WO2006061914A1 - Inducteur et pompe - Google Patents

Inducteur et pompe Download PDF

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Publication number
WO2006061914A1
WO2006061914A1 PCT/JP2004/018676 JP2004018676W WO2006061914A1 WO 2006061914 A1 WO2006061914 A1 WO 2006061914A1 JP 2004018676 W JP2004018676 W JP 2004018676W WO 2006061914 A1 WO2006061914 A1 WO 2006061914A1
Authority
WO
WIPO (PCT)
Prior art keywords
inducer
wing
blades
blade
pump
Prior art date
Application number
PCT/JP2004/018676
Other languages
English (en)
Japanese (ja)
Inventor
Kosuke Ashihara
Original Assignee
Ebara Corporation
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 Ebara Corporation filed Critical Ebara Corporation
Priority to PCT/JP2004/018676 priority Critical patent/WO2006061914A1/fr
Publication of WO2006061914A1 publication Critical patent/WO2006061914A1/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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2277—Rotors specially for centrifugal pumps with special measures for increasing NPSH or dealing with liquids near boiling-point

Definitions

  • the present invention relates to an inducer and a pump.
  • the inductor disposed on the upstream side of the main impeller so that the rotation axis coincides with the rotation axis of the main impeller.
  • the present invention relates to a reducer and a pump equipped with the inducer.
  • the pump impeller (hereinafter referred to as the main impeller) Cavitation may occur in the flow path. If cavity is generated in the main impeller flow path, the flow path may be blocked by the cavity bubbles and the pump may not be able to pressurize.
  • the difference between the total pressure at the inlet of the pump and the saturated vapor pressure represents a margin for pump cavity generation, and this pressure difference is called NPSH (Net Positive Suction Head).
  • NPSH Network Positive Suction Head
  • the pump suction performance is evaluated by this N P S H, and a pump that has a boosting performance even with a low N P S H is said to have high suction performance. If the pump suction performance is high, the pump can be operated at high speed and the pump can be downsized.
  • an inducer has been attached to the tip of the main shaft to improve pump suction performance.
  • This inducer is arranged on the upstream side of the main impeller such that the main impeller and the rotation axis are the same, and is rotated at the same rotational speed as the main impeller via the main shaft.
  • the inducer is a mixed flow type or axial flow type impeller having a plurality of blades, and has a shape characteristic that the number of blades is smaller and the blade length is longer than the main impeller.
  • wing 1 1 three wings of helical shape (spiral shape) 1 1-1, 1 1-2, 1 1-3 (hereinafter collectively referred to as wing 1 1) Is fixed to the outer peripheral surface of the cylindrical or columnar shaft portion 5.
  • the lengths of these wings 11 along the wings are all equally configured.
  • inducers are designed to achieve high suction performance, so it is preferable to reduce the number of inducer blades as much as possible. Since an inducer with only one blade has a problem of rotational balance, the number of blades of a normal inducer is 2 to 5 blades. Also, inductors with an even number of blades may cause alternate blade cavityation, so a three-blade inducer is generally preferred.
  • the boosting performance of an inducer increases as the number of blades of the inducer increases.
  • the suction performance of the inducer increases as the number of blades decreases, the boosting performance and suction performance of the inducer are in a trade-off relationship. If the inducer requires high suction performance and high boosting performance at the same time due to the pump specifications, an inducer with an intermediate blade may be used.
  • An inducer with an intermediate wing has an intermediate wing that is shorter than the entire wing in a flow path formed between the wings of the normal length (full wing).
  • the rear wing of the intermediate wing is in the same position as all wings on the meridian plane, but the leading edge of the intermediate wing is located downstream of the leading edge of all wings. Therefore, an inducer with an intermediate blade has a feature that the number of blades is small at the inlet and the number of blades is large at the outlet. With this, with the middle wing
  • the inducer has a high suction performance because it has a wider inlet channel and is less likely to be blocked by cavity bubbles, compared to an inducer with all blades.
  • the inducer with intermediate blades has high boosting performance due to the large number of blades at the outlet.
  • Document 2 shows that pump impellers with intermediate blades have higher suction performance than pump impellers without intermediate blades.
  • Document 3 discloses an impeller for a sewage pump with one full blade and one intermediate blade.
  • the trailing edge of the intermediate blade (sub blade) is more rotational than the symmetrical position around the rotation axis of the trailing edge of all blades (main blade). It is in the position shifted.
  • This impeller for sewage pumps has one inlet blade to prevent clogging of the inlet due to dirt, and two outlet blades to make the pump efficiency practically sufficient. is there. Since the center of gravity of these intermediate wings and all wings are all separated from the rotation axis, the rotation balance cannot be obtained with only the middle wing and all wings.
  • a two-blade type inducer can be considered as an inducer that can achieve high suction performance.
  • this type of inducer can be expected to have a high suction performance due to the small number of blades at the inlet, but the boosting performance is low due to the small number of blades at the outlet.
  • an inducer with an intermediate blade that can be expected to have a high suction performance and a high pressure boosting performance always has an even number of blades due to its shape characteristics, and the minimum number of blades in an inducer used in an actual pump.
  • Fig. 2A and Fig. 2B show an inducer with a conventional intermediate wing that has two full wings and two intermediate wings.
  • the intermediate blades 1 2-1, 1 2-2 (hereinafter collectively referred to as the intermediate blade 1 2) are all blades 1 1-1, 1 1-2 (Hereinafter collectively referred to as all blades 1 1) are located at the center in the circumferential direction of the rotation axis, and the length of the intermediate blade 1 2 is the length of all blades 1 1 Half a minute.
  • the trailing edge 1 2— 1 a, 1 2— lb on the meridian plane 1 2 is the same as the trailing edge 1 1 1 lb, 1 1— 2 b of the entire wing 1 1, but the intermediate wing 1 2
  • the leading edge 1 2-1 a, 1 2— 2 a is located downstream of the leading edge 1 1— la, ll _ 2 a of the entire wing 1 1.
  • This inducer with intermediate blades has two inlet blades and four outlet blades, so the inlet is wide, so high suction performance can be achieved, and high boosting performance can be achieved.
  • the present invention has been made in view of such problems of the prior art.
  • the number of blades at the inlet is one, the number of blades at the outlet is three, and the center of gravity of the entire blade is on the rotating shaft. It is an object of the present invention to provide an inducer excellent in both suction performance and boosting performance that does not cause a balance, and a pump equipped with such an inducer.
  • the present invention is an inducer disposed on the upstream side of a main impeller, and includes three blades having different lengths along the blades. The positions of the leading edges of the wings on the meridian plane are different from each other.
  • the trailing edge positions of the three blades are aligned with each other on the meridian plane. In a preferred aspect of the present invention, the trailing edges of the three blades are uniformly arranged around the rotation axis in a plane perpendicular to the rotation axis.
  • the three wings are composed of a first wing, a second wing, and a third wing, and a winding angle from a trailing edge of the first wing is 2 3 0 + A to 2 5 0 + A.
  • the winding angle from the trailing edge of the second wing is 1 1 0 + A to 1 3 0 + A °, and the winding angle from the trailing edge of the third wing is A ° (However, A represents a constant satisfying the condition 0 ⁇ A).
  • the winding angle is the center angle of the wing centered on the rotation axis from the trailing edge to the leading edge.
  • the firing angle from the trailing edge of the first wing is 2 4 0 + A °
  • the firing angle from the trailing edge of the second wing is 1 2 0 + A °
  • the winding angle from the trailing edge of the third wing can be A °.
  • A is a constant common to the three blades, and any value can be selected within the range of 0 ⁇ A.
  • the lengths of the three wings along the wings are different, so there are one wing at the entrance, two wings at the center, and three wings at the exit. . Furthermore, when the wing angle of each blade relative to the position of the trailing edge satisfies the above relationship, the center of gravity of the three blades is positioned on the rotation axis.
  • the inducer of the present invention since the number of blades at the inlet is one, even if a cavity bubble is generated on the suction surface near the inlet of the first blade, the flow path on the suction surface side at the inlet of the inducer Has a wide opening angle of 3600 °, and the inlet of the inducer is not easily blocked.
  • the opening angle is the channel breakage around the rotation axis.
  • the center angle of a surface which represents the size of the space between adjacent wings. Due to the pressure increase of the first blade, the cavitation bubbles generated on the suction surface of the second blade are smaller than those of the first blade, and the flow angle on the suction surface side also has an opening angle of 2400 °.
  • the opening angle of the flow path on the suction side is 120 °, but the cavity bubbles generated in the third wing by the pressurizing action of the first wing and the second wing are even smaller. Therefore, the possibility of blockage is low.
  • the inducer of the present invention having the above-described configuration has a high suction performance, and the number of blades at the inducer outlet is three, so that it has a sufficiently high boosting performance in practice.
  • the inducer having the above configuration has the characteristics of high suction performance, high boosting performance, and no rotation imbalance.
  • Another aspect of the present invention is a pump comprising a main impeller housed in a casing, a main shaft to which the main impeller is fixed, and the inducer.
  • the inducer described above has a high suction performance and a high pressure increase performance, the suction performance of a pump including this inducer can be improved. Therefore, it is possible to increase the speed and size of the pump.
  • the present invention can be said to have solved the contradictory proposition regarding the number of blades of the inducer.
  • the number of inducer blades should be reduced from the viewpoint of achieving high suction performance by avoiding blockage of the flow path due to cavity bubbles, but the number of blades will be increased from the point of achieving high boosting performance. Should.
  • such a contradictory proposition can be satisfactorily solved with extremely high effects by using three wings having different lengths from each other rather than simply compromising both performances.
  • the positions of the trailing edges of the blades on the meridional surface are aligned with each other.
  • the displacement of the positions of the trailing edges of the blades is an excellent object of the present invention. It does not immediately affect the suction performance and boost performance.
  • the inducer of the present invention has high suction performance and high boosting performance, and does not cause rotation imbalance. Therefore, the inducer of the present invention
  • the pump arranged on the upstream side of the main impeller can exhibit higher suction performance than conventional pumps, and can contribute to speeding up and downsizing of the pump.
  • FIG. 1A is a perspective view showing a conventional inducer having three blades
  • FIG. 1B is a side view of the inducer shown in FIG. 1A.
  • FIG. 2A is a perspective view showing a conventional inducer with intermediate blades having two full blades and two intermediate blades
  • FIG. 2B is a side view of the inducer shown in FIG. 2A.
  • FIG. 3 is a cross-sectional view schematically showing a pump provided with an inducer according to an embodiment of the present invention.
  • FIG. 4A is a side view showing an inducer according to an embodiment of the present invention
  • FIG. 4B is a perspective view of the inducer according to an embodiment of the present invention
  • FIG. 4C is an embodiment of the present invention. It is another perspective view of the inducer which concerns on a form.
  • FIG. 5 is a schematic diagram showing the first wing, the second wing, and the third wing on the meridian plane of the inducer according to the embodiment of the present invention.
  • FIG. 6A is a perspective view showing a first wing according to an embodiment of the present invention
  • FIG. 6B is a plan view showing the first wing.
  • FIG. 7A is a perspective view showing a second wing according to an embodiment of the present invention
  • FIG. 7Bj is a plan view showing the second wing.
  • FIG. 8A is a perspective view showing a third wing according to an embodiment of the present invention
  • FIG. 8B is a plan view showing the third wing.
  • Fig. 9 is a schematic diagram showing the occurrence of cavitation in a conventional inducer with three blades.
  • FIG. 10 is a schematic diagram showing a state of occurrence of cavitation in a conventional inducer having two full blades and two intermediate blades.
  • FIG. 11 is a schematic diagram showing a cavitation occurrence state of an inducer according to an embodiment of the present invention.
  • FIG. 3 is a cross-sectional view schematically showing a pump provided with the inducer of the present invention.
  • the pump has a main impeller (pump impeller) 7 accommodated in a casing 6, an inducer 8 according to the present invention, a main impeller 7 and an inducer 8 fixed thereto.
  • Main shaft 9 is provided.
  • Seal members 10 A and 10 B for preventing the pressurized fluid from leaking from the high pressure side to the low pressure side are respectively provided on the upstream side and the downstream side of the main impeller 7.
  • the inducer 8 is arranged upstream of the main impeller 7 so that the rotation axis (the central axis of the main shaft 9) is the same as that of the main impeller 7, and the main impeller is driven via the main shaft 9 by a drive source (not shown). It rotates at the same rotational speed as car 7.
  • the fluid (liquid) flows in from the suction port 6a, is pressurized by the inducer 8 while generating a cavity, and further boosted by the main impeller 7 to the extent that the required pump head is obtained.
  • the inducer 8 is boosting the fluid up to a pressure at which no cavity is generated in the main impeller 7, the suction performance of the pump is improved as compared with the case of the main impeller 7 alone.
  • FIG. 4A to 4C show in detail an inducer according to an embodiment of the present invention.
  • 4A is a side view of an inducer according to an embodiment of the present invention
  • FIG. 4B is a perspective view of an inducer according to an embodiment of the present invention
  • FIG. 4C is an embodiment of the present invention. It is another perspective view of the inducer which concerns on.
  • FIG. 5 is a schematic diagram showing the first wing, the second wing, and the third wing on the meridian plane of the inducer according to the embodiment of the present invention.
  • the inducer in this embodiment includes a cylindrical or cylindrical shaft portion 5 and three blades 1 fixed to the outer peripheral surface of the shaft portion 5.
  • the first wing 1 is composed of the first wing 1-1, the second wing 1 1-2, and the third wing 1-3 (hereinafter collectively referred to as wing 1).
  • the lengths of the first wing 1 1, the second wing 1-2, and the third wing 1 1 3 are different from each other.
  • the positions on the meridian plane are different from each other.
  • the trailing edge of wing 1 on the meridian plane 1 — lb, 1-2 b, 1-3 b is in the same position.
  • the trailing edges of the three blades 1 at the inducer exit 1 1 1 b to l— 3 b are evenly spaced at 120 ° intervals around the center.
  • the rolling angles from the trailing edges of the three wings 1 are set as follows.
  • A is a constant common to the three blades 1 and represents a value larger than 0.
  • the roll angle is the center angle of the wing centered on the axis of rotation from the trailing edge to the leading edge.
  • the winding angle of the first blade 1-1 may be 230 + A to 250 + A °
  • the winding angle of the second blade 1-2 is 1 10 + ⁇ to 130 + A °. If there is.
  • FIG. 6A is a perspective view showing a first wing according to an embodiment of the present invention
  • FIG. 6B is a plan view showing the first wing
  • FIG. 7A is a perspective view showing a second wing according to an embodiment of the present invention
  • FIG. 7B is a plan view showing the second wing
  • FIG. 8A is a perspective view showing a third wing according to an embodiment of the present invention
  • FIG. 8B is a plan view showing the third wing.
  • the constant A is set to 120, and the blades from the trailing edges 1—1 b to l_3 b of the three blades 1 are scattered.
  • the angles are set as follows.
  • Second wing 1—2 240 °
  • the inducer of the present embodiment is configured with one wing at the inlet, two wings at the center, and three wings at the outlet.
  • the constant A mentioned above is preferably 60 ⁇ A ⁇ 180. If A is 60, the length of the third wing 1-3 is too short to expect pressure boosting performance. Meanwhile, 180 ⁇ A If this is the case, the flow paths formed between the three blades 1 will be too long, and the resistance of the fluid will increase and the pressurizing performance will decrease.
  • the winding angle of the second blade 1 1 2 is 2400 °
  • the winding angle of the third blade 1 1 3 is 1 20 °
  • the second blade The positions of the trailing edges 1 1 2 b and 1 _ 3 b of 1 1 2 and the third wing 1 1 3 are shifted from each other by 120 °.
  • the total winding angle of the second wing 1 _ 2 and the third wing 1-3 is the same as the winding angle of the first wing 1 1 1 3 60 °
  • the second The center of gravity when the wings 1 and 2 and the third wings 1 and 3 are combined is located on the axis of rotation. 1st wing 1 1 1
  • the winding angle is 3 6 0.
  • the center of gravity of the first wing 1-1 1 is on the axis of rotation
  • the overall center of gravity of the first wing 1-11, the second wing 1-2, and the third wing 1-3 also rotates. Will be on the axis. Accordingly, the rotation balance of the inducer according to the present embodiment is balanced. In this way, the leading edges of each blade 1 — 1 a to 1 1 3 a are shifted from each other by 120 °, so that the entire blade 1 can be increased or decreased by the same firing angle in each blade 1.
  • the center of gravity is on the axis of rotation. Therefore, even if the above-described constant A is an arbitrary value, the center of gravity of the entire blade 1 is located on the rotation axis, and a rotation balance can be obtained.
  • FIG. 9 to FIG. 11 show the state of occurrence of the oscillation of the inducer according to one embodiment of the present invention and the conventional inducer.
  • Figures 9 to 11 show the wings of the inducer.
  • the first wing is shown overlapping on both the left and right sides to make the flow path easy to understand, but in reality there is only one first wing.
  • Fig. 9 is a schematic diagram showing the state of occurrence of cavitation in the conventional inducer shown in Fig. 1 having three all blades.
  • this type of inducer an interval of a size corresponding to an opening angle of 120 ° is formed between the blade 1 1 ⁇ 2 and the adjacent blade 1 1 ⁇ 3.
  • the opening angle refers to the central angle of the cross section of the flow channel centered on the rotation axis, and represents the size of the interval between adjacent blades.
  • FIG. 10 is a schematic view showing the state of occurrence of cavitation in the conventional inducer shown in FIG. 2 having two full blades and two intermediate blades. Since the number of blades at the inlet of this type of inducer is two, there is a gap between each blade 1 1 1 1 and the next blade 1 1—2 that corresponds to an opening angle of 1800 °. Is formed. Therefore, even if cavitation bubbles 20 are generated on the suction surface of all blades 11 near the inlet, the flow path is wider than that of the inducer (three blades type) shown in FIG. Cavitation bubbles generated on the suction surface of the intermediate blade 1 2 near the inlet
  • the size of 30 is smaller than the size of the cavity bubble 20 generated on the suction surface of all blades 11 because of the pressure increasing action by all blades 11.
  • the opening angle between the adjacent intermediate blades 12 and all blades 11 is 90 °, and the flow path on the suction surface side of the intermediate blades 12 is relatively narrow. For this reason, if the cavity bubble 30 generated on the suction surface of the intermediate blade 12 is large to some extent, the flow path on the suction surface side of the intermediate blade 12 is likely to be blocked.
  • the number of blades at the outlet is four, so the inducer shown in Fig. 10 has higher boosting performance than the inducer shown in Fig. 9 (all third blade type).
  • FIG. 11 is a schematic diagram showing a cavitation occurrence state of an inducer according to an embodiment of the present invention.
  • the opening angle at the inlet is 3.60 °. Therefore, even if a cavity bubble 20 occurs on the negative BE surface of the first wing (all wings) 11 near the entrance, it is difficult to block because the flow path is very wide.
  • the size of the cavity bubble 30 generated on the suction surface near the inlet of the second blade 1-2 is generated on the suction surface of the first blade 1-1 due to the pressurizing action of the first blade 1-1. Cavitation bubbles to be smaller.
  • the flow path on the suction surface side of the second blades 1 and 2 has a relatively large opening angle of 2400 degrees with the adjacent first blade 1 and 1, so this flow path is also very blocked. Hateful.
  • the size of 40 is smaller than the cavitation bubble 30 generated on the suction surface of the second blade 1-2 because of the pressurizing action of the first blade 1-11 and the second blade 1-2.
  • the flow path on the suction surface side of the third blades 1 to 3 has a large opening angle with the adjacent first blade 11 to 1120 °, so this flow path is also difficult to block.
  • the inducer according to the present embodiment since the number of blades at the outlet is three, the inducer according to the present embodiment has a high boosting performance equivalent to the inducer (all blades three-blade type) shown in FIG. According to the above configuration, the inducer of the present invention has a high suction performance and a high boosting performance, and does not cause rotation imbalance.
  • the attachment positions of the three blades 1 with respect to the rotation shaft (shaft portion 5) are uniform in the circumferential direction of the rotation shaft. That is, the trailing edges 1 lb to 1 3 b of the three blades 1 are separated from each other by 120 ° as center angles around the rotation axis in a plane perpendicular to the rotation axis. They are arranged at equal intervals and are mounted so that the positions of the trailing edges 1 1 1 b to 1 3 b of the three blades 1 are the same on the meridian plane.
  • the present invention includes three wings 1 having different lengths, and the leading edges of these wings 1 are different from each other on the meridian plane of 1a-1_3_a.
  • the trailing edges 1— lb to 1-3 b of each blade 1 do not necessarily have to be evenly installed around the axis of rotation at intervals of 120 °, The positions of the trailing edges 1 1 1 b to 1 3 b on the meridian do not have to be aligned.
  • the present invention includes an inducer disposed on the upstream side of the main impeller so that the rotation axis coincides with the rotation axis of the main impeller, and the inducer. Available for pumps.

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

Abstract

La présente invention concerne un inducteur dans lequel les pales sont au nombre de une à une entrée et de trois à une sortie, le centre de gravité d’une lame entière étant positionné sur son axe de rotation pour empêcher qu’un déséquilibre en rotation ne se produise et où tant la performance d’aspiration que de suralimentation sont excellentes. La présente invention concerne également une pompe munie de l’inducteur. L’inducteur (8) comprend trois pales (1-1), (1-2) et (1-3) disposées du côté montant d’une turbine principale (7) et ayant des longueurs différentes les unes des autres le long des pales. Les trois pales (1-1), (1-2) et (1-3) sont disposées de manière à ce que la position des bords avant (1-1a), (1-2a) et (1-3a) des trois pales (1-1), (1-2) et (1-3) soient différentes les unes des autres dans les plans méridiens.
PCT/JP2004/018676 2004-12-08 2004-12-08 Inducteur et pompe WO2006061914A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2004/018676 WO2006061914A1 (fr) 2004-12-08 2004-12-08 Inducteur et pompe

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Application Number Priority Date Filing Date Title
PCT/JP2004/018676 WO2006061914A1 (fr) 2004-12-08 2004-12-08 Inducteur et pompe

Publications (1)

Publication Number Publication Date
WO2006061914A1 true WO2006061914A1 (fr) 2006-06-15

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10371151B2 (en) 2014-01-12 2019-08-06 Alfa Corporate Ab Self-priming centrifugal pump
US10422337B2 (en) 2014-01-12 2019-09-24 Alfa Laval Corporate Ab Self-priming centrifugal pump

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5038004Y1 (fr) * 1970-02-03 1975-11-05
JPH02238197A (ja) * 1988-09-16 1990-09-20 Nnc Ltd インペラポンプ
JPH1018992A (ja) * 1996-07-01 1998-01-20 Ishikawajima Harima Heavy Ind Co Ltd インデューサ付き液体ポンプ
JP2001289193A (ja) * 2000-04-05 2001-10-19 Ebara Corp 汚水ポンプ
JP2002516960A (ja) * 1998-05-27 2002-06-11 株式会社荏原製作所 ターボ機械の羽根車
US6435829B1 (en) * 2000-02-03 2002-08-20 The Boeing Company High suction performance and low cost inducer design blade geometry
WO2003038284A1 (fr) * 2001-11-01 2003-05-08 Ishigaki Company Limited Turbopompe

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5038004Y1 (fr) * 1970-02-03 1975-11-05
JPH02238197A (ja) * 1988-09-16 1990-09-20 Nnc Ltd インペラポンプ
JPH1018992A (ja) * 1996-07-01 1998-01-20 Ishikawajima Harima Heavy Ind Co Ltd インデューサ付き液体ポンプ
JP2002516960A (ja) * 1998-05-27 2002-06-11 株式会社荏原製作所 ターボ機械の羽根車
US6435829B1 (en) * 2000-02-03 2002-08-20 The Boeing Company High suction performance and low cost inducer design blade geometry
JP2001289193A (ja) * 2000-04-05 2001-10-19 Ebara Corp 汚水ポンプ
WO2003038284A1 (fr) * 2001-11-01 2003-05-08 Ishigaki Company Limited Turbopompe

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10371151B2 (en) 2014-01-12 2019-08-06 Alfa Corporate Ab Self-priming centrifugal pump
US10422337B2 (en) 2014-01-12 2019-09-24 Alfa Laval Corporate Ab Self-priming centrifugal pump

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