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WO2010117868A2 - Machine de compression à double fonction - Google Patents

Machine de compression à double fonction Download PDF

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Publication number
WO2010117868A2
WO2010117868A2 PCT/US2010/029595 US2010029595W WO2010117868A2 WO 2010117868 A2 WO2010117868 A2 WO 2010117868A2 US 2010029595 W US2010029595 W US 2010029595W WO 2010117868 A2 WO2010117868 A2 WO 2010117868A2
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
compression machine
mode
water
duty
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.)
Ceased
Application number
PCT/US2010/029595
Other languages
English (en)
Other versions
WO2010117868A3 (fr
Inventor
Haiping Ding
Michael A. Stark
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.)
Carrier Corp
Original Assignee
Carrier 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 Carrier Corp filed Critical Carrier Corp
Priority to US13/255,198 priority Critical patent/US20110314847A1/en
Priority to CN201080015309.8A priority patent/CN102388223B/zh
Publication of WO2010117868A2 publication Critical patent/WO2010117868A2/fr
Publication of WO2010117868A3 publication Critical patent/WO2010117868A3/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • 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

  • This invention relates generally to compression machines for building cooling and heating application or ice thermal storage application and, more particularly, to a compression machine having dual compressors, one compressor dedicated for water chilling and the other compressor dedicated for water heating or ice thermal storage.
  • a common type of compression chiller includes a tube-in-shell heat exchanger that functions as a refrigerant vapor condenser, a tube-in-shell heat exchanger that functions as a refrigerant liquid evaporator, and a centrifugal compressor that has an inlet in refrigerant flow communication with the evaporator and an outlet in refrigerant flow communication with the condenser.
  • water is passed through the heat exchange tubes in heat exchange relationship with hot refrigerant vapor discharged from the compressor into the shell of the condenser and flowing over the heat exchange tubes.
  • the refrigerant vapor is condensed and the water flowing through the heat exchange tubes is heated.
  • the condensed liquid refrigerant is passed through an expansion device and thereby expanded to form a lower pressure, lower temperature refrigerant liquid/vapor mixture.
  • the refrigerant liquid/vapor mixture is delivered into the shell of the evaporator and dispersed to flow over the heat exchange tubes therein.
  • water passing through the heat exchange tubes is cooled and the refrigerant liquid/vapor mixture is heated and the liquid refrigerant evaporated.
  • the refrigerant vapor exits the shell of the evaporator and passes back the inlet of the compressor, thereby completing the refrigerant flow circuit.
  • compression machines of this type typically employ a single compressor
  • compression machines employing two compressors are also known.
  • a compression chiller using two individual centrifugal compressors arranged in series is disclosed in U.S. Pat. No. 5,875,637.
  • the first compressor receives through its inlet low pressure refrigerant vapor from the evaporator and discharges refrigerant vapor at an intermediate pressure to the inlet of the second compressor.
  • the refrigerant vapor is further compressed in the second compressor and discharged to the condenser at a relatively higher discharge pressure.
  • a compression machine provided for selective operation in one of a first duty mode and a second duty mode.
  • the compression machine includes: a refrigerant condenser, an expansion device, a refrigerant evaporator, and a compression device disposed in a serial refrigerant flow relationship.
  • the compression device includes a first compressor and a second compressor, each of which is arranged to receive lower pressure refrigerant vapor from the evaporator and to deliver higher pressure vapor to the condenser independently of the other.
  • the first compressor is selected for optimum operation of the compression machine in the first duty mode and the second compressor is selected for optimum operation of the compression machine in the second duty mode.
  • the first duty mode has a first lift requirement and the second duty mode has a second lift requirement that is greater than the first lift requirement.
  • the first duty mode may be a water-cooling mode and the second duty mode may be one of a water-heating mode or a brine cooling mode.
  • a controller may be provided in operative association with each of the first compressor and the second compressor, selectively operates the first compressor when operating the compression machine in a water-cooling mode and selectively operates the second compressor when operating the compression machine in a water-heating mode.
  • the controller directs electric power to a first drive motor for driving the first compressor when operating the compression machine in a water-cooling mode and directs electric power to a second drive motor for driving the second compressor when operating the compression machine in a water-heating mode.
  • each of the first compressor and the second compressor comprises a centrifugal compressor.
  • a method for operating a compression machine for selectively cooling water or heating water, the compression machine having a condenser and an evaporator in refrigerant flow communication with the condenser, a first compressor for receiving refrigerant vapor from the evaporator and delivering refrigerant vapor to the condenser, and a second compressor for receiving refrigerant vapor from the evaporator and delivering refrigerant vapor to the condenser.
  • the method includes the steps of: selectively operating the compression machine in one of a water cooling mode or a water heating mode; operating the first compressor when operating the compression machine in a water cooling mode; and operating the second compressor when operating the compression machine in a water heating mode.
  • a method for designing a compression machine for selective operation in one of a first duty mode or a second duty mode, the compression machine having a condenser and an evaporator in refrigerant flow communication with the condenser, a first compressor for receiving refrigerant vapor from the evaporator and delivering refrigerant vapor to the condenser, and a second compressor for receiving refrigerant vapor from the evaporator and delivering refrigerant vapor to the condenser.
  • the method includes the steps of: selecting the first compressor to perform optimally in the first duty mode, and selecting the second compressor to perform optimally in the second duty mode.
  • the first duty mode has a first lift requirement and the second duty mode has a second lift requirement that is greater than the first lift requirement.
  • the step of selecting the first compressor to perform optimally in the first duty mode comprises selecting the first compressor to perform optimally in a water-cooling mode; and the step of selecting the second compressor to perform optimally in the second duty mode comprises selecting the second compressor to perform optimally in one of a water-heating mode or a brine-cooling mode.
  • FIG. 1 is perspective view of an exemplary embodiment of a compression machine in accordance with the invention
  • FIG. 2 is a schematic diagram depicting the compression machine of
  • the compression machine 10 includes a refrigerant condenser 20, an expansion device 25, a refrigerant evaporator 30, and a compression device disposed in a serial refrigerant flow relationship.
  • the compression device includes a first compressor 40 and a second compressor 50, each of which is arranged to receive lower pressure refrigerant vapor from the evaporator 30 and to deliver higher pressure refrigerant vapor to the condenser 20 independently of the other.
  • Separate drive motors 42, 52 are provided in operative association with the first compressor 40 and the second compressor 50, respectively.
  • the first drive motor 42 drives only the first compressor 40.
  • the second drive motor 52 drives only the second compressor 50.
  • each of the first compressor 40 and the second compressor 50 comprises a centrifugal compressor.
  • the condenser 20 is a liquid-cooled condenser and may any one of various conventional designs.
  • the condenser 20 may be a tube-in-shell condenser, wherein a heat transfer fluid, most commonly, and in the application described herein, water, is passed through a multiple-tube heat exchanger (not shown) housed in a closed shell into which is introduced high pressure, high temperature refrigerant vapor discharged from the compression device.
  • the high temperature refrigerant passes over the exterior of the tubes of the heat exchanger in heat exchange relationship with the water passing through the tubes of the heat exchanger, whereby the refrigerant vapor is cooled and condensed to a refrigerant liquid and the water is heated.
  • the high pressure, condensed refrigerant liquid passes from the condenser 20 to the evaporator 30 through a refrigerant passage 11 in which is disposed an expansion device 25.
  • the refrigerant liquid expands to a lower pressure and a lower temperature to form a refrigerant vapor or a saturated mixture of refrigerant liquid and refrigerant vapor at the lower pressure and the lower temperature.
  • the lower pressure, lower temperature vapor or liquid/vapor mixture is delivered via the passage 11 to and introduced into the shell of the evaporator 30.
  • the evaporator 30 also may any one of various conventional designs.
  • the evaporator 30 may be a tube-in-shell evaporator, wherein a heat transfer fluid, most commonly, and in the application described herein, water or a chemical salt solution (brine), is passed through a multiple-tube heat exchanger (not shown) housed in a closed shell into which is introduced the lower pressure, lower temperature refrigerant liquid in traversing the expansion device 25.
  • a heat transfer fluid most commonly, and in the application described herein, water or a chemical salt solution (brine)
  • a multiple-tube heat exchanger housed in a closed shell into which is introduced the lower pressure, lower temperature refrigerant liquid in traversing the expansion device 25.
  • the lower temperature refrigerant liquid collects in the shell immersing the tubes of the heat exchanger.
  • the water or brine passing through the tubes passes in heat exchange relationship with the liquid refrigerant in which the tubes are immersed, whereby the refrigerant liquid is heated and evaporated to a refrigerant vapor and the water or brine is cooled.
  • the first compressor 40 and the second compressor 50 are each arranged in the refrigerant flow circuit between the evaporator 30 and the condenser 20.
  • a refrigerant line 47 has an outlet opening into the shell of the condenser 20 and an inlet in communication with the discharge outlet of the first compressor 40 whereby the first compressor 40 discharges higher pressure, hot refrigerant vapor into the condenser 20.
  • a refrigerant line 57 has an outlet opening into the shell of the condenser 20 and an inlet in communication with the discharge outlet of the second compressor 50 whereby the second compressor 50 discharges higher pressure, hot refrigerant vapor into the condenser 30.
  • a refrigerant line 43 has an inlet opening into the shell of the evaporator 30 and an outlet in communication with the suction inlet of the first compressor 40 whereby the first compressor 40 receives lower pressure refrigerant vapor from the evaporator 30.
  • a refrigerant line 53 has an inlet opening into the shell of the evaporator 30 and an outlet in communication with the suction inlet of the second compressor 50 whereby the first compressor 50 receives lower pressure refrigerant vapor from the evaporator 30.
  • a first flow shut-off valve 45 is interdisposed in refrigerant line 43 upstream with respect to refrigerant flow of the suction inlet to the first compressor 40.
  • a second flow shut-off valve 55 is interdisposed in refrigerant line 53 upstream with respect to refrigerant flow of the suction inlet to the second compressor 50.
  • the compression machine 10 may also include a control system 80 for selectively operating the first compressor 40 and the second compressor 50.
  • the control system may include a first controller 80-1 that is operatively associated with the first compressor 40 and its drive motor 42 and a second controller 80-2 that is operatively associated with the second compressor 50 and its drive motor 52, and a motor starter 82 that is capable of selectively starting either the first compressor 40 or the second compressor 50 as directed.
  • the control system may also include a master controller (not shown) that selectively independently commands the first and second controllers 80-1, 80-2.
  • the control system 80 associated with the compression machine 10 may include a single controller for controlling the first and second compressors 40, 50 respectively.
  • control system 80 may be configured to operate the compression machine 10 in a water-cooling mode during the summer cooling season to supply chilled water to an air conditioning system (not shown) of a building associated with the compression machine 10.
  • the control system 80 operates the compression machine 10 in a water-heating mode during the winter heating season to provide hot water to the air conditioning system of a building associated with the compression machine 10.
  • the compression machine 10 may need to supply chilled water at a temperature in the vicinity of about 7 0 C (about 45 0 F) during the summer cooling system, and need to supply hot water at a temperature in the vicinity of about 50 0 C (about 122°F) during the winter heating season.
  • control system 80 may be configured during the summer to operate the compression machine 10 in a brine-cooling mode to supply chilled brine to an air conditioning system (not shown) of a building associated with the compression machine 10 during the hours of the day when the building is occupied and to supply chilled brine to an ice-storage system (not shown) to make ice during the hours of the night when the building occupancy is lower, such as typically at night. Chilling brine for the air-conditioning duty would have a lower lift requirement than chilling brine for ice-making duty.
  • the compression machine 10 is designed for selective operation in one of a first duty mode and a second duty mode.
  • the first compressor 40 is selected for optimal operation of the compression machine 10 in the first duty mode, for example a water-cooling mode
  • the second compressor 50 is selected for optimal operation of the compression machine 10 in the second duty mode, for example a water-heating mode or a brine cooling mode.
  • first compressor 40 is selected for optimal operation of the compression machine for providing chilled water passing from the refrigerant evaporator at a temperature in the range of from about 2°C to about 12°C (about 35°F to about 54°F).
  • second compressor 50 is selected for optimal operation of the compression machine for providing heated water passing from the refrigerant condenser at a temperature in the range of from about 4O C to about 6O C (about 104 F to about 140 F). In an embodiment, the second compressor 50 is selected for optimal operation of the compression machine 10 for providing chilled brine to an ice thermal storage system (not shown) for use in making ice.
  • the controller 80 closes the flow shut-off valve 55 in refrigerant line 53 thereby isolating the second compressor 50 from the refrigerant circuit, supplies electric power to the starter 82, and commands the starter 82 to activate the first drive motor 42 for driving only the first compressor 40.
  • the controller 80 closes the flow shut-off valve 45 in refrigerant line 43 thereby isolating the first compressor 40 from the refrigerant circuit, supplies electric power to the starter 82, and commands the starter 82 to activate the second drive motor 52 for driving only the second compressor 50. Therefore, when operating the compression machine 10 in the first duty mode, the first compressor 40 is operated and the second compressor 50 is shutdown and isolated from the refrigerant circuit. Conversely, when operating he compression machine 10 in the second duty mode mode, the second compression 50 is operated and the first compressor 40 is shut down and isolated from the refrigerant circuit.
  • the compression machine 10 is designed for optimal energy efficiency in both the water-cooling mode and the water-heating or brine cooling mode by selecting as the first compressor 40 a first compressor selected to perform optimally in a water cooling mode only, and by selecting as the second compressor 50 a second compressor selected to perform optimally in one of a water heating mode or brine cooling mode.
  • the second compressor 50 for optimal capacity and efficiency in the water heating mode or ice storage mode, wherein the lift required could be as much as about twice the lift required in the water cooling mode
  • the first compressor 40 may be selected for optimal efficiency and performance to meet the lower lift demands, while the second compressor 50 may be selected for optimal efficiency and performance to meet the higher lift demands.
  • water for delivery to the evaporator 30 may be drawn from a outside water source at a temperature of about 7 0 C (about 45 0 F) and the hot water leaving the condenser 20 to meet space heating demand may need to be at a temperature of about 50 0 C (about 122 0 F), while in the summer, water for delivery to the condenser 20 may be from the outdoor water source at a temperature of about 32°C (about 90 0 F) and the chilled water leaving the evaporator 30 to meet air conditioning demand may need to be at a temperature of about 7 0 C (about 45 0 F).
  • the designer would necessarily need to size the compressor to meet the maximum lift requirement and compression capacity demand associated with the second duty mode and simply expect lower than optimal efficiency performance during operation in the first duty mode.
  • the compression machine 10 of the invention provides for optimal performance in both the lower lift requirement first duty mode and the higher lift requirement second duty mode.
  • the first compressor 40 and the second compressor 50 are designed to not operate at the same time.
  • the first compressor 40 is selected for operation in, and is only operated, when the compression machine 10 operates in the water-cooling mode
  • the second compressor 50 is selected for operation in, and is only operated, when the compression machine 10 operates in the water-heating mode.
  • only one motor starter 82 only one motor starter 82.
  • the second compressor 50 which is the compressor selected for operation in the second duty mode, that is the duty mode having the higher lift requirement, is positioned opposite the end at which the water enters the evaporator.
  • the second compressor 50 should be positioned as far as practical from the water inlet end to the condenser to avoid liquid carry-over inside the evaporator, which is driven by the pressure difference between the condenser and the evaporator.
  • the terminology used herein is for the purpose of description, not limitation. Specific structural and functional details disclosed herein are not to be interpreted as limiting, but merely as basis for teaching one skilled in the art to employ the present invention.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Compressor (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne une machine de compression comprenant un condensateur de réfrigération, un dispositif d'expansion, un évaporateur de réfrigération, un premier compresseur et un deuxième compresseur. Chaque compresseur est prévu pour recevoir de la vapeur de réfrigération à une pression inférieure en provenance de l'évaporateur et délivrer de la vapeur à une pression supérieure au condensateur indépendamment de l'autre compresseur. Le premier compresseur fonctionne quand la machine de compression opère dans un premier mode de fonctionnement, par exemple un mode de refroidissement par eau. Le deuxième compresseur fonctionne quand la machine de compression opère dans un deuxième mode de fonctionnement, par exemple un mode de chauffage d'eau ou un refroidissement de saumure. Le premier compresseur est sélectionné pour des performances optimales dans la première fonction uniquement, et le deuxième compresseur est sélectionné pour des performances optimales dans le deuxième mode de fonctionnement uniquement.
PCT/US2010/029595 2009-04-09 2010-04-01 Machine de compression à double fonction Ceased WO2010117868A2 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US13/255,198 US20110314847A1 (en) 2009-04-09 2010-04-01 Dual duty compression machine
CN201080015309.8A CN102388223B (zh) 2009-04-09 2010-04-01 双任务压缩机器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US16797809P 2009-04-09 2009-04-09
US61/167,978 2009-04-09

Publications (2)

Publication Number Publication Date
WO2010117868A2 true WO2010117868A2 (fr) 2010-10-14
WO2010117868A3 WO2010117868A3 (fr) 2011-01-13

Family

ID=42936831

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2010/029595 Ceased WO2010117868A2 (fr) 2009-04-09 2010-04-01 Machine de compression à double fonction

Country Status (3)

Country Link
US (1) US20110314847A1 (fr)
CN (1) CN102388223B (fr)
WO (1) WO2010117868A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019197209A1 (fr) * 2018-04-13 2019-10-17 Trumpf Schweiz Ag Procédé pour commander au moins un ventilateur centrifuge dans une machine frigorifique et ventilateur centrifuge

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITFI20130118A1 (it) * 2013-05-21 2014-11-22 Nuovo Pignone Srl "compressor with a thermal shield and methods of operation"
USD828250S1 (en) * 2015-08-31 2018-09-11 Cummins Inc. Compression relief brake system
CN105841402A (zh) * 2016-05-19 2016-08-10 欧悦冰雪投资管理（北京）有限公司 一种回油结构及包括该结构的制冰机组
CN107014141B (zh) * 2017-03-28 2020-04-21 南京国通制冷技术有限公司 一种冷冻冷藏柜性能测试装置用空气处理系统
CN111059657A (zh) * 2019-12-11 2020-04-24 珠海格力电器股份有限公司 一种制冷制冰空调机组和控制方法

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4262488A (en) * 1979-10-09 1981-04-21 Carrier Corporation System and method for controlling the discharge temperature of a high pressure stage of a multi-stage centrifugal compression refrigeration unit
US4646530A (en) * 1986-07-02 1987-03-03 Carrier Corporation Automatic anti-surge control for dual centrifugal compressor system
JPH10132400A (ja) * 1996-10-24 1998-05-22 Mitsubishi Heavy Ind Ltd パラレル型冷凍機
EP1422483B1 (fr) * 2002-11-21 2015-10-14 LG Electronics Inc. Appareil de conditionnement d'air
KR100465723B1 (ko) * 2002-12-20 2005-01-13 엘지전자 주식회사 공기조화기의 냉방 운전 방법
US7207183B2 (en) * 2004-04-12 2007-04-24 York International Corp. System and method for capacity control in a multiple compressor chiller system
JP4195031B2 (ja) * 2004-11-04 2008-12-10 ウィニアマンド インコーポレイテッド 空気調和機の容量制御装置
US7478539B2 (en) * 2005-06-24 2009-01-20 Hussmann Corporation Two-stage linear compressor
US7628027B2 (en) * 2005-07-19 2009-12-08 Hussmann Corporation Refrigeration system with mechanical subcooling
KR100700545B1 (ko) * 2005-08-10 2007-03-28 엘지전자 주식회사 복수의 압축기를 구비한 공기조화기의 운전제어장치 및방법

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019197209A1 (fr) * 2018-04-13 2019-10-17 Trumpf Schweiz Ag Procédé pour commander au moins un ventilateur centrifuge dans une machine frigorifique et ventilateur centrifuge
US12429061B2 (en) 2018-04-13 2025-09-30 Teqtoniq Gmbh Method for controlling at least one radial blower in a cooling system, and radial blower

Also Published As

Publication number Publication date
CN102388223B (zh) 2017-06-30
WO2010117868A3 (fr) 2011-01-13
CN102388223A (zh) 2012-03-21
US20110314847A1 (en) 2011-12-29

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