EP2386520B1 - Fuel valve - Google Patents
Fuel valve Download PDFInfo
- Publication number
- EP2386520B1 EP2386520B1 EP10005085A EP10005085A EP2386520B1 EP 2386520 B1 EP2386520 B1 EP 2386520B1 EP 10005085 A EP10005085 A EP 10005085A EP 10005085 A EP10005085 A EP 10005085A EP 2386520 B1 EP2386520 B1 EP 2386520B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- main valve
- valve
- closed position
- fuel pump
- inlet
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 239000000446 fuel Substances 0.000 title claims description 54
- 230000009471 action Effects 0.000 claims description 21
- 238000007789 sealing Methods 0.000 claims description 19
- 239000007788 liquid Substances 0.000 claims description 18
- 125000006850 spacer group Chemical group 0.000 claims description 7
- 239000012528 membrane Substances 0.000 description 17
- 238000000034 method Methods 0.000 description 7
- 230000008569 process Effects 0.000 description 7
- 238000011144 upstream manufacturing Methods 0.000 description 4
- 239000012530 fluid Substances 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 230000000977 initiatory effect Effects 0.000 description 1
- 230000010534 mechanism of action Effects 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000001960 triggered effect Effects 0.000 description 1
Images
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B67—OPENING, CLOSING OR CLEANING BOTTLES, JARS OR SIMILAR CONTAINERS; LIQUID HANDLING
- B67D—DISPENSING, DELIVERING OR TRANSFERRING LIQUIDS, NOT OTHERWISE PROVIDED FOR
- B67D7/00—Apparatus or devices for transferring liquids from bulk storage containers or reservoirs into vehicles or into portable containers, e.g. for retail sale purposes
- B67D7/06—Details or accessories
- B67D7/42—Filling nozzles
- B67D7/44—Filling nozzles automatically closing
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B67—OPENING, CLOSING OR CLEANING BOTTLES, JARS OR SIMILAR CONTAINERS; LIQUID HANDLING
- B67D—DISPENSING, DELIVERING OR TRANSFERRING LIQUIDS, NOT OTHERWISE PROVIDED FOR
- B67D7/00—Apparatus or devices for transferring liquids from bulk storage containers or reservoirs into vehicles or into portable containers, e.g. for retail sale purposes
- B67D7/06—Details or accessories
- B67D7/42—Filling nozzles
- B67D7/44—Filling nozzles automatically closing
- B67D7/46—Filling nozzles automatically closing when liquid in container to be filled reaches a predetermined level
- B67D7/48—Filling nozzles automatically closing when liquid in container to be filled reaches a predetermined level by making use of air suction through an opening closed by the rising liquid
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B67—OPENING, CLOSING OR CLEANING BOTTLES, JARS OR SIMILAR CONTAINERS; LIQUID HANDLING
- B67D—DISPENSING, DELIVERING OR TRANSFERRING LIQUIDS, NOT OTHERWISE PROVIDED FOR
- B67D7/00—Apparatus or devices for transferring liquids from bulk storage containers or reservoirs into vehicles or into portable containers, e.g. for retail sale purposes
- B67D7/06—Details or accessories
- B67D7/42—Filling nozzles
- B67D7/44—Filling nozzles automatically closing
- B67D7/52—Filling nozzles automatically closing and provided with additional flow-controlling valve means
Definitions
- the invention relates to a nozzle, comprising an inlet, an outlet pipe, a main valve for controlling the flow of liquid between the inlet and outlet pipe, a lever for operating the main valve, a first automatic safety shutdown, which moves the main valve in the closed position when the liquid level in a filling vessel reaches a arranged in the region of the outlet pipe level sensor, a second automatic safety shutdown, which moves the main valve in the closed position, when the liquid pressure at the inlet is below a minimum value, and means for biasing the main valve in the closed position, a variable opening cross section of the main valve depending on the fluid pressure at the inlet causes.
- Such a nozzle is for example off US 4,331,187 known.
- Dispensing valves also called nozzles, at petrol stations are usually designed as so-called automatic dispensing valves. They have an automatic shut-off, which prevents overflowing of the filled tank. This automatic safety shutdown usually acts on the main valve of the dispensing valve.
- dispensers offer the user a preselection of the amount of fuel to be refueled. For example, if payment in the form of an advance payment is made directly at the pump by coins, bills or credit cards, the advance payment amount made may determine the amount of fuel to be dispensed. Other dispensers allow, regardless of the type of payment, the preselection of a certain amount of fuel or an amount to be paid by pressing a button.
- the problem in this context is that in the described minimum delivery operation shortly before reaching a preselected amount of fuel also only a small pressure at the inlet of the dispensing valve occurs.
- the pressure drop at the inlet of the dispensing valve may be delayed or even increase again when, for example, fuel extracted from a cold earth tank heats up in a sunlit black fuel hose between the dispenser and the dispensing valve.
- the present invention has for its object to provide a nozzle of the type mentioned, which allows a structurally simple and inexpensive way, on the one hand safe operation even at low flow and on the other side, the main valve after a complete shutdown of the fuel pump securely closes ,
- the invention solves this problem with a nozzle mentioned above in that the main valve under the action of the device for biasing the main valve in the closed position in full hose operation such tilted is pressed into the closed position, that its tightness is reduced.
- a dispensing valve is a device for manually controlling fuel flow during a refueling operation.
- the inlet is that portion of the dispensing valve through which fuel is supplied from the dispenser.
- the main valve is the device that controls the fuel flow.
- the term main valve does not imply that there must be a second valve, secondary valve or the like.
- the shift lever is the device by which the user controls the main valve.
- the outlet tube is the device through which the fuel flow is directed into the container to be filled.
- the first automatic safety shut-off moves the main valve to the closed position when a level sensor located in the area of the discharge pipe is activated.
- a level sensor located in the area of the discharge pipe may be activated.
- it may be a flow and / or pressure sensor described in more detail below, as known in the prior art.
- the second automatic safety shut-off also moves the main valve to the closed position when the liquid pressure at the inlet of the dispensing valve falls below a minimum or threshold value.
- the device for biasing the main valve in the closed position is applied to the main valve permanently with a force acting in the closed position force or bias.
- the purpose of this device is in particular, in the so-called full hose operation, in which the fuel pump of the pump no longer promotes and the connecting hose between the dispenser and dispensing valve is fully liquid, to prevent emptying of the hose through the dispensing valve.
- the requirements for such a device are defined in DIN EN1302: 2001, section 6.B.6 (discontinuation test).
- This device may in particular be a so-called full tube spring, which permanently exerts a force in the direction of the closed position.
- the force must be such that on the one hand, the said leak test is passed, on the other hand, it may only be so large that the slightest at minimum promotion still provided pressure already sufficient for partial opening of the main valve against the force of this full hose spring.
- Another purpose of said device is to make the opening cross section of the main valve variable depending on delivery pressure and flow rate, so that via the main valve, a pressure drop takes place, which allows a pressure control of said second automatic safety shutdown.
- Pressing tilted into the closed position means that the axial guidance of the valve encloses an angle with the valve Axial direction of the valve seat, so that the valve over the circumference of the valve seat terminates differently tight.
- the canting can also take place in that the force acting in the closing direction does not act symmetrically on the valve in full hose operation in the axial direction and thus presses it into the closed position in a tilted manner.
- This tilting is carried out according to the invention only under the action of the device for biasing the main valve in the closed position in full hose operation.
- Full hose operation means that no fluid delivery takes place, but that the main valve has not been closed again by the user either by one of the described first or second automatic safety shutdowns.
- Said device which generally comprises a full hose spring, then prevents leakage of the pump connecting the dispenser and the nozzle through the nozzle.
- the tightness of the main valve in full hose operation is reduced. Reduced means that it is less than a symmetrical, non-tilted preload in the closed position by a device acting on the same force (full tube spring).
- the tightness is preferably reduced to a level that provides a sufficient effect as leakage protection in full hose operation.
- the core of the invention is targeted by the constructive action described to reduce the tightness of the main valve in full hose operation, on the one hand, the required leakage protection is still guaranteed and on the other hand in full hose operation by this leak pressure at the inlet drops so far that the switching threshold of the second automatic safety shutdown, So the minimum pressure at the inlet, below which this second automatic safety shutdown moves the main valve in the closed position, safely falls below.
- the reduced tightness thus ensures that after switching off the fuel pump possibly still existing pressure surplus or, for example, by thermal expansion of cold fuel in a warm hose building pressure is reduced to ensure below the minimum pressure of the second automatic safety shutdown.
- a suitable device such as a closing spring usually exerts a significantly higher force on the main valve in the direction of the closed position than the described full hose spring , Furthermore, this stronger closing force acts so that the described canting, as it is in full hose operation, not or possibly present to such an extent that the complete tightness of the main valve under the required operating conditions, including after restarting the feed pump and the construction of a corresponding pressure at the inlet of the dispensing valve is guaranteed.
- the full hose spring act on the main valve from the inlet side
- the separate closing spring acts from a direction downstream of the main valve, as described in more detail in the exemplary embodiment.
- the main valve is inventively preferably designed as a cone valve.
- the poppet may include a guide configured to urge the main valve against the valve seat under asymmetric force distribution under the action of the main valve biasing means in the full-hose closed position.
- the valve cone guide form an angle with the axial axis of symmetry of the valve seat, so that the valve cone is pressed asymmetrically, that is, obliquely into the valve seat under the effect of the device designed in particular as a full hose spring. Over the circumference of the valve seat then differ the sealing pressures of the valve.
- the sealing pressure of the main valve in full hose operation is between 0.1 and 0.15 bar.
- the sealing pressure In the area of application of DIN EN13012: 2001, the sealing pressure must be at least 0.1 bar, as in the leakage test according to section 6.B.6 of this standard the tightness is tested under a one-meter liquid column. On the other hand, however, the sealing pressure should be low enough that it maintains a technically safe distance from switching threshold of the second automatic safety shutdown.
- the term sealing pressure refers to that liquid pressure at the inlet of the dispensing valve, in which the main valve in full-hose operation can pass no or at most slight amounts of liquid; Minor fluid quantities in this context are defined in DIN EN13012: 2001, section 6.B.6.
- the minimum delivery rate of the pump and thus the flow rate of the dispensing valve in this minimum conveying operation can be, for example 21 / min.
- a pressure of 0.27 bar may be present at the inlet.
- the second automatic safety shutdown must not yet trigger. If the fuel pump stops completely after reaching the preselected flow rate, the main valve closes under the action of the pre-breather spring. Due to the design according to the invention, the tightness of the main valve is now reduced so much that any existing (or emerging for example by sunlight on the hose) pressure surplus at the inlet escapes through a leakage at the main valve until the sealing pressure in full hose operation (for example, 0.1 bar) is reached.
- the switching threshold of the second automatic safety shutdown is preferably placed approximately in the middle between the operating pressure at minimum flow rate and the sealing pressure of the main valve in full hose operation.
- the switching threshold can be set, for example, to 0.17 bar. It then has a clear distance to the operating pressure at minimum flow on the one hand and the sealing pressure on the other. This prevents that at low fluctuations in the operating pressure in the minimum delivery mode, the second automatic safety shutdown already tripped unintentionally or that stops after stopping the fuel pump in the pump just this triggering.
- the switching threshold of the second automatic safety shutdown can thus according to the invention, for example, at least 0.05 bar, preferably at least 0.1 bar above the sealing pressure of the main valve in full hose operation.
- the main valve has a valve stem guide, which canted under the action of the device for biasing the main valve in the closed position in full hose operation and the valve stem of the main valve at an angle to the axis of symmetry of the main valve seat.
- the valve stem is deliberately misaligned in this way.
- the valve stem guide can be a component held in the flow channel of the inlet, which component guides the valve stem by means of a preferably cylindrical sleeve and has holding regions extending radially outwards, in particular holding arms which hold the valve stem guide in the radially outer region of the inlet. These holding regions extending radially outwards are preferably designed for axial support or abutment against an abutment.
- the full-tube spring exerts a force acting in the closing direction on the main valve, it generally rests on an upstream end piece of the valve stem on the one hand and on an axial end face of the valve stem guide on the other hand. It presses in this way the valve stem guide in the axial direction downstream against the abutment in the inlet.
- the valve stem guide can be tilted by pressing against the abutment. This means that the valve stem guide sleeve forms an angle with the axis of symmetry of the main valve or valve seat.
- the tilting can be effected according to the invention, for example, by the holding areas of the valve stem guide in the area of the contact surfaces Having the abutment in portions of the circumference in the axial direction facing spacers. These spacers only on a part of the circumference of the valve stem guide tilt the valve stem guide and thus also the valve stem leading shaft guide sleeve against the axis of symmetry and thus cause the Vollschlauchfeder tilted the main valve in the valve seat and thus reduces the sealing pressure.
- the invention further relates to a valve stem guide for a nozzle according to the invention. It has a shaft guide sleeve for guiding a valve stem and extending from the shaft guide sleeve radially outwardly extending holding areas, preferably retaining arms. These holding areas are designed for axial contact with an abutment in the inlet of a dispensing valve. According to the invention it is provided that the shaft guide sleeve assumes an angular position during pressing of the holding portions of a rotationally symmetrical abutment, in which its axis of symmetry deviates from the axis of symmetry of the rotationally symmetrical abutment. This can for example be done by the previously described only in some areas of the circumference in the axial direction facing spacers.
- An inventive bleed valve (colloquially also called fuel nozzle) has a valve housing 1, a connected to a hose, not shown, inlet 2 for liquid, an outlet pipe 3 and a shift lever 4. Inside the valve housing 1, the main valve is arranged.
- This main valve has a conical valve seat 5 and a poppet 6.
- the valve cone 6 is divided into two partial bodies 6a and 6b.
- the upstream upstream in the flow direction of the main valve body 6a is fixedly connected to the valve stem 7.
- the second part body 6b is arranged axially displaceably on the valve stem 7, the two part bodies 6a and 6b are pressed apart by a spring 8 so that an axial gap indicated at 9 can form therebetween.
- valve stem 7 is guided by a valve stem guide, which has a shaft guide sleeve 10 and from this shaft guide sleeve 10 radially outwardly extending holding portions 11. These holding regions 11 are indicated at 12 axially on an abutment formed in the valve housing 1.
- a full tube spring 13 is designed as a compression spring and is located on the upstream axial end of the valve stem guide sleeve 10 on the one hand and on a head or tail 14 of the valve stem 7 on the other. It endeavors to pull the main valve into the closed position, in which the partial body 6a sealingly comes into contact with the valve plug seat 5.
- the main valve will be at the in Fig. 1 and 2 shown closed position additionally pressed by a downstream closing spring 15 in the closed position, as described below.
- the closing spring 15 presses a hollow outer bulb 16 against the downstream end face of the main valve, namely the second part of the body 6b.
- the closing force of the closing spring 15 is thus applied via the outer piston 16 to the second part body 6b. It is so large that the two partial bodies 6a and 6b of the valve cone are compressed against the action of the spring 8 and the valve is completely sealed at any operating pressure on the inlet side.
- the closing force of this closing spring 15 is thus significantly greater than that exerted by the full hose spring 13 in the closing direction on the main valve force.
- the closing spring 15 and the outer piston 16 used for force transmission press the main valve from the downstream side completely symmetrical (thus not skewed or tilted) in the associated valve seat. 5
- an inner piston 17 is arranged axially displaceable.
- the inner piston 17 is of a return spring 18 biased toward the closed position.
- the inner piston 17 can be moved downstream by actuating the shift lever 4 in the axial direction.
- the shift lever pin 31 connected to the shift lever 4 which engages in a radially extending bore or groove 19 of the inner piston 17, pushes this inner piston 17 downstream against the bias of the return spring 18 in the axial direction.
- the inner piston 17 is arranged axially displaceably in the outer piston 16, however, inner piston 17 and outer piston 16 can be kinematically connected to one another by means of a locking device to be described so that the downstream movement of the inner piston 17 also moves the outer piston 16 coupled thereto downstream and Thus, the closing force of the closing spring 15 takes from the body part 6b of the main valve.
- This connection or locking of outer bulb 16 and inner bulb 17 by locking elements designated as membrane rolls 20 is basically known in the prior art and described, for example, in US Pat US 4,331,187 or DE 10 2008 010 998 B3 , In the in the FIGS.
- the membrane rollers 20 are arranged in such aligned recesses of the outer piston 16 and inner piston 17 that outer piston 16 and inner piston 17 are locked together and by an operation of the shift lever 4 inner piston 17 and outer piston 16 together against the force of the closing spring 15 and return spring 18th be moved axially downstream. If the shift lever 4 is only slightly actuated and accordingly only a small axial displacement of the two pistons takes place, first the second part body 6b of the main valve is relieved and the spring 8 can the first part body 6a and the second Partial body 6b drive apart in the axial direction, so that the gap 9 forms. The tightness of the main valve is now reduced and at pending inlet 2 pump pressure, the flow of small amounts of fuel to the outlet pipe 3 is possible.
- the fueling process can be terminated by the shift lever 4 released by the user or any latching of the shift lever 4 is released. Closing spring 15 and return spring 18 then push inner piston 17 and outer piston 16 back into the closed position and close the main valve.
- Both the first and second automatic safety shutdown are based on the principle of extracting the membrane rollers 20 from the grooves or recesses of the inner piston 17 and outer piston 16 and in this way to release their interlock.
- the outer bulb 16 can then snap under the action of the closing spring 15 back into the closed position and pressurize the main valve again from the downstream with the described large closing force.
- the inner piston 17 is due to the still pulled lever 4 initially in the axially downstream shifted position.
- the recesses for the membrane rollers 20 in the inner piston 17 on the one hand and outer bulb 16 on the other hand are no longer aligned with each other.
- the membrane rolls 20 may be raised by means of a holder 22 (refer to the illustration of FIGS Fig. 2 ) are pulled out of the recesses in the inner piston 17 and cancel in this way the locking between the inner piston 17 and outer piston 16.
- This extraction of the holder 22 and thus the membrane rollers 20 can happen on the one hand under the action of pressure changes on both sides of a membrane 23 (first automatic safety shutdown) and on the other in that the piston 25 under the action of the spring 24 from the in Fig. 2 shown position moves upward while under the action of the telescopic coupling 26 also pulls the holding device 22 upwards and by pulling out the membrane rollers 20, the lock between inner piston 17 and outer piston 16 triggers.
- the first automatic safety shutdown operates in a conventional manner by means of the membrane 23.
- the space above the diaphragm 23 communicates with a conventional sensor line, which at the outlet tip of the outlet pipe empties. Achieved in the course of a refueling the liquid level the outlet pipe and thus the end of this sensor line, the pressure conditions change on both sides of the membrane 23 such that the pressure above the membrane is reduced and thus the holder 22 upwards and the membrane rollers 20 thus out of its locked position pulls out.
- the locking of inner piston 17 and outer piston 16 is released, the closing spring 15 can push the outer piston 16 in the closed position, close the main valve and thus terminate the refueling process.
- a fuel tank is to be completely filled.
- the fueling process is carried out here in a conventional manner with full pump pressure of the pump until the described first automatic safety shutdown after rising of the liquid level to the end of the outlet pipe 3 pulls the membrane 23 upwards, the membrane rolls 20 lifts out and thus snapping back the outer bulb 16 in the Closed position causes and the main valve closes.
- the nozzle can now be hung back to the pump and is ready for a new refueling process.
- the closing spring 15 presses the main valve with high force in the closed position, so that complete tightness is ensured at any pressure occurring at the inlet 2 during operation.
- the user selects a certain amount of fuel (or a certain amount to be paid) that is insufficient to completely fill the tank.
- the fueling process is started as described above. Shortly before reaching the preselected fuel quantity, the delivery rate of the fuel pump in the fuel pump is significantly reduced in order to be able to precisely control the preselected fuel quantity. For example, the delivery rate can be reduced shortly before reaching the preselected amount of fuel to about 2 1 / min.
- the delivery rate is in the embodiment before the main valve and thus also in the pressure port channel 21 and in the space 27 above the piston 25, a pressure of 0.27 bar. This pressure is sufficient to the piston 25 in the in Fig. 2 leave shown lower position and thus maintain the lock between the inner piston 17 and outer piston 16. With this low delivery rate, the main valve or its first partial body 6 is already pulled under the action of the full tube spring 16 in the direction of the closed position such that only a small opening gap remains.
- the fuel pump After reaching the preselected amount of fuel, the fuel pump switches off completely and there is the so-called full hose operation.
- the invention provides that the full hose spring 13, the main valve in full hose operation tilted presses in the closed position and reduces its tightness.
- a holding portion or holding arm 11 of the valve stem guide has a pointing in the axial direction of the spacer body 28.
- This spacer comes at 12 ( Fig. 2 ) on the abutment of the valve housing 1 to the system and thereby causes the valve stem guide is not aligned under the action of the compression spring designed as a full hose spring 13 with the symmetry axis of the valve seat 5, but obliquely or canted sits in the inlet.
- This reduced sealing pressure causes after switching off the fuel pump on reaching the preselected amount of fuel, the first still existing pressure of 0.27 bar at the inlet (in principle, for example, by sunlight on a black fuel hose can still increase) within a short time and reliably to about Degrades 0.1 bar.
- the switching threshold of the second automatic safety shutdown of 0.17 bar is safely undercut. When falling below this switching threshold, that is, a drop in the pressure in the pressure port channel 21 and space 27 above the piston 25, the force of the spring 24 exceeds the force exerted on the piston 25 from above from the space 27 compressive force, the second automatic safety shutdown triggers now, the piston 25 moves upwards and pulls the membrane rollers 20 out of their locking position.
- the invention ensures that the full hose operation does not last indefinitely, but that reliably triggers the second automatic safety shutdown and thus brings the main valve back into the fully loaded with the closing force of the closing spring 15 position. If the closing spring 15 acts from downstream on the main valve, this is the force of the full hose spring 13 far exceeding force application completely symmetrical, so that no more tilting or misalignment occurs, which could reduce the tightness.
- FIGS. 3 to 5 show for better understanding once again different operating states of the inventive dispensing valve.
- Fig. 3 the closed position is shown, in which the force of the closing spring 15 acts on the outer valve 16 from downstream to the main valve.
- the two partial bodies 6a and 6b are against the action of the spring 8 compressed, the application of force to the main valve in the closed position is symmetrical.
- Fig. 4 a position is shown in which the main valve is slightly open and is biased by the full hose spring 13 in the closed position.
- a pressure of 0.27 bar at the inlet a low flow takes place.
- Fig. 5 shows the full hose operation, in which the main valve is merely urged by the full hose spring 13 in the closed position. Due to the tilted guidance of the valve stem 7 by the valve stem guide 10, 11, the sealing pressure in the region 30 is reduced in the manner described to about 0.1 bar.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Loading And Unloading Of Fuel Tanks Or Ships (AREA)
- Fuel-Injection Apparatus (AREA)
- Mechanically-Actuated Valves (AREA)
Description
Die Erfindung betrifft ein Zapfventil, mit einem Einlass, einem Auslaufrohr, einem Hauptventil zur Steuerung des Flüssigkeitsstroms zwischen Einlass und Auslaufrohr, einem Schalthebel zur Betätigung des Hauptventils, einer ersten automatischen Sicherheitsabschaltung, die das Hauptventil in die Schließstellung bewegt, wenn der Flüssigkeitsspiegel in einem zu befüllenden Behälter einen im Bereich des Auslaufrohrs angeordneten Füllstandssensor erreicht, einer zweiten automatischen Sicherheitsabschaltung, die das Hauptventil in die Schließstellung bewegt, wenn der Flüssigkeitsdruck am Einlass einen Mindestwert unterschreitet, und eine Einrichtung zur Vorspannung des Hauptventils in die Schließstellung, die einen veränderlichen Öffnungsquerschnitt des Hauptventils abhängig von dem Flüssigkeitsdruck am Einlass bewirkt.The invention relates to a nozzle, comprising an inlet, an outlet pipe, a main valve for controlling the flow of liquid between the inlet and outlet pipe, a lever for operating the main valve, a first automatic safety shutdown, which moves the main valve in the closed position when the liquid level in a filling vessel reaches a arranged in the region of the outlet pipe level sensor, a second automatic safety shutdown, which moves the main valve in the closed position, when the liquid pressure at the inlet is below a minimum value, and means for biasing the main valve in the closed position, a variable opening cross section of the main valve depending on the fluid pressure at the inlet causes.
Ein solches Zapfventil ist beispielsweise aus
Zapfventile, auch Zapfpistolen genannt, an Tankstellen sind in der Regel als sogenannte automatische Zapfventile ausgebildet. Sie besitzen eine automatische Abschaltung, die ein Überlaufen des befüllten Tanks verhindert. Diese automatische Sicherheitsabschaltung wirkt in der Regel auf das Hauptventil des Zapfventils.Dispensing valves, also called nozzles, at petrol stations are usually designed as so-called automatic dispensing valves. They have an automatic shut-off, which prevents overflowing of the filled tank. This automatic safety shutdown usually acts on the main valve of the dispensing valve.
Viele Zapfsäulen bieten dem Benutzer eine Vorwahl der zu tankenden Kraftstoffmenge an. Wenn beispielsweise die Bezahlung in Form einer Vorauszahlung unmittelbar an der Zapfsäule durch Münzen, Geldscheine oder Kreditkarten erfolgt, kann der geleistete Vorauszahlungsbetrag die abzugebende Kraftstoffmenge bestimmen. Andere Zapfsäulen erlauben unabhängig von der Art der Bezahlung die Vorwahl einer bestimmten Kraftstoffmenge oder eines zu bezahlenden Betrags per Tastendruck.Many dispensers offer the user a preselection of the amount of fuel to be refueled. For example, if payment in the form of an advance payment is made directly at the pump by coins, bills or credit cards, the advance payment amount made may determine the amount of fuel to be dispensed. Other dispensers allow, regardless of the type of payment, the preselection of a certain amount of fuel or an amount to be paid by pressing a button.
Bei der Vorwahl einer bestimmten Füllmenge wird in aller Regel das Ende des Tankvorgangs nicht ausgelöst durch das Auslösen der beschriebenen Sicherheitsabschaltung bei vollem Tank, sondern durch das Erreichen der vorgewählten Kraftstoffmenge. Die Steuerung dieser Kraftstoffmenge erfolgt in der Regel durch eine entsprechende Ansteuerung der Kraftstoffpumpe in der Zapfsäule. Kurz vor dem Erreichen der gewünschten Füllmenge wird die Förderleistung der Pumpe verringert, bei Erreichen der vorgewählten Füllmenge wird dann die Pumpe vollständig abgeschaltet.In the preselection of a certain capacity is usually the end of the refueling process not triggered by the triggering of the described safety shutdown at full tank, but by reaching the preselected amount of fuel. The control of this amount of fuel is usually carried out by a corresponding control of the fuel pump in the pump. Shortly before reaching the desired filling capacity of the pump is reduced, on reaching the preselected capacity, the pump is then completely switched off.
Da in diesem Fall die automatische Sicherheitsabschaltung des Zapfventils nicht auslöst, kann grundsätzlich das Zapfventil in seiner noch geöffneten Stellung zurück in die Zapfsäule gehängt werden, was bei nachfolgenden Tankvorgängen zu einem unkontrollierten Ausfluss von Kraftstoff führen kann.Since in this case the automatic safety shutdown of the dispensing valve does not trigger, basically the dispensing valve can be hung in its open position back into the dispenser, which can lead to an uncontrolled outflow of fuel in subsequent refueling operations.
Es ist daher bereits vorgeschlagen worden (
Problematisch ist in diesem Zusammenhang, dass in dem beschriebenen Minimalförderbetrieb kurz vor Erreichen einer vorgewählten Kraftstoffmenge ebenfalls nur ein geringer Druck am Einlass des Zapfventils auftritt. Auf der anderen Seite kann sich auch nach vollständigem Abschalten der Kraftstoffförderpumpe der Druckabfall am Einlass des Zapfventils verzögern oder sogar sich der Druck wieder vergrößern, wenn beispielsweise aus einem kalten Erdtank geförderter Kraftstoff sich in einem sonnenbeschienen schwarzen Kraftstoffschlauch zwischen Zapfsäule und Zapfventil erwärmt.The problem in this context is that in the described minimum delivery operation shortly before reaching a preselected amount of fuel also only a small pressure at the inlet of the dispensing valve occurs. On the other hand, even after complete shutdown of the fuel delivery pump, the pressure drop at the inlet of the dispensing valve may be delayed or even increase again when, for example, fuel extracted from a cold earth tank heats up in a sunlit black fuel hose between the dispenser and the dispensing valve.
Der vorliegenden Erfindung liegt die Aufgabe zugrunde, ein Zapfventil der eingangs genannten Art zu schaffen, das auf konstruktiv einfache und günstige Art und Weise einerseits einen sicheren Betrieb auch bei geringer Förderleistung erlaubt und auf der anderen Seite das Hauptventil nach einem vollständigen Abschalten der Kraftstoffförderpumpe sicher schließt.The present invention has for its object to provide a nozzle of the type mentioned, which allows a structurally simple and inexpensive way, on the one hand safe operation even at low flow and on the other side, the main valve after a complete shutdown of the fuel pump securely closes ,
Die Erfindung löst diese Aufgabe bei einem eingangs genannten Zapfventil dadurch, dass das Hauptventil unter der Wirkung der Einrichtung zur Vorspannung des Hauptventils in die Schließstellung im Vollschlauchbetrieb dergestalt verkantet in die Schließstellung gedrückt wird, dass dessen Dichtigkeit reduziert ist.The invention solves this problem with a nozzle mentioned above in that the main valve under the action of the device for biasing the main valve in the closed position in full hose operation such tilted is pressed into the closed position, that its tightness is reduced.
Zunächst seien einige im Rahmen der Erfindung verwendete Begriffe erläutert.First, some terms used in the invention are explained.
Die Anforderungen an die Bau- und Arbeitsweise von automatischen Zapfventilen für die Benutzung an Zapfsäulen sind in der DIN EN13012:2001 geregelt. Dort definierte Begriffe werden auch in der vorliegenden Anmeldung verwendet.The requirements for the construction and operation of automatic dispensing valves for use at dispensers are regulated in DIN EN13012: 2001. Terms defined there are also used in the present application.
Ein Zapfventil ist eine Vorrichtung zur manuellen Kontrolle des Treibstoffdurchflusses während eines Betankungsvorgangs. Der Einlass ist derjenige Bereich des Zapfventils, durch den Treibstoff von der Zapfsäule zugeführt wird. Das Hauptventil ist diejenige Vorrichtung, die den Treibstofffluss kontrolliert. Der Begriff Hauptventil impliziert nicht, dass es ein zweites Ventil, Nebenventil oder dergleichen geben muss. Der Schalthebel ist die Vorrichtung, durch die der Benutzer das Hauptventil steuert. Das Auslaufrohr ist die Vorrichtung, durch die der Treibstofffluss in den zu befüllenden Behälter geleitet wird.A dispensing valve is a device for manually controlling fuel flow during a refueling operation. The inlet is that portion of the dispensing valve through which fuel is supplied from the dispenser. The main valve is the device that controls the fuel flow. The term main valve does not imply that there must be a second valve, secondary valve or the like. The shift lever is the device by which the user controls the main valve. The outlet tube is the device through which the fuel flow is directed into the container to be filled.
Die erste automatische Sicherheitsabschaltung bewegt das Hauptventil in die Schließstellung, wenn ein im Bereich des Auslaufrohrs angeordneter Füllstandssensor aktiviert wird. Es kann sich insbesondere um einen unten noch näher beschriebenen Strömungs- und/oder Drucksensor handeln, wie er im Stand der Technik bekannt ist.The first automatic safety shut-off moves the main valve to the closed position when a level sensor located in the area of the discharge pipe is activated. In particular, it may be a flow and / or pressure sensor described in more detail below, as known in the prior art.
Die zweite automatische Sicherheitsabschaltung bewegt das Hauptventil ebenfalls in die Schließstellung, wenn der Flüssigkeitsdruck am Einlass des Zapfventils einen Mindest-oder Schwellwert unterschreitet.The second automatic safety shut-off also moves the main valve to the closed position when the liquid pressure at the inlet of the dispensing valve falls below a minimum or threshold value.
Die Einrichtung zur Vorspannung des Hauptventils in die Schließstellung beaufschlagt das Hauptventil permanent mit einer in die Schließstellung wirkenden Kraft oder Vorspannung. Zweck dieser Einrichtung ist es insbesondere, im sogenannten Vollschlauchbetrieb, bei dem die Kraftstoffpumpe der Zapfsäule nicht mehr fördert und der Verbindungsschlauch zwischen Zapfsäule und Zapfventil voll Flüssigkeit steht, ein Leerlaufen des Schlauches durch das Zapfventil zu verhindern. Die Anforderungen an eine solche Einrichtung sind festgelegt in DIN EN1302:2001, Ziffer 6.B.6 (Auslaufprüfung). Diese Einrichtung kann insbesondere eine sogenannte Vollschlauchfeder sein, die permanent eine Kraft in Richtung der Schließstellung ausübt. Die Kraft muss dergestalt bemessen sein, dass zum Einen die genannte Auslaufprüfung bestanden wird, zum Anderen darf sie nur so groß sein, dass der geringste bei Minimalförderung noch vorgesehene Druck bereits zum teilweisen Öffnen des Hauptventils gegen die Kraft dieser Vollschlauchfeder ausreicht. Ein weiterer Zweck der genannten Einrichtung ist es, den Öffnungsquerschnitt des Hauptventils abhängig von Förderdruck und Durchflussrate variabel zu gestalten, so dass über das Hauptventil ein Druckabfall stattfindet, der eine Drucksteuerung der genannten zweiten automatischen Sicherheitsabschaltung gestattet.The device for biasing the main valve in the closed position is applied to the main valve permanently with a force acting in the closed position force or bias. The purpose of this device is in particular, in the so-called full hose operation, in which the fuel pump of the pump no longer promotes and the connecting hose between the dispenser and dispensing valve is fully liquid, to prevent emptying of the hose through the dispensing valve. The requirements for such a device are defined in DIN EN1302: 2001, section 6.B.6 (discontinuation test). This device may in particular be a so-called full tube spring, which permanently exerts a force in the direction of the closed position. The force must be such that on the one hand, the said leak test is passed, on the other hand, it may only be so large that the slightest at minimum promotion still provided pressure already sufficient for partial opening of the main valve against the force of this full hose spring. Another purpose of said device is to make the opening cross section of the main valve variable depending on delivery pressure and flow rate, so that via the main valve, a pressure drop takes place, which allows a pressure control of said second automatic safety shutdown.
Erfindungsgemäß ist nun vorgesehen, dass das Hauptventil unter der Wirkung der Einrichtung zur Vorspannung des Hauptventils in die Schließstellung im Vollschlauchbetrieb dergestalt verkanntet in die Schließstellung gedrückt wird, dass dessen Dichtigkeit reduziert ist.According to the invention, it is now provided that the main valve under the action of the device for biasing the main valve in the closed position in the full hose operation is pressed so mislaid in the closed position that its tightness is reduced.
Verkantet in die Schließstellung drücken bedeutet, dass die Axialführung des Ventils einen Winkel einschließt mit der Axialrichtung des Ventilsitzes, so dass das Ventil über den Umfang des Ventilsitzes unterschiedlich dicht abschließt. Stattdessen oder zusätzlich kann auch die Verkantung dadurch erfolgen, dass die in Schließrichtung wirkende Kraft im Vollschlauchbetrieb in Axialrichtung nicht symmetrisch auf das Ventil wirkt und es damit verkantet in die Schließstellung drückt. Diese Verkantung erfolgt erfindungsgemäß nur unter der Wirkung der Einrichtung zur Vorspannung des Hauptventils in die Schließstellung im Vollschlauchbetrieb. Vollschlauchbetrieb bedeutet, dass keine Flüssigkeitsförderung stattfindet, dass aber das Hauptventil weder durch eine der beschriebenen ersten oder zweiten automatischen Sicherheitsabschaltungen noch manuell durch den Benutzer wieder geschlossen wurde. Die genannte Einrichtung, die in der Regel eine Vollschlauchfeder umfasst, verhindert dann ein Auslaufen des die Zapfsäule und das Zapfventil verbindenden Schlauches durch das Zapfventil.Pressing tilted into the closed position means that the axial guidance of the valve encloses an angle with the valve Axial direction of the valve seat, so that the valve over the circumference of the valve seat terminates differently tight. Instead or in addition, the canting can also take place in that the force acting in the closing direction does not act symmetrically on the valve in full hose operation in the axial direction and thus presses it into the closed position in a tilted manner. This tilting is carried out according to the invention only under the action of the device for biasing the main valve in the closed position in full hose operation. Full hose operation means that no fluid delivery takes place, but that the main valve has not been closed again by the user either by one of the described first or second automatic safety shutdowns. Said device, which generally comprises a full hose spring, then prevents leakage of the pump connecting the dispenser and the nozzle through the nozzle.
Die Dichtigkeit des Hauptventils im Vollschlauchbetrieb ist reduziert. Reduziert bedeutet, dass sie geringer ist als bei einer symmetrischen, nicht verkanteten Vorspannung in die Schließstellung durch eine mit gleicher Kraft wirkende Einrichtung (Vollschlauchfeder). Die Dichtigkeit ist bevorzugt auf ein Niveau reduziert, dass eine noch hinreichende Wirkung als Auslaufschutz im Vollschlauchbetrieb bietet.The tightness of the main valve in full hose operation is reduced. Reduced means that it is less than a symmetrical, non-tilted preload in the closed position by a device acting on the same force (full tube spring). The tightness is preferably reduced to a level that provides a sufficient effect as leakage protection in full hose operation.
Kern der Erfindung ist es, durch die beschriebene konstruktive Maßnahme die Dichtigkeit des Hauptventils im Vollschlauchbetrieb gezielt soweit zu verringern, dass einerseits der erforderliche Auslaufschutz noch gewährleistet ist und andererseits im Vollschlauchbetrieb durch diese Undichtigkeit der Druck am Einlass soweit absinkt, dass die Schaltschwelle der zweiten automatischen Sicherheitsabschaltung, also derjenige Mindestdruck am Einlass, bei dessen Unterschreiten diese zweite automatische Sicherheitsabschaltung das Hauptventil in die Schließstellung bewegt, sicher unterschreitet. Die reduzierte Dichtigkeit sorgt somit dafür, dass ein nach Abschalten der Kraftstoffförderpumpe möglicherweise noch vorhandener Drucküberschuss oder ein sich beispielsweise durch thermische Ausdehnung von kaltem Kraftstoff in einem warmen Schlauch aufbauender Druck abgebaut wird, um ein Unterschreiten des Mindestdruckes der zweiten automatischen Sicherheitsabschaltung zu gewährleisten.The core of the invention is targeted by the constructive action described to reduce the tightness of the main valve in full hose operation, on the one hand, the required leakage protection is still guaranteed and on the other hand in full hose operation by this leak pressure at the inlet drops so far that the switching threshold of the second automatic safety shutdown, So the minimum pressure at the inlet, below which this second automatic safety shutdown moves the main valve in the closed position, safely falls below. The reduced tightness thus ensures that after switching off the fuel pump possibly still existing pressure surplus or, for example, by thermal expansion of cold fuel in a warm hose building pressure is reduced to ensure below the minimum pressure of the second automatic safety shutdown.
Wenn das Hauptventil durch Auslösen der ersten oder zweiten automatischen Sicherheitsabschaltung oder manuell durch Betätigen des Schalthebels in die Schließstellung bewegt wird, übt eine geeignete Einrichtung wie beispielsweise eine Schließfeder in aller Regel eine erheblich höhere Kraft auf das Hauptventil in Richtung der Schließstellung aus als die beschriebene Vollschlauchfeder. Des weiteren wirkt diese stärkere Schließkraft so, dass die beschriebene Verkantung, wie sie im Vollschlauchbetrieb vorliegt, nicht oder allenfalls in einem solchen Maße vorliegt, dass die vollständige Dichtigkeit des Hauptventils unter den erforderlichen Betriebsbedingungen, also auch nach einem Wiederanlaufen der Förderpumpe und dem Aufbau eines entsprechenden Druckes am Einlass des Zapfventils, gewährleistet ist. Beispielsweise kann im Rahmen der Erfindung die Vollschlauchfeder von der Einlassseite her auf das Hauptventil wirken und die separate Schließfeder von einer Richtung stromab des Hauptventils, wie im Ausführungsbeispiel näher beschrieben.When the main valve is moved to the closed position by triggering the first or second automatic safety shutdown or manually by operating the shift lever, a suitable device such as a closing spring usually exerts a significantly higher force on the main valve in the direction of the closed position than the described full hose spring , Furthermore, this stronger closing force acts so that the described canting, as it is in full hose operation, not or possibly present to such an extent that the complete tightness of the main valve under the required operating conditions, including after restarting the feed pump and the construction of a corresponding pressure at the inlet of the dispensing valve is guaranteed. For example, in the context of the invention, the full hose spring act on the main valve from the inlet side, and the separate closing spring acts from a direction downstream of the main valve, as described in more detail in the exemplary embodiment.
Das Hauptventil ist erfindungsgemäß bevorzugt als Kegelventil ausgebildet. Der Ventilkegel kann eine Führung aufweisen, die dergestalt ausgebildet ist, dass das Hauptventil unter der Wirkung der Einrichtung zur Vorspannung des Hauptventils in die Schließstellung im Vollschlauchbetrieb mit asymmetrischer Kraftverteilung gegen den Ventilsitz gedrückt wird. Beispielsweise kann die Ventilkegelführung einen Winkel mit der axialen Symmetrieachse des Ventilsitzes einschließen, so dass der Ventilkegel unter der Wirkung der insbesondere als Vollschlauchfeder ausgebildeten Einrichtung asymmetrisch, also schief in den Ventilsitz gedrückt wird. Über den Umfang des Ventilsitzes unterscheiden sich dann die Dichtdrücke des Ventils.The main valve is inventively preferably designed as a cone valve. The poppet may include a guide configured to urge the main valve against the valve seat under asymmetric force distribution under the action of the main valve biasing means in the full-hose closed position. For example, the valve cone guide form an angle with the axial axis of symmetry of the valve seat, so that the valve cone is pressed asymmetrically, that is, obliquely into the valve seat under the effect of the device designed in particular as a full hose spring. Over the circumference of the valve seat then differ the sealing pressures of the valve.
Erfindungsgemäß ist es bevorzugt, dass der Dichtdruck des Hauptventils im Vollschlauchbetrieb zwischen 0,1 und 0,15 bar beträgt. Im Geltungsbereich der DIN EN13012:2001 muss der Dichtdruck mindestens 0,1 bar betragen, da bei der Auslaufprüfung gemäß Ziffer 6.B.6 dieser Norm die Dichtigkeit unter einer Flüssigkeitssäule von einem Meter geprüft wird. Andererseits soll der Dichtdruck jedoch niedrig genug sein, dass er einen betriebstechnisch sicheren Abstand von Schaltschwelle der zweiten automatischen Sicherheitsabschaltung einhält. Der Begriff Dichtdruck bezeichnet denjenigen Flüssigkeitsdruck am Einlass des Zapfventils, bei dem das Hauptventil im Vollschlauchbetrieb keine oder allenfalls geringfügige Flüssigkeitsmengen durchtreten lässt; geringfügige Flüssigkeitsmengen in diesem Kontext sind definiert in der DIN EN13012:2001, Ziffer 6.B.6.According to the invention, it is preferred that the sealing pressure of the main valve in full hose operation is between 0.1 and 0.15 bar. In the area of application of DIN EN13012: 2001, the sealing pressure must be at least 0.1 bar, as in the leakage test according to section 6.B.6 of this standard the tightness is tested under a one-meter liquid column. On the other hand, however, the sealing pressure should be low enough that it maintains a technically safe distance from switching threshold of the second automatic safety shutdown. The term sealing pressure refers to that liquid pressure at the inlet of the dispensing valve, in which the main valve in full-hose operation can pass no or at most slight amounts of liquid; Minor fluid quantities in this context are defined in DIN EN13012: 2001, section 6.B.6.
Wenn bei Vorwahl einer bestimmten Kraftstoffmenge im Zuge eines Betankungsvorgangs diese vorgewählte Kraftstoffmenge nahezu erreicht ist, wird, wie vorstehend beschrieben, die Förderleistung der Kraftstoffpumpe der Zapfsäule reduziert, damit die vorgewählte Betankungsmenge punktgenau angesteuert und die Kraftstoffpumpe dann abgeschaltet werden kann.If, when preselecting a certain amount of fuel in the course of a refueling operation, this preselected amount of fuel is almost reached, as described above, the Reduces the delivery capacity of the pump fuel pump so that the preselected refueling amount can be precisely controlled and the fuel pump can then be switched off.
Die minimale Förderleistung der Pumpe und damit Durchflussrate des Zapfventils bei diesem Minimalförderbetrieb kann beispielsweise 21/min betragen. Bei dieser Minimalförderleistung kann beispielsweise ein Druck von 0,27 bar am Einlass anliegen. Bei diesem Druck darf die zweite automatische Sicherheitsabschaltung noch nicht auslösen. Stoppt die Kraftstoffpumpe nach Erreichen der vorgewählten Fördermenge vollständig, schließt das Hauptventil unter der Wirkung der Vorschlauchfeder. Durch die erfindungsgemäße Gestaltung ist die Dichtigkeit des Hauptventils jetzt soweit reduziert, dass ein etwaig noch vorhandener (oder beispielsweise durch Sonneneinstrahlung auf den Schlauch entstehender) Drucküberschuss am Einlass durch eine Leckage am Hauptventil entweicht, bis der Dichtdruck im Vollschlauchbetrieb (beispielsweise 0,1 bar) erreicht ist. Die Schaltschwelle der zweiten automatischen Sicherheitsabschaltung wird bevorzugt etwa in die Mitte zwischen dem Betriebsdruck bei Minimalförderleistung und dem Dichtdruck des Hauptventils im Vollschlauchbetrieb gelegt. In dem genannten Beispiel (Druck am Einlass bei Minimalförderleistung 0,27 bar, Dichtdruck im Vollschlauchbetrieb 0,1 bar) kann die Schaltschwelle beispielsweise auf 0,17 bar gelegt werden. Sie hat dann einen deutlichen Abstand zum Betriebsdruck bei Minimalförderleistung einerseits und zum Dichtdruck andererseits. Dies verhindert, dass bei geringen Schwankungen des Betriebsdrucks im Minimalförderbetrieb die zweite automatische Sicherheitsabschaltung bereits ungewollt auslöst oder dass nach dem Stoppen der Kraftstoffförderpumpe in der Zapfsäule eben dieses Auslösen unterbleibt. Die Schaltschwelle der zweiten automatischen Sicherheitsabschaltung kann somit erfindungsgemäß beispielsweise mindestens 0,05 bar, vorzugsweise mindestens 0,1 bar über dem Dichtdruck des Hauptventils im Vollschlauchbetrieb liegen.The minimum delivery rate of the pump and thus the flow rate of the dispensing valve in this minimum conveying operation can be, for example 21 / min. For example, at this minimum delivery rate, a pressure of 0.27 bar may be present at the inlet. At this pressure, the second automatic safety shutdown must not yet trigger. If the fuel pump stops completely after reaching the preselected flow rate, the main valve closes under the action of the pre-breather spring. Due to the design according to the invention, the tightness of the main valve is now reduced so much that any existing (or emerging for example by sunlight on the hose) pressure surplus at the inlet escapes through a leakage at the main valve until the sealing pressure in full hose operation (for example, 0.1 bar) is reached. The switching threshold of the second automatic safety shutdown is preferably placed approximately in the middle between the operating pressure at minimum flow rate and the sealing pressure of the main valve in full hose operation. In the example mentioned (pressure at the inlet at minimum flow rate 0.27 bar, sealing pressure in full hose operation 0.1 bar), the switching threshold can be set, for example, to 0.17 bar. It then has a clear distance to the operating pressure at minimum flow on the one hand and the sealing pressure on the other. This prevents that at low fluctuations in the operating pressure in the minimum delivery mode, the second automatic safety shutdown already tripped unintentionally or that stops after stopping the fuel pump in the pump just this triggering. The switching threshold of the second automatic safety shutdown can thus according to the invention, for example, at least 0.05 bar, preferably at least 0.1 bar above the sealing pressure of the main valve in full hose operation.
Bevorzugt weist das Hauptventil eine Ventilschaftführung auf, die unter der Wirkung der Einrichtung zur Vorspannung des Hauptventils in die Schließstellung im Vollschlauchbetrieb verkantet und den Ventilschaft des Hauptventils unter einem Winkel zur Symmetrieachse des Hauptventilsitzes führt. Der Ventilschaft wird auf diese Weise gezielt schief geführt. Bei der Ventilschaftführung kann es sich um ein im Strömungskanal des Einlasses gehaltertes Bauteil handeln, das mittels einer vorzugsweise zylindrischen Hülse den Ventilschaft führt und sich radial nach außen erstreckende Haltebereiche, insbesondere Haltearme aufweist, die die Ventilschaftführung im radial äußeren Bereich des Einlasses haltern. Diese sich radial nach außen erstreckenden Haltebereiche sind bevorzugt zur axialen Abstützung bzw. Anlage an einem Widerlager ausgebildet. Übt die Vollschlauchfeder auf das Hauptventil eine in Schließrichtung wirkende Kraft aus, stützt sie sich in der Regel an einem stromauf gelegenen Endstück des Ventilschaftes einerseits und an einer axialen Stirnfläche der Ventilschaftführung andererseits ab. Sie presst auf diese Weise die Ventilschaftführung in Axialrichtung stromab gegen das Widerlager im Einlass. Erfindungsgemäß kann vorgesehen sein, dass durch dieses Drücken gegen das Widerlager eine Verkantung der Ventilschaftführung erfolgt. Dies bedeutet, dass die Ventilschaftführungshülse einen Winkel mit der Symmetrieachse des Hauptventils bzw. Ventilsitzes einschließt. Die Verkantung kann erfindungsgemäß beispielsweise dadurch bewirkt werden, dass die Haltebereiche der Ventilschaftführung im Bereich der Kontaktflächen mit dem Widerlager in Teilbereichen des Umfangs in Axialrichtung weisende Distanzkörper aufweist. Diese Distanzkörper lediglich auf einem Teil des Umfangs der Ventilschaftführung verkippen die Ventilschaftführung und damit auch die den Ventilschaft führende Schaftführungshülse gegen die Symmetrieachse und bewirken damit, dass die Vollschlauchfeder das Hauptventil verkantet in den Ventilsitz drückt und damit den Dichtdruck vermindert.Preferably, the main valve has a valve stem guide, which canted under the action of the device for biasing the main valve in the closed position in full hose operation and the valve stem of the main valve at an angle to the axis of symmetry of the main valve seat. The valve stem is deliberately misaligned in this way. The valve stem guide can be a component held in the flow channel of the inlet, which component guides the valve stem by means of a preferably cylindrical sleeve and has holding regions extending radially outwards, in particular holding arms which hold the valve stem guide in the radially outer region of the inlet. These holding regions extending radially outwards are preferably designed for axial support or abutment against an abutment. If the full-tube spring exerts a force acting in the closing direction on the main valve, it generally rests on an upstream end piece of the valve stem on the one hand and on an axial end face of the valve stem guide on the other hand. It presses in this way the valve stem guide in the axial direction downstream against the abutment in the inlet. According to the invention, provision can be made for the valve stem guide to be tilted by pressing against the abutment. This means that the valve stem guide sleeve forms an angle with the axis of symmetry of the main valve or valve seat. The tilting can be effected according to the invention, for example, by the holding areas of the valve stem guide in the area of the contact surfaces Having the abutment in portions of the circumference in the axial direction facing spacers. These spacers only on a part of the circumference of the valve stem guide tilt the valve stem guide and thus also the valve stem leading shaft guide sleeve against the axis of symmetry and thus cause the Vollschlauchfeder tilted the main valve in the valve seat and thus reduces the sealing pressure.
Gegenstand der Erfindung ist ferner eine Ventilschaftführung für ein erfindungsgemäßes Zapfventil. Sie weist eine Schaftführungshülse zur Führung eines Ventilschaftes und sich von der Schaftführungshülse radial nach außen erstreckende Haltebereiche, vorzugsweise Haltearme auf. Diese Haltebereiche sind zur axialen Anlage an einem Widerlager im Einlass eines Zapfventils ausgebildet. Erfindungsgemäß ist vorgesehen, dass die Schaftführungshülse beim Anpressen der Haltebereiche an ein rotationssymmetrisch ausgebildetes Widerlager eine Winkelstellung einnimmt, bei der ihre Symmetrieachse von der Symmetrieachse des rotationssymmetrisch ausgebildeten Widerlagers abweicht. Dies kann beispielsweise geschehen durch die bereits beschriebenen lediglich in Teilbereichen des Umfangs in Axialrichtung weisende Distanzkörper.The invention further relates to a valve stem guide for a nozzle according to the invention. It has a shaft guide sleeve for guiding a valve stem and extending from the shaft guide sleeve radially outwardly extending holding areas, preferably retaining arms. These holding areas are designed for axial contact with an abutment in the inlet of a dispensing valve. According to the invention it is provided that the shaft guide sleeve assumes an angular position during pressing of the holding portions of a rotationally symmetrical abutment, in which its axis of symmetry deviates from the axis of symmetry of the rotationally symmetrical abutment. This can for example be done by the previously described only in some areas of the circumference in the axial direction facing spacers.
Ein Ausführungsbeispiel der Erfindung wird nachfolgend anhand der Zeichnungen beschreiben. Darin zeigen:
- Fig. 1
- einen Schnitt durch einen Teil eines erfindungsgemäßen Zapfventils;
- Fig. 2
- eine vergrößerte Teilansicht aus
Fig. 1 ; - Fig. 3
- in einem Ausschnitt aus
Fig. 1 das Zapfventil in der Schließstellung; - Fig. 4
- das Zapfventil bei geringer Förderrate;
- Fig. 5
- das Zapfventil im Vollschlauchbetrieb;
- Fig. 6
- eine Ansicht der erfindungsgemäßen Ventilschaftführung
- Fig. 1
- a section through a part of a dispensing valve according to the invention;
- Fig. 2
- an enlarged partial view
Fig. 1 ; - Fig. 3
- in a section
Fig. 1 the nozzle in the closed position; - Fig. 4
- the nozzle at low flow rate;
- Fig. 5
- the nozzle in full hose operation;
- Fig. 6
- a view of the valve stem guide according to the invention
Ein erfindungsgemäßes Zapfventil (umgangssprachlich auch Zapfpistole genannt) weist ein Ventilgehäuse 1, einen mit einem nicht dargestellten Schlauch verbundenen Einlass 2 für Flüssigkeit, ein Auslaufrohr 3 und einen Schalthebel 4 auf. Im Inneren des Ventilgehäuses 1 ist das Hauptventil angeordnet. Dieses Hauptventil weist einen konischen Ventilsitz 5 und einen Ventilkegel 6 auf. Der Ventilkegel 6 ist in zwei Teilkörper 6a und 6b unterteilt. Der in Strömungsrichtung des Hauptventils stromauf angeordnete größere Teilkörper 6a ist fest mit dem Ventilschaft 7 verbunden. Der zweite Teilkörper 6b ist axial verschieblich auf dem Ventilschaft 7 angeordnet, die beiden Teilkörper 6a und 6b werden durch eine Feder 8 auseinandergedrückt, so dass sich dazwischen ein bei 9 angedeuteter Axialspalt bilden kann.An inventive bleed valve (colloquially also called fuel nozzle) has a
Der Ventilschaft 7 wird von einer Ventilschaftführung geführt, die eine Schaftführungshülse 10 und von dieser Schaftführungshülse 10 radial nach außen verlaufende Haltebereiche 11 aufweist. Diese Haltebereiche 11 liegen bei 12 angedeutet axial an einem im Ventilgehäuse 1 ausgebildeten Widerlager an.The
Eine Vollschlauchfeder 13 ist als Druckfeder ausgebildet und liegt an dem stromauf gelegenen axialen Ende der Ventilschaftführungshülse 10 einerseits und an einem Kopf- oder Endstück 14 des Ventilschaftes 7 andererseits an. Sie ist bestrebt, das Hauptventil in die Schließstellung zu ziehen, bei der der Teilkörper 6a dichtend am Ventilkegelsitz 5 zur Anlage kommt.A
Das Hauptventil wird bei der in
Wie in den
In dem Außenkolben 16 ist axial verschieblich ein Innenkolben 17 angeordnet. Der Innenkolben 17 wird von einer Rückholfeder 18 in Richtung der Schließstellung vorgespannt. Der Innenkolben 17 kann durch Betätigen des Schalthebels 4 in Axialrichtung stromab bewegt werden. Beim Ziehen des Schalthebels 4 durch den Benutzer drückt der mit dem Schalthebel 4 verbundene Schalthebelbolzen 31, der in eine in Radialrichtung verlaufende Bohrung oder Nut 19 des Innenkolbens 17 eingreift, diesen Innenkolben 17 gegen die Vorspannung der Rückholfeder 18 in Axialrichtung stromab.In the
Wie bereits erwähnt, ist der Innenkolben 17 im Außenkolben 16 axial verschieblich angeordnet, jedoch können Innenkolben 17 und Außenkolben 16 mittels einer zu beschreibenden Verriegelungsvorrichtung kinematisch miteinander verbunden werden, so dass die Stromab-Bewegung des Innenkolbens 17 den damit gekoppelten Außenkolben 16 ebenfalls stromab bewegt und damit die Schließkraft der Schließfeder 15 vom Teilkörper 6b des Hauptventils nimmt. Diese Verbindung bzw. Verriegelung von Außenkolben 16 und Innenkolben 17 durch als Membranrollen 20 bezeichnete Verriegelungselemente ist im Stand der Technik grundsätzlich bekannt und beispielsweise beschreiben in
Wird der Schalthebel 4 weiter gezogen, entfernt sich der Außenkolben 16 weiter vom Hauptventil, sodass dieses jetzt nur noch von der Vollschlauchfeder 13 in die Schließstellung gezogen wird. Der bei einem regulären Betankungsvorgang am Einlass 2 anstehende Pumpendruck ist deutlich größer als der Dichtdruck unter der Wirkung der Vollschlauchfeder 13, so dass Flüssigkeit bzw. Kraftstoff jetzt mit einer hohen Durchflussrate durch das Hauptventil strömen kann. Da die Vollschlauchfeder 13 das Hauptventil jederzeit auch während des Betankungsvorgangs in Richtung Schließstellung zieht, findet über dem Hauptventil ein gewisser Druckabfall statt, der vor dem Hauptventil am Einlass anstehende Druck teilt sich auch einem Druckanschlusskanal 21 mit.If the shift lever 4 is pulled further, the
Der Betankungsvorgang kann beendet werden, indem der Schalthebel 4 vom Benutzer losgelassen bzw. eine etwaige Verrastung des Schalthebels 4 gelöst wird. Schließfeder 15 und Rückholfeder 18 drücken dann Innenkolben 17 und Außenkolben 16 in die Schließstellung zurück und schließen das Hauptventil.The fueling process can be terminated by the shift lever 4 released by the user or any latching of the shift lever 4 is released. Closing
Häufig wird jedoch ein Betankungsvorgang nicht auf diese Weise manuell beendet, sondern durch das Auslösen automatischer Sicherheitsabschaltungen entweder bei vollem Tank oder nach Abschalten der Pumpe bei Erreichen einer vorgewählten Kraftstoffmenge.Frequently, however, a refueling operation is not manually terminated in this manner, but by the initiation of automatic safety shutdowns either at full tank or after switching off the pump upon reaching a preselected amount of fuel.
Sowohl die erste als auch die zweite automatische Sicherheitsabschaltung beruhen auf dem Prinzip, die Membranrollen 20 aus den Nuten bzw. Ausnehmungen von Innenkolben 17 und Außenkolben 16 herauszuziehen und auf diese Weise deren Verriegelung miteinander zu lösen. Der Außenkolben 16 kann dann unter der Wirkung der Schließfeder 15 zurück in die Schließstellung schnappen und das Hauptventil wieder von stromab her mit der beschriebenen großen Schließkraft beaufschlagen. Nach einem solchen Auslösen der Sicherheitsabschaltung befindet sich der Innenkolben 17 aufgrund des nach wie vor gezogenen Schalthebels 4 zunächst noch in der axial stromab verschobenen Stellung. Die Ausnehmungen für die Membranrollen 20 im Innenkolben 17 einerseits und Außenkolben 16 andererseits fluchten nicht mehr miteinander. Erst wenn der Schalthebel 4 gelöst wird und die Rückholfeder 18 den Innenkolben 17 zurück in seine Ausgangsposition bewegen kann, fluchten die Ausnehmungen wieder miteinander und die Membranrollen 20 können gegebenenfalls erneut Innen- und Außenkolben miteinander verriegeln. Auf diese Wiese ist gewährleistet, dass nach einem Auslösen der automatischen Sicherheitsabschaltung ein erneuter Betankungsvorgang nur dann beginnen kann, wenn zunächst der Schalthebel 4 gelöst und in seine Ruheposition zurück bewegt wurde.Both the first and second automatic safety shutdown are based on the principle of extracting the
Die Membranrollen 20 können mittels eines Halters 22 nach oben (Bezug nehmend auf die Darstellung der
Die erste automatische Sicherheitsabschaltung funktioniert in herkömmlicher Weise mittels der Membran 23. Der Raum oberhalb der Membran 23 kommuniziert mit einer herkömmlichen Fühlerleitung, die an der Auslaufspitze des Auslaufrohrs mündet. Erreicht im Zuge eines Betankungsvorgangs der Flüssigkeitsspiegel das Auslaufrohr und damit das Ende dieser Fühlerleitung, ändern sich die Druckverhältnisse beidseits der Membran 23 dergestalt, dass sich der Druck oberhalb der Membran vermindert und diese damit die Halterung 22 nach oben und die Membranrollen 20 damit aus ihrer Verriegelungsstellung herauszieht. Die Verriegelung von Innenkolben 17 und Außenkolben 16 wird gelöst, die Schließfeder 15 kann den Außenkolben 16 in die Schließstellung drücken, das Hauptventil schließen und damit den Betankungsvorgang beenden. Die Details dieses aus dem Stand der Technik bekannten Wirkmechanismus sind beispielsweise beschrieben in
Verschiedene Betankungsvorgänge unter Verwendung eines erfindungsgemäßen Zapfventils seien nachfolgend beschrieben.Various refueling operations using a dispensing valve according to the invention are described below.
In einer ersten Variante soll ein Kraftstofftank vollständig gefüllt werden. Der Betankungsvorgang wird hier in herkömmlicher Weise mit vollem Pumpendruck der Zapfsäule durchgeführt, bis die beschriebene erste automatische Sicherheitsabschaltung nach Anstieg des Flüssigkeitsspiegels bis zum Ende des Auslaufrohrs 3 die Membran 23 nach oben zieht, die Membranrollen 20 heraushebt und damit ein Zurückschnappen des Außenkolbens 16 in die Schließstellung bewirkt und das Hauptventil schließt. Das Zapfventil kann jetzt wieder zurück an die Zapfsäule gehängt werden und ist für einen neuen Betankungsvorgang bereit. Wie bereits erwähnt, drückt die Schließfeder 15 das Hauptventil mit hoher Kraft in die Schließstellung, sodass vollständige Dichtigkeit bei jedwedem im Betrieb auftretenden Druck am Einlass 2 gewährleistet ist.In a first variant, a fuel tank is to be completely filled. The fueling process is carried out here in a conventional manner with full pump pressure of the pump until the described first automatic safety shutdown after rising of the liquid level to the end of the
In einer zweiten Variante wählt der Nutzer eine bestimmte Kraftstoffmenge (oder einen bestimmten zu zahlenden Betrag) vor, der nicht ausreicht, um den Tank vollständig zu füllen. Der Betankungsvorgang wird so begonnen wie vorstehend geschildert. Kurz vor Erreichen der vorgewählten Kraftstoffmenge wird die Förderleistung der Kraftstoffpumpe in der Zapfsäule deutlich reduziert, um die vorgewählte Kraftstoffmenge punktgenau ansteuern zu können. Beispielsweise kann die Förderleistung kurz vor Erreichen der vorgewählten Kraftstoffmenge bis auf etwa 2 1/min reduziert werden. Bei dieser geringen Förderleistung steht im Ausführungsbeispiel vor dem Hauptventil und damit auch im Druckanschlusskanal 21 und im Raum 27 oberhalb des Kolbens 25 ein Druck von 0,27 bar an. Dieser Druck reicht aus, um den Kolben 25 in der in
Nach Erreichen der vorgewählten Kraftstoffmenge schaltet die Kraftstoffpumpe vollständig ab und es tritt der sogenannte Vollschlauchbetrieb ein. Dies bedeutet, dass das Hauptventil noch nicht wieder von der Schließfeder 15 unter Kraftvermittlung des Außenkolbens 16 geschlossen wird, sondern lediglich von der Vollschlauchfeder 13 in der Schließstellung gehalten wird. Ein Auslaufen des Schlauches durch das Zapfventil oder ein Kraftstoffdiebstahl durch ein sogenanntes Melken des Schlauches wird so verhindert. Andererseits muss gewährleistet sein, dass vor dem Einhängen des Zapfventils in die Zapfsäule und damit dem vollständigen Beenden des Betankungsvorgangs der Vollschlauchbetrieb wieder aufgehoben wird und das Hauptventil vollständig durch die sehr viel stärkere Schließfeder 15 in die Schließstellung gedrückt wird, auch wenn der Benutzer vergisst, den beispielsweise verrasteten Schalthebel 4 zurück in seine Ausgangsposition zu bewegen. Mit anderen Worten muss gewährleistet sein, dass die Verriegelung zwischen Innenkolben 17 und Außenkolben 16 aufgehoben wird.After reaching the preselected amount of fuel, the fuel pump switches off completely and there is the so-called full hose operation. This means that the main valve is not closed again by the closing
Zu diesem Zweck ist erfindungsgemäß vorgesehen, dass die Vollschlauchfeder 13 das Hauptventil im Vollschlauchbetrieb verkantet in die Schließstellung drückt und dessen Dichtigkeit reduziert. Wie in
Dieser reduzierte Dichtdruck bewirkt, dass nach dem Abschalten der Kraftstoffpumpe bei Erreichen der vorgewählten Kraftstoffmenge der zunächst noch vorhandene Druck von 0,27 bar am Einlass (der sich prinzipiell beispielsweise durch Sonneneinstrahlung auf einen schwarzen Kraftstoffschlauch noch erhöhen kann) binnen kurzer Zeit und zuverlässig auf etwa 0,1 bar abbaut. Dabei wird die Schaltschwelle der zweiten automatischen Sicherheitsabschaltung von 0,17 bar sicher unterschritten. Bei Unterschreiten dieser Schaltschwelle, das heißt einem Absinken des Druckes im Druckanschlusskanal 21 und Raum 27 oberhalb des Kolbens 25, übersteigt die Kraft der Feder 24 die auf den Kolben 25 von oben aus dem Raum 27 ausgeübte Druckkraft, die zweite automatische Sicherheitsabschaltung löst jetzt aus, der Kolben 25 bewegt sich nach oben und zieht die Membranrollen 20 aus ihrer Verriegelungsstellung heraus. Somit gewährleistet die Erfindung, dass der Vollschlauchbetrieb nicht unbegrenzt andauert, sondern dass verlässlich die zweite automatische Sicherheitsabschaltung auslöst und damit das Hauptventil zurück in die vollständig mit der Schließkraft der Schließfeder 15 beaufschlagte Stellung bringt. Wenn die Schließfeder 15 von stromab her auf das Hauptventil wirkt, erfolgt diese die Kraft der Vollschlauchfeder 13 weit übersteigende Kraftbeaufschlagung vollständig symmetrisch, so dass keine Verkantung oder Schiefstellung mehr eintritt, die die Dichtigkeit vermindern könnte.This reduced sealing pressure causes after switching off the fuel pump on reaching the preselected amount of fuel, the first still existing pressure of 0.27 bar at the inlet (in principle, for example, by sunlight on a black fuel hose can still increase) within a short time and reliably to about Degrades 0.1 bar. The switching threshold of the second automatic safety shutdown of 0.17 bar is safely undercut. When falling below this switching threshold, that is, a drop in the pressure in the
Die
In
Claims (11)
- Fuel pump nozzle, with an inlet (2), a discharge pipe (3), a main valve for controlling the stream of liquid between the inlet (2) and discharge pipe (3), a switching lever (4) for actuating the main valve, a first automatic safety shut-off which moves the main valve into the closed position if the liquid level in a tank to be filled reaches a filling level sensor arranged in the region of the discharge pipe (3), a second automatic safety shut-off which moves the main valve into the closed position if the liquid pressure at the inlet (2) drops below a minimum value, and a mechanism (13) for prestressing the main valve into the closed position, said mechanism bringing about a variable opening cross section of the main valve depending on the liquid pressure at the inlet (2), characterized in that the main valve is pressed into the closed position in a tilted manner under the action of the mechanism for prestressing the main valve into the closed position in the full hose mode such that the tightness of said main valve is reduced.
- Fuel pump nozzle according to Claim 1, characterized in that the mechanism for prestressing the main valve into the closed position has a full hose spring (13).
- Fuel pump nozzle according to Claim 1 or 2, characterized in that the main valve is designed as a conical valve (6) with a valve stem guide (10, 11) and a valve seat (5) and the valve stem guide (10, 11) is designed such that the main valve is pressed against the valve seat (5) with an asymmetrical distribution of force under the action of the mechanism (13) for prestressing the main valve into the closed position in the full hose mode.
- Fuel pump nozzle according to one of Claims 1 to 3, characterized in that the sealing pressure of the main valve in the full hose mode is 0.1 to 0.15 bar.
- Fuel pump nozzle according to one of Claims 1 to 4, characterized in that the switching threshold of the second automatic safety shut-off which moves the main valve into the closed position if the liquid pressure at the inlet (2) drops below a minimum value is 0.15 to 0.25 bar.
- Fuel pump nozzle according to one of Claims 1 to 5, characterized in that the switching threshold of the second automatic safety shut-off which moves the main valve into the closed position if the liquid pressure at the inlet (2) drops below a minimum value is at least 0.05 bar, preferably at least 0.1 bar above the sealing pressure of the main valve in the full hose mode.
- Fuel pump nozzle according to one of Claims 1 to 6, characterized in that the main valve has a valve stem guide (10, 11) which tilts under the action of the mechanism for prestressing the main valve into the closed position in the full hose mode and guides the valve stem (7) of the main valve at an angle to the axis of symmetry of the main valve seat (5).
- Fuel pump nozzle according to Claim 7, characterized in that the valve stem guide (10, 11) is pressed against an abutment (12) in a tilted manner under the action of the mechanism for prestressing the main valve into the closed position in the full hose mode.
- Fuel pump nozzle according to Claim 8, characterized in that, in the region of the contact surfaces with the abutment (12), the valve stem guide (10, 11) has spacers (28) facing in the axial direction in subregions of the circumference.
- Valve stem guide for a fuel pump nozzle according to one of Claims 1 to 9, with a stem guiding sleeve (10) and with holding regions (11) which extend radially outward from the stem guiding sleeve (10) and are designed to bear axially against an abutment (12), characterized in that, when the holding regions (11) are pressed against an abutment (12) of rotationally symmetrical design, the stem guiding sleeve (10) takes up an angular position in which the axis of symmetry thereof differs from the axis of symmetry of the abutment (12) of rotationally symmetrical design.
- Valve stem guide according to Claim 10, characterized in that the holding regions (11) have spacers (28) facing in the axial direction in subregions of the circumference.
Priority Applications (10)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PT100050855T PT2386520E (en) | 2010-05-14 | 2010-05-14 | Fuel valve |
PL10005085T PL2386520T3 (en) | 2010-05-14 | 2010-05-14 | Fuel valve |
EP10005085A EP2386520B1 (en) | 2010-05-14 | 2010-05-14 | Fuel valve |
ES10005085T ES2408212T3 (en) | 2010-05-14 | 2010-05-14 | Nozzle |
DK10005085.5T DK2386520T3 (en) | 2010-05-14 | 2010-05-14 | filling valve |
AU2011201961A AU2011201961B2 (en) | 2010-05-14 | 2011-04-29 | Fuel nozzle |
CN201110133194.9A CN102320548B (en) | 2010-05-14 | 2011-05-11 | Fuel valve |
US13/105,627 US8695648B2 (en) | 2010-05-14 | 2011-05-11 | Fuel pump nozzle |
NZ592812A NZ592812A (en) | 2010-05-14 | 2011-05-12 | Fuel nozzle having a main valve that is closed in a tilted manner to reduce its tightness in a full hose mode |
HK11114055.0A HK1159594A1 (en) | 2010-05-14 | 2011-12-29 | Fuel valve |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP10005085A EP2386520B1 (en) | 2010-05-14 | 2010-05-14 | Fuel valve |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2386520A1 EP2386520A1 (en) | 2011-11-16 |
EP2386520B1 true EP2386520B1 (en) | 2013-04-03 |
Family
ID=42697376
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10005085A Active EP2386520B1 (en) | 2010-05-14 | 2010-05-14 | Fuel valve |
Country Status (10)
Country | Link |
---|---|
US (1) | US8695648B2 (en) |
EP (1) | EP2386520B1 (en) |
CN (1) | CN102320548B (en) |
AU (1) | AU2011201961B2 (en) |
DK (1) | DK2386520T3 (en) |
ES (1) | ES2408212T3 (en) |
HK (1) | HK1159594A1 (en) |
NZ (1) | NZ592812A (en) |
PL (1) | PL2386520T3 (en) |
PT (1) | PT2386520E (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
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EP4105166A1 (en) | 2021-06-14 | 2022-12-21 | ELAFLEX HIBY GmbH & Co. KG | Dispensing valve |
EP4234481A1 (en) | 2022-02-23 | 2023-08-30 | ELAFLEX HIBY GmbH & Co. KG | Dispensing valve |
EP4269327A1 (en) | 2022-04-29 | 2023-11-01 | ELAFLEX HIBY GmbH & Co. KG | Dispensing valve |
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US20110219860A1 (en) * | 2008-09-17 | 2011-09-15 | Franklin Fueling Systems, Inc. | Fuel dispensing nozzle |
US8752597B2 (en) | 2008-09-17 | 2014-06-17 | Franklin Fueling Systems, Inc. | Fuel dispensing nozzle |
DK2687479T3 (en) | 2012-07-20 | 2016-04-25 | Elaflex Hiby Tanktechnik Gmbh & Co Kg | filling Gun |
DK2733113T3 (en) * | 2012-11-14 | 2017-06-19 | Elaflex Hiby Tanktechnik Gmbh & Co Kg | Filling gun with a safety valve |
CN103569934B (en) * | 2013-11-01 | 2016-01-13 | 陈霈 | A kind of nozzle |
CN104986715B (en) * | 2015-07-09 | 2017-11-03 | 优必得石油设备(苏州)有限公司 | Nozzle |
PL3369700T3 (en) | 2017-03-03 | 2021-11-22 | Elaflex Hiby Gmbh & Co. Kg | Dispensing nozzle for two maximum flow-rates |
US10737928B2 (en) | 2018-02-23 | 2020-08-11 | Husky Corporation | Nozzle for delivery of auxiliary or additive fluid for treating exhaust for a diesel motor for autos or truck vehicle or the like |
EP3767153B1 (en) | 2019-07-16 | 2021-10-13 | Oasis Engineering Ltd | Dispensing nozzle for gaseous or liquefied fuel, with delay between coupling and actuating |
MX2022006492A (en) | 2019-11-29 | 2022-07-04 | Elaflex Hiby Gmbh & Co Kg | Filling valve with leakage protection device. |
CN116234767A (en) | 2020-09-29 | 2023-06-06 | 伊莱弗莱克斯希贝股份有限公司 | Self-closing diverter valve |
ES2939285T3 (en) | 2020-09-29 | 2023-04-20 | Elaflex Hiby Gmbh & Co Kg | Gun with dispensing nozzle with switch between two maximum flow rates |
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US5386859A (en) * | 1991-05-29 | 1995-02-07 | Healy Systems, Inc. | Fuel dispensing nozzle having transparent boot |
DE4431547C1 (en) * | 1994-09-05 | 1995-10-12 | Karlheinz Ehlers | Tap valve for filling fuel via tap column into vehicle fuel tank |
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DE102008010988B3 (en) | 2008-02-25 | 2009-07-16 | Elaflex Tankstellentechnik Gmbh & Co | gas pump nozzle |
CN201254452Y (en) * | 2008-07-17 | 2009-06-10 | 浙江宝泰机器有限公司 | Self-closing oil feeder |
CN102159493B (en) * | 2008-09-17 | 2013-09-11 | 富兰克林加油***公司 | Fuel dispensing nozzle |
-
2010
- 2010-05-14 ES ES10005085T patent/ES2408212T3/en active Active
- 2010-05-14 PT PT100050855T patent/PT2386520E/en unknown
- 2010-05-14 PL PL10005085T patent/PL2386520T3/en unknown
- 2010-05-14 EP EP10005085A patent/EP2386520B1/en active Active
- 2010-05-14 DK DK10005085.5T patent/DK2386520T3/en active
-
2011
- 2011-04-29 AU AU2011201961A patent/AU2011201961B2/en active Active
- 2011-05-11 CN CN201110133194.9A patent/CN102320548B/en active Active
- 2011-05-11 US US13/105,627 patent/US8695648B2/en active Active
- 2011-05-12 NZ NZ592812A patent/NZ592812A/en unknown
- 2011-12-29 HK HK11114055.0A patent/HK1159594A1/en unknown
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP4105166A1 (en) | 2021-06-14 | 2022-12-21 | ELAFLEX HIBY GmbH & Co. KG | Dispensing valve |
WO2022263341A1 (en) | 2021-06-14 | 2022-12-22 | Elaflex Hiby Gmbh & Co. Kg | Filling nozzle |
EP4234481A1 (en) | 2022-02-23 | 2023-08-30 | ELAFLEX HIBY GmbH & Co. KG | Dispensing valve |
WO2023161205A1 (en) | 2022-02-23 | 2023-08-31 | Elaflex Hiby Gmbh & Co. Kg | Fuel nozzle |
EP4269327A1 (en) | 2022-04-29 | 2023-11-01 | ELAFLEX HIBY GmbH & Co. KG | Dispensing valve |
WO2023208700A1 (en) | 2022-04-29 | 2023-11-02 | Elaflex Hiby Gmbh & Co. Kg | Filling nozzle |
Also Published As
Publication number | Publication date |
---|---|
AU2011201961A1 (en) | 2012-03-01 |
PT2386520E (en) | 2013-05-28 |
ES2408212T3 (en) | 2013-06-19 |
US8695648B2 (en) | 2014-04-15 |
NZ592812A (en) | 2013-01-25 |
US20110277880A1 (en) | 2011-11-17 |
CN102320548A (en) | 2012-01-18 |
CN102320548B (en) | 2015-03-25 |
EP2386520A1 (en) | 2011-11-16 |
DK2386520T3 (en) | 2013-05-06 |
AU2011201961B2 (en) | 2015-04-02 |
HK1159594A1 (en) | 2012-08-03 |
PL2386520T3 (en) | 2013-08-30 |
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