JP2006233901A - Centrifugal compressor - Google Patents

Centrifugal compressor Download PDF

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JP2006233901A
JP2006233901A JP2005051278A JP2005051278A JP2006233901A JP 2006233901 A JP2006233901 A JP 2006233901A JP 2005051278 A JP2005051278 A JP 2005051278A JP 2005051278 A JP2005051278 A JP 2005051278A JP 2006233901 A JP2006233901 A JP 2006233901A
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gear
main shaft
impeller
vane
centrifugal compressor
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JP4746330B2 (en
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Yoshikuni Kono
好邦 河野
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Mitsubishi Heavy Industries Ltd
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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
    • 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
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable 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
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • 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
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/51—Inlet

Abstract

<P>PROBLEM TO BE SOLVED: To provide a centrifugal compressor capable of improving its durability markedly without increasing its size. <P>SOLUTION: A main shaft 11, an impeller 12 attached to the main shaft 11, a flow-in passage 18 for guiding gas to be compressed into the impeller 12 from an outer side in the radial direction of the main shaft 11 by surrounding the main shaft 11, a plurality of suction vanes 32 arranged to surround the main shaft 11 in the flow-in passage 18 and swinging around a swing axial line parallel with an axial line O of the main shaft 11, respectively, and vane driving devices 33 for swinging each suction vane 32 are provided in a casing 17. Driven gears 42 (first gear) provided in each suction vane 31, driving gears 43 (second gear) arranged adjacent to these driven gears 42 in the direction of swing axial line, a gear driving device 44 for driving the driving gears 43, and a ring gear 46 arranging first gear parts 47 meshing with each driven gear 42 and second gear parts 48 meshing with the driving gears 43 in an adjacent manner in the direction of swing axial line are provided as the vane driving devices 33. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、遠心圧縮機に関するものである。   The present invention relates to a centrifugal compressor.

遠心圧縮機は、主軸と、この主軸に取り付けられた羽根車と、これら主軸と羽根車とを収容するケーシングとを有しており、主軸を回転駆動してケーシング内で羽根車を高速回転させることでケーシング内に取り込んだ気体に遠心力を与え、この遠心力によって気体の圧縮を行う形式の圧縮機である。
ケーシングには、圧縮対象の気体をケーシング内に取り込むための吸込口と、吸込口から吸い込まれた気体を羽根車に導入するための流入路と、羽根車によって圧縮された気体を吐出する吐出口とが設けられている。
流入路は、主軸の周囲を取り囲むようにして設けられており、吸込口から吸い込まれた気体は、流入路によって主軸の径方向外側から径方向内側に向けて案内されて、主軸に取り付けられた羽根車の径方向内側の領域に供給されるようになっている。 The centrifugal compressor has a main shaft, an impeller attached to the main shaft, and a casing that accommodates the main shaft and the impeller, and rotates the main shaft to rotate the impeller at high speed in the casing. This is a compressor of a type that applies a centrifugal force to the gas taken into the casing and compresses the gas by the centrifugal force.
The casing has a suction port for taking the gas to be compressed into the casing, an inflow passage for introducing the gas sucked from the suction port into the impeller, and a discharge port for discharging the gas compressed by the impeller And are provided.
The inflow path is provided so as to surround the periphery of the main shaft, and the gas sucked from the suction port is guided from the radially outer side of the main shaft to the inner side in the radial direction by the inflow channel, and is attached to the main shaft. It supplies to the area | region inside the radial direction of an impeller.

近年、遠心圧縮機の効率を向上させるために、遠心圧縮機には、吸込口から吸い込む気体の量を調節する流量調節機構が設けられるようになってきている。
流量調節機構を有する遠心圧縮機としては、例えば、特許文献１に記載の遠心圧縮機が知られている。
特許文献１記載の遠心圧縮機では、流量調節機構として、流入路内に、主軸の軸線に略直交する面上で揺動可能な吸込ベーンが、主軸の周囲を取り囲むように複数配置されており、この吸込ベーンの主軸に対する角度を変えることで、流入路から羽根車に供給される気体の量（すなわち吸込口から吸い込む気体の量）を調節することができるようになっている。 In recent years, in order to improve the efficiency of the centrifugal compressor, the centrifugal compressor has been provided with a flow rate adjusting mechanism for adjusting the amount of gas sucked from the suction port.
As a centrifugal compressor having a flow rate adjusting mechanism, for example, a centrifugal compressor described in Patent Document 1 is known.
In the centrifugal compressor described in Patent Document 1, a plurality of suction vanes capable of swinging on a surface substantially orthogonal to the axis of the main shaft are disposed in the inflow path as a flow rate adjusting mechanism so as to surround the periphery of the main shaft. By changing the angle of the suction vane with respect to the main shaft, the amount of gas supplied from the inflow path to the impeller (that is, the amount of gas sucked from the suction port) can be adjusted.

吸込ベーンは、主軸と平行に延在する取付軸を有しており、この取付軸には、第１のギアが同軸にして設けられている。
主軸の回りには、第１のギアよりも主軸側に配置されて、各第１のギアと噛み合うとともに主軸の回りに回転自在である環状のリングギアと、第１のギアのうちの一つと噛み合うとともに、主軸と平行に延在してケーシングを貫通する駆動軸を有する第２のギアとが設けられている。すなわち、第２のギアとこれに噛み合う第１のギア、及びリングギアは、主軸の径方向に配列されている。
そして、ケーシングの外側に設けられたギア駆動部によって、駆動軸を介して第２のギアを回転させると、第１のギアのうち、第２のギアと噛み合っている第１のギアが回転する。この第１のギアが回転すると、この第１のギアに噛み合うリングギアも回転するので、リングギアと噛み合っている他の第１のギアも回転することとなる。
この遠心圧縮機では、このように第１、第２のギア、及びリングギアを用いて、第１のギアに接続された吸込ベーンの向きを調節する構成とされている。 The suction vane has an attachment shaft extending in parallel with the main shaft, and a first gear is provided coaxially on the attachment shaft.
An annular ring gear disposed around the main shaft and closer to the main shaft than the first gear, meshes with each first gear and is rotatable about the main shaft, and one of the first gears A second gear having a drive shaft that engages and extends parallel to the main shaft and penetrates the casing is provided. That is, the second gear, the first gear meshing with the second gear, and the ring gear are arranged in the radial direction of the main shaft.
Then, when the second gear is rotated via the drive shaft by the gear driving unit provided on the outer side of the casing, the first gear meshed with the second gear among the first gears is rotated. . When the first gear rotates, the ring gear that meshes with the first gear also rotates, so that the other first gear that meshes with the ring gear also rotates.
In this centrifugal compressor, the direction of the suction vane connected to the first gear is adjusted by using the first and second gears and the ring gear as described above.

特開２００１−２９５７９５号公報（段落［００１０］〜［００１８］、図１〜図３）JP 2001-29595 A (paragraphs [0010] to [0018], FIGS. 1 to 3)

この流量調節機構では、上記のように、ギア駆動部の駆動力は、第２のギアを介して第１のギアのうちの一つに伝達され、この第１のギアからリングギアを介して残りの第１のギアに伝達される。すなわち、第２のギアと噛み合う第１のギアには、自身を駆動する駆動力に加えて、残りの全ての第１のギアを駆動する駆動力が加えられるので、高い強度が要求される。   In this flow rate adjusting mechanism, as described above, the driving force of the gear driving unit is transmitted to one of the first gears via the second gear, and from the first gear via the ring gear. It is transmitted to the remaining first gear. That is, the first gear meshing with the second gear is required to have high strength because the driving force for driving all the remaining first gears is applied in addition to the driving force for driving the first gear.

第１のギアの強度は、その径を大きくするか、もしくは径はそのままでも歯幅のみ大きくすることで高めることができる。
しかし、前記のように第１のギアは周方向に等間隔で多数設けられており、第１のギアの径を大きくすると隣接するギア同士が接触するため、第１のギアの径をあまり大きくすることができない。
また、各部材の配置の関係上、第１のギアの径とリングギアの径との差が大きいので、第１のギア及びリングギアの歯幅を大きくすることによって強度を向上させる場合には、第１のギア及びリングギアの歯幅を非常に大きく取る必要がある。このため、設置スペースの関係から、第１のギア及びリングギアの歯幅をあまり大きく取ることができない。
このように、従来は、遠心圧縮機を大型化することなく耐久性を向上させることは困難であった。 The strength of the first gear can be increased by increasing its diameter, or by increasing only the tooth width even if the diameter remains the same.
However, as described above, a large number of the first gears are provided at equal intervals in the circumferential direction, and when the diameter of the first gear is increased, adjacent gears come into contact with each other. Can not do it.
In addition, due to the arrangement of each member, the difference between the diameter of the first gear and the diameter of the ring gear is large, so when the strength is improved by increasing the tooth width of the first gear and the ring gear. The tooth widths of the first gear and the ring gear need to be very large. For this reason, the tooth | gear width of a 1st gear and a ring gear cannot be taken very large from the relationship of installation space.
Thus, conventionally, it has been difficult to improve durability without increasing the size of the centrifugal compressor.

本発明は、このような事情に鑑みてなされたものであって、大型化することなく耐久性が著しく向上した遠心圧縮機を提供することを目的とする。   This invention is made | formed in view of such a situation, Comprising: It aims at providing the centrifugal compressor which durability improved significantly, without enlarging.

上記課題を解決するために、本発明の遠心圧縮機は以下の手段を採用する。
すなわち、本発明にかかる遠心圧縮機は、主軸と、該主軸に取り付けられた羽根車と、前記主軸及び前記羽根車を収容するケーシングとを有し、該ケーシングが、前記主軸の周囲を取り囲んで圧縮対象の気体を前記主軸の径方向外側から径方向内側に案内して前記羽根車に供給する流入路を有しており、前記主軸を介して前記羽根車を回転駆動することで前記羽根車に供給された気体に遠心力を与えて該気体を圧縮する遠心圧縮機であって、前記流入路内に前記主軸の周囲を取り囲むように複数配置されてそれぞれ前記主軸の軸線に平行な揺動軸線回りに揺動可能な吸込ベーンと、該各吸込ベーンを前記揺動軸線回りに揺動させるベーン駆動装置とを有し、該ベーン駆動装置は、前記各吸込ベーンのそれぞれに対して前記揺動軸線と同軸にして設けられた第１ギアと、該各第１ギアの設置領域に対して前記揺動軸線方向に隣接して設けられる第２ギアと、該第２ギアを回転駆動するギア駆動装置と、前記主軸よりも大径で該主軸と同軸にして設けられて前記第１ギア及び前記第２ギアと噛み合う環状のリングギアとを有しており、該リングギアには、前記各第１ギアと噛み合う第１歯車部と、前記第２ギアと噛み合う第２歯車部とが、前記揺動軸線方向に隣接して設けられていることを特徴とする。 In order to solve the above problems, the centrifugal compressor of the present invention employs the following means.
That is, a centrifugal compressor according to the present invention includes a main shaft, an impeller attached to the main shaft, and a casing that houses the main shaft and the impeller, and the casing surrounds the periphery of the main shaft. The impeller has an inflow path that guides gas to be compressed from the radially outer side to the radially inner side of the main shaft and supplies the gas to the impeller, and the impeller is driven by rotating the impeller through the main shaft. A centrifugal compressor that compresses the gas by applying centrifugal force to the gas supplied to the gas, and a plurality of the centrifugal compressors are arranged in the inflow path so as to surround the periphery of the main shaft, and each of the centrifugal compressors is parallel to the axis of the main shaft. A suction vane swingable about an axis, and a vane drive device for swinging each suction vane about the swing axis, the vane drive device configured to swing the suction vane with respect to each of the suction vanes. Coaxial with the axis of movement A first gear provided; a second gear provided adjacent to the installation region of each first gear in the swing axis direction; a gear driving device that rotationally drives the second gear; and the main shaft An annular ring gear that is larger in diameter than the main shaft and meshes with the first gear and the second gear, and the ring gear meshes with the first gear. One gear portion and a second gear portion meshing with the second gear are provided adjacent to each other in the swing axis direction.

このように構成される遠心圧縮機では、主軸の周囲を取り囲むように配置される複数の吸込ベーンと、これら吸込ベーンを揺動させるベーン駆動装置とが、羽根車に供給する気体の量を調節する流量調節機構を構成している。そして、ベーン駆動装置によって主軸に対する各吸込ベーンの向きを調節することで、流入路内の流路断面積が調節されて、羽根車に供給する気体の量が調節される。
具体的には、ベーン駆動装置のギア駆動装置によって第２ギアを回転駆動することで、第２ギアに噛み合うリングギアが回転させられる。すると、リングギアに噛み合う各第１ギアが回転させられて、各第１ギアが設けられた各吸込ベーンがそれぞれの揺動軸線回りに揺動し、それぞれの主軸に対する向きが調節されて、流入路内の流路断面積の調節が行われる。 In the centrifugal compressor configured as described above, a plurality of suction vanes arranged so as to surround the periphery of the main shaft and a vane driving device that swings these suction vanes adjust the amount of gas supplied to the impeller. The flow control mechanism is configured. Then, by adjusting the direction of each suction vane with respect to the main shaft by the vane driving device, the flow passage cross-sectional area in the inflow passage is adjusted, and the amount of gas supplied to the impeller is adjusted.
Specifically, the ring gear meshing with the second gear is rotated by rotationally driving the second gear by the gear driving device of the vane driving device. Then, each first gear meshing with the ring gear is rotated, each suction vane provided with each first gear is swung around each swing axis, and the direction with respect to each main shaft is adjusted, and the inflow Adjustment of the cross-sectional area of the channel in the channel is performed.

この遠心圧縮機では、全ての第１ギアが、それぞれリングギアに設けられた第１歯車部に噛み合わされており、各第１ギアは、それぞれリングギアから直接駆動力を伝達される。すなわち、各第１ギアは、リングギアに対して並列に接続されているので、これら各第１ギアには、リングギアから、自身が対応する吸込ベーンを揺動させるのに必要な駆動力のみを伝達すればよい。
このように、この遠心圧縮機では、各第１ギアに加わる負荷が少ないので、第１ギアに要求される強度水準が著しく低くなり、第１ギアの大きさや歯幅を大きくしなくても、十分な耐久性が確保される。 In this centrifugal compressor, all the first gears are respectively meshed with first gear portions provided in the ring gears, and each first gear is directly transmitted with a driving force from the ring gear. That is, since each first gear is connected in parallel to the ring gear, each of the first gears has only a driving force necessary for swinging the suction vane corresponding thereto from the ring gear. Can be transmitted.
Thus, in this centrifugal compressor, since the load applied to each first gear is small, the strength level required for the first gear is remarkably lowered, and even if the size and the tooth width of the first gear are not increased, Sufficient durability is ensured.

また、第１ギアと第２ギアとが、主軸の径方向ではなく、主軸の軸線方向に配列されているので、主軸の径方向における遠心圧縮機の寸法を低減することができる。
さらに、このように第２ギアが第１ギアとは揺動軸線方向の位置をずらして配置されていて、第１ギアとは干渉しないので、その径をリングギアの駆動に適した大きさに設定することができる。このため、歯幅を大きくしなくても、十分な耐久性を確保することができ、主軸の軸線方向における遠心圧縮機の寸法を増大させずに済む。 Moreover, since the first gear and the second gear are arranged not in the radial direction of the main shaft but in the axial direction of the main shaft, the size of the centrifugal compressor in the radial direction of the main shaft can be reduced.
Furthermore, since the second gear is arranged so that the position in the swing axis direction is shifted from the first gear and does not interfere with the first gear, the diameter thereof is set to a size suitable for driving the ring gear. Can be set. For this reason, sufficient durability can be ensured without increasing the tooth width, and the size of the centrifugal compressor in the axial direction of the main shaft does not need to be increased.

本発明にかかる遠心圧縮機では、従来の遠心圧縮機に比べて、大型化することなく、耐久性が著しく向上している。   In the centrifugal compressor according to the present invention, the durability is remarkably improved without increasing the size as compared with the conventional centrifugal compressor.

以下に、本発明にかかる遠心圧縮機の一実施形態について、図面を参照して説明する。
図１は、本実施形態の遠心圧縮機１０の要部を示す側断面図である。
遠心圧縮機１０は、主軸１１と、主軸１１に取り付けられた複数の羽根車１２とを有している。 Hereinafter, an embodiment of a centrifugal compressor according to the present invention will be described with reference to the drawings.
FIG. 1 is a side cross-sectional view showing a main part of a centrifugal compressor 10 of the present embodiment.
The centrifugal compressor 10 includes a main shaft 11 and a plurality of impellers 12 attached to the main shaft 11.

本実施形態の遠心圧縮機１０は、入口壁１６及びダイヤフラム１５と、入口壁１６及びダイヤフラム１５の外側に設けられるケーシング１７とを有する、いわゆるバレル形の一軸多段遠心圧縮機として構成されており、図示しない駆動装置によって主軸１１を介して羽根車１２を回転駆動することで、羽根車１２に供給された気体に遠心力を与えてこの気体を圧縮するものである。   The centrifugal compressor 10 of the present embodiment is configured as a so-called barrel-type single-shaft multistage centrifugal compressor having an inlet wall 16 and a diaphragm 15 and a casing 17 provided outside the inlet wall 16 and the diaphragm 15. By rotating and driving the impeller 12 via the main shaft 11 by a driving device (not shown), centrifugal force is applied to the gas supplied to the impeller 12 to compress the gas.

各羽根車１２は、水平割形または輪切形の複数の部材によって形成された入口壁１６及びダイヤフラム１５の内部に収容される。なお、ダイヤフラム１５は各羽根車１２の間を結ぶ流通路を形成する。また、入口壁１６には、主軸１１の周囲を取り囲んで圧縮対象の気体を主軸１１の径方向外側から径方向内側に案内して、羽根車１２のうち第１段目の圧縮に用いられる羽根車１２に供給する流入路１８が設けられている。   Each impeller 12 is accommodated in an entrance wall 16 and a diaphragm 15 formed by a plurality of members that are horizontally split or ring-shaped. The diaphragm 15 forms a flow path connecting the impellers 12. The inlet wall 16 surrounds the periphery of the main shaft 11 and guides the gas to be compressed from the radially outer side to the radially inner side of the main shaft 11, and the blades used for the first stage compression of the impeller 12. An inflow path 18 for supplying the vehicle 12 is provided.

主軸１１及び羽根車１２が収納される入口壁１６及びダイヤフラム１５の両端にはそれぞれ側蓋１７ｂを設けた構成とされており、入口壁１６、ダイヤフラム１５及び側蓋１７ｂはボルトによって強固に結合される。
ケーシング１７の胴部１７ａには、それぞれ主軸１１と略直交する方向に延びる吸込口１９と吐出口（図示せず）とが設けられており、この吸込口１９を通じて流入路１８に圧縮対象の気体が供給され、吐出口を通じて最後段の羽根車１２によって圧縮された気体が外部に吐出されるようになっている。
各側蓋１７ｂには、ガスシール方式の軸封部２１が設けられると共に、バッファガスを供給するための配管（図示せず）が配設されている。また、各側蓋１７ｂには、主軸１１を支持するジャーナル軸受２２が、軸受ケーシング２３を介して保持されている。さらに、吸込口１９側（図１における左側）に位置する軸受ケーシング２３には、スラスト軸受２４が配置されている。 Both ends of the inlet wall 16 and the diaphragm 15 in which the main shaft 11 and the impeller 12 are accommodated are provided with side lids 17b, and the inlet wall 16, the diaphragm 15 and the side lid 17b are firmly connected by bolts. The
The trunk portion 17 a of the casing 17 is provided with a suction port 19 and a discharge port (not shown) that extend in a direction substantially orthogonal to the main shaft 11, and the gas to be compressed is introduced into the inflow path 18 through the suction port 19. The gas compressed by the last stage impeller 12 is discharged to the outside through the discharge port.
Each side lid 17b is provided with a gas seal type shaft seal portion 21 and a pipe (not shown) for supplying a buffer gas. Further, a journal bearing 22 that supports the main shaft 11 is held on each side lid 17b via a bearing casing 23. Further, a thrust bearing 24 is disposed in the bearing casing 23 located on the suction port 19 side (left side in FIG. 1).

図１及び図２に示すように、吸込口１９と第１段目の圧縮に用いられる羽根車１２の吸込口１２ａとを接続する流入路１８には、複数の案内羽根３１が、それぞれ流入路１８を主軸１１の軸線Ｏ方向に横断するようにして固定的に設けられている。
これら案内羽根３１の下流側には、吸込ベーン３２が、流入路１８を主軸１１の軸線方向に横断するようにしてかつ主軸１１の軸線Ｏに略平行な揺動軸線Ｏ１（図２参照）回りに揺動可能にして設けられている。これら各吸込ベーン３２の揺動軸線Ｏ１回りの向きは、ベーン駆動装置３３によって調整されるようになっている。
本実施形態では、これら案内羽根３１及び吸込ベーン３２は、それぞれ２４体ずつ設けられている。 As shown in FIGS. 1 and 2, a plurality of guide vanes 31 are respectively provided in the inflow path 18 that connects the suction port 19 and the suction port 12 a of the impeller 12 used for the first stage compression. 18 is fixedly provided so as to cross the axis O direction of the main shaft 11.
On the downstream side of these guide vanes 31, a suction vane 32 traverses the inflow path 18 in the axial direction of the main shaft 11 and a swing axis O 1 substantially parallel to the axis O of the main shaft 11 (see FIG. 2). It is provided so that it can swing around. The direction of each suction vane 32 around the swing axis O 1 is adjusted by the vane driving device 33.
In the present embodiment, 24 guide vanes 31 and 24 suction vanes 32 are provided.

図２に示すように、各案内羽根３１及び吸込ベーン３２は、流入路１８内で主軸１１を取り囲む円周上に配設されている。そして、各吸込ベーン３２を、図２に実線で示すように主軸１１の径方向に略直交する向きと、図２に破線で示すように主軸１１の径方向に沿った向きとの間でその向きを調整することで、隣接する吸込ベーン３２間の隙間の大きさが調整されるようになっている。すなわち、この遠心圧縮機１０では、吸込ベーン３２の向きを調整することで、各吸込ベーン３２の間を通過して第１段目の圧縮に用いられる羽根車１２の吸込口１２ａに向かう流体の量が調節されるようになっている。   As shown in FIG. 2, the guide vanes 31 and the suction vanes 32 are arranged on a circumference that surrounds the main shaft 11 in the inflow path 18. Each suction vane 32 is arranged between a direction substantially perpendicular to the radial direction of the main shaft 11 as shown by a solid line in FIG. 2 and a direction along the radial direction of the main shaft 11 as shown by a broken line in FIG. By adjusting the direction, the size of the gap between the adjacent suction vanes 32 is adjusted. That is, in this centrifugal compressor 10, by adjusting the direction of the suction vanes 32, the fluid passing through the suction vanes 32 and flowing toward the suction port 12a of the impeller 12 used for the first-stage compression is stored. The amount is adjusted.

ベーン駆動装置３３は、図１に示すように、各吸込ベーン３２に対して主軸１１と略平行な揺動軸線Ｏ１に沿って設けられる取付軸４１と、各取付軸４１に対してそれぞれ同軸にして設けられる従動ギア４２（第１ギア）と、各従動ギア４２の設置領域に対して揺動軸線Ｏ１方向に隣接して設けられる駆動ギア４３（第２ギア）と、駆動ギア４３を回転駆動するギア駆動装置４４と、主軸１１と同軸にして設けられて従動ギア４２及び駆動ギア４３と噛み合う環状のリングギア４６とを有している。
リングギア４６は、主軸１１よりも大径でかつ各取付軸４１のなす円周よりも小径とされており、その外周面には、各従動ギア４２と噛み合う第１歯車部４７と、駆動ギア４３と噛み合う第２歯車部４８とが、揺動軸線Ｏ１方向に隣接して設けられている。
なお、各ギアが噛み合わせられている領域はグリースで満たされており、これにより、各ギアは滑らかに回転することができるようになっている。 As shown in FIG. 1, the vane drive device 33 has a mounting shaft 41 provided along a swing axis O 1 substantially parallel to the main shaft 11 with respect to each suction vane 32, and is coaxial with each mounting shaft 41. A driven gear 42 (first gear) provided in the above-described manner, a drive gear 43 (second gear) provided adjacent to the installation area of each driven gear 42 in the direction of the swing axis O 1 , and the drive gear 43. A gear drive device 44 that rotates and an annular ring gear 46 that is provided coaxially with the main shaft 11 and meshes with the driven gear 42 and the drive gear 43 are provided.
The ring gear 46 has a larger diameter than the main shaft 11 and a smaller diameter than the circumference formed by each mounting shaft 41, and a first gear portion 47 that meshes with each driven gear 42 and a drive gear on the outer circumferential surface thereof. A second gear portion 48 that meshes with 43 is provided adjacent to the direction of the swing axis O 1 .
In addition, the area | region where each gear is mesh | engaged is satisfy | filled with grease, and, thereby, each gear can rotate smoothly.

このように構成される遠心圧縮機１０では、前記のように、主軸１１の周囲を取り囲むように配置される複数の吸込ベーン３２と、これら吸込ベーン３２を揺動させるベーン駆動装置３３とが、第１段目の圧縮を行う羽根車１２に供給する気体の量を調節する流量調節機構を構成している。そして、ベーン駆動装置３３によって主軸１１に対する各吸込ベーン３２の向きを調節することで、流入路１８内の流路断面積が調節されて、第１段目の圧縮を行う羽根車１２に供給する気体の量が調節される。   In the centrifugal compressor 10 configured as described above, as described above, the plurality of suction vanes 32 disposed so as to surround the periphery of the main shaft 11 and the vane driving device 33 that swings the suction vanes 32 are provided. A flow rate adjusting mechanism for adjusting the amount of gas supplied to the impeller 12 that performs the first stage compression is configured. Then, by adjusting the direction of each suction vane 32 with respect to the main shaft 11 by the vane drive device 33, the flow passage cross-sectional area in the inflow passage 18 is adjusted and supplied to the impeller 12 that performs the first stage compression. The amount of gas is adjusted.

具体的には、ベーン駆動装置３３のギア駆動装置４４によって駆動ギア４３を回転駆動することで、駆動ギア４３に第２歯車部４８で噛み合うリングギア４６が回転させられる。すると、リングギア４６の第１歯車部４７に噛み合う各従動ギア４２が回転させられて、各第１ギア４２と接続された各吸込ベーン３２がそれぞれの揺動軸線Ｏ１回りに揺動し、それぞれの主軸１１に対する向きが調節されて、流入路１８内の流路断面積の調節が行われる。 Specifically, when the drive gear 43 is rotationally driven by the gear drive device 44 of the vane drive device 33, the ring gear 46 meshed with the drive gear 43 by the second gear portion 48 is rotated. Then, each driven gear 42 meshing with the first gear portion 47 of the ring gear 46 is rotated, and each suction vane 32 connected to each first gear 42 swings around the respective swing axis O 1 . The direction with respect to each main shaft 11 is adjusted, and the flow path cross-sectional area in the inflow path 18 is adjusted.

この遠心圧縮機１０では、全ての従動ギア４２が、それぞれリングギア４６に設けられた第１歯車部４７に噛み合わされており、各従動ギア４２は、それぞれリングギア４６から直接駆動力を伝達される。すなわち、各従動ギア４２は、リングギア４６に対して並列に接続されているので、これら各従動ギア４２には、リングギア４６から、自身が対応する吸込ベーン３１を揺動させるのに必要な駆動力のみを伝達すればよい。
このように、この遠心圧縮機１０では、各従動ギア４２に加わる負荷が少ないので、従動ギア４２に要求される強度水準が著しく低くなり、従動ギア４２の大きさや歯幅を大きくしなくても、十分な耐久性が確保される。 In the centrifugal compressor 10, all the driven gears 42 are meshed with the first gear portions 47 provided on the ring gears 46, respectively, and each driven gear 42 receives the driving force directly from the ring gear 46. The That is, since each driven gear 42 is connected in parallel to the ring gear 46, each of the driven gears 42 is necessary for swinging the suction vane 31 corresponding thereto from the ring gear 46. Only the driving force needs to be transmitted.
Thus, in this centrifugal compressor 10, since the load applied to each driven gear 42 is small, the strength level required for the driven gear 42 is remarkably lowered, and the size and tooth width of the driven gear 42 are not increased. Sufficient durability is ensured.

また、従動ギア４２と駆動ギア４３とが、主軸１１の径方向ではなく、主軸１１の軸線Ｏ方向に配列されているので、主軸１１の径方向における遠心圧縮機１０の寸法を低減することができる。
さらに、このように駆動ギア４３が従動ギア４２とは揺動軸線Ｏ１方向の位置をずらして配置されていて、従動ギア４２とは干渉しないので、その径をリングギア４６の駆動に適した大きさに設定することができる。このため、歯幅を大きくしなくても、十分な耐久性を確保することができ、主軸１１の軸線Ｏ方向における遠心圧縮機１０の寸法を増大させずに済む。
このように、本実施形態にかかる遠心圧縮機１０によれば、従来の遠心圧縮機に比べて、大型化することなく、耐久性が著しく向上している。 Further, since the driven gear 42 and the drive gear 43 are arranged not in the radial direction of the main shaft 11 but in the axis O direction of the main shaft 11, the size of the centrifugal compressor 10 in the radial direction of the main shaft 11 can be reduced. it can.
Furthermore, such driving gear 43 has been arranged by shifting the position of the swing axis O 1 direction to the driven gear 42, does not interfere with the driven gear 42, suitable for the diameter to drive the ring gear 46 Can be set to size. Therefore, sufficient durability can be ensured without increasing the tooth width, and the size of the centrifugal compressor 10 in the direction of the axis O of the main shaft 11 does not need to be increased.
Thus, according to the centrifugal compressor 10 concerning this embodiment, durability is remarkably improved, without enlarging compared with the conventional centrifugal compressor.

以上、本発明の遠心圧縮機の各実施形態について詳細に説明してきたが、本発明は上記各実施形態に限定されるものではない。   As mentioned above, although each embodiment of the centrifugal compressor of this invention has been described in detail, this invention is not limited to each said embodiment.

例えば、上記各実施形態においては、円盤状の従動ギア４２を採用し、従動ギア４２の円周全体に歯を設けているが、従動ギア４２は、吸込ベーン３２の揺動軸線Ｏ１回りの可動範囲内で従動ギア４２とリングギア４６とが噛み合う範囲にのみ歯を有する形状（例えば揺動軸線Ｏ１を中心点（要）とする扇形状）としてもよい。これにより、材料費の節約、装置の小型化を図ることができる。 For example, in the above embodiments, a disk-shaped driven gear 42 is adopted, is provided with the teeth on the entire circumference of the driven gear 42, the driven gear 42, the suction vanes 32 swing axis O 1 around the A shape having teeth only in a range in which the driven gear 42 and the ring gear 46 mesh within the movable range (for example, a fan shape having the swing axis O 1 as a center point (required)) may be used. This can save material costs and reduce the size of the device.

本発明の一実施形態にかかる遠心圧縮機の要部を示す側断面図である。It is a sectional side view which shows the principal part of the centrifugal compressor concerning one Embodiment of this invention. 本発明の一実施形態にかかる遠心圧縮機の要部を示す軸直交断面図である。It is an axial orthogonal cross section which shows the principal part of the centrifugal compressor concerning one Embodiment of this invention. 本発明の一実施形態にかかる遠心圧縮機のベーン駆動装置の構成を示す図である。It is a figure which shows the structure of the vane drive device of the centrifugal compressor concerning one Embodiment of this invention.

符号の説明Explanation of symbols

１０ 遠心圧縮機
１１ 主軸
１２ 羽根車
１７ ケーシング
１８ 流入路
３２ 吸込ベーン
３３ ベーン駆動装置
４２ 従動ギア（第１ギア）
４３ 駆動ギア（第２ギア）
４４ ギア駆動装置
４６ リングギア
４７ 第１歯車部
４８ 第２歯車部
Ｏ 主軸の軸線
Ｏ１ 揺動軸線 DESCRIPTION OF SYMBOLS 10 Centrifugal compressor 11 Main axis | shaft 12 Impeller 17 Casing 18 Inflow path 32 Suction vane 33 Vane drive device 42 Driven gear (1st gear)
43 Drive gear (second gear)
44 Gear drive 46 Ring gear 47 First gear part 48 Second gear part O Spindle axis O 1 Oscillation axis

Claims (1)

主軸と、該主軸に取り付けられた羽根車と、前記主軸及び前記羽根車を収容するケーシングとを有し、該ケーシングが、前記主軸の周囲を取り囲んで圧縮対象の気体を前記主軸の径方向外側から径方向内側に案内して前記羽根車に供給する流入路を有しており、前記主軸を介して前記羽根車を回転駆動することで前記羽根車に供給された気体に遠心力を与えて該気体を圧縮する遠心圧縮機であって、
前記流入路内に前記主軸の周囲を取り囲むように複数配置されてそれぞれ前記主軸の軸線に平行な揺動軸線回りに揺動可能な吸込ベーンと、
該各吸込ベーンを前記揺動軸線回りに揺動させるベーン駆動装置とを有し、
該ベーン駆動装置は、前記各吸込ベーンのそれぞれに対して前記揺動軸線と同軸にして設けられた第１ギアと、
該各第１ギアの設置領域に対して前記揺動軸線方向に隣接して設けられる第２ギアと、
該第２ギアを回転駆動するギア駆動装置と、
前記主軸よりも大径で該主軸と同軸にして設けられて前記第１ギア及び前記第２ギアと噛み合う環状のリングギアとを有しており、
該リングギアには、前記各第１ギアと噛み合う第１歯車部と、前記第２ギアと噛み合う第２歯車部とが、前記揺動軸線方向に隣接して設けられている遠心圧縮機。 A main shaft, an impeller attached to the main shaft, and a casing that houses the main shaft and the impeller, and the casing surrounds the periphery of the main shaft so that gas to be compressed is radially outward of the main shaft. An inflow passage that is guided radially inward from the blade and supplied to the impeller, and the centrifugal force is applied to the gas supplied to the impeller by rotationally driving the impeller through the main shaft. A centrifugal compressor for compressing the gas,
A plurality of suction vanes that are arranged in the inflow path so as to surround the periphery of the main shaft and can swing about a swing axis parallel to the axis of the main shaft;
A vane drive device that swings each suction vane around the swing axis,
The vane driving device includes a first gear provided coaxially with the swing axis for each of the suction vanes,
A second gear provided adjacent to the installation region of each first gear in the swing axis direction;
A gear driving device for rotationally driving the second gear;
An annular ring gear which is larger in diameter than the main shaft and is provided coaxially with the main shaft and meshes with the first gear and the second gear;
The centrifugal compressor is provided with a first gear portion that meshes with each of the first gears and a second gear portion that meshes with the second gear, adjacent to each other in the swing axis direction.
JP2005051278A 2005-02-25 2005-02-25 Centrifugal compressor Expired - Fee Related JP4746330B2 (en)

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JP2009062965A (en) * 2007-09-10 2009-03-26 Hitachi Plant Technologies Ltd Centrifugal compressor
JP2009174458A (en) * 2008-01-25 2009-08-06 Hitachi Plant Technologies Ltd Centrifugal compressor
JP2010285927A (en) * 2009-06-11 2010-12-24 Hitachi Plant Technologies Ltd Centrifugal compressor
EP2947327A1 (en) * 2012-02-27 2015-11-25 Mitsubishi Heavy Industries Compressor Corporation Rotary machine
EP2402618A4 (en) * 2009-02-27 2018-01-31 Mitsubishi Heavy Industries, Ltd. Suction casing and fluid machine

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JP2001295795A (en) * 2000-04-13 2001-10-26 Mitsubishi Heavy Ind Ltd Centrifugal compressor

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JPH0382899U (en) * 1989-12-07 1991-08-23
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Publication number Priority date Publication date Assignee Title
JP2009062965A (en) * 2007-09-10 2009-03-26 Hitachi Plant Technologies Ltd Centrifugal compressor
JP2009174458A (en) * 2008-01-25 2009-08-06 Hitachi Plant Technologies Ltd Centrifugal compressor
EP2402618A4 (en) * 2009-02-27 2018-01-31 Mitsubishi Heavy Industries, Ltd. Suction casing and fluid machine
JP2010285927A (en) * 2009-06-11 2010-12-24 Hitachi Plant Technologies Ltd Centrifugal compressor
EP2947327A1 (en) * 2012-02-27 2015-11-25 Mitsubishi Heavy Industries Compressor Corporation Rotary machine
EP2821651A4 (en) * 2012-02-27 2015-11-25 Mitsubishi Heavy Ind Compressor Corp Rotary machine
US9835161B2 (en) 2012-02-27 2017-12-05 Mitsubishi Heavy Industries Compressor Corporation Rotary machine
EP2821651B1 (en) 2012-02-27 2018-10-17 Mitsubishi Heavy Industries Compressor Corporation Rotary machine
US10119546B2 (en) 2012-02-27 2018-11-06 Mitsubishi Heavy Industries Compressor Corporation Rotary machine

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