US3643707A

US3643707A - Static-reducing and vapor-reducing loading valve with low-pressure drop

Info

Publication number: US3643707A
Authority: US
Inventors: Harold W Ensign
Original assignee: Cla Val Co
Current assignee: Cla Val Co
Priority date: 1970-09-08
Filing date: 1970-09-08
Publication date: 1972-02-22
Anticipated expiration: 1989-02-22

Abstract

A valve for use in loading the tanks of tank trucks with gasoline or other dangerous liquid. The valve incorporates an automatic flow restrictor for greatly restricting flow when the tank is substantially empty, thus minimizing generation of vapors and static electricity, but for permitting rapid flow when the valve outlet into the tank is submerged. An internal shoulder, of small size and located close to the top of the valve, is provided to greatly reduce the flow velocity of the liquid when the tank is substantially empty. Such shoulder permits high-volume rapid flow to occur with minimized pressure drop. An external deflector causes the liquid to flow generally horizontally when entering the tank.

Description

United States Patent Ensign 1 Feb. 22, 1972 [54] STATIC-REDUCING AND VAPOR- [56] References Cited REDUCING LOADING VALVE WITH LOW PRESSURE DROP UNITED STATES PATENTS [72] inventor: Harold W Ensign Fullerton Calif. 2,791,355 5/1957 Morgan ..l41/286 [73] Assignee: CIa-Val Co., Costa Mesa, Calif. Primary B 1- Filed: Sept. 1970 Anomey- Gausewltz, Carr & Rothenbcrg [21] Appl. No.: 70,247 [57] ABSTRACT Related Application Data A valve for use in loading the tanks of tank trucks with gasoline or other dangerous liquid. The valve incorporates an [63] Continuation-impart of Ser. No. 799,567, Feb. 17, automatic flow restrictor for greatly restricting flow when the 1969. tank is substantially empty, thus minimizing generation of vapors and static electricity, but for permitting rapid flow [52] US. Cl. ..141/286, 137/386, 141/128, when the valve outlet into the tank is submerged. An internal 2/564 shoulder, of small size and located close to the top of the [51] Int. Cl. ..B65b 1/04, B65b 3/04 valve, is provided to greatly reduce the flow velocity of the [58] Field of Search 141/128, 286, 374, 31 l, 392; liquid when the tank is substantially empty. Such shoulder permits high-volume rapid flow to occur with minimized pressure drop. An external deflector causes the liquid to flow generally horizontally when entering the tank.

25 Claims, 4 Drawing Figures Z; 2 5; I] 48 f4 52 x 9/ k If Q I! T R. T j f 2 a if g 1/ /n l/ I! a STATIC-REDUCING AND VAPOR-REDUCING LOADING VALVE WITH LOW-PRESSURE DROP C ROSS-REF ERENCE TO RELATED APPLICATION This application is a continuation-in-part of my copending patent application Ser. No. 799,567, filed Feb. 17, 1969, for Static-Reducing and Vapor-Reducing Loading Valve for Tank Trucks.

DESCRIPTION OF PRIOR ART AND OF RELATED CONSTRUCTIONS Theprior art known to applicant is described in said patent application and in a notice of prior art filed therein.

The loading valve disclosed by said patent application is not prior art against the loading valve described and claimed in the present patent application. However, a description of the deficiencies of the internal deflector means 32 described in said patent application will permit a better understanding of the present internal deflector means (shoulder). Such internal deflector means 32 of said application is located near the bottom of the loading valve, and incorporates a wide shoulder 83 which inclines upwardly and inwardly. The upwardly and inwardly inclined shoulder is so large as to very materially constrict the outlet from the valve into the tank, thereby creating a substantial pressure drop across the valve at high flow volumes.

SUMMARY OF THE INVENTION The loading valve of the present invention has an inlet port on the outlet side of which is movably mounted a flow restrictor, such flow restrictor preferably comprising a poppet or other valve element. Sensing and actuating means are provided to maintain the flow restrictor in a low-flow position relatively adjacent the inlet port when the tank being filled is substantially empty, and to maintain it in a high-flow position relatively remote from the inlet port when there is sufficient liquid in the tank to effectively submerge the outlet from the loading valve. The flow restrictor is adapted, particularly when in such low-flow position, to deflect the in-flowirtg liquid against the interior surface of the outer wall of the valve body. Such outer wall is shaped in such manner that the liquid does not splash but instead hugs the wall and flows in a sheet. An inwardly extending deflector shoulder is provided on such outer wall ofthe valve body, in the path of such sheet. In accordance with the present construction, which is greatly preferred, such shoulder is narrow and is located adjacent the upper portion of the valve. The shoulder greatly impedes the flow of liquid, causing the reduced velocity liquid to substantially fill the valve and to flow out the bottom thereof in splash-free manner, An external deflector is provided to cause the outflowing liquid to travel horizontally instead of vertically.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a schematic transverse sectional view illustrating a tank truck having a fill pipe inserted therein and with the present loading valve at the end of such pipe;

FIG. 2 is a longitudinal sectional view of the loading valve, the section being taken on the broken line indicated at 2-2 in FIG. 3;

FIG. 3 is a horizontal sectional view on line 3-3 of FIG. 2;

and

FIG. 4 is a horizontal sectional view on line 4-4 of FIG. 2.

DESCRIPTION OF THE PREFERRED EMBODIMENT The first portion of this description is substantially identical to major portions of the description contained in said patent application, but modified for purposes of brevity. t

The second portion of this description, under the heading Internal Shoulder Means," comprises a description of the deflector or shoulder which is a great improvement on the internal shoulder or deflector means of such patent application. Thereafter, a summary of operation is given.

The portions of the description of said application which were omitted from the present one were omitted for purposes of brevity. The specification and drawings of said application are hereby incorporated by reference into the present applica tion, as though set forth in full herein.

Referring to FIG. 1, a tank truck 10 is illustrated schematically as incorporating a tank 11 having a fill opening 12 at the upper portion thereof, A fill pipe 13 extends vertically downwardly through fill opening 12 to the tank bottom and has mounted at the lower end thereof the loading valve 14 of the present invention, the arrangement being such that the lower end of the valve seats on the tank bottom. Fill pipe 13 is connected through suitable shutoff valving (not shown) to a source (not shown) of gasoline or other liquid.

Referring next to FIG. 2 in particular, the valve casing or body is illustrated to comprise upper, middle and lower sections 16 18, respectively, which are connected to each other by means of a plurality of circumferentially spaced screws 19 (FIGS. 2 and 3). The upper end of section 16 is connected coaxially, as by the threaded connection 21, to the lower end of fill pipe 13. The middle portion of upper section 16 is necked down at 22 and defines a flow port 23 which is circular in shape and coaxial with the longitudinal axis of the valve, At its region below the necked-down portion 22, upper casing section 16 flares outwardly at 24 and cooperates with remaining portions of the valve to define an annular outlet chamber indicated hereinafter. The flared portion 24' is preferably rounded or generally dome shaped, as shown, in order that liquid directed thereagainst will hug the wall, in the manner of a sheet, particularly when the valve is in the illustrated lowflow position.

The middle section 17 of the valve casing has a cylindrical outer wall 26 (FIGS. 2 and 3) which is connected through a plurality of circumferentially spaced radial webs 27 with a cylindrical intermediate wall 28. Intermediate wall 28, in turn. is connected through two radial webs 29 with a cylindrical central wall 30.

Lower section 18 of the casing has a cylindrical outer wall 31 which merges at its lower end with a somewhat smaller diameter throat portion 32. Such throat portion is much larger in diameter than is the deflector means 32 described in the above-cited patent application. The lower end of section 18 is open (being a discharge annulus as stated hereinafter), and is integral with a plurality (for example, three) of circumferentially spaced legs or posts 33. Such legs are secured by screws 34 to the peripheral portion of an additional deflector means 36 adapted to seat on the bottom of tank 11 as shown in FIG. 1.

The additional deflector means 36 includes a hollow steam 37 which curves inwardly and upwardly coaxially through the throat portion 32. At its upper end, stem 37 is shaped to seat the lower portion of a wall means 38. Such wall means has an outer generally frustoconical wall 39 (FIGS. 2 and 4) the upper edge of which seats against the lower edge of the abovedescribed cylindrical wall 28 and forms an extension thereof. Correspondingly, wall means 38 has an inner wall 41 which is cylindrical in shape and seats against the lower end of central wall 30 to form an extension thereof. The outer and inner walls 38 and 41 ofwall means 38 are connected by radial webs 42 which are located correspondingly to the webs 29 shown in FIGS. 2 and 3, and which seat (as extensions) against the lower ends of such webs 29.

A flow control poppet 44 is movably mounted in the valve casing beneath flow port 23 and operates automatically to change the flow rate from a low-flow condition to a high-flow condition. Poppet 44 has a cylindrical sidewall 45 which telescopes slidably over the exterior cylindrical surfaces of wall 28, there being a packing ring 46 (for example, the illustrated chevron seal) therebetween to prevent excessive leakage of liquid from the interior of the poppet. At its upper end, sidewall 45 merges with a frustoconical upper wall 47 which converges upwardly, and such wall 47 is in turn integral with a downwardly extending tubular sleeve 48 the outer diameter of which is less than the inner diameter of central wall 30.

A combination guide and conduit is provided in the form of a tubular stem 50 which extends slidably through sleeve 48, coaxially of the longitudinal axis of the valve, and is exteriorly threaded at its upper end to receive an adjustable stop nut 51, The stem 50 is press fit in a cylindrical opening through an annular shoulder portion 52 which is formed integrally with and within the wall 30.

Stop nut 51 is normally adjusted to a position such as that illustrated in FIG. 2, and which stops upward travel of poppet 44 prior to the time that the casing section 16 is engaged. Accordingly, there is always a circular flow passage 53 between the poppet and the necked-down portion 22 of the casing. When the poppet is in the illustrated position, or at any other desired upper position (determined by the setting of nut 51), the rate of flow of liquid through port 23 and downwardly into the tank 11 is small. The poppet subsequently moves downwardly to a lower or full-flow position at which the lower edge of wall 45 seats on a stop shoulder 54.

The region of the valve casing above flow port 23 may be termed the inlet chamber 56. Such chamber constantly communicates through the circular flow passage 53 (or through a much larger and corresponding flow passage which exists when the poppet 44 is in its lower or full flow position) with an annulus or outlet chamber 57. The upper portion of such annulus 57 is defined between poppet side wall 45 and the flared portion 24 of easing section 16. The intermediate region of such annulus 57 is defined between

cylindrical walls

26 and 28 of middle section 17. The lower portion of the annulus is defined between walls 31 and 39, the former wall being part of lower section 18 and the latter wall being in the wall means 38.

A chamber 58 is defined generally between poppet wall 47 and an opposed stationary wall 59, the latter extending integrally between the upper ends of

walls

28 and 30. Such chamber 58 (the power chamber) is sealed by the packing ring 46 as previously indicated.

The wall 59 also cooperates with

walls

28 and 30, and also with walls 39 and 41, in defining an annular chamber 61 which may be termed the ballast or reservoir chamber.

Defined below shoulder 52 and within the cooperating cylindrical walls 30 and 41 is a chamber 62 which may be termed the control chamber. Such chamber, having a cylindrical sidewall (a surface of revolution about the axis of the valve), is in constant communication with a spillway or drain chamber 63 which is defined within stem 37. An outlet from the spillway 63 is provided at 64 in the form of a plurality of notches in the lower peripheral portion of the deflector means 36. Thus, there is always a means of communication between spillway 63 and the lowermost part of the interior of tank 11, even though the bottom wall of the tank may in some instances be flat.

The lower end of stem 50 is counterbored to receive a power nozzle 66. Thus, liquid under pressure flows from inlet chamber 56 through the passage 67 in stem 50, and thence at high velocity through nozzle 66. Assuming that the control chamber 62 is initially full of air as distinguished from liquid, a high-velocity jet of liquid emanates from power nozzle 66 and passes coaxially to and into a receiver port 68 in a receiver element 69 (FIGS. 2 and 4).

The illustrated receiver 69 is generally wheel-shaped, having an outer cylindrical portion which is seated between the upper end of stem 37 and a shoulder at the lower portion of inner wall 41. Suitable seals or O-rings 71 are provided to prevent leakage of fluid along the outer cylindrical surface of the receiver. A plurality of web elements 72, FIGS. 2 and 4, connect the outer portion of the receiver to an axial portion thereof incorporating the upwardly facing receiver port 68. Each of the webs 72 has formed therethrough a radial passage 73 adapted to transmit fluid from receiver port 68 to an annular groove 74 in the wall means 38.

Groove 74 communicates with a plurality (illustrated as two) of passages or conduits 76 which extend upwardly through the

webs

42 and 29 to power chamber 58. Because of the action of power nozzle 66, which directs the high-velocity jet accurately into receiver port 68, the great majority of liquid passing through control chamber 62 when it is filled with air, and prior to the time that power chamber 58 is filled with liquid, passes through passages 73 and groove 74 to passages 76 and thus to power chamber 58 to rapidly fill the same with liquid. However, after such chamber 58 is filled, which occurs only a few seconds after initiation of flow through fill pipe 13, the great majority of fluid emanating from power nozzle 66 flows through openings 77 (FIG. 4) in the receiver 69 and thus downwardly through spillway 63 into the bottom of the tank.

Check valves in the form of balls 78 (only one of which is shown in the drawings, FIG. 2) are provided at the upper end of each passage or conduit 76. More specifically, the balls 78 seat in chambers 79 formed in webs 29, and are maintained in such chambers by pins 80. The balls 78 do not substantially impede upward flow of liquid through the passages 76 into power chamber 58, but do prevent downflow of liquid from such chamber through passages 76.

An additional or vent passage 81 communicates through poppet wall 47 with the extreme upper end of power chamber 58, and extends therefrom to the upper end of the outlet chamber or annulus 57. Vent 81 is much smaller in diameter than is the port 68, etc., so that despite the presence of vent 81 a very large pressure may be built up in the power chamber 58 due to inflow from power nozzle 66.

When gasoline or other liquid is initially passed through pipe 13 to inlet chamber 56, power chamber 58 fills very rapidly (as described above) and air therein is vented through port or passage 81 to outlet annulus 57. As soon as chamber 58 fills with liquid, a relatively static condition is created whereby the pressure in chamber 58 is only a small amount less than the inlet pressure present in inlet chamber 56, there being very little pressure drop in the various passages since the only flow therethrough is that necessary to make up for drainage through the small-diameter vent passage 81.

The diameter (and area) of the lower surface of poppet wall 47 is caused to be sufficiently greater than the diameter (and area) of flow port 23 that the upward force acting on the poppet 44, as the result of the pressure in chamber 58, overcomes the downward force acting thereon due to the pressure in chamber 56. Therefore, the poppet rapidly moves upwardly to the extreme position permitted by stop 51 and illustrated in the drawings.

It follows that within a few seconds after application of fluid pressure to the inlet chamber 56, the flow therefrom is constricted greatly. Liquid then flows at high velocity from the inlet chamber through annulus 53 in the form of a sheet or cone of liquid. The sheet of liquid passes downwardly along the upper and peripheral surface of frustoconical poppet wall 47 into contact with the inner surface of the rounded and flared portion 24 of casing section 16, following which the liquid is deflected by an internal deflector means as described in detail hereinafter.

The additional deflector means 36, located at the bottom of the valve, has an upper surface 84 (outer surface of stem 37) which curves downwardly and radially outwardly, the outer end thereof being generally horizontal. Therefore, the liquid flowing downwardly through the discharge annulus 85 (formed between stem 37 and the lower end of casing section 18) engages such surface 84 and therefore is smoothly directed radially outwardly along the bottom of the tank.

The constricting action effected by poppet 44, in combination with the deflecting and velocity reducing actions achieved by the deflector means, cause initial filling of tank 11 to occur in a splash-free manner not characterized by substantial vapor formation or by generation of static electricity.

During the tank-filling operation, air (and, thereafter, liquid) enters control chamber 62 through a path which includes a control port 88 and passage 89, the latter communicating through an inlet 90 with control chamber 62. Air is aspirated through port 88 into passage 89 due to the action of the highgvelocity jet from nozzle 66. The air then strikes a plug 91 and flows downwardly through a passage portion 92 into ballast chamber 61, which is relatively large in size as shown in FIG. 3. The air from the ballast chamber then flows upwardly through a passage portion 93 to the passage 89 and thus to inlet 90 leading to control chamber 62. The passage 89, etc., extend through a web portion 95 of the central casing section 17.

The control port 88 is located sufflciently far above the lower edge of casing section 18 (which defines the upper limit of the outlet annulus from the loading valve) that highvelocity flow of fluid through the loading valve may occur without danger of generating static electric charges or excessive vapors. When the surface of the gasoline or other liquid introduced into tank 11 reaches the elevation of control port 88, such liquid is drawn in through the control port 88 and communicating passage and chamber means to control chamber 62. Chamber 62 therefore fills with liquid, so that the velocity of the jet emanating from nozzle 66 is very greatly reduced due to the impedance of the liquid to jet flow from the nozzle. The pressure present at receiver inlet 68 then drops drastically, with consequent reduction in the static pressure present in power chamber 58. The pressure reduction is sufficiently great that the upward forces acting against poppet 44 are overcome by the downward forces acting thereon, so that the pressure in inlet chamber 56 operates to force poppet 44 downwardly for the full extent of its travel until the lower poppet edge engages seat 54.

During downward poppet movement, liquid from power chamber 58 vents through passage 81 into annulus 57. Such liquid is prevented from venting through passages 76 due to the fact that the balls 78 are then seated. The venting through passage 81 is relatively slow, due to the small cross-sectional area of such passage, which insures that opening of poppet 44 will occur slowly and will not create undesired surges in the lines leading to fill pipe 13. It will thus be seen that the check valves permit rapid shifting of poppet 44 to its constricting position, as is desired in order to prevent static buildup and vapor formation during the initial stages of the tank-loading operation, but cause a slow shifting of the poppet 44 to fully open condition as is desired to prevent line surges.

So long as control chamber 62 is maintained filled or substantially filled with liquid, the poppet 44 remains in its lower position (seated on seat 54) causing the annulus 53 to be very large instead of constricted as shown in FIG. 2. Therefore, the flow from inlet chamber 56 through port 23 to annulus 57 and thence out the bottom of the valve becomes very large as is desired for rapid filling of tank 11 with liquid. If, for any reason, the loading valve 14 is lifted until control port 88 is above the surface of the liquid in tank 11, control chamber 62 becomes cleared of liquid (such liquid draining through openings 77, FIG. 4, and into spillway 63). The jet emanating from power nozzle 66 is then unimpeded by liquid, so that the pressure at receiver inlet port 68 builds up to effect flow of liquid through passages 76 to power chamber 58. Thus, and as described above, poppet 44 is shifted upwardly to the illustrated flow-constricting position.

It is to be understood that the above-described sensing and flow-constricting mechanism, and which is also described and claimed in the above-cited patent application, is not the only one which may be employed. Although greatly less satisfactory, other means (including those incorporating pilot valves and/or other devices) for sensing liquid level and for selectively'restricting flow may be resorted to without avoiding certain of the appended claims.

INTERNAL SHOULDER MEANS When the present loading valve is in the low-flow" condition shown in FIG. 2, the pressure in the inlet chamber 56 is quite high. Such inlet pressure may then be, for example, in the range of from 50 to I00 p.s.i. Because of the presence of such high inlet pressure, the liquid flowing through the very narrow circular flow passage 53 travels at a high velocity. As an example, the present valve, when associated with a flll pipe 13 which is 6 inches in diameter, may deliver from I00 to 150 gallons per minute of liquid when in the low-flow condition of FIG. 2. To produce a flow of this magnitude, the velocity of the liquid passing through the restricted passage 53 must be high.

It is emphasized that the term low-flow" does not refer to low velocity of flow. Instead, the terms refers to a relatively low volume of liquid in comparison to the high volume which is delivered when the valve is in high-flow" condition. The

high volume may be, for example, l,000 gallons per minute when the fill pipe 13 is 6 inches in diameter.

In the construction described in the cited patent application, the fast-flowing liquid (after emanating from passage 53) passes clear down to the deflector means 32, then reverses in direction and floods the valve. Such operation is satisfactory, but produces disadvantages (as indicated above) including a substantial pressure drop across the valve when operating in the high-flow condition.

Because of such pressure drop, a lower valve section 18 (of the valve described in the cited patent application) which is designed for a 4-inch fill pipe 13 can not practically be employed with a 6-inch pipe 13. This is because the pump capacity at many tank-truck-loading racks is insufficiently great to produce a high flow rate (such as 1,000 gallons per minute) through such section 18 described in the cited application. To build such section 18 (and also the central section 17) larger requires a great deal of additional expense and, furthermore, makes it cumbersome to pass the valve through opening 12 in the tank truck.

The construction described in the present patent application makes it fully practical to use the same lower valve section 18 (and central section 17) in conjunction with both 4- inch and 6-inch pipes 13, with no loss of flow volume and no need for new pump capacity. It is emphasized, however, that certain of the appended claims apply to both the construction described in the present patent application and to the construction described in the cited patent application.

In accordance with the present construction, and as above stated, the internal deflector 32 of the cited patent application is omitted and is replaced by a throat portion 32 of much larger diameter (with consequent reduced constriction and lower pressure drop). Instead of the return bent and wide shoulder 83 of the cited application, the present construction provides a narrow internal shoulder or deflector located relatively near the upper end of the valve (but well below port 23). The illustrated shoulder 100 is radial, but it may be somewhat return-bent (upwardly inclined, like shoulder 83 of the cited patent application) if desired.

Shoulder or deflector 100 is very economically formed at the junction between

sections

16 and 17. Thus, the internal diameter of section 16, at such junction, is made about one quarter inch larger than the internal diameter of section 17 at such junction. The width of the shoulder is, therefore, only about one-eighth inch.

The shoulder 100 extends around the full circumference of the valve, except at the few locations (one being shown at the left in FIG. 2) where internal bosses are provided for screws 19. correspondingly, the throat portion 32 of the present construction, and shown at the right in FIG. 2, extends for the full circumference of the valve except at the three legs 33 (one such leg being shown at the left in FIG. 2).

It has been found, surprisingly, that even the extremely small shoulder 100 produces a filling of the annulus or chamber 57 when the valve is in the illustrated low-flow condition. A very fast-flowing sheet of liquid emanates from circular flow passage 53, and then engages the internal curved surface of flared portion 24. Such surface, and the frustoconical upper wall 47 of poppet or constrictor 44, are so shaped and related that the sheet hugs the internal curved surface and then impinges against shoulder 100. The resulting very drastic reduction in flow velocity causes filling or substantial filling of annulus 57. Thereafter, the liquid passes downwardly through annulus 57 and through throat portion 32 (discharge annulus 85) into engagement with the lower or external deflector means 36. The latter element causes the liquid to enter the tank 11 horizontally, in splash-free manner. It is pointed out that if

annuli

57 and 85 were not filled, the inflowing liquid would splash off the deflector means 36 and therefore create vapors and static electricity.

The setting of nut 51 should be such that the minimum gap between poppet wall 47 and the adjacent neck of valve section 16 (around port 23) is very small. Such minimum gap should, preferably, be less than the width of shoulder or deflector 100. The minimum gap should be about one-sixteenth inch (whereas the shoulder width is preferably one-eighth inch as stated above).

It is pointed out that the high-velocity sheet of liquid which passes through the flow passage 53, when the valve is in the constricting position shown in FIG. 2, has a cross-sectional size which is only a fraction of the cross-sectional size of the valve chamber on the outlet side of poppet 44 (that is to say, a fraction of the cross-sectional size of annulus 57). Such fraction is a very small one, the cross-sectional size of the annulus 57 being many times greater than the cross-sectional size of the gap between wall 47 and neck 22 when poppet 44 is in the illustrated constricting or low-flow position. Despite this great difference in sizes, the degree of velocity reduction effected by shoulder 100 is so great that annulus 57 substantially fills with liquid even when the poppet 44 is in the illustrated lowflow position.

The shoulder or ledge 100 constitutes a relatively small deflecting surface which is disposed in the direct path of the stream (sheet) of liquid which passes at high velocity between wall 47 and neck 22 (that is to say, through flow passage 53) when the poppet 44 is in the illustrated low-flow position. It is a feature of the invention that when the poppet 44 is in its high-flow position (seated on shoulder 54), the surface 100 is in the path of only a small part of the large stream of liquid passing through the valve. Therefore, surface 100 creates only a small amount of turbulence and restriction when the poppet is in its high-flow position.

SUMMARY OF OPERATION When the gasoline or other liquid is initially passed into inlet chamber 56 through pipe 13, poppet 44 is in the lower or high-flow position (opposite to the one shown in FIG. 2). However, the fluid pressure in chamber 56 creates a rapid flow of liquid through passage 67 and power nozzle 66 to the inlet port 68 of receiver 69, the pressure at receiver 69 then building up quickly so that liquid flows upwardly through passages 76 and past check valve balls 78 into power chamber 58. The pressure in chamber 58 is sufficient to overcome the inlet pressure at 56, due to the above-stated area differential, so that poppet 44 is shifted upwardly to the constricting or low-flow position determined by stop nut 51. Such constricting or low-flow position is adjusted in such manner, as above described, that the initial flow past the flow-constricting poppet 44 will not be sufficiently great to cause splashing as the liquid enters the tank.

The downflowing liquid is subject to the above-stated actions of the deflector means 100 (as stated in detail under the previous heading) and 36, and therefore emanates horizontally out the bottom of the loading valve in a very smooth, nonsplashing manner. Furthermore, until the high-flow condition is initiated. such flow out the bottom of valve 14 is relatively low in velocity.

The high-velocity jet from power nozzle 66 causes an aspiration of air through control port 88 and connecting passages, as described in detail heretofore. After the level of the liquid in tank 11 reaches the control port. liquid is drawn into the control chamber 62 to fill the same. The velocity of the jet from power nozzle 66 is thus drastically reduced, which reduces the pressure at receiver 69 and therefore in the power chamber 58, so that the poppet 44 shifts downwardly.

When the poppet 44 is in the lower position (seated on shoulder 54), liquid from .pipe 13 may flow very rapidly through the wide-open annulus 53 and out the bottom of the valve into the tank. Such rapidly flowing liquid causes filling of tank 11 in a short period of time, but without substantial generation of vapors or static electricity since the lower portion of the valve is then fully submerged to a depth sufficient to insure against splashing.

For clarity, the appended claims refer to the loading valve in its normal upright position, but this is not to be regarded as a limitation.

The use of such expressions as flow port" and inlet chamher" in the appended claims does not denote that the diameter of the port is necessarily smaller than that of the inlet chamber. For example, the interior cylindrical wall of pipe 13, FIG. 1, could extend down toand have the same diameter as-flow port 23, without substantially affecting the operation of the valve.

I claim:

1. A static-reducing and vapor-reducing fill means for tank trucks and the like, which comprises:

casing means having a discharge opening in the bottom thereof,

movable constrictor means mounted in said casing means and movable between a first position at which flow of liquid through said casing means is constricted and a second position at which flow of liquid through said cas ing means is relatively unconstricted,

means responsive to the level of the liquid in a tank to shift said movable means between said first and second positions,

first deflector means positioned to receive high-velocity liquid flowing through said casing means when said movable means is in said first position and to substantially deflect said high-velocity liquid while the same is still in said casing means and in such manner that the flow velocity thereof is greatly reduced, and

second deflector means to direct said reduced velocity liquid radially outwardly from the bottom of said casing means in a relatively splash-free manner.

2. The invention as claimed in claim I, in which said casing means is substantially circular in cross-sectional shape, in which said movable constrictor means is a movable valve ele ment adapted when in said first position to direct said liquid outwardly against the interior surface of said casing means and thence downwardly along such interior surface in a thin highvelocity sheet, in which said first deflector means comprises an inwardly extending shoulder which receives such highvelocity sheet and greatly reduces the velocity thereof, and in which said second deflector means is radially outwardly extending element disposed below the bottom of said casing means to receive liquid therefrom and direct the same outwardly.

3. The invention as claimed in claim 2, in which said casing means has a circular flow port in the upper portion thereof, in which said movable constrictor means is a poppet which is movably mounted coaxially of said port and therebeneath, said poppet when in said first position being adjacent but spaced from said port, and when in said second position being spaced a much farther distance from said port.

4. The invention as claimed in claim 3, in which said poppet has an upper wall the outer diameter of which is substantially larger than that of said port, and in which the portion of said casing means radially adjacent said poppet is downwardly divergent at regions above said shoulder, whereby to cause liquid to hug said divergent regions and impinge effectively against said shoulder.

S. The invention as claimed in claim 1, in which said first deflector means is small in size and is disposed in the upper portion of said casing means.

6. The invention as claimed in claim 1, in which said means responsive to the level of the liquid in the tank includes a sensing port, and further includes means automatically responsive to the presence or absence of liquid at said sensing port to shift said movable constrictor means between said first and second positions.

7. A loading valve for introducing liquids into tanks in a substantially splash-free manner whereby to minimize generation of vapors and static electricity, which comprises:

a valve body one end of which is adapted to be connected to the end of a fill pipe to receive liquid therefrom,

the other end of said valve body incorporating outlet means to discharge liquid from said valve body into a tank, said valve body defining a valve chamber,

a valve element movably mounted in said valve chamber,

means to move said valve element between a first position at which flow of liquid through said valve chamber is constricted and a second position at which flow of liquid through said valve chamber is relatively unconstricted,

said valve body and said valve element being so related to each other that, when said valve element is in said first position, said liquid flows past said valve element in at least one high-velocity stream the cross-sectional size of which is only a small fraction of thecross-sectional size of said valve chamber on the outlet side of said valve element, and

deflector means provided in said valve chamber on said outlet side of said valve element to deflect said stream sufficiently to cause the same to have a greatly reduced velocity,

the magnitude of said reduction in velocity being sufficiently great that said valve chamber on the outlet side of said valve element substantially fills with said liquid,

whereby said liquid discharges through said outlet means in substantially splash-free manner.

8. The invention as claimed in claim 7, in which said deflector means is so located that it provides relatively little impedance to the flow of said liquid through said valve chamber when said valve element is in said second position.

9. The invention as claimed in claim 7, in which said deflector means is disposed relatively adjacent said valve element and remote from said outlet means.

10. The invention as claimed in claim 7, in which said means to move said valve element is automatically responsive to the level of said liquid in said tank, and moves said valve element to said first position when said level is low, and to said second position when said level is high.

ll. The invention as claimed in claim 7, in which said deflector means is a small-size surface disposed in the direct path of said high-velocity stream when said valve element is in said first position. but disposed in only a small portion of the stream which flows past said valve element when the same is in said second position.

12. The invention as claimed in claim 7, in which a second deflector means is provided adjacent said outlet means to cause said liquid to turn a corner when discharging through said outlet means into said tank.

13. A loading valve for connection to the bottom end of a fill pipe for a tank truck, which comprises:

an elongated valve casing having an inlet port at the upper end thereof,

said valve casing defining, at regions immediately below said inlet port, a valve chamber the diameter of which is substantially greater than the diameter ofsaid port,

a poppet movably mounted in said valve chamber generally coaxially of said port, said poppet having a diameter at least substantially as large as that of said port,

means to move said poppet between a low-flow position relatively adjacent said port and a high-flow position relatively remote therefrom,

ledge means provided on the interior wall of said casing beneath said port and in the path of the liquid which flows through said port when said poppet is in said low-flow position, and

outlet means provided at the bottom end of said casing to discharge liquid therefrom into a tank being loaded,

14. The invention as claimed in claim 13, in which said poppet has an outer diameter substantially larger than the diameter of said inlet port, and in which said poppet is shaped to direct liquid from said port against the interior wall of said casing when said poppet is in said low-flow position.

15. The invention as claimed in claim 13, in which said regions of said valve casing immediately beneath said inlet port diverge downwardly throughout at least a portion of the distance between said port and said ledge means, and in such manner that liquid passing through said port hugs the interior wall of said casing when passing from said port to said ledge means.

16. The invention as claimed in claim 13, in which the upper surface of said poppet is generally conical and diverges downwardly, in which the outer diameter of said upper surface is substantially larger than the diameter of said port, and in which said regions of said valve casing immediately beneath said port diverge downwardly throughout at least a portion of the distance between said port and said ledge means.

17. The invention as claimed in claim 16, in which said downwardly diverging portions of said valve casing are generally rounded, and in which said ledge means is disposed in the upper portion of said valve casing and remote from said outlet means.

18. The invention as claimed in claim 13, in which said ledge means is a narrow ledge disposed in the upper portion of said valve casing and remote from said outlet means.

. 19. The invention as claimed in claim 18, in which the width of said ledge is about one-eighth inch.

20. The invention as claimed in claim 13, in which said ledge means is a narrow ledge disposed in the upper portion of said valve casing and remote from said outlet means, and in which the gap which is present between said poppet and said valve casing when said poppet is in said low-flow position is substantially smaller than the width of said ledge.

21. The invention as claimed in claim 13, in which said casing is formed ofa plurality of connected sections, and in which said ledge means is on an upper edge of one of said sections, said upper edge having an internal diameter substantially smaller than the internal diameter of the lower edge of the section above said one section.

22. The invention as claimed in claim 13, in which said ledge means is a narrow ledge disposed in the upper portion of said valve casing and remote from said outlet means, and in which said outlet means is a circular port generally coaxial with said inlet port and defined by a wall which is somewhat necked down relative to said valve chamber, the degree of necking down being sufficiently small to prevent substantial restriction of flow through said valve casing when said poppet is in said high-flow position.

23. The invention as claimed in claim 13, in which said outlet means is an annular outlet passage generally coaxial with said inlet port, and in which a second deflector is provided below and spaced from said outlet passage to cause liquid discharging vertically downwardly from said valve chamber to turn a corner and flow radially outwardly and horizontally from the loading valve in a substantially splash-free manner, said second deflector having an outer surface at least a portion of which is downwardly divergent.

24. The invention as claimed in claim 13, in which said ledge means is a narrow ledge disposed in the upper portion of said valve casing and remote from said outlet means, in which said outlet means is a circular outlet port generally coaxial with said inlet port and defined by a wall which is somewhat necked down relative to said valve chamber, the degree of necking down being sufficiently small to prevent substantial restriction of flow through said valve casing when said poppet is in said high-flow position, and in which a second deflector is provided below and spaced from said outlet port to cause

Claims

1. A static-reducing and vapor-reducing fill means for tank trucks and the like, which comprises: casing means having a discharge opening in the bottom thereof, movable constrictor means mounted in said casing means and movable between a first position at which flow of liquid through said casing means is constricted and a second position at which flow of liquid through said casing means is relatively unconstricted, means responsive to the level of the liquid in a tank to shift said movable means between said first and second positions, first deflector means positioned to receive high-velocity liquid flowing through said casing means when said Movable means is in said first position and to substantially deflect said highvelocity liquid while the same is still in said casing means and in such manner that the flow velocity thereof is greatly reduced, and second deflector means to direct said reduced velocity liquid radially outwardly from the bottom of said casing means in a relatively splash-free manner.

2. The invention as claimed in claim 1, in which said casing means is substantially circular in cross-sectional shape, in which said movable constrictor means is a movable valve element adapted when in said first position to direct said liquid outwardly against the interior surface of said casing means and thence downwardly along such interior surface in a thin high-velocity sheet, in which said first deflector means comprises an inwardly extending shoulder which receives such high-velocity sheet and greatly reduces the velocity thereof, and in which said second deflector means is radially outwardly extending element disposed below the bottom of said casing means to receive liquid therefrom and direct the same outwardly.

5. The invention as claimed in claim 1, in which said first deflector means is small in size and is disposed in the upper portion of said casing means.

7. A loading valve for introducing liquids into tanks in a substantially splash-free manner whereby to minimize generation of vapors and static electricity, which comprises: a valve body one end of which is adapted to be connected to the end of a fill pipe to receive liquid therefrom, the other end of said valve body incorporating outlet means to discharge liquid from said valve body into a tank, said valve body defining a valve chamber, a valve element movably mounted in said valve chamber, means to move said valve element between a first position at which flow of liquid through said valve chamber is constricted and a second position at which flow of liquid through said valve chamber is relatively unconstricted, said valve body and said valve element being so related to each other that, when said valve element is in said first position, said liquid flows past said valve element in at least one high-velocity stream the cross-sectional size of which is only a small fraction of the cross-sectional size of said valve chamber on the outlet side of said valve element, and deflector means provided in said valve chamber on said outlet side of said valve element to deflect said stream sufficiently to cause the same to have a greatly reduced velocity, the magnitude of said reduction in velocity being sufficiently great that said valve chamber on the outlet side of said valve element substantially fills with said liquid, whereby said liquid discharges through said outlet means in substantially splash-free manner.

11. The invention as claimed in claim 7, in which said deflector means is a small-size surface disposed in the direct path of said high-velocity stream when said valve element is in said first position, but disposed in only a small portion of the stream which flows past said valve element when the same is in said second position.

13. A loading valve for connection to the bottom end of a fill pipe for a tank truck, which comprises: an elongated valve casing having an inlet port at the upper end thereof, said valve casing defining, at regions immediately below said inlet port, a valve chamber the diameter of which is substantially greater than the diameter of said port, a poppet movably mounted in said valve chamber generally coaxially of said port, said poppet having a diameter at least substantially as large as that of said port, means to move said poppet between a low-flow position relatively adjacent said port and a high-flow position relatively remote therefrom, ledge means provided on the interior wall of said casing beneath said port and in the path of the liquid which flows through said port when said poppet is in said low-flow position, and outlet means provided at the bottom end of said casing to discharge liquid therefrom into a tank being loaded.

19. The invention as claimed in claim 18, in which the width of said ledge is about one-eighth inch.

21. The invention as claimed in claim 13, in which said casing is formed of a plurality of connected sections, and in which said ledge means is on an upper edge of one of said sections, said upper edge having an internal diameter substantially smaller than the internal diameter of the lower edge of the section above said one section.

24. The invention as claimed in claim 13, in which said ledge means is a narrow ledge disposed in the upper portion of said valve casing and remote from said outlet means, in which said outlet means is a circular outlet port generally coaxial with said inlet port and defined by a wall which is somewhat necked down relative to said valve chamber, the degree of necking down being sufficiently small to prevent substantial restriction of flow through said valve casing when said poppet is in said high-flow position, and in which a second deflector is provided below and spaced from said outlet port to cause liquid discharging vertically downwardly from said valve chamber to turn a corner and flow radially outwardly and horizontally from the loading valve in a substantially splash-free manner.

25. The invention as claimed in claim 13, in which said means to move said poppet between low-flow and high-flow positions includes sensing and actuating means automatically responsive to the level of liquid in the tank being loaded.