Note: Descriptions are shown in the official language in which they were submitted.
~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
-- 2
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.
~2~
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;
~2~
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.
-- 8 --
~2~
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
-- 10 --
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;
- 12 -
~ 2~34R~
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.
- 13 -
8~
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.
- 14 -
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.
;
- 15 -
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).
- 16 -
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
- 18 -
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,
- 19 -
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
- 20 -
~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.
- 21 -
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.
- 22 -
~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
- 25 -
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.
- 26 -
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
-- 27 --
~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"
- 29 --
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
-- 30 --
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.
- 33 -
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
- 34 -
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.
- 36 -
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.
- 37
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.
- 38 -
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.
- 39 -
