US2256471A - Valve mechanism for motors of pumps - Google Patents

Description

Sept. 23, 1941.

F. D. BUTLER VALVE MECHANISM FOR MOTORS OF PUMPS Filed Ma 27, 1940 SBheets-Sheet l r \\VA\\ UNVENT@IR M.QMM

Sept. 23, 1941. 4 F. D. BUTLER 56,471

VALVE MECHANISM FOR MOTORS OF PUMPS Filed May 27, 1940 3 Sheets-Shee t 2 A I II 3?) I 3? 54,;

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VALVE MECHANISM FOR MOTORS OF PUMPS File d May 27, 1940 5 Sheets-Sheet 5 g; i -n2, Q2

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f- IHNJVENTER Y Patented Sept. 23, 1941 UNETE a a n Frank David Butler, United States Navy Application May 27, 1940, Serial No. 337,450

4 Claims.

(Granted under the act of March 3, 1883, as amended April 30, 1928; 370 0. G. 757) Whilemy present invention relates in general to improvements in valve mechanisms, of the type mentioned, it applies more specifically to valve assemblies wherein the main valve thereof is spool shaped and is equipped with enlarged cylindrical differential valve heads, is actuated in a reciprocating manner by expansive fluid, and, is controlled by an auxiliary valve which is operated mechanically by and in timing with the moving elements of such motor. assembly I provide, a plurality of conically shaped valve surfaces one located adjacent the outer end of each of said valve heads, a plurality of skirt projections one located adjacent the base of each of said comically shaped valve surfaces, at 5 valve chest having a plurality of different sized bore diameters (corresponding to the diameters of said valve heads and said skirt projections) extending parallel and closely adjacent to the main cylinder bore of such motor one located ad- 29 jacent each end of the latter and having access communication therewith, a plurality of conically shaped valve seats corresponding to and upon which said conically valve surfaces seat (when said main valve rests at its extreme ends of 25 travel), a reduced diameter projecting plunger located adjacent the larger of said differential valve heads, an expansive fluid access passage extending from the inside of the latter to the extreme outer end of said plunger, means for ena closing and thus forming a, closed chamber about the latter, and, an auxiliary valve means for opening and closing an exhaust port leading from such closed chamber to the atmosphere for purposes of controlling the reciprocating movements of said main valve and thereby the movements of the main piston of such motor.

With reference to the drawings; Figs. 1 to 5 inclusive illustrate longitudinal sections of the assemblies of the main and auxiliary valves of my invention as applied to a modern motor of reciprocating double acting pump (the auxiliary valve not being shown in Fig. 5), and, Fig. 6 is a transverse section through the assembly as would appear on the dotted line 6-6 of Fig. 5 and illus- 45 trates the installation of the main piston cushioning and the motor cylinder and valve chest drain Valves in location relation to the valve chest and motor cylinder bores.

With reference to the numerals of the draw- In such a valve 10 adapted to be automatically reciprocated within the valve chest 3 and to control the supply of expansive fluid from its source of supply, at flanged connection 4 of such chest, alternately to each sideo'f the piston 5, which latter is reciprocatably mounted within the main bore 6 of the pump motor. This main valve I being further adapted to simultaneously alternately (with the expansive fluid supply cycle just mentioned) release the expended expansive fluid from the opposite end of bore 6 to the exhaust exit connection 7 at the base of said valve chest 3. main valve l to have an elongated tubular shaped intermediate portion with enlarged valve heads 8 one located at each end thereof and which heads have diflerential external diameters which form (when expansive fluid is supplied to chest 3 between such heads) a means of actuating said main valve in one (preferably upward) direction of its travel. A reduced diameter cylindrical plunger 9 extending an appreciable distance beyond the outer endoi the larger valve head is provided and is. adapted to be a slidable fit within a suitable chamber lit (located in the upper cover ll of the valve chest and in tandem with the bore of the latter) for purposes of establish- 7 ing a second differential means (when expansive fluid is allowed to accumulate in said chamber ill), of actuating said main valve in the opposite direction of travel to that previously mentioned. An expansive fluid supply passage I2 is provided and extends from the inward or supply chamber l3 side of the larger valve head through the latter and plunger 9 and terminates in a restricted orifice plug M secured in the extreme outward end of the latter and located adjacent chamber Ill. A series of snap type piston rings l5 are provided in the outer circumferences of each of the valve heads 8 of main valve l for sealing'purposes. A

4Ov plurality of reduced diameter skirt projections I6,

one located adjacent each of said valve heads, are provided for main valve cushioning purposes. These skirt projections it are each adapted to be a. slidable fit within its respective upper or lower cylindrical chamber H and therewith to form dash-pot chambers l3 (between conical valve surfaces IS on valve l and conical valve seats 20) when they enter their respective chambers H. The lower cylindrical chamber H and valve seat 20 being located in the lower ported wearing liner 2, and the upper cylindrical chamber I! and valve seat 251 being located in the valve chest cover H.

A spider type bridging Zl is provided for integrally connecting plunger 9 to the upper valve head of the main valve l, and a series of circum- Such ferentially extending grooves 22 are spaced along the outer surface of said plunger 9 for purposes of collecting moisture and forming a seal baffle means.

Expansive fluid access between the ends of the bore of the main cylinder 6 and the ends of the bore of the valve chest 3 is provided in the form of passages 23 and via the main piston cushioning Valve 24 and combined cushioning and cylinder drain porting 25. Drainage access being provided between the ends of the bore of the main cylinder 6 and. the exhaust side of the valve chest 3 through the porting 25, thence via the drain valve 26 and drain porting 21 into the chest bore.

The flanged cover II is secured to and closes the upper end of the valve chest 3 and is provided with, a projecting portion 29 that bears against the upper end of the upper wearing liner 2, the upper seat 29 adjacent the latter, and the wearing liner 39 for the plunger 9.

When the main valve I is at its extreme downward travel, as illustrated in Figs. 1 and 3, the live expansive fluid (as diagrammatically illustrated by arrows) flows from chest supply space I3 to beneath the main piston 5, and the expended expansive fluid above said piston (as diagrammatically illustrated by arrows) simultaneously escapes to the exhaust connection 1. While when said main valve I is at the extreme upper end of its travel, as illustrated in Figs, 2 and 4, the live expansive fluid (as diagrammatically illustrated by arrows) flows from chest supply space I3 to above the main piston 5, and the expended expansive fluid beneath said piston (as diagrammatically illustrated by arrows) simultaneously escapes to the exhaust connection I at the base of chest 3.

With reference to Fig. 6 and assuming that (as illustrated) the main valve I is at its mid travel position in the chest 3 and that live expansive fluid is being supplied to chest space I3. Bearing in mind that the upper valve head 8 is larger in diameter than the lower valve head 8 we would assume that the effective pressure area difference therebetween would immediately cause the main valve I to travel upward in said chest. However should we allow live expansive fluid (supplied through passage I2 and orifice plug I4) to accumulate in chamber Ill, then as the upper projected area of plunger 9 is greater than the eiiective area difference between the two valve heads 8, the main valve I would be immediately forced downward in said chest. Therefor by continually supplying live expansive fluid to chamher I 3 through a restricted orifice (as in plug I4) and providing a cylindrical type auxiliary valve 32 (as in Figs. 1 and 2) or a poppet type auxiliary valve (as in Figs. 3 and 4) operated by the moving elements of said motor and adapted to close (as Figs. 1 and 3) or open (as in Figs. 2 and 4) a relatively large exhaust passage 33 leading to another exhaust passage 31 and thence to the exhaust side of chest 3, complete control of the longitudinal movement of the main valve I can be attained and consequently control over the movements of the main piston 5.

In Figs. 1 and 2 the auxiliary valve 32, of the assembly illustrated therein, is operated by the adjustable tappet nuts 35 which latter are actuated by the valve rod 3| which latter is actuated by the usual valve rod operating mechanism (not illustrated) operated by a crosshead attached to the main piston rod of the motor. This valve 32 has a reduced diameter portion 38 which registers with and connects exhaust passages 33 and 31 when valve 32 is in position shown in Fig. 2 and covers passage 33 when in position shown in Fig. 1. A wearing liner 34 is provided in cover II for valve 32.

In Figs. 3 and 4 the auxiliary valve 32, of the assembly illustrated therein, is poppet valve or mushroom shaped, is adapted to be opened by the piston 5 striking its lower end (as illustrated in Fig. 4) as such piston approaches the upper end of its travel, is closed by live expansive fluid entering the port 4| (in the boss 49) as the piston 5 is forced downward and clears said port 4| in approaching position in which piston is illustrated in Fig. 3. As this live expansive fluid enters port 4i it passes therefrom through the tubing connection joining this port with the upper end of the enlarged chamber 39 and exerts itself against the enlarged upper area of valve 32 therein thus forcing the latter downward against its conical valve seat 38. A valve 42 is provided, adjacent the chamber 39, for restrict-.

ing manually the rate of flow of the live expansive fluid into chamber 39. The flow of expansive fluid into and away from chamber 39 is illustrated diagrammatically by arrows in Figs. 3 and 4, respectively.

Starting with the main valve I in the position in which it is illustrated in Fig. 5, then if it were to be forced either downward or upward (in manner previously described) from such position to positions in which it is illustrated in Figs. 1 and 3 or 2 and 4 respectively, then the skirt portions I3, as they entered the chambers I'I, would trap exhaust expansive fluid in dash-pot chambers I8 and would compress this fluid therein, thus forming a cushioning means for valve I as it approaches the ends of its travel either downward or upward as the case might be. After compressing such expansive fluid in such chambers I8; the main valve I would then become seated by the conical valve surfaces I9 coming into contact with the conical valve seats 20 and would form pressure tight seals at such locations.

In the construction of these valve assemblies the following should be kept in mind; The main valve should have such minimum internal diameter as not to restrict the size of the exhaust exit extending therethrough; The projected area of the upper end of plunger 9 should be of ample capacity as not to require maximum pressure of the expansive fluid adjacent thereto for its proper operation; The differential differences in the efiective areas of valve heads 8 should be carefully predetermined taking into consideration the weight of the valve I; There should be considerable difierence in the diameters of the orifice in plug I4 and the exhaust passages 33 and 37; The valve surfaces I 9 should be ground joints with the seats 20; And, the plunger 9 should be of such length as to form a good seal with walls of chamber I9 when the former is in its full downward travel position.

The invention described herein may be manufactured and/or used by or for the Government of the United States of America for governmental purposes without the payment of any royalties (thereon or therefor.

7 Having thus set forth and disclosed the nature of this invention, what I claim and desire to secure by Letters Patent is:

1. In a valve assembly mechanism for the motor of a reciprocating pump having an elongated valve chest bore extending parallel and adjacent to the main cylinder bore of such motor, a pluend of said valve chest bore, a plurality of communication passages, one extending between each of said liners and their respective ends of said main cylinder bore, an expansive fluid supply connection having communication with the source of such supply and the intermediate length of said valve chest bore, an exhaust exit connection in communication with the lower end of said valve chest bore, and an elongated tubular main valve member having enlarged valve heads of different outside diameters slidably mounted within said valve liners and covering the ports within the latter; the combination therewith of, a flanged cover closing the upper end of said valve chest bore and having a reduced diameter cylindrical chamber therein in tandem with the bore of the upper of said valve liners and having the upper end thereof closed, a reduced diameter elongated plunger forming a part of said main valve member and extending upward from the larger of the valve heads of the latter and being a slidable fit within said reduced diameter cylindrical chamber and forming an opposition differential means, when expansive fluid is applied, to the urging means of moving said main valve longitudinally due to such pressure being applied to said valve heads of different diameters, an access passage extending through a portion of said larger valve head and said plunger and terminating in the upper end of the latter in a restricted orifice plug secured therein, a plurality of reduced cylindrical skirt extensions one located beyond and adjacent to each of said valve heads, a plurality of conical valve surfaces one located intermediate to each of said valve heads and skirt 7 extensions, a plurality of reduced diameter eylindrical bores one located adjacent the outer end of and in tandem with the bore of each of said ported liners and of such size as to slidably receive said reduced skirt extensions of said main valve, a plurality of conical shaped valve seat surfaces one located intermediate each of the last mentioned tandem bores and each being a ground joint surface with their respective conical valve surfaces of said main valve, an exhaust exit access leading from the closed end of said reduced diameter cylindrical chamber, an auxiliary valve means for intermittently opening and closing said exhaust exit in timing with the movement of the main piston of such motor, and combined means located in the vicinit of the ends of said valve chest and main cylinder bores for cushioning the main piston of such motor as it approaches the end of its travel and for draining the bore of said main cylinder.

2. A main valve, for the motor of a reciprocating expansive fluid actuated pump, consisting of an elongated tubular shaped intermediate portion having a plurality of enlarged tubular shaped valve heads of different outside diameters, one located at each end thereof, a reduced diameter elongated plunger portion extending beyond and adjacent to the larger of said valve heads, a restricted access passage extending from the inner side of the larger of said valve heads to the outer end of said plunger, a plurality of reduced diameter conical shaped valve surfaces one located adjacent each outward end of said tubular valve heads, and, a plurality of tubular skirt projections one extending outward adjacent to and from the base of each of said conical valve surfaces.

3. In a valve mechanism for motor of reciprocating pump, a spool shaped reciprocating main valve having a plurality of valved heads of different diameters one located at each end thereof and each having a conical valve surface at its outward end, a plurality of reduced diameter cylindrical skirt projections integral with said main valve and one located adjacent the base of each conical valve surface mentioned, a reduced diameter projecting plunger integral with said main valve and located adjacent the larger valved head end of the latter, a restricted communication passage extending throughthe larger valved head and said plunger from the inward side of the former to the extreme outward end of the latter, a valve chest having a plurality of tandem bores extending parallel to the main bore of said motor and of such size as to slidably receive said valved heads, skirt projections and plunger of said main valve, a plurality of conical valve seat surfaces one located at each end of said valve chest intermediate the tandem bores of such size as to slidably receive said valved heads and skirt projections, a cover closing one end of said valve chest and containing that portion of the tandem bores of such size as to slidably receive said Plunger and forming a closed chamber thereabouts the outer end of the latter, porting communication extending between each end of said main bore and each adjacent end of said valve chest and terminating in the latter at the'bores of such size as to slidably receive said valved heads, and, means in the form of an auxiliary valve operating in timing with the moving elements of said reciprocating pump for intermittently opening and closing an exhaust passage leading from said closed chamber to the atmosphere.

4. An article of manufacture, for motor of reciprocating expansive fluid actuated pump, consisting of a hollow spool shaped main valve having a plurality of valved heads of different diameters one located at each end thereof and each having a reduced diameter conical valve surface at its outward end, a plurality of reduced diameter cylindrical skirt projections integral with said main valve and one located adjacent the base of each conical valve surface mentioned, a reduced diameter projecting plunger integral with said main valve and located adjacent the larger valved head end of the latter, and, a restricted communication passage extending through the larger valved head and said plunger from the in ward side of the former to the extreme outward end of the latter.

FRANK DAVID BUTLER.

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