EP4330064A1 - Verfahren zur steuerung einer wärmeverwaltungsvorrichtung - Google Patents

Verfahren zur steuerung einer wärmeverwaltungsvorrichtung

Info

Publication number
EP4330064A1
EP4330064A1 EP22727041.0A EP22727041A EP4330064A1 EP 4330064 A1 EP4330064 A1 EP 4330064A1 EP 22727041 A EP22727041 A EP 22727041A EP 4330064 A1 EP4330064 A1 EP 4330064A1
Authority
EP
European Patent Office
Prior art keywords
cooler
refrigerant
pressure
temperature
electronic expansion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP22727041.0A
Other languages
English (en)
French (fr)
Inventor
Mohamed Yahia
Stefan Karl
Jinming Liu
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo Systemes Thermiques SAS
Original Assignee
Valeo Systemes Thermiques SAS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Valeo Systemes Thermiques SAS filed Critical Valeo Systemes Thermiques SAS
Publication of EP4330064A1 publication Critical patent/EP4330064A1/de
Pending legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/323—Cooling devices using compression characterised by comprising auxiliary or multiple systems, e.g. plurality of evaporators, or by involving auxiliary cooling devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00271—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit
    • B60H1/00278—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit for the battery
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3228—Cooling devices using compression characterised by refrigerant circuit configurations
    • B60H1/32281—Cooling devices using compression characterised by refrigerant circuit configurations comprising a single secondary circuit, e.g. at evaporator or condenser side
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/0073—Control systems or circuits characterised by particular algorithms or computational models, e.g. fuzzy logic or dynamic models
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00271—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit
    • B60H2001/00307—Component temperature regulation using a liquid flow
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3236—Cooling devices information from a variable is obtained
    • B60H2001/3255—Cooling devices information from a variable is obtained related to temperature
    • B60H2001/3257—Cooling devices information from a variable is obtained related to temperature of the refrigerant at a compressing unit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3236—Cooling devices information from a variable is obtained
    • B60H2001/3255—Cooling devices information from a variable is obtained related to temperature
    • B60H2001/3263—Cooling devices information from a variable is obtained related to temperature of the refrigerant at an evaporating unit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3269—Cooling devices output of a control signal
    • B60H2001/3285—Cooling devices output of a control signal related to an expansion unit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser

Definitions

  • the invention relates to the field of electric and hybrid motor vehicles and more particularly to a method for managing a thermal management device for such a motor vehicle.
  • a thermal management device comprising a circulation circuit for a refrigerant fluid.
  • This refrigerant circuit generally comprises a compressor, a condenser placed in an external air flow, an expansion device and an evaporator placed in an internal air flow intended for the passenger compartment.
  • This refrigerant circuit can thus cool the internal air flow in a cooling mode in order to ensure optimum comfort for the occupants of the passenger compartment.
  • the refrigerant circuit can also be more complex and allow operation in a heat pump mode in order to heat the internal air flow.
  • the thermal management device and its refrigerant circuit to regulate the thermal of these elements.
  • the refrigerant circuit then generally comprises a heat exchanger as well as a dedicated expansion device for each of these elements as well as various circulation and bypass branches making it possible to ensure good thermal management of these elements at different temperatures.
  • Such architectures require many sensors as well as complex control processes involving the data collected by these sensors in order to ensure proper operation. This thus generates significant costs for the thermal management device.
  • 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 controlling an improved thermal management device allowing a reduction in the number of sensors and thus a decrease in costs.
  • the present invention relates to a method for controlling a thermal management device for an electric or hybrid motor vehicle, said thermal management device comprising a circulation circuit for a refrigerant fluid comprising:
  • main branch comprising a compressor, an external heat exchanger, a first electronic expansion valve, an evaporator,
  • first bypass branch connected in parallel with the first electronic expansion valve and the evaporator, said first bypass branch comprising a second electronic expansion valve arranged upstream of a first cooler in the direction of flow refrigerant fluid, the first cooler being configured to allow heat exchange between the refrigerant fluid and a heat transfer fluid circulating in at least one circulation loop of said heat transfer fluid configured for the thermal management of an element of the motor vehicle, said method comprising, for controlling the opening of the second electronic expansion valve, a step of estimating the discharge temperature of the refrigerating fluid Tro7 at the outlet of the first cooler, said estimation of the discharge temperature Tro7 refrigerant fluid being produced according to the following formula (a):
  • Tro7 Tsat7 + eff7 x (Twi7 — Tsat7 ) with Tsat7 the saturation temperature of the refrigerant at the pressure of said refrigerant Pro7 at the outlet of the first cooler,
  • Gw7 the conductance of the heat transfer fluid determined according to the flow rate of heat transfer fluid Mw7 passing through the first cooler
  • the pressure of said refrigerant fluid Pro7 at the outlet of the first cooler is estimated as a function of the pressure P3 and the temperature T3 in upstream of the compressor, the speed of rotation Ne of said compressor and the opening of the second electronic expansion valve.
  • the circulation circuit of a refrigerant fluid com carries a second bypass branch connected in parallel with the first bypass branch as well as the first electronic expansion valve and the evaporator, said second bypass branch comprising a third electronic expansion valve arranged upstream of a second cooler, the second cooler being configured to allow heat exchanges between the refrigerant fluid and a heat transfer fluid circulating in at least a circulation loop of said heat transfer fluid configured for the thermal management of an element of the motor vehicle distinct from that of the first cooler, said method comprising, for controlling the opening of the third electronic expansion valve, a step of estimation of the discharge temperature of the refrigerating fluid Tro at the outlet of the second cooler, said estimation of the temperature Tro9 refrigerant fluid delivery point being carried out according to the following formula (a’):
  • Tro9 Tsat9 + eff9 x ( Twi9 — Tsat9 ) with Tsat9 the saturation temperature of the refrigerant at the pressure of said refrigerant Pro9 at the outlet of the second cooler,
  • Gw9 the conductance of the heat transfer fluid determined according to the flow rate of heat transfer fluid Mw9 passing through the second cooler
  • CCp9 Gw9 X (Twi9 — Tsat9 ).
  • the flow of refrigerant Mr9 passing through the second cooler is obtained according to the following formula (f):
  • the pressure of said refrigerant fluid Pro9 at the outlet of the second cooler is estimated as a function of the pressure P3 and the temperature T3 upstream of the compressor, the speed of rotation Ne of said compressor and the opening of the third electronic expansion valve.
  • the thermal management device is reversible, the refrigerant circulation circuit comprising:
  • the temperature Tl is measured by a sensor arranged on the main branch downstream of the external heat exchanger, the pressure PI being calculated according to the pressure of the refrigerant P2 measured by a sensor placed on the main branch downstream of the compressor and according to the pressure drops of the crossing of the external heat exchanger.
  • the temperature Tl is measured by a sensor arranged on the main branch downstream of the external heat exchanger, the pressure PI being calculated according to the pressure of the refrigerant P2 measured by a sensor arranged on the main branch downstream of the internal condenser and depending on the opening of the fourth electronic expansion valve as well as the pressure drops of the crossing of the external heat exchanger.
  • the temperature Tl is measured by a sensor arranged on the main branch downstream of the external heat exchanger, the pressure PI being calculated according to the pressure of the refrigerant Pd measured by a sensor placed on the main branch at the outlet of the compressor and according to the pressure drops of the crossing of the internal condenser, the opening of the fourth electronic expansion valve as well as the pressure drops of the crossing of the external heat exchanger.
  • the temperature Tl and the pressure PI are measured by sensors arranged on the main branch downstream of the external heat exchanger.
  • the pressure P3 and the temperature T3 are measured by pressure and temperature sensors arranged on the main branch upstream of the compressor so as to measure the temperature of the fluid entering said compressor .
  • the thermal management device 1 is in an operating mode of simultaneous cooling of the internal air flow and of the element whose thermal management is ensured by the first cooler in which :
  • the thermal management device is in a heat pump operating mode with recovery of heat energy at the level of the element whose thermal management is ensured by the second cooler, in which :
  • the control of the opening of the third electronic expansion valve (8) being carried out as described previously, and if the temperature of the fluid T3 upstream of the compressor is higher than its saturation temperature Tsat at the pressure P3 upstream of the compressor, then the fourth electronic expansion valve is open until the temperature of the fluid T3 upstream of the compressor is less than or equal to its saturation temperature Tsat at pressure P3 upstream of the compressor.
  • the thermal management device is in an operating mode of simultaneous cooling of the internal air flow and of the element whose thermal management is ensured by the first cooler in which:
  • a second part of the refrigerant passes through the second electronic expansion valve and the first cooler, the two parts of refrigerant joining before joining the compressor, the control of the opening of the second electronic expansion valve (8) being made as previously described, and if the temperature of the refrigerant Td at the outlet of the compressor is greater than a maximum tolerance temperature Tdmax of said compressor, then the first electronic expansion valve is open until the temperature of the refrigerant Td at the outlet of the compressor is lower or equal to its maximum tolerance temperature Tdmax of said compressor.
  • the thermal management device is in a heat pump operating mode with recovery of heat energy at the level of the element whose thermal management is ensured by the second cooler, in which :
  • Figure 1 is a schematic representation of a thermal management device according to a first embodiment
  • Figure 2 is a schematic representation of the thermal management device of Figure 1 according to a first cooling mode
  • FIG. 3 is a schematic representation of the thermal management device of Figure 1 according to a second cooling mode
  • Figure 4 is a schematic representation of the thermal management device of Figure 1 according to a third mode of cooling
  • FIG. 5 is a schematic representation of a thermal management device according to a second embodiment
  • Figure 6 is a schematic representation of the thermal management device of Figure 5 according to a first cooling mode
  • Figure 7 is a schematic representation of the thermal management device of Figure 5 according to a second cooling mode
  • Figure 8 is a schematic representation of the thermal management device of Figure 5 according to a third mode of cooling
  • Figure 9 is a schematic representation of the thermal management device of Figure 5 according to a heat pump mode
  • Figure 10 is a schematic representation of the thermal management device of Figure 1 according to an alternative
  • Figure 11 is a schematic representation of the thermal management device of Figure 5 according to a first alternative
  • Figure 12 is a schematic representation of the thermal management device of Figure 5 according to a second alternative.
  • 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 over another and it is easy to interchange such denominations without departing from the scope of the present description.
  • this indexing imply an order in time, 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 in relation to the direction of fluid circulation.
  • FIG 1 shows a schematic representation of a thermal management device 1 for an electric or hybrid motor vehicle according to a first simple embodiment.
  • This thermal management device 1 comprises a circulation circuit for a refrigerant fluid comprising a main branch A as well as a first bypass branch B.
  • This refrigerant fluid can be a refrigerant commonly used in the field of cooling circuits. or air conditioning such as R-1234-yf, R-134a or R744.
  • the main branch A shown in thick lines, comprises in the direction of circulation of the refrigerant fluid, a compressor 2, an external heat exchanger 3, a first electronic expansion valve 4 and an evaporator 5.
  • the exchanger external heat exchanger 3 is more particularly intended to be traversed by an external air flow 300.
  • the external heat exchanger 3 can for example be arranged on the front face of the motor vehicle.
  • the evaporator 5 is for its part intended to be traversed by an internal air flow 200 intended for the passenger compartment.
  • F evaporator 5 can be arranged in particular in a heating, ventilation and air conditioning device, for example located at the rear of the dashboard of the motor vehicle.
  • the main branch A can also include a phase separation device such as an accumulator 12 arranged upstream of the compressor 2.
  • the first bypass branch B is for its part connected in parallel with the first electronic expansion valve 4 and the evaporator 5.
  • the first branch B connects more particularly a first connection point 31 to a second connection point 32.
  • the first connection point 31 is arranged on the main branch A upstream of the first electronic expansion valve 4, between the external heat exchanger 3 and said first electronic expansion valve 4.
  • the second connection point 32 is arranged on the main branch A in downstream of evaporator 5, between said evaporator 5 and compressor 2, more particularly upstream of accumulator 12.
  • the first bypass branch B comprises a second electronic expansion valve 6 arranged upstream of a first cooler 7.
  • This first cooler 7 is in particular configured to allow heat exchange between the refrigerant fluid and a fluid heat transfer fluid circulating in at least one circulation loop (not shown) of said heat transfer fluid configured for the thermal management of an element of the motor vehicle.
  • This element can for example be the batteries of the motor vehicle.
  • the heat transfer fluid may in particular be, for example, water or glycol water.
  • the refrigerant circulation circuit may also include a second bypass branch C connected in parallel with the first bypass branch B as well as the first electronic expansion valve 4 and G evaporator 5.
  • This second branch branch C for this connects a third connection point 33 to a fourth connection point 34.
  • the third connection point 33 is in particular arranged downstream of the external heat exchanger 3 and upstream of the first 4 and/or second 6 electronic expansion valves.
  • the third connection point 33 is arranged on the main branch A downstream of the first connection point 31, between said first connection point 31 and the first electronic expansion valve 4.
  • the fourth connection point 34 is arranged upstream of the compressor 2, more precisely upstream of the accumulator 12, and downstream of the evaporator 5 and/or of the first cooler 7.
  • the fourth connection point 34 is arranged on the main branch A downstream of the evaporator 5, between said evaporator 5 and the second connection point 32.
  • the second bypass branch C comprises a third electronic expansion valve 8 arranged upstream of a second cooler 9.
  • This second cooler 9 is configured to allow heat exchange between the refrigerant fluid and a ca locarrier fluid circulating in at least one circulation loop (not shown) of said heat transfer fluid configured for the thermal management of an element of the motor vehicle distinct from that of the first cooler 7.
  • This element can for example be the power electronics of the motor vehicle .
  • the thermal management device 1 shown in Figure 1 is a simple device which in particular allows operation according to different cooling operating modes illustrated in Figures 2, 3 and 4.
  • the direction of circulation of the refrigerant is indicated by an arrow.
  • the zones and parts of the refrigerant circulation circuit in which the refrigerant circulates are shown in solid lines.
  • the areas and parts of the refrigerant circulation circuit in which no does not circulate the refrigerant are shown in dotted lines. Only the modes of operation in which the management method of the invention is applicable are represented here. Other modes of operation not shown can also be envisaged.
  • Figure 2 shows a first mode of simultaneous cooling of the internal air flow 200 and the element whose thermal management is ensured by the first cooler 7.
  • a first part of the refrigerant passes through the first electronic expansion valve 4 and the evaporator 5.
  • a second part of the refrigerant passes through the second electronic expansion valve 6 and the first cooler 7.
  • the refrigerant is compressed at the compressor 2 and goes to high pressure.
  • the high-pressure refrigerant fluid then passes through the external heat exchanger 3 which here acts as an external condenser. By crossing the external heat exchanger 3, the high-pressure refrigerant fluid releases calorific energy to the external air flow 300.
  • a first part of the high-pressure refrigerant fluid passes through the first electronic expansion valve 4 and suffers a loss of pressure.
  • the low-pressure refrigerant fluid then passes through the evaporator 5 where it absorbs heat energy from the internal air flow 200 cooling it.
  • a second part of the high-pressure refrigerant fluid passes into the first bypass branch B and crosses the second electronic expansion valve 6 and undergoes a loss of pressure.
  • the low-pressure refrigerant fluid then passes through the first cooler 7 at which it absorbs heat energy from the element for which it provides thermal management, here for example the batteries.
  • the two parts of the low-pressure refrigerant fluid meet at the level of the second connection point 32 before joining the compressor 2 for a new cycle.
  • Figure 3 shows a second mode of simultaneous cooling of the internal air flow 200 and the element whose thermal management is ensured by the second cooler 9.
  • a first part of the refrigerant fluid passes through the first electronic expansion valve 4 and the evaporator 5.
  • a second part of the refrigerant passes through the third electronic expansion valve 8 and the second cooler 9.
  • the refrigerant is compressed at the compressor 2 and goes to high pressure.
  • the high-pressure refrigerant fluid then passes through the external heat exchanger 3 which here acts as an external condenser. Passing through the external heat exchanger 3, the high-pressure refrigerant fluid releases calorific energy to the external air flow 300.
  • a first part of the high-pressure refrigerant fluid passes through the first electronic expansion valve 4 and suffers a loss of pressure.
  • the low-pressure refrigerant fluid then passes through the evaporator 5 at the level of which it absorbs calorific energy from the internal air flow 200 cooling it.
  • a second part of the high-pressure refrigerant fluid passes into the second bypass branch C and passes through the third electronic expansion valve 8 and undergoes a loss of pressure.
  • the low-pressure refrigerant fluid then passes through the second cooler 9 at which it absorbs heat energy from the element for which it provides thermal management, here for example the power electronics.
  • the two parts of the low-pressure refrigerant fluid join at the level of the fourth connection point 34 before joining the compressor 2 for a new cycle.
  • Figure 4 shows a third mode of simultaneous cooling of the internal air flow 200 and the element whose thermal management is ensured by the first cooler 7 as well as the element whose thermal management is ensured by the second cooler 9.
  • a first part of the refrigerant passes through the second electronic expansion valve 6 and the first cooler 7.
  • a second part of the refrigerant passes through the first electronic expansion valve 4 and the evaporator 5.
  • a third part of the refrigerant passes through the third electronic expansion valve 8 and the second cooler 9.
  • the refrigerant is compressed at the compressor 2 and goes to high pressure.
  • the high-pressure refrigerant fluid then passes through the external heat exchanger 3 which here acts as an external condenser. Passing through the external heat exchanger 3, the high pressure refrigerant fluid releases calorific energy to the external air flow 300.
  • a first part of the high pressure refrigerant fluid passes in the first bypass branch B and passes through the second electronic expansion valve 6 and undergoes a loss of pressure.
  • the low-pressure refrigerant fluid then passes through the first cooler 7 at which it absorbs calorific energy from the element for which it provides thermal management, here for example the batteries.
  • a first part of the high-pressure refrigerant fluid passes through the first electronic expansion valve 4 and undergoes a loss of pressure.
  • the low-pressure refrigerant then passes through the evaporator 5 at the level of which it absorbs calorific energy from the internal air flow 200 cooling it.
  • a third part of the high-pressure refrigerant fluid passes into the second bypass branch C and passes through the third electronic expansion valve 8 and undergoes a loss of pressure.
  • the low-pressure refrigerant fluid then passes through the second cooler 9 at the level of which it absorbs calorific energy from the element for which it provides thermal management, here for example the power electronics.
  • the second and third parts of the low-pressure refrigerant fluid join at the level of the fourth connection point 34 before joining the first portion of refrigerant fluid having passed through the first bypass branch B at the level of the second connection point 32.
  • the fluid low-pressure refrigerant then joins compressor 2 for a new cycle.
  • the first 4, second 6 and third 8 electronic expansion valves can in particular have a stop function.
  • a shut-off function allows, when the electronic expansion valve is completely closed, blocking the flow of refrigerant.
  • the third electronic expansion valve 8 is closed while the first 4 and second 6 electronic expansion valves are open.
  • the second electronic expansion valve 6 is closed while the first 4 and third 8 electronic expansion valves are open.
  • the third cooling mode of Figure 4 the first 4, second 6 and third 8 electronic expansion valves are open.
  • Figure 5 shows for its part a thermal management device 1 according to a second embodiment.
  • This second embodiment is more complex than the first in the sense that the thermal management device 1 is here invertible, that is to say it is configured to operate according to other operating modes, in particular modes heat pump in which the internal air flow 200 is not cooled but reheated.
  • the refrigerant circulation circuit of Figure 5 differs from that of Figure 1 in that it additionally comprises:
  • the internal condenser 10 is more particularly arranged on the main branch A between the compressor 2 and the fourth electronic expansion valve 11.
  • the internal condenser 10 is in particular intended to be crossed by the internal air flow 200.
  • This internal condenser 10 can in particular be arranged in the heating, ventilation and air conditioning device comprising the evaporator 5. Within this heating, ventilation and air conditioning device, the internal condenser 10 can in particular be arranged downstream of the evaporator 5 in the direction of the internal air flow 200.
  • a blocking member such as a flap (not shown) may in particular be arranged within said heating, ventilation and air conditioning device in order to prevent the internal air flow 200 to cross the internal condenser 200.
  • the third bypass branch D it is meant by the fact that it directly connects the outlet of the external heat exchanger 3 to the inlet of the compressor 2, that it allows a direct connection without passing by other heat exchangers or expansion devices.
  • the third branch D connects in particular a fifth connection point 35 to a sixth connection point 36.
  • the fifth connection point 35 is more particularly arranged on the main branch A downstream of the external heat exchanger 3, between said heat exchanger 3 and the first connection point 31.
  • the sixth connection point 36 is arranged on the branch main A, upstream of the compressor 2, in particular upstream of the accumulator 12, between the second connection point 32 and said compressor 2.
  • the third bypass branch D also includes a first shut-off valve 21.
  • the fourth bypass branch E connects a seventh connection point 37 to an eighth connection point 38.
  • the seventh connection point 37 is disposed on the main branch A upstream of the fourth expansion valve electronic 11, between the internal condenser 10 and said fourth electronic expansion valve IL
  • the eighth connection point 38 is arranged downstream of the fifth connection point 35 and upstream of any one of the first 4, second 6 or third 8 electronic expansion valves. In the example illustrated in FIG. 5, this eighth connection point 38 is arranged on the second bypass branch C, upstream of the third electronic expansion valve 8.
  • the eighth connection point 38 could nevertheless quite be disposed on the first bypass branch B upstream of the second electronic expansion valve 6 or else on the main branch A upstream of the first electronic expansion valve 4.
  • the fourth bypass branch E also comprises a second valve d stop 22.
  • the fourth electronic expansion valve 11 may also include a stop function.
  • the main branch A also includes a non-return valve 23 arranged downstream of the fifth connection point 35.
  • this non-return valve is arranged upstream of the first 31 and third 33 connection points in order to allow the refrigerant fluid coming from the fourth bypass branch E, that is to say from the eighth connection point 38, to circulate to either of the first 4, second 6 or third 8 electronic expansion valves.
  • the thermal management device 1 of Figure 5 can operate according to different operating modes. It can in particular operate according to a first mode of simultaneous cooling of the internal air flow 200 and of the element whose thermal management is ensured by the first cooler 7 as illustrated in FIG. 6. In this first mode of operation, a first part of the refrigerant fluid passes through the first electronic expansion valve 4 and the evaporator 5. A second part of the refrigerant fluid passes through the second electronic expansion valve 6 and the first cooler 7.
  • the refrigerant fluid follows a path identical to that of the first cooling mode of FIG. 2.
  • the first 21 and the second 22 shut-off valves are closed to prevent the refrigerant fluid from circulating in the third D and fourth E derivation branches.
  • the fourth electronic expansion valve 11 is opened to its maximum to allow the refrigerant fluid to pass with little or no loss of pressure.
  • the internal condenser 10 is for its part crossed by the refrigerant fluid with little or no heat exchange with the internal air flow 200, for example thanks to a shutter preventing the internal air flow from crossing said internal condenser 10.
  • the thermal management device 1 of Figure 5 can operate according to a second mode of simultaneous cooling of the internal air flow 200 and the element whose thermal management is ensured by the second cooler 9 as illustrated in FIG. 7.
  • a first part of the refrigerant fluid passes through the first electronic expansion valve 4 and the evaporator 5.
  • a second part of the refrigerant fluid passes through the third electronic expansion valve 8 and the second cooler 9.
  • the refrigerant fluid follows a path identical to that of the second cooling mode of Figure 3.
  • the first 21 and the second 22 shut-off valves are closed to prevent the refrigerant fluid from circulating in the third D and fourth E branch branches.
  • the fourth electronic expansion valve 11 is opened to its maximum to let the refrigerating fluid pass with little or no loss of pressure.
  • the internal condenser 10 is for its part traversed by the refrigerant with little or no heat exchange with the internal air flow 200, for example thanks to a shutter preventing the internal air flow from passing through said internal condenser 10.
  • the thermal management device 1 can also operate according to a third mode of simultaneous cooling of the internal air flow 200 and of the element whose thermal management is ensured by the first cooler 7 as well as of the element whose the thermal management is ensured by the second cooler 9 as illustrated in FIG. 8.
  • a first part of the refrigerant fluid passes through the second electronic expansion valve 6 and the first cooler 7.
  • a second part refrigerant fluid passes through the first electronic expansion valve 4 and the evaporator 5.
  • a third part of the refrigerant fluid passes through the third electronic expansion valve 8 and the second cooler 9.
  • the refrigerant fluid follows a path identical to that of the second cooling mode of Figure 4.
  • the first 21 and the second 22 shut-off valves are closed to e prevent the refrigerant fluid from circulating in the third D and fourth E branch branches.
  • the fourth electronic expansion valve 11 is opened to its maximum to allow the refrigerant fluid to pass with little or no loss of pressure.
  • the internal condenser 10 is for its part crossed by the refrigerant fluid with little or no heat exchange with the internal air flow 200, for example thanks to a shutter preventing the internal air flow from crossing said condenser. internal 10.
  • the thermal management device 1 of Figure 5 can also operate according to a heat pump operating mode with recovery of heat energy at the level of the element whose thermal management is ensured by the second cooler 9, for example the power electronics of the electric or hybrid vehicle.
  • a first part of the refrigerant fluid passes through the fourth electronic expansion valve 11 and the external heat exchanger 3.
  • a second part of the refrigerant fluid passes through the third electronic expansion valve 8 and the second chiller 9.
  • the refrigerant is compressed by the compressor 2 is high pressure passes.
  • the refrigerant fluid then passes through the internal condenser 10 at the level of which it yields energy to the internal air flow 200 passing through said internal condenser 10.
  • a first part of high pressure refrigerant fluid passes through the fourth electronic expansion valve 11 and undergoes a loss of pressure to go to low pressure.
  • the low-pressure refrigerant fluid then passes through the external heat exchanger 3 which here acts as an evaporator by absorbing calorific energy from the external air flow 300.
  • the low-pressure refrigerant fluid then passes into the third branch diversion D because the second shut-off valve 21 is open.
  • a second part of the high-pressure refrigerant fluid passes into the fourth bypass branch E and then passes through the third electronic expansion valve 8 and undergoes a loss of pressure for no also be used at low pressure.
  • the low-pressure refrigerant fluid then passes through the second cooler 9 at the level of which it recovers calorific energy at the level of the element whose thermal management is ensured by the second cooler 9.
  • the first and second part of refrigerant fluid then low pressure meet at the sixth connection point 36 before joining the compressor 2 for a new cycle.
  • the first 4 and second 6 electronic expansion valves are closed.
  • the thermal management device 1 of Figure 5 can also operate according to other operating modes not shown or described such as other heat pump modes as well as dehumidification modes for example.
  • the device 1 For the control of the different operating modes, in particular for the control of the different electronic expansion valves 4, 6, 8, 11, the device 1 requires different sensors, in particular temperature and pressure sensors of the refrigerant circuit. slow in the circulation circuit. Other sensors such as sensors for the temperature of the heat transfer fluid circulating in the heat transfer fluid circulation circuits for the elements whose thermal management is ensured by the first 7 and second 9 coolers or even such as sensors of the temperature of the internal 200 or external 300 air flow are also necessary for the control of the various modes of operation.
  • the present invention thus relates to a control method for the thermal management device 1.
  • This method comprises in particular, for controlling the opening of the second electronic expansion valve 6, a step of estimating the discharge temperature of the refrigerant Tro7 at the outlet of the first cooler 7.
  • the estimation of this discharge temperature of the refrigerant Tro7 makes it possible to dispense with a temperature sensor arranged on the first bypass branch B downstream of the first cooler 7.
  • Tsat7 corresponds to the saturation temperature of the refrigerant at the pressure of said refrigerant Pro7 at the outlet of the first cooler 7. This saturation temperature is available on the pressure/temperature diagram corresponding to the refrigerant.
  • the pressure of the Pro7 refrigerant at the outlet of the first cooler 7 may in particular be estimated according to various parameters such as the pressure P3 and the temperature T3 upstream of the compressor 2, the speed of rotation Ne of the compressor 2 as well as the opening of the second electronic expansion valve 6.
  • the pressure P3 and the temperature T3 can be measured by pressure sensors
  • Twi7 corresponds to the temperature of the heat transfer fluid at the inlet of the first cooler 7.
  • This temperature of the heat transfer fluid Twi7 can be measured for example by a temperature sensor arranged on the heat transfer fluid circulation circuit (not shown) on which is connected the element to be cooled, the thermal management of which is ensured by the first cooler 7, for example the batteries.
  • the parameter eff7 corresponds to the efficiency of the first cooler 7. This efficiency eff7 is more particularly obtained according to the following formula (b):
  • NUT7 corresponds to the number of heat transfer units between the refrigerant fluid and the heat transfer fluid within the first cooler 7. This number of heat transfer units NUT7 is obtained according to the following formula (c):
  • Cpv corresponds to the gas phase heat capacity of the refrigerant. This is a known parameter and depends on the nature of the refrigerant.
  • Gw7 corresponds to the conductance of the heat transfer fluid determined according to the flow rate of heat transfer fluid Mw7 passing through the first cooler 7. This conductance depends on the nature of the heat transfer fluid.
  • the flow rate Mw7 can itself be known by means of a sensor within the heat transfer fluid circuit or else deduced by the operation of a pump for moving the heat transfer fluid within said heat transfer fluid circulation circuit.
  • CCt7 corresponds to the target power of the first cooler 7.
  • This target power CCt7 can in particular be obtained according to the following formula (d):
  • Hrot7 corresponds to the enthalpy of the target refrigerant at the outlet of the first cooler 7. This parameter Hrot7 is determined in particular by the cooling needs of the element whose thermal management is ensured by the first cooler 7, for example the batteries.
  • Hri7 is the enthalpy of the refrigerant fluid at the inlet of the first cooler 7. This enthalpy Hri7 is determined in particular as a function of the temperature T1 of the refrigerant fluid at the outlet of the external heat exchanger 3 when, before passing in the first re cooler 7, the coolant has passed through the external heat exchanger 3. This is notably the case in the first and third cooling modes described above.
  • Gw7 corresponds to the conductance of the heat transfer fluid
  • Twi7 corresponds to the temperature of the heat transfer fluid at the inlet of the first cooler 7
  • Tsat7 corresponds to the saturation temperature of the refrigerant at the pressure of the refrigerant Pro7 at the outlet. of the first chiller 7.
  • the parameter Mr7 present in formulas (c) and (d) corresponds to the flow rate of refrigerated fluid passing through the first cooler 7.
  • This flow rate of refrigerating fluid Mr7 passing through the first cooler 7 can in particular be obtained according to formula (f ) next :
  • Mrl kx S6 x (Ro(Pl - P3))° 5
  • P3 is the pressure of the refrigerant fluid upstream of the compressor 2. As said above, this pressure P3 can be measured by a pressure sensor Cp3 placed on the main branch A upstream of the compressor 2.
  • S6 corresponds to the surface opening of the second electronic expansion valve 6 and k is a coefficient with a value of 0.98.
  • Ro corresponds here to the density of the refrigerant at a temperature Tl and a pressure PI at the outlet of the external heat exchanger 3.
  • the latter can be measured by sensors Ctl, Cpl arranged on the main branch A downstream of the external heat exchanger 3.
  • these sensors Ctl and Cpl are preferably arranged on the main branch A between the external heat exchanger 3 and the first connection point 31 of the first branch branch B.
  • these sensors Ctl and Cpl are preferably arranged on the main branch A between the external heat exchanger 3 and the fifth connection point 35 of the third branch branch D.
  • the temperature T1 is measured by a sensor Ct1 disposed on the main branch A downstream of the external heat exchanger 3.
  • This sensor Ct1 is preferably arranged on the main branch A between the external heat exchanger 3 and the first connection point 31 of the first bypass branch B.
  • the pressure PI is here determined according to the pressure of the refrigerant P2 measured by a Cp2 sensor arranged on the main branch A downstream of compressor 2. More precisely, this Cp2 sensor is arranged between the compressor 2 and the external heat exchanger 3.
  • This pressure sensor Cp2 is generally coupled with a sensor Ct2 of the temperature of the refrigerant.
  • the pressure PI is thus calculated according to the pressure value P2 measured by this sensor Cp2 and the pressure drops of the crossing of the external heat exchanger 3.
  • the temperature Tl is measured by a sensor Ctl arranged on the main branch A downstream of the external heat exchanger 3.
  • This sensor Ctl is preferably arranged on the main branch A between the external heat exchanger 3 and the fifth connection point 35 of the third bypass branch D.
  • the pressure PI is here determined according to the pressure of the refrigerant P2 measured by a Cp2 sensor arranged on the main branch A downstream of the internal condenser 10. More specifically, this sensor Cp2 is arranged between the internal condenser 10 and the fourth electronic expansion valve 11.
  • This pressure sensor Cp2 is generally coupled with a sensor Ct2 of the temperature of the refrigerant fluid. The pressure PI is thus calculated as a function of the pressure value P2 measured by this sensor Cp2 and as a function of the opening of the fourth electronic expansion valve 11 as well as the pressure losses of the crossing of the heat exchanger. external heat 3.
  • the temperature Tl is measured by a sensor Ctl arranged on the main branch A downstream of the external heat exchanger 3.
  • This sensor Ctl is preferably arranged on the main branch A between the external heat exchanger 3 and the fifth connection point 35 of the third bypass branch D.
  • the pressure PI is here determined according to the pressure of the refrigerant Pd measured by a Cpd sensor arranged on the main branch A downstream of the compressor 2. More precisely, this Cpd sensor is arranged between the compressor 2 and the internal condenser 10.
  • This Cpd pressure sensor is generally coupled with a Ctd temperature sensor refrigerant fluid.
  • the pressure PI is thus calculated as a function of the pressure value Pd measured by this sensor Cpd and as a function of the pressure losses of the crossing of the internal condenser 10, of the opening of the fourth electronic expansion valve 11 as well as of the pressure drops of the bushing of the external heat exchanger 3.
  • the pressure P2 can be calculated according to the pressure value Pd measured by the Cpd sensor and according to the pressure drops of the bushing of the internal condenser 10.
  • the control method according to the invention can also be applied for controlling the opening of the third electronic expansion valve 8.
  • the method then comprises a step of estimating the discharge temperature of the refrigerant fluid Tro at the outlet of the second cooler 9. This estimation of the discharge temperature of the refrigerant fluid Tro9 is carried out according to the following formula (a'):
  • Tsat9 corresponds to the saturation temperature of the refrigerant at the pressure of said refrigerant Pro9 at the outlet of the second cooler 9. This saturation temperature is available on the pressure/temperature diagram corresponding to the refrigerant.
  • the pressure of the refrigerant Pro9 at the outlet of the second cooler 9 can in particular be estimated according to various parameters such as the pressure P3 and the temperature T3 upstream of the compressor 2, the speed of rotation Ne of the compressor 2 as well as the opening of the third electronic expansion valve 8.
  • the pressure P3 and the temperature T3 can be measured by pressure Cp3 and temperature Ct3 sensors arranged on the main branch A upstream of the compressor 2 so as to measure the temperature of the refrigerant fluid at the inlet said compressor 2. More specifically, these sensors Cp3 and Ct3 can be arranged upstream of the accumulator 12.
  • Twi9 corresponds to the temperature of the heat transfer fluid at the inlet of the second cooler 9.
  • This temperature of the heat transfer fluid Twi9 can be measured for example by a temperature sensor arranged on the heat transfer fluid circulation circuit (not shown) to which the element to be cooled is connected, the thermal management of which is ensured by the second cooler 9, for example the power electronics of the electric or hybrid vehicle.
  • the parameter eff9 corresponds to the efficiency of the second cooler 9. This efficiency eff9 is more particularly obtained according to the following formula (b'):
  • NUT9 corresponds to the number of heat transfer units between the refrigerant fluid and the heat transfer fluid within the second cooler 9. This number of heat transfer units NUT9 is obtained according to the following formula (c'):
  • Cpv corresponds to the gas phase heat capacity of the refrigerant. This is a known parameter and depends on the nature of the refrigerant.
  • Gw9 corresponds to the conductance of the heat transfer fluid determined according to the flow rate of heat transfer fluid Mw9 passing through the second cooler 9. This conductance depends on the nature of the heat transfer fluid.
  • the flow rate Mw9 can itself be known by means of a sensor within the heat transfer fluid circuit or else deduced by the operation of a pump for moving the heat transfer fluid within said heat transfer fluid circulation circuit.
  • CCt9 corresponds to the target power of the second cooler 9.
  • This target power CCt9 can in particular be obtained according to the following formula (d'):
  • Hrot9 corresponds to the enthalpy of the target coolant at the outlet of the second cooler 9. This parameter Hrot9 is determined in particular by the cooling needs of the element whose thermal management is ensured by the second cooler 9, for example the power electronics of the electric or hybrid vehicle.
  • Hri9 is the enthalpy of the refrigerant fluid at the inlet of the second cooler 9. This enthalpy Hri9 is determined in particular as a function of the temperature T1 of the refrigerant fluid at the outlet of the external heat exchanger 3 when, before pass through the second cooler 9, the coolant has passed through the external heat exchanger 3. This is particularly the case in the first and third cooling modes described above.
  • CCp9 is the potential power of the second cooler 9. This potential power CCp9 of the second cooler 9 can be obtained according to the following formula (e'):
  • CCp9 Gw9 X (Twi9 — Tsat9 ).
  • Gw9 corresponds to the conductance of the heat transfer fluid
  • Twi9 corresponds to the temperature of the heat transfer fluid at the inlet of the second cooler 9
  • Tsat9 corresponds to the saturation temperature of the coolant at the pressure of the coolant Pro9 at the outlet of the coolant.
  • the parameter Mr9 present in the formulas (c′) and (d′) corresponds to the flow rate of refrigerating fluid passing through the second cooler 9.
  • This flow rate of refrigerating fluid Mr9 passing through the second cooler 9 can in particular be obtained according to the formula (f ) following:
  • P3 is the pressure of the refrigerant fluid upstream of the compressor 2. As said above, this pressure P3 can be measured by a pressure sensor Cp3 placed on the main branch A upstream of the compressor 2. S8 corresponds to the surface opening of the third electronic expansion valve 8 and k is a coefficient with a value of 0.98. Ro corresponds here to the density of the refrigerant at a temperature Tl and a pressure PI at the outlet of the external heat exchanger 3.
  • the present invention also relates to a control method, in particular in the various modes of operation described previously.
  • the control of the opening of the second electronic expansion valve 6 is carried out as described above with an estimate of the discharge temperature of the refrigerant Tro7 calculated according to formula (a).
  • the sub-cooling of the refrigerant fluid at the outlet of the heat exchanger 3 is determined as a function of the temperature T1 as well as the saturation temperature Tsat3 of the fluid. refrigerant at the pressure Pl.
  • the parameters Tl and PI can be obtained according to different variants.
  • the saturation temperature Tsat3 is itself dependent on the nature of the refrigerant fluid.
  • This sub-cooling is modulated to approach a target sub-cooling necessary to reach a target temperature of the internal air flow 200 at the outlet of the evaporator 5 and a target temperature of the heat transfer fluid at the outlet of the first cooler 7
  • This modulation of the sub-cooling is obtained in particular by varying the opening of the first electronic expansion valve 4.
  • the control of the first electronic expansion valve 4 can in particular be determined as a function of the temperature T4 at the outlet of the evaporator 5.
  • This temperature T4 can for example be measured by a sensor Ct4 arranged on the main branch A downstream of the evaporator 5.
  • this sensor Ct4 is in particular arranged downstream of the fourth connection point 34 of the second bypass branch C, between said fourth connection point 34 and the second connection point 32 of the first bypass branch B.
  • This particular arrangement of the sensor Ct4 is particularly advantageous because it allows both to have the temperature of the refrigerant fluid at the outlet of the evaporator 5 for example in a mode cooling- ment, but also the temperature of the refrigerant fluid at the outlet of the second cooler 9, for example in a heat pump mode with heat energy recovery at the level of said second cooler 9.
  • the protection of the compressor 2 against overheating can be carried out according to an alternative, if the temperature of the refrigerant Td at the outlet of the compressor 2 is higher than a maximum tolerance temperature Tdmax of said compressor 2, then the first valve of electronic expansion 4 is open until the temperature of the refrigerant Td at the outlet of the compressor 2 is less than or equal to its maximum tolerance temperature Tdmax of said compressor 2.
  • This temperature Td corresponds more particularly to the measurement of the temperature refrigerant by the sensor Ct2 in the embodiments of Figures 1, 5, 10 and 11 or by the sensor Ctd in the embodiment of Figure 12.
  • the control of the opening of the third electronic expansion valve 8 is carried out as described above with an estimate of the discharge temperature of the refrigerating fluid Tro9 calculated according to formula (a′) or else by measurement by means of a sensor Ct4 disposed downstream of the fourth connection point 34 of the second branch C, between said fourth connection point 34 and the second connection point 32 of the first branch B.
  • the control of the opening of the second electronic expansion valve 6 is carried out as described above with an estimate of the discharge temperature of the refrigerant Tro7 calculated according to formula (a).
  • the control of the opening of the third electronic expansion valve 8 is carried out as described above with an estimate of the discharge temperature of the refrigerant fluid Tro9 calculated according to formula (a′) or else by measurement by means of a sensor Ct4 disposed downstream of the fourth connection point 34 of the second branch C, between said fourth connection point 34 and the second connection point 32 of the first branch B.
  • the control of the opening of the third electronic expansion valve 8 is carried out as described above with an estimate of the discharge temperature of the refrigerating fluid Tro9 calculated according to formula (a′) or else by measurement by means of a sensor Ct4 disposed downstream of the fourth connection point 34 of the second branch C, between said fourth connection point 34 and the second connection point 32 of the first branch B.
  • the sub-cooling of the refrigerant fluid at the outlet of the internal condenser 10 is determined according to the temperature T2 as well as the saturation temperature Tsat2 of the refrigerant fluid. at pressure P2.
  • the parameters T2 and P2 can be obtained according to different variants.
  • the saturation temperature Tsat3 is itself dependent on the nature of the refrigerant fluid.
  • This subcooling is modulated to closer to a target sub-cooling necessary to reach a target temperature of the internal air flow 200 at the outlet of the internal condenser 10 and a target temperature of the heat transfer fluid at the outlet of the second cooler 9. This modulation of the sub-cooling is in particular obtained by varying the opening of the fourth electronic expansion valve 11.
  • the protection of the compressor 2 against overheating can be carried out according to an alternative, if the temperature of the refrigerant Td at the outlet of the compressor 2 is higher than a maximum tolerance temperature Tdmax of said compressor 2, then the fourth valve of electronic expansion 11 is open until the temperature of the refrigerant Td at the outlet of the compressor 2 is less than or equal to its maximum tolerance temperature Tdmax of said compressor 2.
  • This temperature Td corresponds more particularly to the measurement of the temperature refrigerant fluid by the Ctd sensor in the embodiment of Figure 12.
  • control method makes it possible to save one or more sensors in the architecture of the thermal management device and also makes it possible to protect the compressor 2 from possible damage due to a refrigerant too overheated.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Temperature (AREA)
  • Air-Conditioning For Vehicles (AREA)
EP22727041.0A 2021-04-29 2022-04-29 Verfahren zur steuerung einer wärmeverwaltungsvorrichtung Pending EP4330064A1 (de)

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FR2104528A FR3122486B1 (fr) 2021-04-29 2021-04-29 Procédé de contrôle d’un dispositif de gestion thermique
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US5007245A (en) * 1989-09-01 1991-04-16 Sundstrand Corporation Vapor cycle system with multiple evaporator load control and superheat control
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JP6595205B2 (ja) * 2015-04-24 2019-10-23 株式会社日立製作所 冷凍サイクル装置
CN109927504B (zh) * 2017-12-19 2021-06-29 杭州三花研究院有限公司 用于车舱和电池的控制方法

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