EP2395288A1 - Balancing valve - Google Patents

Abstract

The valve (1) has a measurement unit for measuring characteristics of fluid passing through the valve. A control unit positions a flap gate (2) of the valve. A data storing unit stores intrinsic and extrinsic parameters of the valve. An independent processing unit is arranged to realize automatic balancing of the parameters from values of the characteristics of the fluid measured by the measuring unit. The processing unit exchanges and modifies the balancing data at the end of adaptation and diagnosis of a hydraulic distribution network (5). Independent claims are also included for the following: (1) a method for automatic static balancing of hydraulic conditions of thermal regulation units integrated into a branch of a hydraulic network (2) a method for automatic dynamic balancing of input pressure of thermal regulation units integrated into a branch of a hydraulic network.

Description

The present invention relates to the field of hydraulic networks of buildings and more precisely to a valve balancing valve having an inlet and an outlet, mounted downstream of a thermal control element integrated into a hydraulic system subject to a substantially constant pressure.

By definition, a balancing valve has the function of controlling the incoming charges in the branches of the hydraulic network comprising thermal regulation elements, such as a thermostatic radiator valve in heating network branches or a control valve for fans. convector in branches of air conditioning networks.

A balancing valve is an essential element to meet the energy rationalization standards in new buildings meeting the requirements of Low Consumption Building (BBC), Very High Energy Performance (THPE), Very High Energy Performance and Renewable Energies ( THPE EnR) or soon Low Consumption building Effinergie or other eco and / or thermal performance labels.

Balancing is for the hydraulic networks of buildings, the final act of the installation chain. This is intended to allow the distribution of the calories of the fluid according to the needs of the building, which implies to have good flow in the right places.

In an installation, the hydraulic networks evolve dynamically, so that the thermal needs and therefore the flow rates of the fluid are not identical according to the seasons, the orientation of the buildings and the activity, however most of the installed systems are limited. balancing valves that provide settings for the times that require the most calories.

It is known to regulate the flow of fluids from installations in buildings through balancing valves and control valves. For example, from a processing unit that determines centrally whether the parameters of the control valves need to be changed. All of its modifications produced by the control valves lead to new settings for the balancing valves.

Nevertheless, these valves use a centralized processing system with remote communication means to coordinate the settings and ensure a diagnostic network.

In addition, the use of remote communication, in particular wireless communication, between all the regulating and balancing valves and the central processing unit reduces the reliability of these balancing valves, which do not receive all of them. in the same way the signals coming from the processing unit.

Tuning the balancing valves is tedious, expensive and requires software dedicated to these settings and advanced knowledge of hydraulics. Due to the hydraulic interaction between the branches of the network, these adjustments are difficult to obtain without methods and / or tools.

This is attributed to the fact that these balancing valves are located at different distances from the treatment system and that the signals can be made to pass through walls or partitions of various thicknesses, considerably reducing the intensity of the signals emitted by the control system. centralized treatment.

The present invention aims to solve all or part of the disadvantages mentioned above.

For this purpose, the subject of the present invention is a valve for balancing a valve comprising an inlet and an outlet, mounted downstream of a thermal regulation element integrated into a branch of a hydraulic network subjected to a pressure (Δ P ) substantially constant, characterized in that it comprises means for measuring a characteristic quantity of the fluid flowing through the automatic balancing valve, means for controlling the positioning of the valve of the automatic balancing valve, storage means of data in which are stored intrinsic and extrinsic parameters of the balancing valve, independent processing means arranged to achieve automatic balancing in the branch from the values of the characteristic quantity of the fluid measured by the measuring means, control means and data stored in the storage means.

This arrangement makes it possible to have a balancing valve operating automatically, independently of network interference, by automatically adjusting to the desired hydraulic condition and in perfect autonomy without the need for a centralized processing system.

The automatic balancing thus produced can be applied to a static and / or dynamic and / or communicating balancing.

According to one embodiment, the processing means allow said static automatic balancing in which the parameters available in the data storage means are compiled with the measurements collected by the measuring means in order to obtain characteristic reference values of the network. hydraulic.

According to one embodiment, the processing means allow dynamic automatic balancing in which reference values, preferably those determined previously, are used to control the valve positioning control means so as to maintain a differential pressure or a flow rate according to the substantially constant case in the branch of the hydraulic network (Δ P ) in which the balancing valve is installed.

According to one embodiment, the processing means make it possible to exchange and modify balancing data for the purpose of adapting and diagnosing the entire hydraulic network.

According to one embodiment, the processing means allow a communication of the valves with a central unit in order to adjust and modify the reference values and thus reduce the hydraulic losses of the network and quantify the generation and distribution energy gains.

This means of treatment makes it possible to have an overview of the installation allowing its rapid diagnosis and thus target a curative or corrective or legal intervention.

According to one embodiment, the measured characteristic quantity of the fluid passing through the balancing valve relates to its flow rate. Alternatively, flow and temperature can be taken into account.

The flow rate of a fluid passing through a valve is easily and accurately measurable.

According to one embodiment, the intrinsic parameters of the balancing valve comprise the hydraulic characteristics supplied by its manufacturer representing the pressure differential (ΔP _valve ) between the inlet and the outlet of the balancing valve as a function of the flow rate ( Q) for a given position of the valve of the balancing valve.

This arrangement makes it possible to easily determine with a good approximation a position of the valve flap corresponding to a pressure differential of the supposedly variable valve to ensure a given flow equal to the desired balancing flow.

According to one embodiment, during automatic static balancing, the processing means calculate the reference characteristic coefficient of the dimensioning of the hydraulic network (Z _Ref ) considered as a function of two or more determined values of flow rate, for example at 75%. and at 50% of the full opening (Q _{Kv 75%} , Q _{Kv 50%} ) for two different positioning (P _75% , P _50% ) of the valve, and corresponding values of the characteristic coefficients of the sizing (Kv _75% , K _V50% ) of the balancing valve deduced from the pressure differentials ( _valve ΔP) given by the intrinsic hydraulic characteristics of the valve.

This arrangement makes it possible to perform a self-calibration of the valve to increase the accuracy of the intrinsic theoretical characteristics of the valve. It can also corroborate the calculated value of the reference characteristic coefficient of the design of the hydraulic network with the theoretical value given by the plans of the architect in the case of a new or renovated building.

According to one embodiment, the extrinsic parameters of the balancing valve comprise a setpoint value (Q _setpoint ) of the flow of the balancing valve corresponding to the estimate of the need for a thermal regulation element in a branch concerned. hydraulic system, such as a radiator or a fan coil.

This arrangement makes it possible to specifically adapt a balancing valve to the branch of the hydraulic network in which it is installed. This estimation of the flow rate is quantifiable by the energy requirement required by the operating temperature conditions of the heating and / or air conditioning elements.

According to the same embodiment, the setpoint value (Q _setpoint ) of the flow rate is programmable in the data storage means of the automatic balancing valve.

This arrangement makes it possible to automatically modify the setpoint value as a function of time and thus of external and internal environmental conditions.

According to one embodiment, during static automatic balancing, the processing means calculate an updated value ( _updated Kv) for the characteristic coefficient of the dimensioning (Kv) of the valve as a function of the determined flow rate (Q _measured ) at the position of the valve corresponding to the setpoint value (Q _setpoint ) and its characteristic coefficient of dimensioning (Kv _setpoint ) of the corresponding balancing valve, and the reference characteristic coefficient of the dimensioning of the hydraulic network (Z _ref ).

This arrangement makes it possible to compensate for perceptible network effects through the difference between the value of the setpoint flow (Q _setpoint ) and the value actually determined (Q _measured ).

According to one embodiment, during static automatic balancing, the processing means calculate a reference pressure differential (ΔP _ref ) of the branch of the hydraulic network with a characteristic coefficient of the dimensioning of the updated valve ( _updated KV). from the formula: $$\mathrm{\Delta }{P}_{\mathit{ref}}={\left(\frac{Q_{\mathit{measured}}}{K_{v_{\mathit{updated}}}}\right)}^2$$

This arrangement makes it possible to acquire reference values that can be exploited for use in installation control or any other intervention on the network.

According to one embodiment, during dynamic automatic balancing, the processing means act on the control means for positioning the valve using an actuator to maintain a reference pressure differential (ΔP _ref ) substantially constant in the branch of the network whatever the need of the hydraulic network.

This arrangement makes it possible to maintain a quasi-constant pressure differential in the branch in which the balancing valve and the thermal regulation element are located, whatever the need of the hydraulic network.

• extraire des moyens de stockage de données une valeur de consigne de débit (Q_consigne),
• calibrer la vanne d'équilibrage en déterminant les débits pour deux ou plusieurs positions connues du clapet de la vanne d'équilibrage correspondant respectivement aux coefficients caractéristiques de la vanne d'équilibrage automatique, par exemple à 75% et 50% de l'ouverture maximale de la vanne,
• calculer le coefficient caractéristique du dimensionnement du réseau hydraulique (Z _réf) et le coefficient caractéristique du dimensionnement (Kv_consigne) de la vanne d'équilibrage correspondant,
• positionner le clapet de la vanne sur sa position correspondant à la valeur calculée,
• déterminer le débit (Qmesuré),

si

• Le débit déterminé (Q_mesuré) est compris dans une plage de valeur déterminé par exemple à plus ou moins 5% de la valeur du débit de consigne (Q_consigne), alors :
• la valeur du débit de consigne (Q_consigne) est remplacée par la valeur du débit déterminé (Q_mesuré),
• le coefficient caractéristique du dimensionnement (Kv_consigne) de la vanne d'équilibrage correspondant au coefficient caractéristique du dimensionnement du réseau hydraulique (Z_réf) devient le coefficient caractéristique du dimensionnement de référence (Kv_réf), et
• le différentiel de pression de référence (ΔP_réf) d'une branche (4) du réseau hydraulique (5) est calculé à partir du coefficient caractéristique du dimensionnement de référence (Kv_réf) et du débit déterminé (Q_mesuré), sinon :
• revenir à l'étape de calcul du coefficient caractéristique du dimensionnement du réseau hydraulique (Z _réf) et du coefficient caractéristique du dimensionnement (Kv_consigne) de la vanne d'équilibrage correspondant.

The subject of the present invention is also a static automatic balancing method for the hydraulic conditions of one or more thermal regulation elements integrated into a branch of a hydraulic network subjected to a substantially constant pressure differential (ΔP) comprising a valve. balancing device as described above characterized in that it comprises in this order the steps of:

• extracting data storage means from a flow setpoint value (Q _setpoint ),
• calibrate the balancing valve by determining the flow rates for two or more known positions of the valve of the balancing valve respectively corresponding to the characteristic coefficients of the automatic balancing valve, for example at 75% and 50% of the maximum opening of the valve,
• calculate the characteristic coefficient of the dimensioning of the hydraulic network (Z _ref ) and the characteristic coefficient of the dimensioning (Kv _{set point} ) of the corresponding balancing valve,
• set the valve flap to its position corresponding to the calculated value,
• determine the flow (Qmesuré),

if

• The determined flow rate ( _measured Q) is within a range of value determined for example at plus or minus 5% of the value of the setpoint flow (Q _setpoint ), then:
• the value of the setpoint flow (Q _setpoint ) is replaced by the value of the determined flowrate (Q _measured ),
• the characteristic coefficient of dimensioning (Kv _setpoint ) of the balancing valve corresponding to the characteristic coefficient of the dimensioning of the hydraulic network (Z _ref ) becomes the characteristic coefficient of the reference dimensioning (Kv _ref ), and
• the reference pressure differential (ΔP _ref ) of a branch (4) of the hydraulic network (5) is calculated from the characteristic coefficient of the reference dimensioning (Kv _ref ) and the determined flow rate (Q _measured ), otherwise:
• return to the step of calculating the characteristic coefficient of the dimensioning of the hydraulic network (Z _ref ) and the characteristic coefficient of the dimensioning (Kv _{set point} ) of the corresponding balancing valve.

• effectuer en premier lieu les étapes de caractérisation décrites dans le procédé d'équilibrage automatique dit statique afin de déterminer les conditions hydraulique de la branche
• attendre après un premier temps déterminé la stabilisation de l'écoulement du fluide au travers de la vanne d'équilibrage (1), ce temps étant paramétrable et de préférence égal à 30 minutes,
• déterminer le débit (Q), en déduire le différentiel de pression (ΔP),
• si le différentiel de pression (ΔP) est compris dans une plage de valeur déterminé par exemple à plus ou moins 5% de la valeur du différentiel de pression de référence (ΔP_réf) :
• revenir à la première étape consistant à attendre après un premier temps déterminé,

sinon :

• calculer le coefficient caractéristique du dimensionnement du réseau hydraulique (Z) et le coefficient caractéristique du dimensionnement (Kv) de la vanne d'équilibrage automatique correspondant,
• positionner le clapet de la vanne d'équilibrage sur sa position correspondant au coefficient caractéristique du dimensionnement (Kv) de la vanne d'équilibrage automatique,
• attendre après un deuxième temps déterminé puis revenir au début de cette étape, ce temps étant paramétrable et de préférence égal à cinq minutes.

The subject of the present invention is also a process for automatically balancing said dynamic input pressure of one or more thermal regulation elements integrated into a branch of a hydraulic network subjected to a substantially constant pressure differential (ΔP). comprising a balancing valve as described above characterized in that it comprises in this order the steps of:

• first perform the characterization steps described in the so-called static automatic balancing process to determine the hydraulic conditions of the branch
• wait, after a first determined time, for the stabilization of the flow of the fluid through the equilibration valve (1), this time being parameterizable and preferably equal to 30 minutes,
• determine the flow rate (Q), deduce the pressure differential (ΔP),
• if the pressure differential (ΔP) is within a given value range, for example plus or minus 5% of the value of the reference pressure differential (ΔP _ref ):
• return to the first step of waiting after a first determined time,

if not :

• calculating the characteristic coefficient of the dimensioning of the hydraulic network (Z) and the characteristic coefficient of dimensioning (Kv) of the corresponding automatic balancing valve,
• position the valve of the balancing valve in its position corresponding to the characteristic coefficient of dimensioning (Kv) of the automatic balancing valve,
• wait after a second determined time and then return to the beginning of this step, this time being configurable and preferably equal to five minutes.

• La figure 1 montre le schéma de principe d'un réseau hydraulique de distribution équipé de vannes équilibrantes selon l'invention.
• La figure 2 montre un exemple d'abaque fourni par le constructeur d'une vanne d'équilibrage.
• La figure 3 explique l'adaptabilité en vectoriel de la vanne d'équilibrage selon l'invention.
• La figure 4 explique l'adaptabilité sur l'abaque du fabricant de la vanne d'équilibrage selon l'invention.
• La figure 5 illustre les différentes étapes de la mise en oeuvre d'une vanne d'équilibrage selon l'invention.
• La figure 6 représente un schéma de la vanne d'équilibrage.

In any case, the invention will be better understood with the aid of the description which follows, with reference to the appended schematic drawing showing, by way of non-limiting example, the principle of operation of a balancing valve according to FIG. invention.

• The figure 1 shows the block diagram of a hydraulic distribution network equipped with balancing valves according to the invention.
• The figure 2 shows an example of an abacus provided by the manufacturer of a balancing valve.
• The figure 3 explains the vector adaptability of the balancing valve according to the invention.
• The figure 4 explains the adaptability on the chart of the manufacturer of the balancing valve according to the invention.
• The figure 5 illustrates the different steps of the implementation of a balancing valve according to the invention.
• The figure 6 represents a diagram of the balancing valve.

As illustrated in figure 1 a balancing valve (1) with a valve (2) has an inlet A and an outlet B, and is mounted downstream of a thermal control element (3) integrated in a branch (4) of a hydraulic network (5) subjected to a substantially constant pressure differential (ΔP) from a pump (6).

Assuming that the hydraulic network (5) is subjected to a substantially constant pressure differential from the pump (6), it is possible to write the equation: $$\mathrm{\Delta }{P}_{\mathit{pump}}=\mathrm{\Delta }{P}_{\mathit{élémentsurleréseau}}+\mathrm{\Delta }{P}_{\mathit{valve}}$$

Wherein, in a manner known per se: Δ P = Q _{élémentsurler é bucket} ² Z, with Zsymbolisant characteristic coefficient of the dimensioning of the hydraulic system (5), a leg (4) or an actuator such as valve equilibrium (1), and Δ P _valve = ( Q / Kv ) ² , with K _v symbolizing the characteristic coefficient of the dimensioning of the valve 1.

This coefficient K _v characteristic of the dimensioning of the valve 1 is representative of the slope of the lines corresponding to the various positions of the valve (2) of the balancing valve (1) of the abacuses illustrated in FIGS. figures 2 and 4 .

The adaptability of the opening of the equilibration valve (1) takes place in two phases: a first automatic so-called static balancing phase whose purpose is to identify the various parameters characterizing the hydraulic network (5) and the balancing valve (1) considered, and a second so-called dynamic dynamic balancing phase intended to adapt the pressure entering a thermal regulation element (3) according to the estimated need of this element (3), this estimate may vary over time in a predetermined manner.

The first so-called static automatic balancing phase first of all makes it possible to perform a self-calibration, starting from flow rates Q passing through the balancing valve (1), for two or more valve opening positions (2). ) valve (1) known.

These measurements are made by measuring means (7) arranged in the balancing valve (1) or on the branch (4) on which the valve 1 is installed.

In addition, the balancing valve (1) also comprises control means (8) for positioning the valve (2) of the balancing valve (1), as well as data storage means (11) in which are stored various intrinsic parameters specific to the balancing valve (1) and various extrinsic parameters depending on the use and operation of the balancing valve (1).

The figure 6 schematizes the balance of equilibrium (1).

The body (9) of the balancing valve (1) supports all the elements. The valve (2) is set in motion by the control means (8), such as an actuator. The measuring means (7) sends the actual hydraulic information to the processing means (10) which processes the information and transmits to the control means (8) the position of the valve (2). The processing means (10) communicate with the storage means (11) the necessary information and transmit the information to a collection system (12).

The measuring means (7), the control means (8) for positioning the valve (2) of the balancing valve (1) and the data storage means (11) are all connected to the processing means. (10) independently arranged in the balancing valve (1) and compiling, during so-called static automatic balancing, the parameters available in the data storage means (11) with the measurements collected by the measuring means ( 7) for controlling, during dynamic so-called automatic balancing, the control means (8) for positioning the valve (2) in order to maintain a constant pressure differential in the branch (4) of the hydraulic network (5) in which balancing valve (1) is installed.

The two or more known valve opening positions are chosen arbitrarily and correspond for example to 75% and 50% of the maximum opening of the equalizing valve (1).

This computational process makes it possible to evaluate the characteristic coefficient Z of the design of the hydraulic network (5).

By the same token, it corroborates architect plans with the hydraulic network (5) actually installed.

With a balancing valve 1 open at 75%, we obtain the equation: $$\mathrm{\Delta }{P}_{\mathit{pump}}={\left(Q_{\mathit{Kv}75\%}\right)}^{2}Z+{\left(\frac{Q_{\mathit{Kv}75\%}}{K{v}_{75\%}}\right)}^2$$

With a balancing valve 1 open at 50%, we obtain the equation: $$\mathrm{\Delta }{P}_{\mathit{pump}}^{\mathit{\text{'}}}={\left(Q_{\mathit{Kv}50\%}\right)}^{2}Z+{\left(\frac{Q_{\mathit{Kv}50\%}}{K{v}_{50\%}}\right)}^2$$

et donc : $$Z_{\mathit{ref}}=Z_{\mathit{circuit}}\frac{1}{{Q_{\mathit{Kv}75\%}}^2-{Q_{\mathit{Kv}50\%}}^2}\times \left[{\left(\frac{Q_{\mathit{Kv}50\%}}{K{v}_{50\%}}\right)}^2-{\left(\frac{Q_{\mathit{Kv}75\%}}{K{v}_{75\%}}\right)}^2\right]$$

However, it has been assumed that the pump (6) works at ΔP constant therefore ΔP ' _pump = ΔP _pump , therefore: $${\left(Q_{\mathit{Kv}75\%}\right)}^2{Z}_{\mathit{circuit}}+{\left(\frac{Q_{\mathit{Kv}75\%}}{K{v}_{75\%}}\right)}^2={\left(Q_{\mathit{Kv}50\%}\right)}^2{Z}_{\mathit{circuit}}+{\left(\frac{Q_{\mathit{Kv}50\%}}{K{v}_{50\%}}\right)}^2$$

and so : $$Z_{\mathit{ref}}=Z_{\mathit{circuit}}\frac{1}{{Q_{\mathit{Kv}75\%}}^2-{Q_{\mathit{Kv}50\%}}^2}\times \left[{\left(\frac{Q_{\mathit{Kv}50\%}}{K{v}_{50\%}}\right)}^2-{\left(\frac{Q_{\mathit{Kv}75\%}}{K{v}_{75\%}}\right)}^2\right]$$

This calculation is performed by the processing means (10) and the calculated value of this coefficient Z _ref characteristic of the dimensioning of the hydraulic network (5) is stored in the data storage means (11).

A predetermined value Q _set flow rate, corresponding to the estimation of the need in the branch (4) concerned, is extracted from the data storage means (11) in which it is stored.

The setpoint flow Q _setpoint is easily estimable in the new but also in the renovation.

In the new, it corresponds to architect calculations.

In the renovation, plans and documentation architect are more rare. However, an estimation of the flow rate is quantifiable by the energy requirement required by the operating temperature conditions of the thermal control elements (3), such as heating and cooling.

d'où : $$K{v}_{\mathit{consigne}}=\frac{Q_{\mathit{consigne}}}{\sqrt{Z_{\mathit{ref}}\times \left({Q^2}_{\mathit{Kv}75\%}-{Q^2}_{\mathit{consigne}}\right)+{\left(\frac{Q_{\mathit{KV}75\%}}{K{v}_{75\%}}\right)}^2}}$$

Still assuming that the hydraulic network (5) is subjected to a substantially constant pressure from the pump (6), it is possible to write the equation: $$\mathrm{\Delta }{P}_{\mathit{pump}}={\left(Q_{\mathit{Kv}75\%}\right)}^{2}Z+{\left(\frac{Q_{\mathit{Kv}75\%}}{K{v}_{75\%}}\right)}^2={\left({\mathrm{<figure-callout\; id="2"\; label="Q\; order"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">Q\; </figure-callout>}}_{\mathit{order}}\right)}^2{Z}_{\mathit{ref}}+{\left(\frac{Q_{\mathit{order}}}{K{\mathrm{<figure-callout\; id="2"\; label="v\; order"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">v\; </figure-callout>}}_{\mathit{order}}}\right)}^2$$

from where : $$K{v}_{\mathit{order}}=\frac{Q_{\mathit{order}}}{\sqrt{Z_{\mathit{ref}}\times \left({{\mathrm{<figure-callout\; id="2"\; label="Q"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">Q</figure-callout>}}^2}_{\mathit{Kv}75\%}-{{\mathrm{<figure-callout\; id="2"\; label="Q"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">Q</figure-callout>}}^2}_{\mathit{order}}\right)+{\left(\frac{Q_{\mathit{KV}75\%}}{K{v}_{75\%}}\right)}^2}}$$

The balancing valve (1) then takes into consideration the value of the characteristic coefficient of the dimensioning of the reference valve K _v setpoint.

Nevertheless, there is a difference between the set flow rate Q filled and _set the value of the actually measured flow rate Q _measured.

This shift, which must be overcome, is mainly due to the effects of the hydraulic network (5).

During a period of stabilization time, the balancing valves (1) remain in adjustment according to a tolerance interval bounded by Q _setpoint , this tolerance range can be parameterized for example at ± 5%. $${\mathit{Q}}_{\mathit{order}\mathit{-}\mathit{5}\mathit{\%}}<{\mathit{Q}}_{\mathit{measured}}<{\mathit{Q}}_{\mathit{order}+\mathit{5}\mathit{\%}}$$

This compensation is done by taking again the previous formula where Qpointsign becomes Q _measured and Q _Kv75% becomes Q _setpoint , which gives: $$K{v}_{\mathit{updated}}=\frac{Q_{\mathit{measured}}}{\sqrt{Z_{\mathit{ref}}\times \left({{\mathrm{<figure-callout\; id="2"\; label="Q"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">Q</figure-callout>}}^2}_{\mathit{order}}-{{\mathrm{<figure-callout\; id="2"\; label="Q"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">Q</figure-callout>}}^2}_{\mathit{measured}}\right)+{\left(\frac{Q_{\mathit{order}}}{K{\mathrm{<figure-callout\; id="2"\; label="v\; order"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">v\; </figure-callout>}}_{\mathit{order}}}\right)}^2}}$$

At stabilization, the coefficient K _v characteristic of the design of the balancing valve (1) and the characteristic coefficient Z of the dimensioning of the so-called "reference" hydraulic network (5) are calculated or recalculated.

These coefficients Z, K _v will be used for installation control or any other intervention on the hydraulic network (5).

At this time, the system also calculates the reference pressure differential ΔP _ref of the circuit. This ΔP _ref will be used in the so-called dynamic phase, detailed below in the text.

In this second automatic dynamic balancing phase, the assumption that the hydraulic network (5) is subjected to a substantially constant pressure differential from the pump (6) is still considered.

The equilibrium valve designers (1) provide the response or abacus diagrams related to the balancing valve (1) as shown in FIG. figure 2 .

These express the pressure differential Δ P between the output B and the inlet A of the valve 1 as a function of the flow rate Q of the fluid flowing through it. On the figure 2 , this chart corresponds to the DN32 valve model of the company COMAP ^® .

The diagonal lines represent the different adjustment positions that the valve (1) can offer. These positions are referenced on the control handle of the valve (1). Their slope is characteristic of the coefficient K _v characteristic of the design of the balancing valve (1).

This abacus requires little knowledge to be interpretable. Indeed, from the required nominal flow and differential pressure Δ P _valve, the fluid passing through the balancing valve (1) in a limb (4) of the hydraulic network (5), we can adjust the valve to balancing (1) at the required position.

For example, for a pressure differential Δ P _valve = 0.1 bar in the branch (4) and for a nominal flow required equal to 900l / h, the adjustment position of the valve 1 must be brought to position number 16 .

It is therefore necessary to adapt the opening of the valve (2) of the balancing valve (1) to the required nominal flow rate, for example when opening or closing a thermal regulation element 3, such as a radiator, and now as much as possible a constant pressure differential in the branch (4) in which the balancing valve (1) is located.

The figure 3 vectorially illustrates such adaptability according to operating conditions of a radiator (3).

When the radiator (3) closes, the flow rate Q decreases in the balancing valve (1), which causes an increase in the impedance of the hydraulic network (5) and therefore an increase in the pressure differential Δ P of the branch (4) of the hydraulic network (5).

However, the balancing valve (1) at time t is in the open position, as if the radiator 3 was in the open position. The adaptability causes a compensation of the pressure differential Δ P by a reduction of the pressure differential ΔP _valve between the output B and the input A of the balancing valve (1) at time t1.

On the figure 3 it is clear that a balancing valve (1) according to the present invention ensures that the reference pressure differential ΔP _ref of the branch (4), calculated at the end of the so-called static automatic phase, tends to remain constant regardless of the need for the hydraulic system (5).

Similarly, if the radiator (3) is to open the balancing valve (1) according to the present invention will ensure to adapt the opening of the balancing valve (1) by adjusting the position of its valve (2 ), in this case by opening more.

The figure 4 illustrates the closure of a radiator (3) on the abacus of the figure 2 .

In this case, the flow Q in the branch (4) decreases so the balancing valve (1) tends to close.

On this same figure 4 , the position of the valve before taking the measurement was P16.

At the measurement, the user closes the radiator (3), which amounts to a flow rate drop Q in the branch (4). In this case, the flow rate Q goes from 900 l / h to 270 l / h. Thus, on the chart a modification of the pressure differential ΔP _valve of the equilibration valve (1) appears in view of the formula: $$\mathrm{\Delta }{P}_{\mathit{circuitdérivé}}={\left(\mathrm{<figure-callout\; id="2"\; label="Q"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">Q</figure-callout>}\right)}^2{Z}_{\mathit{ref}}+{\left(\frac{Q}{K<figure-callout\; id="2"\; label="\; v\; ref"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">\; </figure-callout>v_{\mathit{ref}}{\mathit{}}_{}}\right)}^2\cdot$$

The present invention comes compare Δ Δ P _ref and P at time of measurement, and corrects the setting position of the balancing valve (1), in this case the balancing valve (1) moves from the position P16 at position P8. Thus the balancing valve (1) is adjusted to the flow rate Q corresponding to the need.

By the same calculation process, the balancing valve (1) can take a higher position in the case where the flow increases following the opening of the radiator (3).

Thus, the balancing valve (1) is flexible, autonomous and adapts at every moment to the needs of the hydraulic network (5).

In addition, the latter operates with a single input data, the setpoint flow Q _setpoint is either estimated in the nine by the architect data, or in the renovation corresponding to estimated data of old maintenance or obtained by estimation of a simple software delivered by the company COMAP ^® .

This balancing valve (1) is easy to use, accessible to all and saves time during installation and money throughout its life cycle.

Beyond, its balancing function such a balancing valve (1) will make the control or maintenance of hydraulic network installation (5).

Although the invention has been described in connection with particular examples of embodiment and implementation, it is obvious that it is in no way limited and that it includes all the technical equivalents of the means described and their combinations.

Claims (14)

Balancing valve (1) with flap (2) having an inlet (A) and an outlet (B), mounted downstream of a thermal regulating element (3) integrated in a branch (4) of a hydraulic network (5) subjected to a pressure (Δ P ) substantially constant, characterized in that it comprises: measuring means (7) for a characteristic quantity of the fluid flowing through the balancing valve (1), control means (8) for positioning the valve (2) of the balancing valve (1), data storage means (11) in which intrinsic and extrinsic parameters of the balancing valve (1) are stored, - Independent processing means (10) arranged to perform automatic balancing, in the branch (4) from the values of the characteristic quantity of the fluid measured by the measuring means (7), control means (8) and data stored in the storage means (11). Balancing valve (1) according to claim 1, wherein the processing means (10) allows a so-called static balancing in which the parameters available in the data storage means (11) are compiled with the measurements collected by the means measuring device (7) in order to obtain characteristic reference values of the hydraulic network (5). Balancing valve (1) according to one of claims 1 or 2, wherein the processing means (10) allow dynamic balancing in which reference values, preferably those determined in claim 2, are used for controlling the control means (8) for positioning the valve (2) in such a way as to maintain a pressure differential or a flow rate that is substantially constant in the branch of the hydraulic network (Δ P ) in which the balancing valve (1 ) is installed. Balancing valve (1) according to one of claims 1 to 3 wherein the processing means (10) allow to exchange and modify balancing data for adaptation purposes, diagnosis of the entire network hydraulic (5). Balancing valve (1) according to one of claims 1 to 4, wherein the measured characteristic quantity of the fluid passing through the balancing valve (1) relates to its flow (Q). Balancing valve (1) according to claim 5, wherein the intrinsic parameters of the balancing valve (1) supplied by its manufacturer represent the pressure variation (ΔP _valve ) between the inlet and the outlet of the valve of balancing (1) as a function of the flow (Q) for a given position of the valve (2) of the balancing valve (1). Balancing valve (1) according to claim 6, wherein during the static balancing, the processing means (10) calculate the reference characteristic coefficient (Z _ref ) of the dimensioning of the hydraulic network (5) considered in function : - two or more flow rate values (Q _{Kv 75%} , Q _{Kv 50%} ) determined for two or more positions (P _75% , P _50% ) of the valve (2) different, and - corresponding values of the characteristic coefficients of the dimensioning (Kv _75% , Kv _50% ) of the balancing valve (1) deduced from the pressure differentials (ΔP _valve ) given by the intrinsic parameters of the balancing valve (1) . Balancing valve (1) according to one of Claims 1 to 7, in which the extrinsic parameters of the balancing valve (1) comprise a setpoint value (Q _setpoint ) of the flow of the balancing valve (1). ) corresponding to the estimate of the need for a thermal regulation element (3) in a branch (4) concerned of the hydraulic network (5), such as a radiator (3) or a fan coil. Balancing valve (1) according to claim 8, wherein the setpoint value (Q _setpoint ) of the flow rate is programmable in the data storage means (11) of the balancing valve (1). Balancing valve (1) according to one of claims 8 to 9, provided that claim 6 is dependent on claim 5, wherein during the static balancing, the processing means (10) calculate an updated value (Kv _reactualized ) for the characteristic coefficient of dimensioning (Kv) of the valve according to: from the measured flow rate (Q _measured ) to the position of the valve corresponding to the setpoint value (Q _setpoint ) of the flow rate given by the intrinsic hydraulic characteristics of the valve, the reference flow rate (Q _setpoint ) and its characteristic coefficient of dimensioning (Kv _setpoint ) of the corresponding balancing valve (1), and - the reference characteristic coefficient of the dimensioning of the hydraulic network (Z _ref ). Balancing valve (1) according to claim 10, wherein during the static balancing, the processing means (10) calculate a reference pressure differential (ΔP _ref ) of the branch (4) of the hydraulic network ( 5) with a coefficient characteristic of the dimensioning of the updated valve (Kv _updated ) from the formula: $$\mathrm{\Delta }{P}_{\mathit{ref}}={\left(\frac{Q_{\mathit{measured}}}{K_{v_{\mathit{updated}}}}\right)}^2$$

Balancing valve (1) according to claim 11, wherein during the dynamic balancing, the processing means (10) act on the control means (8) of the positioning of the valve (2) with the aid of an actuator for maintaining a substantially constant reference pressure variation (ΔP _ref ) in the branch (4) of the network (5), whatever the need of the hydraulic network (5). Automatic static balancing process for the hydraulic conditions of one or more thermal regulation elements (3) integrated into a branch (4) of a hydraulic network (5) subjected to a substantially constant pressure differential (ΔP) comprising a balancing valve (1) according to one of claims 1 to 12 characterized in that it comprises in this order the steps of: extracting data storage means (11) from a flow setpoint value (Q _setpoint ), calibrating the balancing valve (1) by determining the flows for two or more known positions of the valve (2) of the balancing valve (1) respectively corresponding to two characteristic coefficients of the valve (1), for example to 75% and 50% of the maximum opening of the valve (1), - calculate the coefficient (Z _ref ) characteristic of the design of the hydraulic network (5) and the characteristic coefficient of the dimensioning (Kv _setpoint ) of the corresponding balancing valve (1), - position the valve (2) of the valve (1) in its position corresponding to the calculated value, - determine the flow rate (Q _measured ), if the determined flow rate ( _measured Q) is within a value range determined for example at plus or minus 5% of the value of the reference flow rate (Q _setpoint ), then: the value of the setpoint flow (Q _setpoint ) is replaced by the value of the determined flowrate (Q _measured ), the characteristic coefficient of the dimensioning (Kv _setpoint ) of the balancing valve (1) corresponding to the coefficient (Z _ref ) characteristic of the design of the hydraulic network (5) becomes the coefficient (Kv _ref ) characteristic of the reference dimensioning, and - the reference pressure differential (ΔP _ref ) of a branch (4) of the hydraulic network (5) is calculated from the characteristic coefficient of the reference dimensioning (Kv _ref ) and the determined flow rate (Q _measured ), otherwise: - Go back to the step of calculating the coefficient (Z _ref ) characteristic of the dimensioning of the hydraulic network (5) and the coefficient (Kv _setpoint ) characteristic of the dimensioning of the balancing equilibrium valve (1) corresponding. Process for automatically balancing said dynamic input pressure of one or more thermal regulation elements (3) integrated in a branch (4) of a hydraulic network (5) subjected to a differential pressure (ΔP) substantially constant comprising a balancing valve (1) according to one of claims 1 to 12, characterized in that it comprises in this order the steps of: - waiting after a first determined time (t1) the stabilization of the flow of the fluid through the balancing valve (1), this time being parameterizable and preferably equal to 30 minutes, - determine the flow rate (Q), deduce the pressure differential (ΔP), if the pressure differential (ΔP) is within a range of values determined for example at plus or minus 5% of the value of the reference pressure differential (ΔP _ref ): returning to the first step of waiting after a first determined time (t1), if not : calculating the coefficient (Z) characteristic of the dimensioning of the hydraulic network (5) and the coefficient (Kv) characteristic of the dimensioning of the corresponding balancing valve (1), - position the valve (2) of the balancing valve (1) in its position corresponding to the coefficient (Kv) characteristic of the design of the balancing valve (1), - Wait after a second time determined and then return to the beginning of this step, this time being configurable for example equal to five minutes.

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