EP1806548A1 - Klimaanlage, durch die ein superkritisches Fluid fliesst - Google Patents

Klimaanlage, durch die ein superkritisches Fluid fliesst Download PDF

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Publication number
EP1806548A1
EP1806548A1 EP07100075A EP07100075A EP1806548A1 EP 1806548 A1 EP1806548 A1 EP 1806548A1 EP 07100075 A EP07100075 A EP 07100075A EP 07100075 A EP07100075 A EP 07100075A EP 1806548 A1 EP1806548 A1 EP 1806548A1
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EP
European Patent Office
Prior art keywords
control signal
compressor
installation according
value
control
Prior art date
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Granted
Application number
EP07100075A
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English (en)
French (fr)
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EP1806548B1 (de
Inventor
Jing Ming Liu
Mohamed Yahia
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Valeo Systemes Thermiques SAS
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Valeo Systemes Thermiques SAS
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Publication of EP1806548A1 publication Critical patent/EP1806548A1/de
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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
    • F25B49/022—Compressor 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
    • 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
    • F25B2600/027—Compressor control by controlling pressure
    • F25B2600/0271—Compressor control by controlling pressure the discharge pressure
    • 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
    • F25B2700/1931—Discharge 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
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser

Definitions

  • the invention relates to air conditioning installations traversed by a supercritical fluid, especially for a motor vehicle.
  • a supercritical fluid for example carbon dioxide (R744) is a high pressure refrigerant.
  • R744 carbon dioxide
  • the use of these refrigerants has developed in the air conditioning systems of vehicles to limit the harmful effects on the environment of fluorinated compounds, conventionally used as a refrigerant.
  • An air-conditioning installation traversed by such a fluid comprises a fluid circuit mainly equipped with a compressor, a gas cooler, an expansion device, and an evaporator.
  • the installation is also equipped with an air conditioning regulator whose role is to control the operation of various components of the air conditioning circuit to provide a cooling capacity meeting the cold demands of users.
  • the air conditioning regulator can control the temperature of the air blown out of the evaporator.
  • the air conditioning regulator also controls the high pressure in order to adjust the opening opening of the expansion device so as to reach the cooling capacity required by the user.
  • the air conditioning regulator of existing embodiments generally fixes the opening of the expansion device without taking into account the actual operating conditions.
  • the regulator when the air conditioning circuit is subjected to a very high thermal load, the regulator imposes a large opening of the expansion device, and therefore a high supercritical refrigerant flow rate, during the start-up phase of the air conditioning.
  • the regulator if it imposes a weak opening of the expansion device, during the start-up phase, this can generate pressure peaks leading to a stop of the compressor and therefore to the shutdown of the air conditioning so that the thermal comfort of the passenger is not reached.
  • the patent application FR 2,856,782 has proposed an air conditioning system, equipped with an expansion device, electronic expansion valve type, in which the initial opening degree of the regulator, at the start of the air conditioning, is calculated, from an estimate of the initial temperature fluid at the entrance of the pressure reducer, the initial pressure of the fluid at the outlet of the expander, and the initial flow rate of the fluid in the expander, and an estimation of the pressure of the fluid at the inlet of the expander which maximizes the coefficient of performance.
  • the initialization of the opening of the electronic expander at the start of the air conditioning is then adapted to the actual conditions of operation of the air conditioning and avoids an overpressure output of the regulator.
  • the invention improves the situation by proposing an air conditioning installation, in particular for a motor vehicle, comprising a refrigerant circuit traversed by a supercritical fluid, said circuit comprising a compressor provided with a control valve whose degree of The opening varies according to the intensity of a control signal, a gas cooler, an expansion device and an evaporator.
  • the invention provides a regulation module able to control the control signal of the compressor valve during the start-up phase of the air conditioning so as to maintain the compressor discharge pressure substantially below the compressor cut-off pressure.
  • the invention also proposes a method of regulating an air conditioning circuit traversed by a supercritical fluid, particularly for a motor vehicle, comprising a compressor provided with a control valve whose degree of opening varies according to the intensity of a control signal.
  • the invention provides control of the control signal of the compressor valve during the start-up phase of the air conditioning so as to maintain the compressor discharge pressure substantially below the compressor cut-off pressure.
  • Figure 1 shows a diagram of an air conditioning circuit 10 to be integrated with a motor vehicle.
  • the air conditioning circuit is flown by a high pressure refrigerant, including carbon dioxide R744.
  • the circuit comprises an externally controlled compressor 14 provided with a variable aperture control valve 140 as a function of a control signal.
  • the compressor is adapted to receive the fluid in the gaseous state and to compress it.
  • the circuit is furthermore equipped with a gas cooler 11 which cools the gas compressed by the compressor, at a substantially constant pressure, with an internal heat exchanger 9, an expansion device 12, in particular a mechanical expansion device. which lowers the pressure of the fluid from the internal exchanger 9, and an evaporator 13 which moves the fluid from the liquid state to the gaseous state, at a substantially constant pressure, to produce a flow of air conditioning sent to the passenger compartment of the vehicle.
  • the gas cooler 11 receives a stream of air 16 which under certain operating conditions is set in motion by a motor-fan unit 15, to evacuate the heat taken from the refrigerant.
  • the evaporator 13 receives an air flow 18 from a blower 20 and produces a flow of conditioned air sent to the cabin.
  • the internal heat exchanger 9 allows a heat exchange between the portion of the fluid flowing from the gas cooler 11 to the expander 12 and the portion of the fluid flowing from the evaporator 13 to the compressor 14.
  • the expansion device is in particular of the mechanical type.
  • Figure 2 is a diagram showing an air conditioning system according to the invention, intended to equip a motor vehicle.
  • the installation is provided with the air conditioning circuit 10 described with reference to FIG.
  • the installation is furthermore equipped with a regulation module or an air-conditioning computer 40 comprising an electronic card 43, a cockpit regulator 41 and an air conditioning loop regulator 42.
  • the cockpit regulator 41 sets the instruction of the evaporation temperature Te cons of the regulator 42.
  • the control signal of the compressor when the cockpit regulator 41 supplies an evaporation temperature setpoint to the regulator of the air conditioning loop 42, the control signal of the compressor, during the start-up phase, is calculated according to a regulation law that uses the difference between the measurement of the evaporator temperature of the compressor and the setpoint of the evaporator temperature of the compressor.
  • the measurement of the evaporation temperature can be provided by a temperature probe 130 placed behind the evaporator 13, in its overheating zone, or in the flow of air passing through the evaporator.
  • the evaporating temperature setpoint represents the target temperature requested in the passenger compartment by a passenger of the vehicle.
  • This regulation law is conventionally used in all the operating cycles of the compressor.
  • the difference between the measurement of the evaporator temperature of the compressor and the set point of the evaporation temperature is very important. Therefore, the control signal imposed on the compressor generates a large opening of the compressor control valve.
  • the expansion device is of mechanical type, this results in a very high discharge pressure at the compressor outlet, which may have pressure peaks. These pressure peaks can cause a stop of the air conditioning by setting high pressure cutoff of the compressor.
  • the Applicant proposes to regulate the control signal of the compressor.
  • the Applicant proposes a climate control module during the start-up phase of the air conditioning, suitable for limiting the pressure peaks and the compressor stops.
  • the regulation module 40 is adapted to control the control signal of the compressor valve during the starting phase of the air conditioning so as to maintain the compressor discharge pressure substantially below the compressor cut-off pressure.
  • the principle of regulation proposed here is based on management of the start-up phase of the air conditioning by means of a control of the discharge pressure or high pressure of the compressor and a progressive regulation of the control signal of the compressor, depending operating parameters of the air conditioning loop.
  • the regulation module implements the regulation of the air conditioning during the start-up phase according to a chosen period, for example of 1 second.
  • the regulation module 40 calculates a current value of the PWM control signal (k), at a given time, and compares this value with an upper threshold of the PWM control signal sup and a lower threshold PWM control signal inf . The control module then adjusts the calculated value of the control signal if it exceeds the aforementioned thresholds.
  • the regulator module further acts on a magnitude related to the PWM control signal to control the rate of change of the signal itself and prevent a sudden change that could generate a peak pressure.
  • the magnitude associated with the control signal is the upper limit of the PWM control signal greater than the PWM control signal must not exceed.
  • the quantity linked to the control signal is the setpoint of evaporation temperature Te cons which is used to regulate the compressor, according to the conventional closed loop control law. This quantity has an influence on the value of the PWM control signal.
  • the regulation module determines the current value of this quantity linked to the control signal at the instant in question, that is to say PWM sup (k) or Te cons (k) as the case may be, so that this quantity has a rate of progressive variation between a lower bound and an upper bound, in a time interval of length defined by a time constant KPWM or K Te respectively.
  • PWM sup (k) or Te cons (k) as the case may be
  • the time constants KPWM for the first embodiment or K Te for the second embodiment are determined according to the operating parameters of the air conditioning circuit.
  • the magnitude related to the PWM control signal sup (k) or Te cons (k) can be calculated with a first-order filter from the lower bound, the upper bound, the time constant, and the value of the quantity calculated at the previous iteration of PWM control sup (k-1) or Te cons (k-1).
  • the notations k and k-1, or k and k + 1, are used to designate two successive iteration instants of the regulation, thus distant from a duration equal to the period of time.
  • the term "precedent” or the expression “previous value” will be used to designate the value of a magnitude at time k-1
  • the term “current” or the expression “current value” will be used to denote the value of a magnitude at time k
  • the term “next” or the expression “next value” will be used to denote the value of a magnitude at time k + 1.
  • the controller module is used to control the evolution of the compressor control signal for limiting the occurrence of pressure peaks and thus maintain the high pressure of the compressor substantially below the HP compressor stop cutoff pressure during the phase of start-up.
  • control module is also adapted to regulate the high pressure in cases where the high pressure of the compressor approaches the compressor cut-off pressure during the start-up phase.
  • the regulation module 40 adjusts the value of the control signal in a chosen relation related to the difference between the high pressure of the compressor HP (k) and the HP cutoff pressure stop .
  • the method is implemented at the start of the air conditioning and is repeated at each moment k, as the start phase is not completed, as indicated in the test of step 3.
  • a conventional control law of the compressor which provides the control signal of the compressor as a function of the evaporation temperature, in particular as a function of the difference between the measurement and the temperature setpoint. of evaporation, is implemented in step 304.
  • This control law can be for example a proportional integral control derivative PID.
  • step 300 it is determined whether the difference between the high pressure of the compressor HP (k) at the instant k considered and a stop HP stop pressure is less than a constant C, for example equal to 5 bar.
  • the HP shut- off pressure is the value of the high pressure that causes the compressor to shut down.
  • the high pressure of the HP compressor (k) at time k can be provided by a sensor 142 or estimated. The verification of the condition of step 300 makes it possible to detect that the high pressure is approaching the cut-off pressure, and therefore a risk of stopping the compressor.
  • step 304 if this pressure difference ⁇ HP (k) - HP off ⁇ is greater than the constant C prefixed, the control signal of the compressor PWM (k), at instant k, is calculated according to the law conventional control according to the evaporation temperature Te, for example as a function of the difference between the measurement of the evaporation temperature Te mes and the setpoint of the evaporation temperature Te cons .
  • the control module calculates the variation of the control signal) PWM (k) at time k, at step 302, depending on the difference HP (k) - HP off , according to equation A1 of Appendix A.
  • the regulation module calculates the PWM control signal (k) of the compressor valve 140 at time k as a function of the value of the PWM control signal (k-1) at the previous time k-1 and the variation of the control signal) PWM (k) determined in step 302.
  • the value of the control signal PWM (k- 1) can be taken equal to the last value of the control signal before the start mode. The value of the PWM control signal (k) thus calculated makes it possible to maintain the discharge pressure of the compressor around the cutoff pressure.
  • Steps 300 to 306 are implemented to avoid stopping the compressor by acting on the PWM control signal as soon as a risk of exceeding the cut-off pressure is detected while maintaining a high pressure level to cool as quickly as possible. possible vehicle interior, that is to say, comply with the instruction requested by the user.
  • the detent module determines the current value of the upper threshold PWM sup (k) that the control signal PWM (k) must not exceed in steps 303 and 308.
  • the current value of the upper threshold of the PWM control signal sup (k) is calculated so that this quantity has a progressive rate of change between a lower bound and an upper bound, in a time interval of length defined by a time constant. KPWM.
  • the pace of the rate of variation is in particular increasing from the lower bound to the upper bound, as illustrated in the diagram of step 303.
  • the upper limit PWM max is represented by the maximum value of the control signal. This maximum value corresponds to the control signal of the compressor, when it is in maximum capacity. It can be for example equal to 90%.
  • the lower limit is represented by the minimum value of the control signal PWM min .
  • This minimum value corresponds to the value of the control signal of the compressor, when it is in minimum displacement. It can be equal for example to 20%.
  • the K PWM time constant may vary during the start-up period. it represents the time taken by the control signal to go from the lower terminal PWM min to the upper terminal PWM max .
  • Determining the upper threshold PWM sup (k) also uses the value of the upper threshold PWM sup (k-1) determined at the previous time k-1. This value is normally stored in memory.
  • the time constant of the filter K PWM can be calculated at each iteration of the control process from the discharge pressure of the compressor HP, the outside temperature Text and the rotation speed N of the compressor.
  • the upper threshold value PWM sup (k) is obtained according to the equation A2, where T ech corresponds to the sampling period of the filter.
  • the evolution of the threshold of the control signal is thus regulated during the time interval. This regulation makes it possible to avoid abrupt variations of the control signal during the start-up phase, and thus to limit pressure peaks.
  • step 310 the control module determines whether the value of the control signal PWM (k) obtained in step 304 or in step 306 is between the current value of the upper threshold PWM sup (k), obtained in step 303, and a lower threshold represented by the minimum value PWM min of the control signal.
  • step 312 if it is determined that the value of the PWM signal (k) determined in step 304 or step 306 exceeds the upper threshold value PWM sup (k) obtained in step 303, the value of the upper threshold PWM sup (k) is assigned to the signal PWM (k). However, when the value of the PWM signal (k) determined in step 304 or step 306 is less than the minimum value of the PWM control signal min , this minimum value PWM min is assigned to the PWM signal (k). In other cases, the value of the PWM signal (k) is not changed.
  • step 314 the control signal PWM (k) obtained in step 312 is applied to the control valve 140 of the compressor. Steps 300 to 314 are then reiterated at the next time k + 1, if it is determined that the startup phase is not completed (step 3).
  • the climate control module thus makes it possible to control the speed of change of the PWM control signal in time during the start-up period.
  • the invention provides a rate of change of the progressive control signal during this phase by means of a regulation of the upper threshold of the control signal and the level of the control signal.
  • it makes it possible to detect a risk of stopping the compressor by controlling the level of the high pressure and to avoid the actual stopping of the compressor by acting on the control signal of the compressor.
  • the regulation of the invention thus reduces the risk of pressure peaks and compressor interruptions that result during the startup phase of the air conditioning.
  • FIG. 5 is a diagram illustrating the evolution over time of the discharge pressure of the compressor (curve a), the suction pressure of the compressor (curve b) and the control signal of the compressor PWM (curve c), during the phase of starting, according to the first embodiment of the invention.
  • the starting phase control method is applied between about 460 seconds and 550 seconds.
  • the start-up phase ends at around 550 seconds.
  • a progressive increase is imposed on the PWM control signal (curve c) to avoid compressor cuts.
  • the regulation is down the control signal between 470 seconds and 480 seconds to prevent the high pressure (curve a) exceeds the HP stop cutoff pressure, for example between 130 and 140 bars (13 to 14 Mpa), and thus a compressor stop.
  • Curve c shows a second effect of regulation during the start-up phase. Indeed, between 510 and 530 seconds, the increase of the PWM signal sent to the compressor valve is limited to about 80% so as to counteract the increase in pressure pressure visible on the curve at 510 seconds. The high pressure (curve a) does not have any pressure peaks likely to exceed the cutoff pressure.
  • Steps 4 and 400 are similar to steps 3 and 300 respectively of Figure 3. These steps will not be described again here.
  • step 402 if the pressure difference ⁇ HP (k) - HP off ⁇ is less than the constant C prefixed, the control signal of the compressor PWM (k), at time k, is calculated according to the relation A1, similarly to step 306 of FIG.
  • step 404 if the pressure difference ⁇ HP (k) - HP off ⁇ is greater than the constant C prefixed, the control signal of the compressor PWM (k), at instant k, is calculated according to the law conventional control according to the difference between the measurement of the evaporation temperature Te mes and a predetermined set of evaporation temperature Te cons (k) at time k.
  • This conventional regulation law can be for example a derivative integral proportional regulation.
  • Step 403 makes it possible to determine this instruction.
  • the goal is to impose a gradual decrease of this setpoint over time, for example using a first order filter using a variable time constant K Te .
  • the current value of the evaporation temperature setpoint Te cons (k) is calculated so that this quantity has a progressive rate of variation between an upper bound and a lower bound, in a time interval of length defined by a constant of time K Te .
  • the pace of the speed of variation is particularly decreasing from the lower bound to the upper bound, as shown in the diagram of step 303.
  • the upper limit is represented by the maximum temperature setpoint Te cons_max of operation of the air conditioning. It can be for example equal to 15 ° C.
  • the lower limit is represented by the target temperature target Te cons_min requested in the cockpit by a passenger. It is generally between 2 ° C and 5 ° c.
  • the time constant K Te may vary during the start-up period. It represents the time taken by the control signal to go from the upper limit Te cons_max to the lower limit Te cons_min .
  • the determination of the current value of the evaporation temperature set point Te cons (k) also uses the value of the upper threshold Te cons (k-1) determined at the instant k-1 above. This value is normally stored in memory.
  • the time constant of the filter K Te can be calculated at each iteration of the control method from the discharge pressure of the compressor HP, the outside temperature Text and the rotation speed N of the compressor.
  • the value of the evaporation temperature setpoint Te cons (k) is obtained according to the equation A3, where T ech corresponds to the sampling period of the filter.
  • the evolution of the evaporation temperature set point is thus regulated during the time interval. This regulation makes it possible to avoid sudden variations of the PWM control signal during the start-up phase, and thus to limit the peaks of pressure.
  • step 410 the control module determines whether the value of the PWM control signal (k) obtained in step 404 or in step 406 is between the upper threshold of the control signal and the lower threshold of the signal control.
  • the upper threshold of the PWM max control signal represents the value of the control signal when the compressor is maximum displacement
  • the lower threshold of the PWM control signal min represents the value of the control signal when the compressor is minimum displacement.
  • step 412 if it is determined that the value of the PWM signal (k) determined in step 404 or step 406 exceeds the maximum PWM max value, the PWM max value is assigned to the PWM signal (k ). Otherwise, if the value of the PWM signal (k) determined in step 304 or step 306 is smaller than the minimum value of the PWM min control signal, the PWM min value is assigned to the PWM signal (k). In other cases, the value of the PWM signal (k) is not changed.
  • step 414 the control signal PWM (k) obtained in step 412 is applied to the control valve 140 of the compressor. Steps 400 to 414 are then reiterated at the next time k + 1, if it is determined that the startup phase is not completed (step 4).
  • the second embodiment makes it possible to impose a progressive increase in the control signal of the PWM compressor, without abrupt variation.
  • the high pressure of the HP compressor is also kept below the HP shutdown pressure of the compressor during the start-up period, which avoids pressure peaks and repetitive compressor shutdowns.
  • the regulation module proposed by the invention is therefore particularly suitable for controlling the start-up phase of an air conditioning circuit traversed by a supercritical fluid, even under the conditions of high thermal loads.
  • a supercritical type fluid such as CO2 requires operation at sometimes very high pressures.
  • the higher the pressures the more difficult it is to maintain a good seal. Therefore, it is particularly desirable, as proposed by the invention, to avoid seeing the high pressure exceed the cutoff threshold of the compressor while achieving the goal of thermal comfort as soon as possible requested by the user of the air conditioning system.
  • the invention applies to any type of expansion device, it is particularly advantageous when the expansion device is of the mechanical type.
  • the invention relates to the air conditioning installation using the start-up phase according to the invention, but it also relates to the method for implementing this start-up phase.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Duct Arrangements (AREA)
  • Air Conditioning Control Device (AREA)
EP07100075A 2006-01-04 2007-01-03 Klimaanlage, durch die ein superkritisches Fluid fliesst Not-in-force EP1806548B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0600058A FR2895787B1 (fr) 2006-01-04 2006-01-04 Installation de climatisation parcourue par un fluide supercritique

Publications (2)

Publication Number Publication Date
EP1806548A1 true EP1806548A1 (de) 2007-07-11
EP1806548B1 EP1806548B1 (de) 2011-02-23

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EP07100075A Not-in-force EP1806548B1 (de) 2006-01-04 2007-01-03 Klimaanlage, durch die ein superkritisches Fluid fliesst

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EP (1) EP1806548B1 (de)
AT (1) ATE499575T1 (de)
DE (1) DE602007012602D1 (de)
FR (1) FR2895787B1 (de)

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EP1482260A1 (de) * 2003-05-30 2004-12-01 Sanyo Electric Co., Ltd. Kühlvorrichtung
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DE602007012602D1 (de) 2011-04-07
EP1806548B1 (de) 2011-02-23

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