EP0152608A2 - 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
EP0152608A2
EP0152608A2 EP84115860A EP84115860A EP0152608A2 EP 0152608 A2 EP0152608 A2 EP 0152608A2 EP 84115860 A EP84115860 A EP 84115860A EP 84115860 A EP84115860 A EP 84115860A EP 0152608 A2 EP0152608 A2 EP 0152608A2
Authority
EP
European Patent Office
Prior art keywords
fans
volume flow
air volume
temperature
pressure
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
EP84115860A
Other languages
German (de)
English (en)
Other versions
EP0152608A3 (en
EP0152608B1 (fr
Inventor
Herbert Hansen
Herbert Hartmann
Siegfried Dipl.-Ing. Haaf
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.)
Linde GmbH
Original Assignee
Linde 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6228078&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0152608(A2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
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
Application granted granted Critical
Publication of EP0152608B1 publication Critical patent/EP0152608B1/fr
Expired legal-status Critical Current

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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 heat of condensation.
  • 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.
  • 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. This is because the fans with full air volume flow and switching off individual compressors can cause the condensing pressure to drop too low.
  • the lower limit of the condensing pressure is given by the expansion valves used and the refrigerant.
  • 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 in that the air volume flow of the fan or fans is controlled depending on the air intake temperature and / or the instantaneous cooling capacity.
  • the invention is based on the idea of switching the optimal number of condensing fans for a predetermined number of compressors in operation. In contrast to the known method, work is no longer carried out with a full air volume flow but with a reduced air volume flow. The saving in energy required to drive the condensing fans is greater than the possible increase in drive energy for the compressors.
  • 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 R22 and R 502 is, for example, between approx. 10 bar and approx. 20 bar.
  • the regulation of the air volume flow according to the invention is particularly provided so that the air volume flow is reduced at a lower air intake temperature.
  • lower air intake temperature i.e. lower outside temperature
  • full air output is first driven in a start-up phase and then the air output is reduced to 2/3 of the original value, for example by reducing the speed of the fans.
  • the energy savings that can be achieved with this are described below.
  • the method according to the invention is applicable to all composite refrigeration systems, e.g. for refrigerated 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 led 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 passed over 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.
  • Via line 16 for example, water is brought in from the space heating circuit and heated in the condenser 15. If the heat of liquefaction is insufficient, 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 in this case as a function of the heating controller 19, which detects the water supply 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 continues to be controlled via 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 the air volume flow is taken over directly by the condensing pressure regulator 20. This regulator causes the air volume flow to be increased. If the pressure falls below the first upper pressure limit, the heating regulator takes over ler 19 again the control of the boiler and fans.
  • control device 13 essentially comprises a microcomputer with associated software, data input and data acquisition, data 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.
  • the control unit includes the following options:
  • 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 and the solenoid valves are switched off 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.

Landscapes

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

Family

ID=6228078

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84115860A Expired EP0152608B1 (fr) 1984-02-17 1984-12-19 Procédé de commande d'une installation frigorifique complexe

Country Status (3)

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

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0239837A2 (fr) * 1986-03-20 1987-10-07 BROWN, BOVERI - YORK Kälte- und Klimatechnik Procédé pour la récupération de la chaleur de condensation d'un système frigorifique et système frigorifique pour la mise en oeuvre du procédé
EP0355180A2 (fr) * 1988-08-17 1990-02-28 Nippon Telegraph And Telephone Corporation Refroidisseur et procédé de régulation
FR2636723A1 (fr) * 1988-09-22 1990-03-23 Danfoss As
DE4008877A1 (de) * 1988-09-22 1991-10-02 Danfoss As Kaelteanlage
FR2748799A1 (fr) * 1996-05-17 1997-11-21 Mc International Procede de regulation d'un condenseur d'installation frigorifique pour economiser l'energie
WO2002086396A1 (fr) * 2001-04-20 2002-10-31 York International Corporation Procede et dispositif d'evacuation de la chaleur du condenseur d'un systeme de refrigeration
CN107356007A (zh) * 2016-06-13 2017-11-17 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

Families Citing this family (2)

* 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
DE102010003915B4 (de) * 2010-04-13 2015-11-19 WESKA Kälteanlagen GmbH Kälteanlage mit Wärmerückgewinnung und Verfahren zum Betreiben der Kälteanlage

Citations (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
US4134274A (en) * 1978-01-26 1979-01-16 The Trane Company System for producing refrigeration and a heated liquid and control therefor
DE2748252A1 (de) * 1977-10-27 1979-05-03 Siemens Ag Verfahren zum regeln des verfluessigungsdruckes im kaeltemittelkreislauf einer waermepumpe
DE3025439A1 (de) * 1979-07-13 1981-05-27 Tyler Refrigeration Corp., Niles, Mich. Energiesparendes kuehlsystem
GB2067275A (en) * 1979-11-22 1981-07-22 Trendpam Eng Ltd Combined refrigeration and heating system

Patent Citations (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
DE3025439A1 (de) * 1979-07-13 1981-05-27 Tyler Refrigeration Corp., Niles, Mich. Energiesparendes kuehlsystem
GB2067275A (en) * 1979-11-22 1981-07-22 Trendpam Eng Ltd Combined refrigeration and heating system

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0239837A2 (fr) * 1986-03-20 1987-10-07 BROWN, BOVERI - YORK Kälte- und Klimatechnik Procédé pour la récupération de la chaleur de condensation d'un système frigorifique et système frigorifique pour la mise en oeuvre du procédé
EP0239837A3 (fr) * 1986-03-20 1990-03-28 BROWN, BOVERI - YORK Kälte- und Klimatechnik Procédé pour la récupération de la chaleur de condensation d'un système frigorifique et système frigorifique pour la mise en oeuvre du procédé
EP0355180A2 (fr) * 1988-08-17 1990-02-28 Nippon Telegraph And Telephone Corporation Refroidisseur et procédé de régulation
EP0355180A3 (en) * 1988-08-17 1990-03-28 Nippon Telegraph And Telephone Corporation Cooling apparatus and control method
FR2636723A1 (fr) * 1988-09-22 1990-03-23 Danfoss As
DE4008877A1 (de) * 1988-09-22 1991-10-02 Danfoss As Kaelteanlage
FR2748799A1 (fr) * 1996-05-17 1997-11-21 Mc International Procede de regulation d'un condenseur d'installation frigorifique pour economiser l'energie
WO2002086396A1 (fr) * 2001-04-20 2002-10-31 York International Corporation Procede et dispositif d'evacuation de la chaleur du condenseur d'un systeme de refrigeration
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
EP1811249A1 (fr) * 2001-04-20 2007-07-25 York International Corporation Procede et dispositif d`evacuation de la chaleur du condenseur d`un systeme de refrigeration
CN107356007A (zh) * 2016-06-13 2017-11-17 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
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

Also Published As

Publication number Publication date
ATE39180T1 (de) 1988-12-15
DE3475564D1 (en) 1989-01-12
EP0152608A3 (en) 1986-04-09
DE3405810A1 (de) 1985-08-22
EP0152608B1 (fr) 1988-12-07

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