EP2386520B1 - Buse de distribution - Google Patents

Buse de distribution Download PDF

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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
Application number
EP10005085A
Other languages
German (de)
English (en)
Other versions
EP2386520A1 (fr
Inventor
Heinz-Ulrich Meyer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Elaflex Hiby Tanktechnik GmbH and Co KG Co
Original Assignee
Elaflex Hiby Tanktechnik GmbH and Co KG Co
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Elaflex Hiby Tanktechnik GmbH and Co KG Co filed Critical Elaflex Hiby Tanktechnik GmbH and Co KG Co
Priority to EP10005085A priority Critical patent/EP2386520B1/fr
Priority to PL10005085T priority patent/PL2386520T3/pl
Priority to ES10005085T priority patent/ES2408212T3/es
Priority to PT100050855T priority patent/PT2386520E/pt
Priority to DK10005085.5T priority patent/DK2386520T3/da
Priority to AU2011201961A priority patent/AU2011201961B2/en
Priority to US13/105,627 priority patent/US8695648B2/en
Priority to CN201110133194.9A priority patent/CN102320548B/zh
Priority to NZ592812A priority patent/NZ592812A/xx
Publication of EP2386520A1 publication Critical patent/EP2386520A1/fr
Priority to HK11114055.0A priority patent/HK1159594A1/xx
Application granted granted Critical
Publication of EP2386520B1 publication Critical patent/EP2386520B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • 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)
  • Mechanically-Actuated Valves (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (11)

  1. Pistolet de distribution, comportant une admission (2), un tuyau de distribution (3), une vanne principale destinée à commander le flux de liquide entre l'admission (2) et le tuyau de distribution (3), un levier de commande (4) pour actionner la vanne principale, un premier dispositif d'arrêt de sécurité automatique qui amène la vanne principale dans la position de fermeture lorsque le niveau de liquide dans un réservoir à remplir atteint un capteur de niveau disposé dans la zone du tuyau de distribution (3), un deuxième dispositif d'arrêt de sécurité automatique qui amène la vanne principale dans la position de fermeture lorsque la pression du liquide au niveau de l'admission (2) est inférieure à une valeur minimale, et un dispositif (13) pour précontraindre la vanne principale dans la position de fermeture induisant sur la vanne principale une section transversale d'ouverture variable en fonction de la pression du liquide au niveau de l'admission (2), caractérisé en ce que, sous l'effet du dispositif pour précontraindre la vanne principale dans la position de fermeture en cas de fonctionnement à tuyau plein, la vanne principale est poussée dans la position de fermeture en étant inclinée de telle sorte que l'étanchéité de celle-ci est diminuée.
  2. Pistolet de distribution selon la revendication 1, caractérisé en ce que le dispositif pour précontraindre la vanne principale dans la position de fermeture comporte un ressort de clapet anti-retour (13).
  3. Pistolet de distribution selon la revendication 1 ou 2, caractérisé en ce que la vanne principale est réalisée sous forme de vanne à boisseau (6) comportant un guidage (10, 11) pour la tige de la vanne et un siège de vanne (5), et le guidage (10, 11) pour la tige de la vanne est réalisé de telle sorte que, sous l'effet du dispositif (13) pour précontraindre la vanne principale dans la position de fermeture en cas de fonctionnement à tuyau plein, la vanne principale est poussée avec une répartition asymétrique des forces contre le siège de vanne (5).
  4. Pistolet de distribution selon l'une quelconque des revendications 1 à 3, caractérisé en ce que, en cas de fonctionnement à tuyau plein, la pression d'étanchéité de la vanne principale est de 0,1 à 0,15 bar.
  5. Pistolet de distribution selon l'une quelconque des revendications 1 à 4, caractérisé en ce que le seuil d'activation du deuxième dispositif d'arrêt de sécurité automatique, qui amène la vanne principale en position de fermeture lorsque la pression du liquide au niveau de l'admission (2) est inférieure à une valeur minimale, est de l'ordre de 0,15 à 0,25 bar.
  6. Pistolet de distribution selon l'une quelconque des revendications 1 à 5, caractérisé en ce que le seuil d'activation du deuxième dispositif d'arrêt de sécurité automatique, qui amène la vanne principale en position de fermeture lorsque la pression du liquide au niveau de l'admission (2) est inférieure à une valeur minimale, se situe à au moins 0,05 bar, de préférence au moins 0,1 bar au-dessus de la pression d'étanchéité de la vanne principale en cas de fonctionnement à tuyau plein.
  7. Pistolet de distribution selon l'une quelconque des revendications 1 à 6, caractérisé en ce que la vanne principale comporte un guidage (10, 11) pour la tige de la vanne qui est incliné, sous l'effet du dispositif pour précontraindre la vanne principale dans la position de fermeture en cas de fonctionnement à tuyau plein, et guide la tige (7) de la vanne principale selon un angle donné par rapport à l'axe de symétrie du siège (5) de la vanne principale.
  8. Pistolet de distribution selon la revendication 7, caractérisé en ce que, sous l'effet du dispositif pour précontraindre la vanne principale dans la position de fermeture en cas de fonctionnement à tuyau plein, le guidage (10, 11) pour la tige de la vanne est poussé en étant incliné contre une contre-butée (12).
  9. Pistolet de distribution selon la revendication 8, caractérisé en ce que le guidage (10, 11) pour la tige de la vanne, dans la zone des surfaces de contact avec la contre-butée (12), comporte des écarteurs (28) orientés dans la direction axiale dans des zones partielles de la périphérie.
  10. Guidage de la tige de vanne pour un pistolet de distribution selon l'une quelconque des revendications 1 à 9, comportant une gaine (10) et comportant des zones de retenue (11), qui s'étendent radialement vers l'extérieur à partir de la gaine (10) et sont réalisées pour venir en appui axial sur une contre-butée (12), caractérisé en ce que la gaine (10) du guidage de la tige de vanne, lorsque les zones de retenue (11) sont pressées contre une contre-butée (12) à symétrie de révolution, est amenée dans une position angulaire, dans laquelle son axe de symétrie s'écarte de l'axe de symétrie de la contre-butée (12) à symétrie de révolution.
  11. Guidage de la tige de vanne selon la revendication 10, caractérisé en ce que les zones de retenue (11) comportent des écarteurs (28) orientés dans la direction axiale dans des zones partielles de la périphérie.
EP10005085A 2010-05-14 2010-05-14 Buse de distribution Active EP2386520B1 (fr)

Priority Applications (10)

Application Number Priority Date Filing Date Title
EP10005085A EP2386520B1 (fr) 2010-05-14 2010-05-14 Buse de distribution
PL10005085T PL2386520T3 (pl) 2010-05-14 2010-05-14 Zawór dozujący
ES10005085T ES2408212T3 (es) 2010-05-14 2010-05-14 Boquerel
PT100050855T PT2386520E (pt) 2010-05-14 2010-05-14 Pistola de abastecimento
DK10005085.5T DK2386520T3 (da) 2010-05-14 2010-05-14 Påfyldningsventil
AU2011201961A AU2011201961B2 (en) 2010-05-14 2011-04-29 Fuel nozzle
US13/105,627 US8695648B2 (en) 2010-05-14 2011-05-11 Fuel pump nozzle
CN201110133194.9A CN102320548B (zh) 2010-05-14 2011-05-11 放液阀
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 (fr) 2010-05-14 2010-05-14 Buse de distribution

Publications (2)

Publication Number Publication Date
EP2386520A1 EP2386520A1 (fr) 2011-11-16
EP2386520B1 true EP2386520B1 (fr) 2013-04-03

Family

ID=42697376

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10005085A Active EP2386520B1 (fr) 2010-05-14 2010-05-14 Buse de distribution

Country Status (10)

Country Link
US (1) US8695648B2 (fr)
EP (1) EP2386520B1 (fr)
CN (1) CN102320548B (fr)
AU (1) AU2011201961B2 (fr)
DK (1) DK2386520T3 (fr)
ES (1) ES2408212T3 (fr)
HK (1) HK1159594A1 (fr)
NZ (1) NZ592812A (fr)
PL (1) PL2386520T3 (fr)
PT (1) PT2386520E (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4105166A1 (fr) 2021-06-14 2022-12-21 ELAFLEX HIBY GmbH & Co. KG Buse de distribution
EP4234481A1 (fr) 2022-02-23 2023-08-30 ELAFLEX HIBY GmbH & Co. KG Soupape de soutirage
EP4269327A1 (fr) 2022-04-29 2023-11-01 ELAFLEX HIBY GmbH & Co. KG Soupape de soutirage
US11999610B2 (en) 2019-11-29 2024-06-04 Elaflex Hiby Gmbh & Co. Kg Filling valve with leakage protection device

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US8752597B2 (en) 2008-09-17 2014-06-17 Franklin Fueling Systems, Inc. Fuel dispensing nozzle
US20110219860A1 (en) * 2008-09-17 2011-09-15 Franklin Fueling Systems, Inc. Fuel dispensing nozzle
ES2565062T3 (es) 2012-07-20 2016-03-31 Elaflex Hiby Tanktechnik Gmbh & Co. Kg Pistola de distribución
PT2733113T (pt) * 2012-11-14 2017-07-03 Elaflex Hiby Tanktechnik Gmbh & Co Kg Pistola de abastecimento com uma válvula de segurança
CN103569934B (zh) * 2013-11-01 2016-01-13 陈霈 一种加油枪
CN104986715B (zh) * 2015-07-09 2017-11-03 优必得石油设备(苏州)有限公司 加油枪
ES2883270T3 (es) 2017-03-03 2021-12-07 Elaflex Hiby Gmbh & Co Kg Pistola de distribución para dos caudales máximos
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
PL3767153T3 (pl) 2019-07-16 2022-02-07 Oasis Engineering Ltd Zawór dozujący dla paliwa gazowego albo skroplonego z opóźnieniem między sprzężeniem a aktywowaniem
US11603309B2 (en) 2019-11-29 2023-03-14 Elaflex Hiby Gmbh & Co. Kg Filling valve with leakage protection device
WO2022069319A1 (fr) 2020-09-29 2022-04-07 Elaflex Hiby Gmbh & Co. Kg Buse de remplissage à fermeture automatique
EP3974374B1 (fr) 2020-09-29 2023-01-11 ELAFLEX HIBY GmbH & Co. KG Buse de distribution avec interrupteur entre deux débits maximaux

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Publication number Priority date Publication date Assignee Title
US11999610B2 (en) 2019-11-29 2024-06-04 Elaflex Hiby Gmbh & Co. Kg Filling valve with leakage protection device
EP4105166A1 (fr) 2021-06-14 2022-12-21 ELAFLEX HIBY GmbH & Co. KG Buse de distribution
WO2022263341A1 (fr) 2021-06-14 2022-12-22 Elaflex Hiby Gmbh & Co. Kg Pistolet de distribution
EP4234481A1 (fr) 2022-02-23 2023-08-30 ELAFLEX HIBY GmbH & Co. KG Soupape de soutirage
WO2023161205A1 (fr) 2022-02-23 2023-08-31 Elaflex Hiby Gmbh & Co. Kg Buse de carburant
EP4269327A1 (fr) 2022-04-29 2023-11-01 ELAFLEX HIBY GmbH & Co. KG Soupape de soutirage
WO2023208700A1 (fr) 2022-04-29 2023-11-02 Elaflex Hiby Gmbh & Co. Kg Buse de remplissage

Also Published As

Publication number Publication date
NZ592812A (en) 2013-01-25
PL2386520T3 (pl) 2013-08-30
PT2386520E (pt) 2013-05-28
DK2386520T3 (da) 2013-05-06
ES2408212T3 (es) 2013-06-19
EP2386520A1 (fr) 2011-11-16
AU2011201961A1 (en) 2012-03-01
US20110277880A1 (en) 2011-11-17
US8695648B2 (en) 2014-04-15
CN102320548A (zh) 2012-01-18
HK1159594A1 (en) 2012-08-03
CN102320548B (zh) 2015-03-25
AU2011201961B2 (en) 2015-04-02

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