US2460617A

US2460617A - Planetary piston fuel pump

Info

Publication number: US2460617A
Application number: US562768A
Authority: US
Inventors: Roy O Balogh
Original assignee: Weatherhead Co
Current assignee: Weatherhead Co
Priority date: 1944-11-10
Filing date: 1944-11-10
Publication date: 1949-02-01
Anticipated expiration: 1966-02-01

Description

Feb. 1, 1949..'

R; o. BALOGH PLANETARY PIsToNl FUEL. PUMP 5 2 Sheets-Sheet 2 Filed Nov. 10, 1944 RoyA 0. BA .L 05H Patented Feb. 1, 1949 rLANETAnY rlsrroN FUEL PUMP any o. naiogh, cleveland. ohio, signor to The Weatherhead Company, Cleveland, Ohio, a corporation of Ohio Application November l0, 1944, Serial No. 562,768

3 Claims. (Cl. 1035-132) This vinvention relates to rotary pumps. Certain pumps have been proposed embodying a rotary runner or ring caused to travel about the cylindrical wall'of a pump chamber and a spring pressed vane reciprocably mounted in a well in the pump chamber between the inlet and outlet openings and slidably engaging the surface of the runner. This arrangement is objectionable, not only because of the initial cost of the spring pressed vane assembly and the liability of the spring to breakage and displacement in service. but because of leakage at the Joint between the free end of the vane and the runner. The principal objects of this invention are to eliminate these dimculties; to increase the eillciency of pumps of this type by effectively sealing the Joint between the vane and the runner; and to simplify and reduce the cost of pumps of this type while increasing the durability and minimizing the requirements for service and repairs.

Other objects of this invention are to maintain a uniform pressure of the runner against the cylindrical wall of the pump chamber, while allowing reasonable manufacturing tolerances and avoiding the danger of excessive pressureior breakage of the parts in the event grit or solid matter should be caught between the runner and the cylindrical wall of the pump chamber; to maintain such uniform pressure without the use of springs or the like ,in the driving mechanism for the runner; to increase the eillciency oi' the vpump by improving the seal between the runner and' the walls of the pump chamber; and to reduce the cost and service requirements and increase the durability of the runner and driving mechanism of the pump.

In the accompanying drawings which illustrate the preferred embodiments of the present-invention:

Fig. 1 is a vtransverse vertical section of the preferred embodiment of this 'invention taken on the line I-I of Fig. 2;

Fig. 2 is a transverse vertical section taken on the line 2-2 of Fig. 1;

Fig. 3 is a vertical section of the runner and vane taken on the line 1-1 of Fig. 2;

Fig. 4 is a side elevation of the runner and'vane;`

Fig. 5 is a transverse sectional view through a modified embodiment of the invention;

Fig. 6 is a transverse section through the ring and vane of the pump shown in Fig. 5: and

Fig. 'I is a side elevation of the runner and vane of Fis. 5.

The embodiment shown in Figs. 1 to 4 includes lindrical pump chamber 6. Two passageways 'l and 5 are provided from the chamber 5. Each passageway may be connected to a pipe through which the fluid is conveyed, and either passage way may be the inlet or outlet, depending upon the direction of rotation of the runner.

A shaft 9 is journalled in the housing on the axis of the cylindrical pump chamber 5, and has a cam I0 eccentrically disposed thereon. Arunner II in'the form of a ring of metal or other suitable material is journalled on the cam I0 and is given an orbital movement around the wall of the pump chamber by rotation of the driving shaft 9. A vane I2 which may be metal or other suitable material is slidablydisposed in a well I3 which extends radially from the cylindrical chamber 5 midway between the

passages

1 and 8. The runner II is coated on its periphery with a layer I4 of rubber or other suitable resilient material which laps over the end edges of the runner II as shown in Fig. 2 and extends outwardly to embrace the opposite ends of the vane I2, as indicated at I5 in Fis. 3.

The runner I I with the resilient layer` I4 thereon constitutes an annulus having a diameter substantially shorter Athan the diameter of the cylindrical chamber 5. The cam I0 is arranged to engage the inner surface of the runner II and to yieldably press the resilient layer Il against the cylindrical wall of the chamber 6. The vane I2 is spaced from the runner I I a substatial distance so that the resilient material is disposed between the end of the vaneand the outer surface of the runner Il. The well I3 is flared .outwardly as indicated at I6 to receive the extension I5 of the resilient layer .|4. Preferably the portion I5 is flared outwardly at a greater angle than the resilient portion I5.so as to permit the resilient portion I5 to move laterally a short distance. The material of the resilient layer I4 also may be extended along the end edges of the vane I2, as indicated at l1. Preferably the axial length of the resilient layer Il, including the portions overlapping the end edges of the runner II, is slightly pump chamber. Similarly the width in the axial greater than the axial length of the chamber 5 when the pump is assembled, so that the annulus consisting of the runner I I and the resilientlayer Il is pressed against the opposite end walls of the a pump housing or casing 5 provided with a cy- M A suitable material is selected which is resistant preferably vulcanized or similarly bonded in place about the runner II and to the end portions of the vane I2. 'I'hus the runner vane and resilient layer I4 becomes in effect an integral unit although by reason ofthe spacing of the end of the vane I2 from the runner II and the resilient nature of the material I5 the vane I2 is free to oscillate in either direction from a true radial position with respect to the vane I I.

In operation the shaft 9 is driven in any suitable way and the passages 1 and 3 are connected to the lines through which it is desired to pump the fluid. When the shaft 9 is rotated in a clockwise direction as seen in Fig, 1, the passage 3 constitutes the inlet, and 1 the outlet, of the pump. As the shaft 9 turns from the position of the parts as seen in Fig. 1, the cam I slides within the runner II and the resilient layer I4 tends to roll about the cylindrical wall 6 of the pump chamber. Rotation of the runner II about its own axis, however, is prevented by the attachment thereto of the vane I2 which is free for reciprocating movement only in thewell I3. Thus the resilient layer I4 slides to a limited extent around the inside of the cylindrical wail 9, the vane I2 being rocked first in one direction and then in the other direction from a true radial position with respect to the runner I I.

The pumping space is effectively sealed in a radial direction by the contact oi the resilient layer I4 with the opposite end walls of the pump chamber 6. Leakage from the high pressure to the low pressure side past the vane I3 is prevented by the resilient material I5 bonded to the inner end of the vane I2. Leakage around the ends of the vane I2 is prevented by the resilient material I1 engaging the opposite ends of the well I3. Leakage through the well I3 is effectively prevented by the close engagement of the sides of the vane I2 with the well and the relatively large area of engagement between the vane and well. Leakage from the high pressure to the low pressure lside past the area in the periphery of the runner which is engaging the cylindrical wall of the chamber 6 at any particular time is prevented by tne pressure of the resilient layer I4 against the cylindrical Wall, the magnitude of which may be predetermined by the relative proportions oi' the parts, depending upon the pressure which it is desired to develop in the particular pump. While the parts are made to press the layer I4 against the cylindrical wall of the pump chamber, any slight eccentricity of the parts resulting from manufacturing tolerances, and any grit or solid material that may 'be trapped between the moving parts, are prevented from creating excessive pressures or breaking or scorlng the engaging members by reason of the yieldability of the resilient layer I4.

In the embodiment shown in Figs, 5, 6 and '1, the housing vis provided with a cylindrical pump chamber 26 and inlet and outlet openingsv 21 and 28. A driving shaft 29 is journalled in the housing on the axis of the cylindrical chamber 26 as in the embodiment previously described. The shaft 29 is formed with a squared portion 30 within the pump chamber 28 which slidably ts in a slot 3| extending diametrically into a cylindrical follower 32. A ball bearing consisting oi an outer race 33, an inner race 34, and a series of balls is fitted over thefollower 32 with theouter race 33 engaging the cylindrical wall of the pump chamber 23. A spring 33 is seated in the slot 3| in the follower 32 and presses shaft.

against the squared portion 30 on the shaft 29. so as normally to urge the inner race 34 into an eccentrically offset position with respect to the shaft 29, as illustrated in Fig. 5.

A vane 31 is slidably mounted in a well 33 extendingradially from the pump chamber 23 between the inlet and outlet passages 21 and 23. The inner end of the vane 31 is spaced a short distance from the periphery of the outer race 33. A body of resilient material 39 such as natural or synthetic rubber or the like is bonded to the outer surface of the outer race 33 and to the inner end and the adjacent portions of the sides of the vane 31. Thus the vane 31 is sealed to the outer race 33 and is permanently connected thereto while being free to rock in either direction'from a true radial position with respect to the race 33. In the operation of the pump illustrated in Figs. 5, 6 and 7, the outer race 33, as in the embodiment previously described, is caused to travel about the cylindrical wall of the pump chamber 28 but is prevented from rotating on its own axis by reason of its connection to the vane 31 which is radially slidabie in the well 38. The outer race 33 is pressed against the cylindrical wall of the pump chamber 29 |by the spring 33 but is yieldable to pass over any inequalities or solid material because of the slidabie fit of the follower 32 over the squared portion 30 of the The leakage from the high pressure side to the low pressure side of the pump past the vane 31 is prevented by the material 39 which is preferably vulcanized or similarly bonded to the parts so as to seal the Joint between the vane 31 and the outer-race 33. Leakage between the axial ends of the race 33 and the end walls of the pump chamber is minimized by simply maintaining a close fit between the parts in this direction. Leakage from the high pressure side to the low pressure side past the point of contact of the race 33 with the cylindrical wall of the chamber 26 is prevented by the tension of the spring 36 which preslses the outer race 33 against the cylindrical wal Although preferred embodiments of the invention have been described in considerable detail it will be understood that the invention is not limited to the particular forms disclosed. For example. the ball or rolle'r bearings, as shown in Fig. 5, to transmit the drive from the shaft to the runner may be used in the embodiment shown in Figs. 1 to 4, inclusive, when it is desired to minimize the friction, and similarly the follower 32 in Fig. 5 ma'y be caused to slidably engage directly within the runner after the manner of the cam in Fig. 1 if the elimination of friction is not of sufficient importance to justify the cost of bearings in the particular installation. Manifestly, many other variations and rearrangements may be resorted to without departing from the scope of the invention as defined in the following claims.

I claim:

1. A rotary pump comprising a housing formed with a substantially cylindrical chamber. a recess extending radially outward therefrom and a port on each side of the recess, a shaft arranged axially in the chamber, a cam on the shaft, a ring Journalled on the cam for orbital movement in spaced relation to the walls of the chamber, a vane formed of material as rigid as that of the housing, said vane extending substantially for the full depth of the recess, and a unitary resilient covering for the ring bonded to the vane, said covering providing a restricted flexible connection between said ring and said vane.

2. A rotary pump comprising a metallic housing formed with a substantially cylindrical chamber, a recess extending radially outward therefrom and a port on each side of the recess. a shaft arranged axially in the chamber. a cam on the shaft, a ring Journalled on the cam i'or orbital movement in spaced relation to the walls of the chamber, a vane of thin metallic material extending substantially for the full depth o! the recess, and a unitaryresilient covering for the tending substantially for the Iull depth, of the recess, and a unitary resilient covering for the ring bonded to the vane, said covering having an integral resilient extension for providing arestrlcted flexible connection between said ring and said metallic vane.

` ROY O. BALOGH.,

REFERENCES CITED The following references are of record in the ille of this patent:

UNITED STATES PATENTS Number Name Date 2,246,488 Fraser June 17, 1941 2,276,355 Van Ranst Mar. 17, 1942 FOREIGN PATENTS Number Country Date '529,681 France Sept. 15, 1921 551,252 France Jan. 4, 1923 619,223 Germany Sept; 25, 1935