Patent Document

FIELD OF THE INVENTION 
     The present invention relates to a quick-coupling device for circuits with circulation of fluids under pressure, comprising a fitting element including a second channel, the socket having a central axis, a first channel internal to the socket, and an inlet of the first channel; the first channel being designed to house the fitting element and being brought into fluid communication with the second channel; the socket further comprising an outer body defining at least part of the first channel and comprising an annular cavity opening on the first channel, a substantially annular locking element at least partly housed in the annular cavity and movable within the cavity, and including a plurality of locking sectors consisting of circular sectors of the locking element which can be mutually moved in a radial direction and define a release position at which the locking element is retracted into the annular cavity in such a manner as to enable movement of the fitting element relative to the socket, and a locking position at which the locking element tightly secures the fitting element to the socket. To move the locking element from the locking position to the release position, an extractor, partly housed in the outer body is slided along the central axis relative to the outer body. 
     DESCRIPTION OF THE PRIOR ART 
     This quick-coupling device is a device conceived to enable the simple, safe and immediate, connection and disconnection of pipes belonging to lines for circulation of fluids, possibly under pressure, without using any particular tool. 
     It is known that the realization of hydraulic lines for fluids under pressure, requires the connection of pipes to tanks, to other pipelines or to other elements using connecting means that achieve fluid passage. 
     This means can have two components, at least one of which is rigidly connected to one of the two pipes usually through welding or forcing operations, or using pipe-clamping bands. These components are usually provided with threads to mutually join them forming the above-mentioned connection. 
     However, quick couplings are presently more and more frequently preferred to the above described means, the coupling device being enabling two pipes to be connected and disconnected through simple and quick manual operations. These couplings usually have two base elements: a socket and a fitting element, to be partially inserted inside the socket. 
     In a first example of a coupling, as described by ISO Standard 8434-1:2007(E), the connection between the fitting element and the socket will be done by a forcing operation. In particular, in the socket the presence of three elements is contemplated: a first base body having a thread, a nut suitable for engagement with the thread and a conical element housed between the two components, inside a suitable cavity formed inside the base body. When the nut is secured to the base body, the conical element is forced between the base body and the fitting element, creating the connection. 
     Another type of coupling device consists of the so-called “quick couplings”. In these couplings, the fitting element has a groove or an annular ridge on the outer surface, while the socket has an outer casing having a cylindrical cavity to house the fitting element. This cavity also has a hollow circular area housing a plurality of locking elements that can be radially moved due to the presence of an elastic O-ring. 
     Initially, the fitting element is inserted inside the socket and the locking elements are pushed by the outer surface of the fitting element inside the hollow circular area thus compressing the elastic ring. When the groove or annular ridge is in corresponding of the locking elements, the elastic ring radially pushes the locking elements which are inserted inside the groove achieving a lock between the fitting element and the socket. 
     Finally, for a quick release of this lock, a sliding body is provided that, when manually pushed by an operator, disengages the locking elements from the groove or annular ridge enabling the separation of the fitting element from the socket. 
     The above-described known art has some important drawbacks. 
     In fact, both types of quick couplings presently known are subject to quick deterioration. 
     In the first example described above, in fact, the engagement and disengagement operations are rather slow, because it is necessary to use of wrenches and the like. 
     In addition, locked elements by friction can become inseparable due to deposits or deterioration of the coupling areas and, therefore, it becomes impossible to replace those faulty components. In some cases, even by using suitable tools such as wrenches, for example, can be insufficient to release the locked elements 
     In the second example, a displacement of the locking elements can occur which can bring to the unsteadiness of the quick coupling, leading to the inability of handling high pressures. 
     A further problem is given by the fact that all known quick couplings are not able to withstand high pressures. 
     Still another problem is represented by the fact that the two types of actuators are not interchangeable with each other, making impossible to couple the fitting element of one with the socket of the other. 
     SUMMARY OF THE INVENTION 
     The purpose of the present invention is to conceive a novel quick-coupling device for pipelines and the like capable of substantially obviating the previously-mentioned drawbacks. 
     Within the scope of this technical task, it is an important aim of the invention to conceive a reliable and durable quick-coupling device. In particular, it is an important aim of the invention to enable the quick-coupling device to be used easily while avoiding the deterioration of the same on prolonged use. 
     A further fundamental aim of the invention is to obtain a quick-coupling device withstanding high pressures. 
     Another important aim of the invention is to provide a device that is at least partly usable with the types of couplings presently known, in particular with the coupling in accordance with ISO Standard 8434-1:2007(E). 
     The novel quick-coupling device for circuits with circulation of fluids under pressure is comprising a fitting element including a second channel, the socket has a central axis, a first channel internal to the socket, and an inlet of the first channel; the first channel is housing the fitting element and being brought into fluid communication with the second channel; the socket is further comprising an outer body defining at least part of the first channel and comprising an annular cavity opening on the first channel, a substantially annular locking element at least partially housed inside the annular cavity and movable within the cavity, and including a plurality of locking sectors consisting of circular sectors of the locking element which are mutually moved in a radial direction from a release position at which the locking element is retracted into the annular cavity in such a manner as to enable free movement of the fitting element relative to the socket, to a locking position at which the locking element tightly secures the fitting element to the socket, an extractor comprising feet, placed between the locking sectors, designed to maintain a minimum distance between the locking sectors and partly housed in the outer body and movable along the central axis relative to the outer body, designed to move the locking element from the locking position to the release position. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The features and advantages of the invention are hereinafter clarified by the detailed description of preferred embodiments of the invention, with reference to the accompanying drawings, in which: 
         FIG. 1  shows a quick-coupling device according to the invention; 
         FIG. 2  shows a partial sectional view of an element of the quick coupling device; 
         FIG. 3  shows a partial sectional view of a component of the element as shown in  FIG. 2 ; 
         FIG. 4  is a sectional view of a second component of the element as shown in  FIG. 2 ; 
         FIG. 5   a  is a sectional view of an assembly consisting of two other components of the element of  FIG. 2 ; 
         FIG. 5   b  is a top view of the assembly shown in  FIG. 5   a;    
         FIG. 6  shows a further component of the element shown in  FIG. 2 ; 
         FIG. 7  shows a partial sectional view of a second element of the quick-coupling device in accordance with the invention; 
         FIG. 8  shows a partial sectional view of a coupling device of known type, in accordance with ISO Standard 8434-1:2007; 
         FIG. 9  shows a possible configuration of the quick-coupling device according to the invention; 
         FIG. 10  shows a second possible configuration of the quick-coupling device according to the invention; 
         FIG. 11  shows a third possible configuration of the quick-coupling device in accordance with the invention. 
     
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     With reference to the drawings, the quick-coupling device for pipelines and the like in accordance with the invention has been generally identified by reference numeral  1 . 
     It is designed to connect, in a quick and easily separable manner, two pipes  20  or, alternatively, one pipe  20  to a device such as a compressor, a tank or other similar device. 
     The quick coupling  1  comprises a socket  2  having a central axis  2   a  and a fitting element  3  to be partly fitted in socket  2  and coupled thereto, preferably being of cylindrical shape. In particular, the fitting element  3  is connected to a pipe  20 , while socket  2  is connected to a tank or the like by threading. 
     The socket  2  and fitting element  3  internally have a first channel  2   d  and a second channel  3   b  respectively, that are mutually connected for fluid passage, when the socket  2   a  and fitting element  3  are fastened to each other. In more detail, the first channel  2   d  is adapted to receive the fitting element  3  through an inlet  2   c . The second channel  3   b , on the contrary, comprises an outlet  3   e  through which the fluid flows from the fitting element  3  to the socket. 
     The fitting element  3 , shown in  FIG. 7 , externally has a coupling surface  3   d  that is substantially cylindrical and with an axis substantially coincident with the central axis  2   a , when the fitting element is inserted in the socket  2 . Furthermore, this coupling surface  3   d  is continuously smooth, i.e. devoid of overhangs or other protruding elements except for a single discontinuity represented by a groove  3   a  that is axially symmetric to, and made to a precise distance from the outlet  3   e , as hereinafter better specified. It also has a counter-surface  3   c  close to the outlet  3   e  and substantially perpendicular to the central axis  2   a.    
     The socket  2  comprises a locking element  4  that can be moved in a radial direction relative to the central axis  2   a  and preferably has an almost circular shape, an outer body  5  defining a first portion of channel  2   c  and designed to contain, at least partially, the locking element  4 , and an extractor  6  defining a second portion of channel  2   c  and adapted to move relative to the outer body  5  in a direction almost parallel to the central axis  2   a.    
     In greater detail, the outer body  5  has an annular cavity  5   a  facing cavity  2   c  and designed to house, at least partially, the locking element  4 . This annular cavity  5   a  extends, as shown in  FIG. 3 , in an inclined direction  5   b  relative to the central axis  2   a  through an angle α in such a manner that the locking element  4 , when it moves in a radial direction towards the central axis  2   a , simultaneously moves in the direction of the central axis  2   a  towards the inlet  2   c . In particular, angle α is substantially included between 45° and 55° and, preferably, angle α is included between 48° and 52°. 
     Finally, the outer body  5  has substantially a cylindrical shape and, preferably, with a shaped outer surface so that it can be easily grasped by wrenches or the like. Further, it can be advantageously provided with an outer thread adapted to be connected, by screwing, with a tank or the like. 
     The locking element  4  also comprises a plurality of locking sectors  7 , preferably four, that are at least partly housed inside the annular cavity  5   a . The locking sectors  7  are adapted to be mutually and radially moved. Furthermore, due to the particular geometry of the annular cavity  5   a , the sectors  7 , during their radial displacement, advantageously move along an inclined direction  5   b , i.e. they simultaneously move in a radial direction and in a direction parallel to the central axis  2   a  toward the inlet  2   c.    
     Said movement allows two different positions of the locking element  4  to be defined: a release position ( FIGS. 10 and 11 ) at which positioning of the locking sectors  7  enables movement of the fitting element  3  relative to the socket  2 ; and a locking position at which the locking sectors mutually and tightly connect said two components. 
     In detail, in the locking position, only a portion of the locking element  4  is inside the cavity  5   a , while in the release position, the locking sectors  7  are spaced apart from each other to a greater extend and almost fully laying inside the cavity  5   a . In conclusion, when moving from the release position to the locking position, there is a reduction in the distance between the locking sectors  7  and a consequent reduction in the diameter of the locking element  4 , respectively. 
     In particular, reduction in the distance between the locking sectors  7  is obtained through a spring  8  externally surrounding the locking element  4 , as shown in  FIGS. 5   a  and  5   b . Said spring is disposed within a housing  7   a  placed on the outer edge, i.e. the one to a greater distance from the central axis  2   a , of each locking sector  7 . In addition, the spring  8  is taking up almost the whole height of the housing  7   a  calculated in a direction parallel to the central axis  2   a , so as to ensure a correct positioning of spring  8  and avoid undesired movements of the same. Furthermore, the spring  8  is a metal helical spring preferably made of steel and preferably a spiral spring of which the ends  8   a  are rectilinear to avoid them being inserted between two locking sectors  7 , when the locking element is in a release position, inhibiting returning to the locking position. In particular, the ends  8   a  are tangent to the circumference defined by spring  8  in a rest position ( FIG. 2 ). 
     Finally, each of the locking sectors  7  has a ridge  7   b  on its face close to the central axis  2   a , as shown in  FIGS. 5   a  and  5   b , which in the locking position enters the cavity  3   a  locking the fitting element  3  and socket  2  with each other. Upon movement to the release position, the ridge  7   b  comes out of the cavity  3   a  enabling mutual motion between the fitting element  3  and the socket  2 . 
     The ridge  7   b  has an upper conical wall  7   c  advantageously extending in an oblique direction  7   d , being inclined through an angle β relative to the central axis  2   a  ( FIG. 5   a ) to allow movement of the locking element  4  from the locking position to the release position, when the fitting element  3  is inserted in socket  2 . In particular, the fitting element  3 , when inserted inside the socket  2 , exerts pressure on the upper conical surface  7   c  causing the sectors  7  to enter the annular cavity  5   a  and therefore allowing full introduction of the fitting element  3 . In particular, angle β is substantially between 45° and 55° and, preferably, it is between 48° and 52°. 
     In addition, due to the presence of a lower wall  7   g , extraction of the fitting element  3  is facilitated. In fact, the extractor  6  is designed to press on said upper conical wall  7   c  so as to move the locking element  4  from the locking position to the release position, thus clearing the groove  3   a  and allowing the fitting element  3  to be pulled out. 
     In addition, the ridge  7   b  has a lower surface  7   e  almost perpendicular to the central axis  2   a , said surface being adapted to interfere with the counter-surface  3   c  of the groove  3   a . Due to this geometry, during the extraction of the fitting element  3 , the lower surface  7   e  abuts against the counter-surface  3   c  preventing the fitting element  3  from being pulled out and aligning it with the axis  2   a . This advantage is also obtained due to the cavity  5   a  that, being inclined in the opposite direction relative to the extraction direction of the fitting element  3 , prevents an undesired separation of the quick-coupling device  1 . Furthermore, the upper surface of the cavity  5   a  promotes the entry of the ridge  7   b  into the groove  3   a  when tightening occurs. 
     Finally, each sector  7  has, below the lower surface  7   e , and preferably also in correspondence of the ridge  7   b , a cylindrical surface  7   f  with an axis substantially coincident with the axis  2   a.    
     The extractor  6  is designed to slide relative to the outer body  5 , in a direction almost parallel to the central axis  2   a  and is advantageously provided, at the lower base opposite to the abutment disc  6   b , with teeth  6   a  ( FIG. 4 ) adapted to be disposed between the locking sectors  7 . In particular, when the locking element  4  moves to a locking position, the locking sectors  7  abut against the teeth  6   a  determining a minimum distance between said locking sectors  7  and, therefore, a minimum size of the locking element  4 . Finally, the number of teeth  6   a  is preferably the same as that of the locking sectors  7 , i.e. four. 
     In addition, the lower base of the extractor  6  and the upper base of the locking element  4  are advantageously inclined with respect to the central axis  2   a  and parallel to each other, so that movements of the extractor  6  gives rise to a displacement of the locking sectors  7  and vice versa. In greater detail, lowering of extractor  6  causes an increase in the sizes of the locking element  4 , i.e. passage of same to a release position ( FIG. 1 ), whereas a reduction in the sizes of the locking element  4 , i.e. a return to the locked position, causes a raising of extractor  6 . 
     In addition, the extractor  6  is partly housed within the outer body  5  and has an almost cylindrical shape. At the base external to the outer body  5  it has an abutment disc  6   b  ( FIG. 4 ) designed to push against the upper edge of the external body  5  when the extractor  6  is pressed against said outer body  5 . 
     Socket  2 , in addition to the above mentioned components, comprises a stop ring  9  adapted to be inserted, once locking between fitting element  3  and socket  2  has been completed, between the abutment disc  6   b  and the outer body  5  to prevent movement of extractor  6  relative to said outer body  5 . Preferably, the stop ring  9  is an open spring ring, i.e. its circumference is split and more specifically, it is a Seger ring or the like. 
     In order to prevent the extractor  6  from coming out of the outer body  5 , the extractor sliding movement is further limited by a retainer  10  shown in  FIG. 2 . This retainer  10  is simultaneously housed inside two grooves  10   a  formed in the extractor  6  and the outer body  5  and always facing each other, at least partly. 
     The retainer  10  preferably consists of an open spring ring so as to facilitate insertion into the grooves  10   a . In particular, during the assembling step, it is enlarged and easily inserted into the grooves  10   a  of extractor  6 . Once it has been positioned, it is allowed to expand so as to adhere to the groove  10   a  and, finally, extractor  6  is forcibly inserted into the outer body  2 . 
     Socket  2  further comprises an O-ring  11  or other similar means designed to ensure the sealing action of the fluid coupling device  1 . The O-ring  11  is advantageously at least partly housed inside a groove  5   c  ( FIG. 3 ) conveniently formed in the outer body  5  under cavity  5   a  and, in order to avoid dangerous displacements of the O-ring  11 , a sealing component  11   a , a ring for example, can be disposed within the groove  5   c , so as to lock the O-ring  11  inside the groove  5   c.    
     Shown in  FIG. 8  is a second possible configuration of the ogive-shaped coupling device according to ISO Standard 8434-1:2007, which is designed to bring into fluid connection two pipes  20  or one pipe  20  connected to a device, such as a tank. 
     In this example, the coupling device comprises a fitting element  3  and a socket  102  having a central axis  102   a  and including a first channel  102   d  designed to house the fitting element  3 . 
     Socket  102 , as shown in  FIG. 8 , has a locking element  104  to secure the fitting element  3  to the socket  102  by tightening, a base body  105  provided with a cavity  105   a  adapted to contain, at least partially, the locking element  104 , and a closing element  106  designed to be secured to the base body  101 , preferably by threading, carrying out said tightening of the locking element  104 . 
     In this preferred embodiment, the closing element  106  is designed to be moved along the central axis  102   a  and to be rigidly secured to the base body  105  by a threaded coupling, while the locking element  104  has an almost cylindrical shape characterised by a frustoconical end adapted to be inserted inside the cavity  105   a . In particular, after the fitting element  3  has been inserted into the socket  102 , the closing element  106 , being secured to the base body  105 , presses the locking element  104  within the cavity  105   a , which locking element is therefore forced between the fitting element  3  and socket  102  thus carrying out the tightening of the fitting element  3  to socket  102 . 
     The socket  102  preferably has sizes in accordance with ISO Standard 8434-1:2007 or subsequent modifications to said ISO Standard. 
     The fitting element  3 , shown in  FIG. 7 , is the one previously described and the given distance of groove  3   a  is greater than the distance between the cavity  105   a  and outlet  3   e  when the fitting element  3  is secured to the socket  102 , so that it does not interfere with said tightening action. 
     Finally, as in the preceding preferred embodiment, groove  3   a  has a counter-surface  3   c , i.e. the surface of groove  3   a  close to the outlet  3   e , that is preferably substantially perpendicular to the central axis  102   a.    
     Operation of the quick-coupling device for pipelines and the like described above as regards structure is the following. 
     Once pipes  20  have been connected to socket  2  and to the fitting element  3 , the fitting element  3  is inserted into socket  2  so that said components are secured to each other. 
     The fitting element  3  passes through the extractor  6  and abuts against the ridges  7   b  of the locking sectors  7 . Then the fitting element  3  starts pressing on said ridges  7   b  causing passage from the locking position to the release position of the locking element  4 . 
     In particular, the locking sectors  7  are moved apart from each other, i.e. the locking element increases its diameter and the locking sectors  7  are almost fully housed within the cavity  5   a  ( FIG. 10 ) thus enabling the fitting element  3  to complete its fitting. In particular, the fitting element  3  continuing its movement comes into contact with the O-ring  11  deforming it and carrying out a fluid-tight connection. 
     When the fitting element  3  is inserted, the groove  3   a  faces the locking sectors  7  that, being pressed by spring  8 , push the ridges  7   b  into said groove  3   a  securing the fitting element  3  to the socket  2  and bringing the locking element  4  back to its locking position, as shown in  FIG. 4 . 
     In addition, due to their displacement, the locking sectors  7  abut the teeth  6   a  causing the locking element  4  to have size close to the minimum size, but not strictly coincident with said minimum size. Consequently, the locking element  4  axially compresses the fitting element  3  centering it on the axis  2   a , in particular by means of the cylindrical surface  7   f.    
     In addition, before locking, the stop ring  9  is preferably introduced between the abutment disc  6   b  and the outer body  5  inhibiting any motion of the extractor  6 , so as to avoid an undesirable disengagement of the quick-coupling device  1 . 
     When the quick-coupling device  1  needs to be disengaged, i.e. the fitting element  3  is needs to be separated from socket  2 , the stop ring  9  is removed from its housing and the extractor is lowered bringing the abutment disc  6   b  almost in contact with the outer body  5 . 
     This movement of the extractor  6  causes passage of the locking element  4  from the locking position to the release position, i.e. ridges  7   b  of the locking sectors  7  come out of the groove  3   a  enabling the fitting element  3  to be pulled out of the socket  2 . 
     Once the fitting element  3  has been pulled out, the locking element  4 , due to action of the spring  8 , goes back to the locking position with the locking sectors  7  being adjacent to teeth  6   a , as shown in  FIG. 11 . 
     The invention enables important advantages to be achieved. 
     A first advantage of the quick-coupling device  1  is represented by the high reliability and duration. 
     In fact, due to the presence of teeth  6   a , the locking sectors  7  going back to the locking position are not submitted to dangerous mutual displacements and their mutual distance is almost unchanged and therefore the tightening strength between fitting element  3  and socket  2  is not diminished. 
     Another advantage is represented by the quick-coupling device ability that is ensured by the particular geometry of the lower surface  7   e  and the counter-wall  3   c . The quick-coupling device  1  is therefore able to withstand pressures up to 350 bars. 
     Still another advantage is provided by the metal spring  8  adapted to have a longer duration and greater spring force, also ensured by the number and shape of the sectors  7 . 
     A further important advantage is represented by the possibility of using the fitting element  3  also with ogive-shaped coupling devices of the type ISO Standard 8434-1:2007 presently known. In fact, the particular height where the groove  3   a  is formed, does not prevent the known quick-coupling devices, as above described, to be connected and fastened. 
     The invention is susceptible of variations falling within the inventive idea. 
     All of the details can be replaced by equivalent elements and the materials, shapes and sizes can be of any nature and magnitude.

Technology Category: f