US2806433A

US2806433A - Leakage control for centrifugal pump shaft seals

Info

Publication number: US2806433A
Application number: US301053A
Authority: US
Inventors: Bour Harry E La
Original assignee: BOUR Co Inc
Current assignee: BOUR Co Inc; LA BOUR COMPANY Inc
Priority date: 1952-07-26
Filing date: 1952-07-26
Publication date: 1957-09-17
Anticipated expiration: 1974-09-17

Description

Sept. 17, r1957 H. E. LA BouR 2,805,433

LEAKGE CONTROL FOR CENTRIFUGAL PUMP SHAFT SEALS I Filed July 2s. 1952 y 4 sheets-sheet 1 INVENToR.

l Sept. 17, 1957 H. E. LA BouR 2,805,433

.LEAKAGE CONTROL FOR CENTRIFUGAL PUMP SHAFT SEALS Filed July 26, 1952 4 Sheets-Sheet 2 VHCUUM E VH POR/)TOR Z9-@- 63 i v 62 i@ w l 33 Q5 QQ 4Z 4@ (QE I 56A' 60 5.9 l' 3 g3 Q7 INVENTOR.

ryaar;

Sept `17, 1957 H. E. LA BOUR 2,806,433

LEAKAGE CONTROL FOR CENTRIFUGAL PUMP SHAFT SEALS Filed Julyl 26, 1952 4 sheets-sheet 3 IN V EN TOR.

Sept' 17, 1957 H. LA BOUR 2,806,433

LEAKVAGE CONTROL FOR CENTRIFUGAI. PUMP SHAFT SEALS Filed July ze. 1952 4 sheets-sheet 4.

IN VEN TOR.

United States Patent @ffice LEAKAGE CGNTROL'FOR CENERIFUGAL PUMP SHAFT SEALS Harry E. La Bour, Elkhart, 1nd assigner to The La Bour Company, Inc., Elkhart, Ind., a corporation of indiana ApplicationrJuly 26, ,1952Serial No. 361,053 4 Claims. (Cl. 163-97) This invention relates to lluid pumps, and more particularly to the control of leakage at the shaft seal of a centrifugal or other rotary pump. The invention is particularly concerned with pumps having a rotary loperating shaft extending out of the'pump casing with which it is intended to make a iluid tight rotary joint or so called shaft seal, the inner end of which is` subject to pressure variations in the pump casing due to variations in ,the pressure of theuid supply, .and the outer end of which shaft seal is subject to a non-related pressure, generally atmosphere.

I shall Ydescribe the invention and -exiplain its principle in connection with a hydraulic centrifugal pumpv of known type, but the problem of control of seal leakage in rotary pumps and .morevspeciticall centrifugalpumps, is not confined to aspecific form of hydraulicpump, ynor to speoic forms of seals.

In the operation of the type G pump, which is a selfpriming pump having a kinetic liquidseal, and which has a construction substantially as shown in my-U. S. Patent No. 2,381,824, .of August 7, 1945 (British specification No. 588,939), I observed that so long as the liquid supplied to the pumpwas deliveredy at apressure not .substantiallyhigherlthan the pressure `prevailing upon the outer end of the liquid seal, the liquid seal Voperated without outward loss of liquid. The seal in that pump is Idesigned to be effective with a full vacuum inside ofthe pump casing, that is, a maximum pressure difference of vr14.7 pounds per square inch. Since it is a self-priming liquid pump, so long as it mustdraw its supply froma lower level, the maximum pressurediiference which can be imposed upon the Asaid seal is said 1.4.7 pounds per squarepinch.

So long as the type G pump, or any similar self-priming centrifugal pump, operates either to lift liquid from `a lower level or has its intake connected to la region in which a partial vacuum is to be maintained, as, `for example, a vacuum evaporator, andthe liquid is always delivered at sub-atmospheric pressure, there is no `tendency for liquid to leak out through the seal because of the preponderanceof outside pressure over inside pressure on the seal.

But if ,the pump, even though it be a self-priming pump, be connected to a source of liquid, the pressure of which imposed upon the pump intake may rise aboveatmospheric, then the prevailing pressure difference onthe seal may be outwardly sniciently to produce an escape of liquid at the seal. This yescape Aof liquid is at all events undesirable, and it may be highly objectionable. For example, when the liquid is corrosive or toxic orvaluable, leakage cannot be tolerated.

The said type G self-priming centrifugal pump above referred to would, because of its self-maintained liquid seal and other features of construction, be of great value in vacuum evaporator service, particularly because the packingless feature overcomes one of the `principal sources of trouble with pumps in vacuum evaporator of inflow of uid ymedium in the intake of'the pump,

Vwhereby the pressure producedby the impeller at the Eatented Sept 17, 1957 corrosive, but it is hot, andrunder normal circumstances the pump would be under vacuum.

The drawback to the Yuse of the typel G pump in vacuum evaporator service is that during the. cycle ,of voperation, .there may be a gravity head of liquid (positive fin value) von the suction `of the pump. At Yother times, there `will bea high vacuum at the same point. .With the type VGv pump, the high vacuum `is handled very .satisfactorily, but positive pressure at the suction .cannot be handled without the danger of passing liquid at the seal, and this is undesirable, and in some cases prohibitive. For a pump having a conventional iibrouspacking seal, leakage .of `air inwardly on .suction service, .and leakage of liqui'd outwardly on gravity feed service may well occur. By by keeping the pressure upon the inner end of the seal at the same pressure (atmospheric) as `the presbyacting upon .the iiuid medium supplied `to it, produces the .desired pressure condition at the inside end of the seal. Through regulation of the inward 4ilow of `fluid medium, the' pressure conditions Vproduced .by the im- .peller can be .suitably controlled.

The object `of Vthe present invention .to perform a .novel `regulating function -of athe pressures imposed upon opposite sides of the pump sealby-introducing a control inner end of the seal may be maintained at orvbelow atmospheric pressure, or may be maintained atr any other desired value which will maintain either substantial equality of pressures at the opposite -endsof theseal or a suitable differential ac :ccvJrdingv to which Vthe outside pressure is higher than the inside pressure, whereby there will lbe no tendency for flow of Vfluid outward-ly at the seal, and lthe seal will not .pass fluid.

The invention aims to provide a combination of ymeans for performing the aforesaid function automatically."

T his invention `utilizes the ability of the impeller acting upon the uid being pumpedwhen the fluid is supplied at atmospheric'pressure or higher tol createpin the region of the inner end of vthe seal, a pressurelower than Vatmospheric pressure by cooperation of a restriction to inliow.` This flow restriction lmay'bey carried to a completeclosure, i. e., shutoli, when the impeller ceases to remove the fluid from the casing, more particularly from the region of the inner end of the seal fas,for example, when the pump is being shut down, or when `it isnlot operating. Y

Normally, the seal is subject at its imner endrto the minimum pressure (or maximum suction) .prevailing in the casing. -But the regulating function maybe. carried out automatically by referenceto the pressure prevailing at some other selected point which will produce the desired pressure upon the inner end of the seal. According to my invention, the Vcontrolling means or flow restriction valve in the intake or pnrnprsuction connection is set to maintain a minimum vacuum when there is a zero head on the supply side of the valve. When the vacuum rises above the minimum value, thevalve is not required to produce a ow restriction, and under those conditions, performs no function and hasl no effect.l The pump, under those circumstances,l operates as though the Avalve were not there. Upon complete loss of vacuum at the pump suction, the valve moves toward closed position to protect the seal against overflow. `This reaches maximum when the pump is shut down.

The invention is not :confined to self-priming pumps,y

t: 3 but may be employed in connection with non-self-priming centrifugal pumps. Also the invention is not limited to liquid seals, but is applicable to pumps having the usual brous -or solid packet stuing boxes or similar rubbing Seals. Thus, for example, a pump of the construction substantially as shown in my Patent No. 2,134,254, of October 25, 1938 (British specification No. 478,862), known as -the type Q pump, presents a similar problem, under certain conditions of operation, and particularly where the liquid to be pumped is supplied under a head above atmosphere, or tluctuates so as at times to be above and at other times to be below atmosphere. Thus, for example, if a pump of the non-self-priming type be employed as a gravity feed pump attached to a storage tank or other source of supply above atmospheric pressure, the seal may be protected against leakage outwardly by means of the present invention. In case the liquid is highly volatile and toxic a self-priming pump cannot be located above the liquid level as the vacuum required to lift the liquid from below the pump and at the same time produce the necessary pressure for How, causes so much vaporization of the liquid that little capacity can be obtained from the pump. In that case, a gravity feed pump, with iibrous packing or other mechanical seal, is preferable.

The pump in that case is located below the liquid level, and consequently, the stuffing box or seal must not only be abnormally tight and efficient, but must be encased and vented to prevent danger from explosion or from the toxic nature of the liquid or vapor evolved. In such case, by maintaining a slight vacuum within the pump at the point where the seal is exposed to internal pressure, in accordance with this invention all outward leakage is prevented. Such vacuum needs to be only very slight, that is, not enough to involve vaporization, but it must be definite and positive at all times. The shutoff provided by the system of my invention may be supplemented by hand operated valves or other shutoff valves as an additional precaution.

There are similar situations where a centrifugal pump is provided with a combination liquid seal while pumping, and an automatically applied rubbing seal or stopper or other closure for shutting off the gap between the casing and the shaft when the impeller `cornes to rest. As an example of such pumps, I refer to my copending U. S. application, Ser. No. 48,586, filed September 10, 1948, now matured into Patent No. 2,621,600 (or see Patent No. 1,346,924 to Wilfley). The maintenance of a slight preponderance of pressure of atmosphere over the pressure prevailing at the inner end of the seal by the flow restricting valve in the intake of the pump, insures in that case against liquid leakage out of the seal while the pump is running, and particularly against the loss of liquid in the interval between effective pumping and closure of the mechanical stopper as the pump is taken out of operation.

While the flow restricting valve may take various forms for performing this novel function, I prefer to use the specific form of valve shown in my copending application, Ser. No. 301,054, tiled July 26, 1952, now matured into Patent No. 2,709,451, which valve is herein disclosed for the purpose of teaching the advantages of the present invention according to the best form of which I am now aware, said valve being claimed per se in the said copending application. I am laware that it has been proposed to employ means internally of the prunp and casing, such as a secondary impeller, effective at a point adjacent the seal to produce a reduction in pressure at the inner end of the seal. Such devices are designed merely to produce a predetermined pressure difference through removal of the liquid from the vicinity of the inner end of the seal, but if the supply pressure at the inner end of the same uctuates, then the resultant pressure at the inner end of the seal may still rise above and exceed the pressure at the outer end of the seal.

Now in order to acquaint those skilled in the art with 4 i the manner of constructing and operating a device embodying my invention, I shall describe, in connection with the Iaccompanying drawings, a specific embodiment of the same.

In the drawings:

Figure 1 is a diagrammatic illustration of a type G self-priming liquid sealed pump equipped with my invention;

Figure 2 is a diagram of a gravity feed type of pump employing fibrous or solid packing for the seal, and equipped with my invention;

Figure 3 is a diagram of connections of the pump shown in Figure 1 toa vacuum evaporator;

Figure 4 is Ia diagram showing the pump of Figure 2 connected to a storage tank for gravity feed therefrom;

Figure 5 is a longitudinal vertical section through the preferred form of valve;

Figure 6 is a side elevational View of the same with certain of the parts broken away to reveal the cam arrangement;

Figure 7 is a fragmentary top plan View of the closure for the guide of the valve plunger; and

Figure 8 is a fragmentary cross section taken through the valve body on the line 8--8 of Figure 5.

Referring now to Figures 1 and 3, the pump illustrated in these figures is the type G pump above referred to, which comprises a main pump body 1, seated upon a supporting pedestal 2, and surmounted by a driving motor 3, carried on a supporting bracket or column 4. Figure 3 illustrates in side elevation the commercial form of the type G pump which is shown in the sectional diagram of Figure 1.

The pump body 1 has an inlet or inlet passageway 5, which leads into an inlet trap 6. The trap 6 has a bottom opening in the form of an annular gap or space between a circular wall of the bottom of the trap 6 and the stationary sealing sleeve 7, which has its upper end sealed to the top wall of the inlet trap 6.

A discharge trap or gas separator 8 surrounds the inlet trap 6, and communicates with a discharge connection 9, which in the preferred form connects with a check valve 10, as shown in Figure 3, and a discharge pipe 12 leading to a suitable discharge point. Between the intake trap 6 and the separator 8, there is provided an impeller chamber 13, in which impeller chamber are disposed a series of blades 14 mounted upon a runner 15 carried by the impeller shaft 16. This runner 15 is in the shape of a attened cylindrical box or drum upon the upper wall of which are mounted the impeller blades 14. The upper wall of the drum is open at the center so that it is annular in form, and it embraces loosely the sealing sleeve 7. The sealing sleeve 7 bears on its lower end an annular horizontal flange 17 which thus divides the sealing drum into ripper and lower liquid retaining spaces joined at their outer peripheries so that a radial section at any point is U-shaped with the bottom of the Ll radially outward. The impeller blades 14 discharge through suitable throats 18 and passageways 19 which communicate with the gas separator space 8.

The entrainment of gas with liquid and peripheral reentry of a liquid into the impeller for performing the gas pumping or evacuating function of the self-priming pump is well known to those skilled in the art.

Assuming that the pump shown in Figure 1 has performed the so called self-priming function, and is operating to move liquid from inlet passageway 5 through the trap 6, impeller blades 14, throats and

passageways

18, 19, into the separator 8, and out the discharge connection 9, and assuming that the source of liquid supply is at a level lower than the pump, then the two sides of the liquid seal extending around the annular disc 17 and sleeve 7 are subjected to a pressure difference. The suction which the pump creates reduces the pressure at the point B, namely, at the radially inner end of the top leg of the kinetic liquid seal maintained between the ange or disc 17 yand the heads of the Ydrum `15. Atmospheric pressure as indicated at Anprevails in the annular space between the impeller shaft v16 and the inside of kthe sleeve Y 7, and extends down to the 'lower leg of the kinetic liquid ,seal lying below the annular flange or disc 17. This kinetic seal is designed to be capable of withstanding the pump. Although the evaporator 22 is located -above 'the lpump..1, so as to,provideigravityjlowfof'liquid evolved, the pump maintains a vacuum on the intake of, the 'pump and on the intake side .of the sealindicatedl atjB during partgof vthe cycle when the evaporator 'is under vacuum. However, if the vacuum evaporator 22 supplies Vliquid .underl'gravity head, and at a rate which maintains a positive pressureabove atmosphere in thepassageway `5 and intake trap 6, .then the pressure upon the inner endA of the seal, as indicated at the point B, may rise above atmospheric Ypressure to the point where ,the seal will L pass liquid outwardly.

In order to maintain the pressure at .the inner tend of theliquid seal, as at point B, at a value which will not 1rise, above the pressure ,prevailing at A, `in this instance, atmospheric pressure, I interpose a flow .restricting and shutoff valve 23. indicated 'diagrammaticallyiniFigure 1 and at 23 1in Figure 3. The form vof valve 2'3.is the preferredform, and it is

shownin detail jin'Figures

5 ,and 6. Referring, however, toFigure 1 the valve 23 comprisesa valve body 24 having the dividing wallV 25 through which are formed the two

valve openings

26 and 26a .covered by a balanced valve comprising a stem 2 7'V bearing the valve vdiscs 28 and 28a movablein Vunison toand from the valve seats of the

openings

26 and 26a. The stem 27 passes through a packing 29 and is connected .to adiaphragm 30. The inner end of. this packingissubject to the pressure prevailin-gon the pump side ofvalve .23. 'The lowersurface vof the diaphragm is ,opento at- A,rrresphere- The upper Surface0fthe,diaphragm is covered bya diaphragmcylinder or chamber 3 2, theginside of which chamber is subject to the-pressure prevailing at B 4 in ,the intake passagewayS by-virtueof theconneetion .33, between saiddiaphragm chamber and ,the ,inside of th e intakepassageway of the pump. Arneedle `valve .or like flowrestriction 34,mayvbe placed in the tubular ,connection-3310 iron out or delay-the effect Aofuctua- `rtions in pressure, if desired. Suchneedle valve is optional. AThe `diaphragm 30 is loaded by the spring 35, which may be. adjusted `to asuitable loading for normallytholding the

vdiscs

28 and 28a over the ,valve openings .26 .and ;2 6a.to close olf the inlet passageway 20 from theinside of the casing of the pump. As -soon as suction is produced inthe-intake side ofthe pump, as in the intake trap 6 Aandpassageway 5 suction acting upon the diaphragm 30 I against the pressure of thespring 35 will raise thevalve r-

discs

28 and 28a .opening communication between :the

Iinside of thepump, casing, that is, the suction side of the pump Aand the intake connection 20 leading to the liquid :supply at the -vacuum evaporator 22.

The operation of -the.system, diagrammatically Villustrated in Figures l and 3, is as follows: Assume that .the pump 1 has its intake passageway 5 and intakeconnections 20 with the valve 23 or the specific form rof valve 23' :connected-in series .between the vacuum ,evaporator 22 and the pump '1. The Vdischarge .connection 9 is conl ,nected .through a check valve to the discharge -pipe,12.

A shutoff valve 37 in the intake connection 2 0 -normally :isolates thepump from the vacuum .evaporator when the parts are idle. Similarly, a manually operated shutoff valve may beincluded in the discharge pipe 12 to shut off Vall return ilow reither as a substitute for the check valve or as a supplement thereto.

Assume that the valves are open and the vacuum evaporator V42(2is subject to vacuum and feeds liquid by .gravity at a rate which does not quite fill the liquid capacity of they p ump so that a vacuum is maintained Yin the inside of the pump casingon the suction side of the same, as at the point B', which is representative of the pressure prevailing at the point jB on the inner end of the liquid seal Aof the pump.

-So long as the pressure prevailing on the intake side of 4the impeller, and hence upon the inner end of the liquid'seal, isless than atmospheric, or not more than the pressureupon the outside of the seal, there is no tendency for the seal to pass liquid outwardly. In that event, the valve 2 3 performs no function, and is open sufficiently to pass all the liquid required to b e pumped without substantialrestriction.

'Under the circumstances that vacuum within the evaporator is insufficient resulting in aV positive gravity head upon the intake side of the pump, so that there would be a preponderance 'of pressure on the inside end of the vseal as comparedwithA the pressure on the outside end ofthe se al, the valve 23 moves towards maximum flow restriction position, namely, towards closed position, and

interposes a restriction to flow which immediately allows thefpump 4to evacuate sufficient Huid to bring the pressure att-he point -B to the proper value, that is, not higher than the pressure at the outer end of the liquid seal, as represented-by the pressure at A.

The pressure at point B where the connection 33 is made -is representative of the pressure at the point B and may be used as a variable pressure suitable for the kregulating function ofthe valve 23. If desired, the connection of the pipe 33 to the interior of the pump at a point closer to the inner end of the liquid seal maybe utilized, but I have found connection of the pipe 33 to the intake passageway 5 or to the top of the trap 6, as providing a satisfactory and reliable indication of the pressure upon ythe inner -end of the kinetic liquid seal.

Thus, the pump 1, in combination with the vacuum control valve y23, will operate without leakage of air inwardly, or liquid outwardly at the seal, eventhoughthe vpressure of liquid or other uid medium supplied to the intake connection of the pump be below or above atmospheric pressure.

Referring now to Figures 2 and 4, I have shown a horizontal pump 40 having an impeller shaft 42. The pump casing itself is4 supported on a bearing bracket 43 which supplies a Asuitable bearing 44 for thepump shaft 42. The said shaft 42 is in turn connected through a coupling 45 to the motor shaft of a motor 46. The bracket 43 and the motor 46 may be mounted upon a suitable base plate 47 ofknown construction. The pump `40 may be any suitable form of non-priming centrifugal pump and the present diagrams relate to the type Qpump disclosed inthe aforesaid U. S. Patent No. 2,134,254, employing an open impeller running concentrically in a channel having a plurality of discharge throats leading to va common discharge connection. However, any suitable known or preferred type of centrifugal pump employing a rotary joint or shaft seal may be utilized in this combination.

A packing gland 48 forms a running seal between the shaft 42 and the adjacent wall of the pump casing 49. This packing gland comprises a metallic sleeve 50 integral with the pump wall 49 and having a recess 52 for receiving a fibrous packing which is compressed in the pocket 52, and against the shaft 42 by the gland follower 53 by means such as is disclosed in the aforesaid patent or in any otherl preferred manner. On the intake side of the impeller 55, the casing 49 is shown as having a flared lor conical wall 56 with an intake passageway 57 leading thereinto. This intake passageway 57 t corresponds .to .the intake passageway 5 shown in Figure 1. An automatic vacuum control valve 23 is interposed between the source of liquid supply, which-in the present instance, as shown in Figure 4, is a liquid storage tank 58, and theV intake side of the impeller S5. The liquid supply connection 59 from the storage tank 58 to the inlet passageway 57 of the pump 40 supplies liquid under a positive head, whereby the pump 40 may be subject to a positive pressure greater than atmosphere and the inner end of the packing gland 4S, particularly at the point B, will be subjected, in the absence of the function of the control valve 23 or 23' to a greater pressure than atmospheric, which atmospheric pressure prevails at the outer end indicated at point A beyond the packing at 52. The discharge connection 64 of the pump casing is connected to a discharge pipe 63 and in the discharge pipe 63 there is disposed a shutoff valve 62 which may be `a hand valve like the valve 60 on the inlet connection. 4

Assume that the storage tank 58 contains a highly volatile toxic liquid which does not permit the use of a selfpriming packingless pump to move the same. Conventional gravity feed pumps have packing or mechanical seals at the shaft, and it is impossible to prevent some leakage at the shaft seal and such leakage is dangerous. The control valve 23 or 23', which is the same as that shown in Figure l, or in Figure 3, being disposed in the intake connection between the source of liquid supply 58 and the pump casing, is set to maintain a slight vacuum at the pump suction at, for example, the point, B', namely, the inner end of the pipe 33, which in this case is projected inside the intake casing to a point which may be termed the eye of the impeller. The pressure at the point B' is representative or responsive to the pressure prevailing at the point B, namely, the inner end of the seal, and when the pressure at point B, or other suitably selected point at the intake side of the impeller, rises above a predetermined value, the valve body moves to a flow restricting position, su-ch as to restore in the intake of the impeller and casing a suitably reduced pressure whereby the pressure upon the inner end of the packing gland 48 is not in excess of the pressure at the outer end of the said packing gland, and thereby the gland will not pass liquid outwardly.

The inner end of the suction connection 33 need not be extended to the very eye of the impeller, but may, in fact, terminate at any desired point inside the casing Where a pressure representative of, or corresponding to the pressure prevailing at the inner end of the packing gland B occurs. I have found that a suitable controlling pressure may be selected at any point on the intake side of the impeller where there is no substantial restriction to iiow between such connection and the impeller.

By maintaining a slight vacuum within the pump at the point where the seal is exposed at its inner end, all outward leakage is prevented. This vaccum needs to be only very slight, not enough to involve serious vaporization, but it must be positive at all times. When the pump is to be shut down, the

automatic valve

23 or 23 closes off, but preferably the

hand valves

60 and 62 are closed as an additional precaution, since all leakage is to be avoided.

In either embodiment, with the control valve in place, regardless of the supply pressure and regardless of the rate of ilow through the pump, a slight vacuum is maintained at the eye of the impeller which communicates with the inner end of the stuffing box, and thereby outward leakage is prevented. This valve can be set for a minimum vacuum which remains substantially constant regardless of the rate of flow, so that normal operation with automatic adjustment of the valve to the rate of llow Icontinues without further consideration by the operator.

While I have shown in Figures l and 2 a relatively simple form of automatic ow restricting valve, I have found in practice that for this particular service there is a tendency for an automatic valve to set up an oscillation which may be termed hunting to nd a condition of balance.

Also, due to certain irregularities of flow which are encountered in pumping liquids, it is desirable to build into the control valve means for preventing too rapid response to variations in pressure and means for preventing variations in flow from inuencing the setting of the valve itself.

As illustrated in Figures 1 and 2, the response of the diaphragm 30 uctuations in pressure on the intake side of the impeller may be stretched out or extended by a flow restriction in the tube 33 which communicates the said fluid pressure. Also, the flow restricting and shutoi valve may be and preferably is a balanced valve whereby the forces acting upon `the valve as the same becomes a ow restriction are substantially equalized or are equalized fully.

I have found that by the utilization of a fluid dashpot the response of the pressure responsive element, such as the diaphragm 30, may be slowed, so that the regulatory effect of shifting the

vlave discs

28 and 28a or like control member Will not cause overthrow and introduce oscillation or hunting.

In Figures 5 and 6, and indicated in outline at 23' in Figures 3 and 4, I have shown the preferred form of valve for the present service.

The specilic valve 23' is intended to be suitable for use in chemical service, and as such, embodies certain specific requirements not necessarily involved in many applications of the invention herein claimed.

It is to be observed that in each embodiment the stuffing box of the ow control valve is located on the controlled side of the flow restricting valve, so that leakage at the same is prevented simultaneously with the prevention of leakage at the pump shaft seal. While the valve regulating diaphragm chamber is preferably connected to the point of highest vacumm source in the pump casing,

Vsuch as at the eye of the impeller, it will generally be suflicient to connect the said diaphragm chamber to a point where pressure representative of that prevailing upon the inner end of the shaft seal prevails.

The specific form of valve shown in Figures 5 to 8, inclusive, and shown in outline at 23 in Figures 3 and 4, comprises a valve body 101 having an inlet 102 and an outlet 103. These connections are shown as flanged couplings, but obviously, other forms of connections may be employed. The body 1 of the valve is provided with a bottom opening which is closed by a cover plate 104 and the top opening is covered by a cover plate 105 which incorporates a stuffing box for the valve operating rod 121. The said stung box 98 may consist of a conventional gland having iibrous or other packing 97 compressed by the gland follower 96 of known construction. This packing for the rod 121 is on the pump side of the valve, so that the suction in the pump will protect this gland from leakage. The separable valve seat cage 106 is made in one piece, with two seats 107 and 108 and with two or

more openings

109 and 110 between the seats. As will be seen from Figure 8, the lateral opening 110 is large enough to -admit the lower section of the valve. The valve cage and assembled unit is inserted through the top of the valve -body ybefore the placing of the cover 105,-and is threaded, or may be otherwise seated into the opening in the web of the valve body 101.

The double valve is made in two pieces to permit the seats being exactly the same diameter and area. This is necessary for an accurately balanced valve. The upper seat 111 is carried in the spacer by multiple arms 113 and threaded connection 114. Spacer 112 at its lower end carries the lower valve member 115 which is assembled by inserting the same through the opening 110 and engaging piloted joint 116 and drawn into rm contact by the nut 117. The lower valve member 115 has multiple openings 118 for the passage of liquid.

The spacer 112 has its upper end disposed within the hub of the upper valve member 111 at 119, and is arranged to be spaced slightly clear of the enlarged end 120 of the stem 121.

The operating mechanism for the balanced valve is attached 'to the valve 'body `through 'bracket 122, 'which at its upper end carries the cam housing 123, which is closed at its lower 'end by vcover 124 equipped with the oil seal 125. Cover 126, .s hown inFigure 7, closes the upper opening in the cam housing in which the roller carrier memberilZSplays.

-Cam housing 123 has a vertical opening 127 between the upper and lower covers 126 and 124, and this opening 127 guides the roller carrier 128, which is attached to the stem 121 of the valve, and which roller carrier 128 carries a cam roller 129 operating in the inclined slot 130 in the cross head member 131, which latter slides in the cross guide slot 132 in cam body 123. At the right hand end, as viewed in Figure 5, the cross head 131 it attached to ilexible diaphragm 133 through the medium of the cylindrical stem 134, which stem extends through the oil seal 135.

Diaphragm 133 has its periphery clamped between the housing member 136 and the cover or chamber mem-ber 137, which latter is provided with an inlet opening 138 for connection as by the tubular connection 33 to the highest vacuum source in the pump or to a point which has a pressure representative of the highest vacuum in the pump.

At the opposite end of cam housing 123 there is an opening 139 covered by a plate 140 which carries the adjusting spring 141, and which housing 123 is closed at its outer end by the threaded plug 142. The spring 141 is compressed between the -bottom of the recess in the housing 140 and a head or anchor plate carried at the outer end of the stem 143. The spring 141 is connected to the cross head 131 through the stem 143.

The cam housing 123 is substantially filled with light oil, and is then sealed as by the plug in the cover plate 126 shown in Figures and 7.

The operation of the valve is as follows: A connection 33 is run from opening 138 to the pump, preferably as near the pump seal opening as possible, ybut at least into the pump suction itself, that is, between the location of the valve 23 and the intake side of the impeller of the pump as shown in Figures 3 and 4. The valve 23 is inserted in the suction line of the pump with the opening 103 towards the pump and the opening 102 connected to the source of supply.

When the pump is not in operation, the spring 141 acting through the cam and roller holds the valve closed.

Now if the pump is started, movement of the impeller will tend to create suction in the intake. As soon as suflicient predetermined vacuum has been built up on the diaphragm 133, it will overcome the spring pressure of the spring 141, and begin to open the valve. This admits liquid to satisfy the suction to the extent permitted by the valve opening under the control of the diaphragm 133. The operation of the valve to maintain the predetermined slight suction on the intake side of the pump is entirely automatic, regardless of the pressure on the supply side of the valve. If the vacuum on Ithe diaphragm 133 falls below the predetermined value, the valve will close until the vacuum increases and again opens the valve. If the pump is shut down, the spring will close the valve and hold it closed until vacuum again is present on the intake side of the pump effective upon the diaphragm 133.

In practice, -it has been found that a vacuum as low as one inch of mercury will start to open the valve. The required amount of opening is of course controlled by the rate of iiow through the valve which is in turn a factor of the pressure differential across the valve.

If the inlet to the valve is under vacuum, the valve stays open. If now, the inlet condition changes to pressure, that is, above atmosphere, the valve will adjust the opening to maintain the full rate of ow under the new pressure conditions always providing, however, that the desired vacuum condition effective upon the inner end of the pump seal is maintained. The valve functions smoothly and without surging. Pressure and flow impact of 1,0 liquid or other mediumiupon the valve itself is balanced, and is not-.effective to shift -the posit-.ion of the valve relative toits seat or relative to the diaphragm.

'I'he slope of the cam 130 actingupon the rol1er129 is preferably below the critical angleJsothat thefcam locks the position of the valve stern. ,whileyfree tozniove :it by variations in pressure upon the diaphragm 133. It is not strictly necessary to make the cam and roller self locking, since the mechanical advantage which the diaphragm has over the valve tends to produce vsuicient resistance that surging or hunting of the valve does not occur.

While this particular form of valve is highly advantageous for the particular service of regulating the pressure upon the pump seal so as to reduce or avoid leakage, other forms of valve may be employed in this service.

In a centrifugal pump, the impeller tends -to set up a pressure difference between the eye of the impeller and the tips of the blades or the periphery of the impeller. The inlet portion of the casing for the impeller will normally assume the same pressure las the eye of the impeller. Likewise, the inner end of the seal will be subject to the same pressure as the eye of the impeller. Employing the pressure in the intake portion of the casing Ias a control for the flow restricting valve has proven practical and satisfactory.

It will be noted that the specific pumps herein referred to and illustrated are open impeller pumps with concentric channels. These characteristics :are preferred, but are not essential to the construction 'and operation of my invention.

By the utilization of the present invention, controlling the pressure difference upon the opposite sides of the seal, a seal of no great holding power may be used where heretofore seals of high holding power have been required.

I do not intend to be limited to the details shown and described, except as they are made essential by recitation of the appended claims.

I claim:

l. In a liquid pumping system, a centrifugal pump having an impeller, a casing therefor with a discharge connection and an inlet connection for liquid to be pumped, a flow control valve for said inlet connection for controlling the ow of fluid into the casing, an impeller operating shaft extending out of the pump casing through an opening therein, means for sealing the shaft to the casing, said sealing means being subject to varying pressure difference between the inside and the outside of said casing by variation of pressure in the casing adjacent the inlet connection, and a fluid pressure difference operated motor connected to the fluid pressure upon the outside of the casing for moving the valve to the unrestricted position and connected to the inlet side of the casing for moving said flow control valve to a position of tlow restriction whereby said fluid difference operated motor will maintain the pressure at the inner end of the seal at or below that at the outer end of the seal.

2. A liquid pumping system according to claim l wherein the fluid pressure difference operated motor has 'a member subject on one side to fluid pressure in the inlet connection of the casing and to atmospheric pressure on the other side, and a spring cooperating with the pressure on the inlet side of the pump casing to move the valve in the direction of greater restriction of uid flow.

3. A liquid pumping system according to claim l wherein the means for sealing the shaft to the casing is of a character to maintain a kinetic liquid seal between the wall of the casing and the impeller operating shaft.

4 A liquid pumping system `according to claim l wherein there is a separator on the discharge side of the casing.

(References` on following page) References Cited in the yle of this patent UNITED STATES PATENTS Delaney June 4, 1912 Tice Nov. 21, 1933 5 Bowen T Iuly 18, 1944 Shaw et al. Dec. 19, 1944 12 -La Bour Aug. 7, 1945 La Bour Aug. 7, 1945 Griswold July 8, 1952 FOREIGN PATENTS Great Bn'tan Dec. 24, 1918