EP0866291A1 - Pompe de chaleur à compression ou machine de refroidissement à compression et sa méthode de régulation - Google Patents

Pompe de chaleur à compression ou machine de refroidissement à compression et sa méthode de régulation Download PDF

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Publication number
EP0866291A1
EP0866291A1 EP98104767A EP98104767A EP0866291A1 EP 0866291 A1 EP0866291 A1 EP 0866291A1 EP 98104767 A EP98104767 A EP 98104767A EP 98104767 A EP98104767 A EP 98104767A EP 0866291 A1 EP0866291 A1 EP 0866291A1
Authority
EP
European Patent Office
Prior art keywords
sensor
compression
temperature
heat pump
condenser
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
EP98104767A
Other languages
German (de)
English (en)
Other versions
EP0866291B1 (fr
Inventor
Andreas Bangheri
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.)
Bangheri Andreas
Original Assignee
Krimbacher Peter
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 Krimbacher Peter filed Critical Krimbacher Peter
Publication of EP0866291A1 publication Critical patent/EP0866291A1/fr
Application granted granted Critical
Publication of EP0866291B1 publication Critical patent/EP0866291B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/063—Feed forward 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
    • F25B2700/195—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
    • F25B2700/21—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
    • 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
    • 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 invention relates to a compression heat pump or compression refrigeration machine according to the preamble of claim 1.
  • the invention further relates to a Method for controlling such a compression heat pump or compression refrigeration machine.
  • Devices according to the preamble of claim 1 are from DE-OS 43 03 533 and WO 96/24016. With these, the regulation is primarily also based on the evaporator superheat temperature, as a secondary
  • the control parameter is also the hot gas temperature, i.e. the temperature of the Refrigerant measured in the area between the compressor and condenser, whereby at an inadmissibly high hot gas temperature, the expansion valve is opened further and the hot gas temperature is thereby lowered.
  • a disadvantage of the known control of the expansion valve based on the evaporator superheating temperature is that the temperature differences used for the control are only very small, so that the regulation is usually only very rough takes place because of a more precise regulation that the facility becomes too expensive would lead.
  • the object of the invention is a compression heat pump or compression refrigerator to provide the type mentioned at the outset, which without price increases allows the apparatus to control the expansion valve much more precisely. According to the invention, this is achieved by a compression heat pump or a compression refrigerator with the features of claim 1.
  • the device according to the invention is therefore to regulate the expansion valve arranged next to the first in the area between the compressor and the condenser Temperature sensor provided a second sensor that detects a value that is a direct one Represents a measure of the condensation temperature. Taking a direct measure for that Condensation temperature is understood to mean that for a given apperative Arrangement from the value recorded by the second sensor without using further measured variables reflecting the current state of the system at least approximately the condensation temperature can be determined.
  • the second sensor designed as a pressure sensor and in the high-pressure area of the refrigerant circuit thus arranged in the area between the compressor and expansion valve. From the dated The pressure recorded by the sensor will directly maintain the condensation temperature.
  • the second sensor as a temperature sensor and to be placed directly on the capacitor, in an area of the same, in which, as far as possible, approximately the condensation temperature under all operating conditions appropriate temperature is present.
  • the second sensor is one in the flow line of the heating circuit arranged temperature sensor.
  • the one recorded by this sensor Temperature deviates only a few degrees Kelvin from the condensation temperature and can use a correction factor in the condensation temperature can be converted.
  • the controlled variable varies significantly more than with a control
  • the expansion valve can be regulated based on the evaporator superheating temperature in the device according to the invention without large apparatus Additional effort can be carried out much more precisely.
  • Controlled variable the difference between the two determined by the two sensors Temperature values used.
  • the refrigerant circuit of the compression heat pump shown schematically in FIG. 1 comprises an evaporator 1, a compressor 2, a condenser 3 and an expansion valve 4.
  • the refrigerant is evaporated in the evaporator, one Amount of heat 5 is absorbed by the environment. That compressed by the compressor 2 Hot gas condenses in the condenser designed as a heat exchanger, wherein an amount of heat 6 is given to the heating circuit 7.
  • An optimal efficiency of the compression heat pump is achieved if that Refrigerant in the evaporator 1 is overheated as little as possible.
  • a small amount of non-evaporated refrigerant is irrelevant since the compressor is cooled by suction gas Compressor is formed, i.e. Engine heat is drawn to the intake gas emitted, remnants of coolant are evaporated.
  • the refrigerant however not heated enough when liquid refrigerant gets into the compressor oil and the oil in the compressor starts to foam. In this case, the supply of Refrigerant in the evaporator 1 is reduced by throttling the expansion valve 4 will.
  • a control device 8 is provided for exact control of the expansion valve 4, which is connected to a temperature sensor 9 and a second sensor 10.
  • the first sensor 9 is used to detect the hot gas temperature of the refrigerant in the area between compressor 2 and condenser 3.
  • the second sensor 10 is in the high pressure range, which extends from the compressor 2 to the expansion valve 4, arranged and is designed as a pressure sensor.
  • the value of the detected by the second sensor 10 Pressure corresponds to the condensation pressure of the refrigerant in the condenser 3 and can be converted directly into the condensation temperature in the condenser.
  • the actual value of the controlled variable is determined in the control device 8 from the difference between the temperatures determined by the two sensors.
  • This actual value lies, for example above a predetermined target value, the expansion valve 4 of the control device 8 opened further.
  • This causes more refrigerant to flow through the Evaporator, resulting in a lower vaporization temperature of the gaseous Refrigerant in the suction gas line 11 and thus also a lower hot gas temperature of the refrigerant in the area between compressor 2 and condenser 3
  • the change in vaporization superheat temperature is significant is less than the change in hot gas temperature.
  • the target value of the difference between the hot gas temperature determined by the first sensor 9 and the condensation temperature determined via the second sensor 10 becomes dependent on the condensation temperature determined via the second sensor 10 set, preferably proportional to this.
  • the reasons for introducing such a dependency are different Amounts of heat at different condensation temperatures in the condenser 3 must be dissipated and the resulting different requirements to the capacitor.
  • the hot gas is initially in one in the condenser in the first heating zone (e.g. from 70 to 50 ° C), then in a condensation zone condenses (e.g.
  • the second sensor 10 is designed as a temperature sensor and in the flow line 13 of the Heating circuit 7 is arranged in the region of the heat exchanger outlet.
  • the second Sensor 10 recorded temperature differs from the condensation temperature only by a few degrees Kelvin and can be entered into this by means of a constant Correction factor (which essentially depends on the refrigerant used and on the Dimensioning of the heat exchanger depends) can be converted.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)
EP98104767A 1997-03-18 1998-03-17 Pompe de chaleur à compression ou machine de refroidissement à compression et sa méthode de régulation Expired - Lifetime EP0866291B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AT46797 1997-03-18
AT467/97 1997-03-18
AT46797 1997-03-18

Publications (2)

Publication Number Publication Date
EP0866291A1 true EP0866291A1 (fr) 1998-09-23
EP0866291B1 EP0866291B1 (fr) 2002-08-14

Family

ID=3491393

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98104767A Expired - Lifetime EP0866291B1 (fr) 1997-03-18 1998-03-17 Pompe de chaleur à compression ou machine de refroidissement à compression et sa méthode de régulation

Country Status (3)

Country Link
EP (1) EP0866291B1 (fr)
AT (1) ATE222344T1 (fr)
DE (1) DE59805146D1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1134518A2 (fr) * 2000-03-15 2001-09-19 Carrier Corporation Procédé de régulation d'un robinet électronique d'expansion basé sur l'étranglement du refroidisseur et sur la surchauffe de sortie
EP1148307A2 (fr) * 2000-04-19 2001-10-24 Denso Corporation Chauffe-eau avec pompe à chaleur
WO2004097308A1 (fr) * 2003-04-30 2004-11-11 Lg Electronics, Inc. Dispositif et procede de commande d'une unite exterieure
CN1329695C (zh) * 2003-05-15 2007-08-01 乐金电子(天津)电器有限公司 室外机的安全运行装置及其方法

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013004786A1 (de) 2013-03-20 2014-09-25 SKA GmbH Gesellschaft für Kältetechnik Kompressionswärmepumpe oder Kompressionskältemaschine sowie Verfahren zur Regelug derselben
DE102020122713B4 (de) 2020-08-31 2024-10-31 Andreas Bangheri Verfahren zum Betreiben einer Wärmepumpe

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0325163A1 (fr) * 1988-01-21 1989-07-26 Linde Aktiengesellschaft Procédé de fonctionnement d'une installation frigorifique et installation frigorifique pour la mise en oeuvre du procédé
US5224354A (en) * 1991-10-18 1993-07-06 Hitachi, Ltd. Control system for refrigerating apparatus
DE4303533A1 (de) 1993-02-06 1994-08-11 Stiebel Eltron Gmbh & Co Kg Verfahren zur Begrenzung der Heißgastemperatur in einem Kältemittelkreislauf und Expansionsventil
WO1996024016A1 (fr) 1995-02-03 1996-08-08 Heatcraft Inc. Appareil de reglage destine a un systeme de refrigeration de locaux
EP0762064A1 (fr) * 1995-09-08 1997-03-12 Fritz Ing. Weider Réglage d'écoulement du réfrigérant d'une pompe à chaleur et procédé

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0325163A1 (fr) * 1988-01-21 1989-07-26 Linde Aktiengesellschaft Procédé de fonctionnement d'une installation frigorifique et installation frigorifique pour la mise en oeuvre du procédé
US5224354A (en) * 1991-10-18 1993-07-06 Hitachi, Ltd. Control system for refrigerating apparatus
DE4303533A1 (de) 1993-02-06 1994-08-11 Stiebel Eltron Gmbh & Co Kg Verfahren zur Begrenzung der Heißgastemperatur in einem Kältemittelkreislauf und Expansionsventil
WO1996024016A1 (fr) 1995-02-03 1996-08-08 Heatcraft Inc. Appareil de reglage destine a un systeme de refrigeration de locaux
EP0762064A1 (fr) * 1995-09-08 1997-03-12 Fritz Ing. Weider Réglage d'écoulement du réfrigérant d'une pompe à chaleur et procédé

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1134518A2 (fr) * 2000-03-15 2001-09-19 Carrier Corporation Procédé de régulation d'un robinet électronique d'expansion basé sur l'étranglement du refroidisseur et sur la surchauffe de sortie
EP1134518A3 (fr) * 2000-03-15 2002-01-16 Carrier Corporation Procédé de régulation d'un robinet électronique d'expansion basé sur l'étranglement du refroidisseur et sur la surchauffe de sortie
EP1148307A2 (fr) * 2000-04-19 2001-10-24 Denso Corporation Chauffe-eau avec pompe à chaleur
EP1148307A3 (fr) * 2000-04-19 2002-01-16 Denso Corporation Chauffe-eau avec pompe à chaleur
US6430949B2 (en) 2000-04-19 2002-08-13 Denso Corporation Heat-pump water heater
WO2004097308A1 (fr) * 2003-04-30 2004-11-11 Lg Electronics, Inc. Dispositif et procede de commande d'une unite exterieure
US6948326B2 (en) 2003-04-30 2005-09-27 Lg Electronics Inc. Apparatus for controlling operation of outdoor unit and its method
CN1311205C (zh) * 2003-04-30 2007-04-18 Lg电子株式会社 控制室外机操作的装置及其方法
CN1329695C (zh) * 2003-05-15 2007-08-01 乐金电子(天津)电器有限公司 室外机的安全运行装置及其方法

Also Published As

Publication number Publication date
ATE222344T1 (de) 2002-08-15
DE59805146D1 (de) 2002-09-19
EP0866291B1 (fr) 2002-08-14

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