US2049794A - Pump - Google Patents

Description

L.1. c. ARMOR PUMP Filed Aug. 20, 1934 :s sheets-sheet 1 lll.

l INVENTOR v TTORNEY yAug. 4, 1936. J. C. ARMOR PUMPy Filed Aug.` 20, 1934 3 Sheets-Sheet IN VENT OR TORNEY v Aug- 4, 1936 J. c.I ARMOR PUMP Filed Aug. 2o, 1934- :s Sheets-sheet s Fig. 9

. INVENTOR M TTORNEY Patented Aug. 4, 1936 UNITED. STATES- PATENT oFFlcl.:

My invention relates to improvements in-rotary pumps which are used for pumping non-- compressible fluids and also for pumping and/or compressing compressible fluids.

One of the objects which I have in view is the I provision in such pumps of means for vsimultaneously pumping two fluids.

Another object in view is the provision of means for automatically reducing or relievingV the load on the pump while the speed of the latter is below a predetermined value whereby to enable the pump to attain the desired operating speed more rapidly and also to automatically maintain such speed.

Another object `in view is the better lubrication of the moving parts of the pump.`

I attain the first mentioned object by employing the space betweenthe outer casing of the pump and the interior cylinder for pumping one fluid and the space Within' said cylinder for pumping the second fluid.

The second named object I attain by providing the space within the casing in front of the rotary blade with a relief passage which is controlled by a governor-controlled valve which latter is automatically closed when the desired speed of the pump is attained.

The third named object I attain by the use of my combined means for lubrication and loadcontrol.

Further objects,l and also novel features ofy construction and of arrangement of parts, will appear from the following description:

In the accompanying drawings, wherein I have illustrated practical embodiments of the principles of my invention, Fig. 1 is a Alongitudinal vertical section through the pump.

Fig. 2 is a cross-sectional view taken on the line 2-2 in Fig. 1.

. Fig. 3 is an end view of the pump looking from the right in Fig. 1. p

Fig. 4 is a sectional view of the revolving blade, as shown in Fig. 2, but showing a ball valve in the duct thereof.

Fig. 5 is a broken view similar to Fig. 1 but showing a modification. i

Fig. 6 is a broken section taken on the line 6-6 in Fig. 5 but on a larger scale.

Fig. 'lis a view similar to Fig. 2 but showing a modification.

Fig. 8 is a similar view showing another modification.

Fig. 9 is a sectional View showing the character of governor-valve for use in connection with the structure illustrated in Fig. 8.

Referring first to Figs. 1, 2 and 3, I represents a cylindrical casing'supported by and having its ends closed bythe heads 2 .and 3. 4 represents a cylinder rotatably mounted within the casing I and having its ends journaled in the annular shoulders 5 formed in the inner walls of the heads. Thus the heads also function as the end closures of the cylinder. The cylinder is mounted eccentrically relative to the casing, as shown, its top in approximate contact with the top in- -terior of the casing.

6 lrepresents a shaft extending axially of the casingv I and having its ends journaled in the heads 2 and 3. Fixedly mounted on the shaft 6 is the radially disposed vane 1 having a. segmentally enlarged counterbalancing hub 8. The vane extends through a slot 9 in the wall of the cylinder tinto approximate contact with the inner wall of the casing I. The walls of the slot 9 are provided with beaded or rounded edges and the sides of the vane l are reversely curved at I0 so that the slot 9 is always sealed against the passage of fluid through the slot. The curved surfaces are carefully calculated so that at angu- 4lar positions the vane completely fills the slot within the chamber II.meshing with a second gear I4 mounted on a jack shaft within the chamber, the two gears forming a pump. Oil is admitted to the gear pump through a port in the face plateto which is connectedthe pipe I5, and

I6 represents a passage cut in the face plate from the discharge side of the gear pump to the small axial passage I1 in the shaft 6. The inner end of the passage I1 connects with a larger axial passage I8 extending through to the other end of the shaft 6 where it is cored out to form the tapered valve seat I9 arranged to be engaged by the tapered end of the slidable plug 20, which latter is provided with longitudinal grooves 2| extending beyond the end of the shaft.

The outer end of the plug 20 is provided with a circumferential groove 2l engaged by the fingers 22 of the bell-crank governor arms 23 pivoted intermediate of their-ends to brackets 24 mounted on the shaft 6. The arms are normally retracted by the spring 25 so that when the shaft 6 is stationary or rotating at less than its predetermined operating speed, the plug 20 is held in its retracted position, shown in Fig. 1, opening the valve seat I9, but when the proper speed is attained the close said valve seat.

26 represents an oil box surrounding the governor-valve and arranged to receive the oil which is expelled when the valve seat I9 is opened. The oil pipe I5 is connected to the bottom of the box 29 for the return supply of oil to the gear-pump I3-I4.

21 represents a. pulley on shaft 5 for rotating the same. It will be understood that any suitable application of power may be used for the shaft.

28 represents the inlet port into the space between the casing I and the cylinder 4, and 29 the outlet port for the same. Assuming the vane 1 to be rotating clockwise in Fig. 2, the port 28 is to the right of the top center of the casing and the port 29 to the left thereof. When the vane is rotated counterclockwise the port arrangement would be reversed. The outlet port 29 is provided with an inwardly closingcheck valve 30.

28 and 29' represent pipes connected respectively to the ports 28 and 29. l

'I'he ports 28 and 29 may be connected up in a circulating system of any kind, such for instance as a refrigerant system, or the port 29 may be connected up for the delivery of air under compression, the intake port 28 being open t o atmosphere.

3| represents a'radial duct in the vane 1 connected at its inner end to the passage I8 in the shaft 6 and extending to the outer end of the vane. The forward edge of the vane is cut away slightly as at 32 at the. outer end of the duct 3| to insure the discharge of lubricant in front of the revolving vane.

The head 3 is provided with two passages 33 and 34 connecting with the interior of the cylinder 4. The passage 33, at the top, is provided with an outwardly opening check valve 35 While the other at the bottom is provided with an inwardly opening check valve 36; The port 33 may be conplug is moved inwardly to nected, as by the pipe 31, to the supply end of a circulating system of any kind, while the port 34 may be connected as bythe pipe 38 to the return end of the same.

In the operation of the pump, the uid, liquid or gas, is drawn into the space between the casing I and the cylinder 4 through the' port 28 filling the space in the rear of the traveling vane 1, while the like uid in front of the vane is forced out of the port 29. As the vane and cylinder revolve together, but on different axes,

. the volume of the vane contained within the cylinder 4 varies from the minimum when the parts are as shown in Fig. 2, to the maximum when the parts have rotated into a position 180 degrees therefrom, and this variation in the effective capacity of the cylinder 4 is takenadvantage of by allowing the desired fluid, such for instance as oil, to be drawn into the cylinder through the port 34 as the area expands and to be expelled through the port 33 as the area contracts.

Thus two differentv pumping or condensing actions are simultaneously performed by the pump. A portion o'f the oll pumped along the shaft 9 through the passages I1 and I8 will be carried outwardly along the vane duct 3| to lubricate the wall of the casing I to prevent friction with the vane.

Again rising pressure in the -space between the casing I and the cylinder 4 will be relievedl out through the duct 3L and the passage I9,- as long as the rotation of the shaft 6 does not attain the ing the pump load and expediting -the attainment of operating speed.

Referring now to Fig. 4, I have provided an outwardly closing ball valve 39 in the outer end of the duct 3I in the vane 1 with a small by-pass 40 for the outward. drip of oil. This provision of ball valve and by-pass is preferable in the case of large compressors where centrifugal force might discharge too much oil through the duct 3 I.

Referring now to Fig.A 5, I have shown the left hand bearing of the shaft 6 provided with an annular receiving chamber 40 into which the lubricant may escape through the ra'dial port or ports 4I from the axial passage I8 when the valve head 42 on the inner end of the valve rod 43 is retracted from the vaive'port I9 bythe springretraction of the governor arms 23. I also provide the end of the shaft I8 with a circumferential fiange or lip 44 to prevent the outward escape supplies the gear pump I.3-I4, may be connected to the bottom of the chamber 43. y

In Figs. 5 and 6,1 show a transversely disposed bore 46 formed in the vane 'I intersecting the ducts 3i adjacent their outer ends, and a spring plate 41 closing such outer ends, the spring plate being heldin place by plugs 48' driven or threaded into the ends of the bore. The lubricant is permitted to escape past the plate 41 through Vsmall by-pass passages 49. In Fig. '7 the vane i is shownunprovided with duct or ducts 3 I, the casing I being provided with a load relief port 50 at a point adjacent the discharge port 29 but in the rear thereof in the direction of traveloi' the vane which is assumed to be clockwise. The port 59 is connected by a pipe 5I to the discharge passage I6 of the pump lil-I4, the wall of' which passage is provided with a threaded port for that purpose. The relief port or ports 9B may be in one of the heads, if preferred.

As the pump is started, or while the pump is operating at a speed less than that at which the governor valve closes, the load on the pump, such as compressed air, is relieved through the port 50, the pipe DI, the passages I6 and I9. As the speed of the pump increases, the governor valve closes, thus causing the pump to assume its full load. In such case the gear pump will force lubricant through the passage I 6, pipe 5I and port 50 into the pump casing I. h

Referring now to Figs. 8 and 9, I have therein shown a solid cylinder or hub 4', provided with a plurality of blades 1' which are slidable radially in slots in the hub. In this case no axial passage is provided in the shaft and the gear pump is not employed; Thefair or other fluid to be Apumped 0r compressed is admitted at 28 and ports 53 and 54 are connected by the pipes v55 and 56, respectively, to the threaded ports which form the outer ends of the alined passages 51 in the valve body 58 which open at their inner end l into the cylindrical bore 59 whose one end ls open to atmosphere. 60 represents a cup-shaped valve which slides in the base oi the body 56 and is arranged to close or open the inner ends of the twin passages 51 in accordance with the position of the valve. The valve 60 is mounted on a stem 6I, which extends through bushing 62 which is xed in the other reduced end of the bore 59 asl by the Washer and nut 63. On the outer protrudl is less than that determined to be the Aproper operating speed for the pump, the valve 60 is retracted, opening the passages 51 to atmosphere, and thus the load is relieved in the pump casing l until the desired speed of the pump is approached, when the speed of rotation of the pulley 64, which is regulated with that of the pump, y causes the arms 61 to spread and thus moves the Valve 60 into position to close the inner ends of the passages 51, thus in eiiect closing the relief ports 53 and 54 and imposing the full load on the pump.

' 69 represents ports in the'valve body 56 connected by small passages 10 with the passages 5l, the passages 1l) being provided with tapered adjustment screws 1l to regulate their effective capacities. The ports 65 are connected by pipes to a suitable oil supply under pressure, not shown, which is at pressure greater than the internal pressure of the pump when the latter is operating under normal load.

Thus when vthe valve 66 closes the inner ends of the passages 51, the oil is forced outwardly'of said passages and through pipes 55 and`56 and ports 55 and 56 into the casing l to lubricate the walls thereof. The quantity of lubricant thus supplied to the pump as it operates may be properly adjusted by means of the screws 1l.

It is evident that any desired number of relief ports may be used as desired, a like number oi?V connections to the body 58 being provided.

While I have illustrated the principles of my invention as applied to rotary pumps, it is obvious that the same may be advantageously applied to piston pumps or to any type of pump wherein it is desirable to relieve or r'educe the load until 'the pump attains its predetermined normal operating speed.

1. In combination with a pump for fluids, means for relieving the load on the pump, means for rendering the load-relieving means inoperative when the pump attains its predetermined speed l of operation, and means for supplying lubricant through the load-relieving means into the interior of the working chamber of the pump while the pump is operating at its predetermined speed.

` 2. In combination with a pump for uids, means for relieving the load on the pump, a valve actuated relatively to the speed of the pump and arranged to close the load-relieving means when the pump attains its predetermined operating speed, and means for supplying lubricant to the pump through the load-relieving means into the interior of the working chamber of the pump when the pump attains its predetermined oper-4 ating speed;

3. In combination with a pump for fluids, an outlet .passage for the relief of compressed gases from the high pressure side of the working chamber of the pump for relieving the load on the pump in starting, a speed-controlled valve for said outlet passage and arranged to close when the pump attains its predetermined operating speed, and a pressure oil supply communicating with said outlet passage and arranged to supply lubricant to the working chamber of the pump when said valve is closed. y

4.- In a rotary pump, the combination with a casing, a shaft extending through said casing and a vane radially disposed on said shaft, of -a passage axial of,said shaft, means for supplying lubricant under pressure to one end of the passage a duct in the vane and communicating at its inner end with the passage and at its other end with the interior of the casing, and a speed-controlled valve at the discharge end of the passage arranged to close when the lpump attains its 25 predetermined speed of operation.

5. In a rotary pump, the combination with a casing, a shaft extending through said casing and a vane radially disposed on said shaft, of a pas-- sage axial of said shaft, a duct in the vane hav- -ing its inner end connected to the passage and i its outer end communicating with the interior of the casing, a speed-controlled valve at one end of the passage arranged to close the latter when the pump attains its predetermined operating of the casing, a speed-controlled Valve at one endw of the passage arranged to close the latter when the pump attains its predetermined operating speed, and a pressure-lubricant supply connected to the passage:

In a rotary pump, the combination with a casing, a shaft extendingfthrough said casing and a vane radially disposed on saidshaft, of a passage axial of said shaft, a duct in the v ane having its inner end connected to the passage and its outer end communicating with the interior of the casing, a speed-controlled valve at one end of the passage arranged to closeI the latter when the pump attains its predetermined operating speed, a pressure-lubricant supply connected to the other end of said passage, and means for returning lubricant from the valve-end of the passage to the lubricant supply. Y

8. In a pumpvfor iluids, the combination of an outlet passage for the escape of pressure from the high pressure side of the pump for relieving the load on the pump, a valve actu'ated relatively to the speed of thepump and arranged to close the outlet passage when the pump attains its normal pump for fluids,

through the load-relieving means into the interior of the working chamber of the pump while I the pump is operating at its predetermined speed,

and means to restrict'the discharge of lubricant through said load-relieving means.

10. In a pump for fluids, the combination of an outlet passage for the escape of pressure from the high pressure side of the chamber for relieving the load on the pump, a valve actuated relatively to the speed of the pump and arranged to close the outlet passage when the pump attains its normal operating speed, means for supplying lubri-V cant to the pump through said outlet passage during the normal operation of the' pump, and 5 means for restricting the flow o1' lubricant through said passage.

JAMES C. ARMOR.

Images