US2139379A - Interchangeable turbine pump head - Google Patents

Description

T, G, MYERS Dec.` 6, 1938.

INTERCHANGEABLE TURBINE PUMP HEAD 6 Sheets-Sheet l Filed Oct. 1934 ATTORNEY De. 6, 1938. I G; kMYERS 2,139,379

INTERCHANGEABLE TURBINE PUMP HEAD Filed Oct. 6, 1934 6 Sheets-Sheet 2 Dec. 6, 1938. T. G. MYERS INTERCHANGEABLE TURBINE PUMP HED Filed oct. 6,. '1934 e sheets-sheet s o/)yaaz @eng/zy VENTO/e ,4 TTORNEY Dec. 6, 193s. T G, MYERS 2,139,379

INTECHANGEABLE TURBINE PUMP HEAD Filed Oct. 6, 1934 6 Sheets-Sheet 4 62 l I/ l l" l 'it f um y l Dec. 6, 1938.

Patented Dec. 6, 1938 INTERCHANGEABLE TURBINE PUMP HEAD Thomas G. Myers, Los Angeles, Calif., assigner to U. S. Electrical Motors, Inc., a corporation of California Application October 6, 1934, Serial No. 747,196

7 Claims.

This invention relates in general to vertical rotary pumps and relates in particular to improvements in driving and adjusting means for pumps of this character. The invention is es- 5 pecially adapted for use with pumps of this general' character known as deep well turbines which, in accordance with accepted practice, include a discharge column having a pump mechanism at its lower end and a discharge head at its upper .l end supporting a power or driving means such as an electric motor. From the driving means a shaft extends down through the discharge column to the pump mechanism and supports rotary impellers in operative position therein, the pump shaft, impellers, and hydraulic load when the pump is in operation being generally carried by thrust bearings supported in the upper part of or above the discharge head.

As is well known in the deep well pump art, an adjustmentmeans is provided between the thrust bearing and the shaft whereby the shaft may be moved vertically to change the position of the impellers relative to the pump bowlsor castings in which they operate, and it is recognized that highest eiliciency in the operation of the pump is obtained only when the impellers are properly axially positioned, and that the adjustment o'f the pump shaft must be such as to compensate for the elongation or stretch of the shaft when the hydraulic load is placed thereon. In the known construction a preliminary vertical adiustment of the pump shaft and of the pump impellers may be made while the shaft is stationary, and this preliminary adjustment can be only approximate and in accordance with the computed elongation when the hydraulic load is applied to the shaft when the impellers operate to force water upwardly through the discharge column of the pump. The present invention comprehends a means whereby the shaft may be adjusted vertically while the pump is in operation so that while the shaft is elongated, the impellers may be brought into positions relative to the pump bowls ywherein they will produce highest operat- 5 ing efficiency as may be determined from a comparison of power consumption and water delivered during various positions of axial adjustment of the impellers.

A further object of the invention is to provide a pump in which the bearing' structure carried above 'the pump head is rigidly secured to the pump head and accurately aligned therewith as the result of the cooperation of the structural parts and in such a manner as to avoid necessity for adjustment, which is often difficult, and it is a further object of the invention to provide a common lubricating means for the bearings of the bearing structure, together with an improved and simplified means for adequately circulating the lubricant continuously through the bearing parts while the pump is in operation.

A further object of the invention is to provide a pump head including a vertical motor so made that the motor may be replaced without removal of the bearing structure. The power required for operation of a pump of this character varies with the volume of water pumped and the lift, or height through which the water is raised. My invention makes it possible to conveniently and at minimum expense replace part or all of the active motor parts of a pump with those of another size to meet changed power requirements. It is a feature of my invention that the discharge head and motor bearing structure may be employed with motors of different capacities.

The characteristics of driving motors of the type employed on vertical pumps depend upon and vary with the diameter of the stator lamina tions and the length of the stack of laminations employed. To make it possible to change the active motor elements of the pump with minimum expense and labor, the invention has for an object to provide a stator shell which may accommodate stators of different lengths and diameters, and it is a further object to provide a motor structure having bearing means adapted to support or accommodate rotors of different power capacities.

A further object of the. invention is to provide a pump structure in which the discharge head and hearing structure may be employed with driving motors having stator shells of different lengths in accordance with the different capacities of such motors.

A further object of the invention is to provide a construction in which all of the driving motors used in combination with a single discharge head will have4 equivalent dimensions as far as the pump structure is concerned.

It is a further object of the invention to provide a pumphaving. a driving motor which may be used in the open and which has means for protecting it from the varying weather conditions encountered, to provide simple and eiective means for the adequate dissipation of heat from the motor and for ventilation thereof, to provide means for increasing the rate of heat dissipation from the motor laminations, and further to provide a motor having a stator which may be removed for the purpose of drying the same without disturbing the rotor or supporting means therefor. f'

It is a further object of the invention to provide a motor having a rotor structure which is improved and simplified and which has'improved electrical characteristics.

It is still another object of this invention to provide a driving motor, of the type disclosed, wherein means are provided whereby the pump shaft may be disconnected from the driving motor when operating conditions arise under which the pumpshaft is vertically supported by means other than the bearing structure provided for that purpose, or when the torque transmitted by the driving motor to the pump shaft exceeds a predetermined value.

Further objects and advantages of the invention. will be made evident throughout the following part of the specification.

Referring to the drawings, which are for illustrative purposes only,

Fig. 1 is a vertically sectioned view of a preferred embodiment of the motor and bearing structure forming a part of my invention.

Fig. 2 is a partly sectioned side elevation showing the discharge head pf my invention on which the motor of Fig. 1 is supported.

Fig. 3 is a vertically sectioned view showing an alternative rotor construction in which inserted rotor bars project so as to form air circulating fans.

Fig. 4 is a partly sectioned side elevation of a driving motor and bearing structure in which circulation fans and air intake and discharge means are disposed at both ends of the motor.

Fig. 5 is a partly sectioned elevational view of a driving motor and bearing structure similar to that of Fig. 4 and having drip-proof air discharge apertures in the stator shell.

Fig. 6 is a sectional view illustrating a variation in the form of rotor shown in Fig. 3.

Fig. '7 is an enlarged fragmentary detail view showing my improved rotor bar which is of particular utility in the type of motor disclosed herein.

As shown in Fig. 1, my invention includes an electric motor having a rotor 3 and a stator 2 which is supported in concentric relation upon a pump head 88, Fig. 2, by means of an adaptor ring or bracket 4 which makes engagement with the discharge head 88 and the stator 2 in such a manner that these parts are automatically aligned. The rotor 3 is mounted upon a tubular shaft 6 which is rotatably supported by a radial bearing 1 and a thrust bearing 8, actual connection of the rotor 3 and the shaft 6 being accomplished through use of a hub 9 having a bore I 0 of a size to receive the upper cylindrical surface I2 of the hollow shaft 6 in closely fitting relation, such, for example, as a press fit; and supplementary thereto the hub 3 may be held in place on the shaft 6 by a lock nut I3 having a lock washer I4.

The inner race of the bearing 1 is pressed on a cylindrical surface I5 formed above a shoulder I 6 on the hollow rotor shaft 6. 'I'he cylindrical surface I5 is preferably slightly larger in diameter than the cylindrical surface I2 which lies adjacent thereto, so that the bearing 1 will slide freely across the cylindrical surface I2 to the larger diameter surface I5 where it is held against the shoulder I6 by the rotor hub 3 and the lock nut I3.

An important feature of the present invention is that the bearing structure for carrying the rotor shaft 6, which in turn supports the rotor 3 and the pump shaft 5I, is supported separately from the replaceable motor parts on the pump head 88 in order that, as previously set forth, the motor parts, such as the stator and rotor, may be removed without the necessity of removing the bearing structure or Without the necessity of disturbing the same. .Accordingly, I provide a rotor support housing or quill I1 which projects upwardly into the motor and has a cylindrical surface 1I which contacts the exterior surface of the outer race of the bearing 1, and in which the bearing 1 is vertically slidable. For

preventing the entrance of foreign material into the rotor support housing I1, a cover plate I8 is provided which rests upon a snap ring I3 which may be expanded Within a shallow groove formed within the upper part of the housing I1. By this construction the cover plate I8 is supported well above the bearing 1 without weakening of the walls of the housing I1 which radially support the bearing 1. The thrust bearing 8 is mounted on a cylindrical wall 2| and rests against a downwardly facing shoulder 20 formed near the lower end of the tubular rotor shaft 6. The extreme lower part of the bearing supporting structure consists of a bearing retaining bowl 22 which is secured to the lower end of the housing I1 by means of bolts 23 and has a bearing seat therein consisting of a cylindrical wall 23 and a radial shoulder 24 on which the outer race of the bearing 8 rests. Since the bearing bowl 22 is separable from the housing I1, it may be readily machined to accommodate thrust bearings 8of'different load carrying capacities. This bearing bowl 22, however, when in operative position, is always concentrically aligned with the housing I1 by reason of the fact that it has a concentric cylindrical face 25 which engages a cylindrical face 21 in the lower end of the housing I1, and further includes a radial face 26 adapted to rest against a radial face 28 formed at the lower end of the housing I1.

The rotor support housing I1 and the bearing bowl 22 are supported in a vertically adjustable manner by a ring 33 having an internal thread 32 engaging an external thread 3l formed on the lower part of the housing I1. Ihe adjusting ring or flange 33 has a downwardly facing surface 34 which rests upon a cooperating annular surface 35 formed in the lower part of the adaptor 4. The member 33 is held in concentric relationship to the adaptor 4 by means of a cylindrical shoulder 38 formed on the member 33 in a position to engage a cylindrical shoulder 31 formed on the adaptor 4. If the threads 3| and 32 are very accurately formed, the shoulders 36 and 31 might readily serve as a means for concentrically aligning the bearing supporting structure with the adaptor 4 which is in turn concentrically aligned with the pump head 88. Ordinarily the threads 3| and 32 will not be sufficiently accurate, and in order to insure practical operative axial alignment of the bearing supporting structure with the pump head, the peripheral part of the bearing bowl 22 is so formed as to present a cylin- .drical surface 4I to a cylindrical surface 4l which is concentric with the axis of the pump head 38, since it is formed in the adaptor 4 concentrically mounted on such pump head 88. For practical purposes it may be considered that the adaptor 4 is an operative part of the pump head 83 and that the aligning cylindrical surface 4I is formed on a part of such pump head, and that when the bearing supporting structure is placed as shown in the drawings, it will at all times be properly aligned with the pump head 88.

The angular position of` the adjusting flange 33 relative to the adaptor 4 may be fixed by screws 38 which pass through openings 39 in the member 33 into threaded engagement with the lower wall of the adaptor 4. Rotation of the bearing supporting structure relative to the adaptor 4 is prevented by providing an opening 42 in the adaptor into which the lower end of a bolt 29 may project in a manner to have vertical movement therein. Vertical adjustment of the complete -bearing structure, consisting of the members l1 and 22 and the bearings 1 and 9 carried therein, may be accomplished by rotating the ring 33 while the housing l1 is prevented from rotating by the screw 28, as previously described. This may be accomplished by removing the locking screws 38 and inserting a suitable wrench through one of the apertures 43 in the adaptor 4, which apertures 43' also provide Ventilating passages for the moi ur structure. The ring 33 may be also turned by use of a suitable Spanner wrench adapted to engage openings 39 therein. After the desired vertical adjustment of the bearing structure is obtained, the locking screws 38 may be replaced in selected openings 39 of which there are a sufficient number to permit the ring 3l to be located in such a plurality of angular positions relative to the adaptor 4 that the vertical position of the bearing structure may be adjusted between very narrow limits.

In Fig. l I show a form of rotor 3 consisting of a stack of rotor laminations l l and rings 44, rotor bars 45, lower iin 4S, and internal bushing or wall 41, all cast integrally from the same metal. The material, such as aluminum or aluminum alloys, ordinarily used for rotor bars is not suiiiciently strong to carry high unit stresses. In large motors the rotor may weigh several hundred pounds. The rotor also is subjected to large radial forces due to the magnetic eld produced in the rotor laminations. 'I'his in combination with the small air gap, commonly employed with induction motors, requires that the rotor be rigidly and accurately supported. In my invention I combine the advantage of casting the walls or members 44, 45, and 41 at one operation with a hub sufficiently strong to carry the weight of the rotor and the stresses which are transmitted from rotor to shaft during operation of the motor and likewise to hold the rotor rigidly in axial position. It is quite true that a cast rotor of the character described could be made entirely from the cast metal specified if the length of the bore engaging the shaft of the rotor were sufficient, but in my improved motor construction it is desired to have a hub 9 of reduced axial length in view of the fact that the housing l1 of the bearing structure projects into the rotor so as to hold the radial bearing 1 substantially intermediate the ends of the rotor. I have produced a rotor having these physical characteristics by making the hub 9 separately from cast steel or cast iron and with grooves 49 in the periphery thereof. In the construction of the rotor 3 the hub 9 is centralized within a mold and within the stack of laminations Il. The casting metal is then poured into the mold to form the members 44, 45, 46, and 41, the latter member or wall 41 making interlocking engagement with the circumferentially grooved portion of the hub 9, thereby locking the parts 9 and 41 securely together. At the completion of the casting operation the rotor may be centered in a lathe by means of the external diameter of the rotor laminatlons and the bore of the rotor then ground or finished to desired size. In Fig. 1 an upper fan 49 for circulation of air is shown on the rotor. Although such fain is shown as a separate part secured in place by screws 59, it may' be, if desired, integrally cast with the upper end ring 44 of the rotor.

The upper end of the pump shaft 5| which extends downwardly to the impellers of the pump, not shown, extends through the hollow rotor shaft 6 and is carried by the bearing structure consisting of the radial bearing 1 and the thrust bearing 8. The upper extremity 58 of the shaft 5I is provided with threads 52 to receive an adjusting nut 53 which is adapted to bear against the upper endeof a drive coupling 54 which is placed upon the upper end of the shaft and engages the upper end of the rotor hub 9. The drive coupling 54 is axially centralized with? relation to the hub 9 by interengagement of cylindrical faces 56 and 51 formed respectively on the hub 9 and the collar or coupling 54. In the lower portion of the coupling 54 are vertical holes 60 adapted to be engaged by the upper ends of pins 59 which are mounted in the upper part of therotor hub 9, so as to transmit rotation from the hub 9 to the drive coupling 54 which in turn drives the shaft 5I through a key 6i.

When the pump is initially installed, adjustment of the shaft 5l is accomplished through rotation of the nut 53 on the threads 52, after which the nut is locked in place by means of a screw 55. After the operation of the pump is started, it may be found desirable to change the setting or adjustment of the shaft, which may be accomplished while the pump is in operation, through use lof the adjusting ring 33, as previously described herein. For practical purposes the nut 53, which is described as a preliminary adjusting means, may not be considered an adjusting means but merely as a part of the connection between the shaft 5| and the rotor, for the ring 33 and its cooperating parts are capable of providing a complete vertical adjustment of the bearing structure-the shaft 5 l, and the rotary pump parts connected to the lower end thereof.

The driving pins 59 may constitute a safety device for preventing injury to the shaft 5l or those parts connected to the lower end thereof. To accomplish this purpose the pins 59 are made of such diameter and of such material that they will shear off when transmission of an excess load from the rotor 3 to the bushing 54 is attempted. The pins 59 and the apertures 69 also serve as a disengaging clutch should the shaft 5l be raised relative to the bearing structure so as to lift the coupling 54 from its position of engagement with the upper end of the hub 9 a distance sufficient to withdraw the pins 59 from the apertures 69.

Ample lubrication of the bearings 1 and 8 is assured by the simple and vnovel means provided for circulation of the lubricant. As will be noted in Fig. 1, an oil chamber 62 is provided in the bearing bowl 22 below the thrust bearing 8. Leakage of oil from this chamber through the shaft opening 52a is prevented by a sleeve or standpipe 63 which projects upwardly from the opening 62a to a point above the oil level and in a position concentric with the shaft 5I. A suitable quantity of lubricant may be supplied to the chamber 62 through a lubricant supply tube 64 which is provided with a removable cap 65 and a drain plug 66, the cap 65 being preferably disposed at the level desired for the lubricant within the chamber 62.

The means for circulating the lubricant consists of a pumping means formed in the tubular shaft 6 as follows: The lower portion of the tubular shaft 6 flares upwardly and outwardly from the lower portion thereof to the shoulder I6 so as to form a conical section 61, and this conical section has vertically extending grooves 69 formed thereon, which grooves slope upwardly and outwardly in keeping with the upward and outward slope of the conical section 61. 'Ihe lower end of the tubular shaft 6 projects below the level of the body of oil contained in the cham.- ber 62 so that oil will enter the grooves 69 by gravity. When the motor is operated, rotation of the tubular shaft 6 produces centrifugal force in the oil in the lower ends of the grooves so that the oil is thrown radially outwardly against the upwardly diverging bottom walls of the grooves so that a resultant upward force is produced in the oil which will cause the same to flow upwardly in the grooves 69 to discharge openings 10 leading to the radial bearing 1. Part of the oil discharged from the openings 10 will pass upwardly through the bearing 1, and in the upper portion of .the housing l1 exterior of the bearing 1 lubricant return grooves 12 are provided. From the bearing 1 the oil flows down the interior face of the housing |1 to a lip 13 which has the purpose of deiiecting the downward ow of oil directly into the bearing 8. In the construction shown the bearings 1 and 8 will be continuously supplied with lubricant as long as there is suiiicient lubricant within the chamber 62 to reach the lower end of the tubular shaft 6. A lubricant return aperture 14 is also provided .for the return of lubricant which may be thrown outwardly from the upper end of the bearing 8. Consequently, the motor may be .operated for an extended period of time without the necessity of replenishing the supply of lubricant in the bearing structure.

The tubular shaft 6 may be conveniently constructed from cast steel or cast iron and may have Vertical ribs 16 for reinforcing the conical portion 61 thereof. When oil or other lubricantof a solvent nature is brought into contact with castings of this type, the oil may collect sand and other sediment from the castings, which is harmful to the bearings. In order to prevent contamination of the lubricant, the unmachined surfaces of the rotor shaft and of the lubricant containing housing are coated with a lacquer which is insoluble in oil or ordinary solvents, thereby preventing the oil from picking up foreign substances.

The provision of Ventilating fans 4B and 49 has been previously noted. In the form illustrated in Fig. 1, air is drawn into the motor structure through the opening 11 formed in a cap 5 which is secured to the upper end of a stator shell 82 which surrounds the stator 2 by means of screws 5a. Over the opening 11 a canopy cap 15 is supported by means of legs |31 The blades 49a of the fan 49 extend upwardly and project outwardly over the upper end of the stator winding 18 and downwardly through vertical passages 19 between the vertical wall 8| of the stator shell 82 and the stator 2, the air being finally discharged through apertures 43 in the adaptor 4. The lower fan 46 circulates air over the walls of the rotor support housing I1, the rotor end ring 44, and the stator end turns 83. 'I'he fan 46 thus serves to eliminate the motor hot spot which would otherwise prevail at the bottom of the rotor.

With the type of construction illustrated, space within the rotor is at a premium. It is therefore desirable to avoid the necessity of providing ventilating passages within the rotor or stator laminations. 'I'o obviate this dimculty the stator is provided with radiating ns 84 which are distributed throughout the length of the stack of stator laminations. The fins 84 produce a turbulence in the air blowing over the stator laminations and thereby greatly increase the eiectiveness of the cooling air. The ins also add to the heat dissipating area in contact with the cooling air. I'he radiating tins may be formed by the use of stator laminations which have a greater external diameter than the remaining laminations used in the stator stack. These larger laminations are properly notchedv to provide space for the stator lamination supporting ribs 85 of the stator shell.

The pump structure associated with the power means above disclosed consists of the discharge head 88 shown in Fig. 2, which has an upper annular face 81 for receiving a cooperating face 88 formed on the lower peripheral part of the adapt-or 4. The means for axially aligning the adaptor 4 with the pump head 88 consists of a concentric wall 89 in a position to receive a concentric ange 9'0 which projects downwardly from the adaptor 4. Screws or bolts 9| may be employed to secure the adaptor 4 to the pump head 88. The head I8 has an internal wall 88a forming a discharge passage 88h to which a discharge column 82 for the pump is connected by means of an adaptor 93 which makes threaded engagement at 4 with the wall 88a. 'Ihe shaft 5| is preferably extended through an oil tube 95 which extends from the upper part of the wall 88a down through the discharge column 92 to the pump proper, notshown, this tube 95 having the purpose of protecting the shaft 5| from water and such abrasive materials as may be carried therein and for conducting oil downwardly around the shaft to lubricate the same in accordance with standard practice. The upper end ofthe oil tube 95 projects upwardly through an`opening 95a in the wall 88a and is supported by a packing nut 96 'winch threads thereinto as shown and which bears against a gland ring 91 adapted to compress a body of packing 88 disposed around the upper end of the oil tube S5. Oil may be supplied to the oil tube through piping 99 which connects With the bore of the packing nut 96. The same discharge head 88 may be used in combination with pumps having a wide range of power requirement. The power required by the pump is a function of the rate of discharge and the hydraulic head or lift which will vary with the distance between the operating water level and the level at which the water is discharged. In my invention the head 88 is not only adapted for use with discharge columns S2 of various diameters but is also adapted to receive driving motors of sizes corresponding to the various power requirements which may be encountered. When a pump is originally installed, the water level inthe well may sta-nd quite high, but after the pump has been operated for a period of time, this level may drop so as to increase the hydraulic head against which the pump must lift. To prevent overloading' of the motor it then becomes necessary to replace the power producing parts thereof. In my invention this may be accomplished with a minimum expense and labor for.

the reason that the bearing structure for carrying the pump shaft and the motor shaft is supported directly from the pump head, making it possible to remove the stator without disturbing the rotor and to remove the rotor without disturbing the rotor shaft or the bearing structure in which it is supported.

From the fact that the stator shell 82 has radial and cylindrical faces and |02 which respectively engage cooperating surfaces |0| and |03 on the adaptor 4, it is evident that whenever the shell 82 is secured in place by means of screws |04, it will automatically assume a position of axial alignment with the axis of rotation which has been established for the rotor 3 and the tubular shaft Gaby which it is supported. Therefore, it is assured that the stator 3, which is secured concentrically within the casing 82, Will be held in proper concentric relation to the rotor 3 and that it or other rotors of similar diametral dimension may be readily placed in operating position and in perfect operating alignment on the head 88. The inner edges of the ribs 85 of the stator shell 82 are in axial alignment with the locating shoulders or surfaces I 00 and |02, and the stator laminations 80 are secured in place by means of stator flanges held in place by means of keys I 06 which project into suitable keyways I06a in the ribs 85. The stator shell 82 may support stators of different lengths, the positions of the keyways |0611 being changed accordingly. One size of rotor hub 9 will support rotors 3 of different lengths, thereby making it possible to use the same size of bearing structure, shaft 5|, and drive coupling 54, with a variety of sizes or lengths of rotors 3 and'stators 2.

With a structure such as hereinbefore described, should it be found necessary to change the power capacity of the pump, the stator shell 82, with its enclosed stator 2, and the rotor 3, with its hub 9, may be removed from the remaining structure. This may be accomplished simply by removing the cap 5, after which the nut 53 and the drive collar 54 may be removedfrom the upper end of the shaft 5|, so that the rotor 3 and its hub 8 may be lifted from the upper end of the tubular shaft 6 after the .removal of nut I3. Likewise, the stator 2 may be removed with they stator shell 82 after removal of the screws |04 by which the shell 82 is connected to the adaptor 4. Replacement of the existing active motor parts, such as the stator 2 and the rotor 3, consists of a reversal of the procedure above set forth. Also, when necessary, the stator 2 may be removed and repaired, reconditioned, or replaced, without necessity of disconnecting the rotor 3 from the shaft 5| or the tubular shaft 6. Accordingly, the removal of the stator may be accomplished without changing the adjustment of the rotating parts of the pump. If a top fan is employed without flared blades such as 49a, it will not be neces-k sary to remove the fan. f

In Fig. 3 I show an alternative form of rotor hub |01 which may be satisfactorily used in the practice of the invention, this rotor hub having a cylindrical wall or bushing |01al on which a stack of rotor laminations is placed. The laminations |08 are concentrically aligned by engagement of the cylindrical surface |I4 therewith, and are held against axial movement by a lower end flange II'5, integrally formed with the wall |01a, and a ring I|6 which is secured in place at the upper end of the hub |01 by a weld |I1. In the rotor structure shown in Fig. 3, the casting of rotor bars.45, end rings 44, and cylindrical wall or bushing 41 is avoided. This rotor has inserted bars I08a with upwardly and downwardly projecting ends 0 and I|2 which respectively engage rings |09 andy III. The projecting portions ||0 and ||2 of the bars |08a respectively form upper and lower fans which will serve to circulate the cooling air in a motor Casing such as disclosed in Fig. 1. In the present construction the ends of the rotor bars I08a are shown projecting into annular grooves I|3 in the rings |09 and I I I, wherein they are secured by brazing. The rotor hub shown in Fig. 3 may be readily placed on and removed from the upper end of the tubular shaft 6, so that it will cooperate with the remaining parts of the pump structure in the manner described relative to the rotor 3 of Fig. 1. Y y

In Fig. 4 a modified form of the rotor of Fig. 3 is shown. In this modified form the end rings |09 and I|| are placed comparatively close to the ends of the stack of rotor laminations, and upper and lower fans ||8 and |22 are secured to the outer faces of the end rings I|09 and III. Each of the fans I-| 8 and |22 is shown as conl sisting of spaced rings I I 9 and |20 between which radial vanes |2I are extended.

In the motor construction shown lin Fig. 4, a ventilation different from that ,of Fig. `1 is shown. In this alternative construction of Fig. 4 a deflector plate 11a. is mounted in the cap 5 in a position to direct air into the space enclosed by the fan II8. 'I'his air is then blown directly outwardly by the vanes |2| against the upper end of the stator winding 18. The air then passes over the top of the stator winding and band for preventing entry of moisture into the shell 82 when the motor is used in an exposed location. When the motor is used .in a protected location, the cover band |24 may be removed, and the air allowed to discharge through the openings |23. At this time some of the air from the lower fan |22 will pass upwardly through the vertical passages 19 and out through the openings |23. The construction shown in Fig. 4 is of particular utility with motors of large power capacity or with .those having long stacks of laminations, since in this new construction a large volume of cooling air is permitted to flow across the motor parts.

Fig. 5 shows a rotor 3 embodying the structural features shown in Figs. 1 and 3, in that it has cast rotor bars 45 and cast end rings 44 and lower fan 48, together with a fan 49 of the character previously disclosed in Fig. 1. The lami-Y nations of the rotor 3', tied together by the cast bars 45 and end rings 44, are placed upon the t hub |01, previously disclosed in Fig. 3, and held against the lower flange ||5 by means of an upper ring IIS secured by a weld I I1. The rotor of Fig. 5 may be formed by stacking the rotor laminations on the hub |01 and then welding the ring I6 in place. This assembly may be then placed in afmold, and the rotor bars 45, end rings 44, and fan 46 may be then cast in place. This rotor construction is of particular utility with long stacks of laminations which require a very rigid support, such rigid supporting of the rotor laminations being accomplished without sacricing other structural features desired in the rotor as previously` herein described.

In the motor .shown in Fig. 5, the cover band |24 is provided with louvers |26 pressed or stamped in the wall of such member |24, whereby to provide openings of weatherproof character in alignment with the openings |23 of the stator shell |21. The upper fan 49 produces a downward ow of air through the stator passages 19, and the lower fan 46 produces a ow of air, part of which will pass upwardly through the lower parts of the vertical passages 19 and subsequently out through the louvers |26. Below the fan 46 a deflector plate |25, similar to that shown in Fig. 4, is employed to direct air to the interior or inlet portion of the fan 46.

The construction shown in Fig. 5 permits a large iiow of cooling air to a motor structure which is weather-proof and drip-proof. In other words, water owing down the exterior of the motor will be diverted outwardly by the louvers |26 and therefore will not ow into the motor interior.

In Fig. 5 a rotor and stator of increased length have been shown in use with a bearing structure of the same size as shown in Fig. 1, this illustrating how the power capacity of a pump may be varied by employing active motor parts, such as rotor and stator, of increased length, and by the use of a stator shell |21 of correspondingly increased length, without the necessity of changing the bearing structure which supports the rotatable parts of the pump structure.'

In Fig. 6 I show still another form of rotor employing a cylindrical wall or bushing |01 on the hub to support laminations which carry rotor bars |08a. In the construction shown in Fig. 6, the weld ||1 of Fig. 3 is replaced by a split ring |28 which ts into a groove |29 in the hub 01, and is held in such groove |29 by an inwardly faced circumferential shoulder |30 formed in the upper part of the ring ||6. To assemble the rotor of Fig. 6, the motor laminations are stacked on the hub |01, and the ring ||6 is then forced downwardly with -suiiicient pressure to permit the split ring |28 to be placed in the groove |29. When the pressure is released from the ring ||6, the stack of laminations expand upwardly and carries the shoulder |30 into -a position around the split ring |28 so as to hold the same in the groove |29. The rotor hub |01 may be provided with tapped holes |38 into which I-bolts may be screwed for lifting the rotor. An advantage of the construction shown in Fig. 6 is that the assembled laminations are not subjected to any heat due to welding. It isthus possible to form all of the surfaces of the hub |01, with the possible exception of the cylindrical surfaces |0 of its bore, to their finished dimension prior to the assemblyr of the rotor.

Fig. 7 illustrates a form of rotor bar |08b which is of especial utility in a motor of this character. In order to provide a rigid construction, it is desirable to make the rotor shaft and the rotor supporting structure amply large. It is also necessary to provide an adequate area of iron in the rotor core to conduct the magnetic flux of the motor, and it is necessary to provide an adequate-area of iron in the rotor teeth to conduct a magnetic fiux between the stator and the rotor laminations. At the same time it is necessary to provide rotor bars which will have. an adequate area to conduct the rotor current.

It has been the general practice to form rotor bars in substantially rectangular cross-sectional form. This results in rotor teeth which are tapered and which consequently produce a high flux density at the narrow portions of the teeth. If it is attempted to increase the width of the rotor teeth by the use of deep and narrow bars, then the area of the iron in the rotor core is re' duced. This in turn results in a high fiux density in the rotor core, which is as objectionable as a high flux density in the rotor teeth. These difficulties are obviated by the rotor construction of Fig. 7, wherein the rotor laminations l have slots |35 punched therein to receive the rotor bars |08b. The slots 35 have a relatively narrow slit or mouth |34 into which a narrow portion |36 of a rotor bar |06b projects. The rotor teeth |32 each have a portion |33 between a pair of adjacent bars .|06b of substantially constant width. Thus, there lis no region in the rotor teeth at which the fiux density is concentrated or at which the fiux density has an objectionably high value. The depth of the rotor slots and of the rotor bars is so proportioned that the maximum flux density within the rotor core |3| does not have a high value, and the depth of the slots |35 is so chosen that the maximum flux density within the rotor core is never greater than the flux density in the rotor teeth. In a majority of cases the maximum flux density in the rotor core does not exceed eighty per cent of that in the rotor teeth. The rotor bars |08b may be cast in place, or they may be formed from copper bar stock rolled to the shape illustrated. The narrow outer portions |36 of the rotor bars |08b, which project into the narrow slits |34, are of particular utility as they produce a doublecage effect which increases the starting torque of the motor.

I claim as my invention:

1. In a vertical rotary pump mechanism: an electric motor having a stator and a rotor; a. rotor shaft; a pump shaft; means for connecting the rotor to the pump shaft; a bearing structure for rotatably supporting the rotor shaft and for vertically supporting the associated pump shaft; means forming a bearing housing for said bearing structure; means for detachably securing the rotor'on said rotor shaft; and a supporting member for independently supporting both said stator and said bearing housing said bearing housing being adjustable with respect to the supporting member.

2. In a vertical electric motor adapted to drive a deep well pump and having a frame, a stator and a rotor: a bushing on which the rotor is coaxially secured having a relatively large bore extending therethrough, a tubular rotor shaft secured in said bore near the upper end thereof and extending below the rotor, a hollow mandrel extending upwardly into the bushing, bearing means in the mandrel to support the rotor shaft, a pump shaft extending through the rotor shaft, means securing the pump shaft to the upper end of the rotor shaft so that it will be driven and supported thereby, means associated with the frame to support the mandrel and its supported parts and adjust it vertically with respect to the frame, said means including a sleeve threadedly engaging said mandrel and rotatably supported on said frame, and means on the frame to malntain the sleeve and the mandrel coaxial with respect to the frame.

3. In a vertical electric motor having a frame and a rotor, a quill adapted rotatably to support the rotor and its associated parts, said quill having an annular surface at its lower end and coaxial with the rotor, there being a bore in the frame which the annular surface engages, thereby maintaining the quill and frame coaxial, and means to adjust said quill vertically with respect to the frame.

4. In a vertical electric motor having a frame and a rotor, a quill adapted rotatably to support the rotor and its associated parts, said quill I having an annular surface at its lower end and coaxial with the rotor, there being a bore in the frame which the annular surface engages, thereby maintaining the quill and `frame coaxial, means to adjust said quill vertically with respect to the frame, said means comprising a thread formed on the exterior of said quill and near its lower end, and an interiorly threaded ring coacting therewith rotatably supported on the frame, means to restrain the quill against rotation, means to maintain the ring coaxial with the quill, and locking means for the ring.

5. In a vertical rotary pump mechanism: an electric motorhaving a stator and a rotor; a tubular rotor shaft; means for supporting said rotor in coaxial relation to said rotor shaft; a pump shaft projecting through said rotor shaft to the top of the rotor shaft; means for vertically supporting said pump shaft on said rotor shaft; bearing means for rotatably supporting said rotor shaft; means forming a bearing housing and a lubricant retaining chamber for said bearing means; and means for circulating a lubricant through said bearing means, said circulating means comprising an upwardly diverging conical wall connected to the lower end of said rotor shaft, said conical wall having vertical oil conducting grooves formed on the interior wall thereof, said oil conducting grooves projecting into the body of lubricant retained within Said bearing housing whereby a rotation of the rotor shaft produces a corresponding rotation of the enclosed lubricant and a resultant rise of the lubricant along the oil conducting grooves, there being apertures for conducting the lubricant from the interior of the rotor shaft to said bearing means, the surfaces of said rotor shaft and of said bearing housing in contact with the lubricant being provided with an impervious coating of insoluble material.

6. In a vertical electric motor having a frame, a stator supported by the frame, and a rotor. a support for the frame, a'quill adapted rotatably to support the rotor and its associated parts, said quill having a threaded base, a support for the frame, and arotatable threaded member supported by the support and adapted to engage threads on the quill for adjusting the quill verti- I cally, said support having/'an opening permitting manipulation of the threaded member while the motor is in operation. Y

7. In a rotor structure for a dynamo electric machine, a hub. member, a stack of. rotor laminations, and means for holding the laminations in place with respect to the 'hub member, comprising an elongated bushing anchored to the hub member, and made from cast material differing from that of the, hub member, whereby the hub member may be made from sufliciently strong material to obviate an axial length thereof as great as that of the bushing, the material of the bushing having a greater coelcient of expansion than the material of the hub. whereby they are held tightly together.

THOMAS G. MYERS.

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