EP3658832B1 - Method for managing an air conditioning circuit of a motor vehicle - Google Patents

Method for managing an air conditioning circuit of a motor vehicle Download PDF

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Publication number
EP3658832B1
EP3658832B1 EP18755870.5A EP18755870A EP3658832B1 EP 3658832 B1 EP3658832 B1 EP 3658832B1 EP 18755870 A EP18755870 A EP 18755870A EP 3658832 B1 EP3658832 B1 EP 3658832B1
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EP
European Patent Office
Prior art keywords
shcomp
pcomp
expansion device
text
opening
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EP18755870.5A
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German (de)
French (fr)
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EP3658832A1 (en
Inventor
Régis BEAUVIS
Jin-ming LIU
Jugurtha Benouali
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Valeo Systemes Thermiques SAS
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Valeo Systemes Thermiques SAS
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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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/06—Superheaters
    • 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
    • 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
    • F25B2600/21—Refrigerant outlet evaporator temperature
    • 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
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—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
    • F25B2700/19—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
    • F25B2700/2106—Temperatures of fresh outdoor air
    • 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
    • F25B2700/2117—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 invention relates to the field of motor vehicles and more particularly to a motor vehicle air conditioning circuit and its cooling mode management method.
  • a refrigerant fluid passes successively through a compressor, a first heat exchanger, called a condenser, placed in contact with an air flow outside the motor vehicle to release heat, an expansion device and a second heat exchanger, called an evaporator, placed in contact with a flow of air inside the motor vehicle to cool it.
  • the expansion device is a thermostatic valve whose bulb is arranged downstream of the evaporator.
  • the expansion device can also be an electronic expansion valve controlled by a central control unit.
  • the document FR 2 928 445 A1 discloses a method for managing an air conditioning circuit inside which a refrigerant fluid circulates in a cooling mode, the refrigerant fluid circulating successively in a compressor, a condenser, an expansion device, and an evaporator intended to recover heat energy from a second heat transfer fluid and transferring it to the refrigerant fluid, said air conditioning circuit comprising a central control unit capable of controlling the opening of the expansion device, said method comprising: a step of calculating the opening of the expansion device from measurements of operating parameters of the air conditioning circuit and a step of opening the expansion device according to the calculated value.
  • One of the aims of the present invention is therefore to remedy, at least partially, the drawbacks of the prior art and to propose a method for managing an improved reversible air conditioning circuit, in particular in cooling mode.
  • SHcomp_in_sp_min is between 3 and 20°K and SHcomp_in_sp_max is between 8 and 25°K.
  • the air conditioning circuit comprises an internal heat exchanger capable of allowing the exchange of calorific energy between the refrigerant fluid at the outlet of the condenser and the refrigerant fluid at the outlet of the evaporator.
  • first element or second element as well as first parameter and second parameter or even first criterion and second criterion, etc.
  • it is a simple indexing to differentiate and name elements or parameters or criteria that are close but not identical.
  • This indexing does not imply a priority of one element, parameter or criterion with respect to another and it is easy to interchange such denominations without departing from the scope of the present description.
  • This indexation does not imply an order in time either, for example to assess such and such a criterion.
  • placed upstream means that one element is placed before another with respect to the direction of circulation of a fluid.
  • placed downstream means that one element is placed after another with respect to the direction of circulation of the fluid.
  • the condenser 5 is intended to release heat energy from the refrigerant fluid into a first heat transfer fluid 50.
  • This first heat transfer fluid 50 can for example be an external air flow when the first heat exchanger is for example placed on the front face of the motor vehicle.
  • the first heat transfer fluid 50 is a fluid circulating in another temperature management loop, for example when the first heat exchanger is a two-fluid exchanger, this is particularly the case in the context of a circuit indirect air conditioning.
  • the evaporator 9 is for its part intended to recover heat energy from a second heat transfer fluid 90 and to transfer it to the refrigerant fluid.
  • This second heat transfer fluid 90 can for example be an air flow going to the passenger compartment when the second heat exchanger is for example placed in a heating, ventilation and air conditioning device.
  • Another possibility can also be that the second heat transfer fluid 90 is a fluid circulating in another temperature management loop, for example when the second heat exchanger is a two-fluid exchanger.
  • the air conditioning circuit 1 also comprises a central control unit 10.
  • This central control unit 10 is in particular connected to the compressor 3 in order to control its speed and thus control the pressure of the refrigerant fluid.
  • Central unity control 10 is also connected to the expansion device 7 in order to control and command its opening and thus control the loss of pressure of the refrigerant fluid when it passes through it.
  • the central control unit 10 can also be connected to a first sensor 11 of the temperature Text of the first heat transfer fluid 50 before it passes through the condenser 5. More precisely, Text can correspond to the outside ambient temperature of the air.
  • the central control unit 10 can be connected to a second sensor 12 of the pressure Pcomp_out of the refrigerant fluid at the outlet of the compressor 3.
  • This second sensor 12 can in particular be arranged downstream of the compressor 3, between said compressor 3 and the condenser 5 .
  • the central control unit 10 can be connected to a third sensor 13 of the pressure Pcomp_in of the refrigerant fluid before it enters the compressor 3.
  • This third sensor 13 can in particular be arranged upstream of the compressor 3, between the evaporator 9 and said compressor 3.
  • the central control unit can be connected to a fourth sensor 14 of the temperature Tcomp_in of the refrigerant fluid before it enters the compressor 3.
  • This fourth sensor 14 can in particular be arranged upstream of the compressor 3, between the evaporator 9 and said compressor 3.
  • the third 13 and fourth 14 sensors can more particularly be only one pressure/temperature sensor arranged upstream of the compressor 3, between the evaporator 9 and the said compressor 3.
  • the central control unit can be connected to a fifth Tevapo temperature sensor 15 of the second heat transfer fluid 90 after it has passed through the evaporator 9.
  • the refrigerant fluid In operation, in cooling mode, as shown in the figure 1b , the refrigerant fluid is in the gaseous phase at low pressure before entering the compressor 3.
  • the refrigerant fluid undergoes an increase in its pressure and passes to high pressure as shown by the arrow 300.
  • the refrigerant fluid then passes through the condenser 5 and transfers enthalpy to the first heat transfer fluid 50 as shown by the arrow 500.
  • the refrigerant fluid first crosses its saturation curve X and passes into a two-phase state.
  • the refrigerant can also cross its saturation curve X a second time to pass into the liquid phase.
  • the difference between the temperature of the refrigerant at the outlet of the condenser 5 and its saturation temperature at this pressure is called sub-cooling SC.
  • the refrigerant fluid then passes through the expansion device 7 and undergoes a loss of pressure to pass to low pressure, as shown by the arrow 700.
  • the refrigerant fluid again crosses its saturation curve X and passes into a two-phase state.
  • the refrigerant fluid then passes through the evaporator 9 in which the refrigerant fluid absorbs calorific energy from the second heat transfer fluid 90, cooling the latter, as shown by the arrow 900.
  • the refrigerant fluid crosses its saturation curve X and then returns to gaseous phase before joining the compressor 3.
  • the air conditioning circuit 1 may also include an internal heat exchanger 20 capable of allowing the exchange of heat energy between the refrigerant fluid at the outlet of the condenser 5 and the refrigerant fluid at the outlet of the evaporator 9.
  • This internal heat exchanger 20 comprises in particular an inlet and an outlet of refrigerant fluid from the condenser 5, as well as an inlet and an outlet of refrigerant fluid from the evaporator 9.
  • the steps are similar to those of FIGS. 1a and 1b, except that the internal heat exchanger 20 absorbs enthalpy from the refrigerant fluid as shown by the arrow 200a and transfers it to the refrigerant fluid at the outlet of the evaporator 9 as shown by the arrow 200b.
  • the subcooling SR of the refrigerant fluid before it passes through the expansion device 7 and the superheat SHcomp_in of the refrigerant fluid before it enters the compressor 3 are both increased under the effect of the heat exchanger internal 20. This allows in particular an increase in the coefficient of performance of the air conditioning circuit 1.
  • the air conditioning circuit 1 can for example be an indirect reversible air conditioning circuit 1 as illustrated in the picture 3 .
  • This indirect reversible air conditioning circuit 1 can operate in different operating modes including a cooling mode.
  • the bypass pipe 30 can connect more specifically a first connection point 31 and a second connection point 32.
  • the first connection point 31 is preferably arranged, in the direction of circulation of the refrigerant fluid, downstream of the evaporator 9, between the said evaporator 9 and the evapo-condenser 13. More particularly, and as illustrated in the picture 3 , the first connection point 31 is arranged between the evaporator 9 and the second expansion device 21. It is however quite possible to imagine that the first connection point 31 is arranged between the second expansion device 21 and the evapo-condenser 13 as long as the refrigerant fluid has the possibility of bypassing the second expansion device 21 or of passing through it without suffering a loss of pressure.
  • the second connection point 32 is for its part preferably disposed downstream of the evapo-condenser 13, between said evapo-condenser 13 and the compressor 3.
  • the indirect reversible air conditioning circuit 1 also comprises a device for redirecting the refrigerant fluid coming from the evaporator 9 to the evapo-condenser 13 or to the bypass line 30.
  • Another alternative can also be to arrange a three-way valve at the level of the first connection point 31.
  • stop valve non-return valve, three-way valve or expansion device with stop function
  • stop function mechanical or electromechanical elements that can be controlled by the central control unit 10.
  • the first refrigerant loop A may comprise, in addition to the internal heat exchanger 20, a second internal heat exchanger 20' allowing heat exchange between the high-pressure refrigerant at the outlet of the heat exchanger internal 20 and the low-pressure refrigerant fluid flowing in the bypass line 30, that is to say coming from the first connection point 31.
  • high-pressure refrigerant fluid is meant a refrigerant fluid having undergone an increase of pressure at the level of the compressor 3 and that it has not yet suffered a loss of pressure due to the electronic expansion valve 7 or the tube orifice 11.
  • This second internal heat exchanger 20 'in comprises a inlet and an outlet of refrigerant fluid from the first connection point 31, as well as an inlet and an outlet of high pressure refrigerant fluid from the internal heat exchanger 20.
  • At least one of the two internal heat exchangers 20, 20′ can be a coaxial heat exchanger, that is to say comprising two coaxial tubes and between which heat exchanges take place.
  • the internal heat exchanger 20 can be a coaxial internal heat exchanger with a length of between 50 and 120mm while the second internal heat exchanger 20' can be a coaxial internal heat exchanger with a length between 200 and 700mm.
  • the first refrigerant fluid loop A may comprise a dehydrating bottle 18 disposed downstream of the bifluid heat exchanger 5, more precisely between said bifluid heat exchanger 5 and the internal heat exchanger 20.
  • a dehydrating bottle 18 disposed on the high pressure side of the air conditioning circuit that is to say downstream of the compressor 3 and upstream of an expansion device, has a smaller footprint as well as a reduced cost compared to other phase separation solutions such as an accumulator which would be placed on the low pressure side of the air conditioning circuit, that is to say upstream of the compressor 3, in particular upstream of the internal heat exchanger 20.
  • the indirect reversible air conditioning circuit 1 comprises within the second heat transfer fluid loop B a device for redirecting the heat transfer fluid coming from the two-fluid heat exchanger 5 to the first circulation pipe 70 and/or to the second heat transfer pipe. circulation 60.
  • the device for redirecting the heat transfer fluid coming from the two-fluid heat exchanger 5 may in particular comprise a fourth shut-off valve 63 arranged on the second circulation pipe 60 in order to block or not the first heat transfer fluid and prevent it from circulate in said second circulation pipe 60.
  • the indirect reversible air conditioning circuit 1 may also include a shutter 310 for obstructing the interior air flow 100 passing through the third heat exchanger 54.
  • This embodiment makes it possible in particular to limit the number of valves on the second heat transfer fluid loop B and thus makes it possible to limit production costs.
  • the device for redirecting the heat transfer fluid coming from the two-fluid heat exchanger 5 may in particular comprise a fourth shut-off valve 63 arranged on the second circulation pipe 60 in order to block or not block the fluid coolant and to prevent it from flowing in said second circulation pipe 60, and a fifth shut-off valve arranged on the first circulation pipe 70 in order to block or not the heat transfer fluid and to prevent it from flowing in said first pipe traffic 70.
  • the second loop of heat transfer fluid B may also include an electric heating element 55 of the heat transfer fluid.
  • Said electrical heating element 55 is in particular arranged, in the direction of circulation of the heat transfer fluid, downstream of the bifluid heat exchanger 5, between said bifluid heat exchanger 5 and the first junction point 61.
  • the refrigerant fluid does not pass through the evapo-condenser 13 but passes through the bypass line 30.
  • the first refrigerant fluid 50 passes for its part into the external radiator 64 in order to evacuate heat energy in the external airflow 200.
  • the refrigerant fluid passes successively through a compressor 3, a condenser 5, an expansion device 7 and an evaporator 9.
  • the present invention relates to a method for managing the air conditioning circuit 1 in cooling mode and more precisely for managing the control of the opening of the expansion device 7 and therefore of the loss of pressure of the refrigerant fluid when it passes through said device. relaxation 7.
  • SHcomp_in_sp_min can be between 3 and 20°K and SHcomp_in_sp_max between 8 and 25°K.
  • SHcomp_in_sp_min and SHcomp_in_sp_max are variable depending on the nature of the refrigerant fluid and the architecture of the air conditioning circuit 1.
  • the value of Shcomp_in_sp allows an optimization of the coefficient of performance of the air conditioning circuit 1 and allows the refrigerant fluid to be in a gaseous state at at least minus 90% as it enters compressor 3.
  • the value of SHcomp_in_sp always between SHcomp_in_sp_min and SHcomp_in_sp_max , allows the refrigerant to be at a temperature below the operating limit temperature of compressor 3 and thus prevents the latter from does not stop by getting to safety.
  • SHcomp_in_sp For a value of Text between T1 and T2, the value of SHcomp_in_sp , always between SHcomp_in_sp_min and SHcomp_in_sp_max , allows an optimization of the coefficient of performance of the air conditioning circuit 1 and of the cooling power of the second heat transfer fluid 90.
  • the control unit 10 During the second step of controlling the overheating Shcomp_in , if SHcomp_in is less than SHcomp_in_sp_min then the control unit 10 will decrease the opening of the expansion device 7 in order to increase the overheating SHcomp_in. Whether SHcomp_in is greater than SHcomp_in_sp_max then the control unit 10 will increase the opening of the expansion device 7 in order to reduce the overheating SHcomp_in.
  • the increase or decrease in the opening of the expansion device 7 is preferably carried out by a proportional integral controller.
  • SHcomp_in is between SHcomp_in_sp_min and SHcomp_in_sp_max, the increase or decrease in the opening of the expansion device 7 is preferably carried out by a proportional controller.
  • the chosen refrigerant is R134a and the temperature Text is 45°C.
  • the management method according to the invention allows an increase in the overheating SHcom_in 102b with respect to the overheating SHcom_in 102a.
  • This overheating SHcom_in 102b is greater because the opening 103b according to the invention is smaller than the opening 103a according to the prior art. Due to this higher SHcom_in 102b overheating, the Tevapo 101b temperature according to the invention is lower than the temperature Tevapo 101a according to the prior art. The coefficient of performance is then increased compared to the prior art, because the compressor 3 is at an identical speed whether for the prior art or for the management method according to the invention.
  • the management method according to the invention allows good management and good control of the opening of the expansion device 7 allowing a good coefficient of performance of the air conditioning circuit 1 in cooling mode.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Description

L'invention se rapporte au domaine des véhicules automobiles et plus particulièrement à un circuit de climatisation de véhicule automobile et son procédé de gestion en mode de refroidissement.The invention relates to the field of motor vehicles and more particularly to a motor vehicle air conditioning circuit and its cooling mode management method.

Les véhicules automobiles actuels comportent de plus en plus souvent un circuit de climatisation. Dans un circuit de climatisation « classique », lors d'un mode de refroidissement, un fluide réfrigérant passe successivement dans un compresseur, un premier échangeur de chaleur, appelé condenseur, placé en contact avec un flux d'air extérieur au véhicule automobile pour libérer de la chaleur, un dispositif de détente et un deuxième échangeur de chaleur, appelé évaporateur, placé en contact avec un flux d'air intérieur du véhicule automobile pour le refroidir.Current motor vehicles increasingly include an air conditioning circuit. In a "conventional" air conditioning circuit, during a cooling mode, a refrigerant fluid passes successively through a compressor, a first heat exchanger, called a condenser, placed in contact with an air flow outside the motor vehicle to release heat, an expansion device and a second heat exchanger, called an evaporator, placed in contact with a flow of air inside the motor vehicle to cool it.

Généralement, le dispositif de détente est une vanne thermostatique dont le bulbe est disposé en aval de l'évaporateur. Le dispositif de détente peut également être une vanne électronique d'expansion contrôlée par une unité centrale de contrôle.Generally, the expansion device is a thermostatic valve whose bulb is arranged downstream of the evaporator. The expansion device can also be an electronic expansion valve controlled by a central control unit.

Par exemple, le document FR 2 928 445 A1 divulgue un procédé de gestion d'un circuit de climatisation à l'intérieur duquel circule un fluide réfrigérant dans un mode de refroidissement, le fluide réfrigérant circulant successivement dans un compresseur, un condenseur, un dispositif de détente, et un évaporateur destiné à récupérer de l'énergie calorifique d'un deuxième fluide caloporteur et de la transférer au fluide réfrigérant, ledit circuit de climatisation comportant une unité centrale de contrôle apte à contrôler l'ouverture du dispositif de détente, ledit procédé comportant: une étape de calcul de l'ouverture du dispositif de détente à partir de mesures de paramètres de fonctionnement du circuit de climatisation et une étape d'ouverture du dispositif de détente selon la valeur calculée. Dans ce genre de cas, il est nécessaire d'avoir une stratégie de contrôle du circuit de climatisation afin de déterminer et contrôler l'ouverture de la vanne électronique d'expansion notamment afin d'obtenir une surchauffe du fluide réfrigérant en sortie de l'évaporateur. Cette surchauffe est notamment utile pour améliorer le coefficient de performance du circuit de climatisation, mais également pour diminuer les risques que du fluide réfrigérant à l'état liquide ne passe dans le compresseur.For example, the document FR 2 928 445 A1 discloses a method for managing an air conditioning circuit inside which a refrigerant fluid circulates in a cooling mode, the refrigerant fluid circulating successively in a compressor, a condenser, an expansion device, and an evaporator intended to recover heat energy from a second heat transfer fluid and transferring it to the refrigerant fluid, said air conditioning circuit comprising a central control unit capable of controlling the opening of the expansion device, said method comprising: a step of calculating the opening of the expansion device from measurements of operating parameters of the air conditioning circuit and a step of opening the expansion device according to the calculated value. In this type of case, it is necessary to have a control strategy for the air conditioning circuit in order to determine and control the opening of the electronic expansion valve, in particular in order to obtain superheating of the refrigerant fluid at the outlet of the evaporator. This overheating is particularly useful for improving the coefficient of performance of the air conditioning circuit, but also for reducing the risks of refrigerant fluid in the liquid state passing through the compressor.

Un des buts de la présente invention est donc de remédier au moins partiellement aux inconvénients de l'art antérieur et de proposer un procédé de gestion d'un circuit de climatisation inversible amélioré notamment en mode refroidissement.One of the aims of the present invention is therefore to remedy, at least partially, the drawbacks of the prior art and to propose a method for managing an improved reversible air conditioning circuit, in particular in cooling mode.

La présente invention concerne donc un procédé, tel que défini dans la revendication indépendante 1, le procédé étant un procédé de gestion d'un circuit de climatisation à l'intérieur duquel circule un fluide réfrigérant dans un mode de refroidissement, le fluide réfrigérant circulant successivement dans :

  • un compresseur,
  • un condenseur destiné à relâcher de l'énergie calorifique du fluide réfrigérant dans un premier fluide caloporteur,
  • un dispositif de détente, et
  • un évaporateur destiné à récupérer de l'énergie calorifique d'un deuxième fluide caloporteur et de la transférer au fluide réfrigérant,
    • ledit circuit de climatisation comportant une unité centrale de contrôle apte à contrôler l'ouverture du dispositif de détente,
    • ledit procédé comportant :
      • une étape de :
        • ∘ calcul de l'ouverture Cestim du dispositif de détente à partir de mesures de paramètres de fonctionnement du circuit de climatisation, et de
        • ∘ détermination d'une surchauffe consigne SHcomp_in_sp en fonction de l'état du fluide réfrigérant en sortie de l'évaporateur et de la température Text du premier fluide caloporteur avant sa traversée du condenseur, SHcomp_in_sp étant comprise entre une surchauffe minimale SHcomp_in_sp_min et une surchauffe maximale SHcomp_in_sp_max, SHcomp_in_sp_min et SHcomp_in_sp_max étant déterminées en fonction de la température Text du premier fluide caloporteur avant sa traversée du condenseur, du débit du deuxième fluide caloporteur traversant l'évaporateur et de la température du deuxième fluide caloporteur avant sa traversée de l'évaporateur,
      • une étape d'ouverture du dispositif de détente selon Cestim et de contrôle de la surchauffe SHcomp_in en faisant varier l'ouverture du dispositif de détente de sorte à atteindre la surchauffe consigne SHcomp_in_sp et maintenir SHcomp_in entre SHcomp_in_sp_min et SHcomp_in_sp_max.
The present invention therefore relates to a method, as defined in independent claim 1, the method being a method for managing an air conditioning circuit inside which a refrigerant fluid circulates in a cooling mode, the refrigerant fluid circulating successively in :
  • a compressor,
  • a condenser intended to release heat energy from the refrigerant fluid into a first heat transfer fluid,
  • a relaxation device, and
  • an evaporator intended to recover heat energy from a second heat transfer fluid and to transfer it to the refrigerant fluid,
    • said air conditioning circuit comprising a central control unit capable of controlling the opening of the expansion device,
    • said method comprising:
      • a step of:
        • ∘ calculation of the Cestim opening of the expansion device from measurements of operating parameters of the air conditioning circuit, and from
        • ∘ determination of a set superheat SHcomp_in_sp according to the state of the refrigerant at the outlet of the evaporator and the Text temperature of the first heat transfer fluid before it passes through the condenser, SHcomp_in_sp being between a minimum superheat SHcomp_in_sp_min and a maximum superheat SHcomp_in_sp_max, SHcomp_in_sp_min and SHcomp_in_sp_max being determined according to the temperature Text of the first heat transfer fluid before it passes through the condenser, the flow rate of the second heat transfer fluid passing through the evaporator and the temperature of the second heat transfer fluid before it passes through the evaporator,
      • a step of opening the expansion device according to Cestim and controlling the overheating SHcomp_in by varying the opening of the expansion device so as to reach the overheating setpoint SHcomp_in_sp and maintain SHcomp_in between SHcomp_in_sp_min and SHcomp_in_sp_max.

Selon l'invention SHcomp_in est calculé selon la formule suivante SHcomp _ in = Tcomp _ in − Tsat Pcomp _ in

Figure imgb0001
dans laquelle,

  • Tcomp_in est la température du fluide réfrigérant en entrée du compresseur, et
  • Tsat(Pcomp_in) est la température de saturation du fluide réfrigérant à la pression Pcomp_in en entrée du compresseur.
According to the invention SHcomp_in is calculated according to the following formula SHcomp _ in = Tcomp _ in − Tsat Pcomp _ in
Figure imgb0001
 in which,
  • Tcomp_in is the temperature of the refrigerant at the compressor inlet, and
  • Tsat(Pcomp_in) is the saturation temperature of the refrigerant at pressure Pcomp_in at the compressor inlet.

Selon l'invention le calcul de l'ouverture Cestim du dispositif de détente est réalisé selon l'une des formules suivantes : Cestim = K1 * Tevapo − Tevapo _ sp + K 2 * Tsat Pcomp _ out − Text

Figure imgb0002
ou Cestim = K1 ′ * Pcomp _ in − Psat Tevapo _ sp + K 2 * Tsat Pcomp _ out − Text
Figure imgb0003
 dans lesquelles,

  • Tevapo est la température du second fluide caloporteur en sortie de l'évaporateur,
  • Tevapo_sp est une température consigne du second fluide caloporteur en sortie de l'évaporateur,
  • Tsat(Pcomp_out) est la température de saturation du fluide réfrigérant à la pression Pcomp_out du fluide réfrigérant en sortie du compresseur,
  • Text est la température du premier fluide caloporteur avant sa traversée du condenseur,
  • Pcomp_in est la pression du fluide réfrigérant en entrée du compresseur,
  • Psat(Tevapo_sp) est la pression de saturation du fluide réfrigérant à la température consigne Tevapo du second fluide caloporteur en sortie de l'évaporateur,
  • K1 étant la pente moyenne ΔC/ΔTevapo avec ΔC étant la variation de l'ouverture du dispositif de détente et de ΔTevapo la variation de Tevapo mesurées lors d'expérimentation où l'on fait varier l'ouverture du dispositif de détente pour un régime du compresseur donné, un débit donné du premier fluide caloporteur traversant le condenseur et selon la valeur de Text,
  • K1'étant la pente moyenne ΔC/ΔPcomp_in avec ΔC étant la variation de l'ouverture du dispositif de détente et de ΔPcomp_in la variation de Pcomp_in mesurées lors d'expérimentation où l'on fait varier l'ouverture du dispositif de détente pour un régime du compresseur donné et un débit donné de premier fluide caloporteur traversant le condenseur et selon la valeur de Text. et
  • K2 étant la pente moyenne ΔC/Δ(Tsat(Pcomp_out) - Text) avec ΔC étant la variation de l'ouverture du dispositif de détente et de Δ(Tsat(Pcomp_out) - Text) la variation de (Tsat(Pcomp_out) - Text) mesurées et calculées lors d'expérimentation où l'on fait varier l'ouverture du dispositif de détente pour un régime du compresseur donné et un débit donné de premier fluide caloporteur traversant le condenseur et selon la valeur de Text.
According to the invention, the calculation of the Cestim opening of the expansion device is carried out according to one of the following formulas: Cestim = K1 * Tevapo − Tevapo _ sp + K 2 * Tsat Pcomp _ out − text
Figure imgb0002
 Where Cestim = K1 ′ * Pcomp _ in − psat Tevapo _ sp + K 2 * Tsat Pcomp _ out − Text
Figure imgb0003
 in which,
  • Tevapo is the temperature of the second heat transfer fluid leaving the evaporator,
  • Tevapo_sp is a setpoint temperature of the second heat transfer fluid leaving the evaporator,
  • Tsat(Pcomp_out) is the saturation temperature of the refrigerant at the pressure Pcomp_out of the refrigerant at the compressor outlet,
  • Text is the temperature of the first heat transfer fluid before it passes through the condenser,
  • Pcomp_in is the pressure of the refrigerant fluid at the compressor inlet,
  • Psat(Tevapo_sp) is the saturation pressure of the refrigerant fluid at the Tevapo setpoint temperature of the second heat transfer fluid at the evaporator outlet,
  • K1 being the average slope ΔC / ΔTevapo with ΔC being the variation of the opening of the expansion device and ΔTevapo the variation of Tevapo measured during experiments where the opening of the expansion device is varied for a speed of the given compressor, a given flow rate of the first heat transfer fluid passing through the condenser and according to the value of Text,
  • K1' being the average slope Δ C /Δ Pcomp_in with Δ C being the variation of the opening of the expansion device and ΔPcomp_in the variation of Pcomp_in measured during experiments where the opening of the expansion device is varied for a given compressor speed and a given flow rate of first coolant passing through the condenser and according to the value of Text. and
  • K2 being the average slope Δ C /Δ( Tsat(Pcomp_out) - Text ) with Δ C being the variation of the opening of the expansion device and Δ( Tsat(Pcomp_out) - Text ) the variation of ( Tsat(Pcomp_out) - Text ) measured and calculated during experiments where the opening of the expansion device is varied for a given compressor speed and a given flow rate of first coolant passing through the condenser and according to the value of Text.

Selon un autre aspect du procédé de gestion, la détermination de la surchauffe consigne SHcomp_in_sp est telle que :

  • pour une valeur de Text inférieure à une valeur définie T1, la valeur de SHcomp_in_sp permet une optimisation du coefficient de performance du circuit de climatisation et permet au fluide réfrigérant d'être dans un état gazeux à au moins 90 % à son entrée dans le compresseur,
  • pour une valeur de Text supérieure à une valeur définie T2, la valeur de SHcomp_in_sp permet au fluide réfrigérant d'être à une température inférieure à la température limite de fonctionnement du compresseur,
  • pour une valeur de Text comprise entre T1 et T2, la valeur de SHcomp_in_sp permet une optimisation du coefficient de performance du circuit de climatisation et de la puissance de refroidissement du deuxième fluide caloporteur.
According to another aspect of the management method, the determination of the set superheat SHcomp_in_sp is such that:
  • for a value of Text lower than a defined value T1, the value of SHcomp_in_sp allows an optimization of the coefficient of performance of the air conditioning circuit and allows the refrigerant fluid to be in a gaseous state at least 90% at its entry into the compressor ,
  • for a value of Text greater than a defined value T2, the value of SHcomp_in_sp allows the refrigerant fluid to be at a temperature below the operating limit temperature of the compressor,
  • for a value of Text between T1 and T2, the value of SHcomp_in_sp allows an optimization of the coefficient of performance of the air conditioning circuit and of the cooling power of the second heat transfer fluid.

Selon un autre aspect du procédé de gestion, SHcomp_in_sp_min est comprise entre 3 et 20 °K et SHcomp_in_sp_max est comprise ente 8 et 25 °K.According to another aspect of the management method, SHcomp_in_sp_min is between 3 and 20°K and SHcomp_in_sp_max is between 8 and 25°K.

Selon un autre aspect du procédé de gestion, lors de l'étape de contrôle de la surchauffe SHcomp_in :

  • si SHcomp_in est inférieure à SHcomp_in_sp_min ou supérieure à SHcomp_in_sp_max, l'augmentation ou la diminution de l'ouverture du dispositif de détente est réalisée par un contrôleur proportionnel intégral,
  • si SHcomp_in est compris entre SHcomp_in_sp_min et SHcomp_in_sp_max, l'augmentation ou la diminution de l'ouverture du dispositif de détente est réalisée par un contrôleur proportionnel.
According to another aspect of the management method, during the SHcomp_in overheating control step:
  • if SHcomp_in is lower than SHcomp_in_sp_min or higher than SHcomp_in_sp_max , the increase or decrease of the opening of the trigger device is carried out by a proportional integral controller,
  • if SHcomp_in is between SHcomp_in_sp_min and SHcomp_in_sp_max, the increase or decrease in the opening of the expansion device is carried out by a proportional controller.

Selon un autre aspect du procédé de gestion, le circuit de climatisation comporte un échangeur de chaleur interne apte à permettre les échanges d'énergie calorifique entre le fluide réfrigérant en sortie du condenseur et le fluide réfrigérant en sortie de l'évaporateur.According to another aspect of the management method, the air conditioning circuit comprises an internal heat exchanger capable of allowing the exchange of calorific energy between the refrigerant fluid at the outlet of the condenser and the refrigerant fluid at the outlet of the evaporator.

D'autres caractéristiques et avantages de l'invention apparaîtront plus clairement à la lecture de la description suivante, donnée à titre d'exemple illustratif et non limitatif, et des dessins annexés parmi lesquels :

  • la figure la montre une représentation schématique d'un circuit de climatisation selon un premier mode de réalisation,
  • la figure 1b montre un diagramme pression/enthalpie du circuit de climatisation de la figure 1a,
  • la figure 2a montre une représentation schématique d'un circuit de climatisation selon un deuxième mode de réalisation,
  • la figure 2b montre un diagramme pression/enthalpie du circuit de climatisation de la figure 2a,
  • la figure 3 montre une représentation schématique d'un circuit de climatisation selon un mode de réalisation particulier,
  • la figure 4 montre un diagramme de l'évolution de la surchauffe en fonction de la température d'un premier fluide caloporteur,
  • la figure 5 montre un diagramme de l'évolution de différents paramètres en fonction du temps lors du fonctionnement du circuit de climatisation.
Other characteristics and advantages of the invention will appear more clearly on reading the following description, given by way of illustrative and non-limiting example, and the appended drawings, among which:
  • figure la shows a schematic representation of an air conditioning circuit according to a first embodiment,
  • the figure 1b shows a pressure/enthalpy diagram of the air conditioning circuit of the picture 1a ,
  • the figure 2a shows a schematic representation of an air conditioning circuit according to a second embodiment,
  • the figure 2b shows a pressure/enthalpy diagram of the air conditioning circuit of the figure 2a ,
  • the picture 3 shows a schematic representation of an air conditioning circuit according to a particular embodiment,
  • the figure 4 shows a diagram of the evolution of the superheat according to the temperature of a first heat transfer fluid,
  • the figure 5 shows a diagram of the evolution of various parameters as a function of time during the operation of the air conditioning circuit.

Sur les différentes figures, les éléments identiques portent les mêmes numéros de référence.In the various figures, identical elements bear the same reference numbers.

Les réalisations suivantes sont des exemples. Bien que la description se réfère à un ou plusieurs modes de réalisation, ceci ne signifie pas nécessairement que chaque référence concerne le même mode de réalisation, ou que les caractéristiques s'appliquent seulement à un seul mode de réalisation. De simples caractéristiques de différents modes de réalisation peuvent également être combinées et/ou interchangées pour fournir d'autres réalisations. L'étendu de l'invention est cependant limité par l'objet des revendications annexées.The following achievements are examples. Although the description refers to one or more embodiments, this does not necessarily mean that each reference is to the same embodiment, or that the features apply only to a single embodiment. Simple features of different embodiments may also be combined and/or interchanged to provide other embodiments. The scope of the invention is however limited by the subject matter of the appended claims.

Dans la présente description, on peut indexer certains éléments ou paramètres, comme par exemple premier élément ou deuxième élément ainsi que premier paramètre et second paramètre ou encore premier critère et deuxième critère etc. Dans ce cas, il s'agit d'un simple indexage pour différencier et dénommer des éléments ou paramètres ou critères proches mais non identiques. Cette indexation n'implique pas une priorité d'un élément, paramètre ou critère par rapport à un autre et on peut aisément interchanger de telles dénominations sans sortir du cadre de la présente description. Cette indexation n'implique pas non plus un ordre dans le temps par exemple pour apprécier tel ou tel critère.In the present description, it is possible to index certain elements or parameters, such as for example first element or second element as well as first parameter and second parameter or even first criterion and second criterion, etc. In this case, it is a simple indexing to differentiate and name elements or parameters or criteria that are close but not identical. This indexing does not imply a priority of one element, parameter or criterion with respect to another and it is easy to interchange such denominations without departing from the scope of the present description. This indexation does not imply an order in time either, for example to assess such and such a criterion.

Dans la présente description, on entend par « placé en amont » qu'un élément est placé avant un autre par rapport au sens de circulation d'un fluide. A contrario, on entend par « placé en aval » qu'un élément est placé après un autre par rapport au sens de circulation du fluide.In the present description, the term “placed upstream” means that one element is placed before another with respect to the direction of circulation of a fluid. On the other hand, the term “placed downstream” means that one element is placed after another with respect to the direction of circulation of the fluid.

La figure la montre un circuit de climatisation 1 simple, notamment pour véhicule automobile, dans lequel circule un fluide réfrigérant. Ce circuit de climatisation 1 comporte dans le sens de circulation du fluide réfrigérant :

  • un compresseur 3,
  • un premier échangeur de chaleur jouant le rôle d'un condenseur 5,
  • un dispositif de détente 7, plus précisément dans le cas présent une vanne électronique d'expansion,
  • un deuxième échangeur de chaleur jouant le rôle d'un évaporateur 9.
Figure la shows a simple air conditioning circuit 1, in particular for a motor vehicle, in which a refrigerant fluid circulates. This air conditioning circuit 1 comprises, in the direction of circulation of the refrigerant fluid:
  • a compressor 3,
  • a first heat exchanger acting as a condenser 5,
  • an expansion device 7, more precisely in the present case an electronic expansion valve,
  • a second heat exchanger acting as an evaporator 9.

Le condenseur 5 est destiné à relâcher de l'énergie calorifique du fluide réfrigérant dans un premier fluide caloporteur 50. Ce premier fluide caloporteur 50 peut par exemple être un flux d'air extérieur lorsque le premier échangeur de chaleur est par exemple disposé en face avant du véhicule automobile. Une autre possibilité peut également être que le premier fluide caloporteur 50 est un fluide circulant dans une autre boucle de gestion de température, par exemple lorsque le premier échangeur de chaleur est un échangeur bifluide, cela est notamment le cas dans le cadre d'un circuit de climatisation indirect.The condenser 5 is intended to release heat energy from the refrigerant fluid into a first heat transfer fluid 50. This first heat transfer fluid 50 can for example be an external air flow when the first heat exchanger is for example placed on the front face of the motor vehicle. Another possibility may also be that the first heat transfer fluid 50 is a fluid circulating in another temperature management loop, for example when the first heat exchanger is a two-fluid exchanger, this is particularly the case in the context of a circuit indirect air conditioning.

L'évaporateur 9 est quant à lui destiné à récupérer de l'énergie calorifique d'un deuxième fluide caloporteur 90 et de la transférer au fluide réfrigérant. Ce deuxième fluide caloporteur 90 peut par exemple être un flux d'air allant vers l'habitacle lorsque le deuxième échangeur de chaleur est par exemple disposé dans un dispositif de chauffage, ventilation et climatisation. Une autre possibilité peut également être que le deuxième fluide caloporteur 90 est un fluide circulant dans une autre boucle de gestion de température, par exemple lorsque le deuxième échangeur de chaleur est un échangeur bifluide.The evaporator 9 is for its part intended to recover heat energy from a second heat transfer fluid 90 and to transfer it to the refrigerant fluid. This second heat transfer fluid 90 can for example be an air flow going to the passenger compartment when the second heat exchanger is for example placed in a heating, ventilation and air conditioning device. Another possibility can also be that the second heat transfer fluid 90 is a fluid circulating in another temperature management loop, for example when the second heat exchanger is a two-fluid exchanger.

Le circuit de climatisation 1 comporte également une unité centrale de contrôle 10. Cette unité centrale de contrôle 10 est notamment reliée au compresseur 3 afin de contrôler son régime et ainsi contrôler la pression du fluide réfrigérant. L'unité centrale de contrôle 10 est également reliée au dispositif de détente 7 afin de contrôler et commander son ouverture et ainsi contrôler la perte de pression du fluide réfrigérant lorsqu'il la traverse.The air conditioning circuit 1 also comprises a central control unit 10. This central control unit 10 is in particular connected to the compressor 3 in order to control its speed and thus control the pressure of the refrigerant fluid. Central unity control 10 is also connected to the expansion device 7 in order to control and command its opening and thus control the loss of pressure of the refrigerant fluid when it passes through it.

L'unité centrale de contrôle 10 peut également être reliée à un premier capteur 11 de la température Text du premier fluide caloporteur 50 avant sa traversée du condenseur 5. Plus précisément, Text peut correspondre à la température ambiante extérieure de l'air.The central control unit 10 can also be connected to a first sensor 11 of the temperature Text of the first heat transfer fluid 50 before it passes through the condenser 5. More precisely, Text can correspond to the outside ambient temperature of the air.

L'unité centrale de contrôle 10 peut être reliée à un deuxième capteur 12 de la pression Pcomp_out du fluide réfrigérant en sortie du compresseur 3. Ce deuxième capteur 12 peut notamment être disposé en aval du compresseur 3, entre ledit compresseur 3 et le condenseur 5.The central control unit 10 can be connected to a second sensor 12 of the pressure Pcomp_out of the refrigerant fluid at the outlet of the compressor 3. This second sensor 12 can in particular be arranged downstream of the compressor 3, between said compressor 3 and the condenser 5 .

L'unité centrale de contrôle 10 peut être reliée à un troisième capteur 13 de la pression Pcomp_in du fluide réfrigérant avant son entrée dans le compresseur 3. Ce troisième capteur 13 peut notamment être disposé en amont du compresseur 3, entre l'évaporateur 9 et ledit compresseur 3.The central control unit 10 can be connected to a third sensor 13 of the pressure Pcomp_in of the refrigerant fluid before it enters the compressor 3. This third sensor 13 can in particular be arranged upstream of the compressor 3, between the evaporator 9 and said compressor 3.

L'unité centrale de contrôle peut être reliée à un quatrième capteur 14 de la température Tcomp_in du fluide réfrigérant avant son entrée dans le compresseur 3. Ce quatrième capteur 14 peut notamment être disposé en amont du compresseur 3, entre l'évaporateur 9 et ledit compresseur 3.The central control unit can be connected to a fourth sensor 14 of the temperature Tcomp_in of the refrigerant fluid before it enters the compressor 3. This fourth sensor 14 can in particular be arranged upstream of the compressor 3, between the evaporator 9 and said compressor 3.

Le troisième 13 et quatrième 14 capteurs peuvent plus particulièrement n'être qu'un seul capteur pression/température disposé en amont du compresseur 3, entre l'évaporateur 9 et ledit compresseur 3.The third 13 and fourth 14 sensors can more particularly be only one pressure/temperature sensor arranged upstream of the compressor 3, between the evaporator 9 and the said compressor 3.

L'unité centrale de contrôle peut être reliée à un cinquième capteur 15 de la température Tevapo du deuxième fluide caloporteur 90 après qu'il ait traversé l'évaporateur 9.The central control unit can be connected to a fifth Tevapo temperature sensor 15 of the second heat transfer fluid 90 after it has passed through the evaporator 9.

En fonctionnement, en mode de refroidissement, comme le montre la figure 1b, le fluide réfrigérant est en phase gazeuse à basse pression avant d'entrer dans le compresseur 3. En traversant le compresseur 3 le fluide réfrigérant subit une augmentation de sa pression et passe à haute pression comme le montre la flèche 300. Le fluide réfrigérant traverse ensuite le condenseur 5 et transfert de l'enthalpie au premier fluide caloporteur 50 comme le montre la flèche 500. le fluide réfrigérant franchit une première fois sa courbe de saturation X et passe dans un état biphasique. Le fluide réfrigérant peut également franchir une deuxième fois sa courbe de saturation X pour passer en phase liquide. La différence entre la température du fluide réfrigérant en sortie du condenseur 5 et sa température de saturation à cette pression est appelée sous-refroidissement SC.In operation, in cooling mode, as shown in the figure 1b , the refrigerant fluid is in the gaseous phase at low pressure before entering the compressor 3. By crossing the compressor 3 the refrigerant fluid undergoes an increase in its pressure and passes to high pressure as shown by the arrow 300. The refrigerant fluid then passes through the condenser 5 and transfers enthalpy to the first heat transfer fluid 50 as shown by the arrow 500. the refrigerant fluid first crosses its saturation curve X and passes into a two-phase state. The refrigerant can also cross its saturation curve X a second time to pass into the liquid phase. The difference between the temperature of the refrigerant at the outlet of the condenser 5 and its saturation temperature at this pressure is called sub-cooling SC.

Le fluide réfrigérant passe ensuite au travers du dispositif de détente 7 et subit une perte de pression pour passer à basse pression, comme le montre la flèche 700. Le fluide réfrigérant franchit de nouveau sa courbe de saturation X et passe dans un état diphasique. Le fluide réfrigérant traverse ensuite l'évaporateur 9 dans lequel le fluide réfrigérant absorbe de l'énergie calorifique du deuxième fluide caloporteur 90, refroidissant ce dernier, comme le montre la flèche 900. Le fluide réfrigérant traverse sa courbe de saturation X et repasse alors en phase gazeuse avant de rejoindre le compresseur 3. La différence entre la température Tcomp_in du fluide réfrigérant avant qu'il ne traverse le compresseur 3 (mesurée par le quatrième capteur 14) et sa température de saturation à cette pression Tsat(Pcomp_in), correspond à une surchauffe SHcomp_in du fluide réfrigérant. Ainsi , Shcomp _ in = Tcomp _ in − Tsat Pcomp _ in .

Figure imgb0004
The refrigerant fluid then passes through the expansion device 7 and undergoes a loss of pressure to pass to low pressure, as shown by the arrow 700. The refrigerant fluid again crosses its saturation curve X and passes into a two-phase state. The refrigerant fluid then passes through the evaporator 9 in which the refrigerant fluid absorbs calorific energy from the second heat transfer fluid 90, cooling the latter, as shown by the arrow 900. The refrigerant fluid crosses its saturation curve X and then returns to gaseous phase before joining the compressor 3. The difference between the temperature Tcomp_in of the refrigerant fluid before it passes through the compressor 3 (measured by the fourth sensor 14) and its saturation temperature at this pressure Tsat(Pcomp_in) , corresponds to SHcomp_in overheating of the refrigerant fluid. Thereby , Shcomp _ in = Tcomp _ in − Tsat Pcomp _ in .
Figure imgb0004

Comme le montre la figure 2a, le circuit de climatisation 1 peut également comporter un échangeur de chaleur interne 20 apte à permettre les échanges d'énergie calorifique entre le fluide réfrigérant en sortie du condenseur 5 et le fluide réfrigérant en sortie de l'évaporateur 9. Cet échangeur de chaleur interne 20 comporte notamment une entrée et une sortie de fluide réfrigérant en provenance du condenseur 5, ainsi qu'une entrée et une sortie de fluide réfrigérant de l'évaporateur 9.As shown in figure 2a , the air conditioning circuit 1 may also include an internal heat exchanger 20 capable of allowing the exchange of heat energy between the refrigerant fluid at the outlet of the condenser 5 and the refrigerant fluid at the outlet of the evaporator 9. This internal heat exchanger 20 comprises in particular an inlet and an outlet of refrigerant fluid from the condenser 5, as well as an inlet and an outlet of refrigerant fluid from the evaporator 9.

En fonctionnement, et comme le montre la figure 2b, les étapes sont similaires à celles des figures la et 1b, à la différence que l'échangeur de chaleur interne 20 absorbant de l'enthalpie au fluide réfrigérant comme le montre la flèche 200a et en la transférant au fluide réfrigérant en sortie de l'évaporateur 9 comme le montre la flèche 200b. Le sous-refroidissement SR du fluide réfrigérant avant qu'il ne traverse le dispositif de détente 7 et la surchauffe SHcomp_in du fluide réfrigérant avant qu'il ne rentre dans le compresseur 3 sont tous deux augmentés sous l'effet de l'échangeur de chaleur interne 20. Cela permet notamment une augmentation du coefficient de performance du circuit de climatisation 1.In operation, and as shown in the figure 2b , the steps are similar to those of FIGS. 1a and 1b, except that the internal heat exchanger 20 absorbs enthalpy from the refrigerant fluid as shown by the arrow 200a and transfers it to the refrigerant fluid at the outlet of the evaporator 9 as shown by the arrow 200b. The subcooling SR of the refrigerant fluid before it passes through the expansion device 7 and the superheat SHcomp_in of the refrigerant fluid before it enters the compressor 3 are both increased under the effect of the heat exchanger internal 20. This allows in particular an increase in the coefficient of performance of the air conditioning circuit 1.

Le circuit de climatisation 1 peut par exemple être un circuit de climatisation inversible indirect 1 comme illustré sur la figure 3. Ce circuit de climatisation inversible indirect 1 peut fonctionner dans différents modes de fonctionnement dont un mode de refroidissement.The air conditioning circuit 1 can for example be an indirect reversible air conditioning circuit 1 as illustrated in the picture 3 . This indirect reversible air conditioning circuit 1 can operate in different operating modes including a cooling mode.

Ce circuit de climatisation inversible indirect 1 comporte notamment :

  • une première boucle de fluide réfrigérant A dans laquelle circule le fluide réfrigérant,
  • une deuxième boucle de fluide caloporteur B dans laquelle circule le premier fluide caloporteur 50, et
  • un échangeur de chaleur bifluide correspondant au condenseur 5 agencé conjointement sur la première boucle de fluide réfrigérant A et sur la deuxième boucle de fluide caloporteur B, de façon à permettre les échanges de chaleur entre ladite première boucle de fluide réfrigérant A et ladite deuxième boucle de fluide caloporteur B.
This indirect reversible air conditioning circuit 1 comprises in particular:
  • a first refrigerant loop A in which the refrigerant circulates,
  • a second heat transfer fluid loop B in which the first heat transfer fluid 50 circulates, and
  • a two-fluid heat exchanger corresponding to condenser 5 arranged jointly on the first loop of refrigerant fluid A and on the second loop of heat transfer fluid B, so as to allow heat exchanges between said first loop of refrigerant fluid A and said second loop of heat transfer fluid B.

La première boucle de fluide réfrigérant A, représentée en trait plein sur la figure 3, comporte plus particulièrement dans le sens de circulation du fluide réfrigérant :

  • ∘ un compresseur 3,
  • ∘ l'échangeur de chaleur bifluide 5, disposé en aval dudit compresseur 3,
  • ∘ un premier dispositif de détente 7, plus précisément une vanne électronique d'expansion,
  • ∘ un évaporateur 9 étant destiné à être traversé par le deuxième fluide caloporteur 90 qui est ici un flux d'air intérieur au véhicule automobile allant vers l'habitacle,
  • ∘ un deuxième dispositif de détente 21, par exemple un orifice tube,
  • ∘ un évapo-condenseur 13 étant destiné à être traversé par un flux d'air extérieur 200 au véhicule automobile, et
  • ∘ une conduite de contournement 30 de l'évapo-condenseur 13.
The first refrigerant fluid loop A, shown in solid line on the picture 3 , comprises more particularly in the direction of circulation of the refrigerant fluid:
  • ∘ a compressor 3,
  • ∘ the two-fluid heat exchanger 5, arranged downstream of said compressor 3,
  • ∘ a first expansion device 7, more precisely an electronic expansion valve,
  • ∘ an evaporator 9 being intended to be crossed by the second heat transfer fluid 90 which here is a flow of air inside the motor vehicle going towards the passenger compartment,
  • ∘ a second expansion device 21, for example a tube orifice,
  • ∘ an evapo-condenser 13 being intended to be crossed by a flow of air 200 outside the motor vehicle, and
  • ∘ a bypass pipe 30 of the evapo-condenser 13.

La conduite de contournement 30 peut relier plus spécifiquement un premier point de raccordement 31 et un deuxième point de raccordement 32.The bypass pipe 30 can connect more specifically a first connection point 31 and a second connection point 32.

Le premier point de raccordement 31 est de préférence disposé, dans le sens de circulation du fluide réfrigérant, en aval de l'évaporateur 9, entre ledit évaporateur 9 et l'évapo-condenseur 13. Plus particulièrement, et comme illustré sur la figure 3, le premier point de raccordement 31 est disposé entre l'évaporateur 9 et le deuxième dispositif de détente 21. Il est cependant tout à fait possible d'imaginer que le premier point de raccordement 31 soit disposé entre le deuxième dispositif de détente 21 et l'évapo-condenseur 13 du moment que le fluide réfrigérant a la possibilité de contourner le deuxième dispositif de détente 21 ou de le traverser sans subir de perte de pression.The first connection point 31 is preferably arranged, in the direction of circulation of the refrigerant fluid, downstream of the evaporator 9, between the said evaporator 9 and the evapo-condenser 13. More particularly, and as illustrated in the picture 3 , the first connection point 31 is arranged between the evaporator 9 and the second expansion device 21. It is however quite possible to imagine that the first connection point 31 is arranged between the second expansion device 21 and the evapo-condenser 13 as long as the refrigerant fluid has the possibility of bypassing the second expansion device 21 or of passing through it without suffering a loss of pressure.

Le deuxième point de raccordement 32 est quant à lui de préférence disposé en aval de l'évapo-condenseur 13, entre ledit évapo-condenseur 13 et le compresseur 3.The second connection point 32 is for its part preferably disposed downstream of the evapo-condenser 13, between said evapo-condenser 13 and the compressor 3.

Le circuit de climatisation inversible indirecte 1 comporte également un dispositif de redirection du fluide réfrigérant en provenance de l'évaporateur 9 vers l'évapo-condenseur 13 ou vers la conduite de contournement 30.The indirect reversible air conditioning circuit 1 also comprises a device for redirecting the refrigerant fluid coming from the evaporator 9 to the evapo-condenser 13 or to the bypass line 30.

Ce dispositif de redirection du fluide réfrigérant en provenance de l'évaporateur 9 peut notamment comporter :

  • une première vanne d'arrêt 22 disposée en aval du premier point de raccordement 31, entre ledit premier point de raccordement 31 et le deuxième dispositif de détente 21,
  • une deuxième vanne d'arrêt 33 disposée sur la conduite de contournement 30, et
  • un clapet antiretour 23 disposé en aval du deuxième échangeur de chaleur 13, entre ledit évapo-condenseur 13 et le deuxième point de raccordement 32.
This device for redirecting the refrigerant fluid coming from the evaporator 9 may in particular comprise:
  • a first shut-off valve 22 disposed downstream of the first connection point 31, between said first connection point 31 and the second expansion device 21,
  • a second shut-off valve 33 arranged on the bypass pipe 30, and
  • a check valve 23 disposed downstream of the second heat exchanger 13, between said evapo-condenser 13 and the second connection point 32.

Une autre alternative (non représentée) peut également être de disposer une vanne trois-voies au niveau du premier point de raccordement 31.Another alternative (not shown) can also be to arrange a three-way valve at the level of the first connection point 31.

Par vanne d'arrêt, clapet antiretour, vanne trois-voies ou dispositif de détente avec fonction d'arrêt, on entend ici des éléments mécaniques ou électromécaniques pouvant être pilotés par l'unité centrale de contrôle 10.By stop valve, non-return valve, three-way valve or expansion device with stop function, is meant here mechanical or electromechanical elements that can be controlled by the central control unit 10.

Comme illustré sur la figure 3, la première boucle de fluide réfrigérant A peut comporter, en supplément de l'échangeur de chaleur interne 20, un deuxième échangeur de chaleur interne 20' permettant un échange de chaleur entre le fluide réfrigérant à haute pression en sortie de l'échangeur de chaleur interne 20 et le fluide réfrigérant à basse pression circulant dans la conduite de contournement 30, c'est-à-dire en provenance du premier point de raccordement 31. Par fluide réfrigérant à haute pression on entend par là un fluide réfrigérant ayant subi une augmentation de pression au niveau du compresseur 3 et qu'il n'a pas encore subi de perte de pression du fait de la vanne électronique d'expansion 7 ou de l'orifice tube 11. Ce deuxième échangeur de chaleur interne 20' comporte notamment une entrée et une sortie de fluide réfrigérant en provenance du premier point de raccordement 31, ainsi qu'une entrée et une sortie de fluide réfrigérant à haute pression en provenance de l'échangeur de chaleur interne 20.As illustrated on the picture 3 , the first refrigerant loop A may comprise, in addition to the internal heat exchanger 20, a second internal heat exchanger 20' allowing heat exchange between the high-pressure refrigerant at the outlet of the heat exchanger internal 20 and the low-pressure refrigerant fluid flowing in the bypass line 30, that is to say coming from the first connection point 31. By high-pressure refrigerant fluid is meant a refrigerant fluid having undergone an increase of pressure at the level of the compressor 3 and that it has not yet suffered a loss of pressure due to the electronic expansion valve 7 or the tube orifice 11. This second internal heat exchanger 20 'in particular comprises a inlet and an outlet of refrigerant fluid from the first connection point 31, as well as an inlet and an outlet of high pressure refrigerant fluid from the internal heat exchanger 20.

Au moins un des deux échangeurs de chaleur interne 20, 20'peut être un échangeur de chaleur coaxial, c'est à dire comportant deux tubes coaxiaux et entre lesquels s'effectuent les échanges de chaleur.At least one of the two internal heat exchangers 20, 20′ can be a coaxial heat exchanger, that is to say comprising two coaxial tubes and between which heat exchanges take place.

De préférence, l'échangeur de chaleur interne 20 peut être un échangeur de chaleur interne coaxial d'une longueur comprise entre 50 et 120mm alors que le deuxième échangeur de chaleur interne 20' peut être un échangeur de chaleur interne coaxial d'une longueur comprise entre 200 et 700mm.Preferably, the internal heat exchanger 20 can be a coaxial internal heat exchanger with a length of between 50 and 120mm while the second internal heat exchanger 20' can be a coaxial internal heat exchanger with a length between 200 and 700mm.

La première boucle de fluide réfrigérant A peut comporter une bouteille déshydratante 18 disposée en aval de l'échangeur de chaleur bifluide 5, plus précisément entre ledit échangeur de chaleur bifluide 5 et l'échangeur de chaleur interne 20. Une telle bouteille déshydratante 18 disposée sur le côté haute pression du circuit de climatisation, c'est à dire en aval du compresseur 3 et en amont d'un dispositif de détente, a un encombrement moindre ainsi qu'un coût réduit par rapport à d'autres solutions de séparation de phase comme un accumulateur qui serait disposé du côté basse pression du circuit de climatisation, c'est à dire en amont du compresseur 3, notamment en amont de l'échangeur de chaleur interne 20.The first refrigerant fluid loop A may comprise a dehydrating bottle 18 disposed downstream of the bifluid heat exchanger 5, more precisely between said bifluid heat exchanger 5 and the internal heat exchanger 20. Such a dehydrating bottle 18 disposed on the high pressure side of the air conditioning circuit, that is to say downstream of the compressor 3 and upstream of an expansion device, has a smaller footprint as well as a reduced cost compared to other phase separation solutions such as an accumulator which would be placed on the low pressure side of the air conditioning circuit, that is to say upstream of the compressor 3, in particular upstream of the internal heat exchanger 20.

La deuxième boucle de fluide caloporteur B, représentée en trait comprenant trois tirets et deux points sur la figure 3, peut comporter quant à elle :

  • ∘ l'échangeur de chaleur bifluide 5,
  • ∘ une première conduite de circulation 70 du premier fluide caloporteur 50 comportant un radiateur interne 54 destiné à être traversé par le flux d'air intérieur 90 au véhicule automobile, et reliant un premier point de jonction 61 disposé en aval de l'échangeur de chaleur bifluide 5 et un deuxième point de jonction 62 disposé en amont dudit échangeur de chaleur bifluide 5,
  • ∘ une deuxième conduite de circulation 60 de fluide caloporteur comportant un radiateur externe 64 destiné à être traversé par le flux d'air extérieur 200 au véhicule automobile, et reliant le premier point de jonction 61 disposé en aval de l'échangeur de chaleur bifluide 5 et le deuxième point de jonction 62 disposé en amont dudit échangeur de chaleur bifluide 5, et
  • ∘ une pompe 17 disposée en aval ou en amont de l'échangeur de chaleur bifluide 5, entre le premier point de jonction 61 et le deuxième point de jonction 62.
The second heat transfer fluid loop B, shown as a line comprising three dashes and two dots on the picture 3 , may include:
  • ∘ the two-fluid heat exchanger 5,
  • ∘ a first circulation pipe 70 for the first heat transfer fluid 50 comprising an internal radiator 54 intended to be crossed by the interior air flow 90 to the motor vehicle, and connecting a first junction point 61 disposed downstream of the heat exchanger bifluid 5 and a second junction point 62 arranged upstream of said bifluid heat exchanger 5,
  • ∘ a second heat transfer fluid circulation pipe 60 comprising an external radiator 64 intended to be crossed by the flow of air 200 outside the motor vehicle, and connecting the first junction point 61 arranged downstream of the two-fluid heat exchanger 5 and the second junction point 62 arranged upstream of said two-fluid heat exchanger 5, and
  • ∘ a pump 17 arranged downstream or upstream of the two-fluid heat exchanger 5, between the first junction point 61 and the second junction point 62.

Le circuit de climatisation inversible indirecte 1 comporte au sein de la deuxième boucle de fluide caloporteur B un dispositif de redirection du fluide caloporteur en provenance de l'échangeur de chaleur bifluide 5 vers la première conduite de circulation 70 et/ou vers la deuxième conduite de circulation 60.The indirect reversible air conditioning circuit 1 comprises within the second heat transfer fluid loop B a device for redirecting the heat transfer fluid coming from the two-fluid heat exchanger 5 to the first circulation pipe 70 and/or to the second heat transfer pipe. circulation 60.

Comme illustré sur la figure 3, le dispositif de redirection du fluide caloporteur en provenance de l'échangeur de chaleur bifluide 5 peut notamment comporter une quatrième vanne d'arrêt 63 disposée sur la deuxième conduite de circulation 60 afin de bloquer ou non le premier fluide caloporteur et l'empêcher de circuler dans ladite deuxième conduite de circulation 60.As illustrated on the picture 3 , the device for redirecting the heat transfer fluid coming from the two-fluid heat exchanger 5 may in particular comprise a fourth shut-off valve 63 arranged on the second circulation pipe 60 in order to block or not the first heat transfer fluid and prevent it from circulate in said second circulation pipe 60.

Le circuit de climatisation inversible indirect 1 peut également comporter un volet d'obstruction 310 du flux d'air intérieur 100 traversant le troisième échangeur de chaleur 54.The indirect reversible air conditioning circuit 1 may also include a shutter 310 for obstructing the interior air flow 100 passing through the third heat exchanger 54.

Ce mode de réalisation permet notamment de limiter le nombre de vannes sur la deuxième boucle de fluide caloporteur B et ainsi permet de limiter les coûts de production.This embodiment makes it possible in particular to limit the number of valves on the second heat transfer fluid loop B and thus makes it possible to limit production costs.

Selon un mode de réalisation alternatif non représenté le dispositif de redirection du fluide caloporteur en provenance de l'échangeur de chaleur bifluide 5 peut notamment comporter une quatrième vanne d'arrêt 63 disposée sur la deuxième conduite de circulation 60 afin de bloquer ou non le fluide caloporteur et de l'empêcher de circuler dans ladite deuxième conduite de circulation 60, et une cinquième vanne d'arrêt disposée sur la première conduite de circulation 70 afin de bloquer ou non le fluide caloporteur et de l'empêcher de circuler dans ladite première conduite de circulation 70.According to an alternative embodiment not shown, the device for redirecting the heat transfer fluid coming from the two-fluid heat exchanger 5 may in particular comprise a fourth shut-off valve 63 arranged on the second circulation pipe 60 in order to block or not block the fluid coolant and to prevent it from flowing in said second circulation pipe 60, and a fifth shut-off valve arranged on the first circulation pipe 70 in order to block or not the heat transfer fluid and to prevent it from flowing in said first pipe traffic 70.

La deuxième boucle de fluide caloporteur B peut également comporter un élément électrique chauffant 55 du fluide caloporteur. Ledit élément électrique chauffant 55 est notamment disposé, dans le sens de circulation du fluide caloporteur, en aval de l'échangeur de chaleur bifluide 5, entre ledit échangeur de chaleur bifluide 5 et le premier point de jonction 61.The second loop of heat transfer fluid B may also include an electric heating element 55 of the heat transfer fluid. Said electrical heating element 55 is in particular arranged, in the direction of circulation of the heat transfer fluid, downstream of the bifluid heat exchanger 5, between said bifluid heat exchanger 5 and the first junction point 61.

En mode de refroidissement, le fluide réfrigérant ne passe pas par l'évapo-condenseur 13 mais passe par la conduite de contournement 30. Le premier fluide réfrigérant 50 passe quant à lui dans le radiateur externe 64 afin d'évacuer de l'énergie calorifique dans le flux d'air externe 200.In cooling mode, the refrigerant fluid does not pass through the evapo-condenser 13 but passes through the bypass line 30. The first refrigerant fluid 50 passes for its part into the external radiator 64 in order to evacuate heat energy in the external airflow 200.

Il est tout à fait possible également d'imaginer une autre architecture du circuit de climatisation 1 sans pour autant sortir du cadre de l'invention du moment qu'en mode refroidissement, le fluide réfrigérant passe successivement par un compresseur 3, un condenseur 5, un dispositif de détente 7 et un évaporateur 9.It is also quite possible to imagine another architecture of the air conditioning circuit 1 without departing from the scope of the invention as long as in cooling mode, the refrigerant fluid passes successively through a compressor 3, a condenser 5, an expansion device 7 and an evaporator 9.

La présente invention concerne un procédé de gestion du circuit de climatisation 1 en mode refroidissement et plus précisément de la gestion du contrôle de l'ouverture du dispositif de détente 7 et donc de la perte de pression du fluide réfrigérant lorsqu'il traverse ledit dispositif de détente 7.The present invention relates to a method for managing the air conditioning circuit 1 in cooling mode and more precisely for managing the control of the opening of the expansion device 7 and therefore of the loss of pressure of the refrigerant fluid when it passes through said device. relaxation 7.

Le procédé de gestion comporte :

  • une première étape de :
    • ∘ calcul de l'ouverture Cestim du dispositif de détente 7 à partir de mesures de paramètres de fonctionnement du circuit de climatisation 1, et de
    • ∘ détermination d'une surchauffe consigne SHcomp_in_sp en fonction de l'état du fluide réfrigérant en sortie de l'évaporateur 9 et de la température Text du premier fluide caloporteur. Dans cette première étape, SHcomp_in_sp est comprise entre une surchauffe minimale SHcomp_in_sp_min et une surchauffe maximale Shcomp_in_sp_max,
  • une deuxième étape d'ouverture du dispositif de détente 7 selon Cestim et de contrôle de la surchauffe SHcomp_in en faisant varier l'ouverture du dispositif de détente 7 de sorte à atteindre la surchauffe consigne SHcomp_in_sp et maintenir SHcomp_in entre SHcomp_in_sp_min et SHcomp_in_sp_max.
The management process includes:
  • a first step of:
    • ∘ calculation of the Cestim opening of the expansion device 7 from measurements of operating parameters of the air conditioning circuit 1, and from
    • ∘ determination of a set superheat SHcomp_in_sp according to the state of the refrigerant fluid at the outlet of the evaporator 9 and the temperature Text of the first heat transfer fluid. In this first step, SHcomp_in_sp is between a minimum superheat SHcomp_in_sp_min and a maximum superheat Shcomp_in_sp_max,
  • a second step of opening the expansion device 7 according to Cestim and controlling the overheating SHcomp_in by varying the opening of the expansion device 7 so as to reach the setpoint overheating SHcomp_in_sp and maintain SHcomp_in between SHcomp_in_sp_min and SHcomp_in_sp_max.

Le calcul de l'ouverture Cestim du dispositif de détente 7 et la détermination de la surchauffe consigne Shcomp_in sont réalisés simultanément par l'unité centrale de contrôle 10.The calculation of the Cestim opening of the expansion device 7 and the determination of the overheating setpoint Shcomp_in are carried out simultaneously by the central control unit 10.

Lors de la première étape, le calcul de l'ouverture Cestim du dispositif de détente 7 est réalisé selon l'une des formules suivantes : Cestim = K 1 * Tevapo − Tevapo _ sp + K 2 * Tsat Pcomp _ out − Text

Figure imgb0005
ou Cestim = K 1 ′ * Pcomp _ in − Psat Tevapo _ sp + K 2 * Tsat Pcomp _ out − Text
Figure imgb0006

  • Tevapo est la température du second fluide caloporteur 90 en sortie de l'évaporateur 9, mesurée par le cinquième capteur 15,
  • Tevapo_sp est une température consigne du second fluide caloporteur 90 en sortie de l'évaporateur 9. Cette température consigne Tevapo_sp est déterminée par l'unité centrale de contrôle 10 en fonction de la température demandée par l'utilisateur à l'intérieur de habitacle par exemple.
  • Tsat(Pcomp_out) est la température de saturation du fluide réfrigérant à la pression Pcomp_out du fluide réfrigérant en sortie du compresseur 3, la pression Pcomp_out étant mesurée par le deuxième capteur 12.
  • Text est la température du premier fluide caloporteur 50 avant sa traversée du condenseur 5, mesurée par le premier capteur 11.
  • Pcomp_in est la pression du fluide réfrigérant en entrée du compresseur 3, mesurée par le troisième capteur 13.
  • Psat(Tevapo_sp) est la pression de saturation du fluide réfrigérant à la température consigne Tevapo du second fluide caloporteur 90 en sortie de l'évaporateur 90.
  • K1 correspond à la pente moyenne ΔC/ΔTevapo avec ΔC étant la variation de l'ouverture du dispositif de détente 7 et de ΔTevapo la variation de Tevapo mesurées lors d'expérimentation où l'on fait varier l'ouverture du dispositif de détente 7 pour un régime du compresseur 3 donné, un débit donné du premier fluide caloporteur 50 traversant le condenseur 5 et selon la valeur de Text. Cette constante K1 est déterminée par expérimentation et par les données stockées dans l'unité centrale de commande 10. La variation de l'ouverture du dispositif de détente 7 ΔC s'effectue entre son ouverture maximum et son ouverture minimum.
  • K1' correspond à la pente moyenne ΔC/ΔPcomp_in avec ΔC étant la variation de l'ouverture du dispositif de détente 7 et de ΔPcomp_in la variation de Pcomp_in mesurées lors d'expérimentation où l'on fait varier l'ouverture du dispositif de détente 7 pour un régime du compresseur 3 donné et un débit donné de premier fluide caloporteur 50 traversant le condenseur 5 et selon la valeur de Text. Cette constante K1' est déterminée par expérimentation et par les données stockées dans l'unité centrale de commande 10. La variation de l'ouverture du dispositif de détente 7 ΔC s'effectue entre son ouverture maximum et son ouverture minimum.
  • K2 correspond à la pente moyenne ΔC/Δ(Tsat(Pcomp_out) - Text) avec ΔC étant la variation de l'ouverture du dispositif de détente 7 et de Δ(Tsat(Pcomp_out)-Text) la variation de (Tsat(Pcomp_out) - Text) mesurées et calculées lors d'expérimentation où l'on fait varier l'ouverture du dispositif de détente 7 pour un régime du compresseur 3 donné et un débit donné de premier fluide caloporteur 50 traversant le condenseur 5 et selon la valeur de Text. Cette constante K1' est déterminée par expérimentation et par les données stockées dans l'unité centrale de commande 10. La variation de l'ouverture du dispositif de détente 7 ΔC s'effectue entre son ouverture maximum et son ouverture minimum.
During the first step, the calculation of the Cestim opening of the expansion device 7 is carried out according to one of the following formulas: Cestim = K 1 * Tevapo − Tevapo _ sp + K 2 * Tsat Pcomp _ out − text
Figure imgb0005
 Where Cestim = K 1 ′ * Pcomp _ in − psat Tevapo _ sp + K 2 * Tsat Pcomp _ out − text
Figure imgb0006
  • Tevapo is the temperature of the second heat transfer fluid 90 at the outlet of the evaporator 9, measured by the fifth sensor 15,
  • Tevapo_sp is a setpoint temperature of the second heat transfer fluid 90 at the outlet of the evaporator 9. This setpoint temperature Tevapo_sp is determined by the central control unit 10 according to the temperature requested by the user inside the passenger compartment, for example .
  • Tsat(Pcomp_out) is the saturation temperature of the refrigerant fluid at the pressure Pcomp_out of the refrigerant fluid at the outlet of the compressor 3, the pressure Pcomp_out being measured by the second sensor 12.
  • Text is the temperature of the first heat transfer fluid 50 before it passes through the condenser 5, measured by the first sensor 11.
  • Pcomp_in is the pressure of the refrigerant fluid entering compressor 3, measured by third sensor 13.
  • Psat(Tevapo_sp) is the saturation pressure of the refrigerant at the setpoint temperature Tevapo of the second heat transfer fluid 90 at the outlet of the evaporator 90.
  • K1 corresponds to the average slope Δ C /Δ Tevapo with Δ C being the variation of the opening of the expansion device 7 and of Δ Tevapo the variation of Tevapo measured during experiments where the opening of the device is varied expansion 7 for a given compressor 3 speed, a given flow rate of the first heat transfer fluid 50 passing through the condenser 5 and according to the value of Text. This constant K1 is determined by experimentation and by the data stored in the central control unit 10. The variation in the opening of the expansion device 7 ΔC takes place between its maximum opening and its minimum opening.
  • K1' corresponds to the average slope Δ C /Δ Pcomp_in with Δ C being the variation of the opening of the expansion device 7 and of Δ Pcomp_in the variation of Pcomp_in measured during experiments where the opening of the expansion device 7 for a given compressor 3 speed and a given flow rate of first heat transfer fluid 50 passing through condenser 5 and according to the value of Text. This constant K1' is determined by experimentation and by the data stored in the central control unit 10. The variation in the opening of the expansion device 7 ΔC takes place between its maximum opening and its minimum opening.
  • K2 corresponds to the average slope Δ C /Δ ( Tsat (Pcomp_out) - Text ) with Δ C being the variation of the opening of the expansion device 7 and of Δ ( Tsat (Pcomp_out) -Text ) the variation of ( Tsat ( Pcomp_out) - Text ) measured and calculated during experimentation where the opening of the expansion device 7 is varied for a given compressor 3 speed and a given flow rate of first heat transfer fluid 50 passing through the condenser 5 and according to the value of Text. This constant K1' is determined by experimentation and by the data stored in the central control unit 10. The variation in the opening of the expansion device 7 ΔC takes place between its maximum opening and its minimum opening.

Les valeurs SHcomp_in_sp_min et SHcomp_in_sp_max sont obtenues par expérimentation et sont déterminées en fonction :

  • de la température Text du premier fluide caloporteur 50 avant sa traversée du condenseur 5,
  • du débit du deuxième fluide caloporteur 90 traversant l'évaporateur 9, et
  • de la température du deuxième fluide caloporteur 90 avant sa traversée de l'évaporateur 9.
Les données concernant SHcomp_in_sp_min et Shcomp_in_sp_max sont stockées dans l'unité centrale de commande 10.The SHcomp_in_sp_min and SHcomp_in_sp_max values are obtained by experimentation and are determined according to:
  • the temperature Text of the first heat transfer fluid 50 before it passes through the condenser 5,
  • the flow rate of the second heat transfer fluid 90 passing through the evaporator 9, and
  • the temperature of the second heat transfer fluid 90 before it passes through the evaporator 9.
The data concerning SHcomp_in_sp_min and Shcomp_in_sp_max are stored in the central control unit 10.

Par exemple, pour un fluide réfrigérant tel que le R134a, SHcomp_in_sp_min peut être comprise entre 3 et 20 °K et SHcomp_in_sp_max comprise ente 8 et 25 °K. SHcomp_in_sp_min et SHcomp_in_sp_max sont variables en fonction de la nature du fluide réfrigérant et de l'architecture du circuit de climatisation 1.For example, for a refrigerant fluid such as R134a, SHcomp_in_sp_min can be between 3 and 20°K and SHcomp_in_sp_max between 8 and 25°K. SHcomp_in_sp_min and SHcomp_in_sp_max are variable depending on the nature of the refrigerant fluid and the architecture of the air conditioning circuit 1.

La détermination de la surchauffe consigne SHcomp_in_sp est notamment illustrée sur le diagramme de la figure 4.The determination of the SHcomp_in_sp setpoint superheat is illustrated in particular on the diagram of the figure 4 .

Pour une valeur de Text inférieure à une valeur définie T1, la valeur de Shcomp_in_sp, toujours comprise entre SHcomp_in_sp_min et SHcomp_in_sp_max, permet une optimisation du coefficient de performance du circuit de climatisation 1 et permet au fluide réfrigérant d'être dans un état gazeux à au moins 90 % à son entrée dans le compresseur 3.For a value of Text less than a defined value T1, the value of Shcomp_in_sp , always between SHcomp_in_sp_min and SHcomp_in_sp_max, allows an optimization of the coefficient of performance of the air conditioning circuit 1 and allows the refrigerant fluid to be in a gaseous state at at least minus 90% as it enters compressor 3.

Pour une valeur de Text supérieure à une valeur définie T2, la valeur de SHcomp_in_sp, toujours comprise entre SHcomp_in_sp_min et SHcomp_in_sp_max, permet au fluide réfrigérant d'être à une température inférieure à la température limite de fonctionnement du compresseur 3 et ainsi évite que ce dernier ne s'arrête en se mettant en sécurité.For a value of Text greater than a defined value T2, the value of SHcomp_in_sp , always between SHcomp_in_sp_min and SHcomp_in_sp_max , allows the refrigerant to be at a temperature below the operating limit temperature of compressor 3 and thus prevents the latter from does not stop by getting to safety.

Pour une valeur de Text comprise entre T1 et T2, la valeur de SHcomp_in_sp, toujours comprise entre SHcomp_in_sp_min et SHcomp_in_sp_max, permet une optimisation du coefficient de performance du circuit de climatisation 1 et de la puissance de refroidissement du deuxième fluide caloporteur 90.For a value of Text between T1 and T2, the value of SHcomp_in_sp , always between SHcomp_in_sp_min and SHcomp_in_sp_max , allows an optimization of the coefficient of performance of the air conditioning circuit 1 and of the cooling power of the second heat transfer fluid 90.

Lors de la deuxième étape de contrôle de la surchauffe Shcomp_in, si SHcomp_in est inférieure à SHcomp_in_sp_min alors l'unité de contrôle 10 va diminuer l'ouverture du dispositif de détente 7 afin d'augmenter la surchauffe SHcomp_in. Si SHcomp_in est supérieure à SHcomp_in_sp_max alors l'unité de contrôle 10 va augmenter l'ouverture du dispositif de détente 7 afin de réduire la surchauffe SHcomp_in. L'augmentation ou la diminution de l'ouverture du dispositif de détente 7 est préférentiellement réalisée par un contrôleur proportionnel intégral.During the second step of controlling the overheating Shcomp_in , if SHcomp_in is less than SHcomp_in_sp_min then the control unit 10 will decrease the opening of the expansion device 7 in order to increase the overheating SHcomp_in. Whether SHcomp_in is greater than SHcomp_in_sp_max then the control unit 10 will increase the opening of the expansion device 7 in order to reduce the overheating SHcomp_in. The increase or decrease in the opening of the expansion device 7 is preferably carried out by a proportional integral controller.

Si SHcomp_in est compris entre SHcomp_in_sp_min et SHcomp_in_sp_max, l'augmentation ou la diminution de l'ouverture du dispositif de détente 7 est préférentiellement réalisée par un contrôleur proportionnel.If SHcomp_in is between SHcomp_in_sp_min and SHcomp_in_sp_max, the increase or decrease in the opening of the expansion device 7 is preferably carried out by a proportional controller.

Le fait d'avoir un contrôle mixte par un contrôleur proportionnel intégral et un contrôleur proportionnel permet d'arriver rapidement à la surchauffe consigne SHcomp_in_sp et de maintenir et de stabiliser efficacement SHcomp_in entre SHcomp_in_sp_min et SHcomp_in_sp_max. The fact of having a mixed control by an integral proportional controller and a proportional controller makes it possible to quickly reach the SHcomp_in_sp setpoint superheat and to effectively maintain and stabilize SHcomp_in between SHcomp_in_sp_min and SHcomp_in_sp_max.

La figure 5 montre un diagramme montrant en traits pleins l'évolution, en fonction du temps, exprimé en minutes, de :

  • la température Tevapo illustrée par la courbe 101a,
  • la surchauffe SHcomp_in illustrée par la courbe 102a, et
  • l'ouverture 103a du dispositif de détente 7, exprimé en impulsions / 100.
The figure 5 shows a diagram showing in solid lines the evolution, as a function of time, expressed in minutes, of:
  • the Tevapo temperature illustrated by the curve 101a,
  • the superheat SHcomp_in illustrated by the curve 102a, and
  • the opening 103a of the expansion device 7, expressed in pulses / 100.

Ces courbes en traits pleins sont réalisées après démarrage pour un circuit de climatisation selon l'art antérieur.These curves in solid lines are produced after start-up for an air conditioning circuit according to the prior art.

En traits pointillés sont représentés l'évolution de la température Tevapo (courbe 101b), de la surchauffe SHcomp_in (courbe 102b) et de l'ouverture (courbe 103b) du dispositif de détente 7 après démarrage pour un circuit de climatisation utilisant un procédé de gestion selon l'invention.In dotted lines are represented the evolution of the temperature Tevapo (curve 101b), of the overheating SHcomp_in (curve 102b) and of the opening (curve 103b) of the expansion device 7 after start-up for an air conditioning circuit using a method of management according to the invention.

Pour ce diagramme de la figure 5, le fluide réfrigérant choisi est le R134a et la température Text est de 45°C.For this diagram of the figure 5 , the chosen refrigerant is R134a and the temperature Text is 45°C.

On remarque alors que le procédé de gestion selon l'invention permet une augmentation de la surchauffe SHcom_in 102b par rapport à la surchauffe SHcom_in 102a. Cette surchauffe SHcom_in 102b est plus importante du fait que l'ouverture 103b selon l'invention est plus faible que l'ouverture 103a selon l'art antérieur. Du fait de cette surchauffe SHcom_in 102b plus importante, la température Tevapo 101b selon l'invention est plus faible que la température Tevapo 101a selon l'art antérieur. Le coefficient de performance est alors augmenté par rapport à l'art antérieur, car le compresseur 3 est à un régime identique que ce soit pour l'art antérieur ou pour le procédé de gestion selon l'invention.It is then noted that the management method according to the invention allows an increase in the overheating SHcom_in 102b with respect to the overheating SHcom_in 102a. This overheating SHcom_in 102b is greater because the opening 103b according to the invention is smaller than the opening 103a according to the prior art. Due to this higher SHcom_in 102b overheating, the Tevapo 101b temperature according to the invention is lower than the temperature Tevapo 101a according to the prior art. The coefficient of performance is then increased compared to the prior art, because the compressor 3 is at an identical speed whether for the prior art or for the management method according to the invention.

Ainsi, on voit bien que le procédé de gestion selon l'invention permet une bonne gestion et un bon contrôle de l'ouverture du dispositif de détente 7 permettant un bon coefficient de performance du circuit de climatisation 1 en mode de refroidissement.Thus, it is clearly seen that the management method according to the invention allows good management and good control of the opening of the expansion device 7 allowing a good coefficient of performance of the air conditioning circuit 1 in cooling mode.

Claims (4)

  1. Method for managing an air-conditioning circuit (1) in which a refrigerant fluid circulates in a cooling mode, the refrigerant fluid circulating successively through:
    • a compressor (3),
    • a condenser (5) intended to release heat energy from the refrigerant fluid into a first heat-transfer fluid (50),
    • an expansion device (7), and
    • an evaporator (9) intended to recover heat energy from a second heat-transfer fluid (90) and transfer it to the refrigerant fluid,
    said air-conditioning circuit (1) comprising a central control unit (10) able to control the opening of the expansion device (7),
    said method comprising:
    • a step of:
    ∘ calculating the opening Cestim of the expansion device (7) from measurements of operating parameters of the air-conditioning circuit (1), and of
    ∘ determining a superheating setpoint SHcomp_in_sp as a function of the state of the refrigerant fluid leaving the evaporator (9) and of the temperature Text of the first heat-transfer fluid (50) before it passes through the condenser (5), SHcomp_in_sp being comprised between a superheating minimum SHcomp_in_sp_min and a superheating maximum SHcomp_in_sp_max, SHcomp_in_sp_min and SHcomp_in_sp_max being determined as a function of the temperature Text of the first heat-transfer fluid (50) before it passes through the condenser (5), of the flow rate of the second heat-transfer fluid (90) passing through the evaporator (9) and of the temperature of the second heat-transfer fluid (90) before it passes through the evaporator (9), the values SHcomp_in_sp_min and SHcomp_in_sp_max being obtained by experimentation and being variable as a function of the nature of the refrigerant fluid and of the layout of the air-conditioning circuit (1),
    • a step of opening the expansion device (7) according to Cestim and of controlling the superheating SHcomp_in by varying the opening of the expansion device (7) so as to achieve the setpoint superheating SHcomp_in_sp and keep SHcomp_in between SHcomp_in_sp_min and SHcomp_in_sp_max,
    in which method SHcomp_in is calculated according to the following formula:
    SHcomp_in = Tcomp_in - Tsat(Pcomp_in),in which Tcomp_in is the temperature of the refrigerant fluid at the inlet of the compressor (3), and Tsat(Pcomp_in) is the saturation temperature of refrigerant fluid at the pressure Pcomp_in at the inlet of the compressor (3), in which method the calculation of the opening Cestim of the expansion device (7) is performed using one of the following formulae: Cestim = K 1 * Tevapo − Tevapo _ sp + K 2 * Tsat Pcomp _ out − Text
    Figure imgb0011
     or Cestim = K 1 ′ * Pcomp _ in − Psat Tevapo _ sp + K 2 * Tsat Pcomp _ out − Text
    Figure imgb0012
     in which formulae,
    Tevapo is the temperature of the second heat-transfer fluid (90) at the outlet of the evaporator (9),
    Tevapo_sp is a temperature setpoint of the second heat-transfer fluid (90) at the outlet of the evaporator (9),
    Tsat(Pcomp_out) is the saturation temperature of the refrigerant fluid at the pressure Pcomp_out of the refrigerant fluid at the outlet of the compressor (3),
    Text is the temperature of the first heat-transfer fluid (50) before it passes through the condenser (5),
    Pcomp_in is the pressure of the refrigerant fluid at the inlet of the compressor (3),
    Psat(Tevapo_sp) is the saturation pressure of the refrigerant fluid at the setpoint temperature Tevapo of the second heat-transfer fluid (90) at the outlet of the evaporator (90),
    K1 being the mean gradient ΔC/ΔTevapo with ΔC being the variation in the opening of the expansion device (7) and ΔTevapo the variation in Tevapo which are measured during experimentation in which the opening of the expansion device (7) is varied for a given speed of the compressor (3), a given flow rate of the first heat-transfer fluid (50) passing through the condenser (5) and according to the value of Text,
    K1' being the mean gradient ΔC/ΔPcomp_in with ΔC being the variation in the opening of the expansion device (7) and ΔPcomp_in the variation in Pcomp_in which are measured during the experimentation in which the opening of the expansion device (7) is varied for a given speed of the compressor (3) and a given flow rate of first heat-transfer fluid (50) passing through the condenser (5) and according to the value of Text, and
    K2 being the mean gradient ΔC/Δ(Tsat(Pcomp_out)-Text) with ΔC being the variation in the opening of the expansion device (7) and Δ(Tsat(Pcomp_out) - Text) the variation in (Tsat(Pcomp_out) - Text) which are measured and calculated during experimentation in which the opening of the expansion device (7) is varied for a given speed of the compressor (3) and a given flow rate of first heat-transfer fluid (50) passing through the condenser (5) and according to the value of Text.
  2. Method for managing an air-conditioning circuit (1) according to Claim 1, characterized in that SHcomp_in_sp_min is comprised between 3 and 20°K and SHcomp_in_sp_max is comprised between 8 and 25°K.
  3. Method for managing an air-conditioning circuit (1) according to one of the preceding claims, characterized in that during the step of controlling the superheating SHcomp_in:
    • if SHcomp_in is below SHcomp_in_sp_min or above SHcomp_in_sp_max, the increase or decrease in opening of the expansion device (7) is performed by a proportional integral controller,
    • if SHcomp_in is comprised between SHcomp_in_sp_min and SHcomp_in_sp_max, the increase or decrease in opening of the expansion device (7) is performed by a proportional controller.
  4. Method for managing an air-conditioning circuit (1) according to one of the preceding claims, characterized in that it comprises an internal heat exchanger (20) able to allow exchanges of heat energy between the refrigerant fluid leaving the condenser (5) and the refrigerant fluid leaving the evaporator (9).
EP18755870.5A 2017-07-28 2018-07-26 Method for managing an air conditioning circuit of a motor vehicle Active EP3658832B1 (en)

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FR1757227A FR3069626B1 (en) 2017-07-28 2017-07-28 METHOD FOR MANAGING A MOTOR VEHICLE AIR CONDITIONING CIRCUIT
PCT/FR2018/051922 WO2019020952A1 (en) 2017-07-28 2018-07-26 Method for managing an air-conditioning circuit of a motor vehicle

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FR2913102B1 (en) * 2007-02-28 2012-11-16 Valeo Systemes Thermiques AIR CONDITIONING INSTALLATION EQUIPPED WITH AN ELECTRICAL RELIEF VALVE
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JP6189098B2 (en) * 2013-06-14 2017-08-30 三菱重工オートモーティブサーマルシステムズ株式会社 Heat pump air conditioning system for vehicles
US20150059373A1 (en) * 2013-09-05 2015-03-05 Beckett Performance Products, Llc Superheat and sub-cooling control of refrigeration system
US9874384B2 (en) * 2016-01-13 2018-01-23 Bergstrom, Inc. Refrigeration system with superheating, sub-cooling and refrigerant charge level control
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FR3069626B1 (en) 2019-12-27

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