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EP1913241B1 - Soupape de regulation de pression pneumatique - Google Patents

Soupape de regulation de pression pneumatique Download PDF

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Publication number
EP1913241B1
EP1913241B1 EP06762542A EP06762542A EP1913241B1 EP 1913241 B1 EP1913241 B1 EP 1913241B1 EP 06762542 A EP06762542 A EP 06762542A EP 06762542 A EP06762542 A EP 06762542A EP 1913241 B1 EP1913241 B1 EP 1913241B1
Authority
EP
European Patent Office
Prior art keywords
diaphragm
outflow opening
regulating valve
pressure regulating
control diaphragm
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.)
Not-in-force
Application number
EP06762542A
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German (de)
English (en)
Other versions
EP1913241A1 (fr
Inventor
Uwe Dr. Meinig
Stephan Ahlborn
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.)
Ing Walter Hengst GmbH and Co KG
Original Assignee
Ing Walter Hengst GmbH and Co KG
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 Ing Walter Hengst GmbH and Co KG filed Critical Ing Walter Hengst GmbH and Co KG
Publication of EP1913241A1 publication Critical patent/EP1913241A1/fr
Application granted granted Critical
Publication of EP1913241B1 publication Critical patent/EP1913241B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M13/00—Crankcase ventilating or breathing
    • F01M13/0011—Breather valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M13/00—Crankcase ventilating or breathing
    • F01M13/0011—Breather valves
    • F01M2013/0016—Breather valves with a membrane

Definitions

  • the present invention relates to a pneumatic pressure control valve for automatic control of the pressure in the crankcase of an internal combustion engine, wherein the pressure control valve is arranged in the course of a crankcase ventilation line, the passage of which by means of the pressure control valve in dependence on the differential pressure between a reference pressure and an applied pressure at an inlet of the pressure control valve automatically variable is, is provided in the pressure control valve, a clamped in a valve housing actuating diaphragm which is acted upon on the one hand by the reference pressure and on the other hand by the gas pressure and spring force, whereby when changing the differential pressure between the adjoining the control diaphragm areas the control diaphragm is adjusted and the control diaphragm the Passage through a first, larger outflow opening and through at least one separate, spaced apart second, smaller, parallel flow-through outflow opening the pressure control valve increased or decreased, wherein at decreasing pressure at the inlet of the pressure control valve by the control diaphragm first the larger outflow opening and only then the smaller outflow opening is
  • crankcase ventilation of modern internal combustion engines the statutory and resulting As a result, the technical requirement that in the crankcase, regardless of the pressure in the intake tract of the internal combustion engine and regardless of the volume or mass flow of the crankcase ventilation gas in all operating conditions or map ranges of the internal combustion engine, taking into account a pressure drop in a usually provided ⁇ lnebelabscheider a negative pressure in a predetermined pressure range, in practice z. B. between 0 and about 30 hPa.
  • pressure control valves are predominantly used in both gasoline and diesel engines in which a function of a force acting on a control diaphragm pressure difference, a flow area of the Valve regulated and thus the crankcase pressure is maintained at a more or less constant value.
  • a high control quality and thus a high degree of independence of the crankcase pressure from the pressure in the intake tract and the flow rate of the crankcase ventilation gas results in pressure control valves with a large area ratio between the control diaphragm surface and regulated by the control diaphragm Abströmquerites from the pressure control valve.
  • a pressure control valve of the type mentioned is known.
  • the first outflow opening is a first Regelfeder and the second outflow opening assigned its own, second control spring.
  • Each control spring exerts on itself on the control diaphragm in each case an opening force acting force.
  • the first control spring should act only on a first membrane area and the second control spring act only on a second, different membrane area.
  • a disadvantage is to be considered in this known pressure control valve, that it requires a relatively large number of items, in particular two different control springs due to the use of two separate control springs. This leads to an increased, manufacturing and assembly costs.
  • Another pressure control valve is off DE 102 49 720 A1 known.
  • This pressure regulating valve is specially designed for an internal combustion engine with a turbocharger.
  • crankcase ventilation must be connected both to the intake manifold upstream of the turbocharger via a first vent line section and to the intake manifold downstream of the turbocharger via a second vent line section.
  • the pressure regulating valve described here has a valve seat cooperating with a valve body, which has a first output channel and a second output channel, wherein in each case one output channel is connected to one of the two aforementioned areas of the intake upstream or downstream of the turbocharger.
  • the second output port is concentrically disposed about the first output port.
  • a separate non-return valve is arranged in each output channel.
  • venting takes place in the intake tract upstream of the turbocharger; If the turbocharger is not in operation, the venting takes place in the area of the intake tract downstream of the turbocharger.
  • this pressure control valve therefore, depending on the turbocharger operating state, either only the first output channel or alternatively only the second output channel flows through the crankcase ventilation gas.
  • This pressure regulating valve has a valve housing, which is composed of a cup-shaped housing lower part and a housing cover.
  • the housing has an opening into the lower housing inlet and a branch opening from the lower outlet spout, whose centrally disposed within the valve housing end portion is formed as a valve seat.
  • the valve has a sealed at its edge in a groove between the housing cover and the lower housing part clamped control diaphragm, which Valve housing divided into a valve chamber and connected via a ventilation duct with the atmosphere ventilation chamber.
  • the membrane has a valve seat facing the valve end at the end of the valve. Furthermore, a compression spring is provided, which is supported on the bottom of the housing base and exerts a force on the membrane in the direction of the housing cover. Furthermore, it is essential in this pressure control valve, that between the valve plate of the diaphragm and the first valve seat on the lower housing part, an intermediate valve is arranged, which has a second valve seat, which faces the membrane and cooperates with the valve plate of the membrane.
  • the intermediate valve has a valve plate which faces the valve seat of the housing base and cooperates therewith, wherein the intermediate valve is arranged on the membrane such that an axial relative movement between the diaphragm and the intermediate valve is possible.
  • a hollow cylindrical part is arranged on the membrane, which is provided on its jacket with openings and in which the intermediate valve is arranged.
  • a further compression spring is preferably arranged between the diaphragm and the intermediate valve, which in the idle state holds open the second valve formed by the intermediate valve and the valve plate of the diaphragm.
  • the object is to provide a pressure control valve of the type mentioned above, which avoids the disadvantages set out and achieved in the case of a simple construction with few items and low assembly costs and low tolerances high control quality and reliable operation become.
  • a pressure control valve of the type mentioned which is characterized in that the control diaphragm is acted upon by a single control spring to generate the spring force, that by the single control spring, the spring force in both a cooperating with the larger outflow membrane area can also be introduced into a membrane region cooperating with the at least one smaller outflow opening, that the membrane region which interacts with the larger outflow opening is adjustable relative to the rest of the control membrane perpendicular to the membrane plane and has an area which is at most 1/5 of the total area of the control membrane, in that the adjusting membrane has an inner rolled fold around the membrane area cooperating with the larger outflow opening and that the membrane area of the adjusting membrane cooperating with the at least one smaller outflow opening is located outside the d he inner roll fold lies.
  • the pressure control valve according to the invention has the advantage of a favorable control characteristic, because the crankcase pressure at high flow rates of the crankcase ventilation gas and low pressure applied to the pressure control valve pressure differences through the large outflow opening is regulated. If there is a drop in the pressure in the crankcase, the control diaphragm initially closes against the spring force of the control spring of the pressure control valve by axially approaching the larger outlet opening. If there is then a further drop in the crankcase pressure, the control diaphragm is adjusted with further deformation of the same single control spring and deformation of the control membrane in itself so that now also narrowed the at least one smaller outlet opening in its cross section and is closed in the limit.
  • the pressure control valve according to the invention allows a compact design with a relatively small area of the control diaphragm.
  • the control diaphragm both deformable as a whole and defined in itself deformable, ie in their different, the various outflow openings assigned areas relative to each other must be adjustable, the control diaphragm around the cooperating with the larger outflow opening membrane area around an inner roll fold, wherein the cooperating with the at least one smaller discharge opening membrane region of the control diaphragm is located outside of the inner roll fold.
  • the inner roll fold provided in the control membrane ensures that an inner region of the control membrane located inside the inner roll fold and an outer region of the control membrane lying outside the inner roll fold can be adjusted relative to one another in a defined and reproducible manner, wherein the various Membrane areas do not interfere with each other in an adjustment relative to each other.
  • the roll fold can be provided to achieve the same function and equivalent means in the membrane, for example, areas of different hardness, which can be produced with two-component material, or material dilutions for targeted local increase in the flexibility of the membrane or a bellows.
  • the pressure control valve according to the invention requires only a single control spring.
  • the pressure control valve thus comes with a very small number of items, which ensures easy and cost-effective production and installation.
  • tolerances of several components subject to tolerances, such as springs unfavorably add up to an undesirably large total tolerance.
  • a preferred embodiment of the invention provides that seen in section parallel to the control diaphragm, the valve housing is round. This shape contributes to a compact design and avoids the need for a stretched or elongated valve housing which would generally be more difficult to accommodate in the area of an internal combustion engine.
  • a further development proposes that the larger outflow opening centrally in the valve housing and the smaller outflow opening is arranged eccentrically in the valve housing. This arrangement also contributes to a compact, space-saving design.
  • An alternative embodiment proposes that in addition to the larger outflow opening are provided symmetrically to and radially outside of this two or more smaller outflow openings.
  • This symmetrical arrangement has advantages, in particular with regard to the design of the control diaphragm, since in this embodiment the control diaphragm itself can also be implemented symmetrically. This simplifies and reduces the production of the control diaphragm and avoids errors in the assembly of the pressure control valve. In addition, this results in symmetrical forces acting on the control diaphragm, which is advantageous for their adjustment and deformation and thus for the function of the valve.
  • the cross-sectional area of the larger outflow opening is greater than the cross-sectional area sum of the two or more smaller outflow openings.
  • a preferred embodiment is characterized in that the at least one smaller outflow opening is bounded by a cooperating with the control diaphragm sealing surface, seen in the closing direction of the adjusting diaphragm behind a likewise cooperating with the control diaphragm, the larger outflow opening bounding sealing surface.
  • the sealing surface of the at least one smaller outflow opening preferably lies behind it by 0.2 to 1.0 mm, preferably by 0.3 to 0.6 mm, behind the sealing surface of the larger outflow opening.
  • this stage can advantageously be generated relatively accurate tool falling.
  • control diaphragm is preferably round over its surface and the inner rolled fold is preferably arranged concentrically to the central axis of the control diaphragm.
  • a further embodiment of the pressure control valve provides that the control spring on the control diaphragm initiates the spring force in an annular region which surrounds the membrane region cooperating with the larger outflow opening, while the membrane region interacting with the at least one smaller outflow opening lies outside this annular region.
  • the introduction of the spring force in the control diaphragm thus takes place here in a membrane part which is located between the cooperating with the different outflow membrane areas.
  • the spring force of the control spring reaches the various membrane areas on short, comparably long paths.
  • control spring introduces its spring force on the control diaphragm in an annular region which encloses both the membrane region cooperating with the larger outflow opening and the membrane region cooperating with the at least one smaller outflow opening.
  • ways in which the spring force of the control spring reaches the membrane areas cooperating with the various outflow openings are different long; These different lengths of way can be used specifically to let the single control spring act to varying degrees on the different membrane areas.
  • the control spring of the pressure control valve according to the invention is preferably a helical spring.
  • the control spring is a low-cost and reliable component that can be manufactured with low tolerances at low production costs.
  • the coil spring offers the possibility to initiate the spring force, as described above, in an annular region in the control diaphragm, without additional measures, which is advantageous for a symmetrical loading of the control diaphragm.
  • the control diaphragm has at least one membrane support body which is arranged radially outwardly of the inner rolled fold in or on the control diaphragm.
  • the control diaphragm With the support body, the control diaphragm can be reinforced and stiffened in desired areas in order to specifically influence the properties and function of the control diaphragm and to achieve a long durability for the purpose of the longest possible trouble-free operation.
  • the active surface of the control diaphragm is maximized by the support body, so that despite small dimensions of the pressure control valve, a good characteristic curve is achieved.
  • the membrane support body can be arranged as a separate component between the control spring and the control diaphragm and thereby preferably linked to the control diaphragm or alternatively integrally connected by injection molding with the control diaphragm and integrated into it.
  • control diaphragm near its outer region has an outer rolled fold.und with an outer edge of the membrane clamped between two interconnected Parts of the valve housing is held. Since the control diaphragm usually consists of a Elastomär- or rubber material, the desired sealing is achieved without the use of special seals by clamping at the same time.
  • the membrane support body mentioned in the preceding paragraph is preferably arranged radially between the inner and the outer roll fold.
  • equivalent means may be provided in the membrane to achieve the same function, for example, as mentioned above in connection with the inner roll fold areas of different hardness, which can be generated with two-component material, or material dilutions for targeted local increase in flexibility the membrane or a bellows.
  • the pressure control valve that the larger outflow opening and the at least one smaller outflow opening open into a common outlet of the pressure control valve.
  • the pressure control valve can be connected to the internal combustion engine via only two lines, namely an inlet leading to the inlet and a line leading away from the outlet.
  • the larger outflow opening and the at least one smaller outflow opening may each open into a separate outlet of the pressure regulating valve.
  • This embodiment may serve to apply the crankcase ventilation gas flowing out of the pressure control valve to two different portions of the intake tract of the associated internal combustion engine, e.g. in front of and behind a throttle or in front of and behind a turbocharger.
  • a development of the embodiment described above provides that in each outlet a check valve is arranged. This will produce an automatic, e.g. achieved by the pressure in each section of the intake tract dependent opening and closing of the two outlets.
  • control diaphragm occupies a defined basic position in the absence of pressure difference within the pressure control valve, a stop is expediently provided in the valve housing and / or on the control diaphragm, which limits the path of movement of the control diaphragm in the opening direction. This ensures that the control diaphragm has a certain distance from the outflow openings in its basic position.
  • a further advantageous embodiment of the pressure control valve is that a stop is preferably provided within the control diaphragm, which prevents a leading movement of the cooperating with the larger outflow diaphragm portion of the control diaphragm in the closing direction relative to the cooperating with the at least one smaller outlet opening membrane region of the control diaphragm or limited.
  • a stop is preferably provided within the control diaphragm, which prevents a leading movement of the cooperating with the larger outflow diaphragm portion of the control diaphragm in the closing direction relative to the cooperating with the at least one smaller outlet opening membrane region of the control diaphragm or limited.
  • the diaphragm region of the control diaphragm which cooperates with the larger outflow opening can only move in the closing direction together with the diaphragm region of the control diaphragm cooperating with the at least one smaller outflow opening. Only the membrane region cooperating with the at least one smaller outflow opening is able to move further in the closing direction, independently
  • this stop is formed within the setting diaphragm by a stopper disc which engages with the membrane area cooperating with the at least one smaller outflow opening on the side facing away from the outflow openings and which is arranged on the other, with the larger outflow opening.
  • the stop disc is a simple component that can be produced inexpensively and quickly and easily connected to the control diaphragm.
  • the smaller outflow opening (s) may be design as a Laval nozzle (s). If there are several smaller outlet openings, the Laval nozzles can have the same or different sizes. This ensures that at pressure differences between the inflow side of the outflow opening (s) and the intake above a certain threshold, for example about 180 hPa, in the narrowest gap, a critical pressure gradient adjusts so that the pressure drop is limited to eg about 180 hPa for the throttling at the gap between the control membrane and the / the smaller discharge opening (s) even at high pressures in the intake system.
  • a certain threshold for example about 180 hPa
  • the pressure control valve according to the invention can optionally be designed as a single unit which can be connected to an internal combustion engine or, alternatively, be integrated into a component of the internal combustion engine, for example its valve cover.
  • the individual parts of the pressure control valve except the control diaphragm and the control spring, are expedient injection molded plastic parts to allow cost-effective mass production with high accuracy.
  • the pressure control valve 1 shown here has a housing 10 which is closed on the top side with a lid 10 '. From the left, an inlet 11 opens into the housing 10. To the right goes from the housing 10, an outlet 12. Both the inlet 11 and the outlet 12 are each formed here as a pipe socket for connecting in each case a continuing, not shown here line.
  • the inlet 11 is usually connected to the crankcase of an associated internal combustion engine; the outlet 12 is usually connected to the intake tract of an internal combustion engine, not shown here.
  • control diaphragm 2 In the housing 10 is between the top and the lid 10 'a control diaphragm 2 with its membrane edge 20 sealingly clamped and held.
  • the control diaphragm 2 separates an area 13 below it in the housing 10 from an upper area 14 lying between the control diaphragm 2 and the cover 10 '.
  • the area 14 communicates with a reference pressure source via a reference pressure port 14', which in the simplest case the surrounding atmosphere can be.
  • a first, larger discharge opening 15 is arranged, which has the shape of a pipe section, the upper end face of which forms an annular sealing surface 15 '. At the lower end of the pipe section, the discharge opening 15 is connected to the outlet 12.
  • Concentric with the larger outflow opening 15 and radially outside the two smaller outflow openings 16 designed as a helical spring control spring 3 in the region 13 of the housing 10 is arranged.
  • the control spring 3 is supported with its lower end on the housing 10 and exerts with its upper end in an annular region 29 an acting in the opening direction spring force on the control diaphragm 2.
  • To secure the position of the control spring 3 relative to the control diaphragm 2 has the latter one integrated membrane support body 24, of which integrally projecting a Federzentrierring 28 downwards, which surrounds the upper end of the control spring 3.
  • the control membrane 2 is seen here in plan view circular and has two concentric rolling folds 21 and 22.
  • the roll fold 21 is arranged as an inner roll fold in a region of the control diaphragm 2, which cooperates between a membrane region 25 which cooperates with the larger outflow opening 15 and a membrane region 26, which cooperates with the two smaller outflow openings 16, is arranged.
  • the second roll fold 22 is arranged as an outer rolled fold directly radially inward from the clamping edge 20 of the control membrane 2.
  • control diaphragm 2 At its side remote from the outflow openings 15, 16 side, the control diaphragm 2 has a central, undercut projection 23 ', on which a stop plate 23 is latched.
  • the stop disc 23 extends in the radial direction outwardly beyond the inner roll fold 21 away into a region above the membrane portion 26, which cooperates with the smaller outflow openings 16.
  • stops 27 which are arranged at the top of the control diaphragm 2 in the radially outer portion immediately radially inward of the outer roll fold 22, a defined, in FIG. 1 shown position of the control diaphragm 2 causes in its open position. In this position, the stops 27 on the underside of the lid 10 'are formed on it, downwardly facing projections.
  • FIG. 1 illustrated operating state in which the control diaphragm 2 is in its upper end position, assumes the pressure control valve 1, if no pressure difference is present, ie in particular at standstill of the associated internal combustion engine.
  • the control spring 3 ensures that the control diaphragm is moved up to the start of the attacks 27 against the lid 10 'upwards or held in this position.
  • FIG. 2 shows a second operating state of the pressure regulating valve 1, which occurs when the pressure in the crankcase of the internal combustion engine drops.
  • This sinking pressure propagates through the inlet 11 into the region 13 below the control diaphragm 2 of the pressure control valve 1 and causes a force acting on the control diaphragm 2 pressure difference and thus an adjusting force.
  • the pressure difference moves against the force of the control spring 3, the control diaphragm 2 in total in the closing direction until, as in FIG. 2 shown, the central diaphragm portion 25 comes into contact with the sealing seat 15 'of the larger discharge opening 15.
  • FIG. 3 shows the pressure control valve 1 from the FIGS. 1 and 2 now in a third operating state, in, after the larger outflow opening 15 now the two smaller outflow openings 16 are closed.
  • This condition occurs when the pressure in the crankcase of the internal combustion engine drops so far that the pressure difference caused thereby now also the so far downwardly cooperating with the smaller outlet openings membrane region 26 of the control diaphragm 2 against the force of the same control spring 3, until the membrane region 26 comes into sealing contact with the sealing seats 16 'of the two smaller outflow openings 16.
  • FIG. 4 shows an enlarged view of the control diaphragm 2 in cross section as a single part. Completely outside, ie in FIG. 4 left and right, the radially outer edge of the membrane 20 is visible, which serves for sealing clamping of the control diaphragm 2 between the housing and its lid. Radially inward on the edge 20 follows the outer Roll fold 22, which serves to adjust the control diaphragm 2 in total.
  • the membrane support body 24 Radially further inward, the membrane support body 24, which is embedded in the remaining membrane 2 follows.
  • the control diaphragm 2 has upwardly projecting ribs, which form the stop 27 for the movement of the control diaphragm 2 in the opening direction, ie upwards.
  • Projecting downwardly, the membrane support body 24 has the one-piece spring centering ring 28.
  • the inner rolled fold 21 then follows, separating the central membrane region 25 from the membrane region 26 which projects radially outwards onto the roll fold 21.
  • the control membrane 2 has the central, undercut projection 23 ', on which the stop plate 23 is latched.
  • the stop disc 23 protrudes in the radial direction outwardly beyond the inner roll fold 21 away over the membrane area 26.
  • Wie die FIG. 4 illustrated the bottom of the stop plate 23 forms in its radially outer region a stop 27 'for the top 26' of the diaphragm portion 26. This ensures that the central diaphragm portion 25 relative to the radially outwardly therefrom membrane portion 26 is not leading in the axial direction leading can adjust. Rather, the central membrane region 26 can only be moved downwards in this direction together with the membrane region 26 located radially outside the inner roll fold. Conversely, however, there is the freedom that the lying radially outward of the inner roll fold 21 membrane portion 26 moves relative to the radially inner membrane portion 25 in the axial direction downwards, as already in connection with the FIG. 3 has been described.
  • Federzentrierring 28 Radially inside of Federzentrierring 28 is an annular portion 29 of the control diaphragm 2, in which the control spring not shown here rests with its upper end and exerts its upward spring force on the control diaphragm 2.
  • FIG. 5 shows the pressure control valve according to the FIGS. 1 to 3 in a longitudinal section along the section line VV in FIG. 1 , Particularly clearly shows the FIG. 5 in that the housing 10 is round and that, accordingly, the control membrane, which is not visible here, has a suitable round outline.
  • the two smaller outflow openings 16 are arranged eccentrically and at a distance, in which case each of their sealing surface 16 'faces the viewer.
  • FIG. 6 shows a modified version of the pressure control valve 1, which differs from the previously described embodiment essentially in that the example according to FIG. 6 dispensed with a stop disk in the control diaphragm 2.
  • the central part of the control diaphragm 2 here forms the diaphragm region 25, which cooperates with the central, larger outflow opening 15. Radial outwardly from this follows the inner rolled fold 21, which in turn continues radially outwardly adjoining the membrane region 26, which cooperates with the two smaller outflow openings 16.
  • Radially outermost here is the control diaphragm 2 by means of their membrane edge 20 sealingly held between the housing 10 and the lid 10 '. Inside the housing 10, the radially outer roll fold 22 lies directly radially inward from the clamping edge 20.
  • the membrane support body 24 is arranged in the control membrane 2, which stiffens this part of the membrane 2.
  • the control diaphragm 2 carries upwardly projecting ribs, which form the stop 27 for limiting the movement of the control diaphragm 2 in the opening direction.
  • the membrane support body 24 has the spring centering ring 28. Radially inwardly of this Federzentrierring 28 which also here the shape of a coil spring having control spring 3 is located at its upper end to the annular portion 29 of the control diaphragm 2 and exerts its spring force in the opening direction, ie upwards, on the control diaphragm 2.
  • FIG. 6 shown operating state of the pressure control valve 1 adjusts when there is no pressure difference across the control diaphragm 2.
  • the control spring 3 pushes the control membrane 2 in the opening direction upwards until it rests with its stop 27 on the underside of the lid 10 '.
  • FIG. 7 shows in a partial vertical section a section of a pressure control valve 1 in a further embodiment.
  • Characteristic of this embodiment is that the two smaller outflow openings 16 are each here in the form of a Laval nozzle.
  • the cross section of the two smaller outflow openings 16 is initially seen relatively small in the flow direction, and then becomes slower again after a smallest diameter.
  • the execution of the smaller outflow openings 16 as Laval nozzles offers the advantage that at pressure differences between the inflow side of the outflow openings 16, here in the region 13 of the valve housing 10, and the outlet 12, which is usually connected to the intake of an associated internal combustion engine, above a certain Limit value, in practice, for example, about 180 hPa, at the narrowest point of the discharge openings 16 sets a so-called critical pressure gradient.
  • a certain Limit value in practice, for example, about 180 hPa
  • FIG. 8 shows in the same representation as the FIG. 1 a further embodiment of the pressure control valve 1. In most parts, the pressure control valve 1 is true with the pressure control valve 1 according to the FIGS. 1 to 3 match.
  • each outlet 12, 12 ' is assigned its own non-return valve 17, 17'.
  • the check valves 17, 17 ' adjust automatically depending on the pressure conditions on the two sides of the check valve 17 and 17', so that depending on the existing pressure conditions automatic opening and closing of the outlet 12 and the outlet 12 'is effected.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Braking Systems And Boosters (AREA)
  • Fluid-Driven Valves (AREA)

Claims (21)

  1. Soupape de régulation de pression pneumatique (1) pour la régulation automatique de la pression dans le carter de vilebrequin d'un moteur à combustion interne, la soupape de régulation de pression (1) étant située sur le tracé d'une conduite de ventilation de carter de vilebrequin dont il est possible de faire varier le passage automatiquement au moyen de la soupape de régulation de pression (1) en fonction de la pression différentielle entre une pression de référence et une pression de gaz appliquée à une entrée (11) de la soupape de régulation de pression (1), une membrane de régulation (2) tendue dans un boîtier de soupape (10) étant prévue, dans la soupape de régulation de pression (1), membrane à laquelle est appliquée, d'une part, la pression de référence et, d'autre part, la pression du gaz ainsi qu'une force élastique, ce par quoi, en cas de modification de la pression différentielle entre les zones (13, 14) adjacentes à la membrane de régulation (2), la membrane de régulation (2) subit un déplacement et la membrane de régulation (2) augmente ou réduit le passage par un premier orifice d'écoulement de plus grande taille (15) et par au moins un deuxième orifice d'écoulement (16), distant du premier, de plus petite taille et permettant un écoulement parallèle, de la soupape de régulation de pression (1), tout d'abord l'orifice d'écoulement de plus grande taille (15) et seulement ensuite l'orifice d'écoulement de plus petite taille (16) pouvant être fermés par la membrane de régulation (2) lorsque la pression baisse au niveau de l'entrée (11) de la soupape de régulation de pression (1),
    caractérisée en ce que
    - la membrane de régulation (2) est soumise à un unique ressort de régulation (3) agissant dans le sens de l'ouverture pour générer la force élastique,
    - l'unique ressort de régulation (3) permet d'introduire la force élastique non seulement dans une zone de la membrane (25) qui coopère avec l'orifice d'écoulement de plus grande taille (15), mais aussi dans une zone de la membrane (26) qui coopère avec l'au moins un orifice d'écoulement de plus petite taille (16),
    - la zone de la membrane (25) qui coopère avec l'orifice d'écoulement de plus grande taille (15) peut subir un déplacement perpendiculaire au plan de la membrane relativement au reste de la membrane de régulation (2) et présente une surface qui représente au maximum 1/5 de la surface totale de la membrane de régulation (2),
    - la membrane de régulation (2) présente un pli roulé intérieur (21) tout autour de la zone de membrane (25) qui coopère avec l'orifice d'écoulement de plus grande taille (15) et
    - la zone de membrane (26) de la membrane de régulation (29) qui coopère avec l'au moins un orifice d'écoulement de plus petite taille (16) se trouve en dehors du pli roulé intérieur (21).
  2. Soupape de régulation de pression selon la revendication 1, caractérisée en ce que la zone de la membrane (25) qui coopère avec l'orifice d'écoulement de plus grande taille (15) présente une surface qui représente au maximum 1/8 de la surface totale de la membrane de réglage (2).
  3. Soupape de régulation de pression selon la revendication 1 ou 2, caractérisée en ce que, vu en coupe parallèlement à la membrane de régulation (2), le boîtier de soupape est rond.
  4. Soupape de régulation de pression selon l'une des revendications 1 à 3, caractérisée en ce que l'orifice d'écoulement de plus grande taille (15) est situé centralement dans le boîtier de soupape (10) et l'orifice d'écoulement de plus petite taille (16) est situé excentriquement dans le boîtier de soupape (10).
  5. Soupape de régulation de pression selon l'une des revendications 1 à 3, caractérisée en ce que l'orifice d'écoulement de plus grande taille (15) est situé centralement dans le boîtier de soupape (10) et en ce que sont prévus, outre l'orifice d'écoulement de plus grande taille (15), symétriquement ou radialement extérieurement par rapport à celui-ci, deux ou plusieurs orifices d'écoulement de plus petite taille (16).
  6. Soupape de régulation de pression selon la revendication 5, caractérisée en ce que la surface de la section de l'orifice d'écoulement de plus grande taille (15) est supérieure à la somme des surfaces des sections des deux ou plusieurs orifices d'écoulement de plus petite taille (16).
  7. Soupape de régulation de pression selon l'une des revendications précédentes, caractérisée en ce que l'au moins un orifice d'écoulement de plus petite taille (16) présente une surface d'étanchéité (16') qui coopère avec la membrane de régulation (2) et qui, vue dans le sens du mouvement de fermeture de la membrane de régulation (2), se trouve derrière une surface d'étanchéité (15') de l'orifice d'écoulement de plus grande taille (15), laquelle coopère également avec la membrane de régulation (2).
  8. Soupape de régulation de pression selon la revendication 7, caractérisée en ce que la surface d'étanchéité (16') de l'au moins un orifice d'écoulement de plus petite taille (16) est en retrait de 0,2 à 1,0 mm, de préférence de 0,3 à 0,6 mm derrière la surface d'étanchéité (15') de l'orifice d'écoulement de plus grande taille (15).
  9. Soupape de régulation de pression selon l'une des revendications précédentes, caractérisée en ce que la membrane de réglage (2), en vue de surface, est ronde et en ce que le pli roulé intérieur (21) est situé concentriquement par rapport à l'axe médian de la membrane de régulation (2).
  10. Soupape de régulation de pression selon l'une des revendications 1 à 9, caractérisée en ce que le ressort de régulation (3) introduit la force élastique sur la membrane de régulation (2) dans une zone annulaire (29) qui entoure la zone de la membrane (25) qui coopère avec l'orifice d'écoulement de plus grande taille (15) tandis que la zone de la membrane (26) qui coopère avec l'au moins un orifice d'écoulement de plus petite taille (16) se trouve en dehors de cette zone annulaire (29).
  11. Soupape de régulation de pression selon l'une des revendications 1 à 9, caractérisée en ce que le ressort de régulation (3) introduit la force élastique sur la membrane de régulation (2) dans une zone annulaire (29) qui entoure non seulement la zone de la membrane (25) qui coopère avec l'orifice d'écoulement de plus grande taille (15), mais aussi la zone de la membrane (26) qui coopère avec l'au moins un orifice d'écoulement de plus petite taille (16).
  12. Soupape de régulation de pression selon l'une des revendications précédentes, caractérisée en ce que le ressort de régulation (3) est un ressort hélicoïdal.
  13. Soupape de régulation de pression selon l'une des revendications précédentes, caractérisée en ce que la membrane de régulation (2) présente au moins un corps d'appui de la membrane (24) qui est situé radialement extérieurement par rapport au pli roulé intérieur (21) dans ou sur la membrane de régulation (2).
  14. Soupape de régulation de pression selon l'une des revendications précédentes, caractérisée en ce que la membrane de régulation (2) présente, à proximité de sa zone extérieure, un pli roulé extérieur (22) et est maintenue serrée, au moyen d'un bord extérieur de la membrane (20), entre deux parties du boîtier de soupape (10) reliées entre elles.
  15. Soupape de régulation de pression selon l'une des revendications 1 à 14, caractérisée en ce que l'orifice d'écoulement de plus grande taille (15) et l'au moins un orifice d'écoulement de plus petite taille (16) débouchent dans une sortie commune (12) de la soupape de régulation de pression (1).
  16. Soupape de régulation de pression selon l'une des revendications 1 à 14, caractérisée en ce que l'orifice d'écoulement de plus grande taille (15) et l'au moins un orifice d'écoulement de plus petite taille (16) débouchent chacun dans une propre sortie (12, 12') de la soupape de régulation de pression (1).
  17. Soupape de régulation de pression selon la revendication 16, caractérisée en ce qu'un clapet anti-retour (17, 17') est situé dans chaque sortie (12, 12').
  18. Soupape de régulation de pression selon l'une des revendications précédentes, caractérisée en ce qu'est prévue, dans le boîtier de soupape (10) et/ou sur la membrane de régulation (2), une butée (27) qui limite la course de la membrane de régulation (2) dans le sens de l'ouverture.
  19. Soupape de régulation de pression selon l'une des revendications précédentes, caractérisée en ce qu'est prévue, à l'intérieur de la membrane de régulation (2), une butée (27') qui empêche ou limite un mouvement vers l'avant de la zone de membrane (25) de la membrane de régulation (2), qui coopère avec l'orifice d'écoulement de plus grande taille (15), dans le sens de la fermeture de ladite zone relativement à la zone de membrane (26) de la membrane de régulation (2) qui coopère avec l'au moins un orifice d'écoulement de plus petite taille (16).
  20. Soupape de régulation de pression selon la revendication 19, caractérisée en ce que la butée (27') est constituée, à l'intérieur de la membrane de régulation (2), par un disque de butée (23) qui recouvre la zone de la membrane (26), qui coopère avec l'au moins un orifice d'écoulement de plus petite taille (16), sur le côté opposé aux orifices d'écoulement (15, 16) et est située sur l'autre zone de la membrane (25) qui coopère avec l'orifice d'écoulement de plus grande taille (15).
  21. Soupape de régulation de pression selon l'une des revendications précédentes, caractérisée en ce que l'orifice d'écoulement ou les orifices d'écoulement de plus petite taille (16) se présentent sous la forme de buse(s) de Laval.
EP06762542A 2005-08-06 2006-07-12 Soupape de regulation de pression pneumatique Not-in-force EP1913241B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202005012403U DE202005012403U1 (de) 2005-08-06 2005-08-06 Pneumatisches Druckregelventil
PCT/EP2006/006795 WO2007017033A1 (fr) 2005-08-06 2006-07-12 Soupape de regulation de pression pneumatique

Publications (2)

Publication Number Publication Date
EP1913241A1 EP1913241A1 (fr) 2008-04-23
EP1913241B1 true EP1913241B1 (fr) 2008-11-19

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EP06762542A Not-in-force EP1913241B1 (fr) 2005-08-06 2006-07-12 Soupape de regulation de pression pneumatique

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EP (1) EP1913241B1 (fr)
AT (1) ATE414843T1 (fr)
DE (2) DE202005012403U1 (fr)
WO (1) WO2007017033A1 (fr)

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CN102906379B (zh) 2010-05-13 2016-06-29 唐纳森公司 发动机曲轴箱通风过滤器组件
DE102011018980A1 (de) 2011-04-28 2012-10-31 Eagle Actuator Components Gmbh & Co. Kg Ventil zur Begrenzung des Drucks im Kurbelwellengehäuse
DE102015101886B4 (de) * 2015-02-10 2022-07-14 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Regelvorrichtung zur Gleichverteilung von Gasen und/oder Flüssigkeiten auf mindestens zwei Behälter
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DE102019202056B4 (de) * 2019-02-15 2020-09-10 Polytec Plastics Germany Gmbh & Co. Kg Druckregeleinrichtung
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Also Published As

Publication number Publication date
DE202005012403U1 (de) 2006-12-21
EP1913241A1 (fr) 2008-04-23
ATE414843T1 (de) 2008-12-15
WO2007017033A1 (fr) 2007-02-15
DE502006002141D1 (de) 2009-01-02

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