JPS5882097A - Axial hydraulic machine - Google Patents
Axial hydraulic machineInfo
- Publication number
- JPS5882097A JPS5882097A JP56179673A JP17967381A JPS5882097A JP S5882097 A JPS5882097 A JP S5882097A JP 56179673 A JP56179673 A JP 56179673A JP 17967381 A JP17967381 A JP 17967381A JP S5882097 A JPS5882097 A JP S5882097A
- Authority
- JP
- Japan
- Prior art keywords
- vane
- stationary
- root
- movable
- attached
- 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
- F04D29/08—Sealings
- F04D29/16—Sealings between pressure and suction sides
- F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
- F04D29/164—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of an axial flow wheel
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
本発明はロータに取付けられた動翼およびケースに取付
けられた静翼を備える軸流流体機械に関するものである
。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an axial flow fluid machine including moving blades attached to a rotor and stationary blades attached to a case.
軸流流体機械りυえは軸流圧縮機は第1図および第2図
に示すように、ロータ1の外周面に取付けられた1II
h翼31と、ケース2の内周面に取・付けられた静翼4
′とを交互に組合せた構造からなシ。An axial flow compressor is a type of axial flow fluid machine, as shown in Figs. 1 and 2.
h blade 31 and stationary blade 4 attached to the inner peripheral surface of case 2
The structure consists of an alternating combination of `` and ``.
前記動翼には10,000rl)mの高速度で回転する
ロータlの遠心力、空気流れによる曲げ応力および振動
などが作用する。The centrifugal force of the rotor 1 rotating at a high speed of 10,000 rl) m, bending stress due to air flow, vibration, etc. act on the rotor blade.
4IK上記遠心力によfi#A3’は半径1方向に引張
られるため、ロータ1に設けた取付溝5と動翼根元部3
’a との嵌合具合によシ、動83′は取付溝5から
脱出するから、そのlIh翼先端の回転径が拡大する。4IK Since fi#A3' is pulled in one radial direction by the above centrifugal force, the attachment groove 5 provided in the rotor 1 and the rotor blade root 3
Depending on the fit with 'a', the movable member 83' escapes from the mounting groove 5, so that the rotation diameter of the tip of the lIh blade increases.
この回転径の拡大は前記嵌合が締め代であっても、ロー
タlおよび動翼3′の弾性範囲内における変形によシ回
避することが至難である。This enlargement of the rotational diameter is extremely difficult to avoid due to deformation within the elastic range of the rotor 1 and the rotor blade 3' even if the fitting is an interference fit.
一般に効率の見地から動翼3/とケース2との間のギャ
ップbは、遠心力と熱膨張による伸びを考慮し、動翼3
′がケース2に接触しないように予め最小に設定されて
いる。もし動翼3′がケース2に接触する場合を考慮し
て、ケース2の内周面が動翼3′の先端に対向する部分
に、第3図に示すように動g 3 /の回転幅に相応す
る摺動部材6、例えばバビットなどの軟質材が鋳込まれ
、あるいは装着されている。Generally, from the standpoint of efficiency, the gap b between the rotor blade 3/ and the case 2 is determined by taking into account elongation due to centrifugal force and thermal expansion.
' is preset to a minimum value so as not to contact the case 2. Considering the case where the rotor blade 3' comes into contact with the case 2, the inner circumferential surface of the case 2 has a rotational width of g 3 / as shown in FIG. A corresponding sliding member 6, for example a soft material such as Babbitt, is cast or fitted.
ところが動翼の取付溝5と動翼根元部3′1との嵌合具
合は加工公差および誤差によシ千差万別であるため、遠
心力による半径方向への脱出量、すなわち回転半径の拡
大量は各翼によシそれぞれ異なる。前記摺動部材6は動
翼3/の材質よシ軟質であるので1回転時に取付溝5か
ら脱出した動翼3′の先端とケース2の内周面に取付け
られた摺動部材6との接触によシ、摺動部材6は動翼3
′の先端によシ削シ取られる。このためjl[3’の脱
出量が零または少量のときには、動翼3′とケース2と
の間のギャップbはさらに拡大されるから、効率はさら
に低下する恐れがある。However, since the fit between the rotor blade attachment groove 5 and the rotor blade root 3'1 varies widely depending on processing tolerances and errors, the amount of escape in the radial direction due to centrifugal force, that is, the rotation radius The amount of expansion differs for each wing. Since the material of the sliding member 6 is softer than that of the rotor blade 3, the tip of the rotor blade 3' that escaped from the mounting groove 5 during one rotation and the sliding member 6 attached to the inner circumferential surface of the case 2 are easily connected to each other. Due to contact, the sliding member 6 is connected to the rotor blade 3
It is removed by the tip of . For this reason, when the escape amount of jl[3' is zero or small, the gap b between the rotor blade 3' and the case 2 is further enlarged, which may further reduce the efficiency.
また静翼41の先端とロータ1の外径および動翼の根元
部37aとの関係についても、効率の見地から静翼4′
の先端と翼根元部3′1との間のギャップCは最小に設
定されている。ところがケース2に取付けられた静翼4
Iは、回転時の遠心力により取付溝5から脱出した動翼
3′の根元部31a本発明は上記欠点を解消することを
目的とするモノテ、ロータに取付けられた動翼およびケ
ースに取付けられた静翼を備える軸流流体機械において
、前記動翼および静翼の一方または双方の先端部に摺動
部材を取付けたことを特徴とするものである。Also, regarding the relationship between the tip of the stator blade 41, the outer diameter of the rotor 1, and the root portion 37a of the rotor blade, the stator blade 4'
The gap C between the tip of the blade and the blade root portion 3'1 is set to a minimum. However, the stationary blade 4 attached to case 2
I is a root portion 31a of the rotor blade 3' which escaped from the mounting groove 5 due to centrifugal force during rotation.The present invention aims to solve the above-mentioned drawbacks. The axial flow fluid machine is equipped with a stator vane, characterized in that a sliding member is attached to the tip of one or both of the rotor vane and the stator vane.
以下本発明の実施例を図面について説明する。Embodiments of the present invention will be described below with reference to the drawings.
第4図および第5図は本実施例に使用される動翼の平面
図および正面図で、との動43はその根元部3aにアリ
溝6aが設けられると共に、先端部3bにダブルテール
形のアリ溝6bが設けられている。前記アリ溝6a、6
bには摺動部材7a。4 and 5 are a plan view and a front view of the rotor blade used in this embodiment. The rotor blade 43 is provided with a dovetail groove 6a at its root portion 3a, and has a double tail shape at its tip portion 3b. A dovetail groove 6b is provided. The dovetail grooves 6a, 6
b is a sliding member 7a.
7b、例えばバビットなどの密着性を有する軟質の合金
材がそれぞれ嵌入されている。この摺動部材7a、7b
は上記のようにアリ溝6a、6bを設けることなく、接
着剤によシ直接に動Ijt3の根元部3aおよび先端3
bにそれぞれ接着させてもよい。7b, a soft alloy material having adhesive properties, such as Babbitt, is fitted respectively. These sliding members 7a, 7b
As mentioned above, without providing the dovetail grooves 6a and 6b, the base part 3a and the tip 3 of the Ijt3 can be directly moved with adhesive.
They may be adhered to b.
#g6図および第7図は本実施例に使用される静翼の平
面図および正面図で、との静翼4はその先端に上記Wh
Jlt3と同様に摺動部材8が取付けられている。この
ような構造のlll11g3および静翼4を備える軸流
流体機械の構成は、第1図および第2図に示す従来例と
同一であるから1図面および説明を省略する。Figure #g6 and Figure 7 are a plan view and a front view of the stator blade used in this example, and the stator blade 4 has the above-mentioned Wh on its tip.
A sliding member 8 is attached like Jlt3. The configuration of the axial fluid machine including the ll11g3 and stationary blades 4 having such a structure is the same as the conventional example shown in FIGS. 1 and 2, so one drawing and explanation will be omitted.
本発明は上記のように構成したので、fiJI(3およ
び静翼4の先端に取付けた摺動部材7b、8が遠心力に
よりケース2の内周面およびlIJ翼根元部にそれぞれ
接触しても、摺動部材7b、8が廟耗するだけであるか
ら、動翼3および静翼4が破損して事故を起すのを防止
する仁とができる。同時に動翼3とケース2との間のギ
ャップbおよび靜Jl14とlIh14根元部3aとの
間のギャップCは零となるから、圧縮機の効率上、有利
となるばかりでなく、前記ギャップb、cが回転中に設
定ギャップ以上に拡大するのを防止すること−I1.!
できる。Since the present invention is configured as described above, even if the sliding members 7b and 8 attached to the tip of the fiJI (3 and the stationary blade 4) contact the inner circumferential surface of the case 2 and the base of the lIJ blade due to centrifugal force, Since the sliding members 7b and 8 only wear out, it is possible to prevent the moving blades 3 and the stationary blades 4 from being damaged and causing an accident. Since the gap b and the gap C between the base part 3a of the Jl14 and the lIh14 are zero, this is not only advantageous in terms of the efficiency of the compressor, but also the gaps b and c expand beyond the set gap during rotation. -I1.!
can.
以上説明したように本発明によれば、運転中に動翼およ
び静翼の各先端がケースおよび動翼根元部にそれぞれ接
触しても、破損事故を起すのを未然に防止することがで
きる。また運転中における動翼とケースとの間および静
翼と動翼根元部との閣の各ギャップを、設定ギャップ以
上に拡大するのを防止することができる。As explained above, according to the present invention, even if the tips of the rotor blade and the stator blade come into contact with the case and the base of the rotor blade, respectively, during operation, it is possible to prevent damage from occurring. Furthermore, it is possible to prevent the gaps between the moving blade and the case and between the stator blade and the root of the moving blade from expanding beyond the set gap during operation.
第1図および#I2図は従来の軸流圧縮機の断面図およ
びその要部の拡大詳細断面図、第3図は第1図のケース
の改良断面図、第4図および第5図は本発明の細流流体
機械に使用される動翼の一実施例を示す平面図および正
面図、第6図および第7図は本発明の軸流流体機械の静
翼の一実施例を示す平面図および正面図である。
3・・・動翼b3a・・・根元部、4・・・静翼、7a
、7b。
8・・・摺動部材。
代理人 弁理士 薄田利幸
YJl 目
第 2 図
3匁
χ 3 日
¥34 図
冗乙目
江
拓5 図
!−(−
f
v77 口Figures 1 and #I2 are a sectional view of a conventional axial flow compressor and an enlarged detailed sectional view of its main parts, Figure 3 is an improved sectional view of the case in Figure 1, and Figures 4 and 5 are from this book. FIGS. 6 and 7 are plan views and front views showing one embodiment of the rotor blades used in the trickle-flow fluid machine of the invention, and FIGS. It is a front view. 3... Moving blade b3a... Root part, 4... Stationary blade, 7a
, 7b. 8...Sliding member. Agent Patent Attorney Toshiyuki Usuda YJl 2nd Figure 3 Momme 3 ¥34 per day Figure 5! -(- f v77 mouth
Claims (1)
れた静翼を備える軸流流体機械において、前記動翼およ
び静翼の一方または双方の先端部に摺動部材を取付けた
ことを特徴とする細流流体機械。 2、静翼の先端に対向する動翼の根元部に摺動部材を取
付けたことを特徴とする特許請求の範囲第1項記載の細
流流体機械。 3、上記摺動部材は合金材からなることt−e徴とする
特許請求の範囲第1項または第2項記載の軸流流体機械
。[Scope of Claims] 1. In an axial flow fluid machine including a moving blade attached to a rotor and a stator blade attached to a case, a sliding member is attached to the tip of one or both of the moving blade and the stator blade. A trickle fluid machine characterized by: 2. The trickle fluid machine according to claim 1, characterized in that a sliding member is attached to the base of the rotor blade facing the tip of the stationary blade. 3. The axial flow fluid machine according to claim 1 or 2, wherein the sliding member is made of an alloy material.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP56179673A JPS5882097A (en) | 1981-11-11 | 1981-11-11 | Axial hydraulic machine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP56179673A JPS5882097A (en) | 1981-11-11 | 1981-11-11 | Axial hydraulic machine |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS5882097A true JPS5882097A (en) | 1983-05-17 |
Family
ID=16069868
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP56179673A Pending JPS5882097A (en) | 1981-11-11 | 1981-11-11 | Axial hydraulic machine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5882097A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60159398A (en) * | 1984-01-19 | 1985-08-20 | エムテイーユー・モトレン‐ウント・タービネン‐ユニオン・ミユンヘン・ジーエムビーエツチ | Blade wheel of axial flow compressor |
EP1942254A2 (en) * | 2006-12-28 | 2008-07-09 | General Electric Company | Methods and apparatus for fabricating a fan assembly for use with turbine engines |
-
1981
- 1981-11-11 JP JP56179673A patent/JPS5882097A/en active Pending
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60159398A (en) * | 1984-01-19 | 1985-08-20 | エムテイーユー・モトレン‐ウント・タービネン‐ユニオン・ミユンヘン・ジーエムビーエツチ | Blade wheel of axial flow compressor |
JPH0160680B2 (en) * | 1984-01-19 | 1989-12-25 | Mtu Muenchen Gmbh | |
EP1942254A2 (en) * | 2006-12-28 | 2008-07-09 | General Electric Company | Methods and apparatus for fabricating a fan assembly for use with turbine engines |
JP2008163946A (en) * | 2006-12-28 | 2008-07-17 | General Electric Co <Ge> | Method and apparatus for fabricating fan assembly for use with turbine engine |
EP1942254A3 (en) * | 2006-12-28 | 2011-08-03 | General Electric Company | Fan assembly |
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