EP2242966A1 - Procédé de commande d'un côté échangeur de chaleur par rejet de chaleur d'un circuit de réfrigération - Google Patents

Procédé de commande d'un côté échangeur de chaleur par rejet de chaleur d'un circuit de réfrigération

Info

Publication number
EP2242966A1
EP2242966A1 EP09712018A EP09712018A EP2242966A1 EP 2242966 A1 EP2242966 A1 EP 2242966A1 EP 09712018 A EP09712018 A EP 09712018A EP 09712018 A EP09712018 A EP 09712018A EP 2242966 A1 EP2242966 A1 EP 2242966A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
heat
controlling
heat exchanging
exchanging side
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP09712018A
Other languages
German (de)
English (en)
Other versions
EP2242966B1 (fr
Inventor
Bernd Heinbokel
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.)
Carrier Corp
Original Assignee
Carrier Corp
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 Carrier Corp filed Critical Carrier Corp
Priority to EP09712018A priority Critical patent/EP2242966B1/fr
Publication of EP2242966A1 publication Critical patent/EP2242966A1/fr
Application granted granted Critical
Publication of EP2242966B1 publication Critical patent/EP2242966B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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
    • F25B49/027—Condenser control arrangements
    • 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
    • F25B2600/19—Refrigerant outlet condenser temperature

Definitions

  • the invention relates to a method of controlling a heat-rejection heat exchanging side of a refrigerant circuit and a refrigerant system adapted to carry out said method.
  • Refrigerating systems using a condenser for transferring heat from the refrigerant to the environment are well-known in the art. It is also known to manually set a desired amount of subcooling for the refrigerant in the condenser. Sub- cooling shall herein be understood as cooling the refrigerant below its condensation temperature. Taking into account said desired amount of subcooling (also referred to as reference subcooling value), the subcooling of the refrigerant is then controlled by a control algorithm. If the reference subcooling value is set too low, gaseous state refrigerant may exit the condenser (as the refriger- ant temperature is generally not perfectly uniform upon exiting the condenser), which can lead to instabilities in the condenser control. Setting the reference subcooling value too high leads to an unnecessarily high refrigerant pressure in the condenser. Both scenarios lead to an energetically inefficient operation of the condenser and the overall refrigerating system.
  • Exemplary embodiments of the invention include a method of controlling a heat-rejection heat exchanging side of a refrigerant circuit.
  • the method comprises the steps of providing a heat-rejection heat exchanging side comprising at least one heat-rejection heat exchanger, wherein a refrigerant is cooled against a secondary medium; obtaining a refrigerant condensation temperature
  • FIG. 1 shows a schematic of a portion of a refrigerant circuit comprising a condenser
  • FIG. 2 shows a schematic of a portion of another refrigerant circuit comprising a condenser and a subcooling unit
  • FIG. 3 shows an exemplary function of the temperature of a refrigerant and of a secondary medium over the length of a condenser.
  • FIG. 1 shows a portion of a refrigerant circuit comprising a set of compressors 2, a condenser 4, and an expansion device 6.
  • the set of compressors 2 and the condenser 4 as well as the condenser 4 and the expansion device 6 are connected by refrigerant conduits, respectively.
  • a refrigerant is flown through the set of compressors 2, to the condenser 4, through the condenser 4, to the expansion device 6, and through the expansion device 6.
  • the set of compressors 2 represent the inlet to the heat-rejection heat exchanging side of the refrigerant circuit
  • the expansion device 6 represents the outlet of the heat-rejection heat exchanging side of the refrigerant circuit.
  • the remainder of the refrigerant circuit is not shown in FIG. 1, as its concrete structure is irrelevant to the invention.
  • the refrigerant is flown through the expansion device 6, through an evaporator, and back to the set of compressors 2.
  • the remainder of the refrigerant circuit may also com- prise two separate portions, for example a refrigerator portion and a freezer
  • the refrigerant flow is split up after expansion device 6, advancing to two different evaporators, wherein each of the evaporators may be associated with an additional expansion device. There may also be an additional compressor on the way back from the evaporator of the freezer portion to the set of compressors 2.
  • the invention may also be applied to a refrigerant circuit using CO 2 as a refrigerant, which may be operated transcritically at times. In this case the refrigerant may be flown to a refrigerant collector after the expansion device 6.
  • the invention is generally applied to the refrigerating system, when it is operated subcritically, i.e. when condensation takes place in the heat-rejection heat exchanging side of the refrigerant circuit.
  • the invention may also be applied to any other design of the remainder of the refrigerant circuit.
  • the condenser 4 is shown as an air-cooled condenser with a fan (illustrated schematically in FIG. 1) blowing air over a structure, through which the refrigerant is flown. That means that air is acting as a secondary medium in the exem- plary embodiment of FIG. 1.
  • a controller (not shown) is associated with the heat-rejection heat exchanging side of the refrigerant circuit. The controller is connected to a plurality of sensors for receiving a number of momentary values of system parameters. Based on these values, the controller carries out a control algorithm and controls one or more actuators in order to take appropriate measures.
  • a temperature sensor measures the ambient air temperature, particularly the air temperature in the shade in close proximity to the condenser. This sensed temper- ature represents the temperature the air initially has when interacting with the refrigerant in the condenser 4, i.e. when blown at the condenser 4 by the fan. This value is hereinafter referred to as secondary medium inlet temperature
  • a second sensor measures the temperature of the refrigerant upon leaving the condenser 4, herein referred to as refrigerant outlet temperature T ro .
  • This sensor may be located at the end - in refrigerant flow direction - of the condenser 4, somewhere in the refrigerant conduit between condenser 4 and ex- pansion device 6, and particularly right before the expansion device 6.
  • a third sensor measures the refrigerant pressure in the heat-rejection heat exchanging side of the refrigerant circuit.
  • this refriger- ant pressure sensor can be located anywhere between these two elements. It can be located in the conduit between the set of compressors 2 and the condenser 4, in the condenser 4, in the conduit between the condenser 4 and the expansion device 6, and particularly right before the expansion device 6. It is apparent that a combined temperature and pressure sensor can be used between the condenser 4 and the expansion device 6 in order to sense the refrigerant outlet temperature T ro and the refrigerant pressure. Using given knowledge about the properties of the refrigerant, the controller can calculate the refrigerant condensation temperature T c from the momentary refrigerant pressure condition.
  • the controller receives the obtained values of the refrigerant condensation temperature T c , the refrigerant outlet temperature T ro , and the secondary medium inlet temperature T sm i. It relates these values in order to yield a relative sub- cooling value.
  • the controller computes the difference between the refrigerant condensation temperature T 0 and the refrigerant outlet temperature T ro . According to the definition above, this difference represents an actual subcooling value for the refrigerant. Furthermore, the controller computes the difference between the refrigerant condensation temperature T c and the secondary medium inlet temperature T smi .
  • the computed difference is referred to as maximum potential subcooling value of the refrigerant.
  • a relative subcooling value RSC is then calculated by dividing the actual subcooling value by the maximum potential subcooling value.
  • the relative subcooling value is a measure of which portion of the possible subcooling is achieved by the present refrigerating system under the momentary system conditions.
  • a control algorithm relates the relative subcooling value, and potentially other relative subcooling values at previous points in time, to a reference relative subcooling value.
  • these control methods are well-known in the art, a detailed description thereof shall be omitted for brevity.
  • any combination of P, I, and D elements can be used to generate an appropriate control algorithm.
  • the parametrization of the selected type may be adapted to the particular system under consideration.
  • Using delay elements (T elements) may also be considered when design- ing an appropriate control algorithm.
  • a Pl control algorithm has been found to yield good results.
  • the controller may control the performance of the set of compressors 2 and/or the flow rate through the expan- sion device 6, using those as actuators.
  • Each of these measures or their combination will have an influence on the refrigerant pressure in the heat-rejection heat exchanging side of the refrigerant circuit, thereby affecting the refrigerant condensation temperature T 0 .
  • the controller has appropriate means at its disposal to have an influence on the refrigerant condensation temperature T 0 , which affects the momentary relative subcooling value, which in turn makes it possible for the controller to bring the relative subcooling value to a desired reference relative subcooling value.
  • the refrigerant condensation temperature T c may also be influenced by controlling the refrigerant amount in the heat-rejection heat exchanging side of the refrigerant circuit. This may be effected by providing a bypass-structure to the heat-rejection heat exchanging side of the refrigerant circuit, wherein the bypass-structure comprises a refrigerant collector.
  • the refrigerant collector may be used to temporarily store refrigerant deducted from the refrigerant circuit. This results in an efficient control of the refrigerant amount and, therefore, the refrigerant condensation temperature T c in the heat-rejection heat exchanging side of the refrigerant circuit. Valves or any other suitable devices may be provided to control the amount of refrigerant in the refrigerant collector.
  • the reference relative subcooling value in the exemplary embodiment of FIG 1 lies between 0.5 and 0.7.
  • the refrigerant circuit may comprise only one compressor, whose performance may be adjustable.
  • the refrigerant in the condenser may be cooled against another secondary medium.
  • the secondary medium could be air enriched with water particles, water or a brine.
  • appropriate means would be necessary to sense the temperature of the secondary medium shortly before starting the heat exchange with the refrigerant.
  • adequate circulating means e.g. a pump
  • heat-rejection heat exchanging means e.g. secondary medium conduits
  • FIG. 2 shows a portion of another refrigerant circuit which differs from the portion of FIG. 1 in that the heat-rejection heat exchanging side of the refrigerant circuit does not only comprise a condenser 4, but also a subcooling unit 8.
  • the refrigerant flows through the condenser 4 before flowing through the subcooling unit 8.
  • the refrigerant is cooled down further therein after being condensed in the condenser 4.
  • the refrigerant is also cooled against a secondary medium.
  • the sec- ondary medium of the subcooling unit 8 may be the same as or different from the secondary medium of the condenser 4.
  • the temperature of the secondary medium of the subcooling unit 8 before interacting with the refrigerant determines the maximum potential subcooling value
  • said temperature is obtained by a temperature sensor or other appropriate means and used as T sm ⁇ by the controller.
  • the refrigerant outlet temperature T ro is obtained by a sensor between the subcooling unit 8 and the expansion device 6, particularly right before the expansion device 6.
  • the controller may in an exemplary embodiment be adapted to switch the subcooling unit on or off.
  • the secondary medium inlet temperature T sm of the subcooling unit will go into the calculation of the relative sub- cooling value, whereas the secondary medium inlet temperature T sm , of the condenser will be looked at, when the subcooling unit is switched off.
  • These temperatures may be different, particularly in the case of different secondary media being used.
  • switching the subcooling unit on/off may lead to different refrigerant outlet temperatures T r0 .
  • the subcooling unit will be switched off.
  • the controller is still able reach a desired relative subcooling value by influencing the refrigerant condensation temperature T c .
  • FIG. 3 shows an exemplary function of the temperature of the refrigerant and of the secondary medium over the length of a condenser, wherein the refrigerant and the secondary medium exhibit a counter-flow relationship.
  • the x-axis represents the distance the refrigerant and the secondary medium travel in the condenser, which is a particularly insightful way of looking at the temperature development when refrigerant and secondary medium flow side by side.
  • the secondary medium enters the condenser at point Xi having the secondary medium inlet temperature T sm ⁇ . It leaves the condenser at point X 2 , at which point it has been heated up to the secondary medium outlet temperature T smo .
  • the refrigerant enters the condenser at point x 2 flowing towards point X 1 . While flow- ing through the condenser, the refrigerant is first cooled down from the refrigerant inlet temperature T n to the refrigerant condensation temperature T 0 . For the most part of the length of the condenser, the refrigerant temperature remains constant at the refrigerant condensation temperature T c . During this time energy is continuously transferred from the refrigerant to the secondary medi- um, which results in the refrigerant being condensed, but not in a further decrease in temperature.
  • a co-flow relationship or a counter-flow relationship or perpendicular flow directions of the refrigerant and the secondary medium or any combination thereof may be considered, when designing a condenser, and may all lead to different results in terms of relative subcooling values. However, the controller may then take appropriate measures to cause the refrigerant condensation temperature T c to take on a value that leads to the relative subcooling value equal to the reference subcooling value.
  • Exemplary embodiments of the invention as described above allow for an energetically efficient control of a heat-rejection heat exchanging side of a refrigerant circuit, resulting in an optimum stable refrigerant subcooling and refrigerant pressure. They further allow for generating an aggregate metric, i.e. the relative subcooling value, which reflects a plurality of system aspects. Different ambient temperatures, which provide for varying load conditions throughout the course of a day and throughout the different seasons, have an influence on the relative subcooling value via the secondary medium inlet temperature, at least in a case when the heat-rejection heat exchanging side is cooled by air.
  • the type of heat-rejection heat exchanger used for example a condenser or a gas cooler, does not only have an influence on the refrigerant outlet temperature (as described above), but also on the secondary medium inlet temperature, both of which are reflected in the relative subcooling value.
  • Setting a reference relative subcooling value therefore allows for an efficient control of a heat-rejection heat exchanging side of a refrigerant system, irrespective of the type of heat-rejection heat exchanger used, irrespective of the size of the whole refrigerating system, irrespective of the load conditions, irrespective of the refrigerant used, and irrespective of the season and time of day, which are associated with varying ambient temperatures.
  • the control will achieve an optimum amount of subcooling. Thus it prevents re- frigerant to exit the heat-rejection heat exchanger in a gaseous state, which is
  • the step of calculating a relative subcooling value comprises calculating an actual subcooling value by subtracting the refrigerant outlet temperature from the refrigerant condensation temperature. This allows for the amount of subcooling of the refrigerant to have an influence on the aggregate metric, which is controlled by the control method. This helps in ensuring an optimum subcooling of the refrigerant.
  • the calculating of a relative subcooling value comprises calculating a maximum potential subcooling value by subtracting the secondary medium inlet temperature from the refrigerant condensation temperature. Calculating this difference allows for relating the refrigerant condensation temperature to the environment surrounding the heat-rejection heat exchanger, thus generating an appropriate basis that the refrigerant subcooling value can be compared with.
  • the calculating of a relative subcooling value may also comprise setting the actual subcooling value in relation to the maximum potential subcooling value. This allows for yielding an aggregate metric based on the refrigerant outlet temperature, the refrigerant condensation temperature, and the secondary medium inlet temperature, which can serve as a basis for a control method that is easy to be implemented and efficient to be carried out.
  • the relative subcooling value RSC may particularly be calculated according to the formula
  • the reference relative subcooling value is above 0.5. This allows for a sufficient amount of subcooling in order to prevent refrigerant to leave the heat-rejection heat exchanger in a gaseous state. It therefore provides a stable control of the amount of subcooling of the refrigerant.
  • the reference relative subcooling value may be between 0.5 and 0.7. This also prevents the amount of subcooling to become excessive and therefore prevents unnecessarily high refrigerant pressure in the heat-rejection heat exchanger. Depending on system considerations, the reference relative subcooling value may also be in a range from 0.3 to 0.5 or in a range from 0.7 to 0.8.
  • controlling of the relative subcooling value is effected by controlling the refrigerant condensation temperature.
  • Controlling the refrigerant condensation temperature may be effected by controlling the refrigerant pressure in the heat-rejection heat exchanging side of the refrigerant cir- cuit.
  • the performance of the set of compressors and/or the flow rate through the expansion device can be controlled easily, this allows for the control method to be implemented efficiently and in a cost saving manner.
  • the flow rate through said side may be con- trolled at the same time, allowing for an efficient control adaptable to all load conditions.
  • obtaining the refrigerant condensation temperature comprises sensing the refrigerant pressure in the heat-rejection heat exchan- ging side of the refrigerant circuit and calculating the refrigerant condensation temperature from the refrigerant pressure and refrigerant properties.
  • refrigerant properties generally relate pressure and condensation temperature
  • the condensation temperature can be deduced from the readings of a pressure sensor. This is advantageous as pressure sensors with short response times to pressure changes exist.
  • the refrigerant may be CO 2 . It may also be R404a or any type of hydrocarbons or of halogenized fluorhydrocarbons or ammonia or any other refrigerant suitable for the particular refrigerant circuit under consideration.
  • the heat-rejection heat exchanging side of the refrigerant circuit may comprise a condenser. It is also possible that the heat-rejection heat exchanging side of the refrigerant circuit comprises a condenser and a subcooling unit. It may also comprise any combination of any number of any types of heat exchangers suitable for the refrigerating system under consideration. This allows for designing a refrigerating system that is adapted to the particular size, performance, cost, and noise requirements, with the individual heat exchangers potentially being spaced apart.
  • the method of the invention may be carried out by a refrigerating system com- prising a refrigerating circuit with a heat-rejection heat exchanging side and having a controller associated therewith.
  • a refrigerating system com- prising a refrigerating circuit with a heat-rejection heat exchanging side and having a controller associated therewith.
  • the advantages associated with the various embodiments of the invention may equally be attained by adapting said refrigerating system in such a way that it is capable of carrying out these features.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

L’invention concerne un procédé de commande d'un côté échangeur de chaleur par rejet de chaleur d'un circuit de réfrigération. Le procédé consiste à: mettre en œuvre un côté échangeur de chaleur par rejet de chaleur comprenant au moins un échangeur de chaleur par rejet de chaleur (4), un frigorigène étant refroidi en fonction d'un milieu secondaire; atteindre une température de condensation du frigorigène (Tc) dans le côté échangeur de chaleur par rejet de chaleur; atteindre une température de de sortie du frigorigène (Tro); atteindre une température d'entrée du milieu secondaire (Tsmi); calculer une valeur relative de sous-refroidissement en rapportant la température de condensation du frigorigène (Tc), la température de de sortie du frigorigène (Tro) et la température d'entrée du milieu secondaire (Tsmi); et contrôler la valeur relative de sous-refroidissement par rapport à une valeur relative de sous-refroidissement de référence.
EP09712018A 2008-02-20 2009-02-16 Procédé de commande d'un côté échangeur de chaleur par rejet de chaleur d'un circuit de réfrigération Active EP2242966B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP09712018A EP2242966B1 (fr) 2008-02-20 2009-02-16 Procédé de commande d'un côté échangeur de chaleur par rejet de chaleur d'un circuit de réfrigération

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP08003127 2008-02-20
PCT/EP2009/001063 WO2009103472A1 (fr) 2008-02-20 2009-02-16 Procédé de commande d'un côté échangeur de chaleur par rejet de chaleur d'un circuit de réfrigération
EP09712018A EP2242966B1 (fr) 2008-02-20 2009-02-16 Procédé de commande d'un côté échangeur de chaleur par rejet de chaleur d'un circuit de réfrigération

Publications (2)

Publication Number Publication Date
EP2242966A1 true EP2242966A1 (fr) 2010-10-27
EP2242966B1 EP2242966B1 (fr) 2012-11-07

Family

ID=40852150

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09712018A Active EP2242966B1 (fr) 2008-02-20 2009-02-16 Procédé de commande d'un côté échangeur de chaleur par rejet de chaleur d'un circuit de réfrigération

Country Status (2)

Country Link
EP (1) EP2242966B1 (fr)
WO (1) WO2009103472A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5447499B2 (ja) * 2011-12-28 2014-03-19 ダイキン工業株式会社 冷凍装置

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04251162A (ja) * 1991-01-07 1992-09-07 Nippondenso Co Ltd 冷凍サイクル制御装置
JP3511708B2 (ja) * 1995-01-10 2004-03-29 ダイキン工業株式会社 空気調和装置の運転制御装置
JP3063574B2 (ja) * 1995-06-26 2000-07-12 株式会社デンソー 空調装置
JP2000304374A (ja) * 1999-04-22 2000-11-02 Yanmar Diesel Engine Co Ltd エンジンヒートポンプ
JP2002081767A (ja) * 2000-09-07 2002-03-22 Hitachi Ltd 空気調和装置
JP2003166762A (ja) * 2001-11-29 2003-06-13 Hitachi Ltd 空気調和装置
JP3903342B2 (ja) * 2003-03-13 2007-04-11 株式会社日立製作所 空気調和機
AU2008310483B2 (en) * 2007-10-10 2011-09-08 Daikin Industries, Ltd. Air conditioner

Non-Patent Citations (1)

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Title
See references of WO2009103472A1 *

Also Published As

Publication number Publication date
WO2009103472A1 (fr) 2009-08-27
EP2242966B1 (fr) 2012-11-07

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