WO2011099419A1 - 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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- WO2011099419A1 WO2011099419A1 PCT/JP2011/052274 JP2011052274W WO2011099419A1 WO 2011099419 A1 WO2011099419 A1 WO 2011099419A1 JP 2011052274 W JP2011052274 W JP 2011052274W WO 2011099419 A1 WO2011099419 A1 WO 2011099419A1
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- centrifugal compressor
- ring groove
- impeller
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- circumferential direction
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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
- 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 higher efficiency, light weight, and stable operation compared to a reciprocating compressor, but its allowable operating range (ie, centrifugal compression).
- the range of flow values to the machine is limited.
- a phenomenon such as a large fluid separation occurs in the internal flow field, and an unstable operation phenomenon occurs, resulting in stall and surge. Bring.
- the efficiency and pressure ratio of the compressor are rapidly reduced, the life is shortened, and as a result, it is damaged within a short time. Therefore, by adopting various methods, the occurrence of unstable phenomena such as stalling of the compressor is delayed, and the stable operating range is expanded.
- the centrifugal compressor is provided with a casing treatment.
- a suction ring groove downstream from the front edge of the impeller and a reflux ring groove upstream from the front edge of the impeller are formed on the inner peripheral surface of the casing surrounding the impeller of the centrifugal compressor. ing.
- the fluid in the flow path defined on the inner peripheral surface of the casing is caused to flow from the suction ring groove into the casing, and the fluid is supplied from the reflux ring groove. Return to the flow path upstream from the leading edge of the impeller.
- the flow rate to the impeller is increased and the operation of the centrifugal compressor is stabilized. In this way, the stable operating range is expanded.
- Patent No. 3001902 JP 2007-127109 A Japanese Patent No. 4100030 Japanese Patent No. 4107823 US Pat. No. 4,930,979
- the uneven pressure distribution in the circumferential direction has not been considered. That is, since the scroll flow path, which is the flow path of the fluid sent from the impeller in the centrifugal compressor, has an asymmetric shape with respect to the rotation axis, a nonuniform pressure distribution in the circumferential direction occurs in the fluid on the centrifugal compressor outlet side. . As a result, the upstream flow field is also affected, and the circumferential flow field at the inlet of the centrifugal compressor becomes asymmetric with respect to the rotation axis. In the conventional casing treatment, a suction ring groove that is symmetrical with respect to the rotation axis is formed, so that the asymmetry of the flow field inside the centrifugal compressor cannot be considered. That is, the casing treatment cannot be optimized over the entire circumference. This limits the expansion of the stable operating range of the centrifugal compressor.
- an object of the present invention is to further expand a stable operating range without reducing efficiency in a centrifugal compressor having a casing treatment.
- a rotary shaft (3) that is rotationally driven and an impeller (5) that is fixed to the rotary shaft are provided, and the impeller sends out suction fluid radially outward of the rotary shaft.
- a centrifugal compressor that compresses A casing (7) having an inner peripheral surface surrounding the impeller;
- a reflux path (9) for returning fluid from a position downstream from the impeller full blade leading edge (6a) to a position upstream from the impeller full blade leading edge is formed inside the casing,
- the reflux path opens to the downstream position on the inner peripheral surface and opens to the upstream position on the inner peripheral surface, and the suction ring groove (9a) formed in the circumferential direction around the rotation axis.
- a centrifugal compressor having an asymmetric self-circulating casing treatment, characterized in that an axial position or width distribution of the suction ring groove in the circumferential direction is asymmetric with respect to the rotation axis.
- asymmetric self-circulating casing treatment self-circulating means that the fluid circulates through the above-described reflux path
- asymmetric casing treatment means the axial position or width of the suction ring groove.
- the distribution in the circumferential direction is asymmetric with respect to the rotation axis.
- the fluid pressure distribution in the circumferential direction becomes non-uniform upstream from the leading edge of all impeller blades,
- the axial position or the axial width of the suction ring groove is changed according to the circumferential position so as to reduce the non-uniformity of the fluid pressure distribution.
- the distribution in the circumferential direction of the axial position or width of the suction ring groove is asymmetric with respect to the rotation axis, so that the stable operating range is further expanded without reducing the efficiency. be able to.
- FIG. 3A An example of the distribution of the circumferential direction of the fluid pressure in a casing internal peripheral surface is shown.
- the axial distance Sr distribution of the suction ring groove with respect to the impeller front blade front edge is shown.
- the optimum axial distance Sr distribution of the suction ring groove with respect to the leading edge of the impeller blades is shown.
- FIG. 1 is a longitudinal sectional view of a centrifugal compressor 10 having an asymmetric self-circulating casing treatment according to a first embodiment of the present invention.
- the centrifugal compressor 10 includes a rotating shaft 3 that is rotationally driven and an impeller 5 that is fixed to the rotating shaft 3, and the impeller 5 supplies suction fluid to the scroll flow path 4 that is radially outward of the rotating shaft 3.
- the impeller 5 has an impeller full blade 6 and an impeller half blade 8.
- reference numeral 6 a indicates the impeller full blade leading edge
- reference numeral 6 b indicates the impeller full blade trailing edge
- reference numeral 8 a indicates the impeller half blade leading edge
- reference numeral 8 b indicates the impeller half blade trailing edge.
- the leading edge means the upstream end
- the trailing edge means the downstream end.
- the circumferential direction around the rotating shaft 3 is simply referred to as the circumferential direction
- the direction parallel to the rotating shaft 3 is simply referred to as the axial direction
- the radial direction with respect to the rotating shaft 3 is simply referred to as the radial direction.
- a position in the circumferential direction is simply referred to as a circumferential position
- a position in the axial direction is simply referred to as an axial position.
- the centrifugal compressor 10 further includes a casing 7 having an inner peripheral surface 7 a extending in the circumferential direction so as to surround the impeller full blades 6. Inside the casing 7, a reflux path 9 is formed for returning fluid from a position downstream from the impeller full blade leading edge 6 a to a position upstream from the impeller full blade leading edge 6 a.
- the downstream side position is between the impeller all blades leading edge 6a (the most upstream position in the axial direction) and the impeller all blades trailing edge 6b (the most downstream position in the axial direction).
- the reflux path 9 includes a suction ring groove 9a, a reflux ring groove 9b, and a ring guide path (ring guide groove) 9c.
- the suction ring groove 9a opens to the downstream position on the inner peripheral surface 7a and extends in the circumferential direction.
- the suction ring groove 9a extends from the opening position in the casing 7 in the radial direction.
- the reflux ring groove 9b opens in the upstream position on the inner peripheral surface 7a and extends in the circumferential direction.
- the reflux ring groove 9b extends radially from the opening position into the casing 7.
- the ring guide path 9c extends in the axial direction and connects the suction ring groove 9a and the return ring groove 9b.
- the ring guide path 9c is closed by the closing member 11 in FIG.
- the “ring” of the suction ring groove 9a, the reflux ring groove 9b, and the ring guide path 9c means that they are ring-shaped when viewed from the axial direction.
- FIG. 2 due to the asymmetry of the scroll flow path 4 shown in FIG. 2, the flow field in the suction ring groove 9 a does not have symmetry with respect to the rotation axis 3.
- FIG. 1 only one side (the upper side in FIG. 1) is shown with the rotary shaft 3 as a boundary. However, in FIG. 2, the rotary shaft 3, the scroll flow path 4, and the entire impeller blades 6 are viewed from the axial direction. Is shown.
- the suction fluid that has flowed into the impeller full blades 6 is sent out by the impeller full blades 6 to the scroll flow path 4 located radially outward, and flows in the scroll flow path 4 in the circumferential direction. It flows outward in the radial direction.
- FIG. 1 the suction fluid that has flowed into the impeller full blades 6 is sent out by the impeller full blades 6 to the scroll flow path 4 located radially outward, and flows in the scroll flow path 4 in the circumferential direction. It flows outward in the radial direction.
- the fluid flow field (fluid pressure and flow rate) does not have symmetry in the scroll flow path 4.
- Such flow field asymmetry also affects the flow field upstream of the scroll flow path 4.
- the flow field also has no symmetry in the suction ring groove 9a.
- the circumferential fluid pressure distribution is non-uniform.
- the reflux path 9 is formed symmetrically with respect to the rotating shaft 3, that is, the axial position of the suction ring groove 9a of the reflux path 9 is between the circumferential positions. If it is made constant, the fluid pressure distribution in the circumferential direction becomes non-uniform downstream from the impeller full blade leading edge 6a.
- the distribution in the circumferential direction of the axial position of the suction ring groove 9 a is asymmetric with respect to the rotating shaft 3.
- each circumference is reduced so as to reduce the non-uniformity of the fluid pressure distribution in the vicinity of the leading edge 6a upstream of the impeller full blade leading edge 6a (hereinafter referred to as a pressure distribution correction axial position).
- the axial position of the suction ring groove 9a at the directional position is changed according to the circumferential position.
- the axial position of the reflux ring groove 9b is the same as the pressure distribution correction axial direction position or upstream of the pressure distribution correction axial position.
- FIG. 3A shows each parameter of the reflux path 9.
- FIG. 3B shows the reflux path of FIG. 3A.
- S r corresponds to the axial position of the suction ring groove 9a, is the axial distance from the impeller full blade leading edge 6a to the suction ring groove 9a.
- br is the axial width of the suction ring groove 9a.
- S f corresponds to the axial position of the return ring grooves 9b, is the axial distance from the impeller full blade leading edge 6a up to the reflux ring groove 9b.
- b f is the axial width of the reflux ring groove 9b.
- b b is the radial width of the ring guideway 9c.
- h b is the depth of the suction ring groove 9a or the reflux ring groove 9b.
- S r or b r has the greatest influence on the stable operating range of the centrifugal compressor 10. That is, among the above dimensions, S r or b r has the largest influence on the pressure difference between the suction ring groove 9 a and the return ring groove 9 b and the fluid flow rate in the return path 9. Therefore, in the first embodiment, the S r, are adjusted for each circumferential position so as to reduce the non-uniformity of the fluid pressure distribution in the pressure distribution corrected axial position.
- FIG. 4 shows an example of the fluid pressure distribution in the circumferential direction at the pressure distribution correction axial position.
- the horizontal axis indicates the phase angle around the rotation axis 3 (that is, the circumferential position), and the vertical axis indicates the fluid pressure normalized.
- the white square mark in FIG. 4 shows the fluid pressure measured by experiment. Of the phase angles in FIG. 4, 0 ° is shown in FIG.
- FIG. 5A shows the axial position of the suction ring groove 9a at each circumferential position (that is, the above-mentioned S r ) for reducing the non-uniformity of the fluid pressure distribution shown in FIG.
- the horizontal axis represents the phase angle around the rotating shaft 3 (i.e., the circumferential direction position)
- the vertical axis represents the axial distance S r from the impeller full blade leading edge 6a to the suction ring groove 9a.
- FIG. 2 shows a position of 0 ° and a position of ⁇ .
- FIG. 5B shows the optimal Sr distribution obtained by numerical simulation.
- FIG. 6A shows the pressure ratio of the centrifugal compressor to the flow rate.
- the horizontal axis indicates a value obtained by normalizing the flow rate to the centrifugal compressor, and the vertical axis indicates the pressure ratio of the centrifugal compressor as a ratio.
- FIG. 6B shows the efficiency of the centrifugal compressor with respect to the flow rate.
- the horizontal axis indicates a value obtained by normalizing the flow rate to the centrifugal compressor
- the vertical axis indicates the efficiency of the centrifugal compressor as a ratio.
- C P is specific heat at constant pressure
- T 1t is the temperature at the inlet side of a centrifugal compressor
- T 2t is the temperature at the outlet side of the centrifugal compressor
- P 1t is of the centrifugal compressor inlet side
- P 2t is the pressure on the outlet side of the centrifugal compressor
- ⁇ is the specific heat ratio
- a black square mark and a curve with a solid line passing over the square mark indicate the case of the example of the first embodiment (that is, a centrifugal compressor having an asymmetric casing treatment).
- the casing treatment is abbreviated as CT.
- a white square mark and a curve by a one-dot chain line passing over the square mark indicate a conventional centrifugal filter having a reflux path in which the axial position of the suction ring groove 9a is constant at each circumferential position.
- the case of a compressor ie a centrifugal compressor with an axisymmetric casing treatment
- a white circle and a curved line by a broken line passing over the circle indicate a case of a centrifugal compressor having no reflux path (that is, a centrifugal compressor having no casing treatment).
- Pa indicates the limit operating point on the small flow rate side where the embodiment of the present invention does not generate a surge
- Pb indicates the small flow rate side where the centrifugal compressor having an axisymmetric casing treatment does not generate a surge
- Pc indicates the limit operating point on the small flow rate side where the centrifugal compressor having no casing treatment does not generate a surge.
- the efficiency is not lowered as compared with the centrifugal compressor having the axisymmetric casing treatment.
- the distribution in the circumferential direction of the axial position of the suction ring groove 9a is the rotation axis. To be asymmetric.
- FIG. 7A shows the width of the suction ring groove 9a at each circumferential position (that is, b r described above) for reducing the non-uniformity of the fluid pressure distribution shown in FIG. 7A
- the horizontal axis indicates the phase angle around the rotating shaft 3 (i.e., the circumferential direction position) and the vertical axis shows the width b r of the suction ring groove 9a.
- FIG. 2 shows a position of 0 ° and a position of ⁇ .
- the suction ring groove 9a having a b r as shown in FIG. 7A since reducing the non-uniformity in the circumferential direction of the fluid pressure distribution in the pressure distribution corrected axial position, Fluid separation, stall, surge, etc. can be more effectively suppressed. As a result, the stable operating range of the centrifugal compressor 10 can be further expanded.
- FIG. 7B shows the optimum distribution of br obtained by numerical simulation.
- FIG. 8A shows the pressure ratio of the centrifugal compressor to the flow rate.
- the horizontal axis indicates a value obtained by normalizing the flow rate to the centrifugal compressor, and the vertical axis indicates the pressure ratio of the centrifugal compressor as a ratio.
- FIG. 8B shows the efficiency of the centrifugal compressor with respect to the flow rate.
- the horizontal axis indicates a value obtained by normalizing the flow rate to the centrifugal compressor
- the vertical axis indicates the efficiency of the centrifugal compressor as a ratio.
- a black square mark and a curve with a solid line passing over the square mark indicate the case of the example of the second embodiment (that is, a centrifugal compressor having an asymmetric casing treatment).
- the casing treatment is abbreviated as CT.
- a black triangular mark and a curve by a solid line passing over the triangular mark indicate the conventional centrifugal compression in which the axial position of the suction ring groove 9a is constant at each circumferential position.
- Shows the case of a machine ie a centrifugal compressor with an axisymmetric casing treatment.
- a white circle and a curve with a broken line passing over the circle indicate a case of a centrifugal compressor having no reflux path (that is, a centrifugal compressor having no casing treatment).
- the asymmetric casing treatment according to the embodiment of the present invention is provided in the centrifugal compressor, so that it is compared with the case where the axisymmetric casing treatment is provided and the case where the casing treatment is not provided.
- a stable operating range can be expanded while maintaining basically the same efficiency.
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Abstract
Description
前記インペラを囲む内周面を有するケーシング(7)を備え、
前記ケーシングの内部には、インペラ全羽根前縁(6a)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(9)が形成され、
該還流路は、前記内周面における前記下流側位置に開口して前記回転軸回りの周方向に形成される吸引リング溝(9a)と、前記内周面における前記上流側位置に開口して前記周方向に形成される還流リング溝(9b)と、を有し、
前記回転軸の軸方向における位置を軸方向位置とし、
前記吸引リング溝の軸方向位置または幅の前記周方向における分布が、前記回転軸に関して非対称になっている、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が提供される。
なお、「非対称自己循環ケーシングトリートメント」について、「自己循環」とは、上述の還流路により流体が循環することをいい、「非対称ケーシングトリートメント」とは、吸引リング溝において、その軸方向位置または幅の周方向分布が、前記回転軸に関して非対称になっている構成をいう。
前記流体圧力分布の不均一を低減するように、吸引リング溝の軸方向位置または軸方向幅を周方向位置に応じて変化させている。
図1は、本発明の第1実施形態による、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10の縦断面図である。遠心圧縮機10は、回転駆動される回転軸3と、該回転軸3に固定されるインペラ5とを備え、該インペラ5により、回転軸3の半径方向外側のスクロール流路4に吸入流体を送出して圧縮する。インペラ5は、インペラ全羽根6とインペラ半羽根8とを有する。図1において、符号6aは、インペラ全羽根前縁を示し、符号6bは、インペラ全羽根後縁を示し、符号8aは、インペラ半羽根前縁を示し、符号8bは、インペラ半羽根後縁を示す。前縁は、上流端を意味し、後端は下流端を意味する。
なお、第1実施形態において、回転軸3回りの周方向を単に周方向といい、回転軸3と平行な方向を単に軸方向といい、回転軸3に対する半径方向を単に半径方向といい、前記周方向における位置を単に周方向位置といい、前記軸方向における位置を単に軸方向位置という。
なお、第1実施形態において、吸引リング溝9a、還流リング溝9b、およびリング案内路9cの「リング」とは、これらが軸方向から見てリング状であることを意味する。
また、第1実施形態と違って、還流路9を、回転軸3に関し対称に形成した場合には、すなわち、還流路9の吸引リング溝9aの軸方向位置を、各周方向位置の間で一定にした場合には、インペラ全羽根前縁6aより下流において周方向の流体圧力分布は、不均一となる。
また、インペラ全羽根前縁6aより下流で圧力が低い周方向位置では、インペラ全羽根前縁6aより上流でも圧力が低くなる。従って、インペラ全羽根前縁6aより下流における周方向の流体圧力分布と、インペラ全羽根前縁6aより上流における周方向の流体圧力分布とは、同様の分布となる場合が多い。
すなわち、第1実施形態によると、インペラ全羽根前縁6aより上流における前縁6a付近(以下、圧力分布修正軸方向位置という)での前記流体圧力分布の不均一を低減するように、各周方向位置における吸引リング溝9aの軸方向位置を、周方向位置に応じて変化させている。なお、還流リング溝9bの軸方向位置は、圧力分布修正軸方向位置と同じか、または、圧力分布修正軸方向位置より上流側である。
そこで、第1実施形態では、Srを、圧力分布修正軸方向位置での流体圧力分布の不均一さを低減するように各周方向位置毎に調整している。
第1実施形態では、さらに、図5AのようなSrを有する吸引リング溝9aにより、圧力分布修正軸方向位置における周方向の流体圧力分布の不均一を低減するので、流体剥離、失速、サージなどを一層効果的に抑制できる。その結果、遠心圧縮機10の安定した作動範囲をさらに拡大することができる。
図6Bは、流量に対する遠心圧縮機の効率を示す。図6Bにおいて、横軸は、遠心圧縮機への流量を正規化した値で示し、縦軸は、遠心圧縮機の効率を比率で示す。
本発明の第2実施形態による遠心圧縮機10を説明する。第2実施形態において、以下で説明しない点は、上述の第1実施形態と同じである。
図8Bは、流量に対する遠心圧縮機の効率を示す。図8Bにおいて、横軸は、遠心圧縮機への流量を正規化した値で示し、縦軸は、遠心圧縮機の効率を比率で示す。
6a インペラ全羽根前縁、6b インペラ全羽根後縁、7 ケーシング、
7a ケーシングの内周面、8 インペラ半羽根、8a インペラ半羽根前縁、
8b インペラ半羽根後縁、9 還流路、9a 吸引リング溝、
9b 還流リング溝、9c リング案内路、10 遠心圧縮機、11 閉塞部材
Claims (1)
- 回転駆動される回転軸(3)と、該回転軸に固定されるインペラ(5)とを備え、該インペラにより、前記回転軸の半径方向外側に吸入流体を送出して圧縮する遠心圧縮機であって、
前記インペラを囲む内周面を有するケーシング(7)を備え、
前記ケーシングの内部には、インペラ全羽根前縁(6a)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(9)が形成され、
該還流路は、前記内周面における前記下流側位置に開口して前記回転軸回りの周方向に形成される吸引リング溝(9a)と、前記内周面における前記上流側位置に開口して前記周方向に形成される還流リング溝(9b)と、を有し、
前記回転軸の軸方向における位置を軸方向位置とし、
前記吸引リング溝の軸方向位置または幅の前記周方向における分布が、前記回転軸に関して非対称になっている、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。
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JP2011553815A JP5583701B2 (ja) | 2010-02-09 | 2011-02-03 | 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と、遠心圧縮機に非対称自己循環ケーシングトリートメントを設ける方法 |
US13/578,188 US9816522B2 (en) | 2010-02-09 | 2011-02-03 | Centrifugal compressor having an asymmetric self-recirculating casing treatment |
EP11742163.6A EP2535598B1 (en) | 2010-02-09 | 2011-02-03 | Centrifugal compressor using an asymmetric self-recirculating casing treatment |
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CN201010110311A CN101749279A (zh) | 2010-02-09 | 2010-02-09 | 基于变开槽位置的离心压气机非对称自循环处理机匣 |
CN201010110299.8 | 2010-02-09 | ||
CN201010110311.5 | 2010-02-09 | ||
CN201010110299A CN101749278A (zh) | 2010-02-09 | 2010-02-09 | 基于变开槽宽度的离心压气机非对称自循环处理机匣 |
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10364818B2 (en) | 2013-09-27 | 2019-07-30 | Ihi Corporation | Centrifugal compressor and turbocharger |
WO2019150415A1 (ja) * | 2018-01-30 | 2019-08-08 | 三菱重工エンジン&ターボチャージャ株式会社 | コンプレッサケーシング、これを備えたコンプレッサ、およびコンプレッサケーシングの加工方法 |
EP3862575A1 (en) | 2020-02-06 | 2021-08-11 | Mitsubishi Heavy Industries, Ltd. | Compressor housing with a recirculation structure, compressor including said compressor housing, and turbocharger including said compressor |
JPWO2021234886A1 (ja) * | 2020-05-21 | 2021-11-25 |
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US10273973B2 (en) * | 2010-02-09 | 2019-04-30 | Ihi Corporation | Centrifugal compressor having an asymmetric self-recirculating casing treatment |
DE102014200588B4 (de) | 2013-12-20 | 2015-08-27 | Aktiebolaget Skf | Lageranordnung |
JP6497183B2 (ja) * | 2014-07-16 | 2019-04-10 | トヨタ自動車株式会社 | 遠心圧縮機 |
CN114391065A (zh) * | 2019-10-09 | 2022-04-22 | 株式会社Ihi | 离心压缩机 |
CN111441991A (zh) * | 2020-04-03 | 2020-07-24 | 中船重工龙江广瀚燃气轮机有限公司 | 一种改善压气机性能用带背腔的轴线斜槽式处理机匣 |
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Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10364818B2 (en) | 2013-09-27 | 2019-07-30 | Ihi Corporation | Centrifugal compressor and turbocharger |
WO2019150415A1 (ja) * | 2018-01-30 | 2019-08-08 | 三菱重工エンジン&ターボチャージャ株式会社 | コンプレッサケーシング、これを備えたコンプレッサ、およびコンプレッサケーシングの加工方法 |
EP3862575A1 (en) | 2020-02-06 | 2021-08-11 | Mitsubishi Heavy Industries, Ltd. | Compressor housing with a recirculation structure, compressor including said compressor housing, and turbocharger including said compressor |
US11530708B2 (en) | 2020-02-06 | 2022-12-20 | Mitsubishi Heavy Industries, Ltd. | Compressor housing, compressor including the compressor housing, and turbocharger including the compressor |
JPWO2021234886A1 (ja) * | 2020-05-21 | 2021-11-25 | ||
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Also Published As
Publication number | Publication date |
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JP5583701B2 (ja) | 2014-09-03 |
EP2535598B1 (en) | 2018-06-06 |
EP2535598A4 (en) | 2017-09-20 |
US20120315127A1 (en) | 2012-12-13 |
JPWO2011099419A1 (ja) | 2013-06-13 |
EP2535598A1 (en) | 2012-12-19 |
US9816522B2 (en) | 2017-11-14 |
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