WO2017018405A1 - ポンプ - Google Patents

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Publication number
WO2017018405A1
WO2017018405A1 PCT/JP2016/071819 JP2016071819W WO2017018405A1 WO 2017018405 A1 WO2017018405 A1 WO 2017018405A1 JP 2016071819 W JP2016071819 W JP 2016071819W WO 2017018405 A1 WO2017018405 A1 WO 2017018405A1
Authority
WO
WIPO (PCT)
Prior art keywords
casing
flange
mating surface
seal member
recesses
Prior art date
Application number
PCT/JP2016/071819
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
考之 宮本
守彦 小中原
道子 杉山
雄次郎 山田
Original Assignee
株式会社 荏原製作所
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 株式会社 荏原製作所 filed Critical 株式会社 荏原製作所
Priority to CN201680044167.5A priority Critical patent/CN107850079B/zh
Publication of WO2017018405A1 publication Critical patent/WO2017018405A1/ja

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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
    • F04D29/08—Sealings
    • 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
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/10—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing

Definitions

  • the present invention relates to a pump for transferring a fluid.
  • a pump for transferring a fluid such as liquid or gas includes an impeller, a rotating shaft to which the impeller is fixed, and a casing that houses the impeller and forms a fluid flow path.
  • the impeller rotates in the casing to increase the pressure of the fluid in the casing, and the pressurized fluid is discharged from the casing to the outside through the discharge port.
  • a split-structure casing consisting of an upper casing and a lower casing.
  • a sealing structure for sealing a gap between these two upper and lower casings a technique for sealing the gap by sandwiching a sealing member such as a string-like seal member or an O-ring between the mating surfaces of the upper and lower casings is known. .
  • the conventional technique using such a seal member has the following problems.
  • an object of the present invention is to provide a pump having a seal structure that can reliably prevent fluid leakage with a simple structure.
  • one aspect of the present invention includes a rotating shaft, an impeller fixed to the rotating shaft, an upper casing and a lower casing that house the impeller, the upper casing, and the lower casing.
  • a sealing member sandwiched between the casing, and the upper casing and the lower casing each include an upper flange and a lower flange having mating surfaces sandwiching the sealing member, and the upper flange and the lower flange.
  • the plurality of recesses are located on the outer peripheral side of the mating surface of the upper flange. In a preferred aspect of the present invention, the plurality of recesses are arranged over the entire circumference of the mating surface of the upper flange.
  • the fastening hole formed in the upper flange extends through a region between two adjacent recesses of the mating surface of the upper flange. To do.
  • the fastening hole formed in the upper flange is a through hole without a thread groove, and the fastener is screwed into the fastening hole formed in the lower flange. It is a screw hole.
  • the seal member is a gasket.
  • Another aspect of the present invention is sandwiched between a rotating shaft, an impeller fixed to the rotating shaft, an upper casing and a lower casing that house the impeller, and the upper casing and the lower casing.
  • the upper casing and the lower casing each include an upper flange and a lower flange having mating surfaces sandwiching the seal member, and the upper flange and the lower flange include the upper casing and the lower flange, respectively.
  • a plurality of fastening holes into which a plurality of fasteners for fastening the lower casing are inserted are formed, and a plurality of recesses are formed on the mating surface of the lower flange. It is a pump.
  • the plurality of recesses are positioned on the outer peripheral side of the mating surface of the lower flange. In a preferred aspect of the present invention, the plurality of recesses are arranged over the entire circumference of the mating surface of the lower flange.
  • the fastening hole formed in the lower flange extends through a region between the two adjacent recesses of the mating surface of the lower flange. To do.
  • the fastening hole formed in the lower flange is a through hole without a thread groove, and the fastener is screwed into the fastening hole formed in the upper flange. It is a screw hole.
  • the seal member is a gasket.
  • the contact area between the mating surface and the seal member can be reduced, and as a result, the mating surface and the seal The contact pressure with the member can be increased. Therefore, the seal member can reliably prevent fluid leakage.
  • FIG. 1 It is a perspective view which shows the both suction centrifugal pump which concerns on one Embodiment of this invention. It is the figure which looked at the lower casing of both suction centrifugal pumps from the top. It is the figure which looked at the upper casing of both suction vortex pumps from the bottom. It is a figure which shows the sealing member pinched
  • FIG. 1 is a perspective view showing a double suction centrifugal pump according to an embodiment of the present invention.
  • Both suction centrifugal pumps of this embodiment include a casing 3 having an upper and lower split structure having an upper casing 3a and a lower casing 3b.
  • FIG. 2 is a view of the lower casing 3b of both suction spiral pumps as viewed from above
  • FIG. 3 is a view of the upper casing 3a of both suction spiral pumps as viewed from below.
  • the double suction centrifugal pump includes a rotary shaft 1, a double suction impeller 2 fixed to the rotary shaft 1, and a casing 3 that houses the impeller 2 and forms a fluid flow path.
  • the casing 3 has a spiral shape. Examples of the fluid include liquids such as water and oil, and gases such as air.
  • the casing 3 includes the upper casing 3a and the lower casing 3b.
  • the upper casing 3 a and the lower casing 3 b are aligned with each other on a horizontal plane that passes through the central axis of the rotary shaft 1.
  • the rotating shaft 1 is supported by a shaft support portion 40 formed in the upper casing 3a and the lower casing 3b. A gap between the rotary shaft 1 and the shaft support portion 40 is sealed by the shaft seal portion 11.
  • the lower casing 3b is formed with a suction port 6 for sucking fluid and a discharge port 7 for discharging the fluid pressurized in the casing 3.
  • the suction port 6 and the discharge port 7 open in directions opposite to each other in a direction orthogonal to the rotation shaft 1.
  • suction chambers 4, 4 located on both sides of the impeller 2 and a discharge chamber 5 located in the center of the casing 3 are formed inside the casing 3.
  • the discharge chamber 5 is formed between the suction chambers 4 and 4, and the discharge chamber 5 communicates with the suction chambers 4 and 4.
  • the impeller 2 is disposed in the discharge chamber 5.
  • the suction chambers 4, 4 communicate with the suction port 6, and the discharge chamber 5 communicates with the discharge port 7.
  • a driving device (not shown) is connected to the end of the rotating shaft 1.
  • the fluid is sucked into the casing 3 through the suction port 6.
  • the fluid passes through the suction chambers 4 and 4 and flows into the impeller 2 in the discharge chamber 5.
  • the fluid is pressurized by the action of the rotating impeller 2 and centrifugal force, and discharged to the discharge chamber 5.
  • the fluid is further pressurized while flowing through the spiral discharge chamber 5 and discharged from the discharge port 7.
  • the upper casing 3a is provided with an upper flange 8 projecting outward from its lower end
  • the lower casing 3b is provided with a lower flange 9 projecting outward from its upper end.
  • the upper flange 8 and the lower flange 9 have a mating surface 21 and a mating surface 20 that face each other.
  • the mating surface 21 of the upper flange 8 and the mating surface 20 of the lower flange 9 have the same shape.
  • a plurality of recesses 14 are formed on the mating surface 21 of the upper flange 8. These recesses 14 are located on the outer peripheral side of the mating surface 21. More specifically, the recessed portions 14 are formed along the outer peripheral surface 8a of the upper flange 8, and each recessed portion 14 extends to the outer peripheral surface 8a. These recesses 14 are arranged at equal intervals over the entire circumference of the mating surface 21 of the upper flange 8.
  • the upper flange 8 has a plurality of through holes 16 without thread grooves
  • the lower flange 9 has a screw hole (female screw) into which a plurality of screws 10 (see FIG. 1) as fasteners are screwed. 17 is formed.
  • the through hole 16 extends through a region of the mating surface 21 between two adjacent recesses 14. The positions of the through holes 16 correspond to the positions of the screw holes 17. In the example shown in FIG. 3, the distance A between the through holes 16 adjacent to each other is about 10 cm.
  • the plurality of through holes 16 are formed at equal intervals along the circumferential direction of the upper flange 8, and the plurality of screw holes 17 are formed at equal intervals along the circumferential direction of the lower flange 9.
  • the through hole 16 and the screw hole 17 are collectively referred to as a fastening hole.
  • the screw 10 is inserted into the through hole 16 and further screwed into the screw hole 17, whereby the upper casing 3a and the lower casing 3b are fastened together.
  • the recess 14 is formed on the mating surface 21 of the upper flange 8 in which the through hole 16 is formed. This is because if the recess 14 is formed on the mating surface 20 of the lower flange 9, the length of the screw hole 17 is shortened by the depth of the recess 14, and the fastening force of the screw 10 is reduced.
  • the recess 14 is It may be formed on either the mating surface 21 of the flange 8 or the mating surface 20 of the lower flange 9.
  • the upper flange 8 and the lower flange 9 are fastened by the screw 10 in a state where the seal member 22 is sandwiched between the mating surface 21 of the upper flange 8 and the mating surface 20 of the lower flange 9.
  • the seal member 22 is divided into a suction side seal member 22A and a discharge side seal member 22B.
  • the seal member 22 is a plate-like gasket made of an elastic material such as rubber.
  • a plurality of holes 25 through which the screw 10 passes are formed in the seal member 22. The positions of these holes 25 correspond to the positions of the through holes 16 and the screw holes 17.
  • the seal member 22 is disposed between the mating surface 20 and the mating surface 21.
  • the screw 10 is inserted into the through hole 16 and the hole 25 and screwed into the screw hole 17.
  • the upper flange 8 and the lower flange 9 are fastened to each other by a screw 10 with a seal member 22 sandwiched therebetween.
  • the recess 14 may be formed when the upper casing 3a is manufactured by casting, or the recess 14 may be formed by a machine tool after manufacturing the upper casing 3a.
  • FIG. 5 is a side view of the double suction centrifugal pump according to the present embodiment.
  • FIG. 6 is an enlarged view of region A shown in FIG. A sealing member 22 is sandwiched between the mating surface 20 and the mating surface 21.
  • the thickness of the upper flange 8 and the lower flange 9 is about 40 mm
  • the thickness of the seal member 22 is about 1 mm
  • the depth of the recess 14 is about 0.15 mm.
  • the depth of the recessed portion 14 and the thickness of the seal member 22 are exaggerated for easy understanding of the drawing.
  • the seal member 22 can reliably prevent fluid leakage.
  • the plurality of recesses 14 are spaced apart from each other and arranged over the entire circumference of the mating surface 21. If a plurality of recesses 14 are connected to each other and arranged, when the upper casing 3a and the lower casing 3b are fastened to each other, a bending moment acts on the upper casing 3a by the fastening force of the screw 10, and the upper flange 8 It will be deformed. As a result, a gap is formed between the seal member 22 and the mating surfaces 20 and 21, and fluid may leak from the gap.
  • the region existing between the two adjacent recesses 14 on the mating surface 21 of the upper flange 8 is the seal member 22. Is supported by the mating surface 20 of the lower flange 9. Therefore, even when the screw 10 is tightened, the upper flange 8 is not deformed, and the sealing member 22 can sufficiently exhibit its sealing function. According to the present embodiment, a highly reliable sealing performance can be achieved with a simple structure in which the plurality of recesses 14 are formed on the mating surface 21 of the upper flange 8.
  • the present invention has a simple configuration in which the seal member 22 is simply sandwiched between the mating surface 20 and the mating surface 21, so that the workability is better than using a string-like seal member, Costs can be reduced compared to using an O-ring.
  • a plurality of recesses 14 may be formed on the mating surface 21 so that the through holes 16 pass only through the recesses 14. Even in this case, it is possible to increase the contact pressure between the mating surfaces 20 and 21 and the seal member 22, but in order to prevent the deformation of the upper flange 8 when the screw 10 is tightened, the embodiment shown in FIG. Form is preferred.
  • FIG. 7 is a view of the lower casing 3b of the double suction centrifugal pump according to another embodiment as viewed from above.
  • FIG. 8 is a view of the upper casing 3a of both suction centrifugal pumps as viewed from below.
  • a screw hole (female screw) 17 into which a plurality of screws 10 (see FIG. 1) as fasteners are screwed is formed in the upper flange 8, and a plurality of through holes 16 without a screw groove are provided on the bottom.
  • a flange 9 is formed.
  • a plurality of recessed portions 14 are formed on the mating surface 20 of the lower flange 9. These recesses 14 are located on the outer peripheral side of the mating surface 20. More specifically, the recess 14 is formed along the outer peripheral surface 9a of the lower flange 9, and each recess 14 extends to the outer peripheral surface 9a. These recessed portions 14 are arranged at equal intervals over the entire circumference of the mating surface 20 of the lower flange 9. The through hole 16 extends through a region of the mating surface 20 of the lower flange 9 between two adjacent recesses 14.
  • the plurality of recesses 14 may be formed on both the mating surface 21 of the upper flange 8 and the mating surface 20 of the lower flange 9.
  • the present invention can also be applied to a single suction pump. That is, the present invention can be applied to any pump having a casing divided into two.
  • Other examples of the pump to which the present invention is applied include an axial flow pump and a horizontal shaft diagonal flow pump.
  • the present invention can be used for a pump for transferring a fluid.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Gasket Seals (AREA)
PCT/JP2016/071819 2015-07-27 2016-07-26 ポンプ WO2017018405A1 (ja)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201680044167.5A CN107850079B (zh) 2015-07-27 2016-07-26 泵

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015147907A JP6625360B2 (ja) 2015-07-27 2015-07-27 ポンプ
JP2015-147907 2015-07-27

Publications (1)

Publication Number Publication Date
WO2017018405A1 true WO2017018405A1 (ja) 2017-02-02

Family

ID=57884427

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2016/071819 WO2017018405A1 (ja) 2015-07-27 2016-07-26 ポンプ

Country Status (3)

Country Link
JP (1) JP6625360B2 (zh)
CN (1) CN107850079B (zh)
WO (1) WO2017018405A1 (zh)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7213141B2 (ja) * 2018-06-22 2023-01-26 株式会社荏原製作所 両吸込渦巻ポンプ
TWI715192B (zh) * 2019-09-12 2021-01-01 建準電機工業股份有限公司 流體輸送裝置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS623989U (zh) * 1985-06-24 1987-01-10
JPH11230444A (ja) * 1998-02-18 1999-08-27 Mesco Inc 送水用パイプの接合構造
JP2014134162A (ja) * 2013-01-11 2014-07-24 Hitachi Ltd 両吸込渦巻ポンプ

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3652180A (en) * 1970-07-13 1972-03-28 Wilfley & Sons Inc A Centrifugal pump and seal means therefore
CN201031798Y (zh) * 2007-04-02 2008-03-05 山东省章丘鼓风机厂有限公司 一种自冷却耐磨无泄漏双吸泵
CN101408188A (zh) * 2008-11-21 2009-04-15 江苏国泉泵业制造有限公司 一种带副叶轮密封的双吸泵
CN101865049A (zh) * 2010-05-21 2010-10-20 隆鑫工业有限公司 曲轴箱合箱面密封结构
CN103133415A (zh) * 2011-11-22 2013-06-05 上海连成（集团）有限公司 一种新型便于减轻腔清砂的双吸泵结构

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS623989U (zh) * 1985-06-24 1987-01-10
JPH11230444A (ja) * 1998-02-18 1999-08-27 Mesco Inc 送水用パイプの接合構造
JP2014134162A (ja) * 2013-01-11 2014-07-24 Hitachi Ltd 両吸込渦巻ポンプ

Also Published As

Publication number Publication date
JP6625360B2 (ja) 2019-12-25
CN107850079B (zh) 2020-09-18
CN107850079A (zh) 2018-03-27
JP2017025870A (ja) 2017-02-02

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