Self-closing flow divider valve

Abstract

The subject of this invention is a diversion valve for distributing fluid, having an inlet (2) for connecting a fluid supply line, a main channel (16) connecting the inlet (2) to an outlet (25), a main valve (5) for controlling the total volume flow through the main channel (16), and a vacuum line (9) leading into the main channel (16). According to the invention, the main channel (16) turns downstream of the main valve (5) into a sub-channel (10) and into at least one bridging channel (20a-20e) extending parallel to the sub-channel (10), wherein the sub-channel (10) and / or at least one bridging channel (20a-20e) have mechanisms for prioritizing fluid flow, the mechanisms being designed such that the relative share of the total volume flow through the sub-channel (10) decreases when the total volume flow increases, wherein the sub-channel (10) has a taper (33) and the vacuum line (9) enters the sub-channel (10) in the region of the taper (33). The sub-channel according to the invention significantly improves vacuum generation, thereby improving the reliability of the automatic shutdown device powered by vacuum.

Description

Technical Field

[0001] This invention relates to a diverter valve for distributing fluid. The diverter valve includes an inlet for connecting a fluid supply line and a main channel connecting the inlet to an outlet. Furthermore, the diverter valve includes a main valve for controlling the total volumetric flow through the main channel and a vacuum line leading into the main channel. Such a diverter valve is known, for example, from document EP 2 386 520 A1. In this known diverter valve, a vacuum is generated using the Venturi effect via the vacuum line leading into the main channel. In the region of the main valve, the cross-section of the main channel decreases, thereby accelerating the fluid flowing through the diverter valve in the region of the main valve, where the dynamic pressure increases and the static pressure decreases in the region of the tapered cross-section. The reduction in static pressure can be used to generate a negative pressure via the vacuum line. The vacuum can, for example, be used in a known manner to load an automatic shut-off device. Background Technology

[0002] In previously known diverter valves, the volumetric flow rate to be discharged by the diverter valve can typically be variably set. The opening stroke of the main valve can usually be manually selected by the position of the handle, and thus the volumetric flow rate can be set. Furthermore, diverter valves for dispensing aqueous urea solution (Adblue) are known, which are standardly designed to discharge a first maximum volumetric flow rate, wherein a second maximum volumetric flow rate, greater than the first maximum volumetric flow rate, can be set by interaction with the fuel tank of a motor vehicle (see EP 3 369 700 A1).

[0003] One problem with the aforementioned flow divider valves is that, due to the variable volumetric flow, the vacuum generated by the volumetric flow also experiences corresponding fluctuations. Therefore, in principle, an automatic shut-off device loaded by vacuum must be designed to ensure safe shut-off within a preset vacuum range subject to fluctuations. Ensuring this structurally is complex. Especially when the volumetric flow is too small or the volumetric flow fluctuations are too large, the tolerance requirements and costs for the manufactured components are very high. Building upon existing technology, the object of this invention is to provide a flow divider valve capable of achieving improved vacuum generation. This object is achieved by means of the features of this invention. Summary of the Invention

[0004] According to the invention, the main channel transitions downstream of the main valve into a sub-channel and then into at least one bridging channel extending parallel to the sub-channel. The sub-channel and / or at least one bridging channel have mechanisms for prioritizing fluid flow, said mechanisms being designed such that the relative proportion of the total volumetric flow flowing through the sub-channel decreases as the total volumetric flow increases. Furthermore, according to the invention, the sub-channel has a tapered section, in which a vacuum line enters the sub-channel in the region of the tapered section.

[0005] First, some terms used within the scope of this invention will be explained. If the main channel branches into two parallel extending channels (sub-channels and bridging channels), this in the sense of this specification means that the main channel separates at the transition, allowing fluid to flow through either the sub-channels or the bridging channels. The geometry or orientation of the channels relative to each other is not limited to the term "parallel." The tapering of the sub-channels can be achieved, in particular, by reducing the flow cross-section given by the wall of the sub-channel in the flow direction. The sub-channels can preferably form a Venturi nozzle together with the vacuum line leading into them.

[0006] The main valve is preferably coupled to the switching lever in a manner known in principle, so as to allow the main valve to move between a closed position and an open position. Furthermore, the main valve can be coupled to an automatic shut-off device. In particular, it can be proposed that the automatic shut-off device be designed in a manner known in principle (e.g., see EP 2 386 520 A1) to move the main valve to the closed position independently of the position of the switching lever.

[0007] According to the invention, vacuum generation is decoupled from the main valve and from the total volumetric flow through the main channel via a sub-channel having a tapered section with a vacuum line connected thereto. Specifically, the sub-channel defines a portion of the flow cross-section of the main channel and is separated from the remaining portion of the flow cross-section, the remaining portion being associated with at least one bridging channel.

[0008] Because the main channel transitions into the sub-channels and bridging channels, a portion of the total volumetric flow can flow through the sub-channels, and another portion can flow through the bridging channels. By influencing the distribution of the total volumetric flow to the two parallel extending channels according to the total volumetric flow using the mechanism for prioritizing fluid flow according to the invention, the relative share flowing through the sub-channels decreases as the total volumetric flow increases. For example, this means that when the total volumetric flow is small, a larger relative share of the total volumetric flow can flow through the sub-channels. For example, it can be proposed that, in the case of low total volumetric flow between 0 and 5 l / min, the total volumetric flow flows completely or substantially completely through the sub-channels. Therefore, even when the total volumetric flow is small, a relatively high “sub-channel volumetric flow” can be generated in the sub-channels (due to the smaller flow cross-section compared to the entire main channel), which can then be used to generate the desired vacuum.

[0009] The reduced relative proportion of the total volumetric flow through the sub-channels means that, even with a large total volumetric flow (e.g., 5 L / min), one or more bridging channels are used to accommodate a portion of the total volumetric flow. Therefore, as the total volumetric flow increases, a larger proportion is guided through the bridging channels, making the "sub-channel volumetric flow" rise less forcefully, or even remain constant in optimal conditions. Consequently, the vacuum generated by the tapering section also varies less forcefully as the total volumetric flow increases, or even remains constant over a large operating range. In this case, the automatic shut-off device connected to the vacuum line experiences a constant vacuum over a large operating range, ensuring automatic shut-off over a large flow range with a simple structural design.

[0010] Mechanisms for prioritizing fluid flow can be designed to deflect and / or control fluid flow. Specifically, such mechanisms can be designed to deflect a relatively large portion of the total volumetric flow into a sub-channel when the total volumetric flow is small, and to deflect a relatively large portion of the total volumetric flow into at least one bridging channel when the total volumetric flow is large. For this purpose, mechanisms for prioritizing fluid flow can, for example, have rigid deflecting sections for deflecting the fluid flow. Alternatively or additionally, mechanisms for prioritizing fluid flow can also be proposed to have movable deflecting sections designed to at least partially close the sub-channels and / or at least one bridging channel, depending on the type of valve.

[0011] In a preferred embodiment, the mechanism for prioritizing fluid flow includes an overflow valve designed to at least partially close the bridging channel. The overflow valve can also preferably be designed to completely close the bridging channel. Because the bridging channel can be at least partially or completely closed by the overflow valve, the flow rate through the sub-channel can be controlled. Specifically, when the total volumetric flow rate is low, the total volumetric flow rate can be completely directed through the sub-channel by completely closing the overflow valve. When the total volumetric flow rate is high, a portion of the total volumetric flow rate can be directed through the bridging channel by opening the overflow valve, thereby reducing the relative share of the total volumetric flow rate through the sub-channel. The overflow valve can also have a controllable, variable valve lift, allowing the volumetric flow rate through the bridging channel to be controlled by the valve lift. A closable overflow valve ensures uniform flow through the sub-channel, thereby ensuring uniform vacuum generation. If multiple (parallel-extending) separate bridging channels exist, multiple or even all of the bridging channels can each have an overflow valve.

[0012] Preferably, the relief valve can be opened by a dominant fluid pressure upstream of it. This has the advantage that, in the case of a small flow rate with a correspondingly small fluid pressure, the relief valve initially remains closed, allowing a larger or total fluid volume to flow through the sub-channel first and ensuring a safe vacuum is created there. In the case of a larger flow rate, the fluid pressure upstream of the relief valve increases, causing the relief valve to open under fluid pressure and accommodate a portion of the fluid flow through the main channel. The portion of the fluid flow through the sub-channel and the resulting vacuum are thus automatically homogenized. One or more relief valves can particularly have a shut-off body pre-tightened to a closed position upstream. Thus, the fluid pressure-dependent openability of the relief valve can be achieved in a simple manner. In principle, within the scope of this invention, active control of the relief valve, for example, by an actuation mechanism that operates the relief valve according to the total volumetric flow, is feasible.

[0013] In a preferred embodiment, the main channel has at least two bridging channels extending parallel to the sub-channels, wherein preferably each of the two bridging channels includes a relief valve for closing the bridging channel. The relief valves preferably each have a shut-off body pre-tightened to a closed position upstream and are capable of opening by the fluid pressure preceding the relief valve. With the presence of two bridging channels, fluid can flow through the sub-channels either through one bridging channel or the other. This further improves the reliability of vacuum generation because, in the event of bridging channel failure (e.g., due to blockage or malfunction of the associated relief valve), the other bridging channel is always still available and can accommodate at least a portion of the fluid flow.

[0014] Preferably, in an embodiment with two bridging channels, the first relief valve in the relief valve is designed to move to the open position when a first fluid pressure is exceeded, wherein the second relief valve in the relief valve is designed to move to the open position when a second fluid pressure different from the first fluid pressure is exceeded. For example, the preload of the closing body of the first relief valve can be different from the preload of the closing body of the second relief valve. Alternatively or additionally, the closing bodies of the first and second relief valves can also have upstream-facing faces capable of loading fluid pressure, the faces being different from each other due to different shapes and / or different sizes. For example, the face of the first relief valve can be larger than the face of the second relief valve. The upstream dominant fluid pressure is converted into a larger force due to the larger area, causing the relief valve with the larger face to open first, and the relief valve with the smaller face to open only at higher fluid pressures. With the above-described design of the relief valve, it is possible to pre-set which fraction of the volumetric flow should flow through the sub-channel with high precision and safety, thereby setting the vacuum generated there with high reliability over a large flow range.

[0015] In a preferred embodiment, the main valve has a valve body and a valve stem disposed downstream of the valve body, wherein at least one section of a sub-channel is disposed radially alongside the valve stem. Currently, radially disposing a section of the sub-channel alongside the valve stem means that this section begins at the intersection of the valve stem with an assumed axis perpendicular to the axial direction of the valve stem. By radially disposing the sub-channel alongside the valve stem, a vacuum can be generated directly downstream of the main valve in a space-saving manner. The distance to any potential automatic switching device can be kept small, thereby reducing the size or length of the space or pipeline to be evacuated. This further improves the operating range of the automatic shut-off device. Furthermore, since the sub-channel is disposed alongside the valve stem, no modifications to the mechanism connected to the valve stem to operate the main valve are required, and either no modifications to the automatic shut-off device connected thereto are necessary.

[0016] The sub-channels and at least one bridging channel are preferably uniformly distributed around the valve stem in the circumferential direction. The number of bridging channels can be more than two, preferably more than three, and more preferably more than five. The uniform arrangement results in a uniformly distributed fluid flow and minimizes turbulence. The valve stem is preferably positioned substantially centrally relative to the cross-section of the main channel, wherein the sub-channels and / or bridging channels are more preferably positioned eccentrically relative to the cross-section of the channel.

[0017] In a preferred embodiment, the diverter valve includes an automatic shut-off device for operating the main valve, wherein the vacuum line is connected to the automatic shut-off device. The structure of such an automatic shut-off device is known in principle and will not be explained in more detail here.

[0018] The diverter valve can have a settable first maximum volume flow and a second maximum volume flow different from the first maximum volume flow. Design schemes for diverter valves discharging different maximum volume flows are known in principle, for example, from document EP 3 369700. As shown within the scope of this invention, the advantages of this invention are particularly effective in such diverter valves because the flow through the sub-channels can be optimized for both maximum volume flows by means of one or more bridging channels, and especially by means of one or more associated relief valves. Therefore, optimal vacuum can be guaranteed for both maximum volume flows, thus ensuring reliable and safe operation of the automatic shut-off device.

[0019] To set the first or second maximum volume flow, EP 3 369 700 A1 proposes achieving the first and second maximum volume flows by limiting the maximum open position of the main valve, wherein the interaction between the signal element in the tank and the main valve is realized via an automatic shut-off device of the diverter valve. This solution enables reliable and safe settling of the first and second maximum volume flows; however, it is costly in design because it requires intervention with the automatic shut-off device of the diverter valve.

[0020] In a preferred embodiment, the flow divider valve includes the following features:

[0021] - It has a configurable first maximum volume flow and a second maximum volume flow that is different from the first maximum volume flow, wherein the second maximum volume flow is greater than the first maximum volume flow.

[0022] - The diverter valve has a settable flow restrictor, constructed separately from the main valve, which is designed to selectively limit fluid flow to a first or second maximum volumetric flow.

[0023] - The diverter valve has an actuation device designed to interact with a signal element associated with the fuel tank of the same motor vehicle and to selectively set the flow restrictor to a first or second maximum volume flow.

[0024] The above-described concept of a diverter valve having first and second maximum volume flow has, when necessary, the inventive content of features that are independent of the present invention.

[0025] In this context, the term "diverter valve" can refer to a device used to control the flow of liquid during the refueling process. DIN EN 13012 specifies the requirements for the construction and operation of automatic diverter valves used at distribution columns.

[0026] In this preferred embodiment, the diverter valve has a settable flow restrictor designed to selectively limit fluid flow to a first or second maximum volumetric flow. This means that, under a preset constant fluid pressure at the diverter valve inlet, the respective maximum volumetric flow can only pass through the flow restrictor. Specifically, the user can control the volumetric flow up to the correspondingly set first or second maximum volumetric flow using a switching lever and a main valve coupled thereto. Thus, the respective maximum volumetric flow limits the maximum liquid discharge per unit time. The second maximum volumetric flow is higher than the first maximum volumetric flow. The preferred embodiment is not limited to a diverter valve having exactly two settable maximum volumetric flows, but also includes embodiments in which the flow restrictor can be set to three or more settable maximum volumetric flows.

[0027] In the above embodiment, the settable flow restrictor is constructed separately from the main valve. This means that the flow restrictor can be set to a first or second maximum flow rate independently of the state of the main valve. The flow restrictor can be disposed upstream or downstream of the main valve, spaced apart from it.

[0028] By constructing the configurable flow restrictor according to the invention separately from the main valve and independent of the main valve and its automatic shut-off control device, selective restriction of fluid flow is achieved. Therefore, the structure of the diverter valve is simplified and functional safety is improved without the need for costly modifications to the automatic shut-off control device and / or the main valve.

[0029] Furthermore, the separation of the flow restrictor from the main valve allows for significantly simpler maintenance in case of failure. Additionally, the flow restrictor can be designed for installation in existing diverter valves if necessary.

[0030] In one embodiment, the flow restrictor is disposed downstream of the main valve. Preferably, the flow restrictor is disposed in the outlet pipe of the diverter valve. By disposing of the flow restrictor in the outlet pipe of the diverter valve, the outlet pipe can be replaced as a separate unit, enabling simple maintenance in case of failure. Furthermore, the flow restrictor according to the invention can be installed on the diverter valve by replacing the outlet pipe.

[0031] The settable first maximum volumetric flow rate can be less than 15 l / min, preferably between 5 l / min and 15 l / min, more preferably between 5 l / min and 10 l / min. Additionally or alternatively, the settable second maximum volumetric flow rate can be less than 50 l / min, preferably between 10 l / min and 50 l / min, more preferably between 20 l / min and 40 l / min.

[0032] Preferably, the flow restrictor is standardly set to a settable first maximum volume flow, wherein a settable second maximum volume flow is only set when the operating device detects a signal element. Here, the detection of the signal element can be achieved, in particular, through the interaction between the operating device and the signal element. By standardly setting a smaller first maximum volume flow, a smaller volume flow is standardly discharged, wherein a larger volume flow is allocated only when it is ensured, by identifying the corresponding signal element, that the fuel tank to be refueled is also suitable for a larger second maximum volume flow according to its size.

[0033] In a preferred embodiment, the actuation device is designed to interact with a toroidal magnet with a filled support according to ISO 22241-4. Therefore, in this case, the signal element can include a toroidal magnet with a filled support according to ISO 22241-4.

[0034] The operation of the flow restrictor for selectively setting a first or second maximum volumetric flow can be achieved magnetically and / or mechanically (e.g., by means of an elastic element) and / or pneumatically (e.g., by means of compressed air) and / or electrically (e.g., by means of a servo motor). In a preferred embodiment, the operating device has a movably disposed magnetic element designed to mechanically operate the flow restrictor. The magnetic force generated between the magnetic element and the annular magnet can be mechanically transmitted to the flow restrictor to operate it. In particular, the magnetic element can be connected to the flow restrictor via a mechanical signal transmission device (e.g., via a transmission rod).

[0035] The flow restrictor can have a throttle valve body, wherein, preferably, a mechanical signal transmission device or transmission rod is connected to the throttle valve body. Magnetic force can be transmitted to the throttle valve body via the transmission rod to open or close the flow restrictor. Preferably, when operating the flow restrictor, the throttle valve body can be moved in a first direction via the signal transmission device. Preferably, a reset element connected to the throttle valve body is also provided, the reset element being particularly designed to push the throttle valve body in a direction opposite to the first direction.

[0036] Furthermore, the flow restrictor can have a throttle valve support, wherein the throttle valve body is preferably movable downstream to a closed position, in which the throttle valve body abuts against the throttle valve support. In the above embodiment, the flow restrictor can also be referred to as a throttle valve. Preferably, the throttle valve body is movable to a closed position to selectively restrict the fluid flow rate to a first maximum volume flow, and is movable to an open position to selectively restrict the fluid flow rate to a second maximum volume flow. The movement to the open position can be achieved by transmitting magnetic force to the throttle valve body via a signal transmission device. The movement of the throttle valve body to the closed position can be achieved, for example, by a reset element time or supported by a reset element. Alternatively or additionally, the movement of the throttle valve body to the closed position can also be achieved by the throttle valve body being pressed into the closed position by fluid pressure when the diverter valve is inserted into a filled support without an annular magnet.

[0037] Specifically, setting the flow restrictor to the first maximum volume flow can be achieved by moving the throttle valve body to the closed position, the movement being generated by a reset element or fluid pressure. If the diverter valve is inserted into a filler support with an annular magnet, a magnetic force is generated between the annular magnet and the magnet element. In the preferred embodiment described herein, the magnetic force acting between the annular magnet and the magnet element is designed to resist the closing force generated by fluid pressure and any possible reset element from bringing the throttle valve body to the open position, and to overcome the closing force generated by fluid pressure to hold it in the open position.

[0038] The flow guiding device is preferably located upstream of the throttle valve body, and is configured to reduce the closing force exerted on the throttle valve body by the flowing fluid. For this purpose, the flow guiding device can particularly have a guiding surface inclined relative to the axial direction of the throttle valve body. The guiding surface can also be designed to direct the fluid force from the upstream rear of the throttle valve body in a radial direction (i.e., perpendicular to the axial direction of the throttle valve body), such that preferably at least a portion of the fluid flow is guided past the rear. For example, it can be proposed that the guiding surface is designed to direct the fluid flow radially outward from the axis extending centrally through the throttle valve body. This can induce lateral circulation in the throttle valve body, thereby reducing the closing force generated by the fluid.

[0039] The mobility of the throttle valve body in the upstream direction can be limited by a stop. By limiting the mobility of the throttle valve body, the throttle valve body occupies a defined position in the open position.

[0040] Preferably, a bypass channel is provided to bridge the flow restrictor. Due to the bypass channel, the flow restrictor does not completely block fluid flow through the diverter valve, but only causes a reduction in fluid flow. Preferably, the bypass channel is designed to allow a first maximum volume flow when the flow restrictor is closed. The bypass channel can have a through opening extending through the throttle valve body for fluid flow. Alternatively or additionally, the bypass channel can also have a secondary arm spaced apart from the flow restrictor, the secondary arm extending parallel to the fluid flow guiding through the open flow restrictor.

[0041] The diverter valve can have a safety valve located downstream of the flow restrictor, which is actuated to a closed position by a reset element downstream, wherein the safety valve can be moved to an open position by interaction with a filling support of the tank. Such a safety valve is known, for example, from EP 2 733 113 A1. The diverter valve preferably also has an automatic shut-off device that automatically interrupts the refueling process when the tank is full. For this purpose, a probe line can be provided extending to the outlet end of the diverter valve and being pneumatically connected to the automatic shut-off device. Design details of such an automatic shut-off device can be found, for example, in EP 2 386 520 A1. On one hand, the safety valve serves as an anti-drip valve to prevent undesirable overflow of residual fluid, for example, when the main valve is closed.

[0042] In particular, it can be proposed that the actuating device be movable relative to the valve stem of the safety valve, wherein the valve stem of the safety valve preferably has a cavity in which the magnetic element of the actuating device is movably disposed. It has been shown that the arrangement of the magnetic element within the valve stem of the safety valve achieves a particularly space-saving structure. If the actuating device has a transmission rod, the transmission rod can be guided through a through opening in the rear wall of the valve stem.

[0043] The subject of this invention is also a method for distributing fluid by means of a diverter valve according to the invention, wherein a first portion of the fluid flow is directed through a sub-channel and a second portion of the fluid flow is directed through at least one bridging channel, wherein the portion of the fluid flow directed through the sub-channel is used to generate a vacuum.

[0044] At least one bridging channel preferably has an overflow valve, wherein the overflow valve is used to set the proportion of fluid flow through the sub-channel. The method according to the invention can be improved by other features already described above in conjunction with the diverting valve according to the invention. Attached Figure Description

[0045] Advantageous embodiments of the invention will now be explained by way of example with reference to the accompanying drawings. The drawings show:

[0046] Figure 1 A lateral cross-sectional view of the flow divider valve according to the present invention is shown;

[0047] Figure 2 Show Figure 1 A magnified view of a specific part of the image;

[0048] Figure 3 Show along Figure 1 The cross-sectional view of line HH shown in the figure;

[0049] Figure 4 This is shown after operating the main valve where there is no fluid flow. Figure 2 The portion shown;

[0050] Figure 5 This illustrates the process of distributing fluid with a first maximum volumetric flow. Figures 1 to 4 The flow divider valve according to the present invention;

[0051] Figure 6 Show Figure 5 A magnified view of a specific part of the image;

[0052] Figure 7 This illustrates the process of distributing fluid with the second maximum volumetric flow. Figures 1 to 6 The flow divider valve according to the present invention;

[0053] Figure 8 Show Figure 7 A magnified view of a specific area;

[0054] Figure 9 A lateral cross-sectional view of the outlet pipe of the diversion valve according to the invention is shown before the main valve is operated;

[0055] Figure 10 A lateral cross-sectional view of the outlet pipe through the diversion valve according to the invention is shown during the distribution of fluid having a first maximum volume flow.

[0056] Figure 11 A lateral cross-sectional view of the outlet pipe through the diversion valve according to the invention is shown during the distribution of fluid having a second maximum volume flow. Detailed Implementation

[0057] The diverter valve includes a housing 1 with an inlet 2, to which a supply line for conveying fluid can be connected (not shown). An outlet pipe 3 is inserted at the front end of the housing 1, with an outlet 25 located at the front end of the outlet pipe. The outlet 25 can, for example, be introduced into the vehicle's filler supports 22, 26 (see...). Figure 5 and 7 ).

[0058] The main channel 16 extends from the inlet 2 to the outlet 25, and a main valve 5 for controlling the total volumetric flow is installed in the main channel. The main valve 5 includes a main valve body 6 (see...). Figure 2 The main valve body 6 is movable to abut against the main valve support 27 to close the main valve 5. For this purpose, the valve body 6 is coupled to the switching lever 4 and the automatic shut-off device 30 via the valve stem 15 in a manner known in principle. The valve stem 15 has an outer sleeve 24, which, in the closed position (see...) Figure 1 and 2 The valve body 6 is pressed against the valve support 27 by a large closing force. The valve stem 15 also includes an inner piston 12 that is movably designed relative to the outer sleeve 24, the inner piston being pushed upstream by a reset element 13 (see...). Figure 2 The valve body 6 is connected to the inner piston 12. When the user operates the switching lever 4, the outer sleeve 24 of the valve stem 15 moves downstream and thus protrudes from the valve body 6. The valve body 6 is now only pressed into the closed position by the reset force of the reset element 13 (see also...). Figure 4 The reset force of the reset element 13 is so small that the valve body 6, together with the inner piston 12, can be moved to the open position by normal fluid pressure.

[0059] The automatic shut-off device 30 is designed to move the main valve 5 to the closed position independently of the position of the switching lever 4. The operation of the automatic shut-off device is known in principle (see, for example, EP 2 386 520 A1) and will not be explained in detail here.

[0060] Figures 1 to 8 A probe line (not shown) extends from the automatic shut-off device 30 through the outlet pipe 3 to the outlet 25. The probe line is pneumatically connected to the shut-off device 30. When fluid is being dispensed, the fluid level reaches the front end of the outlet pipe 3 and covers the probe line, resulting in a pressure change that triggers the automatic shut-off device 30, and thus causes the main valve 5 to close regardless of the position of the switching lever 4.

[0061] The diverter valve is designed to selectively discharge either a first maximum volume flow or a second maximum volume flow. For this purpose, the diverter valve includes a throttling valve disposed in the outlet pipe, designed to selectively restrict fluid flow to either the first or second maximum volume flow. The throttling valve is operated by interaction with an annular magnet in a filling support according to ISO 22241-4. Standardly, i.e., if the annular magnet is not present, the diverter valve is set to discharge the first maximum volume flow. If the outlet pipe 3 is therefore introduced into a filling support without an annular magnet, at most the first maximum volume flow can be discharged by operating the switching lever 4. Currently, the first maximum volume flow is 9 l / min. If the outlet pipe 3 is introduced into a filling support according to ISO 22241-4 with an annular magnet, the second maximum volume flow, currently 20 l / min, can be discharged using the diverter valve. Figures 9 to 11 Explain in more detail how the throttle valve works.

[0062] The automatic shut-off device 30 requires a vacuum to operate. This vacuum is created as follows: The main channel 16, downstream of the main valve 5 in region 14, transitions to the sub-channel 10 and to the five bridging channels 20a to 20e extending parallel to it (see...). Figure 3 ).

[0063] The sub-channel 10 is defined by the wall portion 31. The sub-channel 10 has an opening 32 defined by the wall portion 31 and a section 33 that tapers in the flow direction starting from the opening 32 (see...). Figure 2 In the region of section 33, there is an inlet point 8 in the sub-channel 10 from the vacuum line 9. Due to the tapering section 33, the fluid velocity in the sub-channel 10 increases, causing the static pressure to decrease. This allows a vacuum to be generated via the vacuum line 9, thereby enabling the activation of the automatic shut-off device 30. Downstream of the inlet point 8 of the vacuum line 9, the sub-channel 10 widens again. In this respect, the sub-channel 10, together with the vacuum line, forms a venturi nozzle.

[0064] Bridging channels 20a to 20e each have mechanisms for prioritizing fluid flow, which are currently designed as relief valves 21a to 21e, respectively, wherein relief valves 21d and 21e are not visible in the cross-sectional view shown. The following description... Figure 2 The overflow valve 21c shown is an example. The overflow valve includes a rod 19 and a closing body 17, the closing body being tensioned upstream to a closed position by a reset element 18. Figures 1 to 3 In this configuration, main valve 5 is closed, preventing fluid flow through main channel 16. The closing body 17 of relief valve 21c is correspondingly held in the closed position by reset element 18. The remaining relief valves... Figures 1 to 3 The corresponding part is in its closed position.

[0065] The reset elements 18 of the relief valves 21a to 21e currently have different reset forces, resulting in the need for different fluid pressures to open the relief valves 21a to 21e. This will be discussed in conjunction with the following. Figures 5 to 8 To provide a more detailed explanation.

[0066] By manipulating the switching lever 4, the valve stem 15 is moved downstream, causing the outer sleeve 24 of the valve stem 15 to separate from the valve body 6 (see...). Figure 4 If no fluid is being supplied at inlet 2, valve body 6, as already explained, initially remains in the closed position, where it is pressed against valve support 27 by reset element 13. This is in Figure 4 The explanation is as follows.

[0067] Only when fluid with a certain pressure is supplied at inlet 2 will valve body 6 yield to the opening pressure and overcome the force of reset element 13 to move to the open position. This is in Figure 5 and Figure 6 As shown in the diagram, fluid is now able to enter sub-channel 10 and the region 14 before bridging channels 20a-20e from inlet 2. A portion of the fluid flows into sub-channel 10 here, and another portion flows toward overflow valves 21a-21e. Since overflow valves 21a-21e are first pushed into the closed position by reset element 18, a larger portion of the fluid initially flows through sub-channel 10, causing flow and a vacuum to be created there shortly after the main valve 5 is opened. After a short time, fluid pressure is built up on the upstream front of the closing body 17 of overflow valves 21a-21e, the fluid pressure depending on the fluid delivery pressure, the open position of the main valve, and the flow cross-section available for fluid flow in the diversion valve downstream of overflow valves 21a-21e.

[0068] exist Figure 5 and Figure 6 The diagram shows the diverter valve according to the invention after the outflow pipe has been introduced into the filling support 22 of the vehicle and the main valve has been opened. The filling support 22 is designed according to ISO 22241-5 and does not have an annular magnet. Accordingly, the throttle valve located in the outflow pipe 3 is in the closed position, and a maximum flow rate of approximately 9 l / min through the outflow pipe is achieved here.

[0069] In this state, there exists a fluid pressure in region 14 before the relief valves 21a to 21e sufficient to overcome the force of the reset element 18 and move the closing body of the relief valve 21c to the open position (see...). Figure 6 The reset elements 18 of the overflow valves 21a, 21b, and 21c shown in the figure currently have different magnitudes of reset force. Specifically, the reset force of valve 21c is less than that of valve 21b, and the reset force of valve 21b is less than that of valve 21a. This results in… Figure 5and Figure 6 In the dominant state, relief valve 21a remains closed and relief valve 21b occupies the intermediate position, in which low flow is feasible, wherein valve 21c is fully open (see...). Figure 6 The reset force of the relief valve is specifically set such that the fluid flow obtained through sub-channel 10 presents an optimal value for vacuum generation. The relief valves 21d and 21e, which are not identifiable in this figure, also have a greater reset force than relief valve 21b and therefore remain closed.

[0070] Figure 7 and Figure 8 The diagram shows the diverter valve according to the invention after the diverter valve is introduced into the filling support 26 according to ISO 22241-4, which has an annular magnet 23. The annular magnet 23 operates the throttle valve in a manner explained in detail below, so that the diverter valve is now able to discharge a maximum volume flow of 20 l / min. Due to the increased maximum volume flow, a higher fluid pressure fills the region 14 before the sub-channel 10 and the bridging channels 20a-20e, causing all relief valves 21a-21e to open (see...). Figure 8 By opening all overflow valves, the volumetric flow through subchannel 10 is combined with... Figure 5 and Figure 6 The conditions shown can be kept almost identical. The vacuum generated by sub-channel 10 is therefore substantially constant, regardless of whether a first maximum volume flow of approximately 9 l / min or a second maximum volume flow of approximately 20 l / min is discharged by means of the diverter valve. Even in the case of other volume flows that can be set, particularly by means of the handle and the main valve opening position corresponding to the handle position, the overflow valve according to the invention results in a uniform vacuum.

[0071] Figure 9 A lateral cross-sectional view of the outlet pipe 3 through the diverter valve according to the invention is shown. In the figure, probe line 34 is visible, which is pneumatically connected to an automatic shut-off device 30. If, during fluid distribution, the fluid level reaches the front end of the outlet pipe and covers probe 34, the resulting pressure change triggers the automatic shut-off device 30, thereby closing the main valve 5.

[0072] In the region of the outflow end of the outflow pipe 3, a safety valve 7 is also provided, the safety valve having a valve stem 35 and the safety valve being closed downstream close to the valve support 36 (see...). Figure 10 A magnet 37 is provided at the upstream end of the valve stem 35.

[0073] The outlet pipe 3 also has a sleeve 39 movable in its axial direction, the sleeve being preloaded by a spring 40. Figure 9The blocking position is shown in the diagram. An annular working magnet 41 is provided at sleeve 39. Through the magnetic interaction with magnet 37, the valve stem 35 and the safety valve are positioned... Figure 9 The closed position is shown in the figure.

[0074] The probe line 34 has a probe line valve 38 and a valve stem 42 located at the outlet end, the valve stem 42 being closed by abutting a valve support at its outlet end. The valve stem 42 includes an actuating magnet 43 at its opposite end, the actuating magnet holding the valve stem 42 in the closed position through interaction with an actuating magnet 41.

[0075] exist Figure 9 In the indicated state, the main channel 16 is closed by means of safety valve 7. Furthermore, probe line 34 is closed by probe line valve 38. If the main valve 5 is operated by means of switching lever 4 in this state, fluid distribution is prevented because the outflow pipe is closed by safety valve 7.

[0076] Furthermore, a configurable flow restrictor is located in the outlet pipe 3, which is currently configured via a throttle valve 49. By means of the throttle valve 49, the flow of fluid through the diverter valve or through the outlet pipe 3 can be selectively restricted to a first maximum volume flow or a second maximum volume flow. The throttle valve 49 has a valve body 50, which is connected to a magnetic element 52 via a transmission rod 51. The magnetic element 52 is disposed in a cavity 53 within the valve stem 35 of the safety valve 7 and is movable relative to the valve stem 35 in the axial direction of the outlet pipe 3. The transmission rod 51 is also movable relative to the valve stem 35 and is guided through a through opening located in the upstream-facing rear wall of the valve stem 35.

[0077] The magnet element 52 and the transmission rod 51 together form an operating device for the throttle valve 49. Figure 9 In the indicated state, valve body 50 is in the closed position, in which it abuts downstream against valve seat 54 of throttle valve 49. Valve body 50 is pushed downstream relative to valve stem 35 by reset element 55 and thereby tensioned into valve seat 54. Figure 10 and 11 Explain the operation of the control devices 51 and 52 and how to set the throttle valve 49 to the second maximum volume flow.

[0078] Figure 10 The outflow pipe 3 is shown after it enters the filling support 22 of the vehicle's fuel tank. Furthermore, with... Figure 9 Unlike other valves, the main valve 5 is moved to the open position by manipulating the switching lever 4. Currently, the filling support 22 is a passenger car urea tank filling support without annular magnets according to ISO 22241-5.

[0079] The filler support 22 is designed in a manner known in principle (see EP 3 369 700 A1) to allow the sleeve 39 to be positioned upstream relative to the sleeve when entering the outlet pipe 3. Figure 9 The blocking position shown is moved to the open position. As the sleeve 39 moves, the active magnet 41 connected to it also moves upstream relative to the outflow pipe 3. The active magnet drives the magnet 37 fixed at the valve stem 35 and the actuating magnet 43 fixed at the valve stem 42 through magnetic interaction, and thus the probe line valve 38 and the safety valve 7 open.

[0080] The magnetic element 52 is sufficiently far from the active magnet 41 that it is unaffected by or only negligibly affected by the displacement of the active magnet 41. Since the magnetic element 52, the transmission rod 51, and the valve body 50 connected thereto can move relative to the valve stem 35 and be pushed into the closed position by the reset element 55, the valve body 50 remains in the closed position. Figure 9 and Figure 11 An invisible through-opening exists in the cross-sectional view of the valve support 54, through which a certain volumetric flow can pass through the outlet pipe 3, even in the closed position of the valve body 50. This certain volumetric flow is at most as large as the first maximum volumetric flow of the throttle valve, which is currently 9 l / min. The volumetric flow through the opening of the main valve 5 is therefore limited to the first maximum volumetric flow of the diverter valve by the closed throttle valve 49. The through-opening may be added to or replaced by the through-opening in the valve support 54; alternatively, a through-opening may also be provided in the valve body 50.

[0081] Figure 11 The diagram shows the outflow pipe after it is introduced into the filling support 26, and... Figure 10 Unlike the filling support 22, the filling support 26 is a filling support for a passenger car urea tank according to ISO 22241-4, featuring an annular magnet 23. Similarly... Figure 10 As shown, the main valve 5 is in the open position.

[0082] If already combined Figure 10 As described, when the outflow tube is introduced, the sleeve 39 moves relative to the outlet tube 3 by filling the support 26, thereby opening the probe line valve 38 and the safety valve 7 by the interaction between the acting magnet 41 and the magnets 37 and 43.

[0083] Furthermore, currently, annular magnet 23 and magnetic element 52 interact. Specifically, annular magnet 23 and magnetic element 52 are arranged such that when the outflow pipe 3 is introduced into the filling support 26, similar poles initially oppose each other, thus applying a repulsive force to magnetic element 52. Here, magnetic element 52 is designed such that the magnetic force exceeds the opposing reset force of reset element 55. The repulsive force thus causes magnetic element 52 to move upstream relative to outflow pipe 3. Due to the connection formed between magnetic element 52 and valve body 50 via transmission rod 51, valve body 50 moves to the open position against the reset force of reset element 55. The movement of valve body 50 is defined upstream by stop 56.

[0084] With the throttle valve 49 in the open position, and under the preset fluid pressure at the inlet of the diverter valve, and... Figure 10 Compared to the closed position shown, a larger volumetric flow can pass through the outlet pipe. Specifically, in the illustrated state, with the main valve 5 fully open, the throttle valve 49 is designed to allow a second maximum volumetric flow to exit through the outlet pipe 3, which is currently 20 l / min. The magnetic force acting between the annular magnet 23 and the magnetic element 52 is so great that the valve body 50 remains in the open position against the fluid pressure and against the reset force of the reset element 55.

Claims

1. A flow divider valve for distributing fluid, the flow divider valve having: an inlet (2) for connecting a fluid supply line; a main channel (16) connecting the inlet (2) to an outlet (25); a main valve (5) for controlling the total volume flow through the main channel (16); and a vacuum line (9) leading into the main channel (16). Its features are, The main channel (16) turns downstream of the main valve (5) into a sub-channel (10) and into at least two bridging channels (20a-20e) extending parallel to the sub-channel (10), wherein the sub-channel (10) and / or at least two of the bridging channels (20a-20e) have mechanisms for prioritizing fluid flow, the mechanisms being designed to reduce the relative share of the total volume flow through the sub-channel (10) as the total volume flow increases, wherein the sub-channel (10) has a taper (33), and the vacuum line (9) enters the sub-channel (10) in the region of the taper (33).

2. The flow splitting valve of claim 1, wherein, The mechanism used for prioritizing fluid flow is designed to deflect and / or control the fluid flow.

3. The flow divider valve of claim 1 or 2, wherein, The mechanism for prioritizing fluid flow has overflow valves (21a, 21b, 21c, 21d, 21e) designed to at least partially close the bridging channels (20a-20e).

4. The flow splitting valve of claim 3, wherein, The relief valves (21a, 21b, 21c, 21d, 21e) can be opened by the dominant fluid pressure upstream of the relief valves (21a, 21b, 21c, 21d, 21e).

5. The flow splitting valve of claim 4, wherein, The overflow valves (21a, 21b, 21c, 21d, 21e) have a shut-off body (17) that is pre-tightened to the closed position upstream.

6. The flow splitting valve of claim 4, wherein, The two bridging channels (20a-20e) extending parallel to the sub-channel (10) each have an overflow valve (21a, 21b, 21c, 21d, 21e) for at least partially closing the bridging channel (20a-20e), wherein the overflow valve (21a, 21b, 21c, 21d, 21e) each has a shut-off body (17) pre-tightened to a closed position upstream, and is capable of being opened by the dominant fluid pressure preceding the overflow valve (21a, 21b, 21c, 21d, 21e).

7. The flow splitting valve of claim 6, wherein, The first relief valve in the relief valves (21a, 21b, 21c, 21d, 21e) is designed to move to the open position when a first fluid pressure is exceeded, and the second relief valve in the relief valves (21a, 21b, 21c, 21d, 21e) is designed to move to the open position when a second fluid pressure different from the first fluid pressure is exceeded.

8. The flow divider valve according to claim 7, wherein, The preload of the closing body (17) of the first overflow valve (21a) is different from the preload of the closing body (17) of the second overflow valve (21b).

9. The flow splitting valve of claim 1 or 2, wherein, The main valve (5) has a valve body (6) and a valve stem (15) disposed downstream of the valve body (6), wherein at least one segment of the sub-channel (10) is disposed next to the valve stem (15) in the radial direction.

10. The flow splitting valve of claim 9, wherein, The sub-channel (10) and at least two of the bridging channels (20a-20e) are distributed around the valve stem (15) in the circumferential direction.

11. The flow splitting valve of claim 10, wherein, The sub-channel (10) and at least two of the bridging channels (20a-20e) are evenly distributed around the valve stem (15) in the circumferential direction.

12. The flow splitting valve of claim 1 or 2, wherein, The subchannel (10) and the vacuum line (9) leading into the subchannel (10) form a Venturi nozzle.

13. The diverter valve according to claim 1 or 2, further comprising an automatic shut-off device (30) for operating the main valve (5), wherein, The vacuum line (9) is connected to the automatic shut-off device (30).

14. The flow divider valve according to claim 1 or 2, having the following characteristics: - the flow divider valve has a settable first maximum volume flow and a second maximum volume flow different from the first maximum volume flow, wherein The second maximum volumetric flow is greater than the first maximum volumetric flow. The diverter valve has a settable flow restrictor, constructed separately from the main valve, designed to selectively limit fluid flow to either the first maximum volumetric flow or the second maximum volumetric flow. - The diverter valve has an operating device designed to interact with a signal element associated with the fuel tank of the same motor vehicle, and the operating device is designed to selectively set the flow restrictor to either the first maximum volume flow or the second maximum volume flow.

15. A method for dispensing a fluid by means of a flow dividing valve according to any one of claims 1 to 14, wherein, A first portion of the fluid flow is directed through a sub-channel (10), and the remaining portion of the fluid flow is directed through at least two bridging channels (20a-20e), wherein the portion of the fluid flow directed through the sub-channel (10) is used to generate a vacuum.

16. The method of claim 15, wherein, At least two of the bridging channels (20a-20e) each have an overflow valve (21a, 21b, 21c, 21d, 21e), wherein the overflow valve (21a, 21b, 21c, 21d, 21e) is used to set the proportion of the fluid flow through the sub-channel (10).

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