JPH0377396B2 - - Google Patents
Info
- Publication number
- JPH0377396B2 JPH0377396B2 JP21949686A JP21949686A JPH0377396B2 JP H0377396 B2 JPH0377396 B2 JP H0377396B2 JP 21949686 A JP21949686 A JP 21949686A JP 21949686 A JP21949686 A JP 21949686A JP H0377396 B2 JPH0377396 B2 JP H0377396B2
- Authority
- JP
- Japan
- Prior art keywords
- gas
- impeller
- main gas
- line
- shaft
- 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
Links
- 238000007789 sealing Methods 0.000 claims description 6
- 239000003518 caustics Substances 0.000 claims description 5
- 239000007789 gas Substances 0.000 description 94
- 239000003921 oil Substances 0.000 description 7
- 238000011144 upstream manufacturing Methods 0.000 description 5
- 238000000034 method Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000000203 mixture Substances 0.000 description 3
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 2
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000007797 corrosion Effects 0.000 description 2
- 238000005260 corrosion Methods 0.000 description 2
- 229910021529 ammonia Inorganic materials 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 150000004649 carbonic acid derivatives Chemical class 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000001257 hydrogen Substances 0.000 description 1
- 229910052739 hydrogen Inorganic materials 0.000 description 1
- 125000004435 hydrogen atom Chemical class [H]* 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 229910052757 nitrogen Inorganic materials 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
- 238000003786 synthesis reaction Methods 0.000 description 1
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は例えばアンモニア合成プラントに利用
され、中間吸込ガスラインを有する一軸多段遠心
圧縮機に係り、特に水素と窒素の中間吸込ガスに
炭酸塩などの腐蝕性成分が含んでいる場合に、中
間吸込ガスから軸封部を保護するのに好適な一軸
多段遠心圧縮機に関する。Detailed Description of the Invention [Field of Industrial Application] The present invention relates to a single-shaft multi-stage centrifugal compressor that is used, for example, in an ammonia synthesis plant and has an intermediate suction gas line. This invention relates to a single-shaft multi-stage centrifugal compressor suitable for protecting the shaft seal from intermediate suction gas when the compressor contains corrosive components such as.
従来この種の圧縮機はケーシング内に設けられ
た回転軸に多数の羽根車が配設されており、その
軸端側にはそれぞれ軸封部が設けられている。
Conventionally, in this type of compressor, a large number of impellers are arranged on a rotating shaft provided in a casing, and a shaft seal is provided at each end of the shaft.
これら軸封部にはシール油を供給するとともに
シール油の機内への流入を防止するためにシール
ガスフローとして吐出ガスの一部を供給してい
る。 Seal oil is supplied to these shaft seals, and a portion of the discharged gas is also supplied as a seal gas flow to prevent the seal oil from flowing into the machine.
この吐出ガスとしては、リサイクルラインから
供給されるリサイクルガス（中間吸込ガス）と主
ガスラインからの主ガスが混合された混合ガスが
使用されている。 As this discharged gas, a mixed gas is used, which is a mixture of recycle gas (intermediate suction gas) supplied from the recycle line and main gas from the main gas line.
これらシールガスとシール油はドレーナにより
気液分離されてそれぞれ外部へ排出される。 These seal gas and seal oil are separated into gas and liquid by a drainer and discharged to the outside.
また、上記とは異なる方法としては、シールガ
スフローを積極的に生成するために外部から清浄
な、かつ必要な圧力を有するバツフアガスを別の
圧力供給源から差圧制御により軸封部に供給する
ものがある。 In addition, as a method different from the above, in order to actively generate a sealing gas flow, clean buffer gas having the necessary pressure is supplied from the outside to the shaft sealing part by differential pressure control from another pressure supply source. There is something.
なお、この種の装置として関連するものには例
えば特開昭57−206800号、実開昭49−127664号な
どが挙げられる。 Incidentally, related devices of this type include, for example, Japanese Unexamined Patent Publication No. 57-206800 and Utility Model Application No. 49-127664.
上記従来技術のうち、前者のシールガス供給方
法においては、圧力バランス上どうしても軸封部
やドレーナに混合ガスが流入する。この混合ガス
中に含まれるリサイクルガスにはプロセス上炭酸
塩などの腐蝕性成分が含まれているため、軸封部
やドレーナが腐蝕してこれらの寿命が低下するな
どの問題点がある。
Among the conventional techniques described above, in the former seal gas supply method, the mixed gas inevitably flows into the shaft seal and the drainer due to pressure balance. Since the recycled gas contained in this mixed gas contains corrosive components such as carbonates due to the process, there are problems such as corrosion of the shaft seal and drainer, shortening their lifespan.
また、後者のシールガス供給方法では新たに圧
力供給源を必要とするため、コスト高になる。 Furthermore, the latter seal gas supply method requires an additional pressure supply source, resulting in high costs.
本発明の目的は軸封部などの寿命向上およびコ
スト低減を図るようにした一軸多段遠心圧縮機を
提供することにある。 SUMMARY OF THE INVENTION An object of the present invention is to provide a single-shaft multistage centrifugal compressor that improves the life of shaft seals and reduces costs.
上記目的を達成するため本発明は、主ガスの吸
込口と、回転軸に配設され主ガスを圧縮する多数
の羽根車と、前記回転軸の軸端側にそれぞれ設け
られた軸封部と、前記主ガスよりも高圧で腐食性
物質を含む中間吸込ガスの吸込口と、前記中間吸
込ガスを圧縮し前記主ガスラインの最終段羽根車
から吐出されるガスと合流させるように前記主ガ
スラインの最終段羽根車と背中合わせに同一回転
軸に設置された羽根車とを備え、前記主ガスライ
ンの最終段羽根車の仕事量が中間吸込ガスライン
の羽根車の仕事量よりも小さくなるように構成
し、これによつて最終段羽根車の上流側の主ガス
ラインに前記中間吸込ガスラインの吸込圧力より
も圧力の高い部分をつくり、この部分の主ガスを
前記軸封部に供給するガス供給ラインを設けたこ
とを特徴とするものである。
In order to achieve the above object, the present invention includes a main gas suction port, a large number of impellers disposed on a rotating shaft for compressing the main gas, and a shaft sealing section provided at each end of the rotating shaft. , a suction port for an intermediate suction gas containing a corrosive substance at a higher pressure than the main gas, and a main gas such that the intermediate suction gas is compressed and merged with the gas discharged from the final stage impeller of the main gas line. The final stage impeller of the line and the impeller installed back to back on the same rotating shaft are provided, so that the amount of work of the final stage impeller of the main gas line is smaller than the amount of work of the impeller of the intermediate suction gas line. This creates a part in the main gas line upstream of the final stage impeller with a pressure higher than the suction pressure of the intermediate suction gas line, and supplies the main gas in this part to the shaft sealing part. This is characterized by the provision of a gas supply line.
上記本発明によれば、主ガスラインの最終段羽
根車の仕事量（圧縮比またはヘツド）が中間吸込
ガスラインの羽根車の仕事量（圧縮比またはヘツ
ド）よりも小さくなるように構成して最終段羽根
車の上流側の主ガスラインに前記中間吸込ガスラ
インの吸込圧力よりも圧力の高い部分をつくり、
この部分の主ガスをガス供給ラインを介して前記
軸封部に供給する構成としているので、腐食性物
質を含まないまたはその含有量の少ない主ガスが
軸封部に供給され、腐食性物質を含む中間吸込ガ
スは軸封部に流入するのを阻止される。この結
果、軸封部の寿命向上につながる。また、軸封部
に外部から清浄なバツフアガスを供給するもので
はないからコス低減にもつながる。
According to the present invention, the amount of work (compression ratio or head) of the final stage impeller of the main gas line is smaller than the amount of work (compression ratio or head) of the impeller of the intermediate suction gas line. Creating a part in the main gas line upstream of the final stage impeller with a pressure higher than the suction pressure of the intermediate suction gas line,
Since the main gas in this part is supplied to the shaft seal via the gas supply line, the main gas that does not contain corrosive substances or contains a small amount of corrosive substances is supplied to the shaft seal, and the corrosive substances are removed. The intermediate suction gases contained therein are prevented from flowing into the shaft seal. As a result, the life of the shaft seal is improved. Furthermore, since clean buffer gas is not supplied to the shaft seal from the outside, costs can be reduced.
以下、本末栄の一軸多段遠心圧縮機の一実施例
を図面により説明する。
Hereinafter, one embodiment of Honsueei's single-shaft multistage centrifugal compressor will be described with reference to the drawings.
第１図および第２図は本発明の圧縮機の全体構
造を示す概略図で１は圧縮機のケーシング、２は
このケーシング１内に設けられた回転軸で、この
回転軸２には羽根車３が多数（この場合は３ａ〜
３ｅの５段）に取付けられており、駆動機（図示
せず）により高速回転するようになつている。４
は一段目の羽根車３ａ（主ガス吸込用羽根車）に
主ガスを供給する主ガス吸込口、５は最終段羽根
車３ｄと背中合わせに設置された羽根車３ｅに水
素と窒素などの中間吸込ガスを供給するために設
けられた中間ガス吸込口、６は主ガスラインに配
設された最終段羽根車３ｄからの主ガスと羽根車
３ｅからの中間ガスが混合された混合ガスを外部
へ供給する吐出口、これら主ガスライン側の最終
段羽根車３ｄと中間ガスライン側（リサイクルラ
イン）の羽根車３ｅは前述したように背中合わせ
に配設されている。７は最終段羽根車３ｄの上流
側、すなわち主ガスラインに配設された羽根車３
ｃ（この場合は３段目）の吐出側からスラストバ
ランスピストン１１に主ガスの一部を供給するシ
ールガス供給ライン、８はスラストバランスピス
トン１１とバランスラビリンス１２の間隙を通つ
た混合ガスを主ガス吸込口４に戻すシールバラン
スライン、９はスラストバランスライン、１０
ａ，１０ｂはスラストバランスライン９の圧力よ
り若干高く調整された圧力を有するシール油で、
このシール油はシールリング１３ａ，１３ｂに供
給される。１４ａ，１４ｂは混合ガスとシール油
を分離するドレーナー、１５ａ，１６ｂはオリフ
イス、１６は油溜めを示す。 1 and 2 are schematic diagrams showing the overall structure of the compressor of the present invention. 1 is a casing of the compressor, 2 is a rotating shaft provided in this casing 1, and this rotating shaft 2 has an impeller. 3 is the majority (in this case, 3a~
3e (5 stages)), and is rotated at high speed by a drive machine (not shown). 4
5 is a main gas suction port that supplies the main gas to the first stage impeller 3a (main gas suction impeller), and 5 is an intermediate suction port for hydrogen, nitrogen, etc. to the impeller 3e installed back to back with the final stage impeller 3d. An intermediate gas suction port 6 provided for supplying gas supplies a mixed gas, which is a mixture of the main gas from the final stage impeller 3d disposed in the main gas line and the intermediate gas from the impeller 3e, to the outside. The supply outlet, the final stage impeller 3d on the main gas line side, and the impeller 3e on the intermediate gas line side (recycle line) are arranged back to back as described above. 7 is an impeller 3 disposed on the upstream side of the final stage impeller 3d, that is, on the main gas line.
A seal gas supply line 8 supplies a part of the main gas from the discharge side of c (third stage in this case) to the thrust balance piston 11; Seal balance line returning to gas suction port 4, 9 is thrust balance line, 10
a and 10b are seal oils whose pressure is adjusted slightly higher than the pressure of the thrust balance line 9;
This seal oil is supplied to seal rings 13a, 13b. 14a and 14b are drainers that separate the mixed gas and seal oil, 15a and 16b are orifices, and 16 is an oil reservoir.
第３図〜第５図は、第１図および第２図に示す
圧縮機の内部構造を示す断面図、図において、前
記主ガスを圧縮する最終段羽根車３ｄと中間吸込
ガスを圧縮する羽根車３ｅは背中合わせに設置さ
れており、最終団羽根車３ｄの吸込圧力は羽根車
３ｅの吸込圧力より常に高くなるように形成され
ている。すなわち、回転する最終段羽根車３ｄの
入口から出口までの間に流れが羽根車３ｄから与
えられる仕事量（ヘツド量）を、羽根車３ｅでの
仕事量に比べて少なくなるようにする。この具体
的な一例としては、第５図に示す如く羽根車３ｄ
の羽根３d1の出口角度β３d1を羽根車３ｅの羽根
３e1の出口角度β３e1より小さくする。この場合
には、羽根車３ｄと羽根車３ｅの出口部は同一空
間であり、両羽根車の吐出圧力は等しく、両羽根
車を流れるガスの種類がほぼ同一であると仮定す
る。 FIGS. 3 to 5 are cross-sectional views showing the internal structure of the compressor shown in FIGS. 1 and 2. In the figures, the final stage impeller 3d compresses the main gas and the impeller compresses the intermediate suction gas. The wheels 3e are installed back to back, and the suction pressure of the final group of impellers 3d is always higher than the suction pressure of the impeller 3e. That is, the amount of work (head amount) given to the flow from the impeller 3d between the inlet and the outlet of the rotating final stage impeller 3d is made smaller than the amount of work done by the impeller 3e. As a specific example of this, as shown in FIG.
The exit angle β3d 1 of the blade 3d 1 is made smaller than the exit angle β3e 1 of the blade 3e 1 of the impeller 3e . In this case, it is assumed that the outlet portions of the impeller 3d and the impeller 3e are in the same space, the discharge pressures of both impellers are equal, and the types of gases flowing through both impellers are approximately the same.
また、上記とは異なる他の例としては、羽根車
３ｄの径を羽根車３ｅの径より小さくしてもよい
し、羽根車３ｄの無次元化した流量係数を大きく
するようにしてもよい。 Further, as another example different from the above, the diameter of the impeller 3d may be made smaller than the diameter of the impeller 3e, or the dimensionless flow coefficient of the impeller 3d may be made larger.
次に本発明の圧縮機の動作について説明する。
主ガス吸込口４から供給された主ガスは一段目の
羽根車３ａから順次羽根車３ｂ、羽根車３ｃおよ
び最終段羽根車３ｄを経て昇圧された後、中間ガ
ス吸込口５より羽根車３ｅを介して昇圧された中
間吸込ガスと混合して吐出口６から吐出される。
このとき、吐出口６における主ガスと中間吸込ガ
スの吐出圧力（例えば150Kg／cm2）は同じであり、
最終段羽根車３ｄの吸込圧力は羽根車３ｅの吸込
圧力よりも高くなつているため、最終段羽根車３
ｄの上流側の三段目の羽根車３ｃの主ガスの吐出
圧力（例えば140Kg／cm2）は羽根車３ｅの中間吸
込ガスの吸込圧力（例えば13Kg／cm2）より高くな
る。中間吸込ガスと混合する前の羽根車３ｃの吐
出側の主ガスの一部はシールガス供給ライン７を
経て軸封部を形成するスラストバランスピストン
１１の中間部に供給される。この主ガスの一部は
中間吸込ガスの圧力より高いため、図示矢印イの
如く機内に向つて流れ、また一部は図示矢印ロの
如くバランスラビリンス側に流れると共にスラス
トバランスライン８を介して主ガス吸込口４に戻
される。最終的に軸封部を流れた主ガスの一部は
ドレーナー１４ｂに流入する。 Next, the operation of the compressor of the present invention will be explained.
The main gas supplied from the main gas suction port 4 is pressurized through the first stage impeller 3a, the impeller 3b, the impeller 3c, and the final stage impeller 3d. The intermediate suction gas is mixed with the intermediate suction gas whose pressure has been increased through the intermediate suction gas, and the mixture is discharged from the discharge port 6.
At this time, the discharge pressures (for example, 150 Kg/cm 2 ) of the main gas and intermediate suction gas at the discharge port 6 are the same,
Since the suction pressure of the final stage impeller 3d is higher than the suction pressure of the impeller 3e, the final stage impeller 3
The main gas discharge pressure (for example, 140 Kg/cm 2 ) of the third impeller 3c on the upstream side of d is higher than the suction pressure (for example, 13 Kg/cm 2 ) of the intermediate suction gas of the impeller 3e. A portion of the main gas on the discharge side of the impeller 3c before being mixed with the intermediate suction gas is supplied via the seal gas supply line 7 to the intermediate portion of the thrust balance piston 11 forming a shaft seal. Part of this main gas is higher in pressure than the intermediate suction gas, so it flows toward the inside of the machine as shown by arrow A, and part of it flows toward the balance labyrinth side as shown by arrow B, and also flows through the thrust balance line 8 to the main gas. The gas is returned to the gas suction port 4. A portion of the main gas that has finally flowed through the shaft seal portion flows into the drainer 14b.
上述した如く、本発明の圧縮機においては、特
にバツフアーガスや中間吸込ガスを供給すること
なく、清浄な主ガスの一部を軸封部やドレーナー
に供給することができるので、腐蝕や有害生成物
から軸封部やドレーナーを保護することができ
る。したがつて、これらの寿命向上が図れる。ま
た、バツフアーガスのガス供給源を特に設ける必
要がないため、コスト低減も図れる。 As mentioned above, in the compressor of the present invention, a part of the clean main gas can be supplied to the shaft seal and the drainer without particularly supplying buffer gas or intermediate suction gas, so that corrosion and harmful products can be avoided. The shaft seal and drainer can be protected from damage. Therefore, their lifespan can be improved. Further, since there is no need to provide a special gas supply source for buffer gas, cost reduction can be achieved.
本発明の一軸多段遠心圧縮機によれば、主ガス
を圧縮する最終段羽根車と中間吸込ガスを圧縮す
る羽根車とを背中合わせに配設し、主ガスライン
側の最終段羽根車の吸込圧力を中間吸込ガスライ
ン側の羽根車の吸込圧力よりも常に高くなるよう
にし、最終段羽根車の上流側の主ガスの一部を軸
封部へ供給するように構成したので、軸封部など
の寿命向上およびコスト低減を図ることができる
などの効果を有する。
According to the single-shaft multistage centrifugal compressor of the present invention, the final stage impeller that compresses the main gas and the impeller that compresses the intermediate suction gas are arranged back to back, and the suction pressure of the final stage impeller on the main gas line side is is always higher than the suction pressure of the impeller on the intermediate suction gas line side, and a part of the main gas on the upstream side of the final stage impeller is supplied to the shaft seal, so that the shaft seal, etc. This has the effect of improving the service life and reducing costs.
第１図および第２図は本発明の一軸多段遠心圧
縮機の全体構造を示す概略図、第３図は第１図お
よび第２図に示す圧縮機の内部構造を示す断面
図、第４図は本発明における羽根車を説明するた
めの概略図、第５図は第４図の−線断面図で
ある。
１……ケーシング、３……羽根車、３ｄ……主
ガス用の最終段羽根車、３ｅ……中間吸込ガス用
の羽根車、４……主ガス吸込口、５……中間吸込
ガス吸込口、６……吐出口、７……シールガス供
給ライン。
1 and 2 are schematic diagrams showing the overall structure of the single-shaft multistage centrifugal compressor of the present invention, FIG. 3 is a sectional view showing the internal structure of the compressor shown in FIGS. 1 and 2, and FIG. 4 5 is a schematic diagram for explaining the impeller in the present invention, and FIG. 5 is a sectional view taken along the line -- in FIG. 4. 1... Casing, 3... Impeller, 3d... Final stage impeller for main gas, 3e... Impeller for intermediate suction gas, 4... Main gas suction port, 5... Intermediate suction gas suction port , 6...Discharge port, 7...Seal gas supply line.
Claims (1)
を圧縮する多数の羽根車と、前記回転軸の軸端側
にそれぞれ設けられた軸封部と、前記主ガスより
も高圧で腐食性物質を含む中間吸込ガスの吸込口
と、前記中間吸込ガスを圧縮し前記主ガスライン
の最終段羽根車から吐出されるガスと合流させる
ように前記主ガスラインの最終段羽根車と背中合
わせに同一回転軸に設置された羽根車とを備え、
前記主ガスラインの最終段羽根車の仕事量が中間
吸込ガスラインの羽根車の仕事量よりも小さくな
るように構成し、これによつて最終段羽根車の上
流側の主ガスラインに前記中間吸込ガスラインの
吸込圧力よりも圧力の高い部分をつくり、この部
分の主ガスを前記軸封部に供給するガス供給ライ
ンを設けたことを特徴とする一軸多段遠心圧縮
機。 ２ 主ガスラインの最終段羽根車の羽根出口角度
を中間吸込ガスラインの羽根車の羽根出口角度よ
りも小さく構成することによつて、主ガスライン
の最終段羽根車の仕事量を中間吸込ガスラインの
羽根車の仕事量よりも小さくしたことを特徴とす
る特許請求の範囲第１項に記載の一軸多段遠心圧
縮機。[Scope of Claims] 1. A main gas suction port, a large number of impellers arranged on the rotating shaft and compressing the main gas, a shaft sealing part provided on the shaft end side of the rotating shaft, and the main gas inlet. a suction port for an intermediate suction gas containing corrosive substances at a higher pressure than the gas; and an inlet at the end of the main gas line such that the intermediate suction gas is compressed and merged with the gas discharged from the final stage impeller of the main gas line. Equipped with a stage impeller and an impeller installed back to back on the same rotating shaft,
The work of the final stage impeller of the main gas line is configured to be smaller than the work of the intermediate suction gas line. 1. A single-shaft multi-stage centrifugal compressor, characterized in that a gas supply line is provided which creates a section with a pressure higher than the suction pressure of the suction gas line and supplies the main gas of this section to the shaft sealing section. 2 By configuring the blade exit angle of the final stage impeller of the main gas line to be smaller than the blade exit angle of the impeller of the intermediate suction gas line, the amount of work of the final stage impeller of the main gas line can be reduced to The single-shaft multi-stage centrifugal compressor according to claim 1, characterized in that the work volume of the single-shaft multi-stage centrifugal compressor is smaller than that of a line impeller.
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21949686A JPS6375392A (en) | 1986-09-19 | 1986-09-19 | Single-shaft multistage centrifugal compressor |
| US07/025,972 US4725196A (en) | 1986-09-19 | 1987-03-16 | Single-shaft multi-stage centrifugal compressor |
| DE3711553A DE3711553A1 (en) | 1986-09-19 | 1987-04-06 | SINGLE-SHAFT MULTI-STAGE RADIAL COMPRESSOR |
| DE8717902U DE8717902U1 (en) | 1986-09-19 | 1987-04-06 | Radial compressor for compressing fresh gas and cycle gas |
| CN87102697.XA CN1004017B (en) | 1986-09-19 | 1987-04-11 | Single-shaft multi-stage centrifugal compressor |
| IT8767327A IT1208874B (en) | 1986-09-19 | 1987-04-17 | SINGLE SHAFT CENTRIFUGAL COMPRESSOR PARTICULARLY FOR GAS COMPRESSION IN INDUSTRIAL PLANTS |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21949686A JPS6375392A (en) | 1986-09-19 | 1986-09-19 | Single-shaft multistage centrifugal compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6375392A JPS6375392A (en) | 1988-04-05 |
| JPH0377396B2 true JPH0377396B2 (en) | 1991-12-10 |
Family
ID=16736361
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP21949686A Granted JPS6375392A (en) | 1986-09-19 | 1986-09-19 | Single-shaft multistage centrifugal compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JPS6375392A (en) |
| IT (1) | IT1208874B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10145381B2 (en) | 2014-01-23 | 2018-12-04 | Mitsubishi Heavy Industries Compressor Corporation | Geared centrifugal compressor with pressure adjustment portion to balance axial thrust |
-
1986
- 1986-09-19 JP JP21949686A patent/JPS6375392A/en active Granted
-
1987
- 1987-04-17 IT IT8767327A patent/IT1208874B/en active
Also Published As
| Publication number | Publication date |
|---|---|
| IT8767327A0 (en) | 1987-04-17 |
| IT1208874B (en) | 1989-07-10 |
| JPS6375392A (en) | 1988-04-05 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4725196A (en) | Single-shaft multi-stage centrifugal compressor | |
| CA1321177C (en) | Sealing and dynamic operation of a liquid ring pump | |
| US4734018A (en) | Vacuum pump with plural labyrinth seal portions | |
| US5599164A (en) | Centrifugal process pump with booster impeller | |
| CA2196901A1 (en) | Dry gas seal contamination prevention system | |
| US20020056374A1 (en) | Gas separation with split stream centrifugal turbomachinery | |
| US5507625A (en) | Liquid ring pumps | |
| US4311004A (en) | Gas compression system and method | |
| JPS585495A (en) | Liquid sealed vacuum pump | |
| EP1094201A1 (en) | Partial recovery of the energy lost in steam turbine leakages | |
| JPH0377396B2 (en) | ||
| JPH0642475A (en) | Single screw compressor | |
| CN112400064B (en) | Regenerative blower-compressor with shaft bypass fluid circulation port | |
| AU739307B2 (en) | Multi-stage side channel pump | |
| US2543923A (en) | Radial air compressor | |
| CN207673632U (en) | A kind of gas-liquid delivery promotion centrifugal oil pump | |
| JP2008190487A (en) | Centrifugal type fluid machine | |
| JP2014062504A (en) | Centrifugal fluid machine | |
| JPS60166791A (en) | Fluid compressor | |
| US4012164A (en) | Rotor with recirculation | |
| US4003673A (en) | Fluid pressurizer | |
| JPH066957B2 (en) | Turbo compressor with intermediate suction | |
| SU700689A1 (en) | Centrifugal pump for handling gas-liquid media | |
| CN115750353B (en) | Shielding multistage self-cooling compressor | |
| JPH0972292A (en) | Compound multi-stage centrifugal compressor provided with two group impellers coaxially |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |