EP2428485B1 - Zapfventil - Google Patents

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Publication number
EP2428485B1
EP2428485B1 EP10009496.0A EP10009496A EP2428485B1 EP 2428485 B1 EP2428485 B1 EP 2428485B1 EP 10009496 A EP10009496 A EP 10009496A EP 2428485 B1 EP2428485 B1 EP 2428485B1
Authority
EP
European Patent Office
Prior art keywords
shut
main valve
piston
closed
liquid
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
EP10009496.0A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2428485A1 (de
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 DK10009496.0T priority Critical patent/DK2428485T3/en
Priority to EP10009496.0A priority patent/EP2428485B1/de
Priority to ES10009496.0T priority patent/ES2454667T3/es
Priority to PT100094960T priority patent/PT2428485E/pt
Priority to PL10009496T priority patent/PL2428485T3/pl
Priority to AU2011211357A priority patent/AU2011211357B2/en
Priority to NZ594538A priority patent/NZ594538A/xx
Priority to CN201110280142.4A priority patent/CN102442629B/zh
Priority to US13/231,557 priority patent/US8347924B2/en
Publication of EP2428485A1 publication Critical patent/EP2428485A1/de
Priority to HK12103612.8A priority patent/HK1163046A1/xx
Application granted granted Critical
Publication of EP2428485B1 publication Critical patent/EP2428485B1/de
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
    • B67D7/04—Apparatus or devices for transferring liquids from bulk storage containers or reservoirs into vehicles or into portable containers, e.g. for retail sale purposes for transferring fuels, lubricants or mixed fuels and lubricants
    • 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

Definitions

  • the invention relates to a main valve for a nozzle, as well as a nozzle.
  • Dispensing valves at filling stations are usually designed as so-called automatic dispensing valves. They have an automatic shut-off, which prevents an overflow of a tank to be filled. This automatic safety shutdown usually works the main valve of the dispensing valve. Furthermore, it is known to provide a second automatic safety shutdown, which completely closes the main valve of the dispensing valve even when the pressure at the inlet of the dispensing valve falls below a certain threshold. In this way, it should be ensured that after switching off the fuel delivery pump in the pump and thereby causing drop in pressure at the inlet of the dispensing valve, an automatic closing takes place.
  • the main valves of nozzles have to achieve certain pressure tightness when closed.
  • the pressure tightness is usually dependent on the strength of a closing spring, with which the main valve is closed.
  • the closing spring ensures, in particular with automatic safety shutdown for moving a shut-off of the main valve in the closed position.
  • a high closing spring force is required to achieve the required tightness.
  • the present invention seeks to provide a main valve for a nozzle, as well as a nozzle in which pressure surges are reduced or avoided in automatic safety shutdown of the main valve.
  • the invention relates to a main valve for a nozzle with a shut-off for closing a liquid line and a reducible by moving the shut-off from the open position in the closed position displacement chamber, wherein the displacement space upstream and downstream of the shut-off with the liquid line via secondary lines fluidly connected, and the secondary line with the liquid line upstream of the Absperr endeavors is closed in the closed position of the shut-off.
  • the invention further relates to a dispensing valve, comprising an inlet, an outlet pipe, a main valve for controlling the liquid flow between the inlet and outlet pipe with a shut-off body and a displaceable by moving the shut-off of the open position in the closed position displacement chamber, wherein the displacement chamber with the inlet and the outlet pipe is fluidly connected via secondary lines, and the secondary line is closed with the inlet in the closed position of the shut-off.
  • a dispensing valve is a device for manually controlling a fluid flow, for example, the fuel flow during a refueling operation.
  • the inlet is that portion of the dispensing valve through which liquid is supplied, for example, from the dispenser.
  • the main valve is the device that controls the fluid 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 spout is the device through which the liquid flow is discharged, e.g. in a container to be filled.
  • the secondary line between the displacement chamber and the liquid line upstream of the shut-off valve is also closed when closing the main valve.
  • an intermediate position is provided between the open position and the closed position of the shut-off body, and the secondary line to the liquid line is closed upstream of the shut-off at a position of the shut-off between intermediate position and closed position. If the shut-off body is moved from the open position into the closed position, both secondary lines to the liquid line are initially opened upstream and downstream of the shut-off body. During the closing process, liquid can therefore flow out of the displacement space through both secondary lines. After reaching the intermediate position, the secondary line is closed to the liquid line upstream of the shut-off. The liquid can then flow out of the displacement chamber only through the secondary line to the liquid line downstream of the shut-off body.
  • the damping effect is therefore dependent on the position of the shut-off body between the open position and the closed position, in particular whether the shut-off body is between the open position and the intermediate position or between the intermediate position and the closed position.
  • the damping effect can be kept low by appropriate dimensioning of the secondary line between the displacement chamber and liquid power upstream of the shut-off.
  • shut-off By dimensioning the secondary line between the displacement chamber and liquid power downstream of the shut-off may have a higher damping effect for the area in which the shut-off between intermediate position and closed position is reached. Due to the increased damping effect, the closing movement of the shut-off body can be braked so that pressure surges are effectively prevented or at least significantly reduced.
  • the area between open position and intermediate position can preferably be twice as large, preferably four times larger than the area between intermediate position and closed position.
  • shut-off body is designed as a valve cone.
  • a corresponding shut-off can close a valve seat in a known manner.
  • the displacement chamber is a cavity formed by a housing and a piston guided therein, wherein the piston is preferably connected to the shut-off body by a valve stem.
  • one of the two secondary lines may be formed by a gap between the piston and the housing.
  • the other secondary line may preferably be formed by a throttle channel in the valve stem and / or shut-off.
  • the throttle channel is preferably designed for a maximum flow of 0.1 to 0.2 1 fuel per minute.
  • the fluid pressure is present upstream of the shut-off body.
  • this results in a pressure difference across the piston.
  • a pressure which is present in the liquid line upstream of the shut-off body is reduced to this opening-acting force.
  • Elements that are to secure the shut-off in the closed position can then be dimensioned smaller.
  • a so-called full hose operation can occur.
  • the connecting hose between the petrol pump and the dispensing valve is full of liquid and the delivery pump does not deliver any fuel.
  • a full hose securing can be provided, which acts on the shut-off with a force in the direction of the closed position.
  • the full-tube fuse can be designed as a magnetic tension element with two mutually displaceable, magnetically attracting components. By such a magnetic tension element of the shut-off can be kept in the closed position.
  • the holding force of the magnetic tension element In order to open the main valve, the holding force of the magnetic tension element must be overcome so that the shut-off can be moved to the open position. In the closed position can be ensured by a magnetic tension element that the main valve does not open unintentionally, especially not in full hose operation.
  • the magnetic tension element can be designed such that in the open position of the main valve it exerts no or only very little force in the closing direction on the shut-off body and / or the main valve.
  • a compression spring may be provided for the magnetic tension element, which permanently exerts force in the direction of the closed position on the shut-off body.
  • This compression spring can be configured as a full hose spring, which applies sufficient force for full hose operation. But it can also be a support spring, which applies enough force to move the shut-off in the sphere of action of the magnetic tension element. The fuse for the full hose operation is then essentially applied by the magnetic tension element.
  • the full hose securing can preferably be arranged in the displacement space. If the displacement chamber as described is formed by a housing with a piston guided therein, for example, one part of the magnetic tension element can be fastened to the piston, the other part can be fastened to the housing. Due to the mechanical connection between piston and shut-off the latter is secured in full hose operation.
  • the invention further relates to a nozzle with a main valve according to the invention.
  • a main valve for the description of the main valve, reference is made to the above statements.
  • the main valve between the inlet and outlet pipe is arranged, which together form the liquid line.
  • the secondary line of the main valve which is the displacement chamber with the liquid line upstream connects the shut-off valve, ends in the nozzle according to the invention in the inlet.
  • the other bypass which connects the displacement chamber with the liquid line downstream of the shut-off valve, terminates in the outlet tube.
  • the dispensing valve may further comprise a first automatic safety shut-off, which moves the shut-off of the main valve in the closed position, when the liquid level reaches in a container to be filled a arranged in the region of the outlet pipe level sensor. Furthermore, a second automatic safety shutdown can be provided, which moves the shut-off of the main valve in the closed position when the liquid pressure at the inlet falls below a minimum value.
  • the individual components of the dispensing valve and / or the main valve are coordinated so that when closing the main valve by an automatic safety shutdown the closing time is less than 1 s, more preferably 0.2 to 0.5 s.
  • the closing time is u.a. depending on the dimensions of the secondary lines, the ratio of the area between the open position and intermediate position to the area between intermediate position and closed position, the spring force of the closing spring for moving the shut-off in the closed position and the shape of the piston and housing in which the piston is guided.
  • the inventive dispensing valve 1 shown in the figures (colloquially also called fuel nozzle) is modular, so that different embodiments of the individual components can be combined with each other according to a modular principle. It has a valve housing 2, one with fuel inlet 3, an outlet pipe 4 and a shift lever 5. The dispensing valve 1 is connected via a connecting hose 90 with a dispensing pump comprising a fuel delivery pump (not shown).
  • a valve cartridge is arranged, which forms the main valve 10 of the dispensing valve 1.
  • the liquid flow between inlet 3 and outlet pipe 4 can be controlled.
  • the main valve 10 has a conical valve seat 11 and a check valve 12 designed as a plug. Through the shut-off body 12, the leading through the valve seat 11 liquid line 6 can be closed.
  • the shut-off body 12 is divided into two axially mutually displaceable, substantially rotationally symmetrical part body 12a and 12b, which are pressed apart by a spring 13 so that it can form an axial gap therebetween.
  • the upstream in the flow direction from the inlet 3 to the outlet 4 upstream of the main valve 10 arranged larger body part 12a can close the valve seat 11 pressure-tight.
  • valve stem 14 At the larger part body 12a of the shut-off body 12, a fixedly connected to this, coaxial valve stem 14 is provided.
  • the end of the valve stem 14 remote from the shut-off body 12 is designed as a piston 15, which is guided over a housing 16 which is stationary relative to the valve seat 12.
  • the housing 16 is arranged in the liquid line 6.
  • the piston 15 and the housing 16 form a cavity which serves as a displacement chamber 20.
  • the displacement chamber 20 is via a throttle channel 21 called secondary line 22 ', which leads through the valve stem 14 and the shut-off body 12, with the fluid line 6 downstream of the shut-off body 12 and the outlet pipe 4 fluidly connected.
  • the throttle channel 21 is designed for a fuel flow of 0.1 to 0.2 liters per minute.
  • the displacement chamber 20 is further fluidly connected to the region upstream of the shut-off body 12 and the inlet 3.
  • a seal 18 is provided, with which the secondary line 22 formed by the gap 17 is closed at least in the closed position of the shut-12. This prevents fuel from being able to pass from the inlet 3 via the secondary line 22, the displacement chamber 20 and the throttle channel 21 to the outlet pipe 4 when the main valve 10 is closed.
  • a magnetic tension member 30 is provided as a full hose assurance, which is arranged on the one hand to the upstream axial end of the piston 15 and on the other hand to the housing 16. It endeavors to pull the main valve 10 into the closed position, in which the partial body 12a of the shut-off body 12 sealingly comes into contact with the valve plug seat 11.
  • a compression spring 31 is furthermore provided which likewise presses the part body 12a of the shut-off body 12 in the direction of the closed position.
  • the magnetic tension element 30 and the compression spring 31 secure the shut-off body 12 in the closed position so that the main valve 10 remains closed in full hose operation and thus an idling of the dispensing valve, as it u.a. is required in EN 13012 is prevented.
  • Full hose operation means that the fuel pump of the dispenser no longer delivers, but the connection hose 90 between the pump and dispensing valve 1 is full of fuel.
  • the magnetic tension element 30 is designed so that the force exerted by it on the shut-off body 12 in the direction of the closed position in the open position of the shut-off 12 is not or only to a very limited extent.
  • the compression spring 31 acts in the open position of the shut-off 12 continue on this one. Compared to a main valve 10 in which the fuse for the full hose operation is done exclusively by a full hose spring, the force acting in the direction of the closed position force in the open position of the shut-off 12 is still significantly reduced, whereby the pressure drop across the main valve 10 can be reduced.
  • the shut-off body 12 of the main valve 10 may additionally be pressed by a closing spring 40 arranged downstream of the shut-off body 12 in the closed position.
  • the closing spring 40 comprises a hollow outer bulb 41, which can press against the shut-off body 12, namely the second partial body 12b, with a closing force in the direction of the closed position. The closing force is so great that the two part bodies 12a and 12b of the shut-off body 12 are compressed against the action of the spring 13 and the main valve 10 at any, pending in the inlet operating pressure completely sealed, especially if the fuel pump in the pump still promotes.
  • the closing force of the closing spring 40 is significantly greater than that exerted by the magnetic tension member 30 and the compression spring 31 in the closing direction on the main valve force.
  • the closing spring 40 and the outer piston 41 used for force transmission press the shut-off body 12 into the associated valve seat 11.
  • an inner piston 42 is arranged axially displaceable.
  • the inner piston 42 is biased by a return spring 43 in the direction of the closed position.
  • the inner piston 42 can by pressing the shift lever. 5 be moved away from the shut-off body 12 in the axial direction.
  • the shift lever bolt 44 connected to the shift lever 5 which engages in a radially extending bore or groove 45 of the inner piston 42, presses this inner piston 42 in the mentioned direction.
  • the inner piston 42 is arranged axially displaceably in the outer piston 41, however, inner piston 41 and outer piston 42 can be kinematically connected to one another by means of a locking device, so that the outer piston 41 also moves when the inner piston 42 moves.
  • This connection or locking of outer piston 41 and inner piston 42 by locking elements 46 designated as locking elements is known in the art and, for example. Describe in US 4,331,187 or DE 10 2008 010 988 B3 , In the in the Figures 2 and 3 illustrated position, the locking rollers 46 are arranged in mutually aligned recesses of the outer piston 41 and inner piston 42, that outer piston 41 and inner piston 42 are locked together and are moved together by an actuation of the shift lever 5.
  • the pump pressure at the inlet 2 during a regular refueling operation is significantly greater than the sealing pressure under the action of the magnetic tension element 30, the compression spring 31 and the differential pressure over the piston Piston 15, so that liquid or fuel can now flow at a high flow rate through the main valve 10.
  • the fueling process can be terminated by the shift lever 5 released by the user or a possible locking of the shift lever 5 is released.
  • the closing spring 40 and return spring 43 then press inner piston 42 and outer piston 41, and thus also the shut-off body 12 back into the closed position and close the main valve 10th
  • Both the first and second automatic safety shut-off 50 are based on the principle of extracting the locking rollers 46 from the grooves or recesses of the inner piston 42 and outer piston 41 and in this way to release their locking.
  • the outer bulb 41 can then snap back under the action of the closing spring 40 in the closed position and the shut-off body 12 of the main valve 10 again act on the described large closing force.
  • the inner piston 42 is due to the still drawn lever 5 initially still the shifted position.
  • the recesses for the locking rollers 46 in the inner piston 42 on the one hand and outer piston 41 on the other hand are no longer aligned with each other. Only when the shift lever 5 is released and the return spring 43 can move the inner piston 42 back to its original position, the recesses are aligned again with each other and the locking rollers 46 can optionally again inner and outer pistons 41, 42 lock together. In this way, it is ensured that after triggering one of the automatic safety shutdown 50, a refueling operation can only begin when first the shift lever 5 has been released and moved back to its rest position.
  • the first safety shutoff closes the main valve 10 by pulling out the locking rollers 46, as soon as a sensor 52 or similar. It is stated that the to be filled tank is full.
  • the details of this known from the prior art mechanism of action are described for example in DE 10 2008 010 988 B3 and require no further explanation here.
  • the second, also known from the prior art safety shutdown 50 causes that when falling below a minimum pressure in the inlet 3, the main valve 10 is automatically closed. The minimum pressure is undershot, for example, when switching off the fuel pump.
  • the locking rollers 46 are pulled out of the inner piston 42 and the outer piston 41 is pressed by the action of the closing spring 40 on the shut-off body 12 to move it to the closed position. Since, as mentioned, the spring force of the closing spring 40 to achieve the required tightness in the closed position is high, and the acceleration of the outer bulb 41 and the shut-off body 12 is high. In the prior art, the shut-off 12 impinges unrestrained on the valve seat 11, resulting in pressure surges in the nozzle and - via the liquid in the connecting hose 90 - also in the pump, especially in the fuel pump comes.
  • the displacement chamber 20 is filled in the open position of the main valve 10 with fuel.
  • the fuel can pass from the fluid line 6 into the displacement chamber 20 via the secondary line 22 formed by the gap 18 between the piston 15 and the housing 16 and / or the throttle channel 21. If the main valve 10 should now be closed by the closing spring 40 (or in another way), then the liquid must be displaced in the Verdrändungsraum 20 to its reduction from this. Since only the secondary line 22 and the throttling channel 21 are available for this purpose, clear flow resistances arise, which counteract the damping of the movement of the shut-off body 12 and brake it.
  • the stroke of the piston 15 and thus also the shut-off body 12 is in the illustrated embodiment, 5 mm between the open position (see. Fig. 4b ) and closed position (cf. Fig. 4a ). Starting from the open position, an intermediate position is provided after 4 mm along this stroke, the in Figure 4c is shown.
  • the shut-off body 12 and thus also the piston is first moved from the open position to the intermediate position.
  • the liquid can flow out of the displacement chamber 20 through the secondary line 22 and the throttle channel 21, wherein the flow can be distributed equally to the secondary line 22 and the throttle channel 21.
  • There is a damping effect which limits the acceleration or the speed with which the shut-off body moves into the closed position.
  • the seal 18 closes the secondary line 21, so that the fuel from the displacement chamber 20 can then only flow out through the throttle channel 20.
  • the flow resistance for a position of the piston 15 and the shut-off body 12 between the intermediate position and the closed position is increased compared to one between the open position and intermediate position, whereby the damping effect increases.
  • the shut-off body 12 is thus further braked, in such a way that it impinges when on the valve seat 11 causes no or only a very small surge of pressure. Nevertheless, the pressure tightness of the main valve 10 is not limited.
  • the seal 18 is to seal the gap 17 and thus the secondary line 22 soft sealing. It seals the gap 17 not only in a certain position of the piston 15 and the shut-off body 12, but in all positions within a range, namely in the range between the intermediate position and the closed position.
  • spring force of the closing spring 40 may be coordinated so that a closing of the main valve 10 by one of the two safety shutdowns 50, 51 in less than 1 s, preferably in a closing time of 0.2-0.5 s.
  • the pressure prevailing in the inlet 3 acts on the surface of the shut-off body 12, with which the valve seat 11 is closed. Since ambient pressure prevails in the outlet pipe 4 when closed, the pressure prevailing in the inlet 3 or the resulting pressure difference thus acts to open the main valve 10. However, since ambient pressure also prevails in the displacement chamber 20 due to the throttle channel 21, it acts on the shut-off body 12 facing side of the piston 15 prevailing pump pressure or the resulting pressure difference Even if the pressure difference across the piston 15 is less than via the shut-off body 12, the force acting on the shut-off body 12 due to pressure in the inlet 3 is reduced. The full hose securing and / or the closing spring 40 can be adapted to this reduced force.
  • the closing spring 40 only has to achieve the required in the standard EN 13012 base density of 3.5 bar, since any additional security is ensured by the pressure difference across the piston 15.
  • a weaker closing spring as is possible by the described pressure difference across the piston 15, the ease of use of the dispensing valve 1 increases. In particular, less force is required to operate the shift lever 5.
  • the forces to be transmitted via the locking rollers 46 between the inner and outer pistons 42, 41 are reduced, which allows smaller-sized and / or less durable - and thus more favorable - locking rollers 46. Due to the weaker closing spring 40 and the outer bulb can be made cheap plastic.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Loading And Unloading Of Fuel Tanks Or Ships (AREA)
  • Lift Valve (AREA)
  • Safety Valves (AREA)
  • Feeding And Controlling Fuel (AREA)
EP10009496.0A 2010-09-13 2010-09-13 Zapfventil Active EP2428485B1 (de)

Priority Applications (10)

Application Number Priority Date Filing Date Title
DK10009496.0T DK2428485T3 (en) 2010-09-13 2010-09-13 dispensing nozzle
EP10009496.0A EP2428485B1 (de) 2010-09-13 2010-09-13 Zapfventil
ES10009496.0T ES2454667T3 (es) 2010-09-13 2010-09-13 Válvula de suministro
PT100094960T PT2428485E (pt) 2010-09-13 2010-09-13 Válvula de distribuição
PL10009496T PL2428485T3 (pl) 2010-09-13 2010-09-13 Zawór dozujący
AU2011211357A AU2011211357B2 (en) 2010-09-13 2011-08-10 Fuel pump nozzle
NZ594538A NZ594538A (en) 2010-09-13 2011-08-11 Fuel pump nozzle with an internal displacement space connected to the liquid line by secondary lines
CN201110280142.4A CN102442629B (zh) 2010-09-13 2011-09-06 放液阀
US13/231,557 US8347924B2 (en) 2010-09-13 2011-09-13 Fuel pump nozzle
HK12103612.8A HK1163046A1 (en) 2010-09-13 2012-04-12 Fuel valve

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP10009496.0A EP2428485B1 (de) 2010-09-13 2010-09-13 Zapfventil

Publications (2)

Publication Number Publication Date
EP2428485A1 EP2428485A1 (de) 2012-03-14
EP2428485B1 true EP2428485B1 (de) 2014-01-01

Family

ID=43499950

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10009496.0A Active EP2428485B1 (de) 2010-09-13 2010-09-13 Zapfventil

Country Status (10)

Country Link
US (1) US8347924B2 (zh)
EP (1) EP2428485B1 (zh)
CN (1) CN102442629B (zh)
AU (1) AU2011211357B2 (zh)
DK (1) DK2428485T3 (zh)
ES (1) ES2454667T3 (zh)
HK (1) HK1163046A1 (zh)
NZ (1) NZ594538A (zh)
PL (1) PL2428485T3 (zh)
PT (1) PT2428485E (zh)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103539058A (zh) * 2012-07-10 2014-01-29 成都科盛石油科技有限公司 一种操作简便的加油枪
US10081532B2 (en) * 2016-02-19 2018-09-25 Opw Fueling Components, Llc Dispensing nozzle with magnetic assist
EP3369700B1 (de) * 2017-03-03 2021-07-07 ELAFLEX HIBY GmbH & Co. KG Zapfventil für zwei maximale volumenströme
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
EP4269327A1 (de) * 2022-04-29 2023-11-01 ELAFLEX HIBY GmbH & Co. KG Zapfventil

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Also Published As

Publication number Publication date
PL2428485T3 (pl) 2014-06-30
US8347924B2 (en) 2013-01-08
AU2011211357A1 (en) 2012-03-29
NZ594538A (en) 2013-02-22
PT2428485E (pt) 2014-04-03
US20120073700A1 (en) 2012-03-29
CN102442629A (zh) 2012-05-09
AU2011211357B2 (en) 2016-01-14
CN102442629B (zh) 2016-09-14
HK1163046A1 (en) 2012-09-07
ES2454667T3 (es) 2014-04-11
DK2428485T3 (en) 2014-03-17
EP2428485A1 (de) 2012-03-14

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