• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    This quick coupling member (100) comprises a tubular body (102) defining an internal channel (C100) for passage of fluid under pressure and a longitudinal axis (X100), means (104, 116, 124) of closing the internal channel on the side of a front face (108) and a member (124) for discharging the internal channel (C100), movable between a first position, in which it closes a discharge passage connecting the internal channel to the outside the body, and a second position, in which it does not close this passage. The discharge member is a ring (124) which is part of the internal channel closing means and which is mounted movably between its two positions around a central member (116), which is also part of the closure means , and within a peripheral piece (104), a first surface of the discharge ring is part of the front face (108). The discharge ring (124) at least partially defines the discharge passage with the central member (116) or with the peripheral piece (104). In its first position, the discharge ring (124) is in sealing engagement against the central member (116), on a first sealing circumference, and in sealing engagement against the peripheral piece (104), on a second circumference d sealing. A minimum diameter of the second sealing circumference is strictly greater than a maximum diameter of the first sealing circumference. The connecting member (100) comprises a resilient return member of the discharge ring (124) to its first position.
    公开号:FR3052226A1
    申请号:FR1655186
    申请日:2016-06-07
    公开日:2017-12-08
    发明作者:Alain-Christophe Tiberghien；Christophe Durieux；Frederic Morel；Mathieu Sallaz
    申请人:Staeubli Faverges SCA；
    IPC主号:
    专利说明:

    The invention relates to a quick-disconnect element used for the detachable connection of pressurized fluid lines and which comprises, inter alia, a sound discharge member. internal channel. The invention also relates to a quick coupling incorporating such a coupling element.
    In the field of connections for pressurized fluid lines, there may be a safety problem which arises when the residual pressure in a fluid line connected to a coupling element reaches a high value, for example when the temperature of a fluid contained in this pipe increases, which induces an increase in the pressure in this pipe. In case of significant pressure in the internal volume of a coupling element, it may be difficult to couple the two elements of a connector to connect two pipes. In some cases, such overpressure can damage certain components of a circuit connected to a pipe in overpressure.
    To solve this problem, it is known, for example from US Pat. No. 4,703,774, to install, within a closure valve of a coupling element, a ball subjected, on the one hand, to pressure prevailing within this connecting element and, secondly, the action of a return spring and the ambient pressure. This ball forms a discharge valve of the coupling element in case of overpressure. It limits the pressure of the fluid within the coupling element. This solution is suitable for an underwater connection, such as that contemplated in US Pat. No. 4,703,774, which may be of relatively large size. On the other hand, it is difficult to implement with a connection of reduced dimensions because the available space in the center of the connecting element may be insufficient to accommodate a ball of suitable size. In addition, the operating range of the discharge valve formed by the ball is relatively limited. A large pressure is required within the coupling element to take off the ball from its seat, that is to say to trigger the discharge of the fluid, against the action exerted by the return spring. It is these disadvantages that the invention intends to remedy more particularly by proposing a new quick-coupling element in which the discharge junction can be reliably produced, even for connections of relatively small diameter, and by widening the operating range of the discharge member (s). For this purpose, the invention relates to a quick coupling element for the removable joining of pressurized fluid lines, this element comprising a tubular body, defining an internal channel for the passage of fluid under pressure and a longitudinal axis of the pressure element. connection, and means for closing the internal channel on the side of a front face of the coupling element. This coupling element also comprises a discharge member of the internal channel, which discharge element is movable between a first position, in which it closes a discharge passage connecting the internal channel to the outside of the body, and a second position, in which it does not close this discharge passage. According to the invention, the discharge member is a discharge ring which is part of the closing means of the inner channel and which is mounted around a central member, which is also part of these closure means, and inside a peripheral room. In addition, a first surface of the discharge ring is part of the front face. The discharge ring is movable, relative to the central member and parallel to the longitudinal axis, between its first and second positions. The discharge ring defines, at least in part, the discharge passage with the central member or with the peripheral piece. In its first position, the discharge ring is in sealing engagement against the central member, on a first sealing circumference, and in sealing engagement against the peripheral piece, on a second sealing circumference. A diameter of the second sealing circumference is strictly greater than a diameter of the first sealing circumference. In addition, the coupling element comprises a resilient return member of the sealing ring towards its first position.
    Thanks to the invention, the discharge ring, which has an annular shape by construction, has, on the side of the internal channel of the coupling element, a second surface which is defined radially between the first sealing circumference and the second sealing circumference, with a sealing section area sufficient for the pressure of the fluid present in this internal channel to act effectively against the elastic return member to move the discharge ring from its first axial position towards its second axial position, when necessary in view of the value of this pressure. The area of this second surface may be larger than the area of a ball portion exposed to the internal pressure of a coupling member, without having to increase the diameter of this connecting member. The invention is therefore suitable for connections of relatively small diameter, in particular a connection of internal passage diameter less than or equal to 25 mm. In addition, given the geometry of the discharge ring, it can be moved from its first position to its second position under the effect of an internal pressure of the relatively small coupling element. The invention thus makes it possible to optimize the operating ranges of the discharge member.
    Within the meaning of the invention, a diameter of a sealing circumference is a diameter equal to that of this circumference if this circumference is zero radial thickness. If the sealing circumference has a nonzero radial thickness, a diameter of this circumference is a diameter whose value is between the minimum diameter and the maximum diameter of this sealing circumference.
    According to advantageous but non-mandatory aspects of the invention, such a coupling element may incorporate one or more of the following features, taken in any technically permissible combination: - In its first position, the discharge ring bears, in one direction parallel to the longitudinal axis, against a sealing seat formed by the central member and closes the discharge passage that it defines with the central member. - The closure means further comprises a valve which is positioned radially to the longitudinal axis between the central member and the body, this valve forming the peripheral piece and surrounding the discharge ring at the face. before. - The closure means further comprises a valve which is positioned, radially to the longitudinal axis, between the central member and the body and which is positioned, at the front face, radially inside the the discharge ring. In the second position of the discharge ring, the discharge passage extends between the valve and the discharge ring. - The tubular body forms the peripheral piece and defines with the discharge ring the discharge passage that the discharge ring closes when in its first position and in sealing engagement with the tubular body. - The central body is integral with the body and comprises a surface which constitutes a part of the front face. - The central member and the discharge ring belong to a moving element, parallel to the longitudinal axis and relative to the body, between an advanced position, where the moving element is in sealing contact with the body and closes the internal channel and a retracted position where a fluid passage is provided between the moving assembly and the body. - In its first position, the discharge ring bears, on the first sealing circumference, against a surface of the central member which is frustoconical and convergent towards the front face. - The frustoconical surface has an apex angle between 60 and 120 °. - In uncoupled configuration of the coupling element, the discharge passage opens on the front face. In uncoupled configuration of the coupling element and when the discharge ring is in its first position, respective front faces of the closure means are aligned in a plane perpendicular to the longitudinal axis.
    According to a second aspect, the invention also relates to a quick coupling for the removable joining of pressurized fluid lines, this connection comprising a female connector element and a complementary male connector element. According to the invention, at least one of these connecting elements is as mentioned above.
    Advantageously, in the coupled configuration of the coupling, at least one mechanical closure member of the internal channel of the coupling element is in a retracted position, where it defines with the body of this coupling element an annular passage for the fluid. under pressure. According to the embodiments envisaged, the mechanical closing member of the internal channel which has this function can be the valve, the discharge ring, the assembly formed by the valve and the discharge ring or any other sealing means. This mechanical shutter member opens, in coupled configuration of the connector, a flow passage of the fluid present in the inner channel of a first element of the connector, to the internal channel of the second complementary element of the coupling. This passage is formed between the mechanical shutter member and the body or between this mechanical shutter member and the central member. The invention will be better understood and other advantages thereof will emerge more clearly in the light of the following description of five embodiments of a coupling element according to its principle given solely by way of example and with reference to the accompanying drawings in which: - Figure 1 is an axial section of a connector according to the invention comprising a female connector element also according to the invention - Figure 2 is an enlarged view of detail II in FIG. 1; FIG. 3 is an exploded perspective view of an internal subassembly of the female element of the connector of FIG. 1; FIG. 4 is a view similar to FIG. a discharge ring is in a configuration different from that of FIG. 2; FIG. 5 is a partial section along line VV in FIG. 4; FIG. 6 is a section similar to FIG. small scale the, during coupling of the male and female elements of the coupling, - Figure 7 is a section similar to Figure 6, when the coupling elements are coupled, - Figure 8 is an axial section of a male element of connection according to a second embodiment of the invention, - Figure 9 is an axial section along the lines IX-IX in Figure 8, there is indicated in VIII-VIII the sectional plane of Figure 8, - the FIG. 10 is a longitudinal section of a connecting element according to a third embodiment of the invention; FIG. 11 is an enlarged view of detail XI in FIG. 10; FIG. in a similar detail to FIG. 11 for a connecting element according to a fourth embodiment of the invention; FIG. 13 is a detail view similar to FIG. 11 for a coupling element according to a fifth embodiment; and - Figure 14 is a detail view a FIG. 11 for a coupling member according to the sixth embodiment.
    The connection R shown in FIGS. 1 to 7 comprises a female coupling element 100 and a male coupling element 200 intended to be fitted into each other. The male element 200 comprises a body 202 which defines a longitudinal axis X200 of the male element 200 and inside which is mounted a valve 204 resiliently loaded by a spring 206 towards a seat 2022 formed by a radial surface internal of the body 202, which is frustoconical and convergent towards the front face 208 of the connecting element 200.
    In this description, the forward direction of a coupling element is defined as the direction oriented in the direction of the fitting or coupling, that is to say towards the complementary coupling element when they are aligned and ready to be fitted as shown in Figure 1. Conversely, the rear direction of a connector element is defined as the direction opposite to the complementary coupling element. This rear direction is turned towards a pipe at the end of which is mounted the connecting element. The proximal portion of a connector member is its rearward portion, while the distal portion of a connector member is its forward portion.
    The body 202 of the male element 200 defines an internal channel C200 of pressurized fluid circulation, which is fluidly connected to a pipe C2 at the end of which is mounted the element 200. In the example, the pipe C2 is made in a frame 400 which comprises a housing 402 in which the C2 pipe opens and in which is received a rear portion of the male element 200 which is immobilized in this housing by a ring 210, an outer thread 2102 engages with a tapping 4022 of the housing 402. Two seals 212 and 214 are respectively provided between the rear part of the body 202 and the peripheral surface of the housing 402, on the one hand, and between the outer peripheral surface of the body 202 and the ring 210. A ring 216 is immobilized in the rear part of the body 202 by means of a circlip 218. This ring 216 serves as a stop for the spring 206 which can effectively press the flap 204 against the seat 2022. The valve 204 is equipped with an external peripheral groove 2042 in which is inserted a seal 220 which provides the insulation between the channel C200 and the outside of the male element 200, towards the before the male coupling member 200 beyond the seat 2022 with respect to this channel.
    The front face 208 is formed of two portions formed respectively by the front face 2044 of the valve 204, which is disk-shaped and centered on the axis X200, and the front face 2024 of the body 202, which is annular in shape, also centered on the axis X200 and which surrounds the front face 2044. The female element 100 of the connection R comprises, meanwhile, a body 102 which is screwed into a housing 302 of a frame 300. The body 302 defines a internal channel C100 of the female element 100 in which the fluid under pressure can flow, and a longitudinal axis X100 of this female element. The body 102 is provided with an external thread 1022 which cooperates with a tapping 3022 of the housing 302. A seal 112 is interposed between the outer peripheral surface of the body 102 and the peripheral surface of the housing 302.
    The frame 300 defines a pipe C1 which opens into the housing 302 and which is in permanent communication with the internal channel C100. The female connector element 100 comprises a valve 104 which is resiliently loaded by a spring 106 towards a seat 1024 formed by an internal frustoconical surface of the body 102, this surface being convergent towards the front of the female element. The valve 104 is provided with a rear skirt 1042 configured to bear against the seat 1024 when the female connector member 100 is in closed configuration, that is to say when the valve 104 isolates the channel C100 internal from the outside of the female connector member 100. A seal 120 is disposed in an inner peripheral groove 1026 of the body 102, which is axially aligned, along the axis X100, with the valve 104 in closed configuration of the female connector element 100. Thus, the seal 120 contributes to isolate the volume C100 from the outside. A pusher 116 is immobilized in the body 100 and comprises a rod 1162 and a base 1164 disposed at the rear of the rod 1162 and which is pierced with four orifices 1166 which put in permanent fluid communication the housing 302 and the internal channel C100. The pusher 116 is immobilized in the body 102 by means of a circlip 118. The spring 106 is supported on the base 1164 of the pusher 116. The pusher 116 also comprises a flange 1163 formed on the front of the rod 1162 and a nose 1165 which extends the rod 1162 beyond the flange 1163 and which is provided with an external peripheral groove 1167 and three longitudinal grooves 1169 regularly distributed around the axis X100. 1168 is the end face of the pusher 116 opposite to the base 1164 which is disk-shaped and which constitutes the front face of the pusher 116.
    A discharge ring 124 is mounted around the nose 1165 of the pusher 116 and defines an external peripheral groove 1242 in which is housed a seal 126 which abuts against an inner radial surface 1046 of the valve 104 when the latter is in contact. closed configuration of the internal channel C100. For the sake of clarity, the seal 126 is not shown in FIG.
    A spring 128 is mounted around the nose 1165, inside the discharge ring 124, and abuts, on the rear, against an internal shoulder 1244 of the discharge ring 124 and, on the front, against a stop ring 130, itself retained on the pusher 116 by means of a circlip 132 engaged in the groove 1167.
    A seal 134 is disposed in a groove 1172 formed in a frustoconical surface 1074 which delimits the flange 1163 forwards, that is to say on the side of the face 1168 of the pusher 116. The surface 1174 is convergent forward, towards the axis X100 and we note <3 its vertex angle. The value of this angle a is between 60 and 120 °, preferably 90 °.
    The various seals of the female elements 100 and 200 male are preferably made of synthetic or natural elastomer. In practice, the seals are o-rings with circular section when they are not stressed, which is visible, for example, for the seal 134 in FIG. 4. The other parts of these connecting elements are, preferably made of metal or composite material.
    1308 is noted the annular surface of the stop ring 130 opposite the spring 128. Note 1248 the annular surface of the sealing ring 124 formed on the front of this ring and which is arranged opposite the collar 1163 in the mounted configuration of the female connector member 100. The annular surface of the valve 104 opposite the spring 106 is noted. 1028 is a frustoconical surface of the body 102 which delimits this body on the front, in opposition to the Thread 1022. The surface 1028 converges forward. Finally, there is 1028 'a frustoconical surface before the body 102 which is divergent forward and which is located axially along the axis X100, between the front of the body 102 and the groove 1026.
    The surfaces 1168, 1308, 1248, 1048, 1028 'and 1028 are concentric and together constitute the front face 108 of the female connector member 100. Specifically, the surface 1028 radially surrounds the surface 1028', which radially surrounds the surface. 1048, which radially surrounds the surface 1248, which radially surrounds the surface 1308 radially surrounding the surface 1168, which is centered on the axis X100. In practice, all surfaces 1168, 1308, 1248, 1048 and 1028 'are centered on the X100 axis.
    The bodies 102 and 202 are each generally cylindrical and hollow, with a circular section. Similarly, the valves 104 and 204, the pusher 107 and the rings 124 and 130 are circular section, the circular section of the base 1164 and that of the nose 1165 being modified to create the orifices 1166 and grooves 1169.
    In the uncoupled configuration of the coupling shown in FIGS. 1 and 2, a frustoconical rear surface 1245 of the discharge ring 124 bears against both the seal 134 and facing and / or bearing against the surface 1174 of the pusher 116. The surface 1174, which is fixed with respect to the body 102 like the pusher 116 to which it belongs, forms a seat for receiving the frustoconical surface 1245, this seat being equipped with the gasket 134. The frustoconical surface 1245 is convergent towards the front. the discharge ring 124, that is to say in the direction of its front face 1248 and has an apex angle equal to manufacturing tolerances close to the angle CL In this configuration, the discharge ring 124 is in sealing against the pusher 116 on an annular sealing circumference CE1 and whose maximum diameter D1 is noted. This maximum diameter is, in practice, very close to, or equal to, the maximum diameter of the seal 134 when compressed between the parts 116 and 124. The minimum diameter of the sealing circumference CE1 is very close to, or equal to at, the minimum diameter of the seal 134 in this configuration. Thus, the circumference CE1 is annular and frustoconical, with a radial thickness not zero.
    Moreover, and still in this configuration, the sealing ring 124 is in sealing contact, through the seal 126 that it carries and on a second sealing circumference CE2, with the internal radial surface 1046 of the valve 104 As the internal radial surface 1046 of the valve 104 is radial to the axis X100, the radial thickness of the circumference CE2 and zero or, in practice, almost zero. D2 is the diameter of the sealing circumference CE2, which is in practice equal to the diameter of the inner radial surface 1046 of the valve 104. A sealing contact between two parts of the coupling, or a sealing support between these two parts, can be defined with respect to two surfaces opposite parts. There is a clearance that is filled by one or more intermediate sealing means that participate in the sealing function between the two parts. In other words, a part is in sealing contact against or with another part if their direct contact is sufficient to perform a sealing function, or if there are sealing means which fill the gap between these two parts, in particular at the level of a sealing circumference.
    The diameter D2 is strictly greater than the diameter D1, which corresponds to the fact that the circumference CE2 is farther from the axis X100 than the circumference CE1 and that these circumferences are disjoint.
    A rear surface 1246 of the discharge ring 124, whose area is non-zero, is exposed to the pressure in the channel C100. The pressure C100 is also exerted on the portion 1245A of the surface 1245 which extends radially beyond the seal 134 in the configuration of FIGS. 1 and 2. In total, the pressure in the channel C100 is exerted on the ring discharge 124, on a surface equivalent to the difference of the areas of the sections defined by the outer diameters of the joints 126 and 134.
    The surface 1246 is frustoconical and converges towards the rear, that is to say opposite to the surface 1248.
    The operation of the connecting element 200 is as follows:
    In the configuration shown in Figures 1 and 2, the front faces 1168, 1308, 1248 and 1048 are aligned in a plane perpendicular to the axis X100.
    In uncoupled configuration, the members 104, 116 and 124 seal the front opening of the body 102 which is bordered by the seal 120. In particular, the spring 128 pushes the discharge ring 124 in contact with the seal 134 and the surface 1174. Given the presence of the seals 120, 126 and 134, the internal channel C100 is isolated from the outside of the connecting element 100.
    Consider the case where the C1 pipe is connected to an electronic installation that should be cooled with a heat transfer fluid. In uncoupled configuration of the elements 100 and 200 of the connection R, the temperature of this heat transfer fluid can increase under the effect of the heat dissipation from electronic components of the aforementioned installation. In this case, the pressure of the coolant within the internal channel C100 increases. This pressure is exerted especially on the rear surface 1246 of the discharge ring 124, and on the portion 1245A of the surface 1245, the sum of these surfaces having a non-zero area.
    When the pressure force exerted on the surfaces 1246 and 1245A is sufficient to overcome the elastic return force exerted by the spring 128, the discharge ring 124 is moved from its first position shown in Figure 2 to its second position 4, in which the surface 1245 is spaced from the surface 1174 and the seal 134. The fluid present in the internal channel C100 can then flow between the facing surfaces 1245 and 1174, and then inside. the discharge ring 124 to open at the front face 108 of the female connector element 100, around the surface 1168. In FIG. 4, the arrows E100 represent the theoretical flow of the fluid in a discharge passage P100 which is defined between the pieces 116 and 124. This flow E100 through the passage P100 is made normally possible when the discharge ring 124 is in its second position. As can be seen in the lower part of FIG. 4, this discharge passage P100 includes the grooves 1169, downstream of the frustoconical surface 1245. However, it can be seen in the upper part of FIG. 4 that the fluid can also flow in the passage of FIG. P100 discharge around the nose 1165 outside the grooves 1169, since the mounting of the stop ring 130 around the nose 165 is not waterproof.
    During the displacement of the discharge ring 124 around the pusher 116 and along the axis X100, between its first axial position shown in Figure 2 and its second axial position shown in Figure 4, the seal 126 remains in contact with the inner radial surface 1046 of the valve 104 at the circumference CE2, so that the seal between this valve 104 and the discharge ring 124 remains assured.
    When the pressure within the channel C100 has decreased due to the evacuation of a portion of the fluid through the discharge channel P100 identified above, the spring 128 is capable of pushing the ring 124 rearward, c that is to say to move it from its second axial position shown in Figure 4 to its first axial position shown in Figure 2. The discharge channel P100 is then closed and the internal conduit C100 again isolated from the outside of the female connector element 100.
    The parts 116 and 124 to 134 form a telescopic subassembly SE of the female connector element 100 which is visible in FIG. 3, except for the representation of the seal 126, and which makes it possible to control the discharge towards the outside of a portion of the fluid contained in the channel C100, as a function of the pressure of the fluid in this channel.
    When it is necessary to couple the elements 100 and 200, and as represented in FIG. 6, the X100 and X200 axes are aligned to form a common axis XR which is the fitting fitting axis, the front faces 108 and 208 being then opposite. The connecting elements 100 and 200 are then brought closer to one another along the axis XR, which has the effect of bringing the part 2024 of the front face 208 against the valve 104 and the faces before 1168 and 1248 of the pusher 116 and the discharge ring 124 against the valve 204. This has the effect of pushing the valves 104 and 204 respectively inside the body 102 and 202, against the forces exerted by the springs 106 and 206. This is followed by the start-of-fitting configuration shown in FIG. 6, where the internal channels C100 and C200 are still isolated from each other.
    Continuing the movement of fitting, one reaches the configuration of Figure 7 where the valves 104 and 204 are in retracted positions where they define, respectively with the bodies 102 and 202, annular passages, to the point that the internal channels C100 and C200 are in communication, which represents the flow arrows ER, in the case where a heat transfer fluid is delivered by the male connector 100 to reload the pipe C1 from the pipe C2. In this configuration, the discharge ring 124 and the pusher 116 remain in abutment against the valve 204, while the body 202 remains in abutment against the valve 104.
    In practice, the valve 204 is provided, in a different plane from that of Figure 7, fluid passage channels for the flow in the direction of the arrows ER.
    Alternatively, the flow takes place from the pipe C1 to the pipe C2, that is to say in the opposite direction to that of the arrows ER. According to an unrepresented aspect of the invention, a locking system of the elements 100 and 200 of the coupling in coupled configuration can be provided, especially in the form of a ball system, bayonet (s) or claws. A ball lock system is shown for the third embodiment of Figures 10 and 11.
    FIGS. 1, 6 and 7 show that, during the coupling of the elements 100 and 200, that is to say during the transition from the configuration of FIG. 1 to the configuration of FIG. 124 and the pusher 116 of the telescopic subassembly SE do not move relative to each other along the axis X100. The discharge ring 124 remains in its first position where it closes the discharge passage P100. The same goes for the uncoupling of the elements 100 and 200 which is carried out by progressively moving away from the elements, that is to say going from the configuration of FIG. 7 to that of FIG. 6, then to that of FIG. Thus, the coupling and uncoupling of the coupling elements takes place without opening of the passage P100, which avoids the filling of the volumes contained between the pusher 116 and the valve 124.
    The position shown in FIG. 4 is not the position of maximum spacing between the surfaces 1245 and 1174. This maximum spacing position results from several factors, such as the length of the nose 1165, the characteristics of the spring 128, the the dimensions of the ring 124, the difference in the areas of the sections formed by the diameters of the seals 126 and 134, as well as the dimensions of the stop ring 130. In practice, this position of maximum spacing is only rarely reached, because a spacing of a few millimeters or a few tenths of a millimeter between the surfaces 1245 and 1174 is enough to discharge a few drops of the fluid present in the internal channel C100 to lower the pressure in this channel, to the point that the discharge ring 124 returns to its first position under action of spring 128.
    The setting of the internal pressure of the female coupling element 100 for which the discharge ring 124 moves from its first position to its second position can be performed by acting on the characteristics of the spring 128, on the geometry of the discharge ring. 124, especially on the ratio of diameters D1 and D2. In this respect, the difference between the diameters D1 and D2, that is to say the difference between the diameters of the joints 126 and 134, makes it possible to create the surfaces 1246 and 1245A of the ring 124 whose projection in a perpendicular plane the axis X100 has a sufficient area for the pressure force to effectively drive the discharge ring 124 forward, from the first position of Figure 2 to the second position of Figure 4, while the The area of this surface is substantially greater than the area of a ball installed on the axis of a connecting element, as provided in the state of the art.
    The discharge sealing seat, formed by the surface 1245, is different from the opening sealing seat of the inner channel 100 in the coupling phase, formed by the surface 1024. The inner passage diameter of the fitting R can be relatively low, especially less than 25 mm, without being a disadvantage to achieve an efficient discharge system near the front face 108 of the connecting member 100. The use of the discharge ring 124, which presents in this mode execution of the annular surfaces 1246 and 1245A exposed to the pressure in the channel C100, improves its sensitivity to pressure and its reactivity in case of overpressure. In other words, the discharge ring 124 of the connecting element 100 is sensitive to a lower pressure than a ball of the state of the art.
    As in the first position of the discharge ring 124, the sealing zone between the pusher 116 and the discharge ring 124 is formed in a frustoconical plane, at the interface between the surfaces 1245 and 1174 and the seal 134, the axial stroke, parallel to the axis X100, of the ring 124 necessary for the discharge is low, which limits the friction to which the seals are subjected, including the seal 126.
    In addition, the displacement of the discharge ring 124 under the effect of a pressure increase in the internal channel C100 is directly visible from the outside because the surface 1248 is part of the front face 108 of the female element of In fact, in the second position of the discharge ring 124, this surface 1248 is axially offset, along the axis X 100 with respect to the surfaces 1168 and 1048, as can be seen in FIG. 4.
    Since, during the coupling and uncoupling phases of the male and female elements of the connection R, the elements 116 and 124 do not move relative to each other along the axis X100, the discharge passage P100 remains closed during these phases, which ensures that the coupling element 100 only leaks when it is in uncoupled configuration, under the effect of an overpressure in the internal channel C100.
    In the second to sixth embodiments of the invention shown in FIGS. 8 and following, elements similar to those of the first embodiment bear the same references and are not described in detail. In what follows, we mainly mention what distinguishes these embodiments from the first.
    In the second embodiment shown in FIGS. 8 and 9, the male coupling member 200 is equipped with a discharge ring 224 which is mounted, not on a pusher fixed relative to the body 202, but around the valve 204 which is movable relative to this body, along the axis X200. The parts 204 and 224 belong to a moving body E along the axis X200 inside the body 202 and which is subjected to the action of the spring 206 and to the action of the pusher of a female element which may be a conventional female element, without discharge ring, where the female element 100 of the first embodiment. During the movements of the crew E, the pieces 204 and 224 maintain their relative position along the axis X200. In the uncoupled configuration of the coupling, the crew E bears against a seat formed by the body 202 and closes the internal channel C200 forwards. In coupled configuration, a fluid passage is provided between this equipment E and the body 202, with a provision similar to that shown in Figure 7 for the valve 204 inside the body 202. The crew E here plays the role of the valve 204 of the first embodiment. It is movable between an advanced position and a retracted position which respectively correspond to the uncoupled and coupled configurations of the coupling.
    The discharge passage is here defined radially between the valve 204 and the discharge ring 224 when the discharge ring is in its second position.
    As in the first embodiment, the discharge ring 224 carries a seal 226 which bears against a peripheral piece which is here formed by the body 202, whereas, in the first embodiment, this peripheral piece is formed by the valve 104. More specifically, the seal 226 bears radially against an inner radial surface 2026 of the body 202.
    As in the first embodiment, a spring 228 pushes back the discharge ring 224 by bearing against a seal 234 carried by the valve 204. The spring 228 is supported on a stop ring 230 immobilized on a nose before 2045 the pusher 204 through a circlip 232. The discharge ring 224 is slidably mounted on the nose before 2045.
    As in the first embodiment, there are 2024 and 2044 respective front faces of the body 202 and the valve 204. Note also 2248 and 2308 the respective front faces of the rings 224 and 230. The front face 2024 surrounds the front face 2248 , which surrounds the front face 2308, which surrounds the front face 2044. The front faces 2024, 2248 and 2308 are annular and flat. The front face 2248 is disk-shaped. In uncoupled configuration of the male coupling element 200 and when the discharge ring closes the discharge passage P200, the front faces 2024, 2248, 2308 and 2044, which together constitute the front face 208 of the element 200, are aligned in a plane perpendicular to the axis X200 as visible in Figures 8 and 9.
    As in the first embodiment, the support of the discharge ring 224 on the valve 204 takes place, in the closed position, on two sealing circumferences CE1 and CE2 which are distinct, which makes it possible to define a frustoconical annular surface. 2246 on which can exert a part of a pressure force due to the pressure of the fluid within the internal channel C200 defined by the body 202. This pressure force is also exerted partly on a portion 2245A of a surface 2245 defined as in the first embodiment. The first sealing circumference CE1 is defined around the joint 234 and D1 is denoted as its maximum diameter. The second sealing circumference CE2 is defined at the interface between the seal 226 and the surface 2026. D2 is denoted by its diameter. The diameter D2 is strictly greater than the diameter D1.
    The third to sixth embodiments relate to the case where the invention is implemented within a female coupling element, comparable to the element 100 of the first embodiment. It could also be implemented within a male coupling element comparable to the element 200 of the second embodiment.
    In the third embodiment of the invention, the contact zone between the discharge ring 124 and the pusher 116 is not frustoconical, as in the first two embodiments, but cylindrical with a circular base. The seal 134 is engaged in a groove 1172 formed in an outer cylindrical surface with a circular base 1174 of the pusher 116. On the other hand, an inner radial surface 1247 of the discharge ring 124, which is cylindrical with a circular base, is configured to contact the seal 134 in the first position of the discharge ring 124, which defines a first sealing circumference CE1. The surface 1247 is lined, on the side of the discharge ring turned away from the front face 108, by a zone 1249 accessible from the internal channel C100 in the first position of the discharge ring. This zone 1249 has an increased diameter relative to that of the surface 1247. When the discharge ring is pushed forward, under the effect of a pressure exerted on a rear surface 1246 of this discharge ring, the zone 1249 arrives opposite the seal 134, along the axis X100. This has the effect of opening a discharge passage P100 through which the fluid contained in the internal channel C100 of the coupling element can flow. In FIG. 11, the location of the discharge passage P100 is represented by an arrow opening on the front face 108 of the element 100, even if, in the position of the discharge ring shown in this figure, this passage is closed. . Note that the sealing circumference CE2 between the seal 126 carried by the discharge ring 124 and the valve 104 has a diameter D2 strictly greater than the diameter D1.
    The fourth embodiment of the invention shown in Figure 12 proceeds from an approach similar to that of the third embodiment. In this embodiment, the discharge passage P100, shown under the same conditions as in FIG. 11, is defined between the discharge ring 124 and the valve 104. The internal radial surface 1046 of the valve 104, which is in abutment radial against the seal 126 in the first position of the discharge ring 124 shown in Figure 12, extends, on the side of the front face 108, by a zone 1049 of increased diameter relative to that of the surface 1046. When the discharge ring 124 is pushed to the left of Figure 12, the seal 126 is found axially aligned with the zone 1049 in a plane normal to the axis X100 to which the seal 126 belongs, so it is no longer at This has the effect of opening the discharge passage P100, through which can flow the fluid contained in the internal channel C100 of the coupling element.
    In the embodiment of Fig. 12, two sealing circumferences CE1 and CE2 are defined, with the same approach as in the embodiment of Figs. 10 and 11. The essential difference between the third and fourth embodiments is that in the third embodiment, the discharge passage is provided at the radial level of the first circumference CE1 while in the embodiment of Figure 12, the discharge passage is provided at the second circumference CE2.
    In the third and fourth embodiments mentioned above, the valve 104 and the discharge ring 124 are each provided with a plurality of through radial orifices 1041, respectively 1241, which allow the pressure of the fluid to be distributed inside the body 102 , in particular during the movements of the valve 104 vis-à-vis the seat 1024, without the risk of trapping fluid between the valve 104 and the body 102.
    In the third and fourth embodiments, as only visible in FIG. 10, the female coupling element 100 is provided with a ball lock system 160 intended to cooperate with a peripheral groove of a complementary male coupling element. . The radial position of these balls with respect to the axis X100 is controlled by a ring 162.
    Also, in these two embodiments, a circlip 132 is used to retain the discharge ring 124 on the valve 104, forming a stop resistant to the force exerted by the spring 128.
    In the fifth embodiment of the invention shown in Figure 13, the valve 104 is mounted around the pusher 116 on the front of the connector, being subjected to the action of the spring 106. The valve 104 belongs to the means of closing of the internal channel C100 of the connecting member 100. In this embodiment, the central member comprises the pusher 116 and the valve 104. The sealing ring 124 is here interposed radially between a main portion 104A of the valve 104 and the body 102 of the coupling member 100. An auxiliary portion 104B of the valve 104 radially surrounds a rear bead 124A of the discharge ring 124.
    The discharge ring 124 is subjected to the action of a resilient return spring 128 which pushes it towards the inside of the body 102, with respect to the valve 104, and towards its first position. To do this, the spring 128 is received in a housing 104C, defined radially between the parts 104A and 104B of the valve 104, and resting on a stop ring 130, itself immobilized in the housing 104C relative to the valve 104 by means of a circlip 132.
    The valve 104 and the sealing ring 124 are provided with several orifices 1041, respectively 1241, which help that the pressure prevailing in the conduit C100 of the coupling element also applies to the discharge ring 124, in the housing 104C and up to a surface 1246 of the heel 124A turned away from the front face 108.
    In practice, the pressure in the duct C100 applies to all surfaces of the discharge ring 124 located to the right of the joints 120 and 134 in Figure 13. The pressure forces are canceled in pairs, except at the level a ring corresponding to a projection parallel to the axis X100 of the area between the joints 120 and 134 perpendicular to X100 on the surface 1246. The resultant, on the discharge ring 124, the pressure in the duct C100 is therefore a force directed to the left in FIG. 13, that is to say towards the front face 108.
    When the pressure in the conduit C100 increases, the force exerted on the surface 1246 has the effect of passing the discharge ring 124 from its first position shown in solid lines in Figure 13 to its second position shown in dash .
    Note 1247 the outer peripheral surface of the discharge ring 124 against which the seal 120 is in radial support. This surface 1247 is bordered, opposite to the front face 108, by a peripheral groove 1249, which is axially offset, along the axis X100, relative to the seal 120 when the discharge ring 124 is in its first position. position. This groove 1249 is aligned axially with this seal when the discharge ring is in its second position. Thus, in this second position, a discharge passage P100 is created between the discharge ring 124 and the body 102 of the connecting element 100.
    As in FIGS. 11 and 12, the location of the discharge passage P100 is represented by an arrow in FIG. 13, even though this passage is closed in the illustrated configuration.
    In this embodiment, the first sealing circumference CE1 is defined between the valve 104 and the sealing ring 124, with a diameter D1 and the second sealing circumference CE2 is defined between the sealing ring 124 and the sealing ring 124. body 102, with a diameter D2, strictly greater than the diameter D1.
    In the sixth embodiment of the invention shown in FIG. 14, the discharge passage P100 comprises a first portion P102 defined between the surfaces 1245 and 1174 respectively formed on the discharge ring 124 and on the pusher 116 as in FIG. first embodiment, and a second portion P104 formed by channels 1176 and 1178 formed within the nose 1165 of the pusher 116. In the first, second and sixth embodiments of the invention, when in its first position , the discharge ring 124 or 224 bears against a seat formed by the surface 1174 or by a corresponding surface of the valve 204, in a direction inclined relative to the axis X100 or X200, thus partly in a direction parallel to this axis. Alternatively, the surfaces 1174 and the like may be perpendicular to these axes, in which case the support of the ring discharges against its seat is parallel to the axis X100 or X200. In all cases, for these embodiments and in this first position, the discharge ring closes the discharge passage P100 formed at least partially between the central member and the discharge ring at the first circumference CE1. In the first, second and sixth embodiments, the first sealing circumference CE1 has a non-zero radial thickness. Alternatively, this radial thickness may be zero or almost zero, as for the second sealing circumference CE2.
    A sealing circumference is generally defined as the curve according to which two mechanical parts can maintain a tight contact, in other words a sealing engagement with or without an intermediate sealing means, such as a seal, and this permanently or removably. These sealing circumferences have the function of limiting the passage of fluid between the mechanical parts. They are preferably defined according to the internal or external contact surfaces of the annular seals. When considering a sealing circumference CE1 or CE2, and when the latter has a non-zero radial thickness, a diameter of this sealing circumference is a diameter whose value is between the maximum diameter and the minimum diameter of this sealing circumference. In the example of the first, second and sixth embodiments, all the diameters of the sealing circumference CE1 are strictly smaller than the diameter D2, since the maximum diameter D1 is smaller than the diameter D2.
    As a variant, the invention provides that one or the other of the circumferences CE1 and CE2 has a non-zero radial thickness.
    In the first, second, third and sixth embodiments the discharge passage P100 or P200 is no longer closed in the second position of the discharge ring at the first circumference CE1 which is smaller than the second circumference CE2. In the fourth and fifth embodiments the discharge passage P100 is made at the second circumference CE2, which is larger than the first circumference CE1.
    In all embodiments, the surfaces forming the front faces 108 and 208 are, with the exception of the frustoconical surfaces 1028 and 1028 ', perpendicular to the longitudinal axis X100 or X200 of the connecting element 100 or 200 to which they belong. In uncoupled configuration of the connector and except in case of leakage through the discharge passage, the front faces are flat, except for these surfaces 1028 and 1028 '. Thus, the closure members and the central member do not have a protruding shape and form a face of the connector perpendicular to its longitudinal axis which can be easily cleaned in uncoupled configuration of the connector. The invention is not limited to the embodiments mentioned above and several variants can be envisaged.
    In particular, the connection mode between the connecting elements 100 and 200 and the pipes C1 and C2 may be different from that shown. For example, the rear portions of the connecting members 100 and 200 may comprise tubular tips of "fir tail" type on which can be reported constituent pipes of the pipes C1 and C2. The use of the terms "around" and "inside" indicates the relative position of a first piece relative to a second piece, these pieces not necessarily being directly in contact with one another, but may delimit between them a space in which a mechanical part may be radially interposed.
    The valve seals, in particular the seals 120, 126 and 220 may be mounted indifferently on a closure element or on the complementary element against which this seal is in contact in the embodiments shown. In addition, the seal 134 or 234 may be mounted on the discharge ring 124 or 134, in which case it bears against the central member 116 or 204 when the discharge ring is in its first position.
    According to the embodiments, the gasket 134 or 234 may be a gasket other than an O-ring, in particular a non-circular section gasket which is bonded to the valve 204 or to the closure means opposite to the valve relative to the passage P100, to the instead of being inserted into a throat.
    The grooves 1169 which constitute an axial part of the discharge passage P100 may be provided in a different number of three or have a profile different from that shown in FIG.
    The shape of the discharge ring 124 may be different from that shown in the figures, provided that it keeps two sealed contact circumferences CE1 and CE2 with different diameters, D1 and D2.
    A coupling R can comprise a single element equipped with a discharge ring 124 or 224 and according to the invention or its two male and female elements are in accordance with the invention. The invention applies to connections for liquid or gaseous fluids.
    The features of the embodiments and variants described above may be combined to generate new embodiments of the invention.
    权利要求:
    Claims (14)
    [1" id="c-fr-0001]
    1, -Element (100; 200) of a quick connector (R) for the detachable joining of pressurized fluid lines (C1, C2), which connecting member comprises a tubular body (102; 202) defining an internal channel (C100; C200) for passing fluid under pressure and a longitudinal axis (X100; X200) of the coupling element; means (104, 116, 124; 204, 224) for closing the internal channel on the d-side; a front face (108; 208) of the connecting element; - a member (124; 224) for discharging the internal channel (C100; C200) movable between a first position in which it closes a discharge passage (P100); P200) connecting the inner channel to the outside of the body, and a second position, in which it does not close the discharge passage, characterized in that - the discharge member is a discharge ring (124; ) which is part of the inner channel (C100; C200) closing means (104, 116, 124; 204, 224) which is mounted around a central member (116; 204; 104) also forming part of the closure means of the inner channel, and within a peripheral piece (104; 202; 102) - a first surface (1248; 2248) of the discharge ring is part of the front face (108; 208); - the discharge ring is movable with respect to the central member and parallel to the longitudinal axis (X100; X200), between its first and second positions - the discharge ring (124; 224) defines, at least in part, the discharge passage (P100; P200) with the central member (116; 204) or with the peripheral piece (104; 102) and - in its first position, the discharge ring (124; 224) is in sealing engagement against the central member (116; 204; 104) on a first sealing circumference ( CE1), and in sealing engagement against the peripheral piece (104; 202; 102), on a second sealing circumference (CE2), - a diameter (D2) of the second sealing circumference (CE2) is strictly greater than a diameter (D1) of the first sealing circumference (CE1), and - the connecting member (100; 200) comprises a member (128; 228) for elastic return of the discharge ring (124; 224) to its first position.
    [2" id="c-fr-0002]
    2. - Fitting element according to claim 1, characterized in that, in its first position, the discharge ring (124; 224) bears, in a direction parallel to the longitudinal axis (X100, X200), against a sealing seat (1174) formed by the central member (116; 204) and sealing the discharge passage (P100; P200) that the discharge ring defines with the central member
    [3" id="c-fr-0003]
    3. - Fitting element according to one of the preceding claims, characterized in that the closure means (104, 116, 124) further comprises a valve (104) which is positioned radially to the longitudinal axis (X100), between the central member (116) and the body (102), the valve forming the peripheral piece and surrounding the discharge ring (124) at the front face (108).
    [4" id="c-fr-0004]
    4. - Fitting element according to claim 2, characterized in that the closure means (104, 116, 124) further comprises a valve (104) which is positioned radially to the longitudinal axis (X100). between the central member (116) and the body (102) and positioned at the front face (208) within the discharge ring (224).
    [5" id="c-fr-0005]
    Connecting element according to one of Claims 3 to 4, characterized in that, in the second position of the discharge ring (124; 224), the discharge passage (P100; P200) extends between the valve (104; 204) and the discharge ring.
    [6" id="c-fr-0006]
    6. - Fitting element according to claim 1, characterized in that the tubular body (102) forms the peripheral piece and defines with the discharge ring (124) the discharge passage (P100) that the discharge ring closes when it is in its first position and in tight support with the tubular body.
    [7" id="c-fr-0007]
    7. - discharge element according to one of the preceding claims, characterized in that the central member (116) is integral with the body (102) and comprises a surface (1168) which constitutes a portion of the front face (108) .
    [8" id="c-fr-0008]
    8. - Fitting element according to one of claims 1 to 6, characterized in that the central member (204) and the discharge ring (224) belong to a moving body (E), parallel to the longitudinal axis (X200) and relative to the body (202), between an advanced position, where the moving assembly is in sealing contact with the body (202) and closes the internal channel (C200), and a retracted position, where a passage of fluid is formed between the moving equipment and the body.
    [9" id="c-fr-0009]
    9. - coupling element according to one of the preceding claims, characterized in that, in its first position, the discharge ring (124; 224) is supported on the first (CE1) sealing circumference against a surface (1174) of the central member (116; 204) which is frustoconical and convergent towards the front face (108, 208).
    [10" id="c-fr-0010]
    10. - Fitting element according to claim 9, characterized in that the frustoconical surface (1174) has an apex angle (CI) of between 60 and 120 °.
    [11" id="c-fr-0011]
    11. - Fitting element according to one of the preceding claims, characterized in that, in uncoupled configuration of the connecting element (100, 200), the discharge passage (P100; P200) opens on the front face (108). 208).
    [12" id="c-fr-0012]
    12. - coupling element according to one of the preceding claims, characterized in that, in uncoupled configuration of the coupling element (100; 200) and when the discharge ring (124; 224) is in its first position, respective front faces (1048, 1168, 1248, 2048, 2248) of the closure means (104, 116, 124, 204, 224) are aligned in a plane perpendicular to the longitudinal axis (X100, X200).
    [13" id="c-fr-0013]
    13. - Quick coupling (R) for the detachable joining of pipes (C1, C2) of fluid under pressure, this connection comprising a female coupling element (100) and a male coupling element (200) complementary to the element of female connector, characterized in that at least one of the connecting elements (100, 200) is according to one of the preceding claims.
    [14" id="c-fr-0014]
    14. - quick coupling according to claim 13, characterized in that, in the coupled configuration of the connector (R), at least one mechanical member (104, 204, 224) for closing the internal channel (C100; C200) of the connecting element (100; 200) is in a retracted position where it defines with the body (102; 202) of this connecting element a passage for the flow (ER) of the fluid under pressure.
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    同族专利:
    公开号 | 公开日
    FR3052226B1|2019-05-10|
    US20170350547A1|2017-12-07|
    TR201901138T4|2019-02-21|
    JP6936627B2|2021-09-15|
    CA2969308A1|2017-12-07|
    EP3255332A1|2017-12-13|
    EP3255332B1|2018-12-12|
    CN107477295B|2020-12-15|
    US10190713B2|2019-01-29|
    JP2017219201A|2017-12-14|
    CN107477295A|2017-12-15|
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    CN104567521A|2014-12-16|2015-04-29|中航光电科技股份有限公司|Radiator|
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    US4703774A|1985-12-04|1987-11-03|Vetco Gray Inc.|Subsea safety check valve system|
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    US9512948B2|2012-10-16|2016-12-06|Parker Hannifin Manufacturing Germany GmbH & Co. KG|Coaxial high-pressure coupling with overpressure relief|WO2018062431A1|2016-09-29|2018-04-05|ニッタ株式会社|Pipe joint and joint connection device|
    US10781957B2|2017-01-24|2020-09-22|Staubli Faverges|Fluid coupling element and fluid-coupling comprising such an element|
    US10941892B2|2017-02-17|2021-03-09|Hewlett Packard Enterprise Development Lp|Valved connector|
    FR3084436B1|2018-07-24|2021-01-15|Staubli Sa Ets|QUICK COUPLING FOR THE REMOVABLE JUNCTION OF TWO PIPES CARRIED BY A PRESSURIZED FLUID|
    FR3101389B1|2019-09-30|2021-10-22|Staubli Sa Ets|Fluidic connection|
    法律状态:
    2017-06-27| PLFP| Fee payment|Year of fee payment: 2 |
    2017-12-08| PLSC| Search report ready|Effective date: 20171208 |
    2018-06-26| PLFP| Fee payment|Year of fee payment: 3 |
    2019-06-25| PLFP| Fee payment|Year of fee payment: 4 |
    2021-03-12| ST| Notification of lapse|Effective date: 20210206 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1655186A|FR3052226B1|2016-06-07|2016-06-07|RAPID CONNECTION ELEMENT WITH DISCHARGE MEMBER AND RAPID CONNECTION COMPRISING SUCH A MEMBER|
    FR1655186|2016-06-07|FR1655186A| FR3052226B1|2016-06-07|2016-06-07|RAPID CONNECTION ELEMENT WITH DISCHARGE MEMBER AND RAPID CONNECTION COMPRISING SUCH A MEMBER|
    US15/610,006| US10190713B2|2016-06-07|2017-05-31|Quick coupling element with discharge member and coupling member comprising such an element|
    CA2969308A| CA2969308A1|2016-06-07|2017-06-01|Quick-connect element with discharge mechanism and quick connect containing such an element|
    TR2019/01138T| TR201901138T4|2016-06-07|2017-06-06|Quick coupler with discharge element and coupling with such a quick coupler.|
    JP2017111314A| JP6936627B2|2016-06-07|2017-06-06|A quick coupling element with a discharge member and a coupling member containing such an element|
    EP17174499.8A| EP3255332B1|2016-06-07|2017-06-06|Quick coupling element with discharge member and coupling member comprising such a quick coupling element|
    CN201710418984.9A| CN107477295B|2016-06-07|2017-06-06|Quick-connect element with a venting member and connecting member comprising such an element|
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