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Publication numberUS3106169 A
Publication typeGrant
Publication dateOct 8, 1963
Filing dateNov 13, 1961
Priority dateNov 13, 1961
Publication numberUS 3106169 A, US 3106169A, US-A-3106169, US3106169 A, US3106169A
InventorsLuchsinger John W, Prosser Rae A
Original AssigneeUnion Carbide Corp
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Intensifier high pressure valve and block assembly
US 3106169 A
Abstract  available in
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Claims  available in
Description  (OCR text may contain errors)

1963 R. A PROSSER ETAL 3,

INTENSIFIER HIGH PRESSURE VALVE AND BLOCK ASSEMBLY Filed NOV. 15, 1961 INVENTORS RAE A. PROSSER JOHN W. LUCHSINGER By yma. W

ATTOR V United States Patent Ofltice 3,106,169 Patented Oct. 8, 1963 3,106,169 INTENSIFIER HIGH PRESSURE VALVE AND BLOCK ASSEMBLY Rae A. Presser, outh Charleston, and John W. Lushsinger, Charleston, W. Va., assignors to Union Carbide Corporation, a corporation of New York Filed Nov. 13, 1961, Ser. No. 151,697 2 Claims. (Cl. 103--228) The present invention relates to an improved fluid system valve and more particularly to a high pressure valve ideally suited for use in intensifier systems wherein fluids are raised from low suction or intake pressures in the order of about 2000 p.s.i.g. to relatively high discharge pressures in the order of 35,000 p.s.i.g. and above, by means of reciprocating piston and plunger type pumps and intensifiers. Apparatus according to the present invention permits size reduction of parts subjected to discharge pressures over known devices for such use and provides for mitigation of cyclic fatigue loading normally encountered in known valves adapted for high pressure applications.

Valves suitable for high pressure cyclic pumping operations at discharge pressures in the order of 35,000 p.s.i.g. and upward are known in the valve art to be prone to material fatigue failures due to the continual application and relaxation of pressure loads especially against sharp edges and corners in the valve interior passages where stress concentrations occur. Present efforts directed towards mitigation of these fatigue failures in high pressure valves are addressed generally to reducing the severity of stress concentrations, where such are known to occur, by rounding off sharp edges and filleting sharp corners at valve passage intersections and transition points. It has been found, however, that while rounding oif and filleting techniques reduce stress concentrations to some extent, these techniques have not effected reduction of stresses to the order of stress levels obtaining in straight sections of the valve passages. V

In conventional low pressure compressor equipment operating at below about 35,000 p.s.i.g., stress concentration problems and related fatigue failures are mitigated by the use of components having suflicient structural strength to withstand maximum stresses encountered. In high pressure equipment, however, components of suiiicient structural strength to Withstand expected fatigue stresses at high stress concentration points would have to be made unusually massive and necessarily cumbersome. Practical considerations frequently militate against or even prevent such a solution to this problem.

The present invention provides a valve uniquely suitable for high pressure fluid pumping which, in operation, produces no excessive stress concentrations from cyclic loading. The valve of this invention operates successfully and continuously without failure or repair for periods longer than those experienced with known high pressure valves at discharge pressures above 35,000 p.s.i.g.

Apparatus according to the present invention comprehends an annular suction, center discharge type high pressure valve assembly in a valve block designed so that on a pump piston or plunger suction stroke fluid flows into an annular space and through a suflicient number of holes connecting to a concentric groove covered by a suction valve disc and then into a pump cylinder; and on the discharge stroke, the fluid is forced through a hole in the center of the suction valve disc through a center discharge passage located through the center of the valve block, through a poppet valve and out into the discharge line. With this design, a minimum number of stress raisers are present and such common stress raisers as 2 are found in intersecting bores in a reciprocating cylinder are eliminated. In addition, the main valve block body is protected from discharge pressure and is subjected only to suction pressure of the pumped fluid. Fatigue cracking of these valves and valve block parts which has been a problem is thereby minimized.

With the foregoing and other features in view, which shall more fully hereinafter appear, the present invention comp-rises novel constructions, combinations and arrangements of components as will now be described in detail and as recited in theappended claims and illustrated in the accompanying drawing, which is a sectional view through a valve according to our invention, showing internal passages and components thereof.

Referring to the drawing, a valve body portion 17, is shown afiixed to a pump 11, which includes a reciprocating piston 13. A dischargepassage 19 extends through a group of core block members 49, 51, 53 and 55 disposed interiorly of body portion 17. Precise details according to which the discharge passage and its radially enlarged sections and the other passages discussed here are formed and disposed in the core block members, as well as more complete descriptions of the several core block members themselves, are set forth hereinafter. Discharge passage 19 connects a port 15 of pump 11 to a fluid outlet 21. A first longitudinally extending radially enlarged section '23 in discharge passage 19 is located adjacent the port 15 of pump 11 and connects thereto through a hole in a facia block 55. A second longitudinally extending radially enlarged section 25 in discharge passage 19 is located interior of the valve body portion 17 in a thrust block 49. An annular recess 27', formed by recessed peripheral edges on the thrust block 49 and a first follower block 51, transversely surrounds bore 19 and is located in a longitudinally displaced position in the valve body portion 17 with respect to first radially enlarged section 23 of the discharge passage 19. A multiplicity of suction passages 29 connects annular recess 27 with first radially enlarged section 23 of discharge passage 19 and an intake passage 31 connects annular recess 27 with a fluid inlet 33 at a point on the body portion exterior. An inlet valve member 35, in the form of an annular disc having a centrally located opening 37 therethrough in registration with discharge passage 19, is arranged in first radially enlarged section 23 of the discharge passage 19 and moves reciprocally therein in longitudinal direction from a first position to a second position during each discharge stroke of piston 13 and from said second position to said first position during each suction stroke of piston 13, said member being actuated by the pumped fluid. A facia surface 39 on inlet valve member 35 covers the ends of and closes the second passages 29 when member 35 is in the suction position during a discharge stroke of the piston 13 and uncovers the ends of and opens the suction passages 29 when member 35 is in the first position during a suction stroke of the piston 13. An outlet valve member 41, which may be of the poppet valve type, is arranged in second radially enlarged section 25 of discharge pas-sage 19 and moves reciprocally therein in longitudinal direction from a first position to a second position during each discharge stroke of piston 13 and from said second position to said first position during each suction stroke of piston 13 actuated by the pumped fluid. In the embodiment illustrated, outlet valve member 41 is in the form of a cylinder having a chamfered surface 43 at one end. A longitudinal center passage 45 extends part way through the member 41 and connects to a multiplicity of pas-sages 47 extending between passage 45 and the chamfered surface 43. When outlet valve member 41 is in its first position during a suction stroke of piston 13,

skilled in the mechanical arts.

3 bore 19 is closed by one end of the member covering the bore at its point of intersection with second enlarged section 25. When outlet valve member 41 is in its second position during a discharge stroke of piston 13, bore 19 is opened with fiow continuity obtaining through the passages 47 and passage 45 in member 41.

In the embodiment shown in the drawing, discharge passage 19, first radially enlarged section 23 of discharge passage 19, second radially enlarged section 25 of discharge passage 19, annular recess 27 and suction passages 29 are defined within valve body portion 17 by an array of core members comprising a thrust block 49, a first follower block 51, a second follower block 53 and a facia block 55, arranged in concentric alignment in a counterbore 57 and a core bore 59 in the valve body portion 17. A bore and counterbore through the center of thrust block 49 define respectively the fluid outlet end of and the second radially enlarged section 25 of discharge passage 19. Milled or otherwise formed recessed peripheral edges on mating faces of thrust block 49 and first follower block 51, together with a portion of wall surface of counterbore 57, define the annular recess 27. Suction passages 29 are rilled or otherwise formed in first follower block 51. First radially enlarged section 23 of discharge passage 19 is defined by a center hole in second follower block 53. Facia block 55 provides an annular bearing surface for inlet valve member 35 in its first or suction position.

All surfaces serving valving functions are flat lapped surfaces, and are prestressed in assembly. .0 rings 61 are provided in peripheral grooves on the thrust block and first follower block to effect sealing, and weep holes 63 and 65 are provided for seepage draining. The valve body may be aflixed to the pump and component prestressing effected by means of stud bolts 67. Connector means such as 69 and 71 may be provided to connect fluid inlet 33 and fluid outlet 21 to inlet and discharge conduits.

In operation, the apparatus of the present invention functions as follows:

Under an assumed inlet line pressure of about 2000 p.s.i.g. and an assumed discharge line pressure of about.

50,000 p.s.i.g., fluid flows through inlet 33, intake passage 31, annular recess 27, suction passages 29, first radially enlarged section 23 of discharge passage 19and pump port into a pumping chamber of reciprocating pump 11, during each suction stroke of the piston 13. During a suction stroke, inlet valve member 35 is held in its first position under inlet pressure, permitting fluid fiow through the first radially enlarged section 23 of discharge passage 39 from suction passages 2? and outlet valve member 41 is held in its first position under a pressure differential obtaining between the inlet and discharge line pressures, closing discharge passage l? at its intersection with the interface defined between thrust block 49 and first follower block 51. Upon completion of a suction stroke and the start of a discharge stroke, inlet valve member 35 is moved to its second position by a pressure diflerential obtaining between the initial discharge pressure and the inlet pressure, closing suction passages 29, and outlet valve member 41 is moved to its second position, opening discharge passage 19. During the discharge stroke, piston 13 forces fluid from the pumping chamber, through pump port 15, first radially enlarged section 23, discharge passage 19, second radially enlarged section 25 and fluid outlet 21 into the discharge line. The above operation is cyclically repeated during continuous operation.

The foregoing disclosure and the drawing will reveal to persons familiar with the art that only three components of the illustrated embodiment of our invention are subjected to cyclic loading, viz, first follower block 51, second follower block 53 and facia block 55. None of these components has a flow surface discontinuity which could become a stress concentration point.

In the light of the foregoing disclosure, it is conceivable that modifications to our invention will occur to persons Accordingly, it is to be '4 understood that while in the foregoing description, certain specific details have been set forth, variations may be made in these without departing from the spirit of the present invention. The foregoing description is intended to clarify understanding of this invention and no unnecessary limitations should be understood therefrom.

What is claimed is:

1. A fluid intensifier valve adapted for connection to a discharge port of a pump which contains a reciprocating piston, comprising, in combination, a body portion having a discharge passage connecting to said port and extending longitudinally through a multiplicity of core block members disposed interiorly of said body portion to a fluid outlet, a first longitudinally extending radially enlarged section in said discharge passage adjacent said discharge port and thereto connecting, a second longitudinally extending radially enlarged section in said discharge passage, an annular recess interior of the body portion transversely surrounding said discharge passage, longitudinally displaced from said first radially enlarged section of said discharge passage and defined by said core block members and an internal wall of said body portion, a multiplicity of suction passages connecting said annular recess and said first radially enlargedsection and an intake passage connecting said annular recess to a fluid inlet at the body portion exterior; an inlet valve member in said first radially enlarged section adapted to move reci rocally in longitudinal direction from a first position to a second position during a discharge stroke of the reciprocating piston and from said second position to said first position during a suction stroke of the reciprocating piston and having an opening extending therethrough in registration with said discharge passage and a surface arranged to close said suction passages when in said second position and to open said suction passages when in said first position; and a discharge valve member in said second radially enlarged section adapted to move reciprocally in longitudinal direction from a first position to a second position during a discharge stroke of the reciprocating piston and from said second position to said first position during a suction stroke of the reciprocating piston, said discharge valve member having means adapted to close the discharge passage when in said first position and to open said discharge passage when in said second position.

2. A fluid intensifier valve adapted for connection to an open ended cylinder which contains a reciprocating piston, comprising, in combination, a body portion having a face adapted for connection to said open ended cylinder, a bore connecting to said open ended cylinder and extending longitudinally through a multiplicity of core block members disposed interiorly of said body portion to a fluid outlet, a first counterbore in one of said core block members adjacent the face, a second counterbore in another of said core block members interior of the body portion, an annular recess arranged coaxially With respect to said bore and defined by said bore block members and an internal wall of said body portion, a multiplicity of radially and longitudinally extending passages connecting said annular recess and said first counterbore, and a radially extending passage connecting said annular recess to a fluid inlet at the body portion exterior; an annular valve disc in said first counterbore adapted to move reciprocally in longitudinal direction from a first position to a second position during a discharge stroke of the reciprocating piston and from the second position to the first position during a suction stroke of the recprocating piston and having an opening extending therethrough in registration with the bore and an annular surface arranged to close the multiplicity of radially and longitudinally extending passages connecting the annular recess and said first counterbore when in said second position and to open said passages when in said first position; and a poppet valve member in said second counterbore adapted to move reciprocally in longitudinal direction from a first position to a second position during a discharge stroke of the reciprocating pistoniand from said second position to said first position during a suction stroke of the recprocating piston and having a surface arranged to close the bore when in said first position and to open the bore when in said second position.

References Cited in the file of this patent UNITED STATES PATENTS 1,476,794 Berry Dec. 11, 1923 & Berry Sept. 4, 1928 Herzmark Aug. 14, 1945 Krugler Apr. 4, 1950 Paluch et a1 Jan. 26, 1954 Neugebauer Mar. 1, 1955 Augustin Oct. 13, 1959

Patent Citations
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US1682736 *Mar 5, 1927Sep 4, 1928Carl W FlossCompressor piston
US2382716 *Feb 10, 1943Aug 14, 1945Nicolas HerzmarkCompressor
US2502525 *Jul 5, 1944Apr 4, 1950Phillips Petroleum CoControlled cycle relief valve
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US2703102 *Dec 28, 1951Mar 1, 1955Neugebauer Franz JSpring loaded valve for high-speed air and gas compressors
US2908287 *Sep 4, 1957Oct 13, 1959Bendix Westinghouse AutomotiveCompressor valve structure
Referenced by
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US3185106 *Aug 28, 1963May 25, 1965Ingersoll Rand CoSpark pumps
US3659967 *May 27, 1970May 2, 1972Kobe IncHydraulic intensifier
US3702624 *Sep 12, 1969Nov 14, 1972Pumpenfabrik UrachPiston pump
US3709638 *Oct 22, 1970Jan 9, 1973Japan Steel Works LtdPlunger pump cylinder for use in treating highly corrosive fluid
US3777779 *Jul 28, 1971Dec 11, 1973B SchwallerCompressor valve assembly
US4026322 *Feb 11, 1976May 31, 1977Flow Industries, Inc.Reciprocating pump check valve assembly
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US5092744 *Mar 14, 1990Mar 3, 1992Possis CorporationIntensifier
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US5636975 *Apr 4, 1994Jun 10, 1997Reynolds Metals CompanyInlet and discharge valve arrangement for a high pressure pump
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Classifications
U.S. Classification417/567, 417/569, 137/512.3, 137/512
International ClassificationF16K27/00
Cooperative ClassificationF16K27/00
European ClassificationF16K27/00