EP2791595A1 - Procédé de régulation d'un système de refroidissement cryogénique - Google Patents
Procédé de régulation d'un système de refroidissement cryogéniqueInfo
- Publication number
- EP2791595A1 EP2791595A1 EP12813127.3A EP12813127A EP2791595A1 EP 2791595 A1 EP2791595 A1 EP 2791595A1 EP 12813127 A EP12813127 A EP 12813127A EP 2791595 A1 EP2791595 A1 EP 2791595A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- cryogenic
- bath
- fluid
- heat
- heating means
- 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
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
Definitions
- the invention relates to a method for regulating a cryogenic cooling system, and to a cryogenic cooling system for implementing such a method.
- the invention relates to cooling systems that can deliver large (medium and / or peak) cooling capacities of several tens to several thousand watts.
- Cryogenic cooling systems such as helium coolers
- helium coolers are generally designed to provide constant cooling capacity. They are therefore particularly suited to stationary or slightly variable thermal loads over time.
- some applications require large and highly variable cooling capacities. For example, the cooling of superconducting magnets of certain scientific installations, such as tokamaks intended for the study of nuclear fusion.
- the first solution is implemented in the document WO 2009/024705. It has two disadvantages. Firstly, the cooler must be sized on the basis of the peak cooling capacity, which implies an additional investment cost compared to the case of a design based on the average cooling capacity. Second, the need to allow variations in the delivered cooling capacity prevents the optimization of energy efficiency (because the latter is maximum for a single operating point), which leads to additional operating costs. In installations with high cooling capacity, energy efficiency can be a major challenge. As an example, the cooling system of the future Japanese tokamak JT-60SA will absorb an average electrical power of 6 kW and a peak power of 12 kW.
- the graph of FIG. 1 shows the instantaneous thermal power P (t) and the average thermal power dissipated by a superconducting magnet of said tokamak JT-60SA.
- the chiller operates at constant power, depending on the average heat load, and a buffer absorbs fluctuations in thermal load.
- the experimental ITER tokamak under construction, includes a cryogenic system whose general structure is described in the following articles:
- Figure 2 illustrates the structure of such a system.
- the superconducting magnets that constitute ST pulsed thermal charges are cooled by a heat transfer fluid (supercritical helium) which circulates in a primary circuit CFP and transfers the heat absorbed to a cryogenic bath BC (diphasic helium , liquid and vapor).
- a cryogenic bath BC diphasic helium , liquid and vapor.
- the cryogenic bath is connected to a RL helium cooler / liquefier operating according to the Claude cycle (see J.-C. Boissin et al., "Cryogenics: implementation of low temperatures”). , Engineering Techniques, B 2,382).
- Such a cooler comprises a compression zone and a cold zone (“cold box”) coupled by valves.
- the role of the compression zone is to provide a gas flow (helium) under a high pressure of about 20 bar.
- the role of the cold zone is to provide a cooling capacity to keep an installation cold. It consists of several HX1 - HX5 countercurrent exchangers that allow heat exchange between the low pressure (LP) and high pressure (LP) channels, T1 and T2 turbines in which part of the thermal energy of the gas is converted into work, and a Joule Thomson VJT expansion valve at the end of the HP high-pressure channel. At the outlet of this expansion valve, the helium is partially liquefied (LHe) and feeds the thermal bath BC; concomitantly, helium in the vapor state (VHe) is discharged to the LP low pressure channel.
- LHe low pressure
- VHe vapor state
- the pulsed thermal source ST (superconducting magnet) is cooled by means of a primary fluid circuit CFP in which supercritical helium circulates.
- This fluidic circuit comprises two heat exchangers: a first heat exchanger X1, connected to said heat source, and a second heat exchanger X2, immersed in the cryogenic bath. If no damping of the variations in the heat load were foreseen, the chiller would be subject to serious malfunctions, which could lead to safety shutdowns or even breakdowns. For example, an increase in the load would cause an increase in the cold return flow, and therefore an increase in pressure at the inlet and outlet of the compressor C, which can induce a thermal overload of its motor, an inadmissible variation in the outlet pressure, etc. .
- the invention aims to overcome the aforementioned drawbacks of the prior art. More specifically, it aims to allow the regulation of a cryogenic cooling system so as to "smooth" the temporal variations of a non-stationary heat load with a cyclic operation, that is to say periodic or quasi-periodic operation.
- Quasi-periodic means an operating regime in which the thermal load periodically takes, at times referred to as "cycle ends", the same value (for example: zero) without being strictly periodic; for example, the power dissipated from one cycle to another may vary by ⁇ 10% or more.
- An object of the invention making it possible to achieve this goal is constituted by a method of regulating a cryogenic cooling system comprising: a cryogenic bath provided with a conduit for supplying a cryogenic fluid in the liquid state, two-phase or supercritical and a conduit for discharging a cryogenic fluid in the vapor state, said conduits being connected to a cryogenic cooler; a so-called primary fluid circuit, in which a heat transfer fluid circulates, comprising a first heat exchanger for extracting heat from a heat source having a cyclic operation, and a second heat exchanger for yielding said heat to said cryogenic bath, means for regulating flow rates bulk fluidic fluid through said supply duct, said exhaust duct and said primary fluid circuit; and a means for heating said cryogenic bath, characterized in that said control method comprises: the slaving of the mass fluid flow through said evacuation conduit of the cryogenic bath to a set value M2, said slaving being obtained by acting at both on a said control means and on said heating means of the cryogenic bath, adjusting said
- cooler By cooler is meant a liquefier system or refrigerator, or a system that operates partially as a liquefier and partially as a refrigerator.
- a basic principle of the invention is as follows.
- the regulation of the cooling system requires setting a set value M2 of the flow rate of steam leaving the cryogenic bath, m2.
- this is detrimental to energy efficiency.
- said adjustment of the instruction M2 can be carried out by applying to M2 a correction equal to ⁇ AM2 only when the average power ( ⁇ N BAM ) dissipated by said heating means is outside the range [W min , W max ] with
- said adjustment of the setpoint M2 can be carried out by applying to M2 a correction equal to ⁇ 2 at each operating cycle of said heat source, with:
- the slaving of the mass fluid flow through said cryogenic bath evacuation pipe to a set value M2 can be obtained by acting on both a control means of the mass fluidic flow through said primary fluid circuit and said cryogenic bath heating means; and a means for controlling the mass flow rate through said cryogenic bath feed conduit can be controlled to maintain a constant average liquid level in said cryogenic bath - thereby ensuring equal flow rates into and out of any moment.
- said means for regulating the mass flow rate through said primary fluid circuit may be chosen from: a valve or bypass valve system of said primary fluid circuit and a pump.
- the slaving of the mass fluid flow through said cryogenic bath evacuation pipe to a set value M2 can be obtained by acting on both a control means of the mass flow rate through said exhaust pipe and said cryogenic bath heating means, the method also comprising: controlling the mass flow rate through said cryogenic bath supply line to a set value M1 and a first adjusting said set value M1 to maintain a level n of liquid in said cryocool, measured at each cycle or period of operation of said heat source, within a predefined range 0 ⁇ N mi n ⁇ n ⁇ N max (between two periodic measurements, the level may come out of this range, however bounded by 0 and the capacity of the thermal bath tank).
- a step of adjusting said setpoint M1 can be performed at each operating cycle of said heat source, based on the value of said liquid level at a given time of said cycle.
- the method may also comprise a second adjustment of said setpoint value M1, identical and concomitant with said adjustment of the instruction M2. Under these conditions, the equality of incoming and outgoing flows is almost assured, for example at less than 5%.
- Another object of the invention is a cryogenic cooling system comprising: a cryogenic bath provided with a conduit for supplying a cryogenic fluid in the liquid, two-phase or supercritical state and an evacuation duct; a cryogenic fluid in the vapor state, said conduits being connected to a cryogenic cooler, a so-called primary fluid circuit, in which a heat transfer fluid circulates, comprising a first exchanger for extracting heat from a heat source having a cyclic operation, and a second heat exchanger for yielding said heat to said cryogenic bath, means for controlling the mass flow rates through said supply line, said exhaust duct and said primary fluid circuit, means for heating said cryogenic bath; and means for controlling said mass fluid flow control means and said heating means of said cryogenic bath; characterized in that said control means is configured or programmed to implement a control method as described above.
- the control means may be a computer or processor programmed in a timely manner.
- FIG. 1 a time diagram of the heat generated by a pulsed thermal load (superconducting magnet of a tokamak);
- Figure 2 is a general diagram of a cryogenic cooling system known from the prior art;
- FIG. 3 a simplified diagram of a cryogenic cooling system suitable for the implementation of the invention
- FIG. 4 a diagram illustrating a method of regulating this system without smoothing thermal loads
- FIG. 5 a diagram illustrating a control method according to a first variant of said first embodiment of the invention
- FIG. 6 a diagram illustrating a regulation method according to a second variant of said first embodiment of the invention.
- Figure 7 is a flowchart of a method according to said first embodiment of the invention.
- FIG. 8 a diagram illustrating a regulation method according to said second embodiment of the invention.
- flow will always be understood to mean a mass flow rate.
- the cryogenic cooling system of FIG. 3 comprises a cryogenic bath BC connected to a helium cooler RL which may be of the type illustrated in FIG. 2.
- the cryogenic bath is at a pressure of 1 bar and at a temperature of 4. 2 K, which corresponds to a condition of saturation, and therefore of equilibrium between the liquid and vapor phases.
- the mass flow m1 of helium in the diphasic state (liquid / vapor) entering the bath is regulated by the valve V1 disposed on the supply duct HP (typically a Joule-Thomson valve, allowing the expansion of the supercritical helium circulating in the HP duct and its conversion into two-phase liquid-vapor fluid); the mass flow rh2 of helium in the vapor state leaving the bath is regulated by the valve V5 disposed on the exhaust pipe BP; the liquid level n (t) in the bath is measured using a sensor.
- Heating means (electrical resistance) MCB is arranged in the cryogenic bath to cause the evaporation of a part of the cryogenic helium contained therein (heat flow: Wbain (t)).
- cryogenic bath is in thermal contact (heat flow: W2 (t)) with an exchanger X2 of the primary fluid circuit CFP in which circulates supercritical helium whose flow is regulated by the valve V2 and the pump P; T (t) is the temperature of the supercritical helium serving as heat transfer fluid at the inlet of the exchanger X2.
- An SVC bypass system consisting of the two valves V3 and V4 makes it possible to deflect a portion of the heat transfer fluid so that it does not circulate in the exchanger X2.
- the non-stationary heat source ST is thermally connected to the primary fluidic circuit via the exchanger X1 (heat flow: W1 (t)).
- the liquid level n (t) inside the saturated bath must have a constant mean value if one integrates over a sufficient time (typically on a T 0 cycle for a periodic or more generally cyclic scenario):
- equation (2) does not derive directly from (1) because the pressure and temperature can vary inside the bath (moving along the saturation curve) producing n-level fluctuations (t). ) even if the equality of the incoming and outgoing mass flows implies a constant mass inside the bath.
- Equation (3) ⁇ is the difference between the enthalpy H2 of the fluid exiting the bath and the enthalpy H1 of the incoming fluid, L sa t is the latent heat of this fluid and x (t) is the proportion of steam in the rh1 flow.
- the feed rate m1 is the nominal operating point of the chiller, which ensures maximum efficiency.
- the invention proposes two alternative regulation schemes which make it possible, unlike that of FIG. 4, to smooth the load thermal induced by a non-stationary heat source before it reaches the RL cooler.
- FIG. 5 illustrates a first variant of the first regulation scheme.
- the average value of the additional injected power ⁇ W ba in> is calculated for each cycle and this is compared with a maximum value W max (for reasons of economy) and a minimum value W min (to have a margin of operational safety). If these limits are exceeded, in one direction or the other, a correction - positive or negative - is made on the value of the setpoint of the outgoing flow.
- This correction must be chosen so that it never exceeds the acceptable range of power ⁇ Wbain> and oscillates between a value that is too large and too small.
- Stage I corresponds to the setting of the level setpoint N, of the initial outflow setpoint.
- This regulation is performed for at least one period T 0 of operation of the thermal source ST.
- the correction ⁇ 2 can also take other values; for example, it may depend on the difference between the measured average power and a target value equal to (W m ax-W m j n ) / 2:
- Step III does not have to be performed.
- the different flow control means and the heating means are controlled by a control means (MP reference), which can be a computer programmed in a timely manner.
- MP reference can be a computer programmed in a timely manner.
- the flow control in the primary circuit is performed by acting on the speed of the pump P and not on the bypass system. It would also be possible to regulate this flow by acting on the valve V2, but this is generally more delicate and thermodynamically unfavorable.
- FIG. 8 illustrates a second control scheme. While in the control scheme of FIGS. 5 to 7 it is the primary circuit which absorbs the fluctuations of thermal load, in that of FIG. 8 this thermal buffer function is assigned to the cryogenic bath BC. This The latter must therefore be able to temporarily store or destock some of the heat transferred to it by the primary circuit.
- the variation in pressure in the bath has the effect of changing the temperature of the bath, because one moves along the saturation curve, and to fluctuate the liquid level while the total mass of the cryogenic fluid in the bath is constant .
- This effect is predictable, but complex: depending on the initial conditions, a heat injection can decrease or (which is counterintuitive) increase the level of the liquid. Therefore, it is no longer possible to use a simple level measurement to ensure the equality of rh1 and rh2 rates.
- the valve V5 or the cold compressor makes it possible to regulate the outflow; the incoming flow can be regulated by means of the Joule-Thomson feed valve V1.
- AM cycle p L S [n (t + TQ) - n (t)]
- the valve V1 slaves the incoming flow m1 to the setpoint M1, while the valve V5 slaves the outflow rh2 to the setpoint M2 (initially equal to M1, but this is not more necessarily true then); when this is insufficient, the power W ba injected by the heating means MCB is used for this purpose.
- This regulation is carried out during at least one period or cycle T 0 of operation of the thermal source ST.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1161483A FR2983947B1 (fr) | 2011-12-12 | 2011-12-12 | Procede de regulation d'un systeme de refroidissement cryogenique. |
PCT/IB2012/056952 WO2013088303A1 (fr) | 2011-12-12 | 2012-12-04 | Procédé de régulation d'un système de refroidissement cryogénique |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2791595A1 true EP2791595A1 (fr) | 2014-10-22 |
EP2791595B1 EP2791595B1 (fr) | 2017-05-03 |
Family
ID=47522759
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP12813127.3A Not-in-force EP2791595B1 (fr) | 2011-12-12 | 2012-12-04 | Procédé de régulation d'un système de refroidissement cryogénique |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2791595B1 (fr) |
FR (1) | FR2983947B1 (fr) |
WO (1) | WO2013088303A1 (fr) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR3013813B1 (fr) * | 2013-11-26 | 2015-12-04 | Commissariat Energie Atomique | Procede et dispositif de regulation d'un systeme de refroidissement cryogenique |
FR3042589B1 (fr) | 2015-10-14 | 2017-11-24 | Commissariat Energie Atomique | Procede de regulation d'un systeme de refroidissement cryogenique |
CN116130199B (zh) * | 2023-04-13 | 2023-06-30 | 江西联创光电超导应用有限公司 | 一种超导磁体的开关装置 |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5606870A (en) | 1995-02-10 | 1997-03-04 | Redstone Engineering | Low-temperature refrigeration system with precise temperature control |
FR2919713B1 (fr) | 2007-08-03 | 2013-12-06 | Air Liquide | Procede de refrigeration d'un fluide, par exemple d'helium, destine a alimenter un consommateur de fluide, ainsi qu'a une installation correspondante |
FR2957406A1 (fr) * | 2010-03-12 | 2011-09-16 | Air Liquide | Procede et installation de refrigeration en charge pulsee |
-
2011
- 2011-12-12 FR FR1161483A patent/FR2983947B1/fr not_active Expired - Fee Related
-
2012
- 2012-12-04 EP EP12813127.3A patent/EP2791595B1/fr not_active Not-in-force
- 2012-12-04 WO PCT/IB2012/056952 patent/WO2013088303A1/fr active Application Filing
Also Published As
Publication number | Publication date |
---|---|
WO2013088303A1 (fr) | 2013-06-20 |
FR2983947B1 (fr) | 2014-01-10 |
EP2791595B1 (fr) | 2017-05-03 |
FR2983947A1 (fr) | 2013-06-14 |
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