JP2005194933A - Centrifugal compressor - Google Patents

Centrifugal compressor Download PDF

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JP2005194933A
JP2005194933A JP2004001732A JP2004001732A JP2005194933A JP 2005194933 A JP2005194933 A JP 2005194933A JP 2004001732 A JP2004001732 A JP 2004001732A JP 2004001732 A JP2004001732 A JP 2004001732A JP 2005194933 A JP2005194933 A JP 2005194933A
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diffuser
passage width
gas
centrifugal compressor
scrolls
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JP4466080B2 (en
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Akihiro Yamagata
章弘 山方
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IHI Corp
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IHI Corp
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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
    • F04D29/464—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps adjusting flow cross-section, otherwise than by using adjustable stator blades
    • 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
    • F05D2250/52—Outlet

Abstract

<P>PROBLEM TO BE SOLVED: To provide high compression efficiency for a wide flow range with simple structure compared with the prior art. <P>SOLUTION: A centrifugal compressor comprises: an impeller 1 accelerating gas by its rotation; a diffuser 2 that is a channel through which the gas supplied from the impeller 1 flows, for converting kinetic energy of the gas into pressure; a pair of scrolls 3A, 3B that are channels communicating with the diffuser 2, for collecting the gas output from the diffuser 2 and outputting the gas to the outside; and a passageway width changing means for variably setting the passageway width, so that the passageway width becomes narrow for making the diffuser 2 communicate with only one scroll 3A, or so that the passageway width becomes wide for making the diffuser 2 communicate with both of the scrolls 3A, 3B. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

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

例えば、特開平１１−０３０１９９号公報には、広い流量範囲に亘る圧縮効率の向上を目的とした遠心圧縮機が開示されている。この遠心圧縮機は、ディフューザの通路幅とスクロールの断面積とを独立して可変することにより、ディフューザの通路幅の変化に合わせてスクロールの断面積が変化させることが可能であり、よってディフューザとスクロールとの最適なマッチング状態を実現することができるので広い流量範囲に亘る高圧縮効率を実現するものである。
特開平１１−０３０１９９号公報 For example, Japanese Patent Application Laid-Open No. 11-030199 discloses a centrifugal compressor for the purpose of improving compression efficiency over a wide flow rate range. In this centrifugal compressor, the cross-sectional area of the scroll can be changed in accordance with the change in the passage width of the diffuser by independently varying the passage width of the diffuser and the cross-sectional area of the scroll. Since an optimum matching state with the scroll can be realized, high compression efficiency over a wide flow rate range is realized.
Japanese Patent Laid-Open No. 11-030199

ところで、上記従来技術ではディフューザの通路幅とスクロールの断面積とを独立して可変するため、機械的構成や制御構成や複雑であり、よって実用的ではない。したがって、より簡単な構成で広い流量範囲に亘る高圧縮効率を実現するための技術の開発が待望されていた。   By the way, in the above prior art, the passage width of the diffuser and the cross-sectional area of the scroll are independently variable, so that the mechanical configuration, the control configuration, and the complexity are complicated, and therefore not practical. Therefore, development of a technique for realizing high compression efficiency over a wide flow rate range with a simpler configuration has been awaited.

本発明は、従来よりも簡単な構成で広い流量範囲に亘る高圧縮効率を実現することを目的とするものである。   An object of the present invention is to realize high compression efficiency over a wide flow rate range with a simpler configuration than the conventional one.

上記目的を達成するために、本発明では、回転によって気体を加速するインペラと、該インペラから供給された気体が通過する流路であって、気体の運動エネルギーを圧力に変換するディフューザと、該ディフューザに連通する流路であって、ディフューザから出力された気体を収集して外部に出力する一対のスクロールとを備え、ディフューザを一方のスクロールのみに連通させるようにディフューザの通路幅を幅狭状態に、あるいはディフューザを両方のスクロールに連通させるようにディフューザの通路幅を幅広状態に可変設定する通路幅可変手段を具備する、という解決手段を採用する。   In order to achieve the above object, in the present invention, an impeller that accelerates gas by rotation, a flow path through which the gas supplied from the impeller passes, and a diffuser that converts kinetic energy of the gas into pressure, A flow path that communicates with the diffuser, and has a pair of scrolls that collect the gas output from the diffuser and output it to the outside, and the diffuser passage width is narrow so that the diffuser communicates with only one of the scrolls Alternatively, a solution means is provided which includes a passage width varying means for variably setting the diffuser passage width in a wide state so that the diffuser communicates with both scrolls.

本発明によれば、ディフューザの通路幅が幅狭状態に設定された場合はディフューザは一方のスクロールのみに連通する一方、ディフューザの通路幅が幅広状態に設定された場合にはディフューザは両方のスクロールに連通する。つまり、ディフューザの通路幅を幅広状態とし、かつ２つのスクロールを利用する動作状態（第１動作モード）とディフューザの通路幅を幅狭状態とし、かつ１つのスクロールを利用する動作状態（第２動作モード）とが選択的に設定される。すなわち、本発明では、通路幅を幅狭状態と幅広状態とに切り替えることによって第１動作モードと第２動作モードとを２者択一的に設定することが可能であり、したがって簡単な構成で実質的に広い流量範囲に亘って高圧縮効率を実現することができる。   According to the present invention, when the diffuser passage width is set to a narrow state, the diffuser communicates with only one scroll, while when the diffuser passage width is set to a wide state, the diffuser Communicate with. That is, an operation state in which the diffuser passage width is in a wide state and two scrolls are used (first operation mode) and an operation state in which the diffuser passage width is in a narrow state and one scroll is used (second operation) Mode) is selectively set. In other words, in the present invention, the first operation mode and the second operation mode can be set alternatively by switching the passage width between the narrow state and the wide state, and therefore, with a simple configuration. High compression efficiency can be achieved over a substantially wide flow range.

以下、図面を参照して、本発明の一実施形態について説明する。
図１は、本実施形態に係る遠心圧縮機の要部断面図である。図１（ａ）は本遠心圧縮機の第１動作モードの設定状態を示し、図１（ｂ）は本遠心圧縮機の第２動作モードの設定状態を示している。また、これら各図において、符号１はインペラ、２はディフューザ、３Ａ，３Ｂはスクロール、４はディフューザプレート（可動プレート）、５はバネ（弾性材）、６は圧縮空気供給源、またＤ1，Ｄ2はディフューザ２の通路幅である。これら各構成要素のうち、ディフューザプレート４、バネ５及び圧縮空気供給源６は、本実施形態における通路幅可変手段を構成している。 Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a cross-sectional view of a main part of a centrifugal compressor according to this embodiment. FIG. 1A shows the setting state of the first operation mode of the centrifugal compressor, and FIG. 1B shows the setting state of the second operation mode of the centrifugal compressor. In these figures, reference numeral 1 is an impeller, 2 is a diffuser, 3A and 3B are scrolls, 4 is a diffuser plate (movable plate), 5 is a spring (elastic material), 6 is a compressed air supply source, and D1 and D2 Is the passage width of the diffuser 2. Among these components, the diffuser plate 4, the spring 5, and the compressed air supply source 6 constitute a passage width varying means in this embodiment.

インペラ１は、軸Ｌを回転中心として回転自在に支持されており、回転することによって回転軸方向（図面右側）から吸い込んだ空気を加速させてディフューザ２に送り込む。ディフューザ２は、図示するようにインペラ１の回転半径方向に設けられた流路であり、上記インペラ１から回転半径方向に吹き出された空気が通過する。このディフューザ２は、周知のようにインペラ１から供給された空気の運動エネルギーを圧力に変換する機能を有する。ここで、第１動作モードの場合、ディフューザ２の通路幅Ｄ1は、図１（ａ）に示すように幅広状態に設定され、一方、第２動作モードの場合には、ディフューザ２の通路幅Ｄ2は、図１（ｂ）に示すように幅狭状態に設定される。   The impeller 1 is supported so as to be rotatable about the axis L as a center of rotation, and the air sucked from the direction of the rotation axis (right side of the drawing) is accelerated and sent to the diffuser 2 by rotating. The diffuser 2 is a flow path provided in the rotational radius direction of the impeller 1 as illustrated, and the air blown out from the impeller 1 in the rotational radius direction passes therethrough. The diffuser 2 has a function of converting the kinetic energy of air supplied from the impeller 1 into pressure as is well known. Here, in the first operation mode, the passage width D1 of the diffuser 2 is set to a wide state as shown in FIG. 1A, whereas in the second operation mode, the passage width D2 of the diffuser 2 is set. Is set in a narrow state as shown in FIG.

一般的な遠心圧縮機ではスクロールが１つだけ設けられるが、本遠心圧縮機は、特徴的な構成として一対のスクロール３Ａ，３Ｂを備えている。これらスクロール３Ａ，３Ｂは、ディフューザ２の外周に周回状に設けられると共にディフューザ２に連通した流路である。各スクロール３Ａ，３Ｂは、ディフューザ２から排出された空気（圧縮空気）を収集して圧縮空気として外部に出力する。本遠心圧縮機では、第１動作モードの場合、通路幅Ｄ1が幅広状態に設定されたディフューザ２から両方のスクロール３Ａ，３Ｂに空気が供給される一方、第２動作モードの場合には、通路幅Ｄ2が幅狭状態に設定されたディフューザ２から一方のスクロール３Ａのみに空気が供給される。   In a general centrifugal compressor, only one scroll is provided, but this centrifugal compressor includes a pair of scrolls 3A and 3B as a characteristic configuration. These scrolls 3 </ b> A and 3 </ b> B are flow paths that are provided around the outer periphery of the diffuser 2 and communicate with the diffuser 2. Each of the scrolls 3A and 3B collects air (compressed air) discharged from the diffuser 2 and outputs it as compressed air to the outside. In the present centrifugal compressor, air is supplied to both scrolls 3A and 3B from the diffuser 2 in which the passage width D1 is set to the wide state in the first operation mode, while in the second operation mode, the passage is provided. Air is supplied only to one scroll 3A from the diffuser 2 in which the width D2 is set to a narrow state.

続いて、通路幅可変手段の構成について説明する。ディフューザプレート４は、可動自在に支持された部材であり、その表面４ａは、図示するようにディフューザ２の一面（右側面）を構成している。このディフューザプレート４がディフューザ２の他面（左側面）から最も離間した状態つまりディフューザ２に対して最も後退した状態が第１動作モードの設定状態であり、一方、ディフューザプレート４がディフューザ２の他面（左側面）に最も接近した状態つまりディフューザ２に対して最も前進した状態が第２動作モードの設定状態である。   Subsequently, the configuration of the passage width varying means will be described. The diffuser plate 4 is a member that is movably supported, and its surface 4a constitutes one surface (right side surface) of the diffuser 2 as shown. The state in which the diffuser plate 4 is farthest from the other surface (left side surface) of the diffuser 2, that is, the state in which the diffuser plate 4 is most retracted with respect to the diffuser 2 is the setting state of the first operation mode. The state closest to the surface (left side), that is, the state most advanced with respect to the diffuser 2 is the setting state of the second operation mode.

バネ５は、図１（ａ）に示すように、ディフューザプレート４がディフューザ２に対して最も後退した状態となるようにディフューザプレート４を付制する。これに対して、圧縮空気供給源６は、圧縮空気を供給することによってディフューザプレート４がディフューザ２に対して最も前進した状態となるようにディフューザプレート４を後方から押圧する。すなわち、本遠心圧縮機は、圧縮空気供給源６の圧縮空気の供給をＯＮ／ＯＦＦすることによって第２動作モードと第１動作モードとが二者択一的に設定される。   As shown in FIG. 1A, the spring 5 urges the diffuser plate 4 so that the diffuser plate 4 is in the most retracted state with respect to the diffuser 2. On the other hand, the compressed air supply source 6 presses the diffuser plate 4 from behind so that the diffuser plate 4 is most advanced with respect to the diffuser 2 by supplying compressed air. That is, in the centrifugal compressor, the second operation mode and the first operation mode are alternatively set by turning ON / OFF the supply of compressed air from the compressed air supply source 6.

次に、このように構成された本遠心圧縮機の作用効果について図２を参照して説明する。図２は、第１動作モードの動作特性Ｘと第２動作モードの動作特性Ｙとを示している。第１動作モードの場合、動作特性Ｘに示すようにスクロール３Ａ，３Ｂから外部に出力される圧縮空気の圧力は比較的大きな流量範囲で最大となるが、第２動作モードの場合には、動作特性Ｙに示すようにスクロール３Ａから外部に出力される圧縮空気の圧力は第１動作モードの場合よりも小さな流量範囲で最大となる。   Next, the function and effect of the centrifugal compressor thus configured will be described with reference to FIG. FIG. 2 shows the operation characteristic X in the first operation mode and the operation characteristic Y in the second operation mode. In the first operation mode, as shown in the operation characteristic X, the pressure of the compressed air output to the outside from the scrolls 3A and 3B becomes the maximum in a relatively large flow rate range. As shown by the characteristic Y, the pressure of the compressed air output to the outside from the scroll 3A becomes maximum in a smaller flow rate range than in the first operation mode.

したがって、本遠心圧縮機によれば、２つのスクロール３Ａ，３Ｂを設けると共にディフューザプレート４を前進／後退させて第１動作モードと第２動作モードとを２者択一的に選択設定することによって、つまり比較的簡単な構成によって実質的に広い流量範囲に亘って高圧縮効率を実現することができる。例えば、動作域が比較的大流量の場合は第１動作モードで運転することによって高い圧力を得ることが可能であり、一方、動作域が比較的小流量の場合には、第１動作モードから第２動作モードに切り替えて運転することによって高い圧力を得ることが可能である。   Therefore, according to this centrifugal compressor, by providing the two scrolls 3A and 3B and moving the diffuser plate 4 forward / backward, the first operation mode and the second operation mode can be selected and set alternatively. In other words, high compression efficiency can be realized over a substantially wide flow rate range with a relatively simple configuration. For example, when the operating range is a relatively large flow rate, it is possible to obtain a high pressure by operating in the first operating mode. On the other hand, when the operating range is a relatively small flow rate, from the first operating mode, It is possible to obtain a high pressure by switching to the second operation mode and operating.

なお、本発明は、上記実施形態に限定されるものではなく、例えば以下のような変形が考えられる。すなわち、上記実施形態では、通路幅可変手段をディフューザプレート４、バネ５及び圧縮空気供給源６から構成したが、通路幅可変手段の構成はこれに限定されるものではない。圧縮空気供給源６に代えて例えばシリンダーを用いてディフューザプレート４を前進させることによって第２動作モードを実現するようにしても良い。   In addition, this invention is not limited to the said embodiment, For example, the following modifications can be considered. That is, in the above embodiment, the passage width varying means is constituted by the diffuser plate 4, the spring 5, and the compressed air supply source 6. However, the configuration of the passage width varying means is not limited to this. The second operation mode may be realized by moving the diffuser plate 4 forward using, for example, a cylinder instead of the compressed air supply source 6.

本発明の一実施形態に係わる遠心圧縮機の要部断面図である。It is principal part sectional drawing of the centrifugal compressor concerning one Embodiment of this invention. 本発明の一実施形態に係わる遠心圧縮機の動作特性を示すグラフである。It is a graph which shows the operating characteristic of the centrifugal compressor concerning one Embodiment of this invention.

符号の説明Explanation of symbols

１…インペラ、２…ディフューザ、３Ａ，３Ｂ…スクロール、４…ディフューザプレート（可動プレート）、５…バネ（弾性材）、６…圧縮空気供給源、Ｄ1，Ｄ2…ディフューザの通路幅

DESCRIPTION OF SYMBOLS 1 ... Impeller, 2 ... Diffuser, 3A, 3B ... Scroll, 4 ... Diffuser plate (movable plate), 5 ... Spring (elastic material), 6 ... Compressed air supply source, D1, D2 ... Passage width of diffuser

Claims (2)

回転によって気体を加速するインペラと、
該インペラから供給された気体が通過する流路であって、気体の運動エネルギーを圧力に変換するディフューザと、
該ディフューザに連通する流路であって、ディフューザから出力された気体を収集して外部に出力する一対のスクロールとを備え、
前記ディフューザを一方のスクロールのみに連通させるようにディフューザの通路幅を幅狭状態に、あるいは前記ディフューザを両方のスクロールに連通させるようにディフューザの通路幅を幅広状態に、可変設定する通路幅可変手段を具備することを特徴とする遠心圧縮機。 An impeller that accelerates the gas by rotation;
A flow path through which a gas supplied from the impeller passes, and a diffuser that converts the kinetic energy of the gas into pressure;
A flow path communicating with the diffuser, comprising a pair of scrolls for collecting and outputting the gas output from the diffuser to the outside;
A passage width variable means for variably setting the diffuser passage width in a narrow state so that the diffuser communicates with only one scroll, or the diffuser passage width in a wide state so that the diffuser communicates with both scrolls. A centrifugal compressor characterized by comprising: 通路幅可変手段は、
ディフューザの一面を構成すると共に可動自在に支持された可動プレートと、
ディフューザの通路幅が幅広状態となるように前記可動プレートをディフューザに対して後退するように付制する弾性材と、
ディフューザの通路幅が幅狭状態となるように前記可動プレートをディフューザに対して前進するように押圧する圧縮空気供給源と
を具備することを特徴とする請求項1記載の遠心圧縮機。
The passage width variable means is
A movable plate that constitutes one surface of the diffuser and is movably supported;
An elastic material for restraining the movable plate to retreat with respect to the diffuser so that the passage width of the diffuser is wide;
2. The centrifugal compressor according to claim 1, further comprising: a compressed air supply source that presses the movable plate so as to move forward with respect to the diffuser so that a passage width of the diffuser is in a narrow state.
JP2004001732A 2004-01-07 2004-01-07 Centrifugal compressor Expired - Fee Related JP4466080B2 (en)

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WO2008129953A1 (en) * 2007-04-20 2008-10-30 Mitsubishi Heavy Industries, Ltd. Centrifugal compressor
JP2010065669A (en) * 2008-09-12 2010-03-25 Mitsubishi Heavy Ind Ltd Centrifugal compressor
JP2010071241A (en) * 2008-09-19 2010-04-02 Mitsubishi Heavy Ind Ltd Centrifugal compressor
WO2011114487A1 (en) * 2010-03-18 2011-09-22 トヨタ自動車株式会社 Centrifugal compressor and turbo supercharger
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WO2006115197A1 (en) * 2005-04-21 2006-11-02 Daikin Industries, Ltd. Blower device
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EP1930602A2 (en) 2006-12-07 2008-06-11 Kabushiki Kaisha Toyota Jidoshokki Centrifugal compressor
WO2008129953A1 (en) * 2007-04-20 2008-10-30 Mitsubishi Heavy Industries, Ltd. Centrifugal compressor
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