WO2011099417A1 - 非対称自己循環ケーシングトリートメントを有する遠心圧縮機 - Google Patents
非対称自己循環ケーシングトリートメントを有する遠心圧縮機 Download PDFInfo
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- WO2011099417A1 WO2011099417A1 PCT/JP2011/052272 JP2011052272W WO2011099417A1 WO 2011099417 A1 WO2011099417 A1 WO 2011099417A1 JP 2011052272 W JP2011052272 W JP 2011052272W WO 2011099417 A1 WO2011099417 A1 WO 2011099417A1
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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
- F04D29/4206—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
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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
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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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
- F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
- F04D29/685—Inducing localised fluid recirculation in the stator-rotor interface
Definitions
- the present invention relates to a centrifugal compressor having an asymmetric self-circulating casing treatment.
- Centrifugal compressors are used in various types of turbomachines such as superchargers for vehicles and ships, industrial compressors, and aero engines.
- a turbo compressor using a centrifugal compressor has advantages such as high efficiency, light weight, and stable operation over a reciprocating compressor, but its allowable operating range (ie, centrifugal compression).
- the flow range of the machine is limited.
- an unstable phenomenon such as a large fluid separation occurs in the internal flow field, resulting in stalling and thus surge.
- the efficiency and pressure ratio of the compressor are rapidly reduced, the life is shortened, and as a result, the compressor is damaged in a short time. Therefore, by adopting various measures, instability phenomena such as the stall of the compressor are suppressed, and the stable operation range is expanded.
- a casing treatment for a centrifugal compressor is used to expand the stable operating range.
- Casing treatments are disclosed in Patent Documents 1 to 5, for example.
- Patent No. 3001902 JP 2007-127109 A Japanese Patent No. 4100030 Japanese Patent No. 4107823 US Pat. No. 4,930,979
- casing treatment is currently considered to be an effective means for expanding the stable operating range of a centrifugal compressor.
- the conventional casing treatment is configured to be axisymmetric with respect to the rotation axis of the impeller.
- a casing treatment that is axisymmetric with respect to the rotation axis is referred to as “axisymmetric casing treatment”
- a casing treatment that is asymmetric with respect to the rotation axis is referred to as “asymmetric casing treatment”.
- the scroll flow path of the casing is asymmetrically configured with respect to the rotation axis of the impeller. Circumferential distortion occurs in the flow of the compressor, affecting the upstream flow parameter, and the circumferential flow parameter inside the compressor impeller and vaneless diffuser exhibits asymmetry.
- the configuration of the conventional axisymmetric casing treatment does not take into account the characteristics of the asymmetry of the flow field inside the compressor, so the effect of expanding the stable operation range by the casing treatment cannot be achieved in the entire circumferential direction. Therefore, it is necessary to employ an asymmetric self-circulating casing treatment in order to realize the effect of expanding the optimum stable operation range in the entire circumferential direction.
- FIG. 1A is a half sectional view of a centrifugal compressor having a self-circulating casing treatment
- FIG. 1B is an explanatory view of the self-circulating casing treatment.
- the impeller 13 has an impeller full blade 11 and an impeller half blade 12.
- ZZ is the center of rotation of the impeller 13.
- the self-circulating casing treatment generally includes a suction ring groove 1, a ring guide path 2, and a return ring groove 3.
- the main configuration parameters of the self-circulation casing treatment is the axial distance S r relative to the suction ring groove 1 of the impeller all the blade leading edge 4, the width b r of the suction ring groove, reflux ring groove 3 of the impeller all the blade leading edge 4 the axial distance S f for the width b f of reflux ring groove, and the depth h b reflux ring groove, the width b b etc. of the ring guideway 2.
- an object of the present invention is to optimize the circumferential distribution of the axial distance S r or the width b r of the suction ring groove with respect to the leading edge of the impeller blades, thereby reducing the stable operating range while maintaining efficiency. It is to provide a centrifugal compressor having an asymmetric self-circulating casing treatment that can be expanded to the side.
- the present invention includes a suction ring groove (1), a ring guide path (2), and a return ring groove (3) on the inner peripheral surface of a casing, and a centrifugal having an asymmetric self-circulation casing treatment that forms a self-circulation flow path.
- the axial distance S r of the upstream end face of the suction ring groove with respect to the impeller blade front edge (4) or the width b r of the suction ring groove is represented by A ( ⁇ ⁇ D ⁇ ⁇ D) 2 + A 0 , Distributed in a parabolic shape in the circumferential direction,
- the range of the initial phase angle ⁇ 0 is 0 ⁇ ⁇ 0 ⁇ 2 ⁇
- the domain of the circumferential angle ⁇ of the casing is ⁇ 0 ⁇ ⁇ ⁇ ⁇ 0 + 2 ⁇
- A is a parabola parameter at the axial distance S r or the width b r
- a 0 is the extreme value of the axial distance S r or the width b r when the corresponding circumferential angle ⁇ is equal to the ⁇ at the extreme point of the parabola distribution. .
- the ratio between the A and the impeller diameter D in the axial distance S r is, 0.005 / D ⁇
- the ratio between the extreme value A 0 of the axial distance S r and the impeller diameter D is in the range of 0.01 ⁇
- the ratio between the A and the impeller diameter D in the width b r is, 0.005 / D ⁇
- the ratio between the extreme value A 0 of the width b r and the impeller diameter D is in the range of 0.01 ⁇
- the casing comprises an outer shell (5) and a core (6),
- the suction ring groove (1) is provided on the wall surface of the core (6), and the inner wall surface of the outer shell and the outer wall surface of the core form the ring guide path (2) and the return ring groove (3). .
- the present invention adopts an asymmetric self-circulating casing treatment in which the position or width of the suction ring groove is distributed in a parabolic shape, so that the stable operating range of the centrifugal compressor is higher than that of an axially symmetric self-circulating casing treatment. It has been confirmed in the examples described later that the efficiency can be maintained so that the efficiency is basically unchanged.
- FIG. 3 is a half cross-sectional view of a centrifugal compressor having a self-circulating casing treatment. It is explanatory drawing of a self-circulation casing treatment. It is a front schematic diagram of the outer shell of a casing. It is a half cross-sectional schematic diagram of the outer shell of a casing. It is a schematic diagram of the casing of a compressor. It is a structure schematic diagram of the core of a casing. It is a schematic diagram of the suction ring groove in the core. It is a position schematic diagram of initial phase angle theta 0 in an example. It is a distribution schematic axial distance S r of the suction ring groove corresponding to different initial phase angle theta 0.
- FIG. 4 is a relationship diagram between normalized mass flow rate and efficiency in Example 1.
- It is a schematic diagram of the casing of a compressor. It is a structure schematic diagram of the core of a casing. It is a schematic diagram of the suction ring groove in the core. It is a distribution schematic diagram of the width b r of the suction ring groove corresponding to different initial phase angles ⁇ 0 .
- It is a related figure of the normalized mass flow rate in Example 2, and a pressure ratio. It is a related figure of the normalized mass flow rate in Example 2, and efficiency.
- FIG. 2A, 2B, and 3 to 5 are schematic views showing the first embodiment of the present invention.
- FIG. 2A is a schematic front view of the outer shell 5 of the casing
- FIG. 2B is a schematic cross-sectional view
- FIG. 4 is a schematic diagram of the casing
- FIG. 4 is a schematic diagram of the configuration of the core 6 of the casing
- FIG. 5 is a schematic diagram of the suction ring groove in the core.
- the centrifugal compressor according to the present invention has a suction ring groove 1, a ring guide path 2, and a return ring groove 3 on the inner peripheral surface of the casing to form a self-circulation flow path.
- the self-circulation flow path is a return path for returning fluid from a position downstream of the impeller blade front edge to an upstream position of the impeller blade front edge by the suction ring groove 1, the ring guide path 2, and the return ring groove 3. means.
- the casing 10 of the centrifugal compressor of the first embodiment includes an outer shell 5 and a core 6, and the suction ring groove 1 is provided on the wall surface of the core 6.
- the inner wall surface and the outer wall surface of the core 6 form the ring guide path 2 and the reflux ring groove 3.
- Asymmetric self circulation casing treatment of the first embodiment the position of the suction ring groove 1, i.e. against the impeller total blade leading edge 4, the axial distance S r of the upstream end surface 1a of the suction ring groove 1, parabolic in the circumferential direction Is distributed.
- the axial distance S r is expressed by Equation (1).
- S r A ( ⁇ ⁇ D ⁇ ⁇ D) 2 + A 0 (1)
- the ratio between the characteristic parameter A of the parabola and the impeller diameter D is in the range of 0.005 / D ⁇
- the position of the suction ring groove 1 in accordance with the designed parabolic distribution is a curve on the circumferential cylindrical surface of the core 6 and is indicated by a one-dot chain line in FIG.
- the outer shell 5 of the casing is fixed, and the core 6 is rotated around the rotation axis center ZZ of the impeller 13 (see FIG. 1).
- a parabolic distribution of the position (axial distance S r ) of the suction ring groove 1 corresponding to a different initial phase angle ⁇ 0 is obtained. That is, the outer shell 5 and the core 6 of the casing 10 are connected by the screw 7.
- n (four in this example) screw holes are evenly arranged in the circumferential direction, and the axial distance S r corresponding to n different initial phase angles ⁇ 0 is set. A distribution curve is obtained.
- the optimum initial phase angle ⁇ 0 is determined from n different initial phase angles ⁇ 0 by compressor performance tests.
- FIG. 6 is a schematic diagram of the position of the initial phase angle ⁇ 0 in the embodiment
- FIG. 7 is a schematic diagram of the distribution of Sr values of the suction ring grooves corresponding to different initial phase angles ⁇ 0 . 2A and 2B, since a total of four screw holes are provided in the outer shell 5 of the casing 10, the parabolic distribution of the axial distance Sr of the four different suction ring grooves 1 shown in FIG. can get.
- FIG. 7 is a distribution schematic diagram of the axial distance S r of the suction ring groove 1 corresponding to different initial phase angles ⁇ 0 .
- the solid line is a parabolic distribution in the circumferential direction of the axial distance S r of the suction ring groove 1, and there are various expression formats based on changing the selection of the initial phase angle ⁇ 0 in the circumferential direction.
- ⁇ 0 is an initial phase angle
- the casing 10 is a circle of one circumference of 0 ⁇ ⁇ 0 ⁇ 2 ⁇ (0 ° ⁇ ⁇ 0 ⁇ 360 °)
- the defined range of the circumferential angle ⁇ of the casing Is ⁇ 0 ⁇ ⁇ ⁇ ⁇ 0 + 2 ⁇ ( ⁇ 0 ⁇ ⁇ ⁇ ⁇ 0 + 360 °).
- air in the flow path of the self-circulating casing treatment flows in from the suction ring groove 1 and flows out through the ring guide path 2 and the reflux ring groove 3.
- the specific operation principle is that the suction ring groove 1 of the self-circulating casing treatment sucks the gas in the impeller blade tip region and releases the gas from the return ring groove 3 through the ring guide path 2.
- the air in the flow path of the self-circulating casing treatment is discharged from the suction ring groove 1 through the reflux ring groove 3 and the ring guide path 2.
- the reflux ring groove 3 communicates the flow in the circumferential direction of the inlet, thereby increasing the uniformity of the flow at the compressor inlet, weakening the shock wave at the inlet, and the discharge flow of the suction ring groove 1 enhances the circulation capacity. By doing so, the occlusion boundary was expanded. However, due to the lack of suction power in the mode of operation close to blockage, the expansion of the casing treatment to the blockage boundary is less noticeable than the expansion to the stall boundary.
- the following is an example of expanding the stable operating range by adopting an asymmetric self-circulating casing treatment of a centrifugal compressor with a parabolic distribution in the groove position for a centrifugal compressor of a certain size.
- FIG. 8A is a graph showing the relationship between the normalized mass flow rate and the pressure ratio in Example 1.
- FIG. 8B is a relationship diagram between normalized mass flow rate and efficiency in Example 1.
- 8A and 8B show an asymmetric self-circulating casing treatment ("asymmetric self-circulating CT") with a parabolic distribution of groove positions, an axisymmetric self-circulating casing treatment (“axisymmetric self-circulating CT”), and a casing treatment. It is a performance comparison figure of the compressor when there is no (“No CT”).
- asymmetric self-circulating casing treatment asymmetric self-circulating CT
- the stable operating range of the compressor can be expanded to the low flow rate side, and the efficiency can be basically kept unchanged. It was confirmed that it was possible.
- FIG. 9 to 11 are schematic views showing a second embodiment of the present invention.
- FIG. 9 is a schematic view of the casing 10 of the compressor.
- FIG. 10 is a schematic view of the configuration of the core 6 of the casing 10.
- FIG. 3 is a schematic diagram of the suction ring groove 1 in the core 6. 2A and 2B are common to the first embodiment.
- the centrifugal compressor of the present invention has a suction ring groove 1, a ring guide path 2, and a return ring groove 3 on the inner peripheral surface of the casing 10 to form a self-circulation flow path.
- a suction ring groove 1 has a suction ring groove 1, a ring guide path 2, and a return ring groove 3 on the inner peripheral surface of the casing 10 to form a self-circulation flow path.
- the casing 10 of the centrifugal compressor according to the second embodiment includes an outer shell 5 and a core 6, and the suction ring groove 1 is provided on the wall surface of the core 6.
- the inner wall surface and the outer wall surface of the core 6 form the ring guide path 2 and the reflux ring groove 3.
- the width b r of the suction ring groove 1 are distributed in a parabolic shape in the circumferential direction.
- the width b r of the suction ring groove 1 is expressed by Expression (2).
- b r A ( ⁇ ⁇ D ⁇ ⁇ D) 2 + A 0 (2)
- the ratio between the characteristic parameter A of the parabola and the impeller diameter D is in the range of 0.005 / D ⁇
- the ratio between the extreme value A 0 of b r and the impeller diameter D is in the range of 0.01 ⁇
- downstream end face 1 b of the suction ring groove 1 corresponding to the designed parabolic distribution is a curve on the circumferential cylindrical surface of the core 6.
- the outer shell 5 of the casing 10 is fixed, and the core 6 is rotated around the rotational axis center ZZ of the impeller 13 (see FIG. 1) to assemble.
- a parabolic distribution of the width br of the suction ring groove 1 corresponding to a different initial phase angle ⁇ 0 is obtained. That is, the outer shell 5 and the core 6 of the casing 10 are connected by screws 7, and n (four in this example) screw holes are evenly arranged in the outer shell 5 of the casing 10 in the circumferential direction.
- n four in this example
- FIG. 6 is common to the first embodiment and is a schematic view of the position of the initial phase angle ⁇ 0 in the example. Obtained for example, in FIGS. 2A and 2B, the so a total of four screw holes in the outer shell 5 of the casing are opened, parabolic distribution in the width b r of the different suction ring groove 1 of the four shown in FIG. 12 It is done.
- FIG. 12 is a distribution schematic diagram of the width b r of the suction ring groove 1 corresponding to different initial phase angles ⁇ 0 . 12, the solid line is a parabolic distribution in the circumferential direction of the width b r of the suction ring groove 1, based on varying the selection of the circumferential direction of the initial phase angle theta 0, there are a variety of representations.
- ⁇ 0 is an initial phase angle
- the casing 10 is a circle of one circumference of 0 ⁇ ⁇ 0 ⁇ 2 ⁇ (0 ° ⁇ ⁇ 0 ⁇ 360 °)
- the defined range of the circumferential angle ⁇ of the casing Is ⁇ 0 ⁇ ⁇ ⁇ ⁇ 0 + 2 ⁇ ( ⁇ 0 ⁇ ⁇ ⁇ ⁇ 0 + 360 °).
- the air in the flow path of the self-circulating casing treatment flows in from the suction ring groove 1 and flows out through the ring guide path 2 and the reflux ring groove 3 in the low flow rate mode.
- the specific operating principle is that the suction ring groove 1 of the self-circulating casing treatment sucks the gas in the impeller blade tip region and releases the gas from the return ring groove 3 through the ring guide path 2.
- the air in the flow path of the self-circulating casing treatment is discharged from the suction ring groove 1 through the reflux ring groove 3 and the ring guide path 2.
- the reflux ring groove 3 communicates the flow in the circumferential direction of the inlet, thereby increasing the uniformity of the flow at the compressor inlet, weakening the shock wave at the inlet, and the discharge flow of the suction ring groove 1 enhances the circulation capacity. By doing so, the occlusion boundary was expanded. However, due to the lack of suction power in the mode of operation close to blockage, the expansion of the casing treatment to the blockage boundary is less noticeable than the expansion to the stall boundary.
- the following is an example of expanding the stable operating range by adopting an asymmetric self-circulating casing treatment of a centrifugal compressor in which the width b r of the suction ring groove 1 has a parabolic distribution for a certain size centrifugal compressor. .
- FIG. 13A is a graph showing the relationship between the normalized mass flow rate and the pressure ratio in Example 2.
- FIG. 13B is a relationship diagram between normalized mass flow rate and efficiency in Example 2.
- 13A and 13B show a non-axisymmetric self-circulating casing treatment ("asymmetric self-circulating CT") with a parabolic distribution of groove width, an axisymmetric self-circulating casing treatment "axisymmetric self-circulating CT”), and a casing treatment. It is a performance comparison figure of a compressor in case of no ("No CT").
- asymmetric self-circulation casing treatment asymmetric self-circulation CT
- axisymmetric self-circulating casing treatment axisymmetric self-circulating CT
- the present invention employs an asymmetric self-circulating casing treatment in which the position (axial distance S r ) or the width (width b r ) of the suction ring groove 1 is distributed parabolically as compared with the prior art.
- the stable operating range of the centrifugal compressor can be greatly expanded and the efficiency can be basically kept unchanged as compared with the axially symmetric self-circulating casing treatment. It was done.
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Abstract
Description
遠心圧縮機の小流量作動点(すなわち、圧縮機の流量が小さい場合)では、内部の流れ場において大幅な流体剥離などの不安定現象が生じて、失速ひいてはサージをもたらす。その結果、圧縮機の効率と圧力比の急速な低下を招き、寿命が短縮し、ひいては、短時間に損傷してしまう。そのため、様々な対策を採用することで、圧縮機の失速等の不安定現象を抑制して、その安定作動範囲を拡大させている。
図1Aにおいて、インペラ13は、インペラ全羽根11とインペラ半羽根12とを有する。またZ-Zはインペラ13の回転軸中心である。図1Aと図1Bに示すように、自己循環ケーシングトリートメントは、一般的に、吸引リング溝1、リング案内路2、及び還流リング溝3からなる。自己循環ケーシングトリートメントの主な構成パラメータは、吸引リング溝1のインペラ全羽根前縁4に対する軸方向距離Srと、吸引リング溝の幅brと、還流リング溝3のインペラ全羽根前縁4に対する軸方向距離Sfと、還流リング溝の幅bfと、還流リング溝の深さhbと、リング案内路2の幅bb等である。
前記吸引リング溝の上流側端面のインペラ全羽根前縁(4)に対する軸方向距離Sr又は前記吸引リング溝の幅brがA(α・D-β・D)2+A0で表され、周方向において放物線状に分布し、
初期位相角θ0の範囲が0≦θ0≦2πであり、
ケーシングの周方向角度αの定義域がθ0≦α≦θ0+2πであり、
Aは前記軸方向距離Sr又は前記幅brにおける放物線のパラメータであり、
A0は前記放物線の分布の極値点において対応する円周角度βと前記αが等しい場合における前記軸方向距離Sr又は前記幅brの極値である、ことを特徴とするものである。
前記軸方向距離Srの極値A0とインペラ直径Dとの比率が、0.01≦|A0/D|≦0.1の範囲である。
前記幅brの極値A0とインペラ直径Dとの比率が、0.01≦|A0/D|≦0.1の範囲である。
前記吸引リング溝(1)は、中子(6)の壁面に設けられ、前記外殻の内壁面と中子の外壁面が前記リング案内路(2)と還流リング溝(3)を形成する。
図2A、図2B、図3~図5は、本発明の第1実施形態を示す模式図であり、図2Aはケーシングの外殻5の正面模式図、図2Bは半断面模式図、図3はケーシングの模式図、図4はケーシングの中子6の構成模式図、図5は中子における吸引リング溝の模式図である。
自己循環流路とは、吸引リング溝1、リング案内路2、及び還流リング溝3により、インペラ全羽根前縁より下流側位置からインペラ全羽根前縁より上流側位置へ流体を戻す還流路を意味する。
Sr=A(α・D-β・D)2+A0 ・・・(1)
すなわち、ケーシング10の外殻5と中子6は、ネジ7によって連結される。ケーシング10の外殻5には、周方向にn個(この例では4つ)のネジ孔が均等に配置されており、n個の異なる初期位相角θ0に対応する軸方向距離Srの分布曲線が得られる。圧縮機の性能試験によって、n個の異なる初期位相角θ0から最適な初期位相角θ0を確定する。
図2Aと図2Bにおいて、ケーシング10の外殻5に合計4つのネジ孔が設けられているので、図7に示される4種の異なる吸引リング溝1の軸方向距離Srの放物線状分布が得られる。
図7において、実線は、吸引リング溝1の軸方向距離Srの周方向における放物線状分布であり、周方向の初期位相角θ0の選定を変えることに基づき、多様な表現形式がある。そのうち、θ0は初期位相角であり、ケーシング10は0≦θ0≦2π(0°≦θ0≦360°)の1周の円であり、図中、ケーシングの周方向角度αの定義域がθ0≦α≦θ0+2π(θ0≦α≦θ0+360°)である。
具体的な作動原理は、自己循環ケーシングトリートメントの吸引リング溝1がインペラ翼端領域の気体を吸引し、リング案内路2を経て、還流リング溝3から気体を放出することにある。
周方向上の対応する位置で還流効果がより良くなるように、周方向において放物線状に分布した吸引リング溝1の溝位置(軸方向距離Sr)を用いることで、還流の作用をより効果的に用いて、圧縮機の安定作動範囲を拡大する。
図8Aと図8Bは、溝位置が放物線状分布である非対称自己循環ケーシングトリートメント(「非対称自己循環CT」)と、軸対称自己循環ケーシングトリートメント(「軸対称自己循環CT」)と、ケーシングトリートメントのない(「CTなし」)の場合の圧縮機の性能比較図である。
図9~図11は、本発明の第2実施形態を示す模式図であり、図9は圧縮機のケーシング10の模式図、図10はケーシング10の中子6の構成模式図、図11は、中子6における吸引リング溝1の模式図である。
また、図2Aと図2Bは第1実施形態と共通である。
br=A(α・D-β・D)2+A0 ・・・(2)
すなわち、ケーシング10の外殻5と中子6は、ネジ7によって連結され、ケーシング10の外殻5には、周方向にn個(この例では4つ)のネジ孔が均等に配置されており、n個の異なる初期位相角θ0に対応する分布曲線が得られ、圧縮機の性能試験によって、最適な初期位相角θ0を確定する。
例えば、図2Aと図2Bにおいて、ケーシングの外殻5に合計4つのネジ孔が開けられているので、図12に示される4種の異なる吸引リング溝1の幅brの放物線状分布が得られる。
図12において、実線は、吸引リング溝1の幅brの周方向における放物線状の分布であり、周方向の初期位相角θ0の選定を変えることに基づき、多様な表現形式がある。そのうち、θ0は初期位相角であり、ケーシング10は0≦θ0≦2π(0°≦θ0≦360°)の1周の円であり、図中、ケーシングの周方向角度αの定義域がθ0≦α≦θ0+2π(θ0≦α≦θ0+360°)である。
具体的な作動原理は、自己循環ケーシングトリートメントの吸引リング溝1がインペラ翼端領域の気体を吸引し、リング案内路2を経て、還流リング溝3から気体を放出することにある。
周方向上の対応する溝幅で還流効果がより良くなるように、周方向において放物線状に分布した吸引リング溝1の溝幅brを用いることで、還流の作用をより効果的に用いて、圧縮機の安定した作動範囲を拡大するようにする。
図13Aと図13Bは、溝幅が放物線状分布である非軸対称自己循環ケーシングトリートメント(「非対称自己循環CT」)と、軸対称自己循環ケーシングトリートメント「軸対称自己循環CT」)と、ケーシングトリートメントのない(「CTなし」)の場合の圧縮機の性能比較図である。
1a 上流側端面、1b 下流側端面、
2 リング案内路、
3 還流リング溝、4 インペラ全羽根前縁、
5 外殻、6 中子、7 ネジ、
10 ケーシング、11 インペラ全羽根、
12 インペラ半羽根、13 インペラ
Claims (4)
- ケーシングの内周面に吸引リング溝(1)、リング案内路(2)、及び還流リング溝(3)を有し、自己循環流路を形成する非対称自己循環ケーシングトリートメントを有する遠心圧縮機において、
前記吸引リング溝の上流側端面のインペラ全羽根前縁(4)に対する軸方向距離Sr又は前記吸引リング溝の幅brがA(α・D-β・D)2+A0で表され、周方向において放物線状に分布し、
初期位相角θ0の範囲が0≦θ0≦2πであり、
ケーシングの周方向角度αの定義域がθ0≦α≦θ0+2πであり、
Aは前記軸方向距離Sr又は前記幅brにおける放物線のパラメータであり、
A0は前記放物線の分布の極値点において対応する円周角度βと前記αが等しい場合における前記軸方向距離Sr又は前記幅brの極値である、ことを特徴とする非対称自己循環ケーシングトリートメントを有する遠心圧縮機。 - 前記軸方向距離SrにおけるAとインペラ直径Dとの比率が、0.005/D≦|A|≦0.02/Dの範囲であり、
前記軸方向距離Srの極値A0とインペラ直径Dとの比率が、0.01≦|A0/D|≦0.1の範囲である、ことを特徴とする請求項1に記載の非対称自己循環ケーシングトリートメントを有する遠心圧縮機。 - 前記幅brにおけるAとインペラ直径Dとの比率が、0.005/D≦|A|≦0.05/Dの範囲であり、
前記幅brの極値A0とインペラ直径Dとの比率が、0.01≦|A0/D|≦0.1の範囲である、ことを特徴とする請求項1に記載の非対称自己循環ケーシングトリートメントを有する遠心圧縮機。 - 前記ケーシングは、外殻(5)と中子(6)からなり、
前記吸引リング溝(1)は、中子(6)の壁面に設けられ、前記外殻の内壁面と中子の外壁面が前記リング案内路(2)と還流リング溝(3)を形成する、ことを特徴とする請求項1乃至3のいずれかに記載の遠心圧縮機。
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2018141405A (ja) * | 2017-02-28 | 2018-09-13 | 三菱重工業株式会社 | 遠心圧縮機および排気タービン過給機 |
US11066982B2 (en) | 2019-02-27 | 2021-07-20 | Mitsubishi Heavy Industries, Ltd. | Centrifugal compressor and turbocharger |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10823196B2 (en) * | 2018-08-10 | 2020-11-03 | Pratt & Whitney Canada Corp. | Compressor diffuser with diffuser pipes varying in natural vibration frequencies |
US11098650B2 (en) | 2018-08-10 | 2021-08-24 | Pratt & Whitney Canada Corp. | Compressor diffuser with diffuser pipes having aero-dampers |
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US11378005B1 (en) | 2020-12-17 | 2022-07-05 | Pratt & Whitney Canada Corp. | Compressor diffuser and diffuser pipes therefor |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4930979A (en) | 1985-12-24 | 1990-06-05 | Cummins Engine Company, Inc. | Compressors |
JPH031902B2 (ja) | 1979-05-23 | 1991-01-11 | Bosch Gmbh Robert | |
JP2001263296A (ja) * | 2000-03-17 | 2001-09-26 | Hitachi Ltd | ターボ機械 |
JP2004332734A (ja) * | 2003-04-30 | 2004-11-25 | Holset Eng Co Ltd | 圧縮機 |
JP2007127109A (ja) | 2005-11-07 | 2007-05-24 | Mitsubishi Heavy Ind Ltd | 排気ターボ過給機のコンプレッサ |
JP2007224789A (ja) * | 2006-02-22 | 2007-09-06 | Toyota Motor Corp | 遠心圧縮機 |
JP4100030B2 (ja) | 2002-04-18 | 2008-06-11 | 株式会社Ihi | 遠心圧縮機 |
JP4107823B2 (ja) | 2001-09-28 | 2008-06-25 | 三菱重工業株式会社 | 流体機械 |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH675279A5 (ja) * | 1988-06-29 | 1990-09-14 | Asea Brown Boveri | |
DE4027174A1 (de) * | 1990-08-28 | 1992-03-05 | Kuehnle Kopp Kausch Ag | Kennfeldstabilisierung bei einem radialverdichter |
US6290458B1 (en) | 1999-09-20 | 2001-09-18 | Hitachi, Ltd. | Turbo machines |
DE10355240A1 (de) | 2003-11-26 | 2005-07-07 | Rolls-Royce Deutschland Ltd & Co Kg | Strömungsarbeitsmaschine mit Fluidentnahme |
WO2007033199A2 (en) | 2005-09-13 | 2007-03-22 | Ingersoll-Rand Company | Volute for a centrifugal compressor |
GB0600532D0 (en) * | 2006-01-12 | 2006-02-22 | Rolls Royce Plc | A blade and rotor arrangement |
EP1862641A1 (de) * | 2006-06-02 | 2007-12-05 | Siemens Aktiengesellschaft | Ringförmiger Strömungskanal für eine in Axialrichtung von einem Hauptstrom durchströmbare Strömungsmaschine |
US20080044273A1 (en) * | 2006-08-15 | 2008-02-21 | Syed Arif Khalid | Turbomachine with reduced leakage penalties in pressure change and efficiency |
FR2912789B1 (fr) | 2007-02-21 | 2009-10-02 | Snecma Sa | Carter avec traitement de carter, compresseur et turbomachine comportant un tel carter. |
DE102008031982A1 (de) * | 2008-07-07 | 2010-01-14 | Rolls-Royce Deutschland Ltd & Co Kg | Strömungsarbeitsmaschine mit Nut an einem Laufspalt eines Schaufelendes |
JP5948892B2 (ja) | 2012-01-23 | 2016-07-06 | 株式会社Ihi | 遠心圧縮機 |
-
2011
- 2011-02-03 JP JP2011553813A patent/JP5430684B2/ja active Active
- 2011-02-03 US US13/578,137 patent/US9234526B2/en active Active
- 2011-02-03 EP EP11742161.0A patent/EP2535596B1/en active Active
- 2011-02-03 WO PCT/JP2011/052272 patent/WO2011099417A1/ja active Application Filing
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH031902B2 (ja) | 1979-05-23 | 1991-01-11 | Bosch Gmbh Robert | |
US4930979A (en) | 1985-12-24 | 1990-06-05 | Cummins Engine Company, Inc. | Compressors |
JP2001263296A (ja) * | 2000-03-17 | 2001-09-26 | Hitachi Ltd | ターボ機械 |
JP4107823B2 (ja) | 2001-09-28 | 2008-06-25 | 三菱重工業株式会社 | 流体機械 |
JP4100030B2 (ja) | 2002-04-18 | 2008-06-11 | 株式会社Ihi | 遠心圧縮機 |
JP2004332734A (ja) * | 2003-04-30 | 2004-11-25 | Holset Eng Co Ltd | 圧縮機 |
JP2007127109A (ja) | 2005-11-07 | 2007-05-24 | Mitsubishi Heavy Ind Ltd | 排気ターボ過給機のコンプレッサ |
JP2007224789A (ja) * | 2006-02-22 | 2007-09-06 | Toyota Motor Corp | 遠心圧縮機 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2018141405A (ja) * | 2017-02-28 | 2018-09-13 | 三菱重工業株式会社 | 遠心圧縮機および排気タービン過給機 |
US11066982B2 (en) | 2019-02-27 | 2021-07-20 | Mitsubishi Heavy Industries, Ltd. | Centrifugal compressor and turbocharger |
DE102019216414B4 (de) | 2019-02-27 | 2022-11-24 | Mitsubishi Heavy Industries, Ltd. | Zentrifugalkompressor und turbolader |
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