EA043859B1 - METHOD FOR CONTROLLING HOT FLUID DISCHARGE AND HOT FLUID DISCHARGE DEVICE - Google Patents

Description

Field of technology

The invention relates to a method for controlling the dispensing of hot fluid in a dispensing device.

The invention also relates to a device for dispensing hot fluid.

State of the art

Currently, for example, there are various types of dispensing machines and/or dispensing devices for dispensing coffee or other hot drinks such as tea, chamomile, herbal tea, etc. (ie, for dispensing hot fluids for food products), or for mixing fluid to produce food products, such as soups or the like.

For convenience of description, the present document refers to this type of dispensing machines/devices, however, the method according to the invention and the corresponding device can also be used in similar fields in which it is necessary to obtain control and supply of a hot fluid.

These dispensing machines require the fluid to be maintained at a programmed temperature in order to dispense hot beverage with the desired characteristics. The need to maintain a given fluid temperature arises from the fact that temperatures that are too low or too high can result in an unpleasant beverage with an undesirable taste.

Generally speaking, such dispensing machines are equipped with a control system that adapts the operating parameters of the machine depending on a certain outlet temperature and therefore requires a certain thermal inertia to prevent sudden unwanted temperature fluctuations.

More specifically, the sudden temperature fluctuations are not due to the instantaneous response of the fluid outlet temperature sensor connected to the control system to the variability of the fluid flow that may be output;

mains voltage variations;

variability in the temperature of the fluid entering the boiler or heat exchanger of the dispensing device, etc.

In other words, prior art systems are unable to account for these changes and act quickly to get the best possible output from the dispensing machine.

Thus, due to both the slow reading of the sensor to measure the temperature of the hot fluid flowing from the boiler or heat exchanger of the dispenser, and the lack of sensing and control of the variables discussed above, prior art systems are not fully capable of achieving the desired results even in terms of product quality.

Disclosure of the invention

Thus, the technical problem to be solved by the invention is to provide a hot fluid control method and dispensing device that can overcome the disadvantages of the prior art.

It is therefore an object of the invention to provide a hot fluid output control method and a hot fluid dispensing device that allows the parameters of the dispensing device to be precisely adjusted so as to maintain a constant hot fluid output temperature.

A further object of the invention is to provide a method for controlling the delivery of hot fluid and a delivery device that allows savings in terms of energy consumption, whereby it is possible to control suitable heat exchangers or boilers with very low thermal inertia, which are able to reach the desired temperature in a very short time.

Another object of the invention is to provide a method for controlling the dispensing of hot fluid and a dispensing device that prevents unwanted damage to any capsule and/or the device itself.

The said technical problem and said objectives are essentially solved by a method for controlling the dispensing of a hot fluid and a dispensing device comprising the technical features described in one or more claims of the appended claims.

The dependent claims disclose possible embodiments of the invention.

More specifically, said technical problem and said objectives are substantially solved by a method for controlling the dispensing of hot fluid in a dispensing device, comprising the steps of continuously measuring in real time parameters, that is, external variables for the operation of the dispensing device (such as, for example, supply voltage, temperature of the fluid entering the device, the required fluid flow); calculating and therefore immediately adjusting on the basis of these parameters, in a preventive manner during the fluid dispensing phase: the heat supplied by the boiler or the heat exchanger of the dispensing device, and/or the flow rate of the fluid dispensed by the pump, so as to maintain the temperature at the desired value at fluid exiting the boiler or heat exchanger and thus preventing its change.

In addition, the specified technical problem and the specified tasks are essentially solved in a fluid dispensing device comprising a fluid reservoir, a pump configured to

- 1 043859 for extracting a fluid from a reservoir, a boiler or heat exchanger configured to heat the fluid taken by the pump, a nozzle configured to dispense the heated fluid from the boiler or heat exchanger, and a control system for the dispensing device configured to implement the method described higher.

Brief description of drawings

Additional features and advantages of the invention will be better understood from the non-limiting description of a non-exclusive embodiment of a method for controlling hot fluid dispensing and a corresponding hot fluid dispensing device.

The description is given below with reference to the accompanying drawings, which are presented for purposes of illustration only and without limiting the scope of the invention and in which:

in fig. 1 is a schematic representation of a hot fluid dispensing device configured to implement a method for controlling and dispensing a hot fluid in accordance with the invention;

in fig. 2 is a schematic representation of another configuration of components of a dispensing device configured to implement the control method according to the invention;

in fig. 3 shows a schematic representation of the boiler or heat exchanger of the dispensing device according to FIG. 2;

in fig. 3a-3e show corresponding enlarged details from FIG. 3.

Carrying out the invention

In fig. 1 the position number 1 completely designates a device for hot fluid for food products, which for ease of description will be referred to as dispensing machine 1 in the following.

These food products may be of the bulk type or, for example, as shown in the accompanying drawings, contained in extraction tablets or capsules C for the preparation of hot beverages such as coffee, tea, herbal tea and the like. In other words, the term extraction capsules C is used to designate, further, any general type of capsule or dispenser or dispensing device that contains a substance in powder, granular or similar form.

Therefore, the term extraction capsules C herein always means any general type of capsule or dispenser or dispensing device in which the substance is contained in powder form, etc. for preparing hot drinks such as coffee, tea, herbal tea, etc.

Likewise, it should be noted that the boiler or heat exchanger and the corresponding heating element with round sections will be repeatedly named and illustrated by way of example only and without limiting the scope of the invention, since they, individually or both, can also have any other profile (oval, flattened etc.).

Moreover, the heating element need not be considered as a single element, but may also consist of several elements suitably arranged and sized.

Thus, the hot water dispensing control method (in this case, for ease of description, it will be limited to water only) according to the example of the invention is carried out in the dispensing machine 1 or dispensing device 1 such as, for example, shown in FIG. 1.

As illustrated, the fluid dispensing device 1 comprises at least:

power source (E);

a fluid source 2 to be heated;

supply unit 3, configured to collect the fluid to be heated;

boiler or heat exchanger 4;

a dispensing device 5 configured to dispense a hot fluid;

system 6 control and data processing.

As a non-limiting example of the illustrated embodiment, the invention may include:

power source E, which can be electricity;

a source of fluid to be heated, which may be a reservoir 2 for containing fluid;

supply unit, which can be a pump 3.

The control method includes measuring external operating variables of the dispensing device 1.

As described in more detail below, this measurement is obtained using suitable measuring units configured to send appropriate signals to the control unit 6.

The control unit 6 is configured to receive signals from the measuring units and perform cyclic calculations to optimize the control of device components (described in more detail below) depending on the measured values.

The control unit 6 stores the required or desired outlet temperature, that is, the reference temperature value.

In other words, the control method involves measuring all those parameters that, during the use of the dispensing machine 1 and, therefore, during the dispensing of hot water, influence the production

- 2 043859 desired hot drink.

As illustrated, the control and adjustment steps are performed by the control and processing system 6 as follows:

an inlet measurement comprising at least an available inlet power value and an inlet temperature of the fluid towards the boiler or heat exchanger 4;

cyclically calculating the amount of heat that should be supplied to the boiler or heat exchanger 4, and/or the flow rate of the supplied fluid;

subsequent adjustment of the heat value generated by the boiler or heat exchanger 4 and/or the amount of fluid supplied, depending on the measurements of the inlet parameters and the required or desired value of the outlet temperature of the fluid.

All measurement, cyclic calculation and adjustment steps are performed simultaneously and in real time during the fluid dispensing step of the dispensing device 5.

Preferably, the measurement step is performed by measuring the flow rate of water while it is dispensed by the dispensing device 1.

In other words, the method includes measuring the flow rate of water withdrawn from a fluid source, such as, for example, a reservoir 2, of the dispensing machine 1, during the entire dispensing.

Preferably, the measurement step is performed by measuring the mains voltage that is supplied to the dispensing device 1.

In other words, the method includes measuring the supply of electricity by a pump 3 configured to draw water from a reservoir 2, and/or a boiler or heat exchanger 4 configured to heat the water drawn by the pump 3.

It should be noted that the pump 3 and the boiler or heat exchanger 4 are connected to the control unit 6 and are driven by it.

Preferably, the measurement step is carried out by measuring the temperature of the incoming water and, if necessary, simply for checking, also the water flowing out of the boiler or heat exchanger 4 of the dispensing machine 1.

Preferably, the measurement step is performed by measuring a combination of the above-mentioned operating parameters of the machine described above.

A preferred embodiment of the control method involves measuring the three operating parameters described above.

More specifically, the measurement step is preferably carried out by measuring the flow rate of water dispensed by the dispensing machine 1, the mains voltage of the dispensing machine 1 and the temperature of the incoming water, and, if necessary, for verification purposes only, also the water leaving the boiler or heat exchanger 4 of the dispensing machine 1.

The measurement step is carried out continuously in real time during the entire period of operation of the dispensing machine 1, that is, during the dispensing of a hot drink by the dispensing machine 1.

Simultaneously with the measurement step, the control unit 6 performs a cyclic calculation step of heating control variables (boiler or heat exchanger) and/or pump, which will be constantly updated and optimized depending on the signals related to the measurements performed.

In this way, it is possible to maintain the temperature and/or flow of hot water at the required reference values (typical for the particular beverage to be prepared).

Preferably, control of the heat supplied by the boiler or heat exchanger 4 is carried out by changing the amount of heat generated by the electrical resistance 4a of the boiler or heat exchanger between a minimum heat amount and a maximum heat amount.

The terms minimum heat and maximum heat refer to the amounts of heat that can be generated by the boiler or heat exchanger 4 (i.e., say resistor 4a) with zero power supply and full power supply of the boiler or heat exchanger 4.

In other words, by changing the parameters of the supply voltage (and/or current) of the boiler or heat exchanger 4, you can continuously change the heat they generate to heat the water passing through it.

Preferably, the method may include the step of turning off the boiler or heat exchanger 4 in advance of the end of dispensing.

Preferably, this solution makes it possible to recover the energy, which is not proportionally negligible, accumulated within the heat exchanger and any capsule or powder or dispensing compartment, also with subsequent cooling, practically instantaneous, of the heat exchanger, which prevents the formation of limescale during the natural spontaneous cooling time that it would have been much longer. Preferably, control of the water flow is achieved by changing the flow rate of the pump 3 of the dispensing machine 1 between a maximum flow rate and a minimum flow rate.

The expressions minimum flow value (which may be 0) and maximum flow value mean the flow rates that pump 3 can extract from reservoir 2 depending on the minimum value (which may be 0) and the maximum value of the electrical supply to the pump

- 3 043859

3.

In other words, by changing the parameters of the voltage (and/or current) supplied to the pump 3, it is possible to obtain the calculated and required flow rate in order to obtain the best dispensing conditions.

Preferably, by using a heat exchanger with very low thermal inertia, this solution makes it possible to obtain a temperature change with any desired trend curve to optimize the characteristics of the resulting beverage.

The adjustment step is carried out continuously in real time during the entire period of operation of the dispensing machine 1, that is, during the dispensing of a hot drink by the dispensing machine 1, after it is continuously recalculated and updated on the basis of external parameters read continuously and always in real time.

Therefore, the measurement, calculation and adjustment steps are carried out simultaneously during the entire dispensing of hot water by the dispensing machine.

In other words, the control method continuously monitors the external conditions in which the machine operates and calculates and instantly adjusts the machine's dispensing conditions to ensure that the required reference temperature is maintained at all times.

During use, a given water flow rate (and/or vice versa) will be required for a given amount of heat to obtain the desired water output temperature.

For example, for a 4a 50 ohm resistor, which therefore outputs 968 W at a nominal voltage of 220 V, in order to have an output temperature of 90°C - starting from a boiler or heat exchanger inlet water temperature of 20°C - would require a water flow of 3.308 cm3 /With. If the mains voltage drops to 201 V, the method will be able to respond quickly, bringing the water flow to 3.014 cm/s without minimal change in maintaining the temperature at 90°C.

If, on the other hand, for example, a pump currently supplied to its maximum capacity could no longer supply the planned 3.308 cm ³ /s, but only 2.5 cm ³ /s, due to an increase in the outlet back pressure, then the method immediately would calculate and reduce the power supplied to the boiler or heat exchanger 4, bringing it to 731.5 W, limiting the voltage supplied to the boiler or heat exchanger 4 to 191.180 V, again preventing, also in this case, changes in the output temperature of 90°C.

As mentioned above, these calculations are performed instantly, and therefore the method allows the dispensing machine 1 to react equally quickly in the event of sudden changes in operating parameters.

Preferably, the method also includes the step of calculating the preheating time of the dispensing machine as a function of operating parameters measured when starting the dispensing machine 1.

In addition, the method includes adjusting the initial operating parameters to optimize the preheating time.

More specifically, in the case of using special heat exchangers with extremely low thermal inertia, which cannot be controlled by traditional methods, the method makes it possible to obtain, with the advantage, a dispensing machine 1 that is always ready for use, even starting from cold, taking into account an extremely reduced heating phase (which may, for example, be only about two seconds). For this reason, the method, as well as minimizing the energy spent on bringing the system to the required temperature, avoids maintaining the dispensing machine 1 in standby mode at the required temperature, while the additional energy wasted is negligible, as in conventional systems of the prior art.

In addition, the system is configured to avoid any form of idle state after dispensing is completed, in which low power consumption will still occur.

In fact, once a dispense is completed, the system can immediately enter a zero-consumption state until a subsequent dispense request is received.

This subsequent dispensing request reactivates the dispenser in a steady state, meaning the system is ready to immediately begin the dispensing cycle.

On the other hand, in all known implementations there is a continuous consumption without load, which is close to half a watt, which is the limit allowed by current regulations and which, considering 24 hours a day, 365 days a year, represents an additional waste of total energy that does not is insignificant.

Additionally, given the system's extreme responsiveness, it also allows the initial preheat to be increased by a second, thus bringing, in this example, up to 3 full seconds before dispensing begins.

This allows a small amount of initial steam to be produced, providing two main benefits:

the steam immediately diffuses into the entire soluble powder or product of the respective drink and, condensing, heats it quickly and evenly at the desired temperature, allowing even very small doses to be dispensed at the same temperature as longer ones, also with a more efficient extraction since it starts immediately with the right temperature;

This amount of fluid absorbed by the fine particles of lime scale, which can slowly and continuously form during evaporation, promotes its detachment and disintegration, preventing accumulation even when using quite hard water, thereby creating an effective anti-lime effect.

Preferably, this result can be further improved by certain measures directly related to the design of the boiler or heat exchanger 4 (see also Fig. 3-3e), including the following:

the resistor 4a (or heater) of the boiler or heat exchanger 4 may be specially treated to prevent sticking;

the common outer protective tube TCE (forming the tubular body of the heat exchanger 4) can likewise be subjected to specific treatment to prevent sticking;

The overall TCE outer protection pipe can be made directly from a material with natural or intrinsic non-stick properties (e.g. Teflon).

The outer protective tube TCE can also contain an inner spiral SP. This internal SP spiral, which generates a degree of turbulence in the flow that flows through it, may facilitate the detachment of any fine particles that are formed, particularly during possible initial evaporation.

External protective tube TCE according to FIG. 3 may comprise a TCI interior (FIG. 3c) that is suitably soft and/or flexible (eg, silicone) contained within a rigid TR pipe that is capable of withstanding the maximum planned operating pressures. The inner wall is designed to be subject to slight deformations and/or movements due to both the aforementioned turbulences and the pressure pulsations generated by the pumps with vibration occurring during normal use.

Said inner soft and/or elastic wall may, instead of being in direct contact with said outer rigid pipe, be separated from it by a small suitable separation gap I (Fig. 3e), which may also provide a predetermined additional mobility and/or expansion depending on the above-mentioned turbulences and/or pressure pulsations.

In fig. 3d, on the other hand, contains an intermediate solution in which the gap I is only partial and the inner soft and/or elastic wall partially rests directly on the rigid pipe TR.

Preferably, the main method may also include the step of initially calibrating the dispensing device 1.

The calibration step is performed to determine a correction factor (if necessary, automatically updated periodically and without any urgency) to compensate for any minor deviations in the actual outlet temperature measured relative to the expected and desired outlet temperature of the effluent fluid.

The adjustment step is performed taking into account the correction factor. Therefore, the calculation step is carried out taking this factor into account without any delay in subsequent planned adjustments.

It should be noted that the use of this coefficient, unlike traditional systems limited by the inherent delay of the temperature sensors, does not lead to any slowdown in adjustments, since it remains constant and typical for each individual machine, mainly due to the manufacturing tolerances of the various system components .

Preferably, in light of what has been described above, the method is capable of maintaining a constant hot fluid dispensing temperature under all conditions of use with maximum precision.

Preferably, the choice between reducing the heat generated by the boiler or heat exchanger and/or pump fluid flow (or increasing where necessary) is made in a short time, taking into account the measured external operating parameters, before they can affect the result obtained, as opposed to what happens in traditional systems that intervene after noting a change in outcome. Preferably, the control method includes the step of controlling the fluid passing through the boiler or heat exchanger 4 of the dispensing device 1.

The monitoring step is performed to determine any degree of limescale clogging of the dispensing device 1. More specifically, a monitoring step is performed to determine any degree of fouling of the heat exchanger 4.

If the degree of clogging is greater than a threshold value, the method includes the step of signaling to the user about the need to remove limescale from the dispensing device 1.

In other words, the degree of blockage is determined by the amount of limescale accumulated in the heat exchanger 4, which is assessed as dangerous by the machine control unit (which therefore requires the removal of limescale, which is signaled to the user), if in the simplest case it identifies the value , greater than the above threshold value.

If, on the other hand, the degree of clogging were below a threshold value, the dispensing device 1 would continue to operate normally.

Preferably, the monitoring step is performed by measuring the pressure difference of the fluid

- 5 043859 between the inlet section and the outlet section of the boiler or heat exchanger 4.

Thus, this pressure difference is compared with a reference value (in the absence of lime during passage in the heat exchanger 4, it is normal that there may be a small pressure difference between the inlet and outlet).

The degree of clogging described above is proportional to the difference between the measured value of the resulting pressure difference and the reference value.

As limescale continues to form, the cross-sections of the water channels are proportionally reduced, causing a gradual increase in the pressure difference between the inlet and outlet of the heat exchanger 4 (in the absence of limescale, the reference values are usually negligible due to the low resistance to the passage of water in the heat exchanger 4).

In other words, the pressure difference changes depending on the change in deposits generated by the limescale and is converted into a corresponding signal, which will therefore increase as new deposits are generated (or decrease as the deposits decrease if descaling cycles are performed).

As already mentioned, in order to isolate the above-mentioned pressure differences, the heat exchanger 4 can preferably be configured in accordance with the embodiment illustrated in FIG. 3.

Here, the outer protective tube TCE includes a corresponding inner wall in contact with the fluid to be heated, having a groove (ie not smooth) and separated by a predetermined separation distance DS from the heater R, which is quite limited (for example, about one millimeter or less) thus , to form a straight section of passage between the inlet and outlet of the fluid in the heat exchanger.

Thus, this transit section (designed with the specified predetermined distance DS) allows the fluid to flow in the absence of limescale, as shown in FIG. 3a, pass through the heat exchanger 4 along the shortest path between inlet and outlet, passing directly from one helix to the other through the section left free by this distance DS, with approximately straight motion, as if the helix groove were absent.

Under these conditions the corresponding pressure drop between inlet and outlet will be very small.

On the other hand, as shown in FIG. 3b, as the formation of lime scale FC continues, the fluid flow, for which this direct passage becomes increasingly difficult, will be forced to pass through the spiral-shaped groove to an increasingly greater extent, until reaching the extreme case in which it can flow exclusively inside it (see .corresponding arrows).

Under these conditions, both for a much smaller transit section since it is limited only to the inside of the groove, and for a spiral route much longer than the previous straight line, the pressure surge can be significant and therefore very easy to detect and/or measure and/or control.

It should be noted that even if this extreme situation is reached, suitable descaling fluids will flow perfectly through the heat exchanger, which, moreover, should ideally be completely complete at every point.

Thus, the above-mentioned feature allows for the same results to be achieved by using less sensitive and complex detection sensors and/or systems, thereby curbing the increase in cost while increasing the ease and reliability of detection and subsequent descaling.

It should be noted that an intermediate solution using multiple grooves with a longer helix pitch until the linear trend limit is reached instead of a helix may also be preferable.

The advantage will gradually decrease as design simplicity increases.

Preferably, the method may also include the step of blocking the dispensing device 1 so as to avoid exceeding a predetermined maximum value for the degree of clogging.

In other words, after repeated signaling steps, the method may include blocking the dispensing device 1 until the user performs descaling.

Preferably, the method may also include the step of identifying false decalcification from the dispensing device. Therefore, this step also includes, after the above-mentioned blocking of the dispensing device 1, blocking the descaling procedure after a predetermined number of monitoring operations identifying false descaling attempts by the user.

In other words, if the user were to use an ineffective descaling product or, on the other hand, decide to trick the dispensing device 1 by leaving the water circulating without the descaling product, the method could identify that after the scheduled signals there is still the same degree of blockage (if not more) and take into account the number of times this phenomenon occurred. After exceeding a predetermined number of attempts, which have occurred without success and/or with worsening of the degree of the detected blockage, the method can thus prevent further attempts to avoid reaching a possible complete blockage. Thus, if the machine were to enter a maintenance state, it would be safe to know, simply by observing such a complete lockout, that inadequate maintenance had been performed by the user.

Therefore, maintenance can only consist of removing, perhaps simply by a sequence of commands unknown to the public, the blocking of the descaling cycles, which can be carried out again in the correct manner in the maintenance operation itself, without any additional costs for disassembly and replacement of components.

The invention also relates to a dispensing device 1, which comprises the aforementioned fluid reservoir 2, a pump 3 configured to withdraw fluid from the reservoir 2, a boiler or heat exchanger 4 configured to heat the fluid withdrawn by the pump 3, and a nozzle 5, configured to release heated fluid from the boiler or heat exchanger 4.

The dispensing device or machine 1 also includes a control system 6 configured to implement the control method described above.

The term control system 6 refers to all those hardware and software components (ie control electronics) that enable the method described above to be carried out.

In other words, the term control system 6 refers to a set of sensors, processors and programs used to directly assess in real time which parameters of the dispensing device 1 need to be modified depending on measured input or external operating parameters.

For this reason, the control system 6 includes a control unit 7 connected to various components of the dispensing machine 1 to carry out the method described above.

Preferably, the control system 6 includes a first temperature sensor 8a located near the inlet of the boiler or heat exchanger 4.

Preferably, the control system contains a second temperature sensor 8b located near the outlet of the boiler or heat exchanger 4.

Preferably, the first temperature sensor 8a is located outside the boiler or heat exchanger 4, but very close to the inlet of the boiler or heat exchanger 4.

Alternatively, the first temperature sensor 8a may be installed inside the boiler or heat exchanger 4.

Likewise, alternatively, the second temperature sensor 8b can also be located in the interior of the boiler or heat exchanger 4.

Preferably, the first temperature sensor 8a and, if present, the second temperature sensor 8b are configured to measure, respectively, an inlet fluid temperature (toward the boiler or heat exchanger 4) and an outlet fluid temperature from the boiler or heat exchanger 4.

Thus, the control system 6 (ie the control unit 7) can calculate the amount of heat that should be released from the boiler or heat exchanger 4, as well as maintain any updated calibration factor entered by reading the sensor 8b.

Preferably, the control system 6 comprises a turbine 9, preferably located between the reservoir 2 and the boiler or heat exchanger 4.

The turbine 9 is configured to measure (accurately, immediately and continuously) the actual flow rate of the fluid drawn by the pump 3 (taking it, in this example, from the reservoir 2) and supplied to the boiler or heat exchanger 4. As shown, for example, in FIG. 1, turbine 9 is located between reservoir 2 and pump 3.

The control system 6 (ie the control unit 7), such as the one shown in FIG. 1 is also connected to power source E and is designed to check and measure the mains voltage.

In addition, the control system 6, connected to the electrical network and with the help of suitable control devices 10a and 10b, is capable of suitably and immediately changing the energy supplied respectively to the pump 3 and/or to the boiler or heat exchanger 4 (ie to the resistor 4a).

Preferably, the control system 6 includes a first pressure sensor 11 and a second pressure sensor 12, respectively, located in the inlet and outlet sections of the heat exchanger 4 to monitor the pressure of the fluid passing through the boiler or heat exchanger 4.

Alternatively, monitoring can be performed using a single differential pressure sensor connected to the inlet and outlet sections of heat exchanger 4.

The pressure drop in any case is proportionally related to the flow rate of the fluid passing through the heat exchanger 4.

Therefore, in order to have the correct value for the degree of clogging, it is necessary to divide the pressure surge by the flow rate of the measured fluid.

Preferably, the monitoring step is carried out by measurement, during a short initial phase

-

Claims (16)

output, the inlet pressure of the fluid into the heat exchanger 4 and comparing the value with the reference value of the inlet pressure. In fact, in the initial stages, the fluid that passes through the food powder, still dry, will not find any significant resistance, making it unnecessary to measure the outlet pressure as it will be close to 0; therefore, it will be convenient, for example, to use one pressure sensor in the inlet section of heat exchanger 4. According to another embodiment, and preferably, monitoring during the above-mentioned initial dispensing stage can be performed by comparing the actual performance of a fluid delivery unit, such as, for example, pump 3, with the reference performance of pump 3, preferably used at reduced and stabilized performance levels . In fact, a particular pump 3 may have, depending on the energy that is supplied to it, a well-defined output curve, based on which the flow rate of the supplied fluid starts from a maximum value when there is no back pressure flowing, to gradually drop to 0 when the maximum pressure is reached, which it is capable of delivering under these supply conditions. In other words, monitoring is performed based on the back pressure, which can be calculated since the discharge curve from pump 3 is known, as. fluid flow function: since the measuring device is located between the pump 3 and the reservoir 2, that is, for example, the turbine 9, which is capable of determining the amount of fluid supplied to the pump 3, the turbine 9 can equally measure the speed and therefore, in parallel, the above-mentioned flow rate. In other words, if there is no buildup, the initial dispensing will occur at virtually zero back pressure and therefore at the maximum velocity or flow rate planned under those conditions; on the other hand, the presence and increase of limescale formations causing a gradual increase in back pressure downstream of the pump will cause a corresponding gradual decrease in the speed or flow rate measured by the turbine 9, which will therefore provide a corresponding degree of clogging of the dispensing system. In general, the control system 6 is configured to implement the method described above using the described components, which allow immediate control in real time and in every possible operating state of the operating parameters of the entire device. In addition, with the help of the control unit 7, the control system 6 is able, starting from the required reference parameters, to quickly and in real time (preferably during the entire dispensing time of the fluid) adjust the parameters to be modified in order to maintain a constant temperature and/or a suitable temperature change and/or an output fluid stream to produce an optimized hot beverage with the desired characteristics. The invention provides the advantage of allowing the parameters of the dispensing device 1 to be precisely adjusted so as to maintain a constant temperature of the hot fluid at the outlet. The invention provides the advantage of allowing the parameters of the dispensing device 1 to be precisely adjusted so as to appropriately change the outlet temperature of the hot fluid even during dispensing. The invention provides the advantage of allowing the parameters of the dispensing device 1 to be precisely adjusted so as to maintain a constant flow of hot fluid at the outlet. The invention provides the advantage of allowing the parameters of the dispensing device 1 to be precisely adjusted so as to appropriately change the output flow of hot fluid even during dispensing. The invention provides the advantage that savings can be achieved in terms of energy consumption. The invention provides the advantage of effective protection against damage due to the formation of limescale. The invention provides the advantage of avoiding damage or undesirable deterioration of the capsule C and/or the food powder used and/or the dispensing machine 1. CLAIM 1. A method for controlling the dispensing of hot fluid in a fluid dispensing device (1) containing at least: power source (E); a source (2) of fluid to be heated; a supply unit (3) configured to take in the fluid to be heated; boiler or heat exchanger (4); a dispensing device (5) configured to dispense a hot fluid; control and data processing system (6), characterized in that it contains the following steps initiated by the control and data processing system (6): measurement of input parameters including at least the input power value and - 8 043859 inlet temperature of the fluid in relation to the boiler or heat exchanger (4); cyclically calculating the amount of generated heat to be supplied to the boiler or heat exchanger (4) and/or the amount of output fluid; subsequently adjusting the amount of heat generated by the boiler or heat exchanger (4), and/or the amount of fluid output, depending on the measurements of the above input parameters and the required or desired value of the outlet temperature of the fluid; wherein the measurement, cyclic calculation and adjustment steps are performed simultaneously and in real time during the fluid dispensing step via the dispensing device (5). 2. The method according to claim 1, in which the measurement step is performed by measuring: flow rate of fluid supplied by the dispensing device (5); and/or the amount of energy available at the input of the dispensing device (1); and the temperature of the fluid entering said boiler or heat exchanger (4). 3. Method according to claim 1 or 2, wherein the measurement step is carried out by also measuring the outlet temperature of the fluid from said boiler or heat exchanger (4). 4. The method according to any of the preceding claims, also including the step of calibrating the dispensing device (1) to determine a correction factor, preferably cyclically updated, taking into account the expected or desired value of the outlet temperature and the measured actual value of the outlet temperature of the fluid, and the adjustment step is performed taking into account the specified correction factor. 5. The method according to any of the preceding paragraphs, in which the specified adjustment step includes preliminary shutdown of the boiler or heat exchanger (4) before the end of dispensing. 6. A method according to any of the preceding claims, wherein said adjustment of the heat supplied by the boiler or heat exchanger (4) is carried out by changing the amount of heat generated by the electrical resistance (4a) of the boiler or heat exchanger (4) between a minimum amount of heat and a maximum amount of heat ; said step of changing the amount of heat is performed by suitably changing the supply voltage and/or current. 7. The method according to any of the preceding paragraphs, in which the specified adjustment of the flow rate of the dispensed fluid is performed by changing the flow rate of the supply unit (3) of the specified dispensing device (1) between the maximum flow rate value and the minimum flow rate value; said flow rate changing step is performed by suitably changing the supply voltage and/or current. 8. The method according to claim 7, in which the specified step of changing the flow rate is carried out by suitable changing the voltage and/or current of the supply of the electric pump (3) forming the supply unit. 9. The method according to any of the preceding claims, also including the step of calculating the preheating time of the dispensing device (1) depending on the input and operating parameters measured at the beginning of the specified dispensing device (1), and adjusting the specified initial operating parameters to optimize the preheating time . 10. The method of claim 9, wherein said step of calculating the preheating time includes extending for a further predetermined time to generate a predetermined amount of steam, an amount of steam suitable for both preheating the food powder and preventing or at least , limiting the formation of limescale. 11. Device (1) for dispensing hot fluid, comprising a power source (E); a source (2) of fluid to be heated; a supply unit (3) configured to supply the fluid to be heated into the boiler or heat exchanger (4); dispensing device (5), configured to dispense heated fluid from the boiler or heat exchanger (4); system (6) for control and data processing, configured to implement the method according to any of the previous paragraphs. 12. Device (1) according to claim 11, in which said control system (6) comprises a first temperature sensor (8a) located near the inlet of the boiler or heat exchanger (4); said first temperature sensor (8a) is configured to measure the inlet temperature of the fluid entering the boiler or heat exchanger (4). 13. Device (1) according to claim 12, in which said control system (6) contains a second temperature sensor (8b) located near the outlet of the boiler or heat exchanger (4), wherein said second temperature sensor (8b) is configured to measure the output temperature of the fluid leaving the boiler or heat exchanger (4). 14. A device according to any one of claims 11 to 13, in which said control system (6) contains a measuring device or turbine (9) configured to measure the actual flow rate of the fluid supplied to the boiler or heat exchanger (4). 15. Device according to any one of claims 11 to 14, in which said control system (6) is also connected to the power source (E) and is configured to measure the corresponding voltage. 16. The device according to any one of claims 11-15, in which the specified boiler or heat exchanger (4) is manufactured -