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US20100050668A1 - Refrigerant Charge Storage - Google Patents

Refrigerant Charge Storage Download PDF

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Publication number
US20100050668A1
US20100050668A1 US12/516,250 US51625006A US2010050668A1 US 20100050668 A1 US20100050668 A1 US 20100050668A1 US 51625006 A US51625006 A US 51625006A US 2010050668 A1 US2010050668 A1 US 2010050668A1
Authority
US
United States
Prior art keywords
refrigerant
heat exchanger
flowpath
compressor
expansion device
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.)
Abandoned
Application number
US12/516,250
Other languages
English (en)
Inventor
James W. Bush
Biswajit Mitra
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
Assigned to CARRIER CORPORATION reassignment CARRIER CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BUSH, JAMES W., MITRA, BISWAJIT
Publication of US20100050668A1 publication Critical patent/US20100050668A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2345/00—Details for charging or discharging refrigerants; Service stations therefor
    • F25B2345/004—Details for charging or discharging refrigerants; Service stations therefor with several tanks to collect or charge a cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/16—Receivers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/17—Control issues by controlling the pressure of the condenser

Definitions

  • the invention relates to refrigeration. More particularly, the invention relates to transcritical refrigeration systems used for transport or commercial refrigeration.
  • An exemplary frozen goods temperature is about ⁇ 10° F. or less and an exemplary non-frozen perishable temperature is 34-38° F.
  • the operator will predetermine appropriate temperature for each of the two modes. Prior to a trip or series, the technician or driver will enter the appropriate one of the two temperatures. Other operators may have broader requirements (e.g., an exemplary overall range of ⁇ 40-57° F.).
  • U.S. Pat. No. 7,096,679 discloses heating/cooling a reservoir to modulate the amount of refrigerant returned. Heating increases the heat load on the system, thereby making the system less efficient. The heating and cooling may increase the power consumption in the system.
  • U.S. Pat. No. 6,385,980 discloses a flash tank economizer. If the flash tank economizer vapor line is closed for some operating conditions, then the pressure inside the flash tank may increase as described above.
  • Other systems include an accumulator at the downstream end of the evaporator as a charge storage device. These may suffer from excessive oil build up in the bottom of the accumulator and liquid sloshing into the compressor at system startup.
  • this present disclosure may address one to all the above problems, and provide means for regulating charge in the system over same to the entire operating envelope of typical transport and commercial applications.
  • FIG. 1 is a partially schematic view of a first refrigeration system.
  • FIG. 2 is a partially schematic view of a second refrigeration system.
  • An exemplary expansion device 26 is an electronic expansion valve (commonly identified as an EEV or EXV).
  • An electronic expansion valve typically comprises a stepper motor attached to a needle valve to vary the effective valve opening or flow capacity.
  • the opening of the valve may be electronically controlled by a controller 66 which may also control operation of the compressor and other system components.
  • the controller may operate in response to input from one or more user input devices 68 (e.g., switches, electronic controls, and the like) and one or more sensors (e.g., evaporator outlet temperature and/or pressure, discharge pressure and/or temperature, ambient and controlled space temperatures).
  • the evaporator temperature goes down, the liquid refrigerant density in the evaporator increases and greater mass of refrigerant gets stored in the evaporator. In the absence of intervention, the mass flow rate of the circulating charge decreases. At that condition it is desirable to store the least amount of refrigerant in the system 80 . Similarly, when the heat exchangers are at their highest temperatures, the evaporator will store a relatively low amount of refrigerant. To avoid overpressurizing the system 20 , it is desirable to store the most refrigerant in the storage system 80 . Thus, during system startup and pulldown it is desirable to have a maximum amount of charge in the storage system 80 . As the evaporator temperature goes down, the storage system 80 may be controlled to unload progressively more charge into the active cycle.
  • the exemplary system includes a plurality of reservoirs 82 , 83 , and 84 whose chambers 85 , 86 , and 87 are fluidically coupled in parallel with each other and with the expansion device.
  • the reservoirs may each be opened and closed to the primary flowpath 40 by valves at high and low pressure ends of the reservoirs.
  • each reservoir is shown having an associated first (high pressure) valve 90 , 91 , and 92 between that reservoir's inlet 93 , 94 , and 95 and the expansion device inlet location/condition 60 .
  • Each reservoir further has an associated second (low pressure) valve 96 , 97 , and 98 between a second port 99 , 100 , and 101 of that reservoir and the expansion device outlet location/condition 62 .
  • various of the first valves may be integrated with each other, first and second valves may be integrated with each other, or other combinations (e.g., using four-way or greater valve structures).
  • opening and closing of the first and second valves is controlled by the controller responsive to a combination of measured/sensed conditions and/or user-entered parameters (e.g., set temperatures).
  • a combination of measured/sensed conditions and/or user-entered parameters e.g., set temperatures.
  • each reservoir under normal operating conditions, has exactly one of its two valves open while the other valve is closed. The selection of the appropriate combination of open and closed valves will determine the effective charge storage of the system 80 .
  • a condition of maximum stored charge and minimum circulating charge is associated with all of the first valves being open and all of the second valves being closed.
  • a condition of minimum stored charge and maximum circulating charge is associated with all of the first valves being closed and all of the second valves being open.
  • Other combinations of closed and open valves provide one or more intermediate conditions. The nature of those intermediate conditions will depend upon the relative and absolute sizes of the reservoirs.
  • the relative sizes of the first and second reservoirs are selected so that the effective capacity of the second reservoir is twice that of the first reservoir (i.e., the difference in charge amount held by the second reservoir between its two conditions is twice that of the first).
  • the third reservoir is selected to have an effective capacity twice that of the second.
  • the absolute sizes of the reservoirs are selected so that the combined effective capacities provide a desired overall charge storage/buffering capacity. With this exemplary combination of reservoir sizes, six evenly separated intermediate conditions may be obtained between the minimum stored charge and maximum stored charge conditions.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
US12/516,250 2006-11-30 2006-11-30 Refrigerant Charge Storage Abandoned US20100050668A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2006/045823 WO2008066530A2 (fr) 2006-11-30 2006-11-30 Stockage de charge refrigerant

Publications (1)

Publication Number Publication Date
US20100050668A1 true US20100050668A1 (en) 2010-03-04

Family

ID=39468395

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/516,250 Abandoned US20100050668A1 (en) 2006-11-30 2006-11-30 Refrigerant Charge Storage

Country Status (5)

Country Link
US (1) US20100050668A1 (fr)
EP (1) EP2087298A4 (fr)
JP (1) JP2010520985A (fr)
CN (1) CN101548142B (fr)
WO (1) WO2008066530A2 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100199707A1 (en) * 2009-02-11 2010-08-12 Star Refrigeration Limited Refrigeration system
JPWO2016189698A1 (ja) * 2015-05-27 2017-09-07 三菱電機株式会社 圧縮機及び冷凍サイクル装置
US9776473B2 (en) 2012-09-20 2017-10-03 Thermo King Corporation Electrical transport refrigeration system
US10543737B2 (en) 2015-12-28 2020-01-28 Thermo King Corporation Cascade heat transfer system
DE102018129131A1 (de) * 2018-11-20 2020-06-04 Vaillant Gmbh Arbeitsfluid-Management
CN114674095A (zh) * 2022-03-16 2022-06-28 青岛海尔空调器有限总公司 空调器、用于控制空调冷媒的方法、装置和存储介质
CN114674094A (zh) * 2022-03-16 2022-06-28 青岛海尔空调器有限总公司 空调器、用于调控空调冷媒的方法、装置和存储介质
US11644221B1 (en) * 2019-03-05 2023-05-09 Booz Allen Hamilton Inc. Open cycle thermal management system with a vapor pump device

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014104709A1 (de) * 2014-04-02 2015-10-08 Krones Ag Behälterbehandlungsanlage mit Kälteanlage und Verfahren zur Inbetriebnahme einer Kälteanlage einer Behälterbehandlungsanlage
DE102014223956B4 (de) * 2014-11-25 2018-10-04 Konvekta Ag Verfahren zur Überwachung einer Füllmenge eines Kältemittels in einem Kältemittelkreislauf einer Kälteanlage
AT515240B1 (de) * 2015-04-20 2016-04-15 Avl Ditest Gmbh Klimaservicegerät und Verfahren zum Ablassen von Kältemittel aus einer Klimaanlage

Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2401426A (en) * 1942-08-20 1946-06-04 Thomas C Killoran Refrigerating apparatus
FR2257014A1 (en) * 1974-01-07 1975-08-01 Sigaud Pierre IC engine with hydraulic transmission - has hydropneumatic accumulators on low and high pressure circuits
US4554792A (en) * 1981-07-08 1985-11-26 Margulefsky Allen L Method and apparatus for rehabilitating refrigerant
US5758506A (en) * 1996-07-03 1998-06-02 White Industries, Llc Method and apparatus for servicing automotive refrigeration systems
US6000230A (en) * 1997-08-19 1999-12-14 Showa Denko K.K. Method for dividing and charging of non-azeotropic mixed refrigerant
US6134900A (en) * 1998-01-21 2000-10-24 Denso Corporation Supercritical refrigerating system
US6209338B1 (en) * 1998-07-15 2001-04-03 William Bradford Thatcher, Jr. Systems and methods for controlling refrigerant charge
US6385980B1 (en) * 2000-11-15 2002-05-14 Carrier Corporation High pressure regulation in economized vapor compression cycles
US6427460B1 (en) * 1999-04-19 2002-08-06 Luciano Zanon Refrigeration system having a refrigeration cycle which provides optimized consumption
US6606867B1 (en) * 2000-11-15 2003-08-19 Carrier Corporation Suction line heat exchanger storage tank for transcritical cycles
US6739141B1 (en) * 2003-02-12 2004-05-25 Carrier Corporation Supercritical pressure regulation of vapor compression system by use of gas cooler fluid pumping device
US6851269B2 (en) * 2002-09-25 2005-02-08 Horiba, Ltd. Apparatus and method for calculating refill amount of refrigerant
US6923011B2 (en) * 2003-09-02 2005-08-02 Tecumseh Products Company Multi-stage vapor compression system with intermediate pressure vessel
US7010927B2 (en) * 2003-11-07 2006-03-14 Carrier Corporation Refrigerant system with controlled refrigerant charge amount
US7096679B2 (en) * 2003-12-23 2006-08-29 Tecumseh Products Company Transcritical vapor compression system and method of operating including refrigerant storage tank and non-variable expansion device
US20070079891A1 (en) * 2005-10-10 2007-04-12 Farese David J Cascade bank selection based on ambient temperature

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Publication number Priority date Publication date Assignee Title
DE720735C (de) * 1939-09-01 1942-05-14 Paul Neunert Verdampfungskaelteanlage
JPS6060461A (ja) * 1983-09-14 1985-04-08 株式会社日立製作所 冷凍機
JPS61151167U (fr) * 1985-03-13 1986-09-18
NO890076D0 (no) * 1989-01-09 1989-01-09 Sinvent As Luftkondisjonering.
JPH09250849A (ja) * 1996-03-16 1997-09-22 Yoriyuki Oguri 冷媒ガス一時保管用ボンベ及びその使用方法
JP2002340448A (ja) * 2001-05-18 2002-11-27 Fujitsu General Ltd 空気調和機の冷媒回収装置
JP2005083640A (ja) * 2003-09-08 2005-03-31 Toshiba Kyaria Kk 冷凍車用冷凍装置
US7353660B2 (en) * 2004-09-13 2008-04-08 Carrier Corporation Multi-temperature cooling system with unloading

Patent Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2401426A (en) * 1942-08-20 1946-06-04 Thomas C Killoran Refrigerating apparatus
FR2257014A1 (en) * 1974-01-07 1975-08-01 Sigaud Pierre IC engine with hydraulic transmission - has hydropneumatic accumulators on low and high pressure circuits
US4554792A (en) * 1981-07-08 1985-11-26 Margulefsky Allen L Method and apparatus for rehabilitating refrigerant
US5758506A (en) * 1996-07-03 1998-06-02 White Industries, Llc Method and apparatus for servicing automotive refrigeration systems
US6000230A (en) * 1997-08-19 1999-12-14 Showa Denko K.K. Method for dividing and charging of non-azeotropic mixed refrigerant
US6134900A (en) * 1998-01-21 2000-10-24 Denso Corporation Supercritical refrigerating system
US6209338B1 (en) * 1998-07-15 2001-04-03 William Bradford Thatcher, Jr. Systems and methods for controlling refrigerant charge
US6427460B1 (en) * 1999-04-19 2002-08-06 Luciano Zanon Refrigeration system having a refrigeration cycle which provides optimized consumption
US6385980B1 (en) * 2000-11-15 2002-05-14 Carrier Corporation High pressure regulation in economized vapor compression cycles
US6606867B1 (en) * 2000-11-15 2003-08-19 Carrier Corporation Suction line heat exchanger storage tank for transcritical cycles
US6851269B2 (en) * 2002-09-25 2005-02-08 Horiba, Ltd. Apparatus and method for calculating refill amount of refrigerant
US6739141B1 (en) * 2003-02-12 2004-05-25 Carrier Corporation Supercritical pressure regulation of vapor compression system by use of gas cooler fluid pumping device
US6923011B2 (en) * 2003-09-02 2005-08-02 Tecumseh Products Company Multi-stage vapor compression system with intermediate pressure vessel
US7010927B2 (en) * 2003-11-07 2006-03-14 Carrier Corporation Refrigerant system with controlled refrigerant charge amount
US7096679B2 (en) * 2003-12-23 2006-08-29 Tecumseh Products Company Transcritical vapor compression system and method of operating including refrigerant storage tank and non-variable expansion device
US20070079891A1 (en) * 2005-10-10 2007-04-12 Farese David J Cascade bank selection based on ambient temperature

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
English translation of JP 60-060461 *

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100199707A1 (en) * 2009-02-11 2010-08-12 Star Refrigeration Limited Refrigeration system
US10377209B2 (en) 2012-09-20 2019-08-13 Thermo King Corporation Electrical transport refrigeration system
US9776473B2 (en) 2012-09-20 2017-10-03 Thermo King Corporation Electrical transport refrigeration system
US11313593B2 (en) 2015-05-27 2022-04-26 Mitsubishi Electric Corporation Compressor and refrigeration cycle apparatus
JPWO2016189698A1 (ja) * 2015-05-27 2017-09-07 三菱電機株式会社 圧縮機及び冷凍サイクル装置
US10543737B2 (en) 2015-12-28 2020-01-28 Thermo King Corporation Cascade heat transfer system
US11351842B2 (en) 2015-12-28 2022-06-07 Thermo King Corporation Cascade heat transfer system
DE102018129131A1 (de) * 2018-11-20 2020-06-04 Vaillant Gmbh Arbeitsfluid-Management
US11644221B1 (en) * 2019-03-05 2023-05-09 Booz Allen Hamilton Inc. Open cycle thermal management system with a vapor pump device
US11761685B1 (en) 2019-03-05 2023-09-19 Booz Allen Hamilton Inc. Open cycle thermal management system with a vapor pump device and recuperative heat exchanger
US11801731B1 (en) 2019-03-05 2023-10-31 Booz Allen Hamilton Inc. Thermal management systems
US11835271B1 (en) 2019-03-05 2023-12-05 Booz Allen Hamilton Inc. Thermal management systems
CN114674095A (zh) * 2022-03-16 2022-06-28 青岛海尔空调器有限总公司 空调器、用于控制空调冷媒的方法、装置和存储介质
CN114674094A (zh) * 2022-03-16 2022-06-28 青岛海尔空调器有限总公司 空调器、用于调控空调冷媒的方法、装置和存储介质

Also Published As

Publication number Publication date
JP2010520985A (ja) 2010-06-17
EP2087298A2 (fr) 2009-08-12
CN101548142A (zh) 2009-09-30
EP2087298A4 (fr) 2012-04-04
WO2008066530A2 (fr) 2008-06-05
WO2008066530A3 (fr) 2009-04-30
CN101548142B (zh) 2013-04-24

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Legal Events

Date Code Title Description
AS Assignment

Owner name: CARRIER CORPORATION,CONNECTICUT

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BUSH, JAMES W.;MITRA, BISWAJIT;SIGNING DATES FROM 20070312 TO 20070717;REEL/FRAME:019569/0115

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION