Abstract:
A coupler is provided which is mountable to a fitting of a breakaway coupling to facilitate assembly and disassembly of the coupling. The coupling has a first fitting and a second fitting which are held together by a ball in the first fitting which is received in a detent in the second fitting. The second fitting has an outer sleeve on which the detent is formed, and an inner sleeve slideable in the outer sleeve. A latch ring on the inner sleeve is alignable with the groove. A spring biases the inner sleeve and latch ring into a locking position in which the detent balls are urged into engagement with the detent to hold the two fittings together. The coupler includes an open ended housing having a side wall and an end wall. A plate, securable to the second fitting inner sleeve, is received in the coupler housing for axial movement. A cam on an outer surface of the housing end wall is connected to the plate by a rod. The cam is pivotable between a first position in which its camming surface is out of engagement with the housing end wall and a second position in which its camming surface engages the housing end wall. As the cam is moved to the second position, the plate is pulled toward the housing end wall, thereby pulling the second fitting inner sleeve axially in the outer sleeve against the force of the spring to move the latch ring out of alignment with the groove sufficiently to enable the detent ball to move radially in its associated opening and to disengage the groove.

Description:
STATEMENT REGARDING FEDERALLY SPONSORED RESEARCH OR DEVELOPMENT 
     Not Applicable. 
     CROSS-REFERENCE TO RELATED APPLICATIONS 
     Not applicable. 
     BACKGROUND OF THE INVENTION 
     This invention relates to breakaway couplings, and in particular, a breakaway coupling which requires a considerable amount of force (i.e. 200 lbs.) to couple and uncouple. 
     Breakaway couplings are commonly placed in gas delivery hoses at gas stations. Examples of such couplings are shown in U.S. Pat. Nos. 5,365,973 and 4,827,977, which are owned by the same assignee as the instant invention, and which are incorporated herein by reference. As is known, such couplings are provided to stop the flow of gasoline through the hose should a customer inadvertently forget to remove the fuel delivery nozzle from his car before leaving a gas station. When breakaway couplings are used, should a customer forget to remove the nozzle, the coupling will separate, and the valves therein will close to prevent a gasoline spill. However, depending upon the force of the separation, the fuel dispensing equipment can be damaged. It is thus important that the fuel dispenser and its associated components be inspected by trained personnel prior to putting the pump back into service. 
     Current breakaway couplings, however, require very little force to put the coupling back together. For example, in the coupling of the above noted patents, the coupling can be connected with as little as 10 lbs. of force. When the breakaway coupling is disconnected, the customer may attempt to reconnect the coupling. To prevent a customer from reassembling breakaway couplings, shear pin safety breakaway couplings have been developed. However, typical shear pin safety breakaways have a higher separation force than a reconnectable safety breakaway. Thus, dispensing equipment is subjected to undue forces during a driveaway. Shear pin safety breaks are also susceptible to pin degradation. Such degradation is due to nozzle imparted line shock, and can result in nuisance separation. 
     BRIEF SUMMARY OF THE INVENTION 
     A coupler is provided for a breakaway coupling for a fuel line, such as in a gas station fuel line. The breakaway coupling requires in excess of 150 lbs. of force to assemble and disassemble its two fittings, and the coupler is provided to enable someone to assemble (or disassemble) the coupling without the need to exert so much force. 
     The breakaway coupling includes a first fitting which is received in a second fitting. The first fitting includes a hollow sleeve defining a fuel flow path, a check valve movable in the sleeve between a closed position and an opened position to close and open the fuel flow path, openings around a distal end of the first fitting sleeve, and detent balls received in the openings and movable radially in the openings. 
     The second fitting includes an outer hollow sleeve sized to receive the first fitting sleeve and an inner hollow sleeve which is slidably received in the outer sleeve. The outer sleeve has a groove or a series of detents on an inner surface positioned to receive the detent balls when the first and second fittings are assembled together. The inner sleeve defines a fuel flow path through the second fitting and includes a check valve movable in the sleeve between a closed position and an opened position to close and open the fuel flow path. The inner sleeve has a reduced diameter section defining an annular space between the inner and outer sleeves. A latch ring is positionally fixed to the reduced diameter section outer surface. A stop on an inner surface of the outer sleeve limits axial movement of the inner sleeve relative to the outer sleeve. 
     A spring (made from a plurality of spring washers) is positioned between the outer sleeve stop and the latch ring and biases the inner sleeve to normally bear against the outer sleeve stop. The latch ring being positioned to be substantially aligned with the groove when the inner sleeve is in its normal position. Hence, the latch ring will urge the detent balls radially outwardly to engage the groove or detents to hold the two fittings together. To assemble or disassemble the coupling, the force of the spring member must be overcome. The spring member has a spring force greater than the force which can be easily generated by an average person. For example, the spring force is at least 150 lbs. 
     The coupler includes an open ended housing having a side wall and an end wall. A plate is received in the housing and is axial movable in the housing. A cam on an outer surface of the housing end wall is operatively connected to the plate by a rod extending through the housing end wall. The cam has a camming surface and is pivotable between a first position in which the camming surface is out of engagement with the housing end wall and a second position in which it engages the housing end wall. The coupler plate is securable to the second fitting inner sleeve. Preferably, the peripheral surface of the plate is threaded, and the inner surface of the second fitting inner sleeve is threaded, so that the plate can be threadably attached to the inner sleeve. 
     The coupler housing end wall is sized to abut an end surface of the second fitting outer sleeve when the plate is mounted to the second fitting inner sleeve and when the cam is in the first position. As the cam is moved from its first position to its second position, the coupler plate is pulled toward the housing end wall, thereby pulling the second fitting inner sleeve axially in the outer sleeve against the force of the spring to move the latch ring out of alignment with the groove sufficiently to enable the detent ball to move radially in its associated opening and to disengage the groove (or to insert the first fitting into the housing to a position where the detent balls are aligned with the groove with minimal force on behalf of the assembler). The coupler includes a lever handle which is used to move the coupler cam between its first and second positions. Thus, the coupler relies on the leverage of the handle to overcome the spring force. Thus, even though the spring force is much greater than can easily be generated by an average person, by relying on the leverage of the handle, the spring force can be easily overcome and the latch ring can be moved out of alignment with the detents or detent groove to permit assembly or disassembly of the coupling. 
    
    
     BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS 
     FIG. 1 is a perspective view of a fuel delivery nozzle and associated hose with a breakaway coupling in the hose; 
     FIG. 2 is a cross-sectional view of a prior art breakaway coupling when uncoupled; 
     FIG. 3 is a cross-sectional view of the prior art breakaway coupling when coupled; 
     FIG. 4 is an exploded view, partially cut away, of the breakaway coupling of the present invention along with a coupler which can be used to both couple and uncouple the coupling; 
     FIG. 5 is a cross-sectional view of the breakaway coupling when assembled; 
     FIG. 6 is a cross-sectional view of the breakaway coupling in a coupled position with the uncoupler mounted to the coupling; and 
     FIG. 7 is a cross-sectional view similar to FIG. 6, but with the uncoupler moved to a position which allows for only slight force to be used to uncouple or couple the breakaway coupling. 
     Corresponding reference numerals will be used throughout the several figures of the drawings. 
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     The following detailed description illustrates the invention by way of example and not by way of limitation. This description will clearly enable one skilled in the art to make and use the invention, and describes several embodiments, adaptations, variations, alternatives and uses of the invention, including what I presently believe is the best mode of carrying out the invention. 
     Referring initially to FIG. 1, a flexible fuel dispensing hose H has a dispensing nozzle N at its end. The opposite end of the hose H is connected, as is known, to a fuel source such as a tank or a conventional gasoline pump (not shown). A breakaway coupling C is inserted in the hose H, and, as is known, operates to cut off the flow of fuel and vapors through the hose should the coupling be uncoupled, such as by someone driving away from the gas station prior to the nozzle being removed from his car. 
     Nozzle N is of a standard type known in the industry incorporating stage II vapor recovery features, and is designed to dispense fuel such as gasoline into a container such as the gasoline tank of an automobile or into a gasoline can, etc. In this particular embodiment, the nozzle is of the type that has an internal vapor recovery mechanism and is designed to be used with a flexible concentric fuel hose which has the vapor recovery portion of the fuel hose concentric to the fuel flow portion of the fuel hose. 
     A prior art breakaway coupling  1  is shown in FIGS. 2 and 3. The coupling  1  includes two fittings  3  and  5  which are mated together, as described below. The first fitting  3  is downstream and is connected either to the back of the nozzle N or to the portion of the hose extending from the nozzle N. The second fitting  5  is the upstream portion, and is connected to the portion of the hose H extending from the fuel source (i.e., the gas pump). 
     The first fitting  3  includes a nut-like member  7  which is threaded, as at  9 , so that the fitting  3  can be connected to the nozzle, or the fuel line leading to the nozzle. A sleeve  11  extends forwardly from the nut-like member  7  and, as described below, is sized to be received in the second fitting  5 . The sleeve  11  has generally cylindrical internal walls  13  which define a fuel passageway  15  and generally conical walls  17  therein to provide a valve seat for seating a check valve  19 . 
     A spider mount  21  having a plurality of fins  23  is housed in member  7  and includes a sleeve  25  extending axially through the fitting sleeve  11 . The spider  21  is positionally fixed within member  7  by a retaining ring  27  and provides a means for supporting the check valve  19  within the fitting  7 . The check valve  19  contains an integral sleeve  29  which slides on spider sleeve  25 . The sleeve  29  defines a vapor flow path  31 . A spring  33  surrounds spider sleeve  25  and is positioned between the spider fins  23  and the back of the check valve sleeve  29 . The spring  33  thus biases against the back surface of valve sleeve  29  thereby normally biasing the check valve  19  forwardly within fitting  7  to seat against the fitting wall  17 . An O-ring  35  is mounted upon the surface of valve  19  to provide a sealed closure when check valve  19  seats against valve seat  17 . Check valve  19  has an opening  37  at its forward end defined by a circular wall  39 . 
     A series of apertures  41  are formed at the forward end  43  of fitting sleeve  11 . Each aperture holds a detent ball  45  which is fixed within the aperture  41  by peening or any other structural holding means which provides for limited radial movement of the balls  45 . 
     The second fitting  5  also includes a nut-like member  51  having a series of internal threads  53  which are designed to connect the fitting  5  to the up-stream portion of the hose H. An internal sleeve  55  extends from the member  51  and fits securely inside an outer sleeve  57 . The outer sleeve is sized, at its forward end  58 , to receive the first fitting sleeve  11 . The internal sleeve  55  is stepped as at  59  and  61  to define reduced diameter sections of the sleeve  55 . A retaining ring  63  which is fixed within a groove in the outer sleeve  57  provides a stop against which the step  59  rests to limit axial movement of the inner sleeve  55  relative to the outer sleeve  57 . A ring  65  surrounds the inner sleeve  55  just below the first step  59 . The ring  65  includes inner and outer circumferential grooves which receive inner and outer O-rings to provide a fluid tight seal between the inner sleeve  55  and the outer sleeve  57 . A second ring  67  surrounds the sleeve  55  spaced axially from the first ring  65 . The second  67  ring is also grooved to provide a seat for inner and outer O-rings to provide a second fluid tight seal between the inner sleeve  55  and the outer sleeve  57 . A latch ring  69  is axially fixed to the inner sleeve  55  spaced from the second ring  67 . The latch ring  69  is fixed to the sleeve  55  by a retaining ring, but could be secured in other manners as well. A series of pre-loaded wave or disc springs  71  are positioned between the rings  65  and  67 , and a further wave or disc spring  73  is positioned between the ring  67  and the latch ring  69 . An inner groove  74  is positioned on the inner wall of the outer sleeve  57  such that it is partially overlapped by the latch ring  69 . 
     The inner wall  75  of the inner sleeve  55  defines a fuel passageway  76  and a valve seat  77 . A spider mount  79  having a plurality of fins  81  and a spider sleeve  83  is positionally fixed within the inner sleeve  55  by means of the retaining ring  85 . The spider mount  79  supports a check valve  87  within fitting  5 . The check valve  87  has an integral sleeve  89  which is sized to slide over sleeve  83 . An O-ring  91  is provided on the valve  87  to form a seal when the valve  87  seats against the valve seat  77 . An O-ring  93  is provided on the end of the spider sleeve  83  to prevent leakage of fluid between the sleeves  89  and  83 . A spring  95  is positioned between the spider fins  81  and the check valve sleeve  89  to bias the check valve  87  forwardly to normally be in a closed position (as seen in FIG.  2 ). An elongate cylinder  97  extends away from check valve  87  and through, and beyond the end of, the inner sleeve  55 . The cylinder  97  includes a retaining ring  98  and an O-ring  99  at its back end. The cylinder  97  is sized to be received within the opening  37  of the first fitting check valve  19 . 
     To assemble or couple the first fitting  3  to the second fitting  5 , the first and second fittings are aligned so that the second fitting cylinder  97  will pass into the first fitting check valve opening  37  and so that the first fitting sleeve  11  will pass into the second fitting outer sleeve  57 . The two fittings are pressed together until the detent balls  45  in the first fitting are received in the groove  74  in the second fitting outer sleeve. As the first fitting is pressed into the second fitting, the respective check valves of the two fittings will be opened to allow for the flow of fuel and vapors through the coupling  1 . 
     Upon exertion of force, detent balls  45  become disengaged from detent groove  74 . In the prior art device of FIGS. 1 and 2, the force required to disengage the coupling is considerable, on the order of 200 lbs. Similarly, only a slight amount of pressure is required to assemble the two fittings together. As discussed above, because only a slight amount of pressure is required to reassemble the fitting, when a coupling is disengaged, often the customer will simply reassemble the coupling, rather than report the incident. Thus, the gas station operator may not know if the coupling was disengaged, and whether the hose (or the coupling) needs to be checked for possible damage. Therefore, a potentially damaged coupling or hose can be placed into use. 
     The breakaway coupling  101  of the present invention is shown in FIG.  5 . It includes a first fitting  103  and a second fitting  105  which are mated together as will be described below. Unlike the prior art coupling  1 , the breakaway coupling  101  requires a substantial amount of force (i.e., more force than can easily be generated by an average person) to recouple the coupling. For example, the coupling can require upwards of 200 lbs. of force to be recoupled. Because this amount of force is not easily generated by an average person, a coupler  106  (FIG.4) is provided. The coupler  106  attaches to the back end of the second fitting  105 , as will be discussed below, and enables the two fittings to be easily assembled together without the need for the assembler to exert a significant amount of force. 
     The first fitting  103  is downstream and is connected either to the back of the nozzle N or to the portion of the hose extending from the nozzle N. The second fitting  105  is the upstream portion, and is connected to the portion of the hose H extending from the fuel source (i.e., the gas pump). 
     The first fitting  103  includes a nut-like member  107  which is threaded, as at  109 , so that the fitting  103  can be connected to the nozzle, or the fuel line leading to the nozzle. A sleeve  111  extends forwardly from the nut-like member  107  and, as described below, is sized to be received in the second fitting  105 . The sleeve  111  has generally cylindrical internal walls  113  which define a fuel passageway  115  and generally conical walls  117  therein to provide a valve seat for seating a check valve  119 . 
     A spider mount  121  having a plurality of fins  123  is housed in member  107  and includes a sleeve  125  extending axially through the fitting sleeve  111 . The spider  121  is postionally fixed within member  107  by a retaining ring  127  which is received in a groove in the member  107 . The spider  121  supports the check valve  119  within the fitting  107 . The check valve  119  contains an integral sleeve  129 , which slides on spider sleeve  125 . The sleeve  129  defines a vapor flow path  131 . A spring  133  surrounds spider sleeve  125  and is positioned between the spider fins  123  and the back of the check valve sleeve  129 . The spring  133  thus biases against the back surface of valve sleeve  129  thereby normally biasing the check valve  119  forwardly within fitting  107  to seat against the fitting wall  117 , when the fittings are separated (for example, as seen in the prior art fittings of FIGS.  1  and  2 ). An O-ring  135  is mounted upon the surface of valve  119  to provide a sealed closure when check valve  119  seats against valve seat  117 . Check valve  119  has an opening  137  at its forward end defined by a circular wall  139 . 
     A series of apertures  141  are formed at the forward end  143  of fitting sleeve  111 . Each aperture holds a detent ball  145  which is fixed within the aperture  141  by peening or any other structural holding means which provides for limited radial movement of the balls  145 . 
     The second fitting  105  also includes a nut-like member  151  having a series of internal threads  153  which are designed to connect the fitting  105  to the up-stream portion of the hose H. An internal sleeve  155  extends from the member  151  and slidingly fits inside an outer sleeve  157 . The outer sleeve  157  is sized, at its forward end  158 , to receive the first fitting sleeve  111 . The internal sleeve  155  is stepped as at  159  and  161  to define reduced diameter sections of the sleeve  155 . A retaining ring  163 , which is fixed within a groove in the outer sleeve  157 , provides a stop against which the step  159  rests to limit axial movement of the inner sleeve  155  relative to the outer sleeve  157 . A ring  165  surrounds the inner sleeve  155  just below the first step  159 . The ring  165  includes inner and outer circumferential grooves which receive inner and outer O-rings to provide a fluid tight seal between the inner sleeve  155  and the outer sleeve  157 . A second ring  167  surrounds the sleeve  155  spaced axially from the first ring  165 . A series of pre-loaded wave or disc springs  171  are positioned between the rings  165  and  167 . A retaining ring  168  is received in a groove along the outer surface of the inner sleeve  155 , and the second ring  167  rests against the retaining ring  168 . As can be seen, the first ring  163 , the spring washers  171 , and the second ring  167  are positioned between the retaining rings  163  and  168  to limit axial movement of these elements. 
     As noted above, the retaining ring  163  is received in the inner surface of the outer sleeve and the retaining ring  168  is received in the outer surface of the inner sleeve. Thus, the spring washers  171  normally urge the inner sleeve  155  inwardly, relative to the outer sleeve  157 . 
     A latch ring  169  is axially fixed to the inner sleeve  155  spaced slightly forwardly of the second ring  167 . It is held in place on the sleeve  155  by a retaining ring  170 , but could be secured in place in any other conventional manner. An inner groove  174  is positioned on the inner wall of the outer sleeve  157  such that it is partially overlapped by the latch ring  169 . 
     The inner wall  175  of the inner sleeve  155  defines a fuel passageway  176  and a valve seat  177 . A spider mount  179  having a plurality of fins  181  and a spider sleeve  183  is positionally fixed within the inner sleeve  155  by means of the retaining ring  185 . The spider mount  179  supports a check valve  187  within fitting  105 . The check valve  187  has an integral sleeve  189  which is sized to slide over the spider sleeve  183 . An O-ring  191  is provided on the valve  187  to form a seal when the valve  187  seats against the valve seat  177 . An internal O-ring  193  is provided near the top valve sleeve  189  to form a fluid tight seal between the valve sleeve  189  and the spider sleeve  183 . A spring  195  is positioned between the spider fins  181  and the check valve sleeve  189  to bias the check valve  187  forwardly to normally be in a closed position. (The check valve is shown to be opened in FIGS.  5  and  6 ). An elongate cylinder  197  extends away from check valve  187  and through and beyond the end of, the inner sleeve  155 . The cylinder  197  includes a retaining ring  198  and an O-ring  199  at its forward end. The cylinder  197  is sized to be received within the opening  137  of the first fitting check valve  119 . 
     When the coupling  101  is assembled, as seen in FIG. 5, the first fitting sleeve  111  is received in the second fitting outer sleeve  157  and the detent balls  145  are received in the groove  174 . The detent balls  145  are held in the groove  174  by the latch ring  169 . The force of the spring washers  171  urge the sleeve  155  forwardly to the position seen in FIG. 5 to maintain the detent balls  145  in the groove  174  and to prevent the balls  145  from being disengaged from the groove  174 . Additionally, the cylinder  197  is received in the first fitting check valve opening  137  and the cylinder O-ring  199  seals against the opening wall  139 . When the coupling  101  is assembled, the check valves  119  and  187  will be pushed back against their respective springs  133  and  195  so that the check valves  119  and  187  will be in their opened positions. The check valves  119  and  187  and the cylinder  197  define a vapor recovery flow path which is in fluid communication with the vapor recovery flow path through the hose H. When the check valves are opened, the annular space between the sleeves  155  and  111  and the check valves  119  and  189  and the cylinder  197  defines the fuel flow path which fuel follows from the fuel source (gas pump) to the nozzle N. Thus, when the check valves are closed (as when the fittings are separated from each other), the fuel flow path is closed, and fuel cannot flow from the gas pump through the hose. 
     To disassemble the coupling  101 , the detent balls  145  must be disengaged from the detent groove so that the fittings  103  and  105  can be separated from each other. In order to do this, the force pulling the fittings apart must exceed the force of the spring washers  171  (which bears against the sleeve  155  to hold the detent balls  145  in the groove  174 ). The spring washers  171  are designed such that the force required to disassemble the coupling  101  is more than can be easily generated by the average person. For example, in the preferred embodiment, the force required to separate the first and second fittings is 200 lbs. Although this force cannot easily be generated by a person, it can be fairly easily generated by a car being driven from a gas pump with the fuel nozzle still in its fuel tank feed pipe. Thus, the coupling will still become disassembled and accomplish its purpose (i.e., to shut off the flow of fuel and vapors through the hose H when the coupling is disassembled). Additionally, this amount of force is less than the tensile strength of the hose, and the hose should not be damaged when the coupling  101  is separated. 
     Because significant force is required to disengage the coupling  101 , the same amount of force is required to assemble the coupling  101 . To assemble the coupling (i.e., to connect the first and second fittings such that the detent balls  145  are received in the groove  174  and held in place by the ring  169 ), the force of spring washers  171  must similarly be overcome. To make this task easier, the coupler  106  is provided. As described below, when the coupler  106  is used, the coupling  101  can be assembled very quickly and very easily without the need for the person assembling the coupling to exert a significant amount of force. 
     The coupler  106  (FIGS. 4,  6  and  7 ) includes an outer body  201  having a side wall  203  and an end wall  205 . The body  201  is opened at its end opposite the end wall  205 , and the side wall has an end surface  207 . A shaft  209  extends through the body end wall  205 . The shaft is not fixed to the body end wall  205 , and hence, can rotate relative to the body end wall  205  and the body  201 . A plate  211  is positionally fixed to the end of the shaft  205  within the body  201  so that the plate  211  will rotate with the shaft  209 . As shown, the shaft  209  is threaded at its end, and the plate  211  is secured to the shaft  209  by bolts which sandwich the plate  211  and frictionally hold the plate in place on the shaft  209 . Any other conventional means, such as welding, can be used to secure the plate  211  to the shaft  209 . The shaft  209  and plate  211 , can, in fact, be a single unitary piece. The plate  211  is externally threaded along its peripheral wall  213 . 
     A cam  215  is pivotally connected to the opposite, outer, end of the shaft  209 . The cam  215  has a pair of spaced apart cam legs  217 , each of which has a camming surface  219 . A cam plate  221  extends between the cam legs  217  and a handle  223  extends from the cam plate  221 . A pin  225  extends between the cam legs  217  and through the shaft  209  to pivotally mount the cam  215  to the shaft  209 . 
     The operation of the coupler  106  is shown in FIGS. 6 and 7. Although the coupler  106  is shown being used to uncouple the coupling  101 , it will be apparent that the manner in which the coupler  106  operates is the same whether it is being used to assemble or disassemble the coupling  101 . The coupler  106  is initially mounted to the end of the second fitting  105  by threading the coupler plate  211  into the threads  153  of the nut-like member  151 . The plate  211  is threaded into the member  151  until the end surface  207  of the coupler body wall  203  engages the end surface  222  of the second fitting outer sleeve  157 . 
     When the coupler  106  is mounted to the second fitting  105 , the lever  223  is pivoted from the position shown in FIG. 6 to the position shown in FIG. 7 to bring the camming surfaces  219  in contact with the body end wall  205 . When the lever  223  is pivoted in this manner, the coupler body end surface  207  bears against the second fitting outer sleeve  157 , and the plate  211  is pulled upwardly toward the end wall  205 . When the plate  211  is pulled upwardly, the plate  211  pulls with it the second fitting inner sleeve  155  and thus moves the sleeve  155  slightly outwardly relative to the outer sleeve  157 . When this happens, the spring washers  171  are compressed, and, more importantly, the latch ring  169  is pulled out of alignment with the outer sleeve groove  174  allowing the balls  145  to move radially in their openings  141 . Thus, when the coupling  101  is being disassembled, the detent balls  145  can move radially inwardly in their holes to disengage the groove  174 . The first fitting  103  can then easily be removed from the second fitting  105 . Conversely, when the coupling  101  is to be assembled, when the coupler is operated to move the ring  169  out of alignment with the groove  174 , the first fitting  103  can be easily inserted into the second fitting  105 . When the lever  223  is then moved to its position, as seen in FIGS. 4 and 6, the second fitting inner sleeve  155  is moved back to its normal position, and the ring  169  will urge the detent balls radially outwardly into the groove  174  to lock the two fittings together against the force of the spring washers  171 . 
     As can be appreciated, the use of the lever relies on the use of leverage to overcome the force of the spring washers  171  to enable the coupling  101  to be assembled or disassembled. When the coupler  106  is used, the assembler need exert a force which can be easily generated by the average person (i.e., 5-10 lbs.) against the lever to overcome the force of the spring washers  171  to assemble and disassemble the coupling  101 . 
     As various changes could be made in the above constructions without departing from the scope of the invention, it is intended that all matter contained in the above description or shown in the accompanying drawings shall be interpreted as illustrative and not in a limiting sense. For example, the groove  174  could be replaced with detents positioned to receive the detent balls  145 . This would require that the first and second fittings be keyed so that the detent balls would be aligned with the detents when the coupling is assembled. The spring washers  171  could be replaced by a spiral spring. The retaining ring  163  provides a stop to limit axial movement of the inner sleeve  155  relative to the outer sleeve  157 . This ring  163  could be replaced with a shoulder, circumferential rib, or other similar structure formed on the inner surface of the outer sleeve  157 . The retaining ring  168  and the second ring  167  of the second fitting  105  could be omitted. In this case the springs  171  would bear directly against the latch ring  169 . The spring force of the spring  171  can be altered as desired. All that is necessary is that the spring force be greater than that which can be easily generated by an average person and less then the tensile strength of the hose H. A spring force of at least 150 lbs. should be sufficient. These examples are merely illustrative.