EP2559904A1 - Compresseur centrifuge - Google Patents

Compresseur centrifuge Download PDF

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Publication number
EP2559904A1
EP2559904A1 EP10849813A EP10849813A EP2559904A1 EP 2559904 A1 EP2559904 A1 EP 2559904A1 EP 10849813 A EP10849813 A EP 10849813A EP 10849813 A EP10849813 A EP 10849813A EP 2559904 A1 EP2559904 A1 EP 2559904A1
Authority
EP
European Patent Office
Prior art keywords
vane blade
diffuser
side chamber
blade
deformation
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
EP10849813A
Other languages
German (de)
English (en)
Other versions
EP2559904A4 (fr
EP2559904B1 (fr
Inventor
Masakazu Tabata
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.)
Toyota Motor Corp
Original Assignee
Toyota Motor 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 Toyota Motor Corp filed Critical Toyota Motor Corp
Publication of EP2559904A1 publication Critical patent/EP2559904A1/fr
Publication of EP2559904A4 publication Critical patent/EP2559904A4/fr
Application granted granted Critical
Publication of EP2559904B1 publication Critical patent/EP2559904B1/fr
Not-in-force 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
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet

Definitions

  • the present invention relates to a centrifugal compressor in which a vane blade is able to be moved into and out of a diffuser passage.
  • the diaphragm is formed integrally with the vane blade. Therefore, when the diaphragm is not able to be deformed in an accurate manner because of variation in the thickness of the diaphragm or difference in the hardness of a part of the diaphragm from the others thereof, the direction of protrusion of the vane blade will deviate from a specified direction. When the direction of protrusion of the vane blade deviates from the specified direction, the vane blade may bite a peripheral edge portion of a slit through which the vane blade is caused to protrude into the diffuser passage. In addition, the friction at the time of the vane blade passing through the slit may become large, thus giving rise to wear of the vane blade and an increase in a driving force for operating the vane blade.
  • the present invention has been made in view of the above-mentioned circumstances, and has for its object to provide a technique in a centrifugal compressor in which the direction of protrusion of a vane blade is avoided from deviating from a specified direction as a result of a deformation of a deformation member.
  • the present invention resides in a centrifugal compressor which is provided with:
  • a portion of the deformation member, being in contact with the vane blade is not only displaced in the specified direction to cause the vane blade to protrude into the diffuser passage, but also can be displaced in a direction other than the specified direction, too.
  • the vane blade may also move not in the specified direction but in the direction other than the specified direction, in accordance with the deformation of the deformation member.
  • the vane blade and the deformation member are separate bodies from each other.
  • the displacement in the direction other than the specified direction of the portion of the deformation member in contact with the vane blade only causes the portion of the deformation member in contact with the vane blade to move with respect to the vane blade, but does not act on the vane blade, thus making it difficult for the vane blade to move in a direction other than the specified direction.
  • only a displacement in the specified direction of the portion of the deformation member in contact with the vane blade acts on the vane blade, thereby causing the vane blade to move in the specified direction. Accordingly, it is possible to avoid the direction of protrusion of the vane blade from deviating from the specified direction as a result of the deformation of the deformation member.
  • the predetermined amount is an amount which, when the amount of protrusion is equal to or less than that amount, can deal with a case where the operation flow rate of the centrifugal compressor is a large flow rate.
  • the deformation member in cases where the amount of protrusion of the vane blade into the diffuser passage is equal to or less than the predetermined amount, the deformation member can be caused to separate from the vane blade positioned by the stopper. As a result of this, it is possible to avoid heat transfer from the vane blade to the deformation member. Accordingly, it is possible to suppress the deformation member from being thermally deteriorated resulting from the heat transfer from the vane blade.
  • the volume of said anti-diffuser side chamber may be made small until said deformation member and said vane blade positioned by said stopper are separated from each other.
  • the centrifugal compressor operates to make air to be supplied at a high flow rate and at a high supercharging pressure
  • the air flowing through the diffuser passages becomes a high temperature
  • the vane blade which has been caused to be buried into the diffuser passage wall, is similarly at a high temperature.
  • the volume of the anti-diffuser side chamber is made small until the deformation member and the vane blade positioned by the stopper are separated from each other, so the deformation member and the vane blade are separated or away from each other, thus making it possible to avoid the heat transfer from the vane blade of the high temperature to the deformation member.
  • Fig. 1 is a view showing the schematic construction of a centrifugal compressor according to a first embodiment of the present invention.
  • the centrifugal compressor 1 shown in Fig. 1 is provided with a scroll casing 2, and it has an impeller 3 arranged in an axial center inside the scroll casing 2. Air as a gas, which has flowed into the centrifugal compressor 1, is guided to flow into a diffuser passage 5 formed on an outer peripheral side of the impeller 3 by means of vanes 4 which are arranged in a circumferential direction of the impeller 3 at equal intervals.
  • the diffuser passage 5 is sandwiched or enclosed by diffuser passage walls, which are part of the scroll casing 2.
  • One of the diffuser passage walls on a left-hand side of Fig. 1 is composed of a plate-shaped diffuser plate 6, and is formed separately from a casing main body.
  • Space 7, which can be covered with the diffuser plate 6, is formed in the one diffuser passage wall (hereinafter referred to as the diffuser passage wall) on which the diffuser plate 6 is arranged.
  • the space 7 is of a hollow cylindrical shape, and can receive a vane blade 8 which is movable into and out of the interior of the diffuser passage 5.
  • the vane blade 8 is provided with an annular disk 9, and a plurality of blade portions 10 which have their one ends fixed to the disk 9 and are arranged in a circumferential direction at intervals.
  • the diffuser plate 6 is formed with slits 11 into which the blade portions 10 of the vane blade 8 are inserted, respectively. With this construction, when the disk 9 of the vane blade 8 is brought close to the diffuser plate 6, the blade portions 10 of the vane blade 8 protrude from the slits 11, respectively, into the diffuser passage 5.
  • a diaphragm 12 as a deformation member, which serves to divide the space 7 into a diffuser side chamber 7a and an anti-diffuser side chamber 7b, and to deform to change the volume of the anti-diffuser side chamber 7b.
  • the diaphragm 12 is of an annular shape which can swell or expand in the direction of the diffuser side chamber 7a, and is composed of a rubber-like elastic body so as to be elastically deformable, and has an outer edge and an inner edge both fixedly secured to the wall of the space 7 in an airtight manner.
  • the diaphragm 12 can push the disk 9 of the vane blade 8 toward the side of the diffuser passage 5 by being swelled or expanded in a manner such that the anti-diffuser side chamber 7b is made larger.
  • the diaphragm 12 and the disk 9 are different bodies from each other. If the diaphragm 12 has not been deformed to swell, the diaphragm 12 and the disk 9 are separated or away from each other. In other words, the diaphragm 12 is able to be moved away from the disk 9 of the vane blade 8 that is positioned by stoppers 13, by decreasing the volume of the anti-diffuser side chamber 7b.
  • a compression spring 14 as an urging member, which serves to urge the disk 9 of the vane blade 8 so as to cause the vane blade 8 to be buried in the diffuser passage wall.
  • the compression spring 14 is compressed inside the diffuser side chamber 7a, and urges the disk 9 in a direction opposite to the direction of the diffuser passage 5.
  • a stopper 13 which serves to position the disk 9 of the vane blade 8 against the urging of the compression spring 14. If the disk 9 abuts against the stoppers 13 in a state urged by the compression springs 14, respectively, so that there will be no action due to the swelling or expanding deformation of the diaphragms 12, the vane blade 8 can be maintained in a state in which it is caused to be buried in the diffuser passage 5.
  • the centrifugal compressor 1 of this embodiment is provided with a fluid pressure adjusting mechanism 15 which serves to apply fluid pressure to the anti-diffuser side chamber 7b. Between the fluid pressure adjusting mechanism 15 and the anti-diffuser side chamber 7b, there is arranged a fluid passage 16 which circulates or supply fluid from the fluid pressure adjusting mechanism 15 to the anti-diffuser side chamber 7b.
  • Fig. 2 is views showing a protruded state and a buried state of the vane blade according to this embodiment, wherein Fig. 2A shows the protruded state in which the vane blade has been protruded into the diffuser passage, and Fig. 2B shows the buried state in which the vane blade has been buried in the diffuser passage wall.
  • the fluid pressure adjusting mechanism 15 causes fluid to flow into the anti-diffuser side chamber 7b thereby to pressurize the anti-diffuser side chamber 7b, so that the diaphragm 12 is caused to perform swelling deformation, thus increasing the volume of the anti-diffuser side chamber 7b.
  • the diaphragm 12 is displaced to push the disk 9 of the vane blade 8, so the disk 9 is moved in the specified direction of an illustrated arrow A to cause the blade portions 10 of the vane blade 8 to protrude into the diffuser passage 5, whereby the blade portions 10 of the vane blade 8 are protruded from the slits 11, respectively, into the diffuser passage 5, as shown in Fig. 2(a) .
  • Fig. 3 is a view showing a problem of a conventional vane blade.
  • a portion of the diaphragm, being in contact with a disk of the vane blade is not only displaced in a specified direction to cause the disk of the vane blade to protrude into a diffuser passage, but also can be displaced in a direction other than the specified direction, too.
  • the portion of the diaphragm in contact with the disk of the vane blade as shown in a region C of Fig.
  • the vane blade may not move in the specified direction shown by a broken line arrow, in accordance with the swelling deformation of the diaphragm as shown by an arrow B, but may move in a direction other than the specified direction, as shown in the arrow B. If so, the direction of protrusion of the blade portions of the vane blade may deviate from the specified direction, and the blade portions of the vane blade may bite peripheral edge portions of slits to stop moving.
  • Fig. 4 is a view showing a feature of the vane blade according to this first embodiment.
  • the vane blade 8 and a diaphragm 12 are different or separate bodies from each other, and in a portion shown in a region D of Fig. 4 , the diaphragm 12 is only in contact with the disk 9 of the vane blade 8.
  • the fluid pressure adjusting mechanism 15 suck fluid from the anti-diffuser side chamber 7b thereby to reduce the pressure in the anti-diffuser side chamber 7b, so that the diaphragm 12 is caused to perform deflating or retracting deformation, thus decreasing the volume of the anti-diffuser side chamber 7b.
  • the disk 9 is urged by means of the compression springs 14 to abut against the stoppers 13 to be positioned thereby, so that the blade portions 10 of the vane blade 8 are respectively buried in the diffuser passage wall, as shown in Fig. 2B .
  • the fluid pressure adjusting mechanism 15 operates to make small the volume of the anti-diffuser side chamber 7b until it separates the diaphragm 12 from the disk 9 of the vane blade 8 positioned by the stoppers 13, so that the diaphragm 12 takes a steady shape which is not deformed. For this reason, as shown in Fig. 2B , the diaphragm 12 and the disk 9 of the vane blade 8 positioned by the stoppers 13 are separated or away from each other.
  • the centrifugal compressor 1 is operated to make air to be supplied at a high flow rate and at a high supercharging pressure
  • the air flowing through the diffuser passage 5 becomes a high temperature of about 180 degrees C
  • the vane blade 8, which has been buried in the diffuser passage wall is similarly at a high temperature through the action of the air which flows in from the slits 11.
  • the volume of the anti-diffuser side chamber 7b is made small by means of the fluid pressure adjusting mechanism 15 until the diaphragm 12 is separated or away from the disk 9 of the vane blade 8 positioned by the stoppers 13, the diaphragm 12 and the disk 9 of the vane blade 8 are separated or away from each other, thus making it possible to avoid heat transfer from the vane blade 8 of the high temperature to the diaphragm 12.
  • the centrifugal compressor 1 operates so as to make air to be supplied at a high flow rate and at a high supercharging pressure, it is possible to suppress the diaphragm 12, which is rubber-like elastic body, from being thermally deteriorated resulting from the heat transfer from the vane blade 8 of the high temperature, thereby making it possible to improve the endurance reliability of the diaphragm 12.
  • the centrifugal compressor according to the present invention is not limited to the above-mentioned embodiment, but can be subjected to various changes and modifications within the scope not departing from the gist of the present invention.
  • the deformation members there may be used bellows, besides the diaphragms, and as a material therefor, there may also be used resin, metal or the like, besides a rubber-like elastic material.
  • the volume of the anti-diffuser side chamber can be made small by continuously reducing fluid pressure by means of the fluid pressure adjusting mechanism.
  • the driving force to cause the diaphragm to deform may not be adjusted by fluid pressure supplied by means of the fluid pressure adjusting mechanism.
  • the urging members besides the compression springs, there may be used rubber-like elastic bodies, elastic bodies using resin, or the like, in addition to tension springs.
  • the stoppers position the vane blade against the urging of the compression springs there may not only be a case where the vane blade is in a position in which it is buried in the diffuser passage wall, but also a case where the amount of protrusion of the vane blade into the diffuser passage is equal to or less than a predetermined amount.
  • the predetermined amount is an amount which, when the amount of protrusion is equal to or less than that amount, can deal with a case where the operation flow rate of the centrifugal compressor is a large flow rate.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP10849813.0A 2010-04-13 2010-04-13 Compresseur centrifuge Not-in-force EP2559904B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2010/056595 WO2011128975A1 (fr) 2010-04-13 2010-04-13 Compresseur centrifuge

Publications (3)

Publication Number Publication Date
EP2559904A1 true EP2559904A1 (fr) 2013-02-20
EP2559904A4 EP2559904A4 (fr) 2014-12-10
EP2559904B1 EP2559904B1 (fr) 2016-11-23

Family

ID=44798368

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10849813.0A Not-in-force EP2559904B1 (fr) 2010-04-13 2010-04-13 Compresseur centrifuge

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Country Link
EP (1) EP2559904B1 (fr)
JP (1) JP5348316B2 (fr)
WO (1) WO2011128975A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107642506A (zh) * 2017-10-24 2018-01-30 珠海格力电器股份有限公司 一种调节器结构及具有该调节器结构的离心压缩机
CN109356886A (zh) * 2018-12-17 2019-02-19 珠海格力电器股份有限公司 离心式压缩机及扩压器装置

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001329996A (ja) * 2000-05-24 2001-11-30 Ishikawajima Harima Heavy Ind Co Ltd 可変ディフューザ付き遠心圧縮機とその制御方法
DE102006009354A1 (de) * 2006-03-01 2007-09-06 Bayerische Motoren Werke Ag Zentrifugalverdichter

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4333047B2 (ja) * 2001-01-12 2009-09-16 株式会社豊田自動織機 容量可変型圧縮機の制御弁
JP3818142B2 (ja) * 2001-12-13 2006-09-06 石川島播磨重工業株式会社 遠心圧縮機

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001329996A (ja) * 2000-05-24 2001-11-30 Ishikawajima Harima Heavy Ind Co Ltd 可変ディフューザ付き遠心圧縮機とその制御方法
DE102006009354A1 (de) * 2006-03-01 2007-09-06 Bayerische Motoren Werke Ag Zentrifugalverdichter

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2011128975A1 *

Also Published As

Publication number Publication date
JP5348316B2 (ja) 2013-11-20
WO2011128975A1 (fr) 2011-10-20
EP2559904A4 (fr) 2014-12-10
JPWO2011128975A1 (ja) 2013-07-11
EP2559904B1 (fr) 2016-11-23

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