JP2013060882A - Turbo compressor - Google Patents

Turbo compressor Download PDF

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Publication number
JP2013060882A
JP2013060882A JP2011199770A JP2011199770A JP2013060882A JP 2013060882 A JP2013060882 A JP 2013060882A JP 2011199770 A JP2011199770 A JP 2011199770A JP 2011199770 A JP2011199770 A JP 2011199770A JP 2013060882 A JP2013060882 A JP 2013060882A
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Prior art keywords
stage
compressor
lubricating oil
stage compressor
gear
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JP2011199770A
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JP5616866B2 (en
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Toru Yoshioka
徹 吉岡
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Kobe Steel Ltd
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Kobe Steel Ltd
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Priority to JP2011199770A priority Critical patent/JP5616866B2/en
Priority to KR1020120100993A priority patent/KR20130029022A/en
Priority to CN201210335844.2A priority patent/CN102996471B/en
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    • 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
    • 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
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/028—Units comprising pumps and their driving means the driving means being a planetary gear
    • 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
    • F04D29/002—Details, component parts, or accessories especially adapted for elastic fluid pumps
    • 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
    • F04D29/403—Casings; Connections of working fluid especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/06—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with parallel axes
    • 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
    • F05D2210/00—Working fluids
    • F05D2210/10—Kind or type
    • F05D2210/12—Kind or type gaseous, i.e. compressible
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Abstract

PROBLEM TO BE SOLVED: To provide a turbo compressor that can reduce an installation space of the compressor without increasing mechanical loss due to the rebounding of lubricant and facilitating the piping work for cooling water.SOLUTION: In the turbo compressor provided with: a first stage compressor 1 and a second stage compressor 2 each driven by a pinion shaft in a gear case 5 having an input shaft 6a and at least one pinion shaft to which the rotation of the input shaft 6a is transmitted through a gear 4; and gas coolers 11, 12 for cooling a gas discharged respectively from the first stage compressor 1 and a second stage compressor 2, a lubricant tank 13 is arranged in the lower part of the gear case 5, the gas coolers 11, 12 are respectively arranged below the first stage compressor 1 and the second stage compressor 2 and in both side surfaces of the lubricant tank 13 and the lubricant tank axis line C3, the gas cooler axis line C1, C2 and the input shaft 6a are arranged in parallel.

Description

本発明は、羽根車の回転軸が、駆動軸から駆動ギヤを介して駆動されるギヤ内蔵型の多段式ターボ圧縮機に関するものである。   The present invention relates to a gear built-in type multi-stage turbo compressor in which a rotating shaft of an impeller is driven from a drive shaft via a drive gear.

先ず、従来例に係る多段式ターボ圧縮機について、以下添付図６〜９を参照しながら説明する。図６は従来技術１に係る遠心圧縮機の平面図、図７は図６のIV−IV矢視図、図８は従来技術２に係るターボ圧縮機の側断面図、図９は従来技術２に係るターボ圧縮機を複数台設置した場合の冷却水配管系統図の一例である。   First, a multistage turbo compressor according to a conventional example will be described below with reference to FIGS. 6 is a plan view of a centrifugal compressor according to prior art 1, FIG. 7 is a sectional view taken along arrows IV-IV in FIG. 6, FIG. 8 is a side sectional view of a turbo compressor according to prior art 2, and FIG. It is an example of the cooling water piping system diagram at the time of installing a plurality of turbo compressors concerning.

従来技術１に係る遠心圧縮機の圧縮機本体４４は、夫々中空構造の圧縮機基部４５と、ギヤボックスハウジング部４６と、第一段スクロール部４７と、第二段スクロール部４８と、モーター取付台４９とを備え、これら各部を鋳造によって一体的に形成した構造を有している。   The compressor main body 44 of the centrifugal compressor according to the prior art 1 includes a compressor base 45 having a hollow structure, a gear box housing part 46, a first stage scroll part 47, a second stage scroll part 48, and a motor attachment. The base 49 is provided, and these parts are integrally formed by casting.

そして、圧縮機基部４５の内部の一端Ａ側寄りの部分には、潤滑油を貯留する潤滑油貯留室５２が形成され、圧縮機基部４５の内部の他端Ｂ側寄りの部分には、熱交換素子（図示せず）を内装するインタークーラー室５０と、他の熱交換素子（図示せず）を内装するアフタークーラー室５１が形成されている。   A lubricating oil storage chamber 52 for storing lubricating oil is formed in a portion near the one end A side inside the compressor base 45, and a portion near the other end B side inside the compressor base 45 is heated. An intercooler chamber 50 that houses an exchange element (not shown) and an aftercooler chamber 51 that houses another heat exchange element (not shown) are formed.

また、圧縮機基部４５の一端Ａ側寄りの端部には、潤滑油貯留室５２の開口部５６，５７を夫々別箇に覆うように開口部カバー５９，６０が取り付けられ、圧縮機基部４５の他端Ｂ側寄りの端部には、インタークーラー室５０、アフタークーラー室５１の開口部５４，５５を一体的に覆うように開口部カバー５８が取り付けられている。   Opening covers 59 and 60 are attached to the end of the compressor base 45 close to one end A so as to cover the openings 56 and 57 of the lubricating oil storage chamber 52 separately. An opening cover 58 is attached to the end of the other end B side so as to integrally cover the openings 54 and 55 of the intercooler chamber 50 and the aftercooler chamber 51.

前記開口部カバー５８には、両クーラー室５０，５１に内装された熱交換素子に対して冷却媒体の授受を行うための管路（図示せず）が設けられており、圧縮機基部４５の外部から各熱交換素子に対して冷却媒体を流通させることによって、当該冷却媒体と両クーラー室５０，５１の内部の気体との間で熱交換を行い、前記気体を冷却するようになっている。また、前記のアフタークーラー室５１には外部へ開口する気体出口（図示せず）が設けられている。   The opening cover 58 is provided with a pipe (not shown) for transferring a cooling medium to and from the heat exchange elements built in the cooler chambers 50 and 51. By circulating a cooling medium from the outside to each heat exchange element, heat is exchanged between the cooling medium and the gas inside the cooler chambers 50 and 51 to cool the gas. . The aftercooler chamber 51 is provided with a gas outlet (not shown) that opens to the outside.

ギヤボックスハウジング部４６は、前記の圧縮機基部４５の上側部に設けられ、内部には入力軸と出力軸とを有する増速ギヤ機構（図示せず）が内装されている。また、ギヤボックスハウジング部４６の上端には、前記増速ギヤ機構を覆うギヤボックスカバー６１が取り付けられる一方、ギヤボックスハウジング部４６の内部には、増速ギヤの設置部分から前記の潤滑油貯留室５２へ延びる潤滑油回収流路７５が形成されている。   The gear box housing portion 46 is provided on the upper portion of the compressor base 45, and a speed increasing gear mechanism (not shown) having an input shaft and an output shaft is housed therein. A gear box cover 61 that covers the speed increasing gear mechanism is attached to the upper end of the gear box housing portion 46, while the lubricating oil is stored in the gear box housing portion 46 from the speed increasing gear installation portion. A lubricating oil recovery flow path 75 extending to the chamber 52 is formed.

更に、第一段スクロール部４７の内部には、スクロール室６２から前記の圧縮機基部４５の内部のインタークーラー室５０の一端Ａ側寄り端部近傍へ延びる第一段吐出流路６６が形成されており、インペラ（図示せず）が回転することにより気体入口６５から第一段スクロール部４７に流入して圧縮される気体は、第一段吐出流路６６を経てインタークーラー室５０に流入するようになっている。   Further, a first-stage discharge passage 66 extending from the scroll chamber 62 to the vicinity of the end portion near the one end A side of the intercooler chamber 50 inside the compressor base 45 is formed inside the first-stage scroll portion 47. The gas compressed by flowing into the first scroll portion 47 from the gas inlet 65 by the rotation of the impeller (not shown) flows into the intercooler chamber 50 through the first discharge channel 66. It has become.

更に、第二段スクロール部４８の内部には、前記の圧縮機基部４５の内部のインタークーラー室５０の他端Ｂ側寄り端部近傍からスクロール室６７へ延びる第二段吸入流路７０と、スクロール室６７から圧縮機基部４５内部のアフタークーラー室５１の他端Ｂ側より端部近傍へ延びる第二段吐出流路７１とが形成されており、インペラが回転することにより第二段吸入流路７０から第二段スクロール部４８に流入して圧縮される気体は、第二段吐出流路７１を経てアフタークーラー室５１に流入するようになっている（例えば、特許文献１参照）。   Further, in the second stage scroll portion 48, a second stage suction passage 70 extending from the vicinity of the other end B side end portion of the intercooler chamber 50 inside the compressor base 45 to the scroll chamber 67, and the scroll A second-stage discharge flow channel 71 extending from the other end B side of the aftercooler chamber 51 inside the compressor base 45 to the vicinity of the end portion is formed from the chamber 67, and the second-stage intake flow channel is formed by rotating the impeller. The gas that flows into the second-stage scroll portion 48 from 70 and is compressed flows into the aftercooler chamber 51 through the second-stage discharge passage 71 (see, for example, Patent Document 1).

しかしながら、この従来技術１に係る遠心圧縮機は、圧縮機本体４４とインタークーラー室５０及びアフタークーラー室５１、並びに圧縮機本体４４と前記クーラー室５０，５１を接続する配管（図示せず）の一部が一体構造となり、増速ギヤを収納するギアボックスハウジング部６１の底部に底板６１ａが形成されているため、このギアボックスハウジング部６１内に噴射された潤滑油が、前記底板６１ａに当って跳ね返り、増速ギヤに衝突して機械損失を増大させる。その結果、遠心圧縮機の性能低下を招くことになる。   However, the centrifugal compressor according to the prior art 1 is a compressor main body 44, an intercooler chamber 50 and an after cooler chamber 51, and a pipe (not shown) connecting the compressor main body 44 and the cooler chambers 50, 51. Since the bottom part 61a is formed at the bottom of the gear box housing part 61 that houses the speed increasing gear, the lubricating oil injected into the gear box housing part 61 hits the bottom board 61a. Bounces and collides with the speed increasing gear, increasing the mechanical loss. As a result, the performance of the centrifugal compressor is reduced.

一方、従来技術２は、増速ギヤ（図示せず）を収納するギヤケース８１、第１段圧縮機８５及び第２段圧縮機８６からなる圧縮機本体と、第１ガス冷却部８２及び第２ガス冷却部８３、並びに前記圧縮機本体と、第１ガス冷却部８２及び第２ガス冷却部８３を接続する配管の一部（例えば、１段圧縮空気流通路８８や２段圧縮空気流通路８９）を一体構造としたところは、上記従来技術１と同一であるが、図８に示す如く、ギヤケース８１の底板をなくして、潤滑油タンク８７に直接潤滑油が回収される構造になっている（特許文献２参照）。従って、従来技術１の如く、潤滑油が前記底板６１ａに当って跳ね返り機械損失を増大させて、遠心圧縮機の性能低下を招くことはない。   On the other hand, in the related art 2, a compressor body including a gear case 81 that houses a speed increasing gear (not shown), a first stage compressor 85, and a second stage compressor 86, a first gas cooling unit 82, and a second stage. The gas cooling unit 83 and a part of the pipe connecting the compressor main body to the first gas cooling unit 82 and the second gas cooling unit 83 (for example, the first-stage compressed air flow path 88 and the second-stage compressed air flow path 89 ) Is the same as the prior art 1, but as shown in FIG. 8, the bottom plate of the gear case 81 is eliminated, and the lubricating oil is directly collected in the lubricating oil tank 87. (See Patent Document 2). Therefore, unlike the prior art 1, the lubricating oil hits the bottom plate 61a and rebounds, increasing the mechanical loss and causing no deterioration in the performance of the centrifugal compressor.

しかしながら、この様な従来技術２に係るターボ圧縮機は、従来技術１に係る遠心圧縮機と同様、第１ガス冷却部８２及び第２ガス冷却部８３（従来技術１においては、インタークーラー室５０及びアフタークーラー室５１）の軸線方向（第１ガス冷却部８２及び第２ガス冷却部８３の長手方向）が、圧縮機のピニオン軸８４と平行に配置された駆動軸（図示せず）と直交する方向に配置されている。また、前記駆動軸を駆動する駆動モータは、当然駆動軸と同軸方向に取り付けられるため、この様な圧縮機の外形寸法は駆動軸と平行な方向に比較的長く、この駆動軸と直交する方向に短いものとなる。尚、第１ガス冷却部８２及び第２ガス冷却部８３の冷却水の給水取合口及び排水取合口は、それら第１ガス冷却部８２及び第２ガス冷却部８３の軸線方向の端部に配置される。   However, the turbo compressor according to the prior art 2 is similar to the centrifugal compressor according to the prior art 1, the first gas cooling unit 82 and the second gas cooling unit 83 (in the prior art 1, the intercooler chamber 50 and The axial direction of the aftercooler chamber 51) (longitudinal direction of the first gas cooling unit 82 and the second gas cooling unit 83) is orthogonal to a drive shaft (not shown) arranged in parallel with the pinion shaft 84 of the compressor. Arranged in the direction. Also, since the drive motor for driving the drive shaft is naturally mounted in the same direction as the drive shaft, the external dimension of such a compressor is relatively long in the direction parallel to the drive shaft, and the direction perpendicular to the drive shaft. It will be short. In addition, the water supply joint and the drain joint for the cooling water of the first gas cooling section 82 and the second gas cooling section 83 are arranged at the end portions in the axial direction of the first gas cooling section 82 and the second gas cooling section 83. Is done.

従来技術２に係るターボ圧縮機を複数台設置する場合、メンテナンスの便宜上、図９に示す如く、各圧縮機の駆動軸が並列する様にその複数台のターボ圧縮機を配置する。その結果、各冷却部８２，８３への給水取合口９１及び排水取合口９２は、各圧縮機の側面（隣り合う圧縮機の面のうち、互いに対向する面）に配置される。   When a plurality of turbo compressors according to the related art 2 are installed, the plurality of turbo compressors are arranged so that the drive shafts of the compressors are arranged in parallel as shown in FIG. 9 for convenience of maintenance. As a result, the water supply inlet 91 and the drainage outlet 92 to each cooling part 82 and 83 are arrange | positioned at the side surface (surface mutually opposed among the surfaces of an adjacent compressor).

この様に配置した場合、給水取合口９１及び排水取合口９２へ接続される給水配管９１ａ及び排水配管９２ａは、何れも給水主配管９１ｂ及び排水主配管９２ｂに対して屈曲（即ち、給水主配管９１ｂ及び排水主配管９２ｂから略垂直に延びた後、その給水主配管９１ｂ及び排水主配管９２ｂと略平行に延びて各圧縮機に接続する様、略直角方向に屈曲）して配管する必要があり、配管工事が複雑で難しくなる。また、各駆動系のメンテナンスやクーラー本体の抜き取りの作業のための十分なスペースを各圧縮機間に確保する必要があるため、広い設置スペースが必要となる。   When arranged in this manner, the water supply pipe 91a and the drainage pipe 92a connected to the water supply joint 91 and the drainage joint 92 are both bent with respect to the water supply main pipe 91b and the drainage main pipe 92b (that is, the water supply main pipe). After extending substantially vertically from 91b and the drainage main pipe 92b, it is necessary to bend the pipe in a substantially perpendicular direction so as to extend substantially parallel to the water supply main pipe 91b and the drainage main pipe 92b and connect to each compressor. Yes, piping work is complicated and difficult. Moreover, since it is necessary to ensure sufficient space between each compressor for the maintenance of each drive system and the operation | work of extraction of a cooler main body, a wide installation space is needed.

特開平７−１０３１６２号公報JP-A-7-103162 特許第４０４８０７８号公報Japanese Patent No. 4048078

従って、本発明の目的は、潤滑油の跳ね返りによる機械損失を増大させず、圧縮機の設置スペースを小さくすると共に、冷却水の配管工事も容易にできるターボ圧縮機を提供することにある。   Accordingly, it is an object of the present invention to provide a turbo compressor that does not increase mechanical loss due to rebound of lubricating oil, reduces the installation space of the compressor, and facilitates piping work for cooling water.

前記目的を達成するために、本発明の請求項１に係るターボ圧縮機が採用した手段は、入力軸と、この入力軸の回転がギヤを介して伝達される少なくとも１本のピニオン軸とを有するギヤケースの一方の側面に、前記ピニオン軸で駆動される第１段圧縮機が備えられ、かつ他方の側面に前記ピニオン軸で駆動される第２段圧縮機が備えられると共に、これら第１段圧縮機と第２段圧縮機とから吐出されるガスを冷却するガスクーラが夫々備えられたターボ圧縮機において、前記ギヤケースの下部に潤滑油タンクが配設されると共に、前記第１段圧縮機と第２段圧縮機との下方で、かつ前記潤滑油タンクの両側面に前記ガスクーラが夫々配設され、前記潤滑油タンク及び前記夫々のガスクーラの各軸線と前記入力軸が平行に配置されてなることを特徴とするものである。   In order to achieve the above object, means adopted by the turbo compressor according to claim 1 of the present invention includes an input shaft and at least one pinion shaft to which rotation of the input shaft is transmitted via a gear. A first stage compressor driven by the pinion shaft is provided on one side surface of the gear case, and a second stage compressor driven by the pinion shaft is provided on the other side surface. In the turbo compressor provided with gas coolers for cooling the gas discharged from the compressor and the second stage compressor, a lubricating oil tank is disposed below the gear case, and the first stage compressor The gas coolers are disposed below the second stage compressor and on both side surfaces of the lubricating oil tank, and the axes of the lubricating oil tank and the respective gas coolers and the input shaft are disposed in parallel. about It is an feature.

本発明の請求項２に係るターボ圧縮機が採用した手段は、請求項１に記載のターボ圧縮機において、前記潤滑油タンク内に、このタンク内の油溜まり部を上下に画成する中仕切り板が設けられ、前記中仕切り板の端部と前記潤滑油タンクの内壁とによって、前記画成された上下の油溜り部を連通する開孔部が形成されてなることを特徴とするものである。   According to a second aspect of the present invention, there is provided a turbo compressor according to the first aspect of the present invention, wherein the turbo compressor according to the first aspect has a partition that defines an oil reservoir in the tank vertically in the lubricating oil tank. A plate is provided, and an opening is formed by the end of the partition plate and the inner wall of the lubricating oil tank to communicate the defined upper and lower oil reservoirs. is there.

本発明の請求項３に係るターボ圧縮機が採用した手段は、請求項１または２に記載のターボ圧縮機において、前記ガスクーラのハウジングには、このガスクーラの軸線方向に熱交換器を挿通するための貫通穴が形成されてなることを特徴とするものである。   According to a third aspect of the present invention, there is provided the turbo compressor according to the first or second aspect, wherein the heat exchanger is inserted into the housing of the gas cooler in the axial direction of the gas cooler. These through holes are formed.

本発明の請求項１に係るターボ圧縮機によれば、入力軸と、この入力軸の回転がギヤを介して伝達される少なくとも１本のピニオン軸とを有するギヤケースの一方の側面に、前記ピニオン軸で駆動される第１段圧縮機が備えられ、かつ他方の側面に前記ピニオン軸で駆動される第２段圧縮機が備えられると共に、これら第１段圧縮機と第２段圧縮機とから吐出されるガスを冷却するガスクーラが夫々備えられたターボ圧縮機において、前記ギヤケースの下部に潤滑油タンクが配設されると共に、前記第１段圧縮機と第２段圧縮機との下方で、かつ前記潤滑油タンクの両側面に前記ガスクーラが夫々配設され、前記潤滑油タンク及び前記夫々のガスクーラの各軸線と前記入力軸が平行に配置されてなる。   According to the turbo compressor according to claim 1 of the present invention, the pinion is provided on one side surface of a gear case having an input shaft and at least one pinion shaft to which rotation of the input shaft is transmitted via a gear. A first-stage compressor driven by a shaft, and a second-stage compressor driven by the pinion shaft on the other side surface, and from these first-stage compressor and second-stage compressor In each of the turbo compressors each provided with a gas cooler for cooling the discharged gas, a lubricating oil tank is disposed below the gear case, and below the first stage compressor and the second stage compressor, The gas coolers are disposed on both side surfaces of the lubricating oil tank, and the axes of the lubricating oil tank and the respective gas coolers and the input shaft are disposed in parallel.

その結果、ターボ圧縮機の機械損失を増やすことなく、かつ、ガスクーラへの給排水配管を屈曲させずに夫々の主配管に接続できる。そのため、配管工事が簡単で設置スペースも小さくできる上、これら給排水配管が前記圧縮機のメンテナンス上、邪魔になることがない。   As a result, it is possible to connect to each main pipe without increasing the mechanical loss of the turbo compressor and without bending the water supply / drain pipe to the gas cooler. Therefore, the piping work is simple and the installation space can be reduced, and these water supply and drainage pipes do not interfere with the maintenance of the compressor.

本発明の請求項２に係るターボ圧縮機によれば、前記潤滑油タンク内に、このタンク内の油溜まり部を上下に画成する中仕切り板が設けられ、前記中仕切り板の端部と前記潤滑油タンクの内壁とによって、前記画成された上下の油溜り部を連通する開孔部が形成されてなるので、潤滑油タンク内の貯留時間が長くなり、潤滑油中の気泡を消滅させ得る。その結果、前記ギヤや軸受の潤滑及び冷却能力の低下、並びに腐食を防止できる。また、潤滑油の使用量を少なくして、潤滑油タンクの容量も少量化できるので、圧縮機全体の大きさも小型化できるメリットが生じる。   According to the turbo compressor according to claim 2 of the present invention, a partition plate that vertically defines an oil reservoir in the tank is provided in the lubricating oil tank, and an end portion of the partition plate and The inner wall of the lubricating oil tank forms an opening that communicates the defined upper and lower oil reservoirs, so that the storage time in the lubricating oil tank becomes longer and the bubbles in the lubricating oil disappear. Can be. As a result, it is possible to prevent the gears and bearings from being lubricated and lowered in cooling capacity, and corrosion. Further, since the amount of lubricating oil used can be reduced and the capacity of the lubricating oil tank can be reduced, there is an advantage that the size of the entire compressor can be reduced.

本発明の請求項３に係るターボ圧縮機によれば、前記ガスクーラのハウジングには、このガスクーラの軸線方向に熱交換器を挿通するための貫通穴が形成されてなるので、当該ハウジングの鋳造時に中子を両端支持でき、ガスクーラ内部のシールが確実に行える様になる。   In the turbo compressor according to claim 3 of the present invention, the housing of the gas cooler is formed with a through hole for inserting a heat exchanger in the axial direction of the gas cooler. The core can be supported at both ends, and the gas cooler can be securely sealed.

本発明の実施の形態に係る３段式ターボ圧縮機の模式的系統図である。1 is a schematic system diagram of a three-stage turbo compressor according to an embodiment of the present invention. 本発明の実施の形態に係る３段式ターボ圧縮機の電動機を省略した模式的平面図である。FIG. 3 is a schematic plan view in which the motor of the three-stage turbo compressor according to the embodiment of the present invention is omitted. 図２のＡ−Ａ矢視図である。It is an AA arrow line view of FIG. 図２のＢ−Ｂ矢視図である。It is a BB arrow line view of FIG. 本発明の実施の形態に係る３段式ターボ圧縮機を複数台設置した場合の冷却水配管の系統図の一例である。It is an example of the systematic diagram of the cooling water piping at the time of installing two or more units | sets of the three-stage type turbo compressor which concerns on embodiment of this invention. 従来技術１に係る遠心圧縮機の平面図である。It is a top view of the centrifugal compressor which concerns on the prior art 1. FIG. 図６のIV-IV矢視図である。It is the IV-IV arrow line view of FIG. 従来技術２に係るターボ圧縮機の側断面図である。It is a sectional side view of the turbo compressor which concerns on the prior art 2. FIG. 従来技術２に係るターボ圧縮機を複数台設置した場合の冷却水配管の系統図の一例である。It is an example of the system diagram of a cooling water piping at the time of installing the multiple turbo compressor which concerns on the prior art 2. FIG.

先ず、本発明の実施の形態に係るターボ圧縮機につき、３段式ターボ圧縮機に適用した態様例として、以下添付図１〜５を参照しながら説明する。図１は本発明の実施の形態に係る３段式ターボ圧縮機の模式的系統図、図２は本発明の実施の形態に係る３段式ターボ圧縮機の電動機を省略した模式的平面図、図３は図２のＡ−Ａ矢視図、図４は図２のＢ−Ｂ矢視図、図５は本発明の実施の形態に係る３段式ターボ圧縮機を複数台設置した場合の冷却水配管の系統図の一例である。   First, a turbo compressor according to an embodiment of the present invention will be described as an example of an aspect applied to a three-stage turbo compressor with reference to FIGS. FIG. 1 is a schematic system diagram of a three-stage turbo compressor according to an embodiment of the present invention. FIG. 2 is a schematic plan view in which the motor of the three-stage turbo compressor according to the embodiment of the present invention is omitted. 3 is a view taken along the line AA in FIG. 2, FIG. 4 is a view taken along the line BB in FIG. 2, and FIG. 5 is a case where a plurality of three-stage turbo compressors according to the embodiment of the present invention are installed. It is an example of the systematic diagram of cooling water piping.

この３段式ターボ圧縮機は、図１に示す如く、入力歯車６に１−２段ピニオンギヤ７と３段ピニオンギヤ８とを噛み合わして形成されたツインピニオン型の増速機（ギヤ）４を備えている。その増速機４は増速機ハウジング（ギヤケース）５に収容されている。そして、前記入力歯車６は、その中央部分において、入力軸６ａに接続されている。また、入力軸６ａは、増速機ハウジング（ギヤケース）５に内蔵された軸受等（図示せず）により回転可能に支持されている。   As shown in FIG. 1, this three-stage turbo compressor includes a twin-pinion type speed increaser (gear) 4 formed by meshing an input gear 6 with a 1-2-stage pinion gear 7 and a 3-stage pinion gear 8. I have. The gearbox 4 is accommodated in a gearbox housing (gear case) 5. And the said input gear 6 is connected to the input shaft 6a in the center part. The input shaft 6a is rotatably supported by a bearing or the like (not shown) built in the gearbox housing (gear case) 5.

同時に、前記入力軸６ａの一端が、増速機ハウジング５から突出しており、電動機Ｍの出力軸６ｂに接続されている。前記入力軸６ａと出力軸６ｂとの接続は、軸心にずれがあった場合でも振動や騒音を発することなく回転力を伝達可能なよう、カップリング２３を介して接続されている。増速機ハウジング５は、ハウジング下部の増速機下ハウジング５ａと、ハウジング上部の増速機上ハウジング５ｂとから構成されている。そして、増速機下ハウジング５ａが、後述する潤滑油タンク１３の上方に接続されている。   At the same time, one end of the input shaft 6 a protrudes from the gearbox housing 5 and is connected to the output shaft 6 b of the electric motor M. The input shaft 6a and the output shaft 6b are connected via a coupling 23 so that a rotational force can be transmitted without generating vibration and noise even when the shaft center is displaced. The gearbox housing 5 includes a gearbox lower housing 5a at the lower part of the housing and a gearbox upper housing 5b at the upper part of the housing. And the gearbox lower housing 5a is connected above the lubricating oil tank 13 mentioned later.

また、前記入力歯車６には、１−２段ピニオンギヤ７と３段ピニオンギヤ８が噛み合わされており、前記１−２段ピニオンギヤ７はピニオン軸７ａによって、更に、前記３段ピニオンギヤ８はピニオン軸８ａによって回転可能に支持されている。即ち、換言すれば、本発明の実施の形態に係る３段式ターボ圧縮機は、入力軸６ａの回転が入力歯車６、１−２段ピニオンギヤ７を介して伝達されるピニオン軸７ａと、入力軸６ａの回転が入力歯車６、３段ピニオンギヤ８を介して伝達されるピニオン軸８ａを有していると言える。   A 1-2 stage pinion gear 7 and a 3 stage pinion gear 8 are meshed with the input gear 6. The 1-2 stage pinion gear 7 is connected to a pinion shaft 7a, and the 3rd stage pinion gear 8 is further connected to a pinion shaft 8a. Is supported rotatably. That is, in other words, the three-stage turbo compressor according to the embodiment of the present invention includes a pinion shaft 7a in which the rotation of the input shaft 6a is transmitted via the input gear 6 and the first-second pinion gear 7, and the input It can be said that the shaft 6a has a pinion shaft 8a to which the rotation of the shaft 6a is transmitted via the input gear 6 and the three-stage pinion gear 8.

そして、増速機４から見て、１−２段ピニオンギヤ７のピニオン軸７ａの反電動機Ｍ側の一端に第１段インペラ１ａが接続され、この第１段インペラ１ａに第１段圧縮機ケーシング１ｂが周設されている。一方、増速機４から見て、１−２段ピニオンギヤ７のピニオン軸７ａの電動機Ｍ側の他端には第２段インペラ２ａが接続され、この第２段インペラ２ａに第２段圧縮機ケーシング２ｂが周設されている。また、このターボ圧縮機は、増速機４から見て３段ピニオンギヤ８のピニオン軸８ａの反電動機Ｍ側の一端に第３段インペラ３ａが接続され、この第３段インペラ３ａに第３段圧縮機ケーシング３ｂが周設されている。   The first stage impeller 1a is connected to one end on the counter-motor M side of the pinion shaft 7a of the 1-2 stage pinion gear 7 when viewed from the speed increaser 4, and the first stage impeller 1a is connected to the first stage compressor casing. 1b is provided around. On the other hand, a second stage impeller 2a is connected to the other end of the pinion shaft 7a of the 1-2 stage pinion gear 7 on the electric motor M side as viewed from the speed increaser 4, and a second stage compressor is connected to the second stage impeller 2a. A casing 2b is provided around the casing. The turbo compressor has a third-stage impeller 3a connected to one end of the pinion shaft 8a of the three-stage pinion gear 8 on the counter-motor M side as viewed from the speed increaser 4, and the third-stage impeller 3a is connected to the third-stage impeller 3a. A compressor casing 3b is provided around the compressor casing 3b.

これら第１段インペラ１ａ、第２段インペラ２ａ及び第３段インペラ３ａの何れも、第１段圧縮機ケーシング１ｂ、第２段圧縮機ケーシング２ｂ及び第３段圧縮機ケーシング３ｂ内の渦巻室（図示せず）に夫々収納され、第１段圧縮機１、第２段圧縮機２及び第３段圧縮機３が構成されている。   The first stage impeller 1a, the second stage impeller 2a, and the third stage impeller 3a are all swirl chambers in the first stage compressor casing 1b, the second stage compressor casing 2b, and the third stage compressor casing 3b ( 1st stage compressor 1, 2nd stage compressor 2, and 3rd stage compressor 3 are constituted, respectively.

即ち、この３段式ターボ圧縮機には、増速機ハウジング（ギヤケース）５の一方の側面にピニオン軸７ａで駆動される第１段圧縮機１が備えられ、かつ、増速機ハウジング（ギヤケース）５の他方の側面に同じくピニオン軸７ａで駆動される第２段圧縮機が備えられている。そして、この３段式ターボ圧縮機には、増速機ハウジング（ギヤケース）５の一方の側面に、ピニオン軸８ａで駆動される第３段圧縮機３が備えられ、かつ、増速機ハウジング（ギヤケース）５の一方の側面にピニオン軸８ａで駆動される第３段圧縮機３が備えられている。   That is, the three-stage turbo compressor includes a first stage compressor 1 driven by a pinion shaft 7a on one side surface of a speed increaser housing (gear case) 5, and the speed increaser housing (gear case). A second stage compressor driven by the pinion shaft 7a is also provided on the other side surface of 5). The three-stage turbo compressor is provided with a third-stage compressor 3 driven by a pinion shaft 8a on one side surface of a gearbox housing (gear case) 5, and a gearbox housing ( A third stage compressor 3 driven by a pinion shaft 8a is provided on one side surface of the gear case) 5.

図示しない吸込フィルタを介して吸い込まれた空気Ａ０は、第１段圧縮機１によって圧縮され、第１段圧縮空気として第１段圧縮機１の吐出口と第２段圧縮機２の吸込口とを連通する第１段圧縮空気流路２１に導かれる。そして、この第１段圧縮空気は、第１段圧縮空気流路２１を構成する第１段圧縮機吐出配管２１ａと、第２段圧縮機吸込配管２１ｂの間に介設された第１段インタクーラ（ガスクーラ）１１を経て第２段圧縮機２に導入される。   Air A0 sucked in through a suction filter (not shown) is compressed by the first stage compressor 1, and as the first stage compressed air, the discharge port of the first stage compressor 1 and the suction port of the second stage compressor 2 Are guided to the first-stage compressed air flow path 21 communicating with each other. And this 1st stage compressed air is the 1st stage intercooler interposed between the 1st stage compressor discharge piping 21a which comprises the 1st stage compressed air flow path 21, and the 2nd stage compressor suction piping 21b. (Gas cooler) 11 is introduced into second stage compressor 2.

第２段圧縮機２に導入された第１段圧縮空気は、更に第２段圧縮機２によって圧縮され、第２段圧縮空気として第２段圧縮機２の吐出口と第３段圧縮機３の吸込口とを連通する第２段圧縮空気流路２２に導かれる。そして、この第２段圧縮空気は、第２段圧縮空気流路２２を構成する第２段圧縮機吐出配管２２ａと、第３段圧縮機吸込配管２２ｂの間に介設された第２段インタクーラ（ガスクーラ）１２を経て第３段圧縮機３に導入される。そして、この第３段圧縮機３によって圧縮された第３段圧縮空気Ａ３が、圧縮空気の需要先に供給されるように構成されている。ここで、符号２０は、各配管を接続する管継手である。   The first stage compressed air introduced into the second stage compressor 2 is further compressed by the second stage compressor 2, and the second stage compressor 2 discharge port and the third stage compressor 3 serve as the second stage compressed air. To the second-stage compressed air flow path 22 communicating with the suction port. The second-stage compressed air is a second-stage intercooler interposed between the second-stage compressor discharge pipe 22a constituting the second-stage compressed air flow path 22 and the third-stage compressor suction pipe 22b. (Gas cooler) 12 is introduced into the third stage compressor 3. And it is comprised so that the 3rd stage compressed air A3 compressed by this 3rd stage compressor 3 may be supplied to the demand destination of compressed air. Here, the code | symbol 20 is a pipe joint which connects each piping.

そして、本発明の実施の形態に係るターボ圧縮機は、上記の如き３段式ターボ圧縮機において、入力歯車６に１−２段ピニオンギヤ７と３段ピニオンギヤ８とを噛み合わして形成された増速機４の下方に、ひいては、増速機ハウジング（ギヤケース）５の下部に、潤滑油タンク１３が配設される一方、第１段圧縮機１、第２段圧縮機２及び第３段圧縮機３の下方で、かつ潤滑油タンク１３の両側面に、円筒形状を有する第１段インタクーラ１１及び第２段インタクーラ１２が夫々配設されている。   The turbo compressor according to the embodiment of the present invention is an increase formed by meshing the input gear 6 with the 1-2 stage pinion gear 7 and the 3 stage pinion gear 8 in the above-described 3-stage turbo compressor. A lubricating oil tank 13 is disposed below the speed machine 4 and thus below the speed increaser housing (gear case) 5, while the first stage compressor 1, the second stage compressor 2, and the third stage compression. A first-stage intercooler 11 and a second-stage intercooler 12 each having a cylindrical shape are disposed below the machine 3 and on both sides of the lubricating oil tank 13.

同時に、このターボ圧縮機を平面視したとき（図２参照）、潤滑油タンク軸線Ｃ３及び第１段インタクーラ軸線Ｃ１、第２段インタクーラ軸線Ｃ２と圧縮機の入力軸６ａが平行に配置されている。ここで、第１段インタクーラ１１の外殻を構成する第１段インタクーラ胴体（ハウジング）１１ａ、第２段インタクーラ１２の外殻を構成する第２段インタクーラ胴体（ハウジング）１２ａ及びこれら両インタクーラ胴体１１ａ，１２ａに挟まれた潤滑油タンク１３は、鋳物により一体的に形成されている。   At the same time, when the turbo compressor is viewed in plan (see FIG. 2), the lubricating oil tank axis C3, the first stage intercooler axis C1, the second stage intercooler axis C2, and the input shaft 6a of the compressor are arranged in parallel. . Here, the first stage intercooler body (housing) 11a constituting the outer shell of the first stage intercooler 11, the second stage intercooler body (housing) 12a constituting the outer shell of the second stage intercooler 12, and both the intercooler bodies 11a. , 12a, the lubricating oil tank 13 is integrally formed of a casting.

前記第１段及び第２段インタクーラ１１，１２を夫々構成する第１段及び第２段インタクーラ胴体１１ａ，１２ａには、各インタクーラ軸線Ｃ１，Ｃ２方向に貫通穴が形成された略円筒形状を有するものが好ましい。そして、第１段及び第２段インタクーラ胴体１１ａ，１２ａの貫通穴内に、熱交換器１１ｂ，１２ｂが各インタクーラ軸線Ｃ１，Ｃ２方向に挿通して収納されている。   The first-stage and second-stage intercooler bodies 11a, 12a constituting the first-stage and second-stage intercoolers 11, 12 respectively have substantially cylindrical shapes in which through holes are formed in the directions of the respective intercooler axes C1, C2. Those are preferred. The heat exchangers 11b and 12b are inserted in the through-holes of the first-stage and second-stage intercooler bodies 11a and 12a and stored in the directions of the respective intercooler axes C1 and C2.

更に、これら第１段及び第２段インタクーラ１１，１２内の熱交換器１１ｂ，１２ｂを構成する管巣１１ｃ，１２ｃに冷却水を供給、もしくはそれら管巣１１ｃ，１２ｃから（圧縮空気を冷却後の）冷却水を排出して、前記第１段圧縮空気及び第２段圧縮空気を夫々冷却可能に構成されている。尚、符号１３ａは潤滑油タンク蓋を、符号１９ａ，１９ｂはインタクーラ蓋を、また符号１８，１８は第１段及び第２段インタクーラ１１，１２のシール部を示す。   Further, cooling water is supplied to the tube nests 11c and 12c constituting the heat exchangers 11b and 12b in the first and second stage intercoolers 11 and 12, or from the tube nests 11c and 12c (after the compressed air is cooled). The cooling water is discharged so that the first-stage compressed air and the second-stage compressed air can be cooled. Reference numeral 13a denotes a lubricating oil tank lid, reference numerals 19a and 19b denote intercooler lids, and reference numerals 18 and 18 denote seal portions of the first and second stage intercoolers 11 and 12, respectively.

冷却水の給排水取合口（図５に示す符号３１，３２）は、第１段及び第２段インタクーラ胴体１１ａ，１２ａにおける各インタクーラ軸線Ｃ１，Ｃ２方向の両端側の何れか、例えば反電動機Ｍ側の第１段及び第２段インタクーラ蓋１９ａ，１９ａに夫々設けるのが、後述する理由から好ましい。そして、前記給排水取合口の取り付けられていない側のインタクーラ蓋１９ｂ，１９ｂを取り外すことによって、前記熱交換器１１ｂ，１２ｂの第１段及び第２段インタクーラ軸線Ｃ１，Ｃ２方向への挿通が可能に構成されている。   The cooling water supply / drain joint (reference numerals 31 and 32 shown in FIG. 5) is either one of both end sides of the first and second stage intercooler bodies 11a and 12a in the direction of each intercooler axis C1 and C2, for example, on the side of the counter-motor M The first stage and the second stage intercooler lids 19a and 19a are preferably provided for the reasons described later. Then, by removing the intercooler lids 19b, 19b on the side where the water supply / drainage connection port is not attached, the heat exchangers 11b, 12b can be inserted in the first and second intercooler axis C1, C2 directions. It is configured.

この様に、第１段乃至第３段圧縮機１，２，３の下方で、かつ潤滑油タンク１３の両側面の空間に、ガス冷却のための第１段及び第２段インタクーラ１１，１２を設けることによって、圧縮機全体のコンパクト化が可能となった。また、前記熱交換器１１ｂ，１２ｂの第１段及び第２段インタクーラ軸線Ｃ１，Ｃ２方向への挿通が可能な構成としたので、熱交換器１１ｂ，１２ｂの第１段及び第２段インタクーラ１１，１２への装脱着が簡単になり、各インタクーラ１１，１２のメンテナンスが容易になった。更に、潤滑油タンク１３の潤滑油タンク蓋１３ａ側の端面が、電動機に邪魔されることが無くなったので、潤滑油タンク１３への給油も容易となった。   In this manner, the first and second stage intercoolers 11 and 12 for gas cooling are provided below the first to third stage compressors 1, 2 and 3 and in the spaces on both sides of the lubricating oil tank 13. By providing the compressor, the entire compressor can be made compact. Further, since the heat exchangers 11b and 12b can be inserted in the first and second stage intercooler axis C1 and C2 directions, the first and second stage intercoolers 11 of the heat exchangers 11b and 12b can be inserted. , 12 can be easily attached and detached, and maintenance of each intercooler 11, 12 is facilitated. Furthermore, since the end face of the lubricating oil tank 13 on the lubricating oil tank lid 13a side is not obstructed by the electric motor, the lubricating oil tank 13 can be supplied easily.

そしてまた、第１段及び第２段インタクーラ１１，１２を構成する第１段及び第２段インタクーラ胴体１１ａ，１２ａは、これら第１段及び第２段インタクーラ軸線Ｃ１，Ｃ２方向に貫通穴が形成されているので、当該インタクーラ胴体１１ａ，１２ａの鋳造時に、中子をその両端で強固に支持して、当該インタクーラ胴体１１ａ，１２ａの鋳造時の加工精度を向上でき、第１及び第２インタクーラ１１，１２におけるシール部１８，１８のシールが確実に行える様になる。   In addition, the first and second stage intercooler bodies 11a and 12a constituting the first and second stage intercoolers 11 and 12 are formed with through holes in the direction of the first and second stage intercooler axes C1 and C2. Therefore, when casting the intercooler bodies 11a, 12a, the core is firmly supported at both ends thereof, and the processing accuracy at the time of casting the intercooler bodies 11a, 12a can be improved, and the first and second intercoolers 11 can be improved. , 12 can be reliably sealed.

更に、増速機４を収納した増速機ハウジング５は、ハウジング下部の増速機下ハウジング５ａと、ハウジング上部の増速機上ハウジング５ｂとから構成されており、潤滑油タンク１３は、増速機下ハウジング５ａの下部に形成され、更に、潤滑油タンク１３の両側面の空間に、第１段及び第２段インタクーラ１１，１２が設けられている。この様な構成とすることによって、本発明に係るターボ圧縮機のコンパクト化が図られると共に、特に、潤滑油タンク１３の下方ではなく、その両側面の空間に、第１段及び第２段インタクーラ１１，１２が設けられていることで、増速機４を構成するギヤ６〜８と潤滑油タンク１３の潤滑油面との距離を大きくすることができるので、潤滑油の跳ね返りによる機械損失を解消し得る。   Furthermore, the gearbox housing 5 in which the gearbox 4 is housed is composed of a gearbox lower housing 5a at the lower part of the housing and a gearbox upper housing 5b at the upper part of the housing. A first stage and second stage intercoolers 11 and 12 are provided in the space on both sides of the lubricating oil tank 13 formed at the lower part of the lower speed machine housing 5a. By adopting such a configuration, the turbo compressor according to the present invention can be made compact, and in particular, the first stage and second stage intercoolers are not located under the lubricating oil tank 13 but in the spaces on both sides thereof. 11 and 12 can increase the distance between the gears 6 to 8 constituting the speed increaser 4 and the lubricating oil surface of the lubricating oil tank 13, thereby reducing mechanical loss due to the rebound of the lubricating oil. It can be resolved.

即ち、図４において、潤滑油タンク１３に貯留された潤滑油１４は、潤滑油タンク蓋１３ａに設けられた図示しない給油口から油ポンプ１７によって吸い上げられ、１−２段ピニオンギヤ７用のシャワノズル９と３段ピニオンギヤ８用のシャワノズル１０から、入力歯車６、１−２段ピニオンギヤ７及び３段ピニオンギヤ８に向けて噴射され、これら増速機４の潤滑・冷却に利用されるが、高速で回転している増速機４の入力歯車６及び３段ピニオンギヤ８に跳ね飛ばされた潤滑油１４ａは、潤滑油面１４ｂから跳ね返ったとしても増速機４までは届かず、潤滑油１４ａの跳ね返りによる機械損失を解消することができる。ここで、符号２４は入力歯車６の回転方向である。   That is, in FIG. 4, the lubricating oil 14 stored in the lubricating oil tank 13 is sucked up by an oil pump 17 from an oil supply port (not shown) provided in the lubricating oil tank lid 13 a, and the shower nozzle 9 for the 1-2 stage pinion gear 7. Are injected from the shower nozzle 10 for the three-stage pinion gear 8 toward the input gear 6, the first-second stage pinion gear 7 and the third-stage pinion gear 8, and are used for lubrication and cooling of the speed increaser 4, but rotate at high speed. Even if the lubricating oil 14a bounced off the input gear 6 and the three-stage pinion gear 8 of the speed increasing gear 4 bounces off from the lubricating oil surface 14b, the lubricating oil 14a does not reach the speed increasing gear 4, and the lubricating oil 14a rebounds. Mechanical loss can be eliminated. Here, reference numeral 24 denotes the rotation direction of the input gear 6.

また、本発明の実施の形態に係るターボ圧縮機は、図５に示す通り、第１及び第２インタクーラ１１，１２の給水取合口３１，３１及び排水取合口３２，３２が、第１段及び第２段インタクーラ軸線Ｃ１，Ｃ２方向の反電動機Ｍ側のインタクーラ蓋に夫々設けられているので、前記ターボ圧縮機を複数台設置した場合の、給水取合口３１及び排水取合口３２へ接続される給水配管３１ａ及び排水配管３２ａは、何れも給水主配管３１ｂ及び排水主配管３２ｂに対して屈曲させることなく接続可能である。   In addition, as shown in FIG. 5, the turbo compressor according to the embodiment of the present invention includes the first and second intercoolers 11 and 12, the water supply joints 31 and 31 and the drainage joints 32 and 32, in the first stage and Since it is provided on the intercooler lid on the side of the counter-motor M in the direction of the second stage intercooler axis C1, C2, it is connected to the water supply inlet 31 and the drainage inlet 32 when a plurality of the turbo compressors are installed. Both the water supply pipe 31a and the drainage pipe 32a can be connected to the water supply main pipe 31b and the drainage main pipe 32b without being bent.

即ち、給水配管３１ａ及び排水配管３２ａは、給水主配管３１ｂ及び排水主配管３２ｂから略垂直に延びた後、屈曲することなく、その給水配管３１ａ及び排水配管３２ａと略同軸上に配置された給水取合口３１及び排水取合口３２へ接続される。そのため、配管工事が簡単で設置スペースも小さくできる上、これらの配管が圧縮機のメンテナンスの障害となることがない。   That is, the water supply pipe 31a and the drainage pipe 32a extend substantially perpendicularly from the water supply main pipe 31b and the drainage main pipe 32b, and then are not bent, and are arranged substantially coaxially with the water supply pipe 31a and the drainage pipe 32a. Connected to the joint 31 and the drain joint 32. Therefore, the piping work is simple and the installation space can be reduced, and these pipes do not become an obstacle to the maintenance of the compressor.

更に、本発明の実施の形態に係るターボ圧縮機は、図２，４に示す如く、潤滑油タンク１３内に、このタンク１３内の油溜り部１５を上下に画成する中仕切り板１６が設けられている。尚、その中仕切り板１６の端部とタンク１３の内壁とによって、中仕切り板１６にて画成された上下の油溜り部１５を連通する開孔部１６ａが形成されている。   Further, as shown in FIGS. 2 and 4, the turbo compressor according to the embodiment of the present invention has a partition plate 16 that vertically defines an oil reservoir 15 in the tank 13 in the lubricating oil tank 13. Is provided. An opening 16 a that communicates with the upper and lower oil reservoirs 15 defined by the intermediate partition plate 16 is formed by the end of the intermediate partition plate 16 and the inner wall of the tank 13.

増速機４に跳ね飛ばされて油溜り部１５に貯留された潤滑油１４は、潤滑油タンク蓋１３ａに設けられた図示しない給油口から油ポンプ１７に吸い上げられ、再び入力歯車６や１−２段ピニオンギヤ７及び３段ピニオンギヤ８、更には図示しない軸受の潤滑・冷却に供されるが、高速で回転している前記ギヤ６〜８に跳ね飛ばされた潤滑油１４ａは、空気（気泡）を巻き込んで潤滑油タンク１３内の油溜り部１５に戻って来る。この気泡を含んだままの潤滑油１４は、前記ギヤ６〜８や軸受を潤滑・冷却する能力の低下や腐食の原因になったりする。   The lubricating oil 14 splashed off by the speed increaser 4 and stored in the oil reservoir 15 is sucked up by an oil pump 17 from an oil supply port (not shown) provided in the lubricating oil tank lid 13a, and again input gears 6 and 1- Lubricating oil 14a which is used for lubricating and cooling the second-stage pinion gear 7 and the third-stage pinion gear 8 and a bearing (not shown) but is sputtered by the gears 6 to 8 rotating at high speed is air (bubbles). Is returned to the oil reservoir 15 in the lubricating oil tank 13. The lubricating oil 14 still containing bubbles may cause a reduction in the ability to lubricate and cool the gears 6 to 8 and the bearing, and may cause corrosion.

気泡を消去する方法としては、潤滑油タンク１３の容量を大きくして、戻って来た潤滑油１６が再利用されるまでの時間を長くし、気泡を油面に浮き上がらせて飛散させるのが一般的であるが、それでは潤滑油１４が多量に必要になってしまう。上記の如く中仕切り板１６を設けることによって、潤滑油１４が油ポンプ１７に吸い込まれるまでに、前記ギヤ６〜８に跳ね飛ばされて油溜り部１５の潤滑油面１４ｂに落下した潤滑油１４は、中仕切り板１６に画成された上側の油溜り部１５の潤滑油１４の流れに沿って開孔部１６ａを経由し、次いで、中仕切り板１６に画成された下側の油溜り部１５の潤滑油１４の流れに沿って、潤滑油タンク蓋１３ａ方向に向かうことになる。   As a method of eliminating bubbles, the capacity of the lubricating oil tank 13 is increased, the time until the returned lubricating oil 16 is reused is lengthened, and the bubbles are floated and scattered on the oil surface. In general, a large amount of lubricating oil 14 is required. By providing the partition plate 16 as described above, the lubricating oil 14 that has been splashed by the gears 6 to 8 and dropped onto the lubricating oil surface 14 b of the oil reservoir 15 before the lubricating oil 14 is sucked into the oil pump 17. Passes through the opening 16 a along the flow of the lubricating oil 14 in the upper oil reservoir 15 defined in the partition plate 16, and then the lower oil reservoir defined in the partition plate 16. Along the flow of the lubricating oil 14 in the portion 15, the lubricating oil tank lid 13 a is directed.

そのため、潤滑油１４が油ポンプ１７に吸い込まれるまでに確実に長い経路を辿ることになり、再利用されるまでの時間が長くなって、潤滑油１４中の気泡が油面まで浮き上がるので、気泡を増速機ハウジング５内の気相部へ飛散させることができる。   Therefore, a long path is surely taken until the lubricating oil 14 is sucked into the oil pump 17, and the time until the lubricating oil 14 is reused becomes longer, and the bubbles in the lubricating oil 14 rise to the oil surface. Can be scattered to the gas phase portion in the gearbox housing 5.

中仕切り板１６が無い場合は、増速機４から潤滑油タンク１３の潤滑油面１４ｂに落下した潤滑油１４は、最短経路で潤滑油タンク蓋１３ａへ向かうが、これと比較して中仕切り板１６を設けた本発明の実施の形態の場合は、潤滑油タンク１３の潤滑油面１４ｂに落下した前記潤滑油１４は、約３倍長い距離を経由して潤滑油タンク１３を出て行くことになる。   When there is no intermediate partition plate 16, the lubricating oil 14 that has fallen from the speed increaser 4 to the lubricating oil surface 14b of the lubricating oil tank 13 is directed to the lubricating oil tank lid 13a through the shortest path. In the case of the embodiment of the present invention in which the plate 16 is provided, the lubricating oil 14 that has fallen on the lubricating oil surface 14b of the lubricating oil tank 13 leaves the lubricating oil tank 13 via a distance that is approximately three times longer. It will be.

以上説明した通り、本発明の実施の形態に係るターボ圧縮機によれば、増速機４や軸受の潤滑及び冷却能力の低下要因となる潤滑油１４中の気泡を消滅させることができる。更には、潤滑油１４の使用量を少なくし、潤滑油タンク１３の容量も少量化できるので、圧縮機全体の大きさも小型化できるメリットが生じる。   As described above, according to the turbo compressor according to the embodiment of the present invention, it is possible to eliminate bubbles in the lubricating oil 14 that cause a reduction in lubrication and cooling capacity of the speed increaser 4 and the bearing. Furthermore, since the amount of the lubricating oil 14 used can be reduced and the capacity of the lubricating oil tank 13 can be reduced, there is an advantage that the overall size of the compressor can be reduced.

尚、本発明の実施の形態に係るターボ圧縮機については、３段式ターボ圧縮機に適用した態様例を説明したが、本願発明に係るターボ圧縮機は、３段式ターボ圧縮機に限定されることなく、２段式ターボ圧縮機或いは４段以上の多段式ターボ圧縮機においても当然有効である。   In addition, although the example of the aspect applied to the three-stage turbo compressor was described about the turbo compressor which concerns on embodiment of this invention, the turbo compressor which concerns on this invention is limited to a three-stage turbo compressor. Of course, this is also effective in a two-stage turbo compressor or a multistage turbo compressor having four or more stages.

Ａ０：空気，
Ａ３：第３段圧縮空気，
Ｃ１：第１インタクーラ軸線，
Ｃ２：第１インタクーラ軸線，
Ｃ３：潤滑油タンク軸線，
Ｍ：電動機，
１：第１段圧縮機， １ａ：第１段インペラ， １ｂ：第１段圧縮機ケーシング，
２：第２段圧縮機， ２ａ：第２段インペラ， ２ｂ：第２段圧縮機ケーシング，
３：第３段圧縮機， ３ａ：第３段インペラ， ３ｂ：第３段圧縮機ケーシング，
４：増速機（ギヤ），
５：増速機ハウジング（ギヤケース），
５ａ：増速機下ハウジング， ５ｂ：増速機上ハウジング，
６：入力歯車， ６ａ：入力軸， ６ｂ：出力軸，
７：１−２段ピニオンギヤ， ７ａ：ピニオン軸，
８：３段ピニオンギヤ， ８ａ：ピニオン軸，
９，１０：シャワノズル，
１１：第１段インタクーラ（ガスクーラ）， １１ａ：第１段インタクーラ胴体，
１１ｂ：熱交換器， １１ｃ：管巣，
１２：第２段インタクーラ（ガスクーラ）， １２ａ：第２段インタクーラ胴体，
１２ｂ：熱交換器， １２ｃ：管巣，
１３：潤滑油タンク， １３ａ：潤滑油タンク蓋，
１４，１４ａ：潤滑油， １４ｂ：潤滑油面，
１５：油溜り部，
１６：中仕切り板， １６ａ：開孔部，
１７：油ポンプ，
１８：シール部，
１９ａ，１９ｂ：インタクーラ蓋，
２０：管継手，
２１：第１段圧縮空気流路， ２１ａ：第１段圧縮機吐出配管，
２１ｂ：第２段圧縮機吸込配管，
２２：第２段圧縮空気流路， ２２ａ：第２段圧縮機吐出配管，
２２ｂ：第３段圧縮機吸込配管，
２３：カップリング， ２４：回転方向，
３１：給水取合口， ３１ａ：給水配管， ３１ｂ：給水主配管，
３２：排水取合口， ３２ａ：排水配管， ３２ｂ：排水主配管 A0: Air,
A3: Third stage compressed air,
C1: first intercooler axis,
C2: first intercooler axis,
C3: lubricating oil tank axis,
M: electric motor,
1: 1st stage compressor, 1a: 1st stage impeller, 1b: 1st stage compressor casing,
2: 2nd stage compressor, 2a: 2nd stage impeller, 2b: 2nd stage compressor casing,
3: Third stage compressor, 3a: Third stage impeller, 3b: Third stage compressor casing,
4: gearbox (gear),
5: Gearbox housing (gear case),
5a: Housing below the gearbox, 5b: Housing above the gearbox,
6: input gear, 6a: input shaft, 6b: output shaft,
7: 1-2 stage pinion gear, 7a: pinion shaft,
8: Three-stage pinion gear, 8a: Pinion shaft,
9, 10: Shower nozzle,
11: First stage intercooler (gas cooler), 11a: First stage intercooler fuselage,
11b: heat exchanger, 11c: tube nest,
12: Second stage intercooler (gas cooler), 12a: Second stage intercooler fuselage,
12b: heat exchanger, 12c: tube nest,
13: Lubricating oil tank, 13a: Lubricating oil tank lid,
14, 14a: Lubricating oil, 14b: Lubricating oil surface,
15: Oil reservoir
16: Middle partition plate, 16a: Opening part,
17: Oil pump,
18: seal part,
19a, 19b: Intercooler lid,
20: Pipe fitting,
21: First stage compressed air flow path, 21a: First stage compressor discharge pipe,
21b: second stage compressor suction pipe,
22: Second stage compressed air flow path, 22a: Second stage compressor discharge pipe,
22b: Third stage compressor suction pipe,
23: Coupling, 24: Direction of rotation,
31: Water supply joint, 31a: Water supply piping, 31b: Water supply main piping,
32: Drainage joint, 32a: Drainage pipe, 32b: Drainage main pipe

Claims (3)

入力軸と、この入力軸の回転がギヤを介して伝達される少なくとも１本のピニオン軸とを有するギヤケースの一方の側面に、前記ピニオン軸で駆動される第１段圧縮機が備えられ、
かつ他方の側面に前記ピニオン軸で駆動される第２段圧縮機が備えられると共に、
これら第１段圧縮機と第２段圧縮機とから吐出されるガスを冷却するガスクーラが夫々備えられたターボ圧縮機において、
前記ギヤケースの下部に潤滑油タンクが配設されると共に、
前記第１段圧縮機と第２段圧縮機との下方で、かつ前記潤滑油タンクの両側面に前記ガスクーラが夫々配設され、
前記潤滑油タンク及び前記夫々のガスクーラの各軸線と前記入力軸が平行に配置されてなることを特徴とするターボ圧縮機。 A first stage compressor driven by the pinion shaft is provided on one side surface of a gear case having an input shaft and at least one pinion shaft to which rotation of the input shaft is transmitted via a gear.
And a second stage compressor driven by the pinion shaft is provided on the other side surface,
In each of the turbo compressors provided with gas coolers for cooling the gas discharged from the first stage compressor and the second stage compressor,
A lubricating oil tank is disposed below the gear case,
The gas coolers are respectively disposed below the first stage compressor and the second stage compressor and on both side surfaces of the lubricating oil tank,
A turbo compressor, wherein each axis of the lubricating oil tank and each gas cooler and the input shaft are arranged in parallel. 前記潤滑油タンク内に、このタンク内の油溜まり部を上下に画成する中仕切り板が設けられ、前記中仕切り板の端部と前記潤滑油タンクの内壁とによって、前記画成された上下の油溜り部を連通する開孔部が形成されてなることを特徴とする請求項１に記載のターボ圧縮機。   An inner partition plate that vertically defines an oil reservoir in the tank is provided in the lubricating oil tank, and the upper and lower portions defined by the end portion of the inner partition plate and the inner wall of the lubricating oil tank are provided. The turbo compressor according to claim 1, wherein an opening for communicating with the oil reservoir is formed. 前記ガスクーラのハウジングには、このガスクーラの軸線方向に熱交換器を挿通するための貫通穴が形成されてなることを特徴とする請求項１または２に記載のターボ圧縮機。   The turbo compressor according to claim 1 or 2, wherein a through hole for inserting a heat exchanger in an axial direction of the gas cooler is formed in the housing of the gas cooler.
JP2011199770A 2011-09-13 2011-09-13 Turbo compressor Expired - Fee Related JP5616866B2 (en)

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014214746A (en) * 2013-04-26 2014-11-17 株式会社神戸製鋼所 Compression apparatus
WO2017212637A1 (en) * 2016-06-10 2017-12-14 三菱重工コンプレッサ株式会社 Compressor module
DE102016113067A1 (en) * 2016-07-15 2018-01-18 Man Diesel & Turbo Se Geared turbine machine
WO2018150541A1 (en) 2017-02-17 2018-08-23 三菱重工コンプレッサ株式会社 Compressor module
US10641275B2 (en) 2015-09-02 2020-05-05 Kobe Steel, Ltd. Compressor
EP4053408A2 (en) 2021-02-25 2022-09-07 Mitsubishi Heavy Industries Compressor Corporation Compressor module and compressor module designing method

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07103162A (en) * 1993-10-04 1995-04-18 Ishikawajima Harima Heavy Ind Co Ltd Centrifugal compressor
JP2003328998A (en) * 2002-05-17 2003-11-19 Kobe Steel Ltd Turbo compressor

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4082009B2 (en) * 2001-09-25 2008-04-30 株式会社日立プラントテクノロジー Turbo compressor
JP2007332826A (en) * 2006-06-13 2007-12-27 Kobe Steel Ltd Centrifugal compressor
JP4876868B2 (en) * 2006-11-27 2012-02-15 株式会社Ｉｈｉ Turbo compressor
JP5167845B2 (en) * 2008-02-06 2013-03-21 株式会社Ｉｈｉ Turbo compressor and refrigerator

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07103162A (en) * 1993-10-04 1995-04-18 Ishikawajima Harima Heavy Ind Co Ltd Centrifugal compressor
JP2003328998A (en) * 2002-05-17 2003-11-19 Kobe Steel Ltd Turbo compressor

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JP2014214746A (en) * 2013-04-26 2014-11-17 株式会社神戸製鋼所 Compression apparatus
US10641275B2 (en) 2015-09-02 2020-05-05 Kobe Steel, Ltd. Compressor
WO2017212637A1 (en) * 2016-06-10 2017-12-14 三菱重工コンプレッサ株式会社 Compressor module
JPWO2017212637A1 (en) * 2016-06-10 2019-02-07 三菱重工コンプレッサ株式会社 Compressor module
US11236761B2 (en) 2016-06-10 2022-02-01 Mitsubishi Heavy Industries Compressor Corporation Compressor module
DE102016113067A1 (en) * 2016-07-15 2018-01-18 Man Diesel & Turbo Se Geared turbine machine
WO2018150541A1 (en) 2017-02-17 2018-08-23 三菱重工コンプレッサ株式会社 Compressor module
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EP4053408A2 (en) 2021-02-25 2022-09-07 Mitsubishi Heavy Industries Compressor Corporation Compressor module and compressor module designing method

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