EP2148155A1 - Dispositif de refroidissement - Google Patents

Dispositif de refroidissement Download PDF

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Publication number
EP2148155A1
EP2148155A1 EP09405117A EP09405117A EP2148155A1 EP 2148155 A1 EP2148155 A1 EP 2148155A1 EP 09405117 A EP09405117 A EP 09405117A EP 09405117 A EP09405117 A EP 09405117A EP 2148155 A1 EP2148155 A1 EP 2148155A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
cooling
heat
medium
cooling 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.)
Granted
Application number
EP09405117A
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German (de)
English (en)
Other versions
EP2148155B1 (fr
Inventor
Max Aeberhard
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.)
UL Tech AG
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UL Tech AG
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Publication date
Priority claimed from CH01149/08A external-priority patent/CH699233A2/de
Application filed by UL Tech AG filed Critical UL Tech AG
Publication of EP2148155A1 publication Critical patent/EP2148155A1/fr
Application granted granted Critical
Publication of EP2148155B1 publication Critical patent/EP2148155B1/fr
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    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems

Definitions

  • the invention relates to a cooling device and a method for cooling a first medium according to the preamble of claims 1 and 7.
  • Cooling devices are widely used for cooling room air and / or water in buildings. Heat or waste heat generating processes, components or machines can also be maintained by means of cooling devices at or below a predetermined temperature level.
  • cooling devices typically include one or more chillers or heat pumps operating on the principle of reversing the Carnot process.
  • free-cooling devices instead of chillers at sufficiently low outside temperatures to cool a medium.
  • Switching from free-cooling to cooling by means of a chiller and vice versa can be automatic when exceeding or falling below a temperature limit of the outside air detected by a temperature sensor respectively.
  • a disadvantage of such solutions is that the potential of cost-effective and energy-efficient cooling by outside air is only insufficiently exhausted.
  • the medium to be cooled releases heat to a fluid heat carrier, eg water, in a first heat exchanger.
  • a fluid heat carrier eg water
  • the fluid heat carrier is exclusively recooled by a preferably designed as a hybrid recooler outdoor heat exchanger - ie by free-cooling - and returned to the first heat exchanger. With increasing outside temperature, this is no longer sufficient to extract sufficient heat from the heat transfer medium.
  • the heat transfer medium or coolant is additionally deprived of heat by means of a chiller if the sole direct heat removal by free-cooling is no longer sufficient to cool the medium to the desired temperature.
  • the proportion of the chiller provided Cooling capacity is continuously regulated according to the respective requirements.
  • the flow rate of the coolant to the chiller can be controlled or regulated by means of a continuously or continuously adjustable actuator (eg a modulatable multi-way valve) depending on the outside temperature and the load of a controller.
  • a continuously or continuously adjustable actuator eg a modulatable multi-way valve
  • the setting of the actuator is continuously, continuously or stepwise adapted to the particular circumstances in accordance with a predetermined function of the controller.
  • the proportion of cooling power provided by the chiller is thus increased based on this function.
  • a plurality of actuators may also be provided, in particular also further continuously adjustable or adjustable actuators in order to control or regulate the cooling device in the manner according to the invention.
  • the proportion of cooled by the chiller heat transfer stream can be adapted to the respective conditions, for example by one or more funding or pumps with controllable or variable flow rate, so that the cooling potential of the outside air is optimally utilized.
  • the outer heat exchanger or hybrid Recooler not only used for heat dissipation during direct free-cooling, but also for discharging the heat given off by the chiller to the environment or to the outside air. This is a particularly space-saving, cost-effective and energy-efficient variant.
  • a hybrid recooler which dissipates heat to the outside air
  • other heat exchangers could be provided which release heat to another medium such as surface water or to the soil. In a system with the inventive cooling device energy consumption and operating costs are small compared to conventional solutions.
  • the Figures 1a, 1b and 1c schematically show a part of a first embodiment of the inventive cooling device for cooling a first medium at different temperatures of a heat receiving additional medium such as outside air.
  • the first medium can be, for example, room air or outside air, which is supplied to a room, for example a computer or server room of a data center.
  • the first medium may also be, for example, water or another cooling fluid or generally a fluid heat carrier which is used, for example, for cooling equipment, machines or components.
  • active Connecting lines, through which a coolant or a fluid heat carrier flows, are each highlighted by bold, broken lines.
  • the simple cooling device in the Figures 1a, 1b and 1c comprises a first heat exchanger 1, in which the first medium emits heat to a fluid heat carrier, said heat carrier is conveyed by a pump or a conveyor 9 in a cooling network and circulated in lines of this cooling network.
  • the first heat exchanger 1 is, for example, a fin heat exchanger and the first medium is, for example, room air.
  • the first heat exchanger 1 and a second heat exchanger 3 are connected on the primary side via a first connecting line 5 and a second connecting line 7 with each other to a pitch circle of the cooling network.
  • a pump is designed as conveying means 9 for the fluid heat carrier (for example water or another coolant) in this cooling network.
  • the first medium 1 heat is removed in the first heat exchanger.
  • the heat carrier or the coolant releases heat to a second medium.
  • the recooled coolant is fed back to the first heat exchanger 1 via a continuously or continuously adjustable actuator 11.
  • This actuator 11 is a modulating multi-way valve, wherein the supplying portion of the first connection line 5 with one of two inputs of this multi-way valve and the diverting Section of the first connecting line 5 is connected to the output of this multi-way valve.
  • the cooling network additionally comprises a third heat exchanger 13, which is assigned to a recooler 15, and in which heat can be withdrawn from the fluid heat carrier and released to a third medium.
  • the recooler 15 is formed as a hybrid recooler 15, wherein the third heat exchanger 13 is sprayed with water to allow improved heat dissipation to the outside air.
  • the third heat exchanger 13 could also be designed for heat dissipation to the ground or to surface water.
  • the third heat exchanger 13 is coupled to the pitch circle of the cooling network, with a third connecting line 17 connected to a second input of the multiway valve and a fourth connecting line 19 to the second connecting line 7 between the first heat exchanger 1 and the second heat exchanger 3.
  • the third connecting line 17 is also connected via a fifth connecting line 21 to the second connecting line 7, wherein the mouth of this fifth connecting line 21 is closer to the second heat exchanger 3 as the confluence of the fourth connecting line 19, and wherein between these two mouths a further actuator 23 for Breaking and releasing the second connection line 7 is arranged.
  • the actuators 11 and 23 and the conveyor 9 and any other actuators and / or funding are controlled by a (not shown) control or controllable.
  • the controller detects the measurement quantities required for operation, eg the outside temperature and the room temperature to be cooled by means of suitable sensors (not shown) and preferably has an interface for prescribing operating parameters such as a lower limit temperature T1 for the outside air, below that a cooling of the first Medium exclusively by heat to the outside air with the third heat exchanger 13 is possible, and an upper limit temperature T2 for the outside temperature above which cooling of the first medium by direct heat to the outside air or by pure free-cooling is no longer possible.
  • T1 for the outside air
  • T2 an upper limit temperature
  • the control valve 23 is open. This situation corresponds to summer operation, the outside temperature being above the upper limit temperature T2. According to the situation FIG. 1b the outside temperature is below the lower limit temperature T1. This corresponds to winter operation. The recooling of the coolant is 100% by the third Heat exchanger 13.
  • the control valve 23 is closed. According to the situation Figure 1c the outside temperature is between the lower limit temperature T1 and the upper limit temperature T2. This corresponds to the mixed operation.
  • the re-cooling of the coolant takes place both through the second heat exchanger 3 and through the third heat exchanger 13, wherein the percentage of the heat transfer medium flowing through the second heat exchanger 3 on the entire heat transfer flow flowing through the first heat exchanger 1, or an equivalent size in each case by the Position of the multi-way valve 11 is determined.
  • Both the first input and the second input of the multi-way valve 11 are connected to the output thereof, wherein the free opening cross-sections are each given complementary to each other by the respective working position of the multi-way valve 11.
  • the control valve 23 is closed.
  • FIG. 2 shows a further embodiment of the cooling device.
  • the second heat exchanger 3 is designed here as an evaporator of a refrigerating machine 25 and connected in a refrigerant circuit via a compressor 27 with a fourth heat exchanger 29 acting as a condenser.
  • the condenser in turn is connected to the second heat exchanger 3 via a connecting line with an expansion valve 31.
  • the recooler 15 may additionally comprise a fifth heat exchanger 33 arranged in the fourth connecting line 19 in front of the third heat exchanger 13, and a further conveying means 9 and a sixth connecting line 35 with a further actuator 23 between the third connecting line 17 and the fourth connecting line 19 at the beginning of the fifth Heat exchanger 33. Am on the basis of FIGS.
  • the fifth heat exchanger 33 in conjunction with the third heat exchanger 13 and the further conveying means 9 and the opened further adjusting means 23, can be a separate cooling device operable independently of the first pitch circle with the first heat exchanger 1 and the second heat exchanger 3.
  • an independent heat exchanger is provided for removing heat from the refrigerating machine 25, namely the fourth heat exchanger 29.
  • FIG. 3 A preferred further variant of the cooling device is shown in FIG. 3 shown.
  • the fourth heat exchanger 29 acting as a condenser is assigned to the recooler 15.
  • the fourth heat exchanger 29 is analogous to the fifth heat exchanger 33 in an arrangement according to FIG. 2 arranged in the fourth connecting line 19 between the third heat exchanger 13 and the first heat exchanger 1.
  • the chiller 25 can deliver heat to the heat carrier in the cooling network, which can then be dissipated in the third heat exchanger 13 to the environment.
  • the third heat exchanger 13 can thus be used depending on the position of the actuator 11 for the direct removal of heat by means of free-cooling and / or for the indirect removal of heat which is discharged from the chiller 25 at a higher temperature level, the proportion of the chiller 25 recooled heat transfer stream continuously on the entire flowing through the first heat exchanger 1 heat transfer stream between 0% and 100% is adjustable.
  • the fourth heat exchanger 29 absorbs no heat from the chiller 25 and thus serves only as a flow line.
  • Compared to an embodiment according to FIG. 2 can save the space and the cost of a separate heat exchanger of the chiller 25.
  • FIG. 4 shows a schematic representation of another cooling device in which the chiller 25, and the conveying and adjusting means of the hydraulic system are combined to form a unit 26.
  • the first heat exchanger 1 is connected via two main lines 37a, 37b to the heat exchanger 13 of the hybrid recooler 15, wherein in the one main line 37a two circulation pumps 9a, 9b are arranged as conveying means 9.
  • the main lines 37a, 37b are connected to each other via two transverse lines 39a, 39b, each with a control valve 41a, 41b, wherein the transverse lines 39a, 39b between the two circulation pumps 9a, 9b open into the main line 37a.
  • the first transverse line 39a is connected via two connecting lines 43a, 43b to the cooling heat exchanger 3 of the chiller 25, wherein in the connecting line 43a, a pump 9c is arranged with a continuously variable flow rate.
  • the second transverse line 39b is connected via two connecting lines 43c, 43d to the heat-emitting heat exchanger 29 of the chiller 25, wherein in the connecting line 43c, a pump 9d is arranged with continuously variable flow rate.
  • Spray unit 45 for spraying the fins of the heat exchanger 13 with water
  • a catch basin 47 below the inclined heat exchanger 13 for collecting the dripping spray water
  • a pump 49 for conveying the spray water from the catch basin 47 to the spray unit 45.
  • a fan 51 for conveying Outside air through the slats of the heat exchanger 13 (shown by the arrow P). The air flow (supported by evaporating water spray) cools the circulating heat transfer medium in the pipe network.
  • FIGS. 1a, 1b, 1c Analogous to the continuously adjustable multiway valve in the embodiments of the invention according to the FIGS. 1a, 1b, 1c .
  • the heat carrier can be additionally cooled by the chiller 25 with insufficient cooling capacity of the external heat exchanger 13 by the flow rates from the first main line 37a via the cooling heat exchanger 3 of the refrigerator 25 to the second main line 37b and from the second main line 37b via the heat-emitting heat exchanger 29 of the Cooling machine 25 to the first main line 37a of the (not shown) control means of the pumps 9c, 9d controlled or regulated.
  • FIG. 5 shows in principle the proportions of the discharged from the chiller 25 cooling load (curve A) and from the outdoor heat exchanger 13 by pure free-cooling directly discharged cooling load (curve B) on the total discharged cooling load as a function of Ambient or outside temperature T EXT , below the lower limit temperature T1 only the outer heat exchanger 13 is used (chiller not active), and wherein above the second limit temperature T2, the entire heat load is dissipated via the heat exchanger 3 of the chiller.
  • the characteristic curves A and B do not necessarily have to be linear with the outside temperature. They are generally stored as continuous functions of the outside temperature and possibly other parameters in the controller.
  • the control of the heat dissipation by the chiller 25 can be done, for example, solely on the basis of the outside temperature: If the outside temperature is below a lower limit temperature T1, it is ensured by the position of continuously adjustable actuators 11 and / or the respective delivery rate of conveying means 9 with continuously variable delivery rate the first medium - eg room air - is cooled only by free-cooling or by cooling the heat carrier by direct heat dissipation in the outer heat exchanger 13 only.
  • the controller changes the manipulated variables for the continuously adjustable actuators 11 and / or conveying means 9 continuously or continuously or in general according to a predetermined function in the control, whereby an increasing proportion of the coolant through the refrigerating machine 25 and a decreasing proportion of the coolant can be cooled only by pure free-cooling in the outer heat exchanger 13. If the outside temperature reaches an upper limit value, the actuators 11 or conveying means 9 are adjusted so that the total heat load in the heat exchanger 3 of the refrigerating machine 25 is released.
  • the control can also take into account other measured variables in order to calculate the suitable control variables for the actuators 11 or conveying means 9.
  • temperatures and / or volume flows of the coolant can be detected and processed at one or more points in the cooling network.
  • the temperature of the first medium to be cooled that is, for example, the room temperature of a data center to be cooled, belongs to the measured variables processed by the control.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Other Air-Conditioning Systems (AREA)
EP09405117.4A 2008-07-21 2009-07-20 Dispositif de refroidissement Active EP2148155B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH01149/08A CH699233A2 (de) 2008-07-21 2008-07-21 Kühlvorrichtung.
CH01443/08A CH699225A1 (de) 2008-07-21 2008-09-10 Kühlvorrichtung.

Publications (2)

Publication Number Publication Date
EP2148155A1 true EP2148155A1 (fr) 2010-01-27
EP2148155B1 EP2148155B1 (fr) 2017-09-06

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP09405117.4A Active EP2148155B1 (fr) 2008-07-21 2009-07-20 Dispositif de refroidissement

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EP (1) EP2148155B1 (fr)
CH (1) CH699225A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012122150A3 (fr) * 2011-03-10 2012-11-01 Parker Hannifin Corporation Système de refroidissement
US20170077970A1 (en) * 2014-04-03 2017-03-16 Redline Communications Inc. Systems and methods for increasing the effectiveness of digital pre-distortion in electronic communications
US9807908B2 (en) 2011-06-30 2017-10-31 Parker-Hannifin Corporation Pumped liquid cooling system using a phase change fluid with additional subambient cooling
EP3757481A4 (fr) * 2018-02-22 2021-02-17 Mitsubishi Electric Corporation Dispositif de climatisation et unité de traitement d'air
US11022349B2 (en) 2015-07-22 2021-06-01 Carrier Corporation Hydronic system for combining free cooling and mechanical cooling

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4406138A (en) * 1981-11-18 1983-09-27 Honeywell Inc. Load management control air conditioning system
EP0584733A1 (fr) * 1992-08-22 1994-03-02 DaimlerChrysler Aerospace Airbus Gesellschaft mit beschränkter Haftung Dispositif de refroidissement pour avion
US6293106B1 (en) * 2000-05-18 2001-09-25 Praxair Technology, Inc. Magnetic refrigeration system with multicomponent refrigerant fluid forecooling
EP1164338A1 (fr) * 1999-02-24 2001-12-19 Hachiyo Engineering Co., Ltd. Systeme de pompe a chaleur combinant un cycle ammoniac avec un cycle dioxyde de carbone

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4238364A1 (de) * 1992-11-13 1994-05-26 Behr Gmbh & Co Einrichtung zum Kühlen von Antriebskomponenten und zum Heizen eines Fahrgastraumes eines Elektrofahrzeugs
FR2740397B1 (fr) * 1995-10-26 1997-12-05 Valeo Climatisation Dispositif de chauffage-climatisation de l'habitacle d'un vehicule automobile a moteur electrique
EP1089891B1 (fr) * 1998-06-22 2003-12-17 Silentor Holding A/S Systeme de recuperation de chaleur residuelle
EP1515098A1 (fr) * 2003-09-12 2005-03-16 Ingenjörsfirma Kontrollelektronik Hjärtström & Kalén Aktiebolag Méthode et dispositif pour le conditionnement d'un environnement

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4406138A (en) * 1981-11-18 1983-09-27 Honeywell Inc. Load management control air conditioning system
EP0584733A1 (fr) * 1992-08-22 1994-03-02 DaimlerChrysler Aerospace Airbus Gesellschaft mit beschränkter Haftung Dispositif de refroidissement pour avion
EP1164338A1 (fr) * 1999-02-24 2001-12-19 Hachiyo Engineering Co., Ltd. Systeme de pompe a chaleur combinant un cycle ammoniac avec un cycle dioxyde de carbone
US6293106B1 (en) * 2000-05-18 2001-09-25 Praxair Technology, Inc. Magnetic refrigeration system with multicomponent refrigerant fluid forecooling

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012122150A3 (fr) * 2011-03-10 2012-11-01 Parker Hannifin Corporation Système de refroidissement
US9807908B2 (en) 2011-06-30 2017-10-31 Parker-Hannifin Corporation Pumped liquid cooling system using a phase change fluid with additional subambient cooling
US20170077970A1 (en) * 2014-04-03 2017-03-16 Redline Communications Inc. Systems and methods for increasing the effectiveness of digital pre-distortion in electronic communications
US9819373B2 (en) 2014-04-03 2017-11-14 Redline Communications Inc. Systems and methods for increasing the effectiveness of digital pre-distortion in electronic communications
US11022349B2 (en) 2015-07-22 2021-06-01 Carrier Corporation Hydronic system for combining free cooling and mechanical cooling
EP3757481A4 (fr) * 2018-02-22 2021-02-17 Mitsubishi Electric Corporation Dispositif de climatisation et unité de traitement d'air

Also Published As

Publication number Publication date
CH699225A1 (de) 2010-01-29
EP2148155B1 (fr) 2017-09-06

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