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EP2706312B1 - Procédé destiné au fonctionnement d'une machine frigorifique et machine frigorifique - Google Patents

Procédé destiné au fonctionnement d'une machine frigorifique et machine frigorifique Download PDF

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Publication number
EP2706312B1
EP2706312B1 EP12183137.4A EP12183137A EP2706312B1 EP 2706312 B1 EP2706312 B1 EP 2706312B1 EP 12183137 A EP12183137 A EP 12183137A EP 2706312 B1 EP2706312 B1 EP 2706312B1
Authority
EP
European Patent Office
Prior art keywords
compressor
subcooler
expansion valve
refrigerant
valve
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.)
Active
Application number
EP12183137.4A
Other languages
German (de)
English (en)
Other versions
EP2706312A1 (fr
Inventor
Luigi Zamana
Raymond Steils
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.)
Copeland Europe GmbH
Original Assignee
Emerson Climate Technologies GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Emerson Climate Technologies GmbH filed Critical Emerson Climate Technologies GmbH
Priority to EP12183137.4A priority Critical patent/EP2706312B1/fr
Publication of EP2706312A1 publication Critical patent/EP2706312A1/fr
Application granted granted Critical
Publication of EP2706312B1 publication Critical patent/EP2706312B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control 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
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B2600/2509—Economiser 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
    • 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
    • F25B2700/2101—Temperatures in a bypass
    • 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
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Definitions

  • the present invention relates to a method of operating a refrigerator, e.g. a refrigeration system, air conditioner or heat pump, comprising a refrigerant having a closed circuit in which an evaporator, a first compressor and at least one parallel connected second compressor, a condenser, a subcooler and a first expansion valve are arranged successively.
  • a refrigerator e.g. a refrigeration system, air conditioner or heat pump
  • a refrigerant having a closed circuit in which an evaporator, a first compressor and at least one parallel connected second compressor, a condenser, a subcooler and a first expansion valve are arranged successively.
  • Cooling machines of this type and methods for operating the same are known in principle, wherein cooling machines generally produce a cooling effect on their evaporator and a heating effect on their condenser.
  • heat pumps are used to convert heat stored in the soil, groundwater or air into thermal heat. Ideally, the thermal heat or heat energy generated thereby exceeds a necessary for operating the heat pump electrical energy by a multiple. Heat pumps thus represent a resource-saving option for supplying heat.
  • refrigerating machines are refrigerators, freezers or chests or air conditioning systems.
  • some chillers are equipped with several compressors in parallel, whereby one or more compressors are operated simultaneously depending on the required heat or cooling capacity.
  • two parallel compressors available so is also spoken by a tandem compressor.
  • the compressors compress the refrigerant evaporated in the evaporator and discharge the compressed refrigerant at its outputs as so-called pressurized gas having an increased pressure and an elevated temperature. If the compressors are operated at the limit of their capacity, the temperature of the compressed gas may exceed allowable limits and damage the compressors.
  • This form of compressor cooling is disadvantageous in that a separate according to its operating state controlled expansion valve is provided for each compressor. With regard to control effort and production costs, a refrigeration machine having such a compressor cooling is correspondingly complicated and expensive.
  • a method according to the preamble of claim 1 is known from FR 2 598 788 A1 known. Similar methods are further in the US 2005/0235689 A1 . WO 2008/082408 A1 and WO 2008/130359 A1 described.
  • the invention has for its object to provide a simpler method of operating a chiller of the type mentioned, which is accompanied at the same time with lower investment costs for the chiller and contributes to avoiding damage to the compressors and increasing their life.
  • the inventive method provides that liquid refrigerant branched off from the circuit between the condenser and the subcooler, expanded by means of a second expansion valve, at least partially evaporated by the subcooler and then supplied to the first and / or second compressor for cooling.
  • the second expansion valve is regulated by means of a control unit.
  • the second expansion valve is a regulated expansion valve, with the help of which, for example, the overheating of the diverted, expanded and vaporized refrigerant can be regulated.
  • a control unit is needed for the cooling of several and preferably all compressors.
  • Also required for an overheating control sensors for detecting pressure and temperature of the branched, expanded and vaporized refrigerant need to be provided only simply. It can be saved in this way so even more costs.
  • the second expansion valve is controlled in response to overheating of the refrigerant evaporated by the subcooler.
  • the second expansion valve is in this case controlled such that the refrigerant is not only evaporated by the subcooler, but also overheated. Overheating of the refrigerant ensures that the refrigerant has completely evaporated, i. exclusively in gaseous form.
  • overheating is regulated to a value between 0K and 10K.
  • the pressure and the temperature of the diverted refrigerant are advantageously detected after the subcooler, since the overheating of the refrigerant can be determined particularly reliably from these values.
  • a compressed gas temperature of the or each compressor in operation is detected, for example by means of a temperature sensor arranged in the region of the compressor outlet.
  • a temperature sensor arranged in the region of the compressor outlet.
  • the second expansion valve is controlled in dependence on the pressure gas temperature of a compressor when the pressure gas temperature of at least one compressor exceeds a predetermined threshold. Normally, for example, an overheating control of the second expansion valve, so it is switched to a pressure gas temperature control of the expansion valve as soon as the pressure gas temperature of at least one compressor is unacceptably high. In the pressurized gas temperature control mode, the expansion valve is controlled so that the discharge gas temperature again becomes an allowable value. To this end, the overheating of the refrigerant is reduced as much as necessary to a waiver of overheating, i. Avoid complete evaporation of the refrigerant. If necessary, the refrigerant may also only partially evaporate, i. So with a certain amount of liquid, are introduced into the compressor. In this way damage to the compressors can be effectively avoided and their life can be increased.
  • the second expansion valve according to the invention is controlled as a function of the respective highest compressed gas temperature of all compressors in operation.
  • the condition of the compressor with the highest pressure gas temperature can be said to be most critical to the function of the refrigerator. This compressor must therefore be primarily cooled.
  • the regulation of the second expansion valve is therefore dependent on this reason performed by the discharge gas temperature of the compressor with the highest pressure gas temperature.
  • the other compressors in operation are cooled accordingly for easier control, even if not or at least not absolutely necessary.
  • the supply of the refrigerant evaporated by the subcooler is controlled to the first compressor by means of a first shut-off valve and to the second compressor by means of a second shut-off valve, wherein the respective valve associated with the shut-off valve is opened as soon as it starts its operation.
  • a compressor is only supplied with branched-off refrigerant for cooling when it is actually in operation. If a compressor is in operation, it is continuously supplied with refrigerant for cooling.
  • the check valves may for example be designed as solenoid valves.
  • Another object of the invention is a refrigerator with the features of claim 6.
  • the refrigerator according to the invention makes it possible to carry out the method according to the invention, so that the advantages described above can be achieved accordingly.
  • a chiller in the form of a heat pump 10 is shown.
  • the heat pump 10 comprises a main circuit 11 having a refrigerant, the refrigerant flowing through the heat pump 10 in normal operation in a direction indicated by arrows.
  • a first compressor 12 and a second compressor 14 connected in parallel therewith are provided which, if necessary, can operate either individually or both at the same time.
  • gaseous refrigerant also referred to as compressed gas
  • a condenser 16 The compressed by the compressors gaseous refrigerant, also referred to as compressed gas, is liquefied in a condenser 16 and thereby cooled.
  • the liquefied refrigerant is then supplied to a majority through a subcooler 18 through a first expansion valve 20, through which the liquid refrigerant is expanded.
  • the expanded refrigerant is then vaporized in an evaporator 22 and then fed back to the compressors 12, 14.
  • a smaller portion of the refrigerant liquefied in the condenser 16 is diverted from the main circuit 11 between the condenser 16 and the subcooler 18 and supplied to a second expansion valve 24.
  • the branched refrigerant is expanded in the second expansion valve 24 and then exchanges heat in the subcooler 18 with the liquid refrigerant of the main circuit 11, at least partially evaporating it.
  • the liquid refrigerant guided in the main circuit 11 through the subcooler 18 is further cooled by the heat exchange with the branched and expanded refrigerant.
  • the branched refrigerant evaporated in the subcooler is supplied to both the first compressor 12 and the second compressor 14 via injection ports 26 for cooling.
  • the cooling refrigerant is always supplied to a compressor 12, 14 when it is in operation. Only when a compressor 12, 14 is stopped, the cooling refrigerant supply is interrupted by means of a respective compressor 12, 14 associated solenoid valve 28a, 28b.
  • the control of the second expansion valve 24 is performed by a control unit 30 which is connected to temperature sensors 32a, 32b, which detect the temperatures of the compressed gas at the outputs of the compressors 12, 14. Furthermore, the control unit 30 is connected to a temperature sensor 34 and a pressure sensor 36, which detect the temperature and the pressure of the diverted in the subcooler 18 branched refrigerant downstream of the subcooler 18. From the temperature and pressure values detected by the temperature sensor 34 and the pressure sensor 36, the control unit 30 can calculate the overheating of the evaporated refrigerant.
  • the control unit 30 performs overheating control. That the second expansion valve 24 is controlled so as to maintain a desired value of the superheat of the branched refrigerant evaporated by the subcooler 18.
  • control unit 30 switches to compressed gas temperature control and increases the flow of refrigerant through the second expansion valve 24 so as to increase the cooling of the compressors 12, 14 and thus achieve a reduction in the compressed gas temperature below the predetermined threshold.
  • control unit 30 regulates the second expansion valve 24 as a function of the respectively highest pressure gas temperature detected by the temperature sensors 32a, 32b.
  • both compressors 12, 14 are actually operating and the pressurized gas temperature of only one of the compressors 12, 14 is above the predetermined threshold, both compressors 12, 14 are similarly cooled, i. also the respective other compressor 12, 14 undergoes a stronger cooling.
  • control unit 30 switches back to overheating control, which then takes place again on the basis of the measured values detected by the temperature sensor 34 and the pressure sensor 36.

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

Claims (9)

  1. Procédé de fonctionnement d'une machine frigorifique comprenant un circuit fermé (11) qui présente un réfrigérant et dans lequel sont agencés successivement un évaporateur (22), un premier compresseur (12) et au moins un second compresseur (14) connecté en parallèle avec celui-ci, un condenseur (16), un sous-refroidisseur (18) et une première vanne de détente (20),
    dans lequel
    le réfrigérant liquide est dérivé hors du circuit (11) entre le condenseur (16) et le sous-refroidisseur (18), il est détendu au moyen d'une seconde vanne de détente (24), il est évaporé au moins partiellement par le sous-refroidisseur (18) et il est amené au premier et/ou au second compresseur (12, 14) pour être refroidi,
    caractérisé en ce que
    une température de gaz comprimé du ou de chaque compresseur (12, 14) en service est détectée au moyen d'un capteur de température (32a, 32b) disposé dans la zone de la sortie de compresseur respective, et
    la seconde vanne de détente (24) est régulée en fonction de la température de gaz comprimé respective la plus élevée de tous les compresseurs (12, 14) en service, lorsque la température de gaz comprimé d'au moins un compresseur (12, 14) dépasse une valeur seuil prédéterminée.
  2. Procédé selon la revendication 1,
    caractérisé en ce que
    la seconde vanne de détente (24) est régulée au moyen d'une unité de régulation (30).
  3. Procédé selon la revendication 1 ou 2,
    caractérisé en ce que
    la seconde vanne de détente (24) est régulée en fonction d'une surchauffe du réfrigérant évaporé par le sous-refroidisseur (18).
  4. Procédé selon l'une des revendications précédentes,
    caractérisé en ce que
    la pression et la température du réfrigérant dérivé sont détectées en aval du sous-refroidisseur (18) pour effectuer une régulation de surchauffe de la seconde vanne de détente (24).
  5. Procédé selon l'une des revendications précédentes,
    caractérisé en ce que
    l'alimentation du réfrigérant évaporé par le sous-refroidisseur (18) jusqu'au premier compresseur (12) est commandée à l'aide d'une première vanne d'arrêt (28a) et l'alimentation jusqu'au second compresseur (14) est commandée à l'aide d'une seconde vanne d'arrêt (28b), la vanne d'arrêt (28a, 28b) associée au compresseur respectif (12, 14) étant ouverte lorsque celui est mis en service.
  6. Machine frigorifique comprenant un circuit fermé (11) qui présente un réfrigérant et dans lequel sont agencés successivement un évaporateur (22), un premier compresseur (12) et au moins un second compresseur (14) connecté en parallèle avec celui-ci, un condenseur (16), un sous-refroidisseur (18) et une première vanne de détente (20),
    dans laquelle
    un trajet de dérivation est dérivé à partir du circuit (11) entre le condenseur (16) et le sous-refroidisseur (18), qui comprend une seconde vanne de détente (24), est en échange thermique avec le sous-refroidisseur (18) et est relié aux compresseurs (12, 14) pour détendre un réfrigérant liquide, pour l'évaporer au moins partiellement et pour l'amener au premier et/ou au second compresseur (12, 14) pour le refroidir,
    caractérisé en ce que
    une unité de régulation (30) pour réguler la seconde vanne de détente (24) est connectée à des capteurs de température (32a, 32b) dans la zone des sorties des compresseurs (12, 14) et est réalisée pour réguler la seconde vanne de détente (24) en fonction de la température de gaz comprimé respective la plus élevée de tous les compresseurs (12, 14) en service, lorsque la température de gaz comprimé d'au moins un compresseur (12, 14) dépasse une valeur seuil prédéterminée.
  7. Machine frigorifique (10) selon la revendication 6,
    caractérisée en ce que
    l'unité de régulation (30) est connectée à un capteur de pression (36) et à un capteur de température (34) qui sont agencés en aval du sous-refroidisseur (18) dans le trajet de dérivation.
  8. Machine frigorifique (10) selon la revendication 6 ou 7,
    caractérisée en ce que
    l'unité de régulation (30) est réalisée pour réguler la seconde vanne de détente (24) en fonction d'une surchauffe du réfrigérant évaporé par le sous-refroidisseur (19) dans le trajet de dérivation.
  9. Machine frigorifique (10) selon l'une des revendications 6 à 8,
    caractérisée en ce que
    l'alimentation du réfrigérant évaporé par le sous-refroidisseur (18) jusqu'au premier compresseur (12) est susceptible d'être arrêtée à l'aide d'une première vanne d'arrêt (28a) et l'alimentation jusqu'au second compresseur (14) est susceptible d'être arrêtée à l'aide d'une seconde vanne d'arrêt (28b).
EP12183137.4A 2012-09-05 2012-09-05 Procédé destiné au fonctionnement d'une machine frigorifique et machine frigorifique Active EP2706312B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP12183137.4A EP2706312B1 (fr) 2012-09-05 2012-09-05 Procédé destiné au fonctionnement d'une machine frigorifique et machine frigorifique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP12183137.4A EP2706312B1 (fr) 2012-09-05 2012-09-05 Procédé destiné au fonctionnement d'une machine frigorifique et machine frigorifique

Publications (2)

Publication Number Publication Date
EP2706312A1 EP2706312A1 (fr) 2014-03-12
EP2706312B1 true EP2706312B1 (fr) 2019-11-06

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Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111907301B (zh) 2019-05-07 2024-10-25 开利公司 组合式换热器、热交换系统及其优化方法

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007142619A2 (fr) * 2006-06-01 2007-12-13 Carrier Corporation Unité de compresseur à étages multiples pour système de réfrigération

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Publication number Priority date Publication date Assignee Title
US4787211A (en) * 1984-07-30 1988-11-29 Copeland Corporation Refrigeration system
JPH07190520A (ja) * 1993-12-27 1995-07-28 Kobe Steel Ltd 冷凍装置
US6718781B2 (en) * 2001-07-11 2004-04-13 Thermo King Corporation Refrigeration unit apparatus and method
US6474087B1 (en) * 2001-10-03 2002-11-05 Carrier Corporation Method and apparatus for the control of economizer circuit flow for optimum performance
US7997091B2 (en) * 2004-04-22 2011-08-16 Carrier Corporation Control scheme for multiple operating parameters in economized refrigerant system
JP2007255864A (ja) * 2006-03-27 2007-10-04 Mitsubishi Electric Corp 二段圧縮式冷凍装置
EP2097703B1 (fr) * 2006-12-29 2018-04-18 Carrier Corporation Échangeur de chaleur économiseur
CN101688697B (zh) * 2007-04-24 2012-10-03 开利公司 具有双节能器回路的制冷剂蒸汽压缩系统

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007142619A2 (fr) * 2006-06-01 2007-12-13 Carrier Corporation Unité de compresseur à étages multiples pour système de réfrigération

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