Dec. 5, 1939. W. CZARNECKI 2,132,972
ROTARY PUMP Filed Oct. 11, 1937 2 Sheets-Sheet 1 INVENTOR. MA 75-2 CZAZNCK/O BY k Dec. 5, 1939. w. CZARNECKI 2,182,972
ROTARY PUMP I Filed Oct. 11, 1957 2 Sheets-Sheet 2 V v a i, f r
Patented Dec. 5,1939
UNITED sTA'rss ROTARY PURE? Walter Czarnecki, Eddington, Pa, assignor to Eddington Metal Specialty 00., Eddington, Pa, a firm composed of Walter Czarnecki, Sn, Mary Ozarnecki, Nellie Wojsowski, Wesley Gzarneclxi, Stanley Czarnecki, Walter V. Czarnecki, Jr
and Casimer Caarnecki Application October 11, 1937, Serial No. 168,336
. 3 Claims. This invention has to do with rotary pumps of the type commonly employed for the purpose of building up pressure in a fluid fuel that is used with oil burners.
This application is. a continuation in part of the co-pending application of Walter Czarnecki, Serial No. 133,131, filed March 26, 1937, and entitled Fuel supply unit.
vThe present invention has in view as its foremost objective the provision of a rotary pump of a highly improved nature in which a rotor is eccentrically mounted in the cylindrical bore of a housing and which rotor is formed with radial slots in which are positioned vanes. These vanes are designed to be maintained in engagement with the cylindrical bore of the housing and thus slide in the slots as the rotor rotates.
A particular feature of the invention lies in cylindrical rollers, and the slots in which the vanes are received are formed with bottoms that have a curvature complemental to that of the rollers. With this arrangement, friction between the vanes and the cylindrical bore of the housing is reduced to a minimum without a loss in the pressure building-up effects.
Another object of the invention is to provide, in a rotary pump of the character above noted. novel means for effecting a seal whereby escape of fluid from the bore in which it is affected by the vanes is prevented.
.Various other more detailed objects of theinvention will in part become apparent and in part be hereinafter stated as the description of the invention proceeds. 1
The invention, therefore, comprises a rotary i pump including a pump housing 'havinga cylindrical bore in which a rotor is eccentrically mounted, and the rotor is provided with radial slots in which vanes are positioned. Novel means for causing movement of the vanes in the slots to maintain the vanes in engagement with the cylindrical, wall of the bore are provided.
An important feature of the invention is the cylindrical shape of the vanes and the comple- 50 mental shape of the slots in which they operate.
For a full and more complete understanding the invention reference may be had to the following description and accompanying draw-- ings, wherein 011. its-13c) housing ,of a rotary pump made in accordance with the precepts of this invention,
Figure 2 is an enlarged detailed showing taken as a section at right angles to the showing of Figure 1, bringing out the disposition of the rotor in the housing, Figure 3 is a view somewhat similar to Figure 2 developing the end rings for the rotor vanes therein, t Figure 4 is a view similar to Figure 2 of" the modification in which the vanes take the form of cylindrical rollers,
Figure 5 is a detailed sectional view taken at right angles to the showing of Figured,
Figure 6 is a detailed elevational showing of one of the end rings for the modification of Figures 4 and 5,
Figure 7 is a view somewhat similar to Figure 1 of a modified form,
Figure 8 is a detailed view in elevation of the shaft and rotor carried thereby shown in Figure 'I,
Figure 9 is a view developing the elements of the assembly at the end of the shaft of the modification shown in Figure 7 in an exploded relationship, and
Figure 10 is an exploded view somewhat similar to Figure 9 of the packing arrangement at the other end of the shaft Referring now to the drawings, wherein like reference characters denote corresponding parts, the housing for the rotary pump of this invention is referred to in its entirety by the referen e character B. This housing B may be made from any appropriate metal which is machined to accomm'odate the various mechanisms which are shaped portion lllwhich is reduced in diameter as indicated at H, and the portion II is further 40 reduced in diameteras shown at I2, the reduced portion I2 being provided with threads designated l3. Extending throughout the portion i0 is a circular opening or bore l4 which terminates in the shoulder represented at l5. From the shoulder l5, through the portions II and I2, is a circular re'cess IS, the axis of which is out of alignment with the axis of the bore |4.- In other words, the circular recess I 6 is eccentric to the bore ll. v The wall of the portion III is formed with an opening II which is shown in Figure 2 and which establishes communication between the bore i4 and the source of supply of fluid which is to be affected bythe pump. n
A passageway designated |8 extends from the bore l4 to any appropriate point such as the pressure regulating valve illustrated .and described in the above identified co-pending application.-
'screw bolts 22, which extend through openings in the end closure 20 and are screwed into threaded sockets 23 in the main body part B.
The end closure 20 is provided with a cylindrical socket 24 which is eccentric to the axis of the bore l4, that is the axis of the socket 24 constitutes a continuation of the axis of the cylindrical recess l6. Thus, the axes of'the socket 24 and recess l6 are in alignment.
A bushing designated 25 has an outer cylindrical surface which is snugly received in the.
bore l4. It is important to note that the bushing 25 is provided with a cylindrical bore 26, the axis of which is in alignment with the axes of the socket 24 and circular recess l6.
A shaft referred to in its entirety by the reference character S is shown as having one end received in the socket 24- whereby the latter is constituted a bearing for the shaft. This shaft has an enlarged portion at 21 which is received in the bore 26 so that the bearing 25 constitutes a bearing for the shaft S.
In order to prevent longitudinal movement of the shaft S the latter is formed with a flange 4 at 28 and which flange is received in a cut-away pbrtion of the bushing 25 that is shown at 29.
An end bushing designated 30 is fitted in the end of the circular recess |6 within the reduced portion l2, and this bushing 30 is provided with an end fiange at 3| which engages the end of the reduced portion l2.
A cup member 32 has an inner cylindrical wall which is threaded as shown at 33, and this threaded wall 33 is secured onto the threads |3 of the reduced portion l2. The cup member 32 has a bottom 34which is formedwith an opening 35, the axis of which is in alignment with the axis of the circular recess l3. A bearing member 36 is received in a socket 31 which is formed in the bushing 30 and this bearing member 36 has a central bore 38 through which passes the shaft S.
A packing assembly is referred to in its entirety at P and is effective to provide a seal between the shaft S and the bushing 30. Another packing assembly P provides a seal between the shaft S and the bushing 25. A coil spring shown at 39 extends between the packing assemblies P and P respectively, and maintains these packing assemblies in effective position against the bushings 30 and 25.
A similar arrangement for providing seals at similar points in a rotary pump of the same type is clearly illustrated and described in the copending application of Walter Czarnecki, et al., Serial No. 85,908, filed June 13, 1936, entitled Pump, and the specification ofthis patent application is referred to for a detailed description of these packing assemblies.
A passageway is shown at 40 as extending lengthwise through the bushing 25 andis' present for drainage purposes as will "hereinafter be described.
Keyed to the shaft S between the end closure 20 and bushing 25 is a rotor designated 4|; a driving relationship between the rotor 4| and shaft S being established by the key shown at 42.- -The rotor 4| has an outer cylindrical sur-- face designated 43, in which are cut'a plurality of slots 44, the side walls of which are parallel to radii of the rotor; which radii extend between the walls of each slot 44. I
Slidably received in each of the slots 44 are vanes 45 which extend at each end beyond the rotor 4|. Disposed between the rotor 4| and end closure" 20 is an end ring member 46 which end ring member is brought out clearly in Figure 3. This end ring member is duplicated attthe other end of the rotor 4| whereat it is positioned between the extremity of the rotor 4| and bushing 25. Each of the ring members 46 has an outer,
periphery 41 which is snugly received in the bore M, and extending inwardly from this peripheral edge 41 are a plurality of slots 48 which correspond to the slots 44 in the rotor 4|. However, it is notable that each of the slots 48 is wider than the corresponding slot 44, and each of the slots 48 has side edges which are parallel to radii of the bore l4, which radii extend between the walls of the respective slot.
The vanes 45 at each end extend into the slots 48, as shown in Figures 1, and'3, anddue to the slots 48 being wider than the vanes 45, a small amount of relative movement between the extremities of the vanes in these slots 48 in the ring 46 is provided for. It is notable that each vane 45 at all times is in engagement with the bore l4 on its outer edge; and the end portions on the inner edge engage with the bottoms of the slots 48 in the rings 46 at each end.
Provision is made for driving the shaft S in any-preferred manner, as indicated by the flat 49, and when the shaft S is rotated a corresponding rotation is set up in the rotor 4|. Due to' the engagement of the end portions of the vanes 45 with the bottoms of the slots 48 each of the vanes 45 will be maintained in an outermost position with the edges of the vanes 45 in engagement with the bore -|4. Due to the eccentricity existing between the axes of the rotor and the bore M, respectively, the bore- I4 will be effective to force the vanes inwardly in the slots 44 incident to the rotation of the rotor 4|. Assuming that the rotor 4| is rotated in a counterclockwise direction with respect to the showing in Figure 2, it is notable that fluid passing through the openings I! will enter into the space between therotor 4| and the bore l4. The vanes 45 being in their outermost positions with the edges engaging the bore l4 will affect the fluid to build up pressure therein as the shaft ing with reference to a counter-clockwise direc-' tion of the showing of Figures 2 and 3, the pressure of the fluid in this space will obviously inwall of the slot over to the other, so at the time i of maximum pressure on the fluid, which is just at or prior to the time of being forced into the passage l8, the surface of the vane which is forced against the fluid to build up the pressure will be in engagement with the side walls of the slots 48 as shown at 50 in Figure 3.
While the vane and associated pump structure illustrated in Figures 1, 2 and 3 is designed with the vanes and slots of a rectangular cross sectional shape, it is not essential that the vanes be so formed. It is notable that the term vanes" as used throughout this specification is intended to refer to vanes of any shape having the required ability to affect the fluid to build up pressure therein incident to rotation of the rotor in the manner illustrated.
Figures 4, 5 and 6 develop a slightly modified form in which the vanes 5| are cylindrical in shape and operate in complementally shaped slots 52 formed in the rotor 4|. rings 46a will also be formed with similarly shaped notches 53 which are designed to accommodate the cylindrical vanes' 5|.
In actual use the cylindrical blades 5| will probably present a noticeable advantage inherent to their cylindrical formation and mounting which permits them to turn freely. As the rotor 4| is rotated these cylindrical blades 5| will 30 roll over the surface of the bore I4 with a minimum resistance to turning of the rotor.
- Despite the presence of the packing assembly P a certain amount of the fluid fuel being operated on by the pump may escape into the space 35 defined by the circular recess l6. In order to provide for the return of this fluid to the bore H the bushing is provided with the channel 40 which is inclined and opens at its upper end into the pumping chamber defined by the bore 40 I4 and rotor ll. At its lower end the channel 40 opens into the circular recess l8. As the rotor II is rotated a certain amount of suction or partial vacuum is created to draw fluid from the recess l6 and pass it into the pumping cham- 45 her of the bore l4.
Referring now more particularly to Figures '7, 8, 9 and 10 the shaft S is shown as being of a different construction which makes possible the elimination of the seals P and P and the sub- 60 stitution of a highly simplified assembly for accomplishing the same sealing purposes. This shaft 8 is formed with the usual enlarged portion at 21 which is received in the bearing 25. However, the end wall of the bearing 25 which 55 is disposed towards the rotor is formed with a ring-like groove ill in which is fitted a sealing ring 1|.
Adjacent the enlarged portion 21 of the shaft 5 the latter is further enlarged to provide a 90 ring-like flange -12 that bears against the sealing ring 1| and serves to maintain the latter seated in the groove 10. Adjacent to the ring flange 12 the shaft S is reduced in' diameter,'
and keyed thereon is a rotor 13 which is formed with spirally disposed grooves 14 in which operate rotor vanes 45a in the manner above described. It is notable, however, that these rotor vanes 45a will have a shape corresponding to 70 the grooves 14. End ring members 86b may be positioned at each side of the rotor I3 in a manner corresponding to the arrangement illustrated in Figure 1. Due to the spiral formation of the vanes 45a and groove ll the notches 48b in the 75 end rings 46b must be sufflciently wide .to receive Each of the end the extremities of the vanes and allow for lateral play incidentv to rotation of the rotor 13.
It is notable that rotation of the rotor 13 in a proper direction causes the vanes to affect the fluid to urge the latter-in the direction of 5 the ringflange 12, thus creating a tendency to urge this flange 12 against the sealing ring II to maintain the sealed relationship.
This pressure whichis afforded by the fluid during operation of the pump is supplemented 10 to a required extent by an assembly now to be described. The end of the shaft S is formed with a depression 15 that partially receives a ball bearing element 16. This ball bearing element I6 is also partially received in another de- 15 pression ll that is formed in a bearing member 85 being closed by a screw plug 81.
An end closure 88 replaces the end closure 20 and is formed with a portion 89 that is comparable to the portion 2| of the end closure 29. This extension 89 projects into the bore H in a manner above described. However, the end closure 88 differs materially from the end closure 29 in that it is formed with a sleeve-like extension 99 which is provided 'with a bore 9l'that extends through -the end closure including the extension 89.- This bore 9| isthreaded at one end as shown at 92, to receive the plug 88. At its inner end the bore 9| receives the'extremity of the shaft S.
It is evident that the spring 89 exerts pressure 40 on the shaft S through the bearing members 18 and 16 to urge the ring flange 12 against the sealing ring .'II, and this tension may be varied by first taking out the screw plug 81 to afford access to the set screw 84. By using an appropriate tool this set screw may be tightened up or released as occasion demands, to vary the tension afforded by the spring 80.
Referring now more particularly to the sealin arrangement at the other. 'end of the shaft S, it is noted that one part of a packing gland assembly designated 93 is snugly received in the bore l6 and is formed with a bore 94 that receives the shaft S. This member 93 has an end flange 95 that engages the housing B. 65
The member 93 is formed with a packing chamber 96 that surrounds the shaft S and the end portion of the wall of the member 93 which defines the chamber is threaded as shownat 91. An appropriate packing material such as felt is shown at 98 as being packed in the chamber 96; the required pressure being set up by a packing gland 99 that is threaded into the threaded wall 91.
A lock nut shown at I00 is screwed on to the packing gland 99 and serves to lock the same in any adjusted position. From the foregoing it is apparent that the seal P is replaced by the packing gland just previously described, whereas the packing assembly I? is obviated and its sealing functions replaced by the sealing ring II and flange 12 that is formed as a part of the shaft 8.
While preferred specific embodiments of the invention are hereinbefore set forth it is to be clearly understood that I am not to be limited to the exact constructions illustrated and described, because various modifications of these details may be provided in putting the invention into practice within the purview of the appended claims. I
1. A rotary pump of the character described comprising a main body part formed with a bore, said main body part having an extension formed with'a bore that is eccentric to the bore in the main body part, a shaft extending through the said bores, the shaft being eccentrically mounted with respect'to the bore in the main body part, a packing assembly located at the free end of the extension for effecting a seal about the shaft, a bushing in the extension adjacent to the main body part, said bushing being interposed between fthe shaft and the wall of the extension defining the bore, said bushing being formed with a groove on the face adjacent to the main body part, a sealing ring in said groove, the shaft being formed with a ring-like flange engaging said sealing ring, a rotor drivably carried by the shaft and disposed in the bore of the main body part, said rotor having a plurality of spirally disposed grooves, and correspondingly spiralled vanes in said grooves.
2. A rotary pump of the character described comprising a main body part formed with a bore, said main body part having an extension formed with a bore that is eccentric'to the bore in the main body part, a shaft extending through the "said bores, the shaft being eccentrically mounted with respect to the bore in the main body part, a packing assembly located at the free end of the extension for effecting a seal about the shaft, a bushing in the extension adjacent to the main body part, said bushing being interposed between the shaft and the wall of the extension defining the bore, said b'ushing being formed with a groove on the face adjacent to the main body part, a sealing ring in said groove, the shaft being formed with a ring-like flange engaging said sealing ring, a rotor drivably carried by the.
shaft and disposed in the bore of the main body spring. a
part, said rotor having a plurality of spirally disposed grooves, correspondingly spiralled vanes in said grooves, end rings for causing radial movement of the vanes with respect to the rotor, an end closure-for the bore in the main body part, said end closure being formed'with a passageway that receives the extremity of the said shaft, and means carried by the end closure for exerting a pressure on the shaft whereby the ring flange is urged against the sealing ring.
3. A rotary pump of the character described comprising a main body part formed with abore, said main body part having an extension formed with a bore that is eccentric to the bore in the main body part, a shaft extending throiigh the said bores, the shaft being eccentrically mounted with respect to the bore in the main body part,
a packing assembly located at the free end of the extension for effecting a seal about the shaft, 9. bushing in the extension adjacent to the main body'partjsaid bushing being interposed between the shaft and the wall of the extension defining the bore, said bushing being formed with a groove on the face adjacent to the main body part, a
sealing ring in said groove, the shaft being formed with a ring-like flange engaging said sealing ring,
a rotor drivably carried by the shaft and disposed in the, bore of, the main body part, said rotor having aplurality of spirally disposed grooves, correspondingly spiralled vanes in said grooves, end rings for causing radial movement of the vanes with respect to the rotor, an end closure for the bore in the main body part, said end clo-- sure being formed with a passageway that receives the extremity of the said shaft (a spring inthe passageway of the end closure, a bearing assembly interposed between one end of the spring and the end of the shaft, a bearing member associated with the other end of the spring, a plug for the passageway and the end closure, and an adjustable set screw threaded in the plug engaging the last mentioned bearing member and operable to vary the tension afforded by the WALTER CZARNECKI.