JPS62243997A - Control device for vane end gap of centrifugal impeller - Google Patents
Control device for vane end gap of centrifugal impellerInfo
- Publication number
- JPS62243997A JPS62243997A JP61085027A JP8502786A JPS62243997A JP S62243997 A JPS62243997 A JP S62243997A JP 61085027 A JP61085027 A JP 61085027A JP 8502786 A JP8502786 A JP 8502786A JP S62243997 A JPS62243997 A JP S62243997A
- Authority
- JP
- Japan
- Prior art keywords
- gap
- casing
- impeller
- compressor
- detector
- 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
- 238000000034 method Methods 0.000 abstract description 2
- 238000001514 detection method Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 239000002912 waste gas Substances 0.000 description 2
- 206010011469 Crying Diseases 0.000 description 1
- 241001122767 Theaceae Species 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
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
- F04D29/60—Mounting; Assembling; Disassembling
- F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
- F04D29/622—Adjusting the clearances between rotary and stationary parts
-
- 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
- F04D29/60—Mounting; Assembling; Disassembling
- F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
- F04D29/624—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
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】
〔産業上の利用分野〕
本発明は高温ガス或は蒸気によるタービン駆動（Ｊ’１
＋−プソ嵌二會１ゞ、罰坦市０：泣迩ｒ藺すスｔ１のア
ふる。DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention is directed to turbine drive (J'1
+-Puso fit 2 meeting 1ゞ, penalty city 0: crying st1's attack.
従来、高温ガス或は蒸気によるタービン駆動圧縮機にお
いては、タービン翼車部分が高温となるためその回転軸
は熱膨張する。したがって回転軸に直結された圧縮機の
場合は羽根車翼端がケーシングの一部に接触するおそれ
があるために翼端隙間を十分にとっていた。あるいは、
タービン回転軸と圧縮機回転軸とを分離し、両者を軸継
手で連結することによって、タービン回転軸の熱膨張を
軸継手部分で逃がし圧縮機側に影響させないようにして
いた。Conventionally, in a turbine-driven compressor using high-temperature gas or steam, the rotation shaft of the turbine wheel undergoes thermal expansion due to the high temperature of the turbine wheel. Therefore, in the case of a compressor that is directly connected to a rotating shaft, there is a risk that the impeller blade tip may come into contact with a part of the casing, so a sufficient blade tip clearance is required. or,
By separating the turbine rotation shaft and the compressor rotation shaft and connecting them with a shaft joint, thermal expansion of the turbine rotation shaft is allowed to escape through the shaft joint so as not to affect the compressor side.
前記の羽根車翼端隙間を十分とる場合は、タービン回転
軸の熱膨張による伸びは温度により変化するため羽根車
翼端隙間が大きいときは羽根車の性能が低下するという
欠点が、また軸継手を使用する場合は軸受の敗が増加し
、全体構造も大きくなり、機械的損失も増大するという
欠点があった。If the above-mentioned impeller blade tip clearance is sufficient, the elongation due to thermal expansion of the turbine rotating shaft changes depending on the temperature, so if the impeller blade tip clearance is large, the performance of the impeller will decrease. When using this, there were disadvantages such as increased failure of the bearing, an increase in the overall structure, and an increase in mechanical loss.
本発明は前記のような欠点を除去するために、タービン
翼車に直接圧縮機を連結し、しかも回転軸の熱膨張によ
る圧縮機の悪影響も排除したものである。In order to eliminate the above-mentioned drawbacks, the present invention connects a compressor directly to a turbine wheel, and also eliminates the adverse effects of thermal expansion of the rotating shaft on the compressor.
ｃ問題点を解決するための手段〕
本発明は、タービン翼車回転軸に直結された圧縮機を対
象とし、オーブン形の遠心羽根車のｉ端部に対向するケ
ーシング部分を羽根車回転軸の軸方向に移動可能な可動
ケーシングとすると共に、該可動ケーシングと羽根車ｊ
！Ｉ端との隙間検出器を設け、該検出器の検出値と設定
基準値とを比較して最適隙間となるよう可動ケーシング
を移動制御するようにしたものである。Means for Solving Problem c] The present invention is directed to a compressor that is directly connected to the rotating shaft of a turbine impeller, and the casing portion facing the i-end of an oven-shaped centrifugal impeller is connected to the rotating shaft of the impeller. A movable casing that is movable in the axial direction, and a movable casing and an impeller j
! A gap detector with respect to the I end is provided, and the detected value of the detector is compared with a set reference value to control the movement of the movable casing so that the optimum gap is obtained.
タービン翼車回転軸に直結された圧ｔｅａの遠心羽根車
は、該回転軸の熱膨張により軸方向に移動する。このた
め、圧縮機ケーシングのうら羽根車翼端と対向している
部分を可動ケーシングとして軸方向に移動自在に支持し
、この羽根車翼端と可動ケーシングとの隙間を検知する
ための検出器を適所に配備して、常時隙間を検知し、こ
の検出値と設定基準値とを比較して最適隙間となるよう
に調節操作装置を作動させて可動ケーシングを軸方向に
移動さ一部るものである。したがって、圧縮機の羽根車
翼端隙間はタービン翼車回転軸の熱膨張による伸びが変
化しても常に設定基準値に維持され高効率の状態で圧縮
機は運転される。A centrifugal impeller with a pressure of tea directly connected to the rotation shaft of the turbine blade wheel moves in the axial direction due to thermal expansion of the rotation shaft. For this reason, the part of the compressor casing facing the rear impeller blade tip is supported as a movable casing so as to be movable in the axial direction, and a detector is installed to detect the gap between this impeller blade tip and the movable casing. It is placed at a suitable location, constantly detects the gap, compares this detected value with a set reference value, and operates the adjustment device to move the movable casing in the axial direction so that the optimum gap is achieved. be. Therefore, the impeller blade tip clearance of the compressor is always maintained at a set reference value even if the elongation due to thermal expansion of the turbine impeller rotating shaft changes, and the compressor is operated in a highly efficient state.
（実施例） 本発明の好適な実施例を図面にもとづいて説明する。(Example) A preferred embodiment of the present invention will be described based on the drawings.
第１図は燃料電池電力Ｉｉ２備における廃ガス利用のタ
ービン駆動圧縮機に本発明を応用した一例を示すもので
あって、タービン翼車回転軸ｌの両端に第１段および第
２膜圧１ｉｉＩａ２． ３の羽根車４を固着し、各圧縮
機２．３は圧縮機ケーシング５゜インレットベーン６を
備えている。第１段圧縮機２の出口は中間冷却器（図示
せず）を介して第２段圧縮機３の入口に連結されている
。タービン翼車回転軸ｌは、第１段圧縮機２側ではラジ
アルおよびスラスト軸受７で、また第２段圧縮機３側で
はラジアル軸受８で支承されている。タービン翼車回転
軸１は第１段圧縮機２側でスラスト軸受で支承されてい
るから、熱膨張による伸びは第２段圧縮機３側方向であ
るので、第２段圧縮機３の羽根車４は左方向に移動する
。そのために羽根車４翼端に対向する圧縮機ケーシング
部分を可動ケーシング９とし、この可動ケーシング９は
調節操作Ｗ置ｌＯによって、回転軸１の軸方向に移動自
在に操作され、羽根車Ｒｆａと可動ケーシング９との隙
間を調節するようにされている。またこのＲｆａ隙間を
検出するため検出器！ｌが可動ケーシング９とか、圧縮
機ケーシング５の一部等に設けられている。この検出Ｌ
ｔｌｌとしてはインダクタンス型センサが使用される０
次に、第２図〜第４図にもとづいて調節操作装置１０の
具体例を説明すると、可動ケーシング９の圧縮機ケーシ
ング５との摺動面には傾斜溝１７を等間隔で外周面上に
穿設し、この溝１７に係合するガイドピン１６を圧縮機
ケーシング５側に６設する。可動ケーシング９の側面に
は円形ラック１３を固着し、このラック１３に噛合する
扇形ギヤ１２を軸１４、レバー１５を介して左右動させ
るように構成されている。FIG. 1 shows an example in which the present invention is applied to a turbine-driven compressor using waste gas in a fuel cell power supply Ii2 system, in which a first stage and a second film pressure 1iiIa2 are installed at both ends of the turbine wheel rotation axis l. ．． 3 impellers 4 are fixed, and each compressor 2.3 is equipped with a compressor casing 5° inlet vane 6. The outlet of the first stage compressor 2 is connected to the inlet of the second stage compressor 3 via an intercooler (not shown). The turbine wheel rotating shaft l is supported by a radial and thrust bearing 7 on the first stage compressor 2 side, and by a radial bearing 8 on the second stage compressor 3 side. Since the turbine impeller rotating shaft 1 is supported by a thrust bearing on the first stage compressor 2 side, the elongation due to thermal expansion is in the direction of the second stage compressor 3 side, so the impeller of the second stage compressor 3 4 moves to the left. For this purpose, the part of the compressor casing facing the blade tip of the impeller 4 is made into a movable casing 9, and this movable casing 9 is operated to be movable in the axial direction of the rotating shaft 1 by the adjustment operation W and lO, and is movable with the impeller Rfa. The gap with the casing 9 is adjusted. Also a detector to detect this Rfa gap! 1 is provided on the movable casing 9 or a part of the compressor casing 5. This detection L
An inductance type sensor is used as the tll.
Next, a specific example of the adjustment operation device 10 will be explained based on FIGS. 2 to 4. On the sliding surface of the movable casing 9 with the compressor casing 5, inclined grooves 17 are formed on the outer peripheral surface at equal intervals. Six guide pins 16 are provided on the compressor casing 5 side to be bored and engaged with the grooves 17. A circular rack 13 is fixed to the side surface of the movable casing 9, and a sector gear 12 meshing with the rack 13 is configured to be moved left and right via a shaft 14 and a lever 15.
レバー１５の左右動により可動ケーシング９も左右に回
転されることになり、傾斜？Ｉ１７とガイドビン１６が
係合しているから可動ケーシング９は軸方向に移動する
。その結果欄ａ車ｉｌｌ！＠隙間が調節されるものであ
る。Due to the left and right movement of the lever 15, the movable casing 9 is also rotated left and right, causing an inclination? Since the I17 and the guide pin 16 are engaged, the movable casing 9 moves in the axial direction. The result column a car ill! @The gap can be adjusted.
この際、検出器１１の設置個所の具体例としては第２図
に１１．〜ｌｌａで示した。そしてこれら！Ｑ開側所の
一ケ所か或いは複数個所に設けた検出器により翼端隙間
を常時検出しており、この検出値と設定基準値とを比較
して適正隙間を維持するようにレバー１５が畏作される
ものである。この場合検出器１１ｔ は隙間を直接的に
検知しているが、他は間接的に検知している。第５図は
調節操作装Ｈ１Ｏの変形例を示すもので、ケーシング部
分に等間隔に少くとも２個の作動シリンダ１９を設け、
そのピストン２０に可動ケーシング９に連結された連結
棒１Ｂを設はカバ一体２１から油又は空気を供給して可
動ケーシング９を移動させるようにしたものである。第
６図はさらに他の変形例を示すものであって、う・ツク
２２には可動ケーシング９に連結された連結棒を設け、
ビニオン２３とラック２２を噛合させたものである。第
７図は作動シリンダとしては第５図に示したものと同様
であるが、可動ケーシング９の支承方法が異なるもので
ある。即ち、可動ケーシング９の羽根車入口側において
、１８動リング２４の内周面に凹溝を設け、この凹溝に
可動ケーシング９に設けたＬＨ面枝状部２５嵌合すると
共に、作動シリンダのピストン２０の連結棒１８の先端
に可動ケーシング９の作動杆２６の先端をピン結合２７
したものである。圧縮機ケーシングはタービンケーシン
グとｔｌＶｔシているからタービンケーシングの熱変形
が円周方向で一様でないため圧縮機ケーシングもその影
響を受けることとなり、そのために翼端隙間が円周方向
に均一でなくなる。そのために可動ケーシング９を軸方
向移動に加えて傾斜させて円周方向の翼端隙間を均一に
する。このような制御をするために、作動シリンダおよ
び検出器は少なくとも等間隔に３ケ所設け、可動ケーシ
ング９の羽根車入口側では摺動リング２４の凹溝にｆＪ
圃面状２５を嵌合させθ方向の傾斜を許すようにし、作
動杆２６と連結棒１８とはピン結合した。また、ＩＨ動
リング２４と球面状部２５は可動ケーシング９の羽根車
入口側に設けたものを示したが、これは羽根車出口側に
設けてもよい。At this time, as a specific example of the installation location of the detector 11, 11. Indicated by ~lla. And these! The blade tip clearance is constantly detected by a detector installed at one or more locations on the Q-open side, and the lever 15 is activated to maintain the appropriate clearance by comparing this detected value with a set reference value. It is something that is made. In this case, the detector 11t directly detects the gap, but indirectly detects the others. FIG. 5 shows a modification of the adjustment operating device H1O, in which at least two actuating cylinders 19 are provided at equal intervals in the casing part,
A connecting rod 1B connected to the movable casing 9 is provided on the piston 20, and the movable casing 9 is moved by supplying oil or air from the cover unit 21. FIG. 6 shows yet another modification, in which a connecting rod connected to the movable casing 9 is provided in the u-tsuk 22,
The pinion 23 and the rack 22 are meshed together. The working cylinder in FIG. 7 is similar to that shown in FIG. 5, but the method of supporting the movable casing 9 is different. That is, on the impeller inlet side of the movable casing 9, a concave groove is provided on the inner circumferential surface of the 18-movement ring 24, and the LH surface branch portion 25 provided on the movable casing 9 is fitted into this concave groove, and the operating cylinder is The tip of the operating rod 26 of the movable casing 9 is connected with a pin 27 to the tip of the connecting rod 18 of the piston 20.
This is what I did. Since the compressor casing is in tlVt contact with the turbine casing, the thermal deformation of the turbine casing is not uniform in the circumferential direction, so the compressor casing is also affected by it, and as a result, the blade tip clearance is not uniform in the circumferential direction. . For this purpose, the movable casing 9 is moved in the axial direction and tilted to make the blade tip clearance in the circumferential direction uniform. In order to perform such control, actuating cylinders and detectors are provided at at least three locations at equal intervals, and fJ is provided in the concave groove of the sliding ring 24 on the impeller inlet side of the movable casing 9.
The field surface 25 was fitted to allow inclination in the θ direction, and the operating rod 26 and the connecting rod 18 were pin-coupled. Further, although the IH dynamic ring 24 and the spherical portion 25 are shown as being provided on the impeller inlet side of the movable casing 9, they may be provided on the impeller outlet side.
なお、可動ケーシング９は羽根車翼端全体にわたって設
けたものを示したが、これを羽根車の出口側部分と対向
する部分だけとしても差つかえない。Although the movable casing 9 is shown as being provided over the entire blade tip of the impeller, it may also be provided only at the portion facing the outlet side portion of the impeller.
本発明は圧縮機ケーシングにおいて、羽根車翼端と対向
する部分を圧縮機回転軸方向に移動自在の可動ケーシン
グとし、一方、この可動ケーシングと羽根車翼端との隙
間を検知するための隙間検出器を配備し、この検出値と
この隙間の設定括準値とを比較して、常に適正隙間を維
持するように可動ケーシングを移動制御するようにした
から、例えばタービン駆動回転軸が熱膨張して羽根車翼
端と可動ケーシングとの隙間が変化してもこの変化に従
動して常にその隙間を適正に維持できるから圧縮器はど
のような状態においても高効率状態で運転ができるもの
である。The present invention provides a compressor casing in which a portion facing the impeller blade tip is a movable casing that is movable in the direction of the compressor rotation axis, and a gap detection method for detecting the gap between the movable casing and the impeller blade tip. This detection value is compared with the standard value set for this gap, and the movement of the movable casing is controlled to maintain an appropriate gap at all times. Even if the gap between the impeller blade tip and the movable casing changes, the compressor follows this change and can always maintain an appropriate gap, so the compressor can operate at high efficiency under any conditions. .
第１図は本発明装置を廃ガスタービン駆動圧縮機に通用
した場合の一部縦断面図、第２図は本発明装置の要部を
示す一部縦断側面図、第３図は第２図Ａ−Ａ視側面図、
第４図は第３図Ｂ−Ｂ視平面図、第５図は本発明装置の
要部の他の実施例、第６図は本発明装置の要部のさらに
他の実施例、第７図は本発明装置の要部のさらに他の実
施例を示すものである。
ｌ・・・タービン翼車回転軸、２・・・第１段圧縮機、
３・・・第２段圧縮機、 ４・・・羽根車、５・
・・圧縮機ケーシング、６・・・インレットベーン、７
・・・ラジアル及びスラスト軸受
８・・・ラジアル軸受、 ９・・・可動ケーシン
グ、１０・・・調節操作装置、 １１・・・検出器
、１２・・・扇形ギヤ、 １３・・・円形ラッ
ク、１４・・・軸、 １５・・・レバー、
１６・・・ガイドピン、 １７・・・傾斜溝、１
８・・・連結棒、 １９・・・作動シリンダ
、２０・・・ピストン、 ２１・・・カバ一体
、２２・・・ラック、 ２３・・・ピニオン
、２４・・・摺動リング、 ２５・・・球面状部
、２６・・・作動杆、 ２７・・・ピン結合
部。Fig. 1 is a partial vertical sectional view of the device of the present invention applied to a waste gas turbine driven compressor, Fig. 2 is a partial vertical sectional side view showing the main parts of the device of the present invention, and Fig. 3 is the same as Fig. 2. A-A side view,
FIG. 4 is a plan view taken along line B-B in FIG. 3, FIG. 5 is another embodiment of the main part of the device of the present invention, FIG. 6 is a still another embodiment of the main part of the device of the present invention, and FIG. 1 shows still another embodiment of the main part of the device of the present invention. l... Turbine impeller rotation shaft, 2... First stage compressor,
3... Second stage compressor, 4... Impeller, 5...
...Compressor casing, 6...Inlet vane, 7
... Radial and thrust bearing 8 ... Radial bearing, 9 ... Movable casing, 10 ... Adjustment operation device, 11 ... Detector, 12 ... Sectoral gear, 13 ... Circular rack, 14... shaft, 15... lever,
16...Guide pin, 17...Slanted groove, 1
8... Connecting rod, 19... Operating cylinder, 20... Piston, 21... Cover integrated, 22... Rack, 23... Pinion, 24... Sliding ring, 25... - Spherical part, 26... Operating rod, 27... Pin connection part.
Claims (1)
ング部分を羽根車回転軸の軸方向に移動可能な可動ケー
シングとすると共に、該可動ケーシングと羽根車翼端と
の隙間検出器を設け、該検出器の検出値と設定基準値と
を比較して最適隙間となるよう可動ケーシングを移動さ
せるようにしたことを特徴とする遠心羽根車翼端隙間制
御装置。 ２、前記可動ケーシングが調節操作装置により移動させ
られるようにした特許請求の範囲第１項記載の遠心羽根
車翼端隙間制御装置。[Claims] 1. The casing portion facing the blade tip of an open type centrifugal impeller is a movable casing movable in the axial direction of the impeller rotation axis, and the movable casing and the impeller blade tip are connected to each other. 1. A centrifugal impeller blade tip clearance control device, comprising: a clearance detector; the movable casing is moved so that an optimum clearance is obtained by comparing the detected value of the detector with a set reference value. 2. The centrifugal impeller blade tip clearance control device according to claim 1, wherein the movable casing is moved by an adjustment operating device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61085027A JPS62243997A (en) | 1986-04-15 | 1986-04-15 | Control device for vane end gap of centrifugal impeller |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61085027A JPS62243997A (en) | 1986-04-15 | 1986-04-15 | Control device for vane end gap of centrifugal impeller |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1188881A Division JPH0633800B2 (en) | 1989-07-24 | 1989-07-24 | Centrifugal impeller blade tip clearance controller |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62243997A true JPS62243997A (en) | 1987-10-24 |
| JPH0219319B2 JPH0219319B2 (en) | 1990-05-01 |
Family
ID=13847232
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP61085027A Granted JPS62243997A (en) | 1986-04-15 | 1986-04-15 | Control device for vane end gap of centrifugal impeller |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS62243997A (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01173301U (en) * | 1988-05-18 | 1989-12-08 | ||
| JPH0295796A (en) * | 1988-09-30 | 1990-04-06 | Mitsubishi Heavy Ind Ltd | Centrifugal compressor |
| JP2006308098A (en) * | 2005-04-29 | 2006-11-09 | Sulzer Pumpen Ag | Sealing device for attaching the side plate of centrifugal pump and mounting screw used therefor |
| CN102213232A (en) * | 2010-04-06 | 2011-10-12 | 株式会社Ihi | Drive shaft structure, turbo compressor, and turbo refrigerator |
| WO2015151844A1 (en) * | 2014-03-31 | 2015-10-08 | 三菱重工業株式会社 | Centrifugal compressor, supercharger, and method for manufacturing centrifugal compressor |
| JP2015197052A (en) * | 2014-03-31 | 2015-11-09 | 三菱重工業株式会社 | Centrifugal compressor, supercharger, and method of manufacturing centrifugal compressor |
| JP2016079910A (en) * | 2014-10-17 | 2016-05-16 | 三菱重工業株式会社 | Centrifugal compressor and supercharger including the same |
| JP2017517664A (en) * | 2014-03-11 | 2017-06-29 | ヌオーヴォ ピニォーネ ソチエタ レスポンサビリタ リミタータＮｕｏｖｏ Ｐｉｇｎｏｎｅ Ｓ．Ｒ．Ｌ． | Turbomachine assembly |
| US9759224B2 (en) | 2008-06-13 | 2017-09-12 | Weir Minerals Australia Ltd. | Adjustable side liner for a pump |
| EP3587826A1 (en) * | 2018-06-28 | 2020-01-01 | Danfoss A/S | Variable stage compressors |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS473301U (en) * | 1971-02-01 | 1972-09-04 | ||
| JPS52562A (en) * | 1975-06-12 | 1977-01-05 | Philips Nv | Shaving device with holder for cutter |
| JPS611896A (en) * | 1984-05-15 | 1986-01-07 | コングスベルグ ヴアーペンフアブリク | Controller for operation clearance of radial-gas compressor with duplex inflow port |
-
1986
- 1986-04-15 JP JP61085027A patent/JPS62243997A/en active Granted
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS473301U (en) * | 1971-02-01 | 1972-09-04 | ||
| JPS52562A (en) * | 1975-06-12 | 1977-01-05 | Philips Nv | Shaving device with holder for cutter |
| JPS611896A (en) * | 1984-05-15 | 1986-01-07 | コングスベルグ ヴアーペンフアブリク | Controller for operation clearance of radial-gas compressor with duplex inflow port |
Cited By (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01173301U (en) * | 1988-05-18 | 1989-12-08 | ||
| JPH0295796A (en) * | 1988-09-30 | 1990-04-06 | Mitsubishi Heavy Ind Ltd | Centrifugal compressor |
| JP2006308098A (en) * | 2005-04-29 | 2006-11-09 | Sulzer Pumpen Ag | Sealing device for attaching the side plate of centrifugal pump and mounting screw used therefor |
| US8272823B2 (en) | 2005-04-29 | 2012-09-25 | Sulzer Pumpen Ag | Sealing arrangement for the attachment of a side plate of a centrifugal pump and an attachment screw used therewith |
| US9759224B2 (en) | 2008-06-13 | 2017-09-12 | Weir Minerals Australia Ltd. | Adjustable side liner for a pump |
| CN102213232A (en) * | 2010-04-06 | 2011-10-12 | 株式会社Ihi | Drive shaft structure, turbo compressor, and turbo refrigerator |
| US8959949B2 (en) | 2010-04-06 | 2015-02-24 | Ihi Corporation | Turbo compressor |
| US11067096B2 (en) | 2014-03-11 | 2021-07-20 | Nuovo Pignone Srl | Turbomachine assembly |
| JP2017517664A (en) * | 2014-03-11 | 2017-06-29 | ヌオーヴォ ピニォーネ ソチエタ レスポンサビリタ リミタータＮｕｏｖｏ Ｐｉｇｎｏｎｅ Ｓ．Ｒ．Ｌ． | Turbomachine assembly |
| WO2015151844A1 (en) * | 2014-03-31 | 2015-10-08 | 三菱重工業株式会社 | Centrifugal compressor, supercharger, and method for manufacturing centrifugal compressor |
| JP2015197052A (en) * | 2014-03-31 | 2015-11-09 | 三菱重工業株式会社 | Centrifugal compressor, supercharger, and method of manufacturing centrifugal compressor |
| CN106164497A (en) * | 2014-03-31 | 2016-11-23 | 三菱重工业株式会社 | The manufacture method of centrifugal compressor, supercharger and centrifugal compressor |
| JP2016079910A (en) * | 2014-10-17 | 2016-05-16 | 三菱重工業株式会社 | Centrifugal compressor and supercharger including the same |
| CN110657108A (en) * | 2018-06-28 | 2020-01-07 | 丹佛斯公司 | Variable stage compressor |
| EP3587826A1 (en) * | 2018-06-28 | 2020-01-01 | Danfoss A/S | Variable stage compressors |
| CN110657108B (en) * | 2018-06-28 | 2022-10-28 | 丹佛斯公司 | Variable stage compressor |
| US11841173B2 (en) | 2018-06-28 | 2023-12-12 | Danfoss A/S | Variable stage compressors |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0219319B2 (en) | 1990-05-01 |
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