WO2019139199A1 - Compresseur - Google Patents

Compresseur Download PDF

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Publication number
WO2019139199A1
WO2019139199A1 PCT/KR2018/001516 KR2018001516W WO2019139199A1 WO 2019139199 A1 WO2019139199 A1 WO 2019139199A1 KR 2018001516 W KR2018001516 W KR 2018001516W WO 2019139199 A1 WO2019139199 A1 WO 2019139199A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
rotor
labyrinth seal
ring
gas
Prior art date
Application number
PCT/KR2018/001516
Other languages
English (en)
Korean (ko)
Inventor
김영대
Original Assignee
한화파워시스템 주식회사
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 한화파워시스템 주식회사 filed Critical 한화파워시스템 주식회사
Priority to CN201880086114.9A priority Critical patent/CN111587323B/zh
Publication of WO2019139199A1 publication Critical patent/WO2019139199A1/fr

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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
    • F04D29/08—Sealings
    • 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
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer

Definitions

  • the present invention relates to a compressor, and more particularly, to a compressor for allowing inflation gas for cooling to flow into a motor through a blade of a labyrinth seal provided at an inlet of an impeller and a motor.
  • the gas turbine engine can combust the fuel to rotate the turbine.
  • the combustion of the fuel can be performed by a combustor, which requires a large amount of air to be combusted.
  • a compressor may be used to supply sufficient air to the combustor.
  • the compressor compresses and supplies a large amount of air to the combustor, and the combustor can combust the fuel using the supplied air.
  • the motor may include a stator and a rotor. Heat can be generated as the rotor rotates relative to the stator. In order to remove heat between the stator and the rotor, the motor must have separate cooling means, which may increase the overall size and weight of the compressor.
  • a compressor including: an impeller that pressurizes a gas by rotation; a rotor coupled to the impeller and disposed inside the motor housing to transmit rotational power to the impeller; And a labyrinth seal disposed between the impeller and the rotor to restrict the flow of gas pressurized by the impeller into the motor, wherein the labyrinth seal includes a single blade.
  • a bearing disk is provided at one end of the rotor, and the labyrinth seal is provided between the impeller and the bearing disk.
  • the rotor has a shielding ring formed at one end thereof to form a ring-shaped slit with the labyrinth seal. Gas passing through the ring-shaped slit expands and flows into the motor housing in a cooled state.
  • the diameter of the shielding ring is smaller than the diameter of the rotor.
  • a carbon ring is provided on the inner side of the blade in contact with the shielding ring.
  • An elastic ring having an elastic force of a predetermined magnitude or more is provided on the inner side of the blade in contact with the shield ring.
  • the elastic ring has a shape of a disk and is deformed by the pressurized gas to form the ring-shaped slit.
  • the motor housing and the rotor are connected by an air foil bearing.
  • the inflation gas for cooling is introduced into the motor through the impeller and the blade of the labyrinth seal provided at the inlet of the motor, It provides the advantage of eliminating the heat of the motor without having to do so.
  • FIG. 1 is an exploded perspective view of a compressor according to an embodiment of the present invention.
  • FIG. 2 is a perspective view of a compressor according to an embodiment of the present invention.
  • FIG 3 is a perspective view of a labyrinth seal according to an embodiment of the present invention.
  • FIG. 4 is a cross-sectional view of a labyrinth seal according to an embodiment of the present invention.
  • FIG. 5 is a cross-sectional view of a compressor according to an embodiment of the present invention.
  • FIG. 6 is a view showing that a slit is formed between a labyrinth seal and a shield ring according to an embodiment of the present invention.
  • FIG. 7 is a view showing that the gas according to the embodiment of the present invention flows into the interior of the motor housing.
  • FIG. 8 is a view showing gas passing through a slit according to an embodiment of the present invention.
  • FIG. 9 is a perspective view of a labyrinth seal according to another embodiment of the present invention.
  • FIG. 10 is a view showing the gas moving by the labyrinth seal shown in FIG.
  • FIG. 11 is a perspective view of a labyrinth seal according to another embodiment of the present invention.
  • FIG. 12 is a view showing the movement of the gas by the labyrinth seal shown in Fig.
  • FIG. 1 is an exploded perspective view of a compressor according to an embodiment of the present invention
  • FIG. 2 is a perspective view of a compressor according to an embodiment of the present invention.
  • a compressor 10 includes a motor housing 100, a rotor 200, a bearing disk 300, a shield ring 400, a support disk 500, And includes an impeller 700 and a spiral case 800.
  • the motor housing 100 may accommodate a stator (not shown) and the rotor 200 to provide a rotating space of the rotor 200.
  • a stator may be fixedly coupled to the inside of the motor housing 100.
  • the rotor 200 can be rotated by a change in the magnetic force of the stator.
  • the rotor 200 has a circular column shape and a permanent magnet may be provided therein. As the stator provides a varying magnetic force, the rotor 200 becomes rotatable.
  • a coupling rod 210 for coupling with the impeller 700 may be provided at the distal end of the rotor 200.
  • the rotor 200 is coupled to the impeller 700 through the coupling rod 210 and can transmit the rotational power generated in the motor housing 100 to the impeller 700.
  • a bearing disk 300 may be provided at one end of the rotor 200. Specifically, the bearing disk 300 may be coupled to the coupling rod 210 at one end of the rotor 200 to which the impeller 700 is coupled. The bearing disk 300 can rotate integrally with the rotor 200.
  • the bearing disk 300 serves to reduce the friction between the rotor 200 and the motor housing 100.
  • the compressor 10 according to the embodiment of the present invention can connect the rotor 200 and the motor housing 100 with an air foil bearing.
  • the bearing disk 300 may be one side of the airfoil bearing.
  • the motor housing 100 is provided with a disc receiving space (not shown) for receiving the bearing disc 300.
  • the bearing disc 300 can rotate without directly contacting the disc receiving space.
  • the shield ring 400 is disposed in the through hole H (see FIG. 4) of the labyrinth seal 600 so as to restrict the pressurized gas generated at the impeller 700 side from entering the interior of the motor housing 100 Role.
  • the shield ring 400 may be provided at one end of the rotor 200. Specifically, the shield ring 400 is coupled to the bearing disc 300 and rotates together with the bearing disc 300.
  • the support disk 500 is fixedly coupled to the motor housing 100 to support one end of the rotor 200.
  • the rotor 200 is supported by the support disk 500 and can rotate relative to the motor housing 100.
  • the support disk 500 may include a labyrinth seal 600.
  • the labyrinth seal 600 is provided between the impeller 700 and the rotor 200 and functions to restrict gas that is pressurized by the impeller 700 from flowing into the interior of the motor housing 100.
  • the shield ring 400 coupled to the rotor 200 may be rotated inside the labyrinth seal 600. As the shield ring 400 rotates close to the labyrinth seal 600, the introduction of the pressurized gas into the motor housing 100 can be restricted.
  • the labyrinth seal 600 may include a single blade 610. A part of the gas pressurized by the impeller 700 can pass between the labyrinth seal 600 and the shielding ring 400 because it is composed of only one blade 610. Gas penetrating between the labyrinth seal 600 and the shielding ring 400 can be introduced into the motor housing 100 and used for cooling the interior of the motor housing 100.
  • the impeller 700 serves to pressurize the gas by rotation.
  • the impeller 700 can be rotated by receiving the rotational power of the rotor 200.
  • the impeller 700 is coupled to the coupling rod 210 of the rotor 200 and receives rotational power from the rotor 200.
  • the impeller 700 may be coupled to the coupling rod 210 by a nut 220.
  • the coupling rod 210 may be provided with a thread for coupling with the nut 220.
  • the spiral case 800 plays a role of providing a movement path of the gas.
  • the spiral case 800 may include a gas inlet 810, a gas outlet 820, and a gas transfer tube 830.
  • the gas inlet 810 provides a flow path for the gas and the gas outlet 820 can provide a discharge path for the gas.
  • the gas introduced through the gas inlet 810 can be pressurized by the impeller 700.
  • the pressurized gas can be delivered through the gas transfer tube 830 and discharged through the gas outlet 820.
  • FIG. 3 is a perspective view of a labyrinth seal according to an embodiment of the present invention
  • FIG. 4 is a sectional view of a labyrinth seal according to an embodiment of the present invention.
  • Labyrinth seal 600 has the form of a disk and can be combined with shield ring 400 to restrict gas movement.
  • the labyrinth seal 600 may be attached to one side of the support disk 500.
  • the rotor 200 can be supported on the support disk 500 via the labyrinth seal 600.
  • the labyrinth seal 600 may include a single blade 610. A certain amount of the gas generated from the impeller 700 can flow into the interior of the motor housing 100 through the space between the labyrinth seal 600 and the shielding ring 400 because there is only one blade 610.
  • the labyrinth seal 600 may have a through hole H for penetrating the coupling rod 210 and the shield ring 400.
  • One side of the blade 610 adjacent to the through hole H may be reduced in thickness toward the through hole H.
  • the end of the blade 610 forming the edge of the through hole H may have a relatively small thickness.
  • FIG. 4 shows that the entire left side surface of the labyrinth seal 600 is flat and inclined surfaces are included on the right side surface.
  • One surface of the labyrinth seal 600 having a flat surface as a whole is referred to as a first surface and the other surface of the labyrinth seal 600 including an inclined surface is referred to as a second surface.
  • the first surface may be the surface facing the impeller 700 and the second surface may be the surface facing the motor housing 100.
  • the gas pressurized by the impeller 700 can move from the first surface to the second surface.
  • FIG. 5 is a cross-sectional view of a compressor according to an embodiment of the present invention
  • FIG. 6 is a view showing a slit formed between a labyrinth seal and a shield ring according to an embodiment of the present invention
  • the rotor 200 is accommodated in the motor housing 100 and can be rotated by a change in the magnetic force of the stator 900.
  • the permanent magnet 230 may be provided inside the rotor 200.
  • the stator 900 forms a changing magnetic force
  • the rotor 200 can rotate.
  • the impeller 700 can rotate together with the rotor 200 to pressurize the gas.
  • the gas introduced through the gas inlet port 810 is pressurized by the rotational force of the impeller 700 and the pressurized gas can be moved along the gas transfer pipe 830 and then discharged through the gas outlet port 820.
  • An airfoil bearing 110 may be provided in the inner space of the motor housing 100.
  • the rotor 200 can be rotated without being in direct contact with the inner surface of the motor housing 100.
  • the labyrinth seal 600 and the shielding ring 400 may form a ring-shaped slit SL.
  • the width of the slit SL is the distance between the end of the blade 610 of the labyrinth seal 600 and the surface of the shield ring 400 and may be relatively small in size.
  • a part of the gas pressurized by the impeller 700 can be introduced into the interior of the motor housing 100 through the slit SL. Since the width of the slit SL is small, most of the pressurized gas is discharged through the gas outlet 820, but some pressurized gas can be introduced into the interior of the motor housing 100.
  • FIG. 7 shows that some of the gas pressurized by the impeller 700 flows into the interior of the motor housing 100.
  • the gas introduced into the motor housing 100 can be used for cooling the stator 900 and the rotor 200.
  • a bearing disk 300 is provided at one end of the rotor 200 and a labyrinth seal 600 may be provided between the impeller 700 and the bearing disk 300.
  • the gas that has passed through the labyrinth seal 600 can be introduced into the motor housing 100 through the bearing disk 300. At this time, the bearing disk 300 can be cooled by the gas.
  • the diameter of the shield ring 400 may be smaller than the diameter of the bearing disk 300. As a result, the area of the entire surface of the bearing disk 300 exposed to the gas passing through the slit SL increases, and the cooling efficiency of the bearing disk 300 can be improved.
  • FIG. 8 is a view showing gas passing through a slit according to an embodiment of the present invention.
  • some of the gas pressurized by the impeller 700 can pass through the slit SL.
  • the size of the slit SL can be relatively small.
  • the gas generated from the impeller 700 is pressurized and can have a relatively high pressure.
  • the pressurized gas can pass through the slit SL at a high pressure.
  • the gas that has passed through the slit SL can expand in the space SP formed between the labyrinth seal 600 and the bearing disk 300.
  • the gas passing through the ring-shaped slit SL can be expanded and introduced into the interior of the motor housing 100 in a cooled state.
  • FIG. 9 is a perspective view of a labyrinth seal according to another embodiment of the present invention
  • FIG. 10 is a view showing gas moving by the labyrinth seal shown in FIG.
  • the labyrinth seal 601 may include a blade 611 and a carbon ring 621.
  • the carbon ring 621 is provided on the inner side of the blade 611 and can contact the shield ring 400.
  • the carbon ring 621 may be formed along the edge of the through hole H of the labyrinth seal 601.
  • the carbon ring 621 may be in contact with or slightly spaced from the shield ring 400.
  • the blocking ratio between the space on the side of the impeller 700 and the inside of the motor housing 100 may increase as the carbon ring 621 contacts or is slightly spaced from the shield ring 400.
  • Vibration may occur in the motor housing 100 as the rotor 200 rotates.
  • the contact between the carbon ring 621 and the shield ring 400 can be temporarily released when vibration occurs. That is, the distance between the carbon ring 621 and the shield ring 400 increases, and the slit SL can be formed.
  • the gas pressurized by the impeller 700 can be introduced into the interior of the motor housing 100 through the slit SL between the carbon ring 621 and the shield ring 400. Since the slit SL formed between the carbon ring 621 and the shield ring 400 is generated by vibration, the slit SL can be formed to have a very small width. As a result, the expansion rate of the pressurized gas increases, and the temperature reduction efficiency of the gas can be improved.
  • FIG. 11 is a perspective view of a labyrinth seal according to another embodiment of the present invention
  • FIG. 12 is a view showing gas moving by the labyrinth seal shown in FIG.
  • the labyrinth seal 602 may include a blade 612 and an elastic ring 622.
  • the elastic ring 622 may be provided on the inner side of the blade 612 to contact the shield ring 400.
  • the elastic ring 622 has an elastic force of a predetermined magnitude or more and may be formed along the edge of the through hole H of the labyrinth seal 602.
  • the elastic ring 622 can be in contact with the shield ring 400.
  • the space on the side of the impeller 700 and the inside of the motor housing 100 can be completely shut off as the elastic ring 622 contacts the shield ring 400.
  • the elastic ring 622 may have the form of a disc.
  • the elastic ring 622 can be deformed by the pressurized gas.
  • the ring-shaped slit SL can be formed between the elastic ring 622 and the shielding ring 400 as the elastic ring 622 is deformed.
  • the pressurized gas passing through the slit SL can be inflated and introduced into the interior of the motor housing 100 in a state where the temperature is reduced.
  • the slit SL formed between the elastic ring 622 and the shield ring 400 is formed by the force of the pressurized gas, the width thereof can be made very small. As a result, the expansion rate of the pressurized gas increases and the temperature reduction efficiency of the gas can be improved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

La présente invention concerne un compresseur, et concerne un compresseur qui permet à un gaz expansé pour le refroidissement de s'écouler dans un moteur à travers une roue et une pale d'un joint à labyrinthe disposé à une entrée du moteur. Un mode de réalisation de la présente invention comprend : une hélice qui pressurise un gaz tout en tournant ; un rotor couplé à la roue à aubes et disposé dans un carter de moteur, de façon à transmettre une puissance de rotation à la roue à aubes ; et un joint à labyrinthe disposé entre la roue à aubes et le rotor, de façon à restreindre le gaz mis sous pression par la roue à aubes de s'écouler dans le carter de moteur, le joint à labyrinthe comprenant une seule pale.
PCT/KR2018/001516 2018-01-11 2018-02-05 Compresseur WO2019139199A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201880086114.9A CN111587323B (zh) 2018-01-11 2018-02-05 压缩机

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR10-2018-0003647 2018-01-11
KR1020180003647A KR102474772B1 (ko) 2018-01-11 2018-01-11 압축기

Publications (1)

Publication Number Publication Date
WO2019139199A1 true WO2019139199A1 (fr) 2019-07-18

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KR (1) KR102474772B1 (fr)
CN (1) CN111587323B (fr)
WO (1) WO2019139199A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022044764A1 (fr) * 2020-08-24 2022-03-03 株式会社Ihi Compresseur de suralimentation électrique

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007040255A (ja) * 2005-08-05 2007-02-15 Ishikawajima Harima Heavy Ind Co Ltd 電動機付過給機
JP2014240612A (ja) * 2013-06-11 2014-12-25 株式会社Ihi 遠心圧縮機及び過給機
KR20160074326A (ko) * 2014-12-18 2016-06-28 엘지전자 주식회사 터보압축기
KR20160113768A (ko) * 2015-03-23 2016-10-04 한온시스템 주식회사 차량용 공기 블로어
KR20170061507A (ko) * 2015-11-26 2017-06-05 한온시스템 주식회사 차량용 공기 압축기

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JP2011220264A (ja) * 2010-04-12 2011-11-04 Honda Motor Co Ltd 遠心型圧縮機
JP5600542B2 (ja) * 2010-09-29 2014-10-01 株式会社神戸製鋼所 回転機械の軸封装置
CN202228134U (zh) * 2011-10-18 2012-05-23 高现仁 焦炉余热发电汽轮机汽封
CN204239765U (zh) * 2014-09-14 2015-04-01 许亚峰 一种迷宫密封结构
DE102014224283A1 (de) * 2014-11-27 2016-06-02 Robert Bosch Gmbh Verdichter mit einem Dichtkanal
CN106286338A (zh) * 2015-06-02 2017-01-04 上海优耐特斯压缩机有限公司 对采用高速电机的离心压缩机泄漏空气进行冷却的结构
KR101812402B1 (ko) 2016-01-08 2017-12-27 두산중공업 주식회사 터빈의 복합 실링 구조

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007040255A (ja) * 2005-08-05 2007-02-15 Ishikawajima Harima Heavy Ind Co Ltd 電動機付過給機
JP2014240612A (ja) * 2013-06-11 2014-12-25 株式会社Ihi 遠心圧縮機及び過給機
KR20160074326A (ko) * 2014-12-18 2016-06-28 엘지전자 주식회사 터보압축기
KR20160113768A (ko) * 2015-03-23 2016-10-04 한온시스템 주식회사 차량용 공기 블로어
KR20170061507A (ko) * 2015-11-26 2017-06-05 한온시스템 주식회사 차량용 공기 압축기

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022044764A1 (fr) * 2020-08-24 2022-03-03 株式会社Ihi Compresseur de suralimentation électrique
JP7416271B2 (ja) 2020-08-24 2024-01-17 株式会社Ihi 電動過給機

Also Published As

Publication number Publication date
CN111587323B (zh) 2022-08-26
KR102474772B1 (ko) 2022-12-05
CN111587323A (zh) 2020-08-25
KR20190085594A (ko) 2019-07-19

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