JPH01310103A - Moving blade device for axial flow fluid machine - Google Patents
Moving blade device for axial flow fluid machineInfo
- Publication number
- JPH01310103A JPH01310103A JP13754888A JP13754888A JPH01310103A JP H01310103 A JPH01310103 A JP H01310103A JP 13754888 A JP13754888 A JP 13754888A JP 13754888 A JP13754888 A JP 13754888A JP H01310103 A JPH01310103 A JP H01310103A
- Authority
- JP
- Japan
- Prior art keywords
- blades
- rotor
- connecting members
- rotor blades
- rotor blade
- 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
Links
- 239000012530 fluid Substances 0.000 title claims description 19
- 230000002093 peripheral effect Effects 0.000 claims abstract 5
- 230000008878 coupling Effects 0.000 claims 6
- 238000010168 coupling process Methods 0.000 claims 6
- 238000005859 coupling reaction Methods 0.000 claims 6
- 230000035882 stress Effects 0.000 abstract description 13
- 230000008646 thermal stress Effects 0.000 abstract description 6
- 230000000694 effects Effects 0.000 description 6
- 238000013016 damping Methods 0.000 description 5
- 238000006073 displacement reaction Methods 0.000 description 4
- 230000005284 excitation Effects 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 210000005036 nerve Anatomy 0.000 description 1
- 231100000989 no adverse effect Toxicity 0.000 description 1
- 230000003014 reinforcing effect Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Landscapes
- Turbine Rotor Nozzle Sealing (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、軸流流体機械の動翼装置、たとえば蒸気ター
ビンやガスタービン等に採用されている動翼装置の改良
に係り、特に動翼の外周部に動翼支持補強用の翼結合体
を有するこの種動翼装置の改良に関するものである。[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to an improvement of a rotor blade device for an axial flow fluid machine, for example, a rotor blade device employed in a steam turbine, a gas turbine, etc. This invention relates to an improvement of this type of rotor blade device having a blade joint for supporting and reinforcing the rotor blade on the outer periphery of the rotor blade.
従来一般に採用されている大容量のこの種動翼装置は、
複数個の動翼が回転体の周囲に周方向に所定の間隔を保
って配置されており、そしてさらにこの動翼の外周部に
、各動翼の外周側端に固定され、かつ、動翼相互間を連
結保持している翼結合体が設けられている。This type of large-capacity rotor blade device, which has been commonly used,
A plurality of rotor blades are arranged around the rotating body at predetermined intervals in the circumferential direction, and a rotor blade is fixed to the outer circumferential end of each rotor blade on the outer circumference of the rotor blade. A wing assembly is provided that connects and holds the blades together.
この翼結合体については、今までにも多くの改良がなさ
れ、その構造形状は多種、多岐にわたっているが、大き
く分類すると次の２種に分けられよう。その一つとして
１リング構成があげられる。Many improvements have been made to this wing joint so far, and its structural shapes are diverse and diverse, but they can be broadly classified into the following two types. One of them is a one-ring configuration.
すなわち全周すべての動翼を連結体（環状連結袋２２）
で連結するものであり、一般には全周１リング構造と云
われている。２っめは群翼構造と云われているもので、
たとえば実開昭５５−１６３４０５号公報に記載されて
いるように、複数個の動翼単位ごとに連結体に切れ目が
あるものである。In other words, all rotor blades on the entire circumference are connected to each other (annular connection bag 22).
It is generally said to have a one-ring structure around the entire circumference. The second one is called a group wing structure.
For example, as described in Japanese Utility Model Application Publication No. 55-163405, there is a cut in the connecting body for each of a plurality of rotor blade units.
このように形成されたこれらの動翼装置を、振動特性上
から比較してみると、全周１リング構造のものは、群翼
構造のものに比し、固有の振動モードの数は一般に多く
なるが、しかしタービン回転数の整数倍の周波数をもつ
励振力を受けた場合の共振点の数は、群翼構造のものに
比較しはるかに少なくなる。したがってタービンの運転
範囲において共振を回避した動翼設計を行う上で、この
全周１リング構造のものは非常に有利となる。Comparing these rotor blade devices formed in this way in terms of their vibration characteristics, we find that those with a one-ring structure all around the perimeter generally have a greater number of unique vibration modes than those with a group of blades. However, when receiving an excitation force having a frequency that is an integral multiple of the turbine rotational speed, the number of resonance points is far smaller than that of a blade group structure. Therefore, this full-circumference one-ring structure is very advantageous in designing rotor blades that avoid resonance in the operating range of the turbine.
このようにこの種大容量の動翼装置においては、振動特
性の面からは全周１リング構造のものが有利なのである
が、反面このものは全周連結されることから、熱や遠心
力による応力が一部分に集中しがちで、連結体が破損に
至る恐れがある。したがってこの全周一リング構造とす
る場合には、遠心力による機械的な応力及び熱応力が連
結体に影響しないように工夫する必要がある。In this type of large-capacity rotor blade system, a one-ring structure around the entire circumference is advantageous from the perspective of vibration characteristics, but on the other hand, since this type is connected all the way around, it is susceptible to heat and centrifugal force. Stress tends to be concentrated in one part, which can lead to damage to the connecting body. Therefore, when using this one-ring structure all around, it is necessary to take measures to prevent mechanical stress and thermal stress caused by centrifugal force from affecting the connecting body.
この全周１リング構造でありながら比較的連結体に影響
を及ぼさない、すなわち連結体に応力集中が生じない構
成として次のものが知られている。The following is known as a structure that has this one-ring structure all around the circumference but does not relatively affect the connecting body, that is, does not cause stress concentration on the connecting body.
すなわち第９図及び第１０図に基づきそのものを説明す
ると１回転体１の周囲には周方向に間隔を保って動翼２
が配置されており、またこの動翼の外周部に翼結合体Ｊ
が配置されているが、この翼結合体主は複数個の動翼を
連結している連結部材４と、これら連結部材間を接続す
る接続片５より構成されているのである。That is, to explain the matter based on FIGS. 9 and 10, rotor blades 2 are arranged around one rotating body 1 at intervals in the circumferential direction.
is arranged, and a blade assembly J is arranged on the outer periphery of this rotor blade.
The blade assembly is mainly composed of a connecting member 4 that connects a plurality of rotor blades, and a connecting piece 5 that connects these connecting members.
この場合第１０図から明らかとなるように２群の端部に
位置する動翼２ａ、２ｂには肩下げが行われ、すなわち
他の部分の動翼より短長に形成され、この短い動翼と連
結部材との間に接続片５が介在され、そしてこの接続片
は、テノン６のかしめにより連結部材４と結合されるよ
うになっている。In this case, as is clear from FIG. 10, the rotor blades 2a and 2b located at the ends of the second group are shoulder-down, that is, they are formed to have a shorter length than the rotor blades in other parts, and these short rotor blades A connecting piece 5 is interposed between the connecting member and the connecting member, and this connecting piece is connected to the connecting member 4 by caulking a tenon 6.
このように動翼群を形成する連結部材４と、これらの連
結部材間を結合している接続片５により、全体として全
周にわたり切れ目なく連結した１リング翼構造となされ
、かつ接続片の部分、すなわち連結部材の切れ目の部分
で応力集中が緩和されるように形成されているのである
。The connecting members 4 that form the rotor blade group and the connecting pieces 5 that connect these connecting members form a one-ring blade structure that is seamlessly connected over the entire circumference, and the connecting piece portion In other words, the connecting member is formed so that stress concentration is alleviated at the cut portion.
尚この装置に関連するものとして、たとえば実公昭６２
−１２８０３号公報、実開昭６１−５１４０５号公報が
挙げられる。In addition, as related to this device, for example,
-12803, and Japanese Utility Model Application Publication No. 61-51405.
以上のように構成された動翼装置であると、全周の動翼
が結合されることになり、前述もしたように励振力を受
けた場合の共振点の数は、群１Ａ構造のものに比し少な
くなり、また接続片の結合部、すなわち動翼のテノンと
このテノンに嵌合された接続片の穴との関係で、微小な
相対変化は許容されることから連結部材に悪影響を及ぼ
す応力集中は緩和され、この点では有効なものとなるの
であるが１反面この構成であると、隣接鮮麗を互に接結
する接続片が連結部材と同時にテノンによりかしめられ
ることから、同時かしめ作業に神経が費やされること、
また、この接続片を取付けるために、鮮麗の両端にある
動翼を肩下げしなければならず、他の動翼と異なる形状
に加工する必要があるなど、組立てや加工が複雑となる
嫌いがある。In the rotor blade device configured as above, the rotor blades around the entire circumference are connected, and as mentioned above, the number of resonance points when receiving an excitation force is lower than that of the group 1A structure. In addition, minute relative changes are allowed in the relationship between the connecting part of the connecting piece, that is, the tenon of the rotor blade and the hole in the connecting piece fitted to this tenon, so there is no adverse effect on the connecting member. On the one hand, this configuration reduces stress concentration and is effective in this respect, but on the other hand, with this configuration, the connecting pieces that connect adjacent pieces to each other are caulked by the tenon at the same time as the connecting member, so it is difficult to caulk at the same time. Nerves are expended on work,
In addition, in order to attach this connection piece, the rotor blades at both ends of the blade must be lowered, and they must be machined into a shape different from other rotor blades, which complicates assembly and processing. be.
さらに、このように形成された動翼装置の最も重大な璧
点は、接続片と連結部材とを動翼先端部のテノンをかし
めることにより固定するようにしているが、事故時や試
験時等、タービンの回転による遠心力がこの部材に大き
く作用した場合、この接続板と連結部材を固定している
テノン強度は必ずしも十分な余裕がなく、テノン強度に
悪影響を及ぼしてしまい１強度的な面で信頼性が低いと
いうことである。Furthermore, the most important point of the rotor blade device formed in this way is that the connecting piece and the connecting member are fixed by caulking the tenons at the tips of the rotor blades, but in the event of an accident or test, etc., when the centrifugal force due to the rotation of the turbine acts on this member, the tenon strength that fixes this connecting plate and the connecting member does not necessarily have enough margin, and the tenon strength is adversely affected, resulting in a single strength This means that reliability is low.
本発明はこれにかんがみなされたもので、その目的とす
るところは、上記従来技術の欠点をなくし、連結部材の
応力緩和が可能なことは勿論、加工２組立が簡単で、か
つ強度的にも問題のないこの種軸流流体機械の動翼装置
を提供するにある。The present invention has been developed in view of this, and its purpose is to eliminate the drawbacks of the prior art described above, to ease the stress of the connecting member, to simplify processing and assembly, and to improve the strength. The object of the present invention is to provide a rotor blade device for an axial flow fluid machine of this type that is free from problems.
本発明のもう一つの目的は、連結部材の応力緩和が可能
で、かつ強度的にも堅牢であることは勿論、さらに動翼
のねじれ振動を減衰することができるこの種軸流流体機
械の動翼装置を提供するにある。Another object of the present invention is to provide an axial flow fluid machine of this type that is capable of reducing stress in the connecting member and of being robust in terms of strength, as well as damping torsional vibrations of the rotor blades. Located in providing wing equipment.
さらに本発明のもう一つの目的は、蒸気タービンの効率
を向上させることのできる動翼装置を偉えた蒸気タービ
ンを提供するにある。Furthermore, another object of the present invention is to provide a steam turbine equipped with a moving blade device that can improve the efficiency of the steam turbine.
すなわち本発明は、動翼を群ごとに保持している連結部
材を、複数列に形成するとともに、この連結部材の周方
向端部が、隣接する連結部材の列間で同位置とならない
ように配置、すなわち連結部材の切れ目が千鳥状となる
ように配置して所期の目的を達成するようにしたもので
ある。That is, in the present invention, connecting members that hold rotor blades in groups are formed in multiple rows, and circumferential ends of the connecting members are not located at the same position between adjacent rows of connecting members. The intended purpose is achieved by arranging the connecting members in a staggered manner.
又この場合前記連結部材の列同志を抑圧接触させて動翼
上に固定させるようにすると動翼の振動減衰の点で有効
となるのである。Further, in this case, it is effective in damping vibrations of the rotor blades if the rows of the connecting members are brought into pressure contact and fixed on the rotor blades.
又前記連結部材の列間に所定の空隙を設け、この動翼装
置を蒸気タービンに採用することにより、タービンの効
率向上をはかったものである。Further, by providing a predetermined gap between the rows of the connecting members and employing this rotor blade device in a steam turbine, the efficiency of the turbine is improved.
すなわち以上のような構成であると、周方向に隣接して
いる動翼のすべてが、複数列ある連結部材のうちいずれ
かの連結部材にて互いに連結されることになり、全周の
動翼が連結された全周１リング構造のものと同一の作用
をなし、またこれらの結合が千鳥状結合であることから
、ある程度の相対変位は許容され、したがって遠心力に
よる応力や熱応力は許容され、また各動翼に設けられて
いるテノンが負う機械的負荷はすべて同一量で局部的に
大きな負荷となる部分はなくなり、また特に動翼は特殊
な形状のものを必要とせず、すなわち同一形状のもので
よく、動翼の加工は容易となるのである。In other words, with the above configuration, all of the rotor blades that are adjacent to each other in the circumferential direction are connected to each other by one of the connecting members in the plurality of rows, so that the rotor blades on the entire circumference Since it has the same effect as a full-circle ring structure with connected rings, and since these connections are staggered connections, a certain degree of relative displacement is allowed, and therefore centrifugal force stress and thermal stress are allowed. In addition, the mechanical loads carried by the tenons installed on each rotor blade are all the same amount, and there are no locally large loads, and the rotor blades do not need to have a special shape, that is, they have the same shape. This makes it easy to process the rotor blades.
またこの場合連結部材の列間に抑圧接触部があると、動
翼が振動した場合この部分が振動減衰手段として働くの
である。Furthermore, in this case, if there is a suppressing contact portion between the rows of connecting members, this portion acts as a vibration damping means when the rotor blade vibrates.
以下図示した実施例に基づいて本発明の詳細な説明する
。The present invention will be described in detail below based on the illustrated embodiments.
第１図及び第２図にはその動翼装置の要部が斜視図また
平面図で示されている。動翼２は回転体１の周囲に、径
方向にのび、かつ周方向に所定の間隔を保って配置され
ており、そして動翼２の先端には連結部材４ａ、４ｂを
取付けるための２個のテノン、すなわち蒸気流入側に位
置するテノン６ａと蒸気流出側に位置するテノン６ｂが
設けられている。1 and 2 show the main parts of the rotor blade device in a perspective view and a plan view. The rotor blades 2 extend radially around the rotating body 1 and are arranged at a predetermined interval in the circumferential direction, and two connecting members 4a and 4b are attached to the tips of the rotor blades 2. A tenon 6a located on the steam inflow side and a tenon 6b located on the steam outflow side are provided.
連結部材４ａ、４ｂは、それぞれ蒸気流入側と流出側に
、すなわち、略同−半径上で軸方向の異なる位置に２列
設けられている。蒸気流入側の連結部材４ａには１図で
は見えないが動翼間隔に合致したテノン穴が設けられて
おり、このテノン穴部を蒸気流入側テノン６ａに挿入し
た後、このテノン６ａをかしめることによりこの連結部
材４ａと動翼２との結合が行われる。すなわち連結部材
が動翼に固定される。同様に、蒸気流出側連結部材４ｂ
も、蒸気流出側テノン６ｂによって動翼に固定される。The connecting members 4a and 4b are provided in two rows on the steam inflow side and the steam outflow side, that is, at substantially the same radius but at different positions in the axial direction. Although not visible in Figure 1, the steam inflow side connecting member 4a is provided with a tenon hole that matches the rotor blade spacing, and after inserting this tenon hole into the steam inflow side tenon 6a, this tenon 6a is caulked. As a result, the connection member 4a and the rotor blade 2 are connected. That is, the connecting member is fixed to the rotor blade. Similarly, the steam outlet side connecting member 4b
is also fixed to the rotor blade by the steam outlet tenon 6b.
この場合連結部材は複数の動翼に跨がりそれぞれ複数の
動翼を連結して鮮麗構造を形成している。１つの鮮麗構
造を形成する翼本数は。In this case, the connecting member spans the plurality of rotor blades and connects the plurality of rotor blades to each other to form an elegant structure. How many wings form one beautiful structure?
通常４〜８本位である。第２図の場合には４本の場合が
示されている。ここで重要なことは、隣接鮮麗の境、す
なわち、連結部材の切れ目は、蒸気流入側連結部材４ａ
の切れロアと蒸気流出側連結部材４ｂの切れ口８が、互
に円周方向にずれて、隣接する同じ動翼間にないように
配置されることである。すなわち連結部材の周方向端部
が隣接列間で千鳥状となるように形成されることである
。Usually there are 4 to 8 pieces. In the case of FIG. 2, the case of four is shown. What is important here is that the boundary between adjacent lines, that is, the break between the connecting members, is the connection member 4a on the steam inflow side.
The lower cut and the cut 8 of the steam outlet side connecting member 4b are offset from each other in the circumferential direction and are arranged so as not to be located between adjacent rotor blades of the same type. That is, the circumferential end portions of the connecting members are formed in a staggered manner between adjacent rows.
このような翼連結が全周の翼についてなされている。こ
れにより、周方向に隣接するどの動翼も、蒸気流入側連
結部材４ａと蒸気流出側連結部材４ｂのうちどちらか一
方の連結部材で互に連結されることになり、全周の翼を
切れ目なく連結した全周１リング構造となり、機械的に
堅牢な動翼の保持が可能なことは勿論、共振点の少ない
構成となる。Such blade connections are made for the entire circumference of the blade. As a result, any rotor blades that are adjacent to each other in the circumferential direction are connected to each other by one of the steam inflow side connection member 4a and the steam outflow side connection member 4b, and the blades on the entire circumference are connected to each other by a cut. It has a single ring structure connected all around the circumference, which not only makes it possible to maintain a mechanically robust rotor blade, but also has a structure with fewer resonance points.
さらにまたこの構成があると、一部のテノン部のみに負
荷がかかることなく熱応力緩和も可能となるのである。Furthermore, with this configuration, thermal stress can be relaxed without applying a load to only a part of the tenon part.
すなわち連結部材が軸方向に並設されて固定されるので
、テノンが負う負荷はすべて同一となり、一部のテノン
のみが過負荷となることはないのである。又、一般にテ
ノンはテノン穴との関係は、テノン穴径がテノン径より
も、やや太き目に作られるのが普通で、このため、テノ
ンをかしめることによって連結部材４が動翼２に固定さ
れた後であっても、動翼と連結部材の円周方向、軸方向
の微小な相対変位は許容されるのである。That is, since the connecting members are arranged and fixed in parallel in the axial direction, the loads carried by all the tenons are the same, and only some tenons do not become overloaded. In addition, in general, the tenon hole is generally made to have a slightly thicker diameter than the tenon hole, so by caulking the tenon, the connecting member 4 can be attached to the rotor blade 2. Even after being fixed, small relative displacements between the rotor blade and the connecting member in the circumferential direction and the axial direction are allowed.
このようにこの構成であると、一般に全く切れ目のない
全周１リング構造とした時間順となる遠心力や熱応力等
による連結部材の伸び、及び動翼と連結部材の変形差な
どが充分許容され、また連結部材の切れ目で吸収される
ことにより連結部材に過大な応力が発生することはない
のである。With this configuration, the elongation of the connecting member due to centrifugal force, thermal stress, etc., and the difference in deformation between the rotor blade and the connecting member, etc., which are generally a one-ring structure with no breaks in the entire circumference, can be sufficiently tolerated. Moreover, excessive stress will not be generated in the connecting member because it is absorbed by the cut in the connecting member.
さらにまた本実施例であると、この他に翼振動に対する
減衰を高める効果を有効に発揮できる構造とすることも
可能なのである。すなわち、第２図を用いて説明すると
、蒸気流入側連結部材４ａと蒸気流出側連結部材４ｂと
を、互に円周方向に延びる接触面９で両者が抑圧接触と
なるように配置するのである。このようにすると、翼振
動発生時に、各動翼相互の相対振動変位、あるいは、動
翼のねじり振動による、動翼の蒸気流入側と流出側の相
対振動変位が生じた場合、この２つの連結部材の接触面
９に摩擦部分、すなわち振動減衰部分があるため、翼振
動の低減を図ることができるのである。Furthermore, in this embodiment, it is also possible to adopt a structure that can effectively exhibit the effect of increasing damping against blade vibration. That is, to explain using FIG. 2, the steam inflow side connecting member 4a and the steam outflow side connecting member 4b are arranged so that they are in suppressed contact at the contact surfaces 9 that extend in the circumferential direction. . In this way, when a relative vibration displacement occurs between each rotor blade or between the steam inlet side and the steam outlet side of the rotor blade due to torsional vibration of the rotor blade when blade vibration occurs, these two connections Since the contact surface 9 of the member has a frictional portion, that is, a vibration damping portion, it is possible to reduce blade vibration.
尚１以上説明してきた実施例では、一つの連結部材が鮮
麗として連結する翼の本数を４本となし、かつそれが全
周にわたり同じ本数の場合について説明してきたが、一
般に全周の翼本数は、種々の要件、たとえば、熱的、流
体的２強度的、振動的要件等から決められるものであり
、第２図の実施例のように、すべて４本ずつの鮮麗、す
なわち全周同一の鮮麗本数にできない場合がある。その
ような場合には各群の翼本数は異なることになるが、そ
の場合であっても本発明は適用可能である。この場合で
あっても、蒸気流入側の連結部材と蒸気流出側の連結部
材の切れ目は１円周方向の隣接する同じ翼間に重ならな
いようにすることは重要なことである。In the embodiments described above, the number of blades connected with one connecting member is four, and the number of blades is the same over the entire circumference, but in general, the number of blades connected on the entire circumference is is determined based on various requirements, such as thermal, fluid, strength, vibration requirements, etc., and as shown in the example shown in Fig. In some cases, it may not be possible to make a clear number. In such a case, the number of blades in each group will be different, but the present invention is applicable even in such a case. Even in this case, it is important that the cuts between the connection member on the steam inflow side and the connection member on the steam outflow side do not overlap between adjacent blades of the same circumferential direction.
尚第３図には、その例として蒸気流入側の連結部材４ａ
と流出側の連結部材４ｂによって連結される翼の本数が
夫々異なる（４本と５本）場合が示されている。又この
他の例として、蒸気流入側の連結部材で鮮麗として連結
される翼本数は全周同一であるが、隣接している蒸気流
出、側の連結部材間とでは翼本数が異なるような連結構
造の場合もあるであろう。In addition, in FIG. 3, as an example, a connecting member 4a on the steam inflow side is shown.
A case is shown in which the number of blades connected by the connecting member 4b on the outflow side is different (4 and 5). Another example is a connection in which the number of blades connected in a connecting member on the steam inflow side is the same all around, but the number of blades is different between adjacent connecting members on the steam outlet side. It may also be a structure.
さらに、以上述べた実施例では、連結部材は、全周にわ
たり、蒸気流入側と流出側の２列の場合について説明し
たが、第４図に示すように、全周の少なくとも一ケ所連
結部材が蒸気流入側４ａと蒸気流出側４ｂの２列設けら
れ、他の部分はただ１列の連結部材４であっても、この
２列の連結部材４ａ、４ｂと連結部材４とのそれぞれの
切れロア、８が１円周方向に隣接する同じｙｔ間に重な
らないようにすれば前述したものと同様な効果を奏する
であろう。Furthermore, in the embodiments described above, the connection members are arranged in two rows on the steam inflow side and the steam outflow side over the entire circumference, but as shown in FIG. Even if two rows are provided on the steam inflow side 4a and the steam outflow side 4b, and only one row of connecting members 4 is provided in the other parts, the respective cutting lowers of the two rows of connecting members 4a, 4b and the connecting member 4 , 8 do not overlap between the same yt adjacent in the circumferential direction, the same effect as described above will be obtained.
又さらに第５図には他の実施例が示されている。Furthermore, another embodiment is shown in FIG.
すなわちこの図は連結部材の周囲を断面したものである
が、動翼外周がテーパ１０を有するもので。That is, this figure is a cross-section of the periphery of the connecting member, and the outer periphery of the rotor blade has a taper 10.
複数列（図では２列）設けられている連結部材４ａ、４
ｂの、その隣接列間に所定の間隙ｇを設けるのである。Connecting members 4a, 4 provided in multiple rows (two rows in the figure)
A predetermined gap g is provided between adjacent rows of rows b.
このように形成すると、矢印１２で示すように動翼２に
付着した水分が遠心力によりすみやかにこの間隙ｇを介
して動翼装置外部へ排出され、水分によるタービン損失
を減少させることができるのである。すなわち、第１１
図はタービンの動翼装置周囲を示したもので、動翼２と
静翼２０とが交互に配置され蒸気が実線矢印に流れてい
るが、動翼２に付着した水分は実線矢印Ｒで示すように
流れ、間隙ｇより固定子２１側へ排出されるのである。When formed in this way, the moisture adhering to the rotor blade 2 is quickly discharged to the outside of the rotor blade device by centrifugal force through the gap g, as shown by the arrow 12, and turbine loss due to moisture can be reduced. be. That is, the 11th
The figure shows the area around the rotor blade device of a turbine. The rotor blades 2 and stationary blades 20 are arranged alternately, and steam flows in the direction of the solid line arrow. Moisture adhering to the rotor blade 2 is indicated by the solid line arrow R. It flows like this and is discharged from the gap g to the stator 21 side.
尚この水分排出をさらによくするために、第６図に示す
ように連結部材の内周面側に段差りを設けるようにする
と良好であろう。この場合この図のように動翼２の外周
部のテーパ部に段差の切込みを設けるようにしてもよい
し、テーパ部は平滑にして連結部材４ｂの偏部に突堤を
設けるようにしてもよいであろう。In order to further improve this water drainage, it would be good to provide a step on the inner circumferential surface side of the connecting member as shown in FIG. In this case, as shown in this figure, a step cut may be provided in the tapered portion of the outer circumference of the rotor blade 2, or the tapered portion may be made smooth and a jetty may be provided in the uneven portion of the connecting member 4b. It would be nice.
第７図にはさらに他の例が示されている。すなわち以上
述べてきた動翼装置は連結部材を翼に取付ける手段とし
て翼先端部に設けたテノンをかしめるものの場合につい
て説明してきたが、本発明は他の構成のものにも適用可
能であろう。すなわち第７図に示すように連結部材４ａ
、４ｂと動翼２との結合が嵌合結合の場合である。すな
わち翼先端部に設けられている円周方向に延びた２列の
あり溝１４．１５に連結部材４ａ、４ｂが挿入結合され
ているものの場合である。このものの場合であっても挿
入される連結部材は複数列に形成され、かつそれぞれの
連結部材の切れロア、８が、円周方向の隣接翼の同じ翼
間にならないよう、すなわち千鳥状に形成すれば、前述
のものとほぼ同様な効果を奏するであろう。第８図はも
う一つの例で動翼２と一体形に形成され円周方向に延び
る２本の連結部材４ａ、４ｂを、互に隣接翼間の接触部
で溶接（２０）等の手段で連結した場合のものである。Still another example is shown in FIG. That is, although the rotor blade device described above has been described in which a tenon provided at the tip of the blade is caulked as a means for attaching the connecting member to the blade, the present invention may be applied to devices with other configurations. . That is, as shown in FIG.
, 4b and the rotor blade 2 are fitted together. That is, this is the case where the connecting members 4a and 4b are inserted and connected to two rows of circumferentially extending dovetail grooves 14,15 provided at the tip of the blade. Even in this case, the connecting members to be inserted are formed in multiple rows, and the cut lowers 8 of each connecting member are formed in a staggered manner so that they are not located between the same blades of adjacent blades in the circumferential direction. If this is done, the effect will be almost the same as that described above. FIG. 8 shows another example in which two connecting members 4a and 4b integrally formed with the rotor blade 2 and extending in the circumferential direction are welded (20) or the like at the contact portion between adjacent blades. This is when they are connected.
この場合であっても円周方向に部分的に溶接しない切れ
ロア、８を設け、両者が円周方向の隣接する同じ翼間に
なければ良いのである。Even in this case, it is sufficient to provide a cut lower part 8 that is not partially welded in the circumferential direction, and that both of them are not located between the same adjacent blades in the circumferential direction.
以上種々述べてきたように、本発明の動翼装置によれば
、動翼を結合している翼結合体を、複数列の連結部材に
て形成するとともに、この連結部材の周方向端部が隣接
する連結部材間で千鳥状となるように配置したから、複
数個の動翼が連結部材により連結された。いわゆる鮮麗
構造を形成し、またこの連結部材が複数列千鳥状に配置
されていることがら−リング構造ともなり、堅牢にして
熱応力の吸収が可能なことは勿論、連結部材を支持して
いる動翼に遠心力による過大な応力が加わることなく、
かつ動翼の形状も全周同一のものを採用することが可能
となる。As described above, according to the rotor blade device of the present invention, the blade assembly that connects the rotor blades is formed by a plurality of rows of connecting members, and the circumferential ends of the connecting members are Since adjacent connecting members were arranged in a staggered manner, a plurality of rotor blades were connected by the connecting members. It forms a so-called beautiful structure, and since the connecting members are arranged in multiple rows in a staggered manner, it also has a ring structure, which is not only strong and capable of absorbing thermal stress, but also supports the connecting members. without applying excessive stress due to centrifugal force to the rotor blades.
Moreover, it becomes possible to use the same shape of the rotor blades all around the circumference.
また前記複数列の連結部材を、その列間で押圧接触させ
て動翼上に固定するようになしたから。Further, the plurality of rows of connecting members are fixed on the rotor blade by bringing them into pressure contact.
動翼のねじり振動や動翼の変位がこの抑圧接触部で減衰
され、したがって動翼装置の振動をも低減することがで
きる。Torsional vibration of the rotor blade and displacement of the rotor blade are attenuated by this suppressing contact portion, and therefore vibration of the rotor blade device can also be reduced.
さらに蒸気タービンの動翼装置に採用し、かつ前記軸方
向に隣接している連結部材間に所定の間隙を設けること
によって、前述した連結部材の応力緩和が可能なことは
勿論、動翼に付着した水分を速やかにこの間隙より排出
することができるので蒸気タービンの効率をも向上させ
ることができる。Furthermore, by adopting the rotor blade device of a steam turbine and providing a predetermined gap between the connecting members that are adjacent in the axial direction, it is possible to alleviate the stress of the connecting members as described above, and also make it possible to reduce the stress on the rotor blades. Since the absorbed moisture can be quickly discharged from this gap, the efficiency of the steam turbine can also be improved.
第１図は本発明の動翼装置の要部を示す一部断面斜視図
、第２図はその平面図、第３図は本発明の他の実施例を
示す平面図、第４図は本発明の他の実施例を示す一部断
面斜視図、第５図及び第６図は本発明の他の実施例を示
す連結部材周囲の縦断側面１．第７図及び第８図は本発
明の他の実施例を示す一部断面斜視図、第９図は従来の
動翼装置周囲を示す斜視図、第１０図は第９図のＡ−Ａ
線に沿う断面図、第１１図はタービンの要部を示す縦断
側面図である。
１・・・回転体、２・・・動翼、４ａ、４ｂ・・・連結
部材、第１ 口
茶３ 図
ｂ
へ
慕４１２］
ｂ
第 ５ 区
慕ろ困
第８図
月
第９図
第１０圓FIG. 1 is a partially sectional perspective view showing the essential parts of the rotor blade device of the present invention, FIG. 2 is a plan view thereof, FIG. 3 is a plan view showing another embodiment of the present invention, and FIG. FIGS. 5 and 6 are partially sectional perspective views showing other embodiments of the invention. 7 and 8 are partially sectional perspective views showing other embodiments of the present invention, FIG. 9 is a perspective view showing the surroundings of a conventional rotor blade device, and FIG. 10 is an A-A in FIG. 9.
FIG. 11 is a longitudinal sectional view showing the main parts of the turbine. 1...Rotating body, 2...Rotating blade, 4a, 4b...Connecting member, 1st Kuchicha 3 Figure b 412] b 5th Ward 412] circle
Claims (1)
に固定され、かつ所定数の動翼を跨いで動翼を群ごとに
保持している翼結合体とを備えた軸流流体機械の動翼装
置において、前記翼結合体を複数列の連結部材にて形成
するとともに、該連結部材の周方向端部が隣接する連結
部材間で千鳥状となるように配置したことを特徴とする
軸流流体機械の動翼装置。 ２、回転体の周囲に配置された複数個の動翼と、該動翼
に固定され、かつ所定数の動翼を跨いで動翼を群ごとに
保持している翼結合体とを備えた軸流流体機械の動翼装
置において、前記翼結合体を複数列の連結部材にて形成
するとともに、夫々の連結部材が跨いでいる動翼群が隣
接連結部材間では異なるように形成したことを特徴とす
る軸流流体機械の動翼装置。 ３、回転体の周囲に、径方向にのび、かつ周方向に所定
の間隔を保つて固定配置されている複数個の動翼と、該
動翼の外周端面にテノンにより固定され、かつ所定数の
動翼間に跨がり動翼を群ごとに保持している連結部材と
を備えた軸流流体機械の動翼装置において、前記連結部
材に隣接して少なくとももう一つの第２の連結部材を設
けるとともに、この第２の連結部材の動翼群の跨がりが
、前記連結部材と千鳥状にずれて配置されていることを
特徴とする軸流流体機械の動翼装置。 ４、前記連結部材と前記第２の連結部材とが所定の押圧
力をもつて接触配列されたことを特徴とする請求項３記
載の軸流流体機械の動翼装置。 ５、前記連結部材と前記第２の連結部材とが所定の間隙
を介して配列されたことを特徴とする請求項３記載の軸
流流体機械の動翼装置。 ６、回転体の周囲に、径方向にのび、かつ周方向に所定
の間隔を保つて固定配置されている複数個の動翼と、該
動翼の外周端面にテノンにより固定され、かつ該動翼間
を跨ぐように配置されて動翼相互間を連結保持している
環状連結装置とを備えた軸流流体機械の動翼装置におい
て、前記環状連結装置を、弓状の連結部材を突合わせて
環状に形成した有端環状体の複数列により形成するとと
もに、前記連結部材の突合わせ部分が、複数列ある有端
環状体の夫々が同一動翼間に位置しないように配置した
ことを特徴とする軸流流体機械の動翼装置。 ７、回転体の周囲に、径方向にのび、かつ周方向に所定
の間隔を保つて固定配管されている複数個の動翼と、該
動翼の外周端面に固定され、かつ該動翼間を跨ぐように
配置されて動翼相互間を連結保持している環状連結装置
とを備えた軸流流体機械の動翼装置において、前記環状
連結装置を、周方向に複数個に分割された有端環状体を
複数個並設させて形成するとともに、前記夫々の環状体
の端部が、並設された環状体間では同一翼間に位置しな
いように配置したことを特徴とする軸流流体機械の動翼
装置。 ８、動翼を有する回転子と、静翼を有する固定子とを備
え、前記回転子の動翼外周に、動翼を群ごとに保持して
いる動翼結合体を有する蒸気タービンにおいて、前記翼
結合体を複数列の連結部材にて形成するとともに、該連
結部材の周方向端部が隣接する連結部材列間で千鳥状と
なるように配置し、かつ前記連結部材の列間に所定の間
隙を設けるようにしたことを特徴とする蒸気タービン。 ９、回転体の周囲に固定配置された複数個の動翼と、該
動翼の外周端に固定され、かつ所定数の動翼を跨いで動
翼を群ごとに保持している動翼結合体とを備えた軸流流
体機械の動翼装置において、前記動翼結合体の少なくと
も一部を、軸方向に並設された複数列の連結部材にて形
成するとともに、該連結部材の周方向端部が隣接する列
間で千鳥状となるように配置したことを特徴とする軸流
流体機械の動翼装置。[Claims] 1. A plurality of moving blades arranged around a rotating body, and a blade that is fixed to the moving blades and holds the moving blades in groups across a predetermined number of moving blades. In the rotor blade device for an axial fluid machine, the blade assembly is formed of a plurality of rows of connecting members, and the circumferential ends of the connecting members are arranged in a staggered manner between adjacent connecting members. A rotor blade device for an axial flow fluid machine, characterized in that the blades are arranged so that 2. Equipped with a plurality of rotor blades arranged around a rotating body and a blade assembly that is fixed to the rotor blades and holds the rotor blades in groups across a predetermined number of rotor blades. In a rotor blade device for an axial fluid machine, the blade assembly is formed by a plurality of rows of connecting members, and the rotor blade groups straddled by each connecting member are formed to be different between adjacent connecting members. Characteristic moving blade device for axial flow fluid machinery. 3. A plurality of rotor blades extending radially around the rotating body and fixedly arranged at predetermined intervals in the circumferential direction, and a predetermined number of rotor blades fixed by tenons on the outer peripheral end surface of the rotor blades. A rotor blade device for an axial fluid machine comprising a connecting member that spans between the rotor blades and holds the rotor blades in groups, at least one second connecting member adjacent to the connecting member. A rotor blade device for an axial flow fluid machine, characterized in that the second connecting member is arranged astride the rotor blade group in a staggered manner with respect to the connecting member. 4. The rotor blade device for an axial fluid machine according to claim 3, wherein the connecting member and the second connecting member are arranged in contact with each other with a predetermined pressing force. 5. The rotor blade device for an axial fluid machine according to claim 3, wherein the connecting member and the second connecting member are arranged with a predetermined gap in between. 6. A plurality of rotor blades extending radially around the rotating body and fixedly arranged at predetermined intervals in the circumferential direction; In a rotor blade device for an axial flow fluid machine comprising an annular coupling device arranged to straddle the blades and connect and hold the rotor blades, the annular coupling device and the arcuate coupling member are butted together. The connecting member is formed by a plurality of rows of annular bodies formed into an annular shape, and the abutting portions of the connecting member are arranged so that the plurality of rows of annular bodies are not located between the same rotor blades. A rotor blade device for an axial flow fluid machine. 7. A plurality of rotor blades extending radially around the rotating body and fixedly piped at predetermined intervals in the circumferential direction, and a plurality of rotor blades fixed to the outer peripheral end surface of the rotor blades and between the rotor blades In the rotor blade device of an axial flow fluid machine, the rotor blade device is provided with an annular coupling device that is arranged to straddle the rotor blades and connect and hold the rotor blades, the annular coupling device is divided into a plurality of parts in the circumferential direction. An axial flow fluid characterized in that a plurality of end annular bodies are arranged in parallel, and the ends of the respective annular bodies are arranged so that they are not located between the same blades among the annular bodies arranged in parallel. Machine moving blade device. 8. A steam turbine comprising a rotor having moving blades and a stator having stator blades, and having a moving blade assembly holding moving blades in groups on the outer periphery of the moving blades of the rotor, The wing assembly is formed of a plurality of rows of connecting members, and the circumferential ends of the connecting members are arranged in a staggered manner between adjacent rows of connecting members, and a predetermined gap is formed between the rows of connecting members. A steam turbine characterized in that a gap is provided. 9. A plurality of rotor blades fixedly arranged around a rotating body, and a rotor blade coupling that is fixed to the outer peripheral end of the rotor blades and holds the rotor blades in groups across a predetermined number of rotor blades. In the rotor blade device for an axial fluid machine, at least a part of the rotor blade assembly is formed of a plurality of rows of connecting members arranged in parallel in the axial direction, and A rotor blade device for an axial fluid machine, characterized in that end portions are arranged in a staggered manner between adjacent rows.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63137548A JPH0681886B2 (en) | 1988-06-06 | 1988-06-06 | Axial flow machine blades |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63137548A JPH0681886B2 (en) | 1988-06-06 | 1988-06-06 | Axial flow machine blades |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01310103A true JPH01310103A (en) | 1989-12-14 |
| JPH0681886B2 JPH0681886B2 (en) | 1994-10-19 |
Family
ID=15201273
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP63137548A Expired - Lifetime JPH0681886B2 (en) | 1988-06-06 | 1988-06-06 | Axial flow machine blades |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0681886B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5498136A (en) * | 1993-09-17 | 1996-03-12 | Hitachi, Ltd. | Fluid machinery having blade apparatus and blade apparatus for fluid machinery |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5088402A (en) * | 1973-12-12 | 1975-07-16 | ||
| JPS5232401A (en) * | 1975-09-08 | 1977-03-11 | Hitachi Ltd | Indoor boiler control system |
-
1988
- 1988-06-06 JP JP63137548A patent/JPH0681886B2/en not_active Expired - Lifetime
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5088402A (en) * | 1973-12-12 | 1975-07-16 | ||
| JPS5232401A (en) * | 1975-09-08 | 1977-03-11 | Hitachi Ltd | Indoor boiler control system |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5498136A (en) * | 1993-09-17 | 1996-03-12 | Hitachi, Ltd. | Fluid machinery having blade apparatus and blade apparatus for fluid machinery |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0681886B2 (en) | 1994-10-19 |
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