JP2013537274A - Pump material design - Google Patents
Pump material design Download PDFInfo
- Publication number
- JP2013537274A JP2013537274A JP2013528174A JP2013528174A JP2013537274A JP 2013537274 A JP2013537274 A JP 2013537274A JP 2013528174 A JP2013528174 A JP 2013528174A JP 2013528174 A JP2013528174 A JP 2013528174A JP 2013537274 A JP2013537274 A JP 2013537274A
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- Japan
- Prior art keywords
- blade
- tip
- pump member
- section
- incident angle
- Prior art date
- Legal status (The legal status 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 status listed.)
- Granted
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- 238000000034 method Methods 0.000 description 8
- 239000012530 fluid Substances 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 1
- 238000012938 design process Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000000411 inducer Substances 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000012886 linear function Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 230000001629 suppression Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/12—Blades
-
- 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
-
- 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
- F04D29/24—Vanes
- F04D29/242—Geometry, shape
-
- 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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid pumps
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
ポンプ部材は、ハブのすぐ近くの第1のセクションおよび先端のすぐ近くの第2のセクションを有するブレード(20)と、選択された入射角分布に基づくキャビティ高さ分布と、構造上の要求に基づく選択されたブレード厚み分布と、を備える。結果として得られるキャビティ高さ分布は、第1のセクションおよび第2のセクションにおいてブレード厚みと一致し、ブレードに沿ってブレード厚みより大きくなっている。The pump member includes a blade (20) having a first section in the immediate vicinity of the hub and a second section in the immediate vicinity of the tip, a cavity height distribution based on the selected incident angle distribution, and structural requirements. And a selected blade thickness distribution based on. The resulting cavity height distribution is consistent with the blade thickness in the first and second sections and is greater than the blade thickness along the blade.
Description
本開示は、ポンプ部材に関し、より詳細には、ポンプ部材のための設計方法に関する。 The present disclosure relates to a pump member, and more particularly to a design method for a pump member.
流体ポンプは、軸流ポンプおよび遠心流ポンプを含む。従来の設計の慣行では一般に、キャビテーションにより若干の不安定性が誘発されながらも必要とされる吸引性能が達成される。先端隙間の増加、ケーシング処理、および先端渦抑制などの通常の従来の設計慣行では、キャビテーションにより誘発される不安定性を最小限に抑える成功の可能性は制限されており、しばしば吸引性能が低下する結果となる。 The fluid pump includes an axial pump and a centrifugal pump. Conventional design practices generally achieve the required suction performance while cavitation induces some instability. Normal traditional design practices such as increased tip clearance, casing handling, and tip vortex suppression limit the chances of success to minimize instability induced by cavitation and often reduce suction performance Result.
当業者には、開示された非限定的な実施例についての以下の詳細な説明からさまざまな特徴が明らかとなるであろう。詳細な説明に付随する図面は、上記のように簡単に説明可能である。 Various features will be apparent to those skilled in the art from the following detailed description of the disclosed non-limiting examples. The drawings that accompany the detailed description can be briefly described as described above.
図1を参照すると、ポンプ部材、インデューサ(inducer)、およびインペラのブレード20の概略図が示される。キャビテーションは、静圧が流体の蒸気圧の値より低い値に低下すると、ポンプ部材上で生じる。流体力学において多くの種類のキャビテーションが生じることが知られている。
Referring to FIG. 1, a schematic diagram of a pump member, an inducer, and an
式(1)、
φ=Cm/U=tan(β−α) (1)
に示される流れ係数φによって、入口子午線速度Cm、ブレード速さU、ブレード角β、および入射角αの関係が定義される。
Formula (1),
φ = C m / U = tan (β−α) (1)
The relationship between the inlet meridian velocity C m , the blade speed U, the blade angle β, and the incident angle α is defined by the flow coefficient φ shown in FIG.
本願で開示される設計思想は、入射角を従属変数とみなす従来のプロセスとは反対に、ブレード角βの値を、本質的に入射角を独立変数とする入射角αの関数とするものである。Stripling(1962)、Japikse(2001)、およびHashimoto(1997)に与えられている情報は、ブレード角βおよび入射角αを選択する従来の設計慣行を代表するものである。参照することによって本願に含まれる。 The design philosophy disclosed in this application is that the value of the blade angle β is essentially a function of the incident angle α with the incident angle as an independent variable, as opposed to the conventional process in which the incident angle is regarded as a dependent variable. is there. The information given to Stripling (1962), Japan (2001), and Hashimoto (1997) is representative of conventional design practices for selecting blade angle β and incident angle α. It is included in this application by reference.
従来のポンプ部材の設計方法は一般に、正の先端入射角を用いる。シュラウドのないポンプ部材では、この正の先端入射角は、先端隙間と組み合わされて、ポンプ部材の上流に進行することができる先端渦を生成する。この上流への流れは、しばしば逆流と呼ばれる。逆流強度および流量は、先端入射角および先端隙間によって決定される。逆流強度および流量があるレベルに到達すると、逆流は、隣接するポンプ部材ブレードと相互作用することになり、キャビテーション不安定性が生成されることになる。キャビテーション不安定性のモード形状は、逆流および隣接するブレード相互作用の協同によって決定される。 Conventional pump member design methods generally use positive tip incidence angles. In a pump member without a shroud, this positive tip incident angle is combined with the tip clearance to produce a tip vortex that can travel upstream of the pump member. This upstream flow is often referred to as backflow. The reverse flow intensity and flow rate are determined by the tip incident angle and the tip gap. When the backflow intensity and flow rate reach a certain level, the backflow will interact with adjacent pump member blades and a cavitation instability will be created. The mode shape of cavitation instability is determined by the cooperation of backflow and adjacent blade interaction.
ハブから先端までのポンプ部材の最大のど部ブレード厚みは一般に、半径の一次関数となる(図2)。最小および最大ブレード厚みは、構造上の要求によって決定される。従来のポンプ部材の設計プロセスでは、半径(r)にブレード角(β)の正接を掛けたものを定数に等しくなるように維持することによってブレード前縁角が定義される。この設計方法によって、キャビティ体積は、ブレード体積よりかなり大きいものとなる(図2)。これによって、キャビテーションにより誘発される不安定性が生じる。この欠点を解消するために、代替のブレード前縁角分布が必要とされる。 The maximum throat blade thickness of the pump member from the hub to the tip is generally a linear function of radius (FIG. 2). The minimum and maximum blade thickness is determined by structural requirements. In the conventional pump member design process, the blade leading edge angle is defined by keeping the radius (r) multiplied by the tangent of the blade angle (β) equal to a constant. With this design method, the cavity volume is much larger than the blade volume (FIG. 2). This causes instability induced by cavitation. To eliminate this drawback, an alternative blade leading edge angle distribution is required.
ブレード前縁角分布を定義する新規な方法は、ポンプ部材前縁のブレード角および結果として得られる入射角が調整される必要がある(図3)。ポンプ部材は、ハブのすぐ近くの第1のセクションおよび先端のすぐ近くの第2のセクションを有するブレードを備える。キャビティ高さ分布は、選択された入射角分布に基づく。選択されたブレード厚み分布は、構造上の要求に基づく。結果として得られるキャビティ高さ分布は、第1のセクションおよび第2のセクションにおいてブレード厚みと一致し、ブレードに沿ってブレード厚みより大きくなっている。すなわち、ハブ(hub)および先端(tip)における入射角(αh)、(αt)は、キャビティ高さが第1のセクションハブおよび第2のセクション先端のブレード厚みと一致するように選択される。 The new method of defining the blade leading edge angle distribution requires that the blade angle of the leading edge of the pump member and the resulting incident angle be adjusted (FIG. 3). The pump member includes a blade having a first section proximate the hub and a second section proximate the tip. The cavity height distribution is based on the selected incident angle distribution. The selected blade thickness distribution is based on structural requirements. The resulting cavity height distribution is consistent with the blade thickness in the first and second sections and is greater than the blade thickness along the blade. That is, the angles of incidence (α h ), (α t ) at the hub (hub) and tip (tip) are selected so that the cavity height matches the blade thickness of the first section hub and second section tip. The
この方法によって、キャビティ体積は、従来のポンプ部材のキャビティ体積よりかなり小さくなり、ブレード体積に大幅に近接する。キャビティ体積の低減によって、キャビテーションポンプ部材の不安定性が低減される。さらに、この方法によって、優秀な吸引性能が実現された。 By this method, the cavity volume is much smaller than the cavity volume of a conventional pump member and is in close proximity to the blade volume. By reducing the cavity volume, the instability of the cavitation pump member is reduced. Furthermore, excellent suction performance was realized by this method.
Claims (1)
選択された入射角分布と、
構造上の要求に基づく選択されたブレード厚み分布と、
選択された入射角分布に基づくキャビティ高さ分布と、
を備え、結果として得られるキャビティ高さ分布は、第1のセクションおよび第2のセクションにおいてブレード厚みと一致し、ブレードに沿ってブレード厚みより大きくなっていることを特徴とするポンプ部材。 A blade having a first section proximate the hub and a second section proximate the tip;
The selected incident angle distribution, and
Selected blade thickness distribution based on structural requirements; and
A cavity height distribution based on the selected incident angle distribution, and
And the resulting cavity height distribution matches the blade thickness in the first section and the second section and is greater than the blade thickness along the blade.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/US2010/048332 WO2012033495A1 (en) | 2010-09-10 | 2010-09-10 | Pumping element design |
Publications (2)
Publication Number | Publication Date |
---|---|
JP2013537274A true JP2013537274A (en) | 2013-09-30 |
JP5684390B2 JP5684390B2 (en) | 2015-03-11 |
Family
ID=43982215
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2013528174A Active JP5684390B2 (en) | 2010-09-10 | 2010-09-10 | Pump material design |
Country Status (5)
Country | Link |
---|---|
US (1) | US20130170974A1 (en) |
EP (1) | EP2614257A1 (en) |
JP (1) | JP5684390B2 (en) |
CN (1) | CN103080561B (en) |
WO (1) | WO2012033495A1 (en) |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3442220A (en) * | 1968-08-06 | 1969-05-06 | Rolls Royce | Rotary pump |
JPH07247984A (en) * | 1994-03-04 | 1995-09-26 | Kubota Corp | Axial flow pump |
JPH11247788A (en) * | 1998-02-27 | 1999-09-14 | Shin Meiwa Ind Co Ltd | Axial flow pump and aeration device having the same |
US6435829B1 (en) * | 2000-02-03 | 2002-08-20 | The Boeing Company | High suction performance and low cost inducer design blade geometry |
WO2004007970A1 (en) * | 2002-07-12 | 2004-01-22 | Ebara Corporation | Inducer, and inducer-equipped pump |
JP2004353655A (en) * | 2004-01-29 | 2004-12-16 | Sanso Electric Co Ltd | Radial impeller |
US20050129500A1 (en) * | 2003-12-16 | 2005-06-16 | Stangeland Maynard L. | Inducer tip vortex suppressor |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0772529B2 (en) * | 1988-06-20 | 1995-08-02 | 株式会社日立製作所 | Water turbine and its manufacturing method |
CN1017271B (en) * | 1988-11-09 | 1992-07-01 | 株式会社日立制作所 | Water turbine |
-
2010
- 2010-09-10 EP EP10755047.7A patent/EP2614257A1/en not_active Withdrawn
- 2010-09-10 CN CN201080069026.1A patent/CN103080561B/en active Active
- 2010-09-10 JP JP2013528174A patent/JP5684390B2/en active Active
- 2010-09-10 US US13/821,014 patent/US20130170974A1/en not_active Abandoned
- 2010-09-10 WO PCT/US2010/048332 patent/WO2012033495A1/en active Application Filing
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3442220A (en) * | 1968-08-06 | 1969-05-06 | Rolls Royce | Rotary pump |
JPH07247984A (en) * | 1994-03-04 | 1995-09-26 | Kubota Corp | Axial flow pump |
JPH11247788A (en) * | 1998-02-27 | 1999-09-14 | Shin Meiwa Ind Co Ltd | Axial flow pump and aeration device having the same |
US6435829B1 (en) * | 2000-02-03 | 2002-08-20 | The Boeing Company | High suction performance and low cost inducer design blade geometry |
WO2004007970A1 (en) * | 2002-07-12 | 2004-01-22 | Ebara Corporation | Inducer, and inducer-equipped pump |
US20050129500A1 (en) * | 2003-12-16 | 2005-06-16 | Stangeland Maynard L. | Inducer tip vortex suppressor |
JP2004353655A (en) * | 2004-01-29 | 2004-12-16 | Sanso Electric Co Ltd | Radial impeller |
Also Published As
Publication number | Publication date |
---|---|
WO2012033495A1 (en) | 2012-03-15 |
EP2614257A1 (en) | 2013-07-17 |
CN103080561A (en) | 2013-05-01 |
CN103080561B (en) | 2016-06-15 |
JP5684390B2 (en) | 2015-03-11 |
US20130170974A1 (en) | 2013-07-04 |
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