DEVICE AND METHOD FOR CONTROLLING THE AIR-CONDITIONING SYSTEM OF A VEHICLE

Abstract

Described herein is a control device (27) for the air-conditioning system of a vehicle that comprises an evaporator (3), a compressor (4) with externally controlled variable displacement, and an expansion valve (6), the control device (27) comprising a control block (12) that receives a reference temperature (TREF) indicating the temperature of the air that it is desired to reach downstream of the evaporator (3), and an effective temperature (TMIS) indicating the temperature of the air present downstream of the evaporator (3), and supplies a control signal (SC) for the compressor (4) in such a way as to bring the effective temperature (TMIS) to be substantially equal to the reference temperature (TREF), an observer module (16) designed to receive the control signal (SC) and to supply at output a temperature disturbance (ΔTEVAP) indicating a estimate of the oscillatory effect that is generated by the expansion valve (6) on the temperature of the air downstream of the evaporator (3) when the compressor (4) is driven by the control signal (SC); and an adder block (24) designed to depurate from the effective temperature (TMIS) the temperature disturbance (ΔTEVAP) estimated in such a way as to eliminate the oscillatory effect on the effective temperature (TMIS) of the air downstream of the evaporator (3).

Description

The present invention relates to a device and to a method for the control of the air-conditioning system of a vehicle, in particular a motor vehicle such as an automobile, a bus, etc.

As is known, the air-conditioning systems of motor vehicles are typically provided with a closed-loop cooling circuit equipped with an evaporator and a control system capable of regulating the temperature of the air introduced into the passenger compartment.

FIG. 1 shows a control system 1 of a cooling circuit 2, which is traversed by the coolant and comprises in succession: an evaporator 3; a compressor 4, which is designed to take in, at a certain intake pressure, the coolant in the vapour phase from the evaporator 3 so as to obtain a control of the temperature of the air downstream of the evaporator 3 itself; a condenser 5, designed to receive the coolant in the vapour phase from the compressor 4; and an expansion valve 6 designed to receive the coolant in the liquid phase from the condenser 5 to supply it in dual-phase (i.e., vapour phase and liquid phase) to the evaporator 4 itself.

In particular, the compressor 4 is constituted by a compressor with externally controlled variable displacement, on which it is possible to operate by causing the displacement (defined as the working volume, where the coolant is compressed) to vary as the thermal load acting on the air-conditioning system varies.

The possibility of varying the displacement of the compressor is obtained via the electromagnetic regulation valves (not illustrated), which are driven via an external control signal S_C and are designed to control the device that enables modulation of the displacement of the compressor 4.

The control system 1 moreover comprises a control device 7, which is able to generate the control signal S_C of the compressor 4 in such a way as to control the temperature of the air downstream of the evaporator 3 as a function of the deviation between a reference temperature T_REF set by the user by means of an externally controlled selector device 9 and an effective temperature T_MIS indicating the temperature of the air present downstream of the evaporator 3. The effective temperature T_MIS can be measured using a temperature sensor 10, set downstream of the evaporator 3.

The control device 7 comprises an adder block 11 having a first input designed to receive the reference temperature T_REF from the selector device 9, a second input designed to receive the effective temperature T_MIS from the temperature sensor 10, and an output supplying a temperature error e_r, given by the difference between the reference temperature T_REF and the effective temperature T_MIS.

The control device 7 moreover comprises a control block 12, which is designed to receive at input the temperature error e_r and a set of measurement parameters, such as for example Te (external temperature), RPM (engine r.p.m.), and RH (relative humidity) correlated to the exogenous disturbance, and supplies at output, according to the latter, the control signal S_C.

In detail, the control block 12 comprises a compensating network of a proportional-integral (PI) type (not illustrated) and generates a control signal S_C corresponding to a pulse-width modulation (PWM) signal, which drives the electromagnetic valves for regulating the stroke of the pistons, thus determining control of the displacement of the compressor 4. In the case in point, the regulation of the displacement determines a control of the intake pressure of the compressor 4 and, consequently, an indirect control of the temperature of the air downstream of the evaporator 3.

It is moreover known that, in the air-conditioning systems described above, the expansion valve 6 for supplying the coolant to the evaporator 3 is an internally controlled device, operation of which is completely independent of the control implemented on the compressor 4 by the control device 7.

The complete independence existing between the two controls determines, in certain limit conditions of operation of the compressor 4, a discordance in the control of some parameters that characterize operation of the cooling circuit 2, such as for example the intake pressure of the compressor 4 and the temperature of the air downstream of the evaporator 3, in this way causing a condition of instability of the air-conditioning system. In the case in point, during its operation, the expansion valve 6 generates a temperature disturbance ΔT_EVAP of an oscillatory type, which alters the temperature of the air downstream of the evaporator 3, and leads, in certain conditions, to instability of the control.

In fact, said temperature disturbance ΔT_EVAP determines an increase of the intake pressure of the compressor 4, which in certain limit conditions exceeds a threshold delimiting the condition of stability of the air-conditioning system, consequently causing a series of oscillations of the flow rate of the coolant, and of the temperature of the air downstream of the evaporator 3. The generation of said oscillations, generally referred to with the term “hunting phenomenon”, represents a major drawback in the air-conditioning systems described above in so far as it has a negative effect both on the capacity of minimizing the consumption of the air-conditioning system, and on the thermal comfort of the passenger compartment of the vehicle.

The aim of the present invention is consequently to provide a device and method for control of the air-conditioning system of a vehicle that is able to overcome the drawbacks described above.

The above purpose is achieved by the present invention in so far as it relates to a control device of the air-conditioning system of a vehicle, according to what is specified in Claim 1 and, preferably, in any one of the subsequent claims that are directly or indirectly dependent upon Claim 1.

According to the present invention there is moreover provided a method for control of the air-conditioning system of a vehicle, according to what is specified in Claim 8 and, preferably, in any one of the subsequent claims that are directly or indirectly dependent upon Claim 8.

The present invention will now be now described with reference to the annexed plate of drawings, which illustrate a non-limiting example of embodiment thereof and in which:

• • FIG. 1 is a schematic illustration of a control system of an air-conditioning system comprising a control device according to the known art;
  • FIG. 2 is a schematic illustration of a control system of an air-conditioning system comprising a control device according to the teachings of the present invention;
  • FIG. 3 shows a block diagram of an observer module comprised in the control device illustrated in FIG. 2;
  • FIG. 4 shows a system model representing the effects produced by the expansion valve and by the evaporator on the temperature of the evaporator as a function of a control signal generated by the control device.

The present invention is substantially based upon the principle of supplying a reference temperature T_REF indicating the temperature of the air that it is desired to reach downstream of the evaporator; supplying an effective temperature T_MIS that indicates the temperature of the air present downstream of the evaporator; generating a control signal S_C that drives the compressor in such a way as to bring the effective temperature T_MIS to be substantially equal to the reference temperature T_REF; generating, according to the control signal S_C, a temperature disturbance ΔT_EVAP indicating an estimate of the oscillatory effect that is generated by the expansion valve on the temperature of the air downstream of the evaporator when the compressor is driven by the control signal S_C; and finally depurating from the effective temperature T_MIS the temperature disturbance ΔT_EVAP estimated in such a way as to eliminate the oscillatory effect on the effective temperature T_MIS of the air downstream of the evaporator 3.

FIG. 2 is a schematic illustration of a control system 15 of the temperature of the air downstream of an evaporator, which is partially similar to the system 1, and component parts of which will be distinguished, wherever possible, with the same reference numbers that distinguish corresponding parts of the control system 1.

The control system 15 differs from the control system 1 in so far as it comprises an observer module 16 having the function of estimating the temperature disturbance ΔT_EVAP produced by the expansion valve 6 on the temperature T_EVAP=T_MIS of the air downstream of the evaporator 3. In the case in point, the observer module 16 comprises an input designed to receive the control signal S_C of the compressor 4, and an output designed to supply the estimate of the temperature disturbance ΔT_EVAP.

In greater detail, with reference to FIG. 3, the observer module 16 basically comprises a conversion block 17, a gain block 18, and a transformation block 19.

The conversion block 17 receives at input the control signal S_C and supplies at output the intake pressure P_LOW of the compressor 4, which is obtained by regulating the displacement thereof via the control signal S_C. In particular, in the case where the control block 12 generates the control signal S_C corresponding to a PWM signal, the conversion block 17 implements a biunique function between the PWM pulses of the control signal S_C sent to the compressor 4 and the intake pressure P_LOW controlled via the control signal S_C itself.

As regards, instead, the gain block 18 and the transformation block 19, these implement a transfer function F(z) that links the temperature disturbance ΔT_EVAP to the intake pressure P_LOW of the compressor 4.

In the case in point, the transfer function F(z) can be determined on the basis of a behavioural model 20 (illustrated by a dashed line in FIG. 4), which represents the overall effect produced by the evaporator 3 and by the expansion valve 6 on the temperature T_EVAP of the coolant at output from the evaporator 3 itself, during control of the system 15.

The behavioural model 20 basically comprises a block 21, which models the effect of the expansion valve 6 on the temperature T_EVAP of the air downstream of the evaporator 3 as a function of the control signal S_C supplied to the compressor 4, and a block 22, which models the effect of the evaporator 3 on the temperature T_EVAP of the air downstream of the evaporator 3 itself as a function of the control signal S_C supplied at input to the compressor 4.

The behavioural model 20 identifies then the overall behaviour of the expansion valve 6 and of the evaporator 3; said behavioural model 20 can be represented by the following system of equations: x(t+1)=Ax(t)+Bu(t)+Re(t) Y(t)=Cx(t)+Du(t)+e(t)

Where x(t) are the states of the system, u(t) is an input signal corresponding to the intake pressure P_LOW of the compressor 4, y(t) is the output signal corresponding to the effective temperature T_EVAP=T_MIS (T_EVAP=T_EVOUT+ΔT_EVAP) of the air supplied at output from the behavioural model 20, and e(t) is the disturbance ΔT_EVAP introduced by the expansion valve 6 on the temperature of the air T_EVOUT.

Since the disturbance ΔT_EVAP acts directly on the output of the behavioural model 20, it is possible to assume the matrix R=0 and consequently the system of equations described above can be simplified in the following way: x(t+1)=Ax(t)+Bu(t) Y(t)=Cx(t)+Du(t)+e(t)

The aforesaid mathematical system can be solved according to the disturbance e(t)=ΔT_EVAP and on the basis of a set of pre-set known conditions. From said system it is then possible to determine the transfer function F(z) that indicates the ratio between the disturbance e(t)=ΔT_EVAP and the intake pressure P_LOW; said transfer function F(z) is implemented as a whole by the blocks 18 and 19 of the observer module 16: $F\left(z\right)=\frac{\Delta T_{\mathrm{EVAP}}}{P_{\mathrm{LOW}}}={\mathrm{KF}}_1\left(z\right)=K\frac{\mathrm{az}}{z^2-\mathrm{bz}+c}$ where K is the gain that is introduced by the gain block 18, whilst the discrete transfer function $F_1\left(z\right)=\frac{\mathrm{az}}{z^2-\mathrm{bz}+c}$ is implemented by the transformation block 19.

With reference to FIG. 2, the observer module 16 and the control block 12 can be implemented in a control device 27, which comprises, in addition to the adder block 11 (comprised in the control system 1 described above), which supplies at output the temperature error e_r, an adder block 24, which has an input receiving the temperature error e_r, an input receiving the disturbance ΔT_EVAP estimated by the observer module 16, and an output supplying a depurated error e_d given by the difference between the temperature error e_r and the estimated disturbance ΔT_EVAP.

The control device 27 moreover comprises a correction block 25, which has an input receiving the effective temperature T_MIS, and an output supplying a correction coefficient ΔT_COR, which indicates the correction of temperature to be made to the reference signal supplied at input to the control block 12 in such a way as to compensate the deviations present between the reference temperature T_REF and the effective temperature T_MIS as the temperature of the evaporator 3 varies.

In fact, even though the observer block 16 is able to compensate the oscillations, i.e., the “hunting phenomenon”, due to the introduction of the temperature disturbance ΔT_EVAP by the expansion valve 6, the control of the temperature T_EVAP is influenced also by the variations of the temperature of the evaporator 3 itself.

In fact, as the reference temperature T_REF varies, a deviation occurs between the latter and the effective temperature T_MIS, which varies as the temperature of the evaporator 3 varies, thus determining a further error on the control thereof. For this purpose, the correction block 25 contains a table, determined in the experimental stage, containing a plurality of correction coefficients ΔT_COR, each of which is associated to an effective temperature T_MIS.

The control device 27 moreover comprises an adder block 26, which has an input receiving the depurated error e_d and an input receiving the correction coefficient ΔT_COR, and supplies at output an error e_F given by the difference between the depurated error e_d and the correction coefficient ΔT_COR.

During operation, the user sets up the reference temperature T_REF of the air that it is desired to obtain downstream of the evaporator 3, which is supplied at input to the adder block 11 that calculates the error e_r, and at the same time the observer module 16 estimates on the basis of the control signal S_C the disturbance ΔT_EVAP to be subtracted from the error e_r to guarantee the absence of oscillations on the temperature T_EVAP of the evaporator 3.

In this step, the adder block 24 depurates the disturbance ΔT_EVAP from the error e_r in such a way as to generate the depurated error e_d so as to compensate the possible oscillations introduced into the effective temperature T_MIS. At this point the correction block 25 generates, on the basis of the effective temperature T_MIS, the correction coefficient ΔT_COR to be subtracted from the depurated error e_d. The control block 12 receives the depurated error e_d and generates the control signal S_C that drives the electromagnetic valves for controlling the intake pressure of the air of the compressor 4 so as to bring the measured temperature T_MIS=T_EVAP to a value substantially equal to the reference temperature T_REF.

The control device 7 described above is extremely advantageous in so far as it prevents the onset of the hunting phenomenon. The strategy of compensation of the disturbance due to the onset of the hunting phenomenon is always operative, and in the case where the phenomenon is not present, its contribution is zero. Moreover, the control device 7 never changes its structure.

Finally, it is clear that modifications and variations can be made to the control device 27 of the control system 15 described and illustrated herein, without thereby departing from the scope of the present invention, as defined by the annexed claims.

Claims

1. A control device of the air-conditioning system of a vehicle, in particular a motor vehicle; the air-conditioning system comprising an evaporator, a compressor with externally controlled variable displacement set downstream of said evaporator, and an expansion valve set upstream of said evaporator; said control device being characterized in that it comprises: control means for receiving at input a reference temperature (TREF) indicating the temperature of the air that it is desired to reach downstream of the evaporator, and an effective temperature (TMIS) indicating the temperature of the air presents downstream of said evaporator, and designed to supply at output a control signal (SC) for said compressor in such a way as to bring said effective temperature (TMIS) to be substantially equal to said reference temperature (TREF); observer means for receiving at input the control signal (SC), and to supply at output a temperature disturbance (ΔTEVAP) indicating an estimate of the oscillatory effect that is generated by the expansion valve on the temperature of the air downstream of the evaporator when the compressor is driven by the control signal (SC); and first adder means designed to depurate from said effective temperature (TMIS) said temperature disturbance (ΔTEVAP) estimated in such a way as to eliminate the oscillatory effect on said effective temperature (TMIS) of the air downstream of the evaporator.

2. A control device according to claim 1, characterized in that said observer means are designed to estimate said temperature disturbance (ΔTEVAP) on the basis of a system model, and according to said control signal (SC).

3. A control device according to claim 2, characterized in that said observer means comprise conversion means, designed to receive at input the control signal (SC) and to supply at output an intake pressure (PLOW) of the compressor; transformation means, designed to receive at input the intake pressure (PLOW) and designed, as a result of the system model, to supply at output said temperature disturbance (ΔTEVAP).

4. A control device according to claim 3, characterized in that said system model implements a transfer function (F(z)) determined on the basis of a first effect produced by the expansion valve on the temperature (TEVAP) of the evaporator, when the compressor is controlled by the control signal (SC) and on the basis of a second effect produced by the evaporator on the temperature (TEVAP) of the evaporator itself, when the compressor is controlled by the control signal (SC).

5. A control device according to claim 1, characterized in that it comprises second adder means designed to receive at input said reference temperature (TREF) and said effective temperature (TMIS) and to supply at output a first error (er) of temperature of the air downstream of the evaporator, which is correlated to the difference between the reference temperature (TREF) and the effective temperature (TMIS); the first adder means receiving at input the first temperature error (er) and the temperature disturbance (ΔTEVAP) for supplying at output a second temperature error (ed) of the evaporator, which is correlated to the difference between the first temperature error (er) and the temperature disturbance (ΔTEVAP); said controller means generate said control signal (SC) according to said second temperature error (ed).

6. A control device according to claim 1, characterized in that it comprises correction means receiving at input said effective temperature (TMIS) and supplying at output a correction coefficient (ΔTCOR), indicating the correction to be made on the effective temperature (TMIS) to compensate the deviations that arise between the reference temperature (TREF) and the effective temperature (TMIS), as the temperature downstream of the evaporator varies; and third adder means, designed to receive at input the second temperature error (ed) and the correction coefficient (ΔTCOR) and supplying at output a third temperature error (eF) of the evaporator correlated to the difference between the second temperature error (ed) and the correction coefficient (ΔTCOR); said controller means being designed to generate said control signal (SC) as a function of said third error signal (eF).

7. A control device according to claim 1, characterized in that said control signal (SC) is a PWM signal designed to regulate the displacement of the compressor.

8. A control method for an air-conditioning system of a vehicle, in particular a motor vehicle; the air-conditioning system comprising an evaporator, a compressor with externally controlled variable displacement set downstream of said evaporator, and an expansion valve setup stream of said evaporator; said control method comprising the following steps: supplying a reference temperature (TREF) indicating the temperature of the air that it is desired to reach downstream of the evaporator and an effective temperature (TMIS) indicating the temperature of the air present downstream of said evaporator; generating a control signal (SC) for said compressor in such a way as to bring said effective temperature (TMIS) to be substantially equal to said reference temperature (TREF); generating, as a function of the control signal (SC) a temperature disturbance (ΔTEVAP) indicating an estimate of the oscillatory effect that is generated by the expansion valve on the temperature of the air downstream of the evaporator when the compressor is driven by the control signal (SC); and depurating from said effective temperature (TMIS) said temperature disturbance (ΔTEVAP) estimated in such a way as to eliminate the oscillatory effect on said effective temperature (TMIS) of the air downstream of the evaporator.

9. A control method according to claim 8, characterized in that said step of generating a temperature disturbance (ΔTEVAP) comprises the step of estimating said temperature disturbance (ΔTEVAP) on the basis of a system model, and according to said control signal (SC) of said compressor.

10. A control method according to claim 9, characterized in that said step of estimating said temperature disturbance (ΔTEVAP) comprises the step of converting the control signal (SC) into an intake pressure (PLOW) of the compressor; and determining said temperature disturbance (ΔTEVAP) as a result of a transfer function (F(z)) determined on the basis of a first effect produced by the expansion valve on the temperature of the air downstream of the evaporator when the compressor is controlled by the control signal (SC) and on the basis of a second effect produced by the evaporator on the temperature of the air downstream of the evaporator itself when the compressor is controlled by the control signal (SC).