Shut-off valve device for a fuel supply system for supplying an internal combustion engine with gaseous fuel, for example hydrogen, and pressure control device and tank device for a fuel supply system

Abstract

Shut-off valve device (32) for a fuel supply system (10) for supplying an internal combustion engine with gaseous fuel, for example with hydrogen, comprising an inlet (54), an outlet (56), a first valve (58) with a first valve element (82), which is acted upon in an axial closing direction by a first biasing device (62) and can be acted upon in an axial opening direction by a controllable actuator (64), wherein the shut-off valve device (32) further comprises a second valve (60) hydraulically parallel to the first valve (58) with a second valve element (94), which is acted upon in the axial closing direction by an inlet-side fluid pressure and in the axial opening direction by an outlet-side fluid pressure, and which is mechanically coupled to the first valve (58) such that it closes when the first valve (58) closes, wherein the first valve element (82) has two parts (82.1, 82.2) which are connected to each other in the axial direction and which are displaceable relative to each other in the lateral direction.

Description

State of the art

[0001] From the applicant's post-published DE 10 2022 210 615 A1, a shut-off valve device for a fuel supply system for supplying an internal combustion engine with gaseous fuel is already known. The shut-off valve device comprises an inlet, an outlet, and a first valve with a first valve element, which is acted upon in the closing direction by a first biasing device and can be acted upon in the opening direction by a controllable actuator. Furthermore, it is provided that the shut-off valve device comprises a second valve, hydraulically parallel to the first valve, with a second valve element, which is acted upon in the closing direction by an inlet-side fluid pressure and in the opening direction by an outlet-side fluid pressure, and which is mechanically coupled to the first valve in the closing direction such that it closes when the first valve closes.

[0002] DE 10 2005 022 661 A1, filed by the applicant, discloses a quantity control valve for a high-pressure fuel pump. The valve comprises a first valve device and a second valve device arranged fluidically parallel to the first valve device. A mechanical coupling of the two valve devices is provided.

[0003] From US 5,217,200 a solenoid valve is known which has a valve seat and a laterally displaceable valve element.

[0004] From WO 2023 / 083565 A1 of the applicant, a valve device with two control valves, a safety valve and a pressure sensor is known.

[0005] From DE 10 2018 218 425 A1 of the applicant, a tank device for storing compressed fluids, in particular hydrogen, with a tank and a valve device is known. Disclosure of the invention

[0006] The invention is based on the inventors' observation that, in two-stage valves, the design of the tolerance chains cannot be fully optimized for both valve stages simultaneously. Production-related variations in the positions and orientations of the valve components can therefore potentially lead to leaks or even jamming in at least one of the two valve stages.

[0007] To overcome this problem, in a shut-off valve device for a fuel supply system for supplying an internal combustion engine with gaseous fuel, which comprises an inlet, an outlet and a first valve with a first valve element, which is acted upon by a first biasing device in an axial closing direction and can be acted upon by a controllable actuator in an axial opening direction, wherein the shut-off valve device further comprises a second valve hydraulically parallel to the first valve, with a second valve element, which is acted upon by an inlet-side fluid pressure in the axial closing direction and by an outlet-side fluid pressure in the axial opening direction, and which is mechanically coupled to the first valve in the axial closing direction such that it closes when the first valve closes, the invention provides that the first valve element comprises two parts,which are connected to each other in the axial direction and which are displaceable relative to each other in the lateral direction.

[0008] While the axial connection of the two parts allows unrestricted movement of the first valve element in the axial opening and closing directions compared to a single-piece valve element, the orthogonal lateral displacement of the two parts relative to each other allows for compensation of any manufacturing- or aging-related fluctuations in the positions and orientations of the valve components. This effectively prevents leaks and / or jamming in at least one of the two valve stages.

[0009] The invention can be advantageously implemented in that the first valve has a first valve seat, the two parts comprise a first part and a second part, the first valve seat cooperates with the second part in a sealing or permeable manner, the second valve has a second valve seat that cooperates with the second valve element in a sealing or permeable manner, and the first valve seat and the second valve element are jointly formed by a single plastic part. Such a plastic part is easy to manufacture, for example by injection molding, and ensures a high degree of tightness for both valves. It can be made of polyetheretherketone (PEEK), for example. The plastic part can, for example, be inserted into a supporting part that receives it, for example, clipped in or injected. The supporting part can, for example, be displaceably arranged in a housing of the shut-off valve device.

[0010] It can be provided that the first part and the second part are always or at least temporarily in contact with each other on flat surfaces of the first part and the second part. This allows for high force transmission and eliminates or minimizes wear on these parts.

[0011] A simple yet effective way to implement the invention is to connect the first part and the second part in the axial direction by a permanent magnet, which is fixed to the first part or to the second part, or is housed between the first and second parts. The permanent magnet then transmits attractive forces between the first part and the second part in the axial direction, and the first valve opens in response to a sufficiently high current supply to the actuator.

[0012] However, a lateral displacement between the first and second parts is readily possible, for example, in response to corresponding lateral forces that occur when the first valve closes due to an existing misalignment between the first valve element and the first valve seat. The lateral displacement then eliminates the misalignment.

[0013] Advantageously, the first and / or second part is made of a magnetizable material. Advantageously, the first valve seat is made of a non-magnetizable material, for example, plastic, to avoid attractive forces between the first valve seat and the second part.

[0014] Alternatively or additionally, the first part and the second part can be connected to each other by a positive fit in the axial direction, with the positive fit providing some play at least in the lateral direction. In this case, the advantages explained above also apply. In addition, the positive fit geometrically reliably prevents the first part and the second part from becoming lost.

[0015] Within the form fit, an axial gap or axial play between the first part and the second part can also be tolerated or even designed into the design. In this case, the lateral displacement between the first part and the second part, as explained above, is further facilitated.

[0016] This form fit can result in a simple manner from a third part being fixed to the first part, for example by being pressed on, so that a receiving area is created between the first part and the third part, in which the second part is arranged in a form fit.

[0017] Alternatively or additionally, for example, in addition to the provision of a positive connection as explained above, the first part and the second part can be connected to one another in the axial direction via an elastic device that, for example, transmits restoring forces in the lateral direction between the first part and the second part when the second part is laterally deflected relative to the first part. In this way, a zero position of the second part relative to the first part is defined, to which the second part returns when no external lateral forces act on it.

[0018] The invention also relates to a pressure control device for a fuel supply system, for example with hydrogen, comprising a housing, an inlet connection fixed to the housing and an outlet connection fixed to the housing, and a fluid channel leading through the housing from the inlet connection to the outlet connection, wherein the fluid channel can be interrupted by such a shut-off valve device arranged on the housing. In a further development, it can be provided that the pressure control device also has a proportional valve arranged on the housing for throttling a flow through the fluid channel. In a further development, it can be provided that the pressure control device also has a pressure sensor arranged on the housing, which can sense the gas pressure in the fluid channel.

[0019] The housing may preferably be a one-piece housing, for example made of aluminum or steel.

[0020] The pressure control device thus represents a compact, integrated component that simultaneously realizes the aforementioned function.

[0021] The invention also relates to a tank device for storing compressed gases, for example hydrogen, comprising a tank and such a shut-off valve device for closing the tank.

[0022] Embodiments of the present invention are explained below with reference to the accompanying drawings, in which: Fig. 1 a schematic representation of a fuel supply system for supplying an internal combustion engine with gaseous fuel, for example hydrogen, with a pressure control device, which in turn comprises a shut-off valve device; Fig. 2 a perspective view of a first embodiment of the pressure control device of Fig. 1; Fig. 3 a perspective view of a second embodiment of the pressure control device of Fig. 1; Fig. 4 a hydraulic equivalent circuit diagram of the shut-off valve device of the pressure control device of Fig. 2 or from Fig. 3; Fig. 5 a schematic sectional view through a shut-off valve device according to the invention; Fig. 6 an enlarged view of a section of Fig. 5 with forces drawn in; Fig. 7-10 alternative embodiments of shut-off valve devices according to the invention.

[0023] Fig. 1 shows a fuel supply system 10. It serves to supply an internal combustion engine (not shown) with a gaseous fuel, in this case hydrogen.

[0024] The hydrogen is stored under high pressure, for example, 700 bar, in a tank 12. This can be filled via a filling connection 14. A shut-off valve 16 is also provided on the tank 12 to ensure a gas-tight seal. The shut-off valve 16 can be a shut-off valve device, the design of which is explained in detail below.

[0025] The gaseous hydrogen first flows via a pressure line 18 to a filter 20 and from there to a high-pressure pressure regulator 22. This reduces the pressure of the gaseous hydrogen to, for example, 40 bar. The pressure line 18 leads from the high-pressure pressure regulator 22 to a pressure sensor 24, to another filter 26, to an optional temperature control device 28, and finally to a pressure regulator 30.

[0026] The pressure control device 30 comprises a shut-off valve device 32, downstream of which are two hydraulically parallel pressure control valves 34, and a pressure sensor 35 between the shut-off valve device 32 and the two pressure control valves 34. The two pressure control valves 34 are identically constructed and are typically proportional valves. The pressure control device 30 further variably reduces the pressure in the pressure line 18 from the inlet-side pressure of 40 bar, as shown in the example here, to a pressure of, for example, 15 bar or less. The shut-off valve device 32 upstream of the pressure control valves 34 is closed when the fuel supply system 10 is not in operation. This prevents unwanted gas leakage.

[0027] Downstream of the pressure control device 30, the pressure line 18 leads to a distribution chamber 36, which may be configured, for example, as an elongated tube. The gas pressure prevailing in the distribution chamber 36 is detected by a pressure sensor 37.

[0028] Connected to the distribution chamber 36 are several injectors 38, which, in this example, inject the gaseous hydrogen directly into combustion chambers 40 of the internal combustion engine. The gaseous hydrogen is mixed with atmospheric oxygen in the combustion chambers 40, and this mixture is ignited by a respective ignition device 42. Typically, the internal combustion engine is a 2-stroke or 4-stroke piston internal combustion engine of a largely conventional design.

[0029] The fuel supply system 10 and its components are controlled by an electronic control and regulating device 44, which has one or more corresponding microprocessors, a memory for program code, etc. This receives signals from, among others, the temperature sensor 16, the pressure sensor 24, the pressure sensor 37, etc. The control and regulating device 44 controls various components of the fuel supply system 10, including the pressure regulating device 30 and the ignition devices 42. Furthermore, a control device 46 is also controlled by the control and regulating device 44, which in turn specifically controls or regulates the operation of the tank 12 and the tank valve 16.

[0030] The pressure control device 30 is in a first embodiment in Fig. 2 with a single pressure control valve 34. The pressure control device 30 includes a housing 48 with an inlet-side connection piece 50 and an outlet-side connection piece 52. The housing 48 integrates the pressure control valve 34, the shut-off valve device 32, and the low-pressure pressure sensor 35 into a single structural unit. The housing 48 can be a milled aluminum block. Alternatively, it can be made of steel. Fig. 3, which is a second embodiment, are - according to Fig. 1 - two pressure control valves 34 are provided, which are connected in parallel. In this way, a maximum possible flow is achieved compared to the Fig. 2 shown pressure control device 30 is increased, for example doubled.

[0031] The hydraulic structure of the shut-off valve device 32 is based on Fig. 4 schematically. The shut-off valve device 32 comprises an inlet 54 and an outlet 56. The inlet 54 is, in this case, identical to the inlet-side connection piece 50 ( Fig. 1, Fig. 2 or Fig. 3). In this example, the outlet 56 leads to the low-pressure pressure sensor 35 and further to the pressure control valve 34 or the pressure control valves 34. Furthermore, the shut-off valve device 32 includes two valves arranged hydraulically parallel to one another, namely a first valve 58 and a second valve 60. Both valves 58 and 60 are designed as switching valves, each with a closed and an open switching position.

[0032] The first valve 58 has a Fig. 4, which is acted upon in the closing direction by a first preloading device 62 and which can be acted upon in the opening direction by a controllable actuator 64. As will be explained further below, the actuator 64 can be, for example, an electromagnetic actuator.

[0033] The first valve element of the first valve 58 is further acted upon by the fluid pressure prevailing at the inlet 54 in the closed position and by the fluid pressure prevailing at the outlet 56 in the open position, which is indicated by corresponding dashed lines. As will also be explained further below, the flow cross-section of the first valve 58 is relatively small in the open position, which Fig. 4 is indicated by a throttle 66.

[0034] The second valve 60 has a Fig. 4 also has a second valve element, not yet shown, which is acted upon in the opening direction by a second prestressing device 68, and which is also acted upon in the closing direction by the fluid pressure prevailing at the inlet 54 and in the opening direction by the fluid pressure prevailing at the outlet 56, which is again indicated by corresponding dashed lines. A prestressing force F1 of the first prestressing device 62 is greater than a prestressing force F2 of the second prestressing device 68, which may also be omitted. The second valve 60 is mechanically coupled to the first valve 58 in the closing direction such that it closes or is closed when the first valve 58 closes or is closed. However, the coupling is such that the first valve 58 can open without the second valve 60 being mechanically forced into the open position. The mechanical coupling is in Fig. 4 is indicated by a dotted line 70.

[0035] The shut-off valve device 32 functions as follows: When the internal combustion engine is not operating and the fuel supply system 10 is switched off, the actuator 64 is not actuated, i.e., de-energized. The preload force F1 of the first preload device 62 pushes the first valve 58 into the closed position, and this also necessarily pushes the second valve 60 into the closed position. Thus, the shut-off valve device 32 is completely closed. The above-mentioned exemplary fluid pressure of approximately 40 bar prevails at the inlet 54, and the above-mentioned exemplary fluid pressure of approximately 15 bar prevails at the outlet 56.

[0036] When the actuator 64 is energized, the first valve element opens against the preload force F1 of the first preload device 62 and against the hydraulic force of the fluid pressure prevailing at the inlet 54. Hydrogen gas thus flows through the throttle 66 to the outlet 56, causing the pressure there to rise and the pressure at the inlet 54 to fall. This changing pressure difference between the inlet 54 and outlet 56 and the preload force F2 of the second preload device 68 push the second valve element of the second valve 60 into the open position. This releases the comparatively large opening cross-section of the second valve 60, allowing hydrogen gas to flow largely unhindered from the inlet 54 to the outlet 56. The pressure at the outlet 56 is now only slightly lower than at the inlet 54.

[0037] If the shut-off valve device 32 is to be closed again, the activation of the actuator 64 is terminated, for example, it is de-energized. Due to the preload force F1 of the first preload device 62, the first valve element of the first valve 58 is now pushed into the closed position. Due to the mechanical coupling 70, it carries the second valve element of the second valve 60 into the closed position, possibly against the preload force F2 of the second preload device 68.

[0038] An embodiment of the shut-off valve device 32, which is capable of separating its inlet 54 from its outlet 56, will now be described with reference to the Fig. 5 and Fig. 6. The first valve 58 includes the actuator 64, which comprises a magnet assembly 72 with, for example, a ring-shaped electromagnet 76, which is connected to an electrical connection (not shown). Furthermore, the magnet assembly 72 includes a magnet armature plunger 80, which is actuated by a Fig. 5 valve spring 62 arranged above the magnet armature tappet 80 with a Fig. 5 downward force. A corresponding current supply to the electromagnet 76, however, causes a Fig. 5 upward force on the magnet armature plunger 80. The magnet armature plunger 80 forms a first part 82.1 of two parts 82.1, 82.2, which together form the first valve element 82 of the first valve 58. The second part 82.2 of the first valve element 82 is held axially fixed to the first part 82.1 of the first valve element 82 by a permanent magnet 83 fixed in the first part 82.1 of the first valve element 82, but is comparatively easily displaceable laterally, see also Fig. 6.

[0039] The second part 82.2 of the first valve element 82 has a conical contour with which it cooperates with the first valve seat 84 of the first valve 58 - depending on its axial position - in a sealing or permeable manner, thus closing or opening the first valve 58.

[0040] Out of Fig. 6 shows that the axial force Fs acting via the valve spring 62 in the case of the Fig. 6, the axial offset between the valve element 82 of the first valve 58 and the valve seat 84 of the first valve 58 can be broken down into a force Fo orthogonal to the valve seat 84 and a radial force Fr. The radial force Fr is capable of displacing the second part 82.2 of the first valve element 82 laterally as soon as it has overcome any adhesion between the two parts 82.1, 82.2 of the first valve element 82.

[0041] The first valve seat 84 of the first valve 58 is formed on a plastic part 89, which simultaneously also forms the second valve element 94 of the second valve 60, thus cooperating with the second valve seat 98 of the second valve 94 in a sealing or permeable manner, depending on its axial displacement. For its stabilization and axial guidance, the plastic part 89 is clipped into a support part 87 that is axially displaceable.

[0042] The Fig. 7 shows a variant in which the second part 82.2 of the first valve element 82 of the first valve 58 is a solid sphere.

[0043] The Fig. 8 and Fig. 9 show variants in which a third part 82.3 of the first valve element 82 is fixed to the first part 82.1 of the first valve element 82, so that a receiving area is created between the first part 82.1 and the third part 82.3, in which the second part 82.2 of the first valve element 82 is arranged in a form-fitting manner. A permanent magnet 83 as described above ( Fig. 5, Fig. 6 and Fig. 7) can be omitted in these variants.

[0044] The Fig.10 shows a variant in which the first part 82.1 of the first valve element 82 and the second part 82.2 of the first valve element 82 are connected to one another in the axial direction via an elastic device 90 (e.g., a spring). The elastic device 90 also has the effect of transmitting restoring forces in the lateral direction between the first part 82.1 of the first valve element 82 and the second part 82.2 of the first valve element 82 when the second part is laterally deflected relative to the first part. QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] DE 10 2022 210 615 A1

[0001] DE 10 2005 022 661 A1

[0002] US 5,217,200

[0003] WO 2023 / 083565 A1

[0004] DE 10 2018 218 425 A1

[0005]

Claims

[1] Shut-off valve assembly (32) for a fuel supply system (10) for supplying an internal combustion engine with gaseous fuel, for example hydrogen, comprising an inlet (54), an outlet (56), a first valve (58) with a first valve element (82) which is acted upon in an axial closing direction by a first pre-tensioning device (62) and can be acted upon in an axial opening direction by a controllable actuator (64), wherein the shut-off valve assembly (32) further comprises a second valve (60) hydraulically parallel to the first valve (58) with a second valve element (94) which is acted upon by an inlet-side fluid pressure in the axial closing direction and by an outlet-side fluid pressure in the axial opening direction, and which is mechanically coupled to the first valve (58) such that it closes when the first valve (58) closes, wherein the first valve element (82) has two parts (82.1, 82.2) includes components that are connected to each other in the axial direction and that are movable relative to each other in the lateral direction. [2] Shut-off valve device (32) according to claim 1, characterized by , that the first valve (58) has a first valve seat (84), that the two parts (82.1, 82.2) comprise a first part (82.1) and a second part (82.2), that the first valve seat (84) cooperates with the second part (82.2) in a sealing or permeating manner, that the second valve (60) has a second valve seat (98) which cooperates with the second valve element (94) in a sealing or permeating manner. [3] Shut-off valve device (32) according to claim 2, characterized by , that the first valve seat (84) and the second valve element (94) are formed together by a single plastic part (89). [4] Shut-off valve device (32) according to claim 3, characterized by , that the plastic part (89) is an injection-molded part. [5] Shut-off valve device (32) according to claim 3 or 4, characterized by , that the plastic part (89) is inserted into a carrier part (87) which receives it and is slidably arranged in a housing (86) of the shut-off valve assembly (32), for example by clipping or injection molding. [6] Shut-off valve device (32) according to one of claims 2 to 5, characterized by , that the first part (82.1) and the second part (82.2) are in contact with each other at planar surfaces of the first part (82.1) and the second part (82.2). [7] Shut-off valve device (32) according to one of claims 2 to 6, characterized by , that the first part (82.1) and the second part (82.2) are connected to each other in an axial direction by a permanent magnet (83) which is fixed to the first part (82.1) or to the second part (82.2) or is received between the first and the second part (82.1, 82.2). [8] Shut-off valve device (32) according to one of claims 2 to 7, characterized by , that the first part (82.1) and the second part (82.2) are connected to each other by a positive fit in the axial direction, wherein the positive fit has some play at least in one lateral direction. [9] Shut-off valve device (32) according to claim 8, wherein a third part (82.3) is fixed to the first part (82.1), such that a receiving area (91) is formed between the first part (82.1) and the third part (82.3) in which the second part (82.2) is arranged in a form-fitting manner. [10] Shut-off valve device (32) according to any one of claims 2 to 9, characterized by , that the first part (82.1) and the second part (82.2) are connected to each other in the axial direction via an elastic device (90), e.g. a spring. [11] Shut-off valve device (32) according to claim 10, characterized by, that the elastic device (90) transmits restoring forces in a lateral direction between the first part (82.1) and the second part (82.1) when the second part (82.2) is deflected laterally relative to the first part (82.1). [12] Shut-off valve device (32) according to any one of claims 2 to 11, characterized by , that the first part (82.1) simultaneously has the function of a magnetic armature (80) of the first valve (58), which immerses in an energizable magnetic coil (76) of the first valve. [13] Shut-off valve device (32) according to any one of claims 2 to 12, characterized by , that the second part (82.2) is conical or spherical on the axial side facing away from the first part (82.1) or that the second part (82.2) has the shape of a sphere. [14] Shut-off valve device (32) according to one of the preceding claims, characterized by, that the first valve element (82) is acted upon by the outlet-side fluid pressure in the opening direction and that the hydraulically effective area of ​​the first valve element (82) acting in the opening direction is smaller than the hydraulically effective area of ​​the second valve element (94) acting in the opening direction. [15] Pressure regulating device (30) for a fuel supply system comprising a housing (48) with an inlet nozzle (50) fixed to the housing (48) and an outlet nozzle (52) fixed to the housing (48) and a fluid channel leading through the housing (48) from the inlet nozzle (50) to the outlet nozzle (52), wherein the fluid channel can be interrupted by a shut-off valve device (32) arranged on the housing (48) according to one of the preceding claims and which further comprises a proportional valve (34) arranged on the housing (48) for throttling a flow through the fluid channel and further comprises a pressure sensor (35) arranged on the housing (48) which senses the gas pressure in the fluid channel. [16] Tank device for storing compressed gases, comprising a tank (12) and a shut-off valve device (16, 32) according to one of the preceding claims for closing the tank (12).

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