WO2022161596A1 - Élément de limitation de flux pour une soupape de régulation et de mise à l'atmosphère de vapeur de carburant d'un moteur à combustion interne - Google Patents

Élément de limitation de flux pour une soupape de régulation et de mise à l'atmosphère de vapeur de carburant d'un moteur à combustion interne Download PDF

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Publication number
WO2022161596A1
WO2022161596A1 PCT/EP2021/051740 EP2021051740W WO2022161596A1 WO 2022161596 A1 WO2022161596 A1 WO 2022161596A1 EP 2021051740 W EP2021051740 W EP 2021051740W WO 2022161596 A1 WO2022161596 A1 WO 2022161596A1
Authority
WO
WIPO (PCT)
Prior art keywords
flow
internal combustion
combustion engine
fuel vapor
limiting element
Prior art date
Application number
PCT/EP2021/051740
Other languages
German (de)
English (en)
Inventor
Janusz Zurke
Juri Wagner
Original Assignee
Pierburg Gmbh
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 Pierburg Gmbh filed Critical Pierburg Gmbh
Priority to DE112021006934.9T priority Critical patent/DE112021006934A5/de
Priority to PCT/EP2021/051740 priority patent/WO2022161596A1/fr
Publication of WO2022161596A1 publication Critical patent/WO2022161596A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K15/00—Arrangement in connection with fuel supply of combustion engines or other fuel consuming energy converters, e.g. fuel cells; Mounting or construction of fuel tanks
    • B60K15/03—Fuel tanks
    • B60K15/035—Fuel tanks characterised by venting means
    • B60K15/03519—Valve arrangements in the vent line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M25/00—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture
    • F02M25/08—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture adding fuel vapours drawn from engine fuel reservoir
    • F02M25/0836—Arrangement of valves controlling the admission of fuel vapour to an engine, e.g. valve being disposed between fuel tank or absorption canister and intake manifold
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/20—Excess-flow valves
    • F16K17/22—Excess-flow valves actuated by the difference of pressure between two places in the flow line
    • F16K17/24—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member
    • F16K17/28—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only

Definitions

  • the invention relates to a flow restriction element for a fuel vapor switching and ventilation valve
  • Internal combustion engine with a control body, which has a radially inner flow-around body, which can be moved into a flow channel with a nozzle-shaped section, which is formed in a flow housing part, a spring, via which the control body is loaded in a direction pointing out of the nozzle-shaped section, and a at least partially cylindrical housing wall, which is opposite a radial boundary wall of the control body.
  • Such flow restricting elements are used, for example, in fuel vapor switching and ventilation valves, which serve as shut-off and relief valves for the fuel tank. They are fluidly arranged between the vehicle's fuel tank and an activated carbon filter, which is used to absorb fuel vapors, and are intended to compensate for pressure fluctuations in the fuel tank. If there is overpressure or underpressure in the tank, the pressure should be reduced by a mechanical bypass function in the case of overpressure by ventilation to the activated carbon filter and in the case of underpressure by ventilation of the underpressure in the tank should be limited or compensated.
  • the fuel vapor switching and venting valve must be opened immediately before and during the refueling process, on the one hand to ensure that when the tank cap is opened no fuel vapors from overpressure reach the user and on the other hand that no increased pressure builds up in the tank during refueling.
  • the flow restricting elements of these valves serve to prevent overloading of the activated carbon filter.
  • the maximum flow rate to the activated charcoal filter is limited by means of the flow limitation elements to a flow rate that enables the activated charcoal filter to completely filter the fuel vapor in order to prevent fuel vapor from escaping to the outside.
  • the roll-over valves on the tank can be closed and the overpressure in the tank suddenly increases.
  • DE 10 2010 044 336 A1 describes a valve arrangement in which a switching valve can be actuated by means of an electromagnet in order to establish a connection between the tank and the activated carbon filter.
  • the valve body of this valve has a second bearing surface with which the valve body rests against the control body of a pressure relief valve, which rests spring-loaded against the valve body and thus closes a central passage in the valve body as long as there is no overpressure in the tank.
  • the valve body can be moved from the seat against a second spring element, so that the tank is ventilated.
  • an active connection and disconnection of a fluidic connection between the tank and the Activated charcoal filters are manufactured and, in addition, at defined switching points, aeration or venting are made at too high positive or negative pressures.
  • this valve it is not possible to limit the flow to a specific value, since the opening cross-section on the pressure relief valve also increases as the pressure difference increases.
  • a flow-limiting element must be made available, which is moved even when small pressure differences occur and allows a sufficient flow, and thus can be flowed through with as little pressure loss as possible.
  • DE 103 13 662 A1 proposes a flow-limiting valve in which a control body can be displaced into a nozzle-shaped section against the force of a spring if a certain pressure difference is exceeded.
  • a certain pressure difference is exceeded.
  • the switching point of the valve is too late, and there is sufficient flow, or the switching point is shifted in the direction of a lower pressure difference, which, however, leads to low flow rates.
  • the long guide surface of the valve creates increased friction, which leads to undesirably increased necessary opening forces.
  • the flow-limiting element has a control body with a radially inner flow-around body, which is arranged in a flow channel of a flow housing part. He protrudes into a nozzle-shaped Section of the flow channel and is moved out of or into the nozzle-shaped section due to an applied pressure difference and a spring force.
  • the spring force is applied by a spring, via which the control body is loaded in a direction pointing out of the nozzle-shaped section.
  • the flow-limiting element has a radial limiting wall, which is opposite a housing wall that is cylindrical at least in sections, along which the flow-limiting element is guided and moved. Due to the fact that a sealing and sliding ring is arranged on the radial boundary wall of the control body, which is arranged opposite the at least partially cylindrical housing wall and can be displaced with the control body along the at least partially cylindrical housing wall, the control body is guided in the flow housing, through which a Ease of movement is achieved, whereby the operating forces can be lower. Above all, however, the gap between the boundary wall and the cylindrical section of the housing wall is minimized, as a result of which pressure equalization between the front side and the back side of the flow-limiting element is avoided, with existing component tolerances also being compensated for.
  • section-wise cylindrical housing wall is to be understood as meaning a housing wall which, viewed in the direction of movement of the flow control element, has a cylindrical section. This is carried out in particular in the area in which the flow-limiting element with its sliding and sealing ring is arranged in a position further away from the nozzle, so that when it is actuated and displaced towards the nozzle, the said seal and increased activation force are achieved at least in the first section passed through .
  • the distance between the sliding ring and the housing wall can be increased somewhat by conical design of the housing wall in order to reduce friction in this area when the flow-limiting element is in a position that significantly narrows the nozzle.
  • the housing wall accordingly serves as a guide wall and surrounds the control body radially. Furthermore, canting of the flow-limiting element in the flow housing part is avoided by the sliding and sealing ring and instead a smooth, sliding guidance is produced.
  • the sealing and sliding ring is slotted so that the sealing and sliding ring can be inserted by simply bending it open. Furthermore, in this way springing of the sealing and sliding ring can be realized in the radial direction, whereby tolerances can be compensated for both the boundary wall and the housing wall, which also ensures the sealing effect and avoids excessive friction.
  • the slot is preferably formed obliquely, thereby minimizing axial leakage.
  • the sealing and sliding ring is made of an elastically deformable plastic, in particular polyoxymethylene.
  • an elastically deformable plastic in particular polyoxymethylene.
  • a good deformability and sealing effect can be produced and on the other hand, such a material has good sliding properties in order to reduce friction to reduce.
  • this material is inexpensive.
  • a more expensive PTFE sealing ring can also be used, which has even lower friction.
  • the sealing and slide ring is arranged in a radial groove on the radial boundary wall of the control body.
  • the sealing and sliding ring can be held in the radial groove in a form-fitting manner, additional fastening means are therefore not required, but the sealing and sliding ring can be deformed for a short time and then springs back into the radial groove due to its elasticity.
  • the radial groove is preferably delimited axially by an annular wall, the sealing and slide ring axially resting against one of the annular walls depending on the direction of movement of the control body and touching the radial housing wall radially on the outside.
  • the radial boundary wall is formed on a radially outer annular body of the control body, which is connected to the flow-around body via connecting elements between which passage openings are formed, whereby the pressure loss over the flow-limiting element is kept low and at the same time through a larger force application surface is made available to the annular body for actuation, which enables earlier switching of the flow-limiting element.
  • An axial groove is preferably formed on the annular body, into which the end of the spring resting against the annular body projects.
  • the axial groove thus serves as a contact surface for the spring, so that the flow-limiting element is loaded evenly over the circumference in the direction of the electromagnet.
  • the side walls of the axial groove prevent the spring from slipping off the ring. In this way, the flow-restriction element is held in its radial position.
  • the connecting elements are designed as webs which are formed in the circumferential direction between the passage openings on the control body and via which the annular body is fastened to the flow-around body. In this way, the largest possible flow area can be made available and a uniform flow can be achieved.
  • the flow-around body has a spherically or conically shaped flow-around surface, which is arranged opposite an inner surface of the nozzle-shaped section. This equalizes the flow to the activated carbon filter, so that an almost constant flow can be achieved for different pressure differences. Due to the gentle deflection, only a small pressure loss is generated. The flow is accelerated, resulting in a low static pressure on the underside of the flow body, which in turn results in suction.
  • passage openings are arranged at least partially radially within a flow cross section of the nozzle-shaped section of the flow channel. This arrangement of the through-openings keeps the pressure loss across the flow-limiting element low.
  • the ring body is preferably arranged radially outside of the smallest flow cross section of the nozzle-shaped section of the flow channel.
  • the annular body serves as a contact surface for an applied pressure difference or the dynamic pressure arising from the flow, it is located outside of the main flow through the flow channel, so that it causes only a small amount of pressure loss.
  • the flow-limiting element At maximum displacement of the flow-limiting element against the spring force, i.e. when the gap between the spherically or conically shaped flow area around the flow-limiting element and the inner surface of the nozzle-shaped section is minimized, the flow-limiting element lies with the annular body against the axial end of the nozzle-shaped section, which acts as a stop on the housing serves, on. This prevents the flow cross section from closing by defining a maximum possible deflection without requiring additional components.
  • the valve seat body can be made of a different material than the control body. Nevertheless, the connection is easy to establish.
  • the valve seat body has a bearing surface that extends perpendicularly to the central axis of the control body and serves as a valve seat for a valve body. This contact surface or the differential pressure acting on it ensures a passive overpressure function in addition to limiting the flow through the flow-limiting element.
  • the overpressure function is achieved by applying pressure from the tank to the bearing surface inside the valve seat, from which the flow-restricting element is correspondingly lifted as soon as the force due to the pressure difference exceeds the force of the spring.
  • a flow limiting element for a fuel vapor switching and venting valve is thus created, with which the fuel vapor can be passively discharged to the activated carbon filter if the overpressure in the tank is too high compared to the atmosphere.
  • the fuel vapor is prevented from flowing out of the tank and to the activated charcoal filter too quickly by the flow-limiting element according to the invention, which limits the flow for all pressures to a maximum flow, which corresponds to a fuel vapor flow to be absorbed or stored by the activated charcoal filter.
  • This flow rate is already achieved with low pressure differences due to the low pressure losses and the high force application surfaces made available.
  • a frictional force acting in the opposite direction is also minimized, so that the flow-limiting element can be moved even with relatively low actuation forces due to the simple and effective sliding guide. Due to the exact guidance over the circumference, tilting or an inclined position that increases friction is also avoided. Above all, however, a closed dynamic pressure area with minimized leakage is made available, as a result of which the flow forces required for actuation are reduced. This is both through an additional Force application surface on the ring body, where a dynamic pressure can build up, which is also maintained by the sliding and sealing ring, as well as achieved by the increased flow forces due to the increased volume flows on the flow body. At the same time, the manufacturing costs are reduced due to the low geometric tolerances and manufacturing tolerances that must be maintained.
  • FIG. 1 shows a side view of a fuel vapor switching and venting valve with connected components shown schematically.
  • FIG. 2 shows a side view of the fuel vapor switching and venting valve from FIG. 1 with a flow-limiting element according to the invention in a sectional view.
  • FIG. 3 shows a side view of the control body of the flow rate limiting element according to the invention in a sectional view.
  • FIG. 4 shows a perspective representation of a sealing and sliding ring of the flow-limiting element according to the invention
  • the fuel vapor switching and venting valve 10 has a first connection 12 which extends laterally from a housing 14 of the Fuel vapor switching and ventilation valve 10 protrudes and a second axial connection 16 .
  • the first lateral connection 12 is connected to a fuel tank 18 while the second axial connection 16 is connected to an activated carbon filter 20 .
  • a line leads from the activated charcoal filter 20 via a fuel vapor outlet valve 22 to the atmosphere or via a second line, in which a scavenging valve 24 is arranged, to an internal combustion engine 26, where the fuel vapors can be supplied for combustion.
  • the structure of the fuel vapor switching and venting valve 10 can be seen in FIG. It consists of an electromagnet 28, which serves as an actuator, and a coil 32 wound on a coil carrier 30, an inner core 34, an axially displaceable armature 36, and a yoke 38 radially surrounding the coil 32, and one at each axial end of the coil carrier 30 arranged yoke plate 40, which form an electromagnetic circuit.
  • This electromagnet 28 and in particular the yoke 38 is encapsulated with a plastic to form an actuator housing part 42 of the housing 14, which also forms a plug 44 and has an axial opening 48 at the end opposite the core 34, into which a sliding bushing 50 is inserted, the armature 36 leads.
  • This slide bushing 50 is made of a non-magnetizable material and is pot-shaped, with the base 52 resting against the core 34 .
  • the main guide area of the slide bushing 50 is surrounded by a soft-magnetic bushing 54 which is pressed into the return plate 40 and the coil carrier 30 .
  • the slide bushing 50 has a radial expansion 55, from which an expanded region 56 extends at its open end, which is arranged opposite to the wall surfaces of the actuator housing part 42 delimiting the opening 48, with the expanded region 56 of the slide bushing 50 and the the wall surface delimiting the opening 48 is arranged a sealing ring 58 through which a penetration of fuel vapor in the direction of the coil 32 is prevented.
  • a first flow housing part 60 is fastened to the actuator housing part 42, which forms the first connection 12 and in which a valve body 62 can be moved, which is coupled to the armature 36 by a valve rod 64 being fastened to the armature 36, to which the valve body 62 is cardanically fastened is.
  • the valve rod 64 is fastened to the armature 36 by pushing the valve rod 64 through a through hole 66 in the armature 36 until the valve rod 64 rests axially with an extension 68 against the end of the armature 36 pointing toward the valve body 62 .
  • valve rod 64 protrudes from the armature 36 at the opposite end and can be deformed there so that a type of rivet head 70 rests in a circular recess 72 on the side of the armature 36 pointing toward the core 34 .
  • the valve rod 64 also has a type of rivet head 74, which protrudes into the valve body 62, so that the valve body 62 rests against the flat end of the rivet head 74 on the armature side, for which purpose an opening 76 is formed on the valve body 62, the diameter of which is approx Substantially corresponds to the diameter of the valve rod 64.
  • the round side of the rivet head 74 is arranged opposite a projection 78 which projects radially into the interior of the valve body 62 , so that the valve body 62 can only be moved slightly axially relative to the valve rod 64 .
  • a first spring 80 biases the valve body 62 against the flat side of the rivet head 74 on the one hand and the valve body 62 with the armature 36 against a first valve seat 82 formed on the first flow housing part 60 on the other hand by the spring 80 between the valve body 62 and the Extension 55 of the bushing 50 is clamped.
  • valve body 62 rests with a first, radially outer contact surface 84, which is designed as a sealing lip of a sealing element 86, against the first valve seat 82
  • Flow opening 87 surrounds.
  • the sealing element 86 consists of an elastic material, in particular an elastomer, and is fastened to a carrier element 88, via which there is also the connection to the valve rod 64, so that the projection 78 and the opening 76 are formed on the carrier element 88.
  • the carrier element 88 largely covers the sealing element 86 in the direction of the armature 36 and also surrounds it at least partially radially.
  • the sealing element 86 also has a further second bearing surface 90 which is placed radially inside the first bearing surface 84, which is also designed as a sealing lip and is arranged axially closer to the armature 36 than the first bearing surface 84 and with which the sealing element 86 can be lowered onto a second valve seat 92.
  • This second valve seat 92 is axially movable and is formed on a flow-limiting element 94 according to the invention, which when resting on the second bearing surface 90 closes a passage opening 96 formed radially inside the second bearing surface 90 on the sealing element 86 and on the valve body 62.
  • the flow-limiting element 94 is designed in two parts and consists of a valve seat body 98, which consists of a fastening pin 97 and a bearing surface 99 which extends perpendicularly to the central axis and on which the second valve seat 92 is formed, and a control body 100 with a central blind hole 101 , into which the fastening pin 97 of the valve seat body 98 for fastening the control body 100 to the valve seat body 98 extends.
  • the control body 100 has a radially inner flow-around body 102 with a spherically shaped flow-around surface 103, which corresponds to a nozzle-shaped section 104 that is formed on an inner surface 106 of a second flow housing part 108. which is attached to the first flow housing part 60 and forms a flow channel 107 which opens out at the second, axial connection 16 .
  • the regulating body 100 has webs serving as connecting elements 110 , which extend radially outwards from the flow-around body 102 and connect the flow-through body 102 to a radially outer annular body 112 .
  • connecting elements 110 which extend radially outwards from the flow-around body 102 and connect the flow-through body 102 to a radially outer annular body 112 .
  • several passage openings 114 are formed between the connecting elements 110 and between the flow area 103 and the annular body 112 viewed in the circumferential direction.
  • the second flow housing part 108 has a radially inner, annular projection 116, on the inside of which the nozzle-shaped section 104 is formed and whose axial end serves as a stop 118 for the movement of the flow-limiting element 94, which when the annular body 112 rests against the stop 118 is only a narrow Gap 120 between the flow surface 103 and the inner surface 106 of the nozzle-shaped portion 104 releases.
  • the flow-limiting element 94 is loaded by means of a second spring 122, which is clamped between an axial groove 124 of the annular body 112 and a bearing surface 126 on the second flow housing part 108, in the direction of the valve body 62 and away from the stop 118, so that the spring 122 presses the second valve seat 92 presses against the valve body 62 and loads the flow-around body 102 from the smallest cross-section of the nozzle-shaped section 104 .
  • the annular body 112 has a radially outer boundary wall 128 which is arranged radially directly opposite a housing wall 130 of the surrounding flow housing part 60 which is cylindrical at least in sections.
  • a radial groove 132 is formed in this boundary wall 128 and is bounded axially by an annular wall 134 , 135 in each case.
  • a sealing and sliding ring 136 is arranged in the radial groove 132, which is made of polyoxymethylene, for example, and is therefore elastic and has good sliding properties.
  • this sealing and sliding ring 136 has an oblique slot 138 so that the sealing and sliding ring 136 can be bent apart for assembly in order to be inserted into the radial groove 132.
  • the sealing and sliding ring 136 then springs together again in the radial groove and is held axially by the annular walls 134, 135.
  • the control body 100 thus rests against the surrounding cylindrical housing wall 130 via the sealing and sliding ring 136 and compensates for manufacturing tolerances through its radial deformability.
  • the sealing and sliding ring 136 is used accordingly for a uniform guidance of the flow-limiting element 94 in the flow housing part 60, as a result of which frictional forces that occur are minimized and tilting of the flow-limiting element 94 is prevented.
  • valve body 62 rests on the first valve seat 82 and the second valve seat 92 and there is therefore no flow between the connections 12, 16.
  • the sealing and sliding ring 136 prevents the fuel vapor from simply flowing away from the annular body 112 by forming an obstacle to flowing away via the radially outer surface over the entire stroke of the flow-limiting element 94 .
  • the force applied by the applied pressure difference can thus be used almost entirely to move the flow rate limiting element 94, since the entire volume flow acts on the flow-around body 102 and the annular body 112, since pressure equalization via a leakage flow from the inflow side of the annular body 112 to the outflow side between the boundary wall 128 and the housing wall 130, which is cylindrical at least in sections, is prevented by the sealing and slide ring 136, which rests against the annular wall 135 facing away from the flow in the radially inner area and slides and seals on the housing wall 130, which is cylindrical in sections at least, in the radially outer area, at least as long as it is closed located in the cylindrical portion of the housing wall 130.
  • the flow through the gap 120 is changed as a function of the prevailing pressure difference, ie a larger flow cross section is made available as the pressure falls.
  • the shape of the flow body 102 keeps the pressure loss very low, so that a relatively high volume flow can be conveyed even with relatively small pressure differences.
  • the valve body 62 is lifted from the first valve seat 82, since at this pressure the pressure on the valve body 62 due to the pressure difference acting forces are greater than the spring force of the first spring 80. Accordingly, air flows from the second connection 16 through the gap 120 between the control body 100 and the nozzle-shaped section 104 and through the flow opening 87 and radially between the valve body 62 and the first valve seat 82 to the first Connection 12, so that the pressure in the tank is equalized.
  • the flow-limiting element 94 is still in contact with the second bearing surface 90 of the valve body 62 , ie it is moved in the direction of the electromagnet 28 by the second spring 122 . Furthermore, by energizing the electromagnet 28 it is possible to actively actuate the fuel vapor switching and venting valve 10 . This takes place, for example, before the refueling process is initiated, in order to ensure that there are no overpressures or underpressures in the tank 18 at this point in time. By lifting, the valve 10 is in the same state as in the case of a high vacuum in the tank 18. A flow of air from the second port 16 to the first port 12 is also possible, as is a flow of fuel vapor in the opposite direction, with the Function of the flow restriction element 94 is retained.
  • the pressure in the tank 18 caused by refueling can be reduced quickly enough.
  • a sufficient through-flow through the flow-limiting element 94 must be ensured, which is achieved by the shape of the flow-around body 102, which causes very low pressure losses.
  • the dynamic pressure surface of the annular body 112 is arranged radially outside the flow cross section of the nozzle-shaped section 104 of the flow channel 107, while the passage openings 114 are arranged radially inside this cross section.
  • a flow limiting element for a fuel vapor switching and venting valve 10 which, with very low pressure losses during operation, ensures a sufficiently high flow rate at low differential pressures in order to be able to quickly reduce overpressures in the tank, such as those that arise during the refueling process, and still have a reliable flow
  • the maximum permissible flow is limited in order to avoid overloading the activated carbon filter. Due to the reduced friction and the prevention of unwanted pressure equalization through the ring body due to leaks the deflections of the flow limitation element are reproducible. In this way, emission values can be better met.
  • the sealing and slide ring is simple and inexpensive to manufacture and assemble. It should be clear that various changes can be made compared to the embodiment without departing from the scope of the main claim.
  • the shape or structure of the flow-limiting element can also be changed.
  • the shape of the flow body can be changed.
  • the switching point can be individually adjusted with the spring and the additional dynamic pressure area provided, depending on the application. The same applies to the maximum permissible flow, which can also be adjusted by changing the design of the nozzle-shaped section.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Transportation (AREA)
  • Safety Valves (AREA)

Abstract

Des éléments de limitation de flux connu (94) pour des soupapes de commutation et de mise à l'atmosphère de vapeur de carburant (10) de moteurs à combustion interne (26) comprennent : un corps de commande (100) ayant un corps radialement interne (102) autour duquel un flux peut circuler et qui peut être déplacé dans un canal d'écoulement (107) ayant une partie en forme de buse (104) qui est formée dans une partie de boîtier d'écoulement (108) ; un ressort (122) au moyen duquel le corps de commande (100) est chargé dans une direction pointant vers l'extérieur de la partie en forme de buse (104) ; et une paroi de boîtier sensiblement cylindrique (130) qui est opposée à une paroi de délimitation radiale (128) du corps de commande (100). L'objectif de l'invention est d'assurer un flux suffisamment élevé en cas de faibles pressions différentielles et de permettre le réglage fiable d'un flux maximal. À cette fin, une bague d'étanchéité faciale (136) est disposée sur la paroi de délimitation radiale (128) du corps de commande (100), à l'opposé de la paroi de boîtier cylindrique (130) et peut se déplacer le long de la paroi de boîtier cylindrique (130) conjointement avec le corps de commande (100).
PCT/EP2021/051740 2021-01-26 2021-01-26 Élément de limitation de flux pour une soupape de régulation et de mise à l'atmosphère de vapeur de carburant d'un moteur à combustion interne WO2022161596A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112021006934.9T DE112021006934A5 (de) 2021-01-26 2021-01-26 Durchflussbegrenzungselement für ein kraftstoffdampfschalt- und -lüftungsventil einer verbrennungskraftmaschine
PCT/EP2021/051740 WO2022161596A1 (fr) 2021-01-26 2021-01-26 Élément de limitation de flux pour une soupape de régulation et de mise à l'atmosphère de vapeur de carburant d'un moteur à combustion interne

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2021/051740 WO2022161596A1 (fr) 2021-01-26 2021-01-26 Élément de limitation de flux pour une soupape de régulation et de mise à l'atmosphère de vapeur de carburant d'un moteur à combustion interne

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DE (1) DE112021006934A5 (fr)
WO (1) WO2022161596A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
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DE19542703A1 (de) * 1995-11-16 1997-05-22 Walbro Automotive Gmbh Kraftstofftankentlüftungsventil
DE202004001877U1 (de) * 2004-02-07 2004-04-15 Judo Wasseraufbereitung Gmbh Druckminderer
DE10313662A1 (de) 2003-03-26 2004-10-28 Robert Bosch Gmbh Durchflussbegrenzungsventil mit Schwingungsdämpfung
DE102010044336A1 (de) 2010-09-03 2012-03-08 A. Kayser Automotive Systems Gmbh Entlüftungsanordnung für einen Kraftstofftank
WO2015095516A2 (fr) * 2013-12-19 2015-06-25 Eaton Corporation Étrangleur à pression à régulation automatique
DE102018127810A1 (de) * 2018-11-07 2020-05-07 Pierburg Gmbh Axial durchströmbares Fluidventil
WO2020169192A1 (fr) * 2019-02-20 2020-08-27 Pierburg Gmbh Dispositif limiteur de débit pour une vanne de coupure de carburant

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19542703A1 (de) * 1995-11-16 1997-05-22 Walbro Automotive Gmbh Kraftstofftankentlüftungsventil
DE10313662A1 (de) 2003-03-26 2004-10-28 Robert Bosch Gmbh Durchflussbegrenzungsventil mit Schwingungsdämpfung
DE202004001877U1 (de) * 2004-02-07 2004-04-15 Judo Wasseraufbereitung Gmbh Druckminderer
DE102010044336A1 (de) 2010-09-03 2012-03-08 A. Kayser Automotive Systems Gmbh Entlüftungsanordnung für einen Kraftstofftank
WO2015095516A2 (fr) * 2013-12-19 2015-06-25 Eaton Corporation Étrangleur à pression à régulation automatique
DE102018127810A1 (de) * 2018-11-07 2020-05-07 Pierburg Gmbh Axial durchströmbares Fluidventil
WO2020169192A1 (fr) * 2019-02-20 2020-08-27 Pierburg Gmbh Dispositif limiteur de débit pour une vanne de coupure de carburant

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