Multi-way valve and fluid management system

Abstract

The invention relates to a multi-way valve and a fluid management system. A multi-way valve for a pressurized fluid management system includes a dispenser and a gasket. The distributor is used for an interconnection area of the pipeline, a valve core which is arranged in the interconnection area and can rotate around a central axis so as to prevent or allow fluid to flow in the pipeline, and a channel for the fluid. The sealing gasket is radially arranged between the peripheral contour and the valve core and comprises at least one gasket seat, at least one deformable membrane and at least one central opening penetrating through the gasket seat and the deformable membrane, and the deformable membrane comprises a supporting part fixed on the gasket seat and two lips connected with each other at a connecting part located on a transverse plane; each lip is disposed relative to the support portion to respectively form a recess.

Description

Technical Field

[0001] This invention relates to a multi-way valve for use in a pressurized fluid management system, the multi-way valve having a valve core and sealing gaskets. Depending on the specific application, the sealing gaskets are arranged appropriately in the fluid management system to achieve sealing of different pipelines within the system. The invention also relates to a fluid management system having this multi-way valve.

[0002] This invention relates to an application in a fluid management system, such as a thermal management module for cooling fluids, applicable to all types of vehicles, but not limited thereto. In fact, the invention also relates to an application in a fluid management system used in machines, enabling the implementation of advanced fluid management technologies for industrial processes. Background Technology

[0003] Fluid management systems are used to distribute fluid between different fluid loops. Such systems are particularly useful, and even necessary, when fluid should be distributed to at least two distinct fluid paths and / or loops. A fluid management system typically includes a distributor comprising a housing forming multiple fluid flow paths, an interconnecting area where the paths converge (defined by an outer contour and having a central axis), and a valve core capable of rotating about the central axis to block or allow fluid flow in the paths. The valve core typically extends from the interconnecting area and is separated from the outer contour by fluid channels. A device is required to block the inlet of the path according to the loop from which fluid should be supplied.

[0004] In this regard, gaskets can be appropriately arranged at pipelines to achieve a sealed seal. More specifically, the gasket is placed between the valve core and the outer contour so that when pressure is applied to the gasket by the valve core, a sealing contact is formed with the outer contour. There are three types of gaskets in the prior art, all of which are double-sided gaskets, meaning they consist of two opposing surfaces.

[0005] According to the first construction, the sealing gasket consists of two parts. The first part is a rubber component with an elastomer film covering one side; unlike the first part, the second part is made of metal, enabling it to function as a spring. This approach is costly because it requires the use of metal components in addition to the rubber component. Furthermore, the assembly of this sealing gasket is complex because the first and second parts must be correctly positioned to maintain their assembly and alignment after being assembled into the fluid management system.

[0006] In the second configuration, the sealing gasket consists of a single rubber component. However, in this configuration, the valve core has a high rotational torque, and the sealing gasket cannot adequately restrict the valve core's rotational torque. Therefore, the movement of the valve core may cause displacement of the sealing gasket, which in turn can no longer ensure the sealing performance of the pipeline between the gaskets.

[0007] According to the third construction, the gasket consists of a single rubber component, one side of which is covered with a polytetrafluoroethylene (PTFE) film. Although this gasket is less sensitive to the rotational torque of the valve spool, it is still inefficient in limiting the rotational torque of the valve spool and may shift with continuous movement of the valve spool. Furthermore, it applies greater axial compression compared to the aforementioned gaskets made entirely of rubber.

[0008] The sealing gasket constructed as described above is highly sensitive to fluid pressure. In fact, depending on the intended application, fluid can flow in the fluid circuit at pressures up to 5 bar.

[0009] Documents US2022 / 025976A1, US2023 / 279954A1, WO2021 / 013340A1, and CN118176377A disclose a multi-way valve.

[0010] The present invention aims to overcome at least some of the above-mentioned problems and proposes a solution in which the sealing gasket can further limit the rotational torque of the valve core and exhibit better response to the pressure exerted by the fluid flowing in the fluid circuit in terms of sealing performance. Summary of the Invention

[0011] Therefore, the present invention proposes a multi-way valve, comprising:

[0012] - A distributor, which includes a housing having multiple fluid flow lines, an interconnection area for the lines, and a valve core, the interconnection area having a central axis and including a peripheral profile, the valve core being disposed in the interconnection area such that the radial outer surface of the valve core is separated from the peripheral profile by a fluid passage, the valve core (7) also being able to rotate about the central axis to prevent or allow fluid to flow in the lines;

[0013] - A sealing gasket, positioned groundably around each pipe path between the outer contour and the valve core, each gasket comprising:

[0014] - A through-center opening having a longitudinal axis, the center opening being arranged in the prolongement of the conduit to allow fluid to flow through the gasket;

[0015] - A gasket seat, which is arranged around a central opening and has a first surface facing the valve core; and

[0016] - A deformable membrane, comprising a support portion fixed to a second surface of the pad seat opposite to the first surface, and two lips connected to each other at a connection portion on a transverse plane, each lip being arranged relative to the support portion to form a recess.

[0017] The coefficient of dynamic friction between the gasket and the valve core is lower than the theoretical coefficient of dynamic friction between the deformable diaphragm and the valve core.

[0018] The feature is that the first recess faces the opposite direction to the central opening, the second recess faces the central opening, and the lip is movable to seal and block the flow of fluid in the channel.

[0019] The multi-way valve according to the invention solves the problems raised in the prior art. In this respect, in the sealing gasket of the multi-way valve according to the invention, the lip and the support portion are arranged to form a recess facing opposite directions toward the central opening and toward the central opening. Therefore, fluid flowing into the channel from a pipe other than the pipe on which the sealing gasket is installed or the pipe on which the sealing gasket is installed can enter the recess, thereby causing the lip to move and sealably block the flow of fluid in the channel. In this case, the sealing and tightness between the channel and the pipe on which the sealing gasket is installed are significantly improved.

[0020] Furthermore, the presence of the gasket seat restricts the rotational torque of the valve core, thereby limiting or even preventing displacement of the gasket each time it contacts the valve core. In fact, the coefficient of dynamic friction between the gasket seat and the valve core is lower than the theoretical coefficient of dynamic friction between the deformable membrane and the valve core, which limits the rotational torque of the valve core. Therefore, the service life of the gasket is significantly increased, and the maintenance requirements of the multi-way valve are greatly reduced. This is particularly important because such multi-way valves may include multiple gaskets, which, although their service lives are generally similar, may differ in use due to factors such as one pipeline bearing a greater load than another. Therefore, this advantage of the invention becomes more apparent as the number of gaskets in the multi-way valve increases.

[0021] According to different features of the invention, these features can be used together or individually:

[0022] -The sealing gasket is X-shaped, and the gasket seat includes two protrusions at the two ends of the X-shape;

[0023] - Each lip includes a free end, which corresponds to the other two ends of the X-shape;

[0024] - The pad is made of a material selected from pure polytetrafluoroethylene (PTFE), glass fiber filled PTFE, carbon filled PTFE, polyvinylidene fluoride (PVDF), polyether ether ketone (PEEK), polyarylether ketone (PEAK), polyphenylene amide (PPA), polyphenylene sulfide (PPS), polycaprolactam (PA6), and polyamide 66 (PA66).

[0025] - The deformable membrane is made of rubber materials selected from ethylene propylene diene monomer (EPDM), hydrogenated nitrile butadiene rubber (HNBR), ethylene acrylate rubber (AEM), polyacrylate rubber (ACM), silicone honeycomb rubber (VMQ), nitrile butadiene rubber (NBR), polyurethane rubber (PU), and thermoplastic rubber (TPE).

[0026] - The thickness of the pad is 0.05 mm to 1.5 mm, preferably 0.1 mm to 0.5 mm;

[0027] - Each pipe includes an inlet for fluid from the interconnecting area, and wherein the outer profile includes a stop located between the inlets of two adjacent pipes;

[0028] - The stop is a reinforcing ring that forms the outline of the entrance;

[0029] - The multi-way valve includes a gasket section, which includes multiple sealing gaskets separated from each other by a thinning portion, the thinning portion connecting the multiple sealing gaskets;

[0030] - Each sealing gasket has a convex surface facing the overall bend towards the associated conduit.

[0031] The present invention also relates to a fluid management system comprising the multi-way valve as described above. Advantageously, the fluid management system is a thermal management module. Attached Figure Description

[0032] Other objects, features, and advantages of the present invention will become more apparent from the following description with reference to the accompanying drawings, in which:

[0033] Figure 1 This is a perspective view of a distributor applicable to the multi-way valve according to the present invention;

[0034] Figure 2a This is a cross-sectional view of a multi-way valve according to a first embodiment of the present invention, the multi-way valve comprising as follows Figure 1 The distributor shown;

[0035] Figure 2b yes Figure 2a An enlarged view of the multi-way valve shown;

[0036] Figure 3 It shows Figure 2a and 2b A perspective view of the sealing gasket used in the multi-way valve shown;

[0037] Figure 4 The diagram schematically illustrates the assembly state (without filler pattern) and the assembly state (with filler pattern) under the pressure of the fluid to be sealed. Figure 3 Sealing gaskets in the middle;

[0038] Figure 5 This is a cross-sectional view of a multi-way valve according to a second embodiment of the present invention;

[0039] Figure 6 It shows Figure 5 A perspective view of the sealing gasket in the middle;

[0040] Figure 7a and 7b This is a cross-sectional view of a multi-way valve according to a third embodiment of the present invention, wherein the valve core is located in two different positions;

[0041] Figure 8 The diagram schematically illustrates the assembled state (without filler pattern) and the assembled state (with filler pattern) under the pressure of the fluid to be sealed. Figure 7a and Figure 7b Sealing gaskets for multi-way valves in [the system / system];

[0042] Figure 9 It shows Figure 8 A perspective view of the sealing gasket in the middle;

[0043] Figure 10 This is a cross-sectional view of a multi-way valve according to a fourth embodiment of the present invention;

[0044] Figure 11 It shows Figure 10 A perspective view of the sealing gasket in the middle;

[0045] Figure 12 A multi-way valve according to a variant embodiment of the present invention is shown intentionally;

[0046] Figure 13a A multi-way valve with a first construction according to the present invention;

[0047] Figure 13b A multi-way valve with a second construction according to the present invention is shown. Detailed Implementation

[0048] The invention will now be described in conjunction with the accompanying drawings.

[0049] See Figure 1 and Figure 2b This invention relates to a multi-way valve 1 for a management system of pressurized fluid F, the system being designed for installation in a fluid circuit. The invention also relates to a management system (not shown) for fluid F including such a multi-way valve.

[0050] The fluid F used depends on the application of the fluid circuit to which the fluid management system is applied. For example, if the fluid circuit is an automotive cooling circuit, then fluid F is coolant. In such a circuit, the pressure of fluid F can reach 5 bar, so the device is advantageously configured to withstand this pressure.

[0051] The function of a fluid management system is to distribute fluid between different parts of the same fluid loop or between different fluid loops. For example, Figure 1 As shown, the fluid management system includes a multi-way valve with a distributor 2. The distributor 2 includes a housing 3, an interconnecting area 5 having a central axis X, and a valve core 7. The fluid management system is, for example, a thermal management module.

[0052] Housing 3 is the outer shell of distributor 2, used to contain the fluid F flowing within distributor 2. The number of fluid flow lines 4 is multiple, depending on the number of parts in the same loop or the number of loops to be connected. Figure 1 In the illustrated embodiment, there are three flow channels 4. The channels 4 are arranged to give the housing 3 an overall T-shaped form. Two channels 4 are arranged as crossbeams forming the T, while the other channel 4 is arranged as a longitudinal beam forming the T. In this embodiment, the latter channel 4 is therefore substantially perpendicular to the other two channels. This is not the only conceivable arrangement, as two consecutive channels 4 can form a 120° angle, thus achieving substantially the same spacing between the channels 4. Furthermore, the number of channels can also be more than two.

[0053] As previously described, the distributor 2 includes an interconnecting region 5 for the flow channels 4, the interconnecting region 5 having a central axis X. Therefore, the interconnecting region 5 is located at the junction of different channels 4. The interconnecting region 5 includes a peripheral profile 6 formed by the inner surface of the interconnecting region 5, i.e., the inner surface of the wall that radially defines the interconnecting region 5. In the illustrated embodiment, the peripheral profile 6 is generally circular, from which the different fluid flow channels 4 extend. However, the invention is by no means limited to this shape; for a spherical distributor, the peripheral profile 6 may also be spherical. It is understood that the central axis X is located at the center of the interconnecting region 5. In the illustrated embodiment, this central axis X extends perpendicular to the bottom of the interconnecting region.

[0054] The distributor 2 also includes a valve core 7, which is positioned in the interconnection area 5 such that the radial outer surface 7a of the valve core 7 is separated from the peripheral profile 6 by a channel 8 for fluid F. In effect, fluid F flows through this channel from one pipe 4 to another. As previously described, in the illustrated embodiment, the peripheral profile 6 and the valve core 7 are cylindrical. This makes the channel 8 circular. The valve core 7 is rotatable about its central axis X. The valve core 7 is configured to prevent or allow fluid F to flow simultaneously in one or more pipes 4. For example, the valve core 7 can prevent fluid from flowing in one or both pipes, depending on the configuration of the distributor 2, regardless of the number. In the illustrated embodiment, the valve core 7 has an integral cylindrical shape, particularly a hollow cylinder. The valve core 7 can also be a solid cylinder, a semi-cylinder, a solid sphere, or a solid hemisphere without hindering the invention. The advantage of one configuration over another depends on the number of pipes 4 in the distributor and the number of pipes 4 that need to be closed simultaneously.

[0055] The multi-way valve 1 includes a sealing gasket 10 that allows sealing of the conduit 4, thereby preventing fluid F from entering the conduit 4. In this regard, the sealing gasket 10 is radially positioned around each conduit 4 between the outer contour 6 and the valve core 7, and thus located in the channel 8, which enables it to ensure the sealing function of the sealing gasket 10 for the conduit 4 associated with it. For this purpose, according to a preferred embodiment, each conduit 4 includes an inlet 40 that allows fluid F to enter the conduit 4 from the interconnecting region 5, and the outer contour 6 includes a stop 6a located between the inlets 40 of two adjacent conduits. In effect, the inlet 40 is located at the interface between the interconnecting region 5 and the conduit 4 associated with that inlet 40. Each stop 6a is positioned in such a manner that the corresponding sealing gasket 10 can be positioned and stably held at the interface between the interconnecting region 5 and the conduit 4. Depending on the dimensions of the sealing gasket 10 relative to the interconnecting region 5, two stops 6a may be provided between two inlets 40. Alternatively, a single stop may be provided between the crossbeam and the longitudinal beam of the T-shape, for example... Figure 2a As shown.

[0056] exist Figure 2a In the configuration shown, fluid F flows in pipes 4a and 4c (indicated by arrows). It should be noted that valve spool 7 is located opposite the pipe (here, pipe 4b) from which fluid flow is to be blocked. Therefore, the pressure of fluid F enters pipes 4a and 4c, but no fluid flows in pipe 4b. Fluid F arriving from pipes 4a and 4c passes through channel 8 and applies pressure to the sealing gasket, as indicated by arrows. Valve spool 7 has a semi-circular shape, enabling it to close a single pipe (here, pipe 4b). The operation is described below. Fluid F from pipes 4a and 4c is directed to pipe 4b. Simultaneously, the sealing gasket 10 associated with pipe 4b blocks fluid from pipes 4a and 4c. As will be seen later in this description, this mode of operation of the sealing gasket 10 corresponds to the operation mode under external pressure.

[0057] As described below, the multi-way valve 1 may include multiple sealing gaskets 10 according to its construction. Although each sealing gasket 10 can be provided as a single sealing gasket, it is more advantageous, especially when the number of lines is greater than or equal to four, to form a gasket section 11 comprising multiple sealing gaskets 10. In this case, each sealing gasket 10 in the gasket section 11 can perform a sealing function independently of the other sealing gaskets 10. The advantage of the gasket section is that it forms a single and robust assembly, which simplifies its manufacture and installation. This will be discussed later. Figure 13a and Figure 13b To provide a more detailed description.

[0058] Each sealing gasket 10 includes a gasket seat 12, a deformable membrane 14 fixed to the gasket seat 12, and a central opening 18 penetrating the gasket seat 12 and the deformable membrane 14. Figure 3 This is a perspective view of the sealing gasket 10 used in the multi-way valve 1 according to the first embodiment of the present invention, such as... Figure 1 , 2a As shown in Figure 2b. In the illustrated embodiment, the sealing gasket 10 is generally parallelepiped and curved, with its convex surface facing the associated conduit 4. This curvature of the sealing gasket 10 allows it to advantageously conform to the contour of the outer contour 6. Other shapes of the sealing gasket can be considered depending on the shape of the outer contour 6, and the invention is not limited to any particular shape. Figure 3 The pad seat 12, deformable membrane 14, and opening 18 are shown.

[0059] A through-center opening 18 with longitudinal axis A is arranged in the extension direction of the pipe 4 to allow fluid to flow through the sealing gasket 10.

[0060] In this invention, the coefficient of dynamic friction between the gasket seat 12 and the valve core 7 (particularly the outer surface 7a of the valve core) is lower than the theoretical coefficient of dynamic friction between the deformable membrane 14 and the valve core 7. This reduces the rotational torque of the valve core 7, thereby reducing friction between the valve core 7 and the sealing gasket 10. The low coefficient of dynamic friction between the valve core 7 and the gasket seat 12 may be due to the low roughness of the first surface 12a of the gasket seat, material properties, etc. It should be emphasized that the theoretical coefficient of dynamic friction between the deformable membrane 14 and the valve core 7 can be predetermined by measuring a sample excluding the gasket seat 12.

[0061] A pad seat 12 is arranged around a central opening 18. The pad seat 12 includes a first surface 12a facing the valve core 7 and a second surface 12b opposite to the first surface 12a, on which the deformable membrane 14 is fixed. The first surface 12a of the pad seat facing the valve core 7 is also used for direct contact with the valve core 7, while the second surface 12b is not. Therefore, from the perspective of rotational coupling of the valve core 7, the first surface 12a is the functional surface of the pad seat 12, while the second surface 12b is used to fix the deformable membrane 14.

[0062] In this respect, it should be noted that the deformable film 14 can be fixed to the pad seat 12 by any process known to those skilled in the art, such as by adhesive, thermal bonding, etc. According to a specific embodiment of the invention, the deformable film 14 is fixed to the pad seat 12 by hot melt adhesive. As an example, the hot melt adhesive can be ethylene-acrylic acid copolymer (EAA) or any other compound with excellent adhesion.

[0063] In the embodiment shown in the accompanying drawings, the radial dimension (i.e., thickness) of the deformable membrane 14 is significantly larger than the radial dimension of the gasket seat 12. In fact, the gasket seat 12 is in the form of a thin film or layer with a certain thickness along its radial axis, while the dimension of the deformable membrane 14 along this radial axis is an order of magnitude larger than the dimension of the gasket seat 12. In this regard, the gasket seat 12 may also comprise multiple layers. In this case, the gasket seat 12 preferably comprises two layers: a first layer fixed to the deformable membrane 14 to enhance the rigidity of the sealing gasket 10, and a second layer fixed to the first layer to significantly limit the rotational torque of the valve core 7. In this variant embodiment, the coefficient of kinetic friction between the second layer and the valve core 7 is preferably lower than the theoretical coefficient of kinetic friction between the deformable membrane 14 and the valve core 7. For example, the first layer is PTFE, and the second layer is rubber.

[0064] Membrane 14 is deformable under the pressure of the fluid F flowing within the fluid management system. As previously mentioned, the pressure of fluid F can be from 0.1 bar to 5 bar, which is sufficient to deform membrane 14. In this regard, it should be noted that "deformable" refers to the inherent ability of a membrane to change shape relative to its free state under stress. The "free state" refers to the state of membrane 14 when it is not subjected to any stress. The deformability of membrane 14 depends primarily on the elastic properties of the (one or more) materials constituting the membrane, and therefore on the properties of the (one or more) materials used. Thus, at least a portion of the deformable membrane 14 is capable of movement under the influence of the fluid.

[0065] In this invention, the deformable membrane 14 includes a support portion 15 fixed to the second surface 12b of the pad seat, and at least one lip 16 arranged relative to the support portion 15 to form a recess 17 facing away from the central opening 18. The support portion 15 provides support for the lip 16 and also provides a surface for mechanically securing the deformable membrane 14 to the pad seat 12. The lip 16 is the movable portion of the deformable membrane 14. In practice, when fluid F enters the recess 17, the pressure it exerts on the lip 16 causes the lip 16 to move from a pre-tightened position (e.g., ...). Figure 2b (As shown in the enlarged view) Move to the position of the constraint. In Figure 2b , 8 In 10, the free end of the support portion 15 has a protrusion, which does not need to be considered.

[0066] Figure 4The diagram illustrates the transition of the sealing gasket 10 from an assembled state (with the lip 16 in a pre-tightened position) to a pressure-adjusted assembled state (with the lip 16 in a stressed position). The sealing gasket 10 has no filling pattern in the assembled state, while it has a filling pattern in the pressure-adjusted assembled state. It is noteworthy that when the sealing gasket 10 is in the assembled state, the distance between the free end of the lip 16 and the free end of the support portion 15 is closer than when the sealing gasket 10 is in the free state. Figure 2a In the figure, the sealing gaskets 10 are shown in a free state, although they are actually in an assembled state. (This is also mentioned in the figure.) Figure 2b , 5 In 7a, 7b, 8, 10, and 12, the sealing gaskets 10 are shown in a free state, although they are actually in an assembled state. Therefore, their respective lips 16, 16a, 16b should not protrude and extend through the outer contour 6 as shown, but should be shown in a pre-tightened position, thus conforming to the shape of the outer contour 6, as... Figure 4 As shown.

[0067] When the lip 16 is in the pre-tightened position, the pre-tightening force applied by the outer contour 6 to the free end of the lip causes an approximate point contact between the free end and the outer contour 6. This pre-tightened position corresponds to the assembled state of the sealing gasket 10 as described above. When the lip 16 is in the stressed position and deforms, the contact area between the free end of the lip and the outer contour 6 increases because the lip 16 is flattened on the outer contour 6. This improves the seal between the lip 16 and the outer contour 6. This stressed position corresponds to the assembled state of the sealing gasket 10 under pressure as described above. This operating mode corresponds to the "external pressure" operating mode of the sealing gasket 10. In practice, the sealing gasket 10 achieves its sealing function through the pressure of fluid F from a conduit outside the conduit on which the sealing gasket is installed, or from one of the other conduits.

[0068] It should be emphasized that the pre-tightened position can seal the interface between the sealing gasket 10 and the outer contour 6, but this sealing is not sufficient for the fluid F under pressure.

[0069] The recess 17 plays a crucial role in this movement because, facing away from the central opening 18, it obstructs the flow of fluid F in the channel 8 and generates pressure within the fluid F, which is the cause of the movement of the lip 16. In effect, the fluid exerts pressure at every point within the recess 17, resulting in deformation of the lip 16 and a localized increase in pressure. Therefore, the higher the pressure of the fluid F, the greater the fluid pressure generated within the recess 17, and consequently, the higher the pressure exerted on the lip 16. In other words, the sealing gasket 10 of the multi-way valve according to the invention achieves adaptation to the pressure of the fluid F, since the achievement of a seal is directly related to the pressure exerted by the fluid F on the sealing gasket 10 (especially the recess 17). The aforementioned threshold obviously depends on the selected material, the size of the recess, and any other parameters affecting the deformation of the lip 16.

[0070] Therefore, compared to existing multi-way valves, the present invention improves the sealing performance achieved at the pipeline. Furthermore, since the gasket seat 12 restricts the rotational torque of the valve core 7, good sealing performance can be maintained over a long period. Moreover, the solution proposed in this invention is less expensive than some existing solutions (particularly those proposing one of the two parts to be metal).

[0071] According to a preferred embodiment, the gasket seat 12 includes a protrusion 13 for ensuring the sealing performance of the gasket 10 at its interface with the valve core 7. The single protrusion 13 helps improve the sealing performance at the interface between the gasket 10 and the valve core 7 and ensures stability around the contact point with the valve core 7, especially when the gasket 10 is used under low pressure (i.e., pressure less than or equal to 3 bar). Preferably, the protrusion 13 faces the valve core 7; that is, the convex portion formed by the protrusion 13 faces the valve core 7. Therefore, starting from the pre-tightened position, especially in the stressed position, the protrusion 13 applies stress to the valve core 7, which is capable of sealing the interface between the gasket 10 and the valve core 7.

[0072] See Figure 5 and 6 According to the second embodiment (a variant of the first embodiment), the deformable membrane 14 still includes a lip 16, but the gasket seat 12 includes two protrusions 13a and 13b. Using two protrusions 13a and 13b instead of the single protrusion 13 seen in the first embodiment further improves the sealing performance of the interface between the gasket 10 and the valve core 7, while ensuring stability around the contact point with the valve core 7, whether under low or high pressure, i.e., pressures greater than 2 bar and less than 5 bar. This also allows for the prevention of premature wear on the other side of the gasket 10. As in the first embodiment, the deformable membrane 14 ensures this sealing function at the interface between the gasket 10 and the peripheral contour 6.

[0073] See Figure 7a and 7bAccording to a third embodiment, the deformable membrane 14 includes two lips 16a, 16b, which are generally asymmetrical, for example, with respect to the transverse plane P1 of the sealing gasket. A first recess 17a faces away from the central opening 18, and a second recess 17b faces the central opening 18. Each recess 17a and 17b impedes the flow of fluid F in the channel 8 and generates pressure in the flow of fluid F, which is the cause of movement of the lips 16a, 16b. According to this variant embodiment, the lips 16 are connected to each other at a connecting portion 14a on the transverse plane P1. Each lip 16a, 16b is arranged relative to the support portion 15 to form the recesses 17a, 17b described above with reference to the first embodiment. Therefore, when fluid F applies pressure to the associated recesses 17a, 17b, each lip 16a, 16b can move independently of the other lip and seal against the outer contour 6; that is, when the lips 16a, 16b move, they seal against the passage 8.

[0074] The multi-way valve 1 according to this embodiment of the invention is particularly advantageous. In fact, in this embodiment, the sealing gasket 10 performs a sealing function for fluid F arriving via channel 8 from a conduit 4 other than the conduit associated with the sealing gasket, as well as for fluid F arriving via channel 8 from a conduit associated with the sealing gasket 10. The position of the valve core 7 and the conduit 4 from which the fluid F originates determine the operating mode of the sealing gasket. The operating mode of the sealing gasket 10 performing a sealing function for fluid F arriving via channel 8 from a conduit 4 other than the conduit associated with the sealing gasket corresponds to the "external pressure" operating mode of the sealing gasket. The operating mode of the sealing gasket 10 performing a sealing function for fluid F arriving via channel 8 from a conduit associated with the sealing gasket 10 corresponds to the "internal pressure" operating mode of the sealing gasket.

[0075] exist Figure 7a In the configuration shown, fluid F flows in pipes 4a, 4b, and 4c (indicated by arrows). Pressure of fluid F enters pipes 4a and 4c, but no fluid flows in pipe 4d. Valve core 7 is semi-cylindrical, allowing it to simultaneously close up to two pipes 4. Therefore, valve core 7 simultaneously closes pipes 4c and 4d. Operation is described below. Fluid F from pipe 4a is directed to pipe 4b. Simultaneously, the sealing gasket 10 associated with pipe 4c blocks fluid F from pipe 4c, operating in both internal and external pressure modes. As for the sealing gasket associated with pipe 4d, it blocks fluid from pipe 4a, thus operating in an external pressure mode.

[0076] exist Figure 7b In the configuration shown, fluid F flows in all the pipes, and therefore in pipes 4a, 4b, 4c, and 4d (as indicated by the arrows). Figure 7aThe implementation example is the same, with the pressure of fluid F entering pipes 4a and 4c. The valve core 7 is semi-cylindrical, enabling it to close up to two pipes. However, in this case, the valve core 7 is arranged to close only pipe 4a. This results in the following operating mode: Fluid F entering the interconnection zone 5 from pipe 4c is diverted to pipes 4b and 4d, which are not closed by valve core 7. The sealing gasket 10 associated with pipe A operates in two modes: it blocks fluid F from pipe 4a in an internal pressure mode and blocks fluid F from pipe 4c in an external pressure mode.

[0077] Therefore, the third embodiment is particularly advantageous because it ensures sealing under all possible configurations. See also Figure 8 and 9 The principle will be explained in more detail based on this double seal. In this embodiment, as well as in the first and second embodiments, it is the interaction between the fluid F and the recesses 17a and 17b that causes the lips 16a and 16b to move from the pre-tightened position (where the sealing gasket 10 has no filling pattern) to the stressed position (where the sealing gasket 10 has a solid filling pattern). In this embodiment, as in the first and second embodiments, the interaction between the fluid F and the recesses 17a and 17b causes the lips 16a and 16b to move from the pre-tightened position (where the sealing gasket 10 has no filling pattern) to the stressed position (where the sealing gasket 10 has a solid filling pattern). Therefore, this is the reason for the movement of the lips 16a and 16b of the membrane 14. When the pressure applied by the fluid F to the recess 17a increases, it causes the lip 16a to deform and be flattened on the outer contour 6. This seals the channel 8, preventing the fluid F from entering the recess 17a. Similarly, when the pressure of fluid F applied to the recess 17b increases, the lip 16b is flattened on the outer contour 6, thereby sealing the channel 8 and preventing fluid F from entering the recess 17b.

[0078] When pressurized fluid arrives from both sides of the sealing gasket 10, both sealing mechanisms occur simultaneously, with the lips flattening away from each other. However, these mechanisms can operate independently and therefore occur at different times. In this embodiment, the sealing gasket 10 of the multi-way valve 1 according to the invention is thus able to adapt to the external and internal pressures applied to the fluid F.

[0079] See still Figure 8 and Figure 9Particularly advantageously, the sealing gasket 10 is X-shaped, with the two ends of the X corresponding to the two protrusions 13a and 13b of the gasket seat 12. These protrusions 13a and 13b have the same sealing function as those described with reference to the second embodiment. Furthermore, the other two ends of the X-shape correspond to the free ends 160a and 160b of the lips 16a and 16b, respectively. Preferably, the two protrusions 13a and 13b are substantially radially aligned with the free ends 160a and 160b of the lips. More specifically, the first protrusion 13a is substantially radially aligned with the free end 160a of the first lip 16a, and the second protrusion 13b is substantially radially aligned with the free end 160b of the second lip 16b. That is, a deviation of up to 10° relative to the centerline is permissible.

[0080] This configuration is highly advantageous because it significantly improves the mechanical stability of the gasket 10 in all operating modes (i.e., external pressure only, internal pressure only, and both external and internal pressure). In fact, if the fluid F applies pressure to only one of the recesses 17a, 17b, the protrusions 13b, 13a, radially aligned with the free ends of the lips associated with the other recess 17b, 17a, act as annular contact points, preventing the gasket 10 from tilting.

[0081] In this respect, it should be noted that if the gasket 10 comprises only a single protrusion 13 (e.g., located at the radially aligned position of the connection 14a), then when the fluid F applies pressure to only one recess of the gasket 10, the gasket will tilt, causing pressure release on one side of the gasket seat 12, resulting in a loss of contact pressure. In fact, the free surface between the single protrusion and the edge of the gasket seat 12 will be too large, which will reduce the contact pressure and decrease the seal. Conversely, when the pressure applied to the recesses 17a, 17b differs significantly from the pressure applied to the other recess 17b, 17a, the gasket may tip over.

[0082] In this regard, it is advantageous that the first protrusion 13a and the second protrusion 13b are configured to form point-like annular contacts with the valve core 7, respectively. Compared to a case where the contact surface is essentially planar, this helps to balance the pressure on both sides of the sealing gasket 10, thereby significantly improving sealing performance and reducing friction.

[0083] Advantageously, the first surface 12a of the gasket seat is made of polytetrafluoroethylene (PTFE). PTFE has excellent chemical resistance and heat resistance, making it particularly suitable for the intended use involved in this invention. Furthermore, its low coefficient of dynamic friction reduces friction between the gasket and the opposing surface. This characteristic makes it suitable for the sealing gasket 10 of the multi-way valve 1 as in the first embodiment, but even more particularly suitable for the sealing gasket 10 of the multi-way valve 1 as in the third embodiment. In fact, in the latter case, the area of ​​the first surface 12a of the gasket seat is much larger than that of the first surface of the gasket seat 12 in the first embodiment, thus resulting in a larger potential friction surface. Using PTFE to make the gasket seat 12 significantly reduces friction between the first surface 12a of the gasket seat and the valve core 7, thereby limiting the rotational torque of the valve core 7.

[0084] Preferably, the gasket seat 12 is made of a material selected from pure PTFE, glass fiber-filled PTFE, carbon-filled PTFE, polyvinylidene fluoride (PVDF), polyetheretherketone (PEEK), polyaryletherketone (PEAK), polyphenylene amide (PPA), polyphenylene sulfide (PPS), polycaprolactam (PA6), and polyamide 66 (PA66). Glass fiber-filled PTFE and carbon-filled PTFE have better abrasion resistance and dimensional stability than pure PTFE. Therefore, glass fiber-filled PTFE and carbon-filled PTFE are preferred over pure PTFE because they help extend the service life of the sealing gasket 10.

[0085] Depending on the specific implementation that may be used in all embodiments, the deformable membrane 14 is made of a rubber material selected from ethylene propylene diene monomer (EPDM), hydrogenated nitrile butadiene rubber (HNBR), ethylene acrylate rubber (AEM), polyacrylate rubber (ACM), silicone honeycomb rubber (VMQ), nitrile butadiene rubber (NBR), polyurethane rubber (PU), and thermoplastic rubber (TPE). In practice, the material chosen depends primarily on the intended application. EPDM and HNBR are particularly suitable for use as gaskets 10 in coolant thermal management modules. That is, for "oil" applications, the deformable membrane 14 is preferably made of AEM or ACM rubber.

[0086] Advantageously, the thickness of the gasket seat 12 is 0.05 mm to 1.5 mm, preferably 0.1 mm to 0.5 mm, which allows for a balance between obtaining gasket seat 12 with sufficient mechanical strength and the radial dimension of sealing gasket 10.

[0087] See Figure 10 and Figure 11According to the fourth embodiment (a variant of the third embodiment), the deformable membrane 14 still includes two lips 16a and 16b, but the gasket seat 12 includes a protrusion 13. The sealing gasket 10 of the multi-way valve according to this embodiment is particularly advantageous because, in cases of inaccurate assembly (statically indeterminate), it allows for further improvement in sealing performance compared to a sealing gasket with two protrusions 13a, 13b.

[0088] according to Figure 12 In the specific embodiment shown, the stop 6a is a reinforcing ring that forms the contour of the inlet 40. This arrangement prevents any risk of warping of the sealing gasket 10 at its inner diameter (especially at the contour of the opening 18).

[0089] As previously described, the distributor housing 3 forms a plurality of conduits 4. In this embodiment, the distributor 2 includes three to four conduits 4. That is, the distributor may include at least two conduits. In this regard, the multi-way valve 1 may include a gasket section 11 comprising a plurality of sealing gaskets 10 spaced apart from each other by thinned portions 19 connecting the sealing gaskets. An example of this embodiment is as follows: Figure 13a and Figure 13b As shown. Therefore, multiple pipes 4 can be sealed by a single gasket segment 11 containing multiple sealing gaskets 10. The thinned portion 19 connecting the sealing gaskets 10 allows the overall shape of the gasket segment 11 to conform to the shape of the outer contour 6. In this way, the gasket segment 11 can still be manufactured in a planar manner while taking into account the geometry of the distributor 2.

[0090] The constructions shown in the accompanying drawings are merely possible examples of the invention and are not limiting; rather, they include variations of the design that can be implemented by those skilled in the art.

Claims

1. A multi-way valve (1), comprising: - Distributor (2), the distributor (2) includes a housing (3) having a plurality of fluid (F) flow lines (4), an interconnection area (5) for the lines (4), and a valve core (7), the interconnection area (5) having a central axis (X) and including a peripheral profile (6), the valve core (7) being disposed in the interconnection area (5) such that the radial outer surface of the valve core (7) is separated from the peripheral profile (6) by a channel (8) of the fluid (F), the valve core (7) also being able to rotate about the central axis (X) to prevent or allow the fluid (F) to flow in the lines (4); - A sealing gasket (10) is radially positioned around each conduit (4) between the outer contour (6) and the valve core (7), each sealing gasket (10) comprising: - A through-center opening (18) having a longitudinal axis (A) and arranged in the extension direction of the conduit (4) to allow the fluid to flow through the sealing gasket (10); - A pad seat (12), said pad seat (12) being arranged around the central opening (18) and having a first surface (12a) facing the valve core (7); and - A deformable membrane (14), the deformable membrane (14) comprising a support portion (15) fixed on a second surface (12b) opposite to the first surface (12a) of the pad seat, and two lips (16a, 16b) connected to each other at a connecting portion (14a) on a transverse plane (P1), each lip (16a, 16b) being arranged relative to the support portion (15) to form a recess (17a, 17b); The coefficient of dynamic friction between the pad seat (12) and the valve core (7) is lower than the theoretical coefficient of dynamic friction between the deformable membrane (14) and the valve core (7). The first recess (17a) faces the opposite direction to the central opening (18), the second recess (17b) faces the central opening (18), and the lips (16a, 16b) are movable to seal and block the flow of fluid in the channel (8).

2. The multi-way valve (1) according to claim 1, wherein, The sealing gasket (10) is X-shaped, and the gasket seat (12) includes two protrusions (13a, 13b) corresponding to the two ends of the X-shape.

3. The multi-way valve (1) according to any one of the preceding claims, wherein, The pad seat (12) is made of a material selected from pure polytetrafluoroethylene (PTFE), glass fiber filled PTFE, carbon filled PTFE, polyvinylidene fluoride (PVDF), polyether ether ketone (PEEK), polyarylether ketone (PEAK), polyphenylene amide (PPA), polyphenylene sulfide (PPS), polycaprolactam (PA6), and polyamide 66 (PA66).

4. The multi-way valve (1) according to any one of the preceding claims, wherein, The deformable membrane (14) is made of a rubber material selected from ethylene propylene diene monomer (EPDM), hydrogenated nitrile butadiene rubber (HNBR), ethylene acrylate rubber (AEM), polyacrylate rubber (ACM), silicone honeycomb rubber (VMQ), nitrile butadiene rubber (NBR), polyurethane rubber (PU), and thermoplastic rubber (TPE).

5. The multi-way valve (1) according to any one of the preceding claims, wherein, The thickness of the pad seat (12) is 0.05 mm to 1.5 mm, preferably 0.1 mm to 0.5 mm.

6. The multi-way valve (1) according to any one of the preceding claims, wherein, Each pipe (4) includes an inlet (40) for the fluid (F) from the interconnection area (5), and wherein the outer contour (6) includes a stop (6a) located between the inlets (40) of two adjacent pipes (4).

7. The multi-way valve (1) according to claim 6, wherein, The stop (6a) is a reinforcing ring that forms the outline of the entrance (40).

8. The multi-way valve (1) according to any one of the preceding claims, the multi-way valve (1) comprising a gasket section (11) comprising a plurality of sealing gaskets (10) spaced apart from each other by a thinning portion (19) the thinning portion (19) connecting the plurality of sealing gaskets (10).

9. The multi-way valve (1) according to claim 8, wherein, Each sealing gasket (10) has an overall curved shape with the convex side facing the associated conduit (4).

10. A fluid (F) management system comprising a multi-way valve (1) according to any one of claims 1 to 9.

11. The system according to claim 10, wherein, The fluid management system is a thermal management module.

Images