US3146724A

US3146724A - Pumps with pulsation damper

Info

Publication number: US3146724A
Application number: US154928A
Authority: US
Inventors: David J Cornelsen
Original assignee: Armco Inc
Current assignee: Armco Inc
Priority date: 1961-11-20
Filing date: 1961-11-20
Publication date: 1964-09-01
Anticipated expiration: 1981-09-01

Description

p 1964 D. J. CORNELSEN PUMPS WITH PULSATION DAMPER 2 Sheets-Sheet 1 Filed NOV. 20. 1961 WI 'IIIIA- IN V EN TOR.

DAVID J. CORNELSEN A TTORNE Y INVENTOR ATTORNEY 2 Sheets-Sheet 2 DAVID J. CORNELSEN D. J- CORNELSEN PUMPS WITH PULSATION DAMPER I 0 o I Sept. 1, 1964 Filed Nov. 20. 1961 United States Patent 3,146,724 PUlVfPS WITH PULSATION DAMPER David J. Cornelsen, Gainesville, Tex., assignor to Armco Steel Corporation, Middletown, Ohio, a corporation of Ohio Filed Nov. 20, 1961, Ser. No. 154,928 7 Claims. (Cl. 103-223) This invention relates to fluid pressure pulsation damp? ing means. While not limited thereto, the invention is particularly applicable to multiplex plunger pumps of the type employed, for example, in oil fields for pumping water to produce oil by Water flooding. This application is a continuation-in-part of application Serial Number 789,752, filed January 28, 1959, now abandoned.

One type of pump, typical of those to which the present invention is applicable, is described in US. Patent 2,766,- 701, Giraudeau, and comprises a cylinder block having a plurality of parallel bores arranged side-by-side to provide cylinders for a plurality of plungers, each cylinder being equipped with valved inlet and exhaust ports, all of the inlet ports communicating with a single, elongated intake manifold. The plungers are driven out of place so that the plungers move successively through their intake strokes. Such mode of operation tends to set up objectionable fluid pressure pulsations in the intake manifold of the pump and thereby decrease the volumetric efliciency and the valve life and increase the noise and the vibration of the pump.

One of the objects of the invention is to provide a new and improved damper for damping fluid pressure pulsations.

Another object is to provide a multiplex, reciprocatory pump with improved damper means to thereby increase the volumetric efliciency and the valve life and decrease the vibration and the noise of the pump.

A further object is to provide, in a pump of the type referred to, an extremely simple and relatively inexpensive means for effectively damping fluid pressure pulsations which tend to occur in the intake manifold.

Still another object is to devise a pump of the multiplex plunger or equivalent type with an intake pulsation damper which takes up a minimum of space in the pump assembly and is disposed in an out-of-theway location.

In order that the manner in which these and other objects are attained in accordance with the invention can be understood in detail, reference. is had to the accoming drawings, which form a part of this specification, and wherein:

FIG. 1 is a longitudinal, vertical, sectional view, with some parts shown in elevation, of one embodiment of the invention;

FIG. 2 is an end elevational view of the embodiment of FIG. 1 with some parts broken away for clarity of illustration;

FIG. 3 is a fragmentary inverted plan view of a portion of the embodiment of FIG. 1, with some parts broken away for clarity of illustration;

FIG. 4 is a view similar to FIG. 1 but on an enlarged scale relative thereto, illustrating another embodiment of the invention;

FIG. 5 is an end elevational view, with some parts broken away and some in section for clarity, of the embodiment shown in FIG. 4; and

FIG. 6 is an elevational View illustrating a damper of the type shown in FIGS. 4 and 5 applied to a pipe for damping fluid pressure pulsations therein.

Referring now to the drawings, there is shown in FIGS. 1-5 a multiplex plunger pump of the type disclosed in the aforementioned Giraudeau patent. The pump comprises a cylinder block 1 having a plurality of horizontal, parallel bores 2 which extend longitudinally of the pump in a side-by-side relationship. Cylinder block 1 is secured to a frame 3 having an end plate 4 provided with openings aligned with bores 2 of the cylinder block, each of such openings receiving a stufiing box 5. Each stufling box 5 receives a plunger 6 and serves both to guide the plunger during its reciprocatory movement and to seal one end of the bore with which it is associated. At its end opposite the stufiing box, each bore 2 is closed by an end plug 7 bolted to the cylinder block.

Cylinder block 1 is also provided with a plurality of parallel vertical bores 3 intersecting the bores 2, such intersection providing for each bore an inlet port, in which is disposed the usual inlet valve 9, and an outlet port, in which is mounted the usual outlet or exhaust valve 10. The upper ends of bores 8 are each closed with a cap or plug 11 bolted to the cylinder block. Portion 12 of the cylinder block, which can be considered an exhaust manifold, is traversed by a transverse bore 13 intersecting all of the bores 8 so that the upper end portions of bores 8 all communicate with bore 13. At one end, bore 13 is closed by a cap 14. At the other end of bore 13, portion 12 of the cylinder block is provided with a flange 15 and bolts 16 for connection to an outlet fitting (not shown) in the usual manner.

At its bottom, cylinder block 1 is provided with an integral, transversely extending, generally cylindrical, intake manifold 17 having

end flanges

18 and 19. A cap 20 is bolted to flange 18 to close the intake manifold at that end, while flange 19 is equipped with a plurality of bolts 21 for attachment to an input fitting (not shown) in the usual manner. Between

flanges

18 and 19, manifold 17 has an elongated opening 22 which extends along the manifold for substantially the entire length thereof. Opening 22 faces or opens downwardly and is defined by dependent, parallel, straight side walls 23 and opposed, semi-circular end walls 24.

Walls

23 and 24 are integral with cylinder block 1 and have bottom faces which are connected to each other and lie in a common horizontal plane. Opening 22 communicates with each of the inlet ports and the inlet valves therein via bores 8 and the bore of manifold 17. Furthermore, the width of opening 22, i.e., the distance between side walls 23, is approximately the same as the diameter of each of bores 8 so that the opening lies directly opposite and extends across all of bores 8 and is generally center with respect thereto.

Referring now to FIGS. 1-3, the embodiment there shown includes a flexible diaphragm 25 which overlies the bottom face-s of

Walls

23 and 24 and extends completely across opening 22. Bolted to

walls

23 and 24 is a dished casing member 26 which, when viewed in plan, has the same general configuration as opening 22. Thus, member 26 is elongated and has parallel, straight side walls 27 and opposed, semi-circular, end walls 28, such walls being provided with an outwardly extending flange 29 which matches the bottom faces of

walls

23 and 24. Casing member 26 is secured to manifold 17 by a plurality of bolts 39 which extend through flange 29 and are threaded into

walls

23 and 24. The periphery of diaphragm 25 is clamped between flange 29 and

walls

23 and 24 so that when bolts 30 are tightened, the diaphragm close-s and seals opening 22. The diaphragm in conjunction with casing member 26 defines a sealed pulsation damping chamber which, because the other side of the diaphragm is exposed to the interior of the intake manifold, is effective to damp fluid pressure pulsations in the intake manifold.

Threaded into a suitable bore in one side wall 27 of easing member 26 is a pressurization fitting 31 which includes a check valve constructed to allow fluid under pressure to flow into the pulsation damping chamber but to prevent the escape of fluid therefrom. The damping sneer/2a as chamber is pressurized with a compressible fluid such as air and is operative when charged to that degree of pressure required by the operating characteristics of the pump to damp the pressure pulsations Within the intake manifold.

It is to be noted that the semi-circular end portions of easing member 26 and the diaphragm 25 are centered with respect to the outermost bores 8 so that the pulsation damping chamber extends transversely across all of the bores 8. Diaphragm 25 is of such extent and so positioned as to have a portion facing all of the bores 8 so that the diaphragm faces, in the most direct manner possible, all of the several inlet ports of the pump and does not have any obstructions disposed in the Way. Pressure pulsations in the intake manifold cause the medial portion of the diaphragm to move in a direction transverse to the manifold, such direction being substantially normal to the surface of the diaphragm.

Plungers 6 are reciprocated by any suitable driving means (not shown), such as the crank shaft and multiple connecting rod arrangement disclosed in the aforementioned Giraudeau patent. The driving means is so arranged that the plungers 6 operate out of phase, the intake strokes of the several plungers being successive rather than simultaneous. All fiuid pressure pulsations tending to occur in intake manifold 17 as a result of such actuation of the plungers are effectively damped by the damping action of diaphragm 25.

Referring now to FIGS. 4 and 5, the embodiment there shown includes a pump of the type illustrated in FIGS. l-3 and like reference numerals are used to indicate like parts. Attached to manifold 17, in a manner similar to that of diaphragm 25 and casing member 26, by a plurality of bolts 33 are diaphragm 34 and a casing member 35.

Casing member 35 includes a pair of straight, parallel side walls 36, a pair of opposed, semi-circular end walls 37 and a bottom wall 38. The upper faces of

walls

36 and 37 are flat and continuous and abut the bottom faces of

walls

23 and 24. An annular groove 39 extends around the upper portions of

walls

36 and 37 and faces or opens towards

walls

23 and 24. Groove 39 receives a rectangular, annular bead 40 which extends around the periphery of diaphragm 34. Adjacent to groove 39 and on the interior side thereof is a rounded shoulder 41 which abuts that portion of the diaphragm which is adjacent to bead 49. When bolts 33 are tightened, groove 39 and shoulder 41 and

walls

23 and 24 clamp the peripheral portion of the diaphragm, including the bead, therebetween to define a sealed pulsation chamber 42 between diaphragm 34 and easing member 35.

Bottom wall 38 has a bore 43 which at one end communicates with chamber 42 and at its other end is threaded and connected to a pressurization fitting 44, in the form of a check valve similar to fitting 31, which allows the pulsation chamber to be pressurized. The seal due to bead 40 is more effective than the seal of diaphragm 25 so that the chamber 42 can be pressurized for longer periods of time Without leakage of air therefrom.

Diaphragm 34 is flexible and, except at its ends, has a generally W-shaped transverse cross section. The sides and ends of the medial portion extend away from the manifold so that the diaphragm, when in its normal position, bulges between or lies within the walls of the casing member, as shown in the drawings. Such configuration increases the flexibility of the diaphragm and is more effective to damp the pressure pulsations in the intake manifold than diaphragm 25.

Diaphrabm 34 is most effective when the pressures on opposite sides thereof are balanced so that the diaphragm assumes the position indicated in FIGS. 4 and 5. If the pressure in the intake manifold greatly exceeds that in the pulsation chamber, the bottom ridge, indicated by numeral 45, will be turned inside out, and if the pressure in the pulsation chamber greatly exceeds that in the intake manifold, the whole diaphragm will be turned inside out and bulge into the interior of the intake manifold rather than lying between the walls of the casing member.

To insure that the diaphragm is correctly positioned upon pressurization of the pulsation chamber, side walls 36 each include a transparent portion in the form of a cylindrical Window 46 cemented in and extending through the side wall, the remainder of the casing member being opaque. Alternatively, all of the casing member can be transparent. Each window 46 is located halfway along the length of the casing member and at such a height that the bottom of the diaphragm can be seen through the windows when the pressures acting on the diaphragm are balanced and the diaphragm assumes its most effective position.

Normally, the pressurization operation is carried out under such conditions that, if a pressure gage were used to indicate the degree of pressurization, a given pressure reading on the gage would not correspond to the position of the diaphragm, because of the different pressures within the manifold. Thus, the position of the diaphragm can be observed directly and the correct degree of pressurization can be achieved with ease.

Referring now to FIG. 6, the embodiment there shown includes a pipe 47 having a fitting 43 fixedly secured thereto for connection to a damper of the type shown in FIGS. 4 and 5, the damper including a diaphragm 34 and a casing member 35 secured to fitting 48 by a plurality of bolts 33. Pipe 47 has an elongated opening 49 surrounded by the walls of the fitting so that the interior of the pipe communicates through opening 49 with the damper in a manner similar to that by which manifold 17 cooperates with diaphragm 34 and casing member 35.

Since the flow through a pipe is substantially entirely longitudinal, it will be seen that the movement of the diaphragm due to pressure fluctuations is generally transverse to the direction of fiow of fluid within which the pulsations are being damped. Pipe 47 can be connected through a suitable fitting to the intake manifold of a multiplex reciprocatory pump for damping pressure pulsations therein, but the amount of damping would not be as great for a given size damper as if the damper were connected directly to the manifold, as shown in the embodiments illustrated in FIGS. 1-5.

While a plurality of embodiments have been disclosed, the invention is not limited thereto, since it will be apparent that many changes can be made in the details and arrangements of parts without departing from the scope of the invention as defined in the appended claims.

What is claimed is:

1. In a heavy duty, multiplex, reciprocatory pump of the type used in oil fields to pump large quantities of liquid down a well, the combination of a cylinder block having a plurality of parallel horizontal bores and a plurality of parallel vertical bores each intersecting a different one of said horizontal bores and defining a plurality of inlet ports and a plurality of outlet ports a valve operatively associated with each of said ports for controlling the flow of liquid therethrough;

a plunger disposed in each of said horizontal bores for pumping liquid through said ports,

said plungers being reciprocable out of phase so that the intake strokes of said plungers occur in succession; an elongated intake manifold integral with said cylinder block,

said inlet ports all communicating with the interior of said manifold via said vertical bores, said manifold having an opening disposed opposite said vertical bores and centered generally with respect thereto, said opening being elongated in a direction longi- KJ tudinally of said manifold and extending in said direction across all of said vertical bores; the said manifold between said opening and said vertical bores being completely open and unobstructed to provide a direct passage from any one of said bores to said opening;

a single flexible diaphragm extending across said elongated opening and sealingly closing the same;

a dished casing member having an elongated mouth similar in size and shape to said elongated opening in said manifold;

means mounting said casing member on said manifold with the mouth of said casing member aligned with said elongated opening and with said diaphragm extending across and sealingly closing said mouth, said diaphragm and said casing member defining a plusation damping chamber; and

a valved fitting connected to said casing member and operative to allow said damping chamber to be pneumatically pressurized for directly and simultaneously compensating pressure fluctuations occurring within said intake manifold.

2. A pump in accordance with claim 1 and including a transparent wall portion disposed so that said diaphragm can be externally viewed to permit the said damping chamber to be properly pressurized for any given operating conditions of the pump.

3. A pump in accordance with claim 2 wherein said transparent wall portion constitutes at least a portion of said casing member.

4. A pump in accordance with claim 1 wherein said diaphragm has a W-shaped transverse cross section.

5. A pump in accordance with claim 4 wherein said casing member includes a transparent portion through which the bottom of said diaphragm can be seen from the exterior of said casing member to permit the damping chamber to be properly pressurized for any given operating conditions of the pump.

6. In a reciprocating pump of the type used in oil fields to pump liquid down a well, a damper for damping fluid pressure pulsations in the intake manifold of said pump, comprising a casing member open on one side and including a transparent portion,

a flexible diaphragm sealingly closing said open side to define between said diaphragm and said casing member a pulsation damping chamber, said diaphragm being adapted to be directly exposed to the intake manifold of said pump within which occur the pressure pulsations being damped,

and a valved fitting connected to said casing member and operative to allow said damping chamber to be pneumatically pressurized for directly and simultaneously compensating pressure fluctuations occurring within the intake manifold,

said transparent portion being located so that at least a portion of said diaphragm can be viewed when said chamber is pressurized to position said diapragm in its most effective position for any given operating conditions of the pump.

7. In a heavy duty, multiplex, reciprocatory pump of the type used in oil fields to pump large quantities of liquid down a well, the combination of a cylinder block having a plurality of parallel horizontal bores and a plurality of parallel vertical bores each intersecting one of said horizontal bores and a plurality of inlet ports and of outlet ports;

valve means operatively connected for controlling the flow of liquid through said ports;

a plurality of plungers each disposed in a different one of said horizontal bores for pumping liquid through said ports, said plungers being reciprocable out of phase so that the intake strokes thereof occur in succession;

an elongated manifold communicating with all of said vertical bores, said manifold having an opening disposed opposite said vertical bores and centered generally with respect thereto, said opening being elongated in a direction longitudinally of said manifold and extending in said direction across all of said vertical bores;

the said manifold between said opening and said vertical bores being completely open and unobstructed to provide a direct passage from any one of said bores to said opening;

and a damper mounted on said manifold for damping fluid pressure pulsations in said manifold, said damper comprising a dished casing member open on one side and including a transparent portion,

a flexible diaphragm clamped between said casing member and said manifold, said diaphragm extending across said open side and across said opening to define with said casing member a sealed pulsation damping chamber;

and a valved fitting connected to said casing member and operative to allow said damping chamber to be pneumatically pressurized,

said diaphragm including a medial portion which is movable in response to changes in the pressure in said intake manifold,

and said transparent portion being arranged to allow said medial portion to be seen when said medial portion is in at least its most effective position.

References (Iited in the file of this patent UNITED STATES PATENTS FOREIGN PATENTS 128,129 Sweden Nov. 12, 1957

Claims

1. IN A HEAVY DUTY, MULTIPLEX, RECIPROCATORY PUMP OF THE TYPE USED IN OIL FIELDS TO PUMP LARGE QUANTITIES OF LIQUID DOWN A WELL, THE COMBINATION OF A CYLINDER BLOCK HAVING A PLURALITY OF PARALLEL HORIZONTAL BORES AND A PLURALITY OF PARALLEL VERTICAL BORES EACH INTERSECTING A DIFFERENT ONE OF SAID HORIZONTAL BORES AND DEFINING A PLURALITY OF INLET PORTS AND A PLURALITY OF OUTLET PORTS A VALVE OPERATIVELY ASSOCIATED WITH EACH OF SAID PORTS FOR CONTROLLING THE FLOW OF LIQUID THERETHROUGH; A PLUNGER DISPOSED IN EACH OF SAID HORIZONTAL BORES FOR PUMPING LIQUID THROUGH SAID PORTS, SAID PLUNGER BEING RECIPROCABLE OUT OF PHASE SO THAT THE INTAKE STROKES OF SAID PLUNGERS OCCUR IN SUCCESSION; AN ELONGATED INTAKE MANIFOLD INTEGRAL WITH SAID CYLINDER BLOCK, SAID INLET PORTS ALL COMMUNICATING WITH THE INTERIOR OF SAID MANIFOLD VIA SAID VERTICAL BORES, SAID MANIFOLD HAVING AN OPENING DISPOSED OPPOSITE SAID VERTICAL BORES AND CENTERED GENERALLY WITH RESPECT THERETO,