US2655112A

US2655112A - Rotary pump or motor

Info

Publication number: US2655112A
Application number: US294587A
Authority: US
Inventors: White Ambrose
Original assignee: Individual
Current assignee: Individual
Priority date: 1952-06-20
Filing date: 1952-06-20
Publication date: 1953-10-13
Anticipated expiration: 1970-10-13

Description

Oct. 13, 1953 A. wHrrE ROTARY PUMP OR MOTOR .4 Sheets-Sheet l Filed June 2o, 1952 una la \l7 FGJ. f

IN VEN TOR.

SYM @da ATTORNEYS Oct. 13, 1953 A. WHITE 2,655,112

ROTARY PUMP OR MOTOR INVENTOR AMRosg wH/TE ATTORNEYS FIG. Il.

Oct.,I 13, 1953 A. WHITE 1 2,655,112

ROTARY PUMP OR MOTOR 4 Filed June 20; 1952 4 Sheets-Sheet 3 INVENTOR AMIRUM nfl/MIT@ Oct. 13, 1953 A. WHITE 2,655,112

ROTARY PUMP 0R MoToR Filed June 20. 1952 4 Sheets-SheelI 4 m INVENTOR @n E; lL. AMBRQM www@ E:

lon the line Patented Oct. 13, 1953 eine te one simula; power stroke or each, revo- @este a lqlisr. weer. stroke in e e. en. sessie; ddh., iQ provide adequate V11oing :abutm es@ Onesies Space 0r 9 '11; parte zieQSedftQ bien t m- Xth Ato. Create one Single meehme tlifi will @overt gaseous' eti@ liydreulie energy to eleheniloe energy or mechanical. enelfey form o the iliustretesi inthe ecco peeling. drawing ifi which# .euse 1 is a. `Yeliel longitudinal, setti@ O f me emite-mamme;

Figure 2, e t. vetitel hell section. 1119s.-

wel lnQF/ire. Peris; Vv eure 3L cut-@wax secties Qi.' the. ,seroit l with the eisten temoved, uleeely illustrating the ports l5 and 1.6,' end their qriiiectops to the nisssulfe dempers i and 1.. vres tlvely:

El. re s, eleteiled. vfiif olf the Piston T5;

teure e @sketch u the meting abutment 2, .illustraties the dem?? Whiehpermi the, 11e-.S- sise uf the Risers' 5, between the rotor, ',L-.end rotative 'abutment 2.: and'.

sieurs .6., 'ec-elevational View 9i menswetfutius' elet-e ielve'l' Wthts Suspension @ed ediustmet bei? @1l-end vali/ adjustment plete vafz.

Fieulzes '110116, inelusite illustrate e .modifi-esi foim of-'tlie invcn` on pioyidii'jig ai [pl @che ele casing, in COQ A c Y ceitl liottrig abutment 'and having a; jalgeted c'ostuc'tio'ri Vroviding"al1, coolingu 'and seeliiig System. Figure '1. e veticel lungiiudinel Section .of

the'modied form of the inception, teken `on 10 figure 1,4; is an end; perso@ 15 the, Q

2 eight S 5 V*Figure 1.2 is4 e side-pelispective View, paflrttelgly sectioned: showing; ja rotorV of.' the: modified Vilo- -venticmY Figure. 1.3; is.` en end, oerspectiye ofthe tar-yabutment .ofA this.; embodiment 've viewy loi the piston 'used in, the mQdiedi veltiotl- Eieure 17,5,- a sidepetseeetite View, Qt ,one end close-re member iorfthe housing. or; Qasrie Eleni@ 161s e Similar devpersoeetiye of .s d, closure 'slier- V 1:11; Heures lia-rid: 2, the .rotor l, @ed its de.- teuhebly Secured Areisiaolfl- .5.. are sussende@ the completely enclosed casing I8, by bearings LZ, [-2, eine: snai@ 3 which permit, the.. rotor its |51 to, sevqliersely- .in a or uuntefeelokws@ direction Lilie,-

t 2f cen, teYQlve 111,1 letely @H910 'ed with cause.. or eff-ect "ag thrust 'ont the entire lrotor;l and that "rings: 151;fbetweenftheroto la; and' its casing v'Iafaire; provided vto -hold the' said gasfor `liquid in its directed route. Thrust s et, u p;lcy;pa,1g 0 @lamine leakasetetsueen rotor I .,ezid.; ,casing frring' any excess leakage pressure in one end space to the other. In Figures l and 6, the pressure chambers 6 and may be further provided with two identical suspended stationary plate valves 30, 30 (one in each chamber) in cut-off relation to respectively adjacent ends of ports I5 and I6 and connected by means of swivel 33, loosely fitted to a suspension and adjustment bar 3l, which is screwed through a valve adjustment plate 32, that is bolted to the outside of the rotor casing I8. The stationary plate valves 3, 30 are most accurately adjusted by the suspension and adjustment bars 3|, 3l, in pressure chambers 6 and 1, in such a position that the port holes i5 and I6 will be entirely closed when the revolving piston 5, bolted to the rotor I, reaches its point of interengagement with the rotating abutment 2, and that they will be open after the revolving piston 5 passes out of interengagement with the rotating abutment 2.

The adjustable stationary plate valves contribute to the efiiciency and flexibility of operation. When the rotating piston 5 is passing through its period of interengagement with the rotating abutment 2 a condition of opening arises which permits pressure fluid from the admission port hole I5 to pass over the outer end of piston 5 and to the exhaust port hole I6 without performing any useful work. Proper angular setting of the plate valves 30 prevents this loss. These plate valves 30 may also be adjusted to vary cut off so that the fluid within the Work chamber can expand more fully. In starting, the

plate valves

30, 30 can be manually shifted from normal position if necessary in order to pass pressure iiuid through a closed port hole into work chamber 34.

When a gas or hydraulic pressure is built up in pressure chamber 6, Figure l, through the opening 20, in casing I8, or by any other means, and the rotor I, with the xedly secured piston 5, is moved counterclockwise, Figure 2, to a point where the piston 5 has cleared its area of interengagement with the rotating abutment 2, the ,I

port hole I5 will have passed from behind the fstationary plate valve 30, permitting the pressure substance to flow through the block of rotor I,

piston 5, and build up a pressure within the work chamber or cylinder space 34, between the piston 5, and the rotating abutment 2, which will force the piston 5, and the rotor I, to continue its same rotation. At the same time port hole I6 will have passed from behind its stationary plate valve 30, in pressure chamber 1, permitting any pressure trapped between the opposite side of the piston 5, and the rotating abutment 2, to exhaust or escape freely through the piston 5, rotor block I, on to the pressure chamber l, and out through the opening 2l, in casing I8. The revolving inertia set up in the rotor I, piston 5. and rotating abutment 2, at the end o-f the circular power stroke where port hole I5 passes behind the stationary plate valve 30, will,

without the benefit of a flywheel, cause the piston 5 to pass through its interengagement area with the rotating abutment 2, and, therefore, start a new cycle.

If at any time, in the process of converting gaseous and hydraulic pressure to a mechanical energy, it is desirable to reverse the rotation of the mechanical converter, the fluid pressure in pressure chamber 6 is relieved and a pressure is built up in pressure chamber 1, whereas, the same 4 chain of reaction will apply as described in the preceding paragraph.

In Figures l and 2, when the shaft 3 is turned in the bearings I2, I2, rotating the rotor I, and piston 5, in a counterclockwise rotation and through the gear 8, which is made fast to the shaft 3, rotates gear 9, which is made fast to shaft 4, in the bearings I3, I3, and simultaneously turns the rotating abutment 2, in a clockwise rotation in which the arcuate adapter recess 2a in the rotating abutment 2 is in perfect time with the piston 5, which is bolted to the rotor I. The piston 5, moving away from the rotating obstruction 2, creates a decreased pressure in the work chamber 34. This decreased pressure begins in Work chamber 34, at the point where the piston 5 leaves its interengagement with the rotating abutment 2, and, whereas, the port hole I5 passes from behind the plate valve 30, in pressure chamber 6, thereby, causing a decreased pressure in pressure chamber 6, which will readily attract the oW of gas or liquid through the opening 2U, in casing I8. While at the same time, on the opposite side of the piston 5, which is moving in a circular direction toward the rotating abutment 2, a pressure is being built up in work chamber 34, beginning at the point where the piston 5 leaves its interengagement with the rotating abutment 2, and, whereas, the port hole I6 passes from behind the stationary plate valve 30, in chamber 1 permitting the gas or liquid to flow into pressure chamber and out through the opening 2I, in casing 8.

If at any time it is desired to change the direction of the gas or liquid flowing through the mechanical converter, it can be accomplished by reversing the rotation of shaft 3, whereas, 'the same reaction as described in the preceding'paragraph will occur, only, in the reverse order.

The basic aspects of the rotary pump or motor invention described in detail and disclosed in Figs. 1 to 6, inclusive, are carried forward in the modified embodiment of Figs. 7 to 16, inclusive, to provide for a plurality of rotors spaced symmetrically about a single or common rotating abutment for greater and more uniform power output. This modified embodiment provides also for jacketing of the rotors, rotating abutment and rotor pistons for cooling, sealing and lubricating, and for including pump means to circulate fluid in the jacketed parts.

Since this modified form of the invention incorporates much that is common to the principal embodiment, only the features of improvement will be described with particularity. Figs. 7 and 8 taken together show the manner in which a plurality of rotors 4I (in this case three) are disposed symmetrically about a common rotating abutment 42 for individual cooperation therewith. The conical-ended abutment 42 is formed With an arcuate peripheral recess 42a. As will be explained in further detail, each of the rotors 4I is jacketed and has jacketed housing means. The three rotors 4| are maintained in spaced. parallel relation to each other and to the rotatinsg abutment 42 in the manner shown in Fig.

Each of the rotors 4I is mounted on a power shaft 43 and has a spur gear 48 secured on an outer end by a key 5I. Bearing formations 52 are provided at the opposite ends of the shafts 43.

The central rotating abutment 42 is mounted for rotation on and with countershaft 44 supported at spaced end portions by bearing forma- There are a number of advantages in this system of forced circulation for the iiuid cooling or other heat exchange medium. It will insure sealing of all minute openings between the relatively movable parts, and at the same time, provide a degree of lubrication. Regardless of the direction in which the rotors 4| are turning as determined by combustion or pressure uid in either of the pressure chambers 46 or 41, the cooling fluid will be admitted at the exhaust end and discharged at the combustion end of the machine. In this manner the water or other fluid will pick up its latent heat from the expended gases of the exhaust and transfer it back through the machine to the combustion end, thus preventing stress and strain resulting from successive expansion and contraction of the metals cooled.

If small leakage of water reaches the area of burning gases, it may be used beneficially in accordance with the practice of injecting water into internal combustion engines for added efficiency.

The present application is a continuation in part of my co-pending application Serial Number 75,021, filed February 7, 1949, now abandoned.

I am aware that prior to my invention, other types of machines have been made that will convert a gaseous and hydraulic pressure to a mechanical energy, and still others which will convert mechanical energy to a gaseous or hydraulic pressure, using shafts, keys, gears, and various types of rotors, etc. Therefore, I do not claim the aforementioned mechanical parts broadly; but having thus described my invention, what I claim as novel and desire to secure by Letters Patent of the United States is:

l. A rotary pump or motor comprising a rotor shaft; an elongated cylindrical rotor carried on and rotatable with said rotor shaft, said rotor being formed with an annular fluid space adjacent each end and extending inwardly from the peripheral surface of the rotor, an intermediate annular cylinder space also extending inwardly from said peripheral surface, and a pair of closely spaced longitudinally and oppositely extending port passages running from the bottom surface of said cylinder space to respectively adjacent fluid spaces; a countershaft;

a rotating abutment of cylindrical cross section and having a diameter equal :to that of the bottom surface of the rotor cylinder space, carried on and rotatable with said countershaft in line contact relation with said bottom surface, said rotating abutment being formed with an axially extending, symmetrical peripheral recess of arcuate shape, the innermost part of which is spaced from the bottom surface of the rotor cylinder space a distance equal to the depth of said cylinder space; a piston member fixed to said rotor within the cylinder space and over said port passages, said piston member being formed with an outer coniiguration complementally engaging and spanning the recess of the rotating abutment and having circumferentially spaced nozzle openings in said outer configuration leading respectively to said port passages; and a sealed casing fitting closely over and conforming to the sides and ends of said rotor and rotating abutment, said casing having openings communica-ting separately with each of the annular fluid spaces of the rotor.

2. A rotary pump or motor comprising a rotor shaft; an elongated cylindrical rotor carried on and rotatable with said rotor shaft, said rotor being formed with an annular fluid space adjacent each end and extending inwardly from the peripheral surface of the rotor, an intermediate annular cylinder space also extending inwardly from said peripheral surface, and a pair of closely spaced longitudinally and oppositely extending port passages running from the bottom surface of said cylinder space to respectively adjacent fluid spaces; a coun-tershaft; a rotating abutment of cylindrical cross section and having a diameter equal to that of the bottom surface of the rotor cylinder space, carried on and rotatable with said countershaft in line contact relation with said bottom surface, said rotating abutment being formed with an axially extending, symmetrical peripheral recess of arcuate shape, the innermost part of which is spaced from the bottom surface of the rotor cylinder space a distance equal to the depth of said cylinder space; a piston member fixed to said rotor within the cylinder space and over said port passages, said piston member being formed with an outer configuration complementally engaging and spanning the recess of the rotating abutment and having a pair of circumferentially spaced nozzle openings in said outer configuration leading respectively to said port passages and flaring away from each other as smoothly curved continuations of the adjacent ends of said port passages; and a sealed casing fitting closely over and conforming to the sides and ends of said rotor and rotating abutment, said casing having openings communicating separately with each of the annular iiuid spaces of the rotor.

3. The combination of claim 1 in which the ends of the rotating abutment are conical and the cross section of the annular cylinder space of the rotor is formed for complemental engagement with the portion of the rotating abutment received therein.

4. The combination of claim l in which the rotor shaft is formed with a grooved passage connecting the spaces between the ends of said rotor and the casing.

5. A rotary pump or motor comprising a rotor shaft; an elongated cylindrical rotor carried on and rotatable with said rotor shaft, said rotor being formed with an annular fluid space adjacent each end and extending inwardly from the peripheral surface of the rotor, an intermediate annular cylinder space also extending inwardly from said peripheral surface, and a pair of closely spaced longitudinally and oppositely extending port passages running from the bottom surface of said cylinder space to respectively adjacent sides of said fluid spaces; a countershaft; a rotating abutment of cylindrical cross section and having a diameter equal to that of the bottom surface of the rotor cylinder space, carried on and rotatable with said countershaft in line contact relation with said bottom surface, said rotating abutment being formed with an axially extending, symmetrical peripheral recess of arcuate shape, the innermost part of which is spaced from the bottom surface of the rotor cylinder space a distance equal to the depth of said cylinder space; a piston member fixed to said rotor within the cylinder space and over said port passages, said piston member being formed with an outer configuration complementally engaging and spanning the recess of the rotating abutment and having circumferentially spaced nozzle openings in said outer configuration leading respectively to said port passages; a sealed casing fitting closely over and conform- 9 ing completely to the sides and ends of said rotor rotating abutment, said casing having openings communicating separately with each of the annular fluid spaces of the rotor; and a plate valve segment adjustably supported from the case ing and positioned in cooperative relation to the end of the respective longitudinal port passage in each annular fluid space of the rotor.

6. A rotary pump or motor comprising a rotor shaft; an elongated cylindrical rotor carried on and rotatable with said rotor shaft, said rotor being formed with an annular fluid space adjacent each end and extending inwardly from the peripheral surface of the rotor, an intermediate annular cylinder space of symmetrical trapezoidal cross section also extending inwardly from said peripheral surface, and a pair of closely spaced longitudinally and oppositely extending port passages running from the inner bottom surface of said cylinder space to respectively adjacent sides of said fluid spaces; a countershaft; a cylindrical rotating abutment with conical ends having its outer portion complemental to and coextensive with the cross-section of the rotor cylinder space, and carried on and rotatable with said countershaft, said rotating abutment being also formed with an axially extending, symmetrical peripheral recess of arcuate shape, the innermost part of which is spaced from the bottom surface of the rotor` cylinder space a distance equal to the depth of said cylinder space; a piston member flxed to said rotor within the cylinder space and over said port passages, said piston member 'being formed with an outer configuration complementally engaging and spanning the recess of the rotating abutment and having circumferentially spaced nozzle openings in said outer configuration leading respectively to said port passages and flaring away from each other as smoothly curved continuations of the adjacent ends of said port passages; a sealed casing tting closely over and conforming to the sides and ends of said rotor and rotating abutment, said casing being provided with an opening communicating with each of the annular fluid spaces of the rotor, and said rotor shaft being grooved to provide a passage connecting the spaces between the ends of said rotor and the casing; and a plate valve segment adjustably supported from the casing and positioned in cooperative relation to the end of the respective longitudinal port passage in each annular uid space of the rotor.

7. The combination of claim 1 in which the cylindrical rotor is formed to provide cooling fluid passages on opposite ends of each annular fluid space and in the portion thereof inwardly adjacent the intermediate annular cylinder space, and all said fluid passages are intercommunieating.

8. The combination of claim 7 in which the casing is formed with annular jacket spaces surrounding the cylindrical rotor, and in which the piston member is formed with a fluid passage connected with the said adjacent fluid passages of the cylindrical rotor.

9. A rotary pump or motor comprising a p1u rality of spaced, parallel rotor shafts eduidisn tant from each other; an elongated cylindrical rotor carried on and rotatable with each of said rotor shafts, each of said rotors being formed with an annular fluid space adjacent each end extending inwardly from the peripheral surface of the rotor, an intermediate annular cylinder space also extending inwardly from said peripheral surface, and a pair of closely spaced longitudinally and oppositely extending port passages running from the bottom surface of said cylinder space to respectively adjacent fluid spaces; a countershaft extending in spaced parallel relation to and equidistant from each of said rotor shafts; a rotating abutment of cylindrical cross section and having a diameter equal to that of the bottom surface of each rotor cylinder space, carried on and rotatable with said countershaft in line contact relation with each of said bottom surfaces, said rotating abutment being formed with an axially extending symmetrical peripheral recess of arcuate shape, the innermost part of which is spaced from the bottom surface of each rotor cylinder space a distance equal to the depth of said cylinder space; a piston member fixed to each of said rotors Within its cylinder space and over the port passages thereof, said piston members each being formed with an outer configuration complementally engaging and spanning the recess of the rotating abutment in its turn and having circumferentially spaced nozzle openings in said outer configuration leading respectively to the port passages thereof; and a casing fitting closely over and conforming to the sides and ends of each of said rotors and rotating abutr ment, said casings each having an opening receiving an arcuate segment of the rotating abutment, and fluid inlet and outlet openings communicating respectively with the annular fluid spaces of the rotors.

l0. The -combination of claim 9 in which each rotor is formed to provide intercommunicating cooling fluid passages on opposite ends of each annular iiuid space, the rotating abutment is formed with an annular uid passage, each cas ing is formed to provide fluid passages extending annularly about its rotor and in communi1 cation with said rotor fluid passages, and the opposite ends of the annular uid passage of the rotating abutment communicate with said casing fluid passages.

ll. The combination of claim 9 in which each rotor is formed to provide with its casing annular cooling fluid passages extending radially on opposite ends of each annular fluid space, each pair of said annular passages being connected by a passage adjacent the rotor shaft, in which a centrally discharging centrifugal pump is formed in the outer annular passage and a peripherally discharging centrifugal pump is formed in the inner annular passage of one pair, and a centrally discharging centrifugal pump and a peripherally discharging centrifugal pump are formed in converse relation in the other pair, and each casing is formed with annular cooling 'fluid passages interconnected through the fluid abutment to conduct cooling fluid from one end of the rotor to the other.

AMBROSE WHITE.

No references cited.