WO2009140372A1 - Système de réfrigération de transport et procédé de commande - Google Patents

Système de réfrigération de transport et procédé de commande Download PDF

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Publication number
WO2009140372A1
WO2009140372A1 PCT/US2009/043773 US2009043773W WO2009140372A1 WO 2009140372 A1 WO2009140372 A1 WO 2009140372A1 US 2009043773 W US2009043773 W US 2009043773W WO 2009140372 A1 WO2009140372 A1 WO 2009140372A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
vapor
compression system
vapor compression
set forth
Prior art date
Application number
PCT/US2009/043773
Other languages
English (en)
Inventor
Yu H. Chen
Lucy Yi Liu
Original Assignee
Carrier Corporation
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 Corporation filed Critical Carrier Corporation
Priority to CN2009801171122A priority Critical patent/CN102027300A/zh
Priority to EP09747456.3A priority patent/EP2304338A4/fr
Priority to US12/922,612 priority patent/US20110048042A1/en
Priority to JP2011509648A priority patent/JP2011521195A/ja
Publication of WO2009140372A1 publication Critical patent/WO2009140372A1/fr

Links

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
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3205—Control means therefor
    • B60H1/3216—Control means therefor for improving a change in operation duty of a compressor in a vehicle
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3286—Constructional features
    • B60H2001/3292—Compressor drive is electric only
    • 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
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2400/23—Separators
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • 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
    • F25B2600/11—Fan speed control
    • F25B2600/111—Fan speed control of condenser fans
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2104—Temperatures of an indoor room or compartment
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F25B31/008—Cooling of compressor or motor by injecting a liquid
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/027—Condenser control arrangements

Definitions

  • This invention relates generally to transport refrigeration systems and, more particularly, to capacity modulation in a refrigerant vapor compression system operating in a transcritical cycle.
  • Refrigerant vapor compression systems are well known in the art and commonly used for conditioning air to be supplied to a climate controlled comfort zone within a residence, office building, hospital, school, restaurant or other facility.
  • Refrigerant vapor compression systems are also commonly used in transport refrigeration systems for refrigerating air supplied to a temperature controlled cargo space of a truck, trailer, container or the like for transporting perishable items.
  • most of these refrigerant vapor compression systems operate at subcritical refrigerant pressures and typically include a compressor, a condenser, and an evaporator, and expansion device, commonly an expansion valve, disposed upstream, with respect to refrigerant flow, of the evaporator and downstream of the condenser.
  • refrigerant system components are interconnected by refrigerant lines in a closed refrigerant circuit, arranged in accord with known refrigerant vapor compression cycles, and operated in the subcritical pressure range for the particular refrigerant in use.
  • Refrigerant vapor compression systems operating in the subcritical range are commonly charged with conventional fluorocarbon refrigerants such as, but not limited to, hydrochlorofluorocarbons (HCFCs), such as R22, and more commonly hydrofluorocarbons (HFCs), such as R134a, R410A and R407C.
  • HCFCs hydrochlorofluorocarbons
  • HFCs hydrofluorocarbons
  • the refrigerant heat rejection heat exchanger operates as a gas cooler rather than a condenser and operates at a refrigerant temperature and pressure in excess of the refrigerant's critical point, while the evaporator operates at a refrigerant temperature and pressure in the subcritical range.
  • the refrigerant vapor of a vapor compression system operating in the transcritical range is compressed by way of a digital scroll compressor.
  • control methods and apparatus are provided to prevent the digital scroll compressor from becoming overloaded in such a system.
  • FIG. 1 is a schematic illustration of the present invention as incorporated into a vapor compression system.
  • FIGS. 2A and 2B are graphic illustrations of compressor capacity modulation in accordance with the present invention.
  • FIG. 3 is a graphic illustration of the resultant cooling capacity control in accordance with the present invention.
  • FIG. 4 is a graphic illustration of the present invention as incorporated into an economized vapor compression system.
  • FIG. 5 is a schematic illustration of the present invention as incorporated into another type of economized vapor compression system.
  • the invention is shown generally at 10 as incorporated into a refrigerant vapor compression system operating with CO 2 as the refrigerant and having in serial flow relationship, a compressor 11, a refrigerant heat rejecting heat exchanger 12, an expansion device 13 and a refrigerant heat absorbing heat exchanger 14.
  • the system since the system uses CO 2 as the working fluid, it necessarily operates in a transcritical cycle, such that the refrigerant heat rejecting heat exchanger 12, which may be referred to as a condenser, has high pressure refrigerant passing in heat exchange relationship with a cooling medium, most commonly ambient air, in air conditioning systems or transport refrigeration system.
  • the refrigerant heat rejecting heat exchanger 12 constitutes a gas cooler heat exchanger through which supercritical refrigerant passes in heat relationship with the cooling medium.
  • the condenser/gas cooler 12 has a fan 17 driven by a multi-speed motor 18 and controlled in a manner to be described hereinafter.
  • the liquid refrigerant passes from the flash tank receiver 21 to the expansion device 13 where it expands to a lower pressure and temperature before entering the evaporator 14.
  • the evaporator 14 constitutes a refrigerant evaporating heat exchanger through which expanded refrigerant passes in heat exchanger relationship with the heating fluid with the refrigerant being vaporized and typical superheated.
  • the heating fluid passing in heat exchange relationship with the refrigerant constitutes air to be supplied to a perishable cargo storage zone associated with a transport refrigeration unit.
  • the low pressure refrigerant vapor leaves the evaporator 14 and then returns to the suction port of the compression device 11.
  • the compressor 11 comprises a digital scroll compressor such as that described in US Patent 5, 741,120 and commercially available from Copeland Corporation.
  • the digital scroll operates in two stages - the "loaded state”, when the compressor operates like a standard scroll and delivers full capacity and mass flow, and the "unloaded state”, when there is no capacity and no mass flow through the compressor.
  • the digital scroll compressor operates under the concept of cycle time. Each cycle time consists of a "loaded state” time and "unloaded state” time. The digital scroll compressor will effectively reduce compression ratio and therefore compressor discharge temperature through the control of cycle time.
  • the compressor In the "loaded state”, the compressor operates like a standard scroll and delivers full capacity and mass flow.
  • the "unloaded state there is no capacity and no mass flow through the compressor.
  • the duration of these two-time segments determine the capacity modulation of the compressor. For example, as shown in Fig.
  • the capacity is a time averaged summation of the loaded state and unloaded state capacity. By varying the loaded state time and unloaded state time, any capacity from 10% to 100% can be delivered by the compressor. The refrigeration system capacity can therefore adjust precisely to match load demand over a wide range of applications.
  • the digital scroll compressor is designed to have its capacity modulated by a control 22 which delivers a variable duty cycle signal S along line 23 to the digital scroll compressor 11 for that purpose.
  • the control 22 is used to implement further control features so as to limit the compression ratio experienced by the digital scroll compressor 11 in a manner to be described hereinafter.
  • the drive motor 18 for the fan 17 is a multiple speed motor which can be selectively operated at a relatively high speed or a relatively low speed. Thus, it can be a two speed motor or it may be a variable speed motor which can vary its speed over a continuous range. Control of the motor speed is maintained by way of the control 22 along line 24 in a manner to be described hereinafter.
  • a pressure sensor 26 and a temperature sensor 27 are installed at the discharge of the compressor 11 , with their respective outputs being sent to the control 22 along lines 28 and 29, respectively.
  • the system is shown with both a pressure sensor 26 and a temperature sensor 27, it may operate with either of those and without the use of the other. That is, for control purposes, it is desirable to sense a condition that is indicative of the pressure ratio of the compressor 11 , and either the discharge pressure or the discharge temperature can be used for that purpose as will be described hereinafter.
  • Another parameter that is used in the control of the system is the temperature within the space 31 being cooled. This temperature is determined by a temperature sensor 32 which sends a sensed temperature signal to a comparator 33 to be compared with a set point, with the difference being sent along line 34 to the control.
  • a temperature sensor 32 which sends a sensed temperature signal to a comparator 33 to be compared with a set point, with the difference being sent along line 34 to the control.
  • the controller 22 When in the perishable (chill) mode, the controller 22 maintains the supply air temperature at set point, and the compressor 11 is operating at a part load condition. Thus, in order to remove extra capacity from the system, the control 22 first selects a low speed for the gas cooler fan motor 18 and opens valve 19 so as to thereby reduce the compressor discharge pressure. Then the "loaded state" time of the compressor is reduced as much as possible while maintaining the supply air temperature at set point. By reducing compressor discharge pressure, the compressor dome temperature is reduced due to lower compression ratios and, in turn, the compressor reliability is improved.
  • the line A in Fig. 3 shows the manner in which the cooling capacity is varied during operation in this mode.
  • Temperature control in the frozen range is accomplished by cycling the compressor between the loaded stated and unloaded state as the load demand requires.
  • the compressor discharge pressure is at an optimized point through control valve 19, and the fan motor 18 can be operated either at a high or low speed.
  • the line B indicates a typical cooling capacity variation for the frozen mode of operation.
  • the compressor 11 is operating in a full load condition with the maximum capacity being required.
  • the fan motor 18 is run at high speed and a compressor discharge pressure, as indicated by either the pressure sensor 26 or the temperature sensor 27 is maintained at a maximum design point.
  • the control 22 then varies the cycle times of the "loaded state” and "unloaded state” as necessary in order to prevent overloading of the compressor. For example, a maximum compressor discharge temperature may be established at 300 0 F, and as that temperature is approached, the compressor modulation (i.e. the loaded state time as compared with the unloaded time) is decreased in order to prevent that temperature from being exceeded.
  • the line C in Fig. 3 shows a typical cooling capacity variation during the pull down mode of operation.
  • the present invention is applicable to a non-economized digital scroll compressor system. However, it is equally applicable to economized systems of various types as shown in Fig. 4 and Fig. 5, for example.
  • the control system is shown as used with a flash tank economized system driven by a digital scroll compressor 11 having a vapor injection port 36.
  • the flash tank receiver 21 serves not only as a charge control tank, but also as a flash tank economizer. Vapor refrigerant collecting in the portion of the flash tank receiver 21 above the liquid level therein passes from the receiver 21 along line 37 and solenoid valve 38 to the vapor injection port 36.
  • the solenoid valve 38 is controlled by the control 22 in order to turn on and off the economizer operation.
  • FIG. 5 Another type of economized system which the present control method is applicable is shown in Fig. 5.
  • a flash tank is not included but rather an interstage economizer 42 that is simply a brazed plate heat exchanger.
  • Leading into the interstage economizer 42 is solenoid valve 43 and an expansion valve 44.
  • the solenoid valve 43 When the solenoid valve 43 is open, the refrigerant vapor flows from the gas cooler 12, through the solenoid valve 43 and the expansion valve 44 into the interstage economizer 42, with the vapor then being injected into the vapor injection port 36.
  • the solenoid valve is closed, the refrigerant vapor flows along line 46 to the interstage economizer 42, with no economizer operation occurring.
  • a charge storage vessel 45 is provided to serve only the purpose of storing excess charge.

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  • 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)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)

Abstract

L'invention concerne un système de compression de vapeur de réfrigérant utilisant du CO2 en tant que fluide de travail et exécutant un cycle transcritique, la compression du réfrigérant étant réalisée au moyen d'un compresseur à spirale numérique conçu pour un cycle de service variable par modulation d'impulsions en durée. Le taux de compression est maintenu à un niveau acceptable par commande sélective de divers composants dans le système, en fonction du mode d'exécution.
PCT/US2009/043773 2008-05-14 2009-05-13 Système de réfrigération de transport et procédé de commande WO2009140372A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
CN2009801171122A CN102027300A (zh) 2008-05-14 2009-05-13 运输制冷系统及操作方法
EP09747456.3A EP2304338A4 (fr) 2008-05-14 2009-05-13 Système de réfrigération de transport et procédé de commande
US12/922,612 US20110048042A1 (en) 2008-05-14 2009-05-13 Transport refrigeration system and method of operation
JP2011509648A JP2011521195A (ja) 2008-05-14 2009-05-13 輸送冷凍システムおよび運転方法

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US12761308P 2008-05-14 2008-05-14
US61/127,613 2008-05-14

Publications (1)

Publication Number Publication Date
WO2009140372A1 true WO2009140372A1 (fr) 2009-11-19

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ID=41319036

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2009/043773 WO2009140372A1 (fr) 2008-05-14 2009-05-13 Système de réfrigération de transport et procédé de commande

Country Status (5)

Country Link
US (1) US20110048042A1 (fr)
EP (1) EP2304338A4 (fr)
JP (1) JP2011521195A (fr)
CN (1) CN102027300A (fr)
WO (1) WO2009140372A1 (fr)

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CN102434991A (zh) * 2010-09-23 2012-05-02 热之王公司 跨临界蒸气压缩系统的控制
EP2545329A2 (fr) * 2010-03-08 2013-01-16 Carrier Corporation Commande de la capacité et de la pression dans un système de transport réfrigéré
WO2013016403A1 (fr) * 2011-07-26 2013-01-31 Carrier Corporation Logique de commande de la température pour système de réfrigération
CN103307654A (zh) * 2012-03-12 2013-09-18 松下电器产业株式会社 热泵式热水供暖装置
US9776473B2 (en) 2012-09-20 2017-10-03 Thermo King Corporation Electrical transport refrigeration system
EP3875874A1 (fr) * 2020-03-05 2021-09-08 Thermo King Corporation Stratégies de commande de vitesse pour un ventilateur de condensateur dans un système de réfrigération

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EP2180278B1 (fr) * 2008-10-24 2021-01-27 Thermo King Corporation Contrôle de la descente rapide en température dans des systèmes de réfrigération
CN101858621A (zh) * 2010-05-26 2010-10-13 广东欧科空调制冷有限公司 多联式空调机组及其工作方法
US9726416B2 (en) 2011-09-23 2017-08-08 Carrier Corporation Transport refrigeration system with engine exhaust cooling
US20150300713A1 (en) * 2012-08-24 2015-10-22 Carrier Corporation Stage transition in transcritical refrigerant vapor compression system
EP2888542A1 (fr) * 2012-08-24 2015-07-01 Carrier Corporation Commande de pression du côté haut d'un système de compression de vapeur de fluide frigorigène transcritique
US10302342B2 (en) 2013-03-14 2019-05-28 Rolls-Royce Corporation Charge control system for trans-critical vapor cycle systems
US9676484B2 (en) 2013-03-14 2017-06-13 Rolls-Royce North American Technologies, Inc. Adaptive trans-critical carbon dioxide cooling systems
US9718553B2 (en) 2013-03-14 2017-08-01 Rolls-Royce North America Technologies, Inc. Adaptive trans-critical CO2 cooling systems for aerospace applications
US10132529B2 (en) 2013-03-14 2018-11-20 Rolls-Royce Corporation Thermal management system controlling dynamic and steady state thermal loads
WO2014143194A1 (fr) 2013-03-14 2014-09-18 Rolls-Royce Corporation Systèmes de refroidissement à co2 transcritique adaptatifs pour applications aérospatiales
CN104406339B (zh) * 2013-11-12 2018-03-06 江苏春兰动力制造有限公司 一种单螺杆压缩机无级能量调节控制方法
DE102015104464B4 (de) 2015-03-25 2018-08-02 Halla Visteon Climate Control Corporation Verfahren zur Regelung für einen R744-Kältemittelkreislauf
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EP2304338A1 (fr) 2011-04-06
CN102027300A (zh) 2011-04-20
US20110048042A1 (en) 2011-03-03
EP2304338A4 (fr) 2014-09-03
JP2011521195A (ja) 2011-07-21

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