JP3074828B2 - Swirl pump - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a swirl type gas pump such as a swirl type blower or a swirl type liquid pump such as a wesco pump.

[0002]

2. Description of the Related Art This type of vortex pump generally has an impeller having a large number of blades arranged in an annular flow path, and a suction port and a discharge port communicating with the annular flow path, respectively. There is a partition partitioning the space between the discharge port and the suction port with respect to the passage of the blade through a minute gap. By rotating an impeller arranged in the annular flow path, gas or liquid (hereinafter, gas and liquid are collectively referred to as fluid) introduced from the suction port is swirled in the annular flow path. The pressure is swirled and discharged from the discharge port.

[0003] Since this is relatively easy to handle due to its structure, it is used in various fields. However, this structure has a specific problem. That is, the impeller rotates continuously, and the fluid sucked from the suction port is swirled and pressurized in the annular flow path, and is conveyed to the discharge port by the action of the partition. At this time, some fluid is left between the blades of the impeller and
It will be carried . A part of the fluid carried to the suction port side is hereinafter referred to as a carryover flow. The carry-over flow passes through the partition wall and is carried to the suction side, during which the swirling is suppressed. Then, the pressurized carryover flow is opened on the entire blade width on the suction side, and expands almost uniformly in the flow passage. Therefore,
This reduces the amount of fluid sucked in and reduces the effective carrier fluid volume, and thus its properties remain low.

Japanese Patent Laid-Open Publication No. 51-91308 discloses this type of technology.

[0005]

As described above, the high-pressure and large-circulation fluid on the discharge port side flows out of the discharge port. According to the analysis of the present inventors, this carryover flow is an effective transport fluid amount. It has been found that not only does this decrease, but also has the following disadvantageous effects. That is,
When this high-pressure carryover flow is opened on the suction port side, it is opened over the entire blade width at this position, and expands almost uniformly in the flow path without turning. Then, the expansion flow mixes with the fluid flowing from the suction port without changing the wetting length, and causes turbulence in the fluid flowing from the suction port. The fluid flowing from the outside through the suction port due to this turbulence cannot form a swirl flow in the flow path near the suction port, and forms an effective swirl flow only after passing through the mixing region. According to measurements by the inventors' experiments, this mixing region reached a circumferential angle of about 40 degrees from the suction port to the discharge port side. Therefore, in the conventional vortex pump, the angle corresponding to the mixing area, that is, about 4
At 0 degree, since the swirling flow cannot be formed and the pressure cannot be increased, the pressure is low, and it has become clear that this has further adversely affected the characteristic improvement. Further, it has been clarified that the disturbance adversely affects the generation of noise. It is a well-known fact that turbulence of a fluid causes performance degradation in hydraulic and aerodynamics.

The present invention has been made in view of the above points, and an object of the present invention is to provide a vortex pump capable of improving performance.

Another object of the present invention is to provide a vortex pump capable of forming a swirling flow more effectively in the entire flow path.

It is still another object of the present invention to provide a vortex pump capable of forming a swirling flow more smoothly from the vicinity of the suction port.

Still another object of the present invention is to provide a vortex pump capable of utilizing a carryover more effectively.

Still another object of the present invention is to provide a vortex pump capable of reducing the loss of fluid inflow.

[0011]

In order to achieve the above object, a feature of the present invention is to guide a fluid flowing from a suction port in a direction of forming a swirling flow in a flow path. The auxiliary flow supply path for supplying the auxiliary flow is provided.

In this case, the auxiliary flow may be supplied from the outside, but it is advantageous to use a carryover flow.

[0013] The supply angle of the auxiliary flow is forward with respect to the traveling direction of the impeller with respect to the plane forming the minute gap with the impeller of the partition wall, and more specifically, is in the range of 5 to 35 degrees. desirable.

In the present invention, when the carryover flow is used as the auxiliary flow, a communication passage is provided on the suction port side of the partition wall for guiding the carryover flow so as to be discharged obliquely forward with respect to the traveling direction of the blade. It is characterized by the following.

Further, the partition wall is provided with a flow path guide for efficiently guiding the flow guided from the suction port into the annular flow path. The fluid left between the blades is carried to the suction port side with the discharge port closed by the flow path guide. The communication passage may be provided separately from the partition, but is preferably provided in the flow path guide of the partition.

In forming the flow path guide portion on the partition wall, the flow path guide portion may be cut out in a hole shape or may be cut out from the side.

In any case, in forming a communication passage for guiding the carryover in a direction obliquely forward with respect to the traveling direction of the impeller in the flow path guide portion of the partition wall, the position and the position of the impeller Of particular importance is the angle of the front surface with respect to the direction of travel.

That is, in the communication path on the outer peripheral side, it is desirable that the opening position on the side facing the blade is closer to the outer peripheral side than the position corresponding to the blade in the radial direction. More preferably, in the radial direction, it is desirable to be located outside the central portion with respect to the width W of the blade. More preferably, in the radial direction of the blade, (1) with respect to the central portion of the blade.
/ 6) × W 2 , or (1/6) × W or more on the outer peripheral side. In the circumferential direction, the opening position on the side of the communication passage facing the blade is such that, with respect to the traveling direction of the impeller, the rear end is based on the front end of the flow path guide portion of the partition wall, and is the distance between the blade and the blade. About 1.5 to 2.5 times is good. Furthermore, the angle of the surface located forward with respect to the traveling direction of the impeller, which is important for ejecting the carryover flow, is in the traveling direction of the impeller with respect to the surface forming the minute gap with the impeller of the partition. On the other hand, the range of 5 degrees to 35 degrees is good.

In the communication path on the inner peripheral side, it is desirable that the opening position on the side facing the blade is closer to the inner peripheral side than the position corresponding to the blade in the radial direction. More desirably, in the radial direction, it is desirable to be more inward than the center with respect to the width W of the blade, and more desirably, in the radial direction of the blade, (1/1 /
6) × W 2 , or (1/6) × W or more on the inner circumferential side. In the circumferential direction, the opening position on the side of the communication passage facing the blade is such that, with respect to the traveling direction of the impeller, the rear end is based on the front end of the flow path guide portion of the partition wall, and is the distance between the blade and the blade. About 1.5 to 2.5 times is good. Furthermore, the angle of the surface located forward with respect to the traveling direction of the impeller, which is important for ejecting the carryover flow, is in the traveling direction of the impeller with respect to the surface forming the minute gap with the impeller of the partition. On the other hand, the range of 5 degrees to 35 degrees is good.

[0020]

As described above, if an auxiliary flow that guides the fluid flowing from the suction port in the direction of forming the swirling flow in the flow path is supplied to the fluid, the turbulence tends to occur near the suction port. The fluid is dragged by the auxiliary flow in a state where the wetting length is increased and is guided in the swirling direction. Therefore, a swirling flow is formed earlier in the flow path. Therefore, the entire flow path can be used more effectively, and the fluid in the flow path is swirled and pressurized by more blades, so that the pressure can be increased and the performance can be improved.

Further, since the turbulence of the fluid on the suction port side can be further reduced by the auxiliary flow,
Noise can be reduced.

Further, in the case where the carryover flow is used as the auxiliary flow, the carryover flow forming the turbulence can be effectively applied to the swirl, whereby the performance can be further improved.

[0023]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention shown in the drawings will be described below.

The first embodiment shows a case where the present invention is applied to a kind of a vortex type gas pump, that is, the outer peripheral side of a cup type vortex blower. FIG.
FIG. 2 is a cross-sectional view of the vicinity of a suction port and FIG. 2 is a view illustrating FIG. 1 by cutting along a line 2-2. FIG. 3 is a perspective view showing the entire configuration of the embodiment, and a quarter thereof is cut away.
FIG. 4 is a cut-away side view showing the overall configuration, and FIG. 5 is a perspective view of the impeller. FIG. 6 is a front view showing a state where the side cover and the impeller have been removed.

In these figures, 1 is an impeller, 2 is a casing forming an annular flow path 8. Annular channel 8
The cross-section opening in a direction parallel to the axis of the rotating shaft 3 forms a substantially semicircular groove. The annular flow path 8 is formed in an annular shape around the rotation shaft 3 of the motor 4. One end of the annular flow path 8 communicates with the suction port 6a, and the other end communicates with the discharge port 6b. From outlet 6b to inlet 6
The space "a" is partitioned off by a partition wall 10 which opposes the impeller 1 via a minute gap. The suction-side passage 6a 'connected to the suction port 6a and the discharge-side passage connected to the discharge port 6b are provided so as to be parallel in the silencer 7 also serving as a base member. The prime mover 4 is fixed on a silencer 7 also serving as a base member, and the casing 2 is fixed to the prime mover 4.

The impeller 1 has a shroud 9 as shown in FIG.
And a number of blades 5. The shroud 9 has an annular groove 11 that opens in the axial direction facing the annular flow path 8 about the rotation shaft 3. Groove 11
Many are provided in the direction across.

By fixing the impeller 1 to the rotating shaft 3 of the prime mover 4, the opening of the upper annular flow path 8 and the opening of the shroud 9 are opposed to each other. Is formed.

When the motor 4 is driven to rotate, the impeller 1 fixed to the rotating shaft 3 rotates. Then,
As shown in FIGS. 7 and 8, the gas sucked from the suction port 6 a is actuated by the blades 5 of the impeller 1, and
It rotates while drawing a spiral as shown by an arrow in an annular flow path 12 having a circular cross section constituted by the blades and the shroud 9, is pressurized by the blades 5, and is gradually conveyed in the rotation direction F. Then, the pressurized gas is guided to the discharge port 6b by the action of the partition 10, and is discharged therefrom.

FIG. 1 is a sectional view of a main part showing the relationship among the partition 10, the suction and discharge ports 6a and 6b, and the impeller 1. As shown in this figure, a suction-side flow path guide 10a that guides the gas flowing from the suction port 6a to the annular flow path 12 smoothly is provided at the tip of the partition 10 facing the impeller 1. And a discharge-side flow guide 10b for smoothly guiding the discharged gas to the discharge port 6b. As is apparent from this figure, the gas pressurized by the impeller 1 is guided to the discharge port 6b by the action of the partition 10, as shown by the arrow OUT. However, the outlet of the gas 13 left between the blade 5 and the adjacent blade 5 at the time of discharge is closed by the partition wall 10, carried to the suction port 6 a side as it is, and carried over to the suction side. This is called a carryover flow, and the carryover flow is carried to the suction side after passing through the partition wall 10 after the number of turns is reduced. Then, the pressurized fluid is opened over the entire width of the blade 5 on the suction side and expands in the annular flow path 12 almost uniformly without having a swirl. Then, the expanded flow mixes with the gas indicated by the arrow IN flowing from the suction port 6a and disturbs the flow of the flowing gas. Due to this turbulence, gas flowing from outside through the suction port 6a cannot start to form a swirling flow smoothly in the flow path near the suction port 6a, and becomes effective only after passing through the mixing region. A swirling flow will be formed. According to the measurement by the inventor's experiment, as shown in FIG. 8, the mixing area reached a circumferential angle of about 40 degrees from the suction port 6a to the discharge port 6b.

Therefore, according to the present embodiment, as shown in FIG. 1, on the outer peripheral side of the suction-side flow path guide portion 10a of the partition wall 10,
A communication path is provided from the side facing the blade to the suction port. This constitutes an auxiliary flow supply path. By this communication passage 14, the gas 13 left between the blades 5 passes through the communication passage 14 before inflating near the tip of the suction-side flow path guide 10 a, and flows toward the suction port 6 a by an arrow 15.
Spout as shown by. The communication path 14 is provided at an angle α obliquely forward with respect to the traveling direction of the blade 5 in consideration of the fact that the gas ejected from the communication path 14 smoothly turns in the annular flow path 12. What is particularly important here is a surface 14a located forward of the direction of movement of the blades 5 of the communication path 14, and the angle of this surface 14a is α. In the case of the embodiment, the angle of the rear surface 14b is also matched with this,
The radial position of the communication path 14 with respect to the impeller 1 is
As shown in FIG. 2, the blades 5 are arranged on the outer peripheral side. This is because the gas is advantageously compressed outward by the centrifugal force by the blades 5 and a swirling flow is formed.

According to the present embodiment, since the communication path 14 is provided on the outer peripheral portion of the suction-side flow path guide portion 10a of the partition 10, the compressed gas 13 left between the blades 5 by the partition 10 is formed. The carryover flow on the outer peripheral side of the impeller 1 flows out from the communication passage 14 to form a jet 15. This jet 1
5 flows to the inner peripheral side of the casing 2 along the inner wall of the casing 2 and further flows to the inner peripheral side of the impeller 1 to form a swirling flow. At this time, the gas around the jet 15 is dragged by the jet 15 and guided in the turning direction. On the other hand, partition 1
The compressed gas 13 left between the blades 5 by the
Since the gas flows out from the outer peripheral side by the action of the communication passage 14, the gas is vacated on the inner peripheral side between the blades 5, and in the vicinity of the suction port 6a immediately after passing through the suction-side flow path guide portion 10a of the partition wall 10, from the outside. The gas that has flowed into the impeller 1 easily. Therefore, the swirl flow 16 is smoothly generated in the vicinity of the suction port 6a immediately after passing through the suction-side flow path guide 10a due to the generation of the swirl flow by the jet flow 15 and the ease of sucking the gas into the inner peripheral side of the impeller 1. Formed and at the same time the wetting length increases. Accordingly, in the vicinity of the suction port 6a, the mixing area from the suction port 6a to the discharge port 6b is reduced and the wetting length is increased as compared with the related art, so that the vortex blower has the circumferential angle and the wetting length. The effect of the pressure increase will be increased by a corresponding amount. Thus, the vortex blower can increase its discharge pressure and improve performance. Further, due to the generation of the swirling flow 16 by the jet 15 and the ease of sucking the gas into the inner peripheral side of the impeller 1, the swirling flow is smoothly generated in the vicinity of the suction port 6a immediately after passing through the suction-side flow path guide 10a. As a result, the turbulence of the gas in this region is reduced, and accordingly, the generation of noise can be suppressed, and the effect of noise reduction can be obtained.

According to observations made by the inventor through experiments,
It has been confirmed that an angle α of the communication passage 14 with respect to the traveling direction of the blade 5 in the range of 5 degrees to 35 degrees is favorable for forming a swirling flow. Incidentally, in the embodiment, the angle α is set to 20 degrees. In addition, although the diameter of the communication passage 14 is the size in the radial direction, in the embodiment, the width W of the blade 5 is 1/1/3.
It has a width of 3. However, this is an arrangement for obtaining a larger effect, and may be over the entire width of the blade 5, but is preferably on the outer peripheral side. If more effect is desired, the width W of the blade 5 is preferably from the center to the outside, and more preferably (外側) × W or more outside from the center. Further, with respect to the circumferential position of the communication path 14, the point B at the rear end position in the traveling direction of the blade 5 is set at 1.1 of the distance between the blade 5 and the blade 5 from the point A at the tip end of the discharge side flow path guide portion 10b. The range of 5 to 2.5 times was good. However, the opening position of the communication passage 14 on the side facing the impeller 1 is not particularly limited to this position, and it is sufficient that the compressed gas remaining between the blades 5 can be introduced. The opening may be formed on the side flow path guide 10a side, or may be formed so as to straddle both the suction side and the discharge side flow path guides 10a and 10b.

FIG . 9 is a characteristic diagram showing the air volume / static pressure characteristics of the vortex blower employing the present embodiment and the conventional one. Curve A is an aerodynamic characteristic diagram provided with a communication passage according to the present embodiment, and curve B.
FIG. 3 is an aerodynamic characteristic diagram of a conventional one, that is, one having no communication passage. The motor used was 0.75 (KW), the effective diameter of the impeller was 235 (mm), and the rotation speed of the motor was 342.
0 (RPM), the gap between the impeller and the partition is 0.3 (m
m), the case where the angle of the communication passage is 20 degrees is shown. As is clear from this figure, the aerodynamic characteristics of the embodiment can be improved by about 20% as compared with the conventional one.

The second embodiment shows a case in which the present invention is applied to a kind of vortex type gas pump, that is, the inner peripheral side of a cup type vortex blower. FIG. 11 is a sectional view of FIG.
It is a figure cut | disconnected and shown along a -11 line. FIG. 3 is a perspective view showing the entire configuration of the embodiment, and a quarter thereof is cut away. FIG. 5 is a perspective view of the impeller. FIG. 12 is a front view showing a state where the side cover and the impeller have been removed.

The parts configuration, operation principle, and problems in the conventional structure are the same as those in the first embodiment.

According to the present embodiment, as shown in FIG.
A communication passage 1 that communicates with the inner peripheral side of the suction-side flow path guide portion 10a of the partition wall 10 from the surface facing the blade 5 to the suction port 6a side.
4 is provided. This constitutes an auxiliary flow supply path. This communication passage 14 allows the gas 1 remaining between the blades 5
3, before expanding near the tip of the suction-side flow path guide 10 a, blows out through the communication path 14 toward the suction port 6 a as indicated by an arrow 15. The communication passage 14 takes into account that the gas ejected from the communication passage 14 smoothly turns in the annular flow path 12,
The blade 5 is provided at an angle α obliquely forward with respect to the traveling direction. What is particularly important here is a surface 14a located forward of the direction of movement of the blades 5 of the communication path 14, and the angle of this surface 14a is α. The radial position of the communication passage 14 with respect to the impeller 1 is arranged on the inner peripheral side of the blade 5 as shown in FIG . This is to prevent the gas from being compressed outward by the blades 5 due to the centrifugal force and the swirling to be started from the outer peripheral side, while the swirling on the inner peripheral side is delayed.

As described above, according to the present embodiment, since the communication path 14 is provided in the inner peripheral portion of the suction-side flow path guide 10a of the partition 10, the compressed gas left between the blades 5 by the partition 10 is formed. Among 13, the carry-over flow on the inner peripheral side of the impeller 1 flows out from the communication passage 14 to form a jet 15. The jet flow 15 flows along the inner wall of the casing 2 to the inner peripheral side of the casing 2 and further flows to the inner peripheral side of the impeller 1 to form a swirling flow. At this time, the gas around the jet 15 is dragged by the jet 15 and guided in the turning direction. On the other hand, the compressed gas 13 left between the blades 5 by the partition 10
Flows out of the communication passage 14 and is decompressed. Therefore, on the inner peripheral side between the blades 5, in the vicinity of the suction port 6 a immediately after passing through the suction-side flow path guide portion 10 a of the partition 10, gas flowing in from the outside easily flows through the blades. It will flow into the car 1. Therefore, jet 15
The swirl flow 16 is formed near the suction port 6a immediately after passing through the suction-side flow path guide portion 10a due to the generation of the swirl flow due to and the ease of gas suction into the inner peripheral side of the impeller 1. The wetting length also increases. Accordingly, in the vicinity of the suction port 6a, the mixing area from the suction port 6a to the discharge port 6b is reduced and the wetting length is increased as compared with the related art, so that the vortex blower has the circumferential angle and the wetting length. The effect of the pressure increase will be increased by a corresponding amount. Thus, the vortex blower can increase its discharge pressure and improve performance. The swirling flow 16 by the jet 15
Is generated and the gas is easily sucked into the inner peripheral side of the impeller 1, so that the suction port 6a
Since the swirling flow is smoothly formed in the vicinity, the turbulence of the gas in this region is reduced, and accordingly, the generation of noise can be suppressed and the effect of noise reduction can be obtained.

According to observations made by the inventor through experiments,
It has been confirmed that an angle α of the communication passage 14 with respect to the traveling direction of the blade 5 in the range of 5 degrees to 35 degrees is favorable for forming a swirling flow. Incidentally, in the embodiment, the angle α is set to 20 degrees. In addition, although the diameter of the communication passage 14 is the size in the radial direction, in the embodiment, the width W of the blade 5 is 1/1/3.
It has a width of 3. However, this is an arrangement for obtaining a greater effect, and it may extend over the entire width of the blade 5, but it is preferable that the arrangement is based on the inner circumference. If more effect is desired, the width W of the blade 5 should preferably be at least about 1/3 inward from the center. Further, with respect to the circumferential position of the communication path 14, the point B at the rear end position in the traveling direction of the blade 5 is set at 1.1 of the distance between the blade 5 and the blade 5 from the point A at the tip end of the discharge side flow path guide portion 10b. The range of 5 to 2.5 times was good.
However, the opening position of the communication passage 14 on the side facing the impeller 1 is not particularly limited to this position, and it is sufficient that the compressed gas remaining between the blades 5 can be introduced. The opening may be opened on the side flow path guide 10a side, and both the suction side and discharge side flow path guides 10a, 1
An opening may be provided over 0b.

FIG . 13 is a characteristic diagram showing the air volume and air pressure characteristics of the eddy blower employing the present embodiment and the conventional one. Curve A is an aerodynamic characteristic diagram provided with a communication passage according to the present embodiment. FIG. 9 is an aerodynamic characteristic diagram of a conventional one, that is, one having no communication passage. The motor used was 0.75 (KW), the effective diameter of the impeller was 235 (mm), and the rotation speed of the motor was 34.
20 (RPM), the gap between the impeller and the partition is 0.3
(Mm), the case where the angle of the communication passage is 20 degrees is shown. As is clear from this figure, the aerodynamic characteristics of the embodiment can be improved by about 20% as compared with the conventional one.

The third embodiment shows a case in which the present invention is applied to a kind of a vortex type gas pump, that is, an outer peripheral side of a double vane type vortex blower. FIG. FIG. 15 is a sectional view of FIG.
FIG. 16 is a view cut along line -15, and FIG.
It is a figure which cut | disconnects and shows 5 along 16-16 line. FIG.
FIG. 7 is a cut-away side view showing the overall configuration of the embodiment.

In these figures, 101 is an impeller, 1
02 is a casing forming the annular flow path 108 , 115
Is a side cover that forms the annular flow path 108 . The cross section of the annular flow path 108 which opens in a direction parallel to the axis of the rotating shaft 3 forms a substantially semicircular groove. The annular flow path 108 is formed in an annular shape around the rotation shaft 103 of the prime mover 104 . One end of the annular flow passage 108 communicates with the suction port 106a , and the other end thereof forms the discharge port 106b.
Is in communication with Between the discharge port 106b and the suction port 106a , the partition wall opposes the impeller 101 via a minute gap.
It is divided by 110 . The suction-side passage 106a ' connected to the suction port 106a and the discharge-side passage connected to the discharge port 106b are provided so as to be parallel in the silencer 107 which also serves as a base member. The prime mover 104 is fixed on a silencer 107 also serving as a base member, and the casing 102 is fixed to the prime mover 4.

The impeller 101 is Yes constituted by a plurality of blades 105 and hub 116 as shown in FIGS. 15 to 17, as a hard <br/> Bed 116 about the rotary shaft 3, a circular annular channel 108 It has an annular groove 111 which opens in the axial direction on both sides to face the, vane 105 is provided a number in a direction transverse to the groove 111. The impeller 101 is connected to the rotating shaft 10 of the motor 104.
By fixing to 3 , the opening of the upper annular flow path 108 and the opening of the groove 111 face each other, thereby forming an annular flow path 112 having a substantially circular cross section.

Here, when the prime mover 104 is driven to rotate,
The impeller 101 fixed to the rotating shaft 103 rotates.
Then, the gas sucked from the inlet 106a is
By the action of the blade 105 of the blade root wheel 101, annular upper line 1
08 and a groove 111 having a circular cross section having an annular shape.
It rotates while drawing a spiral in the inside 112, is pressed by the blade 105 , and is gradually conveyed in the rotation direction F.
Then, the pressurized gas is guided to the discharge port 106b by the action of the partition 110 , and is discharged therefrom.

FIG. 16 shows the partition 110 and the suction port 106.
FIG. 3 is a cross-sectional view of a main part showing a relationship between a, an outlet 106b, and an impeller 101 . As shown in this figure, barrier ribs 110
The suction port 106a is provided at the tip end facing the impeller 101.
And it includes a suction-side channel guide portion 110a smoothly guided to the annular channel 112, and a discharge side flow passage guide portion 110b for guiding the pressurized gas to smoothly discharge port 106b of the inflow gas from. As is clear from this figure, the gas pressurized by the impeller 101 is guided to the discharge port 106b by the action of the partition 110 . However, when discharging, the blade 1
Gas 113 left between the nozzle 05 and the adjacent blade 105
Is closed at the outlet by the partition wall 110 , carried to the suction port 106a side as it is, and carried over to the suction side. This is called a carryover flow, and the carryover flow is carried to the suction side after passing through the partition wall 110 after the swirl is reduced. Then, the pressurized fluid is opened on the entire side of the blade 105 on the suction side, and expands in the annular flow path 112 almost uniformly without turning. Then, this expansion flow is
Mixed with inflow air body from 106a, disturbs the flow of the gas flowing. Due to this disturbance, the suction port 1
06a cannot start to form a swirling flow smoothly in the flow path near the suction port 106a ,
Only after passing through this mixing region will an effective swirl flow be formed.

Therefore, according to the present embodiment, FIGS.
As shown in, suction-side channel guide portion 110a of the partition wall 110
On the outer peripheral side of the suction port from the side facing its blades 105 1
Providing a communication passage 114 which communicates with the 06 a side. This constitutes an auxiliary flow supply path. The gas 113 remaining between the blades 105 by the communication passage 114 causes the communication passage 11 to expand before inflation near the tip of the suction-side flow guide 110a.
4 , a jet 115 indicated by an arrow on the side of the suction port 106a.
It ejected as. The communication passage 114 is provided at an angle α obliquely forward with respect to the traveling direction of the blade 105 in consideration of the fact that the gas ejected from the communication passage swirls smoothly in the annular flow passage 112 . Of particular importance here is the communication path 114.
Surface 114 located forward with respect to the traveling direction of the blade 105
a , and the angle of the surface 114a is α. For example, Yes in conjunction with this the angle of the plane 114b located behind, also the impeller of the communicating passage 114 101
Is arranged on the outer peripheral side of the blade 105 . This is because the gas is advantageously compressed outward by the centrifugal force by the blades 105 and is advantageous in forming a swirling flow.

[0046] According to this embodiment, since the outer peripheral portion of the suction-side channel guide portion 110a of the partition wall 110 is provided with a communicating passage 114, out of the gas 113 which has been compressed left between the blade 105 by a partition 110 The carry-over flow on the outer peripheral side of the impeller 101 flows out of the communication passage 114 to form a jet 115 . The jet 115 flows on an inner circumferential side of the casing 102 along the inner wall of the casing 102, further impeller
It flows on the inner peripheral side of 101 and forms a swirling flow. At this time, the gas in the periphery of the jet 115 is directed in the turning direction is dragged in the jet 115. On the other hand, the compressed gas 113 left between the blades 105 by the partition wall 110 flows out from the outer peripheral side by the action of the communication passage 114 , and
The gas is vacant on the inner peripheral side between 105 and the partition 11
0 inlet immediately after passing through the suction-side channel guide portion 110a of the
In the vicinity of 106a , gas flowing from the outside easily flows into the impeller 101 . Therefore, due to the generation of the swirling flow by the jet 115 and the ease of sucking the gas into the inner peripheral side of the impeller 101 , the swirling flow 116 is smoothly formed in the vicinity of the suction port 106a immediately after passing through the suction-side flow path guide 110a. Formed and at the same time the wetting length increases. Therefore, since in the vicinity of the suction port 106a increases even mixed region is reduced wetted perimeter length of over discharge port 106b F from the suction port 106a as compared with the prior art, the vortex flow blower in this circumferential angle and wetted perimeter length The effect of the pressure increase will be increased by a corresponding amount. Thus, the vortex blower can increase its discharge pressure and improve performance. Further, due to the generation of the swirling flow by the jet flow 115 and the ease with which the gas is sucked into the inner peripheral side of the impeller 101 , the suction-side flow path guide portion is provided.
Immediately after passing through 110a , the swirling flow is smoothly formed in the vicinity of the suction port 106a , so that the turbulence of gas in this region is reduced, so that the generation of noise can be suppressed and the effect of noise reduction can be obtained. it can.

According to observations made by the inventor through experiments,
Angle α of communication passage 114 with respect to traveling direction of blade 105
It was confirmed that the range of 5 to 35 degrees was favorable for forming a swirling flow. Incidentally, in this embodiment, the angle α is set to 12 degrees. Although a radial size of the communicating passage 114, in the embodiment, the vanes 10
The width W is 1/3 of the width W of the fifth . However, this is an arrangement for obtaining a greater effect, and the blade 105
, But is preferably on the outer peripheral side. If more effect is desired, it is preferable that the width W of the blade 105 be from the center to the outside, and further be about (１ ／) × W or more outside from the center. Further, regarding the circumferential position of the communication passage 114 ,
Rear end position point B to the traveling direction of 105, from the tip point A of the discharge side flow passage guide portion 110b, the blade 105 and the blade 105
The range from 1.5 times to 2.5 times the interval between was favorable. However, the opening position of the communication passage 114 on the side facing the impeller 101 is not particularly limited to this position, as long as the compressed gas remaining between the blades 105 can be introduced. Side channel guide 110a
Of course, the opening may be formed on the suction side and the discharge side flow path guides 110a and 110b .

FIG. 18 is a characteristic diagram showing the air volume and air pressure characteristics of the eddy blower employing this embodiment and the conventional one.
A curve A is an aerodynamic characteristic diagram provided with a communication passage according to the present embodiment, and a curve B is an aerodynamic characteristic diagram of a conventional device, that is, a device having no communication passage. The used motor is 0.75 (KW),
The rotation speed is 3420 (RPM), the gap between the impeller and the partition wall is 0.3 (mm), and the angle of the communication passage is 12 degrees. As is clear from this figure, the aerodynamic characteristics of the example of the present invention are 1% lower than those of the conventional example.
It could be improved by about 0%.

[0049] above, in the third embodiment has been described the case of using the gas left between the blade 105 and the blade 105 by a partition 110 as an auxiliary stream, the gas in a different position as auxiliary flow Needless to say, a gas pressurized by other means may be used. In particular, in this case, the auxiliary flow supply path does not need to be provided in the partition 110 in the form of a communication hole,
The degree of freedom of the position increases. However, implementation by utilizing a gas that remains compressed between the blade 105 and the blade 105 by a partition 110 as an auxiliary stream as in the example, at the same time the gas to be wetted perimeter length utilized which is a factor of disturbance Because of the increase, a great effect can be obtained in various performances such as efficiency.

Although the embodiment has been described with reference to the vortex blower, the present invention is not limited to this, and it is needless to say that the present invention can be applied to a vortex pump in a broad sense such as a vortex gas pump and a vortex liquid pump. It is.

[0051]

As is apparent from the above description, according to the present invention, the swirling flow can be more smoothly formed in the annular flow path, so that the performance of the vortex pump can be improved.

[Brief description of the drawings]

FIG. 1 is a sectional view of a main part of a vortex blower showing one embodiment of the present invention.

FIG. 2 is a cross-sectional view of FIG. 1 cut along line 2-2.

FIG. 3 is a partially cutaway perspective view showing an entire configuration of a vortex blower showing one embodiment of the present invention.

FIG. 4 is a cut-away side view showing an overall configuration of a vortex blower showing one embodiment of the present invention.

FIG. 5 is a perspective view showing an example of an impeller of a vortex blower.

FIG. 6 is a front view showing a state in which a side cover and an impeller of the vortex blower according to the embodiment of the present invention are removed.

FIG. 7 is an explanatory diagram for explaining the principle of a vortex blower.

FIG. 8 is an explanatory diagram for explaining the principle of a vortex blower.

FIG. 9 is an aerodynamic characteristic diagram showing experimental results of one example of the present invention.

FIG. 10 is a sectional view of a main part of a vortex blower showing one embodiment of the present invention.

FIG. 11 is a cross-sectional view of FIG. 10 cut along line 11-11.

FIG. 12 is a front view showing a state in which the side cover and the impeller of the vortex blower according to the embodiment of the present invention are removed.

FIG. 13 is an aerodynamic characteristic diagram showing an experimental result of one example of the present invention.

FIG. 14 is a sectional view of a main part of a vortex blower showing one embodiment of the present invention.

FIG. 15 is a cross-sectional view of FIG. 14 cut along line 15-15.

FIG. 16 is a cross-sectional view of FIG. 15 taken along line 16-16.

FIG. 17 is a cut-away side view showing an overall configuration of a vortex blower showing one embodiment of the present invention.

FIG. 18 is an aerodynamic characteristic diagram showing experimental results of one example of the present invention.

[Description of Signs ] 1,101: impeller, 5,105: blade, 6a, 106
a ... suction port, 6b, 106b ... discharge port, 10, 110 ...
Partition walls, 10a, 110a ... suction side flow path guides, 10b,
110b ... discharge side flow path guide, 14, 114 ... communication passage

──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Toshiharu Yoshitomi 7-11-1, Higashi Narashino, Narashino-shi, Chiba Hitachi, Ltd. Narashino Plant (72) Inventor Kazuo Kobayashi 7-1-1, Higashi-Narashino, Narashino-shi, Chiba Narashino Plant, Hitachi, Ltd. (58) Field surveyed (Int. Cl. ⁷ , DB name) F04D 23/00

Claims (15)

(57) [Claims] An impeller having a number of blades is arranged in an annular flow path, and a suction port and a discharge port communicating with the annular flow path, respectively, and a space between the discharge port and the suction port, Having a partition that partitions the passage of the blade through a minute gap,
By rotating the impeller disposed in the annular flow path, the fluid introduced from the suction port is swirled and pressurized in the annular flow path, and is configured to be discharged from the discharge port. A vortex pump comprising: an auxiliary flow supply path for supplying an auxiliary flow for guiding a fluid flowing from a suction port in a direction of forming the swirling flow. 2. The vortex pump according to claim 1, wherein the auxiliary flow is a carry-over flow carried from the discharge port side to the suction port by an impeller. 3. The angle of supply of the auxiliary flow is in a range of 5 degrees to 35 degrees with respect to the traveling direction of the impeller based on a plane forming a minute gap with the impeller of the partition wall. The vortex pump according to claim 1. 4. An annular flow path, a suction port communicating with the inside of the annular flow path, a discharge port, and a small gap formed between the discharge port and the suction port with respect to a passage of the blade. A swirl pump having a partition that intervenes through the partition, wherein the suction flow side of the partition is configured such that the carryover flow conveyed from the discharge port side by the blade is advanced with respect to a surface forming a minute gap with the impeller of the partition. A vortex pump characterized by having a communication passage for guiding discharge in an obliquely forward direction with respect to the direction. 5. The communication passage discharges the carryover obliquely forward in a range of 5 ° to 35 ° with respect to the traveling direction of the blade with respect to a plane forming a minute gap with the impeller of the partition wall. The vortex pump according to claim 4, wherein 6. The partition according to claim 1, further comprising a flow path guide for guiding the flow guided from the suction port to the annular flow path and the blade, wherein the communication path is provided in the flow path guide. 4. The vortex pump according to 4. 7. The vortex pump according to claim 4, wherein the communication path is a notch provided in the flow path guide. 8. An opening position on a side corresponding to a blade of a communication path provided by cutting out a flow path guide portion, a rear end of the communication path in a circumferential direction with respect to a traveling direction of the blade is formed by a flow path guide portion of a partition wall. 8. The vortex pump according to claim 7, wherein the distance from the rear end is 1.5 to 2.5 times the distance between the blades. 9. An angle of a surface of an opening on a side corresponding to a blade of a communication passage formed by cutting out a flow path guide portion and located forward with respect to a traveling direction of the blade ranges from 5 degrees to 35 degrees. The vortex pump according to claim 7, wherein 10. An opening position on a side corresponding to a blade of a communication path provided by cutting out a flow path guide portion is outside a position corresponding to the blade in a radial direction. A vortex pump as described. 11. An opening position on a side corresponding to a blade of a communication path provided by cutting out a flow path guide portion is a position corresponding to the blade in a radial direction, and is located outside a central portion of the blade. The vortex pump according to claim 7, characterized in that: 12. An opening position on the side corresponding to the blade of the communication passage provided by cutting out the flow path guide portion is a position corresponding to the blade in the radial direction, with respect to the center of the blade.
The vortex pump according to claim 7, wherein the outer circumference is equal to or more than / 6. 13. An opening position on a side corresponding to a blade of a communication path provided by cutting out a flow path guide portion is inside a position corresponding to the blade in a radial direction. A vortex pump as described. 14. An opening position on the side corresponding to the blade of the communication passage provided by cutting out the flow path guide portion is a position corresponding to the blade in the radial direction and inside the central portion of the blade. The vortex pump according to claim 7, characterized in that: 15. An opening position on a side corresponding to a blade of a communication passage provided by cutting out a flow path guide portion is a position corresponding to the blade in the radial direction, and is set at one position with respect to a central portion of the blade.
The vortex pump according to claim 7, wherein the inner diameter is equal to or more than / 6.