Classifications

• • 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
  • B60K15/03504—Fuel tanks characterised by venting means adapted to avoid loss of fuel or fuel vapour, e.g. with vapour recovery systems
• • 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
  • 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
  • F02M25/089—Layout of the fuel vapour installation
• • 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
  • F16K15/00—Check valves
  • F16K15/02—Check valves with guided rigid valve members
  • F16K15/025—Check valves with guided rigid valve members the valve being loaded by a spring
  • F16K15/026—Check valves with guided rigid valve members the valve being loaded by a spring the valve member being a movable body around which the medium flows when the valve is open
• • 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
  • F16K15/00—Check valves
  • F16K15/02—Check valves with guided rigid valve members
  • F16K15/03—Check valves with guided rigid valve members with a hinged closure member or with a pivoted closure member
  • F16K15/031—Check valves with guided rigid valve members with a hinged closure member or with a pivoted closure member the hinge being flexible
• • 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
  • F16K15/00—Check valves
  • F16K15/02—Check valves with guided rigid valve members
  • F16K15/03—Check valves with guided rigid valve members with a hinged closure member or with a pivoted closure member
  • F16K15/035—Check valves with guided rigid valve members with a hinged closure member or with a pivoted closure member with a plurality of valve members
• • 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
  • F16K15/00—Check valves
  • F16K15/14—Check valves with flexible valve members
  • F16K15/144—Check valves with flexible valve members the closure elements being fixed along all or a part of their periphery
• • 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
• • 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
  • F16K17/30—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 spring-loaded
• • 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
  • F16K17/34—Excess-flow valves in which the flow-energy of the flowing medium actuates the closing mechanism
• • 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
  • F16K21/00—Fluid-delivery valves, e.g. self-closing valves
  • F16K21/02—Fluid-delivery valves, e.g. self-closing valves providing a continuous small flow
• • 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
  • F16K24/00—Devices, e.g. valves, for venting or aerating enclosures
• • 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
  • F16K24/00—Devices, e.g. valves, for venting or aerating enclosures
  • F16K24/04—Devices, e.g. valves, for venting or aerating enclosures for venting only
• • G—PHYSICS
  • G05—CONTROLLING; REGULATING
  • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
  • G05D16/00—Control of fluid pressure
  • G05D16/04—Control of fluid pressure without auxiliary power
  • G05D16/0402—Control of fluid pressure without auxiliary power with two or more controllers mounted in series
• • G—PHYSICS
  • G05—CONTROLLING; REGULATING
  • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
  • G05D16/00—Control of fluid pressure
  • G05D16/04—Control of fluid pressure without auxiliary power
  • G05D16/06—Control of fluid pressure without auxiliary power the sensing element being a flexible membrane, yielding to pressure, e.g. diaphragm, bellows, capsule
  • G05D16/063—Control of fluid pressure without auxiliary power the sensing element being a flexible membrane, yielding to pressure, e.g. diaphragm, bellows, capsule the sensing element being a membrane
  • G05D16/0638—Control of fluid pressure without auxiliary power the sensing element being a flexible membrane, yielding to pressure, e.g. diaphragm, bellows, capsule the sensing element being a membrane characterised by the form of the obturator
  • G05D16/0641—Control of fluid pressure without auxiliary power the sensing element being a flexible membrane, yielding to pressure, e.g. diaphragm, bellows, capsule the sensing element being a membrane characterised by the form of the obturator the obturator is a membrane
• • G—PHYSICS
  • G05—CONTROLLING; REGULATING
  • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
  • G05D7/00—Control of flow
  • G05D7/01—Control of flow without auxiliary power
  • G05D7/0106—Control of flow without auxiliary power the sensing element being a flexible member, e.g. bellows, diaphragm, capsule
  • G05D7/012—Control of flow without auxiliary power the sensing element being a flexible member, e.g. bellows, diaphragm, capsule the sensing element being deformable and acting as a valve
• • G—PHYSICS
  • G05—CONTROLLING; REGULATING
  • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
  • G05D7/00—Control of flow
  • G05D7/01—Control of flow without auxiliary power
  • G05D7/0126—Control of flow without auxiliary power the sensing element being a piston or plunger associated with one or more springs
  • G05D7/0133—Control of flow without auxiliary power the sensing element being a piston or plunger associated with one or more springs within the flow-path
  • G05D7/014—Control of flow without auxiliary power the sensing element being a piston or plunger associated with one or more springs within the flow-path using sliding elements
• • G—PHYSICS
  • G05—CONTROLLING; REGULATING
  • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
  • G05D7/00—Control of flow
  • G05D7/01—Control of flow without auxiliary power
  • G05D7/0173—Control of flow without auxiliary power using pivoting sensing element acting as a valve mounted within the flow-path
• • 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
  • B60K2015/03256—Fuel tanks characterised by special valves, the mounting thereof
  • B60K2015/03269—Flap valves
• • 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
  • B60K15/03504—Fuel tanks characterised by venting means adapted to avoid loss of fuel or fuel vapour, e.g. with vapour recovery systems
  • B60K2015/03514—Fuel tanks characterised by venting means adapted to avoid loss of fuel or fuel vapour, e.g. with vapour recovery systems with vapor recovery means
• • 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
  • B60K2015/03561—Venting means working at specific times
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02D—CONTROLLING COMBUSTION ENGINES
  • F02D41/00—Electrical control of supply of combustible mixture or its constituents
  • F02D41/0025—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
  • F02D41/003—Adding fuel vapours, e.g. drawn from engine fuel reservoir
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
  • Y10T137/00—Fluid handling
  • Y10T137/7722—Line condition change responsive valves
  • Y10T137/7837—Direct response valves [i.e., check valve type]
  • Y10T137/7838—Plural

Definitions

• Ventilation flow controller for a vehicle pressure tank
• the invention relates to vehicle tanks. More particularly, the invention relates to pressurized vehicle tanks provided with a ventilation system.
• pressurized vehicle tanks such as fuel tanks
• the ventilation of pressurized vehicle tanks is a known problem which aims to strongly ventilate the pressurized tank when certain events occur, as is particularly the case for hybrid vehicles, during the passage of an operation implementing the electric motor to an operation using the heat engine or when filling the pressurized tank.
• Ventilating systems comprising valve ventilation valves for ventilating the tank when opening a downstream reservoir isolation valve are commercially available as solutions for ventilating such tanks. within a ventilation line, usually close to the canister.
• Such ventilation valves may be protection valves against a possible reversal of the vehicle or filling limit valves.
• the opening of the tank isolation valve causes the passage of the fuel system, formed by the internal volume of the tank and the portion of the internal volume of the ventilation system located downstream of the isolation valve. , from a closed state to an open state. Following this opening, a strong depressurization of the fuel system is required, characterized by a substantial flow of a gas flow, taking place from the tank to the canister. Therefore, there is a risk of clogging of the valve of the ventilation valve due to too high flow rate of the gas flow.
• a holding in the closed position of the ventilation valve can also take place when the isolation valve is opened, when a ripple of the liquid contained in the reservoir takes place following the movements of the vehicle, for example following a sudden braking .
• the valve closes during the depressurization of the tank, completely or partially, because of the chop the pressure downstream of the tank quickly becomes identical to the atmospheric pressure, while that inside the tank remains very high (all at less than the pressure at which the valve can re-open).
• This holding in the closed position of the ventilation valve prevents or makes very complicated the depressurization of the reservoir to an operating pressure, often close to atmospheric pressure.
• capping and holding in the closed position are incompatible with proper operation of the hybrid vehicle in which tank filling operations or engine fueling operations must take place quickly.
• a known solution for solving these problems of capping the ventilation valve is to integrate, within the ventilation line, a flow controller of the flow of ventilation, downstream of the ventilation valve.
• the regulator reduces peripheral access channels available for the gas flow by means of a movable member abutting against a body of the regulator at the outlet of the latter, while maintaining a central access path through the presence a duct inside the movable member.
• such a solution does not allow the regulation of the flow of gas flow once the movable member abuts against the regulator body, which does not allow optimized ventilation performance of the pressurized tank. It also does not solve the problem of reopening the valve due to the pressure difference between the pressure downstream of the regulator and its internal pressure. No commercially known solution solves this problem.
• the object of the invention is to overcome these disadvantages and to improve the ventilation performance of the pressurized tank.
• a ventilation flow regulator for a pressurized vehicle tank which comprises:
• a body having a gas inlet and a gas outlet
• At least one limiter mounted movably relative to the body so as to reduce a section of at least one path of a flow of gas from the inlet to the outlet when a flow rate of the flow at the inlet is greater than a predetermined threshold
• the regulator being arranged so that the section remains non-zero regardless of a flow rate of the flow.
• a ventilation valve provided downstream of the regulator of the invention is able to ventilate without risk of clogging by its valve, longer and at higher pressures than the same valve without such a regulator within of the ventilation line.
• This ventilation is possible thanks to a progressive and not total reduction of a section of at least one gas flow path inside the regulator, this reduction being more important than a reduction of a regulator of the art prior, which allows to ensure optimized ventilation below the capping limit of the valve, without the risk that the flow rate reaches this limit.
• the regulator is arranged so that the section remains non-zero regardless of a position of the limiter relative to the body.
• the limiter is able to reduce the section of at least one path of the flow, of by its mobility, without totally reducing this section.
• the movable limiter is not sufficiently mobile to prohibit the passage of paths to the gas flow.
• the limiter is arranged to always allow a passage, even reduced, to the gas flow, regardless of the flow rate of this flow, in an available path within the regulator.
• the limiter comprises a deformable membrane.
• the deformable membrane has a first thickness, at a first section of the deformable membrane, and a second thickness, at a second section of the deformable membrane, the first thickness and the second thickness being different.
• the deformable membrane so that it has a thickness that varies in places, so that its deformation and displacement are favored according to the gas flow.
• the deformable membrane according to this advantageous variant of the invention has at least two different thicknesses.
• the limiter comprises at least one thinned portion forming a hinge.
• the limiter can reduce the section of a path under the influence of gas flow through its articulation, regardless of the deformation of the membrane.
• the limiter has an additional possibility of reducing the section of a path.
• Such articulation also offers the possibility to the limiter to recover its initial position when the flow rate of the gas flow is reduced.
• the regulator comprises at least one limit stop for the limiter.
• the reduction of the path remains partial.
• the maximum displacement allowed is defined by the moment when the limiter bears against the stop.
• the limiter comprises several deformable membranes, these membranes being able to deform independently of each other.
• the regulation of the flow of the gas flow is further optimized. Indeed, it is possible to reduce the section of the path to multiple locations each corresponding to a deformation of one of the membranes, depending on the flow.
• the device comprises an end stop for each of the deformable membranes.
• the regulator comprises at least one window arranged to be traversed by the flow and which has an axis extending in a radial direction to a main axis of the regulator.
• the flow through the windows can be reduced, which further improves the overall regulation of the gas flow.
• the regulator comprises several windows.
• the limiter is a downstream limiter with reference to the flow and the section being a downstream section
• the regulator comprising an upstream limiter arranged to increase an upstream section of the path when a pressure differential between a pressure upstream of the regulator and a pressure downstream of the regulator is above a predetermined threshold.
• the upstream limiter when the pressure upstream of the regulator is greater than a threshold, the upstream limiter is able to increase the section of a path so as to suddenly allow the passage of a high flow rate of the gas flow. Therefore, such a regulator has the advantage of limiting the risk of overpressure upstream of the regulator.
• the regulator also has the advantage of allowing a balancing between the pressure upstream of the regulator and that downstream, due to the reduction of the upstream section of the path by the upstream limiter when the pressure differential mentioned again becomes lower than the predetermined threshold.
• the upstream limiter is arranged to prohibit the entry of the gas flow inside the regulator when the pressure differential between the pressure upstream of the regulator and the pressure downstream of the regulator is below the threshold. predetermined.
• the regulator makes it possible to ventilate over a pressure range whose minimum pressure value is the pressure necessary to move the upstream limiter so as to allow the flow of gas to pass through the inlet of the regulator.
• a pressure range whose minimum pressure value is the pressure necessary to move the upstream limiter so as to allow the flow of gas to pass through the inlet of the regulator.
• Such a possibility of ventilation over large pressure ranges for example from 35,000 to 15,000 Pascal (Pa) (from 150 to 350 mbar), is appreciated when rapid depressurization is expected so that the entire system rapidly reaches the atmospheric pressure.
• ventilation also becomes possible when a closure of the ventilation valve has occurred, for example due to a choppy movement of the liquid.
• the pressure differential quickly falls below the threshold and the upstream limiter prevents access to the regulator path, leaving the portion of the ventilation line located between the ventilation valve and the pressure regulator. closing.
• the valve of the ventilation valve opens partially and a transfer of flow is possible between the inside of the tank and the portion of the line mentioned, which it rises quickly in pressure to equal the internal pressure of the tank.
• the regulator is as close as possible to the valve of the ventilation valve, thus permitting a rise in pressure of the portion of the line mentioned up to equal the internal pressure of the tank even more rapidly, because of the reduction of the volume to pressurize this portion of the line.
• This pressure balance allows the complete reopening of the ventilation valve. Ventilation is therefore possible over the entire pressure range.
• Below the minimum pressure value of this range the ventilation of the tank must be ensured by a second ventilation valve arranged within the ventilation line following a parallel connection with respect to the flow regulator, this second ventilation valve. not likely to cork on the lower pressure range.
• a regulator equipped with an upstream limiter arranged to prevent the entry of the flow below a certain pressure differential allows the reopening of a capped ventilation valve and a ventilation of the tank over a high ventilation range only .
• the upstream limiter is arranged to increase the section of the path from a predetermined threshold greater than the threshold from which the limiter reduces this same section.
• a direct effect of the difference of these thresholds is a change in hysteresis of the closing pressure of the regulator inlet as a function of the flow rate of the incoming gas flow and the pressure differential between the pressure at the inlet and that at the inlet. at the exit of the regulator.
• Such hysteresis has the advantage of increasing the time during which ventilation is possible. As a result, the time required for complete depressurization of the tank is reduced.
• the upstream limiter comprises at least one rim arranged to reduce a section of the gas flow path, this section being located between the upstream section and the downstream section.
• the rim disposed on the upstream limiter allows the formation of a gas cushion near the section of the path which is reduced by this rim.
• the rim is arranged to direct the flow of gas so as to create turbulence or a vortex of gas to maintain a certain pressure at the inlet of the regulator so as to avoid premature closure of the regulator by the upstream limiter.
• continuous ventilation of the tank is possible.
• the upstream limiter comprises a diaphragm arranged to be stable in two positions only.
• such a diaphragm makes it possible to better control the opening and closing of the regulator inlet because of its double stability. Indeed, the diaphragm positioned in one of its stable positions completely prevents the flow of gas from entering the regulator. Once the pressure upstream of the regulator becomes too great, the diaphragm leaves this first position to adopt its second stable position corresponding to a maximum opening of the inlet. The flow of gas can follow the path that has, in this place, an open area.
• the diaphragm comprises at least one thinned portion forming a stable joint in the two positions.
• the regulator opens and closes in response to pressures in lower pressure ranges to optimize its operation.
• the diaphragm is fixed to an immobile support relative to the body.
• the diaphragm delimits with the support an enclosure in gas communication with the rest of the regulator.
• the enclosure communicates with the part of the regulator where the pressure is the lowest, because of the overall pressure drop of the regulator. This low pressure favors keeping the diaphragm open.
• the diaphragm delimits with the support an enclosure in gas communication with the regulator output.
• the gas contained in the chamber can escape, through an orifice provided in the enclosure , to the regulator output.
• This communication between the chamber and the output of the regulator allows the movements of the diaphragm without requiring compression of the gas in the enclosure.
• the two limiters are rigidly secured.
• the actions of the two limiters are synchronized which avoids the risk that one or more actions of a limiter adversely impact one or more actions of the other limiter.
• the regulator assembly is also simplified.
• the two limiters are mounted movable relative to each other.
• the regulator comprises, for the limiter or at least one of the limiters, at least one spring and / or at least one ballast.
• the limiter can return to its initial position and thus restore the initial section of the path, that is to say the section of the path before moving the limiter. this limiter.
• the limiter or at least one of the limiters comprises a slide arranged to slide along the body.
• the slider is able to close the window or one or more of the windows when sliding along the body.
• the slider when the slider is moved following the application of a force, due to the gas flow, against the latter, the slider can close the ventilation window or slots arranged along the body so as to reduce a section of the road , which makes it possible to regulate more precisely the flow rate of the flow. Indeed, the progressive movement of the slider partially closes, then completely windows according to the flow rate of the flow. Conversely, when the flow rate is less strong, the slider allows a gradual increase in the section of the path through the opening, also progressive, each of the windows previously closed by the slide.
• the invention also relates to a ventilation system of a pressurized vehicle tank.
• This ventilation system comprises at least one ventilation valve and a ventilation flow regulator according to the invention, the regulator being disposed downstream of at least one of the valves by reference to a flow of gas leaving the reservoir.
• the ventilation system comprises an additional ventilation valve arranged with respect to the flow regulator in a parallel connection.
• the regulator comprises an upstream limiter closing access to any path when the pressure differential is below the predetermined threshold, it is still possible to provide a ventilation of the gas flow contained within the reservoir, and this until the total depressurization of the latter.
• the invention also relates to a pressurized vehicle tank provided with a regulator and / or a ventilation system according to the invention.
• the reservoir is a fuel tank.
• FIG. 1 is a schematic representation of a tank equipped with a ventilation system comprising two regulators according to a first embodiment of the invention
• FIGS. 2 and 3 are schematic sectional views of one of the regulators of Figure 1;
• FIG. 4 is a representative graph of a flow / pressure profile of a ventilation valve equipped or not with one of the regulators of FIG. 1;
• FIGS. 5 and 6 are schematic sectional views of a variant of one of the regulators of Figure 1;
• FIGS. 7A, 7B and 7C are schematic sectional views of a limiter of a regulator according to the first embodiment
• FIG. 8 and 9 are schematic sectional views of a controller according to a second embodiment of the invention.
• FIG. 10 is a schematic sectional view of a portion of the regulator of FIGS. - Figure 11 is a schematic sectional view of a variant of the regulator of Figures 8 and 9;
• FIG. 12 and 13 are schematic sectional views of a controller according to a third embodiment of the invention.
• FIG. 14 is a schematic sectional view of a variant of the regulator of FIGS. 12 and 13;
• FIG. 15 is a representative graph of a flow / pressure profile of a ventilation valve equipped or not with a regulator according to the second or the third embodiment of the invention.
• FIG. 16 is a schematic representation of a tank equipped with a ventilation system incorporating a regulator according to the second or third embodiment of the invention.
• FIG. 1 illustrates, for a first embodiment of the invention, a hybrid vehicle pressurized fuel tank 4 comprising an electric motor and a heat engine fueled with fuel from said tank. These two engines are not illustrated.
• the ventilation flow regulator 1 is disposed, within a ventilation system 2 of this tank 4, downstream of a ventilation valve 3 of the tank 4 relative to the direction a flow of gas leaving the tank 4, as illustrated in FIG. 1.
• a tank isolation valve (FTIV) 5 disposed downstream of these elements, within the ventilation system 2, generally close to a canister 6, is opened in order to fill the tank 4 or to change the thermal regime of the hybrid vehicle (not shown), this opening is followed by a strong depressurization of the tank 4.
• the regulator 1 then makes it possible to regulate a ventilation rate of the flow of gas leaving the tank 4 in order to avoid clogging of the ventilation valve 3 with a valve.
• the latter forms a protection valve against a possible overturning of the vehicle (ROV) or a filling limit valve (FLW).
• the regulator 1 comprises a body 11 having a gas inlet 111 and a gas outlet 112, and a single limiter 12 mounted to move relative to the body 11.
• the limiter 12 is arranged to reduce a section of a path 13 of the gas flow from the inlet 111 to the outlet 112 when the flow rate of the flow at the inlet is greater than a predetermined threshold.
• the path 13 is delimited by the body 11 and only it. In the section, it is the limiter 12 which delimits the path 13 alone.
• the regulator 1 comprises a stop 14 provided for the limiter 12 not to reduce completely the section of the path 13. Therefore, the section of the path 13 is never completely reduced by the limiter 12, which ensures ventilation, and whatever the flow rate of the gas flow that enters the regulator 1.
• the limiter 12 comprises a single deformable membrane 121 and also has a thinned portion 122 forming an elastic articulation of this membrane 121 relative to the body 11 on one side of the membrane 121, the remainder of the membrane 121 being free.
• This thinned portion 122 is integral with the rest of the deformable membrane 121. Therefore, the limiter 12 may be deformed under the action of a flow of gas having a high flow rate and can then gradually resume its initial position at the same time. as the flow decreases.
• the deformable membrane 121 and the thinned portion 122 are two separate elements assembled to one another.
• the diaphragm 121 in the rest position, has a position that is little or not inclined with respect to a main axis X of the body 11. As the gas flow increases, this inclination is reduced until the membrane is brought closer together 121 of a configuration in which it would be perpendicular to this axis X.
• the limiter 12 comprises several deformable membranes 121, namely eight in the example, this number not being limiting, these deformable membranes 121 being able to deform independently of one another depending on the action of the gas flow.
• the membranes 121 are arranged in a circle or corolla around the axis X.
• the limiter 12 comprises a thinned portion 122 forming a hinge and a stop 14 for each of the deformable membranes 121, which allows the latter to deform each independently of all the others up to bear against their associated abutment 14 and to resume their initial position depending on the power flow of the gas flow.
• FIG. 7 Such deformation of a membrane 121 or one of the membranes 121 of the limiter 12 according to the first embodiment is illustrated in FIG. 7.
• the membrane 121 or one of the membranes 121 of the limiter 12 presents a variable thickness. Indeed, the thickness of this membrane 121 decreases progressively from the proximal end of the membrane 121, with reference to the thinned portion 122, at the distal end of the membrane, with reference to the thinned portion 122.
• the deformation of the membrane 121 is small, since the drag force of the flux on the membrane 121 is also small.
• FIG. 7B illustrates the deformation of the membrane 121 when the drag force of the flux on the membrane 121 is greater than that of FIG. 7A. This drag force increases in a non-linear manner, thus creating the inflection of the right-hand flow curve illustrated in FIG. 4.
• the restriction of the section of the path 13 is ensured by the thinned portion 122 of the limiter. 12 which, under the action of the gas flow, bears against the abutment 14.
• the regulator 1 As represented in FIGS. 8 to 11, the regulator 1 according to the second embodiment comprises an upstream limiter 1013 and a downstream limiter 1012 rigidly secured. These two limiters 1012, 1013 form a slider.
• This slider has a disk-shaped upstream wall perpendicular to the X axis and a downstream drum. It is slidably mounted relative to the body 11 in the direction of the axis X, in the body 11 and is biased by a spring 15 towards the inlet 111 of gas.
• the barrel of the slider is threaded onto a male barrel rigidly fixed to the gas outlet 112 of the body 111.
• the latter has windows 16 or openings oriented in the direction of the axis X.
• the spring 15 presses the slide so that a closed upstream plane face of the upstream wall of the slide closes the inlet 111 of gas.
• the upstream limiter 1013 When the pressure at the inlet 111 of the regulator 1 is lower than an opening pressure, the upstream limiter 1013 thus prevents any flow of gas from entering a path 13.
• the pressure increases sufficiently at the inlet of the regulator, so that the thrust force of the flow applied on the slide is greater than the force exerted by the spring 15 on the slide, the slide slides along the body 11.
• the flow of gas can then take the single path 13 peripheral of the body 11, bypassing the upstream wall.
• the sliding of the slider along the body 11 consequently closes the access to some of the ventilation windows 16 disposed near the outlet 112 of the body 11 so as to orient the flow.
• the upstream limiter 1013 comprises at the circumference of the upstream wall a cylindrical circular rim 10131 oriented toward the inlet 111 of gas.
• the rim 10131 creates a vortex gas flow acting as a gas cushion and to compensate for the return force of the spring 15, allowing access to the path 13 of more durable gas flow. In order to limit this maximum return force, it is preferable to use a spring 15 as long as possible.
• the spring 15 may be replaced by at least one ballast 17 carried by the slide, for example externally, at the junction between its wall and its shank.
• the regulator 1 must be mounted with its vertical axis X in the ventilation system 2 so that the ballast 17 performs both the function of compensating the thrust force of the incoming flow and also the closing function of the input 111 of the regulator 1 below a certain pressure.
• This variant has the advantage that the restoring force of the ballast 17 does not increase with the movement of the slider since it is constant. Indeed, this force depends only on the mass of the ballast 17 and the force of gravity which are both constant values. It is therefore easier to keep the input 111 of the regulator 1 open longer.
• the regulator 1 As represented in FIGS. 12 to 14, the regulator 1 according to the third embodiment comprises an upstream limiter 1013 and a downstream limiter 1012 mounted movable with respect to each other.
• the downstream limiter 1012 corresponds to the limiter 12 described in FIGS. 5 and 6.
• the upstream limiter 1013 comprises a diaphragm 1032 that is stable in two positions, a closed position, as illustrated in FIGS. 12 and 14, and a maximum open position, as illustrated in FIG. 13.
• the diaphragm 1032 is fixed to a stationary support 18 relative to the body 11, disposed within the body 11.
• the support 18 is flared in shape having a frustoconical intermediate section and is arranged to allow the attachment of the diaphragm 1032 at the periphery of its upstream end.
• the diaphragm 1032 has a shape of symmetry of revolution about the X axis and comprises a thinned peripheral portion 10321, connected to the support 18 and forming a stable joint in the two positions.
• the diaphragm 1032 forms with the stationary support 18 an enclosure, within which is disposed a spring 15 bearing along the axis X on the one hand on the diaphragm 1032 towards the inlet 111 of gas and secondly on the support 18 towards the outlet 112 of gas.
• the stationary support 18 has an axial orifice 181 on the outlet 112 side of the body 11, which makes it possible to regulate the pressure within the enclosure. This regulation facilitates the passage of the diaphragm 1032 from one position to another.
• ventilation windows 16 are arranged near the entrance 111 and the outlet 112 so as to direct the flow on a portion of the path 13 more important.
• a regulator according to the last two embodiments operates in the following manner for a downstream pressure of the constant regulator, generally the atmospheric pressure.
• a downstream pressure of the constant regulator generally the atmospheric pressure.
• the upstream limiter 1013 is moved under the influence of the gas flow, allowing the latter access to the path 13.
• the upstream limiter 1013 is displaced and the section of the path 13 to the input 111 of the regulator 1 is important.
• the flow of gas takes the path 13 of variable sections, due for example to the positioning of windows 16 and / or the presence of the flange 1013, until arriving at the downstream section of the path 13 controlled by the downstream limiter 1012.
• the upstream limiter 1013 can gradually return to its initial position under the spring return effect, and thereby reduce progressively the section of the path 13 to the inlet 111, until completely reduce this section, again prohibiting the entry 111 to the gas flow.
• FIG. 14 shows a variant of this embodiment in which the spring 15 is replaced by a ballast 17.
• the ballast 17 is here resting on the diaphragm 1032, inside the enclosure which it delimits with its 18.
• This variant has the same advantages as those mentioned for the variant of the second embodiment illustrated in FIG. 11.
• FIG. 15 represents a graph showing a ventilation flow curve of a valve without a regulator and a ventilation flow curve of a valve provided with a regulator 1 according to the second or the third embodiment of the invention. It can be observed that, when a ventilation valve 3 is disposed within the ventilation system 2 with this type of regulator 1 downstream, the ventilation is provided by this ventilation valve 3 over a high pressure range, for example from 35000 to 15000 Pascal (Pa) (from 350 to 150 mbar). Note that the pressure at which ventilation can begin, in this example 15000 Pa, is higher than that from which ventilation stops because of the specific arrangement of the upstream limiter 1013. This hysteresis, represented by the portion of the dashed curve, makes it possible to increase the time during which the ventilation valve 3 ventilates, which reduces the time necessary to completely depressurize the tank 4.
• Pa 15000 Pascal
• FIG. 16 which shows a reservoir 4 similar to that of FIG. 1, such a regulator 1 is mounted within the ventilation system 2, preferably downstream of a valve protecting against a possible reversal of the vehicle (ROV ) and thus allows the reopening of the valve of this valve 3 when a plugging of this valve 3 has occurred following a movement of the chop of the liquid contained in the tank 4.
• ROV reversal of the vehicle
• the ventilation of the gas contained in the tank is carried out as follows.
• the internal volume of the tank 4, as well as the line portions P1 and P2 of the ventilation system 2 are at identical pressures, namely 35000 Pa, during the plugging of the valve 3 due to the above-mentioned chop, as shown in FIG.
• the portion P2 passes very quickly to atmospheric pressure due to the fluid communication between the ventilation system 2 and the outside of the system. Consequently, the differential pressure between P1 and P2 causes the movement of the upstream limiter 1013 of the regulator 1 for a very short time necessary for the depressurization of the portion P1, which goes from 35,000 Pa to just under 15,000 Pa, pressure for which the upstream limiter 1013 closes the input 111 of the regulator 1.
• the valve of the valve 3 opens partially due to the pressure difference between the reservoir and the portion P1. Thanks to its reduced volume, the portion P1 very quickly rises to a pressure of 35000 Pa, which allows the complete reopening of the valve of the ventilation valve 3. Subsequently a ventilation of the tank 4 and the portion P1 is possible until at the closing pressure of the regulator 1, namely a little less than 15000 Pa.
• the continuation of the ventilation is provided by a second ventilation valve 3 'disposed relative to the regulator 1 according to a parallel connection.
• the regulator comprises both a spring and a ballast.
• the ventilation system comprises at least two ventilation valves connected in parallel, these two ventilation valves being both regulated by a single regulator disposed downstream of the two valves by reference to a flow of gas leaving the tank.

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• 2016
  • 2016-07-29 FR FR1657419A patent/FR3054609A1/fr active Pending
  • 2016-08-29 FR FR1658011A patent/FR3054610B1/fr active Active
• 2017
  • 2017-07-25 EP EP17740765.7A patent/EP3491229A1/fr active Pending
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