EP2857692A1 - Turbokompressionssystem - Google Patents

Turbokompressionssystem Download PDF

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Publication number
EP2857692A1
EP2857692A1 EP20130796768 EP13796768A EP2857692A1 EP 2857692 A1 EP2857692 A1 EP 2857692A1 EP 20130796768 EP20130796768 EP 20130796768 EP 13796768 A EP13796768 A EP 13796768A EP 2857692 A1 EP2857692 A1 EP 2857692A1
Authority
EP
European Patent Office
Prior art keywords
flow path
valve
impeller
compression
outlet
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.)
Withdrawn
Application number
EP20130796768
Other languages
English (en)
French (fr)
Other versions
EP2857692A4 (de
Inventor
Heon Seok Lee
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.)
Boge Kompressoren Otto Boge GmbH and Co KG
Original Assignee
Kturbo Inc
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 Kturbo Inc filed Critical Kturbo Inc
Publication of EP2857692A1 publication Critical patent/EP2857692A1/de
Publication of EP2857692A4 publication Critical patent/EP2857692A4/de
Withdrawn legal-status Critical Current

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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
    • F04D29/26—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
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage 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
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/04—Units comprising pumps and their driving means the pump being fluid driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/12—Combinations of two or more 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
    • 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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage 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
    • F04D19/00—Axial-flow pumps
    • F04D19/02—Multi-stage pumps
    • F04D19/04—Multi-stage pumps specially adapted to the production of a high vacuum, e.g. molecular 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
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0269—Surge control by changing flow path between different stages or between a plurality of compressors; load distribution between compressors

Definitions

  • the present disclosure relates to a turbo compression system, in detail, the turbo compression system which has plural design points; the characteristics of two-stage turbo compression system and single-stage dual-intake turbo compression system to be selectively converted.
  • Turbo compression system is a system which intakes, compresses and discharges fluids or gases such as refrigerant by the rotation of Impeller installed inside a turbo compressor.
  • turbo compression system is characterized in that the discharge pressure is relatively high.
  • the high-speed rotation of the impeller is embodied by a multiplying gear connected with a constant speed motor.
  • the impeller has been direct connected with the motor.
  • Korean Patent No. 0273433 discloses a turbo compression system having two Compressing Devices which efficiently improves cooling effectiveness of motor by activating circulation of refrigerant which flows into a motor and Korean Patent No. 0304562 discloses a turbo compression system which is easy to process and assemble radial supporting means.
  • the conventional turbo compression system have a problem that the maximum flow rate under the low compression ratio in comparison with the one design point gets smaller than that of a single-stage dual-intake turbo compression system which has two compressing devices.
  • An object of the present disclosure is to provide a turbo compression system having two compressing devices which allows selective conversion between one design point of two-stage turbo compression system for high pressure and the other design point of the single-stage dual-intake turbo compression system for low pressure.
  • an aspect of a turbo compression system comprises a first impeller having a first inlet and a first outlet, compressing fluid flowing in through the first inlet by rotation motion and then discharging out through the first outlet; a second impeller having a second inlet and a second outlet, compressing fluid flowing in through the second inlet by rotation motion and then discharging out through the second outlet; a second discharge flow path connected with the second outlet; a first discharge flow path communicating the second discharge flow path with the first outlet; a first valve provided at the first discharge flow path and controlling flowing of the fluid; a second intake flow path connected with the second inlet and selectively making the fluid flow into the second impeller; a second valve provided at one end of the second intake flow path; and a compression flow path connected with the first valve at one end of the compression flow path and connecting with the second intake flow path at the other end of the compression flow path.
  • the turbo compression system further may comprise a motor having two rotation shafts provided at one side and the other side of the motor and respectively coupled with the first impeller and the second impeller.
  • the first valve may selectively convert between a two-stage compression path in which fluid flowing into the first Inlet are compressed and discharged, passing through the first impeller and the second impeller in sequence and a single-stage compression path in which fluids flowing out of the first outlet and the second outlet are joined and discharged.
  • the second valve may be shut off in case fluid is controlled to flow along with the two-stage compression path, and the second valve may open in case fluid is controlled to flow along with the single-stage compression path.
  • the first valve may control so as to operate as either two-stage turbo compression system or single-stage turbo compression system by selectively opening or closing.
  • the first impeller and the second impeller may have same-sized diameter.
  • the turbo compression system further may comprise a first motor which is connected to the first impeller and rotates the first impeller; and a second motor which is provided separately from the first motor and connected to the second impeller and rotates the second impeller.
  • the first valve may be provided as a three-way valve which communicates either the second discharge flow path or the compression flow path with the first discharge flow path, and the second valve may be provided further away from the second inlet than a distance from a position joining the compression flow path with the second intake flow path, and is provided as a solenoid valve which opens and closes the second intake flow path.
  • the first valve may be provided as a three-way valve which communicates either the second discharge flow path or the compression flow path with the first discharge flow path
  • the second valve is provided at the coupling site of compression flow path and the second intake flow path and also provided as a three-way valve which communicates the second intake flow path with the compression flow path.
  • the first valve may selectively convert between a two-stage compression path in which fluid flowing into the first inlet and passing through the first impeller and the second impeller in sequence, are compressed and discharged, and a single-stage compression flow path in which fluid flowing out of the first outlet and the second outlet are joined and discharged.
  • the second valve may be controlled to communicate the second intake flow path with the second compression flow Path, and in case fluid is controlled to flow along with the single-stage compression path, the second valve may be controlled to communicate the second intake flow path with the Inflow path.
  • the first valve and the second valve are provided as three-way valves.
  • An aspect of a turbo compression system according to the present disclosure may have advantage to increase the maximum flow rate to be capable of operating at a low pressure region over a two-stage turbo compression system with an equivalent capacity.
  • an aspect of a turbo compression system according to the present disclosure may have advantage to increase the operating range to be capable of operating with the minimum flow rate at a low pressure region by operating an aspect of a turbo compression system according to the present disclosure at the design point of the two-stage turbo compression system.
  • FIG. 1 is a view showing schematically a turbo compression system according to the first embodiment of the present disclosure
  • FIG. 2 is a view showing an operating status of the turbo compression system of FIG. 1 , which is operated at the design point(D2) of the two-stage turbo compression system for high pressure
  • Fig. 3 is a view showing an operating status of the turbo compression system of FIG. 1 , which is operated at the design point (D1) of the single-stage dual-intake turbo compression system for low pressure.
  • a turbo compression system 100 comprises a first impeller 120 connected at a outlet of the first impeller 120 with a first discharge flow path 121 which is connected to a second discharge flow path 170 with a first valve(130), a second impeller 160 connected to a second intake flow path 151 in which a fluid is flown by a second valve 150 and connected with a second discharge flow path 170 at a outlet of the second impeller 160, a motor 110 driving the first impeller 120 and the second impeller 160, and a compression flow path 141 of which one end is connected to the first valve 130 and the other end is coupled to the second intake flow path 151 at the downstream of the second valve(150).
  • the first valve 130 is desirable to be provided with a three-way valve and the second valve 150 is desirable to be provided with a solenoid valve.
  • the first valve 130 and the second valve 150 are provided to be capable of controlling their on/off action. Thereby we may select either an operating at the design point (D2) of two-stage turbo compression system for high pressure or an operating at the design point (D1) of single-stage dual-intake turbo compression system for low pressure. It will be described later in detail referring to Fig. 4 .
  • the turbo compression system 100 since the flow path of intake fluid or discharge fluid may be controlled by properly operating the first valve 130 and the second valve 150, the turbo compression system 100 according to the first embodiment of the present disclosure may selectively accomplish one of the single-stage dual-intake turbo compression system under low pressure, the two-stage turbo compression system discharging maximum flow rate under high pressure, and the two-stage turbo compression system discharging minimum flow rate under low pressure.
  • the turbo compression system 100 in case that the second valve 150 is closed and the first valve 130 is controlled to connect the first discharge flow path 121 with the compression flow path 141, the turbo compression system 100 according to the present embodiment operates as the two-stage turbo compression system which can discharge maximum flow rate under high pressure or minimum flow rate under low pressure.
  • the turbo compression system 100 in case that the second valve 150 is open and the first valve 130 is controlled to connect the first discharge flow path 121 with the second discharge flow path 170 and close the compression flow path 141, the turbo compression system 100 according to the present embodiment operates as the single-stage dual-intake turbo compression system which can discharge the flow rate of design point (D1) under low pressure of design point (Dl).
  • the fluid flowing into the first impeller 120 through the first intake path (i) is compressed by the first impeller 120 (single stage compression) and then discharged through the second discharge flow path 170
  • the fluid flowing into the second impeller 160 through the second valve 150 is compressed by the second impeller 160 (single stage compression) and then discharged through the second discharge flow path 170.
  • the operating range to be capable of operating with the minimum flow rate at a low pressure region is increased by operating the turbo compression system 100 according to the present embodiment at the design point (D2) of the two-stage turbo compression system.
  • Fig. 4 is a view showing a pressure (P) -flow rate(Q) diagram at design points(Dl, D2) of the turbo compression system of FIG. 1 .
  • the turbo compression system 100 by properly controlling the operation of the valves 130 and 150, may selectively accomplish one of the two-stage turbo compression system operating at the design point D2 which discharges maximum flow rate under high pressure or discharges minimum flow rate under low pressure, the single-stage dual-intake turbo compression system operating at the design point Dl.
  • the turbo compression system 100 may have the characteristics of both the two-stage turbo compression system and the single-stage dual-intake turbo compression system, because of that, the operating range to be capable of operating with the minimum flow rate at a low pressure region may be increased.
  • the first impeller 120 and the second impeller 160 which are driven by single motor have same-sized diameter in order to have the same compression ratio at an equal rotation speed of the motor.
  • the impellers 120 and 160 may have ones with same-sized diameter or ones with different-sized diameter. That's because it is possible to control compression ratio as much as want by controlling motors separately, when using separate motors.
  • FIG. 5 is a view showing schematically a turbo compression system according to the second embodiment of the present disclosure
  • FIG. 6 is a view showing an operating status of the turbo compression system of FIG. 5 , which is operated at the design point(D2) of the two-stage turbo compression system for high pressure
  • Fig. 7 is a view showing an operating status of the turbo compression system of FIG. 5 , which is operated at the design point (D1) of the single-stage dual-intake turbo compression system for low pressure.
  • the turbo compression system 200 comprises a first impeller 220 connected to a first discharge flow path 232 at its outlet and communicating with a second discharge flow path 270 by passing through a first valve 230 and a first compression flow path 231 in sequence, a first motor 210 driving the first impeller 220, a second impeller 260 connected at its outlet to the second discharge flow path 270 and connected at its inlet to a second intake flow path 243 having a second valve 240 which selectively closes one of the second compression flow path 241 branching off from the second discharge flow path 270 at the first valve 230 and a intake flow path 242 for inflowing fluid to be compressed from outside, and a second motor 250 driving the second impeller 220.
  • first valve 230 and the second valve 240 are also provided with a three-way valve.
  • the turbo compression system 200 may operate as the two-stage turbo compression system which can discharge maximum flow rate under high pressure or minimum flow rate under low pressure.
  • the first valve 230 is controlled to be connected to the second compression flow path 241, and the second valve 240 is controlled to be shut off so as to prevent from inflowing fluid through the intake flow path and also controlled to flow the fluid passing through the first valve 230 into the second impeller 260.
  • first stage compression after the fluid flowing into the first impeller 120 through a first intake flow path 221 is firstly compressed by the first impeller 220 (first stage compression), it is secondary compressed by the second impeller 260 (second stage compression) in which the fluid flows through the second compression flow path 241 and then the fluid is discharged through the second discharge flow path 270.
  • the turbo compression system 100 may operate as the single-stage dual-intake turbo compression system which can discharge the flow rate of design point (D1) under low pressure of design point (Dl).
  • the first valve 230 is open so as to communicating with the first compression flow path 231 and the second valve 240 is controlled to communicating the intake flow path 241 with the second intake flow path 243 so as to allow the fluid to flow in from outside.
  • the fluid flowing into the first impeller 120 through the first intake flow path 221 is compressed by the first impeller 220 (single stage compression) and then discharged through the second discharge flow path 270
  • the fluid flowing into the second impeller 260 through the second valve 250 is compressed by the second impeller 260 (single stage compression) and then discharged through the second discharge flow path 270.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)
EP13796768.3A 2012-05-31 2013-05-31 Turbokompressionssystem Withdrawn EP2857692A4 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR20120058317A KR101360799B1 (ko) 2012-05-31 2012-05-31 2단 터보압축기
PCT/KR2013/004851 WO2013180538A1 (ko) 2012-05-31 2013-05-31 터보압축 시스템

Publications (2)

Publication Number Publication Date
EP2857692A1 true EP2857692A1 (de) 2015-04-08
EP2857692A4 EP2857692A4 (de) 2016-03-02

Family

ID=49673654

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13796768.3A Withdrawn EP2857692A4 (de) 2012-05-31 2013-05-31 Turbokompressionssystem

Country Status (6)

Country Link
US (1) US20150110606A1 (de)
EP (1) EP2857692A4 (de)
JP (1) JP2015518113A (de)
KR (1) KR101360799B1 (de)
CN (1) CN104364530A (de)
WO (1) WO2013180538A1 (de)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9938967B2 (en) 2014-10-29 2018-04-10 Emerson Climate Technologies, Inc. Reciprocating compressor system
CN107044437A (zh) * 2017-05-22 2017-08-15 无锡商业职业技术学院 多级压缩机的调节控制系统

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR577936A (fr) * 1923-02-27 1924-09-12 Erste Bruenner Maschinen Fab Compresseur rotatif polyétagé
CH347295A (de) * 1955-09-19 1960-06-30 Gutehoffnungshuette Sterkrade Verfahren und Einrichtung zur Erhöhung der Wirtschaftlichkeit mehrstufiger Turbokompressoren
FR1334393A (fr) * 1962-06-18 1963-08-09 Rateau Soc Perfectionnement aux dispositifs d'antipompage pour batterie ou groupe de compresseurs
JPS5025105U (de) * 1973-06-28 1975-03-22
KR100253250B1 (ko) 1998-02-26 2000-05-01 구자홍 터보 압축기
KR19990075384A (ko) * 1998-03-20 1999-10-15 이헌석 소형터보압축기
KR100273433B1 (ko) 1998-07-01 2001-01-15 구자홍 터보압축기의 구동모터 냉각구조
KR100304562B1 (ko) 1998-07-23 2001-12-12 구자홍 터보압축기
JP2000097189A (ja) * 1998-09-21 2000-04-04 Teral Kyokuto Inc 増速給水ポンプの配管及び運転制御方法及び制御装置
KR100421390B1 (ko) * 2001-11-20 2004-03-09 엘지전자 주식회사 터보 압축기 냉각장치
US7107972B1 (en) * 2004-08-03 2006-09-19 Accessible Technologies, Inc. Multi-phase centrifugal supercharging air induction system
JP2007064139A (ja) * 2005-09-01 2007-03-15 Shimadzu Corp 高速回転装置
DE102007024584B4 (de) * 2007-05-25 2010-06-02 Audi Ag Vorrichtung zur Aufladung von Brennkraftmaschinen
US20110038737A1 (en) * 2007-11-01 2011-02-17 Ronald David Conry Multi-stage compressor
JP5176574B2 (ja) * 2008-02-06 2013-04-03 株式会社Ｉｈｉ ターボ圧縮機及び冷凍機
GB2469015B (en) * 2009-01-30 2011-09-28 Compair Uk Ltd Improvements in multi-stage centrifugal compressors
JP5320366B2 (ja) * 2010-09-28 2013-10-23 株式会社神戸製鋼所 圧縮装置

Also Published As

Publication number Publication date
CN104364530A (zh) 2015-02-18
US20150110606A1 (en) 2015-04-23
WO2013180538A1 (ko) 2013-12-05
KR101360799B1 (ko) 2014-02-12
KR20130134656A (ko) 2013-12-10
EP2857692A4 (de) 2016-03-02
JP2015518113A (ja) 2015-06-25

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