WO2012081562A1 - 多段ポンプ - Google Patents

多段ポンプ Download PDF

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Publication number
WO2012081562A1
WO2012081562A1 PCT/JP2011/078734 JP2011078734W WO2012081562A1 WO 2012081562 A1 WO2012081562 A1 WO 2012081562A1 JP 2011078734 W JP2011078734 W JP 2011078734W WO 2012081562 A1 WO2012081562 A1 WO 2012081562A1
Authority
WO
WIPO (PCT)
Prior art keywords
discharge
flow path
casing
discharge flow
pump
Prior art date
Application number
PCT/JP2011/078734
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
圭介 永岡
橋本　靖志
真 野口
太輔 中野
Original Assignee
株式会社クボタ
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 株式会社クボタ filed Critical 株式会社クボタ
Priority to CN201180056471.9A priority Critical patent/CN103261697B/zh
Priority to EP11848993.9A priority patent/EP2653727B1/de
Publication of WO2012081562A1 publication Critical patent/WO2012081562A1/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage pumps
    • F04D1/063—Multi-stage pumps of the vertically split casing type
    • 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
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • 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
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet

Definitions

  • the present invention relates to a multi-stage pump such as a single barrel ring cutting type.
  • a multistage pump 71 is provided with a suction casing 73 and a discharge outlet 74 in a pump casing 72 composed of a plurality of components, and a plurality of parts rotating around a rotary shaft 75 in the pump casing 72.
  • Impellers 76a to 76c are provided.
  • a diffuser 77 is provided on the outer side of the exit of each impeller 76a to 76c.
  • the fluid flows through the discharge flow path 80 while turning in the same turning direction 82 as the rotation direction of the impellers 76a to 76c, and is discharged from the discharge port 74.
  • the discharge flow path 80 is formed in an annular shape around the entire axis of the rotary shaft 75, and a part of the discharge flow path 80 and the discharge port 74 are formed in a communication flow path formed radially outward. 81 to communicate with each other. Further, the flow passage cross-sectional area of the discharge flow passage 80 in a plane including the axis 75 a of the rotation shaft 75 is substantially the same over the entire circumference except for the portion of the communication flow passage 81.
  • JP-A-2001-259151 discloses a multistage pump having a configuration in which a fluid sent from a last impeller to a diffuser flows through a discharge passage and is guided to a discharge port.
  • the fluid flowing in the axial direction while swirling in the swiveling direction 82 substantially uniformly along the outer periphery from the diffuser 77 at the final stage swirls the discharge flow path 80 while increasing the flow rate in the swirling direction 82. And is discharged from the discharge port 74 through the communication flow path 81.
  • the discharge channel 80 has a concentric annular channel shape in which the channel cross-sectional area in the plane including the axis 75a of the rotating shaft 75 is the same.
  • a part of the outer periphery of the discharge channel 80 communicates with the communication channel 81 outward.
  • a region communicating with the communication channel 81 in the turning direction 82 is defined as a downstream region 84, and a side opposite to the downstream region 84 across the communication channel 81 is defined as an upstream region 83. To do.
  • the upstream region 83 the flow rate of the liquid flowing into the discharge flow channel 80 is small, and the flow channel cross-sectional area of the discharge flow channel 80 in the plane including the shaft center 75a becomes excessive with respect to this small flow rate.
  • An object of the present invention is to provide a multistage pump capable of reducing the pump casing and preventing the pump efficiency from decreasing.
  • the first invention is provided with a suction opening and a discharge opening in a pump casing
  • a plurality of impellers rotating around the rotation shaft are provided,
  • a multi-stage pump in which the fluid pressurized by the final stage impeller is guided to the discharge port through the final stage pressure recovery unit;
  • a discharge passage is formed in the pump casing to guide the fluid from the pressure recovery part at the final stage to the discharge port,
  • the discharge flow path is formed in a direction turning around the axis of the rotation shaft,
  • the flow passage cross-sectional area of the discharge flow path in the plane including the axis of the rotating shaft is larger in the axial direction and radially inward of the rotating shaft on the downstream side of the flow toward the discharge port than on the upstream side. It is.
  • the fluid sucked into the pump casing from the suction port is sequentially pressurized by a plurality of rotating impellers. Then, the fluid pressurized by the final stage impeller flows through the discharge passage through the final stage pressure recovery section, and is discharged from the discharge port.
  • the liquid flowing out from the pressure recovery unit at the final stage to the discharge flow path flows from the upstream side to the downstream side of the discharge flow path while gradually increasing the flow rate, and is discharged from the discharge port.
  • the channel cross-sectional area of the discharge channel is increased on the downstream side of the flow toward the discharge port compared to the upstream side.
  • the flow path cross-sectional area on the upstream side of the discharge flow path is correspondingly smaller than the flow cross-sectional area on the downstream side. For this reason, a significant decrease in the flow velocity on the upstream side of the discharge flow path is suppressed, and it is possible to prevent stagnation (dead water region) of fluid on the upstream side of the discharge flow path.
  • stagnation dead water region
  • the flow passage cross-sectional area of the discharge flow passage increases in the axial direction and the radial inward direction of the rotating shaft, and does not increase in the radial outward direction. For this reason, the discharge flow path does not expand radially outward, and the pump casing can be downsized in the radial direction.
  • the discharge port side of the discharge flow path is the downstream side, and the opposite side to the flow direction is the upstream side
  • the increase rate of the dimension in the axial direction of the flow path cross section of the discharge flow path in the plane including the axis of the rotation axis is set larger than the downstream area adjacent to the upstream area of the discharge flow path
  • the increasing ratio of the dimension inward in the radial direction of the cross section of the discharge flow path is set to be smaller than the downstream area adjacent to the upstream area of the discharge flow path.
  • the upstream region of the discharge channel is radially inward compared to the downstream region adjacent to this region. Slowly expand without sudden expansion in the direction.
  • the upstream region of the discharge flow path it is possible to suppress the occurrence of separation, turbulence, or stagnation in the flow of fluid closer to the inside in the radial direction, and further prevent the pump efficiency from being lowered. Can do.
  • the increase rate of the dimension in the axial direction of the cross section of the discharge flow path is the dimension in the radial inward direction of the cross section of the discharge flow path Is greater than the rate of increase.
  • the flow passage cross-sectional area of the discharge flow passage in a plane including the axis of the rotation shaft increases linearly at a predetermined rate from the upstream side to the downstream side.
  • the flow passage cross-sectional area of the discharge flow passage does not suddenly expand or contract rapidly, and therefore, the energy loss of the fluid accompanying the change of the flow passage cross-sectional area decreases, and the pump efficiency decreases. Can be further prevented.
  • the pump casing is divided into a suction casing having a suction port, a discharge casing having a discharge port, and an intermediate casing sandwiched between the suction casing and the discharge casing,
  • a fixing means for tightening each casing in the axial direction of the rotating shaft is provided,
  • the discharge channel is formed in the discharge casing,
  • the suction casing has a suction channel that guides fluid from the suction port to the inlet of the impeller housed in the first stage intermediate casing,
  • the intermediate casing has an intermediate flow path for guiding fluid from the outlet of the impeller to the inlet of the next stage impeller,
  • the outer diameters of the discharge channel and the intermediate channel are substantially the same,
  • the fixing means fixes the suction casing and the discharge casing outside the outer diameters.
  • the discharge casing is not extremely larger in the radial direction than the intermediate casing, and the pump casing can be downsized in the radial direction.
  • FIG. 4 is a cross-sectional view of the discharge casing as seen from the axial direction of the rotary shaft of the multistage pump, showing a state where a diffuser is provided.
  • FIG. 6 is a cross-sectional view of the discharge casing as seen from the axial direction of the rotary shaft of the multistage pump, showing a state where the diffuser is removed. It is sectional drawing of the discharge casing which shows each cross section in FIG. It is sectional drawing of the discharge casing which shows each cross section in FIG. It is sectional drawing of the discharge casing which shows each cross section in FIG.
  • FIG. 10 is a graph showing the flow path cross-sectional area of the discharge flow path corresponding to each position V1 to V16 of the discharge flow path of the multistage pump in the third embodiment of the present invention. It is sectional drawing of the conventional multistage pump.
  • FIG. 13 is a view on arrow XX in FIG. 12.
  • reference numeral 1 denotes a single-body ring-cut multistage pump, and a pump casing 2 is provided with a suction port 3 and a discharge port 4. Inside the pump casing 2, a plurality of impellers 6a to 6c that are rotated by a rotating shaft 5 are provided.
  • the pump casing 2 includes a suction casing 7 having a suction port 3, a discharge casing 8 having a discharge port 4, and a plurality of ring-cut intermediate casings 9 a sandwiched between the suction casing 7 and the discharge casing 8. It is divided into 9b.
  • the casings 7, 8, 9a, 9b are fastened and fixed in the axial direction A of the rotary shaft 5 by the fixing means 11.
  • the fixing means 11 has a plurality of fixing bolts 12 and nuts 13. Each fixing bolt 12 is inserted from the axial direction A into the suction casing 7 and the discharge casing 8 located at both ends. Each nut 13 is screwed to both ends of the fixing bolt 12, and thereby the suction casing 7 and the discharge casing 8 are fixed.
  • the rotary shaft 5 is inserted into the pump casing 2 and sealed with a sealing material 15 such as packing at a shaft seal portion 14.
  • the impellers 6 a to 6 c are fitted on the rotary shaft 5 and are housed in the intermediate casings 9 a and 9 b and the discharge casing 8, and rotate integrally with the rotary shaft 5.
  • Each impeller 6 a to 6 c has an outlet 16 and an inlet 17. Further, the outlet 16 is located on the outer side in the radial direction of the rotary shaft 5 than the inlet 17.
  • a suction flow path 19 that guides water 18 (an example of fluid) from the suction port 3 to the inlet 17 of the first stage impeller 6 a is formed.
  • the suction channel 19 is provided in an annular shape so as to surround the outer periphery of the rotary shaft 5 so that the water 18 flows as uniformly as possible into the inlet 17 of the impeller 6a.
  • an intermediate flow path 20 is formed for guiding water 18 from the outlet 16 of each impeller 6a, 6b to the inlet 17 of each subsequent impeller 6b, 6c.
  • the intermediate flow path 20 has annular diffusers 21a and 21b formed outside the outlet 16 of each impeller 6a and 6b.
  • an annular final stage diffuser 21 c (an example of a pressure recovery unit) and a discharge flow path 22 are formed in the discharge casing 8.
  • the final stage diffuser 21c is formed outside the outlet 16 of the final stage impeller 6c.
  • the discharge flow path 22 is a flow path that guides the water 18 that has passed through the final stage diffuser 21 c to the discharge port 4, and is formed in a spiral shape in the direction of turning around the axis of the rotary shaft 5.
  • the discharge port 4 side of the discharge flow path 22 is defined as a downstream side 22a, and the opposite side to the flow direction 23 toward the discharge port 4 is defined as an upstream side 22b.
  • the flow passage cross-sectional area of the discharge flow passage 22 in a plane including the axis 5a of the rotating shaft 5 gradually increases in the axial direction A and the radially inward B of the rotating shaft 5 on the downstream side 22a as compared with the upstream side 22b. To do.
  • the suction port 3 side in the axial direction A is the front and the discharge port 4 side is the rear
  • the flow path cross-sectional area is the rear in the axial direction A (that is, from the intermediate casing 9b to the discharge casing 8).
  • the horizontal axis of the graph (a) in FIG. 8 shows the positions V1 to V16 in the circumferential direction D of the discharge flow path 22 in FIG. 3, and each position V1 to V16 is a position at an angle of 22.5 ° in the circumferential direction D. Is shown.
  • the vertical axis of the graph (a) indicates the length dimension C in the axial direction A of the cross section of the discharge flow path 22 in FIG.
  • the increasing rate of the dimension C of the discharge flow path 22 in the axial direction A is the downstream of the upstream predetermined region 25 including the start end position V1 (start end) of the discharge flow path 22. It is set to be larger than the predetermined area 26 on the side.
  • the increase rate corresponds to the slopes ⁇ 1 and ⁇ 2 in the graph (a), and the slope ⁇ 1 of the upstream predetermined region 25 (region approximately 180 ° from the upstream side) is greater than the slope ⁇ 2 of the downstream predetermined region 26. Is also set to be large.
  • the horizontal axis of the graph (b) in FIG. 8 shows the positions V1 to V16 in the circumferential direction D of the discharge flow path 22 in FIG. 3, and the vertical axis is the radially outer side of the cross section of the discharge flow path 22 in FIG.
  • the length dimension F from the inside to the inside is shown.
  • the rate of increase of the dimension F of the discharge flow path 22 in the radially inward direction B is that the predetermined area 27 on the upstream side including the start end position V1 (start end) of the discharge flow path 22 It is set to be smaller than the adjacent first region 28 on the downstream side.
  • the increase rate corresponds to the slopes ⁇ 1 to ⁇ 3 in the graph (b), and the slope ⁇ 1 of the upstream predetermined region 27 including the start position V1 is smaller than the slope ⁇ 2 of the adjacent downstream first region 28.
  • the slope ⁇ 3 of the second downstream area 29 adjacent to the downstream first area 28 is set to be smaller than the slope ⁇ 1 of the predetermined upstream area 27.
  • the parts provided inside the discharge flow path 22, for example, parts such as a balance disk are arranged at a position B inward in the radial direction, so that the inclination ⁇ 3 of the second region 29 can be set large. This is because it cannot be done. If there is no restriction on the components such as the balance disk as described above, the inclination ⁇ 3 can be the same as or larger than the inclination ⁇ 2.
  • the increasing rate of the dimension C of the discharge flow path 22 in the axial direction A is the dimension F of the discharge flow path 22. Is greater than the rate of increase inward in the radial direction B (that is, the slope ⁇ 1 of the graph (b) in FIG. 8).
  • the outer diameter G1 of the discharge flow path 22 is a flow path (downstream position shown in FIG. 3) communicating with the discharge port 4 from the start end (upstream start position V1 shown in FIG. 3). V16) is kept constant.
  • the outer diameter G1 of the discharge flow path 22 and the outer diameter G2 of the intermediate flow path 20 are substantially the same size, and the outer diameter G3 of the suction flow path 19 is the both outer diameters G1, G2. Smaller than.
  • Each fixing bolt 12 is located outside the outer diameters G1 and G2.
  • the impellers 6a to 6c are rotated by the rotation of the rotating shaft 5.
  • the water 18 sucked into the pump casing 2 from the suction port 3 passes through the suction flow path 19, flows in from the inlet 17 of the first stage impeller 6 a, and flows out from the outlet 16.
  • the water 18 that has flowed out flows through the intermediate flow path 20 through the first stage diffuser 21a, then flows in from the inlet 17 of the next stage impeller 6b, flows out from the outlet 16, and passes through the next stage diffuser 21b. It flows through the flow path 20.
  • the water 18 that has been successively boosted in this way flows in from the inlet 17 of the final stage impeller 6c, flows out of the outlet 16, and flows into the discharge passage 22 through the final stage diffuser 21c. It flows through the discharge flow path 22 and is discharged from the discharge port 4.
  • the water 18 is sequentially boosted by the impellers 6a to 6c and then discharged from the discharge port 4.
  • the water 18 that flows uniformly from the final stage diffuser 21c to the discharge flow path 22 in the circumferential direction swirls from the upstream side 22b to the downstream side 22a of the discharge flow path 22 and flows while gradually increasing the flow rate. It is discharged from the outlet 4.
  • the flow passage cross-sectional area of the discharge flow passage 22 is gradually increased on the downstream side 22a of the flow toward the discharge port 4 as compared with the upstream side 22b.
  • the flow rate on the upstream side 22b of the discharge flow path 22 is smaller than the flow rate on the downstream side 22a, but the flow path cross-sectional area of the upstream side 22b of the discharge flow path 22 corresponds to the flow rate on the downstream side 22a. Since it is smaller than the cross-sectional area, a significant decrease in the flow velocity on the upstream side 22b of the discharge flow path 22 is suppressed. In this way, by suppressing the significant decrease in the flow velocity, it is possible to prevent the stagnation of the water 18 (the dead water region in which the flow of the water 18 is stagnant) from occurring on the upstream side 22b of the discharge flow path 22.
  • the flow passage cross-sectional area of the spiral discharge passage 22 increases in the axial direction A and the radial inward direction B of the rotating shaft 5 from the upstream side 22 b to the downstream side 22 a.
  • it does not increase in the outer circumferential direction.
  • the discharge flow path 22 does not expand radially outward, and the pump casing 2 does not increase in size in the radial direction. Therefore, the pump casing 2 (discharge casing 8) can be downsized in the radial direction even if the pumping efficiency is improved by making the discharge flow path 22 into a spiral shape.
  • the upstream region 27 of the discharge flow path 22 is radially inward compared to the downstream first region 28 adjacent to the region 27. It is expanding moderately without sudden expansion to B.
  • the upstream region 27 of the discharge passage 22 it is possible to suppress the occurrence of separation, turbulence, or stagnation particularly in the flow of the water 18 closer to the inside in the radial direction of the discharge passage 22. A reduction in efficiency can be further prevented.
  • the slope ⁇ 1 of the graph (a) in FIG. 8 is larger than the slope ⁇ 1 of the graph (b) in FIG. 8, in the region on the upstream side of the discharge flow path 22, It is possible to further suppress the occurrence of separation and turbulence in the flow of the water 18, and further prevent the pump efficiency from being lowered.
  • intermediate casings 9 a and 9 b are sandwiched between suction casing 7 and discharge casing 8, fixing bolts 12 are inserted between suction casing 7 and discharge casing 8, and nut 13 is screwed together.
  • the casings 7, 8, 9a and 9b are fixed and the pump casing 2 is assembled.
  • the discharge casing 8 is extremely larger in the radial direction than the intermediate casings 9a and 9b.
  • the pump casing 2 can be reduced in size in the radial direction.
  • outer diameter G1 of the discharge flow path 22 and the outer diameter G2 of the intermediate flow path 20 are substantially the same dimension when the outer diameter G1 and the outer diameter G2 are completely the same.
  • the case where the outer diameter G1 and the outer diameter G2 are slightly different is included.
  • the outer diameter G1 of the discharge flow path 22 is slightly larger than the outer diameter G2 of the intermediate flow path 20, they may be regarded as having substantially the same dimensions.
  • the outer diameter G1 of the discharge flow path 22, the outer diameter G2 of the intermediate flow path 20, and the outer diameter G3 of the suction flow path 19 are substantially the same dimension. It is.
  • the horizontal axis of the graph of FIG. 11 indicates the positions V1 to V16 in the circumferential direction D of the discharge flow path 22 in FIG. 3, and the vertical axis indicates the flow break of the discharge flow path 22 in a plane including the axis 5a of the rotation shaft 5.
  • the flow path cross-sectional area of the discharge flow path 22 gradually increases linearly at a predetermined rate from the upstream start position V1 to the downstream position V16. That is, the positions V1 to V16 in the circumferential direction D of the discharge flow path 22 and the flow path cross-sectional area of the discharge flow path 22 are directly proportional, and the predetermined ratio corresponds to the slope ⁇ of the graph.
  • the flow passage cross-sectional area of the discharge flow passage 22 gradually increases linearly from the upstream side to the downstream side, so the flow passage cross-sectional area of the discharge flow passage 22 suddenly increases or decreases rapidly.
  • the flow velocity does not change with the change in the channel cross-sectional area of the discharge channel 22, the energy loss of the fluid is reduced, and the pump efficiency can be further prevented from being lowered.
  • the multistage pump 1 maintains the relationship between the positions V1 to V16 of the discharge flow path 22 and the cross-sectional area of the flow path shown in the graph of FIG. In the embodiment, the relationship between the positions V1 to V16 of the discharge flow path 22 and the dimensions C and F shown in the graphs of FIGS. 8A and 8B is also maintained. However, although the relationship shown in the graph of FIG. 11 is maintained, the multistage pump 1 which does not maintain the relationship shown in each graph of FIG. 8A and FIG. 8B may be used.
  • the number of impellers 6a to 6c is not limited to three, and two or four or more may be provided.
  • the two intermediate casings 9a and 9b are provided, one or three or more intermediate casings may be provided according to the number of impellers.
  • the pump casing 2 is described as the ring-cut multistage pump 1 that is divided into the suction casing 7, the discharge casing 8, and the plurality of ring-cut intermediate casings 9a and 9b.
  • Other types such as a horizontal division type multistage pump in which the pump casing 2 is divided into a plurality of sections in a cross section parallel to the shaft center 5a may be used.
  • the position of the downstream side 22a of the discharge flow path 22 is shifted rearward without overlapping in the axial direction A with respect to the position of the upstream side 22b. It may be duplicated at the position of the upstream side 22b.
  • the flow passage cross-sectional area of the discharge flow passage 22 gradually increases toward the downstream side 22a.
  • the flow passage cross-sectional area changes to a part between the upstream side 22b and the downstream side 22a. Instead, a region that is kept constant may be formed.
  • discharge flow path 22 is formed over a range of about 360 °, it may be formed in a range smaller or larger than 360 °.
  • the position where the increase ratio and the increase ratio of the dimensions C and F of the flow path cross section of the discharge flow path 22 shown in FIG. 8 change or the number of changes is limited only to the relationship shown by the linear graph.
  • the relationship shown by a curved graph may be used instead.
  • the slope ⁇ 1 is made smaller than the slope ⁇ 2 as shown in the graph (b) of FIG. 8, but the slope ⁇ 2 may be made smaller than the slope ⁇ 1.
  • the inclination ⁇ 2 and the inclination ⁇ 3 may be set to zero. In this case, in the first and second regions 28 and 29 on the downstream side, the dimension F of the cross section of the discharge flow path 22 does not increase and is maintained at a constant value. In order to prevent a decrease in pump efficiency, it is most effective to make the inclination ⁇ 1 smaller than the inclination ⁇ 2 as shown in the graph (b) of FIG.
  • the multistage pump 1 has been described. However, increasing the cross-sectional area of the discharge flow path 22 in the axial direction A and the radially inward direction B has the same effect even in a single-stage pump. Can bring.
  • the diffusers 21a to 21c are used as an example of the pressure recovery unit, but the diffusers 21a to 21c may be provided with blades or without blades. Alternatively, as another example of the pressure recovery unit, one or a plurality of volutes may be used.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
PCT/JP2011/078734 2010-12-14 2011-12-13 多段ポンプ WO2012081562A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201180056471.9A CN103261697B (zh) 2010-12-14 2011-12-13 多级泵
EP11848993.9A EP2653727B1 (de) 2010-12-14 2011-12-13 Mehrstufige pumpe

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2010-277557 2010-12-14
JP2010277557 2010-12-14
JP2011-269503 2011-12-09
JP2011269503A JP5889622B2 (ja) 2010-12-14 2011-12-09 多段ポンプ

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Publication Number Publication Date
WO2012081562A1 true WO2012081562A1 (ja) 2012-06-21

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EP (1) EP2653727B1 (de)
JP (1) JP5889622B2 (de)
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WO (1) WO2012081562A1 (de)

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DE102019001882A1 (de) * 2019-03-19 2020-09-24 KSB SE & Co. KGaA Mantelgehäusepumpe und Herstellungsverfahren für eine Mantelgehäusepumpe
JP2021032163A (ja) * 2019-08-26 2021-03-01 株式会社荏原製作所 ポンプ装置
KR102615546B1 (ko) * 2023-06-28 2023-12-19 윤성업 2축 2속 횡형식 원심 펌프

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JPH01190996A (ja) * 1988-01-22 1989-08-01 Fuji Electric Co Ltd ポンプ
JPH0754798A (ja) * 1993-03-31 1995-02-28 Ksb Ag つぼ形ケーシング構造のうず巻ポンプ
JP2005330878A (ja) * 2004-05-19 2005-12-02 Torishima Pump Mfg Co Ltd 多段流体機械
JP2006152849A (ja) * 2004-11-26 2006-06-15 Teral Kyokuto Inc 遠心ポンプの吐出ケーシング

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GB2204917B (en) * 1987-05-19 1992-01-08 Apv Uk Centrifugal pump
DE102005060895B4 (de) * 2005-12-20 2012-07-19 Sero Pumpsystems Gmbh Kreiselpumpe zur Förderung heißer und/oder leicht ausgasender und/oder gasbeladener Medien
CN200940573Y (zh) * 2006-07-31 2007-08-29 上海凯泉泵业（集团）有限公司 一种新型多级泵
CN200975360Y (zh) * 2006-12-04 2007-11-14 上海连成（集团）有限公司 一种带中间轴承的立式多级泵

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01190996A (ja) * 1988-01-22 1989-08-01 Fuji Electric Co Ltd ポンプ
JPH0754798A (ja) * 1993-03-31 1995-02-28 Ksb Ag つぼ形ケーシング構造のうず巻ポンプ
JP2005330878A (ja) * 2004-05-19 2005-12-02 Torishima Pump Mfg Co Ltd 多段流体機械
JP2006152849A (ja) * 2004-11-26 2006-06-15 Teral Kyokuto Inc 遠心ポンプの吐出ケーシング

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Publication number Publication date
EP2653727A1 (de) 2013-10-23
JP2012140931A (ja) 2012-07-26
CN103261697B (zh) 2016-01-20
EP2653727A4 (de) 2017-06-14
EP2653727B1 (de) 2019-09-11
CN103261697A (zh) 2013-08-21
JP5889622B2 (ja) 2016-03-22

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