EP2806170A1 - Zentrifugalverdichter - Google Patents

Zentrifugalverdichter Download PDF

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Publication number
EP2806170A1
EP2806170A1 EP13738815.3A EP13738815A EP2806170A1 EP 2806170 A1 EP2806170 A1 EP 2806170A1 EP 13738815 A EP13738815 A EP 13738815A EP 2806170 A1 EP2806170 A1 EP 2806170A1
Authority
EP
European Patent Office
Prior art keywords
diffuser
impeller
hub
centrifugal compressor
line
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP13738815.3A
Other languages
English (en)
French (fr)
Other versions
EP2806170A4 (de
EP2806170B1 (de
Inventor
Shuichi Yamashita
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Compressor Corp
Original Assignee
Mitsubishi Heavy Industries Ltd
Mitsubishi Heavy Industries Compressor Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Ltd, Mitsubishi Heavy Industries Compressor Corp filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP2806170A1 publication Critical patent/EP2806170A1/de
Publication of EP2806170A4 publication Critical patent/EP2806170A4/de
Application granted granted Critical
Publication of EP2806170B1 publication Critical patent/EP2806170B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F04D29/444—Bladed diffusers
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • 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
    • 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
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps

Definitions

  • the present invention relates to a centrifugal compressor, and particularly to a centrifugal compressor with a large flow rate.
  • Increasing the flow rate of a centrifugal compressor means to increase the discharge flow rate of a compressor with the same shell size, and further of an impeller with the same outer diameter.
  • the centrifugal compressor mainly includes a suction inlet 1, an impeller 2, a hub 3, a rotary shaft 4, a diffuser 5, and a scroll 6.
  • the impeller 2 is connected to the rotary shaft 4 via the hub 3.
  • the diffuser 5 is provided downstream of the impeller 2, has a flow passage extending in a direction away from the rotary shaft 4, and has an outlet directed in a radial direction in a meridian plane.
  • the scroll 6 is provided downstream of the diffuser 5 and communicates with the outlet of the diffuser 5.
  • the suction inlet 1 plays a roll of guiding a gas to the impeller 2.
  • the centrifugal compressor is configured such that the gas guided to the impeller 2 is sucked into the centrifugal compressor by the impeller 2 being rotated by the rotary shaft 4.
  • the velocity of the gas having passed through the impeller 2 is decreased, and the pressure of the gas is increased, in the diffuser 5.
  • the gas having passed through the diffuser 5 flows into the scroll 6, and thereafter flows into a discharge port, which is not shown. In this way, the centrifugal compressor converts the kinetic energy of the gas to a pressure.
  • FIG. 7 is a cross-sectional view of the diffuser 5 and the impeller 2 of the conventional centrifugal compressor.
  • a large flow rate causes the velocity distribution of the gas sacked through an impeller inlet 2a to be skewed to the hub 3 side at an impeller outlet 2b.
  • the velocity vector is inclined toward an axial direction from the radial direction.
  • an object of the present invention is to solve the problems of the conventional techniques and to achieve higher efficiency in a centrifugal compressor with a large flow rate, not by providing a new mechanism, but by changing a shape of a diffuser.
  • a centrifugal compressor according to a first invention for solving the above-described problems is a centrifugal compressor comprising:
  • a centrifugal compressor according to a second invention for solving the above-described problems is the centrifugal compressor according to the first invention, characterized in that the 9 is such that 0° ⁇ 34°.
  • a centrifugal compressor according to a third invention for solving the above-described problems is the centrifugal compressor according to the first or second invention, characterized in that the diffuser inlet hub-side line is a concave curved line.
  • centrifugal compressor of the first invention since ⁇ - ⁇ >0°, skewing of the velocity distribution of the gas is eliminated, and accordingly a decrease in amount of static pressure recovery is suppressed. Therefore, a higher efficiency of the entire compressor can be achieved.
  • the centrifugal compressor of the second invention since 0° ⁇ 34°, the skewing of the velocity distribution of the gas can be further eliminated.
  • the diffuser inlet hub-side line is a concave curved line, a stagnation region inside the diffuser is reduced. Therefore, a further higher efficiency can be achieved.
  • the apparatus mainly includes a suction inlet 1, an impeller 2, a hub 3, a rotary shaft 4, a diffuser 5, and a scroll 6, as in the case of the conventional centrifugal compressor.
  • the impeller 2 is connected to the rotary shaft 4 via the hub 3.
  • the diffuser 5 is provided downstream of the impeller 2, has a flow passage directed in a direction away from the rotary shaft 4, and has an outlet directed in a radial direction in a meridian plane.
  • the scroll 6 is provided downstream of the diffuser 5, and communicates with an outlet of the diffuser 5. Note that the rotary shaft 4 and the scroll 6 are not shown in FIG. 1 , but are assumed to be the same as those of the conventional technical.
  • the suction inlet 1 plays a role of guiding a gas to the impeller 2.
  • the centrifugal compressor is configured such that the gas guided to the impeller 2 is sucked into the centrifugal compressor by the impeller 2 being rotated by the rotary shaft 4.
  • the velocity of the gas having passed through the impeller 2 is decreased, and the pressure of the gas is increased, in the diffuser 5.
  • the gas having passed through the diffuser 5 flows into the scroll 6, and thereafter flows into a discharge port.
  • a line on the hub 3 side in the inlet of the diffuser 5 (hereinafter, stated as a diffuser inlet hub-side line 5a) is inclined toward an axial direction from the radial direction in the meridian plane.
  • ⁇ an angle formed by the diffuser inlet hub-side line 5a with the radial direction at a point B closest to the impeller outlet 2b in the diffuser inlet hub-side line 5a.
  • an angle formed by a tangent line 3b of a line on the hub 3 side in the impeller 2 (hereinafter, stated as an impeller hub-side line 3a) with the radial direction at a point A closest to an inlet of the diffuser 5 in the impeller hub-side line 3a is represented by ⁇ .
  • the present apparatus is set such that ⁇ - ⁇ >0° as shown in FIG. 5 , and further ⁇ is set such that 0° ⁇ 34°.
  • ⁇ an angle formed by the impeller rear edge 2c with the axial direction is represented by ⁇ .
  • ⁇ has not necessary to be limited, but is set such that 0 ° ⁇ 35°, which is a value used in a general centrifugal compressor.
  • a line of the shroud 7 is also inclined in conjunction with the inclination of ⁇ to confirm with a diffuser width ratio of the conventional shape.
  • the diffuser width ratio is b 3 /b 2 (see FIG. 1 ), and has a value set for each impeller.
  • FIG. 2 shows a result of simulation of the compressor efficiency of the present apparatus, conducted under conditions that ⁇ and ⁇ are certain constant values and only ⁇ is a variable.
  • the horizontal axis represents ⁇ and the vertical axis represents a compressor efficiency improvement rate.
  • the compressor efficiency improvement rate represents a difference, expressed in percentage, between the compressor efficiency of the present apparatus and the compressor efficiency of the conventional technique. As becoming higher in the graph, the compressor efficiency improvement rate indicates that the compressor efficiency of the present apparatus is higher. It can be understood from the graph that the compressor efficiency is improved when 0° ⁇ 34°.
  • the skewing of the velocity distribution of the gas in the diffuser which has conventionally occurred, is eliminated, and accordingly a decrease in the amount of static pressure recovery in the diffuser is suppressed. Therefore, a higher efficiency of the entire compressor can be achieved.
  • FIG. 4 shows differences between the apparatus according to Embodiment 1 and the present apparatus.
  • the diffuser inlet hub-side line 5a is a straight line
  • directing the outlet of the diffuser 5 in the radial direction requires that the angle of the diffuser 5 has to be changed at a certain portion.
  • a stagnation region 11 where the flow of the gas stagnates is formed. Shear stress acts between the gas stagnating in the stagnation region 11 and the flowing gas, leading to a possibility of occurrence of an energy loss.
  • the present apparatus reduces the stagnation region 11.
  • the present apparatus mainly includes a suction inlet 1, an impeller 2, a hub 3, a rotary shaft 4, a diffuser 5, and a scroll 6.
  • the impeller 2 is connected to the rotary shaft 4 via the hub 3.
  • the diffuser 5 is provided downstream of the impeller 2, has a flow passage extending in a direction away from the rotary shaft 4, and has an outlet directed in a radial direction in a meridian plane.
  • the scroll 6 is provided downstream of the diffuser 5 and communicates with the outlet of the diffuser 5.
  • the rotary shaft 4 and the scroll 6 are not shown in FIG. 3 , but are assumed to be the same as those of the conventional technique.
  • the operation of the present apparatus is also the same as those of the apparatus according to Embodiment 1 and of the conventional technique, and is accordingly omitted.
  • the diffuser inlet hub-side line 5b is made to be a concave curved line.
  • An angle formed by a tangent line 5c of the diffuser inlet hub-side line 5b with a radial direction at a point B closest to an impeller outlet 2b in the diffuser inlet hub-side line 5b is represented by ⁇ .
  • the line of the shroud 7, ⁇ , and ⁇ are set such that ⁇ - ⁇ >0° as shown in FIG. 5 , and further ⁇ is set such that 0° ⁇ 34° as in the case of the apparatus according to Embodiment 1.
  • the diffuser inlet hub-side line 5b may be a single arc, or may be a line obtained by smoothly combining a plurality of arcs or ovals, as long as it is a curved line.
  • the present apparatus can reduce the stagnation region 11, which exists in the case of the apparatus according to Embodiment 1. Therefore, the present apparatus can reduce shear stress and makes it possible to achieve higher efficiency.
  • the present invention is favorable as a centrifugal compressor, and in particular a centrifugal compressor with a large flow rate.
EP13738815.3A 2012-01-17 2013-01-11 Zentrifugalverdichter Active EP2806170B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012006714A JP5905268B2 (ja) 2012-01-17 2012-01-17 遠心圧縮機
PCT/JP2013/050360 WO2013108712A1 (ja) 2012-01-17 2013-01-11 遠心圧縮機

Publications (3)

Publication Number Publication Date
EP2806170A1 true EP2806170A1 (de) 2014-11-26
EP2806170A4 EP2806170A4 (de) 2015-11-18
EP2806170B1 EP2806170B1 (de) 2018-12-26

Family

ID=48799138

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13738815.3A Active EP2806170B1 (de) 2012-01-17 2013-01-11 Zentrifugalverdichter

Country Status (5)

Country Link
US (1) US20140369823A1 (de)
EP (1) EP2806170B1 (de)
JP (1) JP5905268B2 (de)
CN (1) CN103998790B (de)
WO (1) WO2013108712A1 (de)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
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CN104428538B (zh) * 2012-07-06 2017-07-04 丰田自动车株式会社 内燃机的增压器的压缩机
KR20150106776A (ko) * 2014-03-12 2015-09-22 한화테크윈 주식회사 원심압축기
CN104314863A (zh) * 2014-10-29 2015-01-28 湖南天雁机械有限责任公司 具有降低轴向载荷功能的压气机叶轮
DE102014226341A1 (de) * 2014-12-18 2016-06-23 Volkswagen Aktiengesellschaft Verdichter, Abgasturbolader und Brennkraftmaschine
US9970452B2 (en) 2015-02-17 2018-05-15 Honeywell International Inc. Forward-swept impellers and gas turbine engines employing the same
CN107614883B (zh) * 2015-05-14 2020-01-14 株式会社电装 离心式送风机
JP2017101636A (ja) * 2015-12-04 2017-06-08 三菱重工業株式会社 遠心圧縮機
GB2555567A (en) * 2016-09-21 2018-05-09 Cummins Ltd Turbine wheel for a turbo-machine
JP7187542B2 (ja) * 2018-04-04 2022-12-12 三菱重工エンジン＆ターボチャージャ株式会社 遠心圧縮機及びこの遠心圧縮機を備えたターボチャージャ
US11143201B2 (en) 2019-03-15 2021-10-12 Pratt & Whitney Canada Corp. Impeller tip cavity
JP2021011828A (ja) * 2019-07-04 2021-02-04 三菱重工業株式会社 多段遠心圧縮機
US11268536B1 (en) * 2020-09-08 2022-03-08 Pratt & Whitney Canada Corp. Impeller exducer cavity with flow recirculation
CN114810668A (zh) * 2022-03-17 2022-07-29 哈尔滨工业大学 涡轮及呼吸机

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US2465625A (en) * 1943-10-18 1949-03-29 Sulzer Ag Centrifugal compressor
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Also Published As

Publication number Publication date
WO2013108712A1 (ja) 2013-07-25
EP2806170A4 (de) 2015-11-18
JP5905268B2 (ja) 2016-04-20
JP2013147935A (ja) 2013-08-01
CN103998790B (zh) 2016-10-19
CN103998790A (zh) 2014-08-20
US20140369823A1 (en) 2014-12-18
EP2806170B1 (de) 2018-12-26

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