US2974644A - Fluid motor - Google Patents

Fluid motor Download PDF

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US2974644A
US2974644A US659538A US65953857A US2974644A US 2974644 A US2974644 A US 2974644A US 659538 A US659538 A US 659538A US 65953857 A US65953857 A US 65953857A US 2974644 A US2974644 A US 2974644A
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fluid
shaft
blocks
chambers
blade
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US659538A
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Michael J Celovsky
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IND TOOL ENGINEERING Co
INDUSTRIAL TOOL ENGINEERING Co
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IND TOOL ENGINEERING Co
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08Characterised by the construction of the motor unit
    • F15B15/12Characterised by the construction of the motor unit of the oscillating-vane or curved-cylinder type

Description

March 14, 1961 M. J. CELOVSKY FLUID MOTOR 3 Sheets-Sheet 1.
Filed May 16, 1957 LIVE 27 far Mme 45.: l/ (a own M. J. CELOVSKY FLUID MOTOR March 14, 1961 3 Sheets-Sheet 2 Filed May 16. 1957 z/ C; avsky .Zzzrarzfar Mex/4E March 14, 1961 J, CELQVSKY 2,974,644
FLUID MOTOR Filed May 16, 1957 3 Sheets-Sheet 3 LIZ "E17 fur MCAMEL J CE'LOl/JAY 2,974,644 FLUID MoToR Michael J. Celovsky, Detroit, Mich., assignor to Industrial Tool Engineering Company, Detroit, Mich., a corporation of Michigan Filed May 16, 1957, Ser. No. 659,538
'1 Claims. (Cl. 121-75) This invention relates to fluid motors and more particularly to a multiple stage fluid motor for assuring continuous rotation of a driven member or shaft structure.
An object of this invention is to provide an improved fluid motor which, by virtue of its mechanical construction lends itself to ease and economy of manufacture.
Another object of this invention is to provide a fluid impeller motor wherein one or more and preferably two juxtaposed rotors are connected to a driven member and are so arranged that one will trail the other to assure continuous rotation of the driven member.
In accordance with the general features of this invention, there is provided in a fluid motor, juxtaposed motor blocks having axially aligned shaft bores, a plurality of fluid impeller chambers between said blocks and into which fluid under pressure is forced, a, driven shaft extending through the block bores and having rotors on the shaft one in each chamber, each rotor having a vane extending radially therefrom with its free end bearing against the wall of the chamber, the vane of one rotor being in predetermined trailing relation to that of the other, a dividing blade projecting radially into each chamber and against which fluid under pressure is forced, and means for projecting each blade into and out of its chamber in a predetermined relation to the impelling action of the associated vane in the chamber and so that as one blade is being retracted out of its dividing position to permit passage of the. associated vane thereby, the other blade is projected into dividing position, the shaft being thus subjected to a substantially continuous rotary action by the action of the fluid against the vanes on the rotors.
, Another feature of the invention, in the foregoing fluid motor, relates to having the withdrawal of each dividing blade arranged to occur with respect to the withdrawal of the other at substantially 180 intervals in the shaft rotation whereby continuous rotation of the driven member is assured. I
Still another feature of the invention relates to the novel arrangement of ports and passages so as to communicate with fluid and outlet passages in the driven shaft structure and so as to be progressively uncovered and closed by the rotation of the shaft structure itself whereby the driven member controls the delivery of fluid to and from the impelling chambers as well as the means for projecting and withdrawing the dividing blades with respect to the impelling chambers. I
Another feature of the. invention relates to the manner in which the impelling chambers are sandwiched between juxtaposed blocks through which the connected shafts or driven members project, the blocks having similar sets of ports and passagesbut one set being arranged so as to operate in trailing relation to that of the other with respect to the withdrawaland projection, of the, dividing blades extending into the respective, impelling chambers.
Other objects and features of this invention may more fully appear from the following detailedde'scription taken sited States Patent in connection with the accompanying drawings which illustrate a single embodiment thereof and in which:
Figure 1 is an enlarged cross-sectional view on substantially the line I-I of Figure 2 broken away and partly in elevation taken through a fluid impeller motor embodying the features of this invention and with the driven member shown in elevation and the dotted lines in the driven member illustrating the passageways therein;
Figure 2 is a bottom elevational view of the structure shown in Figure 1;
Figures 3, 4, 5 and 6 are sectional views taken on substantially the lines IIIIII, IV-IV, V-V and VI-VI in the lefthand block of Figure 1 showing the manner in which ports are arranged to communicate with the longitudinal inlet and outlet passages of the driven shaft member;
Figure 7 is a vertical sectional view taken on substantially the line VII-VII of Figure 1 looking in the direc tion indicated by the arrows and partly in elevation and showing the means for projecting and withdrawing a dividing plate from the lefthand fluid impeller chamber; and
Figure 8 is a somewhat schematic view showing the overlapping relationship of fluid passages with reference to the operation of the vane and blade means.
As shown on the drawings:
A fluid driven shaft structure is provided which in the illustrated form preferably comprises driven members or shafts 10 and 10 which shafts are coupled together in a manner hereafter set forth. Axially extending shaft I bore structure is provided and which defines aligned bores 11 and 11 through which the shafts or driven members 10 and 11' extend. The bores 11 and 11 are disposed in two juxtaposed motor blocks 12 and 12 together comprising a motor housing. As shall become more evident hereinafter, the ports and passageways in one block 12 are substantially similar to those of the other block but are so arranged as to enable a controlling operation of blade projection means to be hereinafter described. In other words, the rotation of the shaft itself controls the connecting and disconnecting of inlet and discharge fluid or hydraulic oil passageways 13 and 14 in the block 12 with longitudinally extending fluid inlet or pressure and outlet or tank in the shaft 10.
The above described axially extending shaft bore structure also defines complemental and aligned impelling chambers 17 and 17', in which are disposed rollers 18 and 18', the chambers being sandwiched between the two juxtaposed blocks 12 and 12' The rollers are carried in opposed relation at the ends of the coupled shafts 10 and 10 for driving the same. Also associated with each of the rotors 18 and 18 is blade projection and retraction means designated generally by the reference characters 19 and 19.
Now, it is believed that a detailed description of the lefthand block 12, its associated rotor 18 and its blade projection and retraction means 19 will sufiice for an understanding of the other half of the numerals in describing each side of the structure with the exception that the numerals employed on the righthand side of Figure 1 will be primed wherever the parts correspond to those on the lefthand side.
A manifold 29 is fastened by means of stud bolts 21 to the motor blocks 12 and 12' which bolts and manifold also maintain the blocks in abutting assembly. Carried by the manifold 20' are the blade projection and retraction means 19 and 1 9. Extending through the manifold are bores 22 and 22 which bores are in vertical. alignment with bores 23 and 237 in the motor blocks 12 and 12'. The bores 22, 23 and 22, 23' are also in vertical alignpassageways 15 and 16, respectively,
ment with the impelling chambers 17 and 17', respectively.
Disposed within the bores 22 and 22' are vertically movable pistons 24 and 24 each having an O-ring seal in assembly therewith. Extending downwardly from the pistons 24 and 24 are guide pins 25 and 25' with the guide pins having springs 26 and 26 wrapped therearound. The lower end of the guide pins bears against plugs 27 and 27 which seal the bores '22 and 22'. Disposed between the plugs and the guide pins are piston impact absorbing members preferably comprised of nylon and the like identified at 23 and 28. Extending upwardly from the other side of the pistons 24 and 24 are piston rods 29 and 29'. The piston rods 29 and 29 extend upwardly into the bores 23 and 23' having connected at the free ends thereof slidable blades or partitions or axially spaced partition blade structures indicated generally at 30 and '30 which are movable with the pistons into and out of engagement with the rotors 18 and 18' according to a predetermined timing cycle. -At the junction of the manifold 20 with the blocks 12 and 12, and more particularly at the junction of the bores 22, 23 and 22, 23' are suitable glands 31 and 31. It will be appreciated the plugs 27, 27' and the glands 31 and 31' serve as the end walls of the cylinder bores 22 and 22' between which the pistons 24, 24 are freely movable. In addition, the piston rods 29 and 29 extend through the glands 31 and 31' and there are chambers 32 and 32' defined between the glands and the blades 30 and 30.
A coupling member 33 including fixed and rotatable portions 34 and 35 are positioned between the blocks 12 and 12' having pins 36 for connecting the fixed portion 34 to blocks and pins 37 for connecting the rotatable portion with the rotors 18 and 18. Between the fixed and rotatable portions 34 and 35 is an O-ring seal 38.
Also provided in the coupling member '33 is a T-shaped slot 39 in communication with chambers 32 and 32. The T-shaped slot is in connection with a T-shaped slot 40 in the manifold to permit free movement of air in the movement of the blades '30 and 30'. The glands 31, 31' are provided with O-ring seals 41, 41' and 42, 42' to prevent fluid from entering into chambers =32, 32.
Carried Within slots (Figure 7) in the rotors 1'8, 18' and secured in position therewith by screws 43, 43 are radially extending vanes 44, 44. The vanes may trail one another by 180 thereby increasing the torque and assuring continuous rotation during the withdrawal and extension of the blades 30, 30.
To operate the means 19, 19 and the vanes 44, 44 a system of fluid inlet and discharge passageways is provided. To this end, the shafts 10, the rotors 44, 44' and the coupling are provided with the continuous pressure and tank passageways and 16. For admitting pressurized fluid into the chambers 17 and 17' and driving the vanes 44, 44', the shafts 10, 10 are peripherally notched or grooved at 45, 45' providing axially spaced shaft fluid passage areas a predetermined distance (Figure 3) about the periphery thereof so as to be able to receive pressurized fluid from the pressure inlet 13. Connecting the notches 45, 45' with the passage 15 are ports 46, 46. Radially aligned with the notches or grooves 45, 45 are T-shaped passages 47, 47 in the blocks 12, 12' which passages are in direct connection with the chambers 17, 17. As the spaced vanes 44, 44' are driven towards the blades 36, 30 fluid on the downstream side of the vanes 44, 44 is channelled into the discharge ports 48, 48 provided in the blades 30, 30. The fluid thus directed is channelled through passage 49, 49 into passages 50, 50' in the respective motor blocks 12, 12'. The fluid moving through-the passages 50, 50' is directed into annular grooves 51, 51' in the shafts through ports 52, 52' (Figure 6) into tank or discharge passageway 16. Provided in the motor block 12' is a tortuous discharge passageway 53 linked with the tank outlet 14.-
. 4 The shaft 10 is provided with an annular groove 54 (Figure 1) in direct connection with the passageway 53. The groove 54 is linked with the tank or discharge passageway 16 by a port 55. Thus, fluid discharged from the chambers 17, 17 travels through ports 48, 48', blade passageways 49, 49', block passageways 5t 5t), shaft grooves 51, 51, ports 52, 52', shaft discharge passageway 16, port 55, groove 54, block passageway 53 and out through the tank outlet 14. For controlling the fluid discharge flow metering pins 56, 56' and'57 have been provided. Metering pins for controlling rotor speed extend upwardly through the manifold 20 into block passageways 50, and have adjusting nuts 58, 58' mounted exteriorly of the manifold 20 for adjusting the pins. Metering pin 57 serves primarly to control the discharge flow to the tank and extends into block discharge passageway 53 adjacent outlet 14.
For operating the blade projection and retraction means a system of fluid passageways have been provided. To this end, shaft pressure ports 59, 59' and 60, 60 are provided in the shafts 10, 10 linking the pressurized axially extending shaft passageway 15 with peripheral shaft grooves 61, 61 and 62, 62' (Figures 1, 4 and 5). Also provided in the shafts 10, '10 are shaft discharge ports 63, 63 and 64, 64 linking the shaft discharge or tank passageway with discharge shaft grooves 65, 65' and 66, 66.
The motor blocks and manifold are provided with angularly shaped passageways 67, 67' and 68, 68' linking grooves mentioned in the paragraph above with the cylinder bores 22, 22 on opposite sides of the pistons 24, 24.
To extend the blades 30, the operation of blade 30' being the same, pressure fluid is admitted through inlet 13 into shaft passage 15 into port 59 outwardly into groove 61 and then into angularly shaped passage 68 into the cylinder defined by the bore 22 causing the piston 24 to move upwardly. As the piston 24 is moved upwardly fluid in the cylinder on the opposite side is urged outwardly through angularly shaped passage 67 into shaft groove 66 through port 64 and into shaft fluid discharge passage 16 through tank outlet 14 in the same manner previously set forth. As the blade is extended against the rotor 18 fluid from chamber 17 moves into blade passage 49 through one of bleed ports 69, 69 provided on the blades 30, 30'. To retract the blade 30 pressurized fluid is admitted from shaft passage 15 through port 60 into shaft groove 62 and then into block passage 67 into the cylinder thereby urging the piston and the blade away from the rotor 18. As the piston is being moved away from the rotor 18, fluid is drawn from passage 49 through the bleed port 69 on the blade 30 into chamber 17. Fluid on the downstream side of the downwardly moving piston moves outwardly through angularly shaped passage 68 into groove 65 and then into port 63 which is connected to the discharge shaft passage 16.
The springs 26, 26 serve to force the blades into contact with the rotors when starting the motor.
In view of the foregoing, it will now be appreciated there is only one pressure and one tank line external connection. All other connections are internal. Each of the rotors and shafts has two lines parallel to the axis thereof. One line is connected to pressure, the other one connected to thetank. The grooves in the composite shaft and rotor assembly line up with the passages in the blocks 12, 12, and depending upon the requirements, the length of the grooves may be varied to force the blade piston in or out according to a timing sequence as required. By connecting these grooves with the longitudinal holes or passages by drilling either the pressure or the tank line can be connected. This way, whenever the groove registers with the port, fluid flows and when the groove is interrupted, the port is closed by the cylindrical section between the grooves.
In Figure 8' is" a schematic timing diagram with the cross hatched and the clear-portions representingfth'e pressure and the discharge'areas respectively as defined by the grooves shown also in Figures 3-6. In other words, a comparative analysis of the shaft grooves has been made illustrating the lengths thereof and whether a particular groove receives pressure or tank fluid (Figure 8). The groove area shownin Figure 3 is represented by the internal or radially innermost groove area at 45. Radially outwardly thereof, are three concentric rings having shaded areas corresponding to the groove area shownin Figures 4, 5 and-6 consecutively.
In view of the foregoing it will now be appreciated that since'thevanes are spaced 180 apartand the porting is the same for both rotors, a very high torque at low working speeds may be attained by the instant fluid motor.
Operation Fluid under pressure enters pressure chamber 17 through the passageway or port 47 exerting pressure on the vane 44. The fluid ahead of the vane is forced out through a passageway orport 48 drilled into the blade 30'which in turn communicates with ring groove 51.
As can be seen from Figure 7, when the vane 44 approaches the blade 30 the latter will have to be pulled out of the way by the piston 24. Beforethis is done it will be necessary to shut off the oil flow to port 47 which is accomplished by closing the port 47 by ending the groove 45 and keeping the. groove 45 closed until the vane has passed port 47 and the blade 30 is once more seated against the rotor 18.
The withdrawal of the piston 44is brought about by means of fluid pressure being directed against the upper side of the piston after flowing through the groove 62. At' the same time interval, the bottom or lower side of the piston is exhausted by the action of the groove 65 being in communication with the shaft discharge'passage 16. While the piston 44 is here fluid operated, the piston may also be mechanically operated. The vane 44' is operated the same way as the first vane 44 but the blade withdrawal takesplace 180 later to give high torque at low working speeds;
From the above description it will now be clear that the motor is provided withfluid operable means for rotating the axially spaced vanes and for actuating the axiallyspaced partitions by conveying pressurized fluid from the inlet port directly against the partitions internally of the housing or more specifically against the pistons which are extensions of the partitions. The fluid operable means includes fluid passage areas disposed internally of the motor and which define fluid passages in communication with the inlet and outlet ports with the fluid passages being arranged to convey fluid to drive the vanes and to actuate the axially spaced partitions across the path of the vanes. The axially spaced partitions have some of the fluid passages in communication therewith or in'communication with" the pistons to which they are connected for actuating the partitions. The fluid operable means further includes axially spaced shaft fluid passage areas 45, 45 defining shaft passages which are in periodic communication with the fluid passages in communication with the partitions whereby the partitions may be actuated by the fluid flowing through the shaft and housing passages during the rotation of the out of phase vanes.
The two rotors 18 and 18' are connected by the coupling 33- which also is drilled to connect the longitudinal pressure and tank passages 15 and 16. The coupling construction here shown is used to facilitate machining and assembling but it is understood that it can be altered Without departing from the present invention.
Mounting flanges and take off arrangements are the same at each motor end, thereby permitting mounting of the motor in such a way that the direction of rotation of the driven member may be" reversed without reversing the rotation of the'rotors- In view of the foregoing, it will now be appreciated how a fluid motor may be constructed to develop a very high torque at low'working speeds which motor is of the type which is highly compact, small in size, and can be regulated over a wide range of speeds.
It will be understood that modifications and variations may be effected without departingfrom the scope of the novel concepts of the present invention.
I claim as my invention:
1. In a fluid motor, juxtaposed motor blocks having axially aligned shaft bores, enlarged axially confronting recessed areas disposed in confronting relation at the junction of said blocks, said recessed areas defining a plurality of fluid impeller chambers between said blocks and intowhich fluid under pressure isforced, seal means disposed axially between the impeller chambers to reduce leakage, a driven shaft extending through said block bores and having rotors on said shaft one in each chamber, each rotor having a vane extending radially therefrom with its free end bearing against the wall of the I chamber, the vane of onerotor being in predetermined trailing relation to that of the other, a dividing blade projecting radially into each chamber and against which the associated vane is adapted to force fluid, and fluid means between said blocks and said shaft for projecting each blad'e into and out of its chamber in a predetermined relation to the impelling action of the associated vane in said chamber and so that as oneblade' is being retracted out of its dividing position to permit passage of the as sociated vane thereby, the other blade is projected into dividing position, said shaft being thus subjected to a sub stantialy continuous rotary action by the action of the fluid against the vanes on said rotors.
2. In a fluid motor, juxtaposed motor blocks having axially aligned shaft bores, a plurality of fluid impeller chambers between said blocks and into which fluid under pressure is forced, a driven shaft extending through said block bores and having rotors on said shaft one in each chamber, each rotor having a vane extending radially therefrom with its free end bearing against the wall of the chamber, the vane of one rotor being in predetermined trailing relation to that of the other, a dividing blade projecting radially into each chamber and against which the associated vane is adapted to force fluid, and means for projecting each blade into and out of its chamberin a predetermined relation to the impelling action of the associated vane in said chamber and so that as one blade is being retracted out of its dividing position to permit passage of the associated vane thereby, the other blade is projected into dividing position, said shaft being thus subjected to a substantially continuous rotary action by the action of the fluid against the vanes on said rotors, said shaft also including longitudinally extending fluid inlet and fluid outlet passages and said blocks each having on opposite sides of said chambers ports adapted to communicate with said passages in a predetermined pattern and passageways in said block leading from said ports to said chambers and to said blade projecting means whereby fluid is delivered to and withdrawn from said chambers and from said means in predetermined manner and so that the shaft impelling action of one rotor and vane will overlap thatof the other.
3. In a fluid motor, juxtaposed motor blocks having axially aligned shaft bores, a plurality of fluid impeller chambers between said blocks and into which fluid under pressure is forced, a driven shaft structure extending through said block bores and having portions of said shaft structure in each chamber, said shaft structure having vanes extending radially therefrom with their free ends bearing against the walls of the chambers, the vane in one chamber being in predetermined trailing relation to that of the other, a dividing blade projecting radially into each chamber and against which the associated vane is adapted to force fluid, and fluid operated means for projecting each blade into and out of its chamber in a predetermined relation to the impelling ac tion of the associated vane in said chamber and so that as one blade is being retracted out of its dividing position to permit passage of the associated vane thereby, the other blade is projected into dividing position, said shaft structure being thus subjected to a substantially continuous rotary action by the action of the fluid against the vanes on said rotors, said shaft structure also including longitundinally extending fluid inlet and fluid outlet passages and said blocks each having on opposite sides of said chambers ports adapted to communicate with said passages in a predetermined pattern and passageways in said blocks leading from said ports to said chambers and to said blade projecting means whereby fluid is delivered to and withdrawn from said chambers and from said means in a predetermined manner and so that the shaft impelling action of one rotor and vane will overlap that of the other.
4. In a fluid mechanism, a pair of adjacent blocks with said blocks having axially aligned bores and confronting axially aligned recessed areas on confronting sides of the blocks, shafts disposed in said bores and projecting into said recessed areas with said shafts being cooperable with said recessed areas in said blocks in defining fluid impeller chambers, vanes connected to said shafts and projecting radially outwardly into said fluid impeller chambers, a coupling structure between said blocks separating said recessed areas and said fluid impeller chambers including fixed and rotary portions, a shaft seal between said fixed and rotatable portions separating said fluid impeller chambers, said coupling structure having structure respectively coupling the fixed portion with the blocks and coupling the rotary portion with the shafts, partition blades projecting radially into said chambers against said shafts and with the vanes moving fluid thereagainst, and means for retracting the blades out of the path of the vanes in the rotation of the vanes in said chambers.
5. In a fluid mechanism, a pair of adjacent blocks with said blocks having axially aligned bores and confronting axially aligned recessed areas on confronting sides of the blocks, shaft structure comprised of shafts disposed in said bores and projecting into said recessed areas with said shafts being cooperable with said recessed areas in said blocks in defining fluid impeller chambers, vanes connected to said shafts and projecting radially outwardly into said fluid impeller chambers, a coupling structure between said blocks separating said recessed areas and said fluid impeller chambers including fixed and rotary portions, a shaft seal between said fixed and rotatable portions separating said fluid impeller chambers, said coupling structure having structure respectively coupling the fixed portion with the blocks and coupling the rotary portion with the shafts, partition blades projecting radially into said chambers against said shafts and with the vanes moving fluid thereagainst, and fluid operated means for retracting the blades out of the path of the vanes in the rotation of the vanes in said chambers, said fluid operated means including fluid inlet and outlet shaft passages in said shaft structure and fluid inlet and outlet block passages in said blocks, piston structure mounted on said fluid mechanism with said piston structure being connected to said vanes and with said inlet and outlet block passages communicating with opposite sides of said piston structure for extension and retraction of the partition blades.
6. In a fluid mechanism, a pair of adjacent blocks with said blocks having axially aligned bores and confronting axially aligned recessed areas on confronting sides of the blocks, shafts disposed in said bores and projecting into said recessed areas with said shafts being cooperable with said recessed areas in said blocks in defining fluid impeller chambers, vanes connected to said shafts and pro jecting radially outwardly into said fluid impeller chambers, a coupling structure between said blocks separating said recessed areas and said fluid impeller chambers including fixed and rotary portions, a shaft seal between said fixed and rotatable portions separating said fluid impeller chambers, said coupling structure having structure respectively coupling the fixed portion with the blocks and coupling the rotary portion with the shafts, partition blades projecting radially into said chambers against said rotors and with the vanes moving fluid thereagainst, a third block overlapping said pair of blocks and with means contemporaneously connecting said third block to said pair of blocks while at the same time connecting said pair of blocks against becoming uncoupled, and means for retracting the blades out of the path of the vanes in the rotation of the vanes in said chambers including piston structure mounted in said third block which piston structure is connected to said blades for the reciprocation of the blades.
7. In a fluid mechanism, a pair of adjacent blocks with said blocks having axially aligned bores and confronting axially aligned recessed areas on confronting sides of the blocks, a shaft structure including shafts disposed in said bores and projecting into said recessed areas with said shafts being cooperable with said recessed areas in said blocks defining fluid impeller chambers, vanes connected to said shafts and projecting radially outwardly into said fluid impeller chambers, a coupling structure between said blocks separating said recessed areas and said fluid impeller chambers including fixed and rotary portions, a shaft seal between said fixed and rotatable portions separating said fluid impeller chambers, said coupling structure having structure respectively coupling the fixed portion with the blocks and coupling the rotary portion with the shafts, partition blades projecting radially into said chambers against said rotors and with the vanes moving fluid thereagainst, and means for retracting the blades out of the path of the vanes in the rotation of the vanes in said chambers, said shafts having longitudinal fluid shaft passages and said blocks having fluid block passages with said passages in said shafts and said blocks carrying inlet and outlet fluid to and away from the fluid impeller chambers.
References Cited in the file of this patent UNITED STATES PATENTS 584,560 Robertson June 15, 1897 625,689 Kingsland May 23, 1899 696,612 Walker Apr. 1, 1902 895,861 Hokanson Aug. 11, 1908 1,310,735 Barstow July 22, 1919 FOREIGN PATENTS 901,640 Germany Ian. 14, 1954
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6065289A (en) * 1998-06-24 2000-05-23 Quiet Revolution Motor Company, L.L.C. Fluid displacement apparatus and method

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US584560A (en) * 1897-06-15 robertson
US625689A (en) * 1899-05-23 Rotary engine
US696612A (en) * 1901-02-14 1902-04-01 James C Walker Motor.
US895861A (en) * 1908-01-14 1908-08-11 John Hokanson Rotary engine.
US1310735A (en) * 1919-07-22 Planoqraph co
DE901640C (en) * 1942-05-30 1954-01-14 Aeg Hydraulic motor

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US584560A (en) * 1897-06-15 robertson
US625689A (en) * 1899-05-23 Rotary engine
US1310735A (en) * 1919-07-22 Planoqraph co
US696612A (en) * 1901-02-14 1902-04-01 James C Walker Motor.
US895861A (en) * 1908-01-14 1908-08-11 John Hokanson Rotary engine.
DE901640C (en) * 1942-05-30 1954-01-14 Aeg Hydraulic motor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6065289A (en) * 1998-06-24 2000-05-23 Quiet Revolution Motor Company, L.L.C. Fluid displacement apparatus and method

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