IT201900012918A1 - PROCESS AND EQUIPMENT FOR MONITORING AND / OR CONTROL OF AN AIR CONDITIONING AND / OR HEATING SYSTEM - Google Patents

Description

DESCRIPTION

attached to a patent application for an INDUSTRIAL INVENTION PATENT entitled:

"PROCESS AND MONITORING EQUIPMENT AND / OR

CONTROL OF AN AIR CONDITIONING SYSTEM AND / OR

HEATING"

FIELD OF THE TROVATO

The invention concerns a monitoring and / or control process of an air conditioning and / or heating system, for example of the HVAC type. In some embodiments, the process and the device according to aspects of the invention can be used to actively control or monitor parameters such as the flow rate of fluid or the temperature of the vector fluid passing through one or more heat exchange units forming part of a plant air conditioning and / or heating. The invention also relates to an air conditioning and / or heating system using the process or and the device according to the invention. The invention can be used both in the civil and industrial fields and advantageously exploited for the control and optimization of air conditioning and / or heating systems at the energy level.

STATE OF THE ART

As is known, heating and / or conditioning systems are increasingly used to maintain environments, such as rooms of units for residential or working use, in desired climatic conditions, for example temperature and / or humidity.

These systems are generally powered by a central unit comprising a heating unit (such as a boiler, heat pump or other) and / or a refrigerating unit; the central unit sends a carrier fluid with desired properties in terms of temperature, flow rate and specific heat to an appropriate distribution circuit. In the environment to be air-conditioned there are then one or more heat treatment units (for example a fan or fan coil) coupled with a portion of the distribution circuit and capable of transferring heat or respectively cold from the vector fluid circulating in the distribution circuit to the environment to serve. The control and optimization of air conditioning and / or heating systems are rather complex tasks, particularly when there are numerous environments served by the same system: think in this regard of systems for offices, hotels, or in general complexes in which there are numerous distinct environments where, therefore, the vector fluid must be conveyed in the optimal conditions of temperature and flow rate in order to guarantee an efficient and optimized heat exchange.

It is clear how the efficiency of the energy exchange in each environment and the control method of the main parameters of the carrier fluid affect the efficiency of the system as a whole and therefore impact on the overall management costs. In particular, in the context of a large plant, it is generally important to appropriately manage parameters such as the flow rate and / or temperature of the carrier fluid, as well as the thermal power exchanged at each exchanger.

Finally, in addition to an intrinsic control complexity given by the multiplicity of environments served by the same plant, there is also great difficulty in recognizing whether the plant is in fact working optimally and therefore close to its ideal working conditions or if vice versa there is they are problems linked to a progressive degradation of performance or inefficiencies linked for example to an incorrect use of one or more terminals (think for example of partially clogged or damaged exchangers).

The known technical solutions have often been found to be inadequate in monitoring the behavior of the plant and in controlling the vector fluid, forcing the plant to operate as a whole in non-optimal conditions.

A further problem is given by the identification of appropriate models that make it possible to represent the behavior of the system well and therefore make it easier to monitor.

PURPOSE OF THE FIND

The aim of the present invention is therefore to solve at least one of the drawbacks and / or limitations of the previous solutions.

In particular, an object of the invention is to suitably control an air conditioning / heating system in order to optimize its energy exchange, avoiding or reducing operating conditions of poor efficiency.

A further object of the invention is to provide a process and a device that allow the detection and modeling of the plant behavior and therefore the characterization of various branches of the plant itself, so as to allow effective monitoring of the plant itself.

In addition, an object of the invention is to provide a device and a control process for conditioning and / or heating systems capable of optimally regulating one or more parameters of the vector fluid passing through the exchangers. In particular, it is an object of the invention to provide a device and a control process which allow to control the temperature and / or flow rate of the carrier fluid so as to avoid or reduce pressure drops and / or thermal losses. An additional purpose of the invention is to make available an air conditioning and / or heating system that allows to improve energy management in a system intended to serve a plurality of distinct environments.

One or more of the objects described above and which will appear better in the course of the following description are substantially achieved by a process and / or by a device and / or by a plant according to one or more of the attached claims.

SUMMARY

Aspects of the invention are described below.

A 1st aspect concerns a monitoring and / or control process of at least one air conditioning and / or heating system (1), said system comprising at least one delivery line (3), at least one return line (4) and a preset number of service lines (5) hydraulically interposed between the delivery line (3) and the return line (4), each service line (5) including at least one heat exchange unit (7).

In a 2nd aspect according to the previous aspect at least one heat exchange modulator (7a) is associated with the heat exchange unit (7).

In a 3rd aspect according to any of the preceding aspects, the process envisages, for at least one of said service lines (5), the phases of:

- circulate a carrier fluid through at least one service line so that the same particle of carrier fluid crossing a first section of the service line upstream of the heat exchange unit (7) crosses a second section of the same service line located downstream of the heat exchange unit (7) successively, with a hydraulic delay (dt) given by a time necessary for the same fluid particle to pass from the first to the second section,

- repeating a cycle which in turn comprises the following sub-phases a plurality of times:

a) determine at least one value of the temperature difference (ΔT) between:

� the temperature (Tt1) of the vector fluid, in correspondence with the first section, measured at a first instant (t1), and

� the temperature (Tt2) of the vector fluid, in correspondence with the second section, measured at a second instant (t2), which is subsequent to said hydraulic delay (dt) with respect to the first instant (t1),

b) detect the value (φ) of the vector fluid flow passing through the heat exchange unit (7), in an instant of detection (tm) subsequent to the first instant (t1) and prior to the second instant (t2),

obtaining in each cycle values, in particular at least one pair of values, comprising the value of said temperature difference (ΔT) and said corresponding value of the vector fluid flow (φ).

In a 4th aspect according to the previous aspect, the process involves the further phase of:

- using at least a plurality of said values, in particular at least a plurality of pairs of said values, obtained in respective cycles, to determine at least one of the following:

or a characteristic function which relates said temperature difference (ΔT) between the first and second sections to said value of the vector fluid flow (φ),

or a characteristic function that relates an exchanged thermal power (dQ / dt) from the heat exchange unit to said value of the vector fluid flow (φ).

In a 5th aspect according to the 3rd or 4th aspect, said process, optionally before carrying out said cycle, involves the execution of one of the following phases:

- receiving a value of the hydraulic delay (dt) between said first and said second section of the same service line,

- determining a value of the hydraulic delay (dt) between said first and said second section of the same service line,

- determining the second instant (t2), which is subsequent to said hydraulic delay (dt) with respect to the first instant (t1).

In a 6th aspect according to the 3rd or 4th said each cycle comprises one of the following sub-phases:

- receiving a value of the hydraulic delay (dt) between said first and said second section of the same service line, or

- determining a value of the hydraulic delay (dt) between said first and said second section of the same service line, or

- determining the second instant (t2), which is subsequent to said hydraulic delay (dt) with respect to the first instant (t1).

In a 7th aspect according to the 5th or 6th aspect there is the sub-phase of determining said hydraulic delay (dt) which includes:

- determining a control volume (V0) relative to a volume of vector fluid comprised between said first and said second section, and

- calculate the hydraulic delay as the time interval from the first instant (t1) and necessary for a volume of vector fluid equal to the control volume (V0) to cross the first section (5a).

In an 8th aspect according to any of the previous three aspects, the sub-phase of determining the second instant (t2) is foreseen, which includes:

- determining a control volume (V0) relative to a volume of vector fluid comprised between said first and said second section, and

- therefore, having measured, starting from the first instant t1 (for example using the flow detector present in each line (5)) the volume of vector fluid that progressively crosses the first section, the instant (t2) is directly calculated as that instant in which a volume of vector fluid equal to the control volume (V0) has passed through the first section (5a).

In a 9th aspect according to any of the previous two aspects the step of determining the control volume (V0) in turn comprises:

- measure a temperature of the carrier fluid at the first section and the second section,

- vary the temperature of the vector fluid entering said service line, - identify an initial instant (ts) in which the temperature of the vector fluid in correspondence with the first section varies, optionally beyond a predetermined threshold,

- identify a final instant (tf) in which the temperature of the vector fluid in correspondence with the second section varies, optionally beyond a predetermined threshold,

- measuring values of the vector fluid flow (φ (t)) during an interval between said initial instant and said final instant,

- calculate the control volume (V0) on the basis of the values assumed by the flow of vector fluid in the interval between said initial instant and said final instant.

In a 10th aspect according to the previous aspect, calculating the control volume (V0) on the basis of the values assumed by the flow of vector fluid in the interval between said <initial instant and said final instant envisages using the following formula:>

in which:

o φ (t) represents the value of the vector fluid flow over time,

o ts is the initial instant,

o tf is the final instant.

In an 11th aspect according to any of the preceding aspects, the detection instant (tm) at which the sub-phase of detecting the value of the vector fluid flow (φ) passing through the heat exchange unit (7) is carried out is an instant intermediate (tm).

In a 12th aspect according to the previous aspect, the intermediate instant (tm) is an instant placed in the middle of the time interval between the first instant (t1) and the second instant (t2).

In a 13th aspect according to any of the preceding aspects, the process comprises the step of determining, by interpolating the values of the temperature difference and of the fluid flow of said plurality of pairs of values, the characteristic function which relates the temperature difference (ΔT) between the first and second sections at the value of the vector fluid flow (φ).

In a 14th aspect according to any one of the aspects preceding the process and in particular said cycle comprises the further sub-phase of determining the thermal power exchanged (dQ / dt) by the heat exchange unit, on the basis of said value of the flow of vector fluid (φ) passing through the heat exchange unit (7) and of said temperature difference (ΔT), obtaining in each cycle a set of three values comprising:

o the value of said temperature difference (ΔT) between the temperature (Tt1) measured at the first instant (t1) and the temperature (Tt2) measured at the second instant (t2),

o the value of said vector fluid flow (φ) measured at the time of detection (tm), and

or the corresponding value of said heat exchanged power (dQ / dt) by the heat exchange unit.

In a 15th aspect according to the previous aspect, the process comprises a further step of determining the characteristic function of the heat exchange unit present in said service line which relates the exchanged thermal power (dQ / dt) with said flow value of vector fluid (φ), said characteristic function of the heat exchange unit being determined using a plurality of said triples of values obtained in respective cycles.

In a 16th aspect according to the previous aspect, the step of determining the characteristic function of the exchanger is performed using a plurality of values of the exchanged thermal power (dQ / dt) and of the vector fluid flow (φ) obtained at the respective cycles.

In a 17th aspect according to any of the preceding aspects, the characteristic function of the heat exchange unit present in said service line that relates the thermal power exchanged with the value of the vector fluid flow is an exponential curve of the type:

where is it:

dQ / dt represents the thermal power exchanged by the specific heat exchange unit,

φ is the flow of the vector fluid entering the heat exchange unit,

A and φ0 are obtained with curve fitting and / or interpolation techniques by approximating the pairs of flow values of the vector fluid (φ) and of the thermal power (dQ / dt) obtained at each cycle.

In an 18th aspect according to the previous aspect, said exponential curve is:

<where:>

where is it:

● dQ / dt represents the thermal power [kW] exchanged by the specific heat exchange unit,

● φ is the flow of the carrier fluid [kg / h] entering the heat exchange unit,

● Temperature [° C] of the vector fluid entering the unit

heat exchange, i.e. in correspondence with the first section at instant t1;

● Temperature [° C] of the air present in the environment where the heat exchange unit operates or of the air entering the heat exchange unit at instant t1;

● Dew temperature (dewpoint) [° C] of the air present in the environment where the heat exchange unit operates at instant t1 or of the air entering the heat exchange unit; the dew temperature is determined with known formulas as a function of the temperature and relative humidity of the air present at instant t1 in the environment where the heat exchange unit operates or of the air entering the heat exchange unit

and where:

a1, a2, n and φ0 are coefficients obtained with curve fitting and / or interpolation techniques by approximating the pairs of flow values of the vector fluid (φ) and of the thermal power (dQ / dt) obtained at each cycle.

In a 19th aspect according to the 17th or 18th aspect, said exponential curve is:

<where:>

and where:

● dQ / dt represents the thermal power [kW] exchanged by the specific heat exchange unit,

● φ is the flow of the vector fluid [kg / h] entering the <thermal,> exchange unit

● Temperature [° C] of the vector fluid entering the unit

heat exchange, i.e. in correspondence with the first section at instant t1;

● Temperature [° C] of the air present in the environment where the heat exchange unit operates or of the air entering the heat exchange unit at instant t1;

and where:

a1, n and φ0 are coefficients obtained with curve fitting and / or interpolation techniques by approximating the pairs of flow values of the vector fluid (φ) and of the thermal power (dQ / dt) obtained at each cycle.

In a 20th aspect according to any of the previous three aspects, the process includes determining an optimal operating range of the heat exchange unit using the characteristic function, in particular using the coefficient φ0 of the exponential curve.

In a 21st aspect according to the previous aspect, the process comprises determining an optimal operating range of the heat exchange unit using the coefficient φ0, imposing that the value of the vector fluid flow does not exceed K φ0, where K is a factor multiplicative> 1.

In a 22nd aspect according to the previous aspect, the process includes determining an optimal operating range of the heat exchange unit using the coefficient φ0, imposing that the value of the vector fluid flow does not exceed 2φ0 or 2.5φ0 or 3φ0.

In a 23rd aspect according to any of the previous three aspects, the process comprises determining an optimal operating range of the heat exchange unit using the coefficient φ0 and imposing that the value of the vector fluid flow does not fall below K ' φ0 where K 'is a multiplicative factor.

In a 24th aspect according to the previous aspect K 'is a multiplicative factor ≤ K.

In a 25th aspect according to the 23rd or 24th aspect, the process includes determining an optimal operating range of the heat exchange unit using the coefficient φ0, imposing

imposing that the vector fluid flow value does not fall below 0.25 φ0 or 0.5φ0 or 0.75φ0.

In a 26th aspect according to any one of the preceding aspects, said cycle provides a sub-phase for verifying the stability of the flow of the vector fluid.

In a 27 ° aspect according to the previous aspect, the process envisages not using, for the phase of determining the characteristic function or functions, the values of temperature difference (ΔT) and flow of vector fluid (φ) obtained in cycles where the stability check was not passed positively.

In a 28 ° aspect according to the 26 ° or 27 ° aspect, said stability verification sub-phase includes

- determine a reference flow (φr) as the ratio between the control volume V0 and said hydraulic delay (dt = t2-t1),

- compare the vector fluid flow (φ) measured at the instant of detection (tm) with the reference flow (φr),

- establish that the stability check has passed if the difference between the reference flow (φr) and the vector fluid flow (φ) is lower than a predetermined threshold (S).

In a 29th aspect according to the previous aspect in which to establish that the stability verification is positively passed if the difference between the reference flow (φr) and the vector fluid flow (φ) is lower than a predetermined threshold (S) provides for the following <check:>

In a 30 ° aspect according to the 28 ° or 29 ° aspect the threshold S is = 10% or 15% or 20% or more depending on the level of stability to be maintained.

In a 31st aspect according to any of the foregoing aspects each line of service comprises:

- at least one flow regulator (8) configured to control the flow of the carrier fluid through the heat exchange unit (7).

In a 32nd aspect according to any one of the foregoing aspects each line of service comprises:

- at least a first thermal sensor (9a) configured to detect the temperature of the vector fluid at the first section (5a) of the service line (5) and a second thermal sensor (9b) to detect the temperature of the vector fluid at the second section (5b) of the same service line (5).

In a 33rd aspect according to any one of the foregoing aspects each line of service comprises:

- at least one hydraulic sensor (10) configured to determine the flow (φ) of vector fluid.

In a 34th aspect according to any of the preceding aspects the process includes:

receiving at least one desired value of an operating parameter comprising one of:

- thermal power exchanged by the carrier fluid as it passes through each heat exchange unit (7),

- heat exchanged by the carrier fluid in a predetermined time interval as it passes through each heat exchange unit (7),

- temperature difference (ΔT) between the temperature (Tt1) of the vector fluid, in correspondence with the first section, measured at a first instant (t1), and the temperature (Tt2) of the vector fluid, in correspondence with the second section, measured at a second time instant (t2); determining, for each heat exchange unit (7), a real value of said operating parameter.

In a 35th aspect according to the previous aspect optionally in which each of said desired values is:

● a set value, or

● a value calculated according to a desired value of the temperature present in the environment where the heat exchange unit operates, or

● a value calculated as a function of a desired value of the air temperature entering the heat exchange unit;

In a 36 ° aspect according to the 34 ° or 35 ° aspect each plant includes at least one central heat treatment group (6) connected at least to the delivery line (3) and comprising:

- at least one pump (12) ed

- at least one refrigeration and / or heating unit (13)

and in which the process also provides for:

- comparing said desired value of the operating parameter with said real value of the same operating parameter,

- if, following said comparison phase, it derives that, for at least one heat exchange unit (7), the real value of the operating parameter deviates by more than a predetermined threshold from the desired value of the same operating parameter - carry out a phase of control includes at least one of:

the. control the central heat treatment group (6) to adjust at least one general parameter selected from: flow rate imposed on the carrier fluid, hydraulic head imposed on the carrier fluid passing through the central group, heating imposed on the carrier fluid passing through the central group, cooling imposed on the fluid vector crossing the central group,

ii. control the flow rate regulator (8) present on the channel (5) of the heat exchange unit (7)

iii. control the heat exchange modulator (7a) associated with the heat exchange unit (7), optionally control the number of revolutions of at least one fan part of the heat exchange modulator.

In a 37th aspect according to any one of the aspects from the 20th to the previous one, during said control phase it is envisaged to maintain the flow of the vector fluid passing through each heat exchange unit within the respective optimal operating range.

In a 38th aspect according to any one of the preceding aspects, the process comprises determining said characteristic function of the heat exchange unit a plurality of times at time intervals spaced apart, for example by one or more days, to consequently collect a plurality of characteristic curves over time. The time intervals are optionally constant.

In a 39th aspect according to any of the preceding aspects, the process comprises a procedure for identifying a malfunction condition performed at predetermined test instants, optionally periodically, for one or more heat exchange units.

In a 40th aspect according to the previous aspect, said procedure for determining a malfunction condition includes the phases of:

- measure at least one real value of the vector fluid flow passing through this heat exchange unit,

- calculating on the basis of said at least one real value of the carrier fluid flow, at least a corresponding calculated value of the temperature difference or of the thermal power exchanged by the carrier fluid in the passage through the heat exchange unit (7), said calculated value being obtained using a characteristic function determined at a predetermined time, in particular the most recently determined characteristic function,

- determine the presence of a malfunction condition of the exchanger based on the comparison between:

the. the calculated value of the temperature difference or of the heat output exchanged using said characteristic function relating to the preset time instant, and ii. a further calculated value of the temperature difference or of the heat output exchanged using said real value of the vector fluid flow and a characteristic function determined at an instant in time prior to the predetermined one.

In a 41st aspect according to the previous aspect, said procedure for determining a malfunction condition includes the phases of:

- measure at least one real value of the vector fluid flow passing through this heat exchange unit,

- determine at least a corresponding real value of said difference in temperature of the vector fluid or heat power exchanged by the vector fluid, in the passage of the vector fluid itself through the heat exchange unit (7) to said real value of the vector flow,

- calculating on the basis of said at least one real value of the carrier fluid flow, at least a corresponding calculated value of the temperature difference or of the thermal power exchanged by the carrier fluid in the passage through the heat exchange unit (7), said calculated value being obtained using a characteristic function determined at a predetermined instant in time, in particular prior to the measurement of the real value of the vector fluid flow,

- determine the presence of a malfunction condition of the exchanger based on the comparison between:

the. the calculated value of the temperature difference or of the heat output exchanged using said characteristic function relating to the preset time instant, and ii. the real value of the temperature difference or of the heat output exchanged.

In a 42nd aspect according to the 40th or 41st aspect in which determining the presence of the malfunction condition includes establishing that a malfunction condition exists if, following said comparison, a discrepancy is obtained between the values object of the comparison higher than a predetermined threshold.

In a 43rd aspect according to the previous aspect in which the procedure includes a step of classifying a type of malfunction detected as:

- malfunction caused by progressive deterioration if said discrepancy, related to the time interval between said predetermined instant and said previous instant, or related to the time interval between the instant of measurement of the real value of the vector fluid flow and said predetermined instant is less than a limit value, - malfunction due to improper use or damage to the terminal if said discrepancy, related to the time interval between said predetermined instant and said previous instant, or related to the time interval between the instant of measurement of the real value of the vector fluid flow and said predetermined instant, is higher than said limit value.

A 44th aspect concerns a monitoring and / or control process of at least one air conditioning and / or heating system (1), said system comprising at least one delivery line (3), at least one return line (4) and one predetermined number of service lines (5) hydraulically interposed between the delivery line (3) and the return line (4), each service line (5) including at least one heat exchange unit (7), and optionally at least a heat exchange modulator (7a) associated with the heat exchange unit (7),

in which said process provides, for at least one of said service lines (5), the phases of:

- circulate a carrier fluid through at least one service line,

- repeating a cycle which in turn comprises the following sub-phases a plurality of times:

a) determine at least one value of the temperature difference (ΔT) between:

� the temperature (Tt1) of the carrier fluid, at a first section of the service line upstream of the heat exchange unit (7) and

� the temperature (Tt2) of the carrier fluid, at the second section of the same service line located downstream of the heat exchange unit (7) subsequently,

b) detect the value (φ) of the vector fluid flow passing through the heat exchange unit (7),

c) determine the heat exchanged power (dQ / dt) from the heat exchange unit, based on the value of the vector fluid flow (φ) passing through the heat exchange unit (7) and the temperature difference (ΔT).

In a 45 ° aspect according to the previous aspect, the step of determining the heat exchanged power (dQ / dt) by the heat exchange unit, on the basis of the value of the vector fluid flow (φ) passing through the heat exchange unit ( 7) and the temperature difference (ΔT), allows to obtain in each cycle a set of three values comprising:

or the value of said temperature difference (ΔT), the

or the value of said vector fluid flow (φ) ed

or the corresponding value of said heat exchanged power (dQ / dt) by the heat exchange unit.

In a 46th aspect according to any of the previous two aspects the process comprises the step of:

- determining a characteristic function of the heat exchange unit present in said service line which relates an exchanged thermal power (dQ / dt) from the heat exchange unit to the value of the vector fluid flow (φ), said characteristic function of heat exchange unit being determined using a plurality of values of heat exchanged and flow of vector fluid obtained in respective cycles.

In a 47th aspect according to the previous aspect, the characteristic function of the heat exchange unit present in said service line that relates the heat power exchanged with the value of the vector fluid flow is an exponential curve <of the type:>

where is it:

dQ / dt represents the thermal power exchanged by the specific heat exchange unit,

φ is the flow of the vector fluid entering the heat exchange unit,

A and φ0 are obtained with curve fitting and / or interpolation techniques by approximating the pairs of flow values of the vector fluid (φtm) and of the thermal power (dQ / dt) obtained at each cycle.

In a 48th aspect according to the previous aspect, in which said exponential curve is:

<where:>

where is it:

● dQ / dt represents the thermal power [kW] exchanged by the specific heat exchange unit,

● φ is the flow of the carrier fluid [kg / h] entering the heat exchange unit,

● Temperature [° C] of the vector fluid entering the unit

heat exchange, i.e. in correspondence with the first section at instant t1;

● Temperature [° C] of the air present in the environment where the heat exchange unit operates or of the air entering the heat exchange unit at instant t1;

● Dew temperature (dewpoint) [° C] of the air present in the environment where the heat exchange unit operates at instant t1 or of the air entering the heat exchange unit; the dew temperature is determined with known formulas as a function of the temperature and relative humidity of the air present at instant t1 in the environment where the heat exchange unit operates or of the air entering the heat exchange unit

and where:

a1, a2, n and φ0 are coefficients obtained with curve fitting and / or interpolation techniques by approximating the pairs of flow values of the vector fluid (φ) and of the thermal power (dQ / dt) obtained at each cycle.

In a 49th aspect according to any of the previous two aspects, said exponential curve is:

<where:>

and where:

● dQ / dt represents the thermal power [kW] exchanged by the specific heat exchange unit,

● φ is the flow of the carrier fluid [kg / h] entering the heat exchange unit,

● Temperature [° C] of the vector fluid entering the unit

heat exchange, i.e. in correspondence with the first section at instant t1;

● Temperature [° C] of the air present in the environment where the heat exchange unit operates or of the air entering the heat exchange unit at instant t1;

and where:

a1, n and φ0 are coefficients obtained with curve fitting and / or interpolation techniques by approximating the pairs of flow values of the vector fluid (φ) and of the thermal power (dQ / dt) obtained at each cycle.

In a 50th aspect according to any of the previous three aspects, the procedure includes determining an optimal operating range of the heat exchange unit using the characteristic function, in particular using the coefficient φ0 of the exponential curve

In a 51st aspect according to the previous aspect, the process comprises determining an optimal operating range of the heat exchange unit using the coefficient φ0, imposing that the value of the vector fluid flow does not exceed K φ0, where K is a factor multiplicative> 1.

In a 52nd aspect according to the previous aspect, the process includes determining an optimal operating range of the heat exchange unit using the coefficient φ0, requiring that the value of the vector fluid flow does not exceed 2φ0 or 2.5φ0 or 3φ0.

In a 53 ° aspect according to any of the previous three aspects, the process comprises determining an optimal operating range of the heat exchange unit using the coefficient φ0 and imposing that the value of the vector fluid flow does not fall below K ' φ0 where K 'is a multiplicative factor.

In a 54th aspect according to the previous aspect K 'is a multiplicative factor ≤ K.

In a 55 ° aspect according to the 53 ° or 54 ° aspect, the process includes determining an optimal operating range of the heat exchange unit using the coefficient φ0, imposing

imposing that the vector fluid flow value does not fall below 0.25 φ0 or 0.5φ0 or 0.75φ0.

In a 56th aspect according to any of the foregoing aspects each line of service comprises:

- at least one flow regulator (8) configured to control the flow of the carrier fluid through the heat exchange unit (7),

- at least a first thermal sensor (9a) configured to detect the temperature of the vector fluid at the first section (5a) of the service line (5) and a second thermal sensor (9b) to detect the temperature of the vector fluid at the second section (5b) of the same service line (5),

- at least one hydraulic sensor (10) configured to determine the flow (φ) of vector fluid.

In a 57th aspect according to any of the preceding aspects the process includes:

receiving at least one desired value of an operating parameter comprising one of:

- thermal power exchanged by the carrier fluid as it passes through each heat exchange unit (7),

- heat exchanged by the carrier fluid in a predetermined time interval as it passes through each heat exchange unit (7),

- temperature difference (ΔT) between the temperature (Tt1) of the vector fluid, in correspondence with the first section, measured at a first instant (t1), and temperature (Tt2) of the vector fluid, in correspondence with the second section, measured at a second time instant (t <2>) which can be coincident with or after the first instant;

determining, for each heat exchange unit (7), a real value of said operating parameter.

In a 58th aspect according to the previous aspect optionally in which the desired value of the operating parameter is:

● a set value, or

● a value calculated according to a desired value of the temperature present in the environment where the heat exchange unit operates, or

● a value calculated as a function of a desired value of the air temperature entering the heat exchange unit;

In a 59th aspect according to any of the preceding aspects each plant comprises at least one central heat treatment group (6) connected at least to the delivery line (3) and comprising:

- at least one pump (12) ed

- at least one refrigeration and / or heating unit (13)

and in which the process also provides for:

- comparing said desired value of the operating parameter with said real value of the same operating parameter,

- if, following said comparison phase, it derives that, for at least one heat exchange unit (7), the real value of the operating parameter deviates by more than a predetermined threshold from the desired value of the same operating parameter, carry out a phase of control includes at least one of:

the. control the central heat treatment group (6) to adjust at least one general parameter selected from: flow rate imposed on the carrier fluid, hydraulic head imposed on the carrier fluid passing through the central group, heating imposed on the carrier fluid passing through the central group, cooling imposed on the fluid vector crossing the central group,

ii. control the flow rate regulator (8) present on the channel (5) of the heat exchange unit (7)

iii. control the heat exchange modulator (7a) associated with the heat exchange unit (7), optionally control the number of sworns of at least one fan part of the heat exchange modulator.

In a 60th aspect according to the previous aspect, said control phase involves maintaining the flow of the vector fluid passing through each heat exchange unit within the respective optimal operating range.

In a 61st aspect according to any one of the preceding aspects, the process comprises the step of determining said characteristic function of the heat exchange unit present a plurality of times at time intervals spaced apart, for example by one or more days, for consequently collecting a plurality of characteristic curves over time.

In a 62nd aspect according to the previous aspect, said procedure for determining a malfunction condition includes the phases of:

- measure at least one real value of the vector fluid flow passing through this heat exchange unit,

- calculating on the basis of said at least one real value of the carrier fluid flow, at least a corresponding calculated value of the temperature difference or of the thermal power exchanged by the carrier fluid in the passage through the heat exchange unit (7), said calculated value being obtained using a characteristic function determined at a predetermined time, in particular the most recently determined characteristic function,

- determine the presence of a malfunction condition of the exchanger based on the comparison between:

the. the calculated value of the temperature difference or of the heat output exchanged using said characteristic function relating to the preset time instant, and ii. a further calculated value of the temperature difference or of the heat output exchanged using said real value of the vector fluid flow and a characteristic function determined at an instant in time prior to the predetermined one.

In a 63rd aspect according to the previous aspect, said procedure for determining a malfunction condition includes the phases of:

- measure at least one real value of the vector fluid flow passing through this heat exchange unit,

- determine at least a corresponding real value of said difference in temperature of the vector fluid or heat power exchanged by the vector fluid, in the passage of the vector fluid itself through the heat exchange unit (7) to said real value of the vector flow,

- calculating on the basis of said at least one real value of the carrier fluid flow, at least a corresponding calculated value of the temperature difference or of the thermal power exchanged by the carrier fluid in the passage through the heat exchange unit (7), said calculated value being obtained using a characteristic function determined at a predetermined instant in time, in particular prior to the measurement of the real value of the vector fluid flow,

- determine the presence of a malfunction condition of the exchanger based on the comparison between:

the. the calculated value of the temperature difference or the heat output exchanged using said characteristic function relating to the preset time instant, and ii. the real value of the temperature difference or of the heat output exchanged.

In a 64th aspect according to the 62nd or 63rd aspect in which determining the presence of the malfunction condition includes establishing that a malfunction condition exists if, following said comparison, a discrepancy is obtained between the values object of the comparison higher than a predetermined threshold.

In a 65th aspect according to the previous aspect in which the procedure includes a step of classifying a type of malfunction detected as:

- malfunction caused by progressive deterioration if said discrepancy, related to the time interval between said predetermined instant and said previous instant, or related to the time interval between the instant of measurement of the real value of the vector fluid flow and said predetermined instant is less than a limit value, - malfunction due to improper use or damage to the terminal if said discrepancy, related to the time interval between said predetermined instant and said previous instant, or related to the time interval between the instant of measurement of the real value of the vector fluid flow and said predetermined instant, is higher than said limit value.

A 66th aspect concerns a process of monitoring and / or control of an air conditioning and / or heating system (1), said system comprising:

- at least one delivery line (3), at least one return line (4),

- a predetermined number of service lines (5) hydraulically interposed between the delivery line (3) and the return line (4), each service line (5) comprising at least one heat exchange unit (7) at least one flow rate regulator (8) configured to control the flow of the carrier fluid through the heat exchange unit (7), ed

- at least one central heat treatment group (6) connected to the respective delivery line (3),

in which said process provides, for at least one of said service lines (5), the phases of:

- circulate a carrier fluid through at least one service line so that the same particle of carrier fluid passing through a first section (5a) of the service line upstream of the heat exchange unit (7) passes through a second section (5b) of the same service line placed downstream of the heat exchange unit (7) successively, with a hydraulic delay (dt) given by a time necessary for the same fluid particle to pass from the first to the second section,

- determine at least one value of the temperature difference (ΔT) between: � the temperature (Tt1) of the vector fluid, at the

first section, detected at a first instant (t1), e

� the temperature (Tt2) of the vector fluid, in correspondence with the second section, measured at a second instant (t2), which is subsequent to said hydraulic delay (dt) with respect to the first instant (t1),

- command at least one of:

� the central heat treatment group (6), � the flow rate regulator (8),

� a heat exchange modulator (7a) associated with the heat exchange unit (7),

as a function of:

� the temperature difference as measured above, or of a real value of an operating parameter which is in turn a function

of the temperature difference as measured above, and is a desired value of an operating parameter.

In a 67 ° aspect according to the previous aspect in which the heat exchange unit comprises a fan, for example active on an air distribution line, and in which the process provides for controlling the fan and in particular for varying the angular speed of the fan according to:

� the temperature difference as measured above, or of a real value of an operating parameter which in turn is a function of the temperature difference as measured above, is the desired value of an operating parameter.

In a 68 ° aspect according to any of the two preceding aspects, said cycle comprises the further steps of detecting the value (φ) of the flow of vector fluid passing through the heat exchange unit (7), in an instant of detection (tm) after the first instant (t1) and prior to the second instant (t2), and determine as the real value of the operating parameter the heat exchanged power (dQ / dt) by the heat exchange unit determined on the basis of said value of the vector fluid flow (φ) passing through the heat exchange unit (7) and of said temperature difference (ΔT).

In a 69 ° aspect according to any of the previous three aspects, the step of controlling at least one of the central heat treatment group (6), the flow rate regulator (8) and the heat exchange modulator (7a) comprises:

- receiving, for each heat exchange unit (7) at least one desired value of an operating parameter comprising one of:

the. thermal power exchanged by the carrier fluid as it passes through each heat exchange unit (7),

ii. heat exchanged by the carrier fluid in a predetermined time interval as it passes through each heat exchange unit (7),

iii. temperature difference (ΔT) between the temperature (Tt1) measured at the first instant (t1) and the temperature (Tt2) measured at the second instant (t2),

- determining, for each heat exchange unit (7), a real value of said operating parameter using at least the value of said temperature difference (ΔT) between the temperature (Tt1) measured at the first instant (t1) and the temperature (Tt2 ) measured at the second instant (t2),

- compare the desired value of the operating parameter with the corresponding real value of the same operating parameter, and - if, following said comparison phase, it derives that, for at least one heat exchange unit (7), the real value of the operating parameter is deviations by more than a predetermined threshold from the desired value of the same operating parameter, carry out a control phase on one or more of the central unit, flow regulator and heat exchange modulator, said control phase being aimed at aligning or reducing a difference between the actual value and the desired value of the operating parameter.

In a 70 ° aspect according to any of the previous aspects from 66 ° to 68 ° the step of controlling at least one of the central heat treatment group (6) and the flow regulator (8) comprises:

- receiving, for each heat exchange unit (7) at least one desired value of an operating parameter comprising one of:

the. thermal power exchanged by the carrier fluid as it passes through each heat exchange unit (7),

ii. heat exchanged by the carrier fluid in a predetermined time interval as it passes through each heat exchange unit 7,

iii. temperature difference (ΔT) between the temperature (Tt1) measured at the first instant (t1) and the temperature (Tt2) measured at the second instant (t2),

- determining, for each heat exchange unit (7), a real value of said operating parameter using at least the value of said temperature difference (ΔT) between the temperature (Tt1) measured at the first instant (t1) and the temperature (Tt2 ) measured at the second instant (t2), and at least the value of said flow of vector fluid (φ) at the instant of detection (tm),

- compare the desired value of the operating parameter with the corresponding real value of the same operating parameter, and - if, following said comparison phase, it derives that, for at least one heat exchange unit (7), the real value of the operating parameter is deviations by more than a predetermined threshold from the desired value of the same operating parameter, carry out a control phase on one or more of the central unit, flow regulator and heat exchange modulator, said control phase being aimed at aligning or reducing a difference between the actual value and the desired value of the operating parameter.

In a 71st aspect according to any one of the previous two aspects, the control phase comprises at least one of:

- command the central heat treatment group (6) to adjust at least one general parameter selected from: flow rate imposed on the carrier fluid, hydraulic head imposed on the carrier fluid passing through the central group, heating imposed on the carrier fluid passing through the central group, cooling imposed on the vector fluid passing through the central group,

- control the flow regulator (8) present on the service line (5) of the heat exchange unit (7),

- control the heat exchange modulator (7a) associated with the heat exchange unit (7).

In a 72nd aspect according to any one of the 66th aspect to the preceding aspect each line of service includes:

- at least a first thermal sensor (9a) configured to detect the temperature of the vector fluid at the first section (5a) of the service line (5) and a second thermal sensor (9b) to detect the temperature of the vector fluid at the second section (5b) of the same service line (5),

- at least one hydraulic sensor (10) configured to determine the flow (φ) of vector fluid.

In a 73rd aspect according to any of the aspects from the 66th to the previous aspect, the process involves the execution of one of the following phases:

- receiving a value of the hydraulic delay (dt) between said first and said second section of the same service line,

- determining a value of the hydraulic delay (dt) between said first and said second section of the same service line,

- determining the second instant (t2), which is subsequent to said hydraulic delay (dt) with respect to the first instant (t1).

In a 74th aspect according to the previous aspect, the step of determining said hydraulic delay (dt) which comprises:

- determining a control volume (V0) relative to a volume of vector fluid comprised between said first and said second section, and

- calculate the hydraulic delay as the time interval from the first instant (t1) and necessary for a volume of vector fluid equal to the control volume (V0) to cross the first section (5a);

or in which the phase of determining the second instant (t2) is envisaged, which includes:

- determining a control volume (V0) relative to a volume of vector fluid comprised between said first and said second section, and

- determine the second instant (t2) as the instant in which, starting from the first instant (t1) the volume of vector fluid passing through the first section (5a), a volume of vector fluid equal to the control volume (V0) went through the first section (5a).

In a 75th aspect according to the previous aspect determining the control volume (V0) in turn comprises:

- measure a temperature of the carrier fluid at the first section and the second section,

- vary the temperature of the vector fluid entering said service line, - identify an initial instant (ts) in which the temperature of the vector fluid in correspondence with the first section varies, optionally beyond a predetermined threshold,

- identify a final instant (tf) in which the temperature of the vector fluid in correspondence with the second section varies, optionally beyond a predetermined threshold,

- measuring values of the vector fluid flow (φ (t)) during an interval between said initial instant and said final instant,

- calculate the control volume (V0) based on the values assumed by the flow of vector fluid in the interval between said initial instant and said final instant.

In a 76th aspect according to the previous aspect, calculating the control volume (V0) on the basis of the values assumed by the flow of vector fluid in the interval between said initial instant and said final instant envisages using the following formula:

in which:

o φ (t) represents the value of the vector fluid flow over time, o ts is the initial instant,

o tf is the final instant.

In a 77th aspect according to any one of the aspects from the 66th to the previous aspect, the detection instant (tm) at which the sub-phase of detecting the value of the vector fluid flow (φ) passing through the heat exchange unit is carried out (7) is an intermediate instant (tm), in particular placed in the middle of the time interval between the first instant (t1) and the second instant (t2).

In a 78th aspect according to any of the 66th to 1st aspects, the process involves a flow stability check which includes:

- determine a reference flow (φr) as the ratio between the control volume V0 and said hydraulic delay (dt = t2-t1),

- compare the vector fluid flow (φ) measured at the instant of detection (tm) with the reference flow (φr),

- establish that the stability check has passed if the difference between the reference flow (φr) and the vector fluid flow (φ) is lower than a predetermined threshold (S).

In a 79 ° aspect according to the previous aspect in which to establish that the stability verification is positively passed if the difference between the reference flow (φr) and the vector fluid flow (φ) is lower than a predetermined threshold (S) provides for the following <check:>

In an 80 ° aspect according to the 78 ° or 79 ° aspect the threshold S is = 10% or 15% or 20% or more depending on the level of stability to be maintained.

An 81st aspect concerns a control unit configured or programmed to perform a process in accordance with any of the previous aspects.

An 82nd aspect conceives a software program which when executed by a control unit programs this control unit to execute a process according to any of the preceding aspects.

An 83rd aspect concerns a storage medium for a software program which, when executed by a control unit, programs this control unit to execute a process according to any of the previous aspects.

An 84th aspect concerns a monitoring and / or control device of an air conditioning and / or heating system (1) comprising control unit (24; 24a, 24b) configured or programmed to carry out the process according to any of the preceding aspects.

An 85th aspect concerns a monitoring and / or control device of an air conditioning and / or heating system (1), said system comprising at least one delivery line (3), at least one return line (4) and a predetermined number of service lines (5) hydraulically interposed between the delivery line and the return line, and at least one central heat treatment group (6) connected to the respective delivery line (3), each service line (5) comprising at least a heat exchange unit (7), optionally at least one heat exchange modulator (7a) being associated with the respective heat exchange unit (7), said device comprising:

- at least one flow regulator (8) configured to control the flow rate of the vector fluid passing through the heat exchange unit (7), - at least one first thermal sensor (9a) configured to detect the temperature of the vector fluid at a first section (5a) of the service line (5) upstream of the heat exchange unit (7) and a second thermal sensor (9b) to detect the temperature of the carrier fluid in correspondence with a second section (5b) of the same service (5) downstream of the heat exchange unit (7), - at least one hydraulic sensor (10) configured to determine the flow (φ) of carrier fluid,

- at least one control unit (24; 24a, 24b) connected or connectable with the flow regulator (8) and / or with the central unit (6), with the first and second thermal sensors (9), with the hydraulic sensor and optionally with the heat exchange modulator (7a), - said control unit (24; 24a, 24b) being configured to carry out the process according to any of the preceding aspects.

An 86th aspect concerns an air conditioning and / or heating system comprising at least one circuit (2) for distributing a vector fluid, each circuit (2) comprising:

- at least one delivery line (3) of the carrier fluid,

- at least one return line (4) of the carrier fluid,

- a plurality of service lines (5) connected directly or indirectly with said delivery line (3) and with said return line (4) and configured to serve respective rooms to be conditioned and / or heated, in which each of said lines service (5) includes in turn:

� at least one heat exchange unit (7), optionally at least one heat exchange modulator (7a) being associated with the respective heat exchange unit (7),

� at least one flow regulator (8) configured to control the flow rate of carrier fluid passing through the heat exchange unit (7), � at least one first thermal sensor (9a) configured to detect the temperature of the carrier fluid in correspondence with a first section (5a) of the service line (5) upstream of the heat exchange unit (7) and a second thermal sensor (9b) to detect the temperature of the carrier fluid in correspondence with a second section (5b) of the same service (5) downstream of the heat exchange unit (7), ed

� at least one hydraulic sensor (10) configured to determine the flow (φ) of vector fluid,

- at least one central heat treatment group (6) located on the respective circuit (2),

- at least one control unit (24; 24a, 24b) connected or connectable with the flow regulator (8) and / or with the central unit (6), with the first and second thermal sensors (9), with the hydraulic sensor (10) and optionally with the heat exchange modulator (7a),

- said control unit (24; 24a, 24b) being configured to carry out the process according to any of the preceding aspects.

BRIEF DESCRIPTION OF THE DRAWINGS

Some embodiments and some aspects of the invention will be described hereinafter with reference to the accompanying drawings, provided for indicative purposes only and therefore not limitative in which:

Figure 1 is a non-limiting schematic of a

conditioning and / or heating in accordance with the present invention; Figures 2 to 4 are respective schematic representations of constructional variants of a service line of a plant in accordance with the present invention;

Figure 5 is a sectional view of a valve that can be used as a flow rate regulator in a service line of an air conditioning and / or heating system in accordance with the present invention;

Figure 6 is a flowchart of a process for monitoring and / or

control in accordance with aspects of the present invention;

� Figure 7 is a Cartesian diagram representing a characteristic function, calculated in accordance with aspects of the invention, relating to a heat exchange unit in a service line of an air conditioning and / or heating system in accordance with the present invention; the flow of the vector fluid passing through the heat exchange unit is indicated on the abscissa and the thermal power supplied by the heat exchange unit is shown on the ordinate;

Figure 8 is a flowchart of a process for monitoring and / or control in accordance with further aspects of the present invention;

Figure 9 is a non-limiting schematic of a variant of an air conditioning and / or heating system in accordance with the present invention.

DEFINITIONS

The figures could illustrate the object of the invention or parts of it through non-scale representations; therefore, parts and components illustrated in the figures relating to the object of the invention could only concern schematic representations.

The term carrier fluid or heat carrier refers to a substance in a liquid or gaseous state capable of receiving, accumulating, transporting and releasing heat. For example, in a heating system it is possible to use water as a carrier fluid, in particular hot water, or mixtures of hot water and glycol. In an air-conditioning system, on the other hand, it is possible to use a gas or natural-type coolants (for example ammonia and carbon dioxide), cold water, mixtures of water with glycol or other anti-freeze substances as the carrier fluid. By flow rate or flow of the vector fluid we mean the mass flow rate, for example expressed in kilograms per hour kg / h of vector fluid.

With thermal power exchanged dQ / dt by the heat exchange unit, for example expressed in kilowatts kW, we mean the heat absorbed or transferred by the heat exchange unit in the unit of time.

The term central heat treatment unit (indicated by 6 in the drawings) refers to a unit comprising a heating unit 13 (for example a boiler unit, or a heat pump, or a solar panel system or other heating device ) configured for heating a vector fluid (typically a liquid) and for feeding the hot vector fluid to a hydraulic distribution circuit that serves one or more suitable heat treatment units or operating users in correspondence with the respective environments to be treated. The central heat treatment unit can also, or alternatively, comprise a refrigeration unit (also indicated by 13 in the accompanying figures) configured for the treatment (cooling) of a carrier fluid and for sending the carrier fluid to a distribution adapted to serve one or more suitable heat treatment units for conditioning the air of the respective rooms to be treated. The central heat treatment unit further comprises at least one pump indicated with 12 in the accompanying drawings, or other means having the task of promoting the circulation of the vector fluid towards and in the distribution circuit.

DETAILED DESCRIPTION

Air conditioning and / or heating system

With reference to the accompanying figures, the reference numeral 1 generally indicates an air conditioning and / or heating system.

As visible for example from Figure 1, the plant 1 comprises a circuit 2 for the distribution of a vector fluid; circuit 2 has at least two main channels, namely: a delivery line 3, for sending the carrier fluid to a predetermined number of users or heat exchange units 7, and a return line 4 in fluid connection with the delivery line delivery 3 and arranged to receive the carrier fluid downstream of each of the units 7. As can be seen from Figure 1, the distribution circuit 2 comprises a plurality of circulation channels or service lines 5 directly or indirectly in connection with the delivery line 3 and with the return line 4 and configured to serve respective rooms to be conditioned and / or heated; each service line 5 is configured to supply at least one respective heat exchange unit 7.

Figure 1 illustrates a preferential, but not limiting, configuration of the invention, in which each service line 5 is interposed between the delivery line 3 and the return line 4 and serves a respective heat exchange unit 7: in this configuration, the lines 5 are arranged in parallel with each other and receive fluid from the delivery line and then return it to the return line after the passage of the fluid from the respective unit 7; in this configuration, it is possible to send to each unit 7 only one type of fluid: for example if the central group 6 includes a heating unit 13 (or refrigerating) each of the channels 5 receives heated (or respectively cooled) fluid from the central group 6 and discharges on the fluid return line which has cooled (or respectively heated) following the passage through the respective unit 7.

However, the possibility of having two or more delivery lines 3 is not excluded: for example, as illustrated in figure 9, a delivery line 3 conveying refrigerant fluid coming from a refrigerating unit 13 of a group 6 and destined to supply a respective distribution circuit 2, and a delivery line 3 coming from a heating unit of the same group 6 or of a distinct central group 6: in figure 9 two distinct central groups 6 are shown which serve respective distribution circuits 2, one circulating hot fluid and a circulating cold fluid. In figure 9 each distribution circuit 2 then has a respective return line 4 which returns the 'used' vector fluid to the corresponding group 6. In the example of figure 9 each distribution circuit 2 serves a plurality of service lines (in figure 9 shows two of them for each circuit 2, merely by way of example), for example placed in parallel with each other. In this case too, a respective heat exchange unit 7 operates on each service line. a unit 6 and a side in which the air to be conditioned or heated circulates) are each placed on a respective of the two distribution circuits 2 shown in figure 9, although the air side is part of the same air handling unit (globally indicated with 77) which can therefore be heated by one of the units 7 and cooled by the other of the units 7.

In a further variant, the central unit can comprise a unit 13 capable of acting both as a heating and cooling unit of the vector fluid and therefore active on a single delivery line which feeds the distribution circuit and therefore the various service lines selectively with hot vector fluid or with fast vector fluid through the intervention of suitable valve systems known per se.

Furthermore, the possibility of having multiple heat exchange units 7 in series on a single line 5 is not excluded.

Returning now to the description of the exemplary plant shown in Figure 1, in this figure a non-limiting configuration of the invention has been schematised in which each return line 4 in fluid communication with the delivery line 3 to define a distribution circuit 2 of the closed-loop vector fluid in which the vector fluid (or the different vector fluids if more delivery lines and more return lines are used) is recirculated inside the distribution circuit 2.

In one configuration (always see figure 1, but the same aspects can be present in the system of figure 9), the system 1 can optionally be equipped with a supply line 27, in fluid communication with the delivery line 3 and / or return 4, configured to allow the addition of carrier fluid in circuit 2 (make-up) and an outlet line 28, in fluid communication with the delivery line 3 and / or with the return line 4, configured to allow the discharge of carrier fluid from circuit 2 (for example for washing operations). A closing valve (element not shown in the accompanying figures), for example a ball valve or a simple "open and close" cock, configured to open and close can be advantageously arranged on each of said supply and outlet lines 27, 28. lines 27 and 28 and thus allow the introduction of fresh carrier fluid or the discharge of used carrier fluid from circuit 2.

As can be seen in Figure 1, the plant 1 provides at least one central heat treatment group 6, comprising at least one pump 12 and at least one cooling and / or heating unit 13. The central group 6 is connected to the delivery line 3 of the circuit 2 and configured to vary at least one of the temperature and flow rate of the carrier fluid in the delivery line 3. The heat treatment unit 6 is generally placed between the delivery line (s) 3 and the return line (s) 4 so as to feed the delivery line or lines and receive the return fluid coming from the return lines. The pump 12 is configured to promote the delivery of the carrier fluid to the delivery line (s) and therefore to the service lines 5. Figure 1 schematically illustrates a configuration of the plant 1 presenting a single central heat treatment unit 6 ; it is however possible to provide a plurality of groups 6 arranged in series or parallel on the delivery line 3 or directly active on a service line 5 or arranged as in figure 9.

As briefly mentioned above, each circuit 2 (ie both the circuit 2 of the plant in Figure 1 and each circuit 2 in Figure 9) includes a plurality of service lines 5; for each service line 5, the system 1 includes at least one exchange unit 7 configured to serve a respective environment to be conditioned and / or heated. Each heat exchange unit 7 (user) can comprise at least one of:

- a fan coil, having a hydraulic side crossed by the carrier fluid and a pneumatic side crossed by air which is exchanged with the environment to be air-conditioned or heated; the fan coil may for example have at least one fan as a heat exchange modulator 7a;

- a convector, for example with a fan as a heat exchange modulator 7a;

- a heat exchanger, for example with an adjustable heat exchange surface acting as a heat exchange modulator 7a;

- a fixed exchanger, such as a classic radiator or a radiant panel without fans or adjustable surfaces.

The heat exchange unit can also be part of an AHU (air handling unit): in this case several heat treatment units 7 can be associated with an AHU and have a respective hydraulic side in which a distinct vector fluid circulates (for example the units 7 can be part of two separate distribution circuits 2, one with heating fluid and one with cooling fluid which can therefore be selectively used to treat the air of the AHU). The AHU has at least one air distribution circuit that serves the various rooms to be conditioned / heated and which is connected to the pneumatic side of the various heat treatment units (for example as shown in figure 9 where the pneumatic side of two units 7 is part of the AHU air distribution circuit The AHU can also have, for example, at least one fan operating on the pneumatic circuit as a heat exchange modulator 7a.

Figure 1 shows cases in which each line 5 and each heat exchange unit 7 arranged on this line 5 directly serve a respective environment to be conditioned. In figure 9, each circuit 2 provides both one or more lines 5 serving a respective unit 7 and therefore a respective environment, and the case in which two or more lines 5 are actually part of an AHU (air handling unit) 77 and therefore at least one air distribution line 70 is needed on which one or more heat exchange modulators 7a can operate, for example consisting of one or more fans.

Leaving now the scheme of the plant 1 as a whole and going down in greater detail to describe the structure of each service line 5, and referring to the examples in Figures 2-4, each service line 5 provides for the use of a device, globally indicated with 50, having monitoring and / or control functions. The device 50 has at least one flow regulator 8 configured to manage the quantity of vector fluid (mass flow) in passage through the respective service line 5. With reference to the direction of circulation of the fluid (see arrows F in figures 2-4) , the flow rate regulator 8 can be arranged on the service line 5 downstream of the heat exchange unit 7 operating on the same service line 5.

In greater detail, the flow rate regulator 8 comprises a valve 16 having a valve body 16a having at least an inlet 17, an outlet 18 and a passage 19 which places the inlet 17 in fluid communication with the outlet 18. The valve body 16a has, at the inlet 17 and the outlet 18 of the valve 16, respective connecting members 29, 30 (figure 5) adapted to allow the valve 16 to be fixed on the circuit 2. The connecting members 29, 30 they can be, for example, threads or quick couplings or other types of connections. The passage 19 has a seat 31 suitable for housing an interception element 20 which has the task of partially or totally intercepting the fluid passing through the valve and is therefore capable of acting as a flow regulator or even as a closing element of the passage 19; the interception element, in cooperation with the valve body 16a, defines a fluid passage port 21 of variable amplitude according to the positions assumed by the interception element 20 relative to the valve body 16a. The interception element 20 is configured to act along a predetermined operating stroke which comprises a plurality of distinct and angularly or translationally offset operating positions. The movement of the interception element 20 can therefore be rotary or translational. In the first case, the movement takes place by rotation according to a movement angle around a rotation axis A which extends transversely with respect to a prevalent development axis C of the channel 19 (Figure 5). In the second case, the movement can take place in a rectilinear direction (configuration not shown). In the event that the interception element 20 performs a rotary movement, the interception element 20 has an external surface of substantially spherical or cylindrical geometry, as can be seen from Figure 5.

The valve 16 also comprises an actuator member 23 connected to the valve body 16a and active on the interception element 20 to move the latter at least between a fully open position, in which the passage opening 21 has maximum area, and a position closing, in which the passage opening 21 is closed. The actuator can also position the interception member in a plurality of intermediate positions between the opening and closing positions, thus allowing to regulate the flow rate crossing the service line 5. In greater detail, the actuator member 23 may comprise an actuator of the electrical or mechanical type, possibly provided with a suitable reduction unit, carried by the valve body 16a and engaged with the on-off element 20. The flow regulator 8 can further comprise at least one position sensor 22 configured to determine the positions assumed by the interception element 20, along u a predetermined operating stroke relative to the valve body 16a, and to transmit a respective signal which therefore allows to know the degree of opening of each valve 16. In a non-limiting embodiment of the invention, the on-off element 20 is configured to assume a plurality of positions along said operating stroke corresponding to different degrees of opening of said passage opening 21: the position sensor 22 can for example comprise an encoder, a potentiometer, or other means configured to emit a signal that allows to determine or that signals the position of the interception member along the operating stroke. For example, the position sensor 22 can be configured to emit a signal at each predetermined step taken by the interception element 20 along the operating stroke, or to emit an amplitude or frequency signal which is a function of the position of the element. interception along the operating stroke. In a non-limiting embodiment of the invention, the flow regulator 8 further comprises a control unit 24 connected to the position sensor 22 and active on the actuator member 23. The control unit 24 is configured to receive the signal from the position sensor 22, processing said signal to establish the relative position of the shut-off element 20 with respect to the valve body 16a. The control unit 24 can also be configured to control the actuator 23, in particular to move the interception element 20 in a controlled manner. The connection by means of the control unit 24 to the sensor 22 and to the actuator member 23 allows the unit 24 to manage and control the movement of the interception element 20. In practice, the control unit 24 can comprise one or more microprocessors programmed to receive the signal from the sensor 22 at the input, thus establishing from it the actual position of each interception member and act on the actuator member 23 as a function of this signal and the desired position to which the interception member 20 is to be brought.

Actuator member 23 and control unit 24 can be part of valve 16 for example operating downstream of each heat treatment unit 7 of the same service line 5 on which said valve 16 is active. In fact, in the example of figure 5, sensor 22, actuator member 23 and control unit 24 define a sort of control head 32 carried stably by the valve body 16a which is adapted to monitor and control the interception element 20.

The device 50 and therefore the plant 1 may comprise various sensors described below. For example, for each service line 5, at least one thermal sensor 9, 9a, 9b can be provided, configured to detect a measured value of a thermal parameter depending on the temperature difference between a first section 5a of an upstream service line 5 of said heat exchange unit 7 and a second section 5b of the same service line 5 downstream of the heat exchange unit 7. Figure 1 illustrates, in correspondence with the service line 5 extending horizontally, a first configuration of the sensor temperature 9 essentially comprising a single differential sensor connected with the first section 5a of a service line 5 upstream of the heat exchange unit 7 and with the second section 5b of the same service line 5 downstream of the same heat exchange unit 7 : the differential sensor is configured to detect the difference in temperature between said first and said second section 5a, 5b of each service line 5. The sensor differential sensor 9 can be physically in the vicinity or on a point of the service line and have detection lines in fluid communication with the first and second sections 5a, 5b of the service line 5. Alternatively, the thermal sensor 9 can be carried by the flow regulator 8 and have a sensing socket right in correspondence with the regulator 8, downstream of the unit 7, as well as presenting a sensing line in fluid communication with the first section 5a of the service line 5 upstream of the same unit 7. Figure 1 (see the other service lines 5) and Figure 2 instead illustrates a second embodiment in which the thermal sensor comprising a first thermal detector 9a configured to detect the temperature in a first section 5a of a service line 5 upstream of the heat exchange unit 7 and a second thermal detector 9b configured to detect the temperature in a second section 5b of the same service line 5 downstream of the heat exchange unit 7. In this second variant, the second detector 9b can be brought by the flow regulator 8 and in particular by the valve 16.

The thermal sensor 9, 9a, 9b can be connected with the control unit 24 of the flow regulator 8 which can be configured to process the signal received from said thermal sensor and calculate the temperature difference between the aforementioned sections (first and second section 5a, 5b) upstream and downstream of the heat exchange unit 7.

The device 50 and therefore the system 1 can also comprise, for each service line 5, at least one hydraulic sensor 10 configured to detect (or allow to determine with known formulas) the flow rate passing through each flow regulator 8. In a configuration of the In system 1, the hydraulic sensor 10 can comprise a flow meter (case shown in Figure 2), for example carried directly by the flow regulator 8, in particular directly by the valve 16, and configured to detect the flow through the regulator 8.

Alternatively, the hydraulic sensor 10 can comprise a sensor capable of measuring a pressure difference (or ratio) between a first section 5c of a service line 5 upstream of said flow regulator 8 and a second section 5d of the same line. 5 downstream of the same flow regulator 8 (case shown in figure 4): knowing the position of the interception organ and the characteristic curve of the mass flow rate / pressure drop of the valve 16, it is possible to obtain the flow rate from the measured value of the difference of pressure. More in detail, the sensor 10 can measure for example a difference or a ratio between the actual pressure present in the section 5c and the prevailing pressure in the section 5d providing an output signal proportional to the difference or ratio between the pressures in the two sections 5c, 5d cited. As can be seen in Figure 4, the first section 5c of the service line 5 can be arranged downstream of the heat treatment unit 7. Alternatively, the first section 5c of the hydraulic sensor 10 can coincide with the first section 5a or be arranged opposite upstream of the heat treatment unit 7). The second section 5d is for example located immediately downstream of the valve 16 or on the valve 16 and directly connected to the channel 19 of the valve 16.

The first and second sections 5c and 5d could also both be located on the valve body of the valve 16 upstream and downstream of the interception element 20.

In a further alternative, the hydraulic sensor 10 can comprise a sensor capable of measuring the pressure in a section of a service line 5 immediately upstream and in a section immediately downstream of a calibrated orifice 52 (case illustrated in Figure 3), or the differential pressure between the two points immediately upstream and downstream of the calibrated orifice 52: the calibrated orifice is preferably placed upstream of the flow regulator so as not to be interfered with; knowing the characteristic mass flow rate / pressure drop of the orifice, it is possible to determine the mass flow through it.

In fact, the sensor 10 can in all the cases described above comprise a differential pressure sensor 26 which receives a first and a second pressure signal at its input and generates at its output a differential signal from which it is possible to calculate the flow rate.

Alternatively, to the use of a differential sensor, it is possible to create a configuration in which the sensor 10 comprises a first detector and a second detector in fluid connection with the respective sections as described above of the same service line 5.

Although in the figures both the hydraulic sensor 10 is placed downstream of the heat exchange unit 7. This sensor 10 could be installed upstream of the heat exchange unit 7 and possibly be physically connected to the first thermal detector 9a. In this case the valve 16 can be physically connected with the second thermal detector 9b and operate downstream of the unit 7.

The hydraulic sensor 10 can be connected to the control unit 24 of the flow regulator 8; the control unit 24 is in this case configured to receive the signal from said hydraulic sensor 10 and calculate the mass flow in passage from it. For example, the control unit 24 is configured to determine the real value of mass flow through the regulator 8 on the basis of the difference between the values of the pressure parameter measured in the first and second sections 5c and 5d by the sensor 10.

As also illustrated in Figures 2-4, the device 50 and therefore the system 1 can also comprise an ambient temperature sensor 11 intended to operate in correspondence with each of the rooms served by the heat exchange units 7. The sensor 11 can be connected with the control unit 24 of the flow regulator 8; the control unit 24 can in this case be configured to receive the signal from the sensor 11 and calculate or read the temperature in correspondence with the environment in which the heat treatment unit 7 operates. The control unit 24 can also be configured to act on the degree of opening of the valve 16 and / or on the heat exchange modulator 7a present in each heat exchange unit so as to regulate the heat exchange modulator 7a (for example a fan) according to the temperature detected by the sensor 11 and of a desired temperature in the environment where the sensor 11 operates.

The device 50 and the system 1 may finally comprise, for each of said lines 5, at least one closing member, partial or total (configuration not shown in the accompanying figures). The closing devices can be positioned at the beginning or at the end of each service line 5 respectively upstream or downstream of each element (sensors, heat treatment units, regulators) active on the same service line 5. In greater detail, each closing member can comprise an on / off valve which closes or opens the supply of each service line 5: in this way the closing members can exclude or not a service line 5 and for example interrupt the heat treatment of a environment for maintenance or similar activities.

Although in the previous description the case of a control unit 24 present on each valve 16 has been described, the control unit 24 can alternatively be a central controller (i.e. a component part of the system, but not necessarily part of each device 50 associated with each line 5) connected to the ambient temperature sensors 11, to the vector fluid temperature sensors 9, 9a, 9b, to the flow sensors 10, to the valves 16, to the modulators 7a, to centrally perform the functions described above for all or for a predetermined number of service lines 5. In a further alternative, the controller 24 can be separated from the individual devices 50 and dedicated to controlling a predetermined group of lines 5: in other words, the system 1 can comprise a plurality of control units 24 each dedicated to the control of a respective sub-group of service lines 5.

In a further alternative, shown in Figures 2-4, the control unit can comprise both local units 24b each mounted on a respective valve and one or more central units 24a connected to the local units 24b: in this case the the functions described can be partly performed by the central unit and partly by the peripheral units under the control of the central unit.

In any case, the control unit or units 24 can also be connected and active on the heat treatment central group (s) 6.

The control unit or units 24 are also configured to carry out the processes described and / or claimed hereinafter.

Monitoring and / or control processes

With reference to the device 50 active on each line 5 and to the conditioning and / or heating system 1 described above, a process of monitoring, and possibly also controlling, of the system 1 is now illustrated, which are to be carried out for at least one of of the service lines 5 (preferably for a plurality of them or even for all) of the steps described below. In describing the process, reference is now made to figure 6.

First of all, the vector fluid is made to reach and circulate through at least one service line (phase A in Figure 6): for example, the vector fluid can cross a plurality of service lines 5 at the same time. As it passes through each service line 5, each particle of carrier fluid crossing at a first instant t1 the first section 5a of the service line 5, upstream of the heat exchange unit 7, will cross the second section 5b of the same service line located downstream of the heat exchange unit 7 successively at a second instant t2, with a hydraulic delay dt given by the time necessary for the same fluid particle to pass from the first to the second section. The hydraulic delay dt depends on the volume of carrier fluid present between the first and second sections (referred to as the control volume V0), as well as on the flow rate or flow of the carrier fluid. Given the typical dimensions of the ducts and exchangers, given the average flow rates typically involved, and considering that the first and second sections are the sections where the temperature sensors are present (for example 9a and 9b), the hydraulic delay dt can typically be tens of seconds or even several minutes. From an operational point of view, the hydraulic delay could be a known datum or a datum calculated on the basis of an average reference value of the vector fluid flow and of the internal volume (Vi) of the duct between the first and second section 5a, 5b (for example, by assigning the value of Vi to V0); alternatively, the process can provide a real determination of the hydraulic delay (phase B in figure 6) carried out by estimating the control volume V0 (volume of vector fluid between the first and second sections 5a, 5b) as described below and therefore determining the hydraulic delay dt (or directly the second instant t2 in which the same fluid particle that crossed the first section 5a reaches the second section 5b) as a function of the control volume V0 and the vector fluid flow φ crossing the service line 5 The determination of the control volume V0 can comprise the following steps which are for example carried out before the actual operational exploitation of the plant 1, for example in a calibration or initialization stage of the plant:

- measuring a temperature of the carrier fluid in correspondence with the first section and the second section; in practice, the temperature in the first section and in the second section are continuously monitored or monitored at regular and sufficiently dense intervals to immediately detect any variation;

- varying the temperature of the vector fluid entering said service line; - identify an initial instant (ts) in which the temperature of the vector fluid in correspondence with the first section varies; this can be done in various ways, for example by verifying whether the derivative of the temperature profile at the first section is greater than a predetermined reference, or if the temperature at the first section exceeds a predetermined threshold, or if the temperature variation in correspondence of the first section varies beyond a certain limit between two successive instants or with respect to a baseline;

- identifying a final instant (tf) in which the temperature of the vector fluid at the second section varies, optionally beyond a predetermined threshold; similarly to the previous phase, this phase can concretely be carried out in various ways, for example by verifying whether the derivative of the temperature profile at the second section is greater than a predetermined reference, or if the temperature at the second section exceeds a predetermined threshold , or if the temperature variation at the second section varies beyond a certain limit between two successive instants or with respect to a baseline; - measure values of the vector fluid flow φ (t) during the time interval between the initial instant ts and the final instant tf; in practice, it is possible to measure the flow over time in order to be able to determine by interpolation the function of the flow over time or to have a sufficiently high number of flow values in the time frame of interest; - calculate the control volume (V0) based on the values assumed by the flow of vector fluid in the interval between the initial instant ts and the final instant tf.

More precisely, the process can provide for calculating the control volume (V0) based on the values assumed by the flow of vector fluid in the interval between the initial instant ts and the final instant tf using the following formula:

in which:

o φ (t) represents the value over time of the vector fluid flow that crosses line 5 and therefore the heat exchange unit 7,

o ts is the initial instant,

o tf is the final instant.

As already mentioned, once the volume V0 is known, it is possible to precisely determine the hydraulic delay dt or directly the second instant t2 (at which the same fluid particle that has passed through the first section 5a at the first instant crosses the second section 5b) as a function of the control volume V0 and the vector fluid flow φ crossing the service line 5. For example, by continuously measuring the flow crossing the service line, the volume that passes through the first section of the same service line and therefore determine when the volume V0 has passed through this first section, thus timing the measurement of the temperature in the second section.

While the vector fluid circulates through the service line 5, the process involves carrying out, and repeating a plurality of times, a cycle (C in figure 6) to collect a plurality of pairs or triples of values of the parameters described below , which will then serve to determine one or more characteristic functions of the heat exchange unit present in the service line in question.

Cycle C includes in particular the following sub-phases:

a) determine (sub-phase C1 which can use the temperature sensors 9a and 9b described above) at least one value of the temperature difference ΔT between the temperature T1 of the carrier fluid measured in correspondence with the first section 5a and detected at a first instant t1, and the temperature of the vector fluid T2 measured at the second section 5b and detected at a second instant t2; as already said, the second instant is subsequent to said hydraulic delay dt with respect to the first instant t1, ie t2 = t1 + dt and the moment in which to carry out the measurement of the temperature T2 is timed as already illustrated above;

b) detect (sub-phase C2 which can make use of the hydraulic sensor 10 described above) the value φ of the flow of vector fluid passing through the heat exchange unit 7, in which the measurement of this flow takes place in an instant of detection tm subsequent to the first instant t1 and prior to the second instant t2.

In practice, in each cycle C at least two values are obtained: the value of the temperature difference ΔT mentioned above and the corresponding value of the vector fluid flow φ at the instant tm; it should be noted that, since the temperature difference ΔT is determined with measurements made in the first and second sections at different times, this temperature difference takes into account the hydraulic delay and is actually resulting from the heat exchange made by the heat exchange unit 7; in other words, the temperature difference ΔT determined in the manner described is not affected by any transients due to fluctuations in the temperature of the fluid in the delivery line or at the inlet to the heat exchange unit since, as mentioned, the temperature difference ΔT it is measured at different instants in order to detect the temperature difference on the same fluid particle; furthermore, the flow of vector fluid is preferably detected at an intermediate instant tm between t1 and t2, or tm = t1 dt / 2, in order to mediate any fluctuations of flow during the interval dt.

In accordance with an aspect of the invention, the process provides for monitoring the temperature as described and then for controlling the central heat treatment unit 6 and / or the flow rate regulator as a function of the temperature difference ΔT as measured above (in each cycle or using pairs or triples of values from several consecutive cycles) as well as a desired value of an operating parameter. For example, in accordance with an aspect of the invention, a control process is provided which provides for receiving at least one desired value of an operating parameter comprising one of:

- thermal power exchanged by the carrier fluid as it passes through each heat exchange unit 7,

- heat exchanged by the carrier fluid in a predetermined time interval in the passage through each heat exchange unit 7, - temperature difference as determined above.

It should be noted that the desired value of each of the mentioned parameters can be:

- or a set value (for example set by a user or a technician or present in a memory that can be accessed by the control entity 24, 24a, 24b),

- or calculated by the process as a function of a desired temperature in the environment in which each heat exchange unit is installed using known formulas and in any case not subject of the present invention (this is the case when the heat exchange units do not have a real air circulation channel),

- or a value calculated according to a desired value of the air temperature entering the heat exchange unit (case in which a heat exchange unit with a real air circulation channel such as a fan coil or a UTA).

In other words, the process can receive a desired temperature value that is desired in the environment served by the heat treatment unit or in the air circulated by the fan coil or by the AHU to which the heat treatment unit is associated: from this desired temperature value and the actual prevailing temperature in the room (or in the air circulated by the AHU or by the fan coil), the process can then establish at which value to set the operating parameter, i.e. what is the desired value of the thermal power exchanged or of the heat exchanged by the carrier fluid as it passes through unit 7 or which is the desired temperature difference across the heat exchange unit.

The process therefore provides for determining, for each heat exchange unit (7), a real value of said operating parameter using the measurement of the temperature difference between the first section at instant t1 and the second section at instant t2 (and in in the case of thermal power and heat exchanged also the value of the vector fluid flow crossing the line 5 in question and therefore the heat exchange unit 7).

Therefore, the process provides for comparing the desired value of the operating parameter with the corresponding real value of the same operating parameter, and if, following said comparison step, it derives that, for at least one heat exchange unit 7, the real value of the operating parameter deviates by more than a predetermined threshold from the desired value of the same operating parameter, carry out a control step aimed at aligning or reducing the difference between the real value and the desired value of the operating parameter. The control phase may include, for example, at least one of:

- command the central heat treatment group 6 to adjust at least one general parameter selected from: hydraulic head or flow rate imposed on the carrier fluid passing through the central group, heating imposed on the carrier fluid passing through the central group, cooling imposed on the carrier fluid passing through the central group ,

- control the flow regulator 8 present on channel 5 of the heat exchange unit 7.

In practice, thanks to the particular new method of determining the temperature difference which is not obtained with synchronous thermal measurements, but vice versa as described above, the temperature difference between upstream and downstream of the exchanger is purified of any transients on the delivery line and therefore also the consequent control actions intervene only when this is actually necessary in order to reach the target set as the desired value of the operating parameter being controlled (be it power or heat exchanged or temperature difference across unit 7 or temperature to reach in an environment), avoiding to intervene for mere transitory oscillations in the temperature and in the delivery flow rate.

In a variant, the cycle also includes a stability verification sub-phase (sub-phase C4) of the flow of the vector fluid: this sub-phase is used in practice to establish whether the flow or flow rate of the vector fluid is sufficiently constant to then discard the pairs of difference values of temperature and flow of carrier fluid collected in a given cycle if the stability check has not given a positive result. In this way, the process described here will not use, for the phase of determining the characteristic function or functions, the pairs of values of temperature difference ΔT and flow of vector fluid φ obtained in cycles where the stability check has not been passed. positively. The stability check sub-phase includes for example:

- determine a reference flow φr as the ratio between the control volume V0 and the hydraulic delay (dt = t2-t1),

- compare the vector fluid flow φ measured in each cycle at instant tm with the reference flow φr,

- establish that the stability check has passed if the difference between the reference flow φr and the vector fluid flow φ is lower than a predetermined threshold S.

By way of example, the following formula can be used:

where S = 10% or 5% or other relatively small percentage (the smaller the greater the stability required for the flow to validate the pairs of values collected at each cycle).

In accordance with a further aspect of the invention, the above mentioned temperature difference values ΔT and the corresponding value of the vector fluid flow φ at the instant tm obtained in each cycle can then be used to determine characteristic functions which estimate the trend of operating parameters of the heat exchange unit (primarily the temperature difference and the heat output exchanged). For this purpose, after having collected a multiplicity of pairs of temperature difference values ΔT = Tt1-Tt2 and of vector fluid flow φ obtained in respective cycles, possibly purified from the pairs relating to cycles where the aforementioned verification of stability, the process can determine one or both of the following functions (phase D in figure 6):

- a characteristic function which relates the temperature difference ΔT between the first and the second section to the value of the vector fluid flow φ, - a characteristic function which relates an exchanged thermal power dQ / dt by the heat exchange unit to the value of the flow of vector fluid φ.

For example, by interpolating the values of the temperature difference and the vector fluid flow of said plurality of pairs of values, it is possible to determine the characteristic function that relates the temperature difference ΔT between the first and the second section to the value of the fluid flow. vector φ (relative as already said at time tm).

Furthermore, the process can provide that at each cycle the further sub-phase (sub-phase C3) is carried out to determine the thermal power exchanged dQ / dt by the heat exchange unit, on the basis of the value of the vector fluid flow φ at the instant tm passing through the heat exchange unit 7 and the temperature difference ΔT = Tt1-Tt2, using the following relationship (where Cp is the specific heat of the carrier fluid at constant pressure and where ρ is the density of the carrier fluid):

In this way, at each cycle a set of three values will be obtained comprising the value of said temperature difference ΔT, the value of the vector fluid flow φ and the corresponding value of said thermal power exchanged dQ / dt by the exchange unit. thermal. At this point, using in particular the pairs of values of thermal power and flow of the vector fluid obtained at each cycle, the process can determine the characteristic function of the heat exchange unit present in said service line which relates the thermal power exchanged with vector fluid flow value. In particular, the step of determining the characteristic function of the exchanger is performed with interpolation or curve fitting techniques known per se using the values of the exchanged thermal power dQ / dt and of the vector fluid flow φ. The shape of the characteristic function can be chosen from parametric curves of various kinds, for example polynomial curves of the second or third or fourth order whose parameters can be determined by imposing that the parametric curve 'passes' through or 'approximates' the pairs of values dQ / dt, φ above.

Once the characteristic function relating to a certain service line has been obtained, this characteristic can be used both for plant monitoring and control as will be clarified later.

In accordance with a further aspect of the invention, the Applicant has identified a type of parametric curves which can effectively represent the characteristic function of the exchanged thermal power dQ / dt as a function of the vector fluid flow φ. The type of curves identified has the double advantage of being simple and, with an appropriate determination of the parameters, of adequately representing heat exchange units, even different from each other, for example fan coils, convectors, radiators, AHUs. This aspect of the invention can be combined with the process described above for determining the flow values of the carrier fluid, the temperature difference and the thermal power using flow and temperature measurements carried out at significantly different instants, or it can also be used in systems where the characteristic function of the heat exchange units uses pairs of synchronous temperature, flux and thermal power difference values, i.e. measured as conventionally occurs at the same instant.

In greater detail, the characteristic function of the heat exchange unit present in said service line that relates the heat output exchanged with the value of the vector fluid flow is an exponential curve of the type:

where is it:

A and φ0 are obtained with curve fitting and / or interpolation techniques by approximating the pairs of flow values of the vector fluid (φ) and of the thermal power (dQ / dt) obtained at each cycle, and

φ is the flow of the vector fluid entering the heat exchange unit.

For example, in a possible solution, the exponential curve is:

<where:>

and where:

● dQ / dt represents the thermal power [kW] exchanged by the specific heat exchange unit,

● φ is the flow of the carrier fluid [kg / h] entering the heat exchange unit,

● Temperature [° C] of the vector fluid entering the unit

heat exchange, i.e. in correspondence with the first section at instant t1;

● Temperature [° C] of the air present in the environment where the heat exchange unit operates or of the air entering the heat exchange unit at instant t1; the choice depends on the type of unit 7, i.e. whether or not this unit has an air circulation duct: in the absence of such a duct, as for example in the case of radiators, the

room temperature, otherwise the inlet temperature to unit 7;

● Dew temperature (dewpoint) [° C] of the air present in the environment where the heat exchange unit operates at instant t1 or of the air entering the heat exchange unit; the dew temperature is determined with known formulas as a function of the temperature and relative humidity of the air present at instant t1 in the environment where the heat exchange unit operates or of the air entering the heat exchange unit. case, the choice of using the temperature relative to the environment or the inlet temperature to unit 7 depends on the type of unit 7, as indicated above.

It should be noted that a1, a2, n and φ0 are coefficients obtained with curve fitting and / or interpolation techniques by approximating the pairs of flow values of the vector fluid φ and of the thermal power dQ / dt obtained at each cycle.

Alternatively, if the condensation effect is neglected, the equation of the characteristic curve takes the following form which, however, is very close to most real cases:

where is it:

and where:

● dQ / dt represents the thermal power [kW] exchanged by the specific heat exchange unit,

● φ is the flow of the carrier fluid [kg / h] entering the heat exchange unit,

● Temperature [° C] of the vector fluid entering the unit

heat exchange, i.e. in correspondence with the first section at instant t1;

● Temperature [° C] of the air present in the environment where the heat exchange unit operates or of the air entering the heat exchange unit at instant t1;

It should be noted that a1, n and φ0 are coefficients obtained with curve fitting and / or interpolation techniques by approximating the pairs of flow values of the vector fluid (φ) and of the thermal power (dQ / dt) obtained at each cycle.

The characteristic function or functions calculated using the above data and equations can be determined a plurality of times at time intervals spaced apart, for example every week or every month, and stored in an appropriate memory in order to have a history of the characteristic curves and therefore a history of the behavior of each heat exchange unit, therefore without the need to store an enormous number of real measured data.

In accordance with an additional aspect, the process includes determining an optimal operating range of the heat exchange unit using the characteristic function determined as described above.

In particular, the process may include the definition of the optimal operating range of the heat exchange unit based on the value of the coefficient φ0 of said exponential curve (phase F in Figure 6).

For example, the process can determine, in particular to delimit, the optimal operating range of the heat exchange unit using the coefficient φ0, imposing that the value of the vector fluid flow does not exceed K φ0, where K is a multiplication factor> 1 The process can similarly provide for delimiting the optimal operating range of the heat exchange unit by imposing that the value of the vector fluid flow does not fall below K 'φ <0>, where K' is a multiplicative factor ≤ K or alternatively ≤ 1. For example, it can be expected that the value of the vector fluid flow does not exceed 3φ0 and that the value of the vector fluid flow does not fall below 0.5φ0.

During the use of the plant, the process in accordance with the invention can therefore perform active control functions. In particular, as shown in the diagram of Figure 8, the process can provide for the step G of receiving at least one desired value of an operating parameter comprising one of:

- thermal power exchanged by the carrier fluid as it passes through each heat exchange unit 7,

- heat exchanged by the carrier fluid in a predetermined time interval in the passage through each heat exchange unit 7, - temperature difference as determined above.

As already mentioned, the desired value of each of the parameters mentioned can in turn be:

- or a set value (for example set by a user or a technician or present in a memory that can be accessed by the control entity 24, 24a, 24b),

- or calculated by the process as a function of a desired temperature in the environment in which each heat exchange unit is installed using known formulas and in any case not subject of the present invention (this is the case when the heat exchange units do not have a real air circulation channel),

- or a value calculated according to a desired value of the air temperature entering the heat exchange unit (case in which a heat exchange unit with a real air circulation channel such as a fan coil or an AHU);

The process can therefore determine (phase H in fig. 8), for each heat exchange unit (7), a real value of said operating parameter, and compare (phase I) the desired value of the operating parameter with the actual value of the same operating parameter, intervening (phase L) if there is an excessive discrepancy between the two. For example, if following the comparison step it derives that, for at least one heat exchange unit (7), the real value of the operating parameter deviates by more than a predetermined threshold from the desired value of the same operating parameter, the process can carry out at least one of the following control phases: - command the central heat treatment group (6) to adjust at least one general parameter selected from: flow rate imposed on the carrier fluid, hydraulic head imposed on the carrier fluid passing through the central group, heating imposed on the fluid vector passing through the central group, cooling imposed on the vector fluid passing through the central group,

- control the flow rate regulator (8) present on the channel (5) of the heat exchange unit (7).

In accordance with an aspect of the invention, the process provides for carrying out the control phase or phases described above, while maintaining the flow of the vector fluid passing through each heat exchange unit within the respective optimal operating range described above (phase F). For example, if it has been established that the maximum acceptable flow must be no more than 3φ0, consequently in the control of the flow regulator 8 or of the central unit 6, the process will in any case ensure that it does not exceed 3φ0. In other words, thanks to the prior determination of the characteristic function and its particular exponential nature, it is simple and intuitive to impose operational limits on the flow during the various control phases. It should also be noted (see figure 7) that by imposing a maximum limit on the flow as a function of the coefficient φ0, the exchanger actually operates in an efficiency zone as flows, for example, higher than 3φ0 would give (in the face of high losses load) very little gain in terms of power exchanged, compared to an important consumption of pumping energy.

The knowledge of the characteristic function relating to the heat exchange unit also allows you to easily carry out a procedure for identifying a malfunction condition of the heat exchange unit itself: for example by identifying a progressive deterioration of the same or sudden problems caused by damage (e.g. for example the presence of a leak) or from inappropriate use of the unit (for example, it may occur that the exchange unit is inadvertently covered with a sheet or other, preventing its efficient heat exchange).

In accordance with an aspect of the invention, the procedure for identifying a malfunction condition is performed at predetermined test instants during plant operation, for example at regular or periodic time intervals. The procedure can be performed for one or more heat exchange units: typically all heat exchange units are periodically tested.

The procedure provides, for each heat exchange unit, to measure at least one real value of the vector fluid flow through the heat exchange unit itself.

In a first alternative, the procedure can therefore determine at least one real value of the temperature difference ΔT or of the thermal power exchanged by the carrier fluid in the passage through the heat exchange unit 7 (using the real flow measurement of the carrier fluid and measuring the head ΔT between the first and second sections upstream and downstream of the heat exchange unit).

In addition to the determination of said real values, the procedure can provide for calculating, on the basis of the real measured value of the flow of carrier fluid, at least a corresponding calculated value of the thermal power exchanged by the carrier fluid in the passage through the heat exchange unit 7 or a calculated value of the temperature difference ΔT, using one of the characteristic functions described above. In practice, the calculated value of the thermal power (or the calculated value of the temperature difference ΔT) represents a value that the heat exchange unit should have under ideal conditions. The characteristic function used is that determined at a reference instant typically prior to the one in which the flow of the vector fluid is measured, so that the comparison takes place between one or more actual actual values and one or more calculated values of the same parameter relating to a previous instant in time.

The presence of a malfunction condition of the exchanger is then determined on the basis of the real value and the calculated value of the exchanged thermal power (or the temperature difference). In particular, the real value and the calculated value are compared, and the process concludes that a malfunction condition exists if the real value deviates from the calculated value by more than a predetermined threshold. In other words, an excessive difference between the real value and the calculated value is considered to be due to a malfunction.

In accordance with a second alternative, the procedure for identifying a malfunction condition involves:

- measure at least one real value of the vector fluid flow through a heat exchange unit,

- calculate on the basis of said at least one real value of the flow of carrier fluid, at least a corresponding calculated value of the temperature difference or of the thermal power exchanged by the carrier fluid in the passage through the heat exchange unit: this calculated value is obtained using a characteristic function determined at a predetermined time, in particular using the most recently determined characteristic function,

- determine the presence of a malfunction condition of the exchanger based on the comparison between:

the. the calculated value of the difference in temperature or of the heat output exchanged using this characteristic function relating to the predetermined instant of time, and

ii. a further calculated value of the temperature difference or of the heat output exchanged using said real value of the vector fluid flow and a characteristic function determined at an instant in time prior to the predetermined one.

In other words, in this second alternative calculated values of the parameter under consideration (temperature difference or heat exchanged power) determined on the basis of characteristic curves in turn calculated at different times are compared in order to compare values relative to different moments in the life of the 'heat exchange unit, without having to make any measurement apart from determining the flow (if not already known).

Once the values (real or calculated) relating to a recent or current instant have been compared with the calculated values relating to a previous instant (using one of the alternatives described), the procedure involves establishing that a malfunction condition exists if, following of said comparison, a discrepancy greater than a predetermined threshold is obtained between the values object of the comparison.

The process also provides for the possibility of carrying out a classification phase of the type of malfunction detected at a predetermined test instant as follows.

In the first alternative, the malfunction is classified as caused by progressive deterioration if the discrepancy in the parameter values (temperature difference or exchanged power) measured at the current instant and calculated using characteristic functions relating to an instant prior to the current one, compared to the interval of time between the current instant and the previous one is less than a limit value. The malfunction is instead classified as due to improper use or damage to the terminal if said discrepancy, related to the time interval between the current measurement instant of the mentioned parameters and the previous instant, is higher than the limit value.

In the second alternative, the malfunction is classified as caused by progressive deterioration if the discrepancy in the parameter values (temperature difference or exchanged power) calculated using characteristic functions relating to a predetermined instant and to an instant prior to the predetermined one, compared to the time interval between the predetermined instant and the previous one is lower than a limit value. The malfunction is instead classified as due to improper use or damage to the terminal if said discrepancy, related to the time interval between said predetermined instant and said previous instant, is higher than the limit value.

In other words, if the discrepancy as determined above is lower than the predetermined threshold, there is no malfunction if the discrepancy is between the predetermined threshold and the limit value (which is greater, for example double the predetermined threshold) there is a malfunction from progressive deterioration, while if the discrepancy exceeds the limit value, then there is a malfunction due to damage (for example leakage of carrier fluid) or improper use of the unit 7.

Monitoring and / or control device

A further aspect of the invention relates to a monitoring and / or control device of the conditioning and / or heating system 1 described above; in particular, the device comprises, for each service line, the flow regulator 8, at least a first thermal sensor 9a configured to detect the temperature of the carrier fluid in correspondence with the first section 5a of the service line 5 and a second thermal sensor 9b for detecting the temperature of the vector fluid at the second section 5b of the same service line 5, at least the hydraulic sensor 10 configured to determine the flow φ of the vector fluid. The device can also comprise the control unit 24 or 24a, 24b which is at least communicatively connected with the flow regulator 8, the first and second thermal sensors 9 and with the hydraulic sensor 10, in order to collect the signals from the sensors and in order to control the flow regulator 8 so as to regulate the flow of vector fluid crossing the service line. In particular, the monitoring and / or control process described above is performed by the control unit 24, or 24a, 24b which can be on board each flow controller or remote, as already illustrated. In other words, the control unit is configured to perform the process according to what is described above or according to the aspects listed above or according to any of the claims attached hereto.

The plant 1 typically comprises a number of control devices equal to the service lines 5 or a single control device that controls all the service lines according to the process described above or a plurality of control devices each dedicated to a subgroup of lines of service.

Control unit 24, 24a, 24b

The plant, the device and the process described and claimed herein use, as already indicated, at least one control unit in charge:

- to the reception of signals from the various sensors and to the monitoring of the processes described or claimed here and of the system / device described or claimed herein, and / or

- to control the same system / device described or claimed herein.

The control unit 24 can be a single unit (centralized or not as already mentioned) or be formed by a plurality of distinct control units depending on the design choices and operational needs.

The term control unit is in any case intended an electronic component which can include at least one of: a digital processor (CPU), an analog circuit, or a combination of one or more digital processors with one or more analog circuits. The control unit can be "configured" or "programmed" to perform some phases: this can be practically achieved by any means that allows the control unit to be configured or programmed. For example, in the case of a control unit comprising one or more CPUs and one or more memories, one or more programs can be stored in appropriate memory banks connected to the CPU or CPUs; the program or programs (software or firmware for example) contain instructions which, when executed by the CPU or CPUs, program or configure the control unit to perform the operations described in relation to the control unit itself. Such programs can be written in any known programming language. The CPUs, if in number equal to two or more, can be connected to each other through a data connection such that their computing powers are shared in any way; the CPUs themselves can be installed in geographically different positions, creating a distributed computing environment through the aforementioned data connection. The CPU or CPUs may be a general purpose processor configured to execute one or more parts of the process or steps described herein or claimed the software or firmware program, or be a dedicated ASIC or processor or FPGA, specifically programmed to run at least part of the operations described here. The memory medium can be non-transient and can be internal or external to the CPU or CPUs and can - specifically - be a memory geographically located remotely from the electronic computer. The memory support can also be physically divided into several portions, or in the form of a "cloud", and the software or firmware program can provide portions stored on geographically divided memory portions.

Alternatively, if the control unit is, or comprises, analog type circuitry, then the control unit circuit may be designed to include circuitry configured, in use, to process electrical signals to perform the related steps. to the control unit described or claimed herein.

Claims (17)

CLAIMS 1. Monitoring and / or control process of at least one air conditioning and / or heating system (1), said system comprising at least one delivery line (3), at least one return line (4) and a predetermined number of service (5) hydraulically interposed between the delivery line (3) and the return line (4), each service line (5) including at least one heat exchange unit (7), and optionally at least one heat exchange modulator (7a) associated with the heat exchange unit (7), in which said process provides, for at least one of said service lines (5), the phases of: - circulate a carrier fluid through at least one service line, - repeating a cycle which in turn comprises the following sub-phases a plurality of times: c) determine at least one value of the temperature difference (ΔT) between: � the temperature (Tt1) of the carrier fluid, at a first section (5a) of the service line upstream of the heat exchange unit (7) and � the temperature (Tt2) of the carrier fluid, in correspondence with the second section (5b) of the same service line located downstream of the heat exchange unit (7) subsequently, d) measure the value (φ) of the carrier fluid flow passing through the heat exchange unit (7), e) determine the heat exchanged power (dQ / dt) by the heat exchange unit, based on the value of the vector fluid flow (φ) passing through the heat exchange unit (7) and the temperature difference (ΔT), optionally obtaining in each cycle a triad of values comprising: or the value of said temperature difference (ΔT), the or the value of said vector fluid flow (φ) ed or the corresponding value of said heat exchanged power (dQ / dt) by the heat exchange unit; - determining a characteristic function of the heat exchange unit present in said service line which relates an exchanged thermal power (dQ / dt) from the heat exchange unit to the value of the vector fluid flow (φ), said characteristic function of heat exchange unit being determined using a plurality of values of heat exchanged and flow of vector fluid obtained in respective cycles, in which the characteristic function of the heat exchange unit present in said service line that relates the thermal power exchanged with the value of the vector fluid flow is an exponential curve of the type: where is it: dQ / dt represents the thermal power exchanged by the specific heat exchange unit, φ is the flow of the vector fluid entering the heat exchange unit, A and φ0 are obtained with curve fitting and / or interpolation techniques by approximating the pairs of flow values of the vector fluid (φtm) and of the thermal power (dQ / dt) obtained at each cycle. 2. Process according to the preceding claim, wherein said exponential curve is: where is it: where is it: ● dQ / dt represents the thermal power [kW] exchanged by the specific heat exchange unit, ● φ is the flow of the carrier fluid [kg / h] entering the heat exchange unit, ● Temperature [° C] of the vector fluid entering the unit heat exchange, i.e. in correspondence with the first section at instant t1; ● Temperature [° C] of the air present in the environment where the heat exchange unit operates or of the air entering the heat exchange unit at instant t1; ● Dew temperature (dewpoint) [° C] of the air present in the environment where the heat exchange unit operates at instant t1 or of the air entering the heat exchange unit; the dew temperature is determined with known formulas as a function of the temperature and relative humidity of the air present at instant t1 in the environment where the heat exchange unit operates or of the air entering the heat exchange unit and where: a1, a2, n and φ0 are coefficients obtained with curve fitting and / or interpolation techniques by approximating the pairs of flow values of the vector fluid (φ) and of the thermal power (dQ / dt) obtained at each cycle. Process according to claim 1 or 2, wherein said exponential curve is: where is it: and where: ● dQ / dt represents the thermal power [kW] exchanged by the specific heat exchange unit, ● φ is the flow of the carrier fluid [kg / h] entering the heat exchange unit, ● Temperature [° C] of the vector fluid entering the unit heat exchange, i.e. in correspondence with the first section at instant t1; ● Temperature [° C] of the air present in the environment where the heat exchange unit operates or of the air entering the heat exchange unit at instant t1; and where: a1, n and φ0 are coefficients obtained with curve fitting and / or interpolation techniques by approximating the pairs of flow values of the vector fluid (φ) and of the thermal power (dQ / dt) obtained at each cycle. 4. Process according to claim 1 or 2 or 3, in which the process comprises determining an optimal operating range of the heat exchange unit using the characteristic function, in particular using the coefficient φ0 of the exponential curve 5. Process according to the preceding claim, in which the process comprises determining an optimal operating range of the heat exchange unit using the coefficient φ0, imposing that the value of the vector fluid flow does not exceed K φ0, where K is a factor multiplicative> 1, optionally imposing that the vector fluid flow value does not exceed 3φ0. 6. Process according to the preceding claim, in which the process comprises determining an optimal operating range of the heat exchange unit using the coefficient φ0 and imposing that the value of the vector fluid flow does not fall below K 'φ0, where K 'is a multiplicative factor ≤ K, optionally imposing that the vector fluid flow value does not fall below 0.5φ0. Process according to any one of the preceding claims, wherein each line of service comprises: - at least one flow regulator (8) configured to control the flow of the carrier fluid through the heat exchange unit (7), - at least a first thermal sensor (9a) configured to detect the temperature of the vector fluid at the first section (5a) of the service line (5) and a second thermal sensor (9b) to detect the temperature of the vector fluid at the second section (5b) of the same service line (5), - at least one hydraulic sensor (10) configured to determine the flow (φ) of vector fluid. Process according to any one of the preceding claims comprising: receiving at least one desired value of an operating parameter comprising one of: - thermal power exchanged by the carrier fluid as it passes through each heat exchange unit (7), - heat exchanged by the carrier fluid in a predetermined time interval as it passes through each heat exchange unit (7), - temperature difference (ΔT) between the temperature (Tt1) of the vector fluid, in correspondence with the first section, measured at a first instant (t1), and temperature (Tt2) of the vector fluid, in correspondence with the second section, measured at a second time instant (t2) which can be coincident with or after the first instant; optionally where each of said desired values is: ● a set value, or ● a value calculated according to a desired value of the temperature present in the environment where the heat exchange unit operates, or ● a value calculated as a function of a desired value of the air temperature entering the heat exchange unit; determining, for each heat exchange unit (7), a real value of said operating parameter. Process according to the preceding claim, wherein each plant comprises at least one central heat treatment group (6) connected at least to the delivery line (3) and comprising: - at least one pump (12) ed - at least one refrigeration and / or heating unit (13) and in which the process also provides for: - comparing said desired value of the operating parameter with said real value of the same operating parameter, - if, following said comparison phase, it derives that, for at least one heat exchange unit (7), the real value of the operating parameter deviates by more than a predetermined threshold from the desired value of the same operating parameter - carry out a phase of control includes at least one of: the. control the central heat treatment group (6) to adjust at least one general parameter selected from: flow rate imposed on the carrier fluid, hydraulic head imposed on the carrier fluid passing through the central group, heating imposed on the carrier fluid passing through the central group, cooling imposed on the fluid vector crossing the central group, ii. control the flow rate regulator (8) present on the channel (5) of the heat exchange unit (7) iii. control the heat exchange modulator (7a) associated with the heat exchange unit (7), optionally control the number of sworns of at least one fan part of the heat exchange modulator. 10. Process according to claim 9, in combination with any one of claims 4 to 6, wherein during said control step it is provided to maintain the flow of the vector fluid passing through each heat exchange unit within the respective optimum range of operation. Process according to any one of the preceding claims, comprising determining said characteristic function of the heat exchange unit present a plurality of times at time intervals spaced apart, for example by one or more days, to consequently collect a plurality of characteristic curves in time. Process according to any one of the preceding claims comprising a procedure for identifying a malfunction condition performed at predetermined test instants, optionally periodically, for one or more heat exchange units, said procedure comprising the steps of: - measure at least one real value of the vector fluid flow passing through this heat exchange unit, - calculating on the basis of said at least one real value of the carrier fluid flow, at least a corresponding calculated value of the temperature difference or of the thermal power exchanged by the carrier fluid in the passage through the heat exchange unit (7), said calculated value being obtained using a characteristic function determined at a predetermined time, in particular the most recently determined characteristic function, - determine the presence of a malfunction condition of the exchanger based on the comparison between: the. the calculated value of the temperature difference or of the heat output exchanged using said characteristic function relating to the preset time instant, and ii. a further calculated value of the temperature difference or of the heat output exchanged using said real value of the vector fluid flow and a characteristic function determined at an instant in time prior to the predetermined one. 13. Process according to any one of the preceding claims from 1 to 11 comprising a procedure for identifying a malfunction condition performed at predetermined test instants, optionally periodically, for one or more heat exchange units, said procedure comprising the steps of: - measure at least one real value of the vector fluid flow passing through this heat exchange unit, - determine at least a corresponding real value of said difference in temperature of the vector fluid or heat power exchanged by the vector fluid, in the passage of the vector fluid itself through the heat exchange unit (7) to said real value of the vector flow, - calculating on the basis of said at least one real value of the carrier fluid flow, at least a corresponding calculated value of the temperature difference or of the thermal power exchanged by the carrier fluid in the passage through the heat exchange unit (7), said calculated value being obtained using a characteristic function determined at a predetermined instant in time, in particular prior to the measurement of the real value of the vector fluid flow, - determine the presence of a malfunction condition of the exchanger based on the comparison between: the. the calculated value of the temperature difference or of the heat output exchanged using said characteristic function relating to the preset time instant, and ii. the real value of the temperature difference or of the heat output exchanged. A process according to claim 12 or 13, in which determining the presence of the malfunction condition comprises establishing that a malfunction condition exists if, following said comparison, a discrepancy greater than a predetermined threshold is obtained between the values being compared. 15. Process according to claim 14, comprising a step of classifying a type of malfunction detected as: - malfunction caused by progressive deterioration if said discrepancy, related to the time interval between said predetermined instant and said previous instant, or related to the time interval between the instant of measurement of the real value of the vector fluid flow and said predetermined instant is below a limit value, - malfunction due to improper use or damage to the terminal if said discrepancy, related to the time interval between said predetermined instant and said previous instant, or related to the time interval between the instant of measurement of the real value of the vector fluid flow and said predetermined instant is higher than said limit value. 16. Device for monitoring and / or control of an air conditioning and / or heating system (1), said system comprising at least one delivery line (3), at least one return line (4) and a predetermined number of service lines (5) hydraulically interposed between the delivery line and the return line, and at least one central group of heat treatment (6) connected to the respective delivery line (3), each service line (5) comprising at least one heat exchange unit (7), optionally at least one heat exchange modulator (7a) being associated with the respective heat exchange unit heat exchange (7), said device comprising: - at least one flow regulator (8) configured to control the flow rate of the vector fluid passing through the heat exchange unit (7), - at least one first thermal sensor (9a) configured to detect the temperature of the vector fluid at a first section (5a) of the service line (5) upstream of the heat exchange unit (7) and a second thermal sensor (9b) to detect the temperature of the carrier fluid in correspondence with a second section (5b) of the same service (5) downstream of the heat exchange unit (7), - at least one hydraulic sensor (10) configured to determine the flow (φ) of carrier fluid, - at least one control unit (24; 24a, 24b) connected or connectable with the flow regulator (8) and / or with the central unit (6), with the first and second thermal sensors (9), with the hydraulic sensor and optionally with the heat exchange modulator (7a), - said control unit (24; 24a, 24b) being configured to carry out the process according to any one of the preceding claims. 17. Air conditioning and / or heating system comprising at least one circuit (2) for distributing a vector fluid, each circuit (2) comprising: - at least one delivery line (3) of the carrier fluid, - at least one return line (4) of the carrier fluid, - a plurality of service lines (5) connected directly or indirectly with said delivery line (3) and with said return line (4) and configured to serve respective rooms to be conditioned and / or heated, in which each of said lines service (5) includes in turn: � at least one heat exchange unit (7), optionally at least one heat exchange modulator (7a) being associated with the respective heat exchange unit (7), � at least one flow controller (8) configured to control the flow rate of carrier fluid passing through the heat exchange unit (7), at least one first thermal sensor (9a) configured to detect the temperature of the carrier fluid in correspondence with a first section (5a) of the upstream service line (5) of the heat exchange unit (7) and a second thermal sensor (9b) to detect the temperature of the carrier fluid in correspondence with a second section (5b) of the same service line (5) downstream of the heat exchange unit ( 7), ed � at least one hydraulic sensor (10) configured to determine the flow (φ) of vector fluid, - at least one central heat treatment group (6) located on the respective circuit (2), - at least one control unit (24; 24a, 24b) connected or connectable with the flow regulator (8) and / or with the central unit (6), with the first and second thermal sensors (9), with the hydraulic sensor (10) and optionally with the heat exchange modulator (7a), - said control unit (24; 24a, 24b) being configured to carry out the process according to any one of the preceding claims.