EP4385942A2 - Dispensing nozzle - Google Patents

Abstract

The subject of the present invention is a dispensing valve for dispensing a fluid, with an inlet (2) for connecting a fluid supply line, a main channel (16) which connects the inlet (2) to an outlet (25), a main valve (5) for controlling a total volume flow through the main channel (16), and with a vacuum line (9) opening into the main channel (16). The main channel (16) has a partial channel (10) with a taper (33) and the vacuum line (9) opens into the partial channel (10) in the region of the taper (33), the main channel downstream of the main valve (5) dividing into a partial channel (10) and into at least one bridging channel (20a - 20e) running parallel to the partial channel (10), the partial channel (10) and/or the at least one bridging channel (20a - 20e) having means for prioritizing the fluid flow, which are designed such that a relative proportion of the total volume flow flowing through the partial channel (10) decreases as the total volume flow increases. According to the invention, the main valve (5) has a valve body (6) and a valve stem (15) arranged downstream of the valve body (6), wherein at least a section of the partial channel (10) is arranged in the radial direction next to the valve stem (15). The partial channel according to the invention significantly improves the vacuum generation, so that the reliability of an automatic shutdown device acted upon by the vacuum is improved.

Description

The present invention relates to a nozzle for dispensing a fluid. The nozzle comprises an inlet for connecting a fluid supply line and a main channel that connects the inlet to an outlet of the nozzle. In addition, the nozzle comprises a main valve for controlling a total volume flow through the main channel and a vacuum line that opens into the main channel. Such a nozzle is known, for example, from the document EP 2 386 520 A1 known. In this known nozzle, a vacuum is generated by utilizing the Venturi effect with the help of the vacuum line that opens into the main channel. In the area of the main valve, the cross-section of the main channel is reduced so that a fluid flowing through the nozzle is accelerated in the area of the main valve, whereby the dynamic pressure increases and the static pressure in the area of the cross-sectional taper decreases. The decrease in the static pressure can be used to generate a negative pressure via the vacuum line. The vacuum can be used in a known manner, for example to actuate an automatic shutdown device.

In previously known nozzles, the volume flow to be delivered by the nozzle is often variably adjustable. For example, the opening stroke of the main valve can usually be manually selected by positioning a hand lever, thus adjusting the volume flow. Nozzles for dispensing an aqueous urea solution (AdBlue) are also known, which are designed as standard to deliver a first maximum volume flow, whereby a second maximum volume flow can be set by interaction with the tank of a motor vehicle, which is greater than the first maximum volume flow (see. EP 3 369 700 A1 ).

A problem with the nozzles described above is that, due to the variable volume flow, the vacuum generated by the volume flow is also subject to corresponding fluctuations. An automatic shutdown device acted upon by the vacuum must therefore fundamentally be designed to ensure safe shutdown within the vacuum range specified by the fluctuations. Ensuring this is complex in terms of construction. In particular, if the volume flow is too low or the volume flow fluctuates too much, the tolerance requirements for the components to be manufactured and the costs are very high. Based on this prior art, the object of the present invention is to provide a nozzle valve which enables improved vacuum generation. This object is achieved with the features of the independent claims. Advantageous embodiments are specified in the dependent claims.

According to the invention, the main channel downstream of the main valve merges into a sub-channel and into at least one bridging channel running parallel to the sub-channel, wherein the sub-channel and/or the at least one bridging channel have means for prioritizing the fluid flow, which are designed such that a relative proportion of the total volume flow flowing through the sub-channel decreases as the total volume flow increases. Furthermore, according to the invention, the sub-channel has a taper, wherein the vacuum line opens into the sub-channel in the region of the taper.

First, some terms used in the context of the invention are explained. If a main channel merges into two parallel channels (partial channel and bridging channel), this means in the sense of the present description that the main channel splits at the transition so that a fluid can flow either through the partial channel or through the bridging channel. can flow. The geometric shape or alignment of the channels relative to one another is not restricted by the term "parallel". A tapering of the partial channel can be achieved in particular by a flow cross-section given by a wall of the partial channel decreasing in the direction of flow. The partial channel can preferably form a Venturi nozzle together with the vacuum line opening into it.

The main valve is preferably coupled in a generally known manner to a switching lever in order to move the main valve between a closed position and an open position. The main valve can also be coupled to an automatic shut-off device. It can be provided in particular that the automatic shut-off device is coupled in a generally known manner (see for example EP 2 386 520 A1 ) is designed to move the main valve into a closed position independently of the position of the control lever.

The partial channel according to the invention, which has a taper with a vacuum line connected to it, decouples the vacuum generation from the main valve and from the total volume flow flowing through the main channel. In particular, a part of the flow cross section of the main channel is delimited by the partial channel and separated from the remaining part of the flow cross section, which is assigned to the at least one bridging channel.

Since the main channel merges into the partial channel and the bridging channel, part of the total volume flow can flow through the partial channel and another part of the total volume flow can flow through the bridging channel. The means according to the invention for prioritizing the fluid flow make it possible to divide of the total volume flow on the two parallel channels depending on the total volume flow is influenced in such a way that as the total volume flow increases, the relative proportion flowing through the sub-channel decreases. This means, for example, that with a small total volume flow, a larger relative proportion of the total volume flow can flow through the sub-channel. For example, it can be provided that with a low total volume flow of between 0 and 5 l/min, the total volume flow flows completely or essentially completely through the sub-channel. As a result, a comparatively high "sub-channel volume flow" can be generated in the sub-channel (due to the smaller flow cross-section compared to the entire main channel) even with a small total volume flow, which in turn can be used to generate a desired vacuum.

A decrease in the relative proportion of the total volume flow that flows through the partial channel means that with larger total volume flows (for example from 5 l/min) the bridging channel(s) are also used to absorb part of the total volume flow. As the total volume flow increases, a larger proportion of the total volume flow is therefore passed through the bridging channels, so that the "partial channel volume flow" increases less or, in the best case, can even be kept constant. As a result, the vacuum generated by the taper also changes less as the total volume flow increases or can even be kept constant over large operating ranges. In this case, an automatic shutdown device connected to the vacuum line experiences a constant vacuum over large operating ranges, so that the shutdown device can ensure automatic shutdown over a large flow range with a structurally simple design.

The means for prioritizing the fluid flow can be designed to divert and/or control the fluid flow. In particular, the means for prioritizing the fluid flow can be designed to direct a larger relative proportion of the total volume flow into the partial channel when the total volume flow is low and to direct a larger relative proportion of the total volume flow into the at least one bridging channel when the total volume flow is high. The means for prioritizing the fluid flow can, for example, have a rigid steering section for directing the fluid flow. Alternatively or additionally, it can also be provided that the means for prioritizing the fluid flow have movable steering sections which are designed to at least partially close the partial channel and/or the at least one bridging channel in the manner of a valve.

In a preferred embodiment, the means for prioritizing the fluid flow comprise an overflow valve which is designed to at least partially close the bypass channel. The overflow valve can further preferably be designed to completely close the bypass channel. By making the bypass channel at least partially or completely closable by the overflow valve, the flow rate that flows through the partial channel can be controlled. In particular, if the total volume flow is low, the total volume flow can be completely guided through the partial channel by completely closing the overflow valve. If the total volume flow is high, part of the total volume flow can be guided through the bypass channel by opening the overflow valve, so that the relative proportion of the total volume flow flowing through the partial channel is reduced. The overflow valve can also have a controllable variable valve stroke, so that the volume flow through the bridging channel can be controlled by the valve stroke. The closable overflow valve can ensure a uniform flow through the partial channel and thus a uniform vacuum generation. If there are several (parallel to each other) separate bridging channels, several of the bridging channels or even all of the bridging channels can each have an overflow valve.

Preferably, the overflow valve can be opened by a fluid pressure prevailing upstream of the overflow valve. This has the advantage that with small flow rates, which are accompanied by a correspondingly low fluid pressure, the overflow valve initially remains closed and thus a larger or the entire fluid quantity initially flows through the partial channel and ensures a reliable vacuum generation there. With larger flow rates, the fluid pressure upstream of the overflow valve increases so that it is opened by the fluid pressure and absorbs part of the fluid flow flowing through the main channel. The portion of the fluid flow flowing through the partial channel and the associated vacuum are automatically equalized in this way. The overflow valve or valves can in particular have a closing body pre-tensioned upstream into a closed position. This makes it easy to open the overflow valves depending on the fluid pressure. Within the scope of the invention, active control of the overflow valves is also possible in principle, for example by an actuating mechanism that actuates the overflow valves depending on the total volume flow.

In a preferred embodiment, the main channel has at least two bridging channels running parallel to the partial channel wherein each of the two bridging channels preferably comprises an overflow valve for closing the bridging channel. The overflow valves preferably each have a closing body pre-tensioned upstream into a closed position and can be opened by a fluid pressure prevailing in front of the overflow valve. By having two bridging channels, the fluid can flow past the partial channel either through one or the other bridging channel. The reliability of the vacuum generation can be further increased as a result, since if one bridging channel fails (for example due to blockage or malfunction of the associated overflow valve), another bridging channel is still available which can absorb at least part of the fluid flow.

Preferably, in an embodiment with two bridging channels, a first of the overflow valves is designed to be moved into the open position when a first fluid pressure is exceeded, wherein a second of the overflow valves is designed to be moved into the open position when a second fluid pressure, different from the first, is exceeded. For example, a preload of the closing body of the first overflow valve can be different from a preload of the closing body of the second overflow valve. Alternatively or additionally, the closing bodies of the first and second overflow valves can also have upstream-facing front surfaces that can be acted upon by the fluid pressure and that differ from one another in terms of different shape and/or size. For example, the front surface of the first overflow valve can be larger than the front surface of the second overflow valve. A fluid pressure prevailing upstream is converted into a larger force due to the larger surface, so that the overflow valve with the larger front surface opens first and the overflow valve with the smaller front surface only opens when the first overflow valve is closed. a higher fluid pressure. The design of the overflow valves described above makes it possible to specify with high accuracy and certainty which portion of the volume flow should flow through the partial channel, so that the vacuum generated there is also set with high reliability over a large flow range.

In a preferred embodiment, the main valve has a main valve body and a valve stem arranged downstream of the main valve body, with at least a section of the partial channel being arranged radially next to the valve stem. The arrangement of the section of the partial channel radially next to the valve stem means in this case that the section is cut by an imaginary axis extending from the valve stem and perpendicular to the axial direction of the valve stem. By arranging the partial channel radially next to the valve stem, the vacuum can be generated in a space-saving manner immediately downstream of the main valve. The distance to any automatic shutdown device that may be present can be kept small, which also means that the size or length of the rooms and lines to be evacuated can be reduced. The working range of the automatic shutdown device can thus be further improved. In addition, due to the arrangement of the partial channel next to the valve stem, it is not necessary to make modifications to the mechanism connected to the valve stem for actuating the main valve or to the automatic shutdown device connected to it.

The partial channel and the at least one bridging channel can preferably be distributed uniformly 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 five. The uniform arrangement leads to a evenly distributed fluid flow and minimizing turbulent flows. Preferably, the valve stem is arranged substantially centrally with respect to a cross section of the main channel, wherein the partial channel and/or the bridging channels are further preferably arranged off-center with respect to the cross section of the main channel.

In a preferred embodiment, the dispensing valve comprises an automatic shut-off device for actuating 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 basically known and will therefore not be explained in more detail here.

The nozzle can have a first adjustable maximum volume flow and a second maximum volume flow that is different from the first. The design of a nozzle for delivering different maximum volume flows is known, for example, from the document EP3 369 700 known in principle. It has been shown within the scope of the invention that the advantages according to the invention are particularly evident in such a nozzle valve, since the flow through the partial channel can be optimally designed for the two maximum volume flows with the help of the bridging channel or channels and in particular with the help of one or more associated overflow valves. An optimal vacuum and thus reliable and safe operation of the automatic shut-off device can thus be guaranteed for both maximum volume flows.

To set the first or second maximum flow rate, the EP 3 369 700 A1 proposed to realize the first and second maximum volume flow by means of a limitation of the maximum opening position of the main valve, whereby an interaction between a signal element of the tank and the main valve via an automatic shut-off device of the nozzle valve. This solution enables reliable and safe adjustment of the first and second maximum volume flow, but the solution is structurally complex because intervention in the automatic shut-off device of the nozzle valve is necessary.

• das Zapfventil weist einen ersten maximalen Volumenstrom und einen zweiten maximalen Volumenstrom auf, wobei der zweite maximale Volumenstrom größer ist als der erste,
• das Zapfventil weist einen separat vom Hauptventil ausgebildeten einstellbaren Strömungsbegrenzer auf, welcher dazu ausgebildet ist, den Fluiddurchfluss wahlweise auf den ersten oder zweiten maximalen Volumenstrom zu begrenzen,
• das Zapfventil weist eine Betätigungseinrichtung auf, die zur Wechselwirkung mit einem dem Tank eines Kraftfahrzeugs zugeordneten Signalelement sowie zur wahlweisen Einstellung des Strömungsbegrenzers auf den ersten oder den zweiten maximalen Volumenstrom ausgebildet ist.

In a preferred embodiment, the dispensing valve comprises the following features:

• the nozzle has a first maximum volume flow and a second maximum volume flow, the second maximum volume flow being greater than the first,
• the nozzle valve has an adjustable flow restrictor which is designed separately from the main valve and is designed to limit the fluid flow optionally to the first or second maximum volume flow,
• the nozzle has an actuating device which is designed to interact with a signal element assigned to the tank of a motor vehicle and to selectively adjust the flow limiter to the first or the second maximum volume flow.

The above-described idea of a nozzle with a first and a second maximum volume flow may have an inventive content independently of the characterizing features of claim 1.

In this case, the term nozzle can refer to a device for controlling the flow of liquid during a refueling process. The requirements for the construction and The operation of automatic nozzles for use at fuel pumps is regulated in DIN EN 13012.

In the preferred embodiment, the nozzle has an adjustable flow limiter which is designed to selectively limit the fluid flow to the first or second maximum volume flow. This means that at a given constant fluid pressure at the nozzle inlet, only the set maximum volume flow can pass through the flow limiter. In particular, the user can use a switching lever and the main valve coupled to it to control the volume flow only up to the set first or second maximum volume flow. The set maximum volume flow thus limits the maximum liquid delivery per unit of time. The second maximum volume flow is higher than the first maximum volume flow. The preferred embodiment is not limited to a nozzle with exactly two adjustable maximum volume flows; it also includes embodiments in which the flow limiter can be set to three or more adjustable maximum volume flows.

In the embodiment described above, the adjustable flow restrictor is designed separately from the main valve. This means that the flow restrictor can be set to the first or second maximum volume flow regardless of the state of the main valve. The flow restrictor can be arranged at a distance from the main valve upstream or downstream of the main valve.

Since the adjustable flow limiter according to the invention is designed separately from the main valve, the optional limitation of the fluid flow is independent of the main valve and its automatic shut-off. Therefore, no complex Modifications to the automatic shut-off and/or the main valve are required, which can simplify the design of the nozzle and increase functional reliability. The arrangement of a flow limiter separate from the main valve also makes repairs much easier in the event of a malfunction. The flow limiter can also be designed to be retrofitted to existing nozzles.

In one embodiment, the flow restrictor is arranged downstream of the main valve. The flow restrictor is preferably arranged in an outlet pipe of the nozzle. By arranging the flow restrictor in the outlet pipe, the outlet pipe can be replaced as a separate unit, so that in the event of a malfunction, it can be easily repaired. It is also possible to retrofit nozzles with the flow restrictor according to the invention by replacing the outlet pipe.

The first adjustable maximum volume flow can be less than 15 l/min, preferably it is between 5 l/min and 15 l/min, more preferably between 5 l/min and 10 l/min. Additionally or alternatively, the second adjustable maximum volume flow can be less than 50 l/min, preferably it is between 10 l/min and 50 l/min, more preferably between 20 l/min and 40 l/min.

Preferably, the flow limiter is set to the first adjustable maximum volume flow as standard, with the second adjustable maximum volume flow only being set when the actuating device detects the signal element. The detection of the signal element can take place in particular through the interaction between the actuating device and the signal element. By setting the second adjustable maximum volume flow as standard If the smaller first maximum volume flow is set, the smaller volume flow is delivered as standard, whereby larger volume flows are only delivered if the detection of the corresponding signal element ensures that the tank to be refuelled is also suitable for the larger second maximum volume flow due to its size.

In a preferred embodiment, the actuating device is designed to interact with a ring magnet of a filler neck according to ISO 22241-4. In this case, the signal element can therefore comprise a ring magnet of a filler neck according to ISO 22241-4.

The flow limiter can be actuated to selectively set the first or second maximum volume flow magnetically and/or mechanically (for example by means of spring elements) and/or pneumatically (for example by means of compressed air) and/or electrically (for example by means of a servomotor). In a preferred embodiment, the actuating device has a displaceably arranged magnetic element which is designed for mechanical actuation of the flow limiter. A magnetic force generated between the magnetic element and the ring magnet can be mechanically transmitted to the flow limiter in order to actuate it. In particular, the magnetic element can be connected to the flow limiter by a mechanical signal transmission device, for example by a transmission rod.

The flow restrictor can have a throttle valve body, wherein the mechanical signal transmission device or the transmission rod is preferably connected to the throttle valve body. The magnetic force can be transmitted to the throttle valve body via the transmission rod in order to to open or close the flow restrictor. The throttle valve body is preferably movable in a first direction when the flow restrictor is actuated by the signal transmission device. Preferably, a return element connected to the throttle valve body is also provided, which can in particular be designed to urge the throttle valve body in a direction opposite to the first direction.

The flow limiter can also have a throttle valve seat, wherein the throttle valve body can preferably be moved downstream into a closed position in which it rests against the throttle valve seat. The flow limiter can also be referred to as a throttle valve in this embodiment. It is preferably provided that the throttle valve body can be moved into the closed position for optionally limiting the fluid flow to the first maximum volume flow and into an open position for optionally limiting the fluid flow to the second maximum volume flow. The movement into the open position can be carried out by the transmission of the magnetic force by means of the signal transmission device to the throttle valve body. The movement of the throttle valve body into the closed position can be carried out by the return element or be supported by it, for example. Alternatively or additionally, the movement of the throttle valve body into the closed position can also be achieved by the throttle valve body being pushed into the closed position by the fluid pressure when the nozzle is inserted into a filler neck without a ring magnet.

In particular, the above-mentioned standard setting of the flow restrictor to the first maximum volume flow can be achieved by the movement of the throttle valve body into the closed position generated by the return element or by the fluid pressure. can be achieved. If the nozzle is inserted into a filler neck which has a ring magnet, a magnetic force acts between the ring magnet and the magnetic element. In the preferred embodiment described here, the magnetic force acting between the ring magnet and the magnetic element is designed to bring the throttle valve body into the open position against a closing force generated by the fluid pressure and by the return element, if present, and to hold it there against the closing forces generated by the fluid pressure.

Preferably, a flow guide device is arranged upstream of the throttle valve body, which is designed to reduce a closing force exerted by the flowing fluid on the throttle valve body. The flow guide device can, in particular, have guide surfaces that are inclined relative to an axial direction of the throttle valve body. The guide surfaces can also be designed to divert the fluid flow from an upstream-facing rear surface of the throttle valve body in the radial direction (i.e. perpendicular to the axial direction of the throttle valve body), so that preferably at least part of the fluid flow is guided past the rear surface. For example, it can be provided that the guide surfaces are designed to divert the fluid flow radially outwards from an axis running centrally through the throttle valve body. This can ensure a lateral flow onto the throttle valve body, which reduces the closing forces generated by the fluid.

The mobility of the throttle valve body can be limited in the upstream direction by a stop. By limiting the mobility of the throttle valve body, it assumes a defined position in the open position. Preferably, a bypass channel is provided that bridges the flow restrictor. Due to the bypass channel, the flow restrictor does not completely prevent the fluid flow through the nozzle valve, but merely reduces the fluid flow. Preferably, the bypass channel is designed to allow the first maximum volume flow to pass when the flow restrictor is closed. The bypass channel can have a through opening for the fluid flow that extends through the throttle valve body. Alternatively or additionally, the bypass channel can also have a secondary arm that is spaced apart from the flow restrictor and runs parallel to a fluid flow that passes through the open flow restrictor.

The nozzle can have a safety valve arranged downstream of the flow limiter, which is forced into a closed position downstream by a return element, wherein the safety valve can be moved into an open position by interaction with a filler neck of the tank. Such a safety valve is known, for example, from EP 2 733 113 A1 Preferably, the nozzle also has an automatic shut-off device that automatically interrupts the filling process when the tank is full. For this purpose, a sensor line can be provided that extends to the outlet end of the nozzle and is in pneumatic connection with the automatic shut-off device. Details of the design of such an automatic shut-off device can be found, for example, in the EP 2 386 520 A1 On the one hand, the safety valve serves as an anti-drip valve to prevent the unwanted leakage of residual amounts of fluid, for example when the main valve is closed.

In particular, it can be provided that the actuating device relative to a valve stem of the safety valve is designed to be displaceable, wherein the valve stem of the safety valve preferably has a cavity in which the magnetic element of the actuating device is arranged displaceably. It has been shown that the arrangement of the magnetic element within the valve stem of the safety valve enables a particularly space-saving construction. If the actuating device has a transmission rod, this can be guided through a through opening in a rear wall of the valve stem.

The present invention further relates to a method for dispensing a fluid with the aid of a dispensing valve according to the invention, in which a first portion of the fluid flow is passed through the partial channel and a second portion of the fluid flow is passed through the at least one bridging channel, wherein the portion of the fluid flow passed through the partial channel is used to generate a vacuum.

Preferably, the at least one bridging channel has an overflow valve, wherein the overflow valve is used to adjust the proportion of the fluid flow flowing through the partial channel. The method according to the invention can be further developed by further features already described above in connection with the nozzle valve according to the invention.

Figur 1:

ein erfindungsgemäßes Zapfventil in einer seitlichen Schnittdarstellung;

Figur 2:

einen Ausschnitt aus der Figur 1 in einer vergrößerten Ansicht;

Figur 3:

eine Querschnittsansicht entlang der in Figur 1 gezeigten Linie H-H;

Figur 4:

den in Figur 2 gezeigten Ausschnitt nach der Betätigung des Hauptventils ohne Fluidstrom;

Figur 5:

das erfindungsgemäße Zapfventil der Figuren 1 bis 4 während der Ausbringung eines Fluids mit einem ersten maximalen Volumenstrom;

Figur 6:

ein Ausschnitt aus der Figur 5 in einer Vergrößerten Ansicht;

Figur 7:

das erfindungsgemäße Zapfventil der Figuren 1 bis 6 während der Ausbringung eines Fluids mit einem zweiten maximalen Volumenstrom;

Figur 8:

ein Ausschnitt aus der Figur 7 in einer Vergrößerten Ansicht;

Figur 9:

eine seitliche Schnittansicht durch ein Auslaufrohr des erfindungsgemäßen Zapfventils vor der Beätigung des Hauptventils;

Figur 10:

eine seitliche Schnittansicht durch das Auslaufrohr des erfindungsgemäßen Zapfventils während der Ausbringung eines Fluids mit dem ersten maximalen Volumenstrom;

Figur 11:

eine seitliche Schnittansicht durch das Auslaufrohr des erfindungsgemäßen Zapfventils während der Ausbringung eines Fluids mit dem zweiten maximalen Volumenstrom.

An advantageous embodiment of the invention is explained below by way of example with reference to the accompanying drawings. They show:

Figure 1:

a nozzle according to the invention in a side sectional view;

Figure 2:

an excerpt from the Figure 1 in an enlarged view;

Figure 3:

a cross-sectional view along the Figure 1 shown line HH;

Figure 4:

the in Figure 2 shown section after actuation of the main valve without fluid flow;

Figure 5:

the inventive nozzle of the Figures 1 to 4 during the application of a fluid with a first maximum volume flow;

Figure 6:

an excerpt from the Figure 5 in an enlarged view;

Figure 7:

the inventive nozzle of the Figures 1 to 6 during the application of a fluid with a second maximum volume flow;

Figure 8:

an excerpt from the Figure 7 in an enlarged view;

Figure 9:

a side sectional view through an outlet pipe of the nozzle valve according to the invention before the main valve is actuated;

Figure 10:

a side sectional view through the outlet pipe of the nozzle according to the invention during the discharge of a fluid with the first maximum volume flow;

Figure 11:

a side sectional view through the outlet pipe of the nozzle according to the invention during the dispensing of a fluid with the second maximum volume flow.

The nozzle comprises a housing 1 with an inlet 2 to which a supply line for supplying a fluid is connected. (not shown). At the front end of the housing 1, a discharge pipe 3 is inserted, at the front end of which an outlet 25 is located. The outlet 25 can, for example, be inserted into a filler neck 22, 26 of a vehicle (see Figures 5 and 7 ).

A main channel 16 extends from the inlet 2 to the outlet 25, in which a main valve 5 is arranged to control the total volume flow. The main valve 5 comprises a main valve body 6 (see Figure 2 ), which can be moved against a main valve seat 27 to close the main valve 5. The valve body 6 is coupled to a switching lever 4 and to an automatic shut-off device 30 via a valve stem 15 in a basically known manner. The valve stem 15 has an outer sleeve 24, which holds the valve body 6 in the closed position (see Figures 1 and 2 ) with a large closing force against the valve seat 27. The valve stem 15 also comprises an inner piston 12 which is designed to be movable relative to the outer sleeve 24 and which is urged upstream by a return element 13 (see Figure 2 ). The valve body 6 is connected to the inner piston 12. When the switching lever 4 is operated by a user, the outer sleeve 24 of the valve stem 15 is moved downstream and thereby lifted off the valve body 6. The valve body 6 is now pressed into the closed position only by the restoring force of the restoring element 13 (see also Figure 4 ). The restoring force of the restoring element 13 is so small that the valve body 6 together with the inner piston 12 can be moved into the open position by a normal fluid pressure.

The automatic shut-off device 30 is designed to move the main valve 5 into a closed position regardless of the position of the switching lever 4. The functioning of the automatic shut-off device is basically known (see for example EP 2 386 520 A1 ) and will not be explained in more detail here.

From the automatic shutdown device 30 extends a Figures 1 to 8 sensor line (not shown) through the outlet pipe 3 to the outlet 25. The sensor line is in pneumatic connection with the shut-off device 30. When the fluid level reaches the front end of the outlet pipe 3 during the discharge of the fluid and covers the sensor line, an accompanying pressure change leads to a triggering of the automatic shut-off device 30 and, as a result, to a closing of the main valve 5, independent of the position of the control lever 4.

The nozzle is designed to optionally deliver a first maximum volume flow or a second maximum volume flow. For this purpose, the nozzle comprises a throttle valve arranged in the outlet pipe, which is designed to optionally limit the fluid flow to the first or second maximum volume flow. The throttle valve is actuated by interaction with a ring magnet of a filler neck according to ISO 22241-4. By default, i.e. if there is no ring magnet, the nozzle is set to deliver the first maximum volume flow. If the outlet pipe 3 is inserted into a filler neck without a ring magnet, the first maximum volume flow can be delivered by operating the switch lever 4. The first maximum volume flow is 9 l/min in this case. If the outlet pipe 3 is inserted into a filler neck according to ISO 22241-4 with a ring magnet, the nozzle can deliver the second maximum volume flow, which is 20 l/min in this case. The functionality of the throttle valve is explained in conjunction with the Figures 9 to 11 explained in more detail.

The functioning of the automatic shutdown device 30 requires that it be subjected to a vacuum. The vacuum is generated as described below. The main channel 16 merges downstream of the main valve 5 in the area 14 into a sub-channel 10 and into five parallel bridging channels 20a to 20e (see Figure 3 ). The partial channel 10 is delimited by a wall 31. The partial channel 10 has an opening 32 defined by the wall 31 and a section 33 tapering conically from the opening 32 in the direction of flow (see Figure 2 ). In the area of section 33 there is an inlet 8 of a vacuum line 9 into the partial channel 10. Due to the tapering section 33, the flow speed of the fluid in the partial channel 10 increases, so that the static pressure drops. This allows a vacuum to be generated via the vacuum line 9 and the automatic shut-off device 30 to be acted upon by it. Downstream of the inlet 8 of the vacuum line 9, the partial channel 10 widens again. The partial channel 10 forms a Venturi nozzle together with the vacuum line.

The bridging channels 20a to 20e each have a means for prioritizing the fluid flow, which in the present case is designed as an overflow valve 21a to 21e, whereby the overflow valves 21d and 21e are not visible in the sectional view shown. The Figure 2 The overflow valve 21c shown in FIG. 1 is described. It comprises a shaft 19 and a closing body 17, which is tensioned upstream into a closed position by a return element 18. In the Figures 1 to 3 the main valve 5 is closed so that no fluid flows through the main channel 16. The closing body 17 of the overflow valve 21c is held in the closed position by the return element 18. The other overflow valves are also in the Figures 1 to 3 accordingly in their closed position.

The return elements 18 of the overflow valves 21a to 21e have different return forces, so that different fluid pressures are required to open the overflow valves 21a to 21e. This will be explained below in connection with the Figures 5 to 8 explained in more detail.

By operating the control lever 4, the valve stem 15 is moved downstream so that the outer sleeve 24 of the valve stem 15 is released from the valve body 6 (see Figure 4 ). If no fluid is supplied to the inlet 2, the valve body 6 initially remains in the closed position, as already explained above, in which it is pressed against the valve seat 27 by the return element 13. This is in the Figure 4 illustrated.

Only when a fluid with a certain fluid pressure is supplied to the inlet 2, the valve body 6 gives way to the opening pressure and moves against the force of the return element 13 into an opening position. This is shown in the Figures 5 and 6 shown. The fluid can now enter from the inlet 2 into the area 14 in front of the partial channel 10 and the bridging channels 20a - 20e. Part of the fluid flows into the partial channel 10 and another part of the fluid in the direction of the overflow valves 21a to 21e. Since the overflow valves 21a to 21e are initially forced into the closed position by the return elements 18, a larger proportion of the fluid initially flows through the partial channel 10, so that a flow occurs there shortly after the main valve 5 opens and a vacuum is generated. After a short time, a fluid pressure builds up on the upstream-facing front surfaces of the closing bodies 17 of the overflow valves 21a to 21e, which depends on the supply pressure of the fluid, the opening position of the main valve and the available flow cross-sections within the nozzle downstream of the overflow valves 21a to 21e.

In the Figures 5 and 6 the nozzle according to the invention is shown after the outlet pipe has been inserted into a filler neck 22 of a vehicle and the main valve has been opened. The filler neck 22 is designed in accordance with ISO 22241-5 and does not have a ring magnet. Accordingly, the throttle valve located in the outlet pipe 3 is in the closed position and allows a maximum flow through the outlet pipe 3 of approximately 9 l/min.

In this state, there is a fluid pressure in the area 14 in front of the overflow valves 21a to 21e which is sufficient to move the closing body of the overflow valve 21c into the open position against the force of the return element 18 (see Figure 6 ). The reset elements 18 of the overflow valves 21a, 21b and 21c shown in this illustration have different reset forces. In particular, the reset force of the valve 21c is smaller than that of the valve 21b, and the reset force of the valve 21b is in turn smaller than the reset force of the valve 21a. This leads to the fact that in the Figures 5 and 6 prevailing condition, the overflow valve 21a remains closed and the overflow valve 21b assumes an intermediate position in which a small flow is possible, with the valve 21c being fully open (see Figure 6 ). The restoring forces of the overflow valves are set in particular so that the resulting fluid flow through the partial channel 10 assumes an optimal value for vacuum generation. The overflow valves 21d and 21e, which cannot be seen in this view, also have a greater restoring force than the overflow valve 21b and therefore remain closed.

The Figures 7 and 8 show the nozzle according to the invention after it has been inserted into a filler neck 26 according to ISO 22241-4 with ring magnet 23. The ring magnet 23 actuates the throttle valve in a manner explained in more detail below, so that the nozzle can now deliver a maximum volume flow of 20 l/min. Due to the increased maximum volume flow, there is a higher fluid pressure in the area 14 in front of the partial channel 10 and the bridging channels 20a-20e, so that all overflow valves 21a-21e open (see Figure 8). By opening all overflow valves, the volume flow flowing through the partial channel 10 can be increased compared to the volume flow in the

Figures 5 and 6 shown state can be kept almost the same. The vacuum generated by the partial channel 10 is thus essentially constant, regardless of whether the first maximum volume flow of approximately 9 l/min or the second maximum volume flow of approximately 20 l/min is delivered with the dispensing valve. Even with other volume flows, which can be set in particular with the aid of the hand lever and an opening position of the main valve corresponding to the hand lever position, the overflow valves according to the invention lead to an equalization of the vacuum generated.

Figure 9 shows a side sectional view through the outlet pipe 3 of the nozzle according to the invention. In this view, the sensor line 34 can be seen, which is in pneumatic connection with the automatic shut-off device 30. When the fluid level reaches the front end of the outlet pipe during the discharge of the fluid and thus covers the sensor line 34, an accompanying pressure change leads to a triggering of the automatic shut-off device 30 and thus to a closing of the main valve 5.

In the area of the outlet of the outlet pipe 3, a safety valve 7 is also provided, which has a valve stem 35 and which closes downstream against a valve seat 36 (please refer Figure 10 ). The upstream end of the valve stem 35 is provided with a magnet 37.

The outlet pipe 3 also has a sleeve 39 which can be displaced along its axial direction and which is moved by a spring 40 into the Figure 9 A ring-shaped magnet 41 is arranged on the sleeve 39, which moves the valve stem 35 and the safety valve into the position shown in the Figure 9 shown closed position.

The sensor line 34 has a sensor line valve 38 arranged at the outlet end with a valve stem 42, which closes against a valve seat with its outlet end. The valve stem 42 comprises an actuating magnet 43 at the opposite end, which holds the valve stem 42 in the closed position by interacting with the active magnet 41.

In the Figure 9 In the state shown, the main channel 16 is closed by the safety valve 7. In addition, the sensor line 34 is closed by the sensor line valve 38. If the main valve 5 is actuated by means of the switching lever 4 in this state, the discharge of the fluid is prevented because the outlet pipe is closed by the safety valve 7.

In the outlet pipe 3 there is also an adjustable flow limiter, which in this case is formed by a throttle valve 49. With the help of the throttle valve 49, a fluid flow through the tap valve or through the outlet pipe 3 can be limited to either the first maximum volume flow or the second maximum volume flow. The throttle valve 49 has a valve body 50, which is connected to a magnetic element 52 by means of a transmission rod 51. The magnetic element 52 is arranged in a cavity 53 within the valve stem 35 of the safety valve 7 and is displaceable relative to the valve stem 35 in the axial direction of the outlet pipe 3. The transmission rod 51 is also displaceable relative to the valve stem 35 and passes through a through opening located in an upstream-facing rear wall of the valve stem 35.

The magnetic element 52 and the transmission rod 51 together form an actuating device for the throttle valve 49. In the Figure 9 In the state shown, the valve body 50 is in a closed position in which it rests downstream against a valve seat 54 of the throttle valve 49. The valve body 50 is pushed downstream relative to the valve stem 35 by a return element 55 and is thereby clamped into the valve seat 54. The functioning of the actuating device 51, 52 and the setting of the throttle valve 49 to the second maximum volume flow is carried out in conjunction with the Figures 10 and 11 explained.

The Figure 10 shows the outlet pipe 3 after it has been inserted into a filler neck 22 of a vehicle tank. In contrast to the Figure 9 In addition, the main valve 5 was moved into an open position by actuating the shift lever 4. The filler neck 22 in this case is the filler neck of a urea tank of a passenger car according to ISO 22241-5 without a ring magnet.

The filler neck 22 is in a basically known manner (see EP 3 369 700 A1 ) is designed to move the sleeve 39 upstream of the outlet pipe 3 relative to the sleeve 39 when inserting the outlet pipe 3. Figure 9 shown blocking position into an open position. When the sleeve 39 is moved, the associated magnet 41 also moves upstream relative to the outlet pipe 3, whereby it is guided by magnetic Interaction takes along the magnet 37 fixed to the valve stem 35 and the actuating magnet 43 fixed to the valve stem 42 and thus opens the sensor line valve 38 and the safety valve 7.

The magnetic element 52 is sufficiently far away from the active magnet 41 so that it is not influenced by the displacement of the active magnet 41 or only in a negligible way. Since the magnetic element 52, the transmission rod 51 and the valve body 50 connected to it are movable relative to the valve stem 35 and are pushed into the closed position by the return element 55, the valve body 50 remains in the closed position. In the sectional view of the Figures 9 to 11 not visible through holes through which a certain volume flow can pass through the outlet pipe 3 even when the valve body 50 is in the closed position. This certain volume flow is at most as large as the first maximum volume flow of the throttle valve, which in this case is 9 l/min. The volume flow passing through the opening of the main valve 5 is therefore limited by the closed throttle valve 49 to the first maximum volume flow of the nozzle valve. In addition to or as an alternative to the through holes in the valve seat 54, through holes can also be provided in the valve body 50 in an alternative embodiment.

The Figure 11 shows the outlet pipe after it has been inserted into a filler neck 26, which, in contrast to the filler neck 22 of the Figure 10 is the filler neck of a urea tank of a passenger car according to ISO 22241-4 with ring magnet 23. Just as in Figure 10 the main valve 5 is in an open position.

When inserting the outlet pipe, the sleeve 39, as already described in connection with the Figure 10 described, is displaced relative to the outlet pipe 3 through the filler neck 26, so that both the sensor line valve 38 and the safety valve 7 are opened by the interaction between the active magnet 41 and the magnets 37 and 43.

In addition, there is an interaction between the ring magnet 23 and the magnetic element 52. In particular, the ring magnet 23 and the magnetic element 52 are arranged in such a way that when the outlet pipe 3 is inserted into the filler neck 26, poles of the same name initially face each other and a repulsive force is thus exerted on the magnetic element 52. The magnetic element 52 is designed in such a way that the magnetic force exceeds the opposing restoring force of the restoring element 55. The repulsive force therefore leads to a displacement of the magnetic element 52 in an upstream direction relative to the outlet pipe 3. Due to the connection of the magnetic element 52 to the valve body 50 formed by the transmission rod 51, the valve body 50 is moved into an open position against the restoring force of the restoring element 55. The movement of the valve body 50 is limited upstream by a stop 56.

In the open position of the throttle valve 49, at a given fluid pressure at the inlet of the nozzle, a larger volume flow can pass through the outlet pipe than in the Figure 10 shown closed position. In particular, the throttle valve 49 in the state shown is designed, when the main valve 5 is sufficiently opened, to allow the second maximum volume flow through the outlet pipe 3, which in the present case is 20 l/min. The magnetic force acting between the ring magnet 23 and the magnetic element 52 is so large that the valve body 50 is held in the open position against the fluid pressure and against the restoring force of the restoring element 55.

Claims (13)

Dispensing valve for dispensing a fluid, with an inlet (2) for connecting a fluid supply line, a main channel (16) which connects the inlet (2) to an outlet (25), a main valve (5) for controlling a total volume flow through the main channel (16), and with a vacuum line (9) opening into the main channel (16), wherein the main channel (16) has a partial channel (10) with a taper (33) and the vacuum line (9) opens into the partial channel (10) in the region of the taper (33), wherein the main channel downstream of the main valve (5) is divided into the partial channel (10) and into at least one bridging channel (20a - 20e) running parallel to the partial channel (10), wherein the partial channel (10) and/or the at least one bridging channel (20a - 20e) have means for prioritizing the fluid flow, which are designed in such a way that a the relative proportion of the total volume flow flowing through the partial channel (10) decreases as the total volume flow increases, wherein the main valve (5) has a valve body (6) and a valve stem (15) arranged downstream of the valve body (6), characterized in that at least a section of the partial channel (10) is arranged in the radial direction next to the valve stem (15). Nozzle according to claim 1, wherein the means for prioritizing the fluid flow are designed to divert and/or control the fluid flow. Nozzle according to claim 1 or 2, wherein the means for prioritizing the fluid flow comprise an overflow valve (21a, 21b, 21c, 21d, 21e) which is designed to at least partially close the bridging channel (20a - 20e). Nozzle according to claim 3, wherein the overflow valve (21a, 21b, 21c, 21d, 21e) can be opened by a fluid pressure prevailing upstream of the overflow valve (21a, 21b, 21c, 21d, 21e), wherein the overflow valve (21a, 21b, 21c, 21d, 21e) preferably has a closing body (17) prestressed upstream into a closed position. Nozzle according to claim 4, in which the main channel (16) has at least two bridging channels (20a - 20e) running parallel to the partial channel (10), each with an overflow valve (21a, 21b, 21c, 21d, 21e) for at least partially closing the bridging channel (20a - 20e), wherein the overflow valves (21a, 21b, 21c, 21d, 21e) each have a closing body (17) prestressed upstream into a closed position and can be opened by a fluid pressure prevailing in front of the overflow valves (21a, 21b, 21c, 21d, 21e). Nozzle according to claim 5, wherein a first of the overflow valves (21a, 21b, 21c, 21d, 21e) is designed to be moved into the open position when a first fluid pressure is exceeded, wherein a second of the overflow valves (21a, 21b, 21c, 21d, 21e) is designed to be moved into the open position when a second fluid pressure different from the first is exceeded. Nozzle according to claim 6, wherein a pre-tension of the closing body (17) of the first overflow valve (21a) is different from a pre-tension of the closing body (17) of the second overflow valve (21b). Nozzle according to claim 1, wherein the partial channel (10) and the at least one bridging channel (20a - 20e) are distributed in the circumferential direction preferably uniformly around the valve stem (15). Nozzle according to one of claims 1 to 8, in which the partial channel (10) and the vacuum line (9) opening into the partial channel (10) form a Venturi nozzle. A dispensing valve according to any one of claims 1 to 9, further comprising an automatic shut-off device (30) for actuating the main valve (5), the vacuum line (9) being connected to the automatic shut-off device (30). Nozzle according to one of claims 1 to 10, with the following additional features: - the nozzle has a first adjustable maximum volume flow and a second maximum volume flow different from the first, the second maximum volume flow being greater than the first, - the nozzle valve has an adjustable flow limiter which is designed separately from the main valve and is designed to limit the fluid flow optionally to the first or second maximum volume flow, - the nozzle has an actuating device which is designed to interact with a signal element assigned to the tank of a motor vehicle and to optionally adjust the flow limiter to the first or second maximum volume flow. Method for dispensing a fluid by means of a dispensing valve according to one of claims 1 to 11, in which a first portion of the fluid flow is passed through the partial channel (10) and the remaining portion of the fluid flow is passed through the at least one bridging channel (20a - 20e), the portion of the fluid flow passed through the partial channel (10) being used to generate a vacuum. Method according to claim 12, wherein the at least one bridging channel (20a - 20e) has an overflow valve (21a, 21b, 21c, 21d, 21e), wherein the overflow valve (21a, 21b, 21c, 21d, 21e) is used to adjust the portion of the fluid flow flowing through the partial channel (10).

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