WO2010057957A1 - Thermostatic valve having an impeller - Google Patents

Abstract

The thermostatic valve (1), housed in a bulb (9), includes a needle (2) for regulating the flow of air-conditioning water, inserted between a flow inlet channel (3) and a flow outlet channel (4), and includes radio circuits (83) for receiving temperature control commands, said circuits being connected to a block (84) for controlling the needle (2), and it includes a centrifugal or centripetal impeller (5) connected between the channels (3, 4), an output shaft (52) of said impeller driving a current generator (6) supplying the radio circuits (83) and the control block (84).

Description

 Thermostatic valve with turbine

1. Field of the invention

The invention relates to thermostatic valves regulating the temperature of a radiator.

2. Prior Art

A thermostatic valve, or thermostat, forms a bulb mounted according to a series connection on the pipe supplying a radiator in hot water from a boiler whose pump can provide a certain flow. A needle valve regulates the flow rate of the hot water flow by throttling the passage in the valve body. The needle is pushed in sliding, by screwing a cap of the bulb pushing a return spring, to the chosen setpoint position. In addition, the bulb contains a temperature sensor and actuator, of bimetallic kind, which modulates the position of the needle, to advance or retreat relative to the set position, depending on whether the ambient temperature is higher or lower than the setpoint.

This prior art has been perfected. It has indeed appeared thermostatic valves in which the above temperature sensor no longer provides the actuator function because it is remote from the bulb and replaced by a remote control receiver which controls an electric actuator controlling the needle. The sensor, associated with a control remote control transmitter at a set temperature, can thus be placed at a distance from the radiator, in order to effectively measure the ambient air temperature of the room, since the remote sensor is no longer subjected to influence of hot spots that constitute the radiator and its supply pipe. 3. Disadvantages of prior art

The thermostatic valve, initially purely mechanical, has thus become electromechanical, so that it is necessary to provide a power source. We can think of feeding it by the sector, but it requires the installation of a cable, and therefore involves a certain cost. Indeed, the power outlets connected to the sector are almost never present in the immediate vicinity of a radiator.

Classically, this function is provided by a battery, which must be replaced periodically. However, in the absence of a remaining charge tester, the user can not determine when to replace that battery. Either he replaces it at a fixed period, if he thinks of it, or he expects the breakdown. In the first case, it will replace a battery that could still serve some time, and in the second case, the radiator is no longer regulated during the duration of the failure. The user must then periodically test the temperature of the radiator to try to determine if this temperature seems to him in agreement with the difference between the ambient temperature and the set temperature, that is to say if its comfort still seems to him assured. Specifically, if the user has a feeling of coldness in the ambient air when he has set the set temperature, he should normally find that the radiator is hot, that is to say that the chain of Servo remote control execution is still functional.

It is understood that such checks are tedious and approximate, that is to say that the state of failure may be detected after several days. This situation can therefore affect the comfort and possibly the health of the occupants of the room, especially if the lack of power immobilizes the needle in the close position. Conversely, immobilization in the open position will cause unnecessary consumption of calories, with further discomfort caused by overheated room. 4. Objectives of the invention

The present invention aims to provide a more user-friendly solution to maintain a power source, by avoiding the problem of monitoring the status of a battery.

It will be noted that, if the invention actually originates from the above problem of supplying an electric circuit for controlling a thermostatic valve, the solution provided by the invention goes beyond the solution of the particular problem exhibited. above, because the invention aims to allow to supply any electrical circuit, whether or not involved in the temperature control function.

More generally, the invention aims to provide local energy kinetic, which can be used in various ways, for example to move any led member, or to produce electric current by relative displacement between an inductor and an armature, for example by rotating a rotor.

5. Essential characteristics of the invention

For this purpose, the present invention relates first of all to a thermostatic valve comprising means for throttling a liquid flow to be regulated, inserted between an inlet channel and a flow starting channel intended to be inserted into a supply pipe for an air-conditioning radiator, valve characterized in that it comprises a turbine, connected between said channels and comprising means for driving a driven member.

The invention is equally applicable to a refrigeration radiator as a heating radiator, since the invention is independent of any thermal aspect at this level. The turbine is thus coupled to the pump, the boiler or a refrigeration system, through the flow of water that it sets in motion, and the turbine can thus recover some of the mechanical energy that the pump transmitted to water. In other words, it is thus possible to constitute a chain of energy transmission, formed by: the electrical network, the pump that it supplies, which translates the electric current that it receives into a kinetic energy transformed into hydraulic energy of the flow of water, the pipe for the flow of water, the valve according to the invention, the turbine of which recovers a part of the hydraulic energy of the particles of the water flow to restore it in the form of mechanical energy readily available on an output shaft or as a rotating magnetic field.

It is therefore a hydraulic connection that connects the upstream motor element, that is to say the pump, to the downstream motor element that constitutes the turbine, and deported relative to the upstream motor element. The interest of such a means of offset is conceivable since a hydraulic connection is largely free from any constraint of shape of the path.

It is then easy to connect to the output shaft, or equivalent, of the turbine to drive any desired driven member, and in particular a power generator of any electrical circuit provided, for example the control means of a needle or equivalent.

In such a case, the generator thus constitutes a final link in the above motor chain, that is to say that, overall, it is the power grid current that is deported to the valve, through the hydraulic circuit, with the transformation, intermediate and temporary on the section "transport", into a kinetic energy of water flow. The turbine and the generator thus constitute, with respect to the functions of the pump and the mains network, elements with inverse functions, which thus makes it possible to restore the physical quantities of departure, that is to say the mechanical energy but also electrical energy. It will therefore be noted that the first result of the invention is to supply mechanical energy through its output means, to drive a driven member. A second result is that one can for example electrically feed circuits if the driven member is a generator. Thus, it is interesting that the turbine is integrated, in a bulb, with the driven member, consisting of a current generator.

In the main application targeted, the current generator is provided for supplying means for receiving temperature control commands connected to control means of the throttling means. This achieves the original goal of electrical autonomy of the temperature control circuits.

Advantageously, the turbine is of the type of radial, centrifugal or centripetal water flow, the inlet channel or respectively the starting channel, opening, on the turbine side, by an internal arrival section, respectively starting, which occupies an axial position with respect to a geometrical axis of rotation of the turbine.

In this case, it is interesting that the starting channel comprises an internal starting section comprising a sleeve surrounding the internal arrival section.

The connection is very compact. It may in particular be of mechanically compatible section with a conventional fitting, so that the valve according to the invention can be substituted for a conventional valve, in the context, for example, of renovation work.

Advantageously, a wheel of the turbine has buckets whose radially outer edge zone has a direction of extension substantially axial with respect to the geometric axis, continuing with a return channel directed obliquely towards the geometric axis to join the internal stretch of departure.

The incident flux is thus returned after a reversal of approximately 180 degrees, which corresponds to an optimum of efficiency since the variation of the momentum of the particles of the incident flux, and thus the transfer of kinetic energy, corresponds to the difference vector of two speed vectors opposite meanings. In other words, the efficiency is optimal if the distance between the two vertices of two vectors of the same amplitude is maximum, that is to say when they are exactly aligned and in opposite directions.

Such a turbine therefore has characteristics of compactness and efficiency that depend only on the geometry of the various arrival and return channels or departure, and the geometry of the buckets. It is therefore conceivable that such a turbine, whose structure is independent of the downstream kinematic chain that it controls, can be used in applications other than the present heating application. It can be provided that the two inner sections are parallel to a direction of a given geometric axis, perpendicular to an extension direction of any one of the two outer sections, the other outer section extending in one direction. any of the two said directions.

There are thus several possibilities of connection to the pipe, which can be straight or have an elbow.

Preferably, the turbine and the generator occupy staggered positions axially along said geometric axis of rotation, the generator being housed in a removable cap at the free end of the bulb. It is thus possible to limit the flooded area, containing the turbine, relative to the rest and thus allow the change of hood without purging or removing the installation.

The throttling means can be of various types, for example a butterfly pivotally mounted about an axis transverse to the channel in question or a curtain blade, movable in rectilinear or circular translation in its plane, to come shear the flow. However, in an interesting embodiment, the throttling means comprise a pin mounted sliding along said geometrical axis and having a front surface with a substantially conical lateral profile, for radially deflecting an incoming flow coming from the internal arrival section. . The needle thus has a dual function, which reduces the volume of material accordingly. It can further be provided that the inner arrival section has an outlet mouth provided with a deflector guiding the incoming flow.

The flow is thus better guided and oriented and is therefore more efficient.

According to an interesting embodiment, a rear section of the needle is slidably mounted in a sleeve constituting said drive means, the sleeve being housed in an axial passage of a flow containment bulkhead.

The set of elements is therefore coaxial, which simplifies the structure.

It can be provided that a radially outer surface of the sleeve constituting the drive means is carried by a bearing housed in the passage of the partition.

The sleeve is thus multifunctional.

It is interesting that the needle is angularly coupled with the turbine.

This limits the wear of the joints provided, since the needle does not have an angular relative speed with respect to the wheel of the turbine.

The turbine may be associated with an adjustable water injection device.

It is thus possible to adjust the driving power of the turbine as needed.

In an interesting embodiment, the injection device comprises two sheets of material facing and mutually movable to occupy several predetermined relative positions, a first sheet having a plurality of injection nozzles and a second sheet having size lights. and arrangements arranged to unmask a variable number of nozzles when one of the sheets passes from one said position to another. There can be provided an adjustment motor of the injection device.

The valve may also include a set of rotational speed measurement of the turbine.

It is advantageous for the valve to be provided with a coupling comprising a shut-off valve arranged to take an intermediate position allowing passage, between the inlet channel and the starting channel, of a jet of sweeping water a front surface of an access control filter to an internal arrival section belonging to the arrival channel.

In an interesting embodiment, the valve comprises connection circuits with a central management unit of an installation comprising a plurality of at least one said valve, connecting circuits arranged to transmit to the central unit data entered locally. and to receive feedback commands from an actuator of a water flow control member.

The invention also relates to a local data transmission network comprising a plurality of at least one valve according to the invention, and a central management unit comprising connecting means arranged to transmit to the at least one valve, through the connection circuits, said control commands of an actuator of a water flow control member.

The central unit may be arranged to a) receive measurements from a set of rotational speed measurement of the turbine constituting said data entered locally, b) comparing a value thus measured with a flow setpoint value commissioning a radiator associated with the valve in question, and c) generate and send back, a said control command to adjust a pressure drop.

6. List of figures

Other characteristics and advantages of the invention will appear more clearly on reading the following description of a preferred embodiment of a thermostatic valve according to the invention, and alternatively presented as a simple example. illustrative and non-limiting, with reference to the accompanying drawings, in which:

FIG. 1 is a schematic view of an air-conditioning installation, here heating by hot water distribution loops connecting a boiler to radiators provided with a thermostatic valve according to the invention, FIG. 2 is a schematic axial sectional view of the thermostatic valve,

FIG. 3 is a detailed view of the valve in axial section, with a drive turbine of a current generator supplying servocontrollers, battery charging and radio communication circuits; FIG. sectional view illustrating a T-connection, connection to the pipe,

FIG. 5, formed from FIGS. 5A, 5B and 5C, in axial sectional views, illustrates three types of connection connections of the valve to the pipeline of the loop,

FIG. 6, formed from FIGS. 6A and 6B, shows the wheel of the turbine, respectively in front view from its axis, and in axial lateral section, and

FIG. 7 shows the elements of FIG. 3, except for a cover and the electrical circuits and the stator of the generator which it carried, which are replaced by only a conventional mechanical needle control cover,

- Figure 8 is an axial sectional view of a variant of the valve Figure 3, centripetal turbine fed tangentially and through a controlled injector, adjusting the incident flow,

FIG. 9 is a perspective view of the turbine FIG. 8,

- Figure 10 is a developed view, very schematic, two cylindrical rings coaxial and superimposed, providing injection, mutually angularly movable to ensure the flow control,

FIG. 11 is a variant of the assembly of FIG. 10, the rings being mutually axially movable,

FIG. 12 is a diagrammatic view in axial section of a mechanism for adjusting the angular position of one of the rings, able to operate as part of a local network for managing said valves in the heating installation. , and

- Figures 13, 14 and 15 are views in axial section illustrating a said T-fitting, having a 3-way valve, shown in different angular positions. 7. Description of the preferred embodiment of the invention

FIG. 1 schematically represents an installation for heating an apartment by a loop distribution of hot water coming from a boiler 100. The distribution circuit comprises a starting pipe 101 and a return pipe 102 between which are connected radiators 200 and 300 in parallel. Specifically, an upstream section of the starting pipe 101 comprises a regulator 103 with a looping pipe 104 ensuring at least a certain flow rate in the overall loop when thermostatic controllers or valves 1, 301 of the radiators 200 and 300 are in the state closed, that is to say with upstream loopback lines 203 and downstream or return 204, respectively 303 and 304, having no flow. The thermostatic valves 1, 301, which are identical, are controlled by radio by respective room temperature sensors 205, 305. FIG. 2 illustrates the structure of the thermostatic valve 1.

The valve 1 essentially comprises four functional slices, namely a base slice, constituted by a hydraulic connection 34, followed by first, second and third stages containing the active components of the valve.

1, housed in a globally cylindrical bulb 9 around a general geometric axis 10 which is also the axis of rotation of a turbine 5.

The connection 34 captures the flow of water from the upstream pipe 203 and injects it into the first stage of the bulb 9 containing a flux regulating needle 2 and the turbine 5. The second stage contains a current generator 6 driven by the turbine 5 for supplying, in the third stage, a set 8 of electric control circuits servocontrol the needle 2.

The connection 34 is inserted at the outlet of the upstream pipe 203 to divert the flow inward of the thermostatic valve 1 by an inlet channel 3 and return it to the return pipe 204 by a starting channel 4.

FIG. 3 is an axial sectional view of the thermostatic valve 1, the connection 34 being represented in full in FIG. 4. FIG. schematically three possible types of forms of the connector 34 and Figure 6 shows a wheel 50 of the turbine 5. In the present description, the axial and radial directions refer to the general axis 10, unless otherwise indicated or evidence. Description of fitting 34.

Referring first to FIG. 4, the connection 34 comprises two parts, namely an arrival channel 3 and a departure channel 4. The arrival channel 3 comprises an upstream section, or an external arrival section, 31, direction of extension or geometric axis of arrival 30, constituting the extension of the upstream pipe 203 in the direction thereof, and, after a right angle bend, a downstream section, or internal arrival section , 32, of geometric axis or direction of internal extension of arrival 39 which is here co linear with the geometric axis 10 of the bulb 9.

The starting channel 4 comprises a downstream section, or outgoing external section, 41, direction of extension or departure geometric axis 40, here collinear with the direction of arrival 30, thus constituting the extension of the upstream pipe 203 according to therefore the direction of it. Before a right-angle bend, the starting channel 4 comprises an upstream section, or internal starting section, 42, with a geometric axis or a starting internal extension direction 49 which is colinear with the direction of internal extension. 39 and therefore also with the geometric axis 10 of the bulb 9. The internal start section 42 comprises a sleeve surrounding, coaxially, the internal arrival section 32. Description of the turbine 5.

As shown in FIGS. 3 and 6, the turbine 5 is of the centrifugal type, since the inlet channel 3 opens, via the internal arrival section 32, at an axial position relative to the geometric axis 10 of rotation of the the turbine 5. The jet of the stream of water coming from the inner arrival section 32 is projected on a deflector to impart on its trajectory, initially in axial direction and in central position, a radial component in order to reach blades 51 of the wheel 50 of the turbine 5, and then to be evacuated peripherally by the centrifugal force. The blades 51, N = 8 in this case (FIG. 6), extend in a spiral direction of extension. obliquely in the opposite direction to that of the rotation of the turbine 5 (arrow F5). If we consider a water particle, it is projected by the deflector in a predetermined direction, purely or partially radial. For an optimal coupling to a blade 51, that is to say a maximum transfer of momentum and therefore of kinetic energy, it is necessary that the blade 51 constitutes an obstacle along the radial trajectory of the particle d water, that is to say over the entire radius of the turbine 5. This avoids having to design the mechanism for percussion of the particle to occur over a very limited radial length, which would cause disturbances flow and therefore poor performance. Due to the rotation of the wheel 50 and the angularly curved shape behind the blades 51, the blade 51 considered has a current contact point, with the water particle, whose position slides radially outwards, of by the radial component of velocity of the particle. During the same radial travel time, the blade 51 rotates at a certain angle, that is to say that, if it were rectilinear and radial, it would tend to escape the path of the water particle. It is therefore the curvature towards the rear (FIG. 6) of the blade 51 which makes it possible to compensate for this "evasion". It will be understood that, for a predetermined radial velocity of the water particle, there is a rotational speed for which the contact point will run over the entire radial length of the blade 51. To provide an increased range of operating speed, the radially outer portion of each blade 51 may have an angular span greater than 360 / N degrees, i.e. a rear edge portion of the blade 51 extends angularly behind a leading edge portion of the blade 51 next. A gutter shape also allows to channel, over the entire length of the blade 51, the flow of water incident.

FIG. 3 shows that the blades 51 are integral with a hub of the wheel 50, forming a sleeve 52 constituting an output shaft, in which is mounted axially sliding a rear section 24 of the needle 2, a head 21 of which has a surface substantially conical frontal 22 oriented axis 10, facing the outlet of the inner arrival section 32. Except the nose area which is more pointed, the angle of conicity is about twice 55 degrees, so that the arrival incident flow tends to be deflected in a radial direction towards the blades 51, with a speed vector retaining however initially an axial component to the front of the bulb 9, that is to say the opposite of the connection 34, this to optimize the coupling.

The internal arrival section 32 has an outlet mouth provided with a deflector 33, funnel generally conical divergent guide the radially deflected arrival stream. Specifically, a frontal zone of the flow of arrival is guided by abutment on the frontal surface 22 and then on the blades 51 and a posterior zone of the flow is guided by the deflector 33, the assembly thus constituting an arrival channel 35 applying a external radial component deflection. The blades 51 have the particularity of having a very marked hollow shape, bucket 55 with a generally radial extension.

Thus, the trough 55 has a radially internal inlet surface 56 located in the extension of the front surface 22 and which is thus partially turned towards the connection 34 and radially outwardly. A radially outer outlet surface 57 is also partly turned towards the connection 34 but also radially towards the general axis 10. In particular, it is seen that a radially outer edge zone 58, where the starting flow leaves contact with the outlet surface 57, is substantially axially oriented. As a result, the starting stream, leaving the buckets 55 to return to the fitting 34, has a large axial velocity component to the fitting 34. It may even be provided that the radially outer edge zone 58 is partially folded towards the coupling 34. general axis 10. To return to the general axis 10 and enter the inner internal portion 42 in the sleeve, the return flow is guided in a return channel 45 constituted by a rear surface of the deflector 33 and a guide surface The return channel 45 is here substantially parallel to the inlet channel 35, with an inclination of about 55 degrees on the general axis 10. The bucket 55 thus forms a trough in the form of a trough. torso chistera. It can also be expected that the front surface 22 has a divergent beam of ribs 23 extending radially spirally in the direction of rotation F5 (Figure 6) to further deflect the incoming flow circularly. Precisely, this makes it possible to increase the circular component of the momentum of the water and thus to increase the hydraulic coupling efficiency water / blades 51.

Note that, alternatively, the turbine 5 may be centripetal type, so with a reversal of the direction of the water path, and therefore a permutation of associated names, such as "arrival" and "departure" or other. The sleeve or hub 52 is housed in an axial passage 94 of a substantially radial watertight septum 93 for confining water, while a cylindrical, radially external support surface of the sleeve 52 is carried by a ring bearing. 95 housed in the passage 94. Two O-rings 25 seal between the cylindrical side surface of the needle 2 and the inner surface of the sleeve 52, and likewise the bearing 95 is of tight type. The second stage is thus "in the open air", and precisely housed, with the third stage, in a removable cap 92 mounted on the bulb body 91.

The needle 2 could be mounted in a fixed angular position, that is to say indexed on the body 91 of the bulb 9 containing the first stage. However, here it is mounted angularly indexed on the sleeve 52, that is to say that the needle 2 is part of the wheel 50 and therefore rotates. The seals 25 are then subjected to no rotational friction, which would represent a wear greater by several orders of magnitude than that due to sliding friction, which is only episodic and at low speed. In addition, a corresponding loss of efficiency is avoided. The second floor contains the generator 6, housed in the removable hood

92 at the free end of the bulb 9. The generator 6 can be removably connected to the drive shaft-shaft 52.

The generator 6 comprises a stator 61 associated with a rotor 62 comprising an inductor 63 in the form of permanent magnets, alternating poles, carried by a hub 64 mounted on the shaft-sleeve 52 and angularly coupled by a coupling rib 53 thereof. The stator 61 comprises a coil which is excited by the alternating magnetic field induced by the rotation of the rotor 62.

The electric current thus generated feeds the circuit assembly 8, by the charging of a battery 81 for supplying a set 82 of electrical or electronic circuits, in particular circuits 83, here radio, for receiving commands from temperature control. The radio circuits 83 thus control, by output signals, an electronic control unit 84 for controlling the needle 2 through an electromechanical actuator in the form of a stepper motor 85, for controlling the incoming water flow, by " "throttling" of the outlet mouth of the inner arrival section 31, this constriction here being a front closure.

Figure 5 illustrates three types of connection 34.

FIG. 5A corresponds to the case of FIG. 3, that is to say that the connection 34 forms a T with a vertical bar along the general axis 10 and whose two branches, on the left and on the right, correspond to the directions 30 and 40 of the arrival and departure channels 4 and 4 respectively. The incoming stream is captured in a central passage of reduced section, representing a downstream section of the outer arrival section 31, then passing a bend of arriving at a right angle and reach the internal arrival section 32, here of the same section, oriented on the general axis 10. The internal starting section 42 forms the indicated sleeve around it and joins the outer outboard section 41 , after a starting elbow at right angles.

It will be noted that the downstream section above the outer arrival section 31 and that of the inner arrival section 32 can be increased to limit the pressure drop, and the bends can be rounded. It is thus possible to expand the drawing in the connection area of the top of the central branch of the T with the branches, this expansion being able to be in the horizontal direction of the directions 30, 40 of the branches and / or in the vertical direction (general axis 10).

In the first case, the connection to the branches taking place over an increased length thereof, the cross section of the inner sections 32, 42 is no longer circular but is elongated substantially in a rectangle, horizontal on Figure 5A, that is to say that it is a three-dimensional shape widened funnel, somewhat flattened in the direction 30, 40 of the branches, to be connected to said increased length. The flow of the sections thus expanded is reconcentrated by the top of the funnel shape constituting the outlet of the internal arrival section 32, thereby restoring a sufficient speed for driving the turbine 5.

Similarly, while the lateral detection bypass constituted by the inner sections 32 and 42 only concerns a portion, here lower in the drawing, of the periphery of the two branches, it is also possible to increase the lateral catching area, that is to say, the top of the trunk of the T, by increasing the section of the inner sections 32, 42 in a direction substantially perpendicular to the plane of Figure 5A. Exposed otherwise, the increased volume of the inner sections 32, 42 can be defined as the volume swept them by turning an angle around the directions 30, 40 branches. This would define a virtual volume funnel virtual summit centered on the axis 30, 40 of the branches and having a vertex angle corresponding to the virtual rotation described above. Moreover, it is conceivable that, in the various embodiments here exposed, the various directions or axes 10, 30, 40 are not necessarily parallel or perpendicular, that is to say that all angles are possible, in the as each component finds its place.

FIG. 5B differs from FIG. 5A in that the positions of the start channel 4 and of the general axis 10 have been permuted, that is to say that it is the starting channel 4 which constitutes the trunk T. The arrival elbow is omitted and the axes 10 and 30 are thus co-linear, so that the pressure drop to the turbine 5 is less. As explained above, the right branch, representing the inner sections of the channels 3 and 4, may be of increased cross section, circular or not, and the top of the trunk of the T, that is to say the outer portion of 41, can be expanded in the plane of Figure 5B, that is to say in the common direction 10 and 30. FIG. 5C differs from FIG. 5B in that the general direction 10 is now collinear with the direction 40 of the starting channel 4, that is to say that it is the arrival channel 3 which constitutes the trunk T. The inward coupling is identical to that of FIG. 5A. Initially, the flow retains its direction in the directional departure channel 40, and the external arrival section 31, of axis 30, constitutes a slight radial obstacle in this starting flow. Again, or may expect to expand the elements.

Thus, in the three cases of FIG. 5, the two internal sections 32, 42 are parallel to the direction of the general axis 10, which is perpendicular to an extension direction 30, 40 of any one of the two sections external 31, 41, while the other outer portion 41, 31 extends in either of said two directions 10 and 30 or 40.

The electrical circuits 82 can thus operate in autarky, as regards the power supply, and receive remote controls by radio so that a slide rod 86, angularly coupled to the rotor of the rotary step motor 85, moves the needle 2 until at a desired axial position, depending on the temperature difference observed by the electronic unit 84 (or by an equivalent block of the remote sensor) between the setpoint temperature and the measured current temperature. The set temperature may have been provided by a radio signal or by a local sensor measuring, for example, a degree of screwing of the cap 92, or the position of a potentiometer. Specifically, the slide rod 86 has a threaded shank housed in a tapping of a fixed sleeve or nut 87, so that the rotation of the slide rod 87, in one direction or the other, causes an axial advance movement. or its retreat thereof and thus also the needle 2, to ensure the desired servocontrol. To allow its sliding, the slide rod 86 can be slidably mounted axially on the rotor, with a male lateral relief, such as a finger, or female which couples it in rotation with the rotor. As a variant, the entire stepping motor 85 is slidably mounted on an inner wall of the cover 92. A helical spring 26, in axial position, bears on the end free, before, of the shaft-sleeve 52 to bias forward a cup-shaped tip secured to the front end of the needle 2, opposite the head 21. Note that the spring 26 is optional if the rod slide 86 is secured to the cup of the front end of the needle 2. There may be provided a battery charge level monitoring circuit 81, for example a circuit which temporarily connects a determined resistance to ensure a certain flow, for example, one tenth of the nominal flow rate In, in order to avoid carrying out an empty measurement, which may not represent the remaining charge. The battery voltage is then measured, numerically or analogically, and compared with a low threshold value. If it passes below the threshold, this means that the needle 2 has remained for a certain time in the closed position, for example in summer. The electronic control unit 84 can then command to open the internal arrival section 32 by a temporary recoil of the needle 2, to restart the turbine 5 for a predetermined time or even until reaching a high threshold of load of the battery 81.

It can also be provided circuits for standby and wake up at least the electronic control unit 84, to limit the average consumption. The reception of a remote control can then control the circuits of standby and wake up so that they wake up the electronic control unit 84. Figure 7 shows that it is possible to remove the assembly constituted by the hood

92 carrying the assembly 8 of electrical circuits and the stator 61 of the generator 6, to replace it with a conventional hood 92A, said site, to screw on the body 91 to manually adjust the axial position of the needle 2 against the restoring force of the spring 26 forwards. It is thus possible to mount the electrical circuitry 8 after the end of a construction site, thus avoiding any risk of damage or theft.

This presentation is an embodiment considered optimal in terms of performance and compactness. There are also other embodiments, for example with a different connection of the connectors 34. In particular, the arrival and departure channels may not be concentric, but be totally disjointed. Similarly, the derivation to the turbine 5 may be only partial, and then the needle head 21 will be housed directly in the pipe in question, with a conventional profile.

For example, it is possible to directly insert the bulb in the pipe concerned, by cutting a section of it. In such a case, if it is still possible to access the electrical circuits, only the turbine 5 will be housed in the inserted section and its output shaft will pass through a passage of the wall of the body 91 of the bulb 9 then modified, possibly after a return. An angle of 90 degrees if the pipe in question does not have an elbow that would allow live exit. Thus having a motor shaft in the open air, it is then free to arrange the generator 6 at any desired location, for example in the hood 92 radial direction relative to the direction 30, 40 of the pipe. Example of dimensioning values With regard to the electrical dimensioning, the power of the circulating pump of the boiler being for example 50 W, with a yield of 25%, it thus has a hydraulic power of 12.5 W .

The maximum hydraulic power taken by each valve 1 is for example set at 0.08 W, which takes a maximum of 0.8 W on an installation of 10 radiators. The mechanical / electrical conversion efficiency of the turbine 5 and the generator 6 is 60%, which results in a maximum useful power of 0.048 W. Thus, for example, there is 16 mA at 3 volts after rectification. It is thus possible to provide two batteries of 80 mA.h in series, whose charging time will be 5 hours.

With regard to the mechanical dimensioning, the bulb 9 of this particular example has a diameter of about 45 millimeters for a length of about 50 mm. The trunk of the connector 34 has an outer diameter of about 25 mm and the branches are of a similar diameter (Figure 4). The diameter of the inner inlet section 32 is about 7 mm and the diameter of the inner start section 42 is about 13 mm for the "wet" wall surface limiting the flow radially outer side, with an inner diameter 10 mm for the "wet" wall surface limiting the flow radially inner side. The section of the internal arrival section 32 is thus 49 × π / 4 mm 2 and that of the internal starting section 42 is (169-100) x π / 4 mm ² = 69 × π / 4 mm ² . The internal arrival section 32 is thus doubly favored with respect to the internal starting section 42, by, on the one hand, an upper section and, on the other hand, in transverse view, a smaller wall surface, since there is only one "wet" wall, radially external side. The flow of the arrival stream is therefore optimal, with a maximum speed on the general axis 10.

As stated at the beginning, the provision of a motive power locally can be exploited outside the scope of this application. For example, you can think of running a fan. If the generator 6 is present, it is possible to supply a light source, for example of the LED type. One can still think of feeding a perfume diffuser, or an alarm sensor, or a broadcast receiver circuit. As a variant of the general diagram exposed, provision can be made for the water of the return flow leaving the turbine 5 via the internal section 42 to be reinjected wholly or partly downstream of the radiator 200 into the return pipe 102. 104. The valve 1 then has three connections, namely the external arrival section 31, which branches functionally, in a first branch, to the outer outward section 41 through a needle or the like, and, according to a second branch, to the turbine 5, the needle or equivalent does not influence the flow arriving on it.

Of course, the second branch requires a short pipe downstream, resulting in an additional connection. The valve 1 is then considered to be a consumer member in its own right, that is to say that it perceives the totality of the differential pressure between the starting pipes 101 and return pipes 102, so that its power is increased. since the pressure drop of the radiator 200 no longer intervenes. It is thus possible to recover hydraulic energy supplied by the pump without however consuming calories. This is interesting in the summer. For the winter, a switch organ can be provided for bring back the output of the second branch in the first branch, that is to say return to the operating diagram of the detailed example.

The assembly according to FIG. 8 illustrates a variant of the turbine valve 1 of FIGS. 3 and 4, in which the homologous elements have retained their reference number, however with the suffix "A". For the sake of homogeneity, the references of new constituents also include the suffix "A".

This variant differs from, inter alia, the drawing of Figure 3 in that in the valve IA, the sleeve 52 constituting the output shaft is omitted. The driving force of the turbine 5A is transmitted not mechanically but by a rotating magnetic field. To do this, the wheel 50A carries a plurality of at least one drive magnet 63A, for example ten, regularly distributed around its periphery. The turbine 5A thus integrates the rotor 62A, in the "wet" stage of the bulb 9A. The windings of the associated stator 61A may be arranged radially to the drive magnets 63A, ie on the outer surface of the bulb 9A, or, as here, in an axial position other, and specifically to the the other side of the bulkhead 93A generally radial, that is to say in the adjacent "dry" stage. Of course, the separating wall thus provided between the rotor 62A and the stator 61 A is a material capable of transmitting the magnetic flux.

Furthermore, the turbine 5A is then centripetal type that is to say that it is fed globally in a reverse path from that discussed with reference to Figures 3 and 4 essentially. The downstream arrival section 32A of the connection 34A, situated exclusively above the axis 10 in FIG. 8, deviates from it obliquely going towards the periphery of the wheel 50A, along a path F32, to reach a volume 95 A ring surrounding an injection device 99A cylindrical adjustable diaphragm itself encircling the wheel 5OA. Motor elements, with references of hundred "1", are explained with reference to FIG. 12.

FIG. 9 is a perspective view showing the wheel 5OA of the turbine 5A. The oblique disposition of the periphery of the blades 5A1, with respect to an axial plane (axis 10) specific to each, shows that the water is injected. tangentially through the arrival channel, in the direction indicated by an arrow F50A, and that its trajectory is progressively deflected substantially in the direction of the axis 10, that is to say a centripetal component direction. The water outlet is effected by the internal starting section 42 A, axial and located just below the axis 10.

Of course, the two types of characteristics, namely the type of the output coupler of the turbine 5, 5 A, mechanical or magnetic, and the type of turbine 5, 5 A, centripetal or centrifugal, can be chosen independently one the other.

It is here provided a device for measuring the speed of rotation of the turbine 5A to, in particular, to determine the flow of water flowing therethrough. For this purpose, a detector circuit 89A measures the frequency of the voltage induced in the winding of the stator 6A1. The detector circuit 89A is for example a counter of the number of alternations, of the same sign or not, of the alternating voltage thus generated, this count being carried out cyclically for periods of time of predetermined value by a time base, for example 1 second. A dual system, periodemeter, is also possible, counting the number of pulses of a high frequency generator on the duration of an alternation. Note that if the generator 6 is not provided, the wheel 50A can however carry a said drive magnet 63A and the detector circuit 89A then comprises a magnetic flux detector winding of the drive magnet 63 A. Alternatively, a transceiver emits a wave to the blades 51A of the wheel 50A to measure the Doppler modulation back. In another variant, the bulb 9A is transparent for optical detection of the rotation of the blades IA, for example by an optical fork, or by detection of an optical mark on the periphery of the wheel 50A. Moreover, it is obvious that the rotational speed measuring device is independent of the type of turbine 5, 5 A.

The operation of the rotational speed measurement is explained below.

The following figures illustrate the injection device 99A. FIG. 10 shows that the injection device 99A comprises a first sheet of material, here a first ring 110 of axis 10, limiting a radially inner portion of the toric volume 95A, thus radially facing the wheel 50A, but the first ring 110 is here drawn in the form of a sheet developed flat, that is to say a rectangle, here vertical, the length of which represents the circular periphery. The axis 10 is drawn horizontally. The first ring 1 10 has a plurality of here N = 4 injection nozzles, namely a first nozzle 11, a second nozzle 112, a third nozzle

113, and a fourth nozzle 114. The nozzles 111 to 114 are oriented in the desired direction of injection, so here with a radial component relative to the axis 10. The nozzles 111 to 114 are here all of the same cross section, that is to say of the same axial extent and of the same angular extent with respect to the axis 10. They are arranged in an alignment along the length of the rectangle, that is to say that they occupy the same position axial. The nozzles 111 to 114 are here equidistributed angularly, so here spaced 90 degrees. The above three indications of equal section, alignment and even distribution of the nozzles 111 to 114 are each optional.

Note that the term "sheet" here means any wall having a sufficient surface to provide the desired water injection passages, such a sheet may have any thickness, depending on other needs.

A second sheet of ring-shaped material 120 is concentrically disposed near the first ring 110, either internally or externally. The second ring 120 has a number of angular sectors equal to said plurality, N = 4, namely a first sector 121, a second sector 122, a third sector 123, and a fourth sector 124, arranged in this order and equidistributed all the 90 degrees for respectively, bijectively, cooperate with the nozzle 111 to 114 of the same rank. The four sectors 121 to 124 have an axial extension at least equal to the homologous value of the nozzles 111 to

114, to be able to totally unmask them. It will be noted, however, that the bijection mentioned above, between each passage 111 to 114 and a particular sector 121 to 124 associated, is only one example, the simplest possible. It is possible to provide several sets of nozzles and / or several sets of such sectors, for example staggered 360 / 2N = 45 degrees with respect to those described, so as to have several layout patterns of the passages or sectors that are different from one game to another. The interest of such reasons is explained below.

Sectors 121 to 124 have associated nozzle unmasking lumens 111 to 114 which have angular extensions of mutually different sizes. Thus, the first sector 121 has an angular extension, with respect to the axis 10, representing at least N times the angular extent of the nozzle 111. For the sake of convenience, the first sector 121 is virtually divided into N = 4 angularly adjacent elementary sectors 121A, 121B, 121C, 121D, arranged in ascending order in FIG. 10, each having a cross section at least equal to that of the nozzle 111. Each of the N elementary sectors 121A to 121D is a elemental light.

The second sector 122, thus occupying a position offset by 90 degrees with respect to the first sector 121, is likewise divided into the same N elementary sectors, respectively 122A, 122B, 123C, 122D. It is the same for the third sector 123 and the fourth sector 124, having elementary sectors 123A, 123B, 123C, 123D and 124A, 124B, 124C, 124D respectively.

The four sectors 121 to 124 differ mutually in that elementary sectors of each are, in increasing number according to the sector rank 121, 123, 123, 124, constituted by a wall zone, therefore opaque, and not by a light elementary. Thus, while all the elementary sectors 121A to 121D of the first sector 121 are elementary lights, the first elementary sector 122A of the second sector 122 is opaque, and it is the same for the first and second elementary sectors 123A, 123B third sector 123 and for the first, second and third elementary sectors 124 A, 124B, 124C of the fourth sector 124.

These opaque elementary sectors are therefore defined here only as a didactic, as specific area of the second ring 120, to explain that the remaining areas of the sectors 121 to 124 are regularly decreasing angular size lights. More precisely, if sectors 121 to 124 were virtually brought back into superimposed positions, by one or more rotations of 360 / N = 90 degrees, the fourth elementary sectors 121D, 122D, 123D, 124D would be elementary lights thus superposed. , whose upper end (in Figure 10) represents an upper end of the overall light defined by the sector 121 to 124 considered. On the other hand, opposite, low ends of the elementary sectors 121A, 122B, 123C, 124D, thus of increasing ranks, at the bottom of the various global lights above would not be superimposed, but mutually offset in height, that is to say say circumferentially on the second ring 120, which explains the adjustment cam function of the desired number of nozzle unmasking 111 to 114.

It is thus conceivable that, if the second ring 120 occupies an angular position for which the first elementary sector 12 IA is facing the nozzle 111, the other nozzles 112 to 114 are facing respective opaque sectors of rank "A" 122A, 123A, 124A. An offset, of an elementary pitch, of the second ring 120, here downwardly of FIG. 10, of the angular extent value of a nozzle 111 to 114, brings the elementary sectors of rank "B": 121B , 122B, 123B, 124B coinciding with respectively the nozzles 111-114. Then, the elementary sector 122B unmasks the second nozzle 112, the other nozzles 111 and 113-114 remaining respectively passing and masked. Two other such offsets gradually unmask the nozzles 113 and 114. A rotation out of the above angular range masks all the nozzles 111 to 114. In general, the desired rotation, to perform the relative shear movement, can be carried out by one or other of the two rings 110, 120. However, it is also possible to provide a "scale" of shifts or additional cam, that is to say additional elementary sectors, in different numbers, beyond the fourth elementary sectors 12 ID, 122D, 123D, 124D, the variation these numbers can possibly be stepped independently of the rank of each sector 121 to 124. It is thus possible, starting from an angular position of total closure, to rotate the second ring 120 in the direction here descending retained to expose the operation, so with the nozzles 111 to 114 which are progressively opened according to their rank. However, by a rotation opening in the opposite direction, here ascending, it can be expected to successively open two diametrically opposed nozzles, such as 111 and 113 or 112 and 114, by fifth, sixth and other elementary sectors. In general terms, it is thus possible to define, for all the possible angular positions of the second ring 120, a pattern of determined numbers of elemental lights each unmasking a nozzle 111 to 114. In the present example, the pattern is repeated modulo 360 / N = 90 degrees. The pattern may, however, vary over 360 degrees if the nozzles 111 to 114 are not uniformly distributed in angular and / or axial position.

As mentioned above, the angular extent of each of the sectors 121 to 124 may be larger than exposed, if it turns out that the adjacent adjacent elementary sectors, such as 121A to 121D, are angularly arranged adjacent. Note, however, that the switching between the opening adjustment positions from 0 to N nozzles 111 to 114 is performed without discontinuity if the elementary sectors are, as here, adjacent.

FIG. 11 illustrates a variant of the assembly of FIG. 10, with two rings 210, 220 which are respective homologues of the first and second rings 110, 120. The elements homologous to those of FIG. 10 bear the same reference number, with however a number of hundred "2". Only the new characteristics of FIG. 1 1 will therefore be exposed. The difference in principle lies in the fact that the first and second rings 210, 220 are mutually axially movable along the axis 10. Therefore, each of the first, second, third, and fourth nozzles 211, 212, 213, 214 is axially offset relative to the others, here increasing with its rank, and the first, second, third and fourth sectors 221, 222, 223, 224 are extended axial, and not circumferential as in Figure 10. The explanation of the operation of the progressive switching arrangement of Figure 10 remains valid, the transposition near the direction of mutual sliding, here axial, first and second rings 210, 220. A composite motion, axial and angular, is conceivable, as well as two such possible movements, but then independent, to offer an extended choice of possibilities of unmasking patterns.

Figure 12 is an axial sectional view showing the second ring 120 angularly movable, secured by a radial disk, an axial shaft 150 angular position control, the assembly forming an axial cup open to the connector 34A. The shaft 150 comprises a ring gear 151 coupled to a pinion 161 driven by an actuator constituted by a stepping adjustment motor 162. In a variant, the adjustment motor 162 is omitted and the angular adjustment is manually controlled by a wheel or equivalent.

FIG. 8 represents the elements above, the cup being however returned to unmask the driving magnets 63A, that is to say that the radial disc above is between the connection 34A and the wheel 50A, this last being carried by a sleeve, not drawn, surrounding the shaft 150.

Alternatively, in the case of the second ring 220, axially movable, the ring gear 151 is replaced by a radial relief, female or male, such as a groove or a bead or an axial rack that drives axially the motor pinion 161 then axially orthogonal to the axis 10. The axial drive mechanism may also be of translation type, that is to say that the motor pinion 161 may also be replaced by a finger, or respectively a fork, to drive the shaft 150 in axial translation in one direction and the other, on bearings provided for this purpose. According to another variant, the position adjustment control of the second ring 120, 220 is effected by radial rather than axial access. The bulb 9 then comprises a radial circular passage of determined geometric axis, facing the toric volume 95 A, through, sealed, by a radial adjustment shaft, internal end of the crank type, or bayonet. An end section, internal to the bulb 9, of the radial adjustment shaft thus extends at a distance from the geometric axis of the radial passage, so that, during the rotation of the radial adjustment shaft, the inner end section traverses an arc in a plane tangential to the second movable ring 120, 220, that is to say a plane parallel to the general axis 10 and at a distance therefrom.

The second movable ring 120, 220 comprises a drive cavity housing the inner end of the radial adjustment shaft allowing it to pivot. Depending on the choice of the position, essentially axial or substantially angularly offset, of the drive cavity relative to the geometric axis of the radial adjustment shaft, the radial adjustment shaft can thus, by a circular path, cause the second angularly movable ring 120, respectively the second axially movable ring 220. The driving cavity may therefore be a groove whose width is adapted to the diameter of the end of the drive shaft and the length of which provides the degree freedom to allow the path of the curve curve above, that is to say with a component "parasite" away from the useful direction, for example purely tangential. However, it may be provided that the second ring 120, 220 considered is mounted so that it is also somewhat mobile in the "parasitic" direction above. In a variant, the angular or axial position of the second ring 120, respectively 220, is regulated by a magnetic coupling comprising a ring gear, angularly and / or axially, of radially external driving magnets 9, cooperating with a ring gear. magnets conducted at opposite poles, fixed on the second ring 120, 220. Any one, led or driven, of the two magnet rings can be replaced by a crown passive material of high permeability, for example ferrite, forming a circular serration, each pair of teeth thus providing, from a tooth tip to the neighbor, a magnetic path of minimum impedance, that is to say of maximum permeability. A driving rotation of the driving ring, made of ferrite or magnets, is thus copied by the driven ring, respectively magnet or ferrite, under the effect of the forces due to the minimum magnetic path maintenance law, it is ie permeability or maximum value coupling.

To ensure better stability, it can be provided, in the case of the second ring 120, rotatable, that the passage from one angular position to the next is performed with further a clutch release clutch in a back and forth in axial sliding. The second ring 120 then comprises at least one toothed ring sector, serration of not equal to or multiple of the value of a said elementary pitch of angular offset, serration which, in any set position, is engaged with an anti-finger. rotation, fixed relative to the bulb 9A. The axial axial movement temporarily releases the above serration, to make it perform the desired elementary angular rotation, and then the coupling again to the anti-rotation finger.

The same principle can be applied, dualally, to the second ring 220, axially movable, that is to say that the circular ring with serration above is replaced by an axial rack and the second ring 220 is driven according to an intermediate disengagement-clutch movement comprising an angular reciprocating movement from one axial position to another.

Note that it can be provided that the first and second rings 110, 120 and 210, 220 are driven by the wheel 50, 50A, that is to say at its speed. It can thus be considered that the wheel 50, 50A, thus provided with rings 110, 120 or 210, 220, is of variable geometry. In such a case, the axial position of the second ring 220, axially movable, will for example be regulated by a said radial adjustment shaft, in engagement with a said cavity of the second ring 220, in the form of a circular groove to thus offer the said degree of freedom wanted in total rotation. In the case of the turbine 5, axial injection, the rings above are replaced by two essentially radial discs and axially opposite, for example located at the outlet of the inner section of arrival 32. This corresponds precisely to the drawing plan of the Figure 9. Conveniently, the desired relative shear movement of the two disks is effected by rotation of one. However, it can be provided that one is a curtain movable in a predetermined radial direction, as in Figure 9, that is to say a kind of guillotine with functional areas that can close the desired nozzles, non-contact areas. functional may possibly not be sealed if the areas facing the other disc provide the desired seal, that is to say the non-circumvention of the nozzles.

Local network of management data transmission

The motor 162 is controlled by an electronic interface circuit 88 A receiving, by radio or by a wire link, the orders of a central management unit 170 managing various such IA valves distributed in an installation.

The central unit 170 receives the flow measurements of each valve IA, coming from the detector circuit 89A and retransmitted by wire circuits or by the radio circuits 83, then operating in transmission, and / or associated water temperature measurements or further measurements of air temperature of corresponding premises, these measurements being provided by sensors integrated to each valve IA or, overall, to the heating installation, or being external.

The flow control of the set of nozzles 111 to 114 thus carried out thus makes it possible to regulate the flow rate in the radiator 200 associated with the valve 1, IA. If, however, the connection 34 comprises a shunt, it will be provided to provide a low flow rate to the radiator 200, and the valve 1, IA can perfectly regulate the flow exceeding the low flow rate.

For the initial tuning of the installation, the central unit 170 can be programmed to control the desired settings, initial balancing of the flow rates of the various radiators 200, 300, mutually in parallel, that is to say set of the respective pressure drops. The measurements of the respective flow rates, for example according to the measured rotational speed of the respective turbines 5 or 5A, are thus acquired and compared with a setpoint value, general or individual, for then, according to a measurement of error as well. acquired, issue orders to move the second ring 120 or 220 in the direction tending to cancel the error. The comparison above obviously takes into account the possible flow of low water.

In general, the initial setting of the pressure drop can be carried out by means of the injection device 99A or by a needle located in series with it, in the bulb 9. The needle can however be provided on the direct path between the external arrival section 3 IA and the external departure section 4 IA, particularly if it is desired a certain independence between the flow of water passing through the radiator 200 and that through the turbine 5A, and possibly starting with a downstream path not passing through the radiator 200, as mentioned above in relation to the application to an LED. Furthermore, the control of the pressure drop calibration can be stored in a memory of the bulb 9, to locally retain the desired position mark even if the connection with the central unit 170 is cut off.

For a precise adjustment of the installation, it is to carry out an iterative process because, as the overall flow of the installation tends to remain constant, the setting of the nominal flow rate of a radiator 200 modifies the supply pressure various radiators 200, 300 and therefore the flow rate of the other radiators 300. An installer spends long hours to perform such a conventional balancing work, and, moreover, he can not hope to achieve, in an economically reasonable time, a perfect balancing. The present system thus constitutes a local area network that performs the desired balancing in a much smaller time and with any desired accuracy.

It may in particular be provided that the installer has a data exchange device, such as a wireless telephone, such as cellular or local cellular telephone, for receiving data from the central unit 170, for example the instantaneous flow rate value, the temperature of the water and that of the local, and others. In ascending order, the installer can transmit commands to the central unit 170, for example to set such flow rate setpoint values, each valve 1, IA being associated with a network address. The type of network, in particular the communication protocol, can be arbitrary, a relatively simple network, not real time, Ethernet type, being well suited since the risk of collision is very limited due to the low traffic. Alternatively, it is the radio circuits 83 of the bulb 9 which are used for radio exchanges above and the data exchange device can then be connected by an infrared or wired connection.

The data exchange device can however be fully integrated in the bulb 9, that is to say that it will be duplicated throughout the installation. The data of the central unit 170 received by the bulb 9 is then displayed on a screen, or broadcast by voice synthesis. The setting control data to be transmitted to the central unit 170 and any voice synthesis repeat control data and other human-machine relationship data can be entered by a keyboard, or touch screen, of the bulb 9 or by speech Recognition.

Alternatively, the water flow to the turbine 5A can be regulated to modulate the power thereof, and thus change its action on the driven member. For example, if the turbine 5 A drives a fan, the CPU 170 will accelerate it in case of growth detection of the ambient air temperature. Similarly, if the turbine 5A drives a generator 6 supplying a room light LED, the supply current will be increased if a brightness sensor indicates to the CPU 170 that the sun is declining. It is therefore a regulation of the turbine 5A which takes into account a totally external need for the heating system.

Thus, in general, the pressure drop adjustment can be performed at the second ring 120, 220, for such an external need, or at the needle 2, for a need internal to the heating system. In the first case, it can be provided, as already indicated, that the valve 1, IA also has a pipe and needle or drawers allowing it to be connected, optionally, in series with the radiator 200 (normal operation) or in parallel (Radiator 200 "cut" or insufficient flow vis-à-vis the external need of the valve 1, IA). Moreover, in operation, the central unit 170 establishes a history of the water flows thus measured. This history thus reflects the thermal needs of the locality considered, which were expressed through the movements of the valve 1, IA. By comparing the history of the various valves 1 or IA, the CPU 170 can thus detect generally excessive flow rates, that is to say excessive thermal leakage in a room. Conversely, generally low flow rates may be indicative of a partial closure of a pipe. An alarm is then generated, for example by editing the history and highlighting outliers.

It should be noted that these aspects of adjustment or calibration of water flow by means of electronic controls can also be processed by a conventional valve, which is turbine-free and has an electrical source, such as a connection to the electric network or a battery or battery. .

FIG. 13 is an axial sectional view illustrating a T-fitting incorporating a 3-way valve, referenced 180, mounted in series on the upstream loopback pipe 203 and constituting a variant 34A of the T-joint 34. At the junction point of the external branches or sections 3 IA, 41 A of the T with its trunk extending along the axis 10, the valve 180 has a rotary switching part comprising first, second and third radial arms 181, 182, 183, equidistant from to a geometric axis of rotation 180X perpendicular to the plane of extension of the T, which arms are carried by a hub 184 housed in a body 185 of the valve 180. The hub 184 has, at an accessible axial end, a relief, here a cavity , With non-circular cross section, here hexagonal, receiving an Allen type adjustment key. In the angular position shown, the first arm 181 is aligned with, and in the direction of, the axis 10 of the valve 1, IA, perpendicular to the extension direction 30, 40 of the branches of the T, that is to say the external arrival section 31 A and the external departure section 4 IA. Thus, the flow of incident water, descending in FIG. 13, from the external arrival section 3 IA is diverted at right angles in the inner arrival section 32 A, locally parallel to the axis 10 and located just above. The free end of the first arm 181 is in sealing contact with a wall zone 187 centered on the axis 10 and generally radial thereto, located at the top of the trunk of the T, that is to say at the end of the The second and third arms 182, 183 are each in contact with a circular zone 180C of an internal wall 180D, on the right-hand side, of the valve 180 opposite to the valve IA, so that there is there is no shunt of this last in this example. It will be noted that the third arm 183 is then redundant with the second arm 182, since they represent two interruptions in series in the virtual direct flow path of the water to the right of the axis 180X.

FIG. 13 being symmetrical with respect to the horizontal axis 10, the water leaves the valve IA passing through the internal starting section 42A situated under the axis 10 and thus under the first arm 181 and it flows in the external departure section 41A.

The valve 180 further comprises a valve 189 connected between the outer arrival section 31A and the outer outward section 4 IA. The valve 189 is here integrated in the hub 184, and it controls a shunt passage of the first arm 181, that is to say a passage generally perpendicular to the radial direction of the first arm 181. The valve 189 is here calibrated at 0.3 bar to short-circuit the incoming external portion 31A and the outer outward portion 41A if the second ring 120, 220 causes an excess of pressure by excessively reducing the flow of water. Thus, such a limitation of the excess pressure drop allows any significant reduction in drive flow of the turbine 1, IA, since the distribution of the flows in the various radiators 200, 300 is not seriously disturbed.

In the angular position illustrated in FIG. 14, the hub 184 has rotated, with respect to the drawing of FIG. 13, by about 15 degrees in one direction (the other direction also being suitable because of the symmetry with respect to the axis 10) to close partially the supply of the valve IA, being effected by the internal arrival section 32A, located just above the axis 10. Above all, such an angular position leaves open a shunt path, between the free end the first arm 181 and the zone, oriented, of generally radial wall 187. In this way, a frontal surface, external side, of a disk filter 188 inserted radially into the apex of the T, that is to say in the above mouth of the inner arrival section 32A leading to the turbine 5 A, is swept by an intense jet, which will cause the pollution particles that are deposited during normal operation. The third arm 183 is then non-functional. In the angular position according to Figure 15, the hub 184 has, relative to the aligned axes 30 and 40 of the branches of the T, a profile symmetrical to that of Figure 13, since it has rotated 180 degrees. Specifically, the ends of a pair of arms, here the second and third arms 182, 183, respectively are in contact with two 180F, 180E areas located on both sides of the mouthpiece constituting the top of the trunk of the T in a wall of left 180B. The V-shaped cap formed by the second and third arms 182, 183 thus closes the internal arrival sections 32A and 42A, thus isolating the valve IA. In addition, the first arm 181 is in contact with the circular zone 180C opposite the axis 10, so that the first and third arms 181, 183 close the external arrival section 3 IA, thus cutting off the supply of the radiator 200 and therefore, redundantly, also cutting power to the valve IA. Thus, the three arms 181, 182, 183 delimit, two by two, three caps able to simultaneously simultaneously obstruct the three passageways of the T 180.

Note however that, alternatively, it may be provided that the arms 181 to 183 are in increased number and / or that they extend in mutually unequal directions and / or that the cylindrical housing, three passages, containing the hub 184 has contact areas, with the arms 181 to 183, having angular extents other than those indicated.

Indeed, in Figures 13 and 14, substantially the lower two-thirds of the arc formed by the circular zone 180C, opposite the axis 10, are useless to ensure the closing of the direct passage to the right of the hub 184, since the second arm 182 alone suffices and cooperates for this purpose with substantially the upper third of the circular zone 180C. It can then be expected that at least the lower half of the circular zone 180C is removed, that is to say that the cylindrical wall 180D is further widened to form a channel section. In such a case, in FIG. 15, a further slight rotation of the hub 184 in the clockwise direction will open the right direct passage and the free ends of the second and third arms 182, 183 will have an angular extent sufficient to tolerate this additional rotation without loss of sealing with the respective zone of the mouth wall 180F and 180E at the top of the trunk of the T, zones 180E, 180F which, in a dual manner, can also be angularly widened.

It can be provided that the hub 184 can also be controlled by an actuator, such as an electric motor preferably powered by the generator 6 and controlled by the central unit 170. A time base thereof can thus cyclically control a temporary passage in the cleaning position of the various filters 188 according to Figure 14. It may also be expected to remotely control a cutoff of the water supply of any valve 1, IA of the installation, to allow the disassembly of a valve 1, IA defective, cutting, totally or not (see variant above), the supply of the radiator 200, 300.

Claims

1. thermostatic valve (1, IA) having means (2) for throttling a liquid flow to be regulated, inserted between an inlet channel (3) and a flow flow starting channel (4) provided for to be inserted in a supply pipe of an air conditioning radiator, valve characterized in that it comprises a turbine (5, 5A), connected between said channels (3, 4) and having a means (52, 63A ) for driving a driven member (6).

2. Valve according to claim 1, wherein the turbine (5) is integrated in a bulb (9, 9A) with the driven member consisting of a current generator (6).

3. Valve according to claim 2, wherein the current generator (6) is provided for supplying means (83) for receiving temperature control commands connected to means (84) for controlling the throttling means ( 2).

4. Valve according to one of claims 1 to 3, wherein the turbine (5, 5A) is of radial water flow type, centrifugal (5) or centripetal (5A), the arrival channel (3) , or respectively the starting channel (4), opening, on the turbine side (5, 5A), by an internal arrival section (32), respectively starting (42), which occupies an axial position with respect to a geometric axis (10) rotation of the turbine (5, 5A).

5. Valve according to claim 4, wherein the starting channel (4) comprises a starting internal section (42) comprising a sleeve surrounding the inner arrival section (32).

6. Valve according to one of claims 4 and 5, wherein a wheel (50) of the turbine (5) has buckets (55), a radially outer edge region (58) has a substantially axial direction of extension relative to the geometrical axis (10), continuing with a return channel (45) directed obliquely towards the geometric axis (10) to join the internal start section (42).

7. Valve according to one of claims 5 and 6, wherein the two inner sections (32, 42) are parallel to a direction of a given geometric axis (10) perpendicular to an extension direction (30, 40). ) of any one of the two outer sections (31, 41), the other outer section (41, 31) extending in either of said two directions (10; 30, 40).

8. Valve according to one of claims 2 to 7, wherein the turbine (5) and the generatrix (6) occupy staggered positions axially along said geometric axis of rotation (10), the generator (6) being housed in a removable cap (92) at the free end of the bulb (9).

9. Valve according to one of claims 4 to 8, wherein the throttling means comprise a needle (2) slidably mounted along said geometric axis (10) and having a front surface (22) of substantially conical side profile, for radially deflecting an arrival flow from the inner arrival section (32).

10. Valve according to one of claims 4 to 9, wherein the inner arrival section (32) has an outlet mouth provided with a deflector (33) for guiding the inflow.

11. Valve according to one of claims 8 to 10, wherein a rear section (24) of the needle (2) is slidably mounted in a sleeve constituting said drive means (52), the sleeve being housed in a passage axial (94) of a bulkhead (93), containment of the flow.

12. Valve according to claim 11, wherein a radially outer surface of the sleeve constituting the drive means (52) is carried by a bearing (95) housed in the passage (94) of the partition (93).

13. Valve according to one of claims 10 to 12, wherein the needle

(2) is angularly coupled with the turbine (5).

14. Valve according to one of claims 1 to 13, wherein the turbine (1, IA) is associated with an adjustable water injection device (99A; 110, 120; 210, 220).

15. Valve according to claim 14, wherein the injection device comprises two sheets of material (110, 120; 210, 220) facing and mutually movable to occupy several predetermined relative positions, a first sheet (110, 210) having a plurality of injection nozzles (111 to 114; 211 to 214) and a second sheet (120, 220) having lights (121 to 124; 221 to 224) of sizes and arrangements arranged to unmask a variable number of Nozzles (1-14) when one of the sheets (110, 120, 210, 220) moves from one said position to another.

16. Valve according to one of claims 14 and 15, comprising a motor (162) for adjusting the injection device (99A).

17. Valve according to one of claims 1 to 16, comprising a set (63 A, 89A) for measuring the speed of rotation of the turbine (5A).

18. Valve according to one of claims 1 to 17, provided with a connector (34A) having a stopcock (180) arranged to take an intermediate position allowing passage between the inlet channel (3) and the departure channel (4), a scanning water jet of a front surface of a filter (188) controlling access to an incoming internal section (32A) belonging to the arrival channel (3).

19. Valve according to one of claims 1 to 18, comprising circuits (83) for connection with a central unit (170) for managing an installation comprising a plurality of at least one said valve (1, IA), link circuits (83, 88A) arranged to transmit locally entered data to the central processing unit (170) and to receive feedback commands from an actuator of a flow rate control member (99A, 180) water (99A, 180).

20. Local data transmission network comprising a plurality of at least one valve (1, IA) according to one of claims 19 and 20, and a central management unit (170) comprising connecting means arranged to transmit to the at least one valve (1, IA), through the connection circuits (83, 88A), of said control commands of an actuator (162, 184A) of a water flow control member ( 99A, 180).

21. Local network according to claim 20, wherein the central unit (170) is arranged to a) receive measurements, from a set (63 A, 89A) for measuring the speed of rotation of the turbine (5A). , constituting said data entered locally, b) comparing a value thus measured with a set value of the commissioning flow rate of a radiator (200) associated with the valve in question (1, IA), and c) generating, and transmit in return, a said control command to adjust a pressure drop.