JPH08159094A - Multistage centrifugal compressor - Google Patents
Multistage centrifugal compressorInfo
- Publication number
- JPH08159094A JPH08159094A JP30109994A JP30109994A JPH08159094A JP H08159094 A JPH08159094 A JP H08159094A JP 30109994 A JP30109994 A JP 30109994A JP 30109994 A JP30109994 A JP 30109994A JP H08159094 A JPH08159094 A JP H08159094A
- Authority
- JP
- Japan
- Prior art keywords
- diffuser
- centrifugal compressor
- stage
- efficiency
- vane
- 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
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【0001】[0001]
【産業上の利用分野】本発明は、多段式遠心圧縮機に関
する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multistage centrifugal compressor.
【0002】[0002]
【従来の技術】図1に、第1段遠心圧縮機1と第2段遠
心圧縮機2とを直列に接続した二段式遠心圧縮機3の概
要を示す。図示するように、第1段遠心圧縮機1のイン
ペラ4と第2段遠心圧縮機2のインペラ5とが、回転軸
6を介して背中合わせに接続されている。回転軸6には
小径歯車7が設けられている。小径歯車7はアイドル歯
車8に噛合されている。アイドル歯車8はモータ9の駆
動軸10に設けられた大径歯車11に噛合されている。
この構成によれば、モータ9が駆動すると、各インペラ
4,5が同期して高速回転することになる。2. Description of the Related Art FIG. 1 shows an outline of a two-stage centrifugal compressor 3 in which a first-stage centrifugal compressor 1 and a second-stage centrifugal compressor 2 are connected in series. As shown in the figure, the impeller 4 of the first-stage centrifugal compressor 1 and the impeller 5 of the second-stage centrifugal compressor 2 are connected back to back via a rotary shaft 6. The rotating shaft 6 is provided with a small diameter gear 7. The small diameter gear 7 is meshed with the idle gear 8. The idle gear 8 is meshed with a large-diameter gear 11 provided on a drive shaft 10 of a motor 9.
With this configuration, when the motor 9 is driven, the impellers 4 and 5 rotate at high speed in synchronization.
【0003】各インペラ4,5は、それぞれハウジング
12a,12b内に収容されている。ハウジング12
は、吸気管13とインペラケース14とディフューザ1
5と渦巻室16とから構成されている。第1段遠心圧縮
機1の渦巻室16aは、連絡管17を介して第2段遠心
圧縮機2の吸気管13bに接続されている。連絡管17
には、インタークーラ18が介設されている。第2段遠
心圧縮機2の渦巻室16bには、吐出管19が接続され
ている。吐出管19には、アフタークーラ20が介設さ
れている。この構成によれば、空気は、第1段遠心圧縮
機1の吸気管13aに吸い込まれ、インペラ4により径
方向外方に加速され、ディフューザ15aにより減速さ
れ速度が圧力に変換されて渦巻室16aに導かれる。渦
巻室16a内の空気は、インタークーラ18により冷却
された後、第2段遠心圧縮機2の吸気管13bに吸い込
まれ、同様にインペラ5→ディフューザ15b→渦巻室
16b→アフタークーラ20へと流れ、吐出管19から
吐出される。The impellers 4 and 5 are housed in housings 12a and 12b, respectively. Housing 12
Is the intake pipe 13, the impeller case 14, and the diffuser 1.
5 and the spiral chamber 16. The swirl chamber 16a of the first-stage centrifugal compressor 1 is connected to the intake pipe 13b of the second-stage centrifugal compressor 2 via a connecting pipe 17. Connecting pipe 17
An intercooler 18 is installed in the. A discharge pipe 19 is connected to the spiral chamber 16b of the second-stage centrifugal compressor 2. An aftercooler 20 is interposed in the discharge pipe 19. According to this configuration, the air is sucked into the intake pipe 13a of the first-stage centrifugal compressor 1, is accelerated radially outward by the impeller 4, is decelerated by the diffuser 15a, and the speed is converted into pressure, whereby the swirl chamber 16a. Be led to. The air in the swirl chamber 16 a is cooled by the intercooler 18, is then sucked into the intake pipe 13 b of the second-stage centrifugal compressor 2, and similarly flows to the impeller 5 → diffuser 15 b → swirl chamber 16 b → aftercooler 20. , Is discharged from the discharge pipe 19.
【0004】上記ディフューザ15a,15bは、図3
に示すように、インペラ4,5の回転方向に沿って斜め
に放射状に配置された複数のベーン21を備えている。
ベーン21は、ある設計点回りの流量に合わせて、その
枚数や取付角度等が設定されている。ベーン21の数を
増やすと、設計点回りの流量での効率が高くなるもの
の、設計点を外れた流量では著しく効率が低くなり、使
用可能な流量範囲が狭くなってしまう。かかるディフュ
ーザ15のベーン21は、従来、第1段遠心圧縮機1と
第2段遠心圧縮機2とで同じソリディティのものが用い
られていた。なお、ソリディティとは、図4に示すよう
に、ベーンのコードをベーンのピッチで割った値をい
う。The diffusers 15a and 15b are shown in FIG.
As shown in FIG. 5, the plurality of vanes 21 are arranged radially in a diagonal direction along the rotation direction of the impellers 4 and 5.
The number of vanes 21 and the mounting angle thereof are set according to the flow rate around a certain design point. When the number of vanes 21 is increased, the efficiency at the flow rate around the design point is increased, but the efficiency is remarkably lowered at the flow rate outside the design point, and the usable flow rate range is narrowed. Conventionally, the vanes 21 of the diffuser 15 have the same solidity in the first-stage centrifugal compressor 1 and the second-stage centrifugal compressor 2. The solidity means a value obtained by dividing the code of the vane by the pitch of the vane, as shown in FIG.
【0005】[0005]
【発明が解決しようとする課題】ところで、上述の如き
二段式遠心圧縮機3においては、吸気管13aから吸い
込まれた空気は、第1段遠心圧縮機1によって圧縮され
その容積が小さくなった後、第2段遠心圧縮機2に吸い
込まれる。従って、ディフューザ15のベーン21を第
1段遠心圧縮機1と第2段遠心圧縮機2とで相似のもの
(同じソリディティのもの)を用いると、図3に示すよ
うに、第2段遠心圧縮機2の使用可能な流量範囲が狭く
なってしまうという問題が生じる。In the two-stage centrifugal compressor 3 as described above, the air sucked from the intake pipe 13a is compressed by the first-stage centrifugal compressor 1 and its volume is reduced. After that, it is sucked into the second stage centrifugal compressor 2. Therefore, if the vanes 21 of the diffuser 15 are similar to each other in the first-stage centrifugal compressor 1 and the second-stage centrifugal compressor 2 (the same solidity), as shown in FIG. There is a problem that the usable flow rate range of the machine 2 becomes narrow.
【0006】例えば、第1段遠心圧縮機1のチョーク点
22は、第2段遠心圧縮機2のチョーク点23に符合
し、第1段遠心圧縮機1のストール点24は、第2段遠
心圧縮機2のストール点25に符合する。このため、第
2段遠心圧縮機2の使用可能な流量範囲が狭くなり、二
段式遠心圧縮機3全体としての使用可能な流量範囲(こ
の範囲は専ら第2段遠心圧縮機2に依存する)が狭くな
っていた。For example, the choke point 22 of the first-stage centrifugal compressor 1 matches the choke point 23 of the second-stage centrifugal compressor 2, and the stall point 24 of the first-stage centrifugal compressor 1 is the second-stage centrifuge. Match the stall point 25 of the compressor 2. Therefore, the usable flow range of the second-stage centrifugal compressor 2 is narrowed, and the usable flow range of the entire two-stage centrifugal compressor 3 (this range depends on the second-stage centrifugal compressor 2 exclusively). ) Was getting narrower.
【0007】また、ディフューザ15のベーン21を第
1段側と第2段側とで相似のものを用いると、全体とし
てそこそこの性能(効率および使用範囲)が得られるよ
うにベーン21のソリディティの設計がなされるため、
第1段側のディフューザ15aの効率が不十分で、第2
段側のディフューザ15bの使用範囲が狭くなってい
た。When the vanes 21 of the diffuser 15 are similar between the first stage side and the second stage side, the solidity of the vanes 21 is adjusted so as to obtain a moderate performance (efficiency and use range) as a whole. Because the design is done,
The efficiency of the diffuser 15a on the first stage side is insufficient,
The use range of the diffuser 15b on the step side was narrow.
【0008】以上の事情を考慮して創案された本発明の
目的は、全体としての効率を向上させ、且つ広い使用範
囲を得ることができる多段式遠心圧縮機を提供すること
にある。An object of the present invention, which was devised in view of the above circumstances, is to provide a multistage centrifugal compressor which can improve the efficiency as a whole and can obtain a wide range of use.
【0009】[0009]
【課題を解決するための手段】上記目的を達成すべく本
発明は、遠心圧縮機を複数直列に接続し、後段側の遠心
圧縮機のディフューザのベーンのソリディティを、前段
側の遠心圧縮機のディフューザのベーンのソリディティ
より小さくしたものである。In order to achieve the above object, the present invention has a plurality of centrifugal compressors connected in series, and the vane solidity of the diffuser of the centrifugal compressor of the latter stage is changed to the centrifugal compressor of the former stage. It is smaller than the diffuser vane solidity.
【0010】[0010]
【作用】上記構成によれば、前段側の遠心圧縮機のディ
フューザのベーンのソリディティが大きいので所定の設
計点回りで高効率を得、後段側の遠心圧縮機のディフュ
ーザのベーンのソリディティが小さいので広い使用範囲
を得る。すなわち、効率の向上は前段側のディフューザ
により達成され、その結果ピークが高まり使用範囲が狭
まってもそれは後段側のディフューザにより解消され
る。よって、全体として効率が向上すると共に使用範囲
が広くなる。According to the above construction, since the vane solidity of the diffuser of the centrifugal compressor on the upstream side is large, a high efficiency is obtained around a predetermined design point, and the solidity of the vane of the diffuser of the centrifugal compressor on the downstream side is small. Get a wide range of use. That is, the improvement in efficiency is achieved by the diffuser on the front stage side, and as a result, even if the peak is increased and the use range is narrowed, it is eliminated by the diffuser on the rear stage side. Therefore, the efficiency is improved as a whole and the usage range is widened.
【0011】[0011]
【実施例】本発明の一実施例を添付図面に基づいて説明
する。An embodiment of the present invention will be described with reference to the accompanying drawings.
【0012】図2は、前述した図1に示す二段式遠心圧
縮機3の各段のディフューザ15a,15bを示す図で
ある。図示するように、第1段遠心圧縮機1のディフュ
ーザ15aのベーン21のソリディティが、第2段遠心
圧縮機2のディフューザ15bのベーン21のソリディ
ティより大きくなっている。具体的には、第1段側のデ
ィフューザ15aのベーン21の数は13枚であり、第
2段側のディフューザ15bのベーン21の数は8枚で
ある。第1段側のディフューザ15aのベーン21の数
(13枚)は図3に示す従来のもの(10枚)より多
く、第2段側のディフューザ15bのベーン21の数
(8枚)は図3に示す従来のもの(10枚)より少な
い。FIG. 2 is a diagram showing the diffusers 15a and 15b at the respective stages of the two-stage centrifugal compressor 3 shown in FIG. As shown, the solidity of the vanes 21 of the diffuser 15 a of the first-stage centrifugal compressor 1 is larger than the solidity of the vanes 21 of the diffuser 15 b of the second-stage centrifugal compressor 2. Specifically, the number of vanes 21 of the diffuser 15a on the first stage side is 13, and the number of vanes 21 of the diffuser 15b on the second stage side is 8. The number of vanes 21 of the first-stage diffuser 15a (13) is larger than that of the conventional one (10) shown in FIG. 3, and the number of vanes 21 (8) of the second-stage diffuser 15b is 8 in FIG. It is less than the conventional one (10 sheets) shown in.
【0013】このため、第1段側のディフューザ15a
の効率はピークが高く使用範囲が狭くなり、第2段側の
ディフューザ15bの効率はピークが低く使用範囲が広
くなる。詳しくは、図2に示すように第1段側のチョー
ク点26が第2段側のチョーク点27に符合し、第1段
側のストール点28が第2段側のストール点29に符合
するように、各段のディフューザ15a,15bのソリ
ディティ(ベーン21のピッチおよびコード即ち枚数お
よび翼弦長)が設定される。よって、空気が第1段遠心
圧縮機1により圧縮されて第2段遠心圧縮機2に導入さ
れても、図中破線で示す従来のものように第2段側の使
用範囲が狭まることはない。すなわち、効率の向上は専
ら前段側のディフューザ15aにより達成され、その結
果ピークが高まり使用範囲が狭まってもそれは後段側の
ディフューザ15bにより解消される。よって、全体と
して効率が向上すると共に使用範囲が広くなる。Therefore, the diffuser 15a on the first stage side
Has a high peak and a narrow use range, and the efficiency of the diffuser 15b on the second stage side has a low peak and a wide use range. Specifically, as shown in FIG. 2, the choke point 26 on the first stage side matches the choke point 27 on the second stage side, and the stall point 28 on the first stage side coincides with the stall point 29 on the second stage side. Thus, the solidity (the pitch and chords of the vanes 21, that is, the number and chord length) of the diffusers 15a and 15b in each stage is set. Therefore, even if air is compressed by the first-stage centrifugal compressor 1 and introduced into the second-stage centrifugal compressor 2, the use range on the second-stage side is not narrowed unlike the conventional one shown by the broken line in the figure. . That is, the improvement in efficiency is achieved only by the diffuser 15a on the front stage side, and as a result, even if the peak is increased and the usage range is narrowed, it is eliminated by the diffuser 15b on the rear stage side. Therefore, the efficiency is improved as a whole and the usage range is widened.
【0014】第1段側のディフューザ15aのベーン2
1のソリディティをどの程度増やし、第2段側のディフ
ューザ15bのベーン21のソリディティをどの程度減
すかについては、個々の機械によってまた効率を優先す
るか使用範囲を優先するかによって異なる。The vane 2 of the diffuser 15a on the first stage side
How much the solidity of 1 is increased and how much the solidity of the vane 21 of the diffuser 15b on the second stage side is decreased depends on the individual machine and whether the priority is given to the efficiency or the usage range.
【0015】なお、本実施例のように二段式遠心圧縮機
のみならず、三段式四段式の遠心圧縮機に本発明を適用
してもよいことは勿論である。この場合、第1段側から
第2段側第3段側へ向けてディフューザのベーンの枚数
が徐々に少なくなっていく。また、ベーン21の数を変
更するのではなく、ベーン21のコードを変更してソリ
ディティを変えてもよい。この場合、前段側ディフュー
ザ15aのベーン21のコードを、後段側ディフューザ
15bのベーン21のコードより長くする。また、ピッ
チとコードの双方を変更してもよい。It is needless to say that the present invention may be applied not only to the two-stage centrifugal compressor as in this embodiment, but also to the three-stage four-stage centrifugal compressor. In this case, the number of vanes in the diffuser gradually decreases from the first stage side toward the second stage side and the third stage side. Further, instead of changing the number of the vanes 21, the code of the vanes 21 may be changed to change the solidity. In this case, the cord of the vane 21 of the front diffuser 15a is made longer than the cord of the vane 21 of the rear diffuser 15b. Further, both the pitch and the chord may be changed.
【0016】[0016]
【発明の効果】以上説明したように本発明に係る多段式
遠心圧縮機によれば、全体としての効率を向上させ、且
つ広い使用範囲を得ることができる。As described above, according to the multi-stage centrifugal compressor of the present invention, the efficiency as a whole can be improved and a wide range of use can be obtained.
【図1】二段式遠心圧縮機の説明図である。FIG. 1 is an explanatory diagram of a two-stage centrifugal compressor.
【図2】本発明の一実施例を示すディフューザの説明図
である。FIG. 2 is an explanatory diagram of a diffuser showing an embodiment of the present invention.
【図3】従来例を示すディフューザの説明図である。FIG. 3 is an explanatory diagram of a diffuser showing a conventional example.
【図4】ソリディティを説明するためのディフューザの
概略図である。FIG. 4 is a schematic view of a diffuser for explaining solidity.
1 第1段遠心圧縮機 2 第2段遠心圧縮機 3 二段式遠心圧縮機 15a 第1段側ディフューザ 15b 第2段側ディフューザ 21 ベーン 1 First Stage Centrifugal Compressor 2 Second Stage Centrifugal Compressor 3 Two Stage Centrifugal Compressor 15a First Stage Diffuser 15b Second Stage Diffuser 21 Vane
Claims (1)
の遠心圧縮機のディフューザのベーンのソリディティ
を、前段側の遠心圧縮機のディフューザのベーンのソリ
ディティより小さくしたことを特徴とする多段式遠心圧
縮機。1. A multi-stage, wherein a plurality of centrifugal compressors are connected in series and the vane solidity of the diffuser of the latter centrifugal compressor is made smaller than the vane solidity of the diffuser of the former centrifugal compressor. Centrifugal compressor.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP30109994A JP3438356B2 (en) | 1994-12-05 | 1994-12-05 | Multi-stage centrifugal compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP30109994A JP3438356B2 (en) | 1994-12-05 | 1994-12-05 | Multi-stage centrifugal compressor |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH08159094A true JPH08159094A (en) | 1996-06-18 |
JP3438356B2 JP3438356B2 (en) | 2003-08-18 |
Family
ID=17892847
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP30109994A Expired - Fee Related JP3438356B2 (en) | 1994-12-05 | 1994-12-05 | Multi-stage centrifugal compressor |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP3438356B2 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1304486A2 (en) * | 2001-10-18 | 2003-04-23 | Nuovo Pignone Holding S.P.A. | Stator blading for centrifugal compressors |
JP2010196706A (en) * | 2009-02-24 | 2010-09-09 | Dyson Technology Ltd | Diffuser |
US9714658B2 (en) | 2011-08-05 | 2017-07-25 | Mitsubishi Heavy Industries Compressor Corporation | Centrifugal compressor |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5273475B2 (en) | 2008-09-02 | 2013-08-28 | 日本電産株式会社 | Inline axial fan |
-
1994
- 1994-12-05 JP JP30109994A patent/JP3438356B2/en not_active Expired - Fee Related
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1304486A2 (en) * | 2001-10-18 | 2003-04-23 | Nuovo Pignone Holding S.P.A. | Stator blading for centrifugal compressors |
EP1304486A3 (en) * | 2001-10-18 | 2009-06-10 | Nuovo Pignone Holding S.P.A. | Stator blading for centrifugal compressors |
JP2010196706A (en) * | 2009-02-24 | 2010-09-09 | Dyson Technology Ltd | Diffuser |
US9714658B2 (en) | 2011-08-05 | 2017-07-25 | Mitsubishi Heavy Industries Compressor Corporation | Centrifugal compressor |
Also Published As
Publication number | Publication date |
---|---|
JP3438356B2 (en) | 2003-08-18 |
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