CA1260984A - Coupling - Google Patents
CouplingInfo
- Publication number
- CA1260984A CA1260984A CA000569936A CA569936A CA1260984A CA 1260984 A CA1260984 A CA 1260984A CA 000569936 A CA000569936 A CA 000569936A CA 569936 A CA569936 A CA 569936A CA 1260984 A CA1260984 A CA 1260984A
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- Canada
- Prior art keywords
- packing
- receiving space
- seal
- packing ring
- taper surface
- Prior art date
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Abstract
COUPLING
(Abstract of Disclosure) A quick connect/disconnect coupling for carrying fluid under pressure includes a latch mechanism requiring two independent movements in two different directions for releasing same. The coupling includes improved seals at various locations along with a slide bearing, and improved support fins for internal valves.
The coupling is keyed in a plurality of different mating pairs of body and stem assemblies so that the stem assemblies having different keys cannot be mated together.
(Abstract of Disclosure) A quick connect/disconnect coupling for carrying fluid under pressure includes a latch mechanism requiring two independent movements in two different directions for releasing same. The coupling includes improved seals at various locations along with a slide bearing, and improved support fins for internal valves.
The coupling is keyed in a plurality of different mating pairs of body and stem assemblies so that the stem assemblies having different keys cannot be mated together.
Description
This application is a division of Canadian Application No. 445,548 filed January 18, 1984 for COUPLING.
Back~round of the _ vention This application relates to the art of couplings and, more particularly, to quick connect/disconnect couplings. Although the invention is particularly applicable to couplings of ~he type described and will be explained with particular reference ~hereto, lt will be appreciated that certain eatures of the invention have broader aspects and may be used with other fittings or fluid containing devices such as control valves, check valves, unions, pipe or tube connectors, or the like.
Conven~ional quick connect/disconnect couplings haYe latch mechanis~s which are so easy to release that accidental or unintentional release ~ay occur. It has been found desirable to construct a latch mechanism which requires a conscious effort to release and is protected against accidental release.
Conventional couplings of the type described are also subject to slight leakage when they are uncoupled or to entrainment of air when they are coupled. Likewise, the various seals and packings are subject to blowout and leakage. It would he desirable, therefore~ to provide a coupling with improved seals and packin8s~ and which would be arranged for minimizin8 any leakage or air entrainment when the coupling is connec~ed ~nd disconnected.
Summar~ the Invention A quick connect/disconnec~ coupling including latch ~eans for releaseably la~ching together body and stem coupling members or assemblies. The la~ch means includes operatin~ means in the form of an operating sleeYe movable between latch holding and latch releasing positions. Stop means carried by the operating sleeve cooperates with abutment means for blocking movement of the operating sleeve to its releasing position until the stop ~eans itself is moved to an unblocking position clear of the abutment means. In one arrangement, the stop means takes the form of a small button movable transYersely of the longitudinal axis of the coupling.
Thus, the button ~ust be held in for clearing the abut~ent while the operating sleeve si~ultaneously ~oves longi~udinally to its latch releasing position. ~he abutment means may take the form of an abutment sleeve within which the operating sleeve is closely received, and a spring acting between the abutment and operating sleeves normally biases the operating sleeve to its latch holding position.
The latch members comprise ~etal stampings having first end portions attached to the body assembly for swinging movement of the opposite end portions toward and away from the coupling longitudinal axis.
The other end portions of the latches have inwardly extending la~ch hooks and ou~wardly extending projections. The latch hooks are receivable in a circumferential groove in ~he stem assembly for latching the ste~ assembly to the body assembly. In the latched position of the latch members, the latch projections bear against the inner surface of the operating sleeve.
Upon ~ovement of the operating sleeve to the latch ~v~
releasing position, ~he la~ch projections are cammed outwardly into a recess in ~he operating sleeve formed by an outwardly extending circumferential bead~ This recess has a cam surface which also cooperates with the latch projections for camming same back ~o a latched position when a coupling is a8ain connec~ed. The abut~ent sleeve also has an outwardly extending circu~ferential bead and the button is located between the beads for protecting same against accidental operation. Purther, the abutment and operating sleeves have outer end portions ~Ihich are reYersely curved inwardly for stiffening purposes.
The body coupling member or assembly includes a body part having a slide part longitudinally slidable thereon. The body and slide parts respectively haYe closely facing outer and inner cooperating cylindrical surfaces. The body part has an inner end spaced radially inward fro~ the inner surface of the slide part and a taper surface extends fro~ such body part end to the outer surface thereof. The taper surface includes a slow taper surface extending from the body part inner end toward the outer surface thereof and merging into a fast taper surface adjacent the intersection thereof with the body part outer surface. The taper surface on the body part is spaced from the inner surface of the slide to define a receiYing space for a packing, and the fast taper surface is disposed adjacent the apex of such receiving space. A backup ring is disposed in the receiving space adjacent the apex thereof and a packing ring is also located in the receiving space outwardly of th~ backup ring. Biasing means normally biases the packing ring and backup ring further into the packing receiving space. Both the backup ring and the packing ring are of a deformable material, with the backup ring being harder and less deformable than the packing ring.
L,~
In one arrangement, a cup-like packing gland is closely receive~ wi~hin the body part, and has an inwardly extending flange inside of the body part and an outwardly extending flange outside of the body part~
The outwardly extending flange engages the packing and the biasing means in the for~ of a coil spring acts between the slide and the inner flange of the gland.
Such arrange~ent causes the slide to normally be hiased in a direction off of the body part while simultaneously ~iasing the packing into the packing receiving space.
The slide is movable longitudinally in one direc~ion further onto the body when a coupling is being connected and is movable longitudinally in an opposite direction off of the body when a coupling is being disconnected. During connection of a coupling, transverse forces tend to cause the slide to interfere with the body and inhibit movement o~ the slide in the one direction. Therefore, the outer terminal end portion of the slide includes an inner circumferential bearing recess and an outer circumferential retainer groove. The recess includes a recess slow taper surface which opposes the outer cylindrical surface of the body part and the slope is outwardly away from the body part longitudinal axis when proceeding longitudinally in the one d~rection which is also away from the body valve.
bearing ring has a generally L-shaped cross-sectional shape including a generally axial leg received in the bearing recess and a generally radial leg extending outwardly at the outer terminal end of the slide. The outer surface o~ the bearing rin8 axial leg generally corresponds with the slope of the recess slow taper ~urface. A bearing ring retainer includes an axial cylindrical portion having inwardly extending detents loosely received in the retainer groove and an inwardly extending retainer flange overlying the radial leg of the bearing ring outwardly thereof. Relatively loose reception of the bearin8 retainer detents in the retainer groove allows limited axial ~ovement of the retsiner ring gnd this also allows some axial movement 5 of the beaFing ringO The internal dia~eter of the axial leg on the bearing ring is preferably slightly smaller than the external diameter of the body part. During moYement of the slide in the one direction, the axial leg of the bearing rin8 is forced into the slide recess, and coope~ation between the inner slow taper surface on the slide recess and correspondin~ outer taper surface on the axial leg of the bearing ring callse the axial leg to contract generally radially into firm bearing en8a8ement with the outer surface of the body part.
lS Thus, the slide rides on a bearing ring having a very low coefficient of fric~ion instead of riding directly o~ the outer surface of the body part when the coupling asse~blies are being connected. ~uring movement o~ the slide in an opposit~ direction while uncoupling the parts, the bearing rin8 is not cammed radially inwardly ineo engagement with the outer surface of the body part for providing free separation when transverse forces are ~ini~al.
The body assembly includes an internal body valve haYing a seal engagable by 8 Yalve seat on the slide for closing the slide and body against fluid flow therethrough. The body valve seal has sloping or tapered surace areas on both the internal and external surfaces thereof for creating a oechanical advantage which increases the compressive stress on hi8h points or irregularities. One end and a peripheral end portion of the body valve seal is surrounded by a metal retainer for resisting blowout of the seal~ On the opposite side of the seal from the metal retainer, a positive metal s$op surface is provided for engagement with a cooperating surfflce on the slide. The cooperating s~op surfaces prevent extruslon of the seal.
The body Yalve is essentially supported within the body by an elongated member and the elongated ~e~ber is, in turn, centrally held wi~hin the body by fins.
Fluid flow must take place past the fins around ~he elongated member. Thus, it is desirable to have such fins be as thin as possible while having sufficient strength to resist longitudinal shearing and compressive orces. In accordance with the present invention, the fins are in the for~ of a pair of fin ~embers each having a generally M-shaped configuration in an end Yiew. Each fin ~e~ber includes outer legs connec~ed by a somewhat U-shaped por~ion having a central curved portion. The cen~ral curved por~ion is spaced from the ter~inal ends of ths outer legs and is curved outwardly away therefro~. A pair of fin members are reversely positioned ~ith the outer leg ends engaging one another and with the curved portions facing one another on the periphery of a common circle. A section of the body ~alve elongated member is located between the curYed portions of the fins.
The stem ~ssembly includes a ste~ member havin~
a poppet ~oYable therein between closed and open positions. The poppet has an external circumferential s~al with sloping or tapered surfaces on both the external and internal periphery thereof. The poppet seal is engageable with a seat on the stem member. One end of the poppet and a peripheral end portion of the poppet seal are surrounded by a ~etal retainer for pre~en~in~ blowout of the poppet seal. One side of the ~etal retainer serves as a positiYe metal stop for cooperation with a corresponding stop OTI the stem member to prevent extrus~on of the poppet seal.
The poppet includes a poppet shaft e~tending ax~slly rearward therefro~ to a central openin~ in a guide me~ber. This guide member includes a pluralitr of c~rcumf~entially-spaced spokes ex~ending outwardly from a central portion having the poppet shaft receiving opening therethrough and having an axially extending circular boss. A coil sprinK has one end closely recsiYed over the circular boss on the guide member and the opposite end engaging the poppet for normally biasing the poppet to its closed position.
When a body and stem asse~bly are connected, the ste~ ~e~ber moves beneath the operating sleeve into en~age~ent with the slide for longitudinally moving same away ~rom the body valve. Longitudinal movement of the body and stem assemblies toward one another also causes lS the body val~e to enter one end of the stem member and engage the poppet for moving same to its open position.
Once the latch hooks are received in the external circumferential groove formed in the stem member, the co~ponents are connected together.
A plurality of pairs of keyed hody and stem asse~blies are arranged so that body asse~blies and stem assemblies having different keys cannot be connected with one another. This is acco~plished by Yarying the internal diameter of the operating sleeve, the external dia~eter of the sten me~ber, the external dia~eter of the body ~alve, and the in~ernal dia~eter of the open ste~ ~e~ber end. Assemblies having different keys will not mate due to interference either between a stem me~ber and operating sleeve or between a body valve and an open end of a stem ~ember.
The principal advantage of the present invention is the provision of an improved quick connec~/disconnect coupling.
Another advantage of the invention is the proYision of a quick connect/disconnect coupling having an i~proved latch mechanism.
Another advantage of ~he invention is the provlsion of a quick connect/disconnect coupling having a latch mechanism which requires movements in two different directions for obtaining a released condition.
An additional advantage of the present in~ention resides in proYiding an i~proved fluid coupling having improved seals.
Still another advantage of the invention is found in the provision of a coupling having an improved bearing arrangemen~ between a body and a longitudinally ~ovable slide.
A further advantage of the invention resides in an i~pro~ed arran8ement for biasing a packing into a packing receiving space.
Still a urther advantage of the present i~vention is found in improYed ~rrange~ents for supportin a body valve and a ste~ poppet respectively within a body asse~bly and a ste~ assembly.
Yet another advantage of the invention is in proYiding an improYed keying arran8ement for insuring that only mating pairs of body and ste~ assemblies can be cooperatively joined.
Still other advantages of the present invention ~5 will become apparent to those skilled in the art upon a readin8 and understanding of the following detailed description~
Brief Description of the Drawings The invention may take ~orm in certain parts and ar~angements of parts, a preferred embodiment of which will be described in detail in the specification and illustrated in the accompanying drawings which form a part hereof and wherein:
PIGUR~ l is a side cross-sectional elevational view showing the coupling of the present invention about ~ .3~f:~
to bo conn~cted or just after it has been dissonnected;
FIGURE 2 is ~ view similar to FIGURE 3 showing the coupling in its eonnected configuration;
~ IGURE 3 is a cross-sectional side elevational Yiew of the body asseubly only of ~IGURES 1 and 2;
FIGURE 4 is a cross-sectional side elevational view of the stem assembly only of FIGURES 1 and 2;
PIGURE 5 is a top plan view of an operating sleeYe used in the latch mechanis~;
FIGURE 6 is a top plan view of a stop button;
FIGURE 7 is a cross-sectional view taken generally along linçs 7-7 of FIGURE 6;
FIGURE 8 is an end view of a spring used in association with the stop ~utton of FIGURES 6 and 7;
FIGURE 9 is a cross-sectional view taken generally alon~ lines 9-9 of FIGURE 8;
FIGU~E 10 is a top plan view taken generally on-line 10-10 of FIGURE 8;
FIGURE 11 is an enlarged partial side elevat~onal view in cross-section showing a packing receiving space;
PIGURE 12 shows the axial cross-sectionai conformation of a packinz ring;
PIGURE 13 shows the axial cross-sectional confor~ation of a backup ring;
PIGURE 14 is an enlarged, partial cross-sectional elevationai view showing a slide bearing between ehe Yalve body part and the 51 ide;
~ IGURE 15 shows the axial cross-sectional confor~ation of a seal ring used between a body and stem;
PI~URE 16 is sn end view showing fin ~embers used to support a body Yal~e bol~;
PIGURE 17 i5 a top plan view taken generally along lines 17-17 of EIGURE 16;
PIGURE 18 is a cross-sectional view taken 3~
~en~rally along lines 1~ of FIGURE 17;
FIGURE 19 is an end view showing a guide member for a psppet;
FIGURB 20 is a cross-sectional view taken generally alon~ lines 20-20 of FIGURE 1~;
FIGURE 21 is a partial cross-sectional view si~ilar to PlGUR~ 1 showin~ the various component dia~eters which are ~odified to provide keyed mating pairs of body and ste~ assemblie~; and, FIGURE 2~ is a table showing examples of Yarious dia~eters in FIGURE Zl which provide keyed ~atinB pairs of body and stem assemblies.
Descri~tion of A Preferred E~bodiment Referrin8 now to the drawings wherein the showings are for purposes of illustrating preferred e~bodi~ents of the invention only and not for purposes of llDiting sa~e, PIGURE 1 shows a ~ating pair of body and ste~ coupl ing me~bers or assemblies A and B, respecti~ely, in a position about to be connected upon ~o~e~ent axially toward one another.
~ ody asse~bly ~ includes a body part or ~ember C having ~ slide part D axially slidable thereon. Slide part D ls nor~ally biased to the right in FIGURE 1 into engagement with a body valve E by means of a coil spring 12. Body valve E is attached to sn elongated member or bolt F and held centrsllr within the body part C by support fins Go Stem assembly B includes a stem part or ~ember H haYing a poppet I disposed therein. Poppet I is 30 nor~ally biased to the left in FIGURE 1 into engagement with a seat adiacent an open end of the stem by means of a coil spring 14. Spring 14 surrounds a ~uide shaft or bolt J extending through an opening in a guide member K
agsinst which spring 14 also acts.
When a mated pair of body and stem assemblies A,B are to be coupled, they are posi~ioned as shown in PIGURE 1. It will be noted that the outer end portion of ste~ ~ember H engages the outer end portion of slide part n and, upon moYement of assemblies A,B toward one another, slide part D retracts to the left in FIGURE 1 out o~ en8agement with body Yalve E. At the same time, body valve E enters the open end of s~em member H and engages poppet I to move same away fro~ its seat, i.e., to the right in FlGUR~ 1. Once the assemblies are connected, the parts are arranged as generally shown in PIGURB ~ and fluid flow can take place through ~he conneceed asse~blies.
Body part C is internally threaded as generally indicated at 16 for connection to another fluid conduit. Other interconnecting means could also be advantageously employed, however. An external circu~ferential groove 18 in the body part C loosely recei~es inwardly extending first end portions 20 of a plurality of latch oembers L. These latch members preferably comprise ~etal stampings, and have an arcuate confor~ation in an end Yiew. The opposite end portions of latch ~embers L include inwardly extending latch hooks 22 and outwardly extending latch projections 24.
A generally cylindrical abut~ent sleeve M îs positioned over body part C and has an outer end portion reversely curved inwardly as generally indicated at 28.
Re~ersely curved end portion 28 has an axially extending portion overlying axially extending portions of first end portions 20 of latch members L to loosely hold same within groove 18 for allowing swinging movement of the latch members opposite end portions toward snd away from coupling longitudinal axis ~0. A snap ring 32 recei~ed in a ~uitable external circumferential groove in body part C retains abutment sleeYe M in position. Abut0ent sleev~ M includes an outwardly extending circumferential b~ad 3~1 for stiffenin8 same agalnst a ~eformation, and also includes a ter~inal end 36~
Operating ~eans in the ~or~ of a generally cylindrieel sleeve N surrounds latch ~embers L and has an outer end portion reversely curved inwardly as gen~rally indicated at 40. An outwardly extending circu~ferential bead 42 provides an inner circu~ferential recess 44 havin~ a gradual slope to pro~lde a ca~ surface for cooperation with latch projeceions 24. In the outward released position of latch ~embers L as shown in FIGURE 1, latch projections 24 ~re received in recess of 44~ This relationship also acts to retain operating sleeve N against complete displacement to the ri8ht from body assembly A. A coil spring ~6 is positioned betwe0n the reversely curved outer end portion of abutment sleeve M and the inner ter~inal end of operating sleeve N for nor~ally biasing operating sleeve N away from abut~ent sleeve M.
~ generally rectangular opening 48 in operating sleeve N receives stop ~eans in the form of stop button 0 haYing a downwardly depending leg S0 freely received throu~h a slot 52 spaced sligh~ly froD rectangular opening 4S. ~ generally circular leaf spring P has an upper flat projec~ion 54 received in the recessed underside of button 0 and noroally biases the stop button upwardly in the view of FIGURE 1. Stop button O
has a leading edge 55 with a slow slope to prevent accidentsl cocking of the button when contacted by an external object having relative movement generally toward abutment sleeve M. Stop button 0 also has an inner o~d 56 engageable with abut~ent sleeve inner end 36 to preven~ further ~ovement of operating sleeve ~
within abutment sleeve M to the left in PIGURE 1 until stop button O is depressed for allowing button inner end 56 to pass beneath end 36 of the abutment sleeve. The inner end portion of operating sleeve N is closely received and guided within abutment sleeve M.
Ste~ assembly B includes cooper~ting coupling ~eans on stem member H in the form of a circumferential groove 60 for receiving latch hooks 22. With ~he co~ponents positioned as shown in PIGURE 1, movement of body part C and ste~ ~ember H tow~rd one ~nother causes slide D to retract to the left. At the same time, latch hooks 22 ride along the ou~er surface of slide ~ and an outer sur~ace portion 62 of stem ~ember H until latch hooks 22 reach groove 60. At this point, latch members L swing inwardly for reception of latch hooks 22 within groove 60. Spring 46 disposed be~ween abu~ment sleeve M
and operating slee~e ~, biases operating sleeve N to the lS ri8ht in PIGURE 1. This causes the cam surface portion of recess 44 to cooperate with la~ch projections 24 for urging latch hooks 22 in~o grooYe 60. This also releases ~perating sleeYe N for ~ovement to the ri8ht fro~ the latch releasing position of ~I~URE 1 to ~he latch holding position of FIGURE 2. In ~he latch holding position, the outer ends of latch projections 24 engage the inner cyl indrical surface of operating sleeve N at a location spaced from recess 44 on the opposite side thereof fro~ reversely curved outer end portion 40. Also, the outer end of reversely curved end portion 40 engages an abut~ent 64 on stem memher H for holding operating sleeve N against further ~ove~ent to the right in PIGURE 2. When latch hooks 22 are received in a latching condition in groove 60, the latch members are positioned substantially 36~ around the groove. This relationship enhances the connected relationship between body and stem coupllng members A,B.
With the co~ponents connected as shown in PIGURB 2, such connection requires ~oYement of operating slee~e N to the left until latch projections 24 are '3 generally aligned with recess 4~. However, 8xial ~ove~en~ of operating sleeve N to the left in FIGURE 2 ls preYente~ because terminal end 56 of stop button O
engages terminal end 36 of the abutment means defined by abut~ent sleeve M. In order to free operating sleeve N
for ~ove~en~ to its releasing position, it is necessary to depress stop button O and hold sa~e depressed while operating slee~e N is urged axially to the left so that stop button ter~inal end 56 will pass beneath abutment ter~inal end 36 as shown in FIGURE 1. Th~s, the latch ~eans requires independent movements in ~wo different directions for ~oving same to a releasing position. The ~ovement of button O is generallr toward and away from coupling longitudinal axis 30 with the motion heing generally pivotal about button projection S8 in slot 52. Once recess 44 is generally aligned with latch projections 24, the biasing action of spring 12 urging slide D to the right is also urging stem member }I eo the right. The cooperating cam surfaces between latch hooks 22 and groove 60 cause the end portions of latch members L to be ca~med generally radially outward for reception of latch projections 24 in recess 44.
It will be noted that stop button O is loca~ed bet~een outwardly extending circu~ferential beads 34,42. Preferably, the ~utton does not project above a plane tan8ent to the outer surfaces of both beads 34 and 42, Thus, button O is protected by the beads against accidental ~ovement to its unblocking position ro~ its noroal blocking position where ~oYement of operating sleeYe N to its latch releasing position is prevented.
3uewardly ~xtending circumferential bead 42 on operating sleeve N also perfor~s the unction of providing an abutment a~ainst which a person's thu~b and fingers ~ay act to ~ove operating sleeve N to the left against the 3s bi~sing force of spring 46.
PIGUR~ 5 si~ply shows the rectangular opening 48 and slot 52 in oper~ting sleeve N ~ith more particulari~y.
PIGURES 6 and 7 show the s~op means defined by stop button 0. It will be recognized tha~ stop button 0 is transYersely cur~ed to the gener~l curvature of operating sleeve N. The underside of s~op button 0 is recessed. An outwsrdly extending flange 70 exten~s outwardly from the button undersid~ along abu~ment end 56 thereof and partly along the opposi~e sides thereof toward projec~ion 50. The flanges along the sides of bu~ton 0 ter~inate sufficiently shor~ of the end having downwardly extending projection 50 for allowing the bu~ton to be positioned within and without operating ~lee~e N. When in the uncocked blockin~ position as shown ~n PIGURE 2 to block move~ent of operating sleeve N into abut~ent sleeve M, flange 70 abuts and approxi~ately confor~s to the inner contour of operating sleer~ N par~ially around the rectangular opening 48 while projection 50 extends downwardly through slot 52.
To ~o~e to the cocked position shown in ~IGURE 1 to ~llow teruinal end 56 ~o partially enter abutment sleeve ~, the button pivots on the portion of operating sleeve N between rectangular openin~ 48 and slot 52. Ter~inal end 56 is within a plane either perpendicular to axls 30 or sloping from the outer periphery of button 0 in a direction both radially inward and axially outward from ter~inal end 36 of abutment sleeve M. This is to prevent a camming force which would work to depress and cock the button when sleeve N is ~oved into sleeve M.
As shown in FIGURES 8~10, button spring P
coDlprises a generally flat leaf spring curved into a generally circular conformation having freely overlapping terminal end portions 72,74 for allowing spring contraction and expansion. The top portion of thfl ~pring opposite ~ro~ the overlapping ends has a gen~rally rectangular çut-out 76 ~herein and an upwardly r~ised pro~ectlon 54. The out~r corners o~ proj~ction 54 are relieved as generally indicated at 80 to generally correspond with the curved corners of button 0 adjacent projection 50. Spring projection 54 is curved to the general transYerse contour of stop button 0 and is sized for reception in the recessed underside of the butto~. Thus, spring P holds stop button 0 in a position normally projecting upwardly through rectangular opening 48 with a button flange 70 en8a8ing the inner surface of opera~ing sleeve N. Depressing stop button 0 ~ay cause spring P to contract by further o~erlspping move~eDt of terminal end portions 72,74 and by de~or~ation of sprin~ projection 54.
Inner body part C and outer slide part D
include closely facing cooperating outer and inner c~lindrical surfaces 81,82, respecti~ely (FIGURE 2).
Body part C has an inner terminal end 84 spaced radially inward fro~ outer surface 81 thereof. A taper surface extends ~rom inner terminal end 84 to inner sur~ace 81.
Rs best shown in FIGURE ll, this taper surface includes a slow taper surface 86 inclined to coupling longitudinal axis 30 at a small angle and merging into a fast taper surface 88 adjacent the lntersection thereof with outer surface 81. In general, slow taper surface 86 is ~ore parallel to axis 30 than perpendicular thereto, while fast taper surface 88 is ~ore perpendicular ~o axis 30 than parallel thereto. The taper surface cooperates with a portion of inner surface 82 on slido D to define a packing receiving space and ~t t~por surface 88 is located adjacent the apex of thi~ 5paco.
A backup ring 90 and a packing ring 92 are positioned in the packing receiving space with backup ring 90 being located adjacent fas~ taper surface 88.
~17-Figuro 13 shows a backup rinB 90 having a cylindrical oue~r surface 94 generally corresponding to inner cyllndr~cal surface B2 of slide D and an inner surface 9~ inclined at substantially the same taper as slow taper surface 86. Backup ring 90 includes opposite parallel ends 98, 100 extending perpendicular ~o outer surface 94, with outer surface 94 merging into end surfaces 98, 100 with smoothly curved convex corners.
All of the seals and packings used in the preferred embodiment here under discussion are preferably construc~ed of ~irgin polytetrafluoroethlyene ("TFE").
Backup ring 90 preferably comprises polyphenylene sulfide (PPS) filled TFE or some other fairly hard yet pliable ~aterial so as to render the backup rin8 lS expandable yet relatively non-deformable compared to packing ring 92. Both TFE and PPS pro~ide excellent co~patibility with an extremely wide ran8e of she~icals. Seals and backup rings of these materials have been found to be longer lasting and more resistant to fsilure than conventional rubber or other elastomeric seals. However, it will be appreciated that other ~aterials also could be employed satisfactorily to accom~odate various environments or coupling applications.
As shown in FIGURE 12, packing ring 92 has a generally cylindrical outer surface 104 and an inner cylindrical inner surface portion 106. Parallel opposite ~nds 108,110 extend perpendicular to outer and - inner surfaces 104,106. Approximately one-half of the axial width of inner surface 106 has a taper surface 112 thereon for cooperation with slow taper surface 86. The slow taper provides a ~echanical advantags which allows packing ring 92 to defor~ and confor~ to irregularities on the surfaces of the various components. This ~echanical advantage and resulting defor0ation enables TPB, which is a relatiYely hard seal~ng ~a~erial7 to provide a Kas tight seal while subjec~ed to relatively low packing loadsa The thickness and axial wid~h of packing ring 92 are slso such that packing ring end 110 5 is spaced axially a substantial distance outwardly beyond hody part end 84.
With particular reference to FIGIIRE 3, a ~enerally cylindrical cup-like packing gland R is closely slidably received within hollow body part C.
Gland R has an axial~y inward extending reversely curved 1ange 116 inside of body part C and a radially outward ~xtending flange 118 disposed axially outward from inner terDinal end 84 thereof for enga8ing terminal end 110 (PIGURE 12) of packing ring 92.
Slide D has an inner inwardly extending portion 120 against whiçh a spring eyelet 122 is positioned.
The biasing ~eans defined by coil spring 12 has one end rcceived o~er eyelet 12Z and the opposite end besring a8ains~ inwardly extending reversely curved flange 116.
The rev~rse curve of flange 116 beneath the end coil of spring 12 combines with the alignment functlon of spring eyelet 122 to contain spring 12 against unseating forces fro~ ~o~ing fluids. Spring 12 defines a slide biasing ~esns for normally biasing slide D in one direction off 25 or away fro~ body part C, and also defines a packing biasing ~eans for urging packin~ 92 and backup ring 90 to the left in FIGURES 1 and 2 tightly into the packing receiving space.
When the coupling is internally pressurized, the pressure force acts on packing ring ~2 to force such packing and backup rin8 gO further into the packin~
receiving space. The taper surf~ce 86 imparts radially outward motion to the packing rin8 for causing such ring to be pressed firmly into the inner surface of the slldo. Tho slow ~per surface 86 proYides a mechanical adv2ntage which amplifies the co~pressiYe stresses on high points and irregularities in ~he packing at points ~here they contact the slide or body. Backup ring 90 prevents extrusion of the packing ring in~o the inter~ace between the outer surface 81 of ~he body and the inn~r surface 82 of the ~.lide. Axial movement of the packing ring causes it to contac~ the backup ring and forces same to move axially. The slow taper surface 86 c~uses the axially moYing backup ring to move radially outward to ir~1y enga8e the inner surface 82 of the slide for preventing the packin~ from extruding past the backup ring. The fast taper surface ~8 reduces the tendency for axial movement of the backup ring.
This co~bines with the less deformable or harder ~aterial composition of the backup ring to minimize the tendency of the backup ring to extrude between the body and slide~
As shown in FIGURE 14, ~he outer end portion of slide D has an internal circumferential recess with a sloping wall 126 in outwardly spaced opposing rela~ionship to body part outer surface 81. Recess sloping wall 126 slopes outwardly away from axis 30 at a slow taper when proceeding fro~ right^to-left in FIGURB
14, and this is also the one direction in which slide D
~oves when the ewo body and ste~ coupling assemblies A,B
are bein8 connected. A TPE bearin8 ring 127 has a ~enerally L-shaped cross-sectional configuration including a larger axial leg 128 received in the internal slide recess and a radial leg 129 extending outwardly along slide terminal end 130. Axial leg 128 has a generally cylindrical inner surface with a diameter slightly less than the external diameter of oxternal cylindrical surface ~1 on body part C. Axial leg 128 has an external surface with a slow taper generally corresponding to the taper on recess slopin~
surface
Back~round of the _ vention This application relates to the art of couplings and, more particularly, to quick connect/disconnect couplings. Although the invention is particularly applicable to couplings of ~he type described and will be explained with particular reference ~hereto, lt will be appreciated that certain eatures of the invention have broader aspects and may be used with other fittings or fluid containing devices such as control valves, check valves, unions, pipe or tube connectors, or the like.
Conven~ional quick connect/disconnect couplings haYe latch mechanis~s which are so easy to release that accidental or unintentional release ~ay occur. It has been found desirable to construct a latch mechanism which requires a conscious effort to release and is protected against accidental release.
Conventional couplings of the type described are also subject to slight leakage when they are uncoupled or to entrainment of air when they are coupled. Likewise, the various seals and packings are subject to blowout and leakage. It would he desirable, therefore~ to provide a coupling with improved seals and packin8s~ and which would be arranged for minimizin8 any leakage or air entrainment when the coupling is connec~ed ~nd disconnected.
Summar~ the Invention A quick connect/disconnec~ coupling including latch ~eans for releaseably la~ching together body and stem coupling members or assemblies. The la~ch means includes operatin~ means in the form of an operating sleeYe movable between latch holding and latch releasing positions. Stop means carried by the operating sleeve cooperates with abutment means for blocking movement of the operating sleeve to its releasing position until the stop ~eans itself is moved to an unblocking position clear of the abutment means. In one arrangement, the stop means takes the form of a small button movable transYersely of the longitudinal axis of the coupling.
Thus, the button ~ust be held in for clearing the abut~ent while the operating sleeve si~ultaneously ~oves longi~udinally to its latch releasing position. ~he abutment means may take the form of an abutment sleeve within which the operating sleeve is closely received, and a spring acting between the abutment and operating sleeves normally biases the operating sleeve to its latch holding position.
The latch members comprise ~etal stampings having first end portions attached to the body assembly for swinging movement of the opposite end portions toward and away from the coupling longitudinal axis.
The other end portions of the latches have inwardly extending la~ch hooks and ou~wardly extending projections. The latch hooks are receivable in a circumferential groove in ~he stem assembly for latching the ste~ assembly to the body assembly. In the latched position of the latch members, the latch projections bear against the inner surface of the operating sleeve.
Upon ~ovement of the operating sleeve to the latch ~v~
releasing position, ~he la~ch projections are cammed outwardly into a recess in ~he operating sleeve formed by an outwardly extending circumferential bead~ This recess has a cam surface which also cooperates with the latch projections for camming same back ~o a latched position when a coupling is a8ain connec~ed. The abut~ent sleeve also has an outwardly extending circu~ferential bead and the button is located between the beads for protecting same against accidental operation. Purther, the abutment and operating sleeves have outer end portions ~Ihich are reYersely curved inwardly for stiffening purposes.
The body coupling member or assembly includes a body part having a slide part longitudinally slidable thereon. The body and slide parts respectively haYe closely facing outer and inner cooperating cylindrical surfaces. The body part has an inner end spaced radially inward fro~ the inner surface of the slide part and a taper surface extends fro~ such body part end to the outer surface thereof. The taper surface includes a slow taper surface extending from the body part inner end toward the outer surface thereof and merging into a fast taper surface adjacent the intersection thereof with the body part outer surface. The taper surface on the body part is spaced from the inner surface of the slide to define a receiYing space for a packing, and the fast taper surface is disposed adjacent the apex of such receiving space. A backup ring is disposed in the receiving space adjacent the apex thereof and a packing ring is also located in the receiving space outwardly of th~ backup ring. Biasing means normally biases the packing ring and backup ring further into the packing receiving space. Both the backup ring and the packing ring are of a deformable material, with the backup ring being harder and less deformable than the packing ring.
L,~
In one arrangement, a cup-like packing gland is closely receive~ wi~hin the body part, and has an inwardly extending flange inside of the body part and an outwardly extending flange outside of the body part~
The outwardly extending flange engages the packing and the biasing means in the for~ of a coil spring acts between the slide and the inner flange of the gland.
Such arrange~ent causes the slide to normally be hiased in a direction off of the body part while simultaneously ~iasing the packing into the packing receiving space.
The slide is movable longitudinally in one direc~ion further onto the body when a coupling is being connected and is movable longitudinally in an opposite direction off of the body when a coupling is being disconnected. During connection of a coupling, transverse forces tend to cause the slide to interfere with the body and inhibit movement o~ the slide in the one direction. Therefore, the outer terminal end portion of the slide includes an inner circumferential bearing recess and an outer circumferential retainer groove. The recess includes a recess slow taper surface which opposes the outer cylindrical surface of the body part and the slope is outwardly away from the body part longitudinal axis when proceeding longitudinally in the one d~rection which is also away from the body valve.
bearing ring has a generally L-shaped cross-sectional shape including a generally axial leg received in the bearing recess and a generally radial leg extending outwardly at the outer terminal end of the slide. The outer surface o~ the bearing rin8 axial leg generally corresponds with the slope of the recess slow taper ~urface. A bearing ring retainer includes an axial cylindrical portion having inwardly extending detents loosely received in the retainer groove and an inwardly extending retainer flange overlying the radial leg of the bearing ring outwardly thereof. Relatively loose reception of the bearin8 retainer detents in the retainer groove allows limited axial ~ovement of the retsiner ring gnd this also allows some axial movement 5 of the beaFing ringO The internal dia~eter of the axial leg on the bearing ring is preferably slightly smaller than the external diameter of the body part. During moYement of the slide in the one direction, the axial leg of the bearing rin8 is forced into the slide recess, and coope~ation between the inner slow taper surface on the slide recess and correspondin~ outer taper surface on the axial leg of the bearing ring callse the axial leg to contract generally radially into firm bearing en8a8ement with the outer surface of the body part.
lS Thus, the slide rides on a bearing ring having a very low coefficient of fric~ion instead of riding directly o~ the outer surface of the body part when the coupling asse~blies are being connected. ~uring movement o~ the slide in an opposit~ direction while uncoupling the parts, the bearing rin8 is not cammed radially inwardly ineo engagement with the outer surface of the body part for providing free separation when transverse forces are ~ini~al.
The body assembly includes an internal body valve haYing a seal engagable by 8 Yalve seat on the slide for closing the slide and body against fluid flow therethrough. The body valve seal has sloping or tapered surace areas on both the internal and external surfaces thereof for creating a oechanical advantage which increases the compressive stress on hi8h points or irregularities. One end and a peripheral end portion of the body valve seal is surrounded by a metal retainer for resisting blowout of the seal~ On the opposite side of the seal from the metal retainer, a positive metal s$op surface is provided for engagement with a cooperating surfflce on the slide. The cooperating s~op surfaces prevent extruslon of the seal.
The body Yalve is essentially supported within the body by an elongated member and the elongated ~e~ber is, in turn, centrally held wi~hin the body by fins.
Fluid flow must take place past the fins around ~he elongated member. Thus, it is desirable to have such fins be as thin as possible while having sufficient strength to resist longitudinal shearing and compressive orces. In accordance with the present invention, the fins are in the for~ of a pair of fin ~embers each having a generally M-shaped configuration in an end Yiew. Each fin ~e~ber includes outer legs connec~ed by a somewhat U-shaped por~ion having a central curved portion. The cen~ral curved por~ion is spaced from the ter~inal ends of ths outer legs and is curved outwardly away therefro~. A pair of fin members are reversely positioned ~ith the outer leg ends engaging one another and with the curved portions facing one another on the periphery of a common circle. A section of the body ~alve elongated member is located between the curYed portions of the fins.
The stem ~ssembly includes a ste~ member havin~
a poppet ~oYable therein between closed and open positions. The poppet has an external circumferential s~al with sloping or tapered surfaces on both the external and internal periphery thereof. The poppet seal is engageable with a seat on the stem member. One end of the poppet and a peripheral end portion of the poppet seal are surrounded by a ~etal retainer for pre~en~in~ blowout of the poppet seal. One side of the ~etal retainer serves as a positiYe metal stop for cooperation with a corresponding stop OTI the stem member to prevent extrus~on of the poppet seal.
The poppet includes a poppet shaft e~tending ax~slly rearward therefro~ to a central openin~ in a guide me~ber. This guide member includes a pluralitr of c~rcumf~entially-spaced spokes ex~ending outwardly from a central portion having the poppet shaft receiving opening therethrough and having an axially extending circular boss. A coil sprinK has one end closely recsiYed over the circular boss on the guide member and the opposite end engaging the poppet for normally biasing the poppet to its closed position.
When a body and stem asse~bly are connected, the ste~ ~e~ber moves beneath the operating sleeve into en~age~ent with the slide for longitudinally moving same away ~rom the body valve. Longitudinal movement of the body and stem assemblies toward one another also causes lS the body val~e to enter one end of the stem member and engage the poppet for moving same to its open position.
Once the latch hooks are received in the external circumferential groove formed in the stem member, the co~ponents are connected together.
A plurality of pairs of keyed hody and stem asse~blies are arranged so that body asse~blies and stem assemblies having different keys cannot be connected with one another. This is acco~plished by Yarying the internal diameter of the operating sleeve, the external dia~eter of the sten me~ber, the external dia~eter of the body ~alve, and the in~ernal dia~eter of the open ste~ ~e~ber end. Assemblies having different keys will not mate due to interference either between a stem me~ber and operating sleeve or between a body valve and an open end of a stem ~ember.
The principal advantage of the present invention is the provision of an improved quick connec~/disconnect coupling.
Another advantage of the invention is the proYision of a quick connect/disconnect coupling having an i~proved latch mechanism.
Another advantage of ~he invention is the provlsion of a quick connect/disconnect coupling having a latch mechanism which requires movements in two different directions for obtaining a released condition.
An additional advantage of the present in~ention resides in proYiding an i~proved fluid coupling having improved seals.
Still another advantage of the invention is found in the provision of a coupling having an improved bearing arrangemen~ between a body and a longitudinally ~ovable slide.
A further advantage of the invention resides in an i~pro~ed arran8ement for biasing a packing into a packing receiving space.
Still a urther advantage of the present i~vention is found in improYed ~rrange~ents for supportin a body valve and a ste~ poppet respectively within a body asse~bly and a ste~ assembly.
Yet another advantage of the invention is in proYiding an improYed keying arran8ement for insuring that only mating pairs of body and ste~ assemblies can be cooperatively joined.
Still other advantages of the present invention ~5 will become apparent to those skilled in the art upon a readin8 and understanding of the following detailed description~
Brief Description of the Drawings The invention may take ~orm in certain parts and ar~angements of parts, a preferred embodiment of which will be described in detail in the specification and illustrated in the accompanying drawings which form a part hereof and wherein:
PIGUR~ l is a side cross-sectional elevational view showing the coupling of the present invention about ~ .3~f:~
to bo conn~cted or just after it has been dissonnected;
FIGURE 2 is ~ view similar to FIGURE 3 showing the coupling in its eonnected configuration;
~ IGURE 3 is a cross-sectional side elevational Yiew of the body asseubly only of ~IGURES 1 and 2;
FIGURE 4 is a cross-sectional side elevational view of the stem assembly only of FIGURES 1 and 2;
PIGURE 5 is a top plan view of an operating sleeYe used in the latch mechanis~;
FIGURE 6 is a top plan view of a stop button;
FIGURE 7 is a cross-sectional view taken generally along linçs 7-7 of FIGURE 6;
FIGURE 8 is an end view of a spring used in association with the stop ~utton of FIGURES 6 and 7;
FIGURE 9 is a cross-sectional view taken generally alon~ lines 9-9 of FIGURE 8;
FIGU~E 10 is a top plan view taken generally on-line 10-10 of FIGURE 8;
FIGURE 11 is an enlarged partial side elevat~onal view in cross-section showing a packing receiving space;
PIGURE 12 shows the axial cross-sectionai conformation of a packinz ring;
PIGURE 13 shows the axial cross-sectional confor~ation of a backup ring;
PIGURE 14 is an enlarged, partial cross-sectional elevationai view showing a slide bearing between ehe Yalve body part and the 51 ide;
~ IGURE 15 shows the axial cross-sectional confor~ation of a seal ring used between a body and stem;
PI~URE 16 is sn end view showing fin ~embers used to support a body Yal~e bol~;
PIGURE 17 i5 a top plan view taken generally along lines 17-17 of EIGURE 16;
PIGURE 18 is a cross-sectional view taken 3~
~en~rally along lines 1~ of FIGURE 17;
FIGURE 19 is an end view showing a guide member for a psppet;
FIGURB 20 is a cross-sectional view taken generally alon~ lines 20-20 of FIGURE 1~;
FIGURE 21 is a partial cross-sectional view si~ilar to PlGUR~ 1 showin~ the various component dia~eters which are ~odified to provide keyed mating pairs of body and ste~ assemblie~; and, FIGURE 2~ is a table showing examples of Yarious dia~eters in FIGURE Zl which provide keyed ~atinB pairs of body and stem assemblies.
Descri~tion of A Preferred E~bodiment Referrin8 now to the drawings wherein the showings are for purposes of illustrating preferred e~bodi~ents of the invention only and not for purposes of llDiting sa~e, PIGURE 1 shows a ~ating pair of body and ste~ coupl ing me~bers or assemblies A and B, respecti~ely, in a position about to be connected upon ~o~e~ent axially toward one another.
~ ody asse~bly ~ includes a body part or ~ember C having ~ slide part D axially slidable thereon. Slide part D ls nor~ally biased to the right in FIGURE 1 into engagement with a body valve E by means of a coil spring 12. Body valve E is attached to sn elongated member or bolt F and held centrsllr within the body part C by support fins Go Stem assembly B includes a stem part or ~ember H haYing a poppet I disposed therein. Poppet I is 30 nor~ally biased to the left in FIGURE 1 into engagement with a seat adiacent an open end of the stem by means of a coil spring 14. Spring 14 surrounds a ~uide shaft or bolt J extending through an opening in a guide member K
agsinst which spring 14 also acts.
When a mated pair of body and stem assemblies A,B are to be coupled, they are posi~ioned as shown in PIGURE 1. It will be noted that the outer end portion of ste~ ~ember H engages the outer end portion of slide part n and, upon moYement of assemblies A,B toward one another, slide part D retracts to the left in FIGURE 1 out o~ en8agement with body Yalve E. At the same time, body valve E enters the open end of s~em member H and engages poppet I to move same away fro~ its seat, i.e., to the right in FlGUR~ 1. Once the assemblies are connected, the parts are arranged as generally shown in PIGURB ~ and fluid flow can take place through ~he conneceed asse~blies.
Body part C is internally threaded as generally indicated at 16 for connection to another fluid conduit. Other interconnecting means could also be advantageously employed, however. An external circu~ferential groove 18 in the body part C loosely recei~es inwardly extending first end portions 20 of a plurality of latch oembers L. These latch members preferably comprise ~etal stampings, and have an arcuate confor~ation in an end Yiew. The opposite end portions of latch ~embers L include inwardly extending latch hooks 22 and outwardly extending latch projections 24.
A generally cylindrical abut~ent sleeve M îs positioned over body part C and has an outer end portion reversely curved inwardly as generally indicated at 28.
Re~ersely curved end portion 28 has an axially extending portion overlying axially extending portions of first end portions 20 of latch members L to loosely hold same within groove 18 for allowing swinging movement of the latch members opposite end portions toward snd away from coupling longitudinal axis ~0. A snap ring 32 recei~ed in a ~uitable external circumferential groove in body part C retains abutment sleeYe M in position. Abut0ent sleev~ M includes an outwardly extending circumferential b~ad 3~1 for stiffenin8 same agalnst a ~eformation, and also includes a ter~inal end 36~
Operating ~eans in the ~or~ of a generally cylindrieel sleeve N surrounds latch ~embers L and has an outer end portion reversely curved inwardly as gen~rally indicated at 40. An outwardly extending circu~ferential bead 42 provides an inner circu~ferential recess 44 havin~ a gradual slope to pro~lde a ca~ surface for cooperation with latch projeceions 24. In the outward released position of latch ~embers L as shown in FIGURE 1, latch projections 24 ~re received in recess of 44~ This relationship also acts to retain operating sleeve N against complete displacement to the ri8ht from body assembly A. A coil spring ~6 is positioned betwe0n the reversely curved outer end portion of abutment sleeve M and the inner ter~inal end of operating sleeve N for nor~ally biasing operating sleeve N away from abut~ent sleeve M.
~ generally rectangular opening 48 in operating sleeve N receives stop ~eans in the form of stop button 0 haYing a downwardly depending leg S0 freely received throu~h a slot 52 spaced sligh~ly froD rectangular opening 4S. ~ generally circular leaf spring P has an upper flat projec~ion 54 received in the recessed underside of button 0 and noroally biases the stop button upwardly in the view of FIGURE 1. Stop button O
has a leading edge 55 with a slow slope to prevent accidentsl cocking of the button when contacted by an external object having relative movement generally toward abutment sleeve M. Stop button 0 also has an inner o~d 56 engageable with abut~ent sleeve inner end 36 to preven~ further ~ovement of operating sleeve ~
within abutment sleeve M to the left in PIGURE 1 until stop button O is depressed for allowing button inner end 56 to pass beneath end 36 of the abutment sleeve. The inner end portion of operating sleeve N is closely received and guided within abutment sleeve M.
Ste~ assembly B includes cooper~ting coupling ~eans on stem member H in the form of a circumferential groove 60 for receiving latch hooks 22. With ~he co~ponents positioned as shown in PIGURE 1, movement of body part C and ste~ ~ember H tow~rd one ~nother causes slide D to retract to the left. At the same time, latch hooks 22 ride along the ou~er surface of slide ~ and an outer sur~ace portion 62 of stem ~ember H until latch hooks 22 reach groove 60. At this point, latch members L swing inwardly for reception of latch hooks 22 within groove 60. Spring 46 disposed be~ween abu~ment sleeve M
and operating slee~e ~, biases operating sleeve N to the lS ri8ht in PIGURE 1. This causes the cam surface portion of recess 44 to cooperate with la~ch projections 24 for urging latch hooks 22 in~o grooYe 60. This also releases ~perating sleeYe N for ~ovement to the ri8ht fro~ the latch releasing position of ~I~URE 1 to ~he latch holding position of FIGURE 2. In ~he latch holding position, the outer ends of latch projections 24 engage the inner cyl indrical surface of operating sleeve N at a location spaced from recess 44 on the opposite side thereof fro~ reversely curved outer end portion 40. Also, the outer end of reversely curved end portion 40 engages an abut~ent 64 on stem memher H for holding operating sleeve N against further ~ove~ent to the right in PIGURE 2. When latch hooks 22 are received in a latching condition in groove 60, the latch members are positioned substantially 36~ around the groove. This relationship enhances the connected relationship between body and stem coupllng members A,B.
With the co~ponents connected as shown in PIGURB 2, such connection requires ~oYement of operating slee~e N to the left until latch projections 24 are '3 generally aligned with recess 4~. However, 8xial ~ove~en~ of operating sleeve N to the left in FIGURE 2 ls preYente~ because terminal end 56 of stop button O
engages terminal end 36 of the abutment means defined by abut~ent sleeve M. In order to free operating sleeve N
for ~ove~en~ to its releasing position, it is necessary to depress stop button O and hold sa~e depressed while operating slee~e N is urged axially to the left so that stop button ter~inal end 56 will pass beneath abutment ter~inal end 36 as shown in FIGURE 1. Th~s, the latch ~eans requires independent movements in ~wo different directions for ~oving same to a releasing position. The ~ovement of button O is generallr toward and away from coupling longitudinal axis 30 with the motion heing generally pivotal about button projection S8 in slot 52. Once recess 44 is generally aligned with latch projections 24, the biasing action of spring 12 urging slide D to the right is also urging stem member }I eo the right. The cooperating cam surfaces between latch hooks 22 and groove 60 cause the end portions of latch members L to be ca~med generally radially outward for reception of latch projections 24 in recess 44.
It will be noted that stop button O is loca~ed bet~een outwardly extending circu~ferential beads 34,42. Preferably, the ~utton does not project above a plane tan8ent to the outer surfaces of both beads 34 and 42, Thus, button O is protected by the beads against accidental ~ovement to its unblocking position ro~ its noroal blocking position where ~oYement of operating sleeYe N to its latch releasing position is prevented.
3uewardly ~xtending circumferential bead 42 on operating sleeve N also perfor~s the unction of providing an abutment a~ainst which a person's thu~b and fingers ~ay act to ~ove operating sleeve N to the left against the 3s bi~sing force of spring 46.
PIGUR~ 5 si~ply shows the rectangular opening 48 and slot 52 in oper~ting sleeve N ~ith more particulari~y.
PIGURES 6 and 7 show the s~op means defined by stop button 0. It will be recognized tha~ stop button 0 is transYersely cur~ed to the gener~l curvature of operating sleeve N. The underside of s~op button 0 is recessed. An outwsrdly extending flange 70 exten~s outwardly from the button undersid~ along abu~ment end 56 thereof and partly along the opposi~e sides thereof toward projec~ion 50. The flanges along the sides of bu~ton 0 ter~inate sufficiently shor~ of the end having downwardly extending projection 50 for allowing the bu~ton to be positioned within and without operating ~lee~e N. When in the uncocked blockin~ position as shown ~n PIGURE 2 to block move~ent of operating sleeve N into abut~ent sleeve M, flange 70 abuts and approxi~ately confor~s to the inner contour of operating sleer~ N par~ially around the rectangular opening 48 while projection 50 extends downwardly through slot 52.
To ~o~e to the cocked position shown in ~IGURE 1 to ~llow teruinal end 56 ~o partially enter abutment sleeve ~, the button pivots on the portion of operating sleeve N between rectangular openin~ 48 and slot 52. Ter~inal end 56 is within a plane either perpendicular to axls 30 or sloping from the outer periphery of button 0 in a direction both radially inward and axially outward from ter~inal end 36 of abutment sleeve M. This is to prevent a camming force which would work to depress and cock the button when sleeve N is ~oved into sleeve M.
As shown in FIGURES 8~10, button spring P
coDlprises a generally flat leaf spring curved into a generally circular conformation having freely overlapping terminal end portions 72,74 for allowing spring contraction and expansion. The top portion of thfl ~pring opposite ~ro~ the overlapping ends has a gen~rally rectangular çut-out 76 ~herein and an upwardly r~ised pro~ectlon 54. The out~r corners o~ proj~ction 54 are relieved as generally indicated at 80 to generally correspond with the curved corners of button 0 adjacent projection 50. Spring projection 54 is curved to the general transYerse contour of stop button 0 and is sized for reception in the recessed underside of the butto~. Thus, spring P holds stop button 0 in a position normally projecting upwardly through rectangular opening 48 with a button flange 70 en8a8ing the inner surface of opera~ing sleeve N. Depressing stop button 0 ~ay cause spring P to contract by further o~erlspping move~eDt of terminal end portions 72,74 and by de~or~ation of sprin~ projection 54.
Inner body part C and outer slide part D
include closely facing cooperating outer and inner c~lindrical surfaces 81,82, respecti~ely (FIGURE 2).
Body part C has an inner terminal end 84 spaced radially inward fro~ outer surface 81 thereof. A taper surface extends ~rom inner terminal end 84 to inner sur~ace 81.
Rs best shown in FIGURE ll, this taper surface includes a slow taper surface 86 inclined to coupling longitudinal axis 30 at a small angle and merging into a fast taper surface 88 adjacent the lntersection thereof with outer surface 81. In general, slow taper surface 86 is ~ore parallel to axis 30 than perpendicular thereto, while fast taper surface 88 is ~ore perpendicular ~o axis 30 than parallel thereto. The taper surface cooperates with a portion of inner surface 82 on slido D to define a packing receiving space and ~t t~por surface 88 is located adjacent the apex of thi~ 5paco.
A backup ring 90 and a packing ring 92 are positioned in the packing receiving space with backup ring 90 being located adjacent fas~ taper surface 88.
~17-Figuro 13 shows a backup rinB 90 having a cylindrical oue~r surface 94 generally corresponding to inner cyllndr~cal surface B2 of slide D and an inner surface 9~ inclined at substantially the same taper as slow taper surface 86. Backup ring 90 includes opposite parallel ends 98, 100 extending perpendicular ~o outer surface 94, with outer surface 94 merging into end surfaces 98, 100 with smoothly curved convex corners.
All of the seals and packings used in the preferred embodiment here under discussion are preferably construc~ed of ~irgin polytetrafluoroethlyene ("TFE").
Backup ring 90 preferably comprises polyphenylene sulfide (PPS) filled TFE or some other fairly hard yet pliable ~aterial so as to render the backup rin8 lS expandable yet relatively non-deformable compared to packing ring 92. Both TFE and PPS pro~ide excellent co~patibility with an extremely wide ran8e of she~icals. Seals and backup rings of these materials have been found to be longer lasting and more resistant to fsilure than conventional rubber or other elastomeric seals. However, it will be appreciated that other ~aterials also could be employed satisfactorily to accom~odate various environments or coupling applications.
As shown in FIGURE 12, packing ring 92 has a generally cylindrical outer surface 104 and an inner cylindrical inner surface portion 106. Parallel opposite ~nds 108,110 extend perpendicular to outer and - inner surfaces 104,106. Approximately one-half of the axial width of inner surface 106 has a taper surface 112 thereon for cooperation with slow taper surface 86. The slow taper provides a ~echanical advantags which allows packing ring 92 to defor~ and confor~ to irregularities on the surfaces of the various components. This ~echanical advantage and resulting defor0ation enables TPB, which is a relatiYely hard seal~ng ~a~erial7 to provide a Kas tight seal while subjec~ed to relatively low packing loadsa The thickness and axial wid~h of packing ring 92 are slso such that packing ring end 110 5 is spaced axially a substantial distance outwardly beyond hody part end 84.
With particular reference to FIGIIRE 3, a ~enerally cylindrical cup-like packing gland R is closely slidably received within hollow body part C.
Gland R has an axial~y inward extending reversely curved 1ange 116 inside of body part C and a radially outward ~xtending flange 118 disposed axially outward from inner terDinal end 84 thereof for enga8ing terminal end 110 (PIGURE 12) of packing ring 92.
Slide D has an inner inwardly extending portion 120 against whiçh a spring eyelet 122 is positioned.
The biasing ~eans defined by coil spring 12 has one end rcceived o~er eyelet 12Z and the opposite end besring a8ains~ inwardly extending reversely curved flange 116.
The rev~rse curve of flange 116 beneath the end coil of spring 12 combines with the alignment functlon of spring eyelet 122 to contain spring 12 against unseating forces fro~ ~o~ing fluids. Spring 12 defines a slide biasing ~esns for normally biasing slide D in one direction off 25 or away fro~ body part C, and also defines a packing biasing ~eans for urging packin~ 92 and backup ring 90 to the left in FIGURES 1 and 2 tightly into the packing receiving space.
When the coupling is internally pressurized, the pressure force acts on packing ring ~2 to force such packing and backup rin8 gO further into the packin~
receiving space. The taper surf~ce 86 imparts radially outward motion to the packing rin8 for causing such ring to be pressed firmly into the inner surface of the slldo. Tho slow ~per surface 86 proYides a mechanical adv2ntage which amplifies the co~pressiYe stresses on high points and irregularities in ~he packing at points ~here they contact the slide or body. Backup ring 90 prevents extrusion of the packing ring in~o the inter~ace between the outer surface 81 of ~he body and the inn~r surface 82 of the ~.lide. Axial movement of the packing ring causes it to contac~ the backup ring and forces same to move axially. The slow taper surface 86 c~uses the axially moYing backup ring to move radially outward to ir~1y enga8e the inner surface 82 of the slide for preventing the packin~ from extruding past the backup ring. The fast taper surface ~8 reduces the tendency for axial movement of the backup ring.
This co~bines with the less deformable or harder ~aterial composition of the backup ring to minimize the tendency of the backup ring to extrude between the body and slide~
As shown in FIGURE 14, ~he outer end portion of slide D has an internal circumferential recess with a sloping wall 126 in outwardly spaced opposing rela~ionship to body part outer surface 81. Recess sloping wall 126 slopes outwardly away from axis 30 at a slow taper when proceeding fro~ right^to-left in FIGURB
14, and this is also the one direction in which slide D
~oves when the ewo body and ste~ coupling assemblies A,B
are bein8 connected. A TPE bearin8 ring 127 has a ~enerally L-shaped cross-sectional configuration including a larger axial leg 128 received in the internal slide recess and a radial leg 129 extending outwardly along slide terminal end 130. Axial leg 128 has a generally cylindrical inner surface with a diameter slightly less than the external diameter of oxternal cylindrical surface ~1 on body part C. Axial leg 128 has an external surface with a slow taper generally corresponding to the taper on recess slopin~
surface
-2~-126. A c~ surface 131 connects the outer surface of radial leg 125 with the inner surface of axial leg 128, and Hids initial assembly as well as wiping action during connection of the coupling asse~blies. Slide D
has an external circumerential ~rooYe 132 spaced a short distance axially from ter~inal end 130 thereof and ls of generally rectangular cross-sectional shape.
Retalning mesns for preven~ng complete displace~ent of the bearin8 ring fro~ the recess while allowin~ ited axial ooYement thereof relative to the slide comprises a ~etal retainer rin8 including an inward~y extending flang~ 133 overlying bearing ring radial leg 129. The axial spacing between flan~e 133 and slide terminal end 130 is substantially greater than the axial thickness of b~arin8 ring radial leg 129. A retainer ring cylindrical portion 134 is closely receiYed over that portion of slide D extending between terminal end 130 and grooYe 132, and which portion has an external dia~eter s~aller than the remainder of slide D by approxi~ately two times the rsdial thickness of retainer ring cylindrical portion 134. A plurality of circu~ferentially-spaced inwardly extending barbs or detents 135 are punched and bent fro~ cylindrical portion 134 and slope inwardly toward axis 30 at a slow taper fro~ right-to-left in FIGUR~ 14. The axial distance between the terminal end o~ cylindrical portion 134 and the terminal end of detents 135 is subs~antially less than the axial width of groove 132. In other words, th~re is a loose fit so that the retainer ring oan move back-and-for~h axially. When the retainer ring is being asse~bled, detents 135 will bend outwardly until they snap back into groove 132. ~ngagement between the terminal end of cylindrical portion 134 and one side of groo~e 132, snd between the terminal ends of detents 135 and the opposite side of groove 132, define ~6V~
the li~its o~ axlal movement f or the retainer ring~
Dur~ng ~oYement of slide D in ~he one direction to connect the coupling, which is moYement of slide D from right-to-left in PIGURE 14, cooperation between the tapering surfaces of the slide recess and the bearing ring axial leg causes axial leg 128 to contract generallr radially in~o firm engagement with body par~
external surface ~1. Thus, durin~ connecting movement, slid~ D rides on bearin8 ring 127 having a very low coef~icient of friction instead of ridin8 on another ~etal surface. This is signi~ican~ in that substantially all of the major coupling components are preferably of stainless steel and galling is a particular problem associated with such material. The lS fir~ engagement of bearing ring axial leg 128 with external surface 81 of body par~ C also perfor~s a tborough wiping action. When slide D is ~hereafter ~o~ed in the opposite direction, i.e., to the right or uncouplin~ direction in FIGURE 14~ bearing rin8 127 is free for limited movement to the left so it doss not co~pressively engage body part C with great force and allows free separation of ~he parts when lateral forces are ~ini~al.
Inwardly extending por~ion 120 of slide D
ter$inates in an axially extending projection 13b having an external circumferen~i~l groove 138 (FIGURE 3) receiving a TF~ seal ring 140, Slide D is part of body assembly A and may be considered a body part. The t~r~inal end portio~ vf slide D having groove 138 therein ~ay be considered a body ter~inal end portion having a terminal end 141. Groove 138 has a groove botto~ and axially-spaced groove sidewalls, including one groove sidewall closest to terminal end 141 and an opposite groove sidewall further therefrom. The groove 3s botto~ slopes outwardly away from axis 30 at a small 2~-anglo ln a direction from ~he one ~roove sidewall ~oward the opposite groove sidewall. As best shown in PICURE
15, seal 140 has an lnner surface 142 sloping at a shallow angle from axis ~0 and an outer cylindrical portion 144. Parallel opposite ends 146,148 extend perpendicular to cylindrical surface 144. Approximately one-half of the width of seal 140 adjacent end 148 has an external sloping surface 150 sloping downwardly tow~rd inner surface 142 at a shallow angle from axis 30~ The botto~ of cylindrical groove 138 is shaped to generally correspond with seal inner sur~ace 142, while an lnner surface portion 152 of ste~ ~ember l~ is shaped to generally correspond with external surfaces 144,150 by haYing stem me~ber cylindrical and sloping surfaces 153,155 (FIGURE 4). The diameter of inner cylindrical surface 82 on slide D is substantially greater than the lar~est external dia~e~er of seal 140. As a result, a pressure force differential will exist when the coupling is pressurized ~o nor~ally bias slide D to the right in FIGURE 2, and to more firmly engage and compress seal 140 beeween slide D and stem me~ber H. A stem seal backup rinB 156 is positioned between the left end of TF~ seal 140 and the left end of groove 138 and, besides preventing extrusion of seal 140, it has the same or 25 si~ilar properties and material composition as packing backup r~ng 90.
Body valve E includes an external recess closely receiving a seal 160, with the surface of the recess corresponding in size and shape with the inner surface of the seal. Seal 160 has both external and intarnal surfaces which are sloped outwardly away fro~
axis 30 in a direction proceeding away from slide D.
This enh~nces the sealing action and allows the seal to conor~ with irregularities. An outer sloping surface 162 on seal 160 corresponds with a ~alve seat 164 on the interior of slide D adjacent the open end. Body val~e E
also includes a sloping stop surface 166 spaced axially and r~dially fro~ seal 160 for cooperation with a corresponding sloping stop surface 168 adjacent the open end o slide D. This cooperation between the stop s surfaces 166, 168 prevents dama8e or extrusion to seal 160 under high pressures. One end and an ou$er peripherlal portion of seal 160 are surrounded by a ~etal retainer ring 170 for preventin~ blowou~ of seal 160 under high fluid pressure conditions. Metal retainer rin8 170 is retained in position by a sultable snap ring 172 positioned in a suitable circumferential ~roove in body valve E. Body valve stop surface 166 is located on the opposite side of seal 160 from metal retainer ring 170 and stop surface 166 is located axially further away from slide D than retainer ring 170.
Poppet I includes an external recess shaped for closely receiving a poppet seal 180 having internal and ~xternal surfaces ~hich are tapered outwardly from axis ~0 in a direction away from ~he open end of stem member H. These internal and external tapering surfaces enahle th~ seal to conor~ with irregularities on the mating surfaces. Seal 180 also has an outer sloping surface 182 for cooperation with a corresponding valve seat 184 adjacent the open inner end of ste~ me~ber H. A
tap~ring stop surface 189 on a metal retainer ring 187 i3 c~operative with a corr~sponding tapered stop surface 188 adjacent the open inner end of stem member H. Under nor~al circumstances, stop surfaces 189,188 will not engage one another, bu~ will do so to prevent extreme defor~ation or extrusion of seal 180 under extremely high pressures. Retainer ring 187 surrounds an end and a peripheral portion of seal 180 to prevent seal blowout and is retained in position by a snap ring 190 received in a suitable groovs in poppet I. Stop surface 189 and 35 retainer ring 187 are located at the same end of i -2~-~eal 180, ~nd retainer ring JB7 is loca~ed axially closer to the open inner end of s~em me~ber l~ th~n is the portion of poppet I on the opposite side of seal lB0 fro~ retainer rin8 187.
Bolt or elongated member P is secured to body vdlY~ ~ in a known ~anner and includes a pair of axially-spaced projections 202,204 bet~een which a circu~ferential grooYe 206 is defined. Suppor~ fins G
include a pair of fin ~embers shown in detail in FIGURES
16-18. Each fin ~ember is generally M-shaped in end view and includes a pair of main legs 208 connected by a generally U-shaped portion having a central curved portion 210 which i~ spaced from the terminal ends and is cur~ed outwardly away therefro~. As bes~ shown in PIGURES 17 and 18, curved central portion 210 is axially offset fro~ ~ain legs 208. When a pair of fin members are reversely positioned with ~he ter~inal ends of main legs 208 thereof engaging one another as shown in FlGURE
16, the inner facing surfaces of curved central portions 210 lie on the periphery of a co~mon circle haYing a dia~eter approxima~ely the same as the diameter of the botto~ of bolt groove 206. In addition~ the distance between the opposite axial ends of curYed central portion 210 is approxi~at~ly the same as the distance between the inner facing surfaces of projections 202,204.
Whe~ a pair of fin members are reversely positioned in coopera~ive relationship around a bolt F
as shown in ~IGURE 3 7 one end of legs 208 engages a circumferential shoulder 212 in the bore of body part C. A snap ring 214 received in a suitable circu~ferential groove retains support fins G in the desired position. As shown in FIGURE 3, curved central portions 210 are axially offset fro~ legs 208 in a dlrcction away fro~ body valve E. The shape and position of th~ fin ~embers allows maxi~um flow through the bor~ of body part C while providing ~a%imu~ s~reng~h or holding body valve E in pvsition and resisting both sho~r and compressive forces.
~s shown in PIGURES l9 and 20, poppet guide 5 ~e~ber ~ includes a plurality of radially extending circumferentially spaced apart spokes 220 issuing from a central area 222. A central opening 224 extends through the cen~r~l area and is surrounded by a circular raised boss 226. The outor ter~inal ends 228 of spokes 220 are curYed to lie on the periphery of a co~on circle and the spokes are equidistan~ly spaced fro~ one another.
~s shown in FIGURE 20, spokes 220 are inclined out of a flat plane in a direction opposiee to ehe projecting direction of circular boss 2260 As shown in FIGURE 4, poppet guide bolt J is surrounded by coil spring 14 and has a terminal end in t~e general shape of a ~runcated cone ~hich abuts a corresponding conical botto~ surface of a bore in poppet I .A shoulder 230 wi thin a stem adapter 232 engages the outer end portions of spokes 220 on poppet guide K. A
s~all diaaeter portion 234 of guide bolt J is closely recei~ed and slidably guided through hole 224. An enlarg~d portion o~ the guide bolt provides an abutment 236 for engagin~ the end of circular boss 226. One end of coil spring 14 is closely received over circular boss 226 and the other end thereof engages the back of an enlar~ed head on the ter~inal end portion of guide bolt J within the bore in poppet I for normally biasing the poppet to its closed position. Th0 $nterior outer end portion of ste~ ~e~ber H is suitably threaded for cooperation with external threads on stem adapter 232t and the i~terior of ste~ adap~er 232 is threaded as indicatod at 240 for connection to another fitting on a conduit. Here, too, in~erconnecting ~eans of types other than threads 240 could be advantageously employed.
~ ith reference to PIGURES 2l and 22, the oxternal diameter portion of stem member H which is receiYed within operating sleeve N is varied by adding çylindrical shims 246 of Yarious thicknesses ther~to.
5 Shus, the external dlameter S of ste~ ~ember H ~ay be selecti~ely varied~ The inner diameter of reversely curved portion 40 of operatin~ sleeve N is varied by machining the portion to variable desired internal diameters T. The largest external dia~eter portion of 10 body val~e E is varied by machining it to variable dia~eters Y. The diame~er of the s~allest internal dianeter portion 250 at the open inner end of stem ~ember H is similarly varied by machining it ~o variable diameters U.
A plurality of pairs of mating body and stem asse~blies are constructed and di~ensioned such that the body asse~bly of one key will ~ate only wi~h a ste~
asse~bly having the same key7 Progressi~ely larger keys have progressively larger external ste~ member diameters S, larger internal operating sleeve diameters T, larger body valve external dia3eters V, and larger stem open end internal diaoeters U. Thus, there is provided a coded sysee~ of couplings including 8 plurality of pairs of keyed ~atin8 body and ste~ asse~blies ~,B. Each body asse~bly includes an inner body valve E and an outer coupling sleeYe defined by.operating sleeve N. Each ste~ asse~bly has a ste~ member H with an external diamster S ~nd an ope~ stem end through which body Yalve ~ is received. Mating body and stem assernhlies are dimensiongd for close reception of ste~ member H within slee~e N and for close reception of body valve ~ within ~nner ste~ ~embe~ end 250. With this arrangement, body and ste~ assemblies having different keys will not mate or connect due to interference either between a stem ~e0ber H and a coupling sleeve N or between a body valve E and 9 stem inner end 250.
~ xamples of various diameters for a plurality of dlfferent keys i5 shown in FIGUR~ 22. A stem asse0bly will not couple with the body of a higher key 5 because of interference between valve body E and internal opening 250. A body assembly having a hi8her key ~ill always have a larger external diameter on body Yalve E than the corresponding internal dia~eter at open end 250 of a s~aller key ste~ assembly. A body asse~bly 10 will not mate or connect with a ste~ assembly of a hi8her key because of interference be~ween the external dia~eter of stem oe~ber H snd the internal diameter sf sleeY~ N. A stem assembly of a higher key will always ha~s a larger external stem member diameter than the lS correspo~ding internal dia~eter of the sleeve on a s~aller key body asse~bly.
The invention has been described with reference to the preferred e~bodiment. ObYiously, modifications and alterations will occur to others upon a reading and 20 understanding of ~his specification. It is intended to include all such ~odifications and alterations insofar as they co~e within the scope of the appended claims or the equivalents thereof.
has an external circumerential ~rooYe 132 spaced a short distance axially from ter~inal end 130 thereof and ls of generally rectangular cross-sectional shape.
Retalning mesns for preven~ng complete displace~ent of the bearin8 ring fro~ the recess while allowin~ ited axial ooYement thereof relative to the slide comprises a ~etal retainer rin8 including an inward~y extending flang~ 133 overlying bearing ring radial leg 129. The axial spacing between flan~e 133 and slide terminal end 130 is substantially greater than the axial thickness of b~arin8 ring radial leg 129. A retainer ring cylindrical portion 134 is closely receiYed over that portion of slide D extending between terminal end 130 and grooYe 132, and which portion has an external dia~eter s~aller than the remainder of slide D by approxi~ately two times the rsdial thickness of retainer ring cylindrical portion 134. A plurality of circu~ferentially-spaced inwardly extending barbs or detents 135 are punched and bent fro~ cylindrical portion 134 and slope inwardly toward axis 30 at a slow taper fro~ right-to-left in FIGUR~ 14. The axial distance between the terminal end o~ cylindrical portion 134 and the terminal end of detents 135 is subs~antially less than the axial width of groove 132. In other words, th~re is a loose fit so that the retainer ring oan move back-and-for~h axially. When the retainer ring is being asse~bled, detents 135 will bend outwardly until they snap back into groove 132. ~ngagement between the terminal end of cylindrical portion 134 and one side of groo~e 132, snd between the terminal ends of detents 135 and the opposite side of groove 132, define ~6V~
the li~its o~ axlal movement f or the retainer ring~
Dur~ng ~oYement of slide D in ~he one direction to connect the coupling, which is moYement of slide D from right-to-left in PIGURE 14, cooperation between the tapering surfaces of the slide recess and the bearing ring axial leg causes axial leg 128 to contract generallr radially in~o firm engagement with body par~
external surface ~1. Thus, durin~ connecting movement, slid~ D rides on bearin8 ring 127 having a very low coef~icient of friction instead of ridin8 on another ~etal surface. This is signi~ican~ in that substantially all of the major coupling components are preferably of stainless steel and galling is a particular problem associated with such material. The lS fir~ engagement of bearing ring axial leg 128 with external surface 81 of body par~ C also perfor~s a tborough wiping action. When slide D is ~hereafter ~o~ed in the opposite direction, i.e., to the right or uncouplin~ direction in FIGURE 14~ bearing rin8 127 is free for limited movement to the left so it doss not co~pressively engage body part C with great force and allows free separation of ~he parts when lateral forces are ~ini~al.
Inwardly extending por~ion 120 of slide D
ter$inates in an axially extending projection 13b having an external circumferen~i~l groove 138 (FIGURE 3) receiving a TF~ seal ring 140, Slide D is part of body assembly A and may be considered a body part. The t~r~inal end portio~ vf slide D having groove 138 therein ~ay be considered a body ter~inal end portion having a terminal end 141. Groove 138 has a groove botto~ and axially-spaced groove sidewalls, including one groove sidewall closest to terminal end 141 and an opposite groove sidewall further therefrom. The groove 3s botto~ slopes outwardly away from axis 30 at a small 2~-anglo ln a direction from ~he one ~roove sidewall ~oward the opposite groove sidewall. As best shown in PICURE
15, seal 140 has an lnner surface 142 sloping at a shallow angle from axis ~0 and an outer cylindrical portion 144. Parallel opposite ends 146,148 extend perpendicular to cylindrical surface 144. Approximately one-half of the width of seal 140 adjacent end 148 has an external sloping surface 150 sloping downwardly tow~rd inner surface 142 at a shallow angle from axis 30~ The botto~ of cylindrical groove 138 is shaped to generally correspond with seal inner sur~ace 142, while an lnner surface portion 152 of ste~ ~ember l~ is shaped to generally correspond with external surfaces 144,150 by haYing stem me~ber cylindrical and sloping surfaces 153,155 (FIGURE 4). The diameter of inner cylindrical surface 82 on slide D is substantially greater than the lar~est external dia~e~er of seal 140. As a result, a pressure force differential will exist when the coupling is pressurized ~o nor~ally bias slide D to the right in FIGURE 2, and to more firmly engage and compress seal 140 beeween slide D and stem me~ber H. A stem seal backup rinB 156 is positioned between the left end of TF~ seal 140 and the left end of groove 138 and, besides preventing extrusion of seal 140, it has the same or 25 si~ilar properties and material composition as packing backup r~ng 90.
Body valve E includes an external recess closely receiving a seal 160, with the surface of the recess corresponding in size and shape with the inner surface of the seal. Seal 160 has both external and intarnal surfaces which are sloped outwardly away fro~
axis 30 in a direction proceeding away from slide D.
This enh~nces the sealing action and allows the seal to conor~ with irregularities. An outer sloping surface 162 on seal 160 corresponds with a ~alve seat 164 on the interior of slide D adjacent the open end. Body val~e E
also includes a sloping stop surface 166 spaced axially and r~dially fro~ seal 160 for cooperation with a corresponding sloping stop surface 168 adjacent the open end o slide D. This cooperation between the stop s surfaces 166, 168 prevents dama8e or extrusion to seal 160 under high pressures. One end and an ou$er peripherlal portion of seal 160 are surrounded by a ~etal retainer ring 170 for preventin~ blowou~ of seal 160 under high fluid pressure conditions. Metal retainer rin8 170 is retained in position by a sultable snap ring 172 positioned in a suitable circumferential ~roove in body valve E. Body valve stop surface 166 is located on the opposite side of seal 160 from metal retainer ring 170 and stop surface 166 is located axially further away from slide D than retainer ring 170.
Poppet I includes an external recess shaped for closely receiving a poppet seal 180 having internal and ~xternal surfaces ~hich are tapered outwardly from axis ~0 in a direction away from ~he open end of stem member H. These internal and external tapering surfaces enahle th~ seal to conor~ with irregularities on the mating surfaces. Seal 180 also has an outer sloping surface 182 for cooperation with a corresponding valve seat 184 adjacent the open inner end of ste~ me~ber H. A
tap~ring stop surface 189 on a metal retainer ring 187 i3 c~operative with a corr~sponding tapered stop surface 188 adjacent the open inner end of stem member H. Under nor~al circumstances, stop surfaces 189,188 will not engage one another, bu~ will do so to prevent extreme defor~ation or extrusion of seal 180 under extremely high pressures. Retainer ring 187 surrounds an end and a peripheral portion of seal 180 to prevent seal blowout and is retained in position by a snap ring 190 received in a suitable groovs in poppet I. Stop surface 189 and 35 retainer ring 187 are located at the same end of i -2~-~eal 180, ~nd retainer ring JB7 is loca~ed axially closer to the open inner end of s~em me~ber l~ th~n is the portion of poppet I on the opposite side of seal lB0 fro~ retainer rin8 187.
Bolt or elongated member P is secured to body vdlY~ ~ in a known ~anner and includes a pair of axially-spaced projections 202,204 bet~een which a circu~ferential grooYe 206 is defined. Suppor~ fins G
include a pair of fin ~embers shown in detail in FIGURES
16-18. Each fin ~ember is generally M-shaped in end view and includes a pair of main legs 208 connected by a generally U-shaped portion having a central curved portion 210 which i~ spaced from the terminal ends and is cur~ed outwardly away therefro~. As bes~ shown in PIGURES 17 and 18, curved central portion 210 is axially offset fro~ ~ain legs 208. When a pair of fin members are reversely positioned with ~he ter~inal ends of main legs 208 thereof engaging one another as shown in FlGURE
16, the inner facing surfaces of curved central portions 210 lie on the periphery of a co~mon circle haYing a dia~eter approxima~ely the same as the diameter of the botto~ of bolt groove 206. In addition~ the distance between the opposite axial ends of curYed central portion 210 is approxi~at~ly the same as the distance between the inner facing surfaces of projections 202,204.
Whe~ a pair of fin members are reversely positioned in coopera~ive relationship around a bolt F
as shown in ~IGURE 3 7 one end of legs 208 engages a circumferential shoulder 212 in the bore of body part C. A snap ring 214 received in a suitable circu~ferential groove retains support fins G in the desired position. As shown in FIGURE 3, curved central portions 210 are axially offset fro~ legs 208 in a dlrcction away fro~ body valve E. The shape and position of th~ fin ~embers allows maxi~um flow through the bor~ of body part C while providing ~a%imu~ s~reng~h or holding body valve E in pvsition and resisting both sho~r and compressive forces.
~s shown in PIGURES l9 and 20, poppet guide 5 ~e~ber ~ includes a plurality of radially extending circumferentially spaced apart spokes 220 issuing from a central area 222. A central opening 224 extends through the cen~r~l area and is surrounded by a circular raised boss 226. The outor ter~inal ends 228 of spokes 220 are curYed to lie on the periphery of a co~on circle and the spokes are equidistan~ly spaced fro~ one another.
~s shown in FIGURE 20, spokes 220 are inclined out of a flat plane in a direction opposiee to ehe projecting direction of circular boss 2260 As shown in FIGURE 4, poppet guide bolt J is surrounded by coil spring 14 and has a terminal end in t~e general shape of a ~runcated cone ~hich abuts a corresponding conical botto~ surface of a bore in poppet I .A shoulder 230 wi thin a stem adapter 232 engages the outer end portions of spokes 220 on poppet guide K. A
s~all diaaeter portion 234 of guide bolt J is closely recei~ed and slidably guided through hole 224. An enlarg~d portion o~ the guide bolt provides an abutment 236 for engagin~ the end of circular boss 226. One end of coil spring 14 is closely received over circular boss 226 and the other end thereof engages the back of an enlar~ed head on the ter~inal end portion of guide bolt J within the bore in poppet I for normally biasing the poppet to its closed position. Th0 $nterior outer end portion of ste~ ~e~ber H is suitably threaded for cooperation with external threads on stem adapter 232t and the i~terior of ste~ adap~er 232 is threaded as indicatod at 240 for connection to another fitting on a conduit. Here, too, in~erconnecting ~eans of types other than threads 240 could be advantageously employed.
~ ith reference to PIGURES 2l and 22, the oxternal diameter portion of stem member H which is receiYed within operating sleeve N is varied by adding çylindrical shims 246 of Yarious thicknesses ther~to.
5 Shus, the external dlameter S of ste~ ~ember H ~ay be selecti~ely varied~ The inner diameter of reversely curved portion 40 of operatin~ sleeve N is varied by machining the portion to variable desired internal diameters T. The largest external dia~eter portion of 10 body val~e E is varied by machining it to variable dia~eters Y. The diame~er of the s~allest internal dianeter portion 250 at the open inner end of stem ~ember H is similarly varied by machining it ~o variable diameters U.
A plurality of pairs of mating body and stem asse~blies are constructed and di~ensioned such that the body asse~bly of one key will ~ate only wi~h a ste~
asse~bly having the same key7 Progressi~ely larger keys have progressively larger external ste~ member diameters S, larger internal operating sleeve diameters T, larger body valve external dia3eters V, and larger stem open end internal diaoeters U. Thus, there is provided a coded sysee~ of couplings including 8 plurality of pairs of keyed ~atin8 body and ste~ asse~blies ~,B. Each body asse~bly includes an inner body valve E and an outer coupling sleeYe defined by.operating sleeve N. Each ste~ asse~bly has a ste~ member H with an external diamster S ~nd an ope~ stem end through which body Yalve ~ is received. Mating body and stem assernhlies are dimensiongd for close reception of ste~ member H within slee~e N and for close reception of body valve ~ within ~nner ste~ ~embe~ end 250. With this arrangement, body and ste~ assemblies having different keys will not mate or connect due to interference either between a stem ~e0ber H and a coupling sleeve N or between a body valve E and 9 stem inner end 250.
~ xamples of various diameters for a plurality of dlfferent keys i5 shown in FIGUR~ 22. A stem asse0bly will not couple with the body of a higher key 5 because of interference between valve body E and internal opening 250. A body assembly having a hi8her key ~ill always have a larger external diameter on body Yalve E than the corresponding internal dia~eter at open end 250 of a s~aller key ste~ assembly. A body asse~bly 10 will not mate or connect with a ste~ assembly of a hi8her key because of interference be~ween the external dia~eter of stem oe~ber H snd the internal diameter sf sleeY~ N. A stem assembly of a higher key will always ha~s a larger external stem member diameter than the lS correspo~ding internal dia~eter of the sleeve on a s~aller key body asse~bly.
The invention has been described with reference to the preferred e~bodiment. ObYiously, modifications and alterations will occur to others upon a reading and 20 understanding of ~his specification. It is intended to include all such ~odifications and alterations insofar as they co~e within the scope of the appended claims or the equivalents thereof.
Claims (27)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A seal between cooperating inner and outer fluid coupling parts having a common longitudinal axis and respectively including closely facing outer and inner surfaces extending generally parallel to said axis, said inner part having a terminal inner end spaced radially inward from said outer surface thereof, said inner part including an external slow taper surface extending therealong from said terminal inner end in a direction outwardly toward said outer surface thereof to define a packing receiving space between said slow taper surface and a portion of said inner surface on said outer part, and a deformable packing ring shaped and sized for close reception in said packing receiving space and having inner and outer packing ring surface portions respectively shaped to generally correspond and cooperate with said slow taper surface and said inner surface of said outer part.
2. The seal as defined in claim 1 including biasing means for biasing said packing ring into said packaging receiving space.
3. The seal as defined in claim 1 including a cup-like packing gland partially received in said inner part at said inner end thereof, said gland having an inwardly extending flange inside of said inner part and an outwardly extending flange outside of said inner part, and spring means engaging said inwardly extending flange and biasing said gland in a direction for engaging said outwardly extending flange with said packing and urging same into said packing receiving space.
4. The seal as defined in claim 1 wherein said slow taper surface turns sharply outward adjacent the intersection thereof with said outer surface of said inner part to define an apex portion of said packing receiving space, and a backup ring separate from said packing ring positioned in said packing receiving space at said apex portion to prevent extrusion of said packing ring between said facing surfaces of said inner and outer parts at said apex portion.
5. The seal as defined in claim 4 wherein said backup ring is constructed of a less deformable material than said packing ring.
6. The seal as defined in claim 5 wherein said packing ring is comprised of TFE and said backup ring is comprised of TFE plus a harder filler material.
7. A seal between cooperating inner and outer fluid coupling parts having a common longitudinal axis and respectively including closely facing outer and inner surfaces extending generally parallel to said axis, said inner part having a terminal inner end spaced radially inward from said outer surface thereof and including an external taper surface extending therealong from said terminal inner end in a direction outwardly toward said outer surface thereof to define a packing receiving space between said taper surface and a portion of said inner surface on said outer part, said taper surface including a slow taper surface portion extending from said terminal inner end toward said outer surface of said inner part and turning sharply outwardly at a short fast taper surface portion adjacent the intersection thereof with said outer surface of said inner part to define an apex portion of said packing receiving space, a deformable packing ring received in said packing receiving space, a deformable backup ring of harder material than said packing ring positioned in said packing receiving space at said apex portion thereof between said packing ring and said fast taper surface portion, and biasing means for biasing said packing ring into said packing receiving space.
8. The seal as defined in claim 7 wherein said packing ring has inner and outer surface portions respectively shaped to generally correspond and cooperate with said slow taper surface portion and said inner surface of said outer part, said packing ring extending axially beyond said terminal inner end of said inner part in a direction away from said inner part and terminating at a packing ring end, and said biasing means being in engagement with said packing ring end.
9. A seal between inner and outer fluid coupling parts respectively having closely facing cooperating outer and inner surfaces, said inner part having a terminal inner end spaced radially inward from said outer surface thereof and including an external taper surface extending therealong from said inner end outwardly toward said outer surface thereof to define a packing receiving space, a packing ring received in said packing receiving space, a packing gland partially received in said inner part at said inner end thereof and having an inwardly extending flange inside of said inner part and an outwardly extending flange outside of said inner part, and biasing means acting on said inwardly extending flange for biasing said gland in a direction for engaging said outwardly extending flange with said packing and urging same into said packing receiving space.
10. The seal as defined in claim 9 wherein said biasing means comprises a coil spring having one end engaging said inwardly extending flange and an opposite end engaging said outer part.
11. The seal as defined in claim 9 wherein said gland is slidably guided for axial movement inside of said inner part.
12. The seal as defined in claim 9 wherein said inner and outer coupling parts respectively define a body and slide, said slide being axially movable in one direction further onto said body and in an opposite direction off from said body, said biasing means also acting on said slide for normally biasing same in said opposite direction, and means for preventing complete displacement of said slide from said body.
13. A seal between cooperating inner and outer fluid coupling parts having a common longitudinal axis and respectively including closely facing outer and inner surfaces extending generally parallel to said axis, said inner part having a terminal inner end spaced radially inward from said outer surface thereof, said inner part including an external slow taper surface extending therealong from said terminal inner end in a direction outwardly toward said outer surface thereof to define a packing receiving space between said slow taper surface and a portion of said inner surface on said outer part, and deformable packing ring shaped and sized for close reception in said packing receiving space and having inner and outer packing ring surface portions respectively shaped to generally correspond and cooperate with said slow taper surface and said inner surface of said outer part, and biasing means including a packing gland member guided centrally within said inner coupling part and having a radially outward extending flange for engaging said packing ring and biasing said packing ring into said packing receiving space.
14. The seal as defined in claim 13 wherein said slow taper surface turns sharply outward adjacent the intersection thereof with said outer surface of said inner part to define an apex portion of said packing receiving space, and a backup ring separate from said packing ring positioned in said packing receiving space at said apex portion to prevent extrusion of said packing ring between said facing surfaces of said inner and outer parts at said apex portion.
15. The seal as defined in claim 14 wherein said backup ring is constructed of a less deformable material than said packing ring.
16. The seal as defined in claim 15 wherein said packing ring is comprised of TFE and said backup ring is comprised of TFE plus a harder filler material.
17. A seal between cooperating inner and outer fluid coupling parts having a common longitudinal axis and respectively including closely facing outer and inner surfaces extending generally parallel to said axis, said inner part having a terminal inner end spaced radially inward from said outer surface thereof, said inner part including an external slow taper surface extending therealong from said terminal inner end in a direction outwardly toward said outer surface thereof to define a packing receiving space between said slow taper surface and a portion of said inner surface on said outer part, a deformable packing ring shaped and sized for close reception in said packing receiving space and having inner and outer packing ring surface portions respectively shaped to generally correspond and cooperate with said slow taper surface and said inner surface of said outer part, and a cup-like packing gland partially received in said inner part at said inner end thereof, said gland having an inwardly extending flange inside of said inner part and an outwardly extending flange outside of said inner part, and spring means engaging said inwardly extending flange and biasing said gland in a direction for engaging said outwardly extending flange with said packing and urging same into said packing receiving space.
18. The seal as defined in claim 17 wherein said outwardly extending flange on said gland is inclined at an angle to apply both axially and radially outwardly directed force components to said packing.
19. The seal as defined in claim 18 wherein said outwardly extending flange on said gland extends outwardly to a point closely adjacent said inner surface on said outer coupling part.
20. A seal between cooperating inner and outer fluid coupling parts having a common longitudinal axis and respectively including closely facing outer and inner surfaces extending generally parallel to said axis, said inner part having a terminal inner end spaced radially inward from said outer surface thereof and including an external taper surface extending therealong from said terminal inner end in a direction outwardly toward said outer surface thereof to define a packing receiving space between said taper surface and a portion of said inner surface on said outer part, said taper surface including a slow taper surface portion extending from said terminal inner end toward said outer surface of said inner part and turning sharply outwardly at a short fast taper surface portion adjacent the intersection thereof with said outer surface of said inner part to define an apex portion of said packing receiving space, a deformable packing ring received in said packing receiving space, a deformable backup ring of harder material than said packing ring positioned in said packing receiving space at said apex portion thereof between said packing ring and said fast taper surface portion, biasing means for biasing said packing ring into said packing receiving space, said packing ring including an outer end portion extending axially beyond said terminal inner end of said inner coupling part, and said biasing means including a packing gland guided within said inner coupling part and carrying a spring centrally therein, said packing gland having a radially extending flange engaging said outer end portion of said packing gland.
21. A seal between inner and outer fluid coupling parts respectively having closely facing cooperating outer and inner surfaces, said inner part having a terminal inner end spaced radially inwardly from said outer surface thereof and including an external taper surface extending therealong from said inner end outwardly toward said outer surface thereof to define a packing receiving space, a packing ring received in said packing receiving space, a packing gland partially received in said inner part at said inner end thereof and having an inwardly extending flange inside of said inner part and an outwardly extending flange outside of said inner part, and biasing means acting on said inwardly extending flange for biasing said gland in a direction for engaging said outwardly extending flange with said packing and urging same into said packing receiving space.
22. The seal as defined in claim 21 wherein said biasing means comprises a coil spring having one end engaging said inwardly extending flange and an opposite end engaging said outer part.
23. The seal as defined in claim 21 wherein said gland is slidably guided for axial movement inside of said inner part.
24. The seal as defined in claim 21 wherein said inner and outer coupling parts respectively define a body and slide, said slide being axially movable in one direction further onto said body and in an opposite direction off from said body, said biasing means also acting on said slide for normally biasing same in said opposite direction, and means for preventing complete displacement of said slide from said body.
25. The seal as defined in claim 21 wherein said outwardly extending flange is configured to urge said packing radially while urging same into said packing receiving space.
26. The seal as defined in claim 23 wherein said outwardly extending flange is inclined at an angle to apply both axial and radially outwardly directed force components to said packing.
27. A seal between cooperating inner and outer fluid coupling parts having a common longitudinal axis and respectively including closely facing outer and inner surfaces extending generally parallel to said axis, said inner part having a terminal inner end spaced radially inward from said outer surface thereof and including an external taper surface extending therealong from said terminal inner end in a direction outwardly toward said outer surface thereof to define a packing receiving space between said taper surface and a portion of said inner surface on said outer part, said taper surface including a slow taper surface portion extending from said terminal inner end toward said outer surface of said inner part and turning sharply outwardly at a short fast taper surface portion adjacent the intersection thereof with said outer surface of said inner part to define an apex portion of said packing receiving space, a deformable packing ring received in said packing receiving space, a deformable backup ring of harder material than said packing ring positioned in said packing receiving space at said apex portion thereof between said packing ring and said fast taper surface portion, biasing means for biasing said packing ring into said packing receiving space, said packing ring having inner and outer surface portions respectively shaped to generally correspond and cooperate with said slow taper surface portion and said inner surface of said outer part, and said packing ring extending axially beyond said terminal inner end of said inner part in a direction away from said inner part and terminating at a packing ring end, and said biasing means being in engagement with said packing ring end.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000569936A CA1260984A (en) | 1983-01-19 | 1988-06-20 | Coupling |
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US06/459,150 US4637432A (en) | 1983-01-19 | 1983-01-19 | Coupling |
| US459,150 | 1983-01-19 | ||
| CA000445548A CA1248992A (en) | 1983-01-19 | 1984-01-18 | Coupling |
| CA000569936A CA1260984A (en) | 1983-01-19 | 1988-06-20 | Coupling |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000445548A Division CA1248992A (en) | 1983-01-19 | 1984-01-18 | Coupling |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1260984A true CA1260984A (en) | 1989-09-26 |
Family
ID=25670272
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000569936A Expired CA1260984A (en) | 1983-01-19 | 1988-06-20 | Coupling |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1260984A (en) |
-
1988
- 1988-06-20 CA CA000569936A patent/CA1260984A/en not_active Expired
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |