WO2004109120A1 - Soufflante centrifuge - Google Patents

Soufflante centrifuge Download PDF

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Publication number
WO2004109120A1
WO2004109120A1 PCT/JP2003/015060 JP0315060W WO2004109120A1 WO 2004109120 A1 WO2004109120 A1 WO 2004109120A1 JP 0315060 W JP0315060 W JP 0315060W WO 2004109120 A1 WO2004109120 A1 WO 2004109120A1
Authority
WO
WIPO (PCT)
Prior art keywords
centrifugal blower
discharge
impeller
casing
discharge port
Prior art date
Application number
PCT/JP2003/015060
Other languages
English (en)
Japanese (ja)
Inventor
Masahiro Murakawa
Eiji Asayama
Original Assignee
Seikow Chemical Engineering & Machinery, Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Seikow Chemical Engineering & Machinery, Ltd. filed Critical Seikow Chemical Engineering & Machinery, Ltd.
Publication of WO2004109120A1 publication Critical patent/WO2004109120A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps

Definitions

  • the present invention relates to a core blower provided with a spiral casing used for air-conditioning equipment or ventilation equipment. [ ⁇ . Technology]
  • the figure is a longitudinal sectional view showing the structure of a blower having a conventional spiral-shaped casing.
  • the casing 10 and the impeller 11 built in the non-winding chamber of the casing 10 are tough.
  • An axial centerline 12 of the discharge P10a of the casing 10 and an axial line of the same direction as the axial direction of the discharge P10a passing through the axis of the impeller 11 (hereinafter referred to as
  • the center line 5) CL1 is parallel to and separated by a predetermined distance.
  • the flow of the fluid flowing on the outer peripheral side is faster than the flow of the fluid flowing on the inner peripheral side. Therefore, when the bending direction of the pipe connected to the discharge port 10a is the same as the rotation direction of the impeller 11, the fluid flows along the bending of the pipe, causing a large pressure loss. However, if the direction of the pipe bending is opposite to the direction of rotation of the impeller 11, the fluid in the fast flowing portion will affect the pipe, causing a large pressure loss at the pipe bending. Occurs. As a result, there is a problem that a predetermined air volume cannot be obtained.
  • the casing 10 is mounted on a base 14 of a centrifugal blower 200 together with a motor 15 for driving the impeller 11.
  • a motor 15 for driving the impeller 11 In the case where the rotation direction of the impeller 11 is the same and only the fluid discharge direction 13 is changed, as shown in FIGS. 6A, 6C and 6E, the same casing is used.
  • the base 1 is positioned so that the center line 1 2 of the discharge port 10 a substantially coincides with the discharge direction 13 (upper, left, and right in the figure) of each fluid. 4 above.
  • the shape of the part to be attached to the base 14 of the casing 10 is different from each other, it is necessary to prepare three types of bases 14 corresponding to the fluid discharge direction 13.
  • the same casing 10 forms the discharge port 10a.
  • the fluid is installed on the base 14 so that the axial center line 12 of each of them substantially coincides with the discharge direction 13 (upper, left, and right in the figure) of each fluid. Also in this case, similarly to the above, it is necessary to prepare three types of bases 14 respectively.
  • the casing 10 of the conventional centrifugal blower 200 shown by a two-dot chain line is moved to the axial center line of the discharge port 10a.
  • 1 2 is arranged on the base 14 so as to approach the first center line CL 1 of the impeller 11.
  • the discharge port of the casing 10 is arranged such that the axial center line 12 of the discharge port 10 a of the casing 10 coincides with the first center line CL 1 of the impeller 11.
  • Elbow joint 16 is attached to 10a.
  • the elbow joint 1 The axial center line 12 a of the newly formed discharge port 16 a at the end of 6 coincides with the first center line CL 1 of the impeller 11.
  • the elbow joint 16 is newly attached to the discharge P10a of the casing 10, so that the casing
  • the centrifugal blower 20 1 disclosed in Japanese Patent Application Laid-Open No. Hei 11-92493 is disclosed. Then, as shown in Fig. 7B, the casing 10 has an axial centerline 12 of the discharge P10a and a first centerline C of the impeller 11 as shown in Fig. 7B.
  • a portion 17 near the discharge P10a of the casing 10 is cut away so as to approach L1 and face in the same direction.
  • the elbow joint 16 is not attached to the discharge port 10a of the casing 10, and the axial centerline 12a of the newly formed discharge port 10b is formed. Approaches the first center line CL 1 of the impeller 11 and faces in the same direction.
  • the size of the centrifugal blower 201 does not increase.
  • the length of the diffuser section 18 of the core blower 201 becomes shorter, the flow velocity in this section 18 cannot be sufficiently reduced.
  • the air flow-static pressure curve L2 of the conventional centrifugal blower is different from the air flow-static pressure curve L2 of the centrifugal blower shown in FIG. 7B. , Shift in the direction where the static pressure decreases for the same air volume As a result, there is a problem that a predetermined air flow cannot be obtained at a predetermined static pressure.
  • An object of the present invention is to provide a centrifugal blower that can reduce the number of types compared to a blower, and a centrifugal blower having a blade built in a spiral casing and a blower.
  • the discharge passage is provided so that the axial center line of the discharge port passes through the axis of the impeller, and the discharge port of the discharge passage is directed toward the flow path.
  • a deceleration portion formed so as to be curved outward so that the flow path is gradually expanded along the discharge direction, and for decelerating a body flowing therethrough efficiently.
  • the fluid flowing quickly can approach the vicinity of the center, and the fluid flowing therethrough can be efficiently decelerated. It can be done. Therefore, even if the pipe that is connected to the discharge passage is bent in the same direction as the rotation direction of the impeller or in the opposite direction, it is difficult for fluid to be separated at this bent portion. In other words, a large pressure loss does not occur, so that the performance of the blower is degraded, and the direction of the wind impeller is changed from the conventional two types to one type. I can do it
  • the deceleration portions may be formed on both sides of the impeller near the discharge port in the discharge passage in the axial direction and in the same direction as the
  • the inner surfaces on both sides in the radial direction of the impeller near the discharge port of the discharge passage of the core blower are formed along the shape of the casing. ⁇ -There is no large pressure loss in the area.
  • the inner surfaces on both sides in the axial direction of the impeller near the discharge P of the discharge passage of the blower have the same width dimension as the axial direction of the impeller in the discharge port of the discharge passage of the blower. Since the width of the casing is larger than the width in the same direction as the axial direction of the impeller, the separation distance on the inner surface is formed so as to gradually increase toward the discharge port.
  • the flowing fluid may cause separation or the like from the inner surface of the discharge passage, which may cause a large pressure loss. Therefore, in the present invention, in order to prevent this, a speed reduction portion is provided at a portion to reduce the pressure. o As a result, it is possible to prevent an increase in pressure loss, thereby preventing a decrease in the performance of the core blower.
  • the radius of curvature of the curved portion is equal to the discharge radius of the discharge passage.
  • the inner diameter of P is formed to be 5 to 20% of the inner diameter of P. According to this configuration, the fluid flowing in the discharge passage of the core blower is efficiently decelerated at the deceleration part. This prevents an increase in pressure loss.
  • the radius of curvature of the curved part of the reduced part is less than 5% of the inner diameter of the discharge outlet of the discharge passage, it is possible to prevent the deterioration of the performance of the core blower. If the deceleration part is too short to efficiently decelerate the fluid, or if the radius of curvature of the curved part of the deceleration part exceeds 20% of the inner diameter of the discharge P in the discharge path, , The singing is large.
  • FIG. 1A is a longitudinal sectional view showing a basic configuration example of a centrifugal blower according to one embodiment of the present invention.
  • FIG. 1B is a plan view showing a basic configuration example of a centrifugal blower according to one embodiment of the present invention.
  • FIG. 1C is a partial cross-sectional view taken along line AA of the discharge passage for the centrifugal blower shown in FIG. 1B.
  • FIG. 2A is a partial cross-sectional view taken along line X1-X1 in FIG. 1B.
  • FIG. 2C is a partial sectional view taken along line AA of FIG. 1B.
  • FIG. 2D is a partial sectional view taken along line X3-X3 in FIG. 1B.
  • FIG. 2E is a partial sectional view taken along line X4-X4 in FIG. 1B.
  • FIG. 3 is a graph showing the relationship between the air volume of the centrifugal blower and the static pressure.
  • FIG. 4A is a front view of a completed centrifugal blower according to one embodiment of the present invention, and shows a configuration example in a case where a fluid discharge direction is vertically upward.
  • FIG. 4B is a front view of a completed centrifugal blower according to one embodiment of the present invention, and shows a configuration example in a case where a fluid discharge direction is rightward.
  • FIG. 4C is a front view of a completed centrifugal blower according to one embodiment of the present invention, and shows a configuration example in a case where a fluid discharge direction is a left direction.
  • FIG. 5 is a longitudinal sectional view showing the configuration of a conventional centrifugal blower provided with a spiral casing.
  • FIG. 6A is a longitudinal sectional view of a completed product of a conventional centrifugal blower, showing an example of a configuration in a case where a fluid discharge direction is vertically upward and a rotation direction of an impeller is counterclockwise.
  • FIG. 6B is a longitudinal sectional view of a completed product of the conventional centrifugal blower, and shows a configuration example in a case where the fluid discharge direction is vertically upward and the rotation direction of the impeller is clockwise.
  • FIG. 6C is a longitudinal sectional view of a completed product of the conventional centrifugal blower, showing an example of a configuration in which the fluid discharge direction is left and the impeller rotation direction is counterclockwise.
  • FIG. 6D is a longitudinal sectional view of a completed product of a conventional centrifugal blower, showing an example of a configuration in which the fluid discharge direction is left and the impeller rotation direction is clockwise.
  • FIG. 6E is a longitudinal sectional view of a completed product of a conventional centrifugal blower, showing an example of a configuration in which the fluid discharge direction is rightward and the impeller rotation direction is counterclockwise.
  • FIG. 6F is a longitudinal sectional view of a completed product of a conventional centrifugal blower, showing an example of a configuration in which the fluid discharge direction is rightward and the impeller rotation direction is clockwise.
  • FIG. 7A shows the base of the conventional centrifugal blower casing shown in Fig. 5 so that the axial center line of the discharge port passes through the axis of the impeller and approaches the center line in the same direction as the axial direction of the discharge port.
  • FIG. 7 is a vertical sectional view of another centrifugal blower in which a centrifugal blower is placed and an elbow joint is attached to a discharge port.
  • Fig. 7B shows the base of the conventional centrifugal blower casing shown in Fig. 5 so that the axial center line of the discharge port passes through the axis of the impeller and approaches the center line in the same direction as the axial direction of the discharge port.
  • FIG. 7 is a vertical cross-sectional view of another centrifugal blower in which a portion near a discharge port of a casing is cut off and is cut off.
  • FIG. 8 is a graph showing the relationship between the air volume and the static pressure of a conventional centrifugal blower.
  • the centrifugal blower 100 includes a spiral casing 1 and an impeller 2 installed in a spiral chamber 1 a of the casing 1.
  • the casing 1 is provided with a discharge passage lb formed so that the flow path expands from the outlet of the spiral chamber 1a.
  • the cross section of the spiral chamber 1a has a substantially rectangular shape, and the cross section gradually changes from the spiral chamber 1a to a circular shape through the discharge passage 1b.
  • the discharge port 1c of the discharge passage 1b has a circular shape.
  • the axial center line 3 of the discharge port 1 c is substantially the same as the center line CL 1 through the axis of the impeller 2 and in the same direction as the axial direction of the discharge port 1 c. They match. That is, the axial center line 3 passes through the axis of the impeller 2.
  • the discharge passage 1b is shown in FIG. 1C.
  • the speed reducing portion 4 for efficiently decelerating the fluid flowing inside and the width direction of the casing 1 in the axial direction of the discharge passage 1b (the same direction as the axial direction of the impeller 2).
  • An inclined portion 5 formed by enlarging at a spread angle ⁇ 1, and a radius of curvature 2 R inward in the radial direction for connecting the inclined portion 5 and the reduction portion 4.
  • a communication portion 6 formed by bending.
  • the spreading angle ⁇ 1 of the inclined portion 5 is set in advance so that the fluid does not separate in the inclined portion 5.
  • the radius of curvature of the curved deceleration section 4 is XI—XI, X2—X2, A—A, X3—X3, X3 in FIG.
  • the radius of curvature R of the reduction portion 4 is set to be equal to the discharge port of the discharge passage 1b.
  • the speed reduction unit 4 is too short to efficiently reduce the fluid. If the radius of curvature R of the reduction section 4 exceeds 20% of the inner diameter D of the discharge port 1c, In addition, the axial height H 2 of the speed reduction unit 4 is set to 0.05 D 0.2 D in accordance with the radius of curvature R of the speed reduction unit.
  • the curve of the deceleration section 4 is actually set in advance by experiment, etc., taking into account the air volume of the blower, the type of fluid to be blown, and the like.
  • H can be set to, for example, 1.5 times or less the inner diameter D of the discharge 1C.
  • the casing 1 of the centrifugal blower 100 according to the present embodiment can be more connected than the conventional case.
  • the inside diameter D of the discharge P 1 C is changed to the inside diameter D of the suction P 8 of the casing 1.
  • the force S that makes the axial centerline 3 of the discharge ⁇ 1c of the discharge passage 1b of the casing 1 coincide with the first centerline CL1 of the impeller 2 is applied to the discharge port 1c.
  • it may be set so as to substantially coincide with the second center line CL 2 of the impeller 2.
  • the centrifugal blower 100 includes a spiral casing 1 and an impeller 2 installed in a spiral chamber 1 a of the casing 1. Axial direction of discharge port 1 c of discharge passage lb of casing 1 W
  • Radius of curvature R of deceleration part 4 0.07D, deceleration part
  • the center line in the same direction as the axial direction of the discharge port 10 a (hereinafter referred to as the vertical center line) CL 1 is in parallel with a predetermined distance, does not have the above-mentioned deceleration section 4, and discharge port 1 of casing 10.
  • the comparative example 2 is different from the embodiment in that the comparative example 2 does not include the deceleration device 4. Therefore, as shown by the two-dot chain line in FIG. 1C, the spreading angle ⁇ 1 of the discharge
  • the centrifugal blower of the present embodiment needs to prepare many types in accordance with the arrangement of the pipes which make the discharge P10a like the centrifugal blower of Comparative Example 1 as described above. There is no. Specifically, as shown in Fig. 4 AC, the number of finished products of the core blower of this embodiment can be reduced from the conventional six types to three types.
  • centrifugal blower which concerns on this invention, types can be reduced compared with the conventional centrifugal blower, without deteriorating performance.
  • the centrifugal blower according to the present invention is useful as a centrifugal blower having high productivity and easy inventory management.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne une soufflante centrifuge (100) permettant un moins grand nombre de types que celui des soufflantes centrifuges sans réduire leurs performances. Une tête de pompe (2) est incluse dans une enveloppe volute (1). L'enveloppe (1) renferme un passage de délivrance (1b) qui est formé de telle manière que la ligne centrale axiale (3) de l'orifice de délivrance (1c) de l'enveloppe (1) passe par l'axe de la tête de pompe (2) et une section réductrice de vitesse (4) qui est formée dans le passage de délivrance (1b), dans la forme incurvée à l'extérieur, à proximité de l'orifice de délivrance (1c) de telle manière que le passage d'écoulement puisse graduellement diverger dans la direction de délivrance du fluide pour réduire efficacement la vitesse du fluide s'écoulant dans le passage d'écoulement.
PCT/JP2003/015060 2003-06-05 2003-11-26 Soufflante centrifuge WO2004109120A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2003-160153 2003-06-05
JP2003160153A JP4590167B2 (ja) 2003-06-05 2003-06-05 遠心送風機

Publications (1)

Publication Number Publication Date
WO2004109120A1 true WO2004109120A1 (fr) 2004-12-16

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2003/015060 WO2004109120A1 (fr) 2003-06-05 2003-11-26 Soufflante centrifuge

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JP (1) JP4590167B2 (fr)
CN (1) CN100404878C (fr)
TW (1) TWI253491B (fr)
WO (1) WO2004109120A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104420431B (zh) * 2013-08-28 2016-08-10 苏州宝时得电动工具有限公司 吹风装置
CA3139766C (fr) 2019-10-17 2023-10-31 Zhongshan Broad-Ocean Motor Co., Ltd. Ensemble volute et ventilateur a tirage induit l'utilisant
CN211082385U (zh) * 2019-10-17 2020-07-24 中山大洋电机股份有限公司 一种蜗壳组件及其应用的引风机
WO2022024267A1 (fr) * 2020-07-29 2022-02-03 三菱電機株式会社 Carter spiralé de soufflante centrifuge, soufflante centrifuge dotée d'un carter spiralé, climatiseur et dispositif de circuit de réfrigération

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5313610U (fr) * 1976-07-19 1978-02-04
JPH03217699A (ja) * 1990-01-23 1991-09-25 Nissan Motor Co Ltd 圧縮機のスクロール構造

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB733533A (en) * 1952-08-26 1955-07-13 Establissements Neu Sa Des Improvements in or relating to centrifugal blowers, compressors, pumps and the like
US3860360A (en) * 1973-09-04 1975-01-14 Gen Motors Corp Diffuser for a centrifugal compressor
JPS5529381Y2 (fr) * 1976-01-19 1980-07-12
JPS59131799A (ja) * 1983-12-19 1984-07-28 Hitachi Ltd 遠心形流体機械のケ−シング
DE50011843D1 (de) * 1999-06-14 2006-01-19 Waertsilae Schweiz Ag Winterth Aufladegruppe für einen Grossdieselmotor
JP2001193682A (ja) * 2000-01-06 2001-07-17 Ebara Corp ボルテックス形ポンプ

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5313610U (fr) * 1976-07-19 1978-02-04
JPH03217699A (ja) * 1990-01-23 1991-09-25 Nissan Motor Co Ltd 圧縮機のスクロール構造

Also Published As

Publication number Publication date
TW200427930A (en) 2004-12-16
JP4590167B2 (ja) 2010-12-01
CN1788168A (zh) 2006-06-14
JP2004360579A (ja) 2004-12-24
TWI253491B (en) 2006-04-21
CN100404878C (zh) 2008-07-23

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