WO2009017517A1 - Procédé et appareil pour commander un système de refroidissement - Google Patents

Procédé et appareil pour commander un système de refroidissement Download PDF

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Publication number
WO2009017517A1
WO2009017517A1 PCT/US2007/088016 US2007088016W WO2009017517A1 WO 2009017517 A1 WO2009017517 A1 WO 2009017517A1 US 2007088016 W US2007088016 W US 2007088016W WO 2009017517 A1 WO2009017517 A1 WO 2009017517A1
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WO
WIPO (PCT)
Prior art keywords
pressure
valve
condenser
fluid
vapor compression
Prior art date
Application number
PCT/US2007/088016
Other languages
English (en)
Inventor
Roger D. Noll
Gary Helmink
Michael Jason Gloeckner
Russell C. Tipton
Benedict J. Dolcich
Original Assignee
Liebert 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 Liebert Corporation filed Critical Liebert Corporation
Priority to CN200780100125A priority Critical patent/CN101815911A/zh
Priority to EP07869467A priority patent/EP2185874A1/fr
Publication of WO2009017517A1 publication Critical patent/WO2009017517A1/fr

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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
    • 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
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration 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
    • F25B2600/00—Control issues
    • F25B2600/17—Control issues by controlling the pressure of the condenser
    • 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
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser

Definitions

  • the inventions disclosed and taught herein relate generally to a cooling system, and more specifically to a system and method of controlling a cooling system.
  • a compressor mechanically elevates the temperature and pressure of a working fluid to achieve a desired vapor state.
  • a heat exchanger typically designated as a condenser, transfers heat from the compressed working fluid to an environment or fluid, thereby condensing the working fluid.
  • An expansion valve or other expansion device lowers the pressure of the condensed working fluid as it enters a second heat exchanger, typically designated as an evaporator, in which heat from the environment to be cooled is transferred to the working fluid.
  • the heated working fluid returns to the compressor, and the cycle is repeated.
  • the condenser transfers heat from the working fluid (i.e, heat from the environment to be cooled) by transferring heat to another environment (e.g., outdoors) or to a cooling fluid (e.g., chilled water / condenser fluid).
  • a typical chilled water condenser comprises a heat exchanger, and a fluid regulating valve. The condenser fluid picks up heat from the refrigerant flowing through the condenser and dumps the heat to the environment. The condenser fluid then flows through the regulating fluid valve and then back to the condenser. An alternate configuration would be to locate the valve after the condenser.
  • a vapor compression cooling system may be designed such that its heat removal (or cooling) capacity matches the heat load generated by the space that is being cooled.
  • the heat load of the space to be cooled will vary according to the various factors, including, for example, the season (outdoor temperature), equipment operating within the space, number of people present in the space, etc.
  • the cooling system must have capacity equal to the maximum heat load of the space to be cooled. However, this will result in selection of a cooling system with a capacity larger than required for most operating conditions. If the cooling system is operating at less than its rated capacity, the cooling system (e.g., refrigerant compressor) may cycle on and off repeatedly.
  • a method of controlling a vapor compression cooling system comprises operating a vapor compression cooling cycle comprising a condensing heat exchanger; determining a pressure or temperature of a fluid leaving the condenser; determining when to change a valve position in response to the pressure or temperature to control a flow of cooling fluid through the condenser.
  • Another aspect of the present invention comprises a vapor compression cooling system having a vapor compression cooling cycle comprising a condenser and a working fluid; a condenser cooling cycle comprising a fluid control valve adapted to vary a cooling fluid flow through the condenser; a transducer associated with the condenser and adapted to transduce either pressure or temperature of the working fluid; and a controller adapted to determine when to vary the position of the fluid control valve in response to the transduced pressure or temperature.
  • Figure 1 illustrates one of many embodiments of a cooling system utilizing aspects of the present invention.
  • Figure 2 is a chart that illustrates an exemplary embodiment of the bands in which the motorized ball valve of a vapor compression system operates.
  • Figure 3 illustrates another embodiment of a vapor compression system utilizing aspects of the present invention.
  • Computer programs for use with or by the embodiments disclosed herein may be written in an object oriented programming language, conventional procedural programming language, or lower-level code, such as assembly language and/or microcode.
  • the program may be executed entirely on a single processor and/or across multiple processors, as a stand-alone software package or as part of another software package.
  • Applicants have created a system and method of controlling the fluid flow through a fluid cooled heat exchanger in a vapor compression cooling system.
  • the thermal capacity of the cooling system can be optimally controlled.
  • the fluid flow and thus the thermal capacity of the cooling system may be optimally controlled in at least two ways: (1) by controlling the amount of heat removed from the condenser by controlling the cooling fluid flow through the condenser and (2) by controlling the amount of heat removed from the condenser by adjusting the heat transfer area of the condenser. For example, increasing the cooling fluid flow through the condenser may increase the cooling capacity of the system because more heat can be transferred from the refrigerant to the cooling fluid.
  • FIG. 1 illustrates an exemplary, and one of many, embodiment of a vapor compression cooling system 100 utilizing aspects of the present invention.
  • the cooling system 100 generally includes a vapor compression cooling loop 102 comprising a compressor 120, a liquid cooled condenser 130, an expansion mechanism 150, evaporator (i.e. heat exchanger) 160 and transducer 190.
  • the working fluid may be any two-phase refrigerant, such as chloroflourocarbons (CFCs), hydroflourocarbons (HFCS), or hydrochlorofluorocarbon (HCFCs) such as R- 22 but not excluding alternative refrigerants.
  • Secondary cooling loop 104 comprises an liquid cooler (i.e. heat exchanger) 170, a flow valve 140 and liquid cooled condenser (i.e. heat exchanger) 130.
  • Cooling system 100 also comprises a control unit 180 that is in communication with valve 140 and transducer 190.
  • Refrigerant is compressed in the compressor 120, which may be a reciprocating, scroll, or other compressor type, and preferably is a digital scroll compressor, such as those offered by Copeland.
  • the compressor 120 After the refrigerant is compressed, it travels through a discharge line 112 to the liquid cooled condenser 130, where heat is removed from the refrigerant.
  • the temperature and/or pressure of the refrigerant is transduced by transducer 190, which may be any type of pressure or temperature transducer known to those of ordinary skill in the art.
  • the refrigerant travels through a first liquid line 114 to an expansion mechanism 150.
  • Expansion mechanism 150 may comprise a valve, orifice or other liquid expansion device known to those of ordinary skill in the art.
  • the expansion mechanism 150 causes a pressure drop in the refrigerant, as the refrigerant passes through the mechanism.
  • the refrigerant travels through second liquid line 116, arriving at evaporator 160.
  • the low-pressure refrigerant absorbs heat from the environment to be cooled. More specifically, air from the environment to be cooled is passed through the evaporator coils so that heat is transferred from the air to the refrigerant. Refrigerant carrying the heat extracted from the environment then returns to the compressor 120 by suction line 118, completing the vapor compression cycle. It will be appreciated that the amount of heat absorbed in the evaporator 160 and the amount of heat transferred in the condenser 130 affect how long and how often compressor 120 must run. Therefore, controlling the amount of heat transferred in the liquid cooled condenser 130 directly affects the operation of compressor 120.
  • liquid cooled condenser 130 transfers heat from the refrigerant to a cooling fluid, which may be a two- phase refrigerant, glycol, water, or other type of fluid.
  • the cooling fluid is preferably chilled water.
  • the chilled water passes through the first cooling fluid line 172 to cooling fluid liquid cooler 170 where the heat from the cooling fluid is rejected into the outside environment by any known means, such as one or more cooling fans. Chilled water then travels to valve 140, which may be an electrically controlled motorized ball valve, solenoid proportional valve, globe valve, or pneumatic, digital, hydraulic, analog or other variable flow restricting device known to a person of ordinary skill in the art.
  • valve 140 is a motorized ball valve.
  • the cooling fluid travels through third cooling fluid line 176 and returns to liquid cooled condenser 130 where heat is transferred from the refrigerant to the cooling fluid.
  • Valve 140 may be controlled manually or by control unit 180.
  • Control unit 180 receives one or more inputs from transducer 190 and outputs one or more control signals to valve 140 or an actuator that controls valve 140.
  • Control unit 180 may use any of a number of control routines to control the valve 140 based on the transduced property of the refrigerant, such as pressure or temperature. Additionally, control unit 180 can be used to control compressor 120. For example, the control unit 180 may instruct the compressor 120, such as a digital scroll compressor, when to cycle on and off.
  • a control routine is implemented in controller 180 to optimally control cooling system 100.
  • a valve position (or flow volume) control routine maybe implemented by control unit 180 to control the opening and closing of valve 140.
  • control unit 180 and control software may be designed to implement a control strategy that serves to maintain the refrigerant discharge pressure within acceptable limits with minimal valve 140 repositions.
  • a preferred valve position control routine is described below. The routine assumes a variable capacity digital scroll compressor is used as compressor 120.
  • One of the goals of the valve position control routine is to avoid placing the valve, to the extent possible, into an opening state (where the valve 140 is continuously opening) or into a closing state (where the valve 140 is continuously closing).
  • the control routine implements a control strategy that makes (or does not make) incremental valve repositions at discrete points in time, such as, for example, generally corresponding to the discrete points in time when the refrigerant pressure is sampled.
  • Another goal is to avoid startup high pressure conditions by opening valve 140 to a predetermined setpoint before the compressor 120 is started.
  • the setpoint is preferably set to 50% along with a thirty second delay.
  • valve position control routine Another goal of the valve position control routine is to have an efficient control strategy that can be implemented in a system, like those associated with Copeland Digital Scroll ® compressors, where the refrigerant pressure is not substantially stable. But rather is typically always increasing or decreasing and where the instantaneous or near-instantaneous rate of change of the refrigerant pressure does not provide reliable information as to the overall direction of change of the refrigerant pressure. To allow the valve position control routine to operate in such environments, the valve position control routine does not use or rely upon, the rate of change of the refrigerant discharge pressure or whether the discharge pressure is increasing (or not) or decreasing (or not) to control the valve 140.
  • the valve position control routine samples the refrigerant discharge pressure, the pressure read by discharge transducer 190, on a predetermined basis and makes a determination to cause (or not to cause) a valve reposition each time a refrigerant discharge pressure reading is obtained.
  • Alternative embodiments of the valve position control routine could use other readings such as the temperature of the discharge transducer 190 to determine whether to cause (or not to cause) a valve reposition each time a reading is obtained. These alternatives may include using different types of refrigerant which may change the pressure settings.
  • valve position control routine operates, in principal, to control the refrigerant discharge pressure such that it remains within an "Acceptable Operating Band.” This is accomplished in the valve position control routine by defining a plurality of different bands of detected refrigerant discharge pressures and then taking (or not taking) action, depending on where a detected discharge pressure falls within the defined bands.
  • the first band defined by the valve position control routine is the
  • Acceptable Operating Band This band reflects the range of refrigerant discharge pressures within which the system is intended to operate.
  • the Acceptable Operating Band was set and fixed as the band between 175 and 210 PSIG.
  • the users of the system will be able to enter a pressure adjustment offset value that will index the operating band by the offset value.
  • the valve position control routine defines four bands reflecting discharge pressures above the upper limit of the Acceptable Operating Band. These bands are illustrated in FIG. 2, which is labeled to identify: (i) a First High Band; (ii) a Second High Band; (iii) a Third High Band; and (iv) a High Band.
  • a First High Band was set as the band between 210-220 PSIG;
  • the Second High Band was set as the band between 220-230;
  • the Third High Band was set as the band between 230- 350 PSIG;
  • the High Band was set as the band of pressures over 350 PSIG.
  • users of the system will be able to enter a pressure adjustment offset value that will index all bands except (iv) High Band by the offset value.
  • the valve position control routine also defines three bands reflecting discharge pressures below the lower limit of the Acceptable Operating Band. These bands are illustrated in FIG. 2, which is labeled to identify: (i) a First Low Band; (ii) a Second Low Band; and (iii) a Low Band.
  • FIG. 2 is labeled to identify: (i) a First Low Band; (ii) a Second Low Band; and (iii) a Low Band.
  • the First Low Band was set as the band between 160-175 PSIG
  • the Second Low Band was set as the band between 100-160 PSIG
  • the Low Band was set as the band below 100 PSIG.
  • the users of the system will be able to enter a pressure adjustment offset value that will index all bands except (iii) Low Band by the offset value.
  • valve position control routine keeps track of whether a repositioning event has occurred in the First High Band, the Second High Band and/or the First Low Band.
  • High Refrigerant Pressure Example The valve position control routine initially starts under "Initial Conditions" where there are no recorded repositioning events for the First High Band, the Second High Band, and/or the First Low Band. If a detected pressure within the Acceptable Operating Band is detected when the Initial Conditions exist, valve position control routine will take no action with respect to the position of the valve 140 (i.e., the position of the valve 140 will not change in response to that detected pressure).
  • valve position control routine may or may not reposition the valve 140. The situation of a detected pressure above the Acceptable Operating Band is discussed first.
  • valve position control routine will open the valve 140 an incremental amount of 5% and will record a repositioning event for the First High Band. If, while Initial Conditions exist, a pressure reading is provided that is above the lower limit of the Second High Band, the valve position control routine will open the valve 140 an incremental amount of 5% and will record a repositioning event for the Second High Band. This repositioning, if made, is additive of any repositioning made as a result of the pressure being above the lower limit of the First High Band.
  • This repositioning if made, is additive of any repositioning made as a result of the pressure being above the lower limit of the First High Band or the Second High Band. Finally, if, while Initial Conditions exist, a pressure reading is provided that is above the lower limit of the High Band, the valve 140 is opened to its fully open (100%) point.
  • valve position control routine changes the system such that the number of repositioning events used to bring the refrigerant discharge pressure back to within the Acceptable Operating Band is limited. This is accomplished in the following manner. [0047] If, once a repositioning event has occurred, a pressure is detected that is above the lower limit of the High Band, the valve position control routine will either: (i) open the valve 140 to its fully open (100%) position (if the valve 140 was not at that point) or (ii) take no action if the valve 140 is already at the 100% open position.
  • valve position control routine will open the valve 140 an additional 10% from its previous position (up to the 100% open position). This 10% open repositioning will occur regardless of the status of any prior repositioning events.
  • valve position control routine will take (or not take) action as follows. If there is no recorded repositioning event for the Second High Band when the pressure is detected, the system will open the valve 140 incrementally 5% and will record a Second High Band repositioning event. If there is a recorded repositioning event for the Second High Band, the valve position control routine will take no action and will allow the valve 140 to remain in its existing position.
  • valve position control routine If, once a repositioning event has occurred, a pressure is detected that is between the lower and upper limits of the First High Band, the valve position control routine will take no action and will allow the valve 140 to remain in its existing position. This is because, under such conditions, a repositioning event would have been recorded for the First high Band. [0051] As the above, indicates, once a repositioning event has occurred, valve position control routine operates such as to avoid placing the valve 140 in an opening state (where the valve 140 is always opening). Specifically, in the valve position control routine, there is only a single, one-time, 5% opening adjustment for a detected pressure within the First High Band, and a single, one-time, 5% opening adjustment for a detected pressure within the Second High Band.
  • valve position control routine uses a timer based control strategy that runs in parallel with the control strategy based on detected pressures, described above.
  • the valve position control routine sets a five minute timer when a pressure is detected that is above the lower limit of the First High Band. Once set, the timer is reset upon: (i) the occurrence of a repositioning event, or (ii) the detection of a pressure below the lower limit of the First High Band. If this five-minute timer "times out" before it is reset, the valve position control routine will open the valve 140 an additional 5%. In this manner, the refrigerant discharge pressure will be driven towards the Acceptable Operating Range using a limited number of repositioning events.
  • the valve position control routine may implement, under certain circumstances, a "closing" valve repositioning, accompanied by a clearing of the record of a repositioning for the First High Band or the Second High Band. Specifically, if a pressure is detected that is 5 PSIG below the lower limit of the Second High Band and there is a record of a repositioning for the Second High Band, the valve position control routine will: (i) determine whether to make an adjustment to the valve and (ii) clear the record of the repositioning for the Second High Band.
  • valve position control routine will: (i) determine whether to make an adjustment to the valve and (ii) clear the record of the repositioning for the First High Band. Once the records for any repositioning in the Second High Band and the First High Band are cleared, such that there are no records of repositioning, the Initial Conditions will be re-established.
  • valve position control routine will close valve 140 4% once, for each detected pressure that is below the upper limit of the First Low Band. A record of such repositioning is kept to ensure that one repositioning is made for such a detected pressure. If, after the initial 4% closure is made in response to the detection of pressure below the upper limit of the First Low Band, pressures are detected that are within the First Low Band, no additional closing repositioning will be made. [0057] If a pressure is detected that is below the upper limit of the
  • valve position control routine will close the valve 140 5% incrementally (up to a minimum closure at the 25% open point) in response to that detected pressure, regardless of any prior repositioning events. [0058] If a pressure is detected that is below the upper limit of the Low
  • valve position control routine will close valve 140 to the 25% open position in response to that detection, if the valve 140 is not already at the 25% open position.
  • valve position control routine may implement, under certain circumstances, an "opening" valve repositioning, accompanied by a clearing of the record of a repositioning for the First Low Band or the Second High Band.
  • valve position control routine will: (i) determine whether to make an adjustment to the valve and (ii) clear the record of the repositioning for the First Low Band.
  • the valve position control routine may be implemented.
  • the system could use the discharge temperature measured by discharge transducer 190 to implement the control strategy.
  • an electronic timing circuit could be designed to control the valve 140 in place of or in addition to the valve position control routine.
  • FIG. 3 illustrates alternative embodiment of a vapor compression system utilizing aspects of the present invention.
  • FIG. 3 illustrates a portion of a traditional vapor compression cooling system 300, such as the one describes in FIG. 1, utilizing paradenser 310, for example the Liebert Paradenser® , in the place of condenser 30.
  • a paradenser is a series of condensers, depicted here as condensers 310a, 310b, and 310c.
  • the system is plumbed such that a manifold 340 is adapted to route cooling fluid through one or more of condenser 310a, 310b, or 31 Oc in paradenser 310.
  • a control unit 380 may be adapted to control the manifold 340 such that cooling fluid is routed to the condensers as needed to optimize system capacity and/or to match the heat load generated by the space that is being cooled.
  • the control unit 380 can direct cooling fluid flow through first fluid flow line 302 when condensers 330b and 330c are not required to reject heat from the refrigerant.
  • the control unit 380 can direct additional cooling fluid flow through second fluid flow line 304 when condenser 330c is not required to reject heat from the refrigerant.
  • control unit 380 can direct cooling fluid flow through first cooling fluid line 306 when all three condensers of the paradenser are needed to reject heat from the refrigerant.
  • control unit 380 would direct cooling fluid through condenser 330c and condenser 330b. As more heat rejection was necessary, control unit 380 could additionally direct cooling fluid through condenser 330a. As more cooling fluid flows through more condensers, more heat can be rejected from the refrigerant.
  • This embodiment could be implemented independent of or in conjunction with the valve position control routine described herein.
  • a condenser that is divided into several parts can be utilized.
  • the divided condenser may be controlled so that fluid is sent to one or more compartments to maximize the efficiency of the condenser.
  • the controllable manifold may be used on the working fluid side of the system to route working fluid to one or more condenser.
  • Further embodiments include multiple valves in multiple cooling systems controlled by a single controller.
  • the various methods and embodiments of the system and method of controlling a fluid flow through a fluid cooled heat exchanger can be included in combination with each other to produce variations of the disclosed methods and embodiments. Discussion of singular elements can include plural elements and vice-versa.

Abstract

L'invention porte sur un système de refroidissement par compression de vapeur ayant une unité de commande apte à recevoir des informations de pression ou de température de fluide de travail pour commander une soupape de commande de fluide de refroidissement de condenseur pour rendre minimaux des changements d'écoulement à travers la soupape.
PCT/US2007/088016 2007-08-01 2007-12-18 Procédé et appareil pour commander un système de refroidissement WO2009017517A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN200780100125A CN101815911A (zh) 2007-08-01 2007-12-18 控制冷却系统的方法和装置
EP07869467A EP2185874A1 (fr) 2007-08-01 2007-12-18 Procédé et appareil pour commander un système de refroidissement

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US11/832,176 2007-08-01
US11/832,176 US20090031735A1 (en) 2007-08-01 2007-08-01 System and method of controlling fluid flow through a fluid cooled heat exchanger

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Publication Number Publication Date
WO2009017517A1 true WO2009017517A1 (fr) 2009-02-05

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EP (1) EP2185874A1 (fr)
CN (1) CN101815911A (fr)
WO (1) WO2009017517A1 (fr)

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KR100758902B1 (ko) * 2004-11-23 2007-09-14 엘지전자 주식회사 멀티 공기조화 시스템 및 그 제어방법
CN109405367A (zh) * 2018-10-29 2019-03-01 珠海格力电器股份有限公司 冷水机组及冷却装置

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US20090031735A1 (en) 2009-02-05
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