• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
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  • 优先权
    • 专利摘要:
    This element (4; 6), male or female quick coupling is intended to be connected to a pipe of fluid under pressure. It comprises a body (42; 62) defining at least one passage (441, 643, 681) of pressurized fluid, a front face and a longitudinal axis (X4; X6) of the coupling member. An inner piece (48; 64) disposed in the body is provided with a surface on the front side, and a bleed passage (482, 484; 642, 644) connecting the pressurized fluid passage and the outside the connection element. An opening mechanism (54, 56, 58, 59; 74, 76, 78, 78) is adapted to be actuated from the front of the coupling member to open the bleed passage. The inner piece (48; 64) is provided with a circumferential groove (484; 644) in which a seal (59; 79) seals the purge passage (482,484; 642,644) in a position of shutter. The opening mechanism is mounted in the inner part and comprises at least one member (58; 78) for controlling the position of the seal (59; 79) relative to the groove (484; 644), this control member being movable between a first inactive position, where it does not move the seal with respect to its closed position, and a second operative position, where it acts directly on the seal (59; 79) to open the bleed passage (482, 484, 642, 644).
    公开号:FR3046211A1
    申请号:FR1563259
    申请日:2015-12-23
    公开日:2017-06-30
    发明作者:Alain-Christophe Tiberghien；Christophe Durieux；Romain Mayer
    申请人:Staeubli Faverges SCA；
    IPC主号:
    专利说明:

    The invention relates to a male or female element of quick coupling, and a quick coupling comprising such an element. The invention relates more particularly to the quick couplings used to connect pressurized fluid lines. With a quick coupling, when connecting two pipes of pressurized fluid, a male element and a female element are pushed into one another to create a flow stream of fluid under pressure. This connection requires pushing valve valves which, in this case, belong to each of the male and female elements of the fitting. These valves are subjected to the internal pressure of each connecting element, which pressure can be significant and caused to increase in its environment, to the point of interfering with the connection maneuver, since the operator may have difficulty overcoming the problem. resistant force exerted by the pressure of the fluid inside the coupling elements against the valves. For example, for a fitting whose valve has an outside diameter of 5 mm, the force to be exerted to connect the male and female elements of the fitting, one of which is connected to a pipe at 160 bar is of the order of 330 newtons (N).
    To overcome this difficulty, it is known, for example FR-A-2,657,138 to provide a purge channel which is open, when connecting the male and female elements of the connector, by means of a member actuated from the face before the connecting element. This allows the escape of a part of the fluid present in the connection and the balancing of the pressure of the fluid inside the connection with respect to the ambient pressure. This facilitates the retreat of the movable valve flaps and makes it easier for the operator to handle.
    However, the system of FR-A-2657138 is based on the incorporation, within a central portion of a coupling, a non-return valve formed by a ball bearing on a sealing seat. Such a non-return valve is relatively bulky, which is not compatible with all sizes of connection. In particular, in some small diameter fittings, only a reduced space is available in the central part of each male or female element, which does not allow to accommodate the known mechanism. In addition, the larger the diameter of the connector, the more the valves can have extended surfaces subjected to the internal pressure of the connector and the greater the forces resistant to fitting are high. It is to these drawbacks that the invention more particularly intends to remedy by proposing a new male or female quick coupling element structure, in which a purge passage can be opened when the male and female elements of the coupling are coupled. fitting, without the need for bulky construction. For this purpose, the invention relates to a male or female quick coupling element intended to be connected to a pressurized fluid line and comprising: a body defining a fluid passage under pressure, a front face and a longitudinal axis of the connecting element; an internal part disposed in the body, which is provided with a surface belonging to the front face, as well as a purge passage connecting the passage of pressurized fluid and the outside of the connecting element; and an opening mechanism to be actuated from the front of the coupling member to selectively open the bleed passage.
    According to the invention, the inner part is equipped with a peripheral groove in which a seal rests which, in a closing portion, closes the purge passage. Moreover, the opening mechanism is mounted on the inner part and comprises at least one member for controlling the position of the seal relative to the groove, this control member being movable between a first inactive position, or it does not move. the seal relative to its closed position, and a second active position, where it acts directly on the seal to open the purge passage.
    Thanks to the invention, the activation of the opening mechanism of the purge channel makes it possible to let a quantity of fluid under pressure escape sufficient to lower the residual pressure in the internal volume of the connecting element, to the point where the pressure exerted on its valve can be easily overcome by the operator during the fitting of the male and female elements into one another. The presence of the seal in the groove of the inner part makes it possible to produce an annular sealing section within the purge passage. The control member makes it possible to create a leak at this seal, when it acts on this seal, in particular to detach the seal from the bottom of the groove against which the seal is based, that is to say say when it is in its closed position. The use of a peripheral groove and a seal provides a good compactness of the opening mechanism of the purge passage and proceeds from a simple, reliable and economical approach. It requires few structural changes compared to a conventional fitting. The invention applies equally to a male or female coupling element.
    According to advantageous but non-obligatory aspects of the invention, such a coupling element may incorporate one or more of the following features, taken in any technically permissible combination: - The coupling element comprises a pusher fixed relative to the body, a valve movable relative to the body between a position in abutment against a seat defined in part by the pusher and located on the side of the front face of the coupling element, where it closes the passage of fluid under pressure, and a position away from the seat , where it defines with the seat a section for passage of fluid under pressure, while the inner part equipped with the peripheral groove and the seal is formed either by the valve or by the pusher. - The control member is actuated, from its first inactive position to its second active position, by a piston disposed in a first housing of the inner part, movable in this housing parallel to the longitudinal axis and intended to be him - even operated from the front. - The control member is a pin disposed in a second housing of the inner part and movable radially relative to the longitudinal axis, between its first inactive position and its second active position, under the action of a cam surface of the piston. - The control member is a split ring disposed between the seal and the bottom of the groove of the inner part. - The split ring is movable between its first inactive position and its second active position, under the action of at least one pin disposed in a second housing of the inner part and itself movable radially relative to the axis longitudinal, between a first inactive position and a second active position, under the action of a cam surface of the piston. - The control member is a piston disposed in a first housing of the inner part, movable in this housing and intended to be itself actuated from the front face. - The piston is movable parallel to the longitudinal axis and defines at least a partial clearance space of the seal, in the inactive position of the piston. - The coupling element comprises means for elastic loading of the piston to a position where it does not actuate the movable member and where it can be actuated from the front face. - The purge passage comprises at least the first housing of the inner part. - The peripheral groove of the inner part is trapezoidal, semicircular or asymmetrical section. - The coupling element comprises a seal retaining member in the peripheral groove, in particular a ring secured to the inner part. - The purge passage opens on the front of the connecting element. - The control member is movable in the purge passage.
    Furthermore, the invention relates to a quick coupling for the removable connection of pressurized fluid lines, this connection comprising a male element and a female element of which at least one is as mentioned above. The invention will be better understood and other advantages thereof will appear more clearly in the light of the description which follows, of six embodiments of a coupling element and a connection according to its principle, given only by way of example and with reference to the accompanying drawings, in which: - Figure 1 is an axial section of the male and female elements of a quick coupling according to the invention, these male and female elements being themselves according to the invention and shown in decoupled configuration; FIG. 2 is an enlarged view of detail II in FIG. 1; FIG. 3 is an enlarged view of detail III in FIG. 1; FIG. 4 is a section similar to FIG. 1, when the male and female elements of the coupling are at the beginning of the coupling phase; FIG. 5 is an enlarged view of detail V in FIG. 4; - Figure 6 is a section similar to Figure 1, during a subsequent phase of the coupling of the coupling elements; - Figure 7 is a section similar to Figure 1, when the connecting elements are coupled; FIG. 8 is a partial section on a larger scale along line VIII-VIII in FIG. 7; - Figure 9 is a section similar to Figure 4 for a connection according to a second embodiment of the invention, which is in an intermediate configuration between that of Figures 4 and 6; - Figure 10 is a partial section similar to Figure 2 for a coupling element according to a third embodiment of the invention; - Figure 11 is a partial section similar to Figure 2 for a coupling element according to a fourth embodiment of the invention; - Figure 12 is a partial perspective view of the coupling member shown in Figure 11; FIG. 13 is a partial section corresponding approximately to FIG. 2 for a coupling element according to a fifth embodiment of the invention, in decoupled configuration; - Figure 14 is a partial section along the line XIV-XIV in Figure 13; - Figure 15 is a partial section similar to Figure 15, when the coupling member is supported on a complementary coupling element which is not shown; FIG. 16 is a partial section along line XVI-XVI in FIG. 15; FIG. 17 is a partial perspective view of the coupling element shown in FIGS. 13 to 16 and FIG. 18 is a partial section similar to FIG. 2 for a coupling element according to a sixth embodiment of FIG. 'invention.
    The connector 2 shown in Figures 1 to 8 comprises a male element 4 and a female element 6 complementary, each aligned on a longitudinal axis X4, respectively X6.
    In operation, the axes X4 and X6 are aligned on a common axis X2 which constitutes the longitudinal axis of the connector 2. In operation, the elements 4 and 6 are each connected to a pressurized fluid line C4 or C6 respectively. For clarity of the drawing, these lines C4 and C6 are shown in phantom only in Figure 1. The male element 4 comprises a body 42 which defines the axis X4 and which is formed of two parts 422 and 424 screwed the one on the other. Inside the body 42 is a valve 44 which is resiliently loaded by a spring 46 in the direction of the front face 4A of the male element 4.
    The front face of a coupling element is the face of this element which is turned towards the complementary element during the coupling of the male and female elements of the coupling. The front face may comprise all the front faces of the parts facing the complementary element which are contained or not in the same plane. The front face of a fitting is opposed to the pipe at the end of which is mounted the fitting. The front face of a male or female connector is therefore provided for the cooperation of the coupling element with a corresponding female or male coupling element. Inside the body 42 is also arranged a pusher 48, which is fixed relative to the body 42 and surrounded by the valve 46. The pusher 48 thus forms an internal part for the male connector element 6.
    The body 42 defines a front surface 42A, annular, perpendicular to the axis X4 and which belongs to the front face 4A. In the same way, the valve 44 defines an annular front surface 44A perpendicular to the axis X4 and which belongs to the front face 4A, whereas the pusher 48 defines an annular front surface 48A, perpendicular to the axis X4 and which belongs to the front panel 4A. The surfaces 42A, 44A and 48A are concentric, the surface 42A surrounding the surfaces 44A and 48A, while the surface 44A surrounds the surface 48A.
    In the closed configuration of the connecting element 4, shown in FIGS. 1 and 2, the valve 46 bears against two seats respectively formed by the internal radial surface 426 of the body 42 and the external radial surface 486 of the pusher 48 situated on the side of the front face 4A of the male connector element 4. The surfaces 426 and 486 are each provided with a groove 428, respectively 488, in which is disposed an O-ring 50, respectively 52. In the closed configuration of the element 4, the O-rings 50 and 52 are respectively in abutment against the outer radial surface 462 and against the inner radial surface 464 of the valve 46. This ensures sealing at the closure of the connecting element 4. The internal volume V4 of the connecting element 4 is then isolated from the outside.
    Furthermore, a piston 54 is disposed in a central recess 482 of the pusher 48, this housing 482 being aligned on the axis X4 and opening on the front surface 48A. 54A is the front face of the piston 54 which is arranged in the center of the front face 4A. The piston 54 is provided with a peripheral groove 542 with asymmetrical section. On the side of the front face 4A, the groove 542 is flared and delimited by a surface 5422 which diverges from the axis X4 in approaching the surface 48A. In other words, the surface 5422 is frustoconical, centered on the axis X4 and converges opposite the front face 4A. Opposite this front face 4A, the groove 542 is delimited by a surface 5424 which is annular and perpendicular to the axis X4.
    A spring 56 is disposed between the piston 54 and the bottom of the housing 482, being compressed by the piston 54 that pushes elastically towards the front face 4A. The housing 482 is a blind hole centered on the axis X4 and which opens at the center of the surface 48A. The housing 482 constitutes a first housing formed in the pusher 48 and belongs to a purge passage of the male connector element 4, defined below.
    A pin 58 is engaged in the groove 542 and constitutes a stop means which opposes the ejection of the piston 54 from the housing 482 by the spring 56.
    Furthermore, the pusher 48 is provided with a peripheral groove 484 in which is disposed an elastomer O-ring 59, whose diameter is selected so that it rests against the bottom of the groove 484. By default, a bore 485 connects the bottom of the groove 484 and the housing 482. The pin 58 is disposed in this bore 485. In other words, the bore 485 constitutes a housing for receiving the pin 58, which protrudes radially towards the axis X4 in the housing 482. This bore 485 constitutes a second housing formed in the pusher 48 and also belongs to the purge passage of the male coupling element 4. In the configuration of FIGS. 1 and 2, the seal 59 exerts a centripetal force on the pin 58 and rests against the bottom of the groove 484, so that it opposes the flow of fluid under pressure to the outside of the coupling element 4. The female coupling element 6 comprises a body 62 which is formed of three s 622, 623 and 624 parts screwed one on the other, namely a front portion 622, an intermediate portion 623 and a rear portion 624. A valve 64 is movably mounted inside the body 62 being loaded to the front face 6A of the element 6 by a spring 66. The valve 64 thus forms an internal part for the female coupling element 6. A pusher 68 radially surrounds the valve 64 and its inner radial surface 686 defines a seat, the side of the front face 6A of the female connector element 6 intended to cooperate with the valve 64. In the example, the pusher 68 is integral with the intermediate portion 623 of the body 62. Other configurations are possible.
    An auxiliary shutter 67 is installed radially between the front portion 622 of the body 62 and the pusher 68. This auxiliary shutter 67 is subjected to the action of a spring 69 which pushes it towards the front face 6A of the 6. This allows to retain in position, in holes 625 of the body 62, a series of balls 61 which serve to lock the elements 4 and 6 in coupled configuration.
    Furthermore, a ring 63 is mounted axially movable around the body 62, being subjected to the action of a return spring 65 which pushes it towards the front face 6A. The ring 63 makes it possible to control the displacement of the balls 61, in a manner known per se.
    The elements 63, 62, 67, 68 and 64 are each provided with an annular surface 63A, 62A, 67A, 68A and 64A, perpendicular to the axis X6 and which defines a portion of the front face 6A of the connection 6.
    The valve 64 is provided with a housing formed in the form of a blind central bore 642 centered on the axis X6 and which opens on the surface 64A. This bore is a first housing arranged in the valve 64 and belongs to a purge passage of the female connector element, defined below. A piston 74 is slidably mounted in this housing 642 and subjected to an elastic force exerted by a spring 76. Note 74A the front face of the piston 74 which is disposed in the center of the front face 6A. A pin 78 is engaged in a peripheral groove 742 of the piston 74, which is bordered by a flared frustoconical surface 7422 which diverges towards the front face 6A and by a surface 7424 perpendicular to the axis X6.
    The pin 78 passes through a bore 645 which opens into a groove 644 formed around the valve 64 and in which an O-ring 79 is installed. The bore 645 constitutes a second housing provided in the valve 64 and also belongs to the bleed passage of the The seal 79 rests against the bottom of the groove 644 by default, so that it opposes the flow of pressurized fluid outwardly from the connecting member 6.
    In a plane perpendicular to the axis X4, respectively to the axis X6, the grooves 484 and 644 are circular in shape.
    Parts 74, 76, 78 and 79 are respectively identical to parts 54, 56, 58 and 59. However, this is not mandatory.
    The external peripheral surface 646 of the valve 64 is equipped with a groove 648 in which is disposed an O-ring 72 which seals the female connector element 6 in a closed configuration, at the interface between the valve 64 and the This isolates the internal volume V6 of the connecting member 6 from the outside.
    In the configuration of Figures 1 and 3, the pistons 54 and 74 each protrude from the corresponding front face 4A or 6A over an axial distance d4, respectively d6, measured parallel to the axis X4 or X6 and which is non-zero. Thus, the pistons 54 and 74 can be actuated by an operator, each from the front face 4A or 6A of the connecting element 4 or 6 to which they belong, by exerting on them, with the aid of a common tool or complementary element respectively 6 or 4, a force having at least one axial component directed rearwardly of the coupling element.
    In the example of the figures, the distances d4 and d6 are identical. This is not mandatory.
    When the front faces 4A and 6A of the male and female elements 4 and 6 are brought into contact with each other, as shown in FIGS. 4 and 5, the pistons 54 and 74 are pushed towards the inside of the housings 482 and 642, respectively against the elastic forces exerted by the springs 56 and 76, towards the bottom of the housings 482 and 642. This recoil movement of the pistons has the effect of axially moving the grooves 484 and 644 opposite the front faces 4A and 6A, that is to say towards the bottom of the housings 482 and 642, which moves the frustoconical surfaces 5422 and 7422 in contact with the pins 58 and 78 which are then pushed radially outwards, that is to say, away from the axis X2, which is then confused with the axes X4 and X6. The pins 58 and 78 are thus ejected from the grooves 542 and 742 and bear respectively against the outer radial surfaces 544 and 744 of the pistons 54 and 74 between these grooves and the front faces 54A and 74A of the pistons 54 and 74. The axial position of the pins 58 and 78 with respect to the front faces 4A and 6A remains unchanged during their radial radial displacement relative to the axis X2.
    The piston surfaces 5422 and 7422 each represent a cam surface along the axis X4 and X6. The action of the cam surfaces 5422 and 7422 of the pistons 54 and 74 on the pins 58 and 78 causes their centrifugal radial displacement relative to the axis X2, which produces a direct action on the seal 59 or 79. This centrifugal displacement pins 58 and 78 has the effect of detaching O-rings 59 and 79 relative to the bottoms of the grooves 484 and 644.
    In the coupling element 4, this creates a leak around the pin 58, through the bore 485. More specifically, pressurized fluid which is in the internal volume V4 of the male coupling element 4, in particular between the Pusher 48 and the valve 44, can flow into the groove 484, into the bore 485 and thence into the housing 482 around the piston 54 and up to the front face 4A, as represented by the arrows F4.
    In the same way, inside the connecting element 6, fluid present in the internal volume V6, in particular between the valve 64 and the pusher 68, can flow into the groove 644 around the pin 78 at in the bore 645 and thence inside the housing 642 around the pin 74 and up to the front face 6A, as represented by the arrows F6.
    These two flows then open at the interface between the two connecting elements 4 and 6, between the front faces 4A and 6A, from which they flow towards the outside of the connection 2, as represented by the arrows F2.
    In other words, a purge passage is created in the connecting element 4, by joining the volumes of the groove 484, the bore 485 and the housing 482. This purge passage connects the internal volume V4 to the face before 4A. It is closed by the seal 59 in the configuration of Figures 1 and 2. In the configuration of Figures 4 and 5, it is opened by the pin 58 which acts directly on the seal 59 to take off the bottom of the groove 484. Here , the adverb "directly" means that the pin 58 is in contact with the seal 59 and exerts a mechanical force on it without interposition of an intermediate piece.
    In the same way, a purge passage is created in the female coupling element 6, by the joining of the volumes of the groove 644 of the bore 645 and the housing 642. This purge passage connects the internal volume V6 to the front face 6A. It is closed by the seal 79 in the configuration of FIGS. 1 and 3. It is open thanks to the action of the pin 79 in the configuration of FIGS. 4 and 5. Here again, the pin 78 acts directly on the seal 79.
    The continued fitting of the male 4 and female 6 elements one into the other allows to reach the configuration of Figure 6, where the pusher 48 has separated the valve 64 of the seat formed by the internal radial surface 686 of the push 68 by pushing against the elastic force exerted by the spring 66, while the pusher 68 has pushed the valve 44 against the elastic force exerted by the spring 46. The fluid communication between the respective internal volumes V4 and V6 of the connecting elements 4 and 6 is not yet established, insofar as the O-ring 52 bears against the internal radial surface of the pusher 68. In this configuration, the body 42 has also pushed back the auxiliary shutter 67 towards the inside of the body 62, against the elastic force exerted by the spring 69. The balls 61 then bear against the outer radial surface 421 of the body 42.
    The balls 61 remain engaged in an internal radial groove 632 of the ring 63, as in the configuration of FIGS. 1 to 5.
    The continuation of the fitting movement makes it possible to reach the coupled configuration of FIGS. 7 and 8.
    In this configuration, the front portion of the pusher 48, which is equipped with the grooves 484 and 488, has passed the front portion of the pusher 68 which has the smaller inside diameter, so that the O-ring 52 is no longer in contact. with the internal radial surface 686 of the pusher 68. This is done by further pushing the valve 64 against the elastic force exerted by the spring 66, on the one hand, and by pushing the valve 44 against the elastic force exerted by the spring 46, on the other hand.
    This makes it possible to create fluid communication between the respective internal volumes V4 and V6 of the elements 4 and 6 of the coupling through the passage section formed between the pusher 68 and the valve 64, and through the passage section formed between the pusher 48. and the valve 44. In the example of the figures, it is considered that the female connector element 6 is connected to a source of pressurized fluid while the male connector element 4 is connected to a load that consumes this fluid, so that the flow of pressurized fluid takes place from right to left in FIG. 7, as represented by the arrows F. These arrows show that the internal volume of each connecting element 4 or 6 defines a fluid passage under pressure. In the coupling element 4, the pressurized fluid passage comprises a central bore 481 of the pusher 48, channels 483 formed in this pusher and which are diverging in the direction of the face 4A and a central bore 441 of the valve 44. the connecting element 6, the pressurized fluid passage comprises a central bore 641 of the valve 64, channels 643 which diverge towards the front face 6A and a central bore 681 of the pusher 68.
    In the configuration of FIGS. 7 and 8, the balls 61 are engaged in an external peripheral groove 423 of the body 42, which locks together the connection elements 4 and 6.
    When changing from the configuration of FIGS. 4 and 5 to those of FIGS. 6, 7 and 8, the pistons 54 and 74 remain stationary in the housings 482 and 642. Thus, the pins 58 and 78 remain ejected from the peripheral grooves 542 and 742 of the piston 54 and 74, and maintain the seals 59 and 79 locally separated from the bottoms of the grooves 484 and 644. The purge passages thus remain open. Figure 8 therefore is representative of the position of the pin 78 and the seal 79 in the configurations of Figures 4 to 7.
    In the configuration of Figures 4 and 5, the pressure force exerted by the spring 56 on the piston 54 is of the order of 1.5N, while the force applied by the pin 58 to separate the seal 59 from the bottom of throat 484 is of the order of 7N. The force required to actuate the opening mechanism to lower the residual pressure of the connector is therefore much lower than the fitting force to be exerted in a fitting of the prior art, which is of the order of 330N as mentioned above.
    In the second to sixth embodiments shown in FIG. 9 and following, elements similar to those of the first embodiment bear the same references. In what follows, only what distinguishes these other embodiments of the first is described.
    In the second embodiment shown in FIG. 9, only the male coupling element 4 is equipped with a mechanism for opening a purge passage, which comprises a piston 54, a spring 56, a pin 58 and a seal 59. The female element 6 of the coupling is a conventional element equipped with a central valve whose front face is aligned with the front face of the female element in the decoupled position of the coupling, and able to push back the piston 54 of the male element 4 in the coupling phase.
    The connector 2 of this embodiment is adapted to the case where the female element 6 of the connector is connected to a source of fluid under pressure, while the male element 4 is connected to the internal pipes of a device whose internal pressure may be caused to increase in the decoupled position of the elements, and the valve 44 contain a sufficiently large internal pressure to interfere with the connection maneuver. The fluid flows from the right to the left in FIG. 9. The invention is compatible with various casings and piston lengths 54 such that, in the decoupled position of the coupling, the front face 54A of the piston 54 can be axially in position. withdrawal relative to the front face 4A of the connecting element and that the piston no longer emerges from the front face 44A of the valve 44, while the control member is in an inactive position. The front face of the complementary female element 6 is then adapted to have a projecting shape capable of further pushing the piston in its central housing 482 in the coupling phase, in order to effect the actuation of the opening mechanism of the element. male.
    According to a not shown variant of the invention, an inverse configuration is implemented. In other words, the female element 6 is equipped with a mechanism for opening a purge passage constituted by a piston, a spring, a pin and a seal, as explained above for the first embodiment of the invention. realization, while the male element is lacking. This variant is adapted to the case where only the male connector element is supplied with fluid under pressure when connecting these elements.
    In the third embodiment shown in FIG. 10, a cage 53 is attached to the pusher 48 to prevent the seal 59 from coming out of the groove 484 when it is pushed back by the pin 58. In the example, this cage 53 is screwed on the pusher 48. Alternatively, it can be mounted on this pusher by other means, in particular by gluing or latching.
    The cage 53 is provided with several lights 532 distributed around the axis X4, one of which is visible in the upper part of FIG. 10, and which allow the passage of fluid towards the groove 484. These lights are therefore part of the purge passage . Between the lights 532, and as visible in the lower part of Figure 10, a web 534 of the ring 53 closes the groove 484, which maintains the seal 59 inside the groove 484.
    Alternatively, other seal retaining members 59 in the groove 484 may be provided, such as one-piece members with the pusher 48.
    In the embodiment of Figures 11 and 12, a split ring 55 is interposed between the pin 58 and the seal 59. This split ring is flat, in that it has a cross section, visible in Figure 11, which is wider in a direction parallel to the axis X4 than in a direction perpendicular to this axis. The split ring 55 distributes the thrust force exerted by the pin 58 when it is displaced, radially to the axis X4, by the piston 54, on an area of the joint 59 which corresponds to a larger angular sector. that the only zone of interaction between the pin 58 and the seal 59 in the first to third embodiments. In addition, since the split ring 55 travels around the pusher 58 over almost its entire circumference, in the vicinity of the bottom of the groove 484, it is elastically deformed when the pin 58 is pushed radially outwards by the piston 54. As the split ring 55 has a tendency to return to its original shape, it tends to push the pin 58 towards the inside of the bore 485 and towards the housing 482. The split ring 55 thus provides an elastic return function of the pin 58 towards its configuration in which it does not push the seal 59 relative to its default shutter position in which this seal 59 closes the purge passage.
    In this embodiment, the split ring 55 constitutes a control member which acts directly on the seal 59, this control member being itself moved by the piston 54 and the pin 58 when it is necessary to open the purge passage. In this embodiment, the effort required to create the leak is greater than in the first to third embodiments because the effort to be exerted to deform the split ring is cumulative with the effort required to move the parts 54 and 58 and to deform the O - ring 59.
    FIG. 12 makes it possible to display certain constituent parts of the coupling element of this embodiment. For clarity of the drawing, the seal 52 is omitted in this figure. Note that, with the removal of the split ring 55, this figure could also relate to the first and second embodiments.
    In the embodiment of Figures 13 to 17, the piston 54 acts directly on the seal 59 which is also received in a groove 484 of the pusher 48. This groove is trapezoidal section.
    Y4 and Z4 respectively denote two axes perpendicular to the axis X4 and perpendicular to each other.
    As seen in Figure 14, the bottom of the groove 484 has an elongate section with its largest transverse dimension parallel to the axis Y4. The seal 59 which has a circular shape by default is deformed to adopt the same shape as the bottom of the groove 484 in the plane of Figures 14 and 16. At two opposite zones which are aligned on the axis Z4, the bottom groove 484 is provided with two holes 485 which put in communication the groove 484 with the first housing 482.
    The housing 482 and the piston 54 have, for their part, a flattened shape with their largest transverse dimensions parallel to the axis Z4.
    Furthermore, the piston 54 is provided with two notches 546 which each form a partial clearance space of the seal 59 in its default sealing position, which corresponds to the configuration of Figure 1 for the first embodiment and which is FIGS. 13 and 14. Thus, in this embodiment, the control member is the piston 54 which acts directly on the gasket 59.
    The spring 56 is engaged in a blind hole 548 of the piston 54.
    In the default configuration of closing the purge passage, the engagement of the seal 59 in the notches 546 has the effect of closing the holes 485, so that the purge passage, formed by the volumes of the groove 484, the holes 485 and housing 482, is closed.
    When the piston 54 is pushed against the elastic force exerted by the spring 56, by a force represented by the arrow E5 in Figure 15, in particular when the front face 4A of the coupling element is set bearing against the front face of a complementary coupling element, the notches 546 of the piston 54 are axially offset relative to the groove 484, which has the effect of pushing the seal 59 radially outwardly relative to the axis X4, by pushing it around the outer radial surface 544 of the piston 54 and creating, at the passages 485, a leak which opens the bleed passage and which allows the fluid contained in the connecting element of the flow to the outside, as represented by the arrows F4 in Figure 15. Figure 16 shows that the seal 59 is peeled locally from the bottom of the groove 484, which facilitates the appearance of the opening leak of the passage of purge.
    In this embodiment, the engagement of the seal 59 in the notches 546 helps to retain the piston 54 in the housing 482.
    Alternatively, the notches 546 may be replaced by areas where the piston 54 has a locally reduced dimension along the axis Z4, to the level of the rear end of the piston. In other words, two shoulders are formed at the top and bottom of the piston in FIGS. 13 to 16. According to another variant, an area of reduced transverse dimensions along the axes Y4 and Z4 may be provided near the end. In both cases, the seal 59 can partially disengage in this or these zones when it is in the closed position of the purge passage. The seal does not block the piston against the action of the spring 56 and a complementary stop member is provided, in particular in the form of a key inserted between leather and flesh, between the housing 482 and the piston 54.
    In the sixth embodiment shown in Figure 18, two pins 58 are used to control the positioning of the seal 59 relative to the groove 484. Two holes 485 are provided, which allows to create a leak in two places around the X4 axis. In the example of Figure 18, two pins 58 are used. Alternatively, more than two pins 58 and more than two holes 485 can be used, these being preferably regularly distributed around the axis X4. In this embodiment, the force required to create the leak is greater than in the first embodiment, since the seal 58 must be deformed at several points to create the leak. The invention is described above in the case where the groove 484 is trapezoidal or semi-circular section. It can also be implemented with an asymmetrical section groove.
    Whatever the embodiment, when uncoupling the male and female elements of the coupling, the spring 56, or 76 pushes the piston 54 or 74 to the front face 4A or 6A, that is to say towards the position by default. In this position, the groove 542 or 742 or the notches 546 of the piston are again aligned with the seal 59 or 79 which can resume its default sealing position where it closes the purge passage. In this position, the pistons 54 and / or 74 are again accessible to an operator and ready to be operated.
    In the examples of FIGS. 1 to 12 and 18, the pins 58 and 78 move only in a direction radial to the axes X4 or X6. Alternatively, their displacement may be oblique with respect to these axes, that is to say both radial and axial. The invention is also applicable to a coaxial coupling of which the male and female elements define two fluid passages under pressure, such as that known from PCT / EP2015 / 078007. In particular, the elements 54, 58 and 59 of the invention can replace the ball of the male element of this known connection.
    The seals 59 and 79 are circular in section. Alternatively, this section is not circular.
    According to another variant, the pins 58 and / or 78 may be replaced by control members having another geometry, such as balls, buttons, latches able to deform and move the seals 59 and / or 79 locally. instead of the pin 58 or 78 or the seal 59, or in addition, other means for retaining the piston 54 or 74 in the housing 482 or 642 may be provided, for example in the form of a screw or a key.
    The spring 56 or 76 may be replaced by another elastic return means, for example a deformable tongue.
    In the embodiments of FIGS. 1 to 12 and 18, the groove 542 or 742 may be replaced by a localized excess thickness of the piston 54 or 74, provided that the piston is angularly indexed about the axis X4 or X6 so that this excess thickness is aligned with the bore (s) 485 or 645. In this case, the passage of the extra thickness at the seal 59 or 79 has the effect of detaching the gasket from the bottom of the groove 484 or 644 and open drilling 485 or 645.
    Whatever the embodiment or variant considered, the compact structure of the opening mechanism of the purge passage allows its implantation within a connection element of relatively small diameter and easy maneuvering during the coupling of the elements. male and female quick coupling. The invention applies to connecting elements and connections for liquid or gaseous fluid.
    The features of the embodiments and alternatives contemplated above may be combined with one another to generate new embodiments of the invention.
    权利要求:
    Claims (15)
    [1" id="c-fr-0001]
    1 (4; 6) male or female quick coupling member (2) for connection to a pipe (C4; C6) of fluid under pressure and comprising - a body (42; 62) defining at least one passage (441, 481, 483; 641, 643, 681) of fluid under pressure, a front face (4A; 6A) and a longitudinal axis (X4; X6) of the coupling member; an inner piece (48; 64) disposed in the body, which is provided with a surface (48A, 64A) belonging to the front face, and a bleed passage (482, 484, 485; 642, 644); , 645) connecting the pressurized fluid passage and the outside of the connecting member; and an opening mechanism (54, 56, 58, 59, 74, 76, 78, 78) for actuating from the front of the coupling member to open the bleed passage, characterized in that: the inner part (48; 64) is equipped with a circumferential groove (484; 644) in which a seal (59; 79) rests in a closed position in which it closes off the purge passage (482, 484; 485; 642, 644, 645); - The opening mechanism is mounted on the inner part and comprises at least one member (58; 78; 55; 54) for controlling the position of the seal relative to the groove, this control member being movable between a first position inactive, where it does not move the seal relative to its closed position, and a second active position, where it acts directly on the seal to open the purge passage.
    [2" id="c-fr-0002]
    2. A male or female quick coupling element according to claim 1, characterized in that it comprises: - a pusher (48; 68) fixed with respect to the body; - a valve (44; 64) movable relative to the body (42; 62) between a position in abutment against a seat (486; 686) defined in part by the pusher and situated on the side of the front face (4A, 6A); of the male or female connector member (4, 6), where it closes the passage of pressurized fluid (441, 481, 483, 641, 643, 681), and a position away from the seat, where it defines with the seat a passage section (F) of fluid under pressure; and in that the inner part equipped with the peripheral groove (484; 644) and the seal (59; 79) is formed by the valve (64) or the pusher (48).
    [3" id="c-fr-0003]
    3. - Male or female element quick coupling according to one of the preceding claims, characterized in that the control member (58; 78; 55) is actuated, passing from its first inactive position to its second active position, by a piston (54; 74) disposed in a first housing (482; 642) of the inner part (48, 64), movable in this housing parallel to the longitudinal axis (X4, X6) and intended to be itself operated from the front face (4A, 6A).
    [4" id="c-fr-0004]
    4. - Male or female quick coupling element according to claim 3, characterized in that the control member is a pin (58; 78) disposed in a second housing (485, 645) of the inner piece (48; ) and movable radially with respect to the longitudinal axis (X4, X6), between its first inactive position and its second active position, under the action of a cam surface (5422, 6422) of the piston (54, 74) .
    [5" id="c-fr-0005]
    5. - male or female element quick coupling according to one of the preceding claims, characterized in that the control member is a split ring (55) disposed between the seal (59) and the bottom of the groove (484) of the inner piece (48).
    [6" id="c-fr-0006]
    6. - male or female element quick coupling according to claims 3 and 5, characterized in that the split ring (55) is movable, between its first inactive position and its second active position, under the action of at least a pin (58) disposed in a second housing (485) of the inner part (48) and itself radially movable relative to the longitudinal axis (X4), between a first inactive position and a second active position, under the action of a cam surface (5422) of the piston (54).
    [7" id="c-fr-0007]
    7. - male or female element quick coupling according to one of claims 1 or 2, characterized in that the control member is a piston (54) disposed in a first housing (482) of the inner part (48) movable in this housing and intended to be itself actuated from the front face (4A).
    [8" id="c-fr-0008]
    8. - male or female element quick coupling according to claim 7, characterized in that the piston (54) is movable parallel to the longitudinal axis (X4) and defines at least one space (546) partial clearance of the seal, in the inactive position of the piston.
    [9" id="c-fr-0009]
    9. - Male or female quick coupling member according to one of claims 3, 4, 6, 7 or 8, characterized in that it comprises means (56; 76; 55) of elastic load of the piston (54; 74) to a position where it does not actuate the control member (58; 78; 55; 54) and where it can be actuated from the front face (4A, 6A).
    [10" id="c-fr-0010]
    10. - Male or female quick coupling member according to one of claims 3 to 9, characterized in that the purge passage (482, 484, 485; 642, 644, 645) comprises at least the first housing (482; 642) of the inner part (48, 64).
    [11" id="c-fr-0011]
    11. - Male or female quick connector element according to one of the preceding claims, characterized in that the peripheral groove (484; 644) is trapezoidal, semicircular or asymmetrical section.
    [12" id="c-fr-0012]
    12. - Male or female element quick coupling according to one of the preceding claims, characterized in that it comprises a seal retaining member (59) in the peripheral groove (484), in particular a ring (53) secured to the inner part (48).
    [13" id="c-fr-0013]
    13. - male or female element quick coupling according to one of the preceding claims, characterized in that the purge passage (482, 484, 485; 642, 644, 645) opens on the front face (4A; 6A) of the connecting element.
    [14" id="c-fr-0014]
    14. A male or female quick connector element according to one of the preceding claims, characterized in that the control member (58; 78; 55; 54) is movable in the purge passage (482, 484, 485; 642, 644, 645).
    [15" id="c-fr-0015]
    15. - Quick coupling (2) for the detachable joining of pipes (C2, C4) of fluid under pressure, this connection comprising a male element (4) and a female element (6), characterized in that at least one male and female elements (4, 6) is according to one of the preceding claims.
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    同族专利:
    公开号 | 公开日
    KR20170075652A|2017-07-03|
    US20170184242A1|2017-06-29|
    EP3184871B1|2018-09-26|
    FR3046211B1|2018-02-16|
    EP3184871A1|2017-06-28|
    CN106907542B|2020-07-10|
    US10094502B2|2018-10-09|
    CN106907542A|2017-06-30|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    FR2657138A1|1990-01-17|1991-07-19|Dart Engineering Ag|RAPID CONNECTION PART WITH PRESSURE REDUCING MEMBER.|
    US6394131B1|2000-11-16|2002-05-28|Abb Offshore Systems, Inc.|Trapped fluid volume compensator for hydraulic couplers|
    DE20205441U1|2002-04-08|2002-06-20|Voswinkel Kg|Coupling part of a pressure medium plug-in coupling|
    US20040144436A1|2003-01-29|2004-07-29|Dennis Zeiber|Ventable manifold|
    EP2669560A1|2012-05-29|2013-12-04|Stäubli Faverges|Discharge and draining device, fitting end and fitting including such a device|
    WO2014060433A1|2012-10-16|2014-04-24|Parker Hannifin Manufacturing Germany GmbH & Co. KG|Coaxial high-pressure coupling having overpressure relief|
    FR2847330A1|2002-11-19|2004-05-21|Staubli Sa Ets|QUICK CONNECTION FOR THE REMOVABLE JOINT OF TWO PIPES|
    FR2889728B1|2005-08-10|2007-10-05|Staubli Faverges Sca|CONNECTOR ASSEMBLY FOR FLUIDIC CIRCUIT|
    FR2927143B1|2008-02-06|2010-03-19|Staubli Sa Ets|FEMALE CONNECTING ELEMENT AND RAPID CONNECTING INCORPORATING SUCH A MEMBER|
    FR2948435B1|2009-07-23|2011-08-12|Staubli Sa Ets|FEMALE CONNECTING ELEMENT AND RAPID CONNECTING INCORPORATING SUCH A MEMBER|
    FR2950950B1|2009-10-01|2012-12-07|Staubli Sa Ets|RAPID COUPLING FEMALE ELEMENT AND RAPID CONNECTION INCORPORATING SUCH A MEMBER|US10781957B2|2017-01-24|2020-09-22|Staubli Faverges|Fluid coupling element and fluid-coupling comprising such an element|
    US10221950B1|2017-08-17|2019-03-05|Stedlin Manufacturing Incorporated|High pressure coupler|
    FR3082588B1|2018-06-15|2020-09-11|Staubli Sa Ets|FLUIDIC CONNECTION|
    FR3096109B1|2019-05-14|2021-05-28|Staubli Sa Ets|Female element and fluidic connection|
    WO2021219251A1|2020-04-30|2021-11-04|Eaton Intelligent Power Limited|Quick release coupling|
    法律状态:
    2016-12-27| PLFP| Fee payment|Year of fee payment: 2 |
    2017-06-30| PLSC| Search report ready|Effective date: 20170630 |
    2017-12-27| PLFP| Fee payment|Year of fee payment: 3 |
    2018-12-26| PLFP| Fee payment|Year of fee payment: 4 |
    2020-10-16| ST| Notification of lapse|Effective date: 20200914 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1563259A|FR3046211B1|2015-12-23|2015-12-23|MALE OR FEMALE ELEMENT FOR RAPID CONNECTION AND RAPID CONNECTION COMPRISING SUCH A MEMBER|FR1563259A| FR3046211B1|2015-12-23|2015-12-23|MALE OR FEMALE ELEMENT FOR RAPID CONNECTION AND RAPID CONNECTION COMPRISING SUCH A MEMBER|
    US15/366,152| US10094502B2|2015-12-23|2016-12-01|Male or female quick coupling element and quick coupling including such an element|
    CN201611176164.5A| CN106907542B|2015-12-23|2016-12-19|Male or female quick coupling element and quick coupling comprising such an element|
    KR1020160174557A| KR20170075652A|2015-12-23|2016-12-20|Male or female quick coupling element and quick coupling including such an element|
    EP16206089.1A| EP3184871B1|2015-12-23|2016-12-22|Male or female quick connection element and quick connection including such an element|
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