EP2196740A2 - Procédé de détermination du facteur de puissance d'une machine frigorifique - Google Patents

Procédé de détermination du facteur de puissance d'une machine frigorifique Download PDF

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Publication number
EP2196740A2
EP2196740A2 EP09014744A EP09014744A EP2196740A2 EP 2196740 A2 EP2196740 A2 EP 2196740A2 EP 09014744 A EP09014744 A EP 09014744A EP 09014744 A EP09014744 A EP 09014744A EP 2196740 A2 EP2196740 A2 EP 2196740A2
Authority
EP
European Patent Office
Prior art keywords
refrigerant
determined
temperature
compressor
performance
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
EP09014744A
Other languages
German (de)
English (en)
Other versions
EP2196740B1 (fr
EP2196740A3 (fr
Inventor
Hans-Jürgen BERSCH
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 Electric GmbH and Co OHG
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 Electric GmbH and Co OHG filed Critical Emerson Electric GmbH and Co OHG
Publication of EP2196740A2 publication Critical patent/EP2196740A2/fr
Publication of EP2196740A3 publication Critical patent/EP2196740A3/fr
Application granted granted Critical
Publication of EP2196740B1 publication Critical patent/EP2196740B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/46—Improving electric energy efficiency or saving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • 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
    • F25B49/005—Arrangement or mounting of control or safety devices of safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • 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
    • F25B2700/193—Pressures 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction 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
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction 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
    • F25B2700/2115—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
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet 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
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator

Definitions

  • the present invention relates to a method for determining the coefficient of performance of a refrigerating machine, in particular a heat pump, comprising a refrigerant having a closed circuit in which an evaporator, a compressor, a condenser and an expansion valve are arranged.
  • the coefficient of performance (COP) of a chiller is the quotient of the heating power of the chiller and the recorded electrical power of the chiller.
  • the electric power consumption of the refrigerating machine is detected by an electricity meter, while the heating power of the refrigerator is detected by a temperature and volume flow measurement on the water side of the refrigerant circuit, i. So behind the condenser, is determined.
  • the temperatures and pressures of the refrigerant are detected at different points of the circuit and used to calculate the coefficient of performance.
  • the electrical power consumption of the chiller is detected.
  • the heating power of the chiller can then be calculated.
  • the invention has for its object to provide a cost-effective method for determining the coefficient of performance of a chiller.
  • a refrigerator in particular a heat pump, comprising a refrigerant having a closed circuit in which an evaporator, a compressor, a condenser and an expansion valve are arranged, with the aid of at least three temperature sensors , which are arranged in the circuit, determined at least three temperatures of the refrigerant. From the determined refrigerant temperatures, enthalpies and pressures of the circuit are calculated, and from differences in the calculated enthalpies, both the heating power and the consumed electric power of the refrigerator are calculated. From the quotient of the calculated heating power and the calculated absorbed electrical power finally the coefficient of performance of the chiller is determined.
  • the coefficient of performance of the refrigerating machine is determined exclusively on the basis of temperature values supplied by three temperature sensors arranged in the refrigerant circuit, assuming some knowledge of the thermodynamic properties of the system, in particular of the refrigerant and of the compressor becomes.
  • a first temperature in the region of the inlet of the compressor, a second temperature in the region of the outlet of the condenser and a third temperature in the region of the outlet of the expansion valve are measured.
  • the refrigerant temperatures measured at these points of the refrigerant circuit are generally sufficient to determine the enthalpies of the circuit and ultimately to determine the coefficient of performance of the refrigerator.
  • a fourth temperature sensor additionally a fourth temperature can be determined and used to determine the coefficient of performance, wherein the fourth temperature is preferably determined in the region of the output of the compressor.
  • At least two temperatures and a pressure of the refrigerant are determined to determine the coefficient of performance of a chiller with the aid of at least two temperature sensors and at least one pressure sensor, which are arranged in the refrigerant circuit. From the determined refrigerant temperatures and the determined refrigerant pressure enthalpies of the circuit and from differences between the enthalpies the heating power and the absorbed electric power of the chiller are calculated. The coefficient of performance of the chiller is then determined from the quotient of the calculated heating power and the calculated absorbed electrical power.
  • the coefficient of performance of the chiller can be determined using a minimum number of sensors and in particular without an electricity meter and thus particularly cost.
  • the determination of the coefficient of performance takes place exclusively on the basis of the measured values supplied by the two temperature sensors and the one pressure sensor, whereby here too knowledge of the system, in particular of the thermodynamic properties of the refrigerant and of the compressor, must be assumed.
  • a first temperature in the region of the inlet of the compressor, a second temperature in the region of the outlet of the condenser and a first pressure in the region of the outlet of the evaporator is measured.
  • a third temperature can be determined and used to determine the coefficient of performance, wherein the third temperature is preferably determined in the region of the output of the compressor. Due to the additional measurement of a third temperature, it is possible to replace calculations that are required with the use of only three sensors for determining the enthalpies, in particular for determining the coolant temperature at the compressor output, by an actual measurement, whereby the determination of the coefficient of performance of the chiller easier, faster and with greater accuracy.
  • a second pressure can be determined and used to determine the coefficient of performance, wherein the second pressure is preferably determined in the region of the outlet of the condenser. Also, the measurement of the second pressure contributes to a faster and more accurate determination of the coefficient of performance of the chiller, by eliminating the need to calculate the pressure value without the direct measurement.
  • a first embodiment of a refrigerator according to the invention is shown.
  • the refrigerator includes a closed circuit 10 having a refrigerant in which an evaporator 12, a compressor 14, a condenser 16, and an expansion valve 18 are disposed.
  • a temperature sensor 28 in the region of the inlet of the compressor 14, a temperature sensor 30 in the region of the outlet of the condenser 16 and a temperature sensor 32 in the region of the outlet of the expansion valve 18 are arranged.
  • the temperature sensors 28, 30, 32 are connected to an evaluation unit 26, which may be integrated into a controller of the refrigerator.
  • Fig. 2 shows for this purpose a Log p, H - diagram of the refrigerant used in the refrigerator, wherein the pressure p of the refrigerant is plotted logarithmically as a function of enthalpy H. Also marked are the limits of saturated liquid 20 and saturated gas 22.
  • the point E in Fig. 2 indicates the state of the refrigerant after expansion by the expansion valve 18.
  • evaporation (EA) and overheating (AB) of the refrigerant take place.
  • the compressor 14 provides a compression (B-C) of the refrigerant, which is accompanied by a corresponding increase in temperature.
  • B-C compression
  • the temperature of the refrigerant may be raised from about + 10 ° C at the exit of the evaporator 12 through the compressor 14 to about + 90 ° C.
  • the condenser 16 is a liquefaction (C-D) of the refrigerant, wherein the liquefaction temperature may be, for example + 50 ° C.
  • the now liquid and only 50 ° C warm refrigerant is then expanded by the expansion valve 18 (D-E), where it cools, for example, to about 0 ° C.
  • T1 the temperature of the gaseous refrigerant at the inlet of the compressor 14, as T2, the temperature of the liquid refrigerant at the outlet of the condenser 16, as T3, the temperature of the expanded refrigerant at the outlet of the expansion valve 18 and T4 the Temperature of the gaseous refrigerant at the outlet of the compressor 14 is designated.
  • the evaporation pressure i. that is, the pressure of the gaseous refrigerant at the outlet of the evaporator 12
  • the condensing pressure i. that is, the pressure of the liquid refrigerant at the outlet of the condenser 16.
  • the enthalpy H1 at the outlet of the condenser 16 the enthalpy H2 at the inlet of the compressor 14 and the enthalpy H3 at the outlet of the compressor 14 are determined.
  • the determination of the temperatures T1, T2, T3 is carried out by measurement with the aid of the temperature sensors 28, 30 or 32.
  • the temperature values T1, T2, T3 detected by the temperature sensors 28, 30, 32 are transmitted to the evaluation unit 26.
  • the evaluation unit 26 calculates the pressure P2 using the pressure equation of the refrigerant used from the received value for the temperature T2 at the outlet of the condenser 16 and the pressure P1 from the temperature value T3 at the outlet of the expansion valve 18.
  • a pressure equation for example, the well-known Clausius-Clapeyron equation can be used.
  • the enthalpy H3, since the temperature T4 is not known, is calculated from the compressor model.
  • the electric power Qel received by the compressor 14 is not determined by an electricity meter, but calculated by a model describing the thermodynamic characteristics of the compressor 14, e.g. a 10-coefficient model.
  • the calculated values apply only to the documented operating point of the compressor 14 at either constant superheating or constant suction gas temperature, ie constant temperature T1 of the refrigerant at the compressor entrance.
  • the values In order to calculate the values of the real operating point, the values must be corrected as a function of the real compressor input temperature T1.
  • the enthalpy H3-H2 can be easily calculated from the enthalpy difference H3-H2.
  • the refrigerant temperature T4 at the compressor output is obtained from the intersection of the enthalpy line H3 with the line of the pressure P2 in the log p, H diagram of FIG Fig. 2 calculated.
  • the heating power Qh and the electric power Qel can be integrated over time to indicate the heating energy and the absorbed electric power.
  • the power consumption of ancillary equipment, such as Pumps, electronics, etc. can be incorporated into the calculation by suitable parameters.
  • Fig. 3 shows a second embodiment of a refrigerating machine according to the invention, which differs from the embodiment described above in that a connected to the evaluation unit 26 fourth temperature sensor 34 is disposed in the region of the output of the compressor 14 to determine the refrigerant temperature T4 at the compressor output.
  • the refrigerant temperature T4 at the compressor outlet need not be estimated with the aid of a compressor model, but it is measured directly.
  • the evaluation unit 26 calculates the pressure P2 using the pressure equation of the refrigerant used from the received value for the temperature T2 at the outlet of the condenser 16 and the pressure P1 from the temperature T3 at the outlet of the expansion valve 18. Subsequently, according to equations (1) to (3), the enthalpies H1, H2 and H3 are determined from the measured temperatures T1, T2, T4 and the calculated pressures P1, P2, and the coefficient of performance is determined therefrom according to equation (6).
  • a third embodiment of a refrigerating machine according to the invention is shown, which differs from that with reference to Fig. 1 described first difference in that instead of the third temperature sensor 32, a pressure sensor 36 is arranged in the region of the outlet of the evaporator 12, there to measure the pressure P1 of the refrigerant.
  • the pressure sensor 36 is connected to the evaluation unit 26 in order to transmit the measured refrigerant pressure P1 to it.
  • the pressure P1 need not be calculated from the refrigerant temperature T3 at the outlet of the expansion valve 18, but it is measured directly. Only the pressure P2 is to be calculated using the pressure equation of the refrigerant used from the temperature T2 at the outlet of the condenser 16, and the refrigerant temperature T4 at the compressor output is as based on Fig. 1 explained with the aid of a compressor model, according to the equations (1) to (3), the enthalpies H1, H2 and H3 and from this according to equation (6) the coefficient of performance of the chiller can be determined.
  • a fourth embodiment of a refrigerating machine according to the invention is shown, which differs from the in Fig. 4 3 shows that a fourth temperature sensor 34 connected to the evaluation unit 26 is arranged in the region of the outlet of the compressor 14 in order to determine the refrigerant temperature T4 at the compressor outlet.
  • the refrigerant temperature T4 at the compressor output need not be calculated by means of a compressor model in this embodiment, but it becomes similar to that in FIG Fig. 2 shown directly measured second embodiment.
  • the pressure P2 from the refrigerant temperature T2 at the outlet of the condenser 16 is also calculated here.
  • a fifth embodiment of a refrigerating machine according to the invention is shown, which differs from the in Fig. 4 3 shows that a second pressure sensor 38 connected to the evaluation unit 26 is arranged in the region of the outlet of the condenser 16 in order to determine the refrigerant pressure P2 at the condenser outlet.
  • the pressure P2 in this embodiment need not be calculated using the pressure equation of the refrigerant used from the temperature T2 at the outlet of the condenser 16, but it is measured directly. Only the refrigerant temperature T4 at the compressor output is in this embodiment as based on Fig. 1 calculated using a compressor model.
  • the enthalpies H1, H2 and H3 are then calculated from the measured temperatures T1, T2 and the measured pressures P1, P2 and the calculated temperature T4 according to equations (1) to (3), and the coefficient of performance is determined therefrom according to equation (6).
  • a sixth embodiment of a refrigerating machine according to the invention is shown, which differs from the in Fig. 6 shown fifth embodiment in that a third temperature sensor 34 connected to the evaluation unit 26 is arranged in the region of the output of the compressor 14 in order to determine the refrigerant temperature T4 at the compressor outlet. Unlike the fifth embodiment, therefore, the refrigerant temperature T4 at the compressor output need not be estimated with the aid of a compressor model in this embodiment, but it is measured directly.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fuzzy Systems (AREA)
  • Mathematical Physics (AREA)
  • Signal Processing (AREA)
  • Thermal Sciences (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP09014744.8A 2008-12-11 2009-11-26 Procédé de détermination du facteur de puissance d'une machine frigorifique Active EP2196740B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008061631A DE102008061631A1 (de) 2008-12-11 2008-12-11 Verfahren zur Bestimmung der Leistungszahl einer Kältemaschine

Publications (3)

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EP2196740A2 true EP2196740A2 (fr) 2010-06-16
EP2196740A3 EP2196740A3 (fr) 2010-09-15
EP2196740B1 EP2196740B1 (fr) 2014-10-29

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EP (1) EP2196740B1 (fr)
DE (1) DE102008061631A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107328048A (zh) * 2017-08-31 2017-11-07 广东美的制冷设备有限公司 空调器及其能效计算方法
CN109140678A (zh) * 2018-08-28 2019-01-04 四川长虹空调有限公司 变频空调系统空调数据及制冷剂参数的回归分析方法
CN110741212A (zh) * 2017-04-25 2020-01-31 艾默生零售解决方案公司 针对制冷系统的动态性能系数计算

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* Cited by examiner, † Cited by third party
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US9574810B1 (en) 2013-01-24 2017-02-21 Advantek Consulting Engineering, Inc. Optimizing energy efficiency ratio feedback control for direct expansion air-conditioners and heat pumps
US9958190B2 (en) 2013-01-24 2018-05-01 Advantek Consulting Engineering, Inc. Optimizing energy efficiency ratio feedback control for direct expansion air-conditioners and heat pumps
FR3001527B1 (fr) * 2013-01-28 2017-08-11 Schneider Electric Ind Sas Procede de diagnostic d'une machine de chauffage, ventilation et climatisation
EP3109573B1 (fr) 2015-06-24 2020-09-09 Emerson Climate Technologies GmbH Cartographie croisée de composants dans un système de réfrigération
US9915570B1 (en) 2016-08-18 2018-03-13 DCIM Solutions, LLC Method and system for managing cooling distribution
CA3049596A1 (fr) * 2018-07-27 2020-01-27 Hill Phoenix, Inc. Systeme de refrigeration co2 a commande de robinet a haute pression en fonction d`un coefficient de rendement
DE102019135437B4 (de) * 2019-12-20 2022-02-03 Hochschule Merseburg Verfahren zur indirekten Druckbestimmung in Kältekreisen
CN113175734B (zh) * 2021-04-21 2022-07-22 海信空调有限公司 计算空调器能力能效的方法、计算机存储介质和空调器
WO2023043363A1 (fr) * 2021-09-20 2023-03-23 Qvantum Industries Ab Pompe à chaleur pour chauffer ou refroidir, procédé et produit programme d'ordinateur pour celle-ci
CN115183508B (zh) * 2022-07-07 2023-11-17 百尔制冷(无锡)有限公司 一种新型跨临界二氧化碳排气压力控制方法及其控制系统
DE102022132680A1 (de) 2022-12-08 2024-06-13 Bayerische Motoren Werke Aktiengesellschaft Verfahren zum Ermitteln einer Masse eines Kältemittels eines Fahrzeugs, Temperiereinrichtung für ein Fahrzeug sowie Fahrzeug, insbesondere Kraftfahrzeug

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0100210A2 (fr) * 1982-07-26 1984-02-08 Honeywell Inc. Dispositif de mesure de coéfficient de performance
US5735134A (en) * 1996-05-30 1998-04-07 Massachusetts Institute Of Technology Set point optimization in vapor compression cycles
US20030019221A1 (en) * 2001-05-11 2003-01-30 Rossi Todd M. Estimating operating parameters of vapor compression cycle equipment
JP2004176938A (ja) * 2002-11-25 2004-06-24 Tgk Co Ltd 冷凍サイクルの制御方法
JP2007278618A (ja) * 2006-04-07 2007-10-25 Daikin Ind Ltd 冷凍装置
EP1914481A2 (fr) * 2004-08-11 2008-04-23 Lawrence Kates Procédé et appareil pour la surveillance de systèmes à cycle réfrigérant

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7051542B2 (en) * 2003-12-17 2006-05-30 Carrier Corporation Transcritical vapor compression optimization through maximization of heating capacity
EP1950511A1 (fr) * 2007-01-26 2008-07-30 Viessmann Werke GmbH & Co. KG Pompe à chaleur

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0100210A2 (fr) * 1982-07-26 1984-02-08 Honeywell Inc. Dispositif de mesure de coéfficient de performance
US5735134A (en) * 1996-05-30 1998-04-07 Massachusetts Institute Of Technology Set point optimization in vapor compression cycles
US20030019221A1 (en) * 2001-05-11 2003-01-30 Rossi Todd M. Estimating operating parameters of vapor compression cycle equipment
JP2004176938A (ja) * 2002-11-25 2004-06-24 Tgk Co Ltd 冷凍サイクルの制御方法
EP1914481A2 (fr) * 2004-08-11 2008-04-23 Lawrence Kates Procédé et appareil pour la surveillance de systèmes à cycle réfrigérant
JP2007278618A (ja) * 2006-04-07 2007-10-25 Daikin Ind Ltd 冷凍装置

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110741212A (zh) * 2017-04-25 2020-01-31 艾默生零售解决方案公司 针对制冷系统的动态性能系数计算
CN110741212B (zh) * 2017-04-25 2021-09-07 艾默生零售解决方案公司 针对制冷系统的动态性能系数计算
CN107328048A (zh) * 2017-08-31 2017-11-07 广东美的制冷设备有限公司 空调器及其能效计算方法
CN109140678A (zh) * 2018-08-28 2019-01-04 四川长虹空调有限公司 变频空调系统空调数据及制冷剂参数的回归分析方法
CN109140678B (zh) * 2018-08-28 2020-11-10 四川长虹空调有限公司 变频空调系统空调数据及制冷剂参数的回归分析方法

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US8775123B2 (en) 2014-07-08
US20100153057A1 (en) 2010-06-17
EP2196740B1 (fr) 2014-10-29
DE102008061631A1 (de) 2010-06-17
EP2196740A3 (fr) 2010-09-15

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