way, conventionally, in the technical field of blowers, various proposals (for example, the proposal disclosed in Japanese Patent Laid-Open No. 63-80096) have been made in order to improve the blowing efficiency.

In reality, however, in any of the proposals, the air flow flowing from above the impeller toward the impeller, which is a drawback peculiar to the centrifugal fan, is located in the gap between the impellers near the base plate. That is, it was not possible to improve the phenomenon that only the downward flow occurred and the upward flow did not occur. Therefore, it is difficult not only to reduce the power consumption but also to increase the blown air volume, but also to reduce the noise. Further, for example, in the impeller having the structure described in Japanese Patent Laid-Open No. 63-80096, there is a problem that integral molding with resin cannot be performed.

Therefore, in view of the above, the present inventors have developed an impeller having the structure described below.

FIG. 8 is a plan view showing an impeller which constitutes a blower according to another embodiment of the present invention, and FIG. 9 is a sectional view taken along the line BB 'of the impeller of FIG.

This impeller 11 is also manufactured by integrally molding a resin similarly to the impeller 6 shown in FIGS. 1 and 2, and includes a base plate 13, a partition plate 15, and a plurality of impeller plates. 17, an upper outer ring 19 and a lower outer ring 21, and a central opening 11a as shown in FIGS. 8 and 9.

As shown in FIG. 8, the base plate 13 has a disk shape when viewed from above, and, as shown in FIG. 9, a base whose cross-sectional shape rises in the center and in the vicinity thereof. It has a shape. Base plate 1
A boss 13a for inserting an output shaft of a motor (not shown) is formed in the central portion of 3.

Each blade 17 is curved in an arc shape as shown in FIG. Each vane plate 17 has an impeller in the bending direction so that the airflow can be guided along the rotation direction of the impeller 11 (= the counterclockwise direction in FIG. 8 in the present embodiment) with as little resistance as possible. The base plates 13 are arranged at substantially equal intervals along the outer edge of the circumferentially formed base plate 13 in a state of being aligned with the rotation direction of the base plate 11.

The upper outer ring 19 and the lower outer ring 21 are provided to reinforce the attachment strength of each vane plate 17 to the base plate 13. The upper outer ring 19 is an outer peripheral end of each vane plate 17. , And the lower outer ring 21 is attached to the lower end portion of the outer peripheral end of each vane plate 17, respectively.

The partition plates 15 are defined by the respective blade plates 17 in order to guide a part of the air flow coming in from the direction of the central opening 11a by the rotation of the impeller 11 toward the upper outer ring 19 direction. It is provided in a plurality of gaps curved in the rotational direction of 11. The partition plate 15 is an annular plate formed with a gradient (taper) so that the inner peripheral edge portion and the outer peripheral edge portion have different heights, and the radial width thereof is: It is set so as to substantially correspond to the radial length of each blade 17. In this embodiment, the partition plate 15
Is provided at an intermediate position in the vertical direction of each vane plate 17 such that the inner peripheral side is low (that is, the outer peripheral side is high) and is concentric with the base plate 13. In addition, the partition plate 15 is the base plate 13
Partition plate 1 regardless of whether it is provided in parallel with
It is desirable that the thickness of the inner peripheral side end portion of 5 is as thin as possible compared to other portions.

Next, the operation of the blower having the above structure will be described with reference to FIGS. 8 and 9.

When the impeller 11 starts rotating in the counterclockwise direction in FIG. 8 due to the activation of the motor (not shown), external air passes through the suction port (not shown) of the casing and enters the casing (not shown). Be sucked. This air flows diagonally downward through the central opening 11a. At this time, a part of the airflow directly flows toward the base plate 13 and flows into the lower portion of each gap partitioned by the partition plate 15. Then, from there, it reaches an enclosure wall (not shown) directly below or obliquely below each gap, flows circumferentially along the enclosure wall, and flows out of the casing from a discharge port (not shown). On the other hand, the remaining airflow including the airflow flowing from the open portion at the top of each gap toward each gap is guided upward by the partition plate 15 and above each gap partitioned by the partition plate 15. Guided to the site. Then, from there, it flows out of the casing through a discharge port (not shown) through the same route as described above.

As described above, according to another embodiment of the present invention, the upper and lower portions of each gap are open, and the partition plate 15 is provided with a slope so that the inner peripheral side is low and the outer peripheral side is high. Will be provided. Therefore, the central opening 11
The partition plate 15 can guide a part of the air flow that flows obliquely downward from above the impeller 11 through a together with the air flow that flows from the upper part of each gap to the upper part of each gap. Further, the airflow that has flowed into the lower portion of each gap can flow out to the casing through the opening just below them and the side opening. Therefore, since the air flow also flows into the upper part of each gap where the air flow does not flow in the conventional blower, the air flow rate is 10%.
It can be increased to some extent.

Further, the central opening 1 is formed by the partition plate 15.
Since the airflow flowing in from 1a can be distributed substantially evenly to the upper part and the lower part of each gap, each vane plate 1
It is possible to reduce the noise by increasing the pressure evenly in all parts of No. 7. Further, the partition plate 15 can further reinforce the attachment strength of each vane plate 17 to the base plate 13.

Further, since the upper, lower, and side portions of each vane plate are open as described above, it has become possible to integrally mold the impeller 11 with resin using a mold.

FIG. 11 is a sectional view of an impeller constituting a blower according to a modification of another embodiment of the present invention.

The impeller 21 according to the present modification includes the blade plates 1
Partition plate 16 having a length of approximately 1/2 of the radial length of 7
Is provided on the inner peripheral side of each blade 17 and each blade 1
A structural feature is that a reinforcing rib 23 having a length that is approximately ½ of the radial length of 7 is provided on the upper portion on the outer peripheral side of each blade 17. Other configurations, for example, that the partition plate 16 is provided with a slope such that the inner peripheral side is low and becomes higher toward the outer peripheral side, are similar to the impeller 11 shown in FIGS. 8 and 9. .

Also in this modification, the same effects as those listed in the above embodiment can be obtained.

Needless to say, the contents described above relate to each embodiment of the present invention, and the present invention is not limited to the contents described above.

[0071]

As described above, according to the present invention,
A blower with high fan efficiency and low noise can be provided.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a blower according to an embodiment of the present invention.

FIG. 2 is a cross-sectional view taken along the line AA ′ of FIG.

FIG. 3 is a schematic diagram of an air volume measuring device of a blower.

FIG. 4 is a schematic diagram of a specific noise measuring device of a blower.

FIG. 5 is a correlation diagram between the specific noise of the blower and the flow coefficient.

FIG. 6 is a schematic diagram of an impeller total pressure efficiency measuring device.

FIG. 7 is a correlation diagram between the total pressure efficiency and the flow coefficient of a single impeller.

FIG. 8 is a sectional view of a blower according to another embodiment of the present invention.

9 is a sectional view taken along the line BB ′ of FIG.

10 is an enlarged cross-sectional view taken along the line CC ′ of FIG.

FIG. 11 is a cross-sectional view of a blower according to a modified example of another embodiment of the present invention.

[Explanation of symbols]

 1, 13 Base plate 2, 15 Partition plate 3 Top plate 4 Blade plate 5 Blade ring flow path 6, 11 Impeller 7 Casing 8 Motor 17 Blade plate 19 Upper outer ring 21 Lower outer ring

[Procedure amendment]

[Submission date] February 27, 1997

[Procedure amendment 1]

[Document name to be amended] Drawing

[Correction target item name] All figures

[Correction method] Change

[Correction contents]

FIG.

[Fig. 2]

[Figure 3]

FIG. 4

FIG. 6

FIG. 10

[Figure 5]

FIG. 7

[Figure 8]

[Figure 9]

FIG. 11

Continued front page (72) Noboru Nihara No. 1-1 Nakajima, Kokurakita-ku, Kitakyushu, Fukuoka Prefecture Totoki Equipment Co., Ltd. (72) Yoshinori Nakamura No. 1-2 Nakajima, Kitakyushu, Kitakyushu, Fukuoka No. 1 Totoki Equipment Co., Ltd. (72) Inventor Makoto Hatakeyama 2-1-1 Nakajima, Kokurakita-ku, Kitakyushu City, Fukuoka Prefecture (72) Inventor Takeshi Uemura Nakajima Kokurakita-ku, Kitakyushu City, Fukuoka Prefecture 2-1, 1-1 Totoki Equipment Co., Ltd.

Claims (15)

[Claims] 1. A rotatable circular substrate, a plurality of blade plates fixed to the substrate along the circumferential direction of the substrate, and a gap formed by each of the blade plates, which is close to the substrate. A partition plate disposed from the inner peripheral side end of each vane plate to the outer peripheral side for partitioning into a gap and a gap separated from the substrate, and by rotating, the inner peripheral side of each vane plate The blower is characterized in that air is taken into the space from the front end side and the air is sent out to the outer peripheral side of each vane plate through the gap. 2. The blower according to claim 1, wherein the partition plate is provided in parallel with the substrate. 3. The blower according to claim 1, wherein the partition plate is provided with a slope so that the inner peripheral side end portion is closer to the substrate than the outer peripheral side end portion. 4. The blower according to any one of claims 1 to 3, wherein the partition plate is formed so that the inner peripheral end portion has a wall thickness as thin as possible. 5. The blower according to claim 1, wherein the partition plates are provided in a plurality of stages from the substrate side of the gap to the tip side. 6. The blower according to claim 1, wherein the partition plates are arranged at equal intervals. 7. The blower according to any one of claims 1 to 6, wherein the partition plate is configured to partition only a portion of each of the gaps near the inner circumference. 8. The blower according to claim 1, wherein an annular plate that covers each of the gaps is provided on a tip end side of each of the vane plates facing the substrate. A blower characterized by that. 9. The blower according to claim 1, wherein each of the gaps farthest from the substrate is open at a tip side. 10. The blower according to claim 7, wherein a reinforcing member is provided on a tip end side of each vane plate to cover only a portion that does not overlap the installation position of the partition plate. 11. The blower according to claim 1, further comprising a ring member for fixing each of the vane plates from an outer peripheral side end portion thereof. 12. The blower according to claim 1, wherein each of the gaps near the substrate is open at a rear end side. 13. The blower according to claim 1, wherein each of the vanes has a flat plate shape. 14. The blower according to claim 1, wherein each of the vanes is curved in an arc shape. 15. The blower according to claim 1, wherein the respective parts are integrally molded of a resin material.