EP2012068A1 - Verfahren zur Regelung der Ausgabetemperatur einer Betriebsflüssigkeit im Auslass einer Kühlmaschine - Google Patents

Verfahren zur Regelung der Ausgabetemperatur einer Betriebsflüssigkeit im Auslass einer Kühlmaschine Download PDF

Info

Publication number
EP2012068A1
EP2012068A1 EP07425349A EP07425349A EP2012068A1 EP 2012068 A1 EP2012068 A1 EP 2012068A1 EP 07425349 A EP07425349 A EP 07425349A EP 07425349 A EP07425349 A EP 07425349A EP 2012068 A1 EP2012068 A1 EP 2012068A1
Authority
EP
European Patent Office
Prior art keywords
set point
tset
load
value
refrigerating machine
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.)
Withdrawn
Application number
EP07425349A
Other languages
English (en)
French (fr)
Other versions
EP2012068A8 (de
Inventor
Alessandro Zen
Luca Cecchinato
Alessandro Beghi
Cristian Bodo
Alessandro Scodellaro
Michele Albieri
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.)
Rhoss SpA
Original Assignee
Rhoss SpA
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 Rhoss SpA filed Critical Rhoss SpA
Priority to EP07425349A priority Critical patent/EP2012068A1/de
Publication of EP2012068A1 publication Critical patent/EP2012068A1/de
Publication of EP2012068A8 publication Critical patent/EP2012068A8/de
Withdrawn legal-status Critical Current

Links

Images

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
    • F25B49/022—Compressor control arrangements
    • 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
    • F24F11/62—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
    • F24F11/63—Electronic processing
    • F24F11/65—Electronic processing for selecting an operating mode
    • 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
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • 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
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
    • 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • 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
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21172—Temperatures of an evaporator of the fluid cooled by the evaporator at the inlet
    • 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
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21173—Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet

Definitions

  • the present invention concerns a method for regulating the delivery temperature of a service fluid in output from a refrigerating machine.
  • the present invention finds useful, but not exclusive, application in the regulation of the delivery temperature of a service fluid in output from a water chiller for centralized air-conditioning systems, to which the following description shall make explicit reference without, however, any loss of generality.
  • a centralized air-conditioning system for the control of the ambient temperature in a building comprises a plurality of fan coils, which are opportunely distributed inside the building and connected with each other via a hydraulic circuit, and a centralized refrigerating machine suited to cool a service fluid, and in particular a coolant liquid substantially composed of water, and to convey this service fluid to the various fan coils via said hydraulic circuit.
  • This refrigerating machine normally indicated by the term “chiller”, comprises an internal circuit in which a working fluid consisting of a refrigerant circulates, a heat exchanger through which the internal circuit passes and that is connected to the hydraulic circuit of the air-conditioning system in correspondence to the refrigerating machine's inlet and outlet for heat exchange between the working fluid and the service fluid, and one or more compressors for implementing a refrigeration cycle on the working fluid through compression of the working fluid itself.
  • Electronic control systems are also known of for controlling the switching on and off of the compressors such that the temperature of the service fluid in input to or output from the refrigerating machine, namely the return temperature or, respectively, the delivery temperature of the service fluid, reaches a predetermined set point value.
  • control systems essentially implement a proportional type of control logic in which the switching on and off of the compressors is carried out on the basis of a direct comparison between a measurement of the return or delivery temperature of the service fluid and a pair of temperature thresholds.
  • control systems exhibit intrinsic limits due to the time constraints between the moments of switching the compressors on and off for the purpose of extending their life. In actual fact, these constraints limit the differential between the temperature thresholds to a minimum value, below which the compressors would operate in technically prohibitive running conditions that could damage them. More in general, on the one hand these time constraints prevent the mentioned control systems from achieving a good level of precision in regulating the temperature of the service fluid and, on the other, from maximizing the energy efficiency of the air-conditioning system.
  • control carried out on the basis of the return temperature is not very precise because a different quantity is controlled from that which is effectively involved by the heat exchange in the fan coils.
  • the object of the present invention is to provide a method for regulating the delivery temperature of a service fluid in output from a refrigerating machine for an air-conditioning system and to create a control device for a refrigerating machine embodying this method, which permit regulation of the delivery temperature in a precise manner and maximization of the system's energy efficiency and, at the same time, are of straightforward and economic embodiment.
  • a method for regulating the delivery temperature of a service fluid in output from a refrigerating machine, a control device for a refrigerating machine and a refrigerating machine in accordance with the attached claims are provided.
  • reference numeral 1 generally designates a block diagram showing the principles of an air-conditioning system comprising a plurality of fan coils 2 opportunely distributed inside a building (not shown) for which it is wished to control the ambient temperature, and a refrigerating machine 3 suited to cool a service fluid 5, in particular a coolant liquid substantially composed of water, and make it circulate through a hydraulic circuit 4 that connects the fan coils 2 to the refrigerating machine 3 itself.
  • the refrigerating machine 3 comprises an internal circuit 6, in which a working fluid 7 consisting of a refrigerant circulates, and an output circuit 8, which connects to the hydraulic circuit 4 of the system 1 in correspondence to an inlet 9 and an outlet 10 of the refrigerating machine 3.
  • a series of devices are arranged along the internal circuit 6 to implement a refrigeration cycle on the working fluid 7, and in particular, a first heat exchanger 11, through which the internal circuit 6 and the output circuit 8 pass and which functions as an evaporator to make the working fluid 7 evaporate at low pressure by absorbing heat from the service fluid 5; a compressor 12, preferably of the scroll type, to carry out adiabatic compression on the working fluid 7 in the vapour state; a second heat exchanger 13 functioning as a condenser, that is to make the working fluid 7 condense so as to release the previously absorbed heat to the outside; and an expansion valve 14 to cool the working fluid 7 and make it partially evaporate so that it is ready for another cycle.
  • a first heat exchanger 11 through which the internal circuit 6 and the output circuit 8 pass and which functions as an evaporator to make the working fluid 7 evaporate at low pressure by absorbing heat from the service fluid 5
  • a compressor 12 preferably of the scroll type, to carry out adiabatic compression on the working fluid 7 in the vapour state
  • the hydraulic circuit 4 of the system 1 and the output circuit 8 of the refrigerating machine 3 form a so-called hydronic circuit 15, including a delivery branch 16, along which the service fluid 5 circulates in a direction D from the heat exchanger 11 to the fan coils 2, and a return branch 17, along which the service fluid 5 returns to the heat exchanger 11. Circulation of the service fluid 5 in direction D is guaranteed by a pump 18 placed along the return branch 17.
  • the refrigerating machine 3 is equipped with a storage tank 19 placed along the delivery branch 16 at a short distance from the heat exchanger 11 to produce thermal inertia in the hydronic circuit 15, which slows the dynamics of the system 1 so as to avoid undesired oscillation phenomena in the regulator valves (not shown) of the fan coils 2.
  • the presence of the storage tank 19 is optional.
  • the refrigerating machine 3 comprises a control device 20 to control the switching on and off of the compressor 12 based on the delivery temperature TLDV of the service fluid 5.
  • control device 20 comprises a first temperature sensor 21 placed along the delivery branch 16 at the outlet of the storage tank 19, or rather at the outlet 10 of the refrigerating machine 3, to measure the delivery temperature TDLV of the service fluid 5, a second temperature sensor 22 placed along the return branch 17 in correspondence to the inlet 9 of the refrigerating machine 3 to measure the return temperature TRET of the service fluid 5, a keypad 23 to accept commands given by a user, and an electronic control unit 24 connected to the sensors 21 and 22, the keypad 23 and the compressor 12.
  • the electronic control unit 24 is suited to control the switching on and off of the compressor 12 based on a comparison between a measurement of the delivery temperature TDLV and a pair of delivery temperature thresholds such that the delivery temperature TDLV converges to a delivery temperature set point TSET between the two delivery temperature thresholds.
  • the electronic control unit 24 is configured to implement the method for regulating the delivery temperature TDLV of the service fluid 5 in accordance with the present invention, which method is described below for the case in which the service fluid 5 is chilled to cool the environments where the fan coils 2 are placed.
  • the underlying principle of this method is to adapt the set point TSET to an estimate of the cooling load produced by the environment to be cooled and surrendered to the hydronic circuit 15.
  • the set point TSET is increased when the cooling load diminishes. Indeed, the more the cooling load drops, the less the heat exchange between the environment and the fan coils 2, and less is the need to cool the service fluid 5. Since the coefficient of performance (COP) of a refrigerating machine 3 increases as the evaporation temperature in the heat exchanger rises, it follows that the rise in the set point TSET as the cooling load drops results in an increase in the overall efficiency of the system 1.
  • COP coefficient of performance
  • the estimated cooling load is defined in terms of fraction of load FL, that is as the ratio between the power that the refrigerating machine 3 must deliver to cool the environment and the maximum refrigeration power that the refrigerating machine 3 can deliver under given nominal conditions.
  • Switching on and off of the compressor 12 takes place respecting precise time constraints between successive switch-ons and/or switch-offs in order to safeguard the integrity of the compressor 12, or rather respecting a minimum time ⁇ t_ON_min between switch-on and switch-off, a minimum time ⁇ t_OFF_min between switch-off and switch-on and a minimum time ⁇ t_ON_ON_min between two successive switch-ons.
  • Figure 2 illustrates the trends of the theoretical periods ⁇ t_ON and ⁇ t_OFF as the fraction of load FL changes for the following time constraints:
  • the asymptotic trends at the ends of the change interval in the fraction of load FL mean that the compressor 12 remains switched on or off for very long periods corresponding to fractions of load FL close to 1 or 0 respectively.
  • FIG. 3 shows a flow chart that describes to steps followed by the method for regulating the delivery temperature TDLV of the service fluid 5 in accordance with the present invention.
  • the method provides a variables initialization phase (block 100), in which:
  • the delivery temperature TDLV and the return temperature TRET are measured via the respective sensors 21 and 22 (block 101).
  • a measurement of the delivery temperature TDLV is compared with the previously mentioned pair of delivery temperature thresholds, in particular with a lower threshold TLOW lesser than the set point TSET (block 102) and with an upper threshold THIG greater than the set point TSET (block 103). If the delivery temperature TDLV is less than or equal to the lower threshold TLOW, then the compressor 12 is switched off (block 104). Instead, if the delivery temperature TDLV is greater or equal to the upper threshold THIG, then the compressor 12 is switched on (block 105).
  • the values of the lower TLOW and upper THIG thresholds are linked to the value of the set point TSET. Hence, for an adjustment to the set point TSET there is a corresponding adjustment of the same sign to the thresholds TLOW and THIG.
  • the lower TLOW and upper THIG thresholds are kept symmetrical with respect to the set point TSET.
  • switch-off time t_OFF (block 106) and switch-on time t_ON (block 107).
  • a counter N_ON of the number of switch-ons is incremented (block 108).
  • the switch-on event starts the on-off cycle of the compressor 12 and a series of calculations are triggered in correspondence to this event that result in an estimate of the cooling load and the adjustment of the set point TSET and the thresholds TLOW and THIG to the estimated cooling load.
  • a real operational period ⁇ t_ON_real, a real stoppage period ⁇ t_OFF_real and a real cycle period ⁇ t_TOT_real are calculated for the compressor 12 (block 109).
  • the cooling load is estimated in function of the measurements of the delivery TDLV and return TRET temperatures and is provided, as previously disclosed, in terms of an estimated fraction of load FL (block 110).
  • the set point TSET is adjusted by adapting it the estimated fraction of load FL (block 112).
  • the adjustment of the set point TSET to the fraction of load FL is only enabled after having checked that the number of switch-ons N_ON has reached a minimum number of switch-ons N_ON_min, preferably equal to 4 (block 113).
  • the purpose of this check is to allow adequate stabilization of the estimation process for the fraction of load FL, as the estimation process is perturbed by adjustment of the set point TSET.
  • a countdown is activated starting from this wait time value ⁇ _WAIT (block 114). Adjustment of the set point TSET is only re-enabled when the countdown expires (block 115). This expedient also has the purpose of allowing sufficient stabilization of the fraction of load FL estimation process.
  • Figure 4 shows a portion of the flow chart regarding block 110 of Figure 3 that shows the sub-phases concerning the calculation of the fraction of load FL of the hydronic circuit 15.
  • ⁇ TQ is the temperature difference between the inlet and outlet of the group of fan coils 2 produced by the thermal power that the environment supplies to the system 1
  • the estimated temperature difference ⁇ TQ undergoes low-pass filtering (block 203), for example, via a first order Chebyshev filter having a cutoff angular frequency of 0.003 rad/s and peak band-pass ripple of 3dB, and is successively processed to obtain a mean value ⁇ TQmean for the measured cycle time ⁇ tCYCLE (block 204).
  • Figure 5 shows a portion of a flow chart that describes the phase of estimating the installation parameter k, indicated by block 200 in Figure 4 , in greater detail.
  • the installation parameter k is estimated on the basis of a formula obtained from an energy balance equation in terms of temperature similar to equation (4) and expressed as a function of temperatures for which there are measurements, or rather of the delivery temperature TDLV and the return temperature TRET.
  • the time shift ⁇ is preferably equal to 5 seconds.
  • Estimation of the installation parameter k in the above-described manner corresponds to an estimate of the capacity and mass flow characteristics of the hydronic circuit 15, which allows the estimate of the fraction of load FL to be automatically tuned to the characteristics of the system 1. This operation is without doubt necessary for the first switch-on of the refrigerating machine 3 after it has been connected to a new system 1, but also during normal operation of the same system 1 to identify load variations due to the deactivation of one or more fan coils 2.
  • Figure 6 shows a portion of flow chart that describes the adjustment phase of the set point TSET, indicated by block 112 in Figure 3 , in greater detail.
  • This phase provides for the calculation of a new set point TSET value via a formula that expresses the temperature of the set point TSET as a function of the estimated fraction of load FL (block 400) :
  • TSET ⁇ TSET max if FL ⁇ FLI TSET min + TSET max - TSET min ⁇ 1 - FL 1 - FLI otherwise
  • TSETmin is the minimum value of the set point TSET corresponding to the maximum fraction of load equal to 1
  • TSETmax is the maximum value of the set point TSET corresponding to the null fraction of load
  • FLI is a value of the fraction of load that separates the relationship between a first segment in which the set point TSET is constant and a second segment in which the set point TSET decreases in a linear manner as the fraction of load FL changes.
  • Formula (10) is considered for three different sets of values of the parameters TSETmin, TSETmax and FLI, listed in the table shown in Figure 8a.
  • Figure 8b shows the three different versions of formula (10) via three respective curves traced in the TSET - FLI plane and indicated as C1, C2 and C3.
  • the three sets of parameters TSETmin, TSETmax and FLI, and therefore the three curves C1, C2 and C3, correspond to three different, user-selectable operating modes of the refrigerating machine 3.
  • a default operating mode corresponds to curve C1 that ensures the best compromise between energy efficiency of the refrigerating machine 3 and regulating precision of the delivery temperature TDLV, as the new value of the set point TSET can vary between the minimum value TSETmin and the maximum value TSETmax for a wide range of values for the fraction of load FL, i.e. between 0.3 and 1.
  • an operating mode corresponds to curve C2 that ensures the best energy efficiency, as the new value of the set point TSET is equal to a high value (TSETmax) over a wide range of values of fractions of load FL, namely between 0 and 0.6, in this way maximizing the coefficient of performance of the refrigerating machine 3.
  • an operating mode corresponds to curve C3 that ensures the best humidity control, as the new value of the set point TSET is different for each value of fraction of load FL and can assume a maximum value TSETmax that is lower than that of the other curves C1 and C2.
  • a set point step ⁇ TSET is determined by calculating the difference between the value just calculated and the previous value of the set point TSET and upwardly limiting the step ⁇ TSET to a maximum value ⁇ TSETmax preferably equal to 4 °C (block 401), while the set point TSET is updated by immediately applying the set point step ⁇ TSET to the previous set point TSET value (block 402).
  • the diagram of the principle of the refrigerating machine 3 shown in Figure 1 can also generically describe a machine suited to heat the service fluid 5 for the purpose of heating the environments in which the fan coils 2 are placed, for example a refrigerating machine 3 of the type operating as a heat pump.
  • the compressor 12 is configured so as to perform the refrigeration cycle in the opposite sense to that previously described, or rather in a manner for which the heat exchanger 11 functions as a condenser to transfer heat from the working fluid 7 to the service fluid 5 and the heat exchanger 13 functions as an evaporator.
  • the method for regulating the delivery temperature TDLV of the service fluid 5 in accordance with the present invention is therefore also applicable in the case in which the refrigerating machine 3 is suited to heat the service fluid 5, it being sufficient to simply invert the mechanism of some of the described phases and change the value of some parameters, and in particular:
  • the main advantage of the above-described method for regulating the delivery temperature TDLV with respect to known art is to increase the overall efficiency of the system 1, whilst still maintaining good precision in regulating the delivery temperature TDLV itself.
  • the adaptation of the set point TSET to the cooling/heating load of the hydronic circuit 15 allows the refrigerating machine 3 to promptly respond to variations in the cooling/heating load of the environment for which it is wished to control the temperature, so that the evaporation temperature can increase in the case where the machine is configured to cool the service fluid 5, or so that the condensation temperature can drop in the case where the machine is configured to heat the service fluid 5, thus maximizing the coefficient of performance in all working conditions.
  • Another advantage is to allow the automatic adaptation of the refrigerating machine 3 to the type of system 1 in which it is installed and to rapidly identify cooling/heating load variations due to the deactivation of one or more fan coils 2, thanks to the estimation operation of the installation parameter k that expresses the capacity and flow characteristics of the system 1.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Signal Processing (AREA)
  • Thermal Sciences (AREA)
  • Fuzzy Systems (AREA)
  • Mathematical Physics (AREA)
  • Air Conditioning Control Device (AREA)
EP07425349A 2007-06-04 2007-06-04 Verfahren zur Regelung der Ausgabetemperatur einer Betriebsflüssigkeit im Auslass einer Kühlmaschine Withdrawn EP2012068A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP07425349A EP2012068A1 (de) 2007-06-04 2007-06-04 Verfahren zur Regelung der Ausgabetemperatur einer Betriebsflüssigkeit im Auslass einer Kühlmaschine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP07425349A EP2012068A1 (de) 2007-06-04 2007-06-04 Verfahren zur Regelung der Ausgabetemperatur einer Betriebsflüssigkeit im Auslass einer Kühlmaschine

Publications (2)

Publication Number Publication Date
EP2012068A1 true EP2012068A1 (de) 2009-01-07
EP2012068A8 EP2012068A8 (de) 2009-07-22

Family

ID=38835073

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07425349A Withdrawn EP2012068A1 (de) 2007-06-04 2007-06-04 Verfahren zur Regelung der Ausgabetemperatur einer Betriebsflüssigkeit im Auslass einer Kühlmaschine

Country Status (1)

Country Link
EP (1) EP2012068A1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014165497A1 (en) * 2013-04-01 2014-10-09 Carrier Corporation Air conditioning system and method for controlling air conditioning system
JP2020012599A (ja) * 2018-07-19 2020-01-23 株式会社コロナ ヒートポンプ式冷水冷房装置
DE102020118762A1 (de) 2020-07-16 2022-01-20 Vaillant Gmbh Massenstromschätzung in linksdrehenden Kreisprozessen

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5610643A (en) * 1979-07-06 1981-02-03 Mitsubishi Electric Corp Water cooler
JPS57150746A (en) * 1981-03-13 1982-09-17 Saginomiya Johnson Control Kk Control system for space cooling apparatus
JPS59107130A (ja) * 1982-12-08 1984-06-21 Hitachi Ltd 冷凍機の運転装置
JPS6066039A (ja) * 1983-09-20 1985-04-16 Sanyo Electric Co Ltd 空気調和機の制御方法
JPS63163725A (ja) * 1986-12-26 1988-07-07 Mitsubishi Electric Corp 空気調和装置
GB2269684A (en) * 1992-07-23 1994-02-16 Hitachi Ltd Refrigerator compressor output control
JP2000179917A (ja) * 1998-12-09 2000-06-30 Sanyo Electric Co Ltd 空調装置の運転方法
JP2002022337A (ja) * 2000-07-13 2002-01-23 Smc Corp 冷却装置の液温制御装置
JP2003222378A (ja) * 2002-01-31 2003-08-08 Toyo Biru Kanri Kk ビル空調システム
JP2003336913A (ja) * 2002-05-22 2003-11-28 Daikin Ind Ltd 冷凍装置の制御方法および冷凍装置
JP2004069134A (ja) * 2002-08-05 2004-03-04 Toshiba Corp 空調システム
JP2005257221A (ja) * 2004-03-15 2005-09-22 Toyo Netsu Kogyo Kk 冷凍機の冷却水制御方法
JP2005282940A (ja) * 2004-03-29 2005-10-13 Orion Mach Co Ltd 冷却装置の動作制御方法

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5610643A (en) * 1979-07-06 1981-02-03 Mitsubishi Electric Corp Water cooler
JPS57150746A (en) * 1981-03-13 1982-09-17 Saginomiya Johnson Control Kk Control system for space cooling apparatus
JPS59107130A (ja) * 1982-12-08 1984-06-21 Hitachi Ltd 冷凍機の運転装置
JPS6066039A (ja) * 1983-09-20 1985-04-16 Sanyo Electric Co Ltd 空気調和機の制御方法
JPS63163725A (ja) * 1986-12-26 1988-07-07 Mitsubishi Electric Corp 空気調和装置
GB2269684A (en) * 1992-07-23 1994-02-16 Hitachi Ltd Refrigerator compressor output control
JP2000179917A (ja) * 1998-12-09 2000-06-30 Sanyo Electric Co Ltd 空調装置の運転方法
JP2002022337A (ja) * 2000-07-13 2002-01-23 Smc Corp 冷却装置の液温制御装置
JP2003222378A (ja) * 2002-01-31 2003-08-08 Toyo Biru Kanri Kk ビル空調システム
JP2003336913A (ja) * 2002-05-22 2003-11-28 Daikin Ind Ltd 冷凍装置の制御方法および冷凍装置
JP2004069134A (ja) * 2002-08-05 2004-03-04 Toshiba Corp 空調システム
JP2005257221A (ja) * 2004-03-15 2005-09-22 Toyo Netsu Kogyo Kk 冷凍機の冷却水制御方法
JP2005282940A (ja) * 2004-03-29 2005-10-13 Orion Mach Co Ltd 冷却装置の動作制御方法

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014165497A1 (en) * 2013-04-01 2014-10-09 Carrier Corporation Air conditioning system and method for controlling air conditioning system
US10215427B2 (en) 2013-04-01 2019-02-26 Carrier Corporation Air conditioning system and method for controlling air conditioning system
JP2020012599A (ja) * 2018-07-19 2020-01-23 株式会社コロナ ヒートポンプ式冷水冷房装置
DE102020118762A1 (de) 2020-07-16 2022-01-20 Vaillant Gmbh Massenstromschätzung in linksdrehenden Kreisprozessen

Also Published As

Publication number Publication date
EP2012068A8 (de) 2009-07-22

Similar Documents

Publication Publication Date Title
EP2588818B1 (de) Verfahren für den betrieb eines dampfkompressionssystems mit einem unterkühlungswert
EP3267127B1 (de) Steuerungsvorrichtung und -verfahren für kältekreislaufvorrichtung
US9810472B2 (en) Synchronous temperature rate control for refrigeration with reduced energy consumption
US12146695B2 (en) Refrigeration appliance with compartment which can be used in a variable manner
US20130305756A1 (en) Synchronous temperature rate control and apparatus for refrigeration with reduced energy consumption
US10107531B2 (en) Method for controlling a chiller system
WO2014113397A1 (en) Air cooled chiller with heat recovery
WO2013088590A1 (ja) 室外機及び空気調和装置
JP6545252B2 (ja) 冷凍サイクル装置
KR20130086225A (ko) 열매체 유량 추정 장치, 열원기 및 열매체 유량 추정 방법
US20100023166A1 (en) Free-cooling limitation control for air conditioning systems
WO2014163831A1 (en) Dual evaporator refrigerator appliance and method of operating the same
EP2000754B1 (de) Verfahren zur Schätzung der Wärmebelastung einer Leitung für eine Betriebsflüssigkeit am Auslass einer Kühlmaschine
JP2009522533A (ja) フラッシュタンクの冷媒制御
EP2012068A1 (de) Verfahren zur Regelung der Ausgabetemperatur einer Betriebsflüssigkeit im Auslass einer Kühlmaschine
EP2012069A1 (de) Verfahren zur Regelung der Ausgabetemperatur einer Betriebsflüssigkeit im Auslass einer Kühlmaschine
CN116576600A (zh) 一种制冷系统间室温度快速稳定控制方法
WO2016066298A1 (en) A method for estimating thermal capacity of foodstuff
WO2019058542A1 (ja) 冷凍装置
EP3249323B1 (de) Verfahren und vorrichtung für die regelung der überhitzung von kompressions-kältekreisläufen mit einem rekuperator
RU2368850C2 (ru) Устройство управления холодильного контура с внутренним теплообменником
Poort et al. Applications and control of air conditioning systems using rapid cycling to modulate capacity
US20220136751A1 (en) Refrigeration cycle apparatus
JP2755037B2 (ja) 冷凍装置
EP2000758B1 (de) Steuervorrichtung für ein Kühlgerät

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK RS

17P Request for examination filed

Effective date: 20090706

AKX Designation fees paid

Designated state(s): DE ES FR GB IT

17Q First examination report despatched

Effective date: 20090814

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20170412

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20170823