JPH0942193A - Rotary pump and fixing method for rotary impeller - Google Patents
Rotary pump and fixing method for rotary impellerInfo
- Publication number
- JPH0942193A JPH0942193A JP7192129A JP19212995A JPH0942193A JP H0942193 A JPH0942193 A JP H0942193A JP 7192129 A JP7192129 A JP 7192129A JP 19212995 A JP19212995 A JP 19212995A JP H0942193 A JPH0942193 A JP H0942193A
- Authority
- JP
- Japan
- Prior art keywords
- side plate
- rotary
- boss
- fitting
- region portion
- 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.)
- Pending
Links
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
- F04D29/20—Mounting rotors on shafts
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は回転ポンプに係り、特
に、回転軸に対する回転羽根車の強固な嵌着技術に関す
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary pump, and more particularly to a technique for firmly fitting a rotary impeller to a rotary shaft.
【０００２】[0002]
【従来の技術】火力発電プラントにおいてボイラ系に高
圧水を供給するボイラ給水ポンプや原子力発電プラント
における原子炉系に高圧水を供給する原子炉給水ポンプ
等は、回転軸に複数枚の回転羽根車を取り付けて高速回
転させることにより遠心力によって昇圧する多段遠心ポ
ンプを使用している。2. Description of the Related Art A boiler feed pump for supplying high-pressure water to a boiler system in a thermal power plant or a reactor feed pump for supplying high-pressure water to a nuclear reactor system in a nuclear power plant is composed of a plurality of rotary impellers on a rotary shaft. It uses a multi-stage centrifugal pump that increases pressure by centrifugal force when it is attached and rotated at high speed.
【０００３】この給水ポンプの構造は、外胴，内胴，回
転体及び軸受の主要部に分けられる。外胴は頑丈な円筒
型であり、両端は頑丈な円板型カバーで塞がれている。
内胴は、高速回転する回転羽根車から吐き出される水流
の流れを変えて静圧を回復する機能を有するディフュー
ザまたはボリュートと、次の回転羽根車への流れを整流
する水返し羽根(案内羽根)を有するステージを備え、輪
切り型と水平２つ割れ型とがある。The structure of the water supply pump is divided into an outer case, an inner case, a rotating body and a main part of a bearing. The outer shell is a sturdy cylinder with both ends covered by a sturdy disc-shaped cover.
The inner shell is a diffuser or volute that has the function of changing the flow of water discharged from a rotating impeller rotating at high speed to restore static pressure, and a water return vane (guide vane) that rectifies the flow to the next rotating impeller. It is equipped with a stage that has a.
【０００４】発電プラントにおいて、給水ポンプは心臓
部と言えるほどの重要な機器であり、その故障は発電プ
ラントの停止に直結する場合もある。そのため、細部に
至るまで信頼性を重視した設計となっている。特に、高
速回転する回転羽根車は回転軸に強固に固着していなけ
ればならず、高い信頼性が要求されている。In the power plant, the water supply pump is an important device at the heart of the power plant, and its failure may directly lead to the shutdown of the power plant. For this reason, the design is focused on reliability in every detail. In particular, a rotary impeller that rotates at high speed must be firmly fixed to the rotary shaft, and high reliability is required.
【０００５】回転羽根車を回転軸に固着する方法は、回
転羽根車の中心に形成した嵌合穴の内壁と回転軸との嵌
合部に隙間を設け、回転軸と回転羽根車の間に配置した
キーによって軸の回転力を回転羽根車に伝えるように嵌
着するルーズフィット法と、回転羽根車を回転軸に焼き
嵌めによって強固に嵌着するタイトフィット法とがあ
る。ルーズフィット法で嵌着した場合は、熱変化や回転
数・流量変化が繰り返し付与されるとアンバランス振動
を生じ易いため、現在では、回転羽根車を回転軸に強固
に嵌着できて信頼性が高いタイトフィット法が多く用い
られている。回転羽根車をタイトフィット法で回転軸に
嵌着した場合であっても、焼き嵌めが緩んだ場合を考慮
して、回転軸と回転羽根車の間にはキーを配置して信頼
性を高めるようにしている。従って、タイトフィット法
による嵌着であっても、ルーズフィット法と同様に、回
転羽根車と回転軸にはキー溝加工がなされる。The method of fixing the rotary impeller to the rotary shaft is such that a gap is formed in the fitting portion between the inner wall of the fitting hole formed at the center of the rotary impeller and the rotary shaft, and the rotary shaft and the rotary impeller are provided. There are a loose fit method in which the arranged keys are fitted so as to transmit the rotational force of the shaft to the rotary impeller, and a tight fit method in which the rotary impeller is firmly fitted onto the rotary shaft by shrink fitting. When the loose fit method is used, unbalanced vibrations are likely to occur when heat changes and changes in the number of revolutions and flow rate are repeatedly applied.Therefore, the rotary impeller can now be firmly attached to the rotating shaft and reliability is improved. A tight fit method is often used. Even if the rotary impeller is fitted to the rotary shaft by the tight fit method, a key is placed between the rotary shaft and the rotary impeller to improve reliability in consideration of loose shrinkage fitting. I am trying. Therefore, even if the fitting is performed by the tight fitting method, key grooves are formed on the rotary impeller and the rotary shaft as in the loose fitting method.
【０００６】ところで、従来の遠心ポンプの回転羽根車
は、遠心力によって水を吐き出す羽根と円板状の側板に
より形成される複数の流路を備える翼部と、該翼部の中
心に形成されて回転軸の外周部と嵌合締結して該羽根車
を回転軸に強固に嵌着する円環状のボス部とからなる。
ボス部は回転羽根車を回転軸に対して安定に取り付ける
ための結合手段であって、軸方向に、側板と羽根の内周
端に連なる側板領域部と側板の厚みを越えて軸方向に突
出する突出領域部をもっている。そして、このボス部の
嵌合穴の内壁面には、回転軸に対する組立て分解性を考
慮して、軸方向中央部に逃げ加工が施されている。一般
に、ボス部に形成されている嵌合穴は、旋削で一括加工
して一定の内径に仕上げられる。従って、回転羽根車を
回転軸に焼き嵌めするときは均一な締代になる。By the way, a rotary impeller of a conventional centrifugal pump has a blade portion having a plurality of flow paths formed by blades for discharging water by a centrifugal force and a disk-shaped side plate, and is formed at the center of the blade portion. And an annular boss portion which is fitted and fastened to the outer peripheral portion of the rotary shaft to firmly fit the impeller to the rotary shaft.
The boss portion is a coupling means for stably attaching the rotary impeller to the rotary shaft, and axially protrudes beyond the thickness of the side plate and the side plate region connected to the inner peripheral ends of the side plate and the blade. Has a protruding area portion that Then, the inner wall surface of the fitting hole of the boss portion is provided with a relief processing at the central portion in the axial direction in consideration of assembling / disassembling property with respect to the rotating shaft. Generally, the fitting hole formed in the boss portion is collectively machined by turning to have a constant inner diameter. Therefore, when the rotary impeller is shrink-fitted onto the rotary shaft, a uniform interference is obtained.
【０００７】[0007]
【発明が解決しようとする課題】ボス部は、その外周部
に連なって形成された側板及び羽根によって拘束されて
実質的に大径部材となる側板領域部と外周が前記側板の
厚みを越えて軸方向に突出して解放された小径の突出領
域部とでは剛性が異なるために、焼き嵌めによる変形量
が相違する。相対的に小外径で低剛性の突出領域部は焼
き嵌めによる変形量が大きく、高剛性の側板領域部に比
較して大きい外形の膨れが生じる。ボス部の変形は、先
に説明したキー溝を押し広げるように作用してコーナ部
に応力集中を生じさせ、焼き嵌め締代が過大であると該
コーナ部で耐力を上回る応力が発生して塑性変形に至
る。そして、ボス部がこのような変形により円周上で均
一な締代量を維持することができなくなると、回転羽根
車全体が軸心に対して直角に固定されなくなって翼部に
倒れ現象が発生し、芯振れも発生する。The boss portion has a side plate region portion and an outer periphery which are constrained by a side plate and blades formed continuously with the outer peripheral portion thereof and become a substantially large diameter member, and the outer periphery exceeds the thickness of the side plate. Since the rigidity is different from that of the small-diameter protruding region that is projected and released in the axial direction, the amount of deformation due to shrink fitting differs. The projecting region having a relatively small outer diameter and low rigidity has a large amount of deformation due to shrinkage fitting, and has a larger outer shape swelling than the side plate region having high rigidity. The deformation of the boss portion acts to spread the key groove described above to cause stress concentration in the corner portion, and if the shrink fitting margin is excessive, stress exceeding the proof stress is generated in the corner portion. Leads to plastic deformation. When the boss portion cannot maintain a uniform tightening amount on the circumference due to such deformation, the entire rotary impeller cannot be fixed at a right angle to the axis, and the phenomenon of falling down on the blade portion may occur. Occurs, and runout also occurs.
【０００８】このような現象の発生を抑制するために焼
き嵌めによる締代を小さくすると、高速回転による遠心
力によって回転羽根車のボス部が膨張し、焼き嵌めによ
る緊縛力が減少し、あるいは消失する。焼き嵌めによる
緊縛力が減少すると、回転軸に対する回転羽根車の固定
がばらついて回転部分にアンバランス量が発生して振動
が増大したり、総ての駆動トルクがキーに作用して該キ
ーの降伏や回転羽根車のかじり付き、キーの剪断破壊等
が生じることになる。If the tightening margin due to shrinkage fitting is reduced in order to suppress the occurrence of such a phenomenon, the boss portion of the rotary impeller expands due to the centrifugal force due to high-speed rotation, and the binding force due to shrinkage fitting decreases or disappears. To do. When the binding force due to shrinkage fitting decreases, the fixing of the rotary impeller to the rotating shaft varies, an unbalance amount is generated in the rotating part, and vibration increases, or all the driving torque acts on the key to cause the key to move. Yielding, galling of the rotary impeller, and shear failure of the key will occur.
【０００９】以上のように、従来の回転ポンプにおける
回転軸と回転羽根車の焼き嵌めによる嵌合固定方法にお
いては、ボス部の剛性の不均一を考慮しておらず、嵌着
部の信頼性に問題があった。As described above, in the fitting and fixing method by shrink fitting the rotary shaft and the rotary impeller in the conventional rotary pump, the unevenness of the rigidity of the boss portion is not taken into consideration, and the reliability of the fitting portion is improved. I had a problem with.
【００１０】本発明の目的は、このような問題を解決し
て高速回転に適した回転ポンプ及び回転羽根車の固定方
法を提案することにある。An object of the present invention is to solve the above problems and propose a method for fixing a rotary pump and a rotary impeller suitable for high speed rotation.
【００１１】特に、遠心ポンプにおける回転羽根車を回
転軸に対して高信頼性をもって固着することができる嵌
着技術を提案することにある。In particular, it is an object of the present invention to propose a fitting technique capable of fixing the rotary impeller of the centrifugal pump to the rotary shaft with high reliability.
【００１２】[0012]
【課題を解決するための手段】本発明は、回転羽根車を
回転軸に強固に嵌着させるボス部と前記回転軸の嵌合部
の締代量を該ボス部の軸方向の位置に応じて異ならせて
該ボス部に異常な変形が発生しないようにした。SUMMARY OF THE INVENTION According to the present invention, a tightening amount of a boss portion for firmly fitting a rotary impeller to a rotary shaft and a fitting portion of the rotary shaft depends on an axial position of the boss portion. To prevent abnormal deformation of the boss portion.
【００１３】ボス部は、その外周に羽根を支える側板が
形成された側板領域部分と側板の厚みを越えて突出した
突出領域部分を備える。そこで、側板領域部分は締代を
多くして緊縛力を大きくし、突出領域部分は締代を少な
くして緊縛力を小さくすることにより、全体的には必要
な緊縛力（固着力）を確保するようにした。The boss portion has a side plate region portion on the outer periphery of which a side plate for supporting the blade is formed and a protruding region portion protruding beyond the thickness of the side plate. Therefore, the necessary tightening force (fixing force) is secured as a whole by increasing the tightening margin in the side plate area to increase the binding force and reducing the tightening margin in the protruding area to decrease the binding force. I decided to do it.
【００１４】[0014]
【作用】その外周に羽根を支える側板が形成された側板
領域部分は高剛性となり、側板の厚みを越えて突出した
突出領域部分は低剛性となる。従って、側板領域部分は
締代を多くして緊縛力を大きくし、突出領域部分は締代
を少なくして緊縛力を小さくすることによりボス部の異
常な変形を防止することができる。The side plate region where the side plates supporting the blades are formed on the outer periphery has a high rigidity, and the protruding region part protruding beyond the thickness of the side plate has a low rigidity. Therefore, it is possible to prevent abnormal deformation of the boss portion by increasing the tightening allowance in the side plate region portion to increase the binding force and reducing the tightening allowance in the protruding region portion to reduce the binding force.
【００１５】[0015]
【実施例】図１は、本発明の一実施例であるボイラ給水
ポンプの縦断側面図である。高速遠心ポンプの代表であ
るボイラ給水ポンプは、バーレルケーシング１の吸込口
２から吸込んだボイラ給水を、高速回転する主軸３に固
定されて該主軸３と共に回転する多段の回転羽根車４に
よって昇圧し、各段の回転羽根車４の外周に配列したデ
イフューザ５へ吐出して静圧を回復し、その後、ステー
ジ６によって外向きの流れを内向きに変える水返し羽根
で整流して次段の回転羽根車４へ導き、このような昇圧
過程を繰返して加圧した水を吐出口７から吐出する構造
である。FIG. 1 is a vertical sectional side view of a boiler feed pump according to an embodiment of the present invention. A boiler feed water pump, which is a representative of high-speed centrifugal pumps, boosts boiler feed water sucked from a suction port 2 of a barrel casing 1 by a multi-stage rotary impeller 4 fixed to a main shaft 3 rotating at high speed and rotating together with the main shaft 3. , The static pressure is restored by discharging to the diffuser 5 arranged on the outer periphery of the rotary impeller 4 of each stage, and then the stage 6 rotates the flow by rectifying it with a water return vane that changes the outward flow inward. The structure is such that the water is guided to the impeller 4 and the pressurized water is discharged from the discharge port 7 by repeating such a pressure increasing process.
【００１６】図２は、このボイラ給水ポンプ（遠心ポン
プ）における主軸３に固定された片吸込み回転羽根車４
の１つを示す斜視図である。回転羽根車４は焼き嵌めに
よって主軸３に強固に嵌着されており、キー溝にキー
（図示せず）を挿入してトルク伝達時に主軸３と回転羽
根車４の間に滑りが発生するのを防止するようにしてい
る。FIG. 2 shows a single suction rotary impeller 4 fixed to a main shaft 3 of the boiler feed water pump (centrifugal pump).
It is a perspective view showing one of the above. The rotary impeller 4 is firmly fitted to the main shaft 3 by shrink fitting, and when a key (not shown) is inserted in the key groove, slippage occurs between the main shaft 3 and the rotary impeller 4 during torque transmission. I try to prevent it.
【００１７】図３は、図２に示したように主軸３に固定
した回転羽根車４の縦断側面面である。回転羽根車４
は、羽根４ａと側板４ｂ，４ｃで囲まれた流路を中心と
し流水を加速する翼部４ｄと、主軸３の外周に強固に嵌
着して該回転羽根車４を該主軸３に固着する円環状のボ
ス部４ｅを備える。ボス部４ｅに形成された嵌合穴の内
壁及び主軸３の外周にはキー溝８が形成され、キー９が
挿入されている。FIG. 3 is a vertical cross-sectional side surface of the rotary impeller 4 fixed to the main shaft 3 as shown in FIG. Rotary impeller 4
Is firmly fitted to the outer periphery of the main shaft 3 and the blade portion 4d that accelerates running water around the flow passage surrounded by the blade 4a and the side plates 4b and 4c, and fixes the rotary impeller 4 to the main shaft 3. An annular boss portion 4e is provided. A key groove 8 is formed in the inner wall of the fitting hole formed in the boss portion 4e and the outer periphery of the main shaft 3, and a key 9 is inserted therein.
【００１８】図４は、回転羽根車４の縦断側面図であ
る。ボス部４ｅは、その外周部に連なって形成された側
板４ｃ及び羽根４ａによって拘束されて実質的に大径部
材となる側板領域部４ｅ1とその外周が前記側板４ｃの
厚みを越えて軸方向に突出して解放された小径の突出領
域部４ｅ2とを備え、嵌合穴４ｆはこれらを貫通してい
る。嵌合穴４ｆの内壁には環状の逃げ溝４ｇ，４ｈが形
成される。逃げ溝４ｇは嵌合穴４ｆの軸方向の中央部に
位置して主軸３に対する挿脱を円滑にするための逃げ溝
として機能し、逃げ溝４ｈは突出領域部４ｅ2の外端部
に位置してキー溝加工時の終端部の逃げ溝として機能す
る。FIG. 4 is a vertical sectional side view of the rotary impeller 4. The boss portion 4e has a side plate region 4e 1 that is substantially a large-diameter member when it is constrained by a side plate 4c and blades 4a that are formed continuously from the outer peripheral portion thereof, and its outer periphery exceeds the thickness of the side plate 4c in the axial direction. And a fitting region 4e 2 having a small diameter that is projected and released to the outside, and the fitting hole 4f penetrates them. Annular relief grooves 4g and 4h are formed on the inner wall of the fitting hole 4f. The escape groove 4g is located at the center of the fitting hole 4f in the axial direction and functions as an escape groove for facilitating the insertion and removal with respect to the main shaft 3, and the escape groove 4h is located at the outer end portion of the projecting region portion 4e 2. And functions as a relief groove at the end of the key groove.
【００１９】ボス部４ｅに形成された前記嵌合穴４ｆの
内径寸法は、側板領域部４ｅ1の内径Ｄａに対して突出
領域部４ｅ2の内径Ｄｂの方を若干大きくし、このボス
部４ｅの嵌合部の締代寸法は、突出領域部４ｅ2の締代
寸法δｂの方が側板領域部４ｅ1の締代寸法δａよりも
小さくなるようにすることにより、突出領域部４ｅ2に
発生する応力が過大になるのを抑制する。The inner diameter of the fitting hole 4f formed in the boss portion 4e is slightly larger at the inner diameter Db of the projected regions portion 4e 2 against the inner diameter Da of the side plate area portion 4e 1, the boss portion 4e tightening margin dimensions of the fitting portion of, by towards the fastening margin dimensions δb of the protruding area part 4e 2 is set to be smaller than the tightening margin dimension δa side plate area portion 4e 1, generating the protruding area part 4e 2 It suppresses the excessive stress.
【００２０】図５〜図７は、実測と解析によって求めた
焼き嵌め時のボス部４ｅの応力と摩擦トルクの関係を示
している。5 to 7 show the relationship between the stress and the friction torque of the boss portion 4e at the time of shrink fitting, which is obtained by actual measurement and analysis.
【００２１】図５は、焼き嵌め時の回転羽根車４のキー
溝８部の最大主応力（但し、材料の耐力との関係で示
す）と側板領域部４ｅ1の締代（但し、標準締代δｏと
の比として示す）との関係を示している。側板領域部４
ｅ1は、標準的締代δｏを越える大きな締代寸法δａと
しても、その外周が側板４ｃによって補強されて比較的
高剛性となっているために変形量が小さく、キー溝８部
の最大主応力は十分に小さい。これに対して従来構造羽
根車の突出領域部は、外径寸法が小さく剛性が低いため
に、側板領域部４ｅ1と同様の締代寸法δａとすると、
キー溝８部の最大主応力が過大になって塑性変形に至
る。しかし、本発明に従えば、突出領域部４ｅ2の嵌合
部の締代寸法δｂは、側板領域部４ｅ1に対して若干小
さくなるため、キー溝８部の最大主応力の増加を抑える
ことができる。FIG. 5 shows the maximum principal stress (however, it is shown in relation to the proof stress of the material) of the key groove 8 of the rotary impeller 4 at the time of shrink fitting and the tightening margin of the side plate region 4e 1 (however, the standard tightening). (Shown as a ratio to the generation δo)). Side plate area part 4
Even if e 1 is a large tightening dimension δa exceeding the standard tightening margin δo, its outer periphery is reinforced by the side plate 4c and has a relatively high rigidity, so the amount of deformation is small, and the maximum key groove 8 main The stress is small enough. On the other hand, since the protruding area of the conventional structure impeller has a small outer diameter and a low rigidity, if the tightening margin δa is similar to that of the side plate area 4e 1 ,
The maximum principal stress in the key groove 8 portion becomes excessive, leading to plastic deformation. However, according to the present invention, the interference dimension δb of the fitting portion of the protruding region portion 4e 2 is slightly smaller than that of the side plate region portion 4e 1 , so that an increase in the maximum principal stress of the key groove 8 portion is suppressed. You can
【００２２】図６は、ボス部４ｅの突出領域部４ｅ2の
締代寸法δｂを一定とし、該突出領域部４ｅ2の外径寸
法Ｄｃ（但し、標準外径Ｄｃｏとの比で示す）を変えた
場合の該突出領域部４ｅ2のキー溝８部の最大主応力
（但し、耐力との比として示す）を示している。ボス部
４ｅにおける突出領域部４ｅ2の外径寸法Ｄｃを多少変
えても、キー溝８部の最大主応力は殆ど変化せず、その
効果は小さい。FIG. 6 shows the outer diameter dimension Dc of the protruding area 4e 2 (shown as a ratio to the standard outer diameter Dco), with the tightening margin δb of the protruding area 4e 2 of the boss 4e being constant. The maximum principal stress (shown as a ratio to the proof stress) of the key groove 8 portion of the protruding region portion 4e 2 when changed is shown. Even if the outer diameter dimension Dc of the protruding region 4e 2 in the boss 4e is slightly changed, the maximum principal stress of the key groove 8 hardly changes, and the effect is small.
【００２３】図７は、側板領域部４ｅ1の締代寸法δａ
（但し、標準締代δｏとの比で示す）を変えた場合の焼
き嵌めによるボス部４ｅ（回転羽根車４）の摩擦トルク
（但し、回転ポンプ出力から求めた必要トルクとの比で
示す）を示している。全体の摩擦トルク（トータル値）
は、焼き嵌め部の面圧によって変化するため、剛性の高
い側板領域部４ｅ1の締代を大きくして面圧を高めるこ
とによってそのおおよそを決定できる。本発明では、突
出領域部４ｅ2の締代寸法δｂは、δａよりも自動的に
小さくなるが、図中（１）＋（２）と（２）＋（３）の
曲線を比較すると明らかなように、ボス部４ｅの全体で
は摩擦トルクが不足することがないようにすることがで
きる。FIG. 7 shows the tightening margin δa of the side plate region 4e 1.
Friction torque of the boss 4e (rotary impeller 4) due to shrinkage fitting (however, indicated by the ratio with the standard tightening margin δo) (however, indicated by the ratio with the required torque obtained from the rotary pump output) Is shown. Overall friction torque (total value)
Varies depending on the surface pressure of the shrink-fitting portion, so that it can be roughly determined by increasing the tightening margin of the highly rigid side plate region 4e 1 to increase the surface pressure. In the present invention, the tightening margin δb of the protruding region 4e 2 is automatically smaller than δa, but it is clear by comparing the curves (1) + (2) and (2) + (3) in the figure. As described above, it is possible to prevent the friction torque from being insufficient in the entire boss portion 4e.
【００２４】以上の実施例は、主軸３と回転羽根車４の
ボス部４ｅの間の締代寸法を該ボス部４ｅに形成する嵌
合穴４ｆの内径寸法Ｄａ，Ｄｂを変えて調整するように
したが、内径寸法Ｄａ，Ｄｂを同一寸法にし、主軸３の
外形寸法を変えて決めるようにすることもできる。この
場合には、主軸３の大径部と小径部の間に環状の逃げ溝
を形成するとよい。In the above embodiment, the tightening margin between the main shaft 3 and the boss 4e of the rotary impeller 4 is adjusted by changing the inner diameters Da and Db of the fitting hole 4f formed in the boss 4e. However, the inner diameters Da and Db may be the same, and the outer dimensions of the main shaft 3 may be changed. In this case, an annular relief groove may be formed between the large diameter portion and the small diameter portion of the main shaft 3.
【００２５】[0025]
【発明の効果】本発明は、回転羽根車を回転軸に嵌着す
るボス部において、その外周に羽根を支える側板が形成
された側板領域部分の締代を多くして緊縛力を大きく
し、側板の厚みを越えて突出した突出領域部分は締代を
少なくして緊縛力を小さくすることにより、全体的には
必要な緊縛力（固着力）を確保しつつ該ボス部の異常な
変形を防止することができる。According to the present invention, the binding force is increased by increasing the tightening margin of the side plate region portion where the side plate supporting the blade is formed on the outer periphery of the boss portion for fitting the rotary impeller to the rotating shaft. The protruding area that protrudes beyond the thickness of the side plate reduces the tightening margin to reduce the binding force, so that the necessary tying force (fixing force) can be secured while abnormal deformation of the boss portion is prevented. Can be prevented.
【００２６】従って、高速回転に適した回転ポンプ及び
回転羽根車を得ることができ、特に、遠心ポンプにおけ
る回転羽根車を回転軸に対して高信頼性をもって固着す
ることができる。Therefore, a rotary pump and a rotary impeller suitable for high-speed rotation can be obtained, and in particular, a rotary impeller in a centrifugal pump can be fixed to a rotary shaft with high reliability.
【図１】本発明の一実施例であるボイラ給水ポンプの縦
断側面図である。FIG. 1 is a vertical sectional side view of a boiler feed pump according to an embodiment of the present invention.
【図２】図１に示したボイラ給水ポンプの主軸に嵌着し
た１つの回転羽根車を示す斜視図である。FIG. 2 is a perspective view showing one rotary impeller fitted to the main shaft of the boiler feed water pump shown in FIG.
【図３】図２に示す主軸と回転羽根車の縦断側面図であ
る。FIG. 3 is a vertical sectional side view of the main shaft and the rotary impeller shown in FIG.
【図４】図２に示す回転羽根車の縦断側面図である。4 is a vertical cross-sectional side view of the rotary impeller shown in FIG.
【図５】回転羽根車におけるボス部の締代とキー溝の最
大主応力の関係を示す特性図である。FIG. 5 is a characteristic diagram showing a relationship between a tightening margin of a boss portion and a maximum principal stress of a key groove in a rotary impeller.
【図６】回転羽根車におけるボス部の突出領域部の外径
と該部のキー溝の最大主応力の関係を示す特性図であ
る。FIG. 6 is a characteristic diagram showing a relationship between an outer diameter of a protruding region portion of a boss portion and a maximum principal stress of a key groove of the rotary impeller.
【図７】回転羽根車におけるボス部の側板領域部及び突
出領域部の焼き嵌めの締代とキー溝の最大主応力の関係
を示す特性図である。FIG. 7 is a characteristic diagram showing the relationship between the interference of the shrinkage of the side plate region and the protruding region of the boss portion of the rotary impeller and the maximum principal stress of the key groove.
３…主軸、４…回転羽根車、４ａ…羽根、４ｂ，４ｃ…
側板、４ｅ…ボス部、４ｅ1…側板領域部、４ｅ2…突出
領域部、４ｇ…逃げ溝、８…キー溝。3 ... Spindle, 4 ... Rotary impeller, 4a ... Blade, 4b, 4c ...
Side plates, 4e ... boss, 4e 1 ... side plate area unit, 4e 2 ... protruding area part, 4g ... relief groove, 8 ... keyway.
Claims (9)
板に羽根を設けた回転羽根車の前記ボスを回転軸に強固
に嵌着して該回転羽根車を該回転軸によって回転するよ
うにした回転ポンプにおいて、 前記ボスは、前記側板の内周側に位置する側板領域部と
該側板の厚みを越えて軸方向に突出した突出領域部を備
え、前記突出領域部は側板領域部よりも少ない締代で回
転軸に嵌着するようにしたことを特徴とする回転ポン
プ。1. A boss of a rotary impeller provided with blades on a disk-shaped side plate that spreads radially from the outer circumference of the boss, and the boss is firmly fitted to a rotary shaft so that the rotary impeller is rotated by the rotary shaft. In the rotary pump described above, the boss includes a side plate region portion located on the inner peripheral side of the side plate and a protrusion region portion that axially protrudes beyond the thickness of the side plate, and the protrusion region portion is more than the side plate region portion. A rotary pump characterized by being fitted onto a rotary shaft with a small tightening margin.
の嵌合穴の内壁の軸方向中央部に環状の逃げ溝を備えた
ことを特徴とする回転ポンプ。2. The rotary pump according to claim 1, wherein the boss is provided with an annular relief groove in an axial center portion of an inner wall of a fitting hole with which the rotary shaft is fitted.
回転軸と嵌合する嵌合穴の内径を前記側板領域部に対し
て突出領域部を大きくしたことを特徴とする回転ポン
プ。3. The boss according to claim 1 or 2,
A rotary pump, characterized in that an inner diameter of a fitting hole for fitting with a rotary shaft is larger in a projecting region portion than in the side plate region portion.
は、前記ボスにおける前記側板の内周側に位置する側板
領域部に嵌着する嵌合部の径よりも該側板の厚みを越え
て軸方向に突出した突出領域部に嵌着する嵌合部の径を
小さくしたことを特徴とする回転ポンプ。4. The rotating shaft according to claim 1, wherein the rotation shaft exceeds the thickness of the side plate more than the diameter of the fitting portion fitted in the side plate region portion of the boss located on the inner peripheral side of the side plate. A rotary pump characterized in that a diameter of a fitting portion fitted in a projecting region portion projecting in an axial direction is reduced.
根車は、回転軸に多段に嵌着されたことを特徴とする回
転ポンプ。5. The rotary pump according to claim 1, wherein the rotary impeller is fitted on the rotary shaft in multiple stages.
板に羽根を設けた回転羽根車の前記ボスを回転軸に焼き
嵌めして固定する回転羽根車固定方法において、 前記ボスにおいて前記側板の内周側に位置する側板領域
部の締代に対して該側板の厚みを越えて軸方向に突出し
た突出領域部の締代を少なくしたことを特徴とする回転
羽根車固定方法。6. A rotary impeller fixing method of shrink-fitting and fixing the boss of a rotary impeller, which has blades on a disk-shaped side plate that spreads radially from the outer periphery of the boss, in the boss. A method for fixing a rotary impeller, characterized in that a tightening margin of a protruding region portion that axially protrudes beyond a thickness of the side plate is reduced with respect to a tightening margin of a side plate region portion located on the inner peripheral side.
嵌合する嵌合穴の内径を前記側板領域部に対して突出領
域部を大きくしたことを特徴とする回転羽根車固定方
法。7. The method of fixing a rotary impeller according to claim 6, wherein the boss has an inner diameter of a fitting hole for fitting with a rotary shaft, the projection area portion being larger than the side plate area portion.
域部に嵌着する嵌合部の径よりも突出領域部に嵌着する
嵌合部の径を小さくすることを特徴とする羽根車固定方
法。8. The blade according to claim 6, wherein the rotary shaft has a diameter of a fitting portion fitted to the protruding region portion smaller than a diameter of a fitting portion fitted to the side plate region portion. Car fixing method.
板に羽根を設けた回転羽根車の前記ボスを回転軸に焼き
嵌めして固定する回転羽根車固定方法において、前記ボ
スにおいて前記側板の内周側に位置する側板領域部の緊
縛力に対して該側板の厚みを越えて軸方向に突出した突
出領域部の緊縛力を小さくすることを特徴とする回転羽
根車固定方法。9. A rotary impeller fixing method for shrink-fitting and fixing the boss of a rotary impeller having blades on a disk-shaped side plate radially extending from the outer periphery of the boss, wherein the side plate is provided on the boss. A method for fixing a rotary impeller, characterized in that the binding force of a projecting region portion that axially projects beyond the thickness of the side plate is made smaller than the binding force of the side plate region portion located on the inner peripheral side of.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7192129A JPH0942193A (en) | 1995-07-27 | 1995-07-27 | Rotary pump and fixing method for rotary impeller |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7192129A JPH0942193A (en) | 1995-07-27 | 1995-07-27 | Rotary pump and fixing method for rotary impeller |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0942193A true JPH0942193A (en) | 1997-02-10 |
Family
ID=16286168
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP7192129A Pending JPH0942193A (en) | 1995-07-27 | 1995-07-27 | Rotary pump and fixing method for rotary impeller |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0942193A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008298287A (en) * | 2007-05-30 | 2008-12-11 | Nuovo Pignone Spa | Fixing system for rotor of rotating fluid machine |
| JP2012233410A (en) * | 2011-04-28 | 2012-11-29 | Mitsubishi Heavy Ind Ltd | Impeller |
| JP2016008537A (en) * | 2014-06-24 | 2016-01-18 | 株式会社Ihi | Centrifugal compressor |
| CN107559206A (en) * | 2017-10-13 | 2018-01-09 | 嘉利特荏原泵业有限公司 | First-stage double-absorption structure Double-casing symmetrical expression radial direction subdivision centrifugal multistage pump multiple centrifugal pump |
| WO2019078316A1 (en) * | 2017-10-20 | 2019-04-25 | 株式会社荏原製作所 | Pump, pump device, and method of disassembling pump device |
| CN114135652A (en) * | 2021-12-16 | 2022-03-04 | 新疆德勤互力工业技术有限公司 | Wear-resisting shaft sleeve structure for sealing speed reducer |
-
1995
- 1995-07-27 JP JP7192129A patent/JPH0942193A/en active Pending
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008298287A (en) * | 2007-05-30 | 2008-12-11 | Nuovo Pignone Spa | Fixing system for rotor of rotating fluid machine |
| JP2012233410A (en) * | 2011-04-28 | 2012-11-29 | Mitsubishi Heavy Ind Ltd | Impeller |
| JP2016008537A (en) * | 2014-06-24 | 2016-01-18 | 株式会社Ihi | Centrifugal compressor |
| CN107559206A (en) * | 2017-10-13 | 2018-01-09 | 嘉利特荏原泵业有限公司 | First-stage double-absorption structure Double-casing symmetrical expression radial direction subdivision centrifugal multistage pump multiple centrifugal pump |
| WO2019078316A1 (en) * | 2017-10-20 | 2019-04-25 | 株式会社荏原製作所 | Pump, pump device, and method of disassembling pump device |
| CN114135652A (en) * | 2021-12-16 | 2022-03-04 | 新疆德勤互力工业技术有限公司 | Wear-resisting shaft sleeve structure for sealing speed reducer |
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