EP3249323B1 - Procédé et dispositif pour réguler le surchauffage dans un circuit de réfrigération par compression avec un récupérateur - Google Patents

Procédé et dispositif pour réguler le surchauffage dans un circuit de réfrigération par compression avec un récupérateur Download PDF

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Publication number
EP3249323B1
EP3249323B1 EP17172660.7A EP17172660A EP3249323B1 EP 3249323 B1 EP3249323 B1 EP 3249323B1 EP 17172660 A EP17172660 A EP 17172660A EP 3249323 B1 EP3249323 B1 EP 3249323B1
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EP
European Patent Office
Prior art keywords
evaporator
outlet
thermal expansion
expansion valve
inlet
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EP17172660.7A
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German (de)
English (en)
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EP3249323A1 (fr
Inventor
Umberto Merlo
Stefano FILIPPINI
Francesco CASELLA
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LU-VE SpA
Politecnico di Milano
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LU-VE SpA
Politecnico di Milano
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Priority to RS20190648A priority Critical patent/RS58816B1/sr
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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
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B2500/19—Calculation of parameters
    • 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
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/191—Pressures near an expansion valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/195—Pressures 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
    • F25B2700/19—Pressures
    • F25B2700/197—Pressures of the evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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 present invention relates, in a first aspect thereof, to a method for controlling overheating or superheating in compression refrigeration cycles with a regenerative heat exchanger.
  • the present invention relates to a system for the implementation of the inventive method.
  • the objective of the control system in compression refrigeration cycles is to maximize the thermal power taken by the evaporator from a heat-carrying fluid, normally the air of a cooling chamber of an air-conditioned area, at the same time avoiding sending a two-phase mixture to the compressor, which could damage it.
  • the terminal section of the evaporator acts as a superheater, so as to send dry superheated vapour to the compressor.
  • control objective is achieved with a simple feedback operation, where the level of superheating is measured at the evaporator outlet and the opening of the thermal expansion valve at the evaporator inlet is suitably modulated so that superheating remains around an opportune "SET POINT" value or reference point.
  • the latter must be sufficiently high to ensure the absence of liquid drops at the compressor intake, with a safety margin during the transients, but at the same time it must be restricted to avoid high gas delivery temperatures.
  • the presence of the superheating section forces the evaporator to work at a temperature, and therefore at a pressure, lower than that which it would be possible to achieve in the absence of the section, penalizing the cooling efficiency.
  • the first control objective is to maintain the vaporization ratio at the evaporator outlet at a predetermined value of less than one, possibly at a value close to that of dry-out so as to ensure the best possible use of the heat exchange surface.
  • the second objective is to ensure sufficient superheating of the refrigerating fluid at the outlet of the recuperator, i.e. at the inlet of the compressor so as to avoid damaging it.
  • the simplest method for achieving this objective is to use the same control strategy used in conventional cycles, namely measuring the level of vapour superheating at the outlet of the recuperator and using a feedback control that acts on the opening of the thermal expansion valve so as to bring it to and keep it approximately at an opportune set point value, corresponding to the cycle's optimal conditioning conditions.
  • the origin of this difficulty is due to the combination of three phenomena.
  • the first is the propagation delay between variations in flowrate of the thermal expansion valve and the corresponding variations in vaporization ratio at the evaporator outlet.
  • the second phenomenon is the extreme non-linearity of the relationship between the vaporization ratio at the evaporator outlet, and therefore at the recuperator inlet, and the superheating level at the recuperator outlet that is used for feedback.
  • This non-linearity is due to the strong dependency on the vaporization ratio of the convective exchange coefficient in the inlet section of the recuperator, which provides the final evaporation section for the refrigerating fluid.
  • the third phenomenon is given by the further coupling introduced in the process by the recuperator, whereby even a modest increase in the vaporization ratio at the inlet entails a strong drop in the exchange coefficient and therefore a drop in the heat taken from the hot side, i.e. an increase in temperature on the hot side, which entails an increase in the vaporization ratio downstream of the thermal expansion valve and therefore a further increase in the vaporization ratio at the evaporator outlet.
  • This positive feedback mechanism is destabilizing and results in hysteresis phenomena that have been experimentally confirmed.
  • EP 2 765 370 A1 discloses a method for controlling superheating in a refrigeration cycle system according to the preamble of claim 1 and a system for controlling superheating in a refrigeration cycle.
  • the aim of the present invention is therefore that of providing a method of controlling superheating in compression refrigeration cycles with regenerative heat exchanger that enables stabilizing the vaporization ratio at the evaporator outlet in an indirect manner.
  • a main object of the present invention is to provide a method of the indicated type that provides the sought stabilization through measurement and evaluation of at least the following parameters:
  • Another object of the present invention is to provide a method of the indicated type that can be implemented with extremely simple and inexpensive instrumentation, in particular a single pressure sensor on the circuit's low-pressure line, positioned at the evaporator outlet, as well as a single temperature sensor and a single pressure sensor, both positioned upstream of the thermal expansion valve.
  • a further object of the present invention is to provide a method of the indicated type that operates on the basis of a new and novel control and regulation algorithm capable of stabilizing operation of the cooling system by directly compensating the effects of: changes in temperature of the air to be cooled; changes in condensation pressure upstream of the thermal expansion valve; changes in flow and temperature of the condenser's refrigerating fluid; and changes in evaporation pressure and in the heat exchange of the recuperator with subsequent variations in the enthalpy content of the refrigerant at the outlet of the recuperator and at the inlet of the thermal expansion valve.
  • a further object of the present invention is to provide a method of the indicated type that is extremely effective not only for local stabilization of the system, but also for large perturbations that involve the entire system.
  • a further object of the present invention is to provide a method of the indicated type that can be easily adapted to handle possible failures of the fans serving the evaporators.
  • a further object of the present invention is to provide a control and regulation system for implementing the inventive method, it being possible to configure this system as a modular device applicable to any cooling chamber or air-conditioned room and/or similar area, either of new construction or even of a pre-existing type, this system ensuring, thanks to the implementation of the inventive method, the maximization of the thermal power taken from the heat-carrying refrigerant by the evaporator, at the same time avoiding sending a two-phase mixture to the system's compressor, which might damage it.
  • the last, but not least object of the present invention is to provide a refrigeration cycle control and regulation system that can be built from readily and commercially available materials/components with reliable operation, as well as economically competitive costs.
  • the previously mentioned aim and the objects, as well as further objects, which shall become clearer hereinafter, are achieved by a method for controlling superheating in a refrigeration cycle system operating by compressing a refrigerating fluid with a regenerative heat exchanger, according to claim 1.
  • FIG. 3 A layout of the refrigeration cycle system with recuperator to which the method of the invention refers is shown in Figure 3 .
  • the system comprises a compressor 1, a condenser 2, a receiver 3 for liquid refrigerant, a heat recuperator or regenerative heat exchanger 4, a thermal expansion valve 5, an evaporator 6 and a transmission line 8, to the valve 5, for the signal detected by the sensor 7.
  • the refrigerating gas is compressed in the compressor 1, then enters the condenser 2 where it changes state, passing to a liquid phase, after which is then sent to the liquid receiver 3.
  • the liquid leaving the receiver 3 is sent to the recuperator 4, where it is cooled by the gas leaving the evaporator 6.
  • the liquid is then made to enter the thermal expansion valve 5, where adiabatic expansion occurs, which forms a liquid/gas mixture that enters the evaporator 6.
  • a change of state occurs from the liquid to gas phase, which, in turn, enters the recuperator 4.
  • the cycle ends with sending the gas from the recuperator 4 to the compressor 1.
  • the main problem in regulating the refrigeration cycle with recuperator 4 is that the variations in vaporization ratio of the evaporator 6 occur at its outlet 9 with a large delay with respect to the conditions at the inlet 10, but this variation is not directly detectable because a two-phase mixture that is in nearly isobaric and isothermal conditions passes through the evaporator and no reliable and inexpensive methods exist for measuring the vaporization ratio of this mixture.
  • the temperature T2 of the air at the inlet of the evaporator 6 must also be measured, to allow its regulation by switching the compressor 1 on and off.
  • the fundamental idea of the inventive method was that of introducing additional process measurements that enable directly stabilizing the ratio of the liquid/gas mixture at the evaporator outlet, which is defined as the ratio between the mass of the gas phase and the total mass.
  • these additional measurements regard:
  • implementation of the proposed method would also require measuring the evaporation pressure inside the evaporator 6.
  • the inventive method operates on the basis of an innovative control algorithm, capable of stabilizing the vaporization ratio at the outlet of the evaporator 6 and based on the following process steps, represented by the pseudocode in Figure 1 .
  • h in h ls P 1 + c p * T 3 ⁇ T ev
  • h ls the enthalpy of the saturated liquid at pressure P1
  • c p the constant-pressure specific heat
  • the opening of the corresponding valve is calculated, using the inverse function of the opening characteristic.
  • stabilization is achieved by directly compensating, according to the inventive method, the effect of the following phenomena:
  • the previously described base algorithm is capable of stabilizing operation of the system.
  • uncertainty in the values of the parameters in particular the equivalent conductance of the evaporator and measurement errors, can result in stabilizing operation of the evaporator at actual values of vaporization ratio at the outlet of the evaporator 6 and of superheating at the inlet of the compressor 1 that are significantly different from those required.
  • Block S represents the above-described algorithm, where X° ev represents the vaporization ratio x° v required at the outlet of the evaporator 6.
  • Block R represents a conventional proportional-integral-derivative (PID) controller.
  • Block P represents the process to be controlled, where T mv and P mv correspond to the temperature and pressure upstream of the valve T3 and P2, P ev corresponds to the evaporation pressure P1, and T vr corresponds to the temperature of the vapour at the outlet of the recuperator T4.
  • the feedback loop for the level of superheating at the outlet of the recuperator 4 is implemented by a PID controller, which acts on the value of the vaporization ratio required at the outlet of the evaporator 6 by using it as a virtual control variable.
  • the above-described control algorithm sets the opening of the thermal expansion valve 5 so as to obtain this vaporization ratio.
  • the starting transient it is assumed to start from conditions in which the evaporator is empty or, in any case, at a very low pressure corresponding to a minimum refrigerant content.
  • the thermal expansion valve is initially opened to a steady value that can be adapted as a function of the evaporation pressure, to take into account the different operating conditions at various temperatures. Then there is a waiting period until the pressure exceeds a threshold value, determined on the basis of the saturation pressure reduced by an opportune margin. Once the threshold is exceeded, the previously defined control and regulation algorithm-method starts.
  • the compressor When the compressor must be stopped, for example, based on the thermostatic control of the air temperature, it is necessary to first completely close the thermal expansion valve, so as to empty the evaporator; the compressor can be stopped when the pressure drops below an opportune minimum threshold.
  • the method and the algorithm employed therein can be advantageously adapted to handle failures of the fans (not shown) serving the evaporators.
  • the only possible strategy is that of identifying the failure condition by introducing a lower superheating threshold, sufficiently distant from the set point to avoid false alarms, but at the same time sufficiently high to avoid the intake of two-phase fluid into the compressor.
  • the thermal expansion valve is immediately closed to avoid flooding the evaporator and the intake of two-phase fluid into the compressor.
  • the controller When the first threshold is exceeded, the controller will initially assume that the functionality of one out of N fans has been lost. In a first approximation, this entails a reduction by a factor of 1/N of the equivalent conductance G of the evaporator. It is therefore possible to modify this parameter in the stabilization algorithm inside block S in Fig. 2 in this sense.
  • the immediate effect of this modification will be a drop in the estimated heat flow Q, which will be followed by an immediate drop in the required flow for the thermal expansion valve m r , which will be immediately carried out by a reduction in the opening of the valve ⁇ v , so as to maintain the heat balance of the evaporator.
  • This operating condition can be reported to the supervising operator, for the latter to activate the maintenance procedure, which is not necessarily immediate.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Claims (7)

  1. Procédé destiné à réguler la surchauffe dans un système à cycle de réfrigération fonctionnant par compression d'un fluide réfrigérant avec un récupérateur (4), ledit système comprenant un compresseur (1) présentant une entrée et une sortie, un évaporateur (6) présentant une entrée (10) et une sortie (9), une soupape de détente thermique (5) couplée à ladite entrée (10) dudit évaporateur (6), et le récupérateur (4) présentant une entrée (9) et une sortie, caractérisé en ce que ledit procédé permet de stabiliser, au moins localement, le fonctionnement dudit évaporateur (6) en exécutant un algorithme de stabilisation pour le fonctionnement de l'évaporateur (6), ledit procédé comprenant, dans l'ordre suivant, au moins les étapes suivantes : calcul de la température d'évaporation (T4) à partir de la pression (P1) mesurée dans l'évaporateur ; calcul de la puissance thermique absorbée par l'évaporateur (6) sur la base de la différence entre la température de l'air (T2) et la température d'évaporation (T4), multipliée par la conductance équivalente ; calcul de l'enthalpie du réfrigérant à l'entrée (10) de la soupape de détente thermique (5) comme fonction de sa température mesurée (T3) ; calcul de l'enthalpie souhaitée à la sortie (9) de l'évaporateur (6) sur la base du rapport de vaporisation souhaité à la sortie (9) de l'évaporateur (6) et de la pression d'évaporation mesurée P1 ; calcul du flux de réfrigérant fournissant un changement d'enthalpie requis entre l'entrée (10) et la sortie (9) de l'évaporateur (6) étant donné la puissance thermique estimée par inversion, connaissant la pression en amont (P2) et en aval (P1) de la soupape de détente thermique (5) et la densité du réfrigérant liquide à l'entrée (10), laquelle est une fonction de la température mesurée (T3), la règle de décharge caractéristique de la soupape (5) pour le calcul de l'ouverture nécessaire pour obtenir le flux calculé ; et envoi du signal d'ouverture calculé de ladite soupape à un actionneur de ladite soupape de détente thermique (5).
  2. Procédé selon la revendication 1, caractérisé en ce que celui-ci comprend une étape supplémentaire de limitation de la vitesse d'ouverture et de fermeture de ladite soupape de détente thermique à une valeur maximum compatible avec la vitesse maximum d'ouverture et de fermeture dudit actionneur.
  3. Procédé selon la revendication 1, caractérisé en ce que celui-ci comprend une étape corrective supplémentaire consistant à renvoyer, avec une bande passante réduite, une valeur de surchauffe vers ladite entrée dudit compresseur, ladite valeur de surchauffe agissant sur une valeur du rapport de vaporisation requis, utilisée comme une variable virtuelle dudit évaporateur.
  4. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que ledit évaporateur comprend un évaporateur avec un seul ventilateur et ledit procédé comprend une étape supplémentaire d'identification d'un état de défaillance possible dudit ventilateur unique en introduisant un seuil de surchauffe inférieur, suffisamment éloigné d'un point défini pour éviter de fausses alertes, mais également suffisamment élevé pour empêcher une décharge de liquide biphasé dans ledit compresseur, ladite soupape de détente thermique étant fermée immédiatement et ledit système de refroidissement étant empêché de continuer à fonctionner lors du dépassement dudit seuil inférieur.
  5. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que ledit évaporateur comprend une pluralité de ventilateurs, ledit procédé comprenant, dans le cas où seul l'un desdits ventilateurs est défaillant, l'étape de réglage d'un seuil d'alerte de surchauffe inférieur et d'un seuil d'arrêt inférieur correspondant dudit système pour permettre audit système de continuer à fonctionner dans des conditions dégradées, sans passer par un état d'arrêt, en attendant des actions de maintenance pas nécessairement immédiates sur ledit ventilateur défaillant pour remettre ledit système dans un état de pleine capacité.
  6. Système destiné à exécuter le procédé selon l'une quelconque des revendications précédentes, le système comprenant
    - au moins un bloc logique (S) basé sur le rapport de vaporisation x°v, requis à la sortie de l'évaporateur (6) pour exécuter un algorithme de stabilisation comprenant, dans l'ordre suivant, au moins les étapes suivantes : calcul de la température d'évaporation (T4) à partir de la pression (P1) mesurée dans l'évaporateur ; calcul de la puissance thermique absorbée par l'évaporateur (6) sur la base de la différence entre la température de l'air (T2) et la température d'évaporation (T4), multipliée par la conductance équivalente ; calcul de l'enthalpie du réfrigérant à l'entrée (10) de la soupape de détente thermique (5) comme fonction de sa température mesurée (T3) ; calcule de l'enthalpie souhaitée à la sortie (9) de l'évaporateur (6) sur la base du rapport de vaporisation souhaité à la sortie (9) de l'évaporateur (6) et de la pression d'évaporation mesurée P1 ; calcul du flux de réfrigérant fournissant un changement d'enthalpie requis entre l'entrée (10) et la sortie (9) de l'évaporateur (6) étant donné la puissance thermique estimée par inversion, connaissant la pression en amont (P2) et en aval (P1) de la soupape de détente thermique (5) et la densité du réfrigérant liquide à l'entrée (10), laquelle est une fonction de la température mesurée (T3), la règle de décharge caractéristique de la soupape (5) pour le calcul de l'ouverture nécessaire pour obtenir le flux calculé ; et envoi du signal d'ouverture calculé de ladite soupape à un actionneur de ladite soupape de détente thermique (5), au moins un bloc logique (R) représentant une régulation de type PID proportionnelle intégrale dérivée, laquelle émet une valeur de vaporisation souhaitée à la sortie (9) de l'évaporateur (6) vers l'au moins un bloc logique (S), et au moins un bloc logique (DT) calculant le niveau de surchauffe sur la base de la pression et de la température de la vapeur à la sortie dudit récupérateur (4) et transmettant ledit niveau de surchauffe audit au moins un bloc logique (R).
  7. Système selon la revendication 6, caractérisé en ce que ledit algorithme de stabilisation généré par ledit bloc (S) fournit, dans des conditions optimales et de fonctionnement normal, le rapport de vaporisation souhaité à la sortie dudit évaporateur et la stabilisation souhaitée en compensant directement l'un des éléments suivants : changement dans la température de l'air, changement dans la pression de condensation en amont de la soupape de détente thermique, changement dans la pression d'évaporation ; et changement dans l'échange de chaleur dans le récupérateur, avec des variations conséquentes dans le contenu enthalpique du réfrigérant à la sortie du récupérateur et à l'entrée de la soupape de détente thermique.
EP17172660.7A 2016-05-24 2017-05-24 Procédé et dispositif pour réguler le surchauffage dans un circuit de réfrigération par compression avec un récupérateur Active EP3249323B1 (fr)

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RS20190648A RS58816B1 (sr) 2016-05-24 2017-05-24 Postupak i sistem za kontrolu pregrevanja u kompresionim rashladnim ciklusima sa rekuperatorom

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ITUA2016A003756A ITUA20163756A1 (it) 2016-05-24 2016-05-24 Metodo e sistema per il controllo del surriscaldamento di cicli frigoriferi a compressione con scambiatore rigenerativo.

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EP (1) EP3249323B1 (fr)
ES (1) ES2729981T3 (fr)
HU (1) HUE044008T2 (fr)
IT (1) ITUA20163756A1 (fr)
PT (1) PT3249323T (fr)
RS (1) RS58816B1 (fr)
TR (1) TR201909685T4 (fr)

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CN115247922B (zh) * 2022-06-27 2024-07-23 浙江中广电器集团股份有限公司 一种防止压缩机冷媒回流到闪蒸罐的自动控制方法
CN116293377B (zh) * 2022-09-08 2026-04-10 华电电力科学研究院有限公司 一种火力发电机组的疏水控制方法及系统

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CA1247385A (fr) * 1984-07-02 1988-12-28 Kosaku Sayo Dispositif de debitmetrie du frigorigene au cours d'un cycle de refrigeration
DE102010001024B4 (de) * 2010-01-19 2015-08-13 Honeywell Technologies Sarl Verfahren für die Steuerung und Regelung von Wärmepumpen und Kühlanlagen
EP2765370A1 (fr) * 2013-02-08 2014-08-13 Panasonic Corporation Appareil à cycle de réfrigération et le générateur d'eau chaude associé

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TR201909685T4 (tr) 2019-07-22
EP3249323A1 (fr) 2017-11-29
HUE044008T2 (hu) 2019-09-30
ES2729981T3 (es) 2019-11-07
RS58816B1 (sr) 2019-07-31
PT3249323T (pt) 2019-06-27
ITUA20163756A1 (it) 2017-11-24

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