US 2207575 A
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Description (OCR text may contain errors)
July 9, 1940- R. R.. BoYLEs ET A1.
Filed July 13, 1938 6 Sheets-Sheet l /ITTOE'NEYS v QL lIIIIIIIII /VL/A/To'esv RALPH E. Bor/L55 EDWARD ,4. WIL HEL M OM V A a mal/425% E MS July 9, 1940. R. R. BoYLEs ETAL 2,207,575
' PUMP Filed July 13. 1938 6 Sheets-Sheet 2 .Z/-VVENTORS RALPH E. Bon E3 EDWARD/l. W/LHE/ M @MM/iwf@ July 9, "1940.
Filed July i3, 1938 R. R. BOYLES Er A1.
6 Sheets-Sheet 5 WW V 4 j N VEN TGRS EAL PH E'. Bo YL ES ED WARD/4. W/LHELM @yf-M "M ff'" if ATTozNEw/s i July 9, 1940. R. BOYLE s Er AL 2,207,575
Filed July 13, 1958 6 Sheets-Sheet 4 NVENTOES RALPH l'. Bo YL. E5 EDWARD AVV/L HELM M WMM July v9, 1940. a R. R. ,BoYLEs Er AL 2,207,575
' PUMP I Filed July 1s, 1938. e sheets-sheet s l 252 fwn/Toes ,B4/ PH E. Box/L E5 FIG ,6 EDWARD AVV/HELM Avro/cnrs July 9, 1940. RR. BoYLEs ETAL 2,207,575
' PUMP l Filed July 13, 1938 6 Sheets-Sheet 6- F/GJ i,
VVENTOES RALPH E. BOY/ ES @Fmg @nu ZKM/L14 ATTORNEYS Patented July 9, 1,940
UNITED STATES PATENT OFFICE PUMP Ralph R. Boyles and Edward A. Wilhelm, St. Paul, Minn., assignors to Waterous Company,` St. Paul, Minn., a corporation of Minnesota Application July 13, 1938, Serial No. 219,012
o both series and parallel operation. At the same time the apparatus must be physically adaptable to a wide variety of makes and models of automotive truck chassis and it must be compact and simple in construction for purposes of rst cost,
subsequent servicing, and ease of operation in the hands of relatively inexperienced mechanics.
Itis an object of this invention to provide a pump structure having the aforesaid characteristics.
It is a further object of the invention to` provide a, pump of the centrifugal type which may be mounted in a variety of positions on a truck chassis of standard construction.
It is a further object of the invention to provide a centrifugal pump mechanism of the multistage type and a cooperating integrally formed transfer valve mechanism by which the pump may be changed from a position in which the pumping stages are operated in parallel with each other to yield a high capacity at relatively low pressure to a position in which the :pumping stagesare operated in s'eries relation to yield a lower capacity at relatively high pressure.
the stages are operated in series relation and provided with additional passageways and means for the direct introduction of water when the stages are operated in parallelv relation.
It is also an object of the invention to provide a simpliied centrifugal pump construction of the multistage type having a housing whichis composed of only two main portions, and it is a further object of the invention to providesuch a pump mechanism including transfer valve means and passageways in only one of said main portions for the ready conversion of said mechanismirom a parallel to a series pumping arrangement.
It is a further object of the invention to provide a, centrifugal pump of the re engine type having widely spaced outlet delivery channels, together with a priming pump of the positive displacement type and automatic valve mechanisms in said widely spaced channels for the automatic priming of said centrifugal pump.
It is a further object of the invention to provide a series-parallel multistage centrifugal pump composed generally of two housings and including an intake passage, one section of said pump passageways and a transfer valve arrangement in one of said housings, and an outlet passageway v and the other of said pump passageways in the other of said housings, which may be disassembled vmerely by separating said housing sections.
The specification is described with reference to the drawings, in which A Figure 1 is a rear elevational view partly in section of the assembled pumping apparatus.
Figure 2 is a front elevational View partly in section of the assembled pumping apparatus.
Figure 3 is a'transverse cross-sectional view in the direction of the arrows 3-3 of Figure 1.
Figure 4. is a plan view partly in section of the upper haii only of the pump casing and discharge pipe connections, the section being at the level. of the line 4-4 of Figure 1.
Figure 5 is a plan view of the lower half only of the pump housing and inlet pipe connections showing the impellers, impeller shaft and bearing housings in place on the housing.
Figure-6 'is a longitudinal cross-section of the pump and housing along the line 6--6 of Figure 5.
Figure 7 is a fragmentary longitudinal section of the volute of the iirst pump along the line 1-1 oi Figure 5,
Figure 8 is a fragmentary longitudinal section of the second volute along the line 8--8 of Figure 5.
Figure 9 is a longitudinal sectional view in th direction of the arrows 9-9 of Figure 3.
Figure 10 is a. plan View of the lower half of the pump housing and inlet pipe connection of a modification of the invention. f
Figure 11 is a plan view partly in section, of the upper half of the pump housing and outlet discharge pipe of the modified form of the pump shown in Figure 10.
'Figure 12 is a longitudinal section through the volute of the first pumping stage of the pump shown in Figures 10 and 11,'a1ong the line l2-I2 of Figure 11.
Figure 13 is a longitudinal section through the volute of the second pumping stage, along the line iii-I3 of Figure 11.l
Figure 14 is a. longitudinal section through the center -discharge passageway along the line |4-I4 of Figure 11.
Figure 15 is a fragmentaryview of a modified form of lower pump body for use in the pump mechanism shown in Figures 1 through 9.
Figure 16 is a, fragmentary side elevation partly in section of the modified form of lower pump bod-y shown in Figure 15.
The pumping arrangement shown in Figures 1 through 9 inclusive consists generally of a lower unit generally designated I0, which forms the lower pump body and inlet water connection, and an upper unit generally designated 80, which forms the pump body and outlet water connection. i
The lower unit I0 of the pump is preferably a casting as shown in Figures 1, 2 and 5 and is formed with a transverse water inlet passage, generally designated I. By referring to the lefthand portion of Figure 5 it will be seen that this passage begins at portion 2 and then is divided by web |5 into branches I4 and I6. Branch I4 continues unobstructedly to the inlet chamber of the first pumping stage, and thence to the right-hand end portion I3. -Branch |6 runs somewhat parallel to I4 but includes two valves.
At the right-hand end of passage I6, as shown in Figure 5, there is positioned a check valve generally designated 20 which is shown in cross-section in Figure 1. The valve 20 consists of a member 2| which has a through passage 22, and a valve face 23 upon which a valve ap 24 operates. The flap 24 is pivoted in vthe member 2| and as shown in Figure 1, is oriented so as to prevent flow of water in the direction of arrow 25. The entire valve body 2| is made cylindrical on its outer surface and is positioned in a cylindrical opening 26 in the lower pump unit casting I0, as shown in Figure 5.l The opening 26 is covered and the valve body-2| is heldin place by a cover plate 28 which is fastened to the lower pump unit casting by a plurality of cap screws 29. The check valve cage 20 being cylindrical may be rotated in its seat to close passageway I3 in the event of failure of the `va1ve flap 24. Thus during operation of the apparatus if valve ap 24 should fail, the entire cage 20 may be rotated 90 degrees and passageway I3 thus closed off. This closure does not preclude the operation of the pump since water may enter the inlet portion 46 by way of channel i2 and passageway I6 through valve 3|.
'A second cylindrical valve-receiving bore is provided in the lower pump unit at 30 and receives a cylindrical transfer valve generally designated 3|. By referring to 'Figure 2 in which this valve is shown in section, it will be seen that this valve consists of a cage 32 which is formed integrally with a plate 33. The plate 33Vserves to close the lower end of the bore 30 in the housing,
and the cage 32, which is apertured, receives the rotatable element of the valve.
Within cage 32 there is pivotally mounteda valve-body 35 having a plurality of passageways 36 and 31 therethrough, as shown in Figure 5. The valve body isuprovided with a lower stub shaft 39 which is tted into a bearing socket in the lower plate portion 33, and with an upwardly extended. shaft 40 upon which an operating gear 4| is mounted. ,'Ifhe shaft 40 protrudes through a portion 44 of the upper pump housing casting which serves to close the upper opening of bore 30 in the lower pump housing casting.
When the transfer valve generally designated 3| is in the position shown by the dotted lines of y Figure 5, the passageways I6 of the lower pumpv unit I0 communicate with passage 36 of the valve 3|, and through it, directly with the inlet chamber 46 of the second pump stage. valve bodyl 35 is positioned with the passage 36, as shown in Figure 5, water may flow from-passage I2 in the direction of arrow 49, through passageway 36 and into chamber v46. Water may likewise flow in the direction of arrow 50 from passage |3 through check valve 20 into the inlet chamber 46.
The passageway from |2^through I4 to chamvber 45 and from I3 through |4 to chamber 45 is always open and water may therefore flow therethrough unrestrictedly either in the direction of arrow 5| or in the direction of arrow 52.-
The lower pump unit I0 is also provided with a passageway extending from the outlet of volute 66-61 of the first pump stage, which discharges downwardly into the lower housing as shown in Figure 7, to the passageway 31 of transfer valve 3|, and thence, as shown in Figure 6, through another passageway 56 in the lower unit |0. Passageway 56 extends from the transfer valve 3| under the pump shaft center bearing 2|0 and upwardly through opening 58 (see Figures 4, 5
and 6) and then through discharge passageway 59 directly to the discharge pipe |00 of the upper pump -unit 00.
The upper unit 80 of the pump body is provided with a portion 69 of the volute of the second pumping stage, which is continuedA around at 10 in the lower unit I0, and then through opening 1|, through passage 12 in the lower pump body and into discharge pipe |00, all as shown in Figure 8. The lower pump unit I0 and inlet pipe casting isA provided with a plurality of integrally formed bed plates 6| and 62 which are spaced apart so as to be adaptable to standard frame widths of automotive vehicles, as illustrated in Figure-1 wherein the frame of the automotive vehicle upon which the pump is mounted is shown in section at 63 and 64. y
As just' explained the upper pump body generally designated 80 comprises passageways which cooperate with those in the lower pump body to form the'volutes of the rst andsecond stages of Athe pump and with a discharge passageway |00 which is positioned so as to be directly above and generally parallel to the inlet passageway of the lower .pump body I0. 'Ihe upper pump body 80 is also provided with a portion 44 which extends to the right, as shownv in Figure 2, so as .to overlie and form a cover for the cylindrical transfer valve opening 30 in the lower pump body |0. The upper and lower'pump bodies when bolted together by bolts 9 form a unitary structure which'may be positioned with the inletand outlet passageways arranged transversely on an automotive chassis. Y
The outer passageways l2 and |3 of the inlets of.the lower pump body |0 are provided respec-I tively with inlet connections 15 and 16 which are Vclosed at the ends with easily removable screw Thus when tion of arrows |01, the check valve element |06 is swungupwardly out of the path of the flow. However, when the pump is not in operation the check valve elements |06 fall downwardly under their own weight into contact with the plate valve seat |04 and a vacuum may thus be drawn in the discharge pipe |00 and in the pump passageways for priming purposes, as will be explained in greater detail hereinafter. 'I'he outer portion of member |05 is formed with a flange I 0 to which is bolted a cutoff valve I I I which may be of any suitable construction. A valve is provided at each discharge end of pipe |00 so that the owfrom the pump may be directed in one or the other, or both directions, and the ow in either direction shut off at will by means of the valve.
By referring to Figure 3 it will be noted that the lower unit I0 of the pump body is provided with a web portion II5 at one side and with a second web portion ||6 at the other. side of the pump. These webs terminate in face plates II1 and I I8.- Web |I1 receives abearing structure as shown at the left side' of Figure 3 and generally designated |20. Web 8 receivesgear housing, generally designated |50, and bearing structure generally designated |2| shown at theright side of Figure 3.
The bearing structure generally shown at |20 comprises a barrel |22 having a flange |23 throughout a portion of its circumference, as shown in Figure 2. The flange v|23 is attached to the face plate ||1 by a plurality of bolts |24. The barrel portion |22 is provided with ayball bearing |25, an end cap |26 and a greaseseal |21. The bearing |25 is thus enclosed in a grease-tight housing. The portion |28 of the barrel which extends toward the pump body is internally threaded to receive a gland collar |30. Collar |30 is threaded at |3| and provided with a gear portion at |32. In web ||5 there is mounted a shaft |33 which carries a worm gear 34 which cooperates with the gear portion |32 of the gland nut and as the shaft |33 yis rotated gland |30 is likewise rotated, and due to the threaded connection at |3|l theg.. ad is moved longitudinally on the pump shaft. In this way it is possible to vary the pressure upon the packing |35. At the opposite end of the pump shaft |40 there is provided ,a somewhat similar housing'-` generally designated I2I which in this instance has an extended barrel portion I4| which passes through the gear housing |50. The barrel |4| supports two ball bearings |42 and |43 on shaft |40. The barrel I4| is provided with a greaseretaining. ring |44 and with a Vgrease-tight cover plate |45 which is attached to the structure by means of bolts |46, and is also provided with a 00 gland nut arranged similarly to that described above with reference to th barrel |20, which' serves toA regulate the press e on packing |41.
' The gear housing generally designated |50, which is mounted between the face plate I|8 of `the pump vstructure and theflange |48 of bearing housing |2| is provided With a shaft |5| which is fitted for connection in the drive shaft line of the automotive vehicle upon which the pumping unit is mounted. The shaft |5| is, car-- ried by bearing |52 and by a pilot bearing |53 which is carried in the end of a second shaft |54,
' also mounted in the housing on a pair .of ball bearings |55. The shaft |5| is provided with a. lsplined portion |56 lupon which there isfslidably mounted a correspondingly. internally splined.;
. ferent diameters.
,shift gear |51 which is arranged to be moved from the position shown in Figure 3 to any of the dotted line positions |58, |59 or |60 by means of a shift fork, a portion of which is indicated at |63. The shifting fork is arranged to be oper- `5 ated by a gear shift unit |64 shown in Figure 1 as being mounted at one side of the gearing housing |50. Shafts I5I and |54 are provided with suitable grease seals at |60 and |69 respectively. 10
'I'he housing |50 is also provided with an idler gear |10 whichis mounted by means of ball bearings |1I upon a fixed shaft |12. As shown in Figure 9, the gear |10 is of such a diameter that it meshes with a gear |15 which is mounted l5 between bearings |42 and |43 upon the pump shaft |40. 'Ihus when gear |51 is in the position shown by the full lines in Figure 3 power from shaft |5I will be transmitted through gears |51 and |10 to gear |15, and the pump shaft |40 20 will accordingly be rotated.
The housing |50 is also provided with another idler gear pair which is composed of an integrally formed unit of two gears of slightly dif- This gear pairis mounted be- 25 low and to one side of gear |51 as shown in Figures 2 and 9.l One of the gears of the pair meshes with slide gear |51 (when the latter is in position |58, Figure 3), and another of the gears of the pair meshes with a gear |8| (see Fig- 30 ures 2 and 9) on the drive shaft of the priming pump, generally designated |85.
The priming pump consists of a casing |86 in which there is mounted a pair of intermeshiug pump gears |81 and |88 whichv are fitted so as to 35 rotate in contact with the interior of casing |86 as is well known ih the art. The housing |86 is provided with an end plate |90 which is attached to the priming pump housing by means of screws |9I. 40
The priming pump |85 is provided with an inlet.. connection |94 which communicates with the main pump outlet pipe |00 (see Figure 6) at flange |95 as shown in Figure 2.
The gear pair |80 is positioned in the housing 45 |50 so as tobe engaged by gear |51 when in the position |58, but to be out of engagement with gear |51 when the latter is moved to position |59. It will be noted that in position |59 gear |51 is just out of contact with gear |98 which is 50 carried by shaft |54. When gear |51 is in the position |60 gear |90 fits neatly into the internal splines |99 of gear |51 so that power will be transmitted from shaft |5| to |54.
VThe gearing arrangement in casing |50 thus 55 i has four operating positions. First, when the gear is in the position shown by the full lines in Figure 3, power will, as previously explained, be transmitted from the shaft |5| to .'the main pump shaft |40. Second, when -the gear |51 60 is in the position |58, power will be transmitted from shaft |5| through gear pair |80 to the priming pump generally designated |85. Third, when thevgear I 51 is in the position |59, shaft |56 is disconnected from both the priming pump 65 and the main pump and alsofrom the automotive drive shaft |54, or is in neutral. Fourth, when the gear |51 is in the position I 60 power will be transmitted from shaft 5| to the drive shaft |54 of the automotive vehicle. 70
The main pump body, as previously explained, is divided into a lower casting generally designated I0, and an upper casting generally designated 80. However, certain of the pump parts are integral throughout their upper and lower 75 y ow of water thus portions. Thus there are provided nosings 200 and 20| which surround the shaft |40 and are adapted to be carried by the split upper and lower housings. Similarly the wear rings 202, 204, 206 and 208 are integral throughout their circumference as is also the center bearing structure which consists of a center housing block 2|0 and insert 2| The block 2 i0 is provided with passageways 2 I2 into which grease may be forced after pumping water through a connection not shown. 'In assembling the pump structure the nosings 200 and 20| are fitted onto the shaft along with the impellers 2|5 and 2|6, the center housing core 2|0,-2|| and rings 202, 204, 206 and 208. The housing is then closed and the center housing core rings and nosings are supported so that slight clearances are maintained between the stationary nosings and the rotatable shaft |40 and between the stationary rings 202, 204, 206 and 208 and the rotatable 'impellers 2|5 and 2|6 adjacent them. This construction is desirable for simplicity ofA manufacture, ruggedness and ease of assembly.
After the pump structure shown in Figures 1 through 9 has been mounted on an automotive vehicle and the necessary mechanical connection made between the drive shaft of the vehicle and the shaft |5|, the pump may be placed inoperation as follows:
Either or bothof the caps 11 are removed and inlet hose connections are made to a source oi' water, such as a fire hydrant, or to a reservoir. Outlet hoses are then connected to one or both of the valves During idle periods the pump is always maintained dry so as vto preclude damage due for instance to freezing conditions, and it is therefore necessary to prime the main pump. When water under pressure is available as atal fire hydrant, water is forced `to the pump butwhen a reservoir or other source is used the pump.
must be primed as follows: Gear shift mechanism |64 is manipulated, first to move the gear |51. out of engagement with gear |98 and into engagement with the gear pair of the priming pump. The engine of vthe automotive vehicle is then speeded up and the priming pump draws air out of the discharge pipe |00 of the main pump and through the communicating pump passageways back to the intake. At this time' check valves |06 are both closed as shown in Figure 2, and air is vthus prevented from entering the main discharge pipe 00 from the hose line or lines which may be attached to the valves lli. The vacuum is thus drawn in the main pump discharge and communicating passageways through the passageways to the inlets |2| 3 through inlet connections 15-16 and to the supply hose, and water is accordingly elevated from the reservoir and the pump is filled. The automotive engine is then idled and gear |51 is moved from the position |58 in which it was in operating connection with gear pair |80 to the position shown in Figure 3. During this time the water which has been drawn into the pump passageways and discharge pipe |00 is maintained in place due to the action of check valves |03 which served to hold the vacuum produced in the system by priming pump |05;`
After-the gear |51 has been shifted to the position shown in Figure 3 the automotive engine is again accelerated and impellers 2|5 and 2|6 are thereafter effective to draw water through the inlet passageway |2V|3 into the pump and discharge the water into the outlet passageway |00. The produced lifts the valve aps |06 and the water is discharged through gate valves to the discharge hoses.
'For parallel operation the transfer valve is rotated by means of hand-wheel 224 which operates through gears 220 and 4| (see Figures 1 and 2) until the valve passageways 36 and 31 are in the positions shownby the dotted lines of Figure 5. In this position passageway 36 connects the passage |6 and inlet chamber 46 (see Figure- 5) and passageg31 connects passage 55 with passage 56 (see Figures 5 and 6). The inlet supply is then by way of passageway I2 and water may flow directly along the path of arrow 5| to the inlet chamber 45 of the first pump stage and may also ow in the direction of arrow 49 to the inlet chamber. of the second pump stage. If the inlet supply should be through passageway I3 water may ow directly in the direction of arrow 52 to chamber 45 of thefflrst pump stage and through the check valve generally designated 20 and in the direction of arrow 50 to chamber 46 of the second pump stage.
Under these conditions the discharge from the volute 66-61 of the first pumping stage is by way of passageway 55, passage 31 in the transfer valve 3|, thence through passage 56, as shownv in Figure 6, through 58, and v thence directly -through passage 59 to the discharge pipe |00 in the upper pump body 80. At the same time discharge from the volute 69-10 of the second stage (see Figures 5 and 8) is directly upward through opening 1| and through passage 12 to the discharge pipe |00. Thus with the transfer valve 3| in the position shown by the dotted lines in Figure 5 the `first and second pumping stages operate in parallel and the-pump mechanism delivers a maximumof water ai; a predetermined pressure.
For series operation the transfer valve 3l is again shifted by means of hand-wheel '224 until passages 36 and 31 are moved to the positions` shown by the dot-dash lines of Figure 5. Passage 36 in the transfer 'valve cylinder will then communicate from the discharge 55 of the flrst'pumping stage: to the inlet chamber 46 of the second pumping-stage. At this time the short curved passage 31 of the transfer valve-is idle. The transfer valve in this latter position thus has the effect first, of blocking the ow from the inlet |2 in the direction of arrow 49 directly to the inlet chamber 46 of the second pumping stage, and second, of interrupting the flow from the discharge passage 55 through the passage 56 of the lower pump body through opening 58 and passage 50 (Figures 10 and 1-1) to the main discharge pipe |00. Underthese conditions series operation of the pump ensues as follows:
Water is drawn into the chamber,45 of the first pumping stage either. in the direction of arrow 5| from inlet passage |2 or infthe direction of arrow 52 from inlet passage I3, depending upon to which side of the machine the inlet hose is connected. The .ow then proceeds throughchamber 45 through the impeller 2|6 to the volute. 66--'61 (see Figure 7) of the first stage,-thence through passageway 55 in the lower pump body through transfer valve passage' 36 (which'is in the position shown by the dot-dash lines of Figure 5) and thence tothe inlet chamber 46 of the second pumping stage. From this point the water is delivered by impeller 2|5 to the volute 69-10 (see Figure 8) of the secondv pumping stage through opening and passage 12 to the main outlet pipe |00. Under these conditions the ,pumping apparatus delivers a maximum pressure with a comparatively smaller ow. At this time also it lwill be noted that pressure is de- 7| a d thence directly upwardlyh() veloped in passageway I6 between the transfer valve and the suction check valve 20 (see Figure 5), and as a result the gate 24 of the check valve 20 is forced shut against the valve face 23 .with the result that back flow into the inlet passage I3 from the inlet of the second stage is prevented.
Whenever desired, the transfer valve 3| may be changed from the position in whichthe pumping stages operate in parallel to the position in which they operate in series, merely by rotating gear 4| (see Figure 2) by means of Worm gear 220 which is mounted upon shaft 22| (see Figure 1). The shaft 22| is pivotally mounted in upstanding lugs 222, formed as an integral portion of the upper pump body 80. Shaft 22| is also provided with an extended portion 223 and a hand wheel 224 so that it may be operated conveniently from one side of the automotive vehicle.
In the device shown in Figures 1 through 9 Water from inlet port I3 may reach the inlet chamber 46 of the second pumping stage through lthe check valve generally designated 20 and passage |6, and to a limited extent flow may-occur from I3 along arrow 52 to and through the inlet chamber of the first pump stage then through I4 oppositely to arrow 5| around the end of web I5 then in the direction of arrow 49 through I6 and 36 again to the inlet chamber 4.6. However this flow is negligible due to the shaping, the passageways and the tortuousness of the path. In the modification shown in Figures 11 through 13 this path has been eased by adequately sizing the passage I4 to accommodate the flow to both pump stages and-by omitting sharp bends. As a consequence flow to the second pumping stage is provided only through the transfer valve 3| and the branch I6 and check valve 20 of therst modication (see Figure 5) are accordingly omitted.
portion of the flow may continue in the direc- .f
tion of arrow through passageway 36 of the transfer valve 3|, to the inlet chamber 46 of the second pumping stage. It will be recalled that in the first modification the flow 50 was directly from the inlet -passage |3 through the check valve 20 to the inlet chamber 46 but in the second modification the inlet flow to the chamber 46 is first taken transversely of the pump and' thence around through the transfer valve t0 the inlet chamber 46. This modification of the invention is otherwise similar tothe first modification, shown in Figures 1 through 9, except `lfor slightly different' shaping of passageway |00, as shown in Figure 11 and of the transfer passage 56 from the vtransfer valve 3| through open` ing 50 and passage 59 to the discharge pipe |00, as will b'e seen by comparing Figure, 14 and Fig- `ure 6. In Figure 14 the center bearing portion lis of reduced diameter' as compared with that' shown in Figure 6. l
In both of the modifications the transfer passage 56 and the transfer valve 3| are located in the lower half of the vpump body. By thus locating those elements of `the mechanism we have been ableto achieve a much smaller overall height of the pump mechanism and a. much more compact and easily accessible pump than in previous mechanisms of this type.
In Figures 15 and 16 there is illustrated a modified form of lower unit for use in the pump shown in Figures 1 through 9. In this modification the web 250 which divides passages I4 and I6 is extended out to the flange end of inlet I3 and the check valve is likewise moved out to the new position as shown at 25|. The inlet gooseneck pipe 252 is provided with a web 253 which terminates in a valve seat portion 254 against which valve 25| seats. The valve 25| is pivoted upon pintle 255 which is in turn supported from the gooseneck inlet casting 252.
It is obvious that many modifications may be made without departing from the spirit of the invention herein described and claimed as follows:
1. A two-stage centrifugal pump comprising a rotary member having first and second stage impellers in spaced relation thereon, an axially divided housing having upper and lower sections,
said housing being formed with an inlet to each impeller in said lower section, andwith first and second volutes part in each section for the first and second impellers respectively, including an outlet passageway in the upper section communicating directly with the second volute, a discharge connection from the first volute to said outlet passageway, said discharge connection being located between the volutes in said lower section, a second inlet to the second impeller, said inlet also being in the lower section, and valve means in said lower section for transferring the fiow from the first volute into the discharge connection or into said second inlet connection.
2. A two-stage centrifugal pump comprising a rotary member having a first and second impeller in spaced relation thereon, a housing for said rotary member and impellers, said housing being divided axially into upper .and lower sections and including intakes and spaced first and.
second volutes for said spaced first and second impellers, respectively, a discharge passage for parallel operation of said impellers, said passage being in the lower housing section between the spaced volutes and beneath said rotary member, an outlet pipe formed on said upper hous- 3. A multiple stage centrifugal pump system 'l adapted for mounting upon an automotive chassis for fire engine service, comprising an open-ended water inlet manifold, an open-ended water outlet manifold of a length substantially corresponding to that of the inlet manifold arranged substantially parallel with and above the outlet manifold, a pump shaft having primaryand secondary imlpellersin spaced relation thereon mounted between said manifplds and in a plane which is substantially at right angles to the manifolds, a pump housing including an intake and discharge volutefor each impeller arranged between said manifolds, said housing being divided into upper and lower portions along a. plane passing through the .said pump shaft, the lower housing being u the discharge volute of the first impeller to the second branch passageway and a transfer valve located in the lower housing for closing the second branch passage from" the intake manifold to the secondary impeller and for directing the flow` from the discharge volute of said primary impeller to the branch passage of the secondary impeller.
4. A multiple stage centrifugal pump system adapted for mounting upon an automotive chassis for nre engine service, comprising an open-ended ,water inlet manifold, an open-ended water outlet manifold of a length corresponding to that of the inlet manifoldl arranged substantially parallel with and above the outlet manifold, a pump shaft having first and second impellers in spaced relation thereon mounted between said manifolds and in a plane which is substantially at right angles to the manifolds, a pump housing including an intake and a discharge volute for each impeller arranged between said manifolds, said housing being divided into upper and lower portions along a plane passing through the said pump shaft, the lower housing being formed with a direct passageway between the intake'manifold and the intake of one of the rst impeller and with a discharge'passage from that impeller to said outlet manifold, saidlower housing also being formed with a branch passageway from the intake manifold to the intake of the second impeller, and a manually controlled valve in said lower housing for simultaneously controlling ow sageway to the second impeller and interrupting' the flow from the intake manifold .through said branch passagewayto the 'second impeller.
5. vA two-stage centrifugal pump system adapted for mounting upon an automotive chassis vfor -fire engine service comprising an open-ended water inlet manifold and support, an open-ended' water outlet manifold of a length corresponding to said inlet manifold length and arranged `sub stantially parallel with and above the outlet manifold', a'pump rotor having first and second impellers thereon arranged between the manifolds and at an angle thereto, a housing includand passageway means and tran ing an inlet for the impellers and with downwardly and upwardly discharging volutesfor the first and second impellers respectively, said housing being divided into upper an lower sections, r valve means in said lower section for in one condition directing ow from the downwardly discharging volute of the first' impeller to the' outlet manifold and for directing uid inflow from fthe inletmanifold to the inlet of the second impeller, and in another' condition for interrupting such inflow and for transferring the ow from thev rst impellervolute to the intake of the second impeller.
6. A multiple stage centrifugal pump system adapted for mounting upon an automotive chassis for re engine service, comprising an open-ended water inlet manifold, an open-ended water outlet manifoldof a length substantially corresponding to that of the inlet manifold arranged substantially parallel with and above the outlet manifold, a pump shaft having ,primary and secondary impellers in spaced relation thereon mounted between said manifolds and in a plane which is substantially at rightangles to the manifolds, a pump housing including an intake and discharge volute for each impeller arranged between said manifolds, said housing being divided into upper and lower portions along a plane passing through the said pump shaft, the lower housing being formed with a direct passageway between the intake manifold and the intake of the primary impeller, a Abranch passageway from the intake manifold to the intake of the secondary impeller, said lower housing also being formed with a transfer passage from the discharge volute of the first impeller to the branch passageway and a transfer valve located in the lower housing for closing the branch passage from the intake manifold to the secondary impeller and for directing the flow from the discharge volute of the vsaid primary impeller to said branch passage of the secondary impeller.
7. A multiple stage centrifugal pump system adapted for mounting upon an automotive chassis for re engineservice, comprising an open-ended water inlet manifold, an open-ended water outlet manifold of a length substantially corresponding to that of the inlet manifold arranged substan-L tially parallel with and above the outlet manifold, apump shaft having primary and secondary impellers in spaced relation thereon mounted be, tween said manifolds and in a plane which is substantially at right angles to the manifolds, a pump housing including an intake and discharge volute" for each impeller arranged between said manifolds, said housing being divided into upper` and lower portions along a plane passing through the said pump shaft, the lower housing being formed with a direct passageway between the intake manifold and the intake of the primary impeller and with first and second branch passageways from the intake manifold tothe intake of the secondary impeller, a check valve in the, rst said branch passageway, said llower housing also being formed with a transferI passage from the discharge volute of the lfirst impeller to the second branch passageway and atransfer vvalve located in the lower housing for closing the second branch passageway from the intake manifold and the secondary impeller and for directing the iiow from the discharge volute of said primary impeller to the branch passage of the secondary impeller, said checkvalve being carried by a cylindrical valve cage positioned transversely of said first branch passageway, said cage being/rotatable to close off said passageway in the eventbf failure of the check valve.