JP2010159704A - Vortex flow blower - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To restrain generation of noise from a vortex flow blower, while maintaining delivery performance of the vortex flow blower. <P>SOLUTION: This vortex flow blower has a casing 11 for arranging a stationary flow passage 20 extending in a circular arc shape between a suction port 23 and a delivery port 24, and an impeller having a three-dimensionally curved blade is rotatably installed in the casing 11. The casing 11 is provided with a partition wall 25 for partitioning between both end parts of the stationary flow passage 20, and a suction side guide 31 for partially covering the suction port 23 is integrally arranged on the partition wall 25, and a suction side end surface 32 extends in the direction for crossing the suction port 23. The suction side guide 31 is formed with an expansion space 35 for reducing pressure in a carry-over flow flowing along the partition wall 25 to the suction port side from the delivery port side on the outer peripheral part side. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a vortex blower that continuously feeds air by applying kinetic energy to the air by rotation of an impeller.

  The vortex blower, that is, the vortex blower has a casing in which an arcuate stationary flow path is formed. An impeller having a shroud provided with an annular groove facing the stationary flow path and a plurality of blades or blades provided in the shroud at predetermined intervals in the circumferential direction across the annular groove is freely rotatable on the casing. The impeller is rotationally driven by an electric motor attached to the casing. The casing is provided with a suction flow channel that communicates with one end of the static flow channel and a discharge flow channel that communicates with the other end of the static flow channel. The discharge channel communicates with the other end of the stationary channel via the discharge port. When the impeller is rotated by an electric motor, the air flowing in from the suction flow path is accelerated between the blades of the impeller from the inner periphery toward the outer periphery and flows into the static flow path, and the inside of the static flow path in the circumferential direction The process of decelerating and boosting pressure while being guided by the above and the process of flowing again between the blades are repeated. As a result, the inflowing air is repeatedly given kinetic energy by the impeller and pressurized. The pressurized air is discharged to the outside through the discharge channel. The casing is provided with a partition partitioning the opposite ends of the stationary flow path so as to face the blade. The partition partitions the opening on the impeller side of the suction flow path and the discharge flow path, and the suction port. Sealed to prevent direct communication with the discharge port.

  The vortex blower with such a structure is widely used as a relatively small-capacity air power source in general industrial machines because the pressure coefficient representing the work per unit impeller outer diameter is higher than that of a centrifugal blower and can be reduced in size and weight. Has been. As a usage form of the vortex blower, there are a case where positive pressure air discharged from the discharge passage is used and a case where negative pressure generated in the suction passage is used. For example, when vortex blowers are used to remove machine tool chips, positive pressure air is used. When vortex blowers are used to suck and convey workpieces, negative pressure air generated in the suction flow path is used. Is done.

  As described in Patent Document 1, the eddy current blower includes a type in which the blade is curved three-dimensionally. The three-dimensional type of blade has a two-dimensional direction along the circumferential surface and an axial direction along the rotation axis. And curved respectively. The vortex blower having this type of blade has an advantage that the discharge pressure can be increased as compared with the vortex blower in which the blade extends straight in the radial direction and becomes a straight type. However, when the discharge pressure is increased, noise radiated to the outside through the suction flow path and the discharge flow path due to pressure fluctuations increases. Therefore, in the vortex blower described in Patent Document 1, a partition wall that partitions between both ends of an arc-shaped stationary flow path is attached to the casing, and a suction port is provided in front of the suction port so as to face the suction port. A guide on the suction side is provided integrally with the partition so as to cover, and a guide on the discharge port side is provided integrally with the partition so as to cover the discharge port in front of the discharge port. Thereby, the noise generated due to the pressure fluctuation is diffracted to reduce the direct sound radiated to the outside.

  In the vortex blower, the fluid flowing in from the suction port is boosted by the impeller and flows out from the discharge port. However, the fluid boosted by the impeller and trapped between the blades passes the discharge port side to guide the fluid. And it is in a state of being blocked by the partition wall and transferred to the suction port side. This transferred fluid is referred to as carryover or carryover. Therefore, if a member in which the guide facing the suction port and the guide facing the discharge port are integrally provided on the partition is attached to the casing, the guide on the suction port side passes through the partition from the guide on the discharge port side. A carry-over flow will be formed.

  Patent Document 2 describes a vortex blower in which a carry-over flow is merged with an inflowing fluid after the carry-over flow passes through the position of a suction port. In this vortex blower, an auxiliary flow supply path is formed in the guide on the suction port side in order to improve aerodynamic performance, and a swirl flow is formed in the impeller by ejecting a carry-over flow as an auxiliary flow from the auxiliary flow supply path. I am doing so. As described above, in the vortex blower of Patent Document 2, the jet performance of the carry-over flow is combined with the inflowing fluid, and the swirling flow is added to the air flowing into the stationary flow path from the suction port so as to improve the discharge performance. ing.

Japanese Patent Laid-Open No. 3-78595 JP-A-5-65891

  However, as described in Patent Document 2, when the carry-over jet is blown toward the static flow path, the pressure of the carry-over flow transferred is higher than the fluid flowing from the suction port into the static flow path. Therefore, when the carry-over flow is opened to the suction side, the flow that flows from the suction port to the blades of the impeller through the stationary flow path is obstructed, and this is one factor that reduces the pressure loss of the vortex blower. It has become.

  On the other hand, in a vortex blower, wind noise with a frequency that is an integral multiple of the number of blades and the multiplier of the number of rotations is usually generated due to interference between the blades and the partition walls. It was found that when a low inflow flow and a high pressure carry-over flow were mixed, a sudden pressure change occurred in the mixing section, and the noise of wind noise was amplified by pressure pulsation.

  In a vortex blower having a curved blade, the circumferential length of the partition wall is longer than that of a straight vortex blower in which the blade is not curved. In addition, if a guide is provided on the partition wall so as to cover the suction port and the discharge port in order to reduce direct sound to the outside of the vortex blower, the circumferential length of the partition wall including the guide becomes longer. As described above, when the circumferential length of the partition wall is increased, the circumferential angle of the stationary flow path for pressurizing the air is reduced, and the length of the stationary flow path is relatively shortened to improve the discharge performance. Can not be made.

  In this way, when the circumferential length of the partition wall increases, an undercut portion that cannot be removed from both the front and back of the casing occurs when the casing is formed by casting or die casting. It becomes impossible to manufacture an integrally structured casing that is integrated with the casing. For this reason, the partition and the guide must be separate parts from the casing, which increases the number of parts, increases the number of manufacturing steps, and increases the material cost.

  An object of the present invention is to suppress the generation of noise from a vortex blower while maintaining the discharge performance of the vortex blower.

  Another object of the present invention is to make it possible to manufacture the casing and the partition wall of the vortex blower integrally.

  The vortex blower of the present invention includes a casing provided with a static flow path extending in an arc shape between a suction port on one end side and a discharge port on the other end side, and an annular groove facing the static flow path. A shroud rotatably mounted on the casing has an impeller in which blades that are three-dimensionally curved in the axial direction and the circumferential direction are provided at predetermined intervals in the circumferential direction across the annular groove. A vortex blower, partitioning between both ends of the stationary flow path and facing the blade through a gap provided in the casing, and having a suction side end surface extending in a direction crossing the suction port; A suction side guide that protrudes in the circumferential direction in front of the suction port and partially covers the suction port is provided integrally with the partition wall, and the blade carries over from the discharge port side to the suction port side along the partition wall by the blade. The flow An expansion space for depressurizing the outer peripheral portion side of the over-de, characterized in that formed on the outer peripheral side of the suction side guide.

  The vortex blower of the present invention is characterized in that a gap between the suction side guide and the blade in the expansion space is set larger than a gap between the partition wall and the blade. The vortex blower according to the present invention is characterized in that the expansion space is provided at a position facing the suction port via the suction side guide. The vortex blower of the present invention is a partition that extends in a circumferential direction at a central portion in the radial direction with respect to the stationary flow path, and projects in a circumferential direction from the suction side end face of the radially inner portion of the stationary flow path. A portion is provided in the suction side guide. The vortex blower according to the present invention is characterized in that the suction side end face of the radially inner portion of the stationary flow path is inclined in the rotation direction.

  The vortex blower of the present invention has a discharge-side guide provided on the partition wall, which has a discharge-side end surface extending in a direction crossing the discharge port and projects in a circumferential direction in front of the discharge port and partially covers the discharge port. It is characterized by. The vortex blower of the present invention is characterized in that the suction side guide, the discharge side guide, and the partition are integrally provided in the casing.

  According to the present invention, the outer surface of the outer peripheral portion of the suction side guide partially covering the suction port is formed with an expansion space for expanding and reducing the carryover flow. After being expanded and depressurized, it is mixed with the inflow air flowing into the static flow path from the suction port, so that the pressure pulsation at the time of mixing is reduced, and the generated noise on the suction port side can be reduced.

  Since the suction side guide partially covers the suction port, the length of the stationary flow path facing the impeller can be increased, and the discharge performance can be improved. Thereby, noise generation from the vortex blower is suppressed while maintaining the discharge performance, and a quiet vortex blower can be obtained.

  Since the suction side guide and the discharge side guide can be provided integrally with the casing together with the partition wall, the casing including the partition wall can be easily manufactured by casting or die casting. Thereby, an eddy current blower can be manufactured at low cost by a small number of parts and a small number of processes.

It is a partially cutaway perspective view showing an eddy current blower according to an embodiment of the present invention. It is a longitudinal cross-sectional view which shows a part of eddy current blower shown by FIG. It is a front view which shows the inner surface of an impeller. It is a perspective view which shows the front side of a casing. It is a front view of a casing. FIG. 6 is a partially enlarged front view of FIG. 5. (A) is the 7A-7A sectional view taken on the line in FIG. 6, (B) is the 7B-7B sectional view taken on the line in FIG.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. As shown in FIG. 1, this vortex blower has a casing 11 in which a pedestal portion 10 is integrated. An electric motor 12 is attached to the casing 11, and the electric motor 12 is fixed to the pedestal 10 with bolts. As shown in FIGS. 1 and 2, the casing 11 has a curved portion 11b integrated with an annular portion 11a, and a cylindrical portion 11c protruding in the axial direction is integrated with an outer peripheral portion of the curved portion 11b. Yes. A rotating shaft 13 of the electric motor 12 passes through the center of the annular portion 11a, and a boss member 14 fitted to the annular portion 11a is attached to the rotating shaft 13 via a bearing. An impeller 15 that is rotationally driven by the electric motor 12 is attached to the rotating shaft 13, and the impeller 15 is provided with a disk portion 16a that is fixed to the rotating shaft 13 and a bending portion 16b that faces the bending portion 11b. The shroud 16 is provided, and an annular groove 17 is formed on the inner surface of the curved portion 16b.

  The annular groove 17 is partitioned by a plurality of blades or blades 18 provided at predetermined intervals in the circumferential direction in the curved portion 16b of the shroud 16, and a centrifugal groove 17a is provided between the blades 18 adjacent in the circumferential direction. It has become. 3 and 7, when the rotational direction of the impeller 15 is R, the blade 18 is curved in the axial direction along the rotational shaft 13 so that the front side in the rotational direction is concave, and the radial center Both ends in the radial direction are curved so as to protrude toward the front side in the rotational direction from the portion. As described above, the blade 18 is a curved type that is three-dimensionally curved in a two-dimensional direction along the circumferential surface and an axial direction along the rotation axis. A casing cover 19 is attached to the cylindrical portion 11 c of the casing 11, and the impeller 15 is covered with the casing cover 19.

  An arcuate stationary flow path 20 is formed on the inner surface of the curved portion 11 b of the casing 11. As shown in FIG. 1, the suction flow path 21 is provided on the pedestal portion 10 of the casing 11 so as to communicate with the outer peripheral side of one end of the static flow path 20, and is communicated with the outer peripheral side of the other end of the static flow path 20. The discharge channel 22 is provided in a pedestal (not shown) parallel to the pedestal 10. As shown in FIGS. 6 and 7, the suction channel 21 communicates with one end of the arc-shaped stationary channel 20 via the suction port 23, and the discharge channel 22 communicates with the other end of the stationary channel 20. The discharge port 24 communicates. In this way, the portion that connects the suction flow channel 21 and the stationary flow channel 20 becomes the suction port 23, and the portion that connects the discharge flow channel 22 and the stationary flow channel 20 becomes the discharge port 24, each of which is stationary. It is provided on the radially outer peripheral side of the flow path 20. In FIG. 6, the blade 18 of the impeller 15 facing the stationary flow path 20 is indicated by a two-dot chain line.

  In the casing 11, a partition wall 25 is provided integrally with the casing 11 so as to partition between both ends of the stationary flow path 20, that is, between the discharge port 24 and the suction port 23. As shown in FIG. 7, the partition wall 25 has a slight gap C1 of about 0.3 to 0.6 mm with respect to the front end surface of the blade 18 when the impeller 15 is mounted on the casing 11. 26 to face each other. However, the gap 26 is exaggerated in FIG.

  A connection port 21b for connecting a suction pipe (not shown) is provided at the outer end of the suction flow path 21 as shown in FIG. 1, and air is supplied to the suction flow path 21 from the outside via the suction pipe. The A connection port for connecting a discharge pipe (not shown) is provided at the outer end of the discharge flow path 22. A silencer 27 is incorporated in the suction passage 21, and a silencer (not shown) is also incorporated in the discharge passage 22.

  As shown in FIGS. 5 to 7, a suction side guide 31 is provided integrally with the partition wall 25 so as to protrude forward from the partition wall 25 in the circumferential direction and partially cover the suction port 23. As shown in FIG. 5, the suction side end face 32 of the suction side guide 31 extends in a direction crossing the suction port 23. A discharge side guide 33 that protrudes from the partition wall 25 in the circumferential direction in front of the discharge port 24 and partially covers the discharge port 24 is provided integrally with the partition wall 25. As shown in FIG. The discharge side end surface 34 of the guide 33 extends in a direction crossing the discharge port 24. Thus, since the suction side guide 31 partially covers the suction port 23, the portion of the suction port 23 that is not covered by the suction side guide 31 directly faces the blade 18. Similarly, the blade 18 directly faces a portion of the discharge port 24 that is not covered by the discharge side guide 33.

  When the impeller 15 is rotationally driven by the electric motor 12, the air that is guided by the suction flow path 21 and flows into the impeller 15 from the stationary flow path 20 as indicated by an arrow I in FIG. 7 is exchanged between the blades 18 of the impeller 15. The centrifugal groove 17a is increased from the inner periphery toward the outer periphery and flows into the stationary flow path 20. Thereby, the process in which the inflowed air is guided in the circumferential direction in the stationary flow path 20 in the circumferential direction, decelerated and boosted, and the process of flowing into the centrifugal groove 17a again are repeated. In this way, while the air flows spirally in the vortex blower, kinetic energy is repeatedly applied by the impeller 15 and pressurized. The pressurized air is guided to the outside through the discharge flow path 22 as indicated by an arrow O in FIG. In FIG. 2, the state in which the inflowing air flows from the inner peripheral side to the outer peripheral side in the centrifugal groove 17a of the impeller 15 and flows from the outer peripheral side to the inner peripheral side in the stationary flow path 20 is indicated by an arrow S. It is shown in

  As described above, the fluid flowing into the stationary flow path 20 from the suction port 23 is pressurized by the impeller 15 and flows out from the discharge port 24. However, the fluid is pressurized by the impeller 15 and the centrifugal groove 17a between the blades 18 is. When the fluid trapped inside passes the discharge port side with the rotation of the impeller 15, the fluid is blocked by the discharge side guide 33, the partition wall 25 and the suction side guide 31 and is carried over to the suction port side. Will be transported. An expansion space 35 is formed on the surface of the outer peripheral portion of the suction side guide 31 to depressurize the carry-over flow transferred to the suction side guide 31 with the rotation of the impeller 15 between the blade 18 and the outer peripheral portion side. ing.

  As shown in FIGS. 4 to 7, the expansion space 35 is formed by partially forming a thin portion 36 on the suction side guide 31, so that a surface 37 of the thin portion 36, a circumferential step surface 38, a diameter The expansion space 35 is opposed to the radially outer peripheral portion at the tip of the blade 18. A dimension C2 between the surface 37 of the thin portion 36 and the blade tip is set larger than a dimension C1 of the gap 26 in the partition wall 25. In the illustrated case, the dimension C2 is set to 5 mm, and is set to about 10 times the gap 26.

  As shown in FIGS. 4 and 5, the suction side guide 31 and the discharge side guide 33 are integrated with the partition wall 25 that divides the both ends of the stationary flow path 20. Except for the portion of the expansion space 35 provided, the surfaces of the suction side guide 31 and the discharge side guide 33 are flush with the surface of the partition wall 25, and the surface of the partition wall 25 is on the inner peripheral side of the annular curved portion 11b. The tip surface is also the same surface.

  As shown in FIG. 5, the expansion space 35 is provided at a position facing the suction port 23 via the thin portion 36 of the suction side guide 31, and the size of the expansion space 35 is set smaller than the suction port 23. Yes. The expansion space 35 is provided close to the suction port 23 toward the outer peripheral side in the radial direction, and overlaps the suction port 23.

  The suction side guide 31 is provided with a partition portion 40 extending in the circumferential direction so as to correspond to the central portion in the radial direction of the blade 18. The end surface of the suction side guide 31, that is, the suction side end surface 32, is a circumferential portion 32 a extending in the radial direction corresponding to the thin portion 36 and the partition portion 40 and extending along the step surface 38 to form the partition portion 40. It has the part 32b and the part 32c extended from the root part of the partition part 40 to the radial direction inner surface of the stationary flow path 20, and the suction side end surface 32 becomes the shape bent entirely. A portion 32c of the suction side end surface corresponding to the radially inner portion of the stationary flow path 20 in the suction side end surface 32 is inclined in the rotational direction so as to proceed in the rotational direction of the impeller 15 toward the radially inner side. Yes.

  On the other hand, the discharge-side end face 34 of the discharge-side guide 33 is inclined toward the radial inner portion of the stationary flow path 20 from the radial inner end of the portion 34a that crosses the discharge port 24 in the radial direction. The inclined portion 34b of the discharge side end face 34 is inclined so as to advance in the opposite direction to the rotational direction of the impeller 15 as it goes inward in the radial direction.

  The carry-over flow trapped in the centrifugal groove 17a with the rotation of the impeller 15 and blocked by the discharge side guide 33, the partition wall 25, and the suction side guide 31 is transferred to the suction port side. As shown in (B), the portion of the carry-over flow that has been transferred to the outer peripheral side of the suction-side guide 31 is in the expansion space 35 provided on the outer peripheral portion of the suction-side guide 31 as indicated by an arrow T. Get in. The carry-over flow that has entered the expansion space 35 expands and is depressurized, and then flows in the circumferential direction on the outer peripheral portion of the stationary flow path 20. On the other hand, the inflow air that has flowed into the suction port 23 from the outside flows into the stationary flow path 20 as shown by an arrow I in FIGS. 5 and 7 and flows into the inner peripheral side of the stationary flow path 20. . As a result, the carry-over flow on the outer peripheral side is mixed with the air flowing in from the suction port 23 after being reduced in pressure, so that the pressure pulsation during mixing is reduced, and wind noise that is noise generated on the suction port 23 side is reduced. Is reduced.

  The clearance C1 between the partition wall 25 and the impeller 15 is set to about 0.3 to 0.5 mm, the clearance C2 of the expansion space 35 is set to about 5 mm, and the clearance C2 of the expansion space 35 is set to the clearance C1. The carry-over flow is expanded in the expansion space 35 and depressurized. If the gap size of the expansion space 35 is made too large, the carry-over flow that has been transferred to the outer peripheral portion tends to flow out to the inner peripheral side of the stationary flow path 20, resulting in performance degradation or fluctuations in the force generated by sudden expansion. However, by adjusting the gap C2, the direction of the expanded air flow can be imparted and the generation of noise due to wind noise can be suppressed.

  A partition portion 40 extending in the circumferential direction is provided in the suction side guide 31 corresponding to the radial center portion of the blade 18, and this partition portion 40 is a central portion of the vortex between the stationary flow path 20 and the centrifugal groove 17 a. The expansion space 35 and the radially inner portion of the suction side guide 31 are partitioned by the partition portion 40. Thereby, as shown by the arrow I, the air which flowed into the inner peripheral part side of the stationary flow path 20 from the suction port 23 flows into the centrifugal groove 17a from the inner peripheral part side of the impeller 15, and the centrifugal groove 17a It flows out from the outer peripheral portion side toward the outer peripheral portion of the stationary flow path 20, and smoothly flows into the centrifugal groove 17 a between the blades 18.

  The clearance on the radially inner side of the suction side guide 31 has the same size as the clearance between the partition wall 25 and the impeller 15, and the carry-over flow passing through that portion does not expand under reduced pressure, but the suction port 23 Therefore, it flows to the inner peripheral side of the stationary flow path 20 without generating wind noise. Moreover, since the suction side end surface portion 32c on the radially inner side is skewed or inclined, the blade 18 and the end surface portion 32c intersect each other as shown by a two-dot chain line in FIG. As the impeller 15 rotates, the blade 18 gradually crosses the end face portion 32c and the carry-over flow flows into the stationary flow path 20 without the carry-over flow flowing into the 20 at the same time. Generation of noise can be suppressed.

  On the other hand, on the discharge side of the stationary flow path 20, the pressurized fluid collides with the discharge side end face 34 of the discharge side guide 33 and a pressure fluctuation occurs. The pressure fluctuation is small and the generation of noise is small. Accordingly, even if the discharge side guide 33 is partially covered as shown in the figure without covering the entire discharge port 24, noise generation from the discharge side does not increase.

  The suction side guide 31 is provided so as to partially cover the suction port 23 and the suction side end surface 32 is provided across the suction port 23, and the discharge side guide 33 is provided so as to partially cover the discharge port 24. Is provided at a position crossing the discharge port 24, so that the circumferential length of the partition wall 25 including the suction side guide 31 and the discharge side guide 33 can be reduced between the suction side guide 31 and the discharge side guide 33 with the suction port 23. It becomes shorter than the case where each of the outlets 24 is entirely covered. The minimum length in the circumferential direction of the partition wall 25 is set by a length that prevents pressure leakage between the suction port 23 and the discharge port 24, and is usually a length corresponding to the circumferential interval of three blades. It is considered that pressure leakage can be prevented by setting the partition wall 25 in the wall. If the number of blades 18 is increased, the circumferential length of the partition wall 25 can be shortened. However, generally, increasing the number of blades tends to lower the aerodynamic performance. There is a limit to shortening the direction length. In the vortex blower of the present invention, by making the circumferential length of the partition wall 25 correspond to the interval of three blades, the sealing performance between the suction port 23 and the discharge port 24 without deteriorating the aerodynamic characteristics. To ensure.

  In this way, the suction side guide 31 is partially covered without covering all of the suction ports 23, and the discharge side guide 33 is also partially covered without covering all of the discharge ports 24. Each of the suction side guide 31 and the discharge side guide 33 can be easily shaped or manufactured integrally with the casing 11 by casting or die casting. As a result, the vortex blower can be manufactured with a small number of parts and a small number of steps, without separating the partition and the guide from the conventional parts. However, the partition wall 25 and the casing 11 may be separate parts.

  If the suction side guide 31 covers the entire suction port 23 and the discharge side guide 33 covers the entire discharge port 24 as in the prior art, the suction side end face 41 as shown by a two-dot chain line in FIG. And the discharge side end face 42 are largely displaced from the suction side end face 32 and the discharge side end face 34 of the present invention, respectively. The conventional suction side end surface 41 is inclined so that the blade 18 passes through the end surface from the inner peripheral side, the discharge side end surface 42 has a radial portion and an inclined portion, and the blade 18 It passes through the end face from the peripheral side. As described above, conventionally, the suction port 23 and the discharge port 24 are entirely covered with the guide so as to suppress noise generation. However, when the carry-over flow is opened to the suction side, the impeller is moved from the suction port to the impeller. This hinders the flow that flows between the blades and reduces the pressure loss of the vortex blower. In addition, since the low-pressure inflow from the suction port and the high-pressure carry-over flow are mixed, a sudden pressure change occurs in the mixing section, and the noise of wind noise is amplified by pressure pulsation.

  On the other hand, when the expansion space 35 is provided in the suction side guide 31, the portion of the carry-over flow that is transferred to the outer peripheral portion side of the suction side guide 31 is in the expansion space 35 provided in the outer peripheral portion of the suction side guide 31. After entering, expanding and depressurizing, the outer peripheral portion of the stationary flow path 20 flows in the circumferential direction. On the other hand, the inflow air that has flowed into the suction port 23 from the outside flows into the static flow channel 20 and flows into the inner peripheral side of the static flow channel 20, and the carry-over flow on the outer peripheral side is reduced in pressure. Since it mixes with the inflow air from the suction inlet 23, the pressure pulsation at the time of mixing becomes small, and the wind noise which is the noise generated in the suction inlet 23 side is reduced.

  In addition, the air flowing in from the suction port 23 is immediately pressurized by the impeller 15, and the length of the stationary flow path 20 facing the impeller 15 is increased, so that the discharge performance can be improved, and the discharge Noise generation from the vortex blower is suppressed while maintaining the performance, and a quiet vortex blower can be obtained.

  As mentioned above, the invention made by the present inventor has been specifically described based on the embodiment. However, the present invention is not limited to the embodiment, and various modifications can be made without departing from the scope of the invention. Needless to say.

DESCRIPTION OF SYMBOLS 11 Casing 11a Annular part 11b Bending part 12 Electric motor 13 Rotating shaft 15 Impeller 16 Shroud 17 Annular groove 17a Centrifugal groove 18 Blade 20 Static flow path 21 Suction flow path 22 Discharge flow path 23 Suction port 24 Discharge port 25 Bulkhead 31 Suction side guide 32 Suction side end surface 33 Discharge side guide 34 Discharge side end surface 35 Expansion space 36 Thin wall portion 38 Circumferential step surface 39 Radial step surface 40 Partition portion

Claims (7)

A casing provided with a stationary flow path extending in an arc shape between a suction port on one end side and a discharge port on the other end side, and an annular groove facing the stationary flow path is provided and is rotatably mounted on the casing. A vortex blower having blades that are three-dimensionally curved in an axial direction and a circumferential direction, and an impeller provided at predetermined intervals in the circumferential direction across the annular groove,
Partitioning between both ends of the static flow path and facing the blade via a gap provided in the casing,
A suction side guide having a suction side end surface extending in a direction crossing the suction port, protruding in a circumferential direction in front of the suction port and partially covering the suction port, integrally provided in the partition;
An eddy current is formed on the outer peripheral side of the suction side guide by the blade, wherein an expansion space is formed on the outer peripheral side of the blade to reduce the carry-over flow that flows along the partition wall from the discharge port side to the suction port side. Blower.   2. The vortex blower according to claim 1, wherein a gap between the suction side guide and the blade in the expansion space is set larger than a gap between the partition wall and the blade.   3. The vortex blower according to claim 1, wherein the expansion space is provided at a position facing the suction port through the suction side guide. 4.   The vortex blower according to any one of claims 1 to 3, wherein the suction side of the radially inward portion of the stationary flow path extends in a circumferential direction at a radial center with respect to the stationary flow path. A vortex blower characterized in that the suction side guide is provided with a partition portion extending in a circumferential direction from an end face.   The vortex blower according to any one of claims 1 to 4, wherein the suction side end face of the radially inner portion of the stationary flow path is inclined in a rotation direction.   The vortex blower according to any one of claims 1 to 5, further comprising: a discharge side end surface extending in a direction crossing the discharge port, and protruding in a circumferential direction in front of the discharge port, wherein the discharge port is partially An eddy current blower comprising a discharge side guide for covering the partition wall.   The vortex blower according to claim 6, wherein the suction side guide, the discharge side guide, and the partition are integrally provided in the casing.

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