JPH0457880B2 - - Google Patents
Info
- Publication number
- JPH0457880B2 JPH0457880B2 JP59063337A JP6333784A JPH0457880B2 JP H0457880 B2 JPH0457880 B2 JP H0457880B2 JP 59063337 A JP59063337 A JP 59063337A JP 6333784 A JP6333784 A JP 6333784A JP H0457880 B2 JPH0457880 B2 JP H0457880B2
- Authority
- JP
- Japan
- Prior art keywords
- rotor
- pressure side
- working fluid
- disk
- flow path
- 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.)
- Expired - Lifetime
Links
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
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/06—Rotors for more than one axial stage, e.g. of drum or multiple disc type; Details thereof, e.g. shafts, shaft connections
- F01D5/066—Connecting means for joining rotor-discs or rotor-elements together, e.g. by a central bolt, by clamps
-
- 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
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/08—Heating, heat-insulating or cooling means
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明は、ロータの外周に翼をつけた多段の軸
流圧縮機に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to a multi-stage axial flow compressor in which blades are attached to the outer periphery of a rotor.
〔発明の背景〕
従来のガスタービン用軸流圧縮機等のターボ機
械においては、例えば特開昭54−71215号公報に
開示されているように、ロータの外周に多数段の
動翼がデイスクを介して取付けられ、このロータ
をケーシング内で高速で回転させることにより、
作動流体を入口側から出口側に流しながら、順次
圧縮し所望の圧力の流体を必要個所に送るように
している。[Background of the Invention] In conventional turbomachines such as axial flow compressors for gas turbines, as disclosed in Japanese Patent Laid-Open No. 54-71215, multiple stages of rotor blades are mounted on a disk around the outer periphery of a rotor. By rotating this rotor at high speed inside the casing,
While the working fluid is flowing from the inlet side to the outlet side, it is sequentially compressed and the fluid at the desired pressure is sent to the required location.
このような構造において、軸流圧縮機を起動し
た場合、作動流体は流路を通り入口側から出口側
に流れていく間に圧力、温度が上昇していき起動
後間もない時点（起動後20分位）では流路に近い
デイスク外周部と、流路から離れたデイスク内周
部とでかなりの温度差が生じる。このため、この
ような時点ではデイスク内周部にかなりの周方向
引張応力が発生する。例えば、16段デイスクで起
動後20分の時点では、デイスク内周には外周との
温度差のための熱応力25Kgｆ／mm2が発生し、これ
と遠心応力50Kgｆ／mm2を加えると、デイスク内周
部には75Kgｆ／mm2の高応力が発生することにな
る。このため、通常使用されているデイスク材の
許容応力60Kgｆ／mm2に比べかなり高くなる。しか
し、デイスク材の許容応力を大きくするには限度
があり、なんとしても熱応力を10Kgｆ／mm2以下に
下げる必要があつた。 In such a structure, when the axial flow compressor is started, the pressure and temperature of the working fluid increase as it flows through the flow path from the inlet side to the outlet side, and the pressure and temperature rise shortly after startup (after startup). (about 20 minutes), a considerable temperature difference occurs between the outer circumference of the disk near the flow path and the inner circumference of the disk far from the flow path. Therefore, at such a point, a considerable tensile stress in the circumferential direction is generated in the inner peripheral portion of the disk. For example, 20 minutes after starting up a 16-stage disk, a thermal stress of 25 kgf/mm 2 occurs on the inner periphery of the disk due to the temperature difference with the outer periphery, and when this is added to centrifugal stress of 50 kgf/mm 2 , the disk A high stress of 75Kgf/mm 2 will be generated in the inner circumference. For this reason, the allowable stress is considerably higher than the allowable stress of 60 kgf/mm 2 for commonly used disk materials. However, there is a limit to increasing the allowable stress of the disk material, and it was necessary to lower the thermal stress to 10 Kgf/mm 2 or less at any cost.
本発明の目的は、上述の欠点がある起動後間も
ない時点において発生する過大の周方向引張熱応
力を減少させ、信頼性の高い軸流圧縮機を提供す
ることにある。
An object of the present invention is to provide a highly reliable axial flow compressor that reduces excessive circumferential tensile thermal stress that occurs immediately after startup, which has the above-mentioned drawbacks.
本発明は、高温、高圧の出口側作動流体を、ロ
ータの中心部の温度が低い間（起動時）のみ、弁
を開いて、ロータ中心部を通して低温、低圧の入
口側にバイパスさせることにより、ロータ中心部
を暖め、外周部と中心部との温度差を減少させ、
ロータ中心孔の熱応力を低下させるもので、熱解
析、応力解析の結果、本方式によると熱応力が
１／３に低下することを確認している。これによ
り、軸流圧縮機の繰り返し起動に伴うロータ中心
孔部の疲労強度を大きく向上させることができ
る。
The present invention bypasses the high-temperature, high-pressure outlet side working fluid through the rotor center to the low-temperature, low-pressure inlet side by opening the valve only while the temperature of the rotor center is low (at startup). Warms the center of the rotor and reduces the temperature difference between the outer periphery and the center.
This method reduces thermal stress in the rotor center hole, and as a result of thermal analysis and stress analysis, it has been confirmed that this method reduces thermal stress to 1/3. As a result, the fatigue strength of the rotor center hole due to repeated activation of the axial compressor can be greatly improved.
また弁の開閉を利用する為に、起動時等ロータ
中心部の温度が低いときにのみ作動流体をロータ
中心部の加熱源として利用し、定常的には弁を閉
じて流体効率を高めることが可能であり、すなわ
ちロータ中心部の加熱源としての利用をやめるこ
とにより、作動流体のエネルギー損失を抑えるこ
とができる。更にロータ中心部を暖めた作動流体
を作動流体主流路の上流側（つまり低圧側）に戻
すことにより、ロータ中心部を暖めた作動流体の
有効利用が図れる。 In addition, since the opening and closing of the valve is used, the working fluid is used as a heating source for the rotor center only when the temperature of the rotor center is low, such as during startup, and the valve is closed regularly to increase fluid efficiency. In other words, by not using the center of the rotor as a heating source, energy loss of the working fluid can be suppressed. Furthermore, by returning the working fluid that has warmed the rotor center to the upstream side (that is, the low pressure side) of the main working fluid passage, the working fluid that has warmed the rotor center can be used effectively.
以下、本発明の軸流圧縮機の一実施例を第１図
〜第５図により説明する。
Hereinafter, one embodiment of the axial flow compressor of the present invention will be described with reference to FIGS. 1 to 5.
第１図は軸流圧縮機のロータとケーシングの主
要部を示し、ロータの上半分は断面図となつてい
る。１はロータ、２はケーシング、３は動翼、４
は静翼、５は初段動翼の付いたスタブシヤフト、
６はデイスクであり、多数枚のデイスクをスタブ
シヤフト５とエンドデイスク７の間にはさみ、ス
タツキングボルト９によつて締付けることによつ
てロータを構成している。軸流圧縮機をガスター
ビンで使う場合この軸流圧縮機ロータと、タービ
ンロータとはトルクチユーブ８によつて連結され
ている。また各段デイスク６の中心部には、欠陥
除去のため一般には中心孔１０設けられている。 FIG. 1 shows the main parts of the rotor and casing of an axial flow compressor, with the upper half of the rotor being a sectional view. 1 is the rotor, 2 is the casing, 3 is the moving blade, 4
is a stator blade, 5 is a stubshaft with a first stage rotor blade,
Numeral 6 is a disk, and a rotor is constructed by sandwiching a large number of disks between a stub shaft 5 and an end disk 7 and tightening them with stacking bolts 9. When an axial compressor is used in a gas turbine, the axial compressor rotor and the turbine rotor are connected by a torque tube 8. Further, a center hole 10 is generally provided in the center of each stage disk 6 for removing defects.
１１は作動流体の流路で１１ａは入口側、１１
ｂは出口側である。１２は流路１１に近いデイス
ク外周部、１３は中心孔１０に近いデイスク内周
部である。１４は出口側デイスクの側面に設けた
半径方向のスリツトであり、１５は入口側デイス
クの側面に設けた半径方向のスリツトである。こ
のスリツト１４の部分の詳細図を第２図に示す。
はたこのスリツト１４の部分をロータの外周側か
ら見た図を第３図に示す。スリツト１４はこれら
の図からわかるように複数本、径方向に放射状に
設ける。これは図示はしていないが、出口側デイ
スクのスリツト１５についても同じである。２２
は中心孔１０の任意の位置に設けた弁であり、こ
の詳細図を第４図，第５図に示す。ここで１６は
固定板で、これはデイスク内周部１３に設けた溝
２３にはめ込んで固定されている。この固定板１
６にはベローズ１７が取り付けられており、その
先には弁輪１８が取り付けられている。図中、Ａ
は低温低圧側、Ｂは高温高圧側である。このよう
な構造の軸流圧縮機を起動した場合、作動流体は
流路１１の入口側１１ａから出口側１１ｂに流れ
ていく間に、圧力、温度が上昇していく。圧縮機
起動直後高温高圧側Ｂの作動流体は、固定板１６
に設けた多数の孔２０を通りかつ弁輪１８と弁体
１９とのすきま２１を通つて低温低圧側Ａに流
れ、従つてロータ各段デイスク６のデイスク内周
部１３の温度を上昇させることができる。この中
心孔１０を流過した作動流体は第１図に示すよう
にスリツト１５を経て主流路１１に戻る。そこで
デイスク内周部１３の温度がある程度上昇すると
これに近接しているベローズ１７が伸び、第５図
に示す如く、弁輪１８と弁体１９が密着し、高温
高圧側Ｂの作動流体の低温低圧側Ａへの流出を止
め、定常運転状態では作動流体がこのバイパスを
通つて流れない通常の圧縮機となる。 11 is a flow path for the working fluid; 11a is the inlet side;
b is the exit side. Reference numeral 12 indicates an outer peripheral portion of the disk near the flow path 11, and reference numeral 13 indicates an inner circumferential portion of the disk near the center hole 10. 14 is a radial slit provided on the side surface of the outlet side disk, and 15 is a radial slit provided on the side surface of the inlet side disk. A detailed view of this slit 14 is shown in FIG.
FIG. 3 shows a view of the slits 14 of the head seen from the outer circumferential side of the rotor. As can be seen from these figures, a plurality of slits 14 are provided radially in the radial direction. Although not shown, the same applies to the slit 15 on the exit side disk. 22
is a valve provided at an arbitrary position in the center hole 10, and detailed views thereof are shown in FIGS. 4 and 5. Here, reference numeral 16 denotes a fixing plate, which is fitted into a groove 23 provided in the inner peripheral portion 13 of the disk and fixed therein. This fixed plate 1
A bellows 17 is attached to the valve 6, and a valve ring 18 is attached to the tip of the bellows 17. In the figure, A
is the low temperature, low pressure side, and B is the high temperature, high pressure side. When an axial flow compressor having such a structure is started, the pressure and temperature of the working fluid increase as it flows from the inlet side 11a of the flow path 11 to the outlet side 11b. Immediately after starting the compressor, the working fluid on the high temperature and high pressure side B flows through the fixed plate 16.
Flows to the low-temperature, low-pressure side A through the numerous holes 20 provided in the valve ring 18 and the gap 21 between the valve ring 18 and the valve body 19, thus increasing the temperature of the inner peripheral portion 13 of the disk 6 of each stage of the rotor. Can be done. The working fluid that has passed through the central hole 10 returns to the main flow path 11 through the slit 15, as shown in FIG. Therefore, when the temperature of the inner circumferential portion 13 of the disk rises to a certain extent, the bellows 17 adjacent thereto expands, and as shown in FIG. The outflow to the low pressure side A is stopped, resulting in a normal compressor in which working fluid does not flow through this bypass in steady operating conditions.
前例のように弁を中心孔１０に設けないで、デ
イスク側面の半径方向のスリツト１４又は１５に
設けてもよい。第６図および第７図に示す例は、
デイスク側面の半径方向スリツト１５に設けたも
のである。デイスク内周部１３の半径方向スリツ
ト１５側にリング状のスリツト２４を設け、ここ
に形状記憶合金でできたリング２５をはめ込んで
おく。圧縮機の起動直後、デイスク内周部１３が
低温である間は、形状記憶合金でできたリング２
５と隣接デイスク端面２７との間にはすきま２６
が存在し、高温高圧側Ｂの作動流体は中心孔１
０、径方向スリツト１５を通つて低温低圧側Ａに
流れ、それによつてデイスク内周部１３は暖めら
れる。デイスク内周部１３を通過した作動流体は
更に第６図矢印の流れに従つてリング２５を設け
たスリツト１５を通過し、作動流体の流路１１の
途中に戻される。デイスク内周部１３の温度が上
昇すると形状記憶合金でできたリング２５も追従
して温度を上げ、形状記憶合金に設定したある温
度以上になると形状記憶合金でできたリング２５
が伸び、第７図に示す如く形状記憶合金でできた
リング２５と隣接デイスク端面とは密着し、高温
高圧側作動流体の低温低圧側への流出を止め、先
述の弁２２と全く同様な働きをする。 The valve may not be provided in the central hole 10 as in the previous example, but may be provided in a radial slit 14 or 15 on the side surface of the disk. The example shown in FIGS. 6 and 7 is
This is provided in the radial slit 15 on the side surface of the disk. A ring-shaped slit 24 is provided on the radial slit 15 side of the inner peripheral portion 13 of the disk, and a ring 25 made of a shape memory alloy is fitted into the slit 24. Immediately after starting the compressor, while the inner circumference of the disk 13 is at a low temperature, the ring 2 made of shape memory alloy
There is a gap 26 between 5 and the adjacent disk end surface 27.
exists, and the working fluid on the high temperature and high pressure side B flows through the center hole 1.
0, flows through the radial slit 15 to the low temperature and low pressure side A, thereby warming the disk inner circumference 13. The working fluid that has passed through the inner circumference of the disk 13 further passes through the slit 15 provided with the ring 25 in accordance with the flow shown by the arrow in FIG. 6, and is returned to the middle of the working fluid passage 11. When the temperature of the inner circumferential portion 13 of the disk rises, the ring 25 made of shape memory alloy follows and increases the temperature, and when the temperature exceeds a certain temperature set for the shape memory alloy, the ring 25 made of shape memory alloy
expands, and as shown in FIG. 7, the ring 25 made of shape memory alloy and the end face of the adjacent disk come into close contact, stopping the flow of the high-temperature, high-pressure side working fluid to the low-temperature, low-pressure side, and functions exactly the same as the valve 22 described above. do.
第８図は、一体ロータの圧縮機に対しての適用
例である。この場合は、中心孔１０、及び前述の
例における半径方向のスリツト１４，１５に代わ
る半径方向の放射状小孔２７，２８をドリル加工
によつて設ける。このようにして設けたバイパス
に対し、弁２２を中心孔１０に取り付けることに
より、前述の例と全く同様に、起動直後のロータ
の熱応力を軽減することができる。 FIG. 8 is an example of application to an integral rotor compressor. In this case, the central hole 10 and small radial holes 27, 28 are provided by drilling, instead of the radial slits 14, 15 in the previous example. By attaching the valve 22 to the center hole 10 with respect to the bypass provided in this way, it is possible to reduce the thermal stress of the rotor immediately after startup, just as in the above example.
上述の各実施例の構造によれば、起動直後、高
温の出口側作動流体をロータの中心部を通して低
圧の入口側にバイパスさせることにより、ロータ
の中心部を暖めロータ起動時の過大な熱応力を減
少させることができ、ロータの繰り返し起動、停
止に伴う疲労強度を高めることができる。さらに
本発明では、弁によつて、ロータ内周部の温度が
適切な温度以上になるとこのバイパス流路を閉じ
ることができ、定常運転中作動流体が低圧側に漏
れ流体性能を損うという心配もない。 According to the structure of each of the above-mentioned embodiments, immediately after startup, the high-temperature outlet side working fluid is bypassed through the center of the rotor to the low-pressure inlet side, thereby warming the rotor center and reducing excessive thermal stress at the time of rotor startup. It is possible to reduce fatigue strength caused by repeated starting and stopping of the rotor. Furthermore, in the present invention, the bypass flow path can be closed by the valve when the temperature of the inner peripheral part of the rotor exceeds an appropriate temperature, so there is no need to worry about the working fluid leaking to the low pressure side during steady operation and impairing fluid performance. Nor.
本発明により、現在要求の高まつている軸流圧
縮機の急速起動、急速立ち上げ、高速化、高圧力
比化に充分対処できるロータを提供することがで
きる。 According to the present invention, it is possible to provide a rotor that can sufficiently cope with the current increasing demands for rapid start-up, rapid start-up, high speed, and high pressure ratio of axial flow compressors.
以上説明したように、本発明によれば、起動後
間もない時点において発生する過大の周方向引張
熱応力を低減させ、信頼性を向上させることがで
き、また定常時には作動流体のエネルギー損失を
抑えることが可能である。更に、起動時にロータ
中心部の暖めに寄与した作動流体をロータの主流
路上流側（入口側）に戻すことにより、作動流体
の有効利用が図れる。
As explained above, according to the present invention, it is possible to reduce excessive circumferential tensile thermal stress that occurs immediately after startup, improve reliability, and reduce energy loss of the working fluid during steady state. It is possible to suppress it. Further, by returning the working fluid that has contributed to warming the rotor center during startup to the upstream side (inlet side) of the main flow path of the rotor, effective use of the working fluid can be achieved.
第１図は本発明の、実施例に係る多段軸流圧縮
機の要部の一部断面正面図、第２図および第３図
は第１図におけるスリツト部の拡大断面図および
ロータ外周からみた拡大図、第４図および第５図
はベローズ型弁の詳細を説明する断面図、第６図
および第７図は形状記憶合金を用いた弁の詳細を
説明する断面図、第８図は本発明の他の実施例に
係る多段軸流圧縮機の要部の一部断面正面図であ
る。
１…ロータ、２…ケーシング、３…動翼、４…
静翼、５…前スタブシヤフト、６…デイスク、７
…エンドデイスク、８…トルクチユーブ、９…ス
タツキングボルト、１０…中心孔、１１…流路、
１２…デイスク外周部、１３…デイスク内周部、
１４，１５…半径方向スリツト、１６…固定板、
１７…ベローズ、１８…弁輪、１９…弁体、２０
…孔、２１…すきま、２２…弁、２３…みぞ、２
４…リング、２５…形状記憶合金でできたリン
グ、２６…すきま、２７…隣接デイスク端面。
FIG. 1 is a partial cross-sectional front view of essential parts of a multistage axial flow compressor according to an embodiment of the present invention, and FIGS. 2 and 3 are enlarged cross-sectional views of the slit portion in FIG. 1 and viewed from the rotor outer periphery. The enlarged view, FIGS. 4 and 5 are sectional views explaining the details of the bellows type valve, FIGS. 6 and 7 are sectional views explaining the details of the valve using shape memory alloy, and FIG. FIG. 7 is a partially sectional front view of a main part of a multistage axial flow compressor according to another embodiment of the invention. 1... Rotor, 2... Casing, 3... Moving blade, 4...
Stationary blade, 5...front stubshaft, 6...disk, 7
... End disk, 8 ... Torque tube, 9 ... Stacking bolt, 10 ... Center hole, 11 ... Channel,
12...Disk outer circumference, 13...Disc inner circumference,
14, 15...Radial slit, 16...Fixing plate,
17...Bellows, 18...Valve ring, 19...Valve body, 20
...hole, 21...gap, 22...valve, 23...groove, 2
4...Ring, 25...Ring made of shape memory alloy, 26...Gap, 27...Adjacent disk end face.
Claims (1)
グ内で回転することにより流路内を流れる作動流
体を順次圧縮するロータを備えた多段の軸流圧縮
機において、前記ロータの中心部に低圧側から高
圧側にわたつて軸方向の孔を設け、この孔の低圧
側および高圧側両端部に径方向の流路を放射状に
設け、主流路の高圧側の作動流体の一部を、該高
圧側径方向流路、前記孔、及び前記低圧側径方向
流路を順次通して主流路の低圧側に戻すように構
成すると共に、前記ロータの中心部に設けられる
孔か前記径方向流路に、ロータ内部の温度によつ
て開閉する弁を入れ、ロータ内部の温度によつて
その作動流体の逃がし量を制御できるように構成
したことを特徴とする軸流圧縮機。 ２ 前記開閉弁として、ロータ内部の温度によつ
て変形する部材を用いたことを特徴とする特許請
求の範囲第２項記載の軸流圧縮機。[Scope of Claims] 1. A multi-stage axial flow compressor including a rotor having multiple stages of blades attached to its outer periphery and sequentially compressing a working fluid flowing in a flow path by rotating within a casing. An axial hole is provided in the center from the low-pressure side to the high-pressure side, and radial flow paths are provided radially at both ends of the hole on the low-pressure side and high-pressure side, and a portion of the working fluid on the high-pressure side of the main flow path is provided. is configured to return to the low-pressure side of the main flow passage through the high-pressure side radial flow path, the hole, and the low-pressure side radial flow path in order, and the hole provided in the center of the rotor An axial flow compressor characterized in that a valve that opens and closes depending on the temperature inside the rotor is inserted in the directional flow path so that the amount of working fluid released can be controlled depending on the temperature inside the rotor. 2. The axial flow compressor according to claim 2, wherein a member that deforms depending on the temperature inside the rotor is used as the on-off valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6333784A JPS60209603A (en) | 1984-04-02 | 1984-04-02 | axial compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6333784A JPS60209603A (en) | 1984-04-02 | 1984-04-02 | axial compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60209603A JPS60209603A (en) | 1985-10-22 |
| JPH0457880B2 true JPH0457880B2 (en) | 1992-09-14 |
Family
ID=13226320
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6333784A Granted JPS60209603A (en) | 1984-04-02 | 1984-04-02 | axial compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60209603A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2756117B2 (en) * | 1987-11-25 | 1998-05-25 | 株式会社日立製作所 | Gas turbine rotor |
| KR20180114765A (en) | 2017-04-11 | 2018-10-19 | 두산중공업 주식회사 | Retainer for gas turbine blade, turbine unit and gas turbine using the same |
| CN107246282A (en) * | 2017-08-17 | 2017-10-13 | 中南大学 | A kind of disc of conical profile combined rotor structure of the circumferential pull bar of gas turbine |
| CN107269316A (en) * | 2017-08-17 | 2017-10-20 | 中南大学 | A kind of disc of conical profile structure of gas turbine central draw bar type rotor |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5846801U (en) * | 1981-09-25 | 1983-03-29 | 株式会社東芝 | Turbine shaft cooling system |
-
1984
- 1984-04-02 JP JP6333784A patent/JPS60209603A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS60209603A (en) | 1985-10-22 |
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