US2470220A

US2470220A - Pump

Info

Publication number: US2470220A
Application number: US501985A
Authority: US
Inventors: Carl W Mott
Original assignee: International Harverster Corp
Current assignee: Navistar Inc
Priority date: 1943-09-11
Filing date: 1943-09-11
Publication date: 1949-05-17
Anticipated expiration: 1966-05-17

Description

May 11,1949. C.W.MQ1'I' 2,410,220

. m Filed Sept. 11, 1943 v 7 Sheetsk-Shet 1 May PUMP

Filed Sept 11 943 7 sheet fl 2 c. w. MOTT 7 May 17, 1949.

PUMP 7 Sheets-Sheet 4 Filed Sept. 1-1, ,1943

May 17, 1949. c. w. MOTT PUMP Filed Sept. 11, 1943 7 Sheets-Sheet 5 v l5 g 0. w'. MOTT May 17, 1949.

PUMP

7 Sheets-Shet 6 Filed Sept. 11, 1943 f ay 37, 1949. c. w. MOTT 2,470,220

PUMP

Filed Sept. 1;, 1943 '7 Sheets-Sheet 7 enema May 11, 1949v UNITED STATES Carl W. Mott, La Grange, asslgnor to Inter- .7 national Harvester Company, a corporation of New Jersey Application September 11, 1943, Serial No. 501,985 u This invention has to do with pumps of the rotary type and with a pump employing a rotor in which pistons are'reciprocated with a pumping action in timed relation with such rotor. The rotor cylinders or pump chambers and the pistons therein are revolved about parallel eccentrically disposed axes to obtain'reciprocation of the pistons relatively to and within the cylinders without incurring reversible movement of either the cylinders or pistons.

A general object of the invention is the provision of a compact pump operable at high-speeds to deliver fluid at a substantial flow rate, and capable of high pressure delivery at both high and low speeds,

Another object is the provision of a novel port and passage arrangement by means of which fluid is drawn into and expelled from the pumping unit with but a small flow resistance.

Another object is the provision of an improved rotary pump having a rotor with radially directed cylinders in which pistons are operable with a sinusoidal movement inwardlyby force imparted thereto by a cam and outwardly by centrifugal force or by centrifugal force augmented by the pressure of fluid pumped by the device. This construction obtains noiseless shockless operation without the use of springs or articulately connected parts, minimizing the weight of the revolved parts and in all conducive to driving of the unit at high speed.

Another object is the provision of a novel pis-' ton-actuating member having an arcuate surface eccentrically embracing the rotor to force the pistons radially inwardly during the discharge phase in the rotor cycle, and bearing means for rotatively supporting the actuating member so it can rotate as the pistons revolve and thereby diminish the relative movement between said member and the pistons. This diminishes wear upon slidingly engaging surfaces on the pistons and on the piston-actuating member, and the wear upon these surfaces is further reduced by curving the piston surfaces so that the line" thereon of contact with the surface of the actuating member shifts to disperse the wear and heat.

Another object is the provision of a communication between the intake passage and the casing chamber enclosing the sliding surfaces of the pistons and their actuating member, so that fluid may occupy this chamber to lubricate the sur-' faces and various bearings of rotatable parts, and so part of this fluid may be that leaking past the pistons.

Another object is the provision of a novel rotor wherein the bottoms of the radial cylinders are 20 Claims. (Cl. 103-161) 2 countersunk to receive tail portions of the pistons and to receive fluid for urging the pistons outwardly. The centrifugal force is thus as sisted in its movement of the pistons, and the pistons are also movable outwardly by such fluid pressure at slow speeds at which the centrifugal force would be insufficient to move the pistons. It is possible, therefore, to operate the pump as slowly as desired.

These piston tails also furnish piston stabilization, making it possible to make the main bodies of the pistons shorter and to place the bottoms of their cylinders nearer to the center of the rotor, whereby the diameter and mass of the pump is tremendously diminished.

A further object is the provision of a ported member together with novel means for pressing it in sliding sealing relation with a ported end face of the pump rotor to separate inlet and outlet passages which communicate with the rotor ports during respective periods in each rotation of 'the rotor. The invention also has as one of its objects the provision of a new wall structure having said sealing member incorporated thereinto and rotatively adjustable to reposition said memher and the inlet and outlet passages of the pump so that the direction of flow through these passages will be unaltered when the direction in rotation of the pumping unit is changed.

A further object is the provision of means for utilizing the outlet high pressure fluid for imposing force upon said sealing member to press it against the rotor end face and thus'compensate for wear between the faces of said member and rotor.

An additional object of the invention is the provision of a cone-shaped end face for the pump rotor for receiving a ported sealing member relatively to which-the rotor rotates and into and from which the fluid is discharged and drawn through the rotor ports.

Still another object is to employ a cone-shaped sealing member as in the next preceding object as .a bearing support for the rotor and cooperable with means for axially adjusting the rotor to take up any looseness developed between the sliding conical surfaces because of wear. This adjusting feature also makes it possible to adjust to overcome wider tolerances of error in manufacture.

These and other desirable objects inherent in and encompassed by the invention will be more structed according to invention;

Fig. 2 is an end elevation of the pump shown in Fig. 1, looking toward the-left end of said pump as viewed in Fig. 1;

Pig, 3 is a fragmentary sectional view taken on the line} .91 Fig. 2 to illustrate inlet and outlet passages in the casing end wall structure;

Fig. 4 is a transverse sectional view taken through the pump at that section containing the rotor, as indicated by the line 4 in Fig. 1; Fig. 5 is a transverse sectional view taken at the line 6 in Fig. 1 to illustrate the position and shape of inlet and outlet ports in a sealing member which is pressed in sliding sealing relation with an end of the rotor;

.Fig. 6 is a fragmentary, longitudinal, sectional view similarly to Fig. 1 through a modified form of the invention which, employs ball members for Fig, Tis a longitudinal sectional view taken centrally through a third form of the invention;

Fig. 8 is a transverse sectional view taken through the pump rotor, as indicated by the line I in F18. "I; I

Fig. 9 is a transverse sectional view taken in the opposite direction to Fig. 8 and illustrating ports, fastening means, and the disposition of an end wall sealing member for the pump rotor;

Fig. 10 is a view taken like Fig. 9 on the line III of Fig. '7 to further illustrate the aforesaid ports, fastening members, and sealing member;

Fig. 11 is a longitudinal sectional view taken centrally through a fourth embodiment of the invention;

Fig. 12 is a transverse sectional view taken through the rotor upon the line l2 of Fig. 11;

Fig. 13 is a transverse sectional view taken in the opposite direction to Fig. 12 for illustrating ports, fastening means, and an end wall sealing member which is pressed in sliding sealing relation with an end. of the rotor;

Fig. 14 is a sectional view taken on the line I4 of Fig. 11 to further illustrate the parts shown in Fig. 13;

Fig. 15 is a fragmentary sectional view taken on the line ii of Fig. 13, showing in detail plungers which'are urged by the pressure of fluid in the pump outlet passage against the sealing member for pressing itfirmly in sliding sealing relation with the pump rotor;

Fig. 16' isa sectional view taken axially and centrally through. another embodiment of the invention; and

Fig. 1'! is an end view of a conical port-sealing member employed in this final embodiment of the invention: a

With continued reference to the drawings, and particularlyto Figs. 1 to 5, the casing in for the pump can be seen :to be generally cylindrical.

The right end of thecasing as viewed in Fig. 1 is closed by anend plate ll having a cylindrical reentrance portion I22 containing a bearing i3 for the receptionaandi support of :a drive shaft l4 formed integrally-with a--:rotor IS. The opposite end ofxth'e :casingfll is .aclosed bya casing end plate; i6 which. is-iheld: in place .by machine bolts ll.- =-Inlet-. and exhaust-sports...respectively desig- ..nated-.-l8and:;i9,'are-formedrin the casing end .plate :16;-

intermediate wall -of the casing,

generally designated .:.2-l,-,:forms one end of a chamber 22 containing the rotor l5 and other movable parts of the" pump unit 23. This wall 2! comprises a portion 24 formed integrally with the casing and having a'cylindrical surface 25 the principles of the 4 in which a sealing member 26 is axially adjustable. Said sealing member has an inner sealing face 21 for bearing in sliding sealing relation with a ported end face 28 of the rotor. The cylindrical periphery of a hole 29 in the sealing member 26 rotatively receives and is in sealing relation with a spindle 3! formed integrally with and projecting endwise from the rotor I5. Rotation of the sealing member 26 is prevented by a pin 32 inserted through a hole 33 in the casing and into a recess 34 in said sealing member.

Pressure of the desired amount between the slidingly engaged

surfaces

21 and 28 on the sealing member 26 and the rotor 15 is maintained by 1. bearing member 35, a washer 36, and a castellated nut 31 having castellations 38, which is screwed onto a threaded section 39 of the spindle 3|. A cotter key 4| inserted through the spindle 3| is cooperable with the castellations 38 for maintaining the desired adjustment.

Pistons 42 in respective radial cylinders 43 of the rotor are urged centrifugally outwardly, during rotation of the rotor, against the circumscribing bearing surface 43 upon the inner side of a I from their cylinders.

cylindrical piston-actuating member 44. This member 44 is jourrialed by means of a ball hearing unit 45 upon the outer periphery of the cats ing reentrant portion 12 to dispose the surface 43, which is perfectly circular in the form illustrated, eccentrically of the rotor axis. Therefore, as best illustrated in Fig. 4, as the rotor rotates, the circular surfac 43 will permit the centrifugal force to move the pistons radially outwardly during one-half of a revolution of the rotor and will serve to force the pistons radially inwardly against the urge of the centrifugal force during the succeeding half revolution.

Ports communicate between bottom portions of the cylinders 43 respectively and the end wall face 28 of the rotor, and the sealing member 26 is so oriented circumferentially of the rotor axis with respect to the offset in the eccentricity of the piston-actuator ring or member 44 that an arcuate inlet port 41 in the face 21 of said sealing member will be traversed by each port 46 while the associated piston is moving radially outwardly, and that an arcuate outlet port 48 is traversed by each port 46 while its associated piston is being forced inwardly by the arcuate member 44. In other words, as best conceived by reference to Figs. 4 and 5, during rotation of the rotor, the rotor ports 46 which are spaced circumferentially about the rotor axis are revolved about this axis when the rotor is rotated and, during one portion of the circular path of revolution of these ports, their associated pistons will be caused to move radially outwardly for drawing fluid into their cylinders and, during a succeeding portion of the path of revolution, the pistons are forced inwardly to expel the fluid That portion of the path traversed by the ports 46 during outward movement of the pistons is the inlet path portion, whereas that traversed by the ports during inward movement of the pistons is the discharge path portion. The inlet path portion for the ports 46 coincides with the arcuate inlet port d1, Fig. 5, while the outlet path portion is coincident with the arculate outlet port 48 in the sealing member 26 (Fig. 5).. Oriented assembly of the sealing member 26 with respect to the direction of eccentricity of the piston-actuating member 44 is assured and expedited by the pin 32 and the sealing member recess 34 which recelves said pin when the sealing member is properly oriented.

In Figs. 3 and 5, the'linlet'port 41 can be seento enlarge in its diameter as it approaches the outer or left side of the sealing member 26 as viewed in Fig. 3, making thls'port correspond generally to the portion of a side wall of a cone.

vA chamber 49 between the end' plate l6 and the sealing wall 21 provides'communication be- 6 tween the inlet ports 18 and 41, Fig. l. Communication between the outlet ports l9 and 48 is pro- I vided by an outlet channel 5|, Fig. 3. Provision is made-for utilizing .thepressure. of the pump fluid for augmenting the centrifugal force in urging the pistons outwardly against the eccentric piston-actuating member 44. InFigs. l and 4, cylinders 43 can be seen to be counterbored at 52 and these counterbores communicate orv intersect to form a chamber 53 in a central position within the rotor. Cylindrical tails 54, formed integrally with the pistons, slide radially within the bores 52 while blocking the communication between the chamber 53 and the cylinders 43.

A lateral channel 55 (Fig. 1) communicates between the rotor chamber 53 and the groove 56 circumscribing the route of the spindle 3|. A short channel 51' (Fig. 5) inthe face 21 in the sealing member 26' provides communication between the outlet port 48 and the groove 56, whereby, during operation of the pump, fluid at high pressure in the outlet port 48 'will be forced inwardly through the channel 51, groove 56, and channel 55 to the chamber 53 for forcing the pistons 42 against the actuator ring 44. This expedient for applying pressure into the chamber through the inlet port I 8, inlet chamber-43, and the ports 41 and 48, Radial outward movement of the piston will continuepntll it reaches the position of the uppermost piston in Fig. 4 and, during the most of this movement, the associated port 46 will be in. registry'withithe inlet port 41, so that, during all ofjthlstime, fluid, will be drawn into the cylinder throughfthe' inlet ports and passages, whereby that portion of the cylinder. beneath the piston will be. filled with fluid. As the filled cylinder rotates counter-clockwise from theuppermost position in Fig. 4, its piston 42 will be forced gradually inwardly by the operating member 44 and, during thisv time, the port 46 will register with the exhaust port 48 in the sealing member 26, so that, while the piston moves from the uppermost position to the lowermost position, the fluid will be expelled through the arcuate port 48, the channel 5| (Fig. 3), and outwardly through the-discharge port 19. Because of the plurality of pistons and cylinders, some of the ports 46 are constantly-communicative with'the'inlet port 41 and likewise some of the ports 46 are constantly communicative with the port 48, so that there is a continuous flow of fluid inwardly through the port 41 and outwardly through the port 48.

ing the firm sliding contact between these faces.

Such adjustment is made by removing the cotter pin 4! and rotating the castellated nut 31 for advancing the

parts

26, 35, and 36 toward the rotor. When the desired firmness of' contact is obtained between the faces'21 and 28, the rotation of the nut 31 will cease and'the cotter pin 3i will be reinserted for maintaining the adjustment.

The operation is as follows:

The sealing member 26 is so oriented with respect to the eccentric displacement of the pistonactuating member 44 that the pump will operate to draw in fluid through the inlet port It! (Figs. 1 and 2) and to expel fluid through the outlet port 19 (Figs. 3 and 2) when the rotor is rotated in the direction of the arrow in Fig. 4. While the piston 42 is in the lowermost position in Fig. 4, it will occupy its most inward position radially of the rotor. As the rotor rotates in the counterclockwise direction as viewed in Fig. 4, the piston in the lowermost position will have a tendency to move radially outwardly under centrifugal force and the pressurefluid upon the inner end of its tail portion. When the port 46 associated with this piston arrives in registry with the lower end of the inlet port 41 (Fig. 5), the piston will have been moved outwardly far enough to have created a low pressure in the bottom of its cylin der, causing fluid to be drawn into the cylinder The speed at which the pump'may be operated 'is increased by making the surface 43 on the actuator member 44 circular so that a sinusoidal movement is'imparted to the pistons 42. Operating speed is also possible in the higher range because of the very slight relative movement required between the outer ends of the pistons and the actuating member 44. This member 44 is freely rotatable upon the ball bearing unit 45, so that it is caused to rotate with "the rotor l5, because of the frictional engagement of the pistons with said member. Therefore, during half of a revolution from one horizontal position to the other. the outer end of each piston will have slid or crept from a line of contact slightly to one side of the piston axis to a line of contact a short distance on the other side thereof, and during the succeeding half revolution, each piston shifts its line of contact across the piston axis back to the initial point. It should be noted that, because of the curved outer end contour of these pistons, the line of contact between the piston and the piston-actuating member 44 is constantly changing, wherefore the pressure upon the piston is not constantly localized. Consequently the heat of friction generated between the pistons and the actuating member 44 is dispersed over asubstantial area at the end of the piston and, of course, over the entire circumferential area of the surface 43.

' Constant lubrication-of the curved outer end surfaces of the pistons and of the actuator member surface 43 is also conducive to high speed operation. The fluid, such as oil, which is pumped by the device will leak to a slight degree outwardly past the pistons into the chamber 22, and some of this fluid which is suitable for lubrication will alight upon the surface 43. Some of the lubricating fluid will also get into the hearing unit 45 for lubricating the same. Excess fluid leakage past the pistons into the chamber 22 can escape into the inlet chamber 49 through a passage 59 in the wall structure 2|. While the pump is at rest the fluid level of a'liquid in the

chambers

49 and 22 will tend to equalize through the communication 49, causing the fluid, such as oil, to rise sufllciently far in the chamber 22 to ton can, therefore, be made of greater diameter and shorter stroke and placed sufliciently near the axis of the rotor so that the pump has a relatively small diameter. In this manner the weight of both the rotor and the pistons becomes less to adapt the pump for high speed operation.

That form of the invention shown in Fig. 6 has parts which for the most part are like those shown in'Fig. 1, and, to expedite this description, corresponding parts are indicated by the same respective reference characters with the addition of the letter a. This second form of while obtaining adequate stabilization. The pisthe invention employs spherical members 42 for the balls are provided with no tails, as 54, on

the pistons 42 and, of course, no bores, as 52,

respective threaded holes 68 in said ring. After the ring 63 has been rotated into position for orienting the sealing member structure 26'' with respect to the outlet portion of the path traversed by the ports 46 in the rotor, the bolts 62 will be tightened for drawing the member 6| into abutment with the end of the casing wall,

whereby the threads on the outer periphery of v the ring 63 are pulled axially against the threads against rotation and to thereby maintain the oriented position of the sealing member 26. 'A plate 69 of suitable bearing metal is employed as a facing for the inner end of the bearing structure 26' and this plate is pressed into sliding sealing relation with a facing bearing plate H forming the end face of the rotor IS. A plurality of dowel pins 12 hold the bearing plate H for rotation with the rotor, and similar pins (not shown) are employed for holding the facing plate 69 in assembly with the structure 26". Holes 13 in. the facing plate ll register with the ports 46*, and an arcuate outlet port 48 in the bearing plate 69 communicates with a channel 14 which extends through the stem 65 of the sealing member structure 26 The outlet passage continues from the channel 14 through a or chamber, as 53, are formed in the rotor l5".

These pistons in the form of balls 42 have the advantage of economical production, and the further advantage of being adapted to roll upon the inner periphery of the actuating member 44, so that no sliding takes place between the actuating member 44' and the balls 42. The operation' of this second embodiment, with the exception of the fluid pressure component of force for urging these balls radially outwardly, is identical to the operation described above for the first embodiment.

The third embodiment shown in Figs. '7 to 10 operates upon the same principle as the first and second embodiments. Consequently, to expedite the description, corresponding parts are desigton-actuating member 44 is joumaled directly' on a cylindrical section 60 of the casing which is arranged eccentrically to the rotor axis, as shown in Fig. 8. The inlet port l8 is formed in an end plate I6 which is secured by bolts H to a plate-like holder member 6| for a sealing member structure 26 Additional bolts 62 are employed for securing the holder member 6| to an annular, externally threaded retaining ring 63. The threads on this ring 83 mesh with threads 66 upon an internal portion of the casing. In assembling that part of the casing wall structure to the left of the rotor l5, as viewed in Fig. '7, the retaining ring or member 63 will first be screwed into the threads 64 to a position approximating that shown in the drawing. Following this, the ported sealing structure 26 will be assembled with the holder member 6! therefor by the insertion of a ported stud 65 on the structure 26 into an opening 66 in-the member 6|. The bolts 62 will be inserted through holes 51 in the member 6! preparatory to this member being carried into axial alinement with the ring 63 and the turning of the bolts 62 into channel 15 in the end plate I6 to the outlet port IS The inlet passage leads from the inlet port l8 through a large hole I6 in the holder member 6| and a space 11 in the ring 63 below a lower chordal edge I8 of the sealing member structure 26 (see Figs. 9 and 10).

Initial pressing of the bearing plate 69 against the bearing plate H on the end face of the rotor is accomplished by a headless set-screw 8 I, of which the groove 82 for receiving the bit of a screwdriver is accessible through a hole 83 in the end plate l6' when a screw-plug 84 is removed. This set-screw 8| is adapted to bear against the outer end of the stem, and to thereby establish a firm pressing relation between the bearings plates 69 and II. After the pump is in operation the pressure of fluid discharged from the rotor into the channel 15 is utilized to augment the force of the screw 8! for pressing the sealing structure upon the outer end of the stem 65 for pressing 26 against the rotor. Pressure of such fluid acts upon the outerend of the stem 65 for pressing said sealing'structure to the right. A sealing member 85 is disposed in a recess 86 into which the outer end of the stem 65 projects to prevent leakage of fluid from the high pressure channel '35 between the stem and the hole 66 therefor in the holder M. A small leakage which will occur simply advances downwardly between an inner face 81 of the holder 6| and an outer face 88 of the sealing member structure into the pump inlet passage for reintroduction into the pump unit.

It should be noted that the exhaust passage communicates with the bearing surface 60 for the piston-actuation member 44 through a small space 89, and further that the fluid in the passage communicates with that part of the casing enclosing the bearing units l3 through the space St between the rotor and the piston-actuating member 44*. Communication between the space 9i and the fluid inlet passage provides for the escape into such passage of fluid forced outwardly of the rotor past the pistons. The space 9| also permits equalization of the fluid level within the inlet passage and the chamber portion of the casing enclosing the bearing units I3 wherefore, when the pump is at rest, the lubricant fluid can supply a lubrication of these bearing units.

Upon an examination of Figs. 8 and 10, which are taken in different directions axially of the pump,'.it is ascertainable that, with the rotor rotating in the direction indicated by the arrows in these two figures, the pistons 42 will be moving radially outwardly while on the lower side of the pump casing, and will be moved inwardly while traversing the upper side of the pump caswherefore the fluid will be forced outwardly of the cylinder through said ports 46 and into the outlet channel of the pump. The general operation is, therefore, the same as that previously described with respect to the first embodiment.

The outer ends of thepis'tons 42 are curved similarly to the pistons 42 of the first embodiment,

whereby the curved surfaces of these pistons are caused to rock upon the inner surface of the actuating member 64*, as well as slide thereon, and this rocking motion of the pistons prevents the heat of friction being applied for any length of' time at a single line of contact between the pistons and actuating member. The actuating member 44 does not rotate so freely upon the casing bearing 66 therefor as upon the ball bearing unit 45 of the first embodiment, although there is a creeping movement of the member within the bearing 66, so that the entire inner surface of this member 44 is ultimately subjected to the same character of pressure. and wear.

Attention is also called to the fact that the chamber 53 at the core of the rotor i5 has no communication with the high pressure outlet 'wardly, and, in this'manner, augment the centrifugal force upon the pistons for keeping them constantly in contact with the actuating member 44 That the embodiment of the invention shown in Figs, 11 to 15 is identical to the embodiment in Figs. 7 to 10, except for certain differences, will be expressly pointed out. Those parts in this embodiment which correspond to those in the first and third embodiments will be designated by the same reference characters with the addition of the letter '0.

Small bolts 95 (not shown, but employed in the third embodiment) are employed for attaching the wear plate 69 to the sealing member structure 26. The inlet and outlet ports l8 and l9 in the casing end plate l6 are shaped somewhat diflerently from those in the third embodiment, and

this end plate l6 provides different accommodations for the headless screw 8 I for initially press- 7 ing the-sealing member structure 26 against the 96 is placed about the stem of the sealing member structure and is slidable in the hole 66.

In this manner the pressure of fiuid in the outlet passage 15 is exerted through the sealing member onto the piston member 96 to cause this passage of the pump, but this chamber 53 fills with fluid from thecylinders 43 during operation of the pump because of the leakage inwardly past the tails 54 This leakage is augmented by an L-shaped channel C in the tail of one of the pistons 42", this channel being of small bore and shown in dotted outline in Fig. 8. The lateral leg CL of this channel C is disposed at such a distance from the inner end of the piston as to be projected outwardly a very short distance from the bottom of the cylinder when the piston is at its outermost position radially of the rotor, so that as the piston is subsequently forced inward- 1y of the rotor, the high pressure communication between the cylinder and the chamber 53 through the channel C will be but for a short time interval after which the lateral CL will be forced out of communication with the cylinder Use of the channel C in. one or more of the piston tailscauses the chamber 53 to be filled quickly after the pump has been at rest and though the pump be initially driven at a slow speed. A noncompressible fluid filling the chamber 53 will be operable to transmit pressure from the inwardly serve as pump plungers to transmit force throughthe body of the fluid" in the chamber 53 to the tails of those pistons which are to be moved Outpiston member to bear inwardly upon the enlarged part of the sealing member structure'26 for automatically augmenting the force of the set-screw 8| for pressing together the slidable wear plates 69 and ll.

A further expedient shown in detail in Fig. 15 is used for pressing the sealing head structure 26 against the end of the rotor. A pair of bores 91 are formed in the inner face of the holder 6l to reciprocally contain plungers 98 for bearing against the outlet face of the enlarged portion of the sealing member 26. The inner ends of these bores 91 communicate with the outlet passage through channels 99, wherefore the pressure of fluidin the outlet passage is imposed upon the outer ends of the plungers 98 to cause them to bear inwardly against the sealing member structure and in this way increase the pressure which is applied thereto for urging it against the end of the rotor. and further to increase the area over which the pressure is applied to the sealin "half of that figure. Under these circumstances the intake and discharge through the normal ports and passages can be provided for by simply loosening the screws 62 rotating the ring 63 and its appendages degrees, and retightening said screws. Index arrows A and B, Fig. 11, spaced 180 degrees about the holder 6| are respectively alinable with the arrow C on the casing in the two adjustments for opposite direction drive of.

11' to expedite this description, those parts identical with or corresponding to parts in the first embodiment are designated by the same respective reference numerals with the letter (1 added.

In this final embodiment, the rotor I includes a thick end plate III having a conical end face 28 The ports 46 leading from the cylinders 43 communicate through said end plate II I to the conical surface 28 The end plate is connected to the main body of the rotor I5 by machine bolts H2. The sealing member 2I5 has a conical sealing face 2'l formed in sliding sealing relation with the conical face 28 and this sealing member is secured in a recess I I3 of the pump casing by means of bolts (not shown), so that this sealing member will be held against rotation with the rotor. An inlet port IIl in the pump casing communicates through a channel 49 with an inlet port 41 in the conical sealing member, whereas an outlet port I9 in the casing communicates through a channel 5| with an outlet port 48 in said sealing member. In Fig. 17, the inlet and outlet ports 41 and 48 are shown in a manner displaying their geometric arrangement upon the sealing member and their respective circumferential extent thereabout.

The outlet port 48 in the sealing member is intersected by a channel H4 formed coaxially with the sealing member and coaxially with a channel 55 in the rotor This latter channel and the channel H4 have enlarged adjacent end sections which fit in close sliding relation with a tube H5, so that said channels and the tube H5 provide communication between the high pressure outlet port 48 and the center chamber 53 in the rotor. Fluid under pressure is thereby maintained upon the inner ends of the piston tails 54 to supplement centrifugal force in holding the pistons outwardly in sliding relation with their bearing surface upon the eccentrically mounted pistonactuating member M during rotationof the pump rotor and of said piston-actuating member. Any leakage occurring between the tube H5 and the side walls of the channels 55 and H4 into a space H6 between the end of the sealing member and the left end of the main body of the rotor I5 is conducted back to the inlet port 41 through a small channel III. Any leakage occurring between the conical sealing surfaces 2'! and 28 in an axial forward direction into the space H6 is similarly conducted into the inlet port 41 and leakage axially rearwardly between the surfaces 21 and 28' will pass through a space I I 8 between the left end of the casing and the left end of the rotor end plate III into the casing. Fluid thus accumulating in the casing, andfluid accumulating in the casing because of leakage radially outwardly between the pistons 42 and their cylinders 43 when attaining a sufficient amount, is drained into the inlet channel '49 through a short passage I IS.

A further distinction between this last embodiment of the invention and the first embodiment is in the increased length of the reentrant casing portion I2 for supporting a pair of axially spaced

ball bearing units

45 and 45 for the rotative support of the piston-actuating member 44. The conical surface 2I provides a bearing support for the rotor and thus cooperates with the ball bearing unit I2I for rotatably supporting the rotor I5 and the drive shaft W A hole I34 through the casing reentrant portion I2 is slightly oversize with respect to the shaft M so that it will not complicate proper alining of the shaft and rotor upon their hearing supports.

12 The desired pressure between the sealing surfaces 21 and 28 is maintained by an adjustable thrust-exerting means comprising a ball bearing unit I2I, having its inner race mounted upon the drive shaft M against a shoulder I22 thereof. The outer race of this ball bearing unit is mounted within a ring I23 having a cylindrical portion I 24 slidable within a recess I25 in the right end wall of the casing and a threaded section I26 tumable into a threaded sect-ion I21 at the outer end of the recess. The desired adjustment for the sealing surfaces 21 and 28 is accomplished by first loosening a set-screw I28, and thus loosening a brass friction member I29 from the cylindrical surface I24 of the ring I23. Thereafter, the ring I23 may be rotated by the use of a spanner wrench engageable with end recesses I3I in said ring, providing a gear I32 is not then assembled with the drive shaft I4. Should this gear I32 be assembled on the shaft M when the adjustment is made, holes I33 in this gear, which are axially alinable respectively with the recesses I 3|, are capable of coreceiving therewith short rods or the like to cause the ring I23 to be rotatively adjusted by simply rotating the gear. After the adjustment is made these rods will be withdrawn and the set-screw I28 'retightened.

The operation of this pump is identical to that of the first embodiment. It is, therefore, not repeated at this point.

While I have herein shown and described preferred embodiments with the view of illustrating the invention, it should be understood that the invention extends to other forms, arrangements, structures and details falling withinthe scope and spirit thereof and not sacrificing all of its material advantages.

What is claimed is:

1. In a pump, a rotor having radially directed cylinders opening into its outer periphery, ports communicating with such cylinders, a closed fluid-containing chamber centrally of the cylinders, and bores communicating between the cylinders and said chamber; pistons reciprocable in said cylinders with an in and out motion radially of the rotor and comprising auxiliary portions disposed reciprocably in said bores to communicatively isolate their cylinders from said chamber and in pressure imposing relation with the fluid in said chamber; a member having a circular force-reaction surface circumscribing the rotor in eccentric relation with the rotor axis to restrain outward axial movement of the pistons by the action of centrifugal force thereon during rotation of th rotor and to complement such centrifugal force in causing in and .out pumping action of the pistons and their auxiliary portions respectively in said cylinders and said bores; and the chamber being operable through the medium of said fluid therein to transmit force from each auxiliary piston portion, as it is moved inwardly, outwardly upon the other piston portions for supplementing the centrifugal force in constantly maintaining the pistons in outward force exerting relation with the ring-like member.

2. In a pump, a rotor having radially directed cylinders opening into its outer periphery, ports communicating with such cylinders, a closed fluid-containing chamber centrally of the cylinders, and bores of less diameter than said cylinders projecting axially therefrom inwardly into communication with said chamber; pistons re- -13 motion radially of the rotor and comprising tail portions on their inner ends projecting into said bores for like motion and for communicatively isolating the cylinders from said chamber, a

member having a circular force reaction surface circumscribing the rotor in eccentric relation with the rotor axis to restrain outward axial movement of the. pistons by the action of centrifugal force thereon during rotation of the rotor and to complement such centrifugal force in causing in'and out pumping action of the pistons and their tail portions respectively in said cylinders and said bors; and the chamber being operable through the medium of said fluid therein to transmit force from each piston tail portion, as it is moved inwardly, outwardly upon the other tail portions for supplementing the centrifugal force in constantly maintaining the pistons in outward force exerting relation with the ring-like member.

3. In a rotary pump of the piston type, a rotor having radial cylinders and counter-bores in the radially inner ends of said cylinders, pistons in said cylinders to cooperate therewith in forming pumping chambers and reciprocable in their respective cylinders to cause expansion and contraction of said chambers, there being ports respectively communicating with said chambers for accommodating ingress and egress of fluid to and from said chamberspursuant to such reciprocation of the pistons, tail portions on said-pistons projecting into said counter-bores, and a piston actuating member having a surface eccentrically oircums'cribing the rotor to restrain outward movement of the pistons in a variable amount and to thus complement the centrifugal force on the pistons to cause in and out pumping motion of the pistons during rotation of the rotor.

' 4. In a rotary pump of the piston type having an inlet duct and a discharge duct through which fluid is discharged from the pump under pressure, a rotor having radial cylinders and counter-bores in the bottoms of said cylinders, pistons reciprocable in said cylinders to pump fluid into the discharge duct,'tail portions on said pistons and projecting into said counter-bores for reciprocation therein pursuant to said reciprocation of the pistons a piston actua ing member having a surface eccentrically circumscribing th rotor to restrain outward movement of the pistons in a variable amount and to thus complement the centrifugal force on the pistons to cause reciprocation of the pistons and tails during rotation of the rotor, means providing communication between the cylinders and the inlet duct during outward movement of the pistons and communication between the cylinders and the discharge duct during inward movement of the pis ons. and channel means communicative between said discharge duct and the counter-bores to impose fluid under pressure against the ends of the piston tails and thus augment the centrifugal force in urging the pistons radia ly outwardly,

5. In a rotary pump of the piston type having an inlet duct and a discharge duct through whichfluid is discharged from the pump under pressure, a rotor having radial cylinders and counterbores in the bottoms of said cylinders. pistons reoiprocable in said cylinders to cause'withdrawal of fluid from the inlet duct and delivery thereof into the discharge duct, tail portions on said pistons and nroiecting into said counter lcores for reciprocation therein pursuant to said reciprocation of the pistons, a piston actuating member having a surface eccentrically circumscribing the rotor to restrain outward movement of the pis- 14 tons in a variable amount and to with the centrifugal force on the'pistons to cause reciprocation of the pistons and tails during rotation of therotor, means providing communi- "cation between the cylinders and the inlet duct during outward movement of thefpistons and communication between the cylindrsand the discharge duct during inward movement of the pistons, said rotor having a cavity with which said counter-bores communicate, and channel means communicative between, the pump discharge duct and the counter-bores through said cavity to impose fluid under pressure against the ends of the piston tails and thus' augment the centrifugal force in urging the pistons radially v outwardly.

6; In a pump, a rotor cylinders opening into its outer periphery, an end face, ports communicating between bottom portions of the cylinders and positions on said end face spaced radially and circumferentially from the rotor axis, a closed chamber centrally of the cylinders, and bores communicating between the cylinders and said chamber; pistons re-' ciprocable in the cylinders with an in and out motion radially of the rotor and comprising auxiliary portions projecting into. said bores for like in and out motion and for communicativelyjisolating the cylinders from saidchamber; a, member having a circular force reaction surface circumscribing the rotor in eccentric relation with the rotor axis to restrain outward axial movement of the pistons by the action of centrifugal force thereon during rotation of its-rotor and to coact with said centrifugal force in causing outward movement of the pistons while they and their cylinder ports traverse an intake portion or their path of revolution about the rotor axis and in causing inward movement while they and their cylinder ports traverse a discharge portion of said path; a fluid discharge line including an apertured sealing member; means maintaining said sealing member in sliding. sealing relation I with the rotor and face while maintaining the aperture in registry with the cylinder ports while they traverse the discharge portion of said path; inlet duct means communicating with said ports only while they traverse the intake portion of said path; and duct means communicating between the rotor chamber and said discharge line to conduct fluid under pressure into said chamber for pressing outwardly upon the piston auxiliary portions.

'T. In combination, a pump casing, a. rotary pumping unit in said casing and having a ported end face for the inlet and discharge of a'lubrieating fiuid, bearing means for said unit and disposed in the casing for lubrication bysuch fluid in' the casing, and said casing including a wall having a portion in sliding sealing relation with the pumping unit end face, said wall providing discharge passage means disposed for successive communicative registration by the ports of said end face during a cyclical phase in the rotation of the unit, said wall also providing inlet passage means communicative with the interior of the casing to provide for delivery of the lubricating fluid thereinto and also disposed for suc- .cessive communicative registration with said thereof and having a ported end face for the inlet thus cooperate having radially directed.

l and discharge of fluid to and from said cylinders, pistons reciprocable in the cylinders to draw fluid thereinto through their respective ports in the end face during outward movement and to discharge the fluid from the cylinders through said ports during inward movement, part of the fluid leaking past the pistons and through the cylinder end openings into the casing during such discharge, means for reciprocating the pistons to cause their outward movement during the traversal of an inlet portion of a circular path followed by said ports during rotation of the rotor and to cause inward movement during the traversal of an outlet portion of such path, and said casing including a wall having a portion in sliding sealing relation with the rotor end face, said wall providing discharge passage means disposed for communicative registration with said ports during their traversal of the outlet path portion, said wall also providing inlet passage means communicative with the interior of the casing to drain said leakage fluid therefrom and also disposed for communicative registration with the rotor ports during their traversal of the inlet path portion.

9. In a rotary pump of the piston type, a pump casing comprising opposed walls, a rotor bearing in one of said walls, a rotor shaft rotatively carried on said bearing, a rotor in said casing constrained for rotation with said shaft and spaced axially from the one wall to provide a lubricant conducting passage for conducting lubricant from the casing onto said bearing, said rotor having radial cylinders opening outwardly in the periphery thereof and having a ported end face for the inlet and discharge of a lubricating liquid into and from said cylinders, there being clearance between said periphery of the rotor and the easing so that liquid can flow therein exteriorly of a the rotor from either end of the rotor to the other, pistons reciprocable in the cylinders to draw such liquid thereinto through their respective ports in said end face during outward movement and to discharge the liquid from the cylinders through said ports during inward movement, part of the liquid leaking past the pistons and outwardly through the cylinders into the casing, means for reciprocating the pistons to cause their outward movement during the traversal of an inlet portion of a circular path followed by said ports during rotation of the rotor and to cause inward movement during the traversal of an outlet portion of such path, and the other wall of saizl casing including a portion in sliding sealing relation with the rotor end face, said wall providing discharge passage means disposed for communicative registration with said ports during their traversal of the outlet path portion, said wall also providing inlet passage means communicative with the interior of the casing to supply such liquid thereto exteriorly 0f the rotor and to drain any excess therefrom caused by said leakage past the pistons, and said inlet passage means also being disposed for communicative registration with the rotor ports during their traversal of the inlet path portion. v

10. In a rotary pump of the piston type, a pump casing comprising opposed walls, a rotor bearing in one of said walls, a rotor shaft rotatively carried on said bearing,a rotor in said casing constrained for rotation with said shaft and spaced axially from the one wall toprovide a lubricant conducting passage for conducting lubricant from the casing onto said bearing, said rotor having radia1 cylinders-opening outwardly in the periphery thereof and having a ported end a face for the inlet and discharge of a lubricating liquid into and from said cylinders, pistons reciprocable in the cylinders to draw such liquid 5 thereinto through their respective ports in said end face during outward movement and to discharge the liquid from the cylinders through said ports during inward movement, part of the liquid leaking past the pistons and outwardly through the cylinders into the casing, an annular piston actuating member journaled in the casing eccentrically of the rotor and having an annular surface circumscribing said rotary periphery to bear against said pistons and thus complement centrifugal force acting thereon to cause said inward and outward motion thereof during rotation of the rotor, there being a clearance space between said periphery of the rotor and the piston actuating member and through which the 20 end thereof to the other, the other casing wall including a portion in sliding sealing relation with the rotor end face, said other wall providing discharge passage means disposed forcommunicative registry with the rotor ports during inward movement of their associated pistons, said other wall also providing inlet passage means communicative with the interior of the casing to supply such liquid thereto exteriorly of the rotor and to drain any excess therefrom caused by leakage past the pistons, and said inlet passage means also being disposed for communicative registration with the rotor ports during their traversal of the inlet path portion.

11. In a pump, a casing having a threaded section with threads directed circumferentially of the casing, a pumping unit in said casing and having a fluid discharge station oriented circumferentially of the casing, a ported discharge mem- 40 ber for disposition at such station for conducting the discharged fluid therefrom, and means for disposing the ported member at said station, comprising an orientation member having a section with threads meshable with and rotatable in the casing threaded section, a holder for the ported member attachable to the orientation member and orientated pursuant to said rotation to dispose the ported member at the discharge station, tension exerting means connected between said orientation member and said holder member for drawing the latter toward the former, and means reactable through the casing to limit the approach of said members and being thus cooperable with the tension exerting means to create an axial stress upon'the meshed threads.

12. In a pump, a casing, a pumping unit in said casing and having a fluid discharge station oriented circumferentially of the casing, a ported discharge member for disposition at such station for conducting discharged fluid therefrom, and an assemblyfor disposing the ported memher at said station, comprising an orientation member rotatable circumferentially of the casing, a holder for the ported member attachable to the orientation member and orientated pursuant to said rotation to dispose the ported member at the discharge station, tension exerting means connected between the orientation member and said holder member for drawing the latter toward the former, and means comprising meshable counterparts respectively upon one of the two last-named members and the casing cooperable with said tension exerting means to prevent rotation of the said members relatively to the casing when said holder member and said liquid can flow exteriorly of the rotor from either 17 orientation member are drawn toward one another as aforesaid.

13. In a pump, a casing,.a pumping unit in said casing and having a fluid discharge station oriented circumferentially of the casing, a ported discharge member for disposition at suchstation for conducting discharged fluidtherefrom, and an assembly for disposing the ported member at said station, comprising an orientation member rotatable circumferentially of the casing, a holder for the ported member attachable to the orientation member and orientated pursuant to said rotation to dispose the ported member at the dis charge station, means preventing simple displacement of the orientation member axially of the casing, and tension exerting means connected between the orientation member and the holder member to draw the latter toward said orientation member and into force imposing relation.

with the casing to tighten said assembly.

14. In a pump, a casing having an index means thereon, a pumping unit having a fluid discharge station occupying respectively different positions circumferentially of the casing when driven in opposite directions, a ported discharge member for disposition at either of said stations for conducting discharged fluid therefrom, and an assembly for selectively disposing the ported member at said stations, comprising an orientation member rotatable circumferentially of the casing, a holder for the ported member attachable to the orientation member and rotatable there-' with to dispose the ported member at either of said stations, index means rotatable with said holder member for complemental disposition with respect to the casing index means to indicate the station at which the discharge member is disposed, tension exerting means connected between the orientation member and said holder member for drawing the latter toward the former, andmeans comprising meshable counterparts respectively upon one of the two last-named members and the casing cooperable with said tension exerting means to prevent rotation of the said members relatively to'the casing when said holder member and said orientation member are drawn toward one another as aforesaid.

15. In a pump, a casing having a reentrant end wall portion containing an opening directed axially of the casing and an exterior bearing generated about an axis parallel to that of the opening but eccentric with respect thereto, a pumprotor shaft extending through said opening, a pump rotor in the casing and constrained for rotation with the shaft, said rotor containing radial cylinders opening outwardly of its periphery and an end face disposed oppositely to the shaft and containing ports leading respectively from bottom portions of the cylinders, pistons in said cylinders, said pistons having outer ends projecting outwardly beyond the rotor periphery, a piston actuating member rotatively supported on the exterior bearing of said reentrant casing portion and having an internal surface embracing the rotor periphery for rotation eccentrically thereof and concentrically of said exterior bearing tolimit outward movement of the pistons while they and their ports traverse an inlet portion of their path of revolution and to force said pistons in wardly while they traverse an outlet portion of said path during rotation of the rotor, and ported means having inlet and outlet ports disposed for communication with the rotor ports respectively while they traverse their inlet and outlet path portions.

16. In a pump, a casing having a reentrant end wall portion containing an opening directed axially of the casing and an exterior surface gene1-,

ated about an axis parallel to that of the opening but eccentric with respect thereto, a pump-rotor shaft extending through said opening, a pump rotor in the casing and constrained for rotation with the shaft, said rotor containing radial cylinders opening outwardly of its periphery and an end face disposed oppositely to the shaft and containing ports leading respectively from bottom portions of the cylinders, pistons insaid cylinders, said pistons having outer ends projecting outwardly beyond the rotor periphery. axially spaced bearing units mounted on the exterior surface of said reentrant casing portion, a piston actuating member supported on said bearing units for rotation about said eccentric axis, said actu ating member having an internal surface embracing the rotor periphery to limit outward movement of the pistons .while they and their ports traverse an inlet portion in their path of revolution and to force said pistons inwardly while they traverse an outlet portion of said path during rotation of the rotor, ported sealing means against which the rotor end face is axially pressable and providing inlet and outlet ports disposed for communication with the rotor ports respectively while they traverse their inlet and outlet path portions, and means on said casing at the outer end of said reentrant portion for adjusting the rotor shaft axially to determine the pressure between the rotor end face and the sealing member.

1'7. In a pump, a rotor having radial cylinders opening radially outwardly thereof, radial bores in the bottoms of the cylinders, ports leading from bottom portions of the cylinders into an end face of such rotor, and channel means communicating with said bores and leading inwardly from said end face coaxially with said rotor, pistons in said cylinders, tails on said pistons projecting into said bores, a piston actuator having a surface eccentrically embracing the rotor to limit outward movement of the pistons during their traversal of an inlet portion of them and their ports in their path of revolution during rotation of the rotor and to force said pistons inwardly during their traversal of an outlet portion in said path of revolution, means having inlet and outlet ducts disposed for communication with the rotor ports respectively while they traverse said inlet path portion and said outlet path portion and having a lateral communicating with the outlet duct and arranged in opposed coaxial relation with the rotor channel means, and a tube disposed in said lateral and said channel to complete communication between the outlet duct and the rotor bores to provide fluid therein under pressure for urging the pistons against the surface of said actuating. member.

18. In a pump, a casing having a bearing in a wall thereof, a drive shaft extending into said casing and rotatably supported upon said bearing, a pumping unit constrained for rotation with said shaft and having a conical end face disposed oppositely from said bearing and containing circumferentially spaced ports in said face through which fluid is received into the unit during their traversal of an inlet portion of a path of revolution about the axis of said unit during rotation thereof and through which ports the received fluid is discharged from the unit during their traversal of an outlet portion of such path of revolution, a sealing member supported on said cas- 19 ing coaxially with the rotor and having a conical bearing and sealing surface disposed within the conical end face of the rotor for cooperating with said bearing in the support of the rotor, said conical member containing circumferentiallyspaced inlet and outlet ports in the conical surface thereof, said inlet port being disposed for registration with the ports of the unit during their traversal of said inlet path portion and said outlet port being disposed for registration with the ports of the unit during their traversal of said discharge path portion, and adjustable means for retaining said pumping unit and said sealing member axially together with said end face and the conical surface of said sealing member in sliding sealing journaled relation.

19. In a rotary pump of the piston type, a'rotor having radial cylinders and intercommunicative counter-bores at the bottoms of said cylinders, pistons reciprocable in said cylinders, tail portions on said pistons projecting into said counterbores, a piston-actuating member having a surface eccentrically circumscribing the rotor to restrain outward movement of the pistons in a variable amount during rotation of the rotor and. being thus cooperable with the centrifugal force on the pistons to cause in and out pumping motion thereof, and at least one of said tail portions containing a channel communicative between said counter-bores and a side wall portion of such tail portion that communicates with the associated cylinder when the associated piston is in a position radially outwardly of the rotor.

20. In a rotary pump of the piston type, a rotor having radial cylinders opening into its outer periphery, ports communicating with inner end portions of the cylinders, a chamber, and bores communicating between the inner ends of the cylinders and said chamber, said ports having a path of revolution about the rotational axis of the rotor; pistons reciprocable in said cylinders and comprising auxiliary portions disposed reciprocably in said bores to at least throttle communicatlon between their respective associated cylinders and said chamber, means for reciprocating the pistons relatively to the cylinders, coordinately with rotor rotation, to cause movement of the pistons outwardly of their cylinders to an outer limit and consequent ingress of fluid through the ports while they traverse an inlet zone in their path of revolution and to cause inward movement of the pistons from such limit and consequent compression of the fluid in the.

cylinders and egress through their ports while they traverse an outlet zone in their path of revolution, and channel means communicative between said chamber and at least one of said cylinders during the compression of fluid therein to insure provision of a. sufficient quantity of fluid in said chamber for transmitting force from inwardly moving cylinder auxiliary portions to the outwardly moving of such portions to urge the same outwardly.

' CARL W. MOTT.

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

UNITED STATES PATENTS Number Name Date 297,329 Wiegand Apr. 22, 1884 1,087,181 Pitman Feb. 17, 1914 1,325,434 Carey et a1 Dec. 16, 1919 1,515,529 Well Nov. 11, 1924 1,635,006 Oliver July 5, 1927 1,778,238 Wilsey Oct. 14, 1930 1,817,063 Carrie et al Aug. 4, 1931 2,103,314 Benedek Dec. 28, 1937 2,273,468 Ferris Feb. 17, 1942 2,245,570 Centervall June 17, 1942 FOREIGN PATENTS Number Country Date 124,069 Great Britain Mar. 20, 1919 406,106 Great Britain Feb.22, 1934