JPS5838301A - Centrifugal impeller device - Google Patents
Centrifugal impeller deviceInfo
- Publication number
- JPS5838301A JPS5838301A JP13581881A JP13581881A JPS5838301A JP S5838301 A JPS5838301 A JP S5838301A JP 13581881 A JP13581881 A JP 13581881A JP 13581881 A JP13581881 A JP 13581881A JP S5838301 A JPS5838301 A JP S5838301A
- Authority
- JP
- Japan
- Prior art keywords
- impeller
- rotating shaft
- impellers
- bearing
- centrifugal
- 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
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
- F01D3/02—Machines or engines with axial-thrust balancing effected by working-fluid characterised by having one fluid flow in one axial direction and another fluid flow in the opposite direction
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
- F04D25/163—Combinations of two or more pumps ; Producing two or more separate gas flows driven by a common gearing arrangement
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
本発明は、遠心式の羽根車を回転さ艙て膨張作用や圧縮
作用等を得ることができるようにした遠心式羽根車装置
に関するものであ一為。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a centrifugal impeller device in which an expansion action, a compression action, etc. can be obtained by rotating a centrifugal impeller.
従来の遠心式羽根車を用いた膨張機あるい辻圧縮機等は
、第1図#lc承すようKr1lJ転軸lの一端部に単
一の羽根車怠を固着し、この閣転軸l#IC発電機等の
回転エネルギ吸収機構(膨張機O場合)中電動機喀の回
転エネルギ発生機構(圧縮機の場合)を装着しえものが
一般的である。In an expander or compressor using a conventional centrifugal impeller, a single impeller is fixed to one end of the rotating shaft l, as shown in Fig. 1. It is common to be equipped with a rotational energy absorption mechanism such as an IC generator (in the case of an expander O) or a rotational energy generation mechanism such as an electric motor (in the case of a compressor).
ところが、単にこれだけのものでは、前記羽根車2を回
転させて膨張作用あるいは圧縮作用を発揮させた場合に
、該羽根車2のへプ3の表面35LK作用する圧力によ
って発生する、羽根車怠を図中右方へ移動させようとす
る力と、前記ハブ30背面31)に作用する圧力によつ
て発生すゐ、羽根車2を図中左方へ移動させようとする
力とのlII#IC差が生じ、該羽根車2を支持する回
転軸に矢−きなスフス)力が作用するととになるという
不都合がある。特に、ヘリウム膨張タービンやヘリウム
スンデレフナ等のように、高圧力、高連回転、高圧縮比
等が要求される装置にシいては、回転軸IK作用する強
大なスフスF力を支えるのが難かしいという問題が姦る
。However, with just this, when the impeller 2 is rotated to exert an expansion action or a compression action, the impeller sag generated by the pressure acting on the surface 35LK of the hep 3 of the impeller 2 can be avoided. lII#IC between the force trying to move the impeller 2 to the right in the figure and the force generated by the pressure acting on the rear surface 31 of the hub 30 and trying to move the impeller 2 to the left in the figure. If a difference occurs and a large force is applied to the rotating shaft that supports the impeller 2, there is a problem that the impeller 2 will become distorted. In particular, for equipment that requires high pressure, high continuous rotation, high compression ratio, etc., such as helium expansion turbines and helium Sunderevna, it is necessary to support the powerful SFC force that acts on the rotating shaft IK. The problem is that it is difficult.
すなわち、20万〜30万−程庫の高速で羽根車を回転
畜せるのが好ましいこの種の装置では、回転軸1を、高
速回転に不向きなころがり軸受の代わ)w−動圧気体軸
受や磁気軸受等を用いて支持することが必要となるが、
このような高速回転用の特殊軸受のみによって前記回転
軸に作用する強大なスフスト力を支持するのは非常にむ
ずかしい、そのため、この種の装置では、前記回転軸を
支持するスフスト軸受として、動圧気体軸受や磁気軸受
と玉軸受とを組み合せたものを採用する等の工夫がなさ
れているが、−ずれも、構造が複雑となり大形化を招く
という不都合がある。In other words, in this type of device where it is preferable to rotate the impeller at a high speed of 200,000 to 300,000 degrees, the rotating shaft 1 is replaced with a rolling bearing (not suitable for high-speed rotation) or a hydrodynamic gas bearing. It is necessary to support it using magnetic bearings, etc.
It is extremely difficult to support the enormous force acting on the rotating shaft using only such special bearings for high-speed rotation.Therefore, in this type of equipment, the dynamic pressure is Efforts have been made to use a combination of a gas bearing or a magnetic bearing and a ball bearing, but these also have the disadvantage of complicating the structure and increasing the size.
ところゝで、このような不都合を解消する一方策として
は、例えば、第2図に示すように回転軸1の一端部に装
着する羽根車2/を両吸込形のもOKして、回転軸1に
スフスト力が作用しないようにすることが考えられる。By the way, one way to solve this problem is, for example, as shown in FIG. It is conceivable to prevent the force from acting on 1.
しかしながら、羽根車2/を両吸込形のものにすると、
羽根車2/の両側に流体を羽根車どへ導くための通路4
等を設けなければならないため、前記回転軸1を支持す
る軸受5と羽根2/との距離を短かく設定することが難
かしくなる。そのため、回転系の固有振動数が低くなら
ざるを得す、高速回転崗きに設計するのに困難を伴なう
とhう不都合がある。However, if the impeller 2/ is of a double suction type,
Passage 4 for guiding fluid to the impeller on both sides of the impeller 2/
etc., it becomes difficult to set a short distance between the bearing 5 that supports the rotary shaft 1 and the blade 2/. Therefore, the natural frequency of the rotating system has to be low, and it is difficult to design a high-speed rotating system.
本発明は、このような事情に着目してなされ丸もので、
共通の回転軸に、鏡対称の形状をなし等価な性能を有し
た対をなす羽根車を背中合せに対向させて装着し、この
回転軸の前記両羽根車間に位置する部位を軸受によシ支
持するととによって前述した不都合を解消することがで
きるようkした遠心式羽根車装置を提供するものである
。The present invention was made with attention to such circumstances, and
A pair of impellers having a mirror-symmetric shape and having equivalent performance are mounted back to back on a common rotating shaft, and a portion of the rotating shaft located between the two impellers is supported by a bearing. Therefore, it is an object of the present invention to provide a centrifugal impeller device that can eliminate the above-mentioned disadvantages.
以下1本発明をコンプレフサに適用した場合の一実施例
につき、第3図を参照して説明する。An embodiment in which the present invention is applied to a compressor will be described below with reference to FIG.
共通の回転軸11の両端に対をなす遠心式羽根車12.
13を背中合せに対向させて固着している0羽根車12
.13は、円板状のハゲ14.160表面14a、15
aK複数枚の羽根1 g−−−2l 7.−をうず巻形
に突設してなるものである。そして、これら両羽根車1
2.13け、相互に鏡対称の形状をなし等価な性能を発
揮するように作られている。そして、前記回転軸1工の
前記両羽根車12.13間に位置する部位をジャーナル
軸受18.18とスフスト軸受19.19とによって回
転自在に支持している。A pair of centrifugal impellers 12 at both ends of a common rotating shaft 11.
0 impeller 12 fixed with 13 facing back to back
.. 13 is a disc-shaped bald surface 14.160 surface 14a, 15
aK multiple blades 1 g---2l 7. - is provided in a spiral shape. And these two impellers 1
2.13 They are designed to have mirror-symmetrical shapes and exhibit equivalent performance. A portion of the rotating shaft 1 located between the two impellers 12.13 is rotatably supported by a journal bearing 18.18 and a thrust bearing 19.19.
前記各軸受18.18.19.19としては、ティルテ
ィングパフド軸受またはフォイル軸受等の動圧気体軸受
や磁気軸受等が採用されている。また、前記回転軸11
の中央部に高周波毫−タ等の回転エネルギ発生機構21
を装着して、該回転軸11を前記羽根車12.13とと
4に高速で回転させるよう和している。なお、22はケ
ーシングであシ、このケーシング22に:は、前記羽根
車12.13の入口に対向する吸込ロ2g&、22a、
前記羽根車12.13の出口にディフューザ221)、
22’t)を介して連通ずるスフロー11/220,2
2Qおよびこれらスクロール22C,220に連通ずる
吐出口22d。As each of the bearings 18, 18, 19, and 19, a dynamic pressure gas bearing such as a tilting puffed bearing or a foil bearing, a magnetic bearing, or the like is employed. Further, the rotating shaft 11
A rotational energy generating mechanism 21 such as a high frequency roller is installed in the center of the
The rotary shaft 11 is coupled to the impellers 12, 13, and 4 to rotate at high speed. Note that 22 is a casing, and in this casing 22 are suction holes 2g&, 22a, facing the inlet of the impeller 12, 13,
a diffuser 221) at the outlet of the impeller 12.13;
11/220,2 connected via 22't)
2Q and a discharge port 22d communicating with these scrolls 22C and 220.
zzl善が=設けである。zzl good = provision.
このような構成のものであれば、吸込口2!!a、22
aから服込まれたヘリウム等の気体−羽根車12.13
に付勢されてディフューザ露2′b122″loからス
フa−A/22 e、 22 Q内に導びかれ、圧縮さ
れた状態で吐出口zzd、z2eLからケーシング22
外へ吐出されるわけであるが、本発明によれば、共通の
回転軸11K、鏡対称の形状をなし等価な性能を有した
対をなす羽根車1!!、13を背中合せに対向させて装
着し、これら両羽根車12.13ic同等の仕事を行な
わせるようにしているので、一方の羽根車12から前記
回転軸1IY−与えられるスフスト力と他方の羽根車1
3から前記回転軸llk与えられるスラスト力とが相殺
し合うこととなシ、該回転軸11にほとんどスフスト力
が作用しまい状態となる。そのため、この回転軸11に
設けるスフスト軸受19.19としては、単なる位置決
め用の小形なものを用いればよく、構成が複雑で大形な
特殊軸受を採用する必要が全くないという実用1優れた
効果が得られる。If it has such a configuration, it is the suction port 2! ! a, 22
Gas such as helium taken in from a - impeller 12.13
is energized by the diffuser dew 2'b122''lo and guided into the space a-A/22e, 22Q, and is compressed into the casing 22 from the discharge ports zzd, z2eL.
However, according to the present invention, a pair of impellers 1 having a common rotation axis 11K, mirror-symmetrical shapes, and equivalent performance! ! , 13 are mounted back-to-back, and both impellers 12 and 13 perform the same work, so that the force applied from one impeller 12 to the rotating shaft 1IY and the other impeller's 1
3 and the thrust force applied to the rotating shaft 11 cancel each other out, resulting in a state in which almost no thrust force is applied to the rotating shaft 11. Therefore, as the Sufst bearing 19.19 provided on this rotating shaft 11, it is sufficient to use a small one for mere positioning, and there is no need to adopt a large special bearing with a complicated structure.Practical 1 Excellent effect is obtained.
しかも、前記回転軸11の前記両羽根車12、工3の背
面間に位置する部位を軸受18.18によって支持する
ようにしているので、これら軸受18.18と羽根車1
2.13との距離をきわめて短かくすることができる。Moreover, since the portion of the rotating shaft 11 located between the impellers 12 and the back surface of the shaft 3 is supported by the bearings 18.18, these bearings 18.18 and the impeller 1
2.13 can be made extremely short.
そのため、前記回転軸11と羽根車12.13とから構
成される回転系の固有振動数を高くすることが容易とな
)、無理なく高速運転を行なわせることができるという
利点もある。Therefore, it is easy to increase the natural frequency of the rotating system composed of the rotating shaft 11 and the impellers 12 and 13), and there is also the advantage that high-speed operation can be performed without difficulty.
なお、前記実施例では、内羽根車間に回転エネルギ発生
機構を配した場合について説明したが、本発明はかなら
ずしもこのようなものに隈られないのは勿論であり、例
えば、第4図に示すようなものであってもよい。すなわ
ち、第4図に示すものは、一方の羽根車13の前端面か
ら回転軸11の端部をさらに突出さぞ、その突出端1l
aIC回転エネルギ発生tala21を接続したもので
ある。In the above embodiment, a case has been described in which a rotational energy generation mechanism is arranged between the inner impellers, but it goes without saying that the present invention is not limited to such a structure.For example, as shown in FIG. It may be something. That is, in the case shown in FIG. 4, the end of the rotating shaft 11 further protrudes from the front end surface of one impeller 13, and the protruding end 1l.
The aIC rotational energy generator tala21 is connected.
また、前記各実施例では、本発明をコンプレッサに適用
した場合について説明したが、本発明はかならずしもこ
のような奄のVC@られす、例えば、ヘリウム膨張ター
ビン等の膨張機にも同様に適用が可能である。しかして
、この場合には、回転軸に回転エネルギ吸収機構を装着
することとなぁ。Further, in each of the above embodiments, the case where the present invention is applied to a compressor has been described, but the present invention is not necessarily applicable to such an expander such as a helium expansion turbine. It is possible. In this case, however, a rotational energy absorption mechanism must be attached to the rotating shaft.
まえ、軸受は、動圧気体軸受や磁気軸受等に隈られない
のは勿論であり、例えば、低速回転仕様の場合にはころ
が)軸受等を採用してもよい。Of course, the bearing is not limited to a hydrodynamic gas bearing, a magnetic bearing, etc.; for example, in the case of low-speed rotation specifications, a roller bearing or the like may be used.
第1図、第2図は従来例を示す部分断面図。
第3図は本発明の一実施例を示す断面図、第4図は本発
明の他の実施例を示す断面図である。
11−−−=−・回転軸、12.13−へ−羽根車、1
8.19−−−−−一軸受1.t 1−−−−−一回転
エネルギ発生機構。
代理人 弁理士 赤憚−博FIGS. 1 and 2 are partial sectional views showing a conventional example. FIG. 3 is a sectional view showing one embodiment of the invention, and FIG. 4 is a sectional view showing another embodiment of the invention. 11----=-・Rotating shaft, 12.13-To-impeller, 1
8.19---One bearing1. t 1---One rotation energy generation mechanism. Agent Patent Attorney Hiroshi Akagi
Claims (1)
走対をなす遠心式羽根車を背中会せに対崗させて装着し
、この回転軸の前記両羽根車閲に位置する部位を軸受に
よ〉回転自在に支持するとともに%この回転軸K11転
工ネ声ギ吸収機構または回転エネルギ発生機構を装着し
たことを特徴とする遠心式羽根車装置。Centrifugal impellers having a mirror-symmetrical shape, having equivalent performance, and forming a running pair are mounted on a common rotating shaft, facing each other back-to-back, and the centrifugal impellers are located in front of both of the impellers on this rotating shaft. 1. A centrifugal impeller device, characterized in that its parts are rotatably supported by bearings, and a rotary shaft K11 is equipped with a rotation energy absorption mechanism or a rotational energy generation mechanism.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP13581881A JPS5838301A (en) | 1981-08-29 | 1981-08-29 | Centrifugal impeller device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP13581881A JPS5838301A (en) | 1981-08-29 | 1981-08-29 | Centrifugal impeller device |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS5838301A true JPS5838301A (en) | 1983-03-05 |
Family
ID=15160518
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP13581881A Pending JPS5838301A (en) | 1981-08-29 | 1981-08-29 | Centrifugal impeller device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5838301A (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6375391A (en) * | 1986-09-17 | 1988-04-05 | Kobe Steel Ltd | Gas lubricated bearing array for two-stage single shaft turbocompressor |
US4952319A (en) * | 1986-12-15 | 1990-08-28 | Mitsubishi Kasei Corporation | Process for separating liquid mixture |
JP2011043071A (en) * | 2009-08-19 | 2011-03-03 | Mitsubishi Heavy Industries Compressor Corp | Arrangement system of machine unit |
CN102979751A (en) * | 2012-09-25 | 2013-03-20 | 西安交大赛尔机泵成套设备有限责任公司 | Single-shaft plusing multiple-shaft type carbon dioxide gas centrifugal compressor unit |
JP2015533981A (en) * | 2012-09-11 | 2015-11-26 | コンセプツ・イーティーアイ・インコーポレーテッド | Overhang turbine and generator system with turbine cartridge |
WO2017059495A1 (en) * | 2015-10-07 | 2017-04-13 | The University Of Queensland | A turbine |
CN109477496A (en) * | 2016-07-13 | 2019-03-15 | 三菱电机株式会社 | Electric blowers and electrical equipment |
-
1981
- 1981-08-29 JP JP13581881A patent/JPS5838301A/en active Pending
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6375391A (en) * | 1986-09-17 | 1988-04-05 | Kobe Steel Ltd | Gas lubricated bearing array for two-stage single shaft turbocompressor |
US4952319A (en) * | 1986-12-15 | 1990-08-28 | Mitsubishi Kasei Corporation | Process for separating liquid mixture |
JP2011043071A (en) * | 2009-08-19 | 2011-03-03 | Mitsubishi Heavy Industries Compressor Corp | Arrangement system of machine unit |
JP2015533981A (en) * | 2012-09-11 | 2015-11-26 | コンセプツ・イーティーアイ・インコーポレーテッド | Overhang turbine and generator system with turbine cartridge |
US10069378B2 (en) | 2012-09-11 | 2018-09-04 | Concepts Nrec, Llc | ORC turbine and generator, and method of making a turbine |
CN102979751A (en) * | 2012-09-25 | 2013-03-20 | 西安交大赛尔机泵成套设备有限责任公司 | Single-shaft plusing multiple-shaft type carbon dioxide gas centrifugal compressor unit |
CN102979751B (en) * | 2012-09-25 | 2015-07-15 | 西安交大赛尔机泵成套设备有限责任公司 | Single-shaft plusing multiple-shaft type carbon dioxide gas centrifugal compressor unit |
WO2017059495A1 (en) * | 2015-10-07 | 2017-04-13 | The University Of Queensland | A turbine |
CN109477496A (en) * | 2016-07-13 | 2019-03-15 | 三菱电机株式会社 | Electric blowers and electrical equipment |
US10947994B2 (en) | 2016-07-13 | 2021-03-16 | Mitsubishi Electric Corporation | Electric blower and electric equipment |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US3868196A (en) | Centrifugal compressor with rotating vaneless diffuser powered by leakage flow | |
US2318990A (en) | Radial flow elastic fluid turbine or compressor | |
US3160108A (en) | Thrust carrying arrangement for fluid handling machines | |
JPS5985401A (en) | Rotary fluid treatment device that reduces fluid leakage | |
US6698929B2 (en) | Turbo compressor | |
JPH1113686A (en) | Turbo machinery | |
JPS5838301A (en) | Centrifugal impeller device | |
Ilberg et al. | Flow theory and performance of tangential fans | |
JPH0219694A (en) | Oil-free vacuum pump | |
US3933007A (en) | Compressing centrifuge | |
JP2750008B2 (en) | Twin shaft reversing axial turbine | |
US4303377A (en) | Turbine-compressor ejector | |
CN111677675A (en) | A centrifugal air compressor | |
JPH0523761Y2 (en) | ||
JPS5838302A (en) | Centrifugal impeller device | |
Doak et al. | A note on the relative importance of discrete frequency and broad-band noise generating mechanisms in axial fans | |
CN107178522A (en) | Centrifugal turbine tool, the method for balancing axial thrust with back vane structure | |
FR2411300A1 (en) | Turbo-compressor with single cantilever rotor - has centrifugal compressor and axial flow turbine between which is seal with dia. chosen to equalise pressures | |
JPH01216095A (en) | Double shaft inversion centrifugal type fluid booster | |
SU1699353A3 (en) | Centrifugal compressor | |
JPS62267597A (en) | Centrifugal impeller | |
SU242923A1 (en) | Single-stage turbo-expander | |
GB618193A (en) | Improvements relating to elastic fluid turbines | |
RU2008439C1 (en) | Partial-pressure microturbine | |
JPS63205494A (en) | Biaxial reversal centrifugal type fluid booster |