JPS5846244A - Reduction gear for gas turbine - Google Patents
Reduction gear for gas turbineInfo
- Publication number
- JPS5846244A JPS5846244A JP56145152A JP14515281A JPS5846244A JP S5846244 A JPS5846244 A JP S5846244A JP 56145152 A JP56145152 A JP 56145152A JP 14515281 A JP14515281 A JP 14515281A JP S5846244 A JPS5846244 A JP S5846244A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- output
- gas turbine
- ring gear
- frequency
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/089—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
Abstract
Description
【発明の詳細な説明】
この発明は、小型の移動可能な１軸式ガスタービン発電
機に用いるガスタービン減速機に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a gas turbine speed reducer used in a small, movable, single-shaft gas turbine generator.
わが国の商業用交流電力の周１・′波数は、東日本では
ＳＯヘルツ、西日本では６０ヘルツであシ、シ九がって
、交流発電機もそれぞれＯＩ５波数に合致した回転数で
運転する必要がある。そこで、ガスタービン発電機では
、ガスタービンＯｗＡ転数を変えて、電力同波数Ｏ切換
えを行なうことも考えられるが、特にｌ軸式ガスタービ
ンは定格回転数以外の運転では著しく出力が低下する欠
点がある。The frequency of commercial AC power in Japan is SO Hz in eastern Japan, and 60 Hz in western Japan, so AC generators must also be operated at rotational speeds that match the OI5 wavenumber. be. Therefore, in a gas turbine generator, it is possible to change the gas turbine OwA rotation speed and switch the power to the same wave number O, but the disadvantage of L-shaft gas turbines in particular is that the output decreases significantly when operating at a speed other than the rated speed. There is.
この発明紘、上記欠点に鑑みてなされたもので、交流電
力の周波数の切換を変速機で行なうとともに、その変速
機の機構は切換動作が確爽で、シフトフォークとリング
歯車との摩耗がなく、保守が容品で耐久性がよいうえに
、回転エネルギＯ損失の少ないガスタービン減速機を提
供することを目的とする。This invention was made in view of the above-mentioned drawbacks.The frequency of alternating current power is switched by a transmission, and the transmission mechanism has a reliable switching operation, and there is no wear between the shift fork and the ring gear. An object of the present invention is to provide a gas turbine speed reducer that is easy to maintain, has good durability, and has low loss of rotational energy.
以下、この発明の一爽施例を図面にしたがって説明する
。EMBODIMENT OF THE INVENTION Hereinafter, a refreshing example of this invention will be described according to the drawings.
第１図において、ｌはガスタービン鵞からの回転出力が
伝達される入力軸で、ケース３内に装着され丸軸受４を
介して軸支されて−る。この入力軸１には互ｉＫ拳数の
異なる第１０人力歯車５と第２の入力歯車６とが固定さ
れておシ、第１の入力歯車５の歯数は１１２の入力歯車
６０歯数よｐ少なく、第１０人力歯車５は電力周波数５
０ヘルツ用で、ｊｌＨ！の入力歯車６は６０ヘルツ用で
ある。In FIG. 1, reference numeral 1 denotes an input shaft to which rotational output from the gas turbine is transmitted, and is mounted within a case 3 and supported via a round bearing 4. A tenth human power gear 5 and a second input gear 6 having different numbers of teeth are fixed to the input shaft 1, and the number of teeth of the first input gear 5 is 60 teeth of the 112 input gear. p less, the 10th human power gear 5 has a power frequency of 5
For 0 hertz, jlH! The input gear 6 is for 60 Hz.
７は交流発電機８へ、入力軸ｌからの駆動力を伝達する
出力軸で、この出力軸７には回転自在の軸受９を介して
第１の出力歯車１Ｇと第２の出力歯車１１とが設けられ
ておシ、この第１の出力歯車ｌＯと第２０出力歯阜ｌｌ
は、それぞれ第１０人力歯車５と第２の入力歯車６とに
常時かみ合うように設定されてｉる。7 is an output shaft that transmits the driving force from the input shaft l to the alternator 8, and this output shaft 7 is connected to a first output gear 1G and a second output gear 11 via a rotatable bearing 9. are provided, and the first output gear lO and the 20th output gear ll
are set to always mesh with the tenth human power gear 5 and the second input gear 6, respectively.
１２は出力軸７と同軸に第１また紘第２の出力歯車ｌＯ
・１１にかみ合うように設定されたリング歯車で、出力
軸７の軸方向１３ヘシフトすることによって、上記第１
の出力歯車１０もしくは第２の出力歯車１１と、出力軸
７に固定された第３の出力歯車１４を介して出力軸７と
を選択的に連結することができる。12 is the first or second output gear lO coaxially with the output shaft 7.
・By shifting in the axial direction 13 of the output shaft 7 with a ring gear set to mesh with the first
The output gear 10 or the second output gear 11 can be selectively connected to the output shaft 7 via the third output gear 14 fixed to the output shaft 7.
１５は上記リング歯車１２の軸方向１３０位置を設定Ｏ
出力歯車１４に設けられた収納孔１６内にスプリング１
７が内蔵されて、その上部に当接し九ボール１８を押圧
して、リング歯車１２の内周の歯を１枚だけ纏３０で示
すように切）欠い九係止溝１Ｇ 、 １９にボール１８
の上半球が挿入して、リング歯車ｌ！の軸方向１３０位
置を設定している。すなわち、リング歯車１８に設けら
れ九左儒Ｏ係止溝１９と第３の出力歯車１４に設けられ
た収納孔１６とにボール１８が介在して、リング歯車１
２０位置を第１の出力歯車１０と第３の出力歯車１４と
を連結してリング歯車１２０軸方向１３への移動を阻止
する。ｔた、リング歯車１２を軸方向１３ｏ左方へシフ
トして、リング歯車１２の右側の停止溝１９と収納孔１
６とにボール１８を介在させれば、第３０出力歯車１４
と第３の出力歯車１４とが連結されることＫｔＤ出力軸
７０回転数が切シ換わる。15 sets the axial direction 130 position of the ring gear 12 O
The spring 1 is installed in the storage hole 16 provided in the output gear 14.
7 is built in, and contacts the upper part of the ball 18 and presses the ball 18, so that only one tooth on the inner periphery of the ring gear 12 is cut out as shown by the ring 30.
Insert the upper hemisphere of the ring gear l! 130 positions in the axial direction are set. That is, the ball 18 is interposed between the locking groove 19 provided in the ring gear 18 and the storage hole 16 provided in the third output gear 14, so that the ring gear 1
20 position connects the first output gear 10 and the third output gear 14 to prevent the ring gear 120 from moving in the axial direction 13. Then, shift the ring gear 12 to the left in the axial direction 13o, and connect the stop groove 19 and the storage hole 1 on the right side of the ring gear 12.
6 and the ball 18, the 30th output gear 14
When the KtD output shaft 70 and the third output gear 14 are connected, the rotation speed of the KtD output shaft 70 is switched.
なお、リング歯車１ｇには、上記係止溝１９に臨んで後
述する操作棒２５０挿入孔３５が設けられて−る。The ring gear 1g is provided with an insertion hole 35 for an operating rod 250, which will be described later, facing the locking groove 19.
第１ｍ！ＩＫ示す２０は上記リング歯車１２を出力軸７
０軸方向１３ヘシフトさせるシフトフォークで、その先
端部２１がリング歯車１２０外岡部に形成され九凹部２
２に嵌入した状態で、シフトフォーク！！０ＫＩＩ定さ
れ九シフトレバ−２３を軸方向１３ヘシフトすれば、そ
れに連動してリング＄３１１１１−シフト門れ第１の、
出力歯車１０％しく紘第２の出力歯−１１と出力軸７と
の連結の選択をすることができる。上記シアーオー２□
。は第３図にヶすよ、に第゛、。出方歯車１Ｇと第２の
出力歯車１１０選択をする場合にのみ係合させ、稼動中
に外せるように、リング歯車１２に対して係脱自−に設
定されている。1st m! 20 shown by IK connects the ring gear 12 to the output shaft 7.
A shift fork for shifting in the 0-axis direction 13, whose tip 21 is formed on the outer wall of the ring gear 120 and has a 9-concave portion 2.
Shift fork with 2 inserted! ! 0KII is set and the 9th shift lever 23 is shifted in the axial direction 13, the ring $31111-shift gate 1st is interlocked with it.
It is possible to select the connection between the output gear 10% and the second output gear 11 and the output shaft 7. Shear-o 2□ above
. It is shown in Figure 3. It is set to engage and disengage automatically from the ring gear 12 so that it is engaged only when the output gear 1G and the second output gear 110 are selected, and can be disengaged during operation.
つぎに、上記実施例Ｏ動作について説明する。゛上記交
流殉電機８から交−同波数５０ヘルツの出力を得るＫは
、リング歯車ｌ！を第１図に示すように設定すればよい
。すなわち、この場合ＫＪ＞ｈて、ガスタービン意を定
格回転数′ｔｓ−転すると、□駆動力線入力軸ｌから、
第１０人力歯車５、第１の出力歯車１Ｇ、 リング歯
車１２、第３の出力歯車１４と伝達され、出力軸７が所
定の回転数で回転され、交流発電機８から交流周波数５
０ヘルツが得られる。Next, the operation of the above embodiment O will be explained.゛K, which obtains an output of AC frequency 50 Hz from the AC power generator 8, is a ring gear l! may be set as shown in FIG. That is, in this case, when KJ>h and the gas turbine is rotated at the rated rotation speed 'ts-, □driving force line from the input shaft l,
It is transmitted to the tenth human power gear 5, the first output gear 1G, the ring gear 12, and the third output gear 14, and the output shaft 7 is rotated at a predetermined number of rotations.
0 hertz is obtained.
つぎに、交流周波数６０ヘルツに変換するには・ガスタ
ービン２を停止した状態で、第２図に示すようにケース
３に設けられ九透孔２４から操作棒２５を挿入し、七Ｏ
突部２６をリング歯車ｌ！Ｏ挿入孔３５へ挿入しソ、収
納孔１６に内蔵され九−−ル１８をスズリーング１７に
抗して押圧して第３の出力歯車１４Ｃ）＊廐２７近くに
壕で下がる。このとき、′操作棒２５の段ｓ２９がリン
グ歯車１２の外局面Ｋａ＊することによ〕、央ＩＢｇが
深く入夛込み過ぎてリング歯車１２０軸力向へＯ参勤を
妨−るのを防止している。この状態で、シフトレバ−２
３を第ｓｌ＋ｏように矢印！８方向へ１帳し、シフトフ
ォーク２０の先端部２１をリング歯車１２０凹郁２２に
嵌入し良状態で、シフトレバ−２３を第１図で示すよう
に軸方１！１１１３の左方へシフトし、りング歯車１２
を第２の出力歯車１１と第３０出力歯車１４とにかみ合
わせ、リング歯車１２の右側Ｏ係止溝１９にボール１８
がスプリングにより抑圧され、その上半球を挿入してリ
ング歯車ｌ！を固定すると歯車の切換えが完了される・
つぎに、シフトレバ−２３を矢印方向３１に回転させて
リング歯車１２からシフトフォーク２０の保合を解き、
ガスタービン２を定格回転数で運転すると、駆動力は入
力軸ｌから、ｇｇの入力歯車６、第２の出力歯車１１１
リング歯車１２、第３の出力ｍ束１４と伝達され、
出力軸７が所定の回転数で回転され、交流発電機８から
、交流周波数６０ヘルツが得られる。Next, to convert the AC frequency to 60 Hz, with the gas turbine 2 stopped, insert the operating rod 25 from the nine holes 24 provided in the case 3 as shown in FIG.
The protrusion 26 is connected to the ring gear l! Insert it into the O insertion hole 35, press the nine-wheel 18 built in the storage hole 16 against the ring 17, and lower it in a groove near the third output gear 14C) * 27. At this time, the stage s29 of the operating rod 25 forms the outer surface Ka* of the ring gear 12, thereby preventing the center IBg from being inserted too deeply and interfering with the rotation in the axial force direction of the ring gear 120. are doing. In this state, shift lever 2
Arrow like 3 to sl+o! 8 directions, fit the tip 21 of the shift fork 20 into the concave 22 of the ring gear 120, and shift the shift lever 23 to the left in the axial direction 1!1113 as shown in Fig. 1. , ring gear 12
is engaged with the second output gear 11 and the 30th output gear 14, and the ball 18 is fitted into the right O locking groove 19 of the ring gear 12.
is suppressed by the spring, and by inserting the upper hemisphere, the ring gear l! When the gears are fixed, the gear switching is completed.Next, rotate the shift lever 23 in the direction of the arrow 31 to release the shift fork 20 from the ring gear 12,
When the gas turbine 2 is operated at the rated speed, the driving force is transmitted from the input shaft l to the gg input gear 6 and the second output gear 111.
The ring gear 12 is transmitted to the third output m bundle 14,
The output shaft 7 is rotated at a predetermined rotational speed, and an alternating current frequency of 60 hertz is obtained from the alternator 8.
すなわち、上記実施例によれば、ガスタービン２と交流
発電機８との間に変速機を介挿しているから、ガスター
ビン２は常に一定の定格回転数で運転しても変速機の歯
車の切シ換えによシ異なつ″た交流電力周波数が得られ
る。ｔた、その変速機の機構はリング歯車１２の係止溝
１９とボール１８を用いているｐツク機構１５により確
実にロックされているため、振動により外れたシするこ
とはなく、さらに、稼動中にはシフトフォーク！！Ｏを
リング歯車１２から保合を解くことかで龜るから、それ
らの接触部に摩擦がないので、保守が容易であるととも
に回転エネルギの損失も１にい。That is, according to the above embodiment, since the transmission is inserted between the gas turbine 2 and the alternator 8, even if the gas turbine 2 is always operated at a constant rated rotation speed, the gears of the transmission do not change. By switching, different AC power frequencies can be obtained.The transmission mechanism is securely locked by a locking mechanism 15 using a locking groove 19 of a ring gear 12 and a ball 18. This prevents the shift fork from coming off due to vibration, and furthermore, during operation, the shift fork!! , maintenance is easy and there is no loss of rotational energy.
以上、説明したように、この発明によれば、電力周波数
の切換がガスタービンの出力を低下させることなくでき
、その変速機の機構は切換動作が確実で、シフトフォー
クとリング歯車との摩耗がなく、保守が容易で耐久性が
よいうえに、回転エネルギの損失の少ないガスタービン
減速機全提供することができる。As explained above, according to the present invention, the power frequency can be switched without reducing the output of the gas turbine, the transmission mechanism ensures reliable switching operation, and the wear of the shift fork and ring gear is reduced. Therefore, it is possible to provide a complete gas turbine speed reducer that is easy to maintain, has good durability, and has little loss of rotational energy.
第１図はこの発明の一実施例を示す断面図、第２図は同
実施例の要部を示す拡大断面図、籐３図は同実施例の歯
車の切シ換え操作を示す側面図である。
１・・・入力軸、５・・・第１の入力歯車、６・・・第
２の入力歯車、７・・・出力軸、 １Ｇ・・・Ｍｌの出
力歯車、１１・・・第２０出力歯車、 １２・・・リン
グ歯車、１３・・・軸方向、１５・・・ロツ／１１４１
１、ｊ！０・・・シフトフォーク。
第１図
４Fig. 1 is a sectional view showing one embodiment of the present invention, Fig. 2 is an enlarged sectional view showing the main parts of the same embodiment, and Fig. 3 is a side view showing the gear switching operation of the same embodiment. be. 1... Input shaft, 5... First input gear, 6... Second input gear, 7... Output shaft, 1G... Ml output gear, 11... 20th output Gear, 12...Ring gear, 13...Axial direction, 15...Rotu/1141
1, j! 0...Shift fork. Figure 1 4
Claims (1)
よび第１！０人力歯車と、出力軸に＠転自在に設定され
て上記第１および第２の入力歯車のそれぞれと常時かみ
合うｊｌｌおよび第２の出力歯車と、出力軸の軸方向ヘ
シフトすることによって上記第１Ｃ）出力歯車もしくは
第２０出力歯車と出力軸とを選択的に連結するりング禽
車と、出力軸に装着されてリング歯車の軸方向位置を設
定するロック機構と、上記リング歯車を出力軸の軸方向
ヘシフトさせるシフトフォークとを真備し、上記シフト
フォークはリング歯車に対して係脱自在に設定されたこ
とを特徴とするガスタービン減速機。α) Input shaft KIi! first and first!0 human power gears having different numbers of teeth O, and a second output gear rotatably set on the output shaft and constantly meshing with each of the first and second input gears. , a ring wheel that selectively connects the first C) output gear or the 20th output gear and the output shaft by shifting in the axial direction of the output shaft; and a shift fork for shifting the ring gear in the axial direction of the output shaft, the shift fork being set to be freely engageable and detachable from the ring gear. .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56145152A JPS5846244A (en) | 1981-09-14 | 1981-09-14 | Reduction gear for gas turbine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56145152A JPS5846244A (en) | 1981-09-14 | 1981-09-14 | Reduction gear for gas turbine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5846244A true JPS5846244A (en) | 1983-03-17 |
| JPH0155339B2 JPH0155339B2 (en) | 1989-11-24 |
Family
ID=15378618
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP56145152A Granted JPS5846244A (en) | 1981-09-14 | 1981-09-14 | Reduction gear for gas turbine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5846244A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6271189A (en) * | 1985-09-25 | 1987-04-01 | トヨタ自動車株式会社 | High frequency heating gas turbine generator |
| JPS6282688A (en) * | 1985-10-07 | 1987-04-16 | トヨタ自動車株式会社 | Radio-frequency heating power source |
| JPS6282687A (en) * | 1985-10-07 | 1987-04-16 | トヨタ自動車株式会社 | Gas-turbine generator for radio-frequency heating |
| JPS62105390A (en) * | 1985-10-31 | 1987-05-15 | トヨタ自動車株式会社 | Radio frequency heater |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4850159A (en) * | 1971-10-27 | 1973-07-14 | ||
| JPS5683641A (en) * | 1979-09-06 | 1981-07-08 | Getrag Getriebe Zahnrad | Stepwise speed changing device for power vehicle |
-
1981
- 1981-09-14 JP JP56145152A patent/JPS5846244A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4850159A (en) * | 1971-10-27 | 1973-07-14 | ||
| JPS5683641A (en) * | 1979-09-06 | 1981-07-08 | Getrag Getriebe Zahnrad | Stepwise speed changing device for power vehicle |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6271189A (en) * | 1985-09-25 | 1987-04-01 | トヨタ自動車株式会社 | High frequency heating gas turbine generator |
| JPS6282688A (en) * | 1985-10-07 | 1987-04-16 | トヨタ自動車株式会社 | Radio-frequency heating power source |
| JPS6282687A (en) * | 1985-10-07 | 1987-04-16 | トヨタ自動車株式会社 | Gas-turbine generator for radio-frequency heating |
| JPS62105390A (en) * | 1985-10-31 | 1987-05-15 | トヨタ自動車株式会社 | Radio frequency heater |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0155339B2 (en) | 1989-11-24 |
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