JPH10115298A - Multi-shaft multi-stage combined type compressor - Google Patents
Multi-shaft multi-stage combined type compressorInfo
- Publication number
- JPH10115298A JPH10115298A JP8269492A JP26949296A JPH10115298A JP H10115298 A JPH10115298 A JP H10115298A JP 8269492 A JP8269492 A JP 8269492A JP 26949296 A JP26949296 A JP 26949296A JP H10115298 A JPH10115298 A JP H10115298A
- Authority
- JP
- Japan
- Prior art keywords
- compressor
- stage
- gas
- shaft
- impeller
- 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
- 230000006835 compression Effects 0.000 claims abstract description 72
- 238000007906 compression Methods 0.000 claims abstract description 72
- 238000011084 recovery Methods 0.000 claims description 36
- 239000007789 gas Substances 0.000 description 60
- 238000009434 installation Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 239000010687 lubricating oil Substances 0.000 description 4
- 239000003921 oil Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification 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
- 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
-
- 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
- F04D29/08—Sealings
- F04D29/10—Shaft sealings
- F04D29/102—Shaft sealings especially adapted for elastic fluid pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/60—Fluid transfer
- F05D2260/602—Drainage
- F05D2260/6022—Drainage of leakage having past a seal
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Gear Transmission (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、異なる圧力ライン
の系統を持つプラント向けの多軸多段コンバインド型コ
ンプレッサに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multi-shaft, multi-stage combined compressor for a plant having different pressure line systems.
【０００２】[0002]
【従来の技術】従来、高圧ラインと低圧ラインの２系統
を持つプラントにガスを供給するのに、高圧ラインには
高圧用のコンプレッサを用い、低圧ラインには低圧用の
コンプレッサを用い、２台のコンプレッサでガスをそれ
ぞれのラインに圧送していた。図８は、ガスを圧縮する
従来の２軸４段型のコンプレッサ５１を示す。このコン
プレッサ５１は、ケーシングが上部歯車室５２と下部歯
車室５３に２分割され、その分割水平面に３組の軸受を
設け、駆動ホイール５４を取付けている駆動軸５５、低
圧段ピニオン軸５８、高圧段ピニオン軸５９を支持して
いる。2. Description of the Related Art Conventionally, to supply gas to a plant having two systems of a high pressure line and a low pressure line, a high pressure compressor is used for a high pressure line and a low pressure compressor is used for a low pressure line. Gas was pumped to each line by a compressor. FIG. 8 shows a conventional two-shaft, four-stage compressor 51 for compressing gas. In the compressor 51, a casing is divided into an upper gear chamber 52 and a lower gear chamber 53, and three sets of bearings are provided on the divided horizontal plane. A drive shaft 55 to which a drive wheel 54 is mounted, a low-pressure stage pinion shaft 58, a high-pressure The step pinion shaft 59 is supported.
【０００３】駆動ホイール５４には、各ピニオン軸５
８，５９の中央に設けたピニオン６０，６１が噛合し、
それらの両端には各々一対の羽根車６２，６３が取付け
られている。羽根車６２，６３は、それぞれ渦巻室６
４，６５とディフューザ６６，６７で覆われている。図
９は、羽根車６２，６３を固定するピニオン軸５８，５
９のシール構造を示す。図に示すように、羽根車６２，
６３によって圧縮されたガスは、軸シール部であるラビ
リンスシール６８により外部への漏れを減少している。
ラビリンスシール６８の側部には大気室６９を介在して
油切り７０を設けている。スペース６９は大気に連通
し、ラビリンスシール６８を介して、圧縮ガスに潤滑油
がまぎれ込まないようにしている。[0003] A drive wheel 54 is provided with each pinion shaft 5.
Pinions 60 and 61 provided at the center of 8, 59 mesh with each other,
A pair of impellers 62 and 63 are attached to both ends thereof. The impellers 62 and 63 are respectively
4,65 and diffusers 66,67. FIG. 9 shows pinion shafts 58, 5 for fixing impellers 62, 63.
9 shows a seal structure of No. 9. As shown in the figure, the impeller 62,
The gas compressed by 63 reduces leakage to the outside by a labyrinth seal 68 which is a shaft seal portion.
An oil drain 70 is provided on the side of the labyrinth seal 68 with an atmosphere chamber 69 interposed therebetween. The space 69 communicates with the atmosphere to prevent lubricating oil from being mixed into the compressed gas via the labyrinth seal 68.
【０００４】[0004]
【発明が解決しようとする課題】上記したように、高圧
ラインと低圧ラインの２系統のラインにガスを供給する
のに、高圧用コンプレッサと低圧用コンプレッサの２台
のコンプレッサを用いるため、設備費や据付け場所を必
要としていた。また、コンプレッサの吐出出力が高くな
ると、ラビリンスシールから外部へのリークガスが多く
なる問題があり、高圧用コンプレッサ側から低圧用コン
プレッサ側へリークガスを回収する必要がある。この場
合、２台のコンプレッサの据付け場所が定まっていない
ため、それに応じてリークガスを回収するための配管工
事が現地で必要になり、コンプレッサの据付け時にも手
間がかかっていた。As described above, since two compressors, a high-pressure compressor and a low-pressure compressor, are used to supply gas to two lines of a high-pressure line and a low-pressure line, equipment costs are reduced. And needed a place for installation. In addition, when the discharge output of the compressor increases, there is a problem that leak gas from the labyrinth seal to the outside increases, and it is necessary to collect the leak gas from the high-pressure compressor side to the low-pressure compressor side. In this case, since the installation locations of the two compressors are not determined, piping work for collecting the leak gas is required on site accordingly, and the installation of the compressor has been troublesome.
【０００５】本発明は上記課題に鑑みてなされたもの
で、２種類のコンプレッサを一つのケーシングに一体に
し、部品点数を減らすとともに、リークされた圧縮ガス
を容易に回収できるようにし、圧縮ガスの外部リークを
低減することのできる多軸多段コンバインド型コンプレ
ッサを提供することを目的とする。[0005] The present invention has been made in view of the above-mentioned problems, and two types of compressors are integrated into one casing to reduce the number of parts and to easily recover leaked compressed gas. It is an object of the present invention to provide a multi-shaft, multi-stage combined type compressor capable of reducing external leakage.
【０００６】[0006]
【課題を解決するための手段】上記目的を達成するため
に、本発明は駆動軸に取付けた駆動ホイールと、この駆
動ホイールに噛合するピニオンと、羽根車と上記ピニオ
ンを支持するピニオン軸と、羽根車を覆う渦巻室とを備
え、羽根車によってガスを圧縮するコンプレッサにおい
て、上記ピニオン及び渦巻室で覆われている羽根車を持
つピニオン軸を、上記コンプレッサに新たに設けて成
り、このピニオン軸の羽根車の回転により、上記コンプ
レッサの既設の圧縮系とは独立した圧縮系で、ガスの圧
縮ができるようにしている。To achieve the above object, the present invention provides a drive wheel mounted on a drive shaft, a pinion meshing with the drive wheel, a pinion shaft supporting the impeller and the pinion, and A spiral chamber for covering the impeller, wherein the compressor compresses gas by the impeller, wherein the pinion and the pinion shaft having the impeller covered by the spiral chamber are newly provided in the compressor. By the rotation of the impeller, the gas can be compressed by a compression system independent of the existing compression system of the compressor.
【０００７】[0007]
【発明の実施の形態】以下、本発明の第１の実施の形態
による多軸多段コンバインド型コンプレッサについて、
図面を参照しながら説明する。図１及び図２は、本発明
に係る３軸６段のコンバインド型コンプレッサ１を示
す。このコンプレッサ１は、一つのコンプレッサでガス
を高圧縮する高圧系圧縮部とガスをそれよりも低圧力で
圧縮する低圧系圧縮部の２系統の圧縮系を備えた構造に
なっている。図１に示すように、その外部構造は、上部
歯車室２と、図では上端部３ａのみ示す中部歯車室３
と、下部歯車室４とに３分割され、上部歯車室２には、
低圧系圧縮部が配設され、中部歯車室３及び下部歯車室
４との間に高圧系圧縮部が配設されている。中部歯車室
３と下部歯車室４との間には、その分割水平面に３組の
軸受を設け、駆動ホイール８を取付けている駆動軸９、
高圧系圧縮部の低圧段ピニオン軸１０及び高圧段ピニオ
ン軸１１を支持している。また、上部歯車室２と中部歯
車室３との間には、その分割水平面に軸受けを設け低圧
系圧縮部のピニオン軸１２を支持している。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a multi-shaft, multi-stage combined type compressor according to a first embodiment of the present invention will be described.
This will be described with reference to the drawings. 1 and 2 show a three-shaft, six-stage combined type compressor 1 according to the present invention. The compressor 1 has a structure including two compression systems, a high-pressure system compression unit that compresses gas with a single compressor at a high pressure and a low-pressure system compression unit that compresses gas with a lower pressure. As shown in FIG. 1, the external structure includes an upper gear chamber 2 and a middle gear chamber 3 shown only in an upper end 3a in the figure.
And the lower gear chamber 4 are divided into three parts.
A low-pressure system compression section is provided, and a high-pressure system compression section is provided between the middle gear chamber 3 and the lower gear chamber 4. Between the middle gear chamber 3 and the lower gear chamber 4, three sets of bearings are provided on the divided horizontal plane, and a drive shaft 9 on which a drive wheel 8 is mounted,
The low-pressure stage pinion shaft 10 and the high-pressure stage pinion shaft 11 of the high-pressure system compression unit are supported. A bearing is provided between the upper gear chamber 2 and the middle gear chamber 3 on a divided horizontal plane to support the pinion shaft 12 of the low-pressure system compression section.
【０００８】図２に示すように、各ピニオン軸１０〜１
２には、それらの中央に設けたピニオン１４〜１６が駆
動ホイール８に噛合し、ピニオン軸１０の端部には一対
の高圧系圧縮部の第１段部１７の羽根車１７ａと第２段
部１８の羽根車１８ａが取付けられ、ピニオン軸１１の
端部には高圧系圧縮部の第３段部１９の羽根車１９ａと
第４段部２０の羽根車２０ａが取付けられている。ま
た、駆動ホイール８の頂き部に配置されているピニオン
１２の端部には低圧系圧縮部の第１段部２１の羽根車２
１ａと第２段２２の羽根車２２ａが取付けられている。
高圧系圧縮部の各羽根車１７ａ〜２０ａは、その順に１
段用渦巻室２４、２段用渦巻室２５、３段用渦巻室２
６、４段用渦巻室２７で覆われ、低圧系圧縮部の各羽根
車２１ａ，２２ａは、１段用渦巻室２８，２段用渦巻室
２９で覆われている。As shown in FIG. 2, each of the pinion shafts 10-1
2, pinions 14 to 16 provided at the center thereof mesh with the drive wheel 8, and an end of the pinion shaft 10 has an impeller 17 a of a first step portion 17 of a pair of high-pressure system compression portions and a second stage. An impeller 18a of the section 18 is attached, and an impeller 19a of the third step section 19 and an impeller 20a of the fourth step section 20 of the high-pressure system compression section are attached to the end of the pinion shaft 11. The end of the pinion 12 disposed at the top of the drive wheel 8 has an impeller 2 of the first step portion 21 of the low-pressure system compression section.
1a and an impeller 22a of the second stage 22 are attached.
Each of the impellers 17a to 20a of the high-pressure system compression section is
Step spiral chamber 24, two-stage spiral chamber 25, three-stage spiral chamber 2
The impellers 21 a and 22 a of the low-pressure system compression section are covered with a first-stage volute chamber 28 and a second-stage volute chamber 29, respectively.
【０００９】図３は、高圧系圧縮部の羽根車を取付けて
いるピニオン軸のシール構造の拡大図である。高圧系圧
縮部の各ピニオン軸のシール構造は同じ構造であるの
で、羽根車１７ａを設けている部位のシール構造につい
てのみ説明する。図に示すように、羽根車１７ａのシー
ル構造３１は、ラビリンスシール３１ａ〜３１ｃの３段
シール構造にし、これらの間にガス回収室Ｂ，Ｃを設け
ている。すなわち、圧力室Ａと第１段ガス回収室Ｂとの
間にシール部である第１段ラビリンスシール３１ａを配
設し、第１段ガス回収室Ｂと第２段回収室Ｃとの間に第
２段ラビリンスシール３１ｂを配設し、第２段ガス回収
室Ｃと大気室Ｄとの間には第３段ラビリンスシール３１
ｃを配設している。そして、第１段ガス回収室Ｂは管路
ｂに接続され、第２段ガス回収室Ｃは管路ｃに接続さ
れ、大気室Ｄは大気と連通し、油切り３４からの潤滑油
が圧縮室Ａ側に入り込むのを防止している。FIG. 3 is an enlarged view of the seal structure of the pinion shaft on which the impeller of the high-pressure system compression section is mounted. Since the seal structure of each pinion shaft of the high-pressure system compression section is the same, only the seal structure of the portion where the impeller 17a is provided will be described. As shown in the figure, the seal structure 31 of the impeller 17a has a three-stage seal structure of labyrinth seals 31a to 31c, and gas recovery chambers B and C are provided therebetween. That is, a first-stage labyrinth seal 31a, which is a seal portion, is provided between the pressure chamber A and the first-stage gas recovery chamber B, and is provided between the first-stage gas recovery chamber B and the second-stage recovery chamber C. A second-stage labyrinth seal 31b is provided, and a third-stage labyrinth seal 31 is provided between the second-stage gas recovery chamber C and the atmosphere chamber D.
c is provided. The first-stage gas recovery chamber B is connected to the pipe b, the second-stage gas recovery chamber C is connected to the pipe c, the atmosphere chamber D communicates with the atmosphere, and the lubricating oil from the oil drain 34 is compressed. It is prevented from entering the room A side.
【００１０】図４は、低圧系圧縮部の羽根車を取付けて
いるピニオン軸のシール構造の拡大図である。低圧系圧
縮部のピニオン軸のシール構造は同じ構造であるので、
羽根車２１ａを設けている部位のシール構造についての
み説明する。図に示すように、羽根車２１ａのシール構
造３６は、ラビリンスシール３６ａ，３６ｂの２段シー
ル構造にし、これらの間にガス回収室Ｆを設けている。
すなわち、圧力室Ｅとガス回収室Ｆとの間にシール部で
ある第１段ラビリンスシール３６ａを配設し、ガス回収
室Ｆと大気室Ｇとの間には第２段ラビリンスシール３６
ｂを配設している。ガス回収室Ｆは管路ｆに接続され、
大気室Ｇは大気と連通し、油切り３８からの潤滑油が圧
縮室Ｅ側に入り込むのを防止している。FIG. 4 is an enlarged view of the seal structure of the pinion shaft to which the impeller of the low-pressure system compression section is attached. Since the seal structure of the pinion shaft of the low-pressure system compression section is the same,
Only the seal structure of the portion where the impeller 21a is provided will be described. As shown in the figure, the seal structure 36 of the impeller 21a has a two-stage seal structure of labyrinth seals 36a and 36b, and a gas recovery chamber F is provided between them.
That is, a first-stage labyrinth seal 36a, which is a seal portion, is provided between the pressure chamber E and the gas recovery chamber F, and a second-stage labyrinth seal 36a is provided between the gas recovery chamber F and the atmosphere chamber G.
b is provided. The gas recovery chamber F is connected to the pipe f,
The atmosphere chamber G communicates with the atmosphere to prevent the lubricating oil from the oil drain 38 from entering the compression chamber E side.
【００１１】図５は、各ガス回収室Ｂ，Ｃ，Ｆに接続さ
れている管路ｂ，ｃ，ｆのリークガスの流れを示す配管
図である。高圧系圧縮部の第１段部１７〜第４段部２０
の第１ガス回収室Ｂに接続されている管路ｂは、高圧系
圧縮部の第１段部１７の入り口に連通し、第１段部１７
〜第４段部２０の第２ガス回収室Ｃに接続されている管
路ｃは、低圧系圧縮部の第１段部２１の入り口に接続さ
れている。また、低圧系圧縮部の第１段部２１、第２段
部２２のガス回収室Ｆに接続されている管路ｆは、低圧
系圧縮部の第１段部２１の入り口に接続されている。な
お、高圧系圧縮部の第１段部１７及び第２段部１８の管
ｃの本数はピニオン軸の外形の大きさに比例して多くす
る。FIG. 5 is a piping diagram showing the flow of leak gas in the pipes b, c, f connected to the gas recovery chambers B, C, F. First stage portion 17 to fourth stage portion 20 of high-pressure system compression section
The pipe b connected to the first gas recovery chamber B communicates with the entrance of the first step 17 of the high-pressure system compression section.
The pipe c connected to the second gas recovery chamber C of the fourth to fourth steps 20 is connected to the entrance of the first step 21 of the low-pressure system compression section. Further, a pipe f connected to the gas recovery chamber F of the first stage 21 and the second stage 22 of the low-pressure system compression unit is connected to the entrance of the first stage 21 of the low-pressure system compression unit. . The number of tubes c of the first stage 17 and the second stage 18 of the high-pressure system compression section is increased in proportion to the size of the outer shape of the pinion shaft.
【００１２】以上、本発明の第１の実施の形態による多
軸多段コンバインド型コンプレッサの構成について説明
したが、次にその作用について説明する。コンプレッサ
１の駆動ホイール８が回転すると、各々の増速比でこれ
に噛合しているピニオン１４〜１６に動力が伝達し、高
圧系圧縮部では羽根車１７ａ〜２０ａの回転により吸引
したガスを所定の圧力まで昇圧させ、低圧系圧縮部で
は、羽根車２１ａ，２２ａにより吸引したガスを所定の
圧力まで昇圧させ、それぞれのラインに圧縮ガスを供給
する。このように、コンプレッサ１は高圧系圧縮部と低
圧系圧縮部の２系統の圧縮部を設けているので、１台の
コンプレッサで圧縮力の異なるガスを２系統のライン
に、同時に送ることができる。The configuration of the multi-shaft multi-stage combined type compressor according to the first embodiment of the present invention has been described above. Next, the operation thereof will be described. When the drive wheel 8 of the compressor 1 rotates, power is transmitted to the meshed pinions 14 to 16 at the respective speed increasing ratios, and in the high-pressure system compression section, the gas sucked by the rotation of the impellers 17a to 20a is removed by a predetermined amount. In the low-pressure system compression section, the gas sucked by the impellers 21a and 22a is raised to a predetermined pressure, and the compressed gas is supplied to each line. As described above, since the compressor 1 is provided with the two systems of the high-pressure system compression unit and the low-pressure system compression unit, one compressor can simultaneously send gases having different compression forces to the two lines. .
【００１３】コンプレッサ１の稼働中は、図３に示す高
圧系圧縮部の圧縮室Ａのガスが、徐々に大気室Ｄ側にリ
ークするため、各室の内圧の大きさは、圧縮室Ａ＞第１
ガス回収室Ｂ＞第２ガス回収室Ｃ＞大気室Ｄの関係にあ
り、低圧系圧縮部の各室の内圧は、圧縮室Ｅ＞ガス回収
室Ｆ＞大気室Ｇの関係にある。また、第１ガス回収室Ｂ
と高圧系圧縮部の第１段部１７の入り口と圧力が均衡し
ており、第２ガス回収室Ｃとガス回収室Ｆは、低圧系圧
縮部の第１段部２１の入り口と圧力が均衡している。During the operation of the compressor 1, the gas in the compression chamber A of the high-pressure system compression section shown in FIG. 3 gradually leaks to the atmosphere chamber D side. First
There is a relation of gas recovery chamber B> second gas recovery chamber C> atmosphere chamber D, and the internal pressure of each chamber of the low-pressure compression section has a relation of compression chamber E> gas recovery chamber F> atmosphere chamber G. Also, the first gas recovery chamber B
The pressure is balanced with the inlet of the first stage 17 of the high-pressure system compression unit, and the pressure of the second gas recovery chamber C and the gas recovery chamber F are balanced with the inlet of the first stage 21 of the low-pressure system compression unit. doing.
【００１４】よって、図４に示すように、比較的圧力の
大きな第１ガス回収室Ｂにリークした圧縮ガスが高圧系
圧縮部の第１段部１７の入り口に回収され、それよりも
圧力の小さい第２ガス回収室Ｃ及びガス回収室Ｆのリー
クした圧縮ガスが合流し、低圧系圧縮部の第１段部２１
の入り口に回収される。このような構成により、各ガス
回収室にリークした圧縮ガスを容易に回収することがで
き、高圧系圧縮部の第２ガス回収室Ｃ、低圧系圧縮部の
ガス回収室Ｆと大気室Ｄ，Ｇとの差圧が小さくなり、最
終的にガスが大気へリークするのを減少し、効率のよい
コンプレッサを提供できる。Therefore, as shown in FIG. 4, the compressed gas leaked into the first gas recovery chamber B having a relatively high pressure is recovered at the entrance of the first stage 17 of the high-pressure system compression section, and the pressure of the compressed gas is increased. The compressed gas leaked from the small second gas recovery chamber C and the small gas recovery chamber F merges into the first stage 21 of the low-pressure system compression section.
Collected at the entrance of With such a configuration, the compressed gas leaked to each gas recovery chamber can be easily recovered, and the second gas recovery chamber C of the high-pressure system compression section, the gas recovery chamber F of the low-pressure system compression section and the atmosphere chamber D, The differential pressure from G is reduced, and finally the leakage of gas into the atmosphere is reduced, and an efficient compressor can be provided.
【００１５】次に、本発明の第２の実施の形態による多
軸多段コンバインド型コンプレッサについて説明する。
図６は、コンプレッサ４１の駆動ホイール４２とその周
部に配置される高圧系圧縮部の低圧段４３及び高圧段４
４、中圧系圧縮部４５、低圧系圧縮部４６を示す。この
コンバインド型のコンプレッサ４１は、４軸８段の例で
あり、この方法にすれば３系統の異なるガスの圧縮をす
ることができる。図７は、コンプレッサ４１の各ガス回
収室に接続されている管路のリークガスの流れを示す配
管図である。高圧系圧縮部と低圧系圧縮部について上記
した図５に示すコンプレッサ１の管路と同じ符号を付し
ており、中圧系圧縮部４５については、図３に示すラビ
リンスシールを３段用いたタイプのものを使用し、第１
回収室ＢをＨとし、これに接続されている管路をｈ、第
２回収室ＣをＪとしこれに接続されている管路をｊとし
ている。Next, a multi-shaft, multi-stage combined type compressor according to a second embodiment of the present invention will be described.
FIG. 6 shows a low-pressure stage 43 and a high-pressure stage 4 of a driving wheel 42 of a compressor 41 and a high-pressure system compression unit disposed around the driving wheel 42.
4, an intermediate pressure system compression unit 45 and a low pressure system compression unit 46 are shown. This combined type compressor 41 is an example having four shafts and eight stages, and this method can compress three different gases. FIG. 7 is a piping diagram illustrating a flow of leak gas in a pipeline connected to each gas recovery chamber of the compressor 41. The high-pressure system compression unit and the low-pressure system compression unit are denoted by the same reference numerals as those of the above-described pipe line of the compressor 1 shown in FIG. 5, and the intermediate-pressure system compression unit 45 uses three stages of labyrinth seals shown in FIG. Use type 1
The recovery chamber B is H, the pipeline connected to it is h, the second recovery chamber C is J, and the pipeline connected to it is j.
【００１６】すなわち、中圧系圧縮部の第１回収室Ｈに
接続されている管路ｈは中圧系圧縮部の第１段の入り口
に接続され、第２回収室Ｊに接続されている管路ｊは、
高圧系圧縮部の第１段部〜第４段部の第２ガス回収室Ｃ
に接続されている管路ｃ及び低圧系圧縮部の第１段部、
第２段部のガス回収室Ｆに接続されている管路ｆと合流
して、低圧系圧縮部の第１段部の入り口に接続されてい
る。なお、高圧系圧縮部と低圧系圧縮部の管路について
は、上記した図５に示すコンプレッサ１の管路と同じで
ある。このように、本実施の形態ではコンプレッサ１に
高圧系圧縮部、中圧系圧縮部及び低圧系圧縮部の３系統
の圧縮部を設けているので、１台のコンプレッサで圧縮
力の異なるガスを３系統のラインに、同時に送ることが
できるとともに、ガスが大気へリークするのを減少し、
効率のよいコンプレッサを提供できる。That is, the pipe h connected to the first recovery chamber H of the intermediate pressure system compression section is connected to the first stage entrance of the intermediate pressure system compression section, and connected to the second recovery chamber J. Pipe j
Second gas recovery chamber C in the first to fourth stages of the high-pressure system compression unit
Pipeline c connected to the first stage of the low-pressure system compression section,
It merges with the pipeline f connected to the gas recovery chamber F of the second stage, and is connected to the entrance of the first stage of the low-pressure system compression unit. Note that the pipelines of the high-pressure system compression section and the low-pressure system compression section are the same as the pipeline of the compressor 1 shown in FIG. 5 described above. As described above, in the present embodiment, the compressor 1 is provided with the three compression units of the high-pressure system compression unit, the medium-pressure system compression unit, and the low-pressure system compression unit. It can be sent to three lines at the same time, reducing gas leakage to the atmosphere,
An efficient compressor can be provided.
【００１７】以上、本発明の各実施の形態について説明
したが、勿論、本発明はこれらに限定されることなく本
発明の技術的思想に基いて種々の変形が可能である。例
えば、上記実施の形態では、３軸６段及び４軸８段のコ
ンプレッサについて説明したが、本発明は２軸４段や３
軸５段（例えば、３軸６段の６段目がないもの）や４軸
７段等のコンプレッサについても適用が可能である。Although the embodiments of the present invention have been described above, the present invention is, of course, not limited to these, and various modifications can be made based on the technical concept of the present invention. For example, in the above embodiment, a three-shaft six-stage compressor and a four-shaft eight-stage compressor have been described.
The present invention is also applicable to compressors having five shafts (for example, three shafts without six stages) and four shafts with seven stages.
【００１８】[0018]
【発明の効果】以上述べたように、本発明の多軸多段コ
ンバインド型コンプレッサは、１つのケーシングに多系
統の圧縮部を設けているので、１台のコンプレッサで圧
縮力の異なるガスを多系統のラインに、同時に送ること
ができる。また、多系統の圧縮機を１つのケーシングに
組み込んだことにより、台板、駆動ホイールを駆動させ
る駆動機及び潤滑油装置等を共用することができ、部品
点数を大幅に減らすことができる。コンプレッサの据付
け面積も、複数個のコンプレッサの設置面積を必要とせ
ず、システム全体をコンパクトにすることができる。さ
らに、設置時に高圧コンプレッサ側から低圧コンプレッ
サ側へリークガスを回収するための現地工事を必要とし
なくなった。As described above, the multi-shaft, multi-stage combined type compressor according to the present invention is provided with a multi-system compression section in one casing. To the same line at the same time. In addition, by incorporating a multi-system compressor into one casing, it is possible to share the drive unit for driving the base plate, the drive wheel, the lubricating oil device, and the like, and it is possible to greatly reduce the number of parts. The installation area of the compressor does not require the installation area of a plurality of compressors, and the whole system can be made compact. Further, at the time of installation, there is no need for on-site work for collecting leak gas from the high-pressure compressor side to the low-pressure compressor side.
【図１】本発明の第１の実施の形態による多軸多段コン
バインド型コンプレッサの斜視図である。FIG. 1 is a perspective view of a multi-shaft, multi-stage combined type compressor according to a first embodiment of the present invention.
【図２】同多軸多段コンバインド型コンプレッサの平断
面図である。FIG. 2 is a plan sectional view of the multi-shaft, multi-stage combined type compressor.
【図３】同多軸多段コンバインド型コンプレッサの高圧
系圧縮部のシール構造を示す縦断面図である。FIG. 3 is a vertical sectional view showing a seal structure of a high-pressure system compression section of the multi-shaft multi-stage combined type compressor.
【図４】同多軸多段コンバインド型コンプレッサの低圧
系圧縮部のシール構造を示す縦断面図である。FIG. 4 is a longitudinal sectional view showing a seal structure of a low-pressure system compression section of the multi-shaft multi-stage combined type compressor.
【図５】同多軸多段コンバインド型コンプレッサのリー
クガスの回収配管図である。FIG. 5 is a piping diagram for collecting leak gas of the multi-shaft multi-stage combined type compressor.
【図６】本発明の第２の実施の形態の多軸多段コンバイ
ンド型コンプレッサの駆動ホイール周部の概略側面図で
ある。FIG. 6 is a schematic side view of a drive wheel periphery of a multi-shaft, multi-stage combined type compressor according to a second embodiment of the present invention.
【図７】同多軸多段型コンプレッサのリークガスの回収
配管図である。FIG. 7 is a piping diagram for collecting leak gas of the multi-shaft multi-stage compressor.
【図８】従来の多軸多段型コンプレッサの斜視図であ
る。FIG. 8 is a perspective view of a conventional multi-shaft, multi-stage compressor.
【図９】同多軸多段型コンプレッサのシール構造を示す
縦断面図である。FIG. 9 is a longitudinal sectional view showing a seal structure of the multi-shaft multi-stage compressor.
１，４１ コンプレッサ ８，４２ 駆動ホイール １０〜１２ ピニオン軸 １４〜１６ ピニオン １７ａ〜２２ａ 羽根車 ３１ａ〜３１ｃ，３６ａ，３６ｂ ラビリンスシール 1,41 Compressor 8,42 Drive wheel 10-12 Pinion shaft 14-16 Pinion 17a-22a Impeller 31a-31c, 36a, 36b Labyrinth seal
Claims (2)
駆動ホイールに噛合するピニオンと、羽根車と上記ピニ
オンを支持するピニオン軸と、羽根車を覆う渦巻室とを
備え、羽根車によってガスを圧縮するコンプレッサにお
いて、上記ピニオン及び渦巻室で覆われている羽根車を
持つピニオン軸を、上記コンプレッサに新たに設けて成
り、このピニオン軸の羽根車の回転により、上記コンプ
レッサの既設の圧縮系とは独立した圧縮系で、ガスの圧
縮ができるようにしたことを特徴とする多軸多段コンバ
インド型コンプレッサ。A drive wheel mounted on a drive shaft, a pinion that meshes with the drive wheel, a pinion shaft that supports the impeller and the pinion, and a spiral chamber that covers the impeller, wherein gas is supplied by the impeller. In the compressor for compression, a pinion shaft having an impeller covered with the pinion and the volute is newly provided in the compressor, and the rotation of the impeller of the pinion shaft allows the compressor to be connected to the existing compression system of the compressor. Is a multi-shaft, multi-stage combined type compressor that is an independent compression system that can compress gas.
数段設け、これらのラビリンスシールの間にリークガス
を収容するガス回収室を設け、このガス回収室と、上記
コンプレッサの圧縮系または新たな圧縮系の入り口とを
連通し、上記ラビリンスシールからのリークガスを回収
できるようにしてなる請求項１に記載の多軸多段コンバ
インド型コンプレッサ。2. A plurality of labyrinth seals are provided on the pinion shaft, and a gas recovery chamber for storing leak gas is provided between the labyrinth seals. The gas recovery chamber and a compression system of the compressor or a new compression system are provided. 2. The multi-shaft, multi-stage combined type compressor according to claim 1, wherein the compressor communicates with an inlet to collect leak gas from the labyrinth seal.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP26949296A JP3572154B2 (en) | 1996-10-11 | 1996-10-11 | Multi-shaft, multi-stage combined type compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP26949296A JP3572154B2 (en) | 1996-10-11 | 1996-10-11 | Multi-shaft, multi-stage combined type compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH10115298A true JPH10115298A (en) | 1998-05-06 |
| JP3572154B2 JP3572154B2 (en) | 2004-09-29 |
Family
ID=17473197
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP26949296A Expired - Fee Related JP3572154B2 (en) | 1996-10-11 | 1996-10-11 | Multi-shaft, multi-stage combined type compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3572154B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2016078199A1 (en) * | 2014-11-22 | 2016-05-26 | 太原理工大学 | Transmission apparatus for contra-rotating impeller ventilation |
| KR20170086610A (en) * | 2014-11-21 | 2017-07-26 | 보이트 파텐트 게엠베하 | Transmission and transmission turbomachine |
| US11326588B2 (en) | 2018-08-08 | 2022-05-10 | Seiko Epson Corporation | Diaphragm-type compressor, projector, cooler, and method for compressing fluid |
-
1996
- 1996-10-11 JP JP26949296A patent/JP3572154B2/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20170086610A (en) * | 2014-11-21 | 2017-07-26 | 보이트 파텐트 게엠베하 | Transmission and transmission turbomachine |
| WO2016078199A1 (en) * | 2014-11-22 | 2016-05-26 | 太原理工大学 | Transmission apparatus for contra-rotating impeller ventilation |
| US11326588B2 (en) | 2018-08-08 | 2022-05-10 | Seiko Epson Corporation | Diaphragm-type compressor, projector, cooler, and method for compressing fluid |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3572154B2 (en) | 2004-09-29 |
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