US20140230471A1 - Compact Cooling System and Method for Accurate Temperature Control - Google Patents

Compact Cooling System and Method for Accurate Temperature Control Download PDF

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Publication number
US20140230471A1
US20140230471A1 US14/343,319 US201114343319A US2014230471A1 US 20140230471 A1 US20140230471 A1 US 20140230471A1 US 201114343319 A US201114343319 A US 201114343319A US 2014230471 A1 US2014230471 A1 US 2014230471A1
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United States
Prior art keywords
refrigerant
accumulator
cooling system
cooling
supply
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Abandoned
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US14/343,319
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English (en)
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Verlaat Bart
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European Organization for Nuclear Research CERN
NIKHEF
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European Organization for Nuclear Research CERN
NIKHEF
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Publication of US20140230471A1 publication Critical patent/US20140230471A1/en
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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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—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
    • F25B23/00—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect
    • F25B23/006—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect boiling cooling systems

Definitions

  • the present invention relates to a compact and structurally simple cooling system and cooling method, in particular to a two-phase cooling system and cooling method for evaporative CO 2 cooling with high temperature accuracy.
  • Carbon dioxide (CO 2 ) cooling was widespread in the late 19 th century and early 20 th century before being replaced by synthetic refrigerants, but is now again gaining increasing attention for many applications in science and technology, ranging from fridges and air-conditioning, in particular for motor vehicles, to ice-skating rings and cooling of detector equipment for high energy physics experiments. A manifold range of applications, both old and new, is described by A. Pearson, “Carbon Dioxide New Uses for an Old Refrigerant”, International Journal of Refrigeration 28 (2005) 1140 -1148.
  • CO 2 cooling is attractive because it offers the combination of high heat transfer coefficients (one order of magnitude higher than traditional refrigerants) with low mass cooling structures.
  • CO 2 has a relatively high evaporation pressure, so that the vapor volumes remain small, resulting in small diameter tubing.
  • CO 2 also has a large latent heat of evaporation, which allows for a reduced fluid flow and even smaller tubing diameters. Since CO 2 cannot exist as a liquid under atmospheric pressure, any leak or spilling of CO 2 will lead to immediate vaporization of the leaked CO 2 , and will not harm the equipment by a liquid spill. This is a clear advantage over conventional liquid refrigerants, and makes CO 2 a good choice for cooling sensitive objects or objects placed in sensitive environments, such as for the temperature control of scientific equipment inside clean laboratories.
  • CO 2 cooling allows for an accurate thermal control of distant setups with only small additional cooling hardware, which is a frequent desire in many high-tech applications today.
  • This cooling system 100 comprises an accumulator vessel 102 for storing a supply of CO 2 in a liquid and vapor mixture.
  • the CO 2 boiling pressure is controlled using a combination of heating and cooling, wherein heating is achieved by means of an electrical heater such as a thermo siphon heater 104 , and cooling of the supply of CO 2 in the accumulator vessel 102 can be performed by employing an integrated cooling spiral 106 connected to an external chiller 108 .
  • the external chiller 108 also serves to sub-cool the refrigerant in the condenser 110 , which is in fluid communication both with the accumulator vessel 102 and a liquid pump 112 .
  • the chiller 108 remains always cooler than the accumulator 102 saturation temperature, and this is needed to provide subcooled liquid inside the pump 112
  • the sub-cooled refrigerant is supplied to a heat exchanger 114 , where the liquid refrigerant is preheated to the saturation temperature by bringing it into thermal contact with a return pipe 116 comprising CO 2 in a mixed liquid/vapor phase returning from the object to be cooled.
  • liquid CO 2 118 with a temperature that corresponds to the boiling temperature of the return pipe 116 is supplied to an evaporator (not shown) in thermal contact with the experiment to be cooled.
  • the pressure drop towards the evaporator causes the supplied liquid to boil in the evaporator and realizes a direct temperature control of the attached experiment via the system pressure regulated in the accumulator 102 .
  • the refrigerant returns to the cooling system 100 via the return pipe 116 , and is channeled through the heat exchanger 114 to the condenser 110 , whereupon the cooling cycle begins anew.
  • the cooling cycle and operation of the conventional 2PACL system is further illustrated in the pressure-enthalpy phase diagram of FIG. 2 .
  • the sub-cooled liquid ( 1 ) is pumped into the system by means of the liquid pump 112 ( 1 - 2 ).
  • the internal heat exchanger ( 2 - 3 ) 114 heats up the pumped sub-cooled liquid to the saturation temperature of the evaporator, causing the inlet of the evaporator always to be saturated after liquid injecting (point 4 within the two-phase zone of the pressure-enthalpy diagram).
  • Point 4 after expansion 3 - 4 in the phase diagram of FIG. 2 designates the moment when the fluid starts boiling due to the initial temperature setting of the liquid temperature in point 3 .
  • the fluid state in the evaporator is two-phase, and nearly independent of the absorbed heat.
  • the independence of the heat absorption is ideal for scientific experiments as a temperature control under loaded and unloaded conditions is often demanded
  • the pressure drop between the evaporator ( 4 - 5 ) and the accumulator connection ( 1 ) is low, and hence the accumulator 102 directly controls the pressure and hence temperature of the evaporator.
  • the conventional CO 2 evaporative cooling system as described with reference to FIGS. 1 and 2 allows for an accurate (isothermal) and direct temperature control of even distant objects to be cooled, and does not require any active components near the object. Tubes of very small diameter are sufficient to provide the refrigerant to the evaporator, possibly over very long transfer lines, while all the active hardware may be placed in a distant cooling plant which can be made easy accessible. This is particularly advantageous for high energy physics experiments, in which the cooling plant is in general far away from the detector device to be cooled, and local control or monitoring of the cooling at the detector device is usually unfeasible due to the high levels of radiation encountered there.
  • a cooling system comprises a liquid pump having an inlet and an outlet, said liquid pump adapted for pumping a liquid refrigerant, an outlet fluid path for said refrigerant, said outlet fluid path connected to said outlet of said liquid pump, and an inlet fluid path for said refrigerant, said inlet fluid path connected to said inlet of said liquid pump, as well as an accumulator adapted for storing a supply of said refrigerant, said accumulator in fluid communication with said inlet fluid path.
  • the system further comprises a condenser adapted for cooling said refrigerant, said condenser arranged in said inlet fluid path between said accumulator and said inlet of said fluid pump, wherein said outlet fluid path is in thermal contact with said accumulator so to allow said refrigerant flowing through said outlet fluid path to exchange heat with said accumulator.
  • the accumulator may hence be cooled by the discharge liquid of the pump, which is always warmer than the saturation temperature of the refrigerant at the pump inlet.
  • This provides a self-regulation that prevents the accumulator from becoming cooler than the saturation temperature of the pump inlet, and hence automatically preserves the sub-cooling level needed to guarantee uninterrupted operation of the liquid pump, without requiring external sub-cooling control by means of a programmable logic control unit.
  • the thermal contact of the outlet fluid path with the accumulator allows to set the temperature of the outgoing refrigerant to the accumulator temperature. This ensures that the refrigerant is set to boiling temperature for delivery to the object to be cooled.
  • the accumulator in thermal contact with the outlet fluid path integrates the functionalities of a standard accumulator and an external heat exchanger of a conventional 2PACL cooling system.
  • the cooling system according to the present invention thus allows dispensing both with a separate heat exchanger and a complex PLC controller, and is hence structurally simpler, smaller and easier to build.
  • the outlet fluid path traverses said accumulator or contacts said accumulator.
  • the cooling system comprises a heat exchanger adapted for exchanging heat with said accumulator, said heat exchanger arranged in said outlet fluid path.
  • said heat exchanger comprises a cooling spiral in fluid communication with said outlet fluid path, said cooling spiral arranged in said accumulator.
  • the cooling system further comprises a chiller or external cold source thermally connected to said condenser, so to cool said refrigerant in said inlet fluid path.
  • said chiller or external cold source is not thermally connected to said accumulator.
  • said system is adapted to cool said supply of refrigerant stored in said accumulator exclusively through thermal contact of the refrigerant vapor with said outlet fluid path.
  • said accumulator is not connected to an external cooling source.
  • the system according to the present invention allows cooling the supply of refrigerant in said accumulator efficiently merely by way of heat exchange with said outlet fluid path and refrigerant vapor.
  • the accumulator does not need to be connected to an external chiller or cooling source, which reduces the complexity and size of the overall cooling system.
  • the accumulator may merely comprise a heating unit for regulating the boiling pressure of the refrigerant by boiling the liquid content in the accumulator.
  • the heating unit may comprise a thermo siphon heater for an efficient contact to the liquid phase. Without a heating unit, the boiling pressure would only be regulated by the outlet fluid path temperature and hence the external chiller temperature. By providing a heating unit, the boiling pressure in the accumulator may be controlled with a better accuracy.
  • the accumulator comprises a heating unit adapted for heating said supply of refrigerant to a predetermined pressure or temperature, in particular to a predetermined boiling temperature or saturation temperature by evaporating the liquid content.
  • Said accumulator may be adapted to adjust a temperature of said refrigerant in said outlet fluid path to a predetermined temperature, in particular to raise the temperature of said refrigerant to said predetermined temperature, in particular to a boiling temperature of said refrigerant, by way of said thermal contact of said accumulator with said outlet fluid path.
  • Said outlet fluid path may be adapted to supply said refrigerant to an object to be cooled after exchanging heat with said accumulator.
  • Said inlet fluid path may be adapted to receive said refrigerant from said object after cooling said object.
  • the cooling system according to the present invention may be an evaporative cooling system, in particular a two-phase evaporative cooling system.
  • said refrigerant is or comprises CO 2 , but other refrigerants may be employed as well.
  • said system further comprises a control unit adapted to control said heating unit and/or said liquid pump, preferably in response to a temperature and/or a pressure measured in said inlet fluid path and/or in said accumulator.
  • the present invention likewise relates to a method for cooling an object, comprising the steps of providing a supply of a refrigerant in an accumulator at a predetermined temperature and/or at a predetermined pressure, providing or supplying at least part of said refrigerant to a condenser for sub-cooling said refrigerant, providing or supplying said sub-cooled refrigerant to a liquid pump, and establishing a thermal contact of said pumped refrigerant with said accumulator to allow said pumped refrigerant to exchange heat with said supply of refrigerant in said accumulator, as well as subsequently providing or supplying said pumped refrigerant to said object to be cooled.
  • the method comprises a step of regulating a boiling pressure of said refrigerant by adjusting a pressure and/or a temperature of said supply of refrigerant in said accumulator.
  • the method comprises a step of adjusting a pressure and/or a temperature of said supply of refrigerant in said accumulator by heating said supply by means of a heating unit.
  • the method comprises a step of adjusting a pressure and/or a temperature of said supply of refrigerant in said accumulator by cooling said supply with said pumped refrigerant.
  • said supply of refrigerant in said accumulator is cooled exclusively with said pumped refrigerant.
  • the method comprises a step of channeling said pumped refrigerant through said accumulator.
  • the method comprises a step of adjusting a temperature of said pumped refrigerant to a predetermined temperature, in particular to a boiling temperature of said refrigerant, by means of said thermal contact with said supply of refrigerant in said accumulator.
  • the method comprises the step of raising said temperature of said pumped refrigerant to said predetermined temperature.
  • the method comprises the step of receiving said refrigerant from said object to be cooled, and providing or supplying said received refrigerant to said condenser.
  • the method according to any of these embodiments may employ a cooling system with some or all of the features as described above.
  • the invention further relates to a data storage device adapted to store computer-readable instructions, such that said computer-readable instructions, when read on a computer connected to a cooling system with some or all of the features as described above, implement on said cooling system a method with some or all of the features as described above.
  • FIG. 1 schematically shows a conventional two-phase accumulator controlled loop cooling system
  • FIG. 2 shows a pressure-enthalpy phase diagram illustrating the cooling cycle in a conventional two-phase accumulator controlled loop cooling system as shown in FIG. 1 ;
  • FIG. 3 schematically shows an integrated two-phase accumulator controlled loop cooling system according to an embodiment of the present invention.
  • the integrated 2PACL cooling system 200 shown in FIG. 3 comprises an accumulator vessel 202 that is similar in design to the accumulator vessel 102 described above with reference to FIG. 1 .
  • the accumulator vessels 202 comprises an electrical heater 204 , such as a thermo siphon heater, for heating and hence evaporating a supply of refrigerant 206 stored in s the accumulator vessel 202 , as well as a cooling spiral 208 for cooling and hence condensing said supply of refrigerant 206 .
  • the accumulator vessel 202 is connected, via a branch line 210 , to an inlet fluid pipe or inlet fluid tube 212 in which a condenser 214 is provided.
  • a condenser 214 may be used interchangeably.
  • the condenser 214 shown in FIG. 3 is generally identical or similar to the condenser 110 described previously with reference to the 2PACL cooling system of FIG. 1 and may be any condenser as conventionally employed in cooling systems.
  • the condenser 214 is connected, via an input line 216 and an output line 218 , to an external chiller 220 .
  • the external chiller 220 may be any conventional chiller as employed in cooling systems or any other cold source, and in general may be similar to the external chiller 108 described with reference to the conventional 2PACL system of FIG. 1 .
  • the external chiller 220 is merely connected to the condenser 214 , and does not also serve to cool the accumulator vessel 202 .
  • the external chiller 220 according to the present invention may hence be smaller, and the amount of piping may also be reduced. No interference between the multiple cooling connections is present anymore.
  • the condenser 214 serves to sub-cool the CO 2 supplied to the condenser 214 from the accumulator vessel 202 via the branch line 210 and inlet fluid pipe 212 . Sub-cooled CO 2 leaves the condenser 214 and is supplied, still via the inlet fluid pipe 212 , to an inlet 222 of a liquid pump 224 .
  • the liquid pump 224 may be similar to the liquid pump 112 described with reference to FIG. 1 , and can in general be any pump suitable for pumping liquid CO 2 (or other fluids if used instead of CO 2 in the invention).
  • An outlet 226 of the liquid pump 224 is connected to an outlet fluid pipe 228 , which supplies the pumped CO 2 to an object to be cooled (not shown).
  • the pumped CO 2 traverses the cooling spiral 208 provided in the accumulator vessel 202 , and hence exchanges heat with the supply of refrigerant 206 stored in said accumulator vessel 202 .
  • the outlet fluid path can hence be subdivided into two sections, a first section 228 a connecting the outlet 226 of the liquid pump 224 to an inlet s of the cooling spiral 208 , and a second section 228 b downstream from an outlet of the cooling spiral 208 .
  • the accumulator vessel 202 will in general be filled with saturated liquid and vapor, and hence the pumped CO 2 in the outlet fluid pipe 228 will have been heated up to the accumulator temperature once it reaches the outlet of the accumulator cooling spiral 208 .
  • the fluid is still supplied via the outlet fluid pipe 228 and is not yet to boiling, although its temperature now coincides with the temperature of the boiling fluid in the accumulator vessel 202 , or nearly so. This is due to the higher pressure in the outlet fluid pipe 228 .
  • the liquid CO 2 at boiling temperature is then supplied to an evaporator (not shown) in thermal contact with the object to be cooled. Once the liquid CO 2 at boiling temperature reaches the evaporator, the pressure is lowered and the fluid starts boiling, thereby cooling the object.
  • the integrated 2PACL according to the present invention is nearly isotherm during boiling from the evaporator to the inlet of the liquid pump. Only the pressure drop in this part of the system causes a small temperature gradient, much smaller than in systems using a liquid cooling flow. In the latter systems, the liquid flow is difficult to control as it is subject to heating during transfer. Local sensor control may be employed, but will usually lead to the system having a low response time. In contrast, the system according to the present invention controls the distant temperature by controlling the pressure, which is transmitted with the speed of sound, and hence almost without any delay.
  • CO 2 in a mixed liquid/vapor phase returns from the object to be cooled and is channeled through the inlet fluid pipe 212 to the condenser 214 for subsequent cooling, and hence the cooling cycle is closed.
  • the cooling cycle of the integrated two-phase accumulator controlled loop cooling system according to the embodiment of FIG. 3 is generally identical to the cooling cycle of a conventional 2PACL cooling system, and hence reference may be made to the phase diagram of FIG. 2 .
  • the functionality of the cooling system according to the embodiment of FIG. 3 is in general very similar to the conventional 2PACL cooling system known from the art.
  • the cooling of the supply of refrigerant 206 stored in said accumulator vessel 202 is achieved exclusively by means of thermal contact with the pumped refrigerant via the cooling spiral 208 , and no external cooling of the accumulator vessel 202 is required.
  • the CO 2 boiling pressure in the accumulator vessel 202 is controlled solely by means of heating via the electrical heater 204 .
  • a control unit 230 controls operation of the electrical heater 204 in response to a pressure in the accumulator vessel 202 detected by means of a pressure gauge 232 . Since the control unit 230 is needed solely for controlling the electrical heater 204 , it does not require a complex programmable logic control such as the control unit 120 described with reference to FIG. 1 .
  • Cooling the supply of refrigerant 206 in the accumulator vessel 202 by means of the discharge liquid of the pump 224 has the additional advantage that the accumulator temperature cannot fall below the temperature of the discharge liquid of the pump, which is higher than the saturation temperature at the pump inlet 222 .
  • the sub-cooling of the pump is guaranteed by the laws of nature, and the risk of evaporation of the refrigerant in the liquid pump 224 is avoided without any additional sub-cooling control, which conventionally also had to be provided by the programmable logic control unit 120 .
  • the invention hence results in a two-phase evaporative CO 2 cooling system that is structurally simpler, more reliable, better to control and cheaper to build, but without compromising on the functionality of a conventional 2PACL system.
  • the integrated 2PACL cooling system according to the present invention is similar in complexity and price to conventional cooling systems employing thermostatic baths, but has the additional advantage of accurate (isothermal) and direct temperature control on distant experiments in combination with very small cooling tubes.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
US14/343,319 2011-09-09 2011-09-09 Compact Cooling System and Method for Accurate Temperature Control Abandoned US20140230471A1 (en)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10429096B2 (en) 2016-03-24 2019-10-01 Laird Technologies, Inc. Combined heater and accumulator assemblies
EP3553422A1 (en) * 2018-04-11 2019-10-16 Rolls-Royce North American Technologies, Inc. Mechanically pumped system for direct control of two-phase isothermal evaporation
US10921042B2 (en) 2019-04-10 2021-02-16 Rolls-Royce North American Technologies Inc. Method for reducing condenser size and power on a heat rejection system
US11022360B2 (en) 2019-04-10 2021-06-01 Rolls-Royce North American Technologies Inc. Method for reducing condenser size and power on a heat rejection system

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US10231357B2 (en) 2015-03-20 2019-03-12 International Business Machines Corporation Two-phase cooling with ambient cooled condensor
FR3124555B1 (fr) * 2021-06-24 2023-09-15 Thales Sa Dispositif et procédé de contrôle de la pression d’un fluide dans une boucle fluide diphasique à pompage mécanique
FR3124552B1 (fr) * 2021-06-24 2023-10-06 Thales Sa Dispositif et procédé de contrôle des instabilités hydrauliques dans une boucle fluide diphasique à pompage mécanique

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Publication number Priority date Publication date Assignee Title
US10429096B2 (en) 2016-03-24 2019-10-01 Laird Technologies, Inc. Combined heater and accumulator assemblies
EP3553422A1 (en) * 2018-04-11 2019-10-16 Rolls-Royce North American Technologies, Inc. Mechanically pumped system for direct control of two-phase isothermal evaporation
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US10921042B2 (en) 2019-04-10 2021-02-16 Rolls-Royce North American Technologies Inc. Method for reducing condenser size and power on a heat rejection system
US11022360B2 (en) 2019-04-10 2021-06-01 Rolls-Royce North American Technologies Inc. Method for reducing condenser size and power on a heat rejection system

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EP2753887A1 (en) 2014-07-16
JP6087359B2 (ja) 2017-03-01
EP2753887B1 (en) 2020-08-12
JP2014526667A (ja) 2014-10-06
WO2013034170A1 (en) 2013-03-14
PL2753887T3 (pl) 2021-03-08

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