US2475247A

US2475247A - Planetary piston fluid displacement mechanism

Info

Publication number: US2475247A
Application number: US536841A
Authority: US
Inventors: Mikulasek John
Original assignee: Individual
Current assignee: Individual
Priority date: 1944-05-22
Filing date: 1944-05-22
Publication date: 1949-07-05
Anticipated expiration: 1966-07-05

Description

July 5 1949 J. MIKULASEK 2,475,247

PLANETARY PISTON FLUID DISPLACEMENT MECHNISM Filed May 22, 1944 3 Sheets-Sheet l July 5, 1949 u J. MlKuLAsEK 2,475,247

PLANETARY PISTON FLUID DISPLACENIENT MECHANISM v Filed May 22, 1944 3 Sheets-Sheet 2 .IuIy 5, 1949. J. MIKULASEK PLANETARY PISTON FLUID DISPLACEMEINT` MECHANISM Filed May 22, 1944 5 Sheets-Sheet I5k I I I I I I I I I IIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIIllllIlIl IIYIIII -IIIIIIIIIII/IIIIIIIIII Patented Jul-y 5., -1 949 PLANETARY PISTON FLUID DISPLACEMENT MECHANISM .lohn Mikulasek, Bellevue, lIowa Application May Z2, 1944, Serial No. 536,841

6 Claims.

`The present invention fis directed to a displacement mechanism yembodying the use of `spiralblades opposit'ely disposed and nested with- 'in a casing with suitable actuating means for `causing `such blades "to rmovably lcooperate and to trap fluid within Vcells formed between the blades and to cause suchiluid to flow from one to the other lof inlet and "outlet openings that `arelocated lin the casing. The present structure set forth in the design ofthe displacementmechanism herein disclosed and described is very sim- `ilar to the displacementmechanisrns disclosed and described in my izo-.pending application S. N. 528,- 304, filed March 27, `1944. The fundamental'principles of the use of oppositelyrelated spiralawith the spirals in each group being angularly'displaced and also with the spirallblades dof one group being offset radially with respect to -the "spiral 'blades vof the other group are all generally and specifically described in `connection with the ,above mentioned co-pending application.

More specifically, one of 'the main objects :of the present invention is'to provide a displacement mechanism having spiral Ablades wherein each blade or each-of thesets of blades of each group are movably'mounted toreduce therelative 1motion vbetween the 'blades by reducingthe eccentricity of `such blades. In Vother words, the :present device-has each oftheloladesmovably mounted in such fashion that the oscillation is accomplished between'the blades byrnoving eachblade or groups ofblades one-half'of the distance normally required by devices wherein .one blade or set or" blades is fixed whilethe other blade or set of blades are solely movable relative to the former.

This relative oscillatory movement 'between the oppositely related blades is'advantageous in elimihating considerable counter-balancing problems which must be consideredto reduce vibrationin such a unit particularly'when the same is being operated at relatively high speeds. This feature or advantage is particularly iwell disclosedin one form of the present device wherein groups o'f spirals or blades are drivenby oppositely disposed eccentrics or cranks, andtherefore it is apparent that .under operation such blades will have equal masses acting in opposition to each other during the oscillation of'such blades.

It is another object of thepresent `invention .to provide la means vin the nature of .a sealing ring that is adapted to move with one .of the sets of 'blades during the oscillation thereof to provide proper communication between the interior of the spiral cellular `chambers andthe dischargeyport l of the pump. l'Such asealing 'ring also provides is obtained of the blade during the continual (Cl. 10S-130) ..2 a means through lthe resilient construction 'embodied therein for exerting axial pressure against one of the sets of spiral -blades to maintain 'the same in-snug operating contact with the `other oppositely `related spiral blades thereby holding such opposit'elyrelated blades in nested and leak- -proofrelationduring the operationof the device.

-Also in connection with the ab'ove'resilient axial pressure, other additional resilient `means 'is disclosed for the purpose of maintaining the respec- -tive convolutions of one of the sets of spiral Another object ofthe `present invention vis to `provide a ydisplacementmechanism wherein the blade supporting discs are bothrotatably mounted in ofi-set relation for carrying 'their corresponding blade `or sets of 'spiral blades in continuous `rotative motion. vHowever, insuch construction,

the generating centers of each of the blades or common vthereto lare offset with respect `to the center of rotation 'of the adjacent vdisc supporting such blade or blades whereby a true oscillation rotation of the disc. Therefore, by offsetting each 'of the vdiscs a predetermined amount, 'and by offsettingI the blade 0r blades of each disc with Athe generating center common tosuch blades eccentrically disposed with respect to the center of rotation it is possible to obtain the rotational movement of the .discs wherein each of the oppositely relatedblades or sets ofvblades are caused to oscillate one-'half of the distance between the spaces of adjacent convolutions of the blades. Furthermoraby using moreblades in each group 'it is posibleto substantially reduce the vibration of the'displacem-ent mechanism to .a Verymini- 'mum inasmuch as the-distances between adjacent `corrvolutions will thereby alsobe reduced.

In displacement mechanisms using .dual rotatingxdiscs for .obtaining the necesaryoscillation `andpumping action of the coacting spiral .blades of each .disc .it is important vto drive bothy of .the discs at constant and synchronized speeds inasmuch as any variation of one of the .disc .blade .units with respect to the other discblade Aunits would cause binding between convolutions of the spiral blades and interfere with the .operation of the pump. It is therefore .another object `of this .invention to provide a driving means for actuating the discs to positively cause concerted movement of both discs and therefore .of thev nested blades of each disc in synchronized speed relation to obtain the highest eiciency possible in a device of this kind.

As will be understood by referring to the drawings and to the co-pending application hereinbefore designated, it will be obvious that as the blades are rotated the sizes of the plurality of cells between the coacting convolutions of the sets of blades will diminish from the radially outer periphery of such blades to the center thereof. However, as these cells are decreased, the action is successive in nature and the fluid trapped within the cells will be steadily compressed so that the relative pressure difference between each successive cell during the progress of this compression will be relatively small counteracting leakage of fluid from the higher pressure cell to the lower pressure cell.

Furthermore, when the displacement mechanism is being operated at higher speeds any such possible leakage of fluid from one of the higher pressured cells to the lower pressured cells will be substantially negligible.

The above mentioned theory augmented by the introduction of resilient means such as referred to for maintaining the blades in nested relation and also the additional means for convolutionally maintaining such blades in operative contact produces a device which is highly efficient and relatively simple in construction.

All other advantages and features not hereinbefore referred to shall be subsequently set forth in the following detailed description having reference to the several illustrations in the accompanying drawings.

In the drawings:

Fig. 1 is a cross-sectional view taken transversely to the axis of a displacement mechanism of the present construction and substantially as viewed along the line I I in Fig. 2;

Fig. 2 is a vertical cross sectional view as taken substantially along the diameter of the pump as viewed on line 2 2 in Fig. 1;

Fig. 3 is another cross-sectional view of a. modified construction of displacement mechanism also taken transversely to the axis of the device and substantially as viewed along the line 3 3 in Fig. 4;

Fig. 4 is a vertical cross-sectional view taken approximately along the line 4 4 in Fig. 3;

Fig. 5 is another transverse sectional view of still another modified construction as viewed substantially along the line 5 5 in Fig. 6;

Fig. 6 is a horizontal cross-sectional view through the device illustrated in Fig. 5 and as taken substantially along the line 6 6 therein; and

Fig. '7 is a fragmentary sectional view taken substantially along the lines 1 1 in Figs. 5 and 6 to illustrate certain details of construction.

It is to be understood that the displacement mechanism of the present invention may have many uses. Although the device has hereinbefore been referred to as a pump, it is also possible to use the displacement mechanism as a blower, compressor, booster pump, vacuum pump, aspirator or in other similar capacities. Furthermore, the fluids being used may vary in nature. For example, if the device is being used as a motor it is possible to supply the same with fluid under pressure that may be air, vapor, thermally heated fluid or expansive gases such as can be vsupplied by internal combustion means, etc.

Therefore, referring to Figs. 1 and 2, the pump is generally indicated by the reference numeral Ill and is enclosed by a casing made in two separable sections I I and I2 respectively, for purposes of assembly. A fluid opening I3 extends from the upper periphery of the pump while a substantially axially disposed opening I4 is provided in the wall of the section I2 of the casing. Disposed within the connes of the casing are the discs I5 and I6, disc I5 being adapted to carry the spiral blades I1 and I8 while the disc I6 carries the

spiral blades

20 and 2|. The discs I5 and I6 are disposed in parallel spaced relation as best shown in Fig. 2 with the blades of one disc oppositely disposed and nested within the convolutions of the blades of the other disc. Furthermore, as illustrated in Fig. 1 it will be noted that the blades I1 and I8 of the disc I5 are disposed in 180 degree angular displacement with respect to each other while the

blades

26 and 2| of disc I6 are also similarly located in relation to their supporting disc. The number of blades in each group may be increased in which case the angular displacement will be equal to 360 degrees divided by the number of blades. Therefore, by using four blades the relative angular displacement therebetween will be degrees.

The mounting means and the mechanism for oscillating the discs I5 and I6 is best illustrated in Fig. 2. A pair of

shafts

22 and 23 are mounted in the casing walls and extend therebetween for driving the eccentrics 24 and 25 adjacent the wall of section I2 of the casing and also the

eccentrics

26 and 21 disposed adjacent the wall of section Il of the casing. The disc I5 is provided with a pair of

bosses

28 and 30 which act as followers, such bosses having the

eccentrics

26 and 21 nested therein. Similarly, the disc I6 is provided with bosses such as 3! and 32 for cooperating with the eccentrics 24 and 25 in a similar manner. Obviously rotation of

shafts

22 and 23 will cause the eccentrics connected with each shaft in degree offset relationship to move the discs I5 and I6 toward and away from each other in oscillatory fashion to produce the pumping action within the cooperating spiral blades of each of said discs. Inasmuch as

shafts

22 and 23 rotate on iixed axes, each disc is provided with openings to permit oscillation of the discs relative to the shafts. Disc I 5 has openings 33 and 34 while disc I6 has

similar openings

35 and 36 for such clearance purposes.

Gears such as 31 and 38 are conveniently secured to

shafts

22 and 23 in any suitable manner, and such gears are driven by a common gear 40 secured to and driven by a shaft 4I that may be connected in any desirable fashion to a source of power.

Each of the eccentrics such as 24 and 25 are provided to carry springs 42 and 43 which react between the eccentrics 24 and 25 and their

respective shafts

22 and 23 to force the disc I6 radially in a direction to maintain contact between the abutting portions of the convolutions of the coacting spiral blades. It will be seen that each eccentric 24 and 25 is slotted as at 44 and 45 for straddling the fiat portions 46 and 41 on each of the

shafts

22 and 23 respectively. Since the contact points between the respective blades will always be in the direction of the high points of the cams 24 and 25, it is seen that the springs 42 and 43 will always act in the same direction as the radially aligned points of line contact between the convolutions of the respective blades.

By the same principle it is obvious that the cam.

pyridine? `illernbers "26 and "i1 may Valso be provided "with similar resilient means to "urge the blades f-If and I8 of the disc 'l5 into operativecontact with their `mating' Ablade convolutions of the opposite disc i6.

inasmuch as the disc i6 oscillates Iduring the ioperaion of the puinp,fit is necessary toprovide somefform of sealing means between suchldisc `'and the wall ofsectio'n -I 2 of the casi-ng to provide suitable communicating means between the in t'erinr o'f the pump 'blades andthe Aports l! tfor col'lveyfir'ir,r iiuids. Therefore a sleeve such as is snugly fitted Awithin the vopening 50 provided in the disc I6 and is ilanged as Aat 5i to 1provide an annular leg which is acted upon by twoor

more springs

5,2 which `are carried Aby the disc 'l5 in the manner best illustratedin Fig-2. Not

only does this sealing means described forrna gap between the interior of the pump andthe opening i4, but the A*salme also provides a r'eactionary means which causes the dis-c foto be urged axially of the pump for n'naintaining the spiral blades in operative end to end nested 're'- lation during the operation-of the pump.

Withthe construction of pump above described and disclosed in Figs. l andr2, it will be seen that upon operation of this pump and due to the oppositely related `'positions of the eccentrics vthereof that `the two *discs and their respective 'blades will at all times "be-operated in radially opposite directions therebyneutralizingvibratory action due to this motion.

VIn the modilied construction of pump'illustrated in Figs. 3 and 4 the casing generally indicated at 55 and comprises the two sections "56 and 51 that are conveniently connected and have a port at the upper periphery of the pump as indicated at 58. A pair of discs 6i] and 6l are parallelly disposed within the 'casing similarlyto the discs l5 and I 6 in the previously described pump but inthe latter case referringto Figs. `3 and 4, the disc 60 is mounted for rotation about an axis a. while the disc El is mounted for rotation upon an axis b, said axes being offset in the manner shown yin Fig. 4. As seen in Fig. 4 the disc Gil terminates axially in a sleeve such as 62 which is journaled in a bearing boss 63 connected with the wall of section 56 of the pump casing 55. A pulley wheelsuch as Gli is keyed at 55 to the sleeve 62 for rotatably driving disc 60 upon its axis a.

The axial portion of the wail casing `section 51 terminates in a tubular port 65 determined by the bearing sleeve 61 which supports the disc 6l by means of sleeve"68 for rotation about the axis o. The inner end of the sleeve 68 is closed as at 10 and a plurality of peripherally located holes such as 1| provide communicating ports between the interior of the pump blade chamber and the port 66.

In this construction, each disc carries two or more spiral blades in cooperative engagement as described in connection with Figs. 1 and 2 and the blades carried by the disc 'ED are designated by 12 and 13 while the blades carried by the disc 6| are designated as 14 and 15. However, in the construction in Figs. 3 and 4 it isse'en that the discs 60 and y6l are vcontinuously rotated about individually x'ed axes. In lthis construction, however, the spiral blades are offset with their respective generic centerseccentrically displaced with respect to the centers *oi rotation of the respective discsill and l'l which carry vsuch blades. The same actoniis "obtained'as inthe l"form described in yconnection with Figs. 'l and "2 but 'the in Figs. 3 and y'f4'obtains"this action tby l. 'continuous 'revolution of the iworklng parts `-of thepuinp. v'Thief-being the 'case it is necessary'tlrt both the discs 60 and 6 1 "-aredriven at the same speeds. Such synchronization of speed may-be obtained with various forms of mechanisms'but in the "present casejuniversal means suchfas indicated generally *at Y1B is `incorporated to establish such Ia drive. A-disc l11 vhas `a stem -18 located'within the sleeve 82 andl a set screw L811 -Yis adapted Vto position the stem 18 `'within the vsleeve '62 Ywhile the -nut 8l threaded upon the end 82 of 4'the' stem 18 'provides a means for 'locking vsuchstem and its attached disc '11 in xed angular relation with respect -to the sleeve -52 'and also thedi-sc.

The'faceifof-disc '11 is provided with a sli'deway i'B33 while the closed `end 10 of ythe'sleeve 68 is provided'wth-asimilar slideway 84 disposed'at right angles tothe slideway83. A circular disc is=interposedibetweenfthe "falce of the disc 11 and the closed end 10 of the sleeve -68 and disc 85 'has slots 8\6"andi1`in' the 'opposite faces Athereof for coactingwithv'the slideways 83 and 84th provide a universal -drive between the blade carrying' discs lill and 81| respectively Therefore,y as `*the 4pulley-wheel'164 is 'rotated by suitable AfbeltIr-ieans each'of the discs 16D and'fGl fvwill be rotated in ian'gular s'ynchronism causing 'the blades'o'f each disc to 'oooperatel'and move in eccentric pathsfddeto their Ioffset relation of their'resepctive'generic centers 'with lrespect to the axes of rotation-*thereby obtaining fluid-compression "as desired. Afny :angular adjustment necessary'between ltheA oppositely disposed spiral blades Ito obtain the correct contact between the respective convolutions-oTsuoh blades may easily be had by adjusting the vset-screav 8U 'andi-by locking the disc"6'01and-'its Acorresipondinfg blades by means of "the mitm to `maintain such .contacting relation 'between the' blades.

Referring now to'Figs. 5,'-6` andi? another modied construction' of displacement "mechanism :is shown having asepafiable'casing :consisting 'of section-sf' :and'fl suitably 'fastened Ytogether' b'y any desirable means. In this case, "the `dises hereinbefore refered to Ain connection Vwith `the other constructions -Aare -rsupplanted "by y-a ypair o'f gears 92 and 293 tor-'carrying the spiral blades 9495 and1 96`91resp`ectively- An offset shaft 98 carries gears f9f9an=d U00 lor driving the-'gears 92 and93 respectively. f'lhis produces a drive which synchronizes @the motion ofthe gears 92 and 93 which here act in the capacity of the discs formerly explained. `Such `gears will -o'bviously move the blades -of-'eafch oppositely related set thetdresiredlmanner. In 'this construction the blades `will :also be olset asin the 'form described in connection with Figs. 3 and 4, such blades being eccentric'ally disposed with respect to the axes' of rotation of the gears whereas `the actual 'motion of veach lof "the .blade sets will be eccentric relatively'to each vother `to obtain the pumpin'gfaction. 'In'this design as well a's vthat illustrated in Figs. 3 and "4 the foil'set :of each set of blades is such that the actual eccentricity fof the blades in one set will'be'fone-'half the radial. distances between ada-oent convolutions of 'the blades.

It is through this rotary motionv that :the os` cillatory motion y'-o'f fthe `"blades is obtained, and i='t"w'il l` also 4be "seen that inthesa-me instance `as in 'thers't construction'wherein the blades move radially towardieah otherland radially Aaway from each "other during lopera-tion, reducing v.

7 bration, the same mechanical equivalents exist in this latter construction of Figs. 5 to 7 inclusive inasmuch as the blades act in the same manner although the bodily rotation thereof is continuous. This also applies to the construction in Fics. 3 and 4.

Referring again to Figs. 5 and 7 inclusive, it will be seen that a peripheral port is provided for fluid passage into the casing whereas another `port |02 is provided as shown in Figs. 6 and 7 for fluid discharge purposes. A sleeve member |93 provides the walls of the port |02 and extends inwardly into the casing to form a bearing |94 for rotatably supporting the hub of the gear 92. Suitable screws or other fastening means such as |00 may be used for securing the sleeve |03 to the side wall of the casing section 90.

A plug such as |07 is secured to the wall of casing section 9i as by means of screws |08 and has an nwardiy extending sleeve member ||0 providing the bearing means for the hub of the gear 93. The flanged portion H2 of the plug |07 has an annular gasket ||3 for sealing the opening llt in the wall of casing section 9|. Similarly, the flange l l5 of the port sleeve |93 is also adapted to seal the opening ||9 in the wall of casing section 99 by means of a suitable gasket such as l il. Furthermore, it is to be noted that these sections consisting of the sleeve port |03 and the plug member |07 are made to be interchangeable so that the discharge port may be located at either side of the pump casing as needed by conditions of operation. It is also possible to use two ports such as defined by the sleeve |03 in the event that the pressures are great enough to deliver fluid from both sides of the casing under certain conditions of operation.

By referring to Fig. 7, it will be seen that the gear 92 is adapted to rotate about the axis C while the gear 93 is adapted to rotate about the axis d to obtain the eccentricity relation somewhat as shown in Figs. 3 and 4. It will also be noted as best illustrated in Fig. 5 that the gears 99 and |09 are located at a point where the pitch circles of the

large gears

92 and 93 coincide producing a proper driving relationship between such eccentrically located gears. It is also possible to locate the offset shaft 90 at 180 degrees to the position indicated in Fig. 5 for driving the

gears

92 and 93. Or, if desired, it is also within the purview of the present invention to locate two units such as the shaft 99 and gears 99 and |00 at both sides of the pump illustrated in Fig. 5 to obtain a dual driving relationship.

It is to be understood that the foregoing description and disclosures are all more or less specically directed to exemplary constructions of the present displacement mechanism and that various changes and modifications are contemplated which will produce equivalent mechanisms or mechanical structures that shall function or produce the same operative requirements in a like manner as will the mechanisms described. It is therefore obvious that the present form, construction, or combination of parts described and illustrated are not to be limited to the exact disclosures excepting insofar as such structures shall be defined and determined by the breadth and scope of the appended claims.

I claim:

1. In a fluid displacement device having a casing with a pair of openings therein, a pair of movable discs in said casing and disposed in parallel spaced relation with respect to each other,

a plurality of spiral blades of equal thickness fil throughout their lengths carried by each disc in equal angular spaced relation, the blades of one disc being radially offset with respect to the blades of said other disc, said blades being nested between said discs with the convolutions of the blades on one dise substantially in contact with the convolutions of the blades on the other disc to provide cells between said blades, reactionary means interposed between a wall of said casing and one of said discs tc urge the latter and its connected blades axially toward the other of said discs and its connected blades to maintain said blades of each disc in nested leakproof relation, and further reactionary means connected with one 0f said discs to maintain the contacting p0rtions of said convolutions of the blades on said one disc in leakproof contact with the convolutions of the blades of the other of said discs, said latter reactionary means being adapted to follow the plurality of aligned contacted points of the respective convolutions of said groups of blades during the movement of said discs, and actuating means for moving said discs to progressively trap fluid within said cells and to conduct said uid from one to the other of said casing openings.

2. In a fluid displacement device, a casing having a pair of openings, two sets of coacting spiral blades having the blades of each set displaced in equal angular relation with respect to each other, said blade sets each being offset radially with the convolutions of one set of blades in contact with the convolutions of the other set of blades to provide cells between said blades sets, oscillatory supporting means f or each set of blades respectively, and actuating means to cause said supporting means to oscillate the blade sets and thereby trap iluid within said cells to conduct the iiuid from one to the other of said openings through said casing, said actuating means comprising drive means including spaced eccentrics for each blade set, the eccentrics for one blade set being oppositely positioned from the eccentrics of the other blade set, and follower means connected with each set 0f blades and operatively connected with the eccentrics for each set of blades respectively to cause said blades to oscillate whenever said drive means functions.

3. In a fluid displacement apparatus, a casing having an inlet and an outlet, a pair of spaced parallel and rotary disks in said casing, said disks having spiral blades extending in overlapping relation, the blades of one disk being radially offset with respect to the blades of the other disk, each disk having a pair of spaced cup-like bearings upon its outer surface, the bearings on one disk being radially oiset with respect to the bearings on the other disk, cams rotatably mounted in said bearings, the cams on one disk being oppositely disposed with respect to the cams on the other disk, a pair of driving shafts, each connecting a cam on one disk with the cam more directly opposite on the other disk and means for rotating said shafts in opposite directions.

4. In a fluid displacement apparatus, a casing having an inlet and an outlet, a pair of spaced parallel and rotary disks in said casing, said disks having spiral blades extending toward each other in overlapping relation, the blades of one disk being radially offset with respect to the blades of the other, a pair of spaced shafts journalled in said casing and extending through said disks, driving connections between said shafts and one disk for moving said disk in one direction and driving means between said shafts and the other disk for forcing such other disk in the opposite direction.

5. In a fluid displacement apparatus, a casing having an inlet and an outlet, a pair of spaced parallel and rotary disks supported in said casing, yielding ineans between one disk and the adjacent wall of the casing to allow lateral movement of such dislz, said disks having spiral blades exm tending in overlapping relation, a pair of spaced driving shafts joulnalled in said casing and extending tin'ough said disks, yielding driving means between said shafts and one of said disks and eiective for shifting such disk in one direction, and driving connections `netween .said shafts and the other disk effective for shifting such disk in the opposite direction.

6. In a fluid displacement apparatus, a casing having an inlet and an outlet, a pair of spaced parallel and rotary disks mounted in said casing, spaced parallel shafts journalled in said casing and extending through said disks, cams secured to said shafts in operative relation to said disks, the cams engaging one disk being oppositely di rected with respect to those engaging the other disk and yielding means between one of said disks and the adjacent Wall of said casing.

JOHN MIKULASEK.

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

UNITED STATES PATENTS