Ultra-fast reversible valve.

Abstract

The invention relates to a valve (V) comprising: a support (PS) with orifices (OPS) in fluidic communication with a first channel (1), a valve (S) having orifices (OS) in fluidic communication with a second channel (2), an electromechanically active actuator (A) configured to move the valve between: an open position in which the valve is spaced from the support to allow fluid to flow between their respective orifices (OS, OPS) and the first and second channels (1, 2), a closed position in which the valve is pressed against the support to close their respective orifices (OS, OPS) and block fluid flow between said channels (1, 2), the support being mounted to move in translation and associated with a spring element (R) acting on said support to follow the movement of the valve when it closes. Figure to be published for the abstract: Figure 2

Description

Title of the invention: Ultra-fast reversible valve. Technical field.

[0001] The present invention relates to a valve configured to be installed in a fluidic circuit.

[0002] The invention relates to the technical field of valves using an actuator to control their opening and / or closing, and more specifically, but not exclusively, to the technical field of ultra-fast valves (whose opening or closing time is less than or equal to 1.5 ms). State of the art.

[0003] A large number of fluidic circuits can incorporate valves and transport various types of fluid, such as liquids or gases. These circuits are used in many different devices, each with varying functions. For example, fluidic circuits are used to operate lifting equipment or wind turbines. They are therefore employed in many technical fields, such as aeronautics. This wide variability in their use is linked to their high efficiency and precision.

[0004] The valves integrated into these circuits can, for example, be electrically actuated valves, which use electrical signals to actuate the movement of the valve's components, thus enabling precise control of the hydraulic or pneumatic flow. This technology facilitates the integration of fluid into automated systems by offering high operational flexibility and immediate valve responsiveness, which is essential in applications requiring precise and dynamic process control.

[0005] Adding a piezoelectric or ferroelectric actuator to these electrically operated valves improves their precision and compactness, thereby enhancing their durability and reliability. A piezoelectric actuator significantly reduces actuation time compared to other conventional systems. Furthermore, their power consumption is virtually zero when held in a position.

[0006] A first type of valve known in the prior art and integrated into fluidic circuits is the "Bath" type valve, which comprises a fixed support that separates it into two distinct chambers. The opening and closing of this valve is determined by the movement of a movable valve, respectively away from or against the fixed support. However, the fluid pressure opposes the closing direction of the valve, resulting in fluid leakage between the chambers, which reduces its closing efficiency.

[0007] Published patent document WO 2023 / 131660 Al discloses a "Bath" type valve in which the direction of fluid flow has been reversed to facilitate valve closure. However, this valve is not suitable for hydraulic circuits in which the direction of valve operation must be reversed.

[0008] The invention aims to overcome at least one of the drawbacks of the aforementioned prior art. More specifically, the invention aims to improve the operation of valves regardless of the direction of fluid flow. This invention improves valve closure when fluid flow opposes valve closure. Presentation of the invention.

[0009] The solution proposed by the invention is a valve for a fluidic circuit comprising: a support in which fluid passage orifices are provided in fluidic communication with a first channel, a valve having fluid passage orifices in fluidic communication with a second channel respectively, said valve cooperating with the support, said valve and said support being arranged along a longitudinal axis, an electromechanically active actuator configured to move the valve along the longitudinal axis, between: a first open position in which the valve is spaced from the support to allow fluid circulation between their respective orifices and fluidic communication of the first channel with the second channel,a second closed position in which the valve is pressed against the support to close their respective orifices and block fluid communication between the first and second channels, the support being mounted to move in translation along the longitudinal axis and being associated with a spring element acting on said support so that said support has the capacity to follow the movement of the valve when it is in the second closed position and subjected to a pressure force tending to detach it from said support.

[0010] When the valve closes, the pressurized fluid entering the first chamber hinders the valve's closure by applying a pressure force against it that opposes the action of the actuator. The spring element associated with the support is also subjected to this pressure, and will therefore cause the support to move and press against the valve.

[0011] This plating ensures the valve remains sealed when closed, even against pressure forces opposing its closing direction. The seal is thus more effective and durable, improving the valve's reliability and efficiency.

[0012] Other advantageous features of the valve that is the subject of the invention are listed below. Each of these features can be considered alone or in combination with the notable features defined above. Each of These features contribute, where applicable, to the resolution of specific technical problems defined further in the description and in which the notable features defined above do not necessarily participate. The latter may, where applicable, be the subject of one or more divisional patent applications.

[0013] According to an advantageous embodiment, the valve is a reversible valve having two operating configurations: a first operating configuration where the first port is a pressurized fluid inlet and the second port is a fluid outlet, so that in use, in the first open position, the fluid flows from the first port to the second port, and a second operating configuration where the first port is a fluid outlet and the second port is a pressurized fluid inlet, so that in use, in the first open position, the fluid flows from the second port to the first port.

[0014] The valve exhibits the same efficiency regardless of the direction of fluid flow, therefore whether the valve is in the first or second operating configuration. Its efficiency also remains the same whether it is in the open or closed position.

[0015] The valve is versatile and reversible, which allows for ease of use. Furthermore, this eliminates the need for multiple valves, each operating according to the desired fluid flow direction. This results in less expensive and more compact fluid circuits, since several valves are replaced by a single one.

[0016] According to an advantageous embodiment, the support is installed in a first chamber incorporating the first channel and the valve is installed in a second chamber incorporating the second channel.

[0017] This type of configuration has the advantage of physically separating the first and second channels, thus facilitating fluid division, particularly when the fluid pressures differ in each of the two chambers. This ensures better management of the flows and their respective pressures, and improves the accuracy and efficiency of fluid regulation. It also improves the valve's durability and simplifies its maintenance.

[0018] According to an advantageous embodiment, when the valve is in the first operating configuration and the valve is in the second closed position, the pressurized fluid in the first chamber exerts a pressure force on said valve tending to detach it from the support, the spring member acting on said support so that said support follows the displacement of the detachment of said valve.

[0019] In the first operating configuration, the fluid flows from the first port to the second port, with the fluid pressure force acting in the opposite direction to the valve closing direction. The presence of the spring element allows the pressure force to also be exerted on the support, inducing its movement and positioning against the valve. This helps maintain effective closure over a very wide fluid pressure range, typically from 0 to 500 bar, applied to both the valve and the support, thus improving valve performance.

[0020] According to an advantageous embodiment, when the valve is in the second operating configuration and the valve is in the second closed position, the pressurized fluid in the second chamber exerts a pressure force on said valve, forcing it against the support.

[0021] When the valve is in its second operating configuration, fluid flows from the second port to the first port, with the second chamber therefore under high pressure. This pressure is exerted on the valve in the closing direction, forcing it against the support. Also, in this second configuration, the valve's tight seal is maintained with the same efficiency. Valve safety is also improved by limiting the risk of fluid leakage. This also reduces the risks of overpressure and mechanical failure of the valve. It should be noted that the spring element has no effect in this configuration.

[0022] According to an advantageous embodiment, the spring element has a stiffness Kr such that Kr < Keq, with Keq the equivalent stiffness of the actuator.

[0023] The stiffness of a spring influences its ability to stretch or retract in response to fluid pressure. Preferably, this stiffness should therefore be adapted to the stiffness of the actuator in order to optimize the mechanical response of the valve, and in particular to ensure that its operation is stable and predictable, even in the event of changes in its operating conditions (for example, a change in the opening and closing speed of the valve or a change in the pressure or temperature of the fluid).

[0024] According to an advantageous embodiment, the spring element consists of one or more stacked Belleville washers, or a grid spring, or a membrane spring, or a compression spring, or a tension spring.

[0025] Different types of springs can therefore be used depending on the type of valve to be developed, but also depending on the fluid circuit in which it is to be installed, the type of fluid, or the pressure that must be applied to it. Similarly, the size or type of actuator selected can influence the choice of spring, since its stiffness depends on the stiffness of the actuator used. Thus, the choice of spring depends on the desired valve configuration. The valve design can thus it can be customized according to the pressure and movement of the fluid, so as to best adapt the valve to its use.

[0026] According to an advantageous embodiment, the actuator consists of a piezoelectric pillar formed by a stacking structure of piezoelectric elements, which pillar extends when energized and retracts when the voltage is no longer applied.

[0027] The use of a piezoelectric pillar is particularly advantageous because it allows for rapid and precise valve actuation. The valve provides an instantaneous and controllable response, which is ideal for applications requiring rapid regulation of fluid flow.

[0028] According to an advantageous embodiment, the piezoelectric pillar is axially prestressed by means of one or more prestressing rods forming spring elements whose restoring force acts in the direction of the retraction of said pillar.

[0029] The pre-stressing of the piezoelectric pillar improves its efficiency and, in particular, its retraction. It also improves the reliability and durability of the actuator, ensuring consistent performance over the long term. Brief description of the figures.

[0030] Other advantages and features of the invention will become more apparent from the description of a preferred embodiment which will follow, with reference to the attached drawings, made by way of indicative and non-limiting examples and on which: - [Fig.1] represents a cross-sectional view of a valve according to the invention, the valve being represented in a first configuration and in an open position. - [Fig.2] represents a cross-sectional view of a valve according to the invention, the valve being shown in a first configuration and in a closed position. - [Fig.3] represents a cross-sectional view of a valve according to the invention, the valve being shown in a second configuration and in an open position. - [Fig.4] represents a cross-sectional view of a valve according to the invention, the valve being shown in a second configuration and in a closed position. - [Fig.5] is a hydraulic diagram of the valve according to the invention in a reversible configuration. Description of the implementation methods.

[0031] As used herein, and unless otherwise indicated, the use of the ordinal adjectives "first", "second", etc., to describe an object simply indicates that different Occurrences of similar objects are mentioned, but this does not imply that the objects thus described must be in a given sequence, whether in time, space, classification, etc. "X and / or Y" means: X alone, Y alone, or X+Y. Generally speaking, it should be noted that in the various attached drawings, the objects are drawn arbitrarily to facilitate their interpretation.

[0032] The invention is described primarily in relation to a hydraulic fluid, but of course this invention is not limited to this application and can be used with a gaseous fluid. The hydraulic fluid can be used as a means of power transmission in a hydraulic system. For example, it could be an incompressible mineral oil capable of rapidly transmitting energy from a pump to actuators and / or devices (cylinder, pump, motor, brake, etc.).

[0033] In the present application, a valve is considered as a two-way, two-position distributor, the two terms being equivalent within the meaning of the present invention.

[0034] Figures 1 to 5 show the general characteristics of a valve according to the invention.

[0035] A valve V according to the invention allows the circulation of a fluid within a fluidic circuit to be controlled. The valves can be more or less complex, and regulate the direction of flow of one or more fluids.

[0036] The valve V according to the invention comprises a hollow body C through which the fluid flows. This body C is rigid; for example, it is made of steel and preferably obtained by casting, or by casting and machining. The valve V extends along a longitudinal axis (XX), with channels (1, 2) connecting the valve V to the fluid circuit positioned along this axis and at each end of the valve. The hollow body C further has an inner face Fi from which preferably extend a first bulge RFI and a second bulge RF2. Each bulge (RFI, RF2) extends around the periphery of the inner face Fi, along and transversely to the longitudinal axis (XX).

[0037] The hollow body C of the valve V preferably comprises two distinct chambers (Cl, C2) along the longitudinal axis (XX), a first chamber Cl integrating the first channel 1, and a second chamber C2 integrating the second channel 2. Thus, the first bulge RFI is preferably positioned in the first chamber Cl, and the second bulge RF2 in the second chamber C2.

[0038] The valve V further includes a support PS configured to move between the first and second bulges (RFI, RF2), depending on the direction of movement and the pressure exerted by the fluid, in particular. While the bulges (RFI, RF2) can physically block the support PS between themselves, limiting its deflection and a possible positioning error, they do not delimit the range of movement of the PS support. This PS support extends transversely to the axis XX of the valve V and includes fluid passage orifices OPS that communicate with the first chamber Cl and the first port 1. Thus, the PS support is advantageously positioned within the first chamber Cl of the valve V. The PS support is rigid, preferably made of steel, and machined. Its diameter is, for example, between 10 mm and 50 mm, and its height (or thickness) between 2 mm and 10 mm. The displacement of the PS support between the first and second bulges (RFI, RF2) means that the PS support is mounted to move in translation within the body C of the valve V, along the longitudinal axis (XX). This assembly will be described below.

[0039] The valve V further comprises a valve S extending transversely to its longitudinal axis (XX), this valve being advantageously positioned in the second chamber C2 incorporating the second port 2. The valve S comprises fluid passage orifices OS in fluidic communication with the second chamber C2 and the second port 2. Like the support PS, the valve S is rigid, preferably made of steel and machined. Its diameter corresponds to the diameter of the support PS, and can, for example, be between 10 mm and 50 mm, its height (or thickness) being between 2 mm and 20 mm. The valve S is movably mounted between an open position and a closed position. According to a preferred embodiment, it is movably mounted in translation within the body C, along the longitudinal axis (XX).

[0040] The PS support and the S valve are in the form of Hörbiger plates of the type described in patent document WO2023 / 131660. For ease of assembly and design, the PS support and the S valve have a general cylindrical shape with a circular cross-section, although other cross-sections may be provided (square, rectangular, oval, oblong ...).

[0041] The orifices (OPS, OS) of the support PS and the valve S respectively are in a cooperative configuration. More particularly, each support PS and each valve S has, at their respective cooperative face (fps, fs), hollow parts corresponding to the orifices (OPS, OS) and solid parts bordering said hollow parts and corresponding to the vertically hatched areas of the support PS and the valve S.

[0042] The valve V further comprises an electromechanically active actuator A which can move the valve S along the longitudinal axis (XX). This actuator A is positioned in the second chamber C2, the valve S then being positioned between the actuator A and the support PS.

[0043] The actuator A preferably consists of a stacking structure of piezoelectric elements or a stacking structure of electrostrictive elements (also referred to hereafter as "pillar") or in a piezoelectric or electrostrictive membrane.

[0044] The pillar elements are advantageously in the form of piezoceramic or piezocomposite washers or discs with a diameter, for example, between 5 mm and 50 mm. The number of washers or discs can vary from 3 to 400 depending on the pillar length (which can range from 5 mm to 200 mm) and / or the mechanical force to be generated. For example, hard PZT (Lead Titanium Zirconate) ceramic washers are used. In the case of a piezoelectric membrane, it is advantageously a component of the polyvinylidine difluoride (PVDF) family, more particularly a PVDF derivative such as PVDF / PDMS (PDMS: polydimethylsiloxane).

[0045] For electrostrictive elements, the materials used may for example include P(VDF-TrFE) polymers (vinylidene fluoride and trifluoroethylene copolymer) or PZN ceramics (lead zinc niobate).

[0046] When actuator A is energized, its piezoelectric or electrostrictive elements become polarized and deform elastically to generate a mechanical stress. In one embodiment, the elastic deformation consists of an elongation of actuator A along the longitudinal axis (XX). In other words, actuator A elongates when energized. And when it is de-energized, actuator A retracts and returns to its original position.

[0047] The activation of actuator A is managed by a control unit, which may, for example, be a processor, microprocessor, or CPU (Central Processing Unit) integrated into an electronic terminal (computer, PLC, etc.). For example, the control signal generated by the control unit and applied to actuator A may have a voltage between 0 V and 1000 V, with a current of 2 A to 10 A. The activation of the actuator (transition from closed to open or vice versa) can take as little as 0.5 ms (2 kHz). The frequency of the opening / closing cycles can then reach 250 Hz. The control unit can adapt the control signal, in terms of voltage and / or current, to optimize performance in terms of speed (opening / closing time) and / or precision of the valve S's movements, and / or noise emitted, etc.For example, a sinusoidal control signal reduces the noise generated by the movement of valve S compared to a square wave control signal. The closing or opening speed will be slightly lower, but the longevity and reliability of the pillar will be improved.

[0048] The actuator A is preferably dimensioned to deliver a mechanical force between 1000 N (Newtons) and 10000 N. The pillar A is further advantageously prestressed axially by means of one or more rods of The prestressing rods Tg form spring elements whose restoring force acts in the direction of the retraction of the pillar. These prestressing rods Tg increase the retraction speed of pillar A tenfold. The plaintiff observed that the switching times of valve V were on the order of 0.5 ms.

[0049] According to an embodiment allowing the best results in terms of speed of switching between the positions of the valve V, the prestressing force applied by the prestressing rod(s) Tg on the pillar A is between 5% and 20% of the mechanical force delivered by said pillar alone (i.e. without prestressing) and / or the prestressing rod(s) Tg have a stiffness between 10% and 20% of the stiffness of the pillar alone. In other words, the original (non-prestressed) pillar A is 5 to 10 times stiffer than the prestressing rods Tg. As an example, pillar A alone has a stiffness of 87.5 MN / m (mega Newtons per meter) in an open circuit (the voltage can then reach 1000V) or 46 MN / m in a closed circuit (short circuit of the pillar), and the set of rods Tg has a stiffness of 16 MN / m (i.e. 5.33 MN / m per rod, if three prestressing rods are used).As another example, if pillar A delivers a mechanical force of 10 kN (Kilo Newton), the prestressing force applied by all the rods Tg is between 0.5 kN and 2 kN (i.e., between 0.15 and 0.7 kN per rod, if three prestressing rods are used).

[0050] The Tg prestressing rods thus make it possible to further reduce the switching times of the V valve, particularly when the fluid pressure is high. The applicant was able to observe experimentally that, compared to a non-prestressed pillar (for example, with the same pillar, but where the elements are bonded together), the Tg prestressing rods reduced the switching time by 20% at 100 bar and by 30% at 300 bar.

[0051] In practice, the axis of translation XX is materialized by a rod Ti on which the valve S is fixed. The extension or retraction of the actuator A induces a translation of this rod Ti along the axis XX, and in fact a translation of the valve S. The latter can be secured to the rod Ti by a tight fit, by welding, by screwing or by any other solution suitable to the person skilled in the art.

[0052] In figures 1 to 4, the support PS includes a central orifice O which serves to guide the rod Ti of the actuator A.

[0053] In Figures 1 and 3, the actuator A is sized to move the valve S a distance xs. In other words, in the open position, the distance between the cooperation face fs of the valve S and a face opposite the cooperation face fps of the support PS is xs. This distance is advantageously between 0 pm and 100 pm. The fluid flow rate that can pass through the orifices (OS, OPS) can be easily controlled by adjusting the voltage applied to the actuator A, which adjustment allows adjustment of the deformation of said actuator and therefore this distance xs. For example, for a displacement distance xs of approximately 100 pm, a flow rate of 10 L / min is obtained for a fluid at 5 bars, a flow rate of 15 L / min for a fluid at 10 bars and a flow rate of 80 L / min for a fluid at 300 bars.

[0054] The valve V according to the invention also includes a spring element R associated with the support PS, which allows translational movement of said support along the longitudinal axis (XX) of the valve V, particularly under the influence of fluid pressure. This spring element R may be, for example, one or more stacked Belleville washers, a grid spring, a diaphragm spring, a compression spring, or a tension spring. This spring element R attaches the support PS to the inner face Fi of the valve V, and more preferably, this element is attached to the second bulge RF2, allowing movement of the support PS between the first and second bulges (RFI, RF2). In practice, the support should not come into contact with RF2.

[0055] The spring element R is advantageously dimensioned so that its deformation, and therefore its displacement capacity of the support PS, is greater than that of the valve S. This dimensioning thus ensures that the valve S remains in the closed position. The best results are obtained when the stiffness Kr of the spring element R is such that Kr < Keq, with Keq being the equivalent stiffness of the actuator A (stiffness of the actuator alone when it is not prestressed or stiffness of the actuator and the prestressing rods Tg when it is prestressed), and preferably when Kr < (SPS / SS) x Keq, with SPS being the effective pressure surface of the support PS and SS the effective pressure surface of the valve S. By "effective pressure surface," we mean the surface of the support PS or the valve S on which the pressure force actually acts.

[0056] Advantageously, the orifices (OS, OPS) of the valve S and the support PS are positioned symmetrically on either side of the center of said valve or support. This balanced arrangement of the orifices allows the pressure to be exerted uniformly on the surface (SPS, SS) of the valve S and the support PS, limiting the risk of deflection and therefore premature wear of the valve V. The shape and size of the orifices (OS, OPS) can also influence the force applied to the surfaces (SPS, SS) of the valve S and the support PS.

[0057] Thus, the valve S, moved by the actuator A, has a first open position and a second closed position of the valve V.

[0058] In its first open position (Figures 1 and 3), the valve S is spaced from the support PS so as to allow fluid to circulate between their respective orifices (OPS, OS) and to connect the first and second chambers (Cl, C2) and the first and second paths (1, 2). The open position of valve V is its normal position, in the absence of activation of actuator A.

[0059] In its second closed position (Figures 2 and 4), the valve S is pressed against the support PS, thus blocking their respective orifices (OPS, OS). Fluid flow between the first port 1 and the second port 2, and between the first and second chambers (C1, C2), is therefore blocked. This closed position is enabled by activating the actuator A via the control unit. Actuator A extends, causing the valve S to move simultaneously and press against the support PS, thereby blocking fluid flow within the valve V.

[0060] Furthermore, the V valve according to the invention is reversible, which means that it has two operating configurations.

[0061] According to a first configuration, the first port 1 is a fluid inlet port into the valve V, and the second port 2 is an outlet port. Thus, when the valve V is in the open position, the flow is from the first port 1 to the second port 2. This configuration is shown in Figures 1 and 2.

[0062] Figure 1 shows the first configuration of valve V in the open position. In this figure, actuator A is not activated, and the piezoelectric pillar is therefore retracted. Valve S is at a distance from support PS, allowing fluid to pass through. The fluid flows from the first port 1 to enter the first chamber CL under pressure. Due to the retraction of the pillar, and therefore the positioning of valve S at a distance from support PS, the fluid can pass through the orifices (OS, OPS) to enter the second chamber C2, with reduced pressure. This pressure reduction is caused by the fluid passing through multiple orifices, reducing the particle velocity and thus the fluid pressure. This fluid then leaves valve V through the second port 2 and rejoins the fluid circuit. In this configuration, the spring element R does not affect the operation of valve V.

[0063] Figure 2 shows the first configuration of valve V in the closed position. In this figure, actuator A is activated, so the pillar extends towards support PS, causing valve S to move towards it. The approach of valve S and support PS should block fluid flow. However, the pressurized fluid, flowing from the first port 1 and entering the first chamber Cl, hinders the closure of valve S by exerting a pressure force against its cooperation face fs. To counteract this effect, the spring element R, which attaches support PS to the inner face Fi of the valve body C, retracts towards valve S under the pressure exerted on the cooperation face fps of support PS. Thus, support PS follows the movement of valve S when it is subjected to a pressure force tending to detach it from the PS support, and will allow the V valve to remain closed by counteracting the effects of the pressure.

[0064] According to a second configuration, the second port 2 is a fluid inlet port for valve V, and the first port 1 is an outlet port. Thus, when valve V is in the open position, the flow is from the second port 2 to the first port 1. This configuration is shown in Figures 3 and 4.

[0065] Fig. 3 shows the second configuration of valve V, in the open position. In this figure, actuator A is not activated, so the pillar is retracted. Valve S is positioned away from support PS, allowing fluid to pass through. The fluid flows from the second port 2 to enter the second chamber C2 under pressure. Due to the retraction of the pillar, and therefore the positioning of valve S away from support PS, the fluid can pass through the orifices (OS, OPS) to enter the first chamber C1, at a reduced pressure. This pressure reduction is caused by the fluid passing through multiple orifices, reducing the particle velocity and thus the fluid pressure. This fluid then leaves valve V through the first port 1 and rejoins the fluid circuit. In this configuration, the spring element R does not affect the operation of valve V.

[0066] Fig. 4 shows the second configuration of valve V, in the closed position. In this figure, actuator A is activated, so the pillar extends towards the support PS, causing valve S to move towards it. The movement of valve S towards the support PS blocks the fluid flow. The fluid enters from the second port 2 and flows into the second chamber C2, assisting the closure of valve V by exerting pressure on valve S, forcing it against the support PS. Therefore, in this configuration, the spring element R does not affect the operation of valve V.

[0067] Figure 5 shows the hydraulic diagram of the valve according to the invention. Fluid circulation is represented here as reversible, when valve V is in the open position and in the absence of activation of actuator A. The second part of the diagram shows valve V in the closed position when actuator A is activated.

[0068] The arrangement of the various elements and / or means and / or steps of the invention, in the embodiments described above, should not be understood as requiring such an arrangement in all implementations. In any event, it will be understood that various modifications may be made to these elements and / or means and / or steps, without departing from the spirit and scope of the invention.

[0069] Furthermore, one or more features exposed only in one embodiment can be combined with one or more other features exposed only in another embodiment. Similarly, one or more Features exposed only in one embodiment can be generalized to other embodiments, even if that feature or those features are described only in combination with other features.

[0070] The use of the verb "comprise", "comprendre" or "include" and its conjugated forms does not exclude the presence of other elements or other steps than those stated in a claim.

Claims

Demands

1. Valve (V) for a fluidic circuit comprising: - a support (PS) in which fluid passage orifices (OPS) are provided in fluidic communication with a first channel (1), - a valve (S) having fluid passage orifices (OS) in fluidic communication with a second channel (2), said valve cooperating with the support (PS), said valve and said support being arranged along a longitudinal axis (XX), - an electromechanically active actuator (A) configured to move the valve (S) along the longitudinal axis (XX), between: • a first open position in which the valve (S) is spaced from the support (PS) to allow fluid circulation between their respective orifices (OS, OPS) and fluidic communication of the first channel (1) with the second channel (2),• a second closed position in which the valve (S) is pressed against the support (PS) to close their respective orifices (OS, OPS) and block fluid communication between the first channel (1) and the second channel (2), characterized in that the support (PS) is mounted to move in translation along the longitudinal axis (XX) and is associated with a spring element (R) acting on said support so that said support has the capacity to follow the movement of the valve (S) when it is in the second closed position and subjected to a pressure force tending to detach it from said support.

2. Valve (V) according to claim 1, wherein said valve is a reversible valve having two operating configurations: - a first operating configuration where the first port (1) is a pressurized fluid inlet and the second way (2) is a fluid outlet, so that in use, in the first open position, the fluid flows from the first way (1) to the second way (2), and - a second operating configuration where the first way (1) is a fluid outlet and the second way (2) is a pressurized fluid inlet, so that in use, in the first open position, the fluid flows from the second way (2) to the first way (1).

3. Valve (V) according to any one of the preceding claims, wherein the support (PS) is installed in a first chamber (Cl) incorporating the first way (1) and the valve (S) is installed in a second chamber (C2) incorporating the second way (2).

4. Valve (V) according to claim 3 taken in combination with claim 2, wherein, when the valve (V) is in the first operating configuration and the valve (S) is in the second closed position, the pressurized fluid in the first chamber (Cl) exerts a pressure force on said valve tending to detach it from the support (PS), the spring member (R) acting on said support so that said support follows the displacement of the detachment of said valve.

5. Valve (V) according to any one of claims 3 or 4 taken in combination with claim 2, wherein, when the valve (V) is in the second operating configuration and the valve (S) is in the second closed position, the pressurized fluid in the second chamber (C2) exerts a pressure force on said valve forcing it against the support (PS).

6. Valve (V) according to any one of the preceding claims, wherein the spring member (R) has a stiffness Kr such that Kr < Keq, with Keq the equivalent stiffness of the actuator (A).

7. Valve (V) according to any one of the preceding claims, wherein the spring element (R) consists of one or more stacked Belleville washers, or a grid spring, or a diaphragm spring, or a compression spring, or a tension spring.

8. Valve (V) according to any one of the preceding claims, wherein the actuator (A) consists of a piezoelectric pillar formed

9. by a stacking structure of piezoelectric elements, which pillar lengthens when energized and retracts when the voltage is removed. Valve (V) according to claim 8, wherein the piezoelectric pillar (A) is axially prestressed by means of one or more prestressing rods (Tg) forming spring elements whose restoring force acts in the direction of the retraction of said pillar.