CA1284804C - Tension actuated uncoupler - Google Patents

Abstract

Abstract of the Disclosure A tension actuated fuel (e.g. gasoline) delivery hose uncoupler is disclosed in which, upon a predetermined tension load being applied to the delivery pump hose, the coupling will automatically uncouple thus releasing one end of the hose which, for example, may remain inserted in the fuel tank of a vehicle driving away from the fuel dispensing pump, and the other portion of the hose which is permanently affixed to the pump. The coupler includes normally closed check valves which, upon uncoupling of the coupler, close thereby preventing spillage of fuel. Further, the coupler is adjustable so that it may be calibrated to uncouple at predetermined tension loads. The uncoupler is structured so as to substanially eliminate the effects of fluid (e.g., gasoline) delivery pressure on the tension load required for uncoupling.

Description

~L2~

TENSION ACTUATED UNCOUPLER

_ross Reference to a Related Applicatio This appllcation relates -to improvemen-ts in the invention disclosed in Canadian Pa-tent Application Serial No. 432,457 filed July 14, 1983.

Backqround o~ the Invention This inven-tion relates primarily to a tension actuated coupler for a fuel (e.g. gasoline) pump delivery hose which will permit one portion of the hose to be uncoupled upon a tension load of predetermined magnitude being applied to the hose thereby to prevent damage to a fuel delivery pump or station. Alternatively, the tension actuated uncoupler of this invention may be incorporated in the lines supplying the Euel delivery station or pump such that iE the pump is run into by a vehicle forceably tearing the pump from its moorings, the supply lines will automatically uncouple and seal. More speciEically, this invention relates to such a coupler in which the hose portions, when uncoupled, are sealed so as to prevent the spillage of gasoline or other li~uid fuel. Still further, this uncoupler is adjustable so that it may be calibrated (preferable at the fac-tory) to accurately uncouple a-t predetermined load levels such that the hose is not uncoupled at unduly low loads, but yet which will be reliably uncoupled at predetermined tension loads so as to positively prevent damage to the fuel delivery pump. Also, this uncoupler is so constructed so as to substantially eliminate inadvertent uncoupling of the uncoupler caused by internal liquid pressure.
In recent years, the advent of self service gasoline retail establishTnents has become a major, if not the predominant, manner in which gasoline and other petroleum fuels are sold at retail. Because customers utilizing sel~ service gasoline pumps are not experienced gasoline service station attendants, and because they do this only occasionally and may be unfamiliar with the gasoline pump, its operation, and the gasoline service station's procedures for dispensing the gasoline and for payment, oftentimes a customer will dispense a quantity of gasoline into his vehicle's tank, pay for the gasoline, re-enter his car and begin to drive away from the service station pump island before he realizes that he has not removed the gasoline pump dispensing nozzle from the filler neck of his fuel tank. In many instances, the nozzle will pull out of the filler neck of the gasoline tank and fall harmlessly to the ground. However, in certain other instances, it is possible to exert exceedingly high tension loads on the fuel delivery hose leading from the delivery pump to the nozzle. More specifically, as an automobile drives oEf, it is possible to exert such a high orce on the delivery hose that either the hose is ripped or torn from the pump, or that the delivery pump is torn free of its moorings to the service station pump island. In either instance, the potential exists for a significant spillage of volatile liquid fuel. Because of the close proximity of electrical power within the gas pump for lighting and the like and because these electrical wires may be ripped from the pump as the pump is pulled from its moorings, electrical sparks oftentimes will ignite any spilled Euel. O~ course, with the close proximity of other vehicles and patrons within the service station, the potential exists for personal injury to several such persons in the event such a pump is pulled from its moorings and considerable physical damage may result to the service station such that it would be closed for a considerable length of time for repairs thus representing a significant economic loss to the operators.
In states which require a vapor recovery system for capturing hydrocarbon (e.g., gasoline) vapors as the vehicle is fueled, it would be necessary for the vapor collection system also to prevent damage to the fuel dispensing pump in the event the vehicle drives away from the fueling site with the filling and vapor collection systems attached or inserted in the fuel tank filler neck.
These problems have been recognized in the past.
Certain safety code requirements require that the spout Eor the dispensing nozzle be of breakaway construction such that at moderate loads, the spout will pull clear of the nozzle thus preventing excessive loads from being applied to the pump. However, in actual practice, the fact that pumps are regularly pulled clear of their moorings would indicate that the concept of the breakaway nozzle does not, in all cases, adequately protect agains~ such accidents. Additionally, reference may be made to U.S. patents such as 584,144, 2,048,388, 2,536,702, 3,883,042 and 4,098,438 which are in the same general field as the present invention.
For many years, dispensing pumps in gasoline stations and the like have been prone to being knocked over by vehicles in instances where the vehicle is errantly driven or is involved in an accident. Typically, dispensing pumps are moored to the service station pump island by means of bolts or the like and delivery pipes for the Euel Erom underground storage tanks are coupled to piping within the dispensing pump. Oftentimes, in the event of a collision, the dispensing pump will be ripped free of its moorings and the supply lines to the pump will be ruptured. Fuel (e.g., gasoline) is typically delivered to the dispensing station or pump from underground storage tanks by a submersible pump. In the event the dispensing pump is ripped free of its moorings and in the event the submersible pump is in operation, it will be appreciated that considerable ~uantities of volatile fuel may be expelled Erom the broken supply lines. In an effort to limit the amount of fuel that can be discharged upon a pump being ripped free o its moorings, certain pilot actuated diaphragm valves and other saEety devices have been developed which block the flow of fuel upon the pump being ripped from its moorings. One such pilot actuated diaphragm valve is shown in U.S. patent 4,284,212. However, these various safety means for blocking the flow of fuel from the ruptured supply lines are complex and add considerably to the cost of installing the delivery pump.

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Clark, U.S. patent 2,860,983 reco~nized this long-standing problem of gasoline dispensing pumps being subject to "pull-away" accidents. Clark dislcosed a ball de-tent coupling which broke away under tension, such as during a pull-away acciden-t.

F~ecently, an uncoupler, substantially identical to FIG. 7 of the previous Canadian paten-t application Serial No. 432,457 filed July 14, 1983, and to F:[G. 7 herein, was made and sold under license to Emco 10 Wheaton of Conneaut, Ohio,. While this uncoupler worked well for its intended purposes, as stated in the above-men-tioned Canadian paten-t application it was Eound, in actual field use, that the uncoupler wouldr under very low application of tension loads thereto, or even under no tension load condition, inexplicably uncouple. I-t was found that the dispensers on which these uncouplers were installed are dispensing gasoline at pressure levels far above the pressure levels considered to be maximum desirable opera-ting pressures, as set forth in standards established by 20 Underwriters Laboratory ~U.L.). Thus, even in view of such prior art uncouplers as disclosed in Scheiwer U.S. patent 2,536,702, and Clark U.S. pa-ten-t 2,860,893, and in view of the instant inventors' earlier embodiment as disclosed in FIG. 7 herein, a need continued Eor a tension actuated uncoupler which not only would reliably uncouple at a predetermined tension load applied thereto, but which was substantially unafeec-ted by variations in fluid pressure levels therewithin or by fluid pressure levels considerably above normally expected operating pressure levels.

Further, in the uncoupler discussed above and shown in FIGS. 7-9 herein, it was somewhat difficult to couple the male fitting ~o the female fitting because sufficient axial insertion forces must be applied to the fittings to cam the locking balls ou-twardly and to cause the locking collar to compress its respective spring. ThiS is especially true when installing the uncoupler in an overhead dispenser, as shown in FIG. 11, because the installer oftentimes must stand on a ladder to re-couple the uncoupler and it is awkward to apply high insertion loads to the uncoupler while standing on a ladder.
In fueling vehicles with liquid propane or liquid natural gas fuels, there has been a need for means that would prevent a spillage of fuel in the event the vehicle drove away from the fueling area with the fueling hose still connected to its fuel tank.
In other applications, automatic quick coupling kits are available for use on hydraulic systems for farm implements and the like which are connected to a tractor and which are powered by the hydraulic system on the tractor such that if the implement becornes inadvertently uncoupled from the tractor, the hydraulic Eittings will automatically and instantaneously break away. Such fittings are commercially available Erom the Pioneer Quick Coupling Division of Parker Corporation, Minneapolis, Minnesota.
Rowever, these so-called breakaway hydraulic hose couplings require brackets to hold the Eemale coupling and these breakaway couplings have no means for adjusting the force at which the couplings will break away or pull apart. Because of this inability to adjust the breakaway force and because of the wide variety of Euel delivery pumps, a single breakaway tension force would not be acceptable.
ntion ~ mong the several objects and features of this invention will be noted the provision of a tension actuated uncoupling Eitting which may be readily installed on existing service station fuel de].ivery pumps and which may be adjust.ed for a particular pump so as to have an uncoupling force which insures that the fitting uncouples at a predetermined tension load level so as to prevent damage to the delivery pump on which it is installed;
The provision of such a tension actuated coupling device which will reliably operate after extended periods of service and under a variety of adverse weather conditions;
The provision of such a tension actuated uncoupling device which may be readily retrofitted to existing fuel delivery pumps without substantial modofication to the pump and which permits the ready replacement of pump delivery hoses;
The provision of such a tension actuated uncoupling device which when uncoupled, instantaneously blocks both the portion o the hose remaining attached to the delivery pump and the portion of the hose attached to the nozzle so as to prevent the spillage of any substantial amount of fuel;

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The provision of such a tension actuated uncoupling device which is protected by a suitable abrasion and impact resistan~ covering so as to prevent damage to automobiles being serviced and so as to protect the coupling fitting;
The provision of such a tension actuated uncoupling device which may also be installed between the fuel lines within the delivery pump and the underground fuel delivery line leadiny :Erom underground supply tanks to the pump island so that in the event a vehicle collides with a delivery pump and rips it free oE its moorings to the pump island, the flow of fuel Erom both the pump and the delivery lines will be instantaneously blocked;
The provision of such a tension actuated uncoupling device in which the tension force required to uncouple the device is substantially unaffected by fluid pressure within the device;
The provision of such an uncoupling device which is easy to manually couple, without the use of tools, even when standing on a ladder;
~0 The provision of such a tension actuated uncoupling fitting which is of lightweight and yet rugged construction, which operates reliably, and which i5 economical to manuEacture and to use; and The provision o:E such an uncoupling device which when it is inadvertantly uncoupled, such as by the driving away of an vehicle with the fuel delivery nozzle remaining inserted in the filler neck of the vehicle such as to cause an uncoupling action of the uncoupler, the hose sections may be readily coupled together such that the ùndamage~ pump may be quickly put into service by the service station operator.

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Other objects and features of this invention will be part apparent and in part pointed out hereinafter.
Briefly statedl a tension actuated uncoupling device of this invention is intended for use in a fuel dispensing system, such as in a service station or the like, having a pump for delivering liquid fuel (e.g., gasoline) via a supply line from a reservoir (such as an underground tank) to a fuel dispensing station. This fuel dispensing station (oftentimes referred to as a fuel delivery pump) has a flexible delivery line or hose with a nozzle at its free end for controlling the delivery of fuel into the fuel tank of a vehicle. More specifically, the improvement of this invention comprises means installed in a line (i.e., in either the supply line or the delivery hose) for uncoupling at least a portion of the line from another portion of the line and for substantially instantaneously blocking the flow of fuel from both portions of the line upon the uncoupling thereof in the event a tension load of a predetermined value is applied to the line upon, for example, the vehicle driving away Erom the pump with the nozzle remaining inserted in the vehicle's fuel tank or upon a vehicle colliding with the dispensing station. The uncoupling means comprises a female quick disconnect fitting secured to one of the line portions and a male quick disconnect fitting secured to the other of the line portions with the male fitting being sealably received within the female fitting thereby to permit the flow of fuel through the line. The male and female fittings each have a substantially similar ~4~

diameter wetted by the fuel Elowing therethrough for substantially eliminating the pressure of the fuel from effecting the predetermined value of the tension force required to uncouple the fittings. The coupler further includes releasable locking means for securing the male fitting within the female fitting, this locking means comprising a plurality oE detent balls or other locking members spaced Erom one another around the female member and being movable radially inwardly and outwardly. A
circumferential groove is provided in the male member in register with the balls when the male and female members are sealably secured together. Further, means is provided on the exterior o~ the ~emale fitting engageable with the balls for resiliently biasing the balls inwardly toward a locking position in which they are at least in part received in the groove on the male fitting thereby to prevent the male and female fittings from being uncoupled, but yet, upon a tension load in excess of a predetermined value being applied to the line portions, the groove on the male member exerts a camming action on the balls forcing the balls radially outwardly thereby to permit the uncoupling oE the line portions at the predetermined tension load.
Further, the above-mentioned means for resiliently biasing the balls inwardly comprises an axially movable collar cammingly engageable with the balls, a barrel on the outside of the balls and the collar, and a spring between a portion of the barrel and the collar for biasing the balls radially inwardly toward their locking positions. The uncoupler has selectively operable means which permit the barrel to move axially with respect to said uncoupler between a release position in which the spring is relatively unstressed such that it is relatively easy to insert the male fitting into the female fitting and an operable position in wh.ich the spring operatively holds the balls in their locking positions such that the line portions will uncouple only upon application o~ the predetermined tension load.
In another embodiment of the present invention, means is provided for applying a fluid or hydraulic back pressure against the above-said means engageable with the balls thereby substantially eliminating the effect of fluid pressure on the tension load required to effect uncoup].ing.
Brîef D ~ ~b~e~D~rawings FIG. 1 is a perspective view of an automobile in a service station having liquid fuel (gasoline) dispensed into the fuel tank of the automobile via a conventional fuel dispensing station or pump with a tension actuated uncoupling device of the present invention installed in the fuel delivery hose between the pump and the dispensing nozzle on the free end of the hose;
FIG. 2 is a view similar to FIG. 1 in which the automobile has driven away :Erom the pump island with the delivery hose remain.ing in the fuel inlet to the automobile's gasoline tank and in which the uncoupling device of this invention has been actuated by the application of a tension load of predetermined value on the hose permitting uncoupling oE the hose portions without 3 substantial spillage of fuel and without damage to the delivery pump;

FIG. 3 is an enlarged side elevational view of the coupling device of the present invention illustrating a female quick disconnect member resealably receiving a ma].e disconnect member;
FIG. 4 is a longitudinal cross sectional view of at least a portion o:E the coupling device of the present invention illustrating means for se~alably locking the male quick disconnect member within the female quick disconnect memher and further illustrating means for a~justably varying the magnitude of the tension force required to be applied to the hose sections thereby to permit uncoupling of the hose sections;
FIG. 5 is a front elevational view of a dispensing station or pump secured to a pump island or other foundation and a fuel delivery line leading from an underground fuel supply tank to the dispensing station with a coupling device coupling fuel lines within the dispensing station to the fuel delivery line;
FIG. 6 is a cross-sectional view of another embodiment of the coupling device of the present invention;
FIG. 7 is a cross-sectional view of still another embodiment o the uncoupling device of the present invention;
FIG. 8 is a view si~nilar to FIG. 7 of a variation of the uncouplin~ device of the present invention in which the seal between the male and :Eemale Eitting is positioned on approximately the same diameter as the maximum wetted diameter of the fittings thereby to substantially eliminate the tendency oE pressure forces within the fittings :Erom effecting the tension force required to uncouple the ~ittings;

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FIG. 9 is also a view similar to FIG. 7 illustrating another means for substantially equalizing -fluid pressure forces exerted on the ~itt.ings;
FIG. 10 is a view of a dispenser having its base mounted to a pump island illustrating the uncoupler of the present invention installed in the dispensing hose between the dispenser and the nozzle assembly with ~lexible hose portions on both sides of the uncoupler so as to ensure that a true tension load is applied to the uncoupler in the event of a "pull-away" accident, as shown in FIG. 2;
FIG. 11 is a view similar to FIG. 10 showing the uncoupler installed on an overhead dispenser;
FIG. 12 is a view similar to FIGS. 7-9 showing still another embodiment of the uncoupler in which the force of the spring biasing the locking balls toward their locking position may selectively be released thereby to permit the coupling of the uncoupler without having to apply relatively high axial insertion loads necessary Eor the locking balls to cammingly move the locking collar against the full force oE its compression spring; and FIGS. 13-15 are, respectively, front, side, and rear elevational views of a barrel surrounding the locking balls, collar and spring carried by the female :Eitting.
Corresponding reEerence characters indicate corresponding parts througho~t the several views o:E the drawings.

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Descr~e~ion of Preferre,d, Embo ~
Re~erring now to the drawings, a fuel dispensing system (i.e., a service station) is indicated in its entirety by reference character 1. As is typical, the service station includes a number of fuel dispensing stations 3, which are normally referred to as pumps.
~owever, these so-called fuel pumps oftentimes do not contain a pump therein, but rather are merely a metering and control station. In this disclosure, however, the term gasoline pump will be utilized to refer to the dispensing station 3. As is typical, the gasoline pumps in a service station are mounted on a pump island or foundation 5 located on the driveway or the service station. Each of the gasoline pumps 3 includes a cabinet 7 which is anchored to the pump island by bolts 9 (see FIG. 5).
As is conventional, gasoline pump 3 includes a fuel dispensing line or hose, as generally indicated at 11, having a manually operated fuel dispensing nozzle 13 on the free end of hose 11 which is selectively manually operable by a person dispensing fuel thereby to control operation of pump 3. Nozzle 13 includes a spout (not shown) which is lnserted into the filler neck of the fuel tank of an automobile A (or other vehicle) for the delivery of fuel into the fuel tank of the automobile. Fuel is delivered to pump 3 by means of a submersible pump 15 (see FIG. 5) via an underground Euel delivery line 17 from a tank T.
Oftentimes, pump 15 will supply fuel to a plurality of gasoline pumps 3. Pump 3 further includes fuel lines 19 within the pump for providing communication between fuel delivery line 17 and fuel dispensing hose 11.

A tension ac-tuated coupler, as generally indicated as 21, is provided within fuel dispensing hose 11 Eor permitting the flow of fuel therethrough when coupled and for uncoupling a-t least one portion 23 of fuel dispensing hose 11 (i.e., the outer portion including nozzle 13) frorn the other portion 25 oE the hose upon the app].ication of a tension load to the hose o.E a predetermined value thereby to prevent or minimize damage to gasoline dispensing pump 3. Additionally, upon uncoupling Oe the hose, coupler 21 substantially instantaneously blocks the flow of fuel from both portions 23 and 25 of the hose thereby to prevent any substantial spillage of fuel and thereby to minimize fire hazards.

More particularly, fuel dispensing hose 11, intermediate its ends, has a swaged female fitting 27 sealably secured to the first hose portion 23 extending from the upper end of pump 3. A female coupling fitting, as generally indicated at 29, is sealably threaded into the swaged female fitting 27. The other half of coupler 21 is constituted by male fitting, as indicated at 31, which is sealably received within female fi-t-ting 29 when male and female Eittings are sealingly coupled together. A threaded nipple 33 extends from the end of the male fitting 31 and :is received in a swaged Eemale fitting 35, similar to swaged .Eemale fitting 27, with this last-said swaged fitting sealably secured to the second portion 25 of fuel dispensing hose l:L.

;

More specific~lly, female fitting 29 is constituted by a female body 37 having a flow passage 39 therethrough with a counterbore 41 in its inner end for receiving the outer portion of male fitting 31. As indicated at 43, female body 37 has a plurality of openings 43 therein extending circumferentially around the female body with each of these openings receiving a respective locking member or detent ball 45. Balls 45 are movable relative to female body 37 radially inwardly and outwardly with respect to female body 37 for purposes as will appear.
Female body 37 further includes a check valve member 47 movable between a closed position (not shown) in which the flow of fuel through central bore 39 is blocked and an open position (as shown in FIG. 4) in which fuel may readily flow through coupler 21 from gasoline pump 3 to nozzle 13. A check valve spring 49 biases check valve member 47 to its closed position. Within central bore 39 oE
female body 37 a snap ring stop 51 is provided so as to serve as an abutment for check valve spring 49. A check valve seat 53 is formed within central bore 39 and is engagable with check valve member 47 when the latter is in its closed position to block the flow oE fuel as described above. The outwardly Eacing shoulder, as indicated at 54, oE seat 53 constitukes a limiting abutment within counterbore 41 adapted to engage the outer end oE male fitting 31 and to prevent inward movement of the male fitting relative to female fitting 29 beyond a predetermined axial distance (i.e., the location of shoulder 54).

Male fitting 31 is constituted by a male fitting body 55 having a central bore 57 extending axially therethrough, the central bore 57 of male fitting body 55 being generally coaxial with central bore 39 of female body 37 when the male fitting is coupled to the female Eitting as shown in FIGs. 3 and 4. As indicated at 59, a circumferential detent groove is provided around the outer end of male fitting body 55 generally in register with detent ball openings 43 in female body 37 when the male and female fittings 29 and 31 are sealably coupled together whereby detent balls 45 may move radially inwardly into register with circumferential groove 59 thereby positively preventing withdrawal of the male fitting from its coupled position within emale fitting 29. As best shown in FIG. 4, circumferential groove 59 has beveled sîdewalls 60 which constitute cam ~aces en~ageable with the detent balls 43 -for cammingly forcing the detent balls radially outwardly upon applying a longitudinal or axial tension load to hose portions 23 and 25. It will be appreciated that if this radially outwardly camming action of beveled cam faces 60 oE
circumferential groove 59 are of sufficient magnitude so as to forceably move balls 45 out of the circumferential groove, female and male Eittings 29 and 31 will become uncoupled and are free to move axially away from one another.
Male fitting 31 has an outer end 61 engageable with shoulder 54 in counterbore 41 oE female body 37 when the male and eemale fittings 29 and 31 are sealably coupled together as shown in FIGS. 3 and 4. Further, male fitting ~Z8~

31 includes a normally closed check valve 63 substantially identical in cons-truction with check valve 47 heretofore described. It will be noted that both check valve 47 and check valve 63 have portions thereof which extend out beyond shoulder 54 of female fitting 29 and which extend out beyond the outer end 61 of male fitting 31 when -the male and female fittings are uncoupled and when the check valves are in their closed positions. Upon inserting male :Eitting 31 into counterbore 41 of :Eemale fittiny 29 and upon :Eorcing the fittings into coupling engagement such that deten-t balls 45 come into register with circumferential groove S9, the protruding ends of check valve members 27 and 63 engage one another and force the check valves from their closed positions to their open positions against the bias of their respective check valve springs. In this manner, the check valves of the male and female fittings are automatically opened upon coupling of coupler 21 and, of course, upon uncoupling of the coupler, the check valves will automatically close thus blocking khe flow of fuel the:refrom. In addition, counterbore 41 includes a seal 64 engageable with the outer end of male fi-tting body 55 as the latter is inserted into the counterbore thereby to positively prevent leakage Oe :Euel :rom the coup].er.

Coupler 21 includes means 65 engageable with detent balls ~5 for biasing the detent balls radially inwardly relative to female fit-ting body 37 and for permitting radial inward and outward movement oE the balls relative to the female fit-ting body. More speciEically, this biasing means 65 is shown to comprise a split collar, as indicated generally at 67, having a plurality of collar members 69 movable independently of one another and engageable with the outer surfaces of respective detent balls 45. Further, means 65 is shown to comprise a circumferential spring 71 engagable with the outer face of split collar 67 for resiliently biasing collar members 69 and the detent balls 45 engageable therewith radially inwardly relative to female Eitting body 37 thereby to maintain the detent balls in engagement with the base of circumferential groove 59 in male fitting body 55 and thereby to positively maintain male fitting 31 in coupled relation with female fitting 29. It will be appreciated that as detent balls 45 are caused to move radially outwardly relative to female body fitting 37, such as by an outward camming force applied to the detent balls by beveled cam faces 60 of circumferential groove 5~ upon the application oE an axial tension load to the male and female fittings, circumferential spring 71 will stretch or ~ increase in length thereby permitting collar members 69 and balls 45 to move radially outwardly.
As best shown in FIG. 4, each collar member 69 extends around a portion of the outer surface of female fitting body 37 and has a first contact point 73 engagable with the outer surEace of its respective detent balls 45 and a second contact point 75 engageable with the outer surface of female fitting body 37, the first and second contact points being spaced axially from one another. Additionally, collar members 67 have another con-tact poin~ intermediate the first contact point 73 and -the second con-tact point 75, this intermediate con-tact point being constituted by a circumferential groove 77 formed in the outer faces of the collar memhers thereby to constitu-te a retaining groove for circumferential spring 71. It will be understood -that, during :Eabrication o:E collar members 69, the location of intermediate groove 77 relative to the first contact point 73 (i.e., relative to the point of contact of the split collar mernbers on the outer surfaces of its ~espec-tive detent balls 45) determines the amount of inward biasing force of the circumferential spring 71 on the deten-t balls.
More specifically, iE the location of intermediate groove 77 is located directly over the point of contact of the split collar members 69 on the detent balls, the maximum inward biasing force is exerted on the detent balls. However, as the location of intermediate groove 77 moves axially away from the balls toward the location of -the second contact point 75, the inward biasing force exerted on the balls proportionately decreases.

Further, coupler 21 is provided with adjustable means for varying the axial tension load applied to :Eittings 29 and 31 required to permit uncoupling of -the rnale and female :Eittings such that the coupler will break apart upon -the applica-tion o:E a predetermined axial tension load thereto. In -the coupler described above, it will be appreciated that by exchanging one circumferential spring 7 having a first spring cons-tant for ano-ther circum:Eerential ~2~4~
spring having a higher or lower spring constant, the inwardly biasing forces exerted on the detent balls may be selectively varied. E'ur-ther, by shiEting the location of the circumferential groove 77 on the outer surfaces of collar member 69 toward and away from the first contact point 73 (i.e., toward or away from the point oE contact of the collar mernbers on the detent balls), -the inwardly resilienk biasing Eorce of the spring 71 on the detent balls may be varied. Also, by changing the angle of beveled cam surfaces 60 of circumferential groove 59 on male fitting body 55, the outward camming force exerted on the balls by an axial tension load on -the fittings 29 and 31 required for uncoupling thereof may be varied.

Still further it will be understood that circumferential spring 71 may be mounted on an ad~ustable screw-type mounting fixture (not shown), similar to a conventional hose clamp, such that the inward biasing force of the spring may be readily varied by adjusting the screw clamping arrangement thereby to increase or decrease the length of the spring. However, it is believed that it be preferable that the adjustment of the predetermined break away tension force Eor coupler 21 should only be done "at the factory" such that Eield service personnel and service station attendants will not be tempted to change the tension loading on spring 71 as this could cause uncoupling of coupler 21 at abnormally low or high tension forces.

The force at which coupler 21 will reliably uncouple is a matter to be determined, depending upon the particular application of coupler 21. For example, if coupler 21 is installed in gasoline dispensing hose 11 and if the gasoline pump 3 is of a known design or model, then it can be determined what magnitude of tension load can be safely transmitted by the pump from hose 11 to the mounting of gasoline pump 3 on its foundation or pump island 5 without damage to nozzle 13, to gasoline dispensing hose 11 and without damage to the gasoline pump. Preferably, the predetermined axial tension load at which coupler 21 will reliably uncouple is selected such that the uncoupling force is, at all times during normal operation of gasoline pump 3, above the normal tension loadings usually imposed on the gasoline delivery hose by normal operations. However, in the event, for example, fuel dispensing nozzle 13 remains inserted in the filling neck of the fuel tank of an automobile A or other vehicle (as shown in FIGS. 1 and 2) and in the event the driver of the vehicle drives the vehicle away from the pump island thus placing an abnormally high axial tension load on the gasoline delivery hose 11, coupler 21 will uncouple thus preventing the application Oe excessive loads on noz%le 13, on fuel delivery hose 11 and on gasoline pump 3 so as to minimize or prevent damage thereto. Further, upon uncoupling of the male and female Eittings, the check valves ~7 and 63 thereo will automatically close thus preventing the spillage oE any sub~tantial amount o~ fuel and thus substantially reducing any potential fire hazard.

~2~48~

Fur-ther, coupler 21 may be utilized to connect the fuel delivery lines 19 within cabinet 7 of gasoline pump 3 to the underground fuel delivery lines 17 supplying fuel to gasoline pump 3 from submersible pump 15. Thus, in the event a substantial tipping Eorce would be applied to the gasoline pump, either caused by an automobile pulling away Erom the pump island with nozzle 13 remaining inserted in the Eiller neck of the vehicle's gasoline tank or caused by a collision between the vehicle and the gasoline pump, the pump will pull free oE -the fuel supply lines 17 and coupler 21 and will prevent any substantial spillage of fuel. It will be appreciated with pump 15 supplying volatile fuel to a plurality of gasoline pumps 13, in instances where gasoline pump 13 is torn from its mounting on pump island 5, pump 15 could continue to deliver substantial quantities of the volatile fuel via the Euel delivery line 15 and thus could create a substantial risk of fire or explosion.

Further, it will be appreciated that with coupler 21 installed on Euel dispensing hose 11, the coupler may be utilized to permi-t the ready exchange of one fuel delivery hose and nozzle assembly with another. Thus, servicing of the nozzles and of the dispen~ing hoses could be readily facilitated. Stil]. Eurther, it will be appreciated that the coupler 21 oE the present invention incorporated in a new fuel dispensing hose and nozzle assembly can be readily retrofitted -to existing gasoline delivery pumps 3 without substantial modiEication to the gasoline pumps. Thus in a ~2l!~8~
short time, all of the gasoline delivery pumps a-t a service station could readily be converted to include the couplers 21 of the presen-t inven-tion.

Also, those skilled in the art will recogni~e that fluid pressure within coupler 21 may exert an a~ial tension load on female fitting 27 and on male fitting 31 such that upon the Eluid pressure within hose 11 exceeding a predetermined pressure level, coupler 21 will automatically uncouple.

Referring now to FIG. ~, another embodiment of the tension actuated coupler is shown in detail, as it is installed on the fuel delivery hose 11. In the disclosure of the second emb~diment of this tension acutated coupler, the coupler is indicated in its entirety by reference character 21'. It will be understood that corresponding parts for the second embodiment of the coupler having a similar construction and function as parts heretofore described in regard to coupler 21 will be indicated by "primed" reference numbers and thus the construc-tion and operation of these components or parts of coupler 21' will not be described in detail for the sake of brevity.

The primary di.EEerence in construction and operation between coupler 21 and coupler 21' is the fact that while both oE the couplers are tension actuated devices intended to uncouple hose portions 23 and 27 from one another upon -the axial tension forces applied to delivery hose 11 or 11' exceeding a predetermined value, coupler 21 - 2~ -~4~

operated on the principle of a camming action being applied to the detent balls 45 by the cam sur~aces 60 in circumferential groove 59 of the male fitting member with these camming forces forcing the detent balls radially outwardly and causing the split collar members 69 to move radially outwardly against the bias of circumferential spring 71. ~lowever, in the second embodiment of the coupler 21', a tension force exerted on the hose is reacted through a shear member, as generally indicated at 81, carried by Eemale fitting body 37' such that the shear member will Eail and shear at a predetermined axial tension load thereby permitting a collar 83 slidably mounted on the exterior of female body 37' to move axially from a retaining position (as shown in FIG. 6) in which the collar surrounds the detent balls 45' and positively prevents the detent balls from moving radially outwardly thus keeping the detent balls engaged with circumferential groove 59' and thus positively coupling the male and female fi-ttings together to a retracted position (i.e., axially shifted to the right as shown in FIG. 6) and which an enlarged inner diameter portion 85 o~ collar 83 moves into register with the detent balls thus permitting the detent balls to move radially outwardly away Erom the male collar members and thus permitting uncoupling oE the hose.
As best shown in FIG. 6, the tension Eorce exerted on slidable collar 83 is exerted through a lanyard 87 securely fastened to the collar and to hose portion 25' with a kink or slack portion, as indicated at 89 provided, in hose portion 25' such that lanyard 87 transfers subs-tantially all of the tension forces in the hose to slidable collar 83. I:-t will be appreciated that shear member 81 may be made oE a relatively easy shearable material, such as lead, brass, or the like whose shear forces may readily be determined such that the shear member 81 will fail reliably at a predetermined -tension load.
Further, once the shear member 81 has failed and once the collar has moved from lts retaining to its released position thus permitting the uncoupling of the hose portions, it will be appreciated that lanyard 87 is so designed as to readily fail under tension forces before any permanent damage may be done to the fuel dispensing station 3 or to the hoses.

As described above in regard to coupler 21', upon the coupler 21 uncoupling, the check valves incorporated within the male and female fittings will instantaneously close thereby preventing the spillage of any substantial amount of fuel.

Referring now to FIG. 7, st.ill another embodiment of tension actuated uncoupler is generally indicated by reference character 21". This other embodiment of tension actuated uncoupler oE the p:resen-t invention is generally similar in construction and operation to the tension uncouplers hereto:~ore descrlbed and the "double primed" reference cha:racters indicate parts having a similar construction and Eunction as parts heretofore disclosed in regard to tension actuated uncoupler 21. Thus, the description of the construction and function of these corresponding parts will not be herein set forth in detail.

Among the prirnary differences between the tension actuated uncoupler 21", as shown in FIG. 7, and tension actuated uncoupler 21, as shown in FIG. 3, is the fact that the means of biasing the securing means or detent balls 45"
inwardly toward their securing position thus holding male fitting 31" coupled and sealed within counterbore 41" of Eemale ~eitting 29" is shown to comprise a collar 101 slidable axially on the outside of Eemale body member 37"
from a retaining position (as shown in FIG. 7) to a released 10 position (not shown, but to the left oE the position of collar 101 shown in FIG. 7) in which detent balls 45" are free to move radially outwardly relative to male body member 55" thus permitting the male and female body members to be uncoupled relative to one another. An outer sleeve 103 is mounted on female body member 37" and encloses slidable collar 101 and permits the collar to move within the space between the inner surface of the outer body member 103 and the outer surface of female body member 37". A compression coil spring 105 is interposed between the end of slidable Z collar 101 opposite detent balls ~5" and a portion of cover member 103 so as to resiliently bias the slidable collar toward its securing position in which the slidable collar holds detent balls ~5" in their locking position, i.e., within groove 57" of male fitting body 55". Further, collar 101 has a cam face 107 thereon engageable by the outer surface of detent balls ~5". It will be understood that upon an axial tension force being applied to the male body member 55" and to the female body member 37", such as upon ~z~
the longitudinal stretching of the opposite ends of the fuel line or hose portions attached thereto, cam surfaces 60"
forming at least in part groove 59" on male body part 55"
exerts a force on detent balls 45" which tends to move the detent balls radially outwardly within opening ~3" of female body member 37" such that the outer faces of the detent balls 45" bear against cam face 107 of slidable collar 101 and exert a component of axially directed force on collar 101 which tends to move collar 101 against the bias of spring 105 thereby to move the collar toward its retracted position and to permit the balls to move out of engagement with cam surfaces 60" of groove 59" and thereby to permit uncoupling of the male and female body members.
It will be appreciated that the tension force at which uncoupler 21" will uncouple will may be varied by adjusting the compression force of spring 105. This may be done by changing one spring for another having a different spring constant. Alternatively, instead of using a snap ring 111 to hold cover 103 in place, as shwon in FIG. 7, cover 103 may be threaded (not shown) on female fitting 37"
so that the cornpression of spring 105 may be regulated.
It will also be appreciated that the axial force exerted on collar 101 is dependent on the angle oE cam faces 60" and cam face 107 on collar 101. By varying the angles of these cam faces, and by changing the spring constant of spring 105, the axial tension forces exerted on tension uncoupler 21 can be selectively varied so that the tension uncoupler 21" will break apart at a preselected axial load applied thereto.

~%~

Further referring to FIG. 7, it will be appreciated that check valve members 47" and 61" are slidably each carried by a respective spider arrangement 109 within the male and female body parts and that the spider members 109 having openings therethrough (not shown) Eor the flow of fluid through fitting 21" when the fitting is in its coupled position as shown in FIG. 7. The spider members :L09 are Eixedly held in place by means oE snap rings 51". Further, it will be appreciated that cover 103 is Eixedly held in place by means of a snap ring 111 which is fitted in place on the exterior of female body fitting 37" and which is received in a corresponding circumferential groove therein.
Each of the check valve members 47" and 61" has a corresponding seal 113 thereon which is engagable with the bore 39" of female fitting body 37" and with bore 57" of male body fitting 55" when the check valve members are in their closed position thereby to positively shut aff the flow of fluid through the fitting members when the fitting 21 is in its uncoupled position.
Even more specifically, it will be noted in FIG. 7 that female body member 37" has a plurality of apertures or openings 43" therein for receiving balls 45" and that the side walls 4~" defining apertures 43" are tapered such that the apertures diverge or expand in a radially outward manner. With the side walls 44" of apertures ~3" tapering outwardly, balls ~5" are free to move radially outwardly upon a tension load being applied to fitting 21" such that the beveled cam surfaces 60" on male body member 31"

cammingly forces the balls 45" outwardly. It will be appreciated that by tapering sidewalls 44", as shown in FIG.
7, the sidewalls are not able -to exert any appreciable frictional force on balls 45" as the balls are forced radially outwardly within their respec-tive openings 43".
Further, those skilled in the art will recogni~e that upon uncoupling, because of the mechanical advantage of cam surface ~0" on balls 45" and of balls 45" on cam :face 107 oE
collar 101, even a relatively small Erictional -Eorce exerted 10 by side walls 44" on balls 45" will require a substan-tially greater tension force to ef:Eect uncoupling. Also, because of the nurnber of balls 45" (e.g., 4-8 balls), the force required to effect uncoupling may vary considerably, depending on how many balls 45" bear on the ~alls 44" of apertures 43" and depending on the resistance afforded to each of the balls. By tapering side walls 44" outwardlyl as shown in FIG. 7, the side walls diverge away from the radial path of the balls and consti-tute a ramp on which the balls may roll without exerting substantial resistance to outward 20 movement oE the balls, but yet preventing substantial axial movement of the balls relative to female fitting member 37".

Referring now to FIG. 8, another embodiment of the tension actuated uncoupler constructed in accordance with the present invention is ind.icated in its entirety by reference character 21a. Ilncoupler 21a is generally similar to uncoupler 21" hereto.Eore described and shown in FIG. 7. Parts of uncoupler 21a having a corresponding function and construction as do parts of uncoupler 21" are denoted by the suf:Eix "a" on the re~erence characters. The primary difEerence between uncoupler 21a and 21" is that uncoupler 2la includes means 150 for substantially eliminating the effect of internal fluid pressure with the uncoupler on the predetermined tension force required to uncouple the uncoupler.
More specifically, uncoupler 21a differs from uncoupler 21" in that the outer end o male fitting 31a is necked down by means of an inwardly tapered shoulder 151a having an axially extending end 153a. Likewise, the female bore ~la of female fitting 31a has an inwardly sloping shoulder 155a having a circumferential groove 157a at the inner end thereof. An o-ring seal 159a is received in groove 157a. O-ring 159a is analogous to seal 64 shown in FIG. 7, except o-ring 159a is moved radially inwardly such that the wetted and unwetted radii of uncoupler 21 are substantially equal. Even more preferably, the wetted and unwetted radii of the uncoupler would be equal thereby to minimize or even eliminate entirely the tendency of fluid `

pressure forces acting on the male and female Eittings so as to substantially eliminate the efEect of fluid pressure on the tension load applied to the uncoup]er so as to result in uncoupling.
In FIG. 9, still another embodiment of the uncoupler oE the present invention is indicated in its entirety by reference character 2]b, with reference characters having a "b" suEfix indicating similar parts having a construction and function similar to those parts heretofore described. ~lowever, uncoupler 21b differs in 3L2~

that it includes means, as indicated at 200, ~or hydraulically coun~erbalancing the effect of fluid pressure exerted on the male and female fittings 31b and 29b, respectively, so that internal fluid pressure within the uncoupler has substantially no effect on the tension loads required to result in uncoupling of the uncoupler. More specifica]ly, hydraulic counterbalancing means 200 includes a port 201 providing communication between central bore 39b of female fitting 29b and an annular chamber 202 defined by the outer surface of female body 37b and the inner surface of sleeve 103b. Slidable collar lOlb is sealed relative to female fitting body 37b and relative to sleeve 103b by seals 203b so as to permit axial sliding movement of collar lOlb without leakage of fluid post seals 203b.
In accordance with this invention, the area of collar lOlb against which fluid pressure in chamber 202 acts is substantially equal to the area of fittings 29b and 31b against which fluid pressure acts to exert an uncoupling force on the uncoupler. This area of the uncoupler against which fluid pressure acts to exert an uncoupling Eorce on the Eittings is an annulus defined by the difference between the unwetted radius and the wetted radius, as shown in FIG.
9. ~rhus, with Eluid flowing through the fittings, the uncoupling Eorces exrted on Eittings 29b and 31b due to fluid pressure Eorces acting on the annulus defined by the difference between the wetted and unwetted radii of the fittings tends to force balls 45b radially outwardly which in turn tends to force collar lOlb toward its retracted ~ 32 -position (i.e., toward the left, as shown in FIG. 9). This uncoupling force is opposed by the hydraulic or fluid pressure forces of the system fluid acting on sleeve lOlb.
Of course, upon a tension load applied to fittings 29b, 31b equal to or greater than the predetermined uncoupling load, the ~ittings will uncouple in the manner heretofore described substantially unaffected by fluid pressure within the uncoupler. Additionally, those skilled in the art will appreciate that a pilot valve (not shown) in communication with chamber 202 could be provided to dump ~luid pressure ~rom chamber 202 such that fluid pressure acting on fittings 29b, 31b would uncouple the fittings upon the fluid pressure being above a predetermined pressure level.
Referring now to FIGS. 10-15, in FIGS. 10 and 11, two different fuel dispensers are illustrated utilizing still another embodiment oE the uncoupler of the present invention, with this other embodiment illustrated in its entirety by reference character 301. As shown in FIG. 10, dispenser 3 is essentially identical to the dispensers illustrated in FIGS. 1 and 2, in that the dispenser is mounted at it~ base on pump island 5. In FIG. 11, the so-called overhead dispenser is illustrated by reference character 3a, in which the dispensin~ hose 11 is suspended from the top of the dispenser substantially above head level. For example, the top portion oE dispensing hose 25 may be located approximately ten feet above ground level.

Still further in accordance with this invention, uncoupling unit 301 is substantially identical to uncoupler 21a, shown in FIG. 8. Since uncoupler 301 is substantially similar to uncoupler 21a heretofore described in regard to FIG. 8, parts of uncoupler 301 having a corresponding function and construction as do the same or similar parts of uncoupler 21a, these parts of uncoupler 301 are denoted by the suEfix "c" on the reference characters in FIGS. 12-15.
The primary di:Eference between the uncoupler 301 and uncoupler 21a is the manner in which the spring Eorce of spring 105c of uncoupler 301 may be released so as to facilitate coupling and locking of the female and male .fitting members 29c and 31c together without the necessity of having to overcome the full force of spring 105c, and once the male and female members are properly connected, to relatively easily permit the full force of spring 105c to resiliently bias locking balls 45c radially inwardly (relative to the female and male members) toward their locking positionj as shown in FIG. 12. It will be appreciated that this facilitates installation and coupling of the male and female fitting members without the use of even simple hand tools, and, even when the installer is standing on a ladder, Eacilitates recoupling the fitting members of uncoupler 301 on an overhead dlspenser 3A, such as is shown in FIG. 1]..
As was heretoEore described in regard -to uncouplers 21" and 21a, the outer barrel or cover 103 was fixedly held in place by means oE a snap ring 111. rrhe spring 105 was interposed between a shoulder on the barrel or cover 103, and the aft end of slidable collar 101 (i.e., the end of the collar opposite cam face 107), such that the spring 105 biases the slide collar toward its position as shown in FIG.
12 so as to cammingly hold the locking balls 45 in their radially inward position in engagement with circumferential groove S9.
Upon inserting male member 31 into female member 29, it was necessary that the balls be cammed radially outwardly, and that the slide collar 101 be moved to the rear compressing spring 105 an amount sufficient to permit the balls to move into engagement with the circumferential groove 59 in male member 31. This often required insertion forces of a relatively high level (e.g., 50-125 pounds).
While the insertion forces were not, in many cases, the same as the tension breakaway loads (due to a shallower cam angle of portions of the outer surface of the male body 55 which cammingly engaged balls 45 as the male and female members were inserted) these insertion forces were nevertheless relatively high. It will be appreciated if the installer were standing on a ladder so as to couple the fittings of uncoupler 301 as shown in FIG. 11, it could be a relatively difficult task to manually exert such insertion Eorces.
In accordance with this invention, cover or barrel 103c oE uncoupler 301, rather than being fixedly locked in place relative to female fitting 29c, is selectively movable from an operable position, as shown in FIG. 12, in which the cover 103c is spaced axially relative to balls ~Sc such that spring lO5c is compressed a desired amount thereby to exert a prede~ermined axial biasing force on collar lOlc which must be overcome by the camming action of cam sur~aces 60c in circumferential groove 59c in male fitting 31c upon application of axial tension loads to hose portions 23 and 25 thereby to overcome the biasing force of spring 105c and to permit slidable collar lOlc to move away ~rom the balls thereby permitting the balls to move radially outwardly from their locking position to their unlocked position, and thus allowing axial separation oE the male and Eemale fi.ttings 31c and 29c, respectively. Further, cover or barrel 103c is axially movable ~rom its locking position toward a release position (not shown) in which the barrel 103c is moved axially away from balls 45c a predetermined amount thereby to release at least some oE the biasing force on spring 105c. Of course, with the biasing force of the spring relaxed, the male fitting 31c may be much more readily inserted into female ~itting 29c and the balls 45c may be much more readily moved radially outwardly toward their unlocked position permitting the balls ~5c to move into register with groove 59c in male fitting 31c. With the male and ~emale members in their coupled position, as shown in FIG. 12, the movable cover or barrel 103c may be moved ax.ially from its released position (not shown) to its operable position (as shown in FIG. 12), in which the Eull biasing ~orce of spring 105c is exerted on collar lOlc.
Barrel 103c may be locked in its operable position.

As best shown in FIG. 14, barrel 103c has a body 3G3 having an inwardly extending circumferential shoulder 305 against which one end of spring 105 is interposed. The rear or righthand portion of body 303 (as shown in FIG. 14) is of reduced inner diameter 307 so as to have a sliding fit on the outer surface of female fittiny 29c. In accordance with this invention, a pair of diametrically opposed pins 309 (see FIG. 12) are provided on opposite sides oE female fitting 29c proximate the rear or right end of barrel 103c when the barrel is in its operable position, as shown in FIG. 12. A first pair of detent grooves, as indicated at 311 (see FIGS. 12 and 15), are provided in barrel 103c so as to engage pins 309, and so as to fixedly hold barrel 103 in its operable position compressing spring 105c its full amount. Spaced at 90 degrees to each of the detent grooves 311, a pair of elongate slots 313 are provided. With barrel 103c in its operable position (as shown in FIG. 12), the barrel may be moved axially inwardly toward collar lOlc a slight amount by further compressing spring 105c so as to move detent grooves 311 out oE engagement with pins 309. In this axial position, the barrel 103c may be rotated 90 degrees in either direction relative to female Eitting 29 so as to move slots 313 into register with pins 309. With the pins 309 in register with the elongate slo~s 313, the manual force on barrel 103c is relaxed and spring 105c will move the barrel axially on the outer surface oE female Eitting 29c from its operable position to its release position (i.e., barrel 103c will move to the right in FIG. 12). The pins 309 will en~age shoulders 315 of the bottoms o~
elongate slots 313 so as to prevent the collar 103c from becoming totally disengaged with female fitting 29c.

In order to couple male fitting 31c and ~emale fitting 29c of uncoupler 301, the collar lOlc is moved to its released position. As heretofore stated, upon inserting male member 31c into female fitting 29ct the locking balls 45c may be moved radially outwardly by the camming action of inserting the male member into the female member such that with spring 105c in its relaxed position, significantly lower i.nsertion forces are required. With the male and female members properly connected, and with barrel 103c in its released position, the spring 105c will exert a sufficient, but relative low, biasing force on the balls so as to positively lock the female and male Eittings together. However, before operation, it is nece~sary that the barrel 103c must be moved axially toward collar lOlc so as to fully compress spring 105c. After the spring has been compressed, the collar is rotated 90 degrees in either direction so that pins 309 move into register with detent grooves 311 in barrel 103c, in which position the barrel is positively maintained in its operative position, and spring 105c is compressed its desired amount. It will be understood that the axial force required to compress spring 105c by axial movement o~ collar 103c is significant].y less than the insertion orces required to move the balls radially outwardly against the full force of spring 1.05c, inasm~ch as the cam angles of cam surfaces 60c and 107c acting on the balls require an axial insertion :Eorce higher than the force required to merely compress the spring.

Additionally, those skilled in the art will recognize that the tension actuated couplers o~ this invention may also have suitable applications for use on the hydraulic systems of various implements, particularly farm implements, which permit uncoupling of hydraulic hoses from the implement to the tractor in the event the implement inadvertantly becomes unhitched from the trac-tor thereby to prevent damage to the hydraulic hoses and to prevent the loss oE hydraulic fluid. Further, those skilled in the art will recognize that the uncoupler of ~his invention would have application in other fuel dispensing systems, such as liquefied propane and liquefied natural gas systems.
; Specifically, if such an uncoupler were used as the dispensing nozzle of a liquefied propane system for filling a vehicle tank, the hose would automatically pull clear of the tank filling coupling upon the automobile driving away from the fuel dispensing pump in the event the attendant or other person dispensing the fuel forgot to disconnect the clispensing hose prior to the vehicle driving away.
In view of the above, it will be seen that the other objects of this invention are achieved ancl other advantageous results obtained.
As various changes could be made in the above constructions without departing from the scope of the invention, it is intended that all matter contalned in the above description or shown in the accompanying drawlng shall be interpreted as illustrative and not in a limiting sense.

Claims (2)

1. A tension actuated uncoupler installable in a line for permitting the flow of a fluid therethrough when coupled and for uncoupling at least a portion of said line from another portion thereof in the event a tension load above a predetermined limit being applied to said line, said uncoupler comprising a female quick disconnect fitting secured to one of said line portions and a male quick disconnect fitting secured to the other portion of said line with the male fitting being sealably secured within said female fitting when said male and female fittings are coupled together thereby to permit the flow of fluid through said line, a plurality of apertures in said female fitting, a plurality of securing balls carried by said female fitting, one said ball in a respective aperture, said balls being engagable with said male fitting for positively holding the fittings together in coupled relation said balls being movable radially inwardly and outwardly between a retaining position in which said balls hold the fittings together in coupled relation and a clear position for permitting uncoupling of the fitting, cam means on said male fitting cammingly engagable with said balls for effecting radial movement of said balls toward the said clear position upon application of a tension load said fittings, a retainer movable axially relative to said female fitting from a retaining position in which said balls are engagable with said male fitting for holding said fittings in coupled relation and a retracted position permitting said balls to move radially thereby to permit uncoupling of said fittings, said retainer having a retainer cam surface for being cammingly engaged by said balls for axial movement of said retainer relative to said female fitting toward its retracted position upon a tension load being applied to said fittings, spring means resiliently biasing said retainer in axial direction toward its retaining position, seal means carried by one of said fittings sealingly engagable with the other fitting, a cover carried by said female fitting surrounding said spring and said retainer, said cover having an inner shoulder thereon with said spring being interposed between said shoulder and said retainer, said cover being axially movable on said female member between and operative position in which said spring exerts an operative biasing force on said retainer such that said tension load above said predetermined limit is required to effect uncoupling of said fittings and a released position in which said spring is at least partially relaxed so as to facilitate coupling of said fittings, at least one protrusion constituting cover holding means extending out from said female fitting and engaging said cover to prevent axial movement of said cover relative to said female fitting by said spring when said spring exerts its operative biasing force on said retainer, and said cover having a slot therein for accommodating said protrusion such that when said slot is in register with said protrusion, said cover is free to move axially relative to said female fitting from its operative to its released position.

2. A tension actuated uncoupler as set forth in claim 1 wherein said cover holding means comprises a pair of diametrically opposed pins protruding outwardly from said female fitting, said cover having a pair of detent recesses therein for receiving a respective one of said pins thereby to positively hold said cover in its operative position, said cover further housing a pair of said slots therein such that with said cover in its operative position upon rotating said cover with respect to said female fitting such that said pins are in register with said slots, said cover may be axially moved between its operative and released positions.