WO2016110377A1 - Vanne anti-retour - Google Patents

Vanne anti-retour Download PDF

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Publication number
WO2016110377A1
WO2016110377A1 PCT/EP2015/079683 EP2015079683W WO2016110377A1 WO 2016110377 A1 WO2016110377 A1 WO 2016110377A1 EP 2015079683 W EP2015079683 W EP 2015079683W WO 2016110377 A1 WO2016110377 A1 WO 2016110377A1
Authority
WO
WIPO (PCT)
Prior art keywords
flap
region
check valve
housing
flow direction
Prior art date
Application number
PCT/EP2015/079683
Other languages
German (de)
English (en)
Inventor
Ondrej FRANTISEK
Thomas Jessberger
Robert Zbiral
Original Assignee
Mann+Hummel 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 Mann+Hummel Gmbh filed Critical Mann+Hummel Gmbh
Publication of WO2016110377A1 publication Critical patent/WO2016110377A1/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
    • 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
    • F16K15/033—Check valves with guided rigid valve members with a hinged closure member or with a pivoted closure member spring-loaded

Definitions

  • the present invention relates to a check valve, for example for an oil circuit of an internal combustion engine.
  • an oil circuit is used in the form of pressure circulation lubrication.
  • the oil collected in an oil sump below the crankshaft is drawn in, passed through an oil filter and conveyed to the lubrication points by means of channels.
  • wet sump lubrication there is also the so-called dry sump lubrication, in which the oil is taken from a separate container.
  • the oil pump needs for the construction of the necessary pressure in the oil circulation system energy and thus contributes to increase the consumption of the internal combustion engine.
  • a check valve is provided in the oil circuit to prevent complete emptying of the oil circuit in the oil pan.
  • the usual design of such a check valve today is a ball check valve.
  • a ball on a valve seat closes the flow of oil in the reverse direction.
  • the ball is pressed by a spring in the valve seat.
  • the ball moves away from the valve seat and opens the valve.
  • a disadvantage of this design is the reduced flow cross-section for the passage of the oil due to the presence of the ball. This results in a high pressure loss at the check valve result.
  • Comparable requirements also exist for check valves in lines for other fluids, for example for liquids such as fuels or coolant in the motor vehicle. Another requirement for check valves is a sufficiently high level of operational safety. In conventional check valves, there is always a jamming, so that the tightness in the reverse direction is insufficient.
  • the check valve for fluids of a motor vehicle has a housing which is adapted to be arranged completely within a fluid line.
  • the housing has an outer surface and an inner flow region.
  • the outer surface is connected to the inside of a fluid line so that a flow around the check valve is not possible.
  • the inner flow area comprises an inflow area and an outflow area.
  • a valve seat for a flap is provided between the inflow region and the outflow region.
  • the housing comprises a flap which is pivotably mounted on the housing about an axis of rotation between a closed position and an open position. The flap is in the closed position on the valve seat and closes the inflow area. In the open position, the flap allows flow through the check valve from the inflow region to the outflow region along a flow direction.
  • a flap designed as a check valve within a fluid line. Since the available space within such a conduit space is very limited and high reliability of the valve function must be achieved, the ball check valve construction has proven in the art. The associated disadvantages such as high pressure losses are accepted.
  • the present invention differs from the conventional construction and uses a flap as a closing element within such a line. By turning away from the usual construction, the pressure losses can be significantly reduced while high reliability can be achieved.
  • This design can be used for many liquid lines, such as in oil lines, fuel lines or in a coolant circuit.
  • a preferred embodiment of the invention provides that the pivot bearing of the flap is arranged in the outflow region. This offers the possibility of protecting the pivot bearing from high temperatures and strong pulsation surges.
  • a particularly preferred embodiment provides that the flap in the open position or the housing divides the outflow area laterally into a discharge area and edge area.
  • the term lateral is here understood to mean the direction of flow.
  • the flap In the open position, the flap extends substantially in the flow direction. Since the inner cross section of a fluid line is generally substantially circular or elliptical, in one embodiment the flap or the transition between the inflow region and the outflow region has a similar basic shape at least in sections. If the flap is pivoted in the flow direction, due to the given geometry, an edge region not covered by the main flow is created. In this edge region essential elements such as a bearing or suspension can be arranged and taken out to a certain extent from the main flow for the function of the flap.
  • this edge region is protected against thermal and mechanical stresses that are exerted by the main flow on the check valve.
  • An embodiment of the invention provides that in the region of the rotary bearing a return spring is provided, which exerts a force on the flap.
  • the return spring may be a torsion spring.
  • the force of the return spring acts on the flap such that the flap is pressed into the closed position.
  • the restoring spring is located in the edge region and, in particular, is arranged concentrically with the axis of rotation.
  • the external shape of a return spring regularly causes strong turbulence.
  • the arrangement in the edge region protected by the main flow reduces the occurrence of such turbulences and minimizes aging-relevant influences on the return spring.
  • a seal may be provided which is attached directly to the housing on the valve seat. The flap has no seal in this embodiment.
  • Such an embodiment allows the attachment of the seal between the flap and valve seat to the housing.
  • the flap is thus easier to manufacture, since no seals must be mounted. With no seal on the flap, the mass of the flap to be moved is lower during a shift so that the valve has improved responsiveness.
  • a circumferential seal For sealing the outer surface of the housing relative to the inside of a line, a circumferential seal may be provided which can be inserted as a separate component in a corresponding groove in the outer surface of the housing.
  • the housing in which the housing has the seal to the inside of the conduit and the circumferential seal for sealing the valve, the housing may be pre-assembled with the seals as a unit or the seals may be injection molded to the housing by means of multi-component injection molding.
  • a diameter in the flow direction becomes smaller in the inflow region.
  • a cross section of the inner flow region perpendicular to the flow direction has a flattening. This embodiment reduces the overall length of the check valve.
  • the axis of rotation can lie below the flattening, as seen behind the flattening and / or perpendicular to the flow direction.
  • the location of the axis of rotation of protected the mainstream, which reduces the formation of turbulence and strong age-related influences.
  • An advantageous embodiment provides that in the outflow region in a circumferential direction, the outer surface is only partially formed. In this way, the available for the main flow inner cross-section increases in the outflow area and reduces pressure losses, without affecting the stability of the check valve.
  • the inflow region is annular or tubular or, in a section transverse to the flow direction, has the shape of a circular segment or circular sector.
  • a uniform inflow of the flowing fluid can take place.
  • the inflow region and thus the entire check valve can be made shorter.
  • the flap is made in one piece, for example by plastic injection molding. An assembly of items is omitted in this embodiment and the reliability of the check valve is improved because no parts can be solved and entrained by the fluid.
  • An embodiment which is advantageous in terms of high operational reliability provides that the flap has a closure surface and the closure surface is made of an elastic material, in particular of an elastomer.
  • the closure surface may conform to the valve seat and the risk of jamming or reverse leakage is significantly minimized.
  • a joint may be provided between the closure surface and the flap.
  • the joint may be a rotary joint or a ball joint. It is thus provided in addition to the pivotal mounting of the flap, another joint that allows movement between the closure surface and the flap.
  • one or two degrees of freedom of the movement can be provided, thus enabling optimum engagement of the closure surface with the valve seat.
  • FIG. 1 shows a perspective isometric view of a first embodiment of a check valve
  • Figure 2 is a side view of the check valve of Figure 1
  • Figure 3 is a plan view of the check valve of Figure 1;
  • Figure 4 is a view opposite to the main flow direction X;
  • Figure 5 is a sectional view taken along a vertical plane through the center line;
  • FIG. 6 shows the sectional view of FIG. 5 with the flap open;
  • FIGS. FIGS. 7-12 show corresponding views for an alternative embodiment of a device according to the invention
  • FIGS. 13-18 show corresponding views for a further alternative embodiment of a non-return valve according to the invention.
  • Figure 19 is a perspective isometric view of another embodiment of a check valve against the flow direction;
  • FIG. 20 shows the view of the check valve of FIG. 19 in the flow direction;
  • Figure 21 is a side view of the check valve of Figure 19 with a flap in a closed position;
  • FIG. 22 shows the side view of FIG. 21 with the flap in an open position;
  • Figure 23 is a front view of the check valve of Figure 19 against the flow direction
  • Figure 24 is a sectional view perpendicular to the flow direction of the check valve of Figure 19;
  • Figure 25 is a perspective isometric view of the housing of the check valve of Figure 19 against the flow direction;
  • FIG. 26 shows the view of the housing of FIG. 25 in the flow direction
  • Figure 27 is an exploded perspective view of the flap of the check valve of the figure
  • FIG. 28 shows a perspective isometric view of a further embodiment of a non-return valve against the flow direction
  • Figure 29 is a side view of the check valve of Figure 28;
  • Figure 30 is a front view of the check valve of Figure 28 against the flow direction
  • Figure 31 is a sectional view taken along the flow direction of the check valve of Figure 28;
  • Figure 32 is an isometric perspective view of a key member of a flap of the check valve of Figure 28;
  • FIG. 33 is a perspective isometric view of another Kiappenbauteiis the flap of
  • Figure 34 is a bottom view of the key member of Figure 33;
  • Figure 35 is a front view of the Kiappenbauteiis of Figure 33;
  • FIG. 36 shows a perspective isometric view of a further embodiment of a check valve opposite to the flow direction;
  • Figure 37 shows the view of the check valve of Figure 36 in the flow direction;
  • Figure 38 is a perspective isometric view of a housing of the check valve of
  • FIG. 39 shows a perspective isometric view of a further embodiment of a check valve opposite to the flow direction;
  • Figure 40 shows the view of the check valve of Figure 39 in the flow direction
  • Figure 41 is a front view of the check valve of Figure 39;
  • Figure 42 is a sectional view parallel to the flow direction of the check valve of Figure 39;
  • FIG. 43 shows a perspective isometric view of a flap component of a flap of the non-return valve of FIG. 39 in the flow direction;
  • FIG. 44 shows the view of the Kiappenbauteiis of Figure 43 against the flow direction.
  • FIG. 45 is a perspective isometric view of another Kiappenbauteiis the flap of
  • Figure 46 is a side view of the further Kiappenbauteiis of Figure 45.
  • FIG. 47 is a plan view of the further Kiappenbauteiis of Figure 45th
  • FIGS. 1-6 show a first embodiment of a check valve 10 according to the invention.
  • the check valve 10 can be used in an oil circuit of an internal combustion engine.
  • the check valve 10 has a housing 12.
  • the housing 12 may be made for example by an injection molding process or other molding process.
  • a preferred embodiment results from the use of plastics such as thermoplastics.
  • the housing 12 is designed so that it can be installed in a conduit, such as an oil line in an oil circuit.
  • the check valve 10 is thereby inserted into the corresponding duct, for example, pressed.
  • the housing 12 gets in close contact with the duct.
  • the housing 12 has an outer surface 14.
  • a circumferential seal 16 may be provided for sealing the outer surface 14 with respect to the inside of a line.
  • the seal 16 can be inserted as a separate component in a corresponding groove in the outer surface 14 of the housing 12.
  • the seal 16 can be structurally integrated into the housing 12 by means of a multicomponent injection molding process ("overmolding").
  • a seal can also be dispensed with, for example with a suitable design of the tolerances of the components involved.
  • an inner flow area 18 is provided in the housing 12.
  • the inner flow region 18 can be seen clearly, in particular in FIGS. 4 to 6.
  • the inner flow region 18 has an inflow region 20, an outflow region 22 and an inner radius R.
  • Liquid, for example oil flows into the check valve 10 via the inflow region 20.
  • the liquid leaves the check valve 10 via the outflow region 22.
  • This flow defines a main flow direction X, which runs essentially along the longitudinal axis of the check valve 10.
  • a valve seat 24 is provided between the inflow region 20 and the outflow region 22, a valve seat 24 is provided.
  • the valve seat 24 serves as a stop for a flap 26 and can be seen in particular in the cross-sectional views of Figures 5 and 6 well.
  • the flap 26 is pivotally mounted about a rotation axis Y.
  • the mounting of the flap 26 has a pin 28 which is received in corresponding bearing recesses or bearing openings 30 in the outflow region 22 and in the flap 26 integrally formed bearing sleeves 32.
  • the bearing sleeves 32 are mounted on the downstream surface of the flap 26.
  • the pin 28 may be fixedly connected to the bearing sleeves 32.
  • the pivotal mounting of the flap 26 takes place in the bearing openings 30.
  • the axis of rotation Y is perpendicular to the main flow axis X, but does not cross it. Rather, the axis of rotation Y is located at least 0.5 times the inner radius R, more preferably 0.4 times the inner radius R away from the outflow direction X.
  • a torsion spring 34 is attached.
  • the torsion spring 34 engages the inner surface of the outflow region 22 and on the downstream surface of the flap 26.
  • the fastening of the spring 34 takes place on the flap 26 by means of a projection 48, in the outflow region 22 by means of a groove 50.
  • the torsion spring 34 presses the Flap 26 against the valve seat 24.
  • the pin 28 and the bearing openings 30 in the housing 12 are arranged in the outflow region 22.
  • the flap 26 also has two damping elements 36.
  • a circumferential flap seal 38 is provided on the flap 26.
  • the flap seal 38 may also be inserted into a groove or formed on the flap 26.
  • the opening and closing of the valve 10 is determined by the position of the flap 26.
  • the flap 26 rotates about the pin 28.
  • the pin 28 is in the housing 12, in particular in the bearing openings 30, inserted or pressed.
  • the torsion spring 34 presses the flap 26 against the valve seat 16 and closes the inflow region 20 with respect to the outflow region 22.
  • the flap 26 remains closed.
  • the flap 26 opens. The liquid then flows from the inflow region 20 to the outflow region 22 through the valve 10 in the direction of the main flow direction X.
  • the inflow region 20 and the outflow region 22 are formed in a streamlined manner.
  • a continuous reduction of the diameter R takes place in a direction perpendicular to the rotation axis Y without the formation of an edge or step;
  • the flow-relevant diameter increases continuously in the main flow direction. In this way, if possible, a laminar flow through the area of the valve seat and the axis of rotation and the edge area 44 remain at least partially protected from the main flow.
  • FIGS. An alternative embodiment of the check valve 10 is shown in FIGS.
  • the same reference numerals show the same or comparable features.
  • the flap 26 is attached to the valve seat 24 without a seal. This embodiment allows a more cost-effective production in the event that a not so high sealing effect is required.
  • FIGS. 13-18 show a further alternative embodiment of the check valve 10.
  • a seal 17 is provided here, which is attached directly to the housing 12 on the valve seat 24.
  • the flap 26 contains in return no seal. This embodiment allows the attaching of the seals 17 and 16 to the housing 12, optionally during a working step. The attachment of a seal on the flap 26 is eliminated.
  • FIGS. 19-27 show views of a further embodiment of a check valve 1 according to the invention.
  • the check valve 110 With regard to the basic functions of the check valve 110, reference is made to the detailed description of the preceding figures in order to avoid repetition.
  • FIGS. 19-47 The basic idea of the embodiments underlying FIGS. 19-47 is to create a possibly largest throughflow cross section and thus the lowest possible pressure loss for such a check valve.
  • the check valve 1 10 can be used for example in a fuel line.
  • the check valve 1 10 has a housing 1 12.
  • the housing 1 12 is made in the present embodiment of metal, for example made of aluminum.
  • the check valve 1 10 is inserted into a corresponding line, for example, pressed in this embodiment as well. In this case, enters an outer surface 1 14 of the housing 1 12 in close contact with the inner conduit of the line. As a result, the liquid can only flow through the interior of the check valve 110.
  • the housing 1 12 has an inner flow region, which can be divided into an inflow region 120 and an outflow region 122. Inflow region 120 and outflow region 122 are connected by a throughflow opening 121.
  • the flow opening 121 has the basic shape of a circle segment.
  • the choice of this geometry is aimed at maximizing the flow-through surface of the throughflow opening 121.
  • other geometries such as a circular sector or elliptical basic shapes with corresponding elliptical shaped segment or sector geometries are conceivable.
  • the throughflow opening 121 can be closed by a flap 126.
  • the flap 126 is located on the downstream side of the flow opening 121 and is shown in Figures 21 and 22 in two different positions. In the figure 21, the closed position of the flap 126 is shown. In Figure 22, an open position of the flap 126 is shown. When the flap 126 is opened, it pivots away from the throughflow opening 121 under the pressure of the inflowing liquid and releases the throughflow opening 121.
  • the outer surface 1 14 of the housing 1 12 is further minimized.
  • An inflow-side housing ring 1 13 carries an outer ring surface 141 which provides the seal with the surrounding pipe and which extends over the entire circumference of the housing ring 13.
  • the outflow region 122 of the housing 1 12 is only formed to less than half, in particular only a quarter or less of the circumference. This can be seen particularly well in FIGS. 19 and 23 for the present embodiment.
  • the inflow region 120 is likewise designed with the smallest possible surface area and is located in the interior of the upstream housing ring 1 13.
  • a pin 128 for the storage of a flap 126 Downstream of the flow opening 121 of the housing 1 12 a pin 128 for the storage of a flap 126 is arranged.
  • the orientation of the pin 128 is horizontal in Figure 23 and is based on the shape of the flow opening 121, in particular on the position of the flattening of the Kreisseg- element.
  • the pin 128 is substantially cylindrical in shape and has a stopper portion 1281 and a bearing portion 1282.
  • the stopper portion 1281 is integrally formed in the outflow portion 122 of the housing 1 12 and has a larger outer diameter than the bearing portion 1282 on.
  • the bearing portion 1282 of the pin 128 protrudes freely in the downstream space of the flow opening 121.
  • an axial cylindrical recess for example a bore 1283.
  • the flap 126 is mounted about the longitudinal axis of the pin 128 pivotable about a rotation axis Y.
  • a first flap element 1261 has two legs 1262, 1263 with bearing sleeves 132.
  • the legs 1263, 1263 are made of a dimensionally stable material such as plastic.
  • the bushings 132 are slid over the pin 128 for assembly and pivotally mount the flap 126 to the pin 128.
  • the inner diameter of the bushings 132 is set smaller than the diameter of the stop portion 1281 of the pin 128.
  • the bore 1283 is then crimped.
  • a cone is driven with a larger diameter than the bore 1283 in the bore 1283 and thus increases the diameter of the free end of the pin 128. This prevents the bearing sleeves 132 or the flap 126 from sliding down from the bearing section 1282 and positions the flap 126 centrally in front of the throughflow opening 121.
  • the two legs 1262, 1263 of the flap 126 connects a connecting web 1264.
  • the connecting web 1264 has an attachment point 1265 on.
  • a closure surface 1266 is fastened as the second flap element.
  • the closure surface 1266 may be made of a thermoplastic elastomer.
  • the geometry of the closure surface 1266 corresponds to the shape of the flow opening 121 and closes the flow opening 121 in the closed position of the flap 126, ie when the closure surface 1266 abuts the flow opening 121.
  • a torsion spring 134 is provided between the two legs 1262, 1263 is concentric with the pin 128 in the region of Bearing portion 1282. This is shown in particular in FIGS. 23 and 24.
  • One end 1341 of the torsion spring 134 is supported on the housing 1 12, in particular on the outflow region 122, in particular on a lower region 1221.
  • the other end 1342 exerts the spring force on the flap 126, in particular on the connecting web 1264 and presses the flap 126, in particular the closure surface 1266, against the flow opening 121.
  • the outflow region 122 has a higher material thickness in its lower region 1221.
  • the closure surface 1266 is made of an elastic material, thus adapts under the spring force to the geometry of the flow opening 121 and closes it.
  • FIGS. 28-35 show views of a further embodiment of a non-return valve 10 according to the invention.
  • the same reference numerals are used according to the embodiment of FIGS. 19-27.
  • the housing 1 12 of FIGS. 28-35 of the check valve 110 is largely identical to that of FIGS. 19-27.
  • An essential difference between the embodiment of FIGS. 28-35 and the previous embodiment is the formation of the connection between the first flap element 2261, which has the flap legs 2261, 2263, and the second flap element 2266, the closure surface 2266.
  • the flap 226 has legs 2262, 2263 with bearing openings 132, which may, for example, have sleeves. But it can also be simple openings without sleeves.
  • the flap legs 2262, 2263 have a semi-cylindrical connecting body 2264 instead of a connecting web.
  • the connecting body 2264 can be clearly seen in particular in FIG. 32 in a perspective view and in FIG. 31 in a sectional view.
  • the convex convex surface of the connecting body 2264 is oriented against the flow direction towards the flow opening 121.
  • the closure surface 2266 has a forked or mouth-shaped receptacle 2267 matching the diameter of the connecting body 2264.
  • the receptacle 2267 surrounds the semi-cylindrical connecting body 2264 between the two legs 2263, 2264 and can be snapped onto the connecting body 2264.
  • the width of the receptacle 2267 along the longitudinal axis of the connecting body 2264 is slightly smaller than the distance of the two legs 2263, 2264.
  • the closure surface 2266 can rotate about the axis of the connecting body 2264 and by means of this degree of freedom the angular position of the closing surface 2266 on the Adjust the flow opening 121 under the spring pressure.
  • the two mutually facing contact surfaces of the receptacle 2267 are not the same width.
  • the lower contact surface in FIG. 33 is narrower than the upper contact surface in order to provide an engagement surface for the spring 134, in particular for the end 1342.
  • the closure surface 2266 has two stop bodies 2268, 2269.
  • the abutment bodies 2268, 2269 restrict the range of movement of the flap 226 parallel to the axis of the pin 128 and thus prevent the closure surface 2266 from sliding back and forth relative to the legs 2163 and 2264.
  • FIGS. 36-38 show views of a further embodiment of a check valve 1 10 according to the invention.
  • the housing 1 12 of the valve 1 10 is made of a plastic.
  • the use of the plastic material makes it possible to attach the flap 126, 226 to the pin 128.
  • the free end of the bearing portion 1282 is provided with a plurality of resilient hooks 1284 which are compressed in the radial direction upon sliding of the bearing sleeves 132 and prevent the flap 126 from sliding down after springing back.
  • FIGS. 39-47 show views of a further embodiment of a check valve 1 10 according to the invention.
  • the housing 1 12 of the embodiment of Figures 39 - 47 corresponds to that of Figures 36 - 38.
  • the housing of Figures 19 - 27 or Figures 28 - 35 are used.
  • the embodiment of FIGS. 39-47 realizes a further alternative connection possibility between the flap limbs and the closure surface.
  • a ball joint is provided in this embodiment for the connection between the flap legs and the closure surface.
  • the flap 126 has a ball joint head 3267 on its closure surface 3266.
  • This has a mushroom-shaped structure.
  • the downstream surface of the ball joint head (in a sense, the hat surface of the mushroom) is essentially the cutout of a spherical surface.
  • a web 3268 is provided.
  • the connection between the two legs 1262, 1263 forms in the present embodiment, the ball joint head 3267 corresponding ball joint socket 3269.
  • This is realized by two resilient hooks 3270, 3271, which engage under the hat of the ball joint head 3267.
  • the web 3268 on the surface of the ball joint head 3267 corresponds to a web receiver 3272 of the ball joint socket 3269 and defines the maximum range of movement of the closure surface 3266 with respect to the throughflow opening 121.
  • This embodiment has the advantage that an adjustment of the closure surface 3166 with respect to the throughflow opening 121 under the spring force applied by the spring 134 to the closure surface 3266 in two degrees of freedom is possible.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Check Valves (AREA)

Abstract

L'invention concerne une vanne anti-retour (10), destinée à un moteur à combustion interne, qui comprend un boîtier (12) qui est adapté pour être disposé entièrement à l'intérieur d'un conduit de fluide, le boîtier possédant une surface extérieure (14), qui peut être reliée au côté intérieur d'un conduit de fluide de sorte qu'un écoulement autour de la vanne anti-retour est impossible, et une zone d'écoulement intérieure (18) qui comporte une zone d'entrée (20) annulaire ou tubulaire et une zone de sortie (22), un siège de vanne (24) destinée à un clapet (26) et située entre la zone d'entrée et la zone de sortie et un clapet (26) monté sur le boîtier de façon à pouvoir pivoter sur un axe de rotation (Y) entre une position fermée et une position ouverte. Dans la position fermée, le clapet est en appui sur le siège de soupape et ferme la zone d'entrée et, dans la position ouverte, il permet un écoulement à travers la vanne anti-retour.
PCT/EP2015/079683 2015-01-08 2015-12-15 Vanne anti-retour WO2016110377A1 (fr)

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Application Number Priority Date Filing Date Title
DE102015000030.6 2015-01-08
DE102015000030 2015-01-08

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019198435A1 (fr) * 2018-04-10 2019-10-17 株式会社パイオラックス Clapet de non-retour de réservoir de carburant
US11098821B1 (en) 2019-10-10 2021-08-24 Cantex International, Inc. Flapper valve

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3133898B1 (fr) * 2022-03-28 2024-02-16 Parker Hannifin Emea Sarl Dispositif pare poussière pour raccords hydrauliques

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2492271A (en) * 1946-10-11 1949-12-27 Aeroquip Corp Flapper valve
DE3838547A1 (de) * 1988-11-14 1990-05-17 Weinhold Karl Rueckschlagklappe
DE202007017181U1 (de) * 2007-12-08 2008-02-28 Norma Germany Gmbh Kupplung zum Verbinden zweier Kühlsystemabschnitte

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2492271A (en) * 1946-10-11 1949-12-27 Aeroquip Corp Flapper valve
DE3838547A1 (de) * 1988-11-14 1990-05-17 Weinhold Karl Rueckschlagklappe
DE202007017181U1 (de) * 2007-12-08 2008-02-28 Norma Germany Gmbh Kupplung zum Verbinden zweier Kühlsystemabschnitte

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019198435A1 (fr) * 2018-04-10 2019-10-17 株式会社パイオラックス Clapet de non-retour de réservoir de carburant
US11415092B2 (en) 2018-04-10 2022-08-16 Piolax, Inc. Fuel tank check valve
US11098821B1 (en) 2019-10-10 2021-08-24 Cantex International, Inc. Flapper valve

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