Pressure-equalising device for a container, container comprising a pressure-equalising device, and vehicle comprising a container

Abstract

The invention relates to a pressure-equalising device which is provided for a container, preferably for a housing of a vehicle battery, and comprises a housing (8) which is provided with at least one inlet (11) for a gas. A semi-permeable membrane (34) is arranged downstream of the inlet (11, 75) in the flow direction of the gas out of the container (8). It is in a first position in front of an outlet (27) and in a second position behind the outlet (27). The pressure-equalising device also has a valve element (36) arranged downstream in the flow direction of the gas. The valve element (36) comprises a through-opening (56) for the gas, which can be closed by a closing body (57). When unpressurised, the closing body (57) closes the through-opening (56). In a venting state, the closing body (57) at least partially opens the through-opening (56).

Description

[0001] Pressure equalization device for a container, container with a pressure equalization device and vehicle with container

[0002] The invention relates to a pressure equalization device for a container according to the preamble of claim 1, a container with such a pressure equalization device according to claim 9 and a vehicle with such a container according to claim 10.

[0003] Traction batteries in electric vehicles are housed in specially designed containers that provide mechanical protection against external influences such as shocks or vibrations. These containers are typically made of lightweight yet robust materials, such as aluminum or composites, to simultaneously reduce vehicle weight and ensure the safety of the battery cells. Furthermore, the containers are often equipped with thermal management systems to regulate battery temperature, thereby optimizing performance and lifespan.

[0004] To allow pressure equalization between the ambient pressure and the internal pressure of the container, a pressure equalization device is provided. Gases can flow from the container interior to the outside or from the outside into the container interior via the inlet and outlet. The valve element is located in the area between the inlet and the outlet and is at least partially gas-permeable. The gas can thus flow through the valve element.

[0005] If excessive pressure occurs in the container, for example due to a malfunction, the valve element is moved from the first position to the second position. In this second position, the gases from inside the container can flow directly from the inlet to the outside through the outlet, bypassing the valve element. This allows high pressure inside the container to be reduced quickly. The invention is based on the objective of designing the generic pressure equalization device, the container, and the vehicle in such a way as to enable pressure equalization.

[0006] This problem is solved according to the invention in the generic pressure equalization device with the characterizing features of claim 1, in the container with the features of claim 9 and in the vehicle with the features of claim 10.

[0007] In the pressure equalization device according to the invention, the closing element closes the passage opening of the valve element when a pressureless state prevails. "Pressureless" here means that the pressure inside the container is equal to the pressure outside the container, or equal to atmospheric pressure, or that no differential pressure is measurable.

[0008] If the pressure in the container is greater than atmospheric pressure, the pressure equalization device is put into a venting state.

[0009] The overpressure acts on the valve element and the closing element, causing the closing element to change its relative position to the valve element. This change in the closing element's position opens the passage, allowing the pressurized gas to flow through the open passage towards the outlet.

[0010] Conversely, if the external pressure is higher than the pressure inside the container, the valve element and the closing element are also moved within the pressure equalization device under the pressure of the outside air. This causes the closing element to change its position relative to the valve element, thus opening the passage. Accordingly, outside air can then flow through the passage into the interior of the container. It is particularly advantageous if the valve element deforms elastically when pressurized. This elastic deformation leads to a change in the position of the closing element relative to the valve element, thereby opening or closing the passage.

[0011] Advantageously, the closing element overlaps and / or undercuts the edge of the valve element's passage opening. This ensures that the closing element cannot completely detach from the valve element and be lost, even if the latter is elastically deformed.

[0012] Preferably, this is achieved by an annular projection on the valve element, which, as already described, extends over and under the closing element. The annular projections can be wide enough that the valve element is engaged by at least one of the two annular projections in any position. This ensures that the closing element cannot completely detach from the valve element in a deformation position and be lost.

[0013] To ensure that gas can reliably flow from or into the container interior, the closure element has at least one cavity for the gas. This cavity is specifically designed to extend into or through the respective annular projection of the closure element.

[0014] Advantageously, the ring projections are provided with several cavities around their circumference, ensuring good flow in both directions.

[0015] The valve element advantageously features a circumferential sealing edge at the perimeter of the passage opening. In the pressure-free state of the pressure equalization device, this sealing edge rests against a mating surface of the closing element, thus blocking the passage opening. The passage opening is dimensioned such that its diameter is slightly smaller than the outer diameter of the valve element. This interaction creates a kind of interference fit, generating an annular tension within the valve element. This annular tension results in a force-fit connection between the passage opening and the valve element, ensuring reliable fixation and sealing.

[0016] As previously mentioned, the valve element has a circumferential sealing edge at the perimeter of the passage opening. When a venting or purging condition occurs, the valve element is elastically deformed due to the acting forces, perpendicular to the stress generated by the ring tension. This deformation causes the sealing edge to assume a defined distance from the opposing surface of the closing element, thereby selectively eliminating the sealing effect and creating a gas- or fluid-permeable condition.

[0017] The container according to the invention is provided with the pressure equalization device according to the invention. If this container is installed in a vehicle, for example, the pressure equalization device ensures that pressure equalization takes place between the inside of the container and the environment.

[0018] The vehicle according to the invention is equipped with the container according to the invention. This also prevents an impermissibly high pressure from building up in the container, which could lead to damage or even destruction of the vehicle.

[0019] The subject matter of the application is not only defined by the subject matter of the individual patent claims, but also by all information and features disclosed in the drawings and the description. These are claimed as essential to the invention, even if they are not explicitly stated in the claims, insofar as they are novel, individually or in combination, compared to the prior art. Further features of the invention are revealed in the additional claims, the description, and the drawings.

[0020] The subject matter of the invention will be explained in more detail with reference to the exemplary embodiments shown in the drawings. These show

[0021] Fig. 1 shows a first embodiment of the pressure equalization device according to the invention in axial section in a pressureless state (neutral position),

[0022] Fig. 2 shows a second embodiment of the pressure equalization device according to the invention in axial section, with a shortened design in a pressureless state (neutral position).

[0023] Fig. 3 shows a part of the pressure equalization device in enlarged detail.

[0024] schematic representation according to Fig. 2 in axial section in pressureless state (neutral position),

[0025] Figs. 4a, 4b show a closing element of the pressure equalization device according to the invention as shown in Figs. 1 and 2 in different perspective views and in two different embodiments.

[0026] Fig. 5 shows the pressure equalization device according to Fig. 2 in axial section in a venting position,

[0027] Fig. 6 shows a part of the pressure equalization device in an enlarged, schematic representation according to Fig. 5 in axial section in a venting position,

[0028] Fig. 7 shows the pressure equalization device according to Fig. 2 in axial section in a ventilation position, Fig. 8 shows a part of the pressure equalization device in enlarged, schematic representation according to Fig. 7 in axial section in a ventilation position.

[0029] The pressure equalization device serves to vent and aerate the interior of a housing, such as the housing of a battery, particularly in an electric vehicle. Battery modules are housed within the casing in a known manner. Each battery module consists of several battery cells.

[0030] The housing, which is advantageously made of metal, has at least one mounting opening for the pressure equalization device. The pressure equalization device is sealed in the mounting opening when installed and ensures pressure equalization between the inside of the housing and the external pressure. The pressure equalization device prevents the housing from deforming noticeably due to fluctuations in external or internal pressure conditions or temperature.

[0031] The housing contains additional components besides the battery modules. These are typical for such batteries and include, for example, components for managing or temperature-controlling the battery modules.

[0032] The housing can have any suitable design. Depending on the size of the housing, one, two, or more pressure equalization devices can be provided. The mounting opening and the pressure equalization device can be located on any suitable side of the housing.

[0033] The pressure equalization device is designed to allow pressure equalization and also to provide emergency venting of the housing should increased pressure occur inside, for example, due to a malfunction. This can happen, for instance, if one or more battery cells or modules are outgassing. In such a case, the pressure equalization device ensures that the interior of the housing can be directly connected to the environment, allowing the pressure inside the housing to be reduced quickly.

[0034] Figure 1 shows a pressure equalization device with a flat support 1 which, in its installed position, rests against an outer surface of the (not shown) housing, in particular a battery housing, in a sealed manner. The support 1 can have any desired shape and has mounting openings 2 for fasteners, such as screws, with which the support 1 can be attached to the outer surface of the housing. The mounting openings 2 are distributed throughout the support 1. Alternatively, a plug-in or snap-in connection can be provided, which allows for simple and quick assembly and, if necessary, can be just as easily disconnected without the need for additional tools.

[0035] The carrier 1 is provided on its underside 3 with an annular groove 4 for receiving a sealing element 5. The sealing element 5 is advantageously a sealing ring that can be easily inserted into the annular groove 4 and which, in the installed position, seals the carrier 1 against the housing.

[0036] The carrier 1 can alternatively be provided with a flat gasket 5 on its underside 3, which is positioned directly between the underside 3 of the carrier and the housing surface. The annular groove 4 for receiving a sealing element 5 can therefore be omitted.

[0037] The carrier 1 is further provided with a receiving opening 6, which is preferably centrally located in the carrier 1 and through which a receptacle 7 of a valve housing 8 projects. The receptacle 7 is advantageously cylindrical and its outer surface rests against an inner wall 9 of the receiving opening 6. A closure element 10 is inserted into the lower end of the receptacle 7, which is clearly visible in Fig. 1. This closure element is connected to the receptacle 7 and has at least one channel 11. If only one channel 11 is provided, it is advantageously located centrally in the closure element 10.

[0038] The locking element 10 further comprises a ring flange 12 projecting radially outwards beyond the receptacle 7, against which the lower end of the receptacle 7 rests.

[0039] The locking element 10 projects into the receptacle 7, sealed by a locking part 13, and its outer surface rests against the inner surface of the receptacle 7. The locking part 13 is preferably positioned in the receptacle 7 by a releasable connection, e.g., a snap-fit ​​connection or by screwing it in.

[0040] The end of the receptacle 7 facing away from the closure element 10 transitions into a support flange 14, which rests on the top surface 16 of the support 1 with at least one sealing element 15 in between.

[0041] The sealing element 15 is advantageously designed in an annular shape and has a sealing lip 17 which rests on the top surface 16 of the support 1 under elastic deformation.

[0042] The sealing element 15 is provided at the outer edge of the support flange 14, which has a circumferential recess 18 for receiving the sealing element 15, into which the sealing element 15 projects. The circumferential recess 18 is provided on the side of the support flange 14 facing away from the support 1.

[0043] The support flange 14 projects radially outwards from a receiving part 19, which is provided with a recess 20 on its end face. The recess 20 is bounded by an annular rim 21, which limits the recess 20 radially outwards. The support flange 14, the receiving part 19, and the rim 21 are advantageously formed integrally.

[0044] A cover 22, which is advantageously formed in one piece, is placed on the receiving part 19. The cover 22 has a flat covering part 23, to the edge of which a sleeve 24 adjoins, which is preferably cylindrical.

[0045] The mantle 24 connects the cover part 23 with a radially outward extending ring flange 25, the outer edge 26 of which runs at an angle towards the support 1.

[0046] The ring flange 25 overlaps and the edge 26 surrounds the sealing element 15, which is thus securely positioned. The edge 26 rests against the radial outer side of the sealing element 15.

[0047] The use of the angled edge 26 and the ring flange 25 increases the mechanical stability of the entire connection and minimizes the risk of damage from stress or vibration. Furthermore, this arrangement also compensates for potential manufacturing tolerances, as the ring flange 25 and the edge 26 hold the sealing element 15 securely and tightly even with minor deviations.

[0048] The outer surface 24 of the lid 22 rests against the outside of the ring-shaped receiving part 19. This makes it easy to mount the lid 22 onto the receiving part 19.

[0049] The cover part 23 has an axial distance from the receiving part 19 or its edge 21.

[0050] The cover 22 can be securely connected to the receiving part 19 in any suitable manner. For example, both parts can be connected by frictional and / or positive locking. The cover 22 can, for instance, be connected to the receiving part 19 via locking lugs. These interlock and ensure a positive locking connection.

[0051] Ventilation openings 27 are provided in the jacket 24 at a distance from each other, which allow gases to escape from the housing to be sealed to the outside, preferably into the environment, and also to enter the housing from the outside, depending on the pressure or flow conditions.

[0052] A diaphragm holder 28 is provided in the receiving part 19. The diaphragm holder 28 comprises a sleeve part 29, which projects into the sleeve-shaped receptacle 7 of the valve housing 8 and rests against its inner wall.

[0053] The sleeve part 29 protrudes from a support part 30, which is designed as a ring flange that lies within the recess 20 of the receiving part 19 of the valve housing 8.

[0054] At the transition from the receptacle 7 to the support flange 14, the support flange 14 is provided with an annular recess 31, on the bottom 32 of which the support part 30 rests with an annular flange part 33.

[0055] The flange part 33 connects the sleeve part 29 to the flange-shaped support part 30 of the diaphragm holder 28. The support part 30 and the flange part 33 are advantageously parallel to each other and at different axial heights of the diaphragm holder 28.

[0056] A membrane 34 is arranged on the support element 30, which preferably consists of polytetrafluoroethylene (PTFE), such as standard PTFE film, expanded PTFE (ePTFE) or a PTFE composite material.

[0057] The membrane 34 is waterproof and semipermeable, so that it completely blocks liquid water, but selectively allows the passage of gas or vapor phases. The membrane 34 preferably rests with its edge region on the support part 30 and is attached to the support part 30 by gluing, vulcanization, ultrasonic welding or mechanical fixing, such as a screw or clamp fastening.

[0058] Alternatively, the membrane 34 can also be attached to the support part 30 by sealing or vulcanizing, whereby the punching and sealing or vulcanizing of the membrane 34 can be carried out in an integrated process step.

[0059] The membrane 34 is also located at a distance from the flange part 33 and the cover part 23 of the lid 22.

[0060] As already mentioned, the membrane 34 is designed to be semipermeable, so that the gas can diffuse through the membrane 34 and escape through the ventilation openings 27 in the cover 22 from the pressure equalization device to the outside, or vice versa.

[0061] Membrane 34 is specifically designed to allow gases to pass through while reliably retaining particles, liquids (especially moisture), and other unwanted substances. This semipermeable property offers crucial advantages, particularly in applications where safe and controlled pressure equalization is required.

[0062] Advantageously, the diaphragm 34 is designed such that it does not project radially beyond the edge of the diaphragm holder 28, but is advantageously set back radially. This prevents damage to the diaphragm 34 during use of the pressure equalization device simply and reliably.

[0063] In the initial position shown in Fig. 1, the membrane holder 28 and the membrane 34 attached to it extend axially beyond the edge of the receiving part 19, which also contributes to the protection of the membrane 34. Alternatively, the membrane holder 28 can also be designed to be very flat or without any significant protrusion or indentation, extending in width, which significantly reduces the overall height of the assembly. This flat design of the membrane holder 28 is particularly suitable for applications where a compact design is required or where the available installation space is limited. Despite the reduced height, the membrane holder 28 remains able to reliably fix the membrane 34 in its intended position and apply the necessary clamping force. Stability and functionality can be ensured through an adapted geometry and suitable material selection.The membrane holder 28 can be made of high-strength materials such as aluminium, stainless steel or reinforced plastics to ensure stability despite low height (see Fig. 2).

[0064] The outer diameter of the membrane holder 28 is smaller than the inner diameter of the rim 21, so that in case of danger the membrane holder 28 can simply be moved axially relative to the rim 21.

[0065] The valve housing 8 is subjected to the force of an elastic return element. Any suitable component that provides the required return force can be used as a return element. Preferably, a compression spring 41, as shown in Fig. 1, is used, which is supported at one end on the annular flange 12 of the closure element 10 and at its other end on a base 42 of an annular groove 43 in the underside 3 of the carrier 1.

[0066] The compression spring 41 surrounds the sleeve-shaped receptacle 7 of the valve housing 8. The compression spring 41 pulls the support flange 14 of the valve housing 8 against the top surface 16 of the support 1, thereby elastically deforming the sealing element 15 and sealing the support flange 14 against the support 1. An actuator (not shown) can also be provided instead of an elastic return element or the compression spring 41.

[0067] Furthermore, the pressure equalization device includes a valve element 36. The valve element 36 is designed such that it gas-tightly surrounds the sleeve part 29 of the diaphragm holder 28. Preferably, this surround is formed by positive locking and / or friction locking, thereby ensuring a reliable connection and uniform pressure transmission.

[0068] Alternatively or additionally, the valve element 36 can be connected to the sleeve part 29 at the end face by gluing, sealing or vulcanizing to ensure a gas-tight connection.

[0069] The valve element 36 is located at an axial distance from the closure element 10, which is attached to the free end of the valve housing 8, preferably by screwing, pressing, snapping or gluing.

[0070] The valve element 36, which advantageously has a circular shape in the axial view, consists of a rubber or a comparable elastomeric material.

[0071] Examples include natural rubber (NR), silicone rubber (VMQ), ethylene propylene diene monomer rubber (EPDM), nitrile rubber (NBR), fluororubber (FKM, e.g. Viton), chloroprene rubber (CR, e.g. Neoprene), polyurethane (PU), thermoplastic elastomers (TPE), styrene-butadiene rubber (SBR), and butyl rubber (HR).

[0072] The circular shape allows for evenly distributed ring stress during installation and operation, which is particularly advantageous in oscillating movements or fluctuating pressure conditions. The material used is selected for its excellent elasticity, ensuring a reliable seal while resisting the repeated deformations that occur during operation. Furthermore, the elastomeric material offers high resistance to aging, chemical influences, and temperature fluctuations, significantly extending the service life of the valve element 36.

[0073] Furthermore, the choice of material allows the valve element 36 to be adapted to specific operating conditions, such as pressure ranges, temperature requirements, or chemical resistance, by using different elastomers or rubber types, as already mentioned by way of example (but not exhaustively). This makes the valve element 36 versatile and suitable for a wide range of applications.

[0074] The valve element 36, as greatly simplified and shown by way of example in Fig. 1, is designed as a flat disk and transitions at the edge into a sleeve 54, with which the valve element 36 is attached to the outside of the sleeve part 29.

[0075] To increase mechanical stability and functional reliability, the valve element 36 can be provided with reinforcing structures. These reinforcements can be, for example, in the form of ribs, ring reinforcements, or structured surfaces to achieve targeted stiffness or flexibility in defined areas of the valve element 36.

[0076] The integration of such reinforcing structures ensures that the valve element 36 functions reliably even under changing pressure conditions, enables controlled valve opening, and simultaneously guarantees a long service life. The sleeve part 29 is provided with a circumferential recess 55 for receiving the jacket 54, which is open towards the end face of the sleeve part 29 and in which the jacket 54 of the valve element 36 can be securely fastened.

[0077] The valve element 36 itself is provided with a central opening 56 into which a closing element 57 is inserted.

[0078] The aforementioned reinforcing structures can be specifically formed around the central opening 56 to ensure increased stability and defined deformation characteristics of the valve element 36. These structures can be designed in the form of ribs, ring reinforcements, or thickenings to specifically increase the load-bearing capacity in this area and optimize the mechanical properties of the valve element 36.

[0079] The valve element 36 and the closing body 57 are designed such that the closing body 57 closes the opening 56 in a neutral position.

[0080] As soon as the valve element 36 is elastically deflected, a passage 58 is created between the edge of the opening 56 or the opening edge 59 of the valve element 36 and the closing body 57.

[0081] In the unpressurized state (Figs. 1, 2 and 5), the valve element 36 with its opening edge 59 seals against a counter surface 60 of the closing body 57 (Figs. 1 and 5).

[0082] In an alternative embodiment to the variant shown in Fig. 1, as shown in Fig. 2, the transition from the receptacle 7 to the support flange 14 is significantly shortened. The elastic return element or compression spring 41 can also be designed as a disc spring or as a spring plate. The shortened transition allows for a more space-saving design overall, which is particularly advantageous in applications with limited installation space.

[0083] At the transition from the receptacle 7 to the support flange 14, the support flange 14 is provided with an annular recess 14b. The support flange 14 with its recess 14b also acts as a buttress and, together with the underside of the diaphragm holder 28, works to securely fix the valve element 36 in its intended position. This arrangement ensures a stable position of the valve element 36 and supports its function within the overall system.

[0084] Preferably, the outer edge 36b (Fig. 2) of the valve element 36 is thickened in this area to ensure improved fixation and stabilization of the valve element 36 in its intended position. This design helps to reliably ensure functionality, and in particular tightness, at different deflections of the valve element 36 under load or pressure.

[0085] For this purpose, a circumferential groove 28b can be provided in the support flange 14 or in its recess 14b and / or in the underside of the diaphragm holder 28, which creates a positive fit with the thickened outer edge 36b of the valve element 36. This groove 28b helps to optimize the positioning and stability of the valve element 36 and prevents slippage or rotation during operation.

[0086] To ensure the necessary clamping of the outer edge 36b of the valve element 36, a clamping force is applied via the cover 22 during assembly. This clamping force is transferred by the diaphragm holder 28 to the outer edge 36b, thereby clamping it firmly against the support flange 14 in its recess 14b. This design ensures reliable fixation and contributes to the sealing and functional reliability of the valve element 36.

[0087] The cover 22 can be securely connected to the receiving part 19 in any suitable manner. For example, both components can be connected by frictional and / or positive locking. The cover 22 can be connected to the receiving part 19 via locking lugs. These interlock and ensure a positive locking connection. Alternatively, the two components can also be screwed together.

[0088] To prevent excessive compression of the valve element 36, particularly of the outer edge 36b to be compressed, a spacer element 80 can be provided between the diaphragm holder 28 and the support flange 14. This spacer element 80 limits the closing force exerted on the valve element 36 by acting as a mechanical stop and defining the maximum compression. This ensures that the valve element 36 is neither damaged nor its functionality impaired. The spacer element 80 can be made of a dimensionally stable material such as metal or a high-strength plastic to withstand the forces permanently.

[0089] As already described in the previous embodiment according to Fig. 1, the valve element 36 itself is provided with a central, preferably circular, opening 56 into which the closing element 57 is inserted. The valve element 36 and the closing element 57 are designed such that, in its neutral position, the closing element 57, as also shown, blocks the opening 56 (Fig. 3) from allowing gas to flow.

[0090] The spacer element 80 is advantageously designed as an annular disk, the outer edge 81 of which is raised by 90°. The edge 81 is surrounded by the edge 21 of the support flange 14 and rests against the edge 21. The membrane holder 28 is advantageously provided with a raised circumferential edge 28a, the end face of which rests against the underside of the cover 22. The edge 81 of the spacer element 80 lies between the edges 28a, 81 of the membrane holder 28 and the spacer 80.

[0091] As shown in Fig. 2, the edge 21 of the support flange 14 and the edge 81 of the spacer 80 are spaced away from the cover 22. Advantageously, the end faces of the edges 21, 81 are flush with each other.

[0092] Fig. 3 shows a portion of the pressure equalization device according to Fig. 2 in an enlarged axial section in the unpressurized state (neutral position). In particular, Fig. 3 schematically illustrates the connection between a valve element 36 and a closing element 57 in the unpressurized state (neutral position). When the pressure in the container and in the environment are equal, i.e., when the pressure is unpressurized, the valve element 36, with a sealing edge 62, rests against a counter surface 60 of the closing element 57 under radial preload. This prevents gas exchange between the interior of the container and the environment.

[0093] The flow arrows shown as examples illustrate that the gas cannot flow outwards beyond the sealing edge 62.

[0094] Conversely, the surrounding gas cannot flow into the container. In this depressurized state, the valve element 36 assumes a planar position, lying in a radial plane of the pressure equalization device.

[0095] The closing element 57, like the opening 56, has a circular cross-section and is provided on its outer surface with a circumferential annular groove 61. The base of the annular groove 61 forms the mating surface 60 for the opening rim 59.

[0096] Alternatively, the closing element 57 can also have an oval cross-sectional shape, which is particularly advantageous in cases of specific flow requirements or space constraints. With an oval cross-section, the annular groove 61 is adapted to the oval shape so that the bottom of the groove 61 continues to serve as a mating surface 60 for the opening edge 59. This design allows for flexible adaptation to different geometries without impairing the sealing and functional properties.

[0097] The mating surface 60 is designed as a conical surface whose diameter decreases towards the cover 22 (see Fig. 1). Alternatively, depending on the application, a conical surface can also be provided whose diameter increases towards the cover 22. The choice of conical surface allows for adaptation to the respective functional requirements, such as targeted force transmission, the distribution of sealing forces, or flow guidance. Depending on the requirements for sealing, flow behavior, or mechanical loads, the angle and length of the conical surface can vary.

[0098] The mating surface 60 can alternatively be cylindrical, so that it has a constant diameter over its entire height. This design provides a uniform contact or sealing surface, which is particularly advantageous in applications where a uniform distribution of forces or stable guidance for the opening edge 59 is required.

[0099] The opening edge 59 of the valve element 36 is designed in axial section such that it has a circumferential sealing edge 62 which runs in a radial plane and extends over the entire circumference of the opening edge 59.

[0100] Extending from the sealing edge 62 are two wall sections 63 and 64, which reach the top 65 and bottom 66 of the valve element 36, respectively. These wall sections 63 and 64 run at opposite angles to each other, forming a conical structure that enables targeted force and sealing distribution along the opening edge 59. The angled position of the wall sections 63 and 64 also contributes to the mechanical stability and prevents deformation of the valve element 36.

[0101] The opening 56 of the valve element 36 and the associated opening edge 59 are designed such that, in the unpressurized state (see Fig. 2), the sealing edge 62 bears against the counter surface 60 with a radial force due to the existing radial tension. This force-fit connection prevents gas from flowing under the sealing edge 62, thus effectively preventing uncontrolled exchange between the interior of the container and the environment, whether from the inside to the outside or vice versa.

[0102] The sealing edge 62 can be designed in different versions to meet the specific requirements of the respective application. In a simple version, the sealing edge 62 is straight or slightly rounded and rests directly on the sealing surface 60.

[0103] Alternatively, the sealing edge 62 can be designed with a round profile, which achieves an even distribution of force.

[0104] Another variant of the sealing edge 62 is the wedge-shaped design, in which it tapers to a narrow point. The design of the sealing edge 62 depends on the pressure conditions, the movement of the components, and the requirements for the sealing effect.

[0105] Preferably, the sealing edge 62 is made of the same material as the valve element 36, thereby ensuring a homogeneous structure and ring tension and also simplifying manufacturing.

[0106] Alternatively, the sealing edge 62 can be manufactured from a different material to specifically adapt it to particular operating conditions. Elastomers are preferably used as suitable materials for this purpose. The choice of material for the sealing edge 62 thus enables optimization with regard to its sealing effect, service life and suitability for use in different environments and operating conditions.

[0107] The annular groove 61 is bounded at both its axial ends by an annular projection 67, 68. These annular projections 67, 68 define the axial limits of the annular groove 61 and serve to precisely position the inserted valve element 36 and to hold it in the intended position.

[0108] The ring projections 67, 68 also contribute to ensuring that the inserted valve element 36 remains securely in the annular groove 61, even under mechanical stress or pressure, thus guaranteeing the long-term functionality of the design.

[0109] The valve element 36 is gripped in the area of ​​the opening 56 by the two ring projections 67, 68 in such a way that the closing element 57 cannot completely detach from the valve element 36 and is captive.

[0110] The valve element 36 can also be partially thickened and / or partially tapered in the area of ​​the opening 56, where it is engaged by the two annular projections 67, 68. Such an adjustment of the material thickness allows for targeted optimization of the mechanical properties of the valve element 36 in the area of ​​the opening 56.

[0111] A thickening in this area increases stability and resistance to pressure differences. Conversely, a tapered section increases the elasticity of the valve element in this area.

[0112] Figures 4a and 4b each show the locking element 57 in a perspective view. More precisely, Figure 4a shows the locking element partially from the side and above, while Figure 4b shows a partially from the side and below. These illustrations clarify the geometric details and the specific design of the locking element 57 from different perspectives.

[0113] In Fig. 4a, the locking element 57 is shown as a unit composed of several components. The locking element 57 has a base body 57b and already includes the annular projection 67. The annular projection 68 is subsequently attached to the base body 57b, in particular by screwing it on.

[0114] Alternatively, both annular projections 67, 68 can be subsequently attached, in particular by screwing, clipping, or fixing them using a similar connection technique. The annular groove 61 is formed between the annular projections 67, 68. This annular groove 61 serves, as already explained, as a receptacle for the valve element 36.

[0115] The geometric design of the annular groove 61 in combination with the two annular projections 67, 68 ensures that the valve element 36 remains securely in place, even under mechanical loads or pressure.

[0116] In contrast to Fig. 4a, in Fig. 4b the closing element 57 is shown as a one-piece component, which comprises the base body 57b and the ring projections 67, 68.

[0117] The modular design according to Fig. 4a offers high flexibility in manufacturing and facilitates both assembly and the replacement of individual components. Thanks to the modular construction, the ring projections 67, 68 can be adapted to different requirements, such as varying heights, geometries, or specific material properties, without having to redesign the base body 57b. This adaptability helps to expand the range of applications and to adapt the design to different technical requirements or operating conditions.

[0118] The base body 57b and the ring projections 67, 68 can be made of different materials to optimally meet the respective mechanical or chemical requirements. For example, the base body 57b can be made of metal and the ring projections 67, 68 of a plastic or an elastomer.

[0119] In the embodiment shown in Fig. 4a, the base body 57b is designed as a hollow body closed at one end, with the mass of the base body 57b being a crucial design criterion. By precisely adjusting the mass, the desired opening pressure required to open the valve element 36 for venting or purging can be defined. This design enables precise control of the pressure behavior and ensures that the closing element 57 reliably fulfills its function under the intended operating conditions.

[0120] It is clearly visible that the annular projections 67, 68 are provided with radially extending flow openings 69, 70 distributed around their circumference. These flow openings 69, 70 enable controlled flow guidance or the passage of gas. The arrangement and number of the flow openings 69, 70 can be adapted depending on the application in order to optimally control the flow characteristics, pressure equalization, or ventilation.

[0121] The flow openings 69, 70 of the two annular projections 67, 68 are aligned with each other in the axial direction of the closing element 57, thus ensuring reliable and undisturbed flow guidance. As can be clearly seen in Fig. 4a, the base body 57b is designed as a hollow body closed at one end. A desiccant can be provided in a recess 57c to support the functionality of the system. For this purpose, the desiccant can be inserted into the recess 57c in the form of a cartridge (not shown) and fixed as required. The cartridge can be secured by a snap mechanism, screws, or a clamping device to ensure a stable position during operation.

[0122] Suitable desiccants include materials such as silica gel or zeolites, which are particularly well-suited due to their high water absorption capacity. This design allows for a targeted reduction of the humidity in the container (not shown).

[0123] Figure 5, unlike Figure 2, shows how the position of the valve element 36 and the closing element 57 changes in a venting position. During venting, as already explained, the pressure inside the container (not shown) is higher than in the surrounding environment.

[0124] The internal pressure is applied uniformly across the entire surface of the valve element 36, thereby exerting a force on the valve element 36 and the closing element 57. As a result of this force, the valve element 36 bulges elastically towards the cover 22. Since the closing element 57 adheres to the opening edge 59 of the valve element 36 due to the existing annular tension in the valve element 36, the closing element 57 follows the movement of the valve element 36 and is displaced towards the cover 22 according to its bulge, without any relative movement occurring between the valve element 36 and the closing element 57. Due to the bulging of the valve element 36 towards the cover 22, additional contact occurs between the valve element 36 and the annular projection 68. This contact forms a flow-restricting barrier. Fig. 6 now shows a part of the pressure equalization device in an enlarged, schematic representation according to Fig.5 in axial section in a vented position, or the vented position with a further increase in internal pressure. Here, the ring tension in the valve element 36 is overcome by the pressure-induced applied force, causing the valve element 36, including the associated opening rim 59, to bulge or expand elastically and lift away from the counter surface 60 of the closing body 57. This allows the gas from the interior of the container to flow through the flow openings 70 of the annular projection 68, the passage 58, and the flow openings 69 of the annular projection 67 towards the cover 22.

[0125] The flow-restricting barrier previously formed by the contact of the valve element 36 with the annular projection 68 is bypassed by the flow opening 70, allowing the gas to flow unhindered towards the diaphragm 34. Should the valve element 36 also contact the annular projection 67 and thereby form a further flow-restricting barrier, this too is bypassed by the flow opening 69. This design ensures that the gas can escape reliably and in a controlled manner despite any potential barriers. The flow path is illustrated by the flow arrows in Fig. 6.

[0126] Figures 7 and 8 illustrate the case where the ambient pressure is greater than the pressure inside the container. Figure 7, unlike Figure 2, shows how the position of the valve element 36 and the closing element 57 changes in a vented position. During venting, as already explained, the pressure inside the container (not shown) is lower than the ambient pressure. The external pressure, usually atmospheric pressure, acts uniformly across the entire surface of the valve element 36, exerting a force on both the valve element 36 and the closing element 57. As a result of this force, the valve element 36 bulges outward toward the closing element 10. This pressure acts on the upper surface 73 of the closing element 57, causing the valve element 36 to be elastically deformed toward the closing element 10.

[0127] With a further increase in external pressure, the annular stress in the valve element 36 is overcome by the pressure-induced applied force, causing the valve element 36, including the associated opening rim 59, to bulge and expand and lift away from the counter surface 60 (see Fig. 8). This allows the gas to flow from the outside through the passage openings 69 of the annular projection 67, the passage 58, and the passage openings 70 of the annular projection 68 towards the closure element 10.

[0128] The flow-inhibiting barrier previously formed by the contact of the valve element 36 with the annular projection 67 is bypassed by the flow opening 69, so that the gas can flow unhindered towards the closure element 10.

[0129] Should the valve element 36 also rest against the annular projection 68 and thereby form a further flow-restricting barrier, this too is bypassed by the flow opening 70. This design ensures that the gas can escape reliably and in a controlled manner despite any potential barriers. The flow arrows in Fig. 8 illustrate the flow path.

[0130] Should very high pressure occur inside the housing, for example due to a battery cell fire within the housing, the high pressure acts on the sealing element 10. This causes the entire valve housing 8 and the diaphragm holder 28 to shift against the force of the compression spring 41. Due to the very high pressure, which also acts on the valve element 36, the diaphragm holder 28 connected to it is shifted relative to the valve housing 8 so far towards the cover part 23 of the lid 22 that the outlet openings 27 of the lid 22 are unobstructed. The gas then does not have to flow through the permeable diaphragm 34, but can flow directly from the interior of the sleeve part 29 to the outside through the outlet openings 27. In this way, the high pressure inside the housing is relieved within a very short time.

[0131] Once the pressure has been released, the compression spring 41 pushes the valve housing 8 and thus the diaphragm holder 28 back into the initial position according to Fig. 1 via the locking element 10.

Claims

Patent claims 1. Pressure equalization device for a container, preferably for a vehicle battery housing with a housing (8) having at least one inlet (11, 75) for a gas, to which a semipermeable membrane (34) is arranged downstream in the direction of gas flow from the container, which in a first position is located upstream of an outlet (27) and in a second position is located downstream of the outlet (27), and with a valve element (36) arranged downstream in the direction of gas flow, characterized in that the valve element (36) has a passage opening (56) for the gas, which can be closed by a closing element (57) which closes the passage opening (56) in a pressureless state and at least partially releases the passage opening (56) in a venting or aeration state.

2. Pressure equalization device according to claim 1 , characterized by the fact that the closing element (57) overlaps and under the opening edge (59) of the passage opening (56) of the valve element (36).

3. Pressure equalization device according to claim 1 or 2, characterized by the fact that The closing element (57) with a ring projection (67, 68) extends over and under the valve element (36).

4. Pressure equalization device according to claim 3, characterized by the fact that The annular projections (67, 68) of the closing element (57) each have at least one flow opening (69, 70) for the gas.

5. Pressure equalization device according to one of claims 1 to 4, characterized in that The opening edge (59) of the passage opening (56) of the valve element (36) has a circumferential sealing edge (62) which, in the unpressurized state of the pressure equalization device, seals against a counter surface (60) of the closing body (57) under the influence of a ring tension and blocks the passage opening (56).

6. Pressure equalization device according to one of claims 1 to 5, characterized in that In the venting and aeration state, the sealing edge (62) is separated from the counter surface (60) of the closing body (57) by elastic deformation of the valve element (36) and the passage opening (56) is free.

7. Pressure equalization device according to claim 6, characterized by the fact that the passage opening (56) of the valve element (36) is expandable, so that the opening edge (59) lifts off from the opposite surface (60) of the closing body (57).

8. Pressure equalization device according to one of claims 4 to 7, characterized in that The valve element (36) in the venting or aeration state rests against the annular projection (67, 68) of the closing body (57) and thereby forms a flow-restricting barrier, whereby this barrier is bypassed by the flow opening (69, 70).

9. Container with at least one pressure equalization device according to one of claims 1 to 8.

10. Vehicle with at least one container according to claim 9.

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