JPH0520597B2 - - Google Patents

Info

Publication number
JPH0520597B2
JPH0520597B2 JP59153906A JP15390684A JPH0520597B2 JP H0520597 B2 JPH0520597 B2 JP H0520597B2 JP 59153906 A JP59153906 A JP 59153906A JP 15390684 A JP15390684 A JP 15390684A JP H0520597 B2 JPH0520597 B2 JP H0520597B2
Authority
JP
Japan
Prior art keywords
diffuser
flow path
annular plate
centrifugal compressor
wall portion
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 - Lifetime
Application number
JP59153906A
Other languages
Japanese (ja)
Other versions
JPS6067797A (en
Inventor
Oo Jakobi Herumasu
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dresser Industries Inc
Original Assignee
Dresser Industries Inc
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Dresser Industries Inc filed Critical Dresser Industries Inc
Publication of JPS6067797A publication Critical patent/JPS6067797A/en
Publication of JPH0520597B2 publication Critical patent/JPH0520597B2/ja
Granted legal-status Critical Current

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
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
    • F01D17/143—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path the shiftable member being a wall, or part thereof of a radial diffuser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers 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

DIFFUSER CONSTRUCTION FOR A CENTRIFUGAL COMPRESSOR Constant flow width through the last stage diffuser of a centrifugal compressor is maintained against widening by the forces of differential pressure via a diffuser defined between oppositely positioned radial faces of a diaphragm and an annular diffuser plate secured spaced from the diaphragm at the desired with. Enabling the diffuser plate to withstand width deflection and/or enlargement is a pressure balance imposed against the rear surface of the plate as compared to the pressure level incurred from the gas flow at the front surface facing the diaphragm. This is achieved by a sealed radial cavity exposed to the rear surface of the plate and in continuous pressure communication with the front surface through a plurality of vent holes extending therebetween.

Description

【発明の詳細な説明】 産業上の利用分野 本発明はターボ機械及びその構造に関する。[Detailed description of the invention] Industrial applications The present invention relates to a turbomachine and its structure.

従来の技術 多段遠心圧縮機は特定のガスの高圧高容積出力
を必要とする場合に広く使用される。大部分のこ
の種圧縮機は注文寸法であり、注文主の仕様書に
適合するように製作する。各部材の公差寸法は狭
い範囲として、機管の所要の設計性能を得る。こ
のような圧縮機はデイフユーザを形成する複数の
部品から構成されている。これら部品は、その端
部同士を接合して配置され、圧縮機を構成する。BACKGROUND OF THE INVENTION Multi-stage centrifugal compressors are widely used where high pressure and high volume output of a particular gas is required. Most compressors of this type are custom-sized and manufactured to meet the customer's specifications. The tolerance dimensions of each member are set within a narrow range to obtain the required design performance of the machine pipe. Such a compressor is composed of a plurality of parts forming a diffuser. These parts are arranged with their ends joined together to form a compressor.

製作精度は高いが、問題点としては、圧縮機の
比較的小さなデイフユーザ巾に関して生じ、例え
ばバレル型直流圧縮機又は背中合せ型圧縮機の最
終段に生ずる。特に、この種の圧縮機では、多数
の部品の全長が、最後のデイフユーザ段の少なく
とも一方の壁が高作動圧力に基づく応力のためわ
ずかに移動することにより変化し、巾が設計許容
値より大きくなる。デイフユーザ流路巾の増加の
例として、圧縮機のケーシング直径60in（150cm）、
差圧30psig（207KPa）の場合0.03in（0.76mm）とな
る。他の例としてケーシング直径24in（60cm）差
圧300psig（2070KPa）の時に約0.04in（1.02mm）程
度となる。 Although the manufacturing accuracy is high, problems arise with the relatively small diffuser width of the compressor, for example in the last stage of a barrel type DC compressor or a back-to-back type compressor. In particular, in this type of compressor, the overall length of a number of parts changes due to the slight movement of at least one wall of the last diffuser stage due to stresses due to high working pressures, and the width is larger than the design tolerance. Become. As an example of increasing the diffuser flow path width, a compressor casing diameter of 60in (150cm),
If the differential pressure is 30psig (207KPa), it will be 0.03in (0.76mm). Another example is approximately 0.04 inches (1.02 mm) when the casing diameter is 24 inches (60 cm) and the differential pressure is 300 psig (2070 KPa).

デイフユーザの巾の変化は、その段の圧縮機の
性能を変化させるため望ましくない。問題点とし
ては知られているが解決方法は提示されていな
い。 Changes in the width of the diff user are undesirable because they change the performance of the compressor in that stage. This is a known problem, but no solution has been proposed.

発明の解決すべき問題点 本発明は遠心圧縮機特に遠心圧縮機の構造を示
し、作動条件でほぼ一定のデイフユーザ巾を保
ち、既知の圧縮機では制御不能の巾の増加を生じ
た部分である。Problems to be Solved by the Invention The present invention shows a structure of a centrifugal compressor, particularly a centrifugal compressor, which maintains a substantially constant diffuser width under operating conditions, and which exhibits an uncontrollable increase in width in known compressors. .

問題点を解決するための手段 本発明による遠心圧縮機は、各インペラの半径
方向外側に位置するデイフユーザを具備し、該デ
イフユーザが、その間に流路を形成する対向して
間隔があけられた独立の第１壁部分と第２壁部分
の間のセクシヨンに形成されたものにおいて、環
状の凹部を、デイフユーザの第１壁部分に該第１
壁部分によつて形成された流路に隣接して設置
し、環状の板を、該環状の凹部に移動可能に配置
し、該環状の板はデイフユーザの流路の一部を形
成する前面を有し、該環状の板の後面は環状の凹
部内に位置し、間隔をあけて配置した複数の通気
孔が、環状の板の前面から後面に貫通して延び、
それにより環状の凹部内の圧力が流路の圧力とほ
ぼ等しくなり、また複数の間隔保持部材を、環状
の板の前面と第２壁部分とに係合した状態で流路
内に設置し、さらに締結手段が該流路を横切つて
環状の板と間隔保持部材を第２壁部分に連結し、
これにより環状の板が第２壁部分に対して固定関
係に保つて流路の巾を規制し、環状の板、間隔保
持部材及び締結手段が第１壁部分に対して移動し
得る点に特徴があり、このために、第１壁部分の
表面は、デイフユーザの流路巾を変化させること
なく、高圧力によつて動くこと可能となる。Means for Solving the Problems A centrifugal compressor in accordance with the present invention includes a diff user located radially outwardly of each impeller, the diff user forming a channel between two oppositely spaced independent diff users forming a flow path therebetween. an annular recess formed in a section between a first wall portion and a second wall portion of the diff user;
an annular plate is disposed adjacent to the flow path formed by the wall portion, and an annular plate is movably disposed in the annular recess, the annular plate having a front surface forming part of the flow path of the diffuser. a rear surface of the annular plate is located within an annular recess, and a plurality of spaced-apart ventilation holes extend through the annular plate from the front surface to the rear surface;
As a result, the pressure in the annular recess becomes approximately equal to the pressure in the flow path, and the plurality of spacing members are installed in the flow path in a state in which they are engaged with the front surface of the annular plate and the second wall portion, further a fastening means connects the annular plate and the spacing member to the second wall portion across the flow path;
This feature is characterized in that the annular plate is maintained in a fixed relationship with the second wall portion to regulate the width of the flow path, and the annular plate, spacing member, and fastening means are movable relative to the first wall portion. This allows the surface of the first wall portion to be moved by high pressure without changing the flow path width of the diffuser.

作 用 本発明による遠心圧縮機は作動条件下でほぼ一
定のデイフユーザ巾を保ち、デイフユーザ巾の増
加は生じない。Operation The centrifugal compressor according to the present invention maintains a substantially constant diffuser width under operating conditions, and no increase in the diffuser width occurs.

本発明遠心圧縮機の構造は比較的簡単であり、
現在までの問題を経済的に解決することが可能と
なつた。 The structure of the centrifugal compressor of the present invention is relatively simple,
It has become possible to economically solve the problems of the past.

実施例 本発明を例示とした実施例並びに図面について
説明する。Embodiments Examples and drawings illustrating the present invention will be described.

第１図は本発明による直流型多段遠心圧縮機を
示し、ハウジング１０の形成する流路は入口１２
から複数の段１４を経て出口１６に連通する。段
１４には回転軸２０に固着した軸線方向に離間し
た複数のインペラ１８を有する。段は一連の流体
連通として形成し、各インペラは外周部に高速ガ
スを排出する。ガスに伝達されたエネルギーはデ
イフユーザセクシヨン２２で流速が低下して圧力
上昇をインペラの下流側で生ずる。デイフユーザ
から固定のガイドベーン２４が流れを偏向させて
次のインペラ１８の次の段に所定方向で流入させ
る。 FIG. 1 shows a direct current type multi-stage centrifugal compressor according to the present invention, in which the flow path formed by the housing 10 is connected to the inlet 12.
The outlet 16 communicates with the outlet 16 through a plurality of stages 14 . Stage 14 has a plurality of axially spaced impellers 18 secured to rotating shaft 20 . The stages are formed as a series of fluid connections, with each impeller discharging high velocity gas around its outer periphery. The energy transferred to the gas is reduced in flow velocity in the diffuser section 22, creating a pressure increase downstream of the impeller. From the diff user, fixed guide vanes 24 deflect the flow into the next stage of the next impeller 18 in a predetermined direction.

各インペラ段の間の固定のダイアフラム２６，
２８，３０，３２はインペラ間に使用する固定素
子例えばデイフユーザ面、ガイドベーン、戻りの
曲り部、ラビリンス等の支持となる。次のベーン
に入る流路内の各ダイアフラムに組合せて、ダイ
アフラムの面とバルブセクシヨン３４との間に所
定巾の流路間〓を形成する。図示の通り、インペ
ラの共通円周距離に接した下流部のデイフユーザ
巾はダイアフラム２６の第１の比較的低圧段から
ダイアフラム３２の最終の比較的高圧段まで順次
減少する。説明上、ダイアフラム３２の所定設計
巾を寸法Ｘとし、この寸法をほぼ一定に保つため
に本発明による構造３５とする。 a fixed diaphragm 26 between each impeller stage;
Reference numerals 28, 30, and 32 support fixed elements used between the impellers, such as a diffuser surface, a guide vane, a return bend, a labyrinth, and the like. In combination with each diaphragm in the flow path entering the next vane, a flow path gap of a predetermined width is formed between the face of the diaphragm and the valve section 34. As shown, the downstream diffuser width tangential to the common circumferential distance of the impeller decreases sequentially from the first relatively low pressure stage of diaphragm 26 to the final relatively high pressure stage of diaphragm 32. For purposes of illustration, the predetermined design width of the diaphragm 32 will be dimension X, and the structure 35 according to the invention will be used to keep this dimension substantially constant.

第２図は背中合せ型圧縮機であり、ハウジング
３６は第１のセクシヨンの吸込口３８、第１セク
シヨン出口４０、第２セクシヨン入口４２、第２
セクシヨン出口４４を有し、両セクシヨンは隔壁
４６によつて分離する。第１図の構造と同様に、
各セクシヨンには複数の順次の段１４を有し、各
段には軸２０に固着した互に離間したインペラ１
８を有する。各段間を流体連通させ、各段のイン
ペラは高速ガスを外周部に排出する。各セクシヨ
ンのインペラ段の間に固定のダイアフラムを有
し、第１セクシヨンのダイアフラム２６′，２
８′，３０′，３２′，４８′と第２セクシヨンのダ
イアフラム２６″，２８″，３０″，３２″，５０″
とによつて夫々のデイフユーザ２２の巾を保つ。
隔壁４６とダイアフラム５０″間のデイフユーザ
を形成する本発明の構造３５は後述する。 FIG. 2 shows a back-to-back compressor in which the housing 36 includes a first section inlet 38, a first section outlet 40, a second section inlet 42, and a second section inlet 42.
It has a section outlet 44 and both sections are separated by a septum 46. Similar to the structure in Figure 1,
Each section has a plurality of sequential stages 14, each stage having spaced apart impellers 1 fixed to a shaft 20.
It has 8. Fluid communication is provided between each stage, and the impeller of each stage discharges high-velocity gas to the outer periphery. Each section has a fixed diaphragm between the impeller stages, and the first section's diaphragms 26', 2
8', 30', 32', 48' and second section diaphragm 26'', 28'', 30'', 32'', 50''
The width of each differential user 22 is maintained depending on the width of each differential user 22.
The structure 35 of the present invention forming the diffuser between the bulkhead 46 and the diaphragm 50'' will be described below.

第３，４図は本発明によつて第１，２図の圧縮
機の最終段のデイフユーザ２２の一定巾Ｘを保つ
装置を示し、環状の板であるデイフユーザ板５４
を、デイフユーザの流路を構成する一方の第１壁
部分であるダイヤフラム壁３２又は隔壁４６に形
成した所定寸法の環状の凹部５６内に係合させ
る。この反対側はデイフユーザの流路を構成する
他方の第２壁部分であるベーン壁３３、ダイヤフ
ラム５０とする。デイフユーザ板５４を複数の円
周方向に離間した締結手段であるボルト５８によ
つて間隔保持部材であるスリーブブツシユ６０を
介して正確な位置に固着する。スリーブブツシユ
６０の寸法はデイフユーザの保つべき寸法Ｘに相
当する。Ｏリングのシール６２は圧力シールを保
つ。 3 and 4 show a device for maintaining a constant width X of the final stage diffuser 22 of the compressor shown in FIGS. 1 and 2 according to the present invention.
is engaged in an annular recess 56 of a predetermined size formed in the diaphragm wall 32 or the partition wall 46, which is one of the first wall portions constituting the flow path of the diffuser. On the opposite side are a vane wall 33 and a diaphragm 50, which are the other second wall portions constituting the flow path of the diffuser. The diffuser plate 54 is fixed in a precise position by a plurality of bolts 58, which are fastening means, spaced apart in the circumferential direction, and through sleeve bushings 60, which are spacing members. The dimensions of the sleeve bushing 60 correspond to the dimension X that should be maintained by the differential user. O-ring seal 62 maintains a pressure seal.

デイフユーザ板５４を有効とするためには、後
面に環状の半径方向の凹み６４を設けて環状の凹
部５６との間に環状溝として環状スペース６５を
形成する。複数の軸線方向の通気孔６６は均圧の
ための半径方向位置とし、デイフユーザ２２内圧
力P1がスペース６５内に常時作用し、スペース
６５内の圧力値P2はデイフユーザ２２内の圧力
P1に同じ又はほぼ近い値となる。この構成によ
つて、デイフユーザ板の前後面間の圧力釣合が保
たれ、既知の構成のデイフユーザ巾を大にする。
高圧力による圧縮機部品の移動作用は生じない。 In order to make the diffuser plate 54 effective, an annular radial recess 64 is provided on the rear surface and an annular space 65 is formed between it and the annular recess 56 as an annular groove. The plurality of axial ventilation holes 66 are positioned in the radial direction for pressure equalization, so that the pressure P 1 inside the differential user 22 always acts in the space 65, and the pressure value P 2 in the space 65 corresponds to the pressure inside the differential user 22.
The value is the same as or almost close to P 1 . This configuration maintains pressure balance between the front and rear surfaces of the diffuser plate and increases the width of the diffuser of known configurations.
There is no movement effect of compressor parts due to high pressure.

第３図の点線はデイフユーザ通路に高圧力が作
用した時の隔壁４６の位置を誇張して示してい
る。隔壁４６は移動するが、デイフユーザ板５４
はその位置に止まり、流路巾Ｘを一定に保持する
点に留意しなければならない。 The dotted line in FIG. 3 exaggerates the position of the partition wall 46 when high pressure is applied to the diffuser passage. Although the bulkhead 46 moves, the diffuser plate 54
It must be noted that the flow path remains at that position and the flow path width X is kept constant.

発明の効果 上述によつて明らかにされた通り、本発明の多
段遠心圧縮機は、デイフユーザの流路を形成する
一方の第１壁部分に環状の凹部を形成して、該環
状の凹部に環状の板を移動可能に配置し、該環状
の板の前面はデイフユーザの流路の一部を形成
し、また後面は環状の凹部内に位置し、間隔をあ
けて配置した複数の通気孔を環状の板の前面から
後面に貫通するように形成して、凹部内の圧力を
流路の圧力とほぼ等しくし、また複数の間隔保持
部材を、環状の板の前面とデイフユーザの流路を
形成する他方の第２壁部分とに係合した状態で流
路内に設置し、流路を横切る締結手段により環状
の板と間隔保持部材を第２壁部分に連結し、これ
により、環状の板が前記第２壁部分に対し固定関
係が保たれて、デイフユーザの流路の巾を規制す
る一方、環状の板、間隔保持部材及び前記締結手
段が第１壁部分に対して移動し得るようにしてあ
るので、第１壁部分が高圧力により移動するよう
な場合であつても、環状の板はその位置に止ま
り、デイフユーザの流路巾を一定にし、既知の圧
縮機のデイフユーザが巾寸法が大となる作動条件
でも一定である。デイフユーザ巾を一定とするこ
とによつて、その段の性能は設計値に合致する値
となり、既知のデイフユーザ巾増大による性能低
下は生じない。同時に、本発明の構造は製造が比
較的簡単、経済的であり、圧縮機性能は向上す
る。Effects of the Invention As clarified above, in the multistage centrifugal compressor of the present invention, an annular recess is formed in one first wall portion forming a flow path of a diffuser, and an annular recess is formed in the annular recess. movably arranged, the front surface of the annular plate forms a part of the flow path of the diffuser, and the rear surface is located within the annular recess and has a plurality of spaced apart ventilation holes formed in the annular shape. A plurality of spacing members are formed to penetrate from the front surface to the rear surface of the annular plate to make the pressure in the recess approximately equal to the pressure in the flow path, and a plurality of spacing members are formed to form a flow path in the diffuser with the front surface of the annular plate. The annular plate and the spacing member are installed in the flow path while being engaged with the other second wall portion, and the annular plate and the spacing member are connected to the second wall portion by means of fastening means that cross the flow path. The annular plate, the spacing member and the fastening means are movable relative to the first wall portion while being maintained in a fixed relationship to the second wall portion to limit the width of the flow path of the diff user. Therefore, even if the first wall portion moves due to high pressure, the annular plate remains in that position, keeping the width of the flow path of the diff user constant, and the diff user of known compressors has a large width. It remains constant even under the operating conditions. By keeping the differential width constant, the performance of that stage will match the design value, and no performance degradation will occur due to the known increase in the differential width. At the same time, the structure of the present invention is relatively simple and economical to manufacture, and compressor performance is improved.

本発明は各種の変型が可能であり、実施例並び
に図面は例示であつて発明を限定するものではな
い。 The present invention can be modified in various ways, and the embodiments and drawings are illustrative and do not limit the invention.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図は本発明による直流型遠心圧縮機の断面
図、第２図は背中合せ型遠心圧縮機の断面図、第
３図は第１，２図の囲つた部分３の拡大断面図、
第４図は第３図の４−４線に沿う部分図である。 １０……ハウジング、１２，３８，４２……入
口、１４……段、１６，４０，４４……出口、１
８……インペラ、２０……回転軸、２２……デイ
フユーザ、２４……ガイドベーン、２６，２８，
３０，３２……ダイアフラム、５４……デイフユ
ーザ板、６５……環状スペース、６６……均圧
孔。 FIG. 1 is a sectional view of a DC centrifugal compressor according to the present invention, FIG. 2 is a sectional view of a back-to-back centrifugal compressor, and FIG. 3 is an enlarged sectional view of the enclosed portion 3 of FIGS.
FIG. 4 is a partial view taken along line 4--4 in FIG. 10... Housing, 12, 38, 42... Inlet, 14... Stage, 16, 40, 44... Outlet, 1
8... Impeller, 20... Rotating shaft, 22... Differential user, 24... Guide vane, 26, 28,
30, 32... diaphragm, 54... diffuser plate, 65... annular space, 66... pressure equalization hole.

Claims (1)

【特許請求の範囲】 １ 各インペラの半径方向外側に位置するデイフ
ユーザを具備し、該デイフユーザが、その間に流
路を形成する対向して間隔があけられた独立の第
１壁部分と第２壁部分の間のセクシヨンに形成さ
れた、多段遠心圧縮機において、 環状の凹部が、前記デイフユーザの第１壁部分
に、該第１壁部分によつて形成された流路に隣接
して設置してあり、 環状の板が、前記凹部に移動可能に配置され、
該環状の板は、デイフユーザの流路の一部を形成
する前面を有し、該環状の板の後面は前記凹部内
に位置し、間隔をあけて配置された複数の通気孔
が前記環状の板の前面から後面に貫通して延び、
それにより前記凹部内の圧力が前記流路の圧力と
ほぼ等しくなり、 複数の間隔保持部材が、前記環状の板の前面と
前記デイフユーザの第２壁部分とに係合した状態
で前記流路内に設置してあり、 締結手段が、前記流路を横切つて、前記環状の
板と間隔保持部材を前記デイフユーザの第２壁部
分に連結し、これにより前記環状の板が前記第２
壁部分に対し固定関係を保つて前記流路の巾を規
制し、前記環状の板、間隔保持部材及び前記締結
手段が、前記第１壁部分に対して移動し得る ことを特徴とする、多段遠心圧縮機。 ２ 請求項１記載の多段遠心圧縮機において、前
記間隔保持部材は、前記環状の板の前面と係合し
て前記デイフユーザ流路に配置された複数の円周
方向に間隔をあけた部材からなり、その設計巾を
確保することを特徴とする多段遠心圧縮機。 ３ 請求項２記載の多段遠心圧縮機において、前
記締結手段は複数のボルトからなり、前記各間隔
保持部材は前記ボルトの一つが貫通して延びるス
リーブブツシユからなることを特徴とする多段遠
心圧縮機。 ４ 請求項３記載の多段遠心圧縮機において、前
記環状の板は、その後面に、前記デイフユーザの
第１壁部分に隣接して環状溝を有し、前記通気孔
は、該環状溝内に延びていることを特徴とする多
段遠心圧縮機。[Scope of Claims] 1. A diff user located radially outwardly of each impeller, the diff user comprising a first wall portion and a second wall that are opposed and spaced apart and forming a flow path therebetween. In a multi-stage centrifugal compressor formed in a section between sections, an annular recess is located in a first wall section of the diffuser adjacent to a flow path formed by the first wall section. an annular plate is movably arranged in the recess;
The annular plate has a front surface forming part of the diffuser flow path, the rear surface of the annular plate is located within the recess, and a plurality of spaced vent holes are provided in the annular plate. Extends through the board from the front to the back,
As a result, the pressure in the recess becomes approximately equal to the pressure in the flow path, and the plurality of spacing members are engaged with the front surface of the annular plate and the second wall portion of the diffuser, and the spacer is in the flow path. and a fastening means connects the annular plate and the spacing member to a second wall portion of the diff user across the flow path, whereby the annular plate connects to the second wall portion of the diff user.
A multi-stage structure, characterized in that the width of the flow path is regulated by maintaining a fixed relationship with the wall portion, and the annular plate, the spacing member and the fastening means are movable with respect to the first wall portion. Centrifugal compressor. 2. The multistage centrifugal compressor according to claim 1, wherein the spacing member includes a plurality of circumferentially spaced members that engage with the front surface of the annular plate and are disposed in the diffuser flow path. , a multi-stage centrifugal compressor characterized by ensuring its design width. 3. The multi-stage centrifugal compressor according to claim 2, wherein the fastening means comprises a plurality of bolts, and each of the spacing members comprises a sleeve bush through which one of the bolts extends. Machine. 4. The multistage centrifugal compressor according to claim 3, wherein the annular plate has an annular groove on its rear surface adjacent to the first wall portion of the diffuser, and the vent hole extends into the annular groove. A multi-stage centrifugal compressor characterized by:
JP59153906A 1983-09-22 1984-07-24 Diffuser structure of centrifugal compressor Granted JPS6067797A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US53488183A 1983-09-22 1983-09-22
US534881 1983-09-22

Publications (2)

Publication Number Publication Date
JPS6067797A JPS6067797A (en) 1985-04-18
JPH0520597B2 true JPH0520597B2 (en) 1993-03-19

Family

ID=24131906

Family Applications (1)

Application Number Title Priority Date Filing Date
JP59153906A Granted JPS6067797A (en) 1983-09-22 1984-07-24 Diffuser structure of centrifugal compressor

Country Status (5)

Country Link
JP (1) JPS6067797A (en)
CA (1) CA1252075A (en)
DE (1) DE3430307A1 (en)
FR (1) FR2552501B1 (en)
IT (1) IT1179392B (en)

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EP3361101A1 (en) 2017-02-10 2018-08-15 Siemens Aktiengesellschaft Return channel of a multistage compressor or expander with twisted vanes
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997033092A1 (en) * 1996-03-06 1997-09-12 Hitachi, Ltd. Centrifugal compressor and diffuser for the centrifugal compressor

Also Published As

Publication number Publication date
FR2552501B1 (en) 1989-11-24
FR2552501A1 (en) 1985-03-29
IT1179392B (en) 1987-09-16
CA1252075A (en) 1989-04-04
IT8448532A0 (en) 1984-07-09
DE3430307A1 (en) 1985-04-04
JPS6067797A (en) 1985-04-18

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