US3050012A

US3050012A - Fluid pump

Info

Publication number: US3050012A
Application number: US736934A
Authority: US
Inventors: Arnold E Biermann
Original assignee: Individual
Current assignee: Individual
Priority date: 1958-05-21
Filing date: 1958-05-21
Publication date: 1962-08-21
Anticipated expiration: 1979-08-21

Description

Aug 21, 1962 A. E. BIERMANN 3,050,012

FLUID PUMP Filed May 21, 195e s sheets-'sheet 1 O/SCHAEG STROKE INVENTOR. /P/VOLD E'. BIER/MAIN TTOE/VE YS Aug. 21, 1962 A. E. BIERMANN FLUID PUMP 3 Sheets-Sheet 2 Filed May 21, 195s INVENTOR, APA/010 E /EPMNN Aug. 21, 1962 A. E. BIERMANN 3,050,012

FLUID PUMP Flled May 2l, 1958 5 Sheets-Sheet 3 aj@ INVENTOR.

ATTORNEYS 3,@551Ll2 Patented Aug. 21, 1962 3,95%,912 FLUllD PUMP Arnold E. Biermann, 4579 W. 212th St., Fairview Park 26, Ohio Filed May 21, 1958, Ser. No. 736,934 7 Claims. (Ci. 103-140) (Granted under Title 35, US. Code (1952), sec. 266) The invention described herein may be manufactured and used by or for the Government of the United States of America :for governmental purposes without the payment of any royalties thereon or therefor.

The present invention relates to fluid pumps and more particularly to rotary type pumps that are capable of handling saturated or boiling liquids.

Heretofore, various rotary pumps were available for pumping liquids. In order to provide satisfactory operation, most of these pumps were provided with an impeller of ilexible material, such as rubber. Since these rubber impellers were relatively deformable, prior pumps have been limited to low pressure operations. Consequently, heretofore known pumps' were not adaptable for handling liquiiied gases.

The present invention provides a novel rotary pump that is capable of handling saturated or boiling liquids. In order to accomplish this, a pump must operate satisfactorily with very low suction pressures. The rotary pump disclosed herein is comprised of a plurality of rotatable vanes of novel construction which are pivotally .mounted on a support rim. The vanes have outer and inner portions with the outer portions being of *a greater mass than the inner portions whereby during rotation the outer portions are biased against the outside wall of the pump housing. However, the inner portions of the vanes are greater in area than the outer portions and consequently when the Vanes are not rotating fluid can be forced yfrom the pump inlet to the discharge port without turning the impeller.

It is therefore a general object of the present invention to provide an eiiicient, high capacity pump that is capable of high pressure development.

Another object of the present invention is to provide a durable pump adaptable to be driven directly from -a high speed motor or turbine. p

Still another object of the present invention is to provide a displacement pump lthrough which fluid can be `forced without appreciable restriction when the pump is not in operation.

Other objects and many of the attendant advantages of this invention wil lbe readily appreciated as the same lbecomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings wherein:

FIGURE l is a longitudinal sectional view showing `an embodiment designed for submerged operation;

FIGURE 2 is a sectional view taken on lines 2-2 of FIGURE l;

FIGURE 3 is an enlarged View showing the construction details of a vane;

FIGURE 4 is a diagrammatic view showing the mathematical relationships of an inner surface of the embodiment of FIGURE l;

FIGURE 5 is a view similar to the view of FIGURE 4, but showing a different surface;

lFIGURE 6 is a longitudinal sectional view showing another embodiment designed for non-submergible `operation;

FIGURE 7 is a sectional view taken on line 7-7 of FIGURE 6;

FIGURE 8 is a diagrammatic view showing the mathematical relationships of the surfaces of the embodiment shown in FIGURE 6;

an inner surface 37, and an inlet duct 29 therein whichhas its external surface 3d varia-bly spaced from the inner surface 37 to form a pump annulus 45. A cylindrical rot-or 11 is rotatably mounted within the housing 12 `rby means of bearings 13, whereby it has a center portion y16 within the pump annulus 45. The rotor 11 has a drive shaft 14 `fixed thereto by means of screws 15 and a plurality of longitudinal slots 17 extending through the wall thickness of the center portion 16. A vane 18 having an irregular transverse cross-section is pivotally mounted in each slot 17 -by means' of a pin 19 which has one end mounted in aflange 21 which is part ofthe forward portion of the rotor 11 and the other end mounted in a support rim 22 which is part of the rearward-portion of rotor 11. f n

Referring particularly to FIGURES 2 and 3 of the drawings, it can be `seen that each of the vanes 18 have a bore, which receives the pin 19, between its

vane tips

38 and 39 which substantially divides the vane 18 into a radially outer portion 23 and a radially inner portion 24 of different masses. The radially outerportion 23 is of a greater ymass than the radially inner portion `24, yso that, when the vanes 13 are rotating, centrifugal forces tendto pivot the vanes 18 into a radial alignment along the circular path of the rotor 11. As shown in FIGURE 2, each vane 18 is mounted within the pump annulus 45 so that its outer and inner portions 23 and Z4 are pivoted clockwise from a line, which passes through its mounting pin 25, radial to the circular path of the rotor 11. Thus, rotation of the rotor 11 will cause the radially Vinner portion 24 to urge its surface 31 against the external surface 34 of the inlet `duct 29 and the radially outer portion23 to urge its surface 35 against Ythe inner surface 37 of the housing 12.

In addition, as `shown in FIGURE 3, the effective area of the radially outer portion 23 subject to fluid pressure within the pump annulus 45 is approximately equal to the transverse length B times the longitudinal length of the vane 18 and this is less than the effective area of the radially inner portion 24 subject to iluid pressure within the pump annulus 45 which is approximately equal to the transverse length A times the longitudinal'length of the vane 18. By this means, the r.tluid pressure acting on the vanes 18 control their position. Thus, when the vanes 18 are rotated, fluid pressure acting on vane sur face 35 will tend to pivot the varies 18 around pins 19 in a counterclockwise movement which urges the tips 3S and 39 yagainst the inner surface 37 of the' housing 12 and the external surface 34 of the inlet duct 29, respectively.

The curvature of surface 31 of each vane 18 andthe curvature of surface 32 of rotor bars 33 are similar to that of the external surface 34 of inlet duct 29 at the narrowest position between the inlet duct 29 and housing 12. The curvature of surface 35 of each Vane 1S and the curvature of surface 36 of each rotor bar 33 areV similar to that of the inner surface 37 of housing 12 at the narrowest position between the inlet duct 29 and housing 12. The curvatures of

surfaces

38 and 39 of each Vane 18 are similar, respectively, to' the curvatures of the external surface 34 of inlet duct 29 and the inner surface 37 of housing 12 at the position of maximum `distance between the inlet `duct 29 and the housing 12.

AAs shown in FIGURE l of the drawings, the inlet duct 29 has a flange portion 41 that is attached to housing 12 pumped. Y

ywhich one vane travels when subjected to the full pressure difference between vthe inlets and discharge ports of the pump whenthe vane'moves from the inlet port to the discharge port. The angle of the working stroke is substantiallythe same as the angular distance between 4two vanes. A

The return stroke maybe dened as the angular distance between two vanes at the instant that one vane closes the discharge port from the chamber formed between said one Vane and a preceding vane. The return stroke is substantially the same as the angular distance between two It "can be seen in FIGURE 2 I 4v This gas, if not vented, could cause a vapor lock and a complete breakdown of pumping would occur. However, the gas vent passageway 48 permits this gas to escape through ports 49 communicating with the passageway 4S and the annulus 17 and a vapor lock condition is prevented.

If desired, uid may be forced through the pump from the inlet port 43 to the discharge port 46V Without rotating the rotor 11. This is made possible as previously discussed in reference to FIGURE 2 because the effective pressure area of the radially inner portion 24 is greater than the effective pressure area of the radially outer portion 23. Thus, when the vanes 18 are in the largest portion of the pump annulus 4S and iuid is forced through the'inlet port 43 and against the vanesurfaces 31 which face the inlet polt 43 a greater force will be exerted on the radially inner portion 24 than the radially outer por- Y tion 23 which results in the vanes 13 pivoting clockwise vanes and also substantially equal in length to the working stroke.

` I The inlet stroke is defined as the angular distance between the freturn stroke and the working stroke when the vane moves from the return stroke to the Working stroke. Likewise, the discharge stroke is defined as the angular distance between the working stroke and A,

' fthe return stroke when the vane moves from the worktimes as Vgreat as R and 1.105 times as great as R.

Likewise, as'shown in FIGURE 4 Vof the drawings,` the portions of the external surface V34 of duct 29 thatV lie within the working stroke and the return stroke are arcs of circles. The radius of that portion of surface 34 Within the working stroke is .756R, and the radius of that portion of surface 34 within the return stroke is .896R.

' The overall width of the vanes 18 is .73 1R.

It can be seen, by referring to FIGURE 5 of the drawings, that with portions of contacting surfaces 34 and 37 being arcs of circles, that the vanes 1S are not pivoted on their V-respective pins 19 throughout the working stroke -and the return stroke. Good sealing is provided during 'these strokes as both ends ofthe vanes 18 are in slidable engagement with the surfaces 34 and 37 of the pump annulus. In order to insure proper sealing, it may be desirable to provide a sealing strip 47 to overcome the effects of thermalV expansion or manufacturing errors. Also a gas vent passageway 48 may -be provided for venting olf the gases that-rnay be entrained in the liquid lbeing In operatiomthe pump may be immersed in the liquid being pumped and the drive shaft 14 may be connected directly to either a high speed motor or a turbine. The fluid being pumped passes through passageway 44 of inlet duct 29 and then through the inlet port Y43 into the pump annulus 45. The vanes 18, which are rotating at high speed, have their outer portions 23 Ybiased against the inner surface 37 of housing 12 and the fluid is moved through the working stroke and out the discharge port 46. The vanes I8 then pass through the return stroke to the inlet stroke and the cycle is repeated. During the return stroke, a small amount of liquid may be carried back to the inlet. As the pump may be handling saturated or boiling liquids, the additional heat added about the pins i9 and away from the surfaces 34 and 37 whereby the fluid may be allowed to pass counterclockwise, without appreciable restriction, or out through th discharge port 46.

A second embodiment ofthe present invention is shown in FIGURES 6 8, inclusive, of the'drawings. A nonsubmergible type pump is shown, having a rotor 51 rotatably mounted in bearing plate 52 and frame 53. As shown in FIGURE 7 of the drawings, vanes 54 have hub portions 55 thereon which' are used to pivotally mount the vanes in sections 56 and 57 of the rotor S1.

The pumphousing 5? is provided with an intake duct 59 that discharges into pumpv annulus 61 through intake port 62, The duid being pumped is discharged through port 63.

The dimensions of the various parts are shown in FIG- URE 8 of the drawing in terms of T, which is the dis tance from center 0 to the'cent'er 'of the hub portion 55 of the vane 54. As shown, the external surface 64 of inlet duct 65 and the internal surface 66 of housing 58 are circular, as opposed to the non-circular surfaces of the corresponding parts of the embodiment shown in FIG- URES l and 2of the drawings. As shown in FIGURE 8 of the drawings, the dimensions of the external surface 64 and the internal surface 66 are, respectively, .SZST and 1.166T. However, as shown, these surfaces are not concentric, as the .8251-1 dimension is offset from point 0 in a downward ldirection by an amount of .0672T, and the 1.166T dimension is offset from point 0 in an upward direction by an amount of :05247 and to the right of the centerline by an amount of .030571 The width of the vanes 54 is .73lT, which is Imeasured between the advanced points of contact of a vane with respect to the wall surfaces at the mid-point of the working stroke.

The operationv of the secondV embodiment shown in FIGURES 5-8 of the drawing is similar to the operation of the first described embodiment. The second embodiment has particular advantages in that it s relatively simple in construction and consequently economical to manufacture. Much simplicity is contributed to having the annulus Walls as true circles, and of having them in a nonconcentric relationship so as to provide the desired effect. Also, the manner of supporting the vanes 54 adds to the simplicity of fabrication and assembly.

A third embodiment of the present invention is` shownv in FIGURES 9 and l0 of the drawings. In this embodiment, a rotor 71 is Vrotatably supported in end plate 72 and inlet duct housing 73. The inlet duct housing 73 has an opening 74 that permits uid to enter passageway 75 and a pair of inlet ports '76 and 77 are provided to permit the fluid to iiow into the pump annulus 7S. The vanes 79 and pins 8l are similar to the vanes and pins of the first embodiment shown inl FIGURES 1-3, inclusive, of, the drawings. One main difference between the rstrembodiment shown in FIGURES 1-3, and the third embodiment shown in FIGURESV 9 and 10, is that the latter embodiment completes two cycles for every revolution of the rotor.

The pump annulus 78, which is bounded by the inner surface 32 of the housing 83 and the outer surface 84 of the inlet duct housing 73, is oval shaped and of such contour as to contact both tips of the vanes 79 throughout each cycle. As shown in FIGURE 9 of the drawings, rotor end plate 35 is attached to the rotor bars 86 by means of screws S7, and pins 8l are tted in end plate S5 to position the Vanes 79. A screw impeller 88 is provided on the rotor shaft 89 for assisting in the inlet charging process.

As shown in FIGURE 10 of the drawings, the walls 91 of the pump annulus are made of a wear resisting material having a low coefcient of friction, for example, Teflon or the like. This material is attached to the Supporting metal walls in any conventional manner, such as by cementing. The vanes 79 are preferably made of hard metal and consequently the wear will be on the softer member having a relatively large area.

In operation, the embodiment shown in FIGURES 9 and l0 of the drawings is similar in many respects to the irst embodiment shown in FIGURES l-3, inclusive, of the drawings. The pump is adaptable for being submerged in the fluid to be pumped, and the fluid enters passageway 75 through opening 74 and then passes through

inlet ports

76 and 77 into the pump annulus 78. The vanes 79, which are capable of high speed rotation, pump the iluid out of

outlets

92 and 93.

It can thus be seen that the various embodiments of the present invention are well adapted to provide an efficient high capacity pump. It can also be seen that the embodiments of the pump shown herein provide a displacement pump through which uid can be forced without appreciable restriction when the pump is not in operation.

Obviously many modifications and variations of the present invention are possible in the light of the above teachings. It is therefore to be understood that the invention may be practiced otherwise than as specifically described.

What is claimed is:

l. A rotary Huid pump comprising:

(a) a housing having an inner peripheral surface deiining an internal space within said housing;

(b) an inlet duct iixedly attached to said housing and extending into said internal space;

(c) said inlet duct having an internal passageway therein and an outer peripheral surface;

(d) said outer peripheral surface of said inlet duct and said inner peripheral surface of said housing being mutually eccentric whereby a pump annulus having a variable transverse cross-sectional area is formed;

(e) inlet port means in said inlet duct communicating said pump annulus and said passageway;

(f) discharge port means in said housing communicating with said pump annulus;

g) a rotor rotatably mounted in said housing and having a substantially cylindrical center portion disposed in said pump annulus;

(h) said cylindrical center portion being substantially spaced from said inner peripheral surface of said housing and said outer peripheral .surface of said inlet duct between said inlet port and said discharge means;

(i) a plurality of rigid vanes;

(j) each said vane having a radially inner portion and a radially outer portion;

(k) said radially outer portion of each said vane having a lesser pressure area than said radially inner portion of each said vane; and

(l) means for pivotally attaching each said vane, substantially between its radially inner portion and its 10 said inlet duct is provided with (a) a gas vent passageway communicating with said pump annulus and venting outside said housing for bleeding gas from said pump annulus.

3. A rotary uid pump as set forth in claim 1 where- (a) said outer peripheral surface varies from a maximum dimension of 0.896R to a minimum distance of 0.7-56R, and said inner peripheral surface varies from a maximum dimension of 1.232R to a minimum distance of 1.105R, R being the dimension from the pivot point of said vanes to the center of rotation of said rotor.

4. A rotary fluid pump comprising:

(a) a housing having an inner peripheral surface defining an internal space within said housing;

(b) an inlet duct tixedly attached to said housing and extending into said internal space;

(f) discharge port means in said housing communicating with said pump annulus;

(g) a rotor rotatably mounted in said housing and having a substantially cylindrical center portion disposed in said pump annulus;

(h) said cylindrical center portion being `substantially spaced from said inner peripheral surface of said housing and said outer peripheral surface of said inlet duct between said inlet port means and said discharge port means;

(i) said center portion having a plurality of longitudinal slots therein;

(j) a plurality of rigid vanes;

(k) each said vane having an irregular transverse crosssection with a radiallyinner portion and a radially outer portion;

(l) said radially inner portion of each said vane having a greater pressure area and a lesser -mass than said radially outer portion of each said vane;

(m) means for pivotally attaching each said vane, substantially between its radially inner portion and its radially outer portion, within one of said longitudinal slots of said center portion in a manner `so that said radially inner portion is in a contiguous relationship with said outer peripheral surface of said inlet `duct and said radially outer portion is in a contiguous relationship with the inner peripheral surface of said housing whereby fluid may be forced from inlet port means to said discharge port means without rotating said rotor.

5. A rotary fluid pump comprising:

(a) a cylindrical housing having an inner peripheral `surface defining an internal space within said housing;

(b) a cylindrical inlet duct xedly attached to said housing and extending into said internal space;

(d) said outer peripheral surface of said inlet duct land the inner peripheral surface of said housing being mutually eccentric whereby a pump annulus 7 having a variable transverse cross-sectional area is ford.

(e)" inletV port means insaid inlet duct communicating said pump annulus Said passageway;

(f) discharge port means in said housing communicating with said pump annulus;

(g) a rotor rotatably mounted in said housing and having a drive shaft on one end and a cylindrical center portion disposed in said pump annulus;

(h) said cylindrical center portion being substantially spaced from said inner Vperipheral surface of said housing and said outer peripheral surface of said inlet duct 4between said inlet port Aand said discharge means;

(i) a plurality of vanes;

(j) each Vsaid vane having a radially inner portion and a radially outer portion;

^ (k) said radially inner portion of each said vane having a greater pressure area than said radially outer portion of each said vane;

(l) each said vane having a hub substantially between `said radially inner portion and said radially outer portion;

(m) each said hub being positioned in said center portion of said rotor whereby said radially outer portion is in a contiguous relationship with said inner peripheral surface of said housing and said radially inner portion is in a contiguous relation with said outer peripheral surface of said inlet duct.

6 A rotary fluid pump as set `forth in claim 5 wherein:

(a) the radius of said outer peripheral surface of said inlet duct is 0.8251 and the radius of said inner peripheral surface of said housing is 1.166T, T being the distance from the pivot point of said vanes to the center of rotation of said rotor.'

7. A rotary fluid pump comprising:

(a) a `housingh-aving an inner peripheral surface defining an internal space within said housing;

(b) an inlet duct xedly attached to said housing and extending into said internal space;

(c) said inlet duct having an internal passageway therein and an outer peripheral surface;A Y said outer peripheral surface of said inlet duct and said inner peripheral surface of said housing being variably spaced whereby a pump Vannulus having a variable transverse cross-sectional area is formed;

(e) inlet Aport means in said inlet duct communicating lsaid pump annulus and said passageway;

(f) discharge port means in said housing communicating with said pump annulus;

(g) a rotor rotatably mounted in said housing andV having a substantially cylindrical center portion disposed in said pump annulus;

(Il) said cylindrical center nQrfiQa being substantially spaced from said inner peripheral surface of'said housing and said outer peripheral surface of said inlet duct in a countuerclockvviseV direction from said inlet port means and'said discharge port means;

(i) said cylindrical centerportion being in a contiguous sealing relationship with said inner peripheral surface of Asaid housing and said outer peripheral surface of said inlet duct in a clockwise direction from said inlet port means to said discharge port means;

(j) a plurality of rigid vanes;

(k) each said vane having a radially inner portion and Ia radially outer portion;

y(l) said radially inner portion of each said vane having Ia lgreater pressure area than said radially outer portion of each said vane; and i (m) means for pivotally attaching each said vane, subvstantially between its radially inner portion and its radially outer portion, to said rotor in -a manner such that said radially outer portion and said radially inner portion of each said vane are pivoted labout an axis perpendicular to and passing through a radius of said cylindrical center portion and so that said radially outer portion is contiguous to said inner peripheral surface of said housing and said radially inner portion is contiguous to said outer peripheral surface `of said inlet duct.

References Cited in the file of this patent UNITED STATES PATENTS 76,274 Turner Mar. 31, 1868 '212,463 Haughey Feb. 18, 1879 1,096,619 Gage May 12, 1914 1,385,084 MacFarlane July 19, 1921 1,516,053 Morgan Nov. 18, 1,924 1,683,143 Peterson Sept. 4, 192B 1,728,029 Barrett Sept. 10, 1929 1,952,142 Peterson Mar. 27, 1934 2,027,015 Bell Jan 7, 1936 2,373,865 Walter Apr. 17, 1945 2,684,035 Kemp July 20, 1954 Y FOREIGN PATENTS 14,702 Great Britain June 23, 1909 47,930 Norway May 19, 1930 51,001 Germany Aug. 3, 1899 165,483 Australia Get. 5, 1955 329,643 Italy Sept. 17, 1935 410,970 France lune 3, 1910 752,398 Germany Oct. 13, 1952 898,697 Germany Dec. 3, 1953