US20150040589A1 - Automatic control method used for defrosting a heat pump for a vehicle - Google Patents

Automatic control method used for defrosting a heat pump for a vehicle Download PDF

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Publication number
US20150040589A1
US20150040589A1 US14/383,657 US201214383657A US2015040589A1 US 20150040589 A1 US20150040589 A1 US 20150040589A1 US 201214383657 A US201214383657 A US 201214383657A US 2015040589 A1 US2015040589 A1 US 2015040589A1
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United States
Prior art keywords
defrosting
external
accumulator
heat exchanger
temperature
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US14/383,657
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English (en)
Inventor
Eudes Quetant
Virginie Goutal
Myriam Pasquini
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Renault SAS
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Renault SAS
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    • 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
    • B60H1/3205—Control means therefor
    • B60H1/3213—Control means therefor for increasing the efficiency in a vehicle heat pump
    • 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
    • B60H1/00899—Controlling the flow of liquid in a heat pump system
    • B60H1/00921—Controlling the flow of liquid in a heat pump system where the flow direction of the refrigerant does not change and there is an extra subcondenser, e.g. in an air duct
    • 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
    • B60H1/3205—Control means therefor
    • B60H1/321—Control means therefor for preventing the freezing of a heat exchanger
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle

Definitions

  • the present invention relates to the field of heat pump systems fitted to some types of motor vehicles, notably electric or hybrid vehicles. More specifically, it relates to a control method for the heat pump system of these vehicles, said method being used to defrost some components of said system when the external air temperature is low.
  • This heat pump is reversible so that it can operate in both heating mode and air conditioning mode. It conventionally comprises a compressor for heating and compressing a refrigerant fluid, an internal heat exchanger forming a condenser in heating mode for heating the internal air in the passenger compartment of the vehicle by heat exchange with the refrigerant fluid flowing from the compressor, an expansion valve for cooling the refrigerant fluid flowing from the internal heat exchanger, and finally an external heat exchanger forming an evaporator in heating mode for heating the refrigerant liquid flowing from the expansion valve by heat exchange with external air.
  • the heat pump also conventionally comprises an accumulator interposed between the external heat exchanger and the compressor, notably for storing the refrigerant fluid before compression by the compressor, and also for providing an oil return flow toward the compressor.
  • frost may form on the outer walls of the external heat exchanger.
  • the amount of frost formed is a function of several parameters, notably the humidity level of the external air and the temperature difference between the refrigerant fluid flowing in the exchanger and the external air. This frosting of the external exchanger then leads to a decrease in the efficiency of the heat pump, which increases the electricity consumption for the same performance level, or reduces the performance for the same level of electricity consumption. This also reduces the maximum power of the system.
  • Another known solution consists in supplying the external heat exchanger directly with of the refrigerant fluid compressed by the compressor.
  • the expansion valve and the internal heat exchanger are no longer present in the refrigerant fluid flow circuit.
  • the external heat exchanger then has refrigerant fluid heated by the compressor flowing through it.
  • the external heat exchanger then operates as a condenser so as to cause the melting of at least some of the frost present on its walls.
  • the temperature of the fluid supplied to the accumulator has already fallen considerably because said fluid has already released much of its heat in the external exchanger to cause the melting of the frost present on the walls of the latter. Consequently, the complete defrosting of the external exchanger does not necessarily result in the complete defrosting of the accumulator, especially if the defrosting of the exchanger has been optimized in terms of time and power (by means of the motor speed of the compressor) to reduce the electricity consumption of the system as far as possible.
  • One object of the invention is to overcome all or some of the aforesaid drawbacks of the prior art.
  • Another object of the invention is to carry out more complete defrosting of the heat pump while having the least possible effect on the other operating modes of the heat pump system.
  • Another object of the invention is to have the least possible effect on the electricity consumption of the system.
  • defrosting be carried out not only on the external exchanger, but also on the accumulator if frosting of the latter is detected.
  • the invention proposes a control method for a heat pump system, notably for a motor vehicle, said system comprising a compressor for heating and compressing a refrigerant fluid, an internal heat exchanger forming a condenser in heating mode for heating internal air by exchange with the refrigerant fluid flowing from the compressor, an expansion valve for cooling the refrigerant fluid and an external heat exchanger forming an evaporator in heating mode for heating the refrigerant liquid flowing from the expansion valve by exchange with external air, an accumulator also being interposed between the external heat exchanger and the compressor for storing the refrigerant fluid before compression, the method being characterized in that it comprises the following steps:
  • a) in heating mode detecting the frosting of the external heat exchanger, b) determining a data element representing the duration of the frosting of the heat exchanger, c) if the duration of the frosting of the external heat exchanger is greater than or equal to a first predetermined maximum duration, sending a command for defrosting the exchanger, and d) if a command for defrosting the exchanger is sent, starting an operation of defrosting the external heat exchanger and, according to a predefined principle, starting an operation of defrosting the accumulator by circulating a fluid compressed by the compressor in said external exchanger and said accumulator.
  • the frosting of the external exchanger is detected, and an operation of defrosting the external heat exchanger and/or an operation of defrosting the accumulator is then started according to a predefined principle.
  • the predefined principle is that an operation of defrosting the accumulator is started on one of every n occasions, where n is an integer greater than or equal to 2, if a command for defrosting the exchanger is sent, and that an operation of defrosting the external heat exchanger is started on the other occasions.
  • step a) of the method further includes a step of detecting the frosting of the accumulator
  • step b) further comprises a step of determining a data element representing the duration of the frosting of the accumulator
  • step c) further comprises the sending of a command for defrosting the accumulator if the duration of the frosting of the external heat accumulator is greater than or equal to a second predetermined maximum duration.
  • the predefined principle is that an operation of defrosting the accumulator is started if a command for defrosting the accumulator is sent, and that an operation of defrosting the external heat exchanger is started if a command for defrosting the exchanger is sent.
  • the operation of defrosting the external exchanger or the accumulator comprises a step of putting the compressor into operation at a first predetermined motor speed, in order to cause hot refrigerant fluid to flow in the external heat exchanger and the accumulator for a duration which is less than or equal to a third predetermined maximum duration C3, said motor speed and said third maximum duration being a function of said defrosting operation.
  • the flow of this hot refrigerant fluid makes it possible to melt the frost present on the outer walls of the external exchanger and, if necessary, the frost present on the outer walls of the accumulator.
  • the system further comprises a motorized fan unit near the external heat exchanger, and the operation of defrosting the external exchanger or the accumulator further comprises, if the external air temperature is above a first predetermined temperature value, a step of putting the motorized fan unit into operation for a duration less than or equal to a fourth maximum duration in order to produce an air flow used to remove the water remaining on the outer walls of said external heat exchanger after the melting of the frost. During this step, the compressor remains in operation.
  • frosting of the external heat exchanger is detected if the external air temperature is below a second predetermined temperature value while, at the same time, the temperature difference between the external air temperature and the temperature of the refrigerant fluid at the outlet of the external heat exchanger is above a third predetermined temperature value.
  • Said third temperature value is advantageously a function of the external air temperature.
  • the frosting of the accumulator is detected if the motor speed of the compressor is above a second predetermined value of motor speed while, at the same time, the external air temperature is below a fourth predetermined temperature value, and the temperature difference between the external air temperature and the temperature of the refrigerant fluid at the outlet of the external heat exchanger is above a fifth predetermined temperature value.
  • Said fifth temperature value is advantageously a function of the external air temperature.
  • the predetermined temperature values may differ according to the type and mission profile of the heat pump system.
  • a first counter is incremented when the frosting of the external heat exchanger is detected, and a second counter is incremented when the frosting of the accumulator is detected.
  • the count value of these two counters can be used to determine the duration of the frosting of the exchanger and the accumulator.
  • said first and second counters are reset to zero when the temperature of the external air is higher than or equal to a sixth predetermined positive temperature value.
  • a sixth predetermined positive temperature value e.g. the temperature of the external air is higher than or equal to a sixth predetermined positive temperature value.
  • step c) a command for defrosting the external exchanger is sent if the count value of the first counter is greater than or equal to a first count value representing said first maximum duration, and a command for defrosting the accumulator is sent if the count value of the second counter is greater than or equal to a second count value representing said second maximum duration.
  • an operation of defrosting the external exchanger or the accumulator is started only if the speed of the vehicle is less than or equal to a predetermined speed of 30 km/h or below. This is because it may be considered that there is no point in starting a defrosting operation above this value, since even if the external exchanger or the accumulator has hot fluid flowing through it, the cold air flowing through the external exchanger will keep the frost present.
  • the defrosting operation is stopped on the occurrence of another demand from the system circuit, this demand being different from defrosting, and taking priority over the latter.
  • This demand may be, for example, a demand for heating or air conditioning for comfort in the passenger compartment.
  • the defrosting operation is performed even if the speed of the vehicle is above said predetermined value of speed.
  • the system comprises a controlled flap valve to prevent dynamic air from flowing through the external exchanger during the defrosting operation.
  • the step of putting the compressor into operation at a first motor speed for a duration which is less than or equal to a third maximum duration comprises the following steps:
  • the step of putting the motorized fan unit into operation for a duration which is less than or equal to a fourth maximum duration comprises the following steps:
  • the compressor is put into operation while the motorized fan unit is being put into operation, to optimize water removal during the blowing phase.
  • the compressor operates at a third motor speed which is less than or equal to said first motor speed. This is because it is simply necessary to cause a refrigerant fluid to flow in the circuit at a temperature which prevents the water produced by the melting of the frost from refreezing, so that it can be removed by blowing.
  • the incrementation interval, or the incrementation speed, of the first and/or second counters is a function of the external temperature, so that a better evaluation can be made of the amount and intensity of frost present on the external exchanger and/or on the accumulator.
  • the incrementation interval, or the incrementation speed, of the first and/or second counters is also a function of the temperature difference between the external air temperature and the temperature of the refrigerant fluid at the outlet of the external heat exchanger, so that a better evaluation can be made of the amount and intensity of frost present on the external exchanger and/or on the accumulator.
  • the state of the counters is read by an external diagnostic tool in order to verify the state of frosting of the components of the heat pump.
  • FIG. 1 is a block diagram of a heating/air conditioning system for which the method of the invention can be used
  • FIG. 2 is a diagram illustrating the operation of the system of FIG. 1 in heating mode
  • FIG. 3 is a diagram illustrating the operation of the system of FIG. 1 in air conditioning mode
  • FIG. 4 is a diagram illustrating the operation of the system of FIG. 1 in defrosting mode
  • FIG. 5 is a flow diagram showing the main steps of a first embodiment of the method of the invention.
  • FIG. 6 is a flow diagram showing the sub-steps of the defrosting operation of FIG. 5 .
  • FIG. 7 is a flow diagram showing the main steps of a second embodiment of the method of the invention.
  • FIG. 8 is a flow diagram showing the main steps of a third embodiment of the method of the invention.
  • FIG. 1 shows a heat pump system 1 for which the method of the invention can be used.
  • This system includes a compressor 10 , an internal heat exchanger 11 forming an internal condenser in heating mode, another internal heat exchanger 12 forming an internal evaporator in air conditioning mode, an expansion valve 13 for the heating mode, an external heat exchanger 14 forming an evaporator in heating mode, an expansion valve 16 for the air conditioning mode, and an accumulator 15 .
  • These various components have a refrigerant fluid flowing through them.
  • Valves V1 and V2 are also provided to modify the path of a refrigerant fluid through these various components according to one of the following operating modes of the system:
  • the valve V1 is a three-way valve comprising an inlet coupled to the outlet of the external heat exchanger 14 , a first outlet coupled to the inlet of the compressor 10 via the accumulator, and a second outlet coupled to an inlet of the expansion valve 16 .
  • the valve V2 is a two-way valve for bypassing the expansion valve 13 in defrosting mode and in air conditioning mode.
  • the system further comprises an external temperature sensor TP1 located in an area outside the passenger compartment of the vehicle, enabling a temperature representing the external temperature to be captured, for example under a rear-view mirror of the vehicle, and a temperature sensor TP2 for measuring the temperature of the refrigerant fluid at the outlet of the exchanger 14 .
  • motorized fan units 17 and 18 are provided to diffuse the air, respectively, through the external exchanger 14 and through the internal exchangers 11 and 12 , and to increase the heat exchanges in the various operating modes of the system.
  • the refrigerant fluid flow circuit of the system changes according to the operating mode in use.
  • the valve V1 In heating mode, shown in FIG. 2 , the valve V1 is operated so as to couple the outlet of the exchanger 14 to the inlet of the compressor 10 via the accumulator 15 .
  • the compressor 10 heats and compresses the refrigerant fluid received from the external heat exchanger 14 which in this case forms an evaporator. Having been compressed in this way, the fluid is then supplied to the exchanger 11 (condenser) which is used to heat the internal air of the passenger compartment by heat exchange with the refrigerant fluid flowing from the compressor.
  • the refrigerant fluid is then cooled and expanded by the expansion valve 13 , and is then supplied to the external exchanger 14 again.
  • the valve V2 In this operating mode, the valve V2 is closed, and therefore the refrigerant fluid does not flow through it.
  • the motorized fan units 17 and 18 are in operation according to the requirements of the system. For example, when the vehicle is driven at high speed, there is no point in putting the motorized fan unit 17 on the front surface of the vehicle into operation.
  • the movement of the fluid in the system is indicated by the arrows.
  • the arrows in solid lines indicate a movement of fluid at high pressure (compressed fluid) and the arrows in broken lines indicate a movement of fluid at low pressure (expanded fluid).
  • the valve V1 In air conditioning mode, shown in FIG. 3 , the valve V1 is operated so as to couple the outlet of the exchanger 14 to the inlet of the expansion valve 16 .
  • This expansion valve is used to expand and cool the refrigerant fluid received from the external heat exchanger 14 which forms a condenser in this operating mode.
  • the expanded refrigerant fluid flows through the evaporator 12 to cool the internal air of the passenger compartment by heat exchange with the refrigerant fluid.
  • the refrigerant fluid then flows through the accumulator 15 and then the compressor 10 . This heats and compresses the refrigerant fluid which then flows through the valve V2 and then the external exchanger 14 .
  • a mixing flap valve not shown in the figure, is provided so that the air flow from the evaporator 12 bypasses the exchanger 11 , thereby maintaining the air conditioning performance.
  • the motorized fan units 17 and 18 are in operation according to the requirements of the system. For example, when the vehicle is driven at high speed, it is unnecessary to put the motorized fan unit 17 on the front surface into operation. At lower speeds, the motorized fan unit 17 must be put into operation to provide effective condensation and to limit the fluid pressure.
  • the refrigerant fluid does not flow through any forced expansion element (expansion valve or tube orifice) of the system.
  • the valve V1 is operated so as to couple the outlet of the exchanger 14 to the inlet of the compressor 10 via the accumulator 15 .
  • the compressor 10 heats and compresses the refrigerant fluid to a small extent.
  • the compressed fluid then flows through the valve V2 and then the external exchanger 14 .
  • the hot fluid flows through the external exchanger 14 and the accumulator 15 , enabling the frost present on their outer walls to be gradually melted.
  • the motorized fan unit 17 is in operation if necessary at the end of defrosting, as will be described below.
  • T ext denotes the temperature of the external air measured by the temperature sensor TP1
  • T S denotes the temperature of the refrigerant fluid at the outlet of the external exchanger 14 , measured by the temperature sensor TP2
  • RPM Comp denotes the number of rotations per minute of the motor of the compressor 10 .
  • the frost forms on the outer walls of the external exchanger 14 and of the accumulator 15 if the external temperature is negative or close to zero, and if the system is operating in heating mode.
  • the frost detection therefore takes place in the heating mode of the system. After detection, the defrosting operations are performed when the system is no longer in heating mode, and preferably when the vehicle is stationary.
  • the method of the invention comprises a set of steps S 10 to S 16 for detecting frosting of the external exchanger 14 and defrosting it, and a set of steps S 20 to S 26 for detecting frosting on the accumulator 15 and defrosting it. These two sets of steps are executed in parallel.
  • the steps relating to the detection of frosting and to the defrosting of the external exchanger will be described first.
  • the method of the invention includes, initially, a step S 10 of detecting frosting of the external exchanger 14 .
  • the external exchanger 14 is detected to be in the frosting condition if:
  • T 1 is, for example, equal to 5° C.
  • T 2 is, for example, equal to 10° C. In this example, this means that T s is therefore at least less than ⁇ 5° C.
  • the value T 2 varies as a function of the external temperature T ext .
  • the value T 2 decreases as the external temperature T ext decreases.
  • the method then includes a step of determining the duration frosting of the external exchanger 14 .
  • This determination is carried out by incrementing a counter COMP1 while the external exchanger remains in a frosting condition (T ext ⁇ T 1 and T ext ⁇ T s >T 2 ) in a step S 11 .
  • the count value of the counter represents the duration of the frosting of the external exchanger.
  • the incrementing of the counter COMP1 is a function of the external temperature. For example, the counter COMP1 is incremented more rapidly if the external temperature T ext is very low. For example, if T ext ⁇ 10° C., the counter is incremented by 2 every second, and if T ext ⁇ 10° C., the counter is incremented by 1 every second.
  • the count value of the counter COMP1 then represents not only the duration but also the intensity of the frosting. There will be more frost if the external temperature T ext is close to 0° C.
  • the incrementing of the counter COMP1 is a function of the difference T ext ⁇ T S . As this difference increases, the counter is incremented more rapidly. For example, if T ext ⁇ T S >15° C., the counter is incremented by 2 every second, and if T ext ⁇ T S ⁇ 15° C., the counter is incremented by 1 every second. In this case, the count value of the counter COMP1 also represents the intensity of the frosting.
  • the counter is not necessarily reset to zero. For example, if the external temperature T ext remains low but the difference T ext ⁇ T S decreases, the frost remains present on the external exchanger. Thus the counter COMP1 is reset to zero only if the temperature T ext is greater than or equal to a temperature value T 5 greater than the temperature T 1 . T 5 is, for example, equal to 8° C.
  • Step S 12 is a step of comparing the temperature T ext with the predefined value T 5 . If T ext T 5 , the counter COMP1 is reset to zero in step S 13 . If T ext ⁇ T 5 , the method continues to the next step. Thus the count value of the counter COMP1 can be retained when the vehicle is stopped or put into a sleep state.
  • the counter COMP1 is also reset to zero if the system is activated in air conditioning mode for a minimum duration. This is because, in this operating mode, the external exchanger operates as a condenser, causing heat to be supplied to the walls of the external exchanger and causing any frost present on the exchanger walls to melt.
  • the next step S 14 is a comparison step.
  • the value of the counter COMP1 is compared with a predetermined count value Ci.
  • the count value Ci corresponds, for example, to a duration D 1 if the counter COMP1 is incremented once every second.
  • the duration D 1 is, for example, equal to 5 minutes.
  • COMP1 denotes both the counter COMP1 and its count value.
  • a command to defrost the external exchanger is therefore sent if the exchanger frosting conditions are present for a duration Di.
  • step S 16 The defrosting operation is then performed in step S 16 .
  • the flow of the refrigerant fluid in this step corresponds to what has been described in relation to FIG. 4 . This step will be described below with reference to FIG. 6 .
  • the counter COMP1 is reset to zero, and there is a return to step S 13 .
  • steps substantially identical to steps S 10 to S 16 denoted S 20 to S 26 in FIG. 5 , are executed in parallel.
  • step S 20 the detection of frosting of the accumulator 15 consists in detecting whether the following conditions are present:
  • the value T 4 varies as a function of the external temperature T ext .
  • step S 21 The duration frosting of the accumulator 15 is then determined, in step S 21 .
  • a counter COMP2 is incremented while the frosting conditions of the accumulator 15 remain present (T ext ⁇ T 3 and T ext ⁇ T S >T 4 and RPM Comp ⁇ Ri).
  • the incrementing of the counter COMP2 is a function of the external temperature.
  • the counter COMP2 is incremented more or less rapidly according to whether the external temperature is higher or lower.
  • the counter COMP2 is reset to zero if the temperature T ext is greater than Or equal to the temperature value T 5 .
  • the method therefore comprises a step S 22 of comparing the temperature T ext with the predefined value T 5 , and, if T ext ⁇ T 5 , the counter COMP2 is reset to zero in step S 23 . If T ext ⁇ T 5 , the method continues to step S 24 .
  • the count value of the counter COMP2 can be retained when the vehicle is stopped or put into a sleep state.
  • the counter COMP2 is also reset to zero if the system is activated in air conditioning mode for a specific minimum duration.
  • step S 24 the value of the counter COMP2 is compared with a predetermined count value C2.
  • the count value C2 corresponds, for example, to a duration D 2 if the counter COMP2 is incremented once every second.
  • the duration D 2 is, for example, equal to 200 minutes. If COMP2>C2, a command is sent to defrost the accumulator in step S 25 . Otherwise the counting continues.
  • step S 26 The defrosting operation is then performed in step S 26 , and, after step S 26 , the counter COMP2 is reset to zero and there is a return to step S 23 .
  • the defrosting operation advantageously starts with a step S 100 of enabling defrosting.
  • the defrosting of the external exchanger and/or the accumulator is enabled only if certain conditions are met. For example, in the example of FIG. 6 , defrosting is enabled only if the speed of the vehicle is less than or equal to a predetermined value of speed V 1 .
  • the speed V 1 is equal to 0.
  • the defrosting operation is enabled only if the vehicle is stationary.
  • Step S 100 is then a step of comparing the vehicle speed with the speed Vi.
  • step S 12 or S 22 the defrosting process is interrupted, and a return is made to step S 12 or S 22 , which is equivalent to waiting for the speed to become less than or equal to V 1 in order to start or restart the defrosting operation. If the vehicle speed is already less than or equal to Vi, the operation of defrosting the external exchanger is enabled. It should be noted that, if the defrosting is interrupted, the compressor and, if necessary, the motorized fan unit as described below in the present description are stopped only if there is no other demand to be met. Otherwise they are used, with different motor speeds if necessary, to meet this other demand.
  • one or more supplementary conditions are added for the enabling of the defrosting operation. For example, at least one of the following conditions is added:
  • the compressor 10 is then put into operation, in step S 101 , at a predetermined motor speed R 2 .
  • the value R 2 is a function of the element to be defrosted.
  • the motor speed is advantageously higher for defrosting the accumulator than it is for defrosting the external exchanger.
  • R 2 is, for example, equal to 5000 r.p.m.
  • R 2 is, for example, equal to 6000 r.p.m.
  • the motor speed R 2 of the compressor is defined as a function of the external temperature T ext . As the external temperature decreases, the motor speed R 2 increases.
  • compressed refrigerant fluid flows through the external exchanger and the accumulator so as to cause the melting of the frost on the outer walls of the external exchanger and at least some of the frost on the outer walls of the accumulator.
  • a counter COMP3 is incremented in a step S 102 as long as the following conditions are present:
  • the method includes a step S 103 of comparing the external temperature T ext with the temperature threshold T 6 and a step S 104 of comparing the temperature T S with the temperature threshold T 7 and of comparing the count value of the counter COMP3 with the count value C3.
  • step S 104 If T S ⁇ T 7 and COMP3 ⁇ C 3 , a return is made to step S 100 . Otherwise, the method continues to step S 106 , in which the external temperature T ext is compared with a positive temperature T 8 .
  • the method continues to a second phase of the defrosting operation during which phase the motorized fan unit 17 located near the external exchanger 14 is put into operation to remove by blowing the residual water which is present on the outer walls of the external exchanger as a result of the melting of the frost during the previous phase of the defrosting operation.
  • This second phase of the defrosting operation is useful only if the external temperature T ext is not highly negative. This is why this second phase is preceded by the step S 106 of comparing the external temperature T ext with the temperature T 8 .
  • T 8 is, for example, equal to ⁇ 10° C. If T ext ⁇ T 8 , the motorized fan unit is not put into operation, as any blowing of external air over the external exchanger would cause the refreezing of much of the residual water present on the outer walls of the exchanger. Consequently there is no benefit in executing this second phase. It is even preferable to avoid it, in order to prevent the refrosting of the walls of the exchanger and thus avoid unnecessary power consumption. The compressor is then stopped in step S 105 . If T ext >T 8 , the motorized fan unit 17 is put into operation in a step S 108 .
  • the compressor is preferably put into operation at a speed R3 of less than F3 ⁇ 4.
  • R3 is, for example, equal to 4000 r.p.m. for the defrosting of the exchanger and the defrosting of the accumulator.
  • This blowing phase is executed as long as the temperature T S is greater than or equal to a positive temperature T 9 and as long as a maximum duration D4 corresponding to a count value C 4 has not been exceeded. This is because, during blowing, the temperature of the fluid flowing through the exchanger falls, and, if this approaches a temperature close to 0° C., there is a risk that the water originating from the melting of the initial frost will freeze.
  • the temperature T 9 is, for example, equal to 2° C., and the duration D 4 corresponding to C 4 is, for example, equal to 2 minutes.
  • T 9 is advantageously close to 0° C.
  • This phase therefore includes a step S 109 of incrementing a counter COMP4 and a step S 110 of comparing the temperature T S with the value T 9 and comparing the count value of the counter COMP4 with the count value C 4 .
  • Step S 108 is advantageously preceded by a step S 107 of enabling defrosting, identical to step S 100 .
  • step S 12 or S 22 If the defrosting is not enabled because of a non-zero vehicle speed or a priority demand, for example a demand for thermal comfort, for pre-conditioning of the passenger compartment or for battery air conditioning, a return is made to step S 12 or S 22 . In this case, the compressor and the motorized fan unit are stopped only if there is no other demand to be met. Otherwise they are used, with different motor speeds if necessary, to meet this other demand.
  • a non-zero vehicle speed or a priority demand for example a demand for thermal comfort
  • the blowing phase is stopped when the temperature T S is less than T 9 or when the count value of the counter COMP4 is greater than or equal to the count value C 4 .
  • the compressor and the motorized fan unit are then stopped, in step S 111 . As long as one or other of these two conditions is not met, the blowing continues and the counter COMP4 is incremented.
  • step S 112 The counters COMP3 and COMP4 are reset to zero, in a step S 112 , only after the compressor, and the motorized fan unit if appropriate, has/have been stopped. A return is then made to step S 13 or S 23 in which the counters COMP1 and COMP2 are reset to zero.
  • the compressor, and the motorized fan unit if appropriate, cease(s) to be used for defrosting as soon as a demand for use with higher priority in the system occurs.
  • the defrosting demand takes priority over one or more other demands.
  • step S 15 it is possible, on the basis of detection of frosting of the exchanger, to send a general frosting command, and then to start an operation of defrosting the exchanger or to start an operation of defrosting the accumulator according to a predefined principle.
  • This specific embodiment is shown in FIG. 7 .
  • the method then includes steps identical to steps S 10 to S 14 of FIG. 5 .
  • the references S 10 to S 15 are also used again in FIG. 7 .
  • the defrosting command that is sent is considered to be a command which is valid both for starting an operation of defrosting the external exchanger and for starting an operation of defrosting the accumulator.
  • a step S′ 16 an operation of defrosting the external exchanger or an operation of defrosting the accumulator is started, according to said predefined principle. For example, an operation of defrosting the accumulator is started on one of every n occasions, where n is an integer greater than or equal to 2, while on the other occasions an operation of defrosting the external exchanger is started.
  • the detection of frosting on the exchanger (S 10 to S 15 ) and the detection of frosting on the accumulator (S 20 to S 25 ) are carried out simultaneously, as described above, while in the defrosting step, denoted S′′ 16 , the defrosting parameters of the circuit will be those of the defrosting of the accumulator if its frosting is detected, or otherwise those of the defrosting of the external exchanger.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
US14/383,657 2012-03-08 2012-11-26 Automatic control method used for defrosting a heat pump for a vehicle Abandoned US20150040589A1 (en)

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FR1252112 2012-03-08
FR1252112A FR2987889B1 (fr) 2012-03-08 2012-03-08 Procede de commande automatique destine au degivrage d'une pompe a chaleur pour vehicule
PCT/EP2012/073558 WO2013131589A1 (fr) 2012-03-08 2012-11-26 Procede de commande automatique destine au degivrage d'une pompe a chaleur pour vehicule

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US20150120112A1 (en) * 2012-04-03 2015-04-30 Renault S.A.S. Method of managing the charging of a traction battery and corresponding devices
US20150246594A1 (en) * 2012-09-18 2015-09-03 Denso Corporation Air conditioner for vehicle
US20160209099A1 (en) * 2015-01-15 2016-07-21 Ford Global Technologies, Llc De-Icing Control in a Vapor Compression Heat Pump System
US20160332504A1 (en) * 2015-05-15 2016-11-17 Ford Global Technologies, Llc System and method for de-icing a heat pump
WO2018088124A1 (fr) * 2016-11-14 2018-05-17 サンデン・オートモーティブクライメイトシステム株式会社 Climatiseur de véhicule
US20220016958A1 (en) * 2020-07-15 2022-01-20 Honda Motor Co., Ltd. Vehicle

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FR3026172B1 (fr) * 2014-09-24 2017-06-02 Valeo Systemes Thermiques Procede de pilotage d'une installation de chauffage, ventilation et/ou climatisation et installation correspondante, avec limitation de debit d'air
FR3049236B1 (fr) * 2016-03-23 2019-05-10 Valeo Systemes Thermiques Dispositif de climatisation pour un vehicule automobile
JP6458079B2 (ja) * 2017-05-19 2019-01-23 本田技研工業株式会社 空調装置

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US4286435A (en) * 1978-10-02 1981-09-01 Carrier Corporation Hot gas defrost system
US4680940A (en) * 1979-06-20 1987-07-21 Vaughn Eldon D Adaptive defrost control and method
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Publication number Priority date Publication date Assignee Title
US20150120112A1 (en) * 2012-04-03 2015-04-30 Renault S.A.S. Method of managing the charging of a traction battery and corresponding devices
US9827859B2 (en) * 2012-04-03 2017-11-28 Renault S.A.S. Method of managing the charging of a traction battery and corresponding devices
US20150246594A1 (en) * 2012-09-18 2015-09-03 Denso Corporation Air conditioner for vehicle
US20160209099A1 (en) * 2015-01-15 2016-07-21 Ford Global Technologies, Llc De-Icing Control in a Vapor Compression Heat Pump System
US10514191B2 (en) * 2015-01-15 2019-12-24 Ford Global Technologies, Llc De-icing control in a vapor compression heat pump system
US20160332504A1 (en) * 2015-05-15 2016-11-17 Ford Global Technologies, Llc System and method for de-icing a heat pump
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WO2018088124A1 (fr) * 2016-11-14 2018-05-17 サンデン・オートモーティブクライメイトシステム株式会社 Climatiseur de véhicule
US20220016958A1 (en) * 2020-07-15 2022-01-20 Honda Motor Co., Ltd. Vehicle

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US10639965B2 (en) 2020-05-05
CN104159759A (zh) 2014-11-19
EP2822788B1 (fr) 2016-11-02
EP2822788A1 (fr) 2015-01-14
FR2987889A1 (fr) 2013-09-13
US20190023104A1 (en) 2019-01-24
CN104159759B (zh) 2017-03-22
KR20140143786A (ko) 2014-12-17
FR2987889B1 (fr) 2014-04-18
KR102108496B1 (ko) 2020-05-08
WO2013131589A1 (fr) 2013-09-12
JP2015520834A (ja) 2015-07-23
JP6177811B2 (ja) 2017-08-09

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