Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
  • F16K37/00—Special means in or on valves or other cut-off apparatus for indicating or recording operation thereof, or for enabling an alarm to be given
  • F16K37/0075—For recording or indicating the functioning of a valve in combination with test equipment
  • F16K37/0083—For recording or indicating the functioning of a valve in combination with test equipment by measuring valve parameters
• • 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
  • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
  • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
  • B60H1/00885—Controlling the flow of heating or cooling liquid, e.g. valves or pumps
• • 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
  • F25B41/00—Fluid-circulation arrangements
  • F25B41/30—Expansion means; Dispositions thereof
  • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
• • 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
  • B60H1/32—Cooling devices
  • B60H2001/3236—Cooling devices information from a variable is obtained
  • B60H2001/3267—Cooling devices information from a variable is obtained related to the operation of an expansion valve
• • 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
  • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
  • F25B2400/04—Refrigeration circuit bypassing means
  • F25B2400/0403—Refrigeration circuit bypassing means for the condenser
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
  • F25B2400/04—Refrigeration circuit bypassing means
  • F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
• • 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
  • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
  • F25B2400/04—Refrigeration circuit bypassing means
  • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
• • 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
  • F25B41/00—Fluid-circulation arrangements
  • F25B41/30—Expansion means; Dispositions thereof
  • F25B41/31—Expansion valves
  • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
  • F25B41/35—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by rotary motors, e.g. by stepping motors
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
  • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
  • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

• the present invention relates to a method for calibrating an expansion valve. More particularly to an expansion valve within a thermal management device of a motor vehicle.
• circuits of the cooling and/or heat pump type are based on the compression and expansion of a heat transfer fluid in order to cool or heat another element such as, for example, an air flow intended for the passenger compartment and/or the batteries in the case of an electric or hybrid vehicle.
• thermal management devices thus comprise at least one compressor to compress the heat transfer fluid and at least one expansion valve to expand it.
• These expansion valves are usually electronic expansion valves whose opening is controlled by a controlled stepper motor. These expansion valves also generally have a maximum closure in which the heat transfer fluid cannot or can hardly pass through the expansion valve, we then speak of a stop function. These expansion valves also have a maximum opening in which the heat transfer fluid can pass through the expansion valve with little or no loss of pressure.
• the expansion valve In order to allow precise control of the opening of the expansion valves and therefore of the loss of pressure of the heat transfer fluid, it is necessary to regularly calibrate said expansion valve.
• the expansion valve generally has a first stop, called low, close to its maximum closure and a second stop, called high, close to its maximum opening.
• the stepper motor is operated until it reaches one or the other of the first or second stops in order to define the exact position of the expansion valve.
• the multiplication of these calibration operations over time and the number of steps taken by the stepper motor to carry them out have an impact on the service life of said motor and therefore on that of the expansion valve.
• the object of the present invention is therefore to remedy at least partially the drawbacks of the prior art and to propose a method for calibrating an electronic expansion valve whose impact on the life of the valve of electronic expansion is limited.
• the present invention therefore relates to a method for calibrating an electronic expansion valve within a thermal management device of a motor vehicle, the opening of said electronic expansion valve being controllable by means of an electric stepper motor, said valve electronic expansion valve comprising a first so-called low stop in the direction of maximum closing of the electronic expansion valve and a second so-called high stop in the direction of maximum opening of the electronic expansion valve, each stop being a reference position making it possible to calibrate the electronic expansion valve, said method comprising the following steps:
• the step of determining the number of steps between the predicted opening position of the electronic expansion valve and the first and second stops comprises an additional step, during said additional step, the number of steps between the initial opening position and the first stop is added to the number of steps between the first stop and the predicted open position and the number of steps between the initial open position and the second stopper is added to the number of steps between the second stopper and the predicted open position.
• the step of determining a forecast position of the electronic expansion valve is carried out according to the future mode of operation of the thermal management device.
• the step of determining a forecast position of the electronic expansion valve is carried out according to the external temperature with respect to a predefined temperature threshold.
• the thermal management device comprises a first electronic expansion valve arranged upstream of a first evaporator:
• the thermal management device comprises a second electronic expansion valve arranged upstream of an evapo-condenser, when the predicted position of the second electronic expansion valve is determined by the future operating mode of the thermal management device and that it is an intermediate position so as to allow the circulation of the refrigerant fluid with a loss of pressure, if a calibration of said second electronic expansion valve is requested, said calibration is carried out on the remote abutment by the smallest number of steps.
• the thermal management device comprises a second electronic expansion valve arranged upstream of an evapo-condenser, when the predicted position of the second electronic expansion valve is a position intermediate so as to allow the circulation of the refrigerant fluid with a loss of pressure, if a calibration of said second electronic expansion valve is requested:
• the thermal management device comprises a second electronic expansion valve arranged upstream of an evapo-condenser:
• the thermal management device comprises a third electronic expansion valve arranged upstream of a second evaporator, said third electronic expansion valve and second evaporator being arranged in parallel with the first electronic expansion valve and first evaporator:
• the electronic expansion valve comprises a position sensor at each stop so as to determine when the opening of said electronic expansion valve is at the stop.
• the electronic expansion valve comprises physical stops such that the abutment position of the opening of the electronic expansion valve is determined by the resistance to rotation perceived by the electric stepper motor.
• Figure 1 shows a schematic representation of a thermal management device
• FIG. 2 shows a schematic representation of the thermal management device of Figure 1 in a first cooling mode or a dehumidification mode
• FIG. 3 shows a schematic representation of the thermal management device of Figure 1 in a second cooling mode
• Figure 4 shows a schematic representation of the thermal management device of Figure 1 in a third cooling mode
• Figure 5 shows a schematic representation of the thermal management device of Figure 1 in a first heat pump mode
• FIG. 6 shows a schematic representation of the thermal management device of Figure 1 in a second heat pump mode
• Figure 7 shows a functional diagram of the steps of the method of calibration
• FIG 8 shows a schematic representation of the calibration stroke of an electronic expansion valve according to a first example
• FIG 9 shows a schematic representation of the calibration stroke calibration of an electronic expansion valve according to a second example
• FIG 10 shows a schematic representation of the calibration stroke of an electronic expansion valve according to a third example.
• identical elements bear the same reference numbers.
• the following embodiments 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.
• first element or second element as well as first parameter and second parameter or else first criterion and second criterion, etc.
• 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 such denominations can easily be interchanged without departing from the scope of the present description. Nor does this indexing imply an order in time, for example, to assess such and such a criterion.
• upstream means that one element is placed before another with respect to the direction of circulation of an air flow or of a fluid.
• downstream we mean that one element is placed after another in relation to the direction of circulation of an air flow or a fluid.
• FIG. 1 firstly shows an example of a thermal management device 1.
• This thermal management device 1 here comprises a heat transfer fluid circuit, more precisely a refrigerant fluid, configured for the thermal management of a flow of internal air 200 intended for the passenger compartment as well as batteries within an electric or hybrid vehicle.
• the thermal management device 1 is in the example presented reversible, that is to say that it is configured to cool the internal air flow 200 and/or the batteries according to different cooling modes but also capable of operating in one or more heat pump modes in order for example to heat the internal air flow 200.
• the thermal management device 1 comprises a so-called main loop A (shown in bold lines) comprising, in the direction of circulation of the refrigerant fluid, a compressor 2, an internal condenser 3, an evaporator condenser 4 and a first evaporator 6. Upstream of the first evaporator 6 is arranged a first expansion device 5. Upstream of the evapo-condenser 4 is also arranged a second expansion device 7.
• the main loop A can also comprise a accumulator 11 of refrigerant fluid arranged upstream of the compressor 2.
• the evapo-condenser 4 is configured to be crossed by an external air flow 300.
• the evapo-condenser 4 is in particular intended to be arranged in front of the motor vehicle.
• the internal condenser 3 and the first evaporator 6 are for their part configured to be traversed by an internal air flow 200 intended for the passenger compartment.
• the internal condenser 3 and the first evaporator 6 are thus for example arranged within a heating, ventilation and air conditioning device (not shown). Within this heating, ventilation and air conditioning device, the first evaporator 6 can be more particularly placed upstream of the internal condenser 3 in the direction of circulation of the internal air flow 200.
• a device for blocking the flow of internal air 200 for example a flap (not shown) can also be present within the heating, ventilation and air conditioning device in order to prevent or not the internal air flow 200 from passing through the internal condenser 3.
• the thermal management device 1 further comprises a first bypass B connecting a first connection point 31 to a second connection point 32.
• the first connection point 31 is arranged on the main loop A downstream of the evapo -condenser 4, between said evapo-condenser 4 and the first expansion device 5.
• the second connection point 32 is arranged on the main loop A downstream of the first evaporator 6, between said first evaporator 6 and the compressor 2 More precisely upstream of the accumulator 11 for example.
• This first bypass B includes a first shut-off valve 21 in order to allow or not the passage of the refrigerant fluid in the said first bypass B.
• the thermal management device 1 also comprises in this example of Figure 1, a second branch C connecting a third connection point 33 to a fourth connection point 34.
• the third connection point 33 is arranged on the main loop A downstream of the internal condenser 3, between said internal condenser 3 and the second expansion device 7.
• the fourth connection point 34 is arranged upstream of the first expansion device 5, between the first connection point 31 and said first expansion device 5.
• the second bypass C comprises a second shut-off valve 22 in order to allow or not the passage of the refrigerant fluid in said second bypass C.
• the main loop A may comprise a non-return valve 23, This non-return valve 23 is arranged on the main loop A upstream of the fourth connection point 34, between the first 31 and the fourth 34 connection point.
• the thermal management device 1 may include a third branch D.
• This third branch D includes a third expansion device 8 disposed upstream of a second evaporator 9 or cooler.
• the third branch D is more particularly connected to the main loop A in parallel with the first evaporator 6 and its first expansion device 5.
• the third branch D thus connects a fifth connection point 35 to a sixth connection point 36.
• the fifth connection point 35 is arranged on the main branch A upstream of the fourth connection point 34, between the non-return valve 23 and said fourth connection point 34.
• the sixth connection point 36 is meanwhile disposed on the first bypass B downstream of the first shut-off valve 21.
• the second evaporator 9 can in particular be connected to an additional heat transfer fluid circuit (not shown) allowing thermal management, for example of the batteries of an electric vehicle or hybrid.
• the second evaporator 9 thus allows the exchange of heat energy between the refrigerant fluid circulating in the third bypass and a heat transfer fluid circulating in an additional heat transfer fluid circuit.
• the first 5, second 7 and third 8 expansion devices can more particularly be respectively a first 5, second 7 and third 8 electronic expansion valve.
• These electronic expansion valves 5, 7, 8 can be controlled by means of an electric stepper motor between a maximum closure in which the electronic expansion valve 5,7,8 blocks the passage of the refrigerant fluid and a maximum opening of the electronic expansion valve 5,7,8 in which the expansion valve can pass the refrigerant fluid with little or no loss of pressure.
• the thermal management device 1 of Figure 1 is thus configured to operate according to different operating modes illustrated in Figures 2 to 6.
• Figures 2 to 6 the direction of circulation of the refrigerant fluid is represented by arrows.
• the dotted lines correspond to sections in which the refrigerant fluid is not caused to circulate.
• Figure 2 shows a first mode of cooling in which the refrigerant is compressed at the level of the compressor 2, passes through the internal condenser 3 without exchanging with the internal air flow 200 and passes through the second electronic expansion valve 7 without suffering pressure loss.
• the refrigerant fluid then passes through the evapo-condenser 4 at the level of which it yields heat energy to the external air flow 300.
• the refrigerant fluid then passes into the first electronic expansion valve 5 at the level of which it undergoes a loss of pressure before crossing the first evaporator 6. By crossing the first evaporator 6, the refrigerant fluid recovers calorific energy from the internal air flow 200 allowing the cooling of the latter.
• the refrigerant then goes to compressor 2.
• the second electronic expansion valve 7 is open to its maximum while the third electronic expansion valve 8 is at its maximum closure.
• the first 21 and second 22 shut-off valves are closed.
• Figure 3 shows a second cooling mode in which the refrigerant is compressed at the compressor 2, passes through the internal condenser 3 without exchanging with the internal air flow 200 and passes through the second electronic expansion valve 7 without suffering pressure loss.
• the refrigerant fluid then passes through the evapo-condenser 4 at the level of which it yields heat energy to the external air flow 300.
• the refrigerant fluid then passes into the third electronic expansion valve 8 at the level of which it undergoes a loss of pressure before crossing the second evaporator 9. By crossing the second evaporator 9, the refrigerant fluid recovers heat energy from the batteries allowing the latter to be cooled.
• the refrigerant then goes to compressor 2.
• the second electronic expansion valve 7 is open to its maximum while the first electronic expansion valve 5 is at its maximum closure.
• the first 21 and second 22 stop valves are closed.
• Figure 4 shows a third cooling mode which is a mixed mode between the first and the second cooling mode.
• the refrigerant fluid is compressed at the level of the compressor 2, passes through the internal condenser 3 without exchanging with the internal air flow 200 and passes through the second electronic expansion valve 7 without suffering a loss of pressure.
• the refrigerant fluid then passes through the evapo-condenser 4 at the level of which it transfers heat energy to the external air flow 300.
• Part of the refrigerant passes through the third electronic expansion valve 8 at which it undergoes a loss of pressure before crossing the second evaporator 9.
• the refrigerant recovers from the calorific energy of the batteries allowing the cooling of the latter.
• Another part of the refrigerant passes through the first electronic expansion valve 5 at which it undergoes a loss of pressure before crossing the first evaporator 6.
• the refrigerant recovers calorific energy of the internal air flow 200 allowing the cooling of the latter.
• the second electronic expansion valve 7 is open to its maximum.
• the first 21 and second 22 stop valves are closed.
• Figure 5 shows a first heat pump mode in which the refrigerant is compressed at the compressor 2 and passes through then the internal condenser 3 at the level of which the refrigerant fluid yields heat energy to the internal air flow 200 to heat the latter.
• the refrigerant fluid then passes into the second electronic expansion valve 7 which it passes through while undergoing a loss of pressure.
• the refrigerant fluid then passes through the evapo-condenser 4 at which the refrigerant fluid recovers calorific energy from the external air flow 300.
• the refrigerant fluid then joins the compressor 2 via the first branch B.
• the first 5 and third 8 electronic expansion valves are closed.
• the first stop valve 21 is open and the second stop valve 22 is closed.
• Figure 6 shows a second energy recovery heat pump mode, in which the refrigerant fluid is compressed at the level of the compressor 2 and then passes through the internal condenser 3 at the level of which the refrigerant fluid yields heat energy to the internal air flow 200 to heat the latter.
• the refrigerant fluid then passes through the second bypass C to join the third electronic expansion valve 8 which it crosses while undergoing a loss of pressure.
• the refrigerant then passes through the second evaporator 9 at which the refrigerant recovers heat energy from the batteries.
• the refrigerant then goes to the compressor.
• the first 5 and second 7 electronic expansion valves are closed.
• the first stop valve 21 is closed and the second stop valve 22 is open.
• Another mode of operation can be a dehumidification mode in which the refrigerant fluid follows a path identical to that illustrated in FIG. 2.
• the refrigerant fluid is compressed at the level of the compressor 2 and then passes through the internal condenser 3 at which the refrigerant fluid yields heat energy to the internal air flow 200 to heat the latter.
• the refrigerant fluid then passes into the second electronic expansion valve 7 which it passes through while undergoing a first loss of pressure.
• the refrigerant fluid then passes through the evapo-condenser 4 at the level of which the refrigerant fluid recovers calorific energy from the external air flow 300.
• the refrigerant fluid then passes into the first electronic expansion valve 5 at the level of which it undergoes a loss of pressure before crossing the first evaporator 6.
• the refrigerant fluid recovers calorific energy from the internal air flow 200 allowing the cooling of the latter.
• the refrigerant then goes to compressor 2.
• the third electronic expansion valve 8 is at its maximum closure.
• the first 21 and second 22 shut-off valves are closed.
• Each stop XI, X2 is a reference position allowing the expansion valve to be calibrated.
• the calibration method according to the invention is illustrated in the diagram of Figure 7. This calibration method more specifically comprises the following steps:
• the thermal management device can enter a final step 105 of using the thermal management device 1 in its chosen mode of operation.
• the planned position Z as well as the first XI and second X2 stops are shown in Figures 8 to 10 showing schematically the opening ranges of an electronic expansion valve 5,7,8.
• the initial position Init of the opening of the expansion valve 5,7,8 is also shown in Figures 8 to 10.
• Such a calibration method thus makes it possible to choose the calibration path comprising the lowest number of steps for the stepper motor. This therefore extends the life of the stepper motor and therefore that of the electronic expansion valve 5,7,8.
• This calibration process can in particular be preceded by a preliminary step 100 of requesting calibration.
• This calibration request is in particular linked to the fact that the calibration can be carried out periodically, according to the manufacturer's instructions and requirements and/or each time the thermal management device 1 is started, for example when the motor vehicle is started. Whether such a preliminary step 100 of requesting calibration is not effective, the thermal management device 1 can be used directly. This is reflected in the diagram of FIG. 7 by a direct connection of this preliminary step 100 to the final step 105 of use of the thermal management device 1.
• the first step 101 of determining a provisional opening position Z of the electronic expansion valve 5,7,8 can in particular be carried out according to the future mode of operation of the thermal management device 1.
• each mode of operation implies a predefined opening position or at least a predefined opening range for each electronic expansion valve 5,7,8.
• the first step 101 of determining a predicted opening position Z of the electronic expansion valve 5,7,8 can also be carried out according to an external temperature with respect to a predefined temperature threshold.
• external temperature is meant here a temperature external to the thermal management device 1.
• This external temperature can be for example the ambient temperature outside the motor vehicle, the temperature of the batteries or even the temperature of a heat transfer fluid circulating in an additional heat transfer fluid circuit. Similar to the operation mode to come, the external temperature can also imply a predefined opening position or at least a predefined opening range for each electronic expansion valve 5,7,8.
• a predefined opening position Z of the electronic expansion valve 5,7,8 it is possible to determine a provisional opening position Z of the electronic expansion valve 5,7,8.
• Figure 8 shows an example in which the planned position Z is located at an opening of the electric expansion valve 5,7,8 close to the first stop XL This implies that the loss of pressure of the refrigerant fluid when it will cross the electronic expansion valve 5,7,8 will be important. This is for example the case for the first electronic expansion valve 5 in the following operating modes mentioned above:
• Figure 9 shows an example in which the predicted position Z is located at an opening of the electronic expansion valve 5,7,8 close to the second stop X2. This implies that the loss of pressure of the refrigerant when it will cross the electronic expansion valve 4,7,8 will be less important than in the example of Figure 8. This is for example the case for the second valve of 7 electronic expansion in dehumidification mode.
• Figure 10 shows an example in which the predicted position Z is located at the level of the first stop XI of the electronic expansion valve 4,7,8. This implies that the electronic expansion valve 5,7,8 will be closed and will not let the refrigerant through.
• the second step 102 of determining the number of steps between the planned opening position Z of the electronic expansion valve 5,7,8 and the first XI and second stops X2 can be carried out without the position of initial opening Init of the electronic expansion valve 5,7,8 is known during the calibration request. In this case, only the number of steps between the planned opening position Z of the electronic expansion valve 5,7,8 and the first X1 and second X2 stops is taken into account.
• the second step 102 of determining the number of steps between the planned opening position Z of the electronic expansion valve 5,7,8 and the first XI and second X2 stops can nevertheless also be carried out when the position d
• the initial opening Init of the electronic expansion valve 5,7,8 is known during the calibration request. It is for example possible to know the initial opening position Init of the electronic expansion valve 5,7,8 by knowing the previous mode of operation of the thermal management device 1.
• the second step 102 then comprises an additional step 102 '.
• the number of steps between the initial opening position Init and the first stop XI is added to the number of steps between the first stop XI and the provisional opening position Z.
• the number of steps between the initial opening position Init and the second stop X2 is also added to the number of steps between the second stop X2 and the planned opening position Z.
• the stop XI or X2 having the lowest number of steps is selected as the reference position to carry out the calibration of the electronic expansion valve 5,7,8.
• the fourth step 104 of calibrating the electronic expansion valve 5,7,8 is itself carried out by opening or closing said electronic expansion valve 5,7,8 up to its reference position d opening on the stop XI, X2 having the lowest number of steps determined by the third step 103.
• the calibration is carried out by closing the electronic expansion valve 5,7,8 until the first stop XI when the latter has been selected as the reference position in the third step 103.
• the calibration is carried out by opening the electronic expansion valve 5,7,8 up to the second stop X2 when the latter has been selected as a reference position in the third step 103.
• the detection of the arrival in abutment XI, X2 of the opening of the electronic expansion valve 5,7,8 may vary depending on the valve model.
• each stop (XI, X2) may include a position sensor at each stop (XI, X2) so as to determine when the opening of said electronic expansion valve 5, 7, 8 is at a stop.
• thermal management device 1 comprising a first electronic expansion valve 5 arranged upstream of a first evaporator 6, such as for example for a thermal management device 1 described in FIG. electronic expansion 5 can assume two different positions depending on the operating modes, an intermediate position or a closed position.
• the number of steps between its planned opening position Z and the first stop XI will necessarily be the lowest because due to the function of the first evaporator 6, the provisional opening position Z will necessarily be closer to the first stop XI than to the second stop X2, as illustrated in figure 8.
• the calibration method and in particular the second step 102 can be carried out either according to the mode of operation to come or according to the external temperature.
• This second electronic expansion valve 7 can assume three different positions depending on the operating modes, an intermediate position, an open position or a closed position.
• the predicted position Z of the second electronic expansion valve 7 is determined by the future mode of operation of the thermal management device 1.
• the second electronic expansion valve 7 can have an intermediate position so as to allow the circulation of the refrigerant fluid with a loss of pressure in the first heat pump mode ( Figure 5) and in the dehumidification mode ( Figure 6) .
• the predicted opening position Z of the second electronic expansion valve 7 will be closer to the first stop XI than to the second stop X2, as illustrated in figure 8. If a calibration is requested, then the latter will then be done on the first stop XI corresponding to the path with the lowest number of steps. In this case, the initial position (if it is known) can be taken into account in the third step 103 of determining the number of steps between the planned opening position Z of the electronic expansion valve 5,7,8 and the first XI and second X2 stops.
• the predicted opening position Z of the second electronic expansion valve 7 will be closer to the second stop X2 than to the first stop XI , as illustrated in figure 9. If a calibration is requested, then the latter will then be done on the second stop X2 corresponding to the path with the lowest number of steps. In this case, the initial position (if it is known) can be taken into account in the third step 103 of determining the number of steps between the planned opening position Z of the electronic expansion valve 5,7,8 and the first XI and second X2 stops.
• the second electronic expansion valve 7 can have a predicted position Z in the closed position so as to block the circulation of a refrigerant fluid in the second heat pump mode (FIG. 6).
• the forecast position Z of the second electronic expansion valve 7 is a closed position
• said calibration is performed on its first stop XI. Indeed, whatever the initial opening position Init of the second electronic expansion valve 7, the number of steps between its planned opening position Z and the first stop XI will necessarily be the lowest, as illustrated in figure 9.
• the second electronic expansion valve 7 can have a predicted position Z in the open position so as to allow the circulation of the refrigerant fluid with little or no loss of pressure in the first (figure 2), second (figure 3) and third ( Figure 4) cooling modes.
• the predicted position Z of the second electronic expansion valve 7 is an open position, if a calibration of said second electronic expansion valve 7 is requested, said calibration is carried out on its second stop X2. Indeed, whatever the initial opening position Init of the second electronic expansion valve 7, the number of steps between its planned opening position Z and the second stop X2 will necessarily be the lowest.
• the provisional opening position Z of the second electronic expansion valve 7 can be determined as a function of the external temperature.
• This external temperature can in particular be measured by means of a dedicated sensor.
• This second embodiment is particularly suitable for the second electronic expansion valve
• the calibration is carried out on the first stop XI.
• This predefined temperature threshold can for example be 25° C. If the outside temperature is lower than 25°C, whether for the first heat pump mode or the dehumidification mode, the predicted opening position Z will be closer to the first stop XI than to the second stop X2, as shown on the face
• This predefined temperature threshold can for example be 25° C. If the external temperature is higher than 25°C, whether for the first heat pump mode or the dehumidification, the planned opening position Z will be closer to the second stop X2 than to the first stop XI, as illustrated in figure 9. Indeed, in heat pump mode, as the external temperature is relatively high, it does not It is not necessary to have a large loss of refrigerant pressure in order to recover heat energy. The same applies to the dehumidification mode.
• thermal management device 1 comprising a third electronic expansion valve 8 arranged upstream of a second evaporator 9, such as for example for a thermal management device 1 described in FIG. electronic expansion 8 can assume two different positions depending on the operating modes, an intermediate position or a closed position.
• the planned opening position Z of the third electronic expansion valve 8 is an intermediate position so as to allow the circulation of the refrigerant fluid with a loss of pressure
• said calibration is performed on its first stop XI.
• the initial opening position Init of the third electronic expansion valve 8 the number of steps between its planned opening position Z and the first stop XI will necessarily be the lowest because due to the function of the second evaporator 9, the provisional opening position Z will necessarily be closer to the first stop XI than to the second stop X2, as illustrated in figure 8.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Thermal Sciences (AREA)
• Air-Conditioning For Vehicles (AREA)
• Electrically Driven Valve-Operating Means (AREA)
• Indication Of The Valve Opening Or Closing Status (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

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Family Applications (1)

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• 2021
  • 2021-04-29 FR FR2104529A patent/FR3122467B1/fr active Active
• 2022
  • 2022-04-26 CN CN202280044865.0A patent/CN117561413A/zh active Pending
  • 2022-04-26 KR KR1020237040639A patent/KR20240001210A/ko unknown
  • 2022-04-26 WO PCT/EP2022/060974 patent/WO2022229138A1/fr active Application Filing
  • 2022-04-26 US US18/556,440 patent/US20240200688A1/en active Pending
  • 2022-04-26 EP EP22725745.8A patent/EP4330607A1/fr active Pending

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