Quick acting coupling for the disconnectable connection of two pipelines

The invention relates to a quick connector which includes specific elements to be fitted one in the other for releasably joining together two pipes conveying a pressurized fluid.

It is known to provide a quick coupling of a button external for controlling a locking mechanism the male coupling element within the element female, for the release of the male element. The drive force of such a button increases with diameter of the fitting and the fluid pressure passing in this connection as the locking mechanism comprises a spring whose spring constant increases with these values. In addition, these locking mechanisms to button are relatively precise and expensive mechanisms.

It is also known to use connections comprising balls and a locking sleeve, the balls being controlled by the position of the sleeve around one of the coupling elements. these fittings require a sufficient free volume around fittings for maneuvering of the sleeve, this volume is not still available.

It is also known, for example US-A-4909545, to arrange on the body of a coupling element ramps receiving lugs projecting radially from the body of the other element. The fitting of the locking requires a combined relative translational movement and rotation of its components, which may decrease the reliability of assemblies made.

It is further known from US-A-3211479 to provide on a fitting, a sleeve adapted to penetrate into a socket equipped, on its inner surface, pins provided for cooperate with ramps provided on the outer surface of muff. At the opening of this fitting, there is a risk dangerous movement of a flexible pipe downstream sub the effect of pressure prevailing in the pipe.

It is also known from US Pat 5,087,086 to maneuver rotating a ring of a female coupling element which defines a locking ramp of a pin carried by a male member of the coupling, this maneuver to make pass this piece of a seat ramp to another seat. A similar maneuver is necessary for other movements of pawn in the ramp. However, it is sometimes impossible to access such a ring for maneuver in rotation, in particular when one of the coupling elements is embedded.

It is at these drawbacks particularly to remedy the invention by providing a new type of connector that allows locking and release without excessive force, including the case of a connection of large diameter and for fluid under high pressure, then it is not necessary laterally touch fitting to maneuver it.

In this spirit, the A connector fast for removably joining two pipes, it coupling comprising first and second elements specific to be fitted one inside the other along a main axis of the connection, the first element comprising at least one ramp receiving a radial projection of the second element, for locking of these elements pass configuration of the connector, wherein<ul><li>the ramp or the projecting portion is formed in or integral with a ring mounted on one of the elements above, being free in rotation and fixed in translation along the main axis of the fitting,</li><li>the ramp forms at least one locking seat the projecting portion pass configuration of the coupling, </li><li>the ramp forms a second seat, offset axially relative to the first seat in an opening direction of the connection, for the locking of the projecting portion decompression configuration of the downstream pipe and</li><li>the ramp is configured such that the displacement of the projecting part in the ramp of its inlet zone towards the first seat, the displacement of the projecting part of the first seat to the second seat the movement of the projecting portion of the second seat to the output of the ramp are obtained by exerting only overall axial forces on one or the other of male or female elements.</li></ul>

Thanks to the invention, the locking movement and Unlock the coupling, with stop in positron decompression may be effected essentially in a axial direction, without requiring rotation by the user. Indeed, the rotation corresponding to locking is obtained by rotational movement Automatic ring relative to the element on which it is mounted, while the decompression is obtained by locking the projecting member on the second seat.

For the purposes of the present invention, the term "fixed in translation "means that the ring is immobilized axially between two stops. Of course, a certain clearance remains eligible, which corresponds to a possibility of axial movements of small amplitude to the ring.

Other advantageous but not mandatory aspects the invention are evident from claims 2 to 10 appended latter.

The invention can be implemented with different embodiments.

According to a first embodiment, the ramp is formed on the inner radial surface of a ring mounted free in rotation and fixed in translation within the female element of the fitting, while the portion projection is fixed relative to the male element.

According to a second embodiment, the ramp is formed on the inner radial surface of a body of the female element of the fitting, while the portion projection is integral with a ring mounted free in rotation and fixed in translation around the male element.

According to a third embodiment, the ramp is formed on the outer radial surface of a ring mounted free in rotation and fixed in translation around the male element of the fitting, while the projecting portion is fixed relative to the female element and extends radially inwardly thereof.

According to a fourth embodiment, the ramp is formed on the outer radial surface of the male element of connection, while the projecting part is integral with a ring mounted free in rotation and fixed in translation in inside the female element, the projecting part extending radially inwardly of that element.

The invention will be better understood and other advantages thereof appear more clearly in light of the following description of six embodiments of a Quick Connect accordance with its principle, given solely by way of example and with reference to the accompanying drawings wherein :<ul><li>Figure 1 is a longitudinal section of principle of a coupling according to the invention, in uncoupled configuration;</li><li>Figure 2 is a view similar to Figure 1, in bandwidth configuration of the connector;</li><li>Figure 3 is a view similar to Figure 1, in channeling relief configuration downstream associated with the connection;</li><li>Figure 4 is a perspective view Part of the connector of Figures 1 to 3, the female element being shown partially in phantom and with a partially broken away;</li><li>Figure 5 is a developed view of a ramp the coupling of Figures 1 to 4;</li><li>Figure 6 is a partial section on a larger scale along line VI-VI in Figure 5;</li><li>Figure 7 is a schematic representation of the evolute of the ramp shown in Figure 5;</li><li>Figure 8 is a view similar to FIG 1 for a coupling according to a second embodiment of the invention;</li><li>Figure 9 is a view similar to FIG 1 for a coupling according to a third embodiment of the invention;</li><li>Figure 10 is a view similar to FIG 1 for a coupling according to a fourth embodiment of the invention. </li><li>Figure 11 is a view similar to Figure 7, for a coupling according to a fifth embodiment of embodiment of the invention;</li><li>Figure 12 is a view similar to Figure 7, for a coupling according to a sixth embodiment of embodiment of the invention.</li></ul>

The connector shown in Figures 1 to 5 comprises In a male member and a female member B provided one and the other with a generally cylindrically shaped section circular. The rear portion of the male element A is fluidly connected to a first pipe, or upstream pipe, C₁While the rear portion of the female element B is connected to a second pipeline or pipeline downstream C₂.

We note XX 'main axis of the connector formed elements A and B, that is to say, the main axis of the elements A and B in the configurations of FIGS 1 to 4, according to axis the direction which these items may be-fitted one in the other.

The element A comprises a body 11 within which is disposed a check valve 12 elastically loaded by a spring 13 exerting a force F₁ tending to press a head 14 of the valve 12 fitted with an O-ring 15 against a seat 16 formed by the body 11. A second O-ring 17 is provided in an annular groove 18 formed therein of the body 11. On its outer radial surface 19, the body 11 is provided with two lugs 20 and 21 diametrically opposed relative to each other and extending in a direction YY 'substantially perpendicular to the axis X-X'. The lugs 20 and 21 are integral with the body 11.

Variable B comprises a body 31 forming a push 32 adapted to penetrate into the internal volume 22 of the body 11 and push the valve 12 against the force F₁.

A ring 33 is mounted in a housing 34 provided in the inner radial surface 35 of the body 31, the ring 33 being free to rotate relative to the body 31 around the axis XX 'and fixed in translation relative to the body along that axis, due to its bearing against the edges 34 opposed<u>at</u> and 34<u>b</u> Housing 34.

A bore 36 connects the housing 34 to outside the element B, through the body 31.

On the inner radial surface 37, the ring 33 is provided with two ramps 40 and 41 formed in the hollow area 37. The geometry of the ramp 40 is developed at the Figure 5 where the trace of the lug 20 is shown in various positions in phantom.

The ramp 40 comprises an input section 401 converging toward a passage 402 extending substantially in a direction parallel to the axis X-X '. A curved portion 403 is also provided, this part extended by a recess 404 whose radius of curvature is such that it can receive and serve as a stop to the lug 20.

During fitting of the male member A in the female member B, the pin 20 is moving in the section 401 of the passage 402, as shown by arrows F₂, F '₂ and F''₂ which correspond to different possible angular orientations of the pins 20 relative the ring 33 from the fitting.

In practice, the progress of the pin 20 corresponds to a relative movement of the lug relative to the ring 33, as the ring rotates about the axis XX '.

The lug 20 then enters the passage 402 and follows the curve 403 as represented by arrow F₃, so that it comes into abutment in the recess 404. It is then in a fitting configuration maximum of the male member A in the female member B.

The user perceives that he has reached the race maximum and can release the element A or element B, according one he has in hand. In this case, the force F₁ tends to push the plunger 32 outward volume 22, this inducing a relative movement of the male elements and female in an opening direction. This implies movement of the lug 20 in the ramp 40 towards a surface 405 inclined with respect to the axis XX ', this displacement is represented by arrow F₄. When the lug 20 rests against the surface 405 and account Given the orientation of this surface relative to the axis X-X ', the pin 20 slides against the surface to an detention in a second recess 406 which geometry is such that it can serve seat engagement of the pin 20 in the ramp 40.

With this position of the pin 20 in the ramp 40, elements A and B are coupled in the position of the Figure 2, which means that the connection is on. A high pressure of the fluid passing through the fitting, has any negative influence on the reliability of the relative immobilization of A and B.

The arrow F₅ represents the progress of the lug 20 the along the surface 405.

When one wishes to disengage the elements A and B, it suffices for the user to exert a new axial force press fitting the male element into the female element, which has the effect of causing the lug 20 in contact with a area 407 inclined with respect to the axis XX 'in a direction opposite to the surface 405. The corresponding relative movement of the lug 20 is shown by the arrow F₆ in Figure 5. The surface 407 extends into a recess 408 forming stopper as the recess 404, the movement of the lug 20 along the surface 407 being represented by arrow F₇.

When the user feels that he has again reached the maximum fitting position of the elements A and B, enough for him to release the item it is holding for the lug 20 is driven from the recess 408 under the influence the effort F₁This is represented by arrow F₈.

The ramp 40 includes a second passage 409 globally parallel to the axis XX ', this passage being extended by a curved portion 410 which leads to a recess 411 forming a second locking seat of the pin 20. Note the outer surface 412 of the ramp 40 at the curved portion 410, the surface for guiding the pin 20 toward the recess 411, as represented by the arrow F_9.

We notice <u>d</u>₁ the distance, taken parallel to the axis XX ', between the center of the pin 20, when in the recess 404 and into the recess 406. This distance is the "on-course" made during the fitting of the elements A and B.

The recesses 404 and 408 are generally aligned in a direction D perpendicular to the axis XX ', the Figure 5 so that the distance <u>d</u>₁ also corresponds to the distance, taken parallel to the axis X-X ', between the center of the lug 20 respectively in place in recesses 406 and 408. This alignment recesses 404 and 408, however, is not mandatory.

We notice <u>d</u>₂ the distance, taken parallel to the axis XX ', between the center of the lug 20 respectively in place in the recesses 406 and 411. The value of the distance<u>d</u>₂ is selected such that when the lug 20 is sits in the recess 411, the coupling is in the configuration of Figure 3, wherein the pusher 32, although still engaged in the volume 22 does not come in recovery of a notch 23 provided on the body 11, this allowing a flow of fluid in the downstream pipe C₂ towards a volume V spared around the plunger 32 and inside the body 31. A notch 38 provided on one edge of the ring 33 allows a discharge of fluid outwardly of the fitting, through the bore 36, this flow being represented by the arrows E in Figure 3.

When the pipe C₂ was purged, simply to the user to exert a new fitting force axial elements A and B, which has the effect of shifting the pin 20 toward a surface 413 inclined relative to the axis XX 'in the same direction as the surface 407, this being represented by the arrow F₁₀ in Figure 5. The lug then progresses along that surface, as represented by the arrow F₁₁ and reaches a third recess 414, from which the lug 20 can be moved as shown by arrow F₁₂, in direction a surface 415 inclined with respect to the axis XX 'in the same direction as the surfaces 405 and 412. The pin 20 may then slide along the surface toward the outlet opening 416 of the ramp 40, as shown by the arrow F₁₃.

The opening 416 corresponds in fact to the opening input of the ramp 41. Indeed, the angle α between the apertures 401 and 416 is equal to about 180 °, each of ramps 40 and 41 extending substantially over half the circumference of the inner ring 33.

From its position in the opening 416, the pin 20 can be easily removed from the rail 40.

The surface 415 defines a surface 415 'inclined in opposite direction with respect to the axis XX ', a beak 415' ' generally aligned axially with the recess 414. This bec opposes an axial introduction of the pin 20 to the recess 414 and deflects it toward the 401 and pass 402, which is represented by the arrow F '₂ to the 5.

Given the geometry of the ramp 40, and that of the ramp 41 which is analog, is obtained effective locking lugs 20 and 21 compared to the female element B only exerting efforts generally axial, that is to say parallel to the axis XX ', on one or the other of the male or female elements of connection. The progression of the lug 20 in the ramp 40, as shown by the arrows F₂ to F₁₂, is therefore obtained by the essentially axial movements of one thereof.

It is therefore possible to manipulate the coupling in accordance to the invention without having access to one of the laterally connector elements, for example in the case where one of these elements is recessed, as shown in phantom, for the element A, in Figure 1.

In addition, the ring 33 is mechanically protected against shocks and against pollution caused by the body 31. The pins 20 and 21 being one piece with the body 11, At the male end is very robust and can be mounted the end of a hose.

To improve the reliability of the lock at the time the passage of the lug 20 in the curved portion 403, may be provide that the outer surface 417 of the part is curved inwardly of the ramp 40, as shown in phantom in Figure 5, this inducing acceleration of the relative velocity of the lug relative the ramp after the passage of the lug at the top of the curved portion 417 This prevents release the axial force towards the recess 404, which assurance that the lug 20 comes right stop in this recess.

In the passage 402, there may be provided a blade elastic 418 attached by a rivet 419 or other means 420 in the bottom of the ramp 40, this blade having 418 tendency, under the effect of its own elasticity, to take off its free end 418<u>at</u> from the bottom 420, as represented by the arrow F₁₄.

When lug 20 is progressing towards the recess 404 as shown by arrow F₁₅ to the 6, it pushes the end 418<u>at</u> of the blade 418 towards the base 420 through an elastic deformation this blade. However, if the pin 20 back towards the passage 402 from the recess 404, it stumbles in the blade 418 without being able to fall back towards the bottom. The blade 418 therefore constitute an anti-return device of the lug 20 when progressing in the ramp 40, which imposes the direction of advance of the pin 20 in the ramp 40 from the input section 401 to open output 416. In particular, it is not possible to uncouple the connector without passing the pin 20 by the second seat or recess 411, which allows decompression of the downstream pipe C₂.

As is more particularly visible in Figure 7, the various surfaces 403, 407 and 413, which lead the recesses 404, 408 and 414 and are inclined relative to the axis X-X ', which are opposite the respectively surfaces 405 and 412, which lead to the seats 406 and 411 and are inclined in opposite direction with respect to this axis.

Thus, upon the exertion of axial movements on one of the constituent parts of the joint, which translated by movements in the direction of arrows vertical in Figure 7, reaches one of these surfaces, either from a renfoncemen t, from a seat.

In other words, the guide surfaces respectively towards the recesses or to the seats, are axially aligned with seats or recesses in which the pins can change management or rest.

In the second, third and fourth modes embodiment of the invention shown in respectively Figures 8 to 10, elements similar to those of the first embodiment bear identical references.

The second embodiment differs from the previous that the ramps, one of which is visible with the reference 40, are formed on the inner radial surface 35 the body 31 of the female element, while the lugs 20 and 21 diametrically opposed are formed on a ring 24 mounted in a groove 25 formed on a radial surface external 19 of the body 11. The male locking elements and female A and B is obtained by the rotation of the ring 24, about the longitudinal axis XX 'of the connector, the ring being immobilized in translation parallel to this axis by its support against the opposing edges 25<u>at</u> and 25<u>b</u> of the 25 throat.

In the third embodiment, two pins 20 and 21 are immobilized on the body 31 of the female element B and protrude from the surface 35 towards the axis X-X '. A ring 26 is provided in a groove 27 formed on the outer radial surface 19 of the body 11, this ring defining ramps 40 and 41 on its surface outer radial 26<u>at</u>. The ring 26 is mounted to rotation in the groove 27 and is immobilized in translation parallel to the axis X-X ', by its support on the opposite edges 27<u>at</u> and 27<u>b</u> throat 27.

In the fourth embodiment of the invention, the ramps 40 and 41 are machined directly on the surface outer radial 19 of the body 11 of the male member, then a ring 39 having two lugs 20 and 21 is housed, with possibility of rotation, in a groove 42 formed on the inner radial surface 35 of the body 31 of the element B. The female ring 39 can rotate freely around the axis X-X 'while it is immobilized in translation parallel to this axis, because it bears against the opposite edges 42<u>at</u> and 42<u>b</u> throat 42.

The second, third and fourth modes embodiment operate in a similar manner to that described with reference to the first embodiment.

In the representation of Figure 11, a ramp 1040 is formed and delimited by surfaces S₁ to S₅ whose each ends with a stop B₁ to B₅. In fact, B stops₂ and B₄ are equivalent seats to 406 seats and 411 of the first embodiment, while the stops B₁, B₃ and B₅ correspond to recesses in which the projecting parts can be redirected in sliding on a surface S₁, S₃ or S₅ to go direction of another surface S₂, S₄ or towards the exit ramp in 1040.

A difference from the first embodiment embodiment also lies in the fact that the ramp 1040 has a common area 1401 of the input and output of an element projecting the type of pin 20.

12 shows a sixth embodiment wherein six surfaces S₁ to S₆ inclined with respect to a longitudinal axis XX 'of the connector define five stops B₁to B₅ two of which, the stops B₂ and B₄ constitute seats for retaining a projecting portion, three further stops B₁, B₃ and B₅ constituting direction change areas the projecting portion within the ramp 4040 and formed. As in the fifth and seventh mode embodiment, the input and the output of the ramp are 4040 4401 consist of a common area.

In the embodiments of Figures 11 and 12, the surfaces S₁ to S₆ are located opposite the stops B₁ at B₅ being offset axially with respect thereto. The Similar observations apply to surfaces and recesses identified in the first mode production.

The technical characteristics of the various modes embodiments can be combined together within the scope of the present invention defined by the appended claims.