EP0152608B1 - Procédé de commande d'une installation frigorifique complexe - Google Patents

Procédé de commande d'une installation frigorifique complexe Download PDF

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Publication number
EP0152608B1
EP0152608B1 EP84115860A EP84115860A EP0152608B1 EP 0152608 B1 EP0152608 B1 EP 0152608B1 EP 84115860 A EP84115860 A EP 84115860A EP 84115860 A EP84115860 A EP 84115860A EP 0152608 B1 EP0152608 B1 EP 0152608B1
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European Patent Office
Prior art keywords
fans
temperature
pressure
approx
volume flow
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Expired
Application number
EP84115860A
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German (de)
English (en)
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EP0152608A3 (en
EP0152608A2 (fr
Inventor
Herbert Hansen
Herbert Hartmann
Siegfried Dipl.-Ing. Haaf
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Linde GmbH
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Linde GmbH
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Application filed by Linde GmbH filed Critical Linde GmbH
Priority to AT84115860T priority Critical patent/ATE39180T1/de
Publication of EP0152608A2 publication Critical patent/EP0152608A2/fr
Publication of EP0152608A3 publication Critical patent/EP0152608A3/de
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Publication of EP0152608B1 publication Critical patent/EP0152608B1/fr
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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
    • 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
    • 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
    • F25B2400/22—Refrigeration systems for supermarkets
    • 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
    • F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser

Definitions

  • the invention relates to a method for controlling a composite refrigeration system with a plurality of compressors and at least one fan for removing the condensing heat, in which the air volume flow of the fan or fans is changed as a function of the air intake temperature and the cooling capacity.
  • a composite refrigeration system essentially consists of several compressors with a common suction line and a common pressure line, a condenser and several evaporators as well as expansion elements which are assigned to the evaporators.
  • the condenser is assigned one or more fans which dissipate the heat generated during the liquefaction of the refrigerant.
  • a certain number of compressors and a certain number of fans are in operation.
  • the operation of the compressors and fans requires a high drive energy. To reduce this, compressors are therefore usually switched off during part-load operation, while the condenser fan or fans continue to be operated at full air output. Although this can achieve a certain reduction in energy consumption, the result of this measure is that the application range of the expansion valves is exceeded.
  • DE-A-3 025 439 describes a cooling system in which one of three cooling fans of the condenser is actuated as a function of the temperature of the air drawn in.
  • the control option is limited to switching this blower on and off at a fixed threshold air intake temperature.
  • US-A-3 739 596 shows a cooling system which is controlled in dependence on the condensing pressure by switching two condensing fans on and off directly by means of pressure switches located in front of the condenser.
  • a similar method is described in GB-A-2 067 275.
  • it is proposed to switch the condenser fans on or off depending on the condensing pressure.
  • the object of the invention is to optimize the ratio of the cooling capacity of the compressors to the power consumption of the compressors and fans, that is to say to minimize the total power consumption in particular with a predetermined cooling capacity.
  • the area of application of the expansion valves should be maintained compared to the known method and the condensing pressure should be optimized.
  • This object is achieved according to the invention in that the air intake temperature T A and the condensing pressure p c are measured and a setpoint Pe , s of the condensing pressure which is dependent on the air intake temperature is set.
  • the instantaneous cooling capacity is recorded indirectly via the condensing pressure.
  • the measured condensing pressure is compared with a setpoint, the calculation of which includes the air intake temperature and system-specific parameters.
  • the air volume flow of the fan or fans is increased or decreased.
  • This regulation of the air volume flow of the condenser fans allows a particularly favorable adaptation of the fan performance to the two parameters air intake temperature and cooling capacity.
  • the optimal number of condenser fans can be switched on for a predetermined number of compressors in operation. In general, a reduced air volume flow is used. The resulting savings can drive the energy required to drive the condenser fans, making the method according to the invention particularly economical.
  • the regulation of the air volume flow according to the invention is in particular provided such that the air volume flow is reduced at a lower air intake temperature.
  • a lower air intake that is, lower the outside temperature is, driven in a start-first full air output, and then the air power is reduced for example by reducing the speed of the fans to 2/3 of the original value.
  • a predetermined range of the condensing pressure must be maintained in a development of the inventive concept. This range is limited on the one hand by a minimum pressure, which is necessary for the expansion valves to work properly, and on the other hand, by a maximum pressure, which is determined by the application limits of the refrigerant compressors.
  • the range of condensing pressure to be observed also depends on the refrigerant used.
  • the range of common refrigerants such as R 22 and R 502 is, for example, between approx. 10 bar and approx. 20 bar.
  • the parameters A and B depend on the properties of the refrigerant used and on the conditions of the refrigeration system.
  • the control of a composite refrigeration system is also provided, in which additional heat recovery is provided for space heating and domestic water heating.
  • the air volume flow is additionally regulated as a function of the hot water supply temperature and / or the room temperature.
  • the evaporation pressure of the refrigerant is increased when the cooling requirement drops. If the ambient temperature and thus the cooling requirement decrease, the evaporation temperature and thus the evaporation pressure of the refrigerant is increased.
  • the lower pressure difference between evaporation and condensing pressure means that less energy has to be applied for compression.
  • the inventive method is applicable to all composite refrigeration systems, such. B. for chilled and frozen sales furniture in supermarkets, for slaughterhouses, cold stores or process engineering systems.
  • compressors 1a, 1b, 1c and 1d connected in parallel are connected to a collecting container 7 via a common suction line 4, a plurality of evaporators 5 and expansion valves 6.
  • evaporators 5 and expansion valves 6 For the sake of simplicity, only one evaporator and one expansion valve are shown, but in practice several evaporators and expansion valves are usually connected in parallel.
  • Liquid refrigerant is stored in the collecting container and fed to the evaporators via the expansion valves 6.
  • the refrigerant suction gas in line 4 is then evenly distributed to the individual compressors of the composite system and sucked in by them.
  • Compressed refrigerant vapor is then passed into a common pressure line 8 and to a condenser 9, in which the vapors are condensed and released in liquid form via line 10 into the collecting container 7.
  • the condenser 9 is equipped with fans 11, 12 which are connected to a control unit 13.
  • the air volume flow circulated by the fans is conducted via the condenser and removes the heat of condensation, so that the refrigerant condensation can take place in the condenser.
  • a temperature sensor 14 is connected to the control unit 13 and detects the temperature in the air intake duct of the condenser.
  • the condenser is also assigned a pressure transmitter 20, which is also connected to the control unit 13.
  • a condenser 15 is also provided in line 8, in which the condensation heat can be used for heating domestic water and / or for space heating.
  • water from the space heating circuit is supplied via line 16 and heated in the condenser 15.
  • a boiler 17 can also be switched on.
  • the hot water is returned to the heat consumers via a pump 18.
  • a heating controller 19, which is connected to the control unit 13, is assigned to the boiler.
  • Parameters A and B are used to adapt to the respective refrigerant and system-specific conditions.
  • the refrigerating capacity can be adapted to this requirement by raising the evaporating temperature (increasing the evaporating pressure) of the refrigerant. As a result, the pressure difference to be overcome by the compressors is reduced, which leads to a corresponding energy saving.
  • the process according to the invention proceeds somewhat differently with heat recovery.
  • the fans are switched as a function of the heating controller 19, which detects the water flow temperature and whose setpoint is shifted from the outside temperature. If the heat of condensation in the condenser 15 is not sufficient to ensure the necessary heating of the water, the boiler 17 is additionally switched on. If the condensing pressure rises to an adjustable first upper limit value during heat recovery, the boiler 17 is still controlled by the heating controller 19. The current air volume flow through the condenser 9 is not changed. However, if the condensing pressure continues to rise and exceeds a second upper limit value, the control of the fans or of the air volume flow is taken over directly by the condensing pressure regulator 20. This controller causes the air volume flow to be increased. When the pressure falls below the first upper pressure limit, the heating controller 19 again takes over the control of the boiler and the fans.
  • control device 13 essentially comprises a microcomputer with associated software, data input and data acquisition, measurement value acquisition and conversion and processing, and an output. Furthermore, a 16-digit alphanumeric display and a 10-key data keyboard are arranged on the control device, among other things, for entering setpoints, for querying actual values, outputting messages, and setting a timer.
  • Each refrigeration consumer is usually assigned a solenoid valve that is switched by a thermostat. If the thermostat of the consumer requests cooling capacity and at least one compressor is in operation, the solenoid valve opens. However, if the pressure on the low pressure side is so low that a pressure switch has responded, all compressors are switched off and the solenoid valves are closed and cannot be opened by the thermostats. In this case, it is intended to pulse the solenoid valve, the thermostat of which requires cooling capacity, that is, to switch it on and off alternately. On the one hand, this ensures that the pressure in the suction line rises and, on the other hand, the evaporator is not overfilled with liquid refrigerant, which prevents damage to the compressor due to liquid hammer.

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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)
  • Agricultural Chemicals And Associated Chemicals (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Claims (7)

1. Procédé de contrôle d'une installation frigorifique complexe avec plusieurs compresseurs et au moins un ventilateur pour la dissipation de la chaleur de condensation dans lequel le courant de volume d'air du ou des ventilateurs est modifié en fonction de la température d'air aspiré et de la capacité frigorifique, caractérisé en ce que l'on mesure la température d'air aspiré TA et la pression de condensation pc et que l'on règle un point de consigne pc,s de la pression de condensation dépendant de la température d'air aspiré TA.
2. Procédé selon la revendication 1, caractérisé en ce que la pression de consigne de condensation pc,s à régler est déterminée selon la formule:
Figure imgb0006
avec
A = paramètre en bars/°C
B = paramètre en bars
TA = température d'air aspiré.
3. Procédé selon la revendication 1, caractérisé en ce que le courant de volume d'air est réglé en mettant en et/ou hors circuit les ventilateurs.
4. Procédé selon la revendication 1, caractérisé en ce que le courant de volume d'air est réglé en modifiant la vitesse de rotation des ventilateurs.
5. Procédé selon une des revendications 1 à 4, caractérisé en ce que le courant de volume d'air est diminué pour une température d'air aspiré moins importante.
6. Procédé pour le contrôle d'une installation frigorifique complexe selon la revendication 1, dans laquelle on a prévu une récupération de chaleur pour le chauffage des locaux et d'eau sanitaire, caractérisé en ce que l'on règle le courant de volume d'air, en outre, en fonction de la température d'eau chaude aller et/ou de la température ambiante.
7. Procédé selon une des revendications 1 à 6, caractérisé en ce que la pression d'évaporation du fluide frigorigène est augmentée si le besoin en froid diminué.
EP84115860A 1984-02-17 1984-12-19 Procédé de commande d'une installation frigorifique complexe Expired EP0152608B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84115860T ATE39180T1 (de) 1984-02-17 1984-12-19 Verfahren zur steuerung einer verbundkaelteanlage.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3405810 1984-02-17
DE19843405810 DE3405810A1 (de) 1984-02-17 1984-02-17 Verfahren zur steuerung einer verbundkaelteanlage

Publications (3)

Publication Number Publication Date
EP0152608A2 EP0152608A2 (fr) 1985-08-28
EP0152608A3 EP0152608A3 (en) 1986-04-09
EP0152608B1 true EP0152608B1 (fr) 1988-12-07

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Family Applications (1)

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EP84115860A Expired EP0152608B1 (fr) 1984-02-17 1984-12-19 Procédé de commande d'une installation frigorifique complexe

Country Status (3)

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EP (1) EP0152608B1 (fr)
AT (1) ATE39180T1 (fr)
DE (2) DE3405810A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10021610A1 (de) * 2000-05-04 2001-11-08 Linde Ag Verfahren zum Betreiben einer (Verbund)Kälteanlage

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3609313A1 (de) * 1986-03-20 1987-09-24 Bbc York Kaelte Klima Verfahren zur rueckgewinnung von verfluessigungswaerme einer kaelteanlage und kaelteanlage zur durchfuehrung des verfahrens
CA1322858C (fr) * 1988-08-17 1993-10-12 Masaki Nakao Appareil de refroidissement et methode de commande connexe
DE3832226A1 (de) * 1988-09-22 1990-04-12 Danfoss As Kaelteanlage und verfahren zur steuerung einer kaelteanlage
DE4008877A1 (de) * 1988-09-22 1991-10-02 Danfoss As Kaelteanlage
FR2748799B1 (fr) * 1996-05-17 1998-07-10 Mc International Procede de regulation d'un condenseur d'installation frigorifique pour economiser l'energie
US6530236B2 (en) * 2001-04-20 2003-03-11 York International Corporation Method and apparatus for controlling the removal of heat from the condenser in a refrigeration system
DE102010003915B4 (de) * 2010-04-13 2015-11-19 WESKA Kälteanlagen GmbH Kälteanlage mit Wärmerückgewinnung und Verfahren zum Betreiben der Kälteanlage
CN107356007B (zh) * 2016-06-13 2024-04-09 北京库蓝科技有限公司 一种自复叠三温变容量输出制冷系统

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3138941A (en) * 1963-06-05 1964-06-30 Westinghouse Electric Corp Controls for refrigeration systems having air cooled condensers
US3390538A (en) * 1967-06-23 1968-07-02 Trane Co Refrigeration system
US3460354A (en) * 1968-03-07 1969-08-12 Dunham Bush Inc Refrigeration system and method
US3739596A (en) * 1971-11-10 1973-06-19 Gen Electric Refrigeration system including head pressure control means
DE2748252A1 (de) * 1977-10-27 1979-05-03 Siemens Ag Verfahren zum regeln des verfluessigungsdruckes im kaeltemittelkreislauf einer waermepumpe
US4134274A (en) * 1978-01-26 1979-01-16 The Trane Company System for producing refrigeration and a heated liquid and control therefor
US4286437A (en) * 1979-07-13 1981-09-01 Tyler Refrigeration Corporation Energy saving refrigeration system
GB2067275B (en) * 1979-11-22 1984-06-06 Trendpam Eng Ltd Combined refrigeration and heating system

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10021610A1 (de) * 2000-05-04 2001-11-08 Linde Ag Verfahren zum Betreiben einer (Verbund)Kälteanlage

Also Published As

Publication number Publication date
DE3475564D1 (en) 1989-01-12
EP0152608A3 (en) 1986-04-09
EP0152608A2 (fr) 1985-08-28
ATE39180T1 (de) 1988-12-15
DE3405810A1 (de) 1985-08-22

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