US3574494A - Fluid machine especially adapted for high pressure applications - Google Patents

Fluid machine especially adapted for high pressure applications Download PDF

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Publication number
US3574494A
US3574494A US797415A US3574494DA US3574494A US 3574494 A US3574494 A US 3574494A US 797415 A US797415 A US 797415A US 3574494D A US3574494D A US 3574494DA US 3574494 A US3574494 A US 3574494A
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fluid
links
working
inlet
pivotally
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US797415A
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Friedrich O Bellmer
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Edison International Inc
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Worthington Corp
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Assigned to STUDEBAKER-WORTHINGTON, INC. reassignment STUDEBAKER-WORTHINGTON, INC. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: WORTHINGTON PUMP INC.
Assigned to EDISON INTERNATONAL, INC. reassignment EDISON INTERNATONAL, INC. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: STUDEBAKER-WORTHINGTON, INC., A CORP. OF DE
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/04—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of internal-axis type

Definitions

  • a fluid machine which is operable as a positive displacement pump, or fluid motor, or as a combined fluid motor and pump, and comprises a working member taking the form of a plurality of pivotally interconnected links which divides a working chamber into inner and outer working chambers and is movable through a cycle of operation therewithin to alternately expand and contract respective portions of said inner and outer working chambers.
  • Inlet and outlet passages are provided in fluid flow communication with each of said inner and outer working chambers and are operable to enable the pumping of fluid therethrough when the fluid machine is utilized as a pump, and/or to admit fluid under pressure thereto and exhaust the same therefrom when the fluid machine is utilized as a fluid motor or a combined fluid motor and pump.
  • This invention relates to a new and improved fluid machine which is adaptable for use as a pump or a fluid motor, or as a combined fluid motor and pump.
  • fluid machines of these general classifications are, of course, very well known, it is believed equally well known that there is substantial room for improvement, in a wide variety of areas, with regard to the current, or state of the art, embodiments thereof. More specifically, it may be readily understood by those skilled in this art that although currently available fluid machines of these classifications do offer satisfactory performance, there is, nonetheless substantial room for improvement thereof in such highly significant and, to some extent, interrelated areas as unduly high initial and operational costs, undue machine complexity both in the design and number of working components, unduly high power consumption resulting from high frictional losses, unduly high mass of the moving or working members, unduly high sliding speeds of the working members with attendant high frictional losses and machine component wear rates and requirements for relatively expensive machine component materials of suitable strength and hardness characteristics, lack of machine reliability and difflculty in replacing worn or damaged components, unduly high noise levels, unduly high space requirements and operational weights with regard to the displacement provided thereby, lack of ready and convenient convertability from the performance of one function to the performance of another
  • Another object of this invention is the provision of a fluid machine which embodies an extremely low speed of the working member despite high drive shaft speeds to thus minimize frictional losses with attendant minimization of machine component wear rates.
  • Another object of this invention is the provision of a fluid machine which is of extremely durable design and construction and extremely simple manner of operation, whereby long periods of satisfactory, maintenance-free operation thereof are assured.
  • Another object of this invention is the provision of a fluid machine which requires but a single major working component of very low relative mass which may be readily and conveniently replaced at low cost.
  • Another object of this invention is the provision of a fluid machine of significantly reduced power consumption requirements resulting from the reduced operational friction therefor.
  • Another object of this invention is the provision of a fluid machine which embodies a very low operational noise level.
  • Another object of this invention is the provision of a fluid machine which is of very low relative weight and requires relatively little space.
  • Another object of this invention is the provision of a fluid machine which, without major internal modification, is readily convertible between such applications as a pump, a fluid motor. and a fluid motor driven pump.
  • a further object of this invention is the provision of a fluid machine which is readily and conveniently reversible in operation without any internal modifications and without loss in efficiency.
  • a still further object of this invention is the provision of a fluid machine which is particularly adaptable for use as a high pressure pump and/or a high torque fluid motor.
  • the fluid machine of the invention comprises a housing having an aperture formed therein and a core section disposed within said aperture and spaced therefrom to form a working chamber therebetween.
  • a single working member which takes the form of a plurality of pivotally interconnected links is disposed within said aperture to surround said core at least in part and divide said working chamber into inner and outer working chambers, respectively.
  • Fluid passages are provided to extend through said housing and core, respectively, into fluid flow communication with said outer and inner working chambers and are operative as inlet and outlet passages to result in the formation of outer and inner working sections of the fluid machine.
  • fluid under pressure is introduced through said inlet passages of the respective inner and outer working sections to move said plurality of pivotally interconnected links through repeated cycles of operation thereof and enable the application thereby of rotational power or torque to power takeoff means in the nature of shaft means.
  • pressurized fluid is admitted to one working section to move the plurality of pivotally interconnected links through repeated cycles of operation and pump fluid through the other of said working sections.
  • FIG. 1 is a side elevational view of a fluid machine constructed in accordance with my invention
  • FIG. 2 is a top elevational view of the fluid machine of FIG.
  • FIG. 3 is an end view of the fluid machine of FIG. 1;
  • FIG. 4 is an opposite end view of the fluid machine of FIG.
  • FIG. 5 is an exploded perspective view of the fluid machine of FIG. 1;
  • FIG. 6 and 7 are enlarged view of first pivotally attached portions of the working member links
  • FIGS. 8 and 9 are enlarged view of second pivotally attached portions of the working member links
  • FIG. 10 through 13, inclusive are end views of the fluid machine of the invention with the front plate removed and illustrate one complete cycle of operation thereof;
  • FIG. 14 is an enlarged view of a portion of the fluid machine illustrating the operation of a fluid machine sealing member at an intermediate point during a cycle of fluid machine operation.
  • a fluid machine constructed in accordance with.the teachings of the invention is indicated generally at 2 and may be seen to comprise a generally cylindrical casing 4 which includes, in the manner best seen in FIGS. 1 and 2, a front plate 6, a housing 8 and a back plate 10 maintained in the depicted side-by-side relationship thereof by a spaced plurality of attachment bolt means as indicated at 12 extending therethrough.
  • a drive shaft 14 extends from the back plate through a drive shaft bushing or bearing 16 provided therefor into operative connection with any convenient source of rotational power, as for example, an electric drive motor as indicated at 18.
  • element 18 could, for example, be operated as transducer means in the nature of an electric generator.
  • Spaced fluid conduits 29, 22, 24 and 26 are provided to extend as shown from the front plate 6 and, assuming externally driven rotation of the drive shaft 14 in the clockwise direction as seen in FIG. 4 for use of the fluid machine 2 as a pump, it may be understood that fluid conduits 20 and 24 will function as inlet conduits while fluid conduits 22 and 26 will function as discharge conduits. Conversely, assuming externally driven rotation of the drive shaft 14 in the counterclockwise direction as seen in FIG. 4, fluid conduits 22 and 26 will func tion as inlet conduits while the fluid conduits 20 and 24 will function as discharge conduits, it thus being made clear that the fluid machine of the invention is readily reversible in operation for reasons described in greater detail hereinbelow.
  • the front plate 6 comprises spaced, generally parallel fluid passages extending completely therethrough and formed in substantial alignment and fluid flow communication with the respective fluid conduits 20, 22, 24 and 26. More specifically, and as indicated in dashed lines in the subject FlG., a fluid passage 28 is formed to extend completely through the front plate 6 in substantial alignment with the fluid conduit 20; a fluid passage 30 is formed to extend completely through the front plate in substantial alignment with the fluid conduit 22, a fluid passage 32 is formed to extend completely through the said front plate in substantial alignment with the fluid conduit 24, a fluid passage 34 is similarly in front plate 6 with regard to the fluid conduit 26.
  • the housing 8 is of the depicted, generally torus-like configuration including a relatively large, generally centrally disposed aperture 36 formed to extend therethrough. Fluid passages or slots as indicated at 38 and 40, respectively, and a generally semicircular cutout as indicated at 42, are formed to extend as shown outwardly from the aperture 36 into the housing 8 for purposes described in greater detail herein below.
  • a generally mushroomshaped core section 44 which, as depicted, is formed integrally therewith.
  • the core section 44 may be formed integrally with either of the front plate 6 or the back plate 10, or as a separate member for suitable attachment in the depicted position thereof within the housing aperture 36.
  • the core section 44 may be seen to comprise fluid passages or slots 46 and 48 formed to extend thereinto from the housing aperture 36 for purposes described in detail hereinbelow. It is believed clear that the core section 44 is, of course formed to be of substantially the same as the housing 8.
  • a flexible seal member 50 which may be of any suitable material in the nature, for example, of steel, is disposed as shown atop the core section 44 and maintained thereon by the simple expedient of inserting the respective curled extremities 51 and 52 thereof into notches provided therefor in the said core section.
  • an attachment screw 54 may be provided as shown to maintain the central portion of the seal member 50 in substantial surface contact with the adjacent core section portion.
  • Flexible seal members 56 and 58 are provided to extend as shown over opposed sides of the housing aperture 36 and are also maintained as depicted by the insertion of the respective curled extremities thereof into notches provided therefor in the housing 8.
  • Each of the seal members 50, 56 and 58 is of substantially the same width which is in turn substantially equal to the thickness of the housing 8.
  • a drive shaft bushing mounting aperture 64 is formed as shown to extend through the back plate 10 and it may be understood that a drive shaft bushing or bearing 16 is disposed in the said back plate by the simple insertion or press fitting of the said bushing in the said mounting aperture.
  • a drive pin mounting aperture 66 is eccentrically disposed as shown in the extremity or end face of the drive shaft 14, and a drive pin 68 is provided for disposition, with freedom for rotation, in the said drive pin mounting aperture.
  • a conventional crank-pin assembly may be formed at the extremity of the drive shaft 14.
  • a working member is indicated generally at 70 and comprises four generally curved arms or links 72, 74, 76 and 78 which are shaped as shown and are linked with freedom for pivotal movement therebetween. More specifically, and as best seen in FIGS. 5, 6 and 7, the respective lower extremities of the links 74 and 76 are formed by ball joints or tongues as indicated at 79 and 80, while the respective upper extremities of the links 72 and 78 are formed by sockets or grooves, as indicated at 81 which are complementally shaped and sized with regard to the said link tongues.
  • the respective upper extremities of the links 74 and 76 are formed respectively by somewhat enlarged, generally cylindrical end portions 86 and 88 with end portion 86 fitting into end portion 88 in tongue and groove manner as best seen in FIG. 9.
  • Aligned bores are formed to expand as shown through the respective link end portions 86 and 88 and the drive pin 68 is extended through these aligned bores to thereby pivotally attach the respective upper extremities of the links 74 and 76, as best seen in FIGS. 8 and 9, while enabling the transmission of power between the drive shaft 14 and the working member 70, or vice versa, as the case may be.
  • the overall width of the working member 70 also remains substantially unchanged at the pivotal connection between links 74 and 76.
  • the respective lower extremities of the links 72 and 78 are also formed by somewhat enlarged, generally cylindrical end portions 90 and 92, each of which comprises a generally centrally disposed bore extending therethrough as indicated at 94 and 96.
  • Attachment pins 98 and 100 are provided to extend respectively through the bores 94 and 96 in the link end portions 90 and 92, with freedom for rotation therebetween and to extend respectively therefrom into spaced bores 102 and 104 provided therefor in the back plate 10 to thus fix the locations of the respective link end portions 90 and 92 relative to the said back plate, and accordingly the housing 8, while enabling free pivotal movement of the links 72 and 78 relative to the housing 8.
  • the width of the working member 70, as assembled, is maintained throughout as substantially equal to the thickness of the housing 8 and core portion 44.
  • the drive shaft 14 is extended through the drive shaft bushing 16 to an extend that will place the end face of the former flush with the end face of the back plate 10, whereupon the drive pin 68 is inserted with freedom for rotation in the drive pin mounting aperture 66.
  • the working member is disposed flush against the end face of the back plate with the drive pin 68 extending through the aligned bores in the respective link end portions 86 and 88, and the respective attachment pins 98 and 100 extending through the respective link-end-portion bores 94 and 96 into the respective housing bores 102 and 104.
  • the housing 8 with the respective seal members 50, 56 and 58 emplaced therein as described, is placed flush against the back plate end face with the core potion 44 fitting, of course, within the working member 70 as made.
  • the front plate 6 is placed over. the housing 8 in flush relationship therewith, and with the core section 44 and working member 70, and the attachment bolts 12 inserted into and tightened through the aligned threaded bores 13 provided therefor in the respective front plate 6, the housing 8, and the back plate 10 to maintain the same in the side-by-side or sandwichlike relationship thereof depicted in FIGS. I and 2 and establish substantially fluidtight seals therebetween.
  • the respective fluid passages 28 and 30 in the front plate 6- will be brought into alignment with the radially outer portions or curved extremities of the respective slots 38 and 40 of the housing 8 to thereby provide for fluid flow communication therebetween while, in like manner, the respective fluid passages 32 and 34 of the front plate 6 will be brought into alignment with the radially inner portions or curved extremities of the slots 48 and 46 of the core portion 44 to thereby establish fluid flow communication therebetween.
  • chamber as indicated generally at C will be formed between the periphery of the core section 46 and the face of theaperture 36 of the housing8. Further, it may be understood that this chamber C will be divided by the working member 70 into an inner fluid working chamber 83 and an outer fluid working chamber 84, with fluid communication therebetween being substantially inhibited by the sealing effects of thesrespective edges of the working member links 72, 74, 76 and 78 againstthe respective inner end faces of the front plate 6 and back plate 10 which results from the substantial equality betweenthe width of the said links and the thickness of the housing 8.
  • a first fluid flow path or'fluid machine working section will be established to extend through fluid conduit and fluid passage 28 in front plate 6, fluid passage or slot 38 in the housing 8, the outer fluid working chamber 84 fonned between the outer surface of the working member-70 and the face of the aperture 36 in the housing 8, the fluid passage in the front plate 6 and the fluid conductor 22'which extends therefrom.
  • a second fluid flow path or fluid machine working section will be formed to extend through fluid conduit 24 and through passage 32 in the front plate 6, fluid passage or slot 48 in the core section 44, the inner working chamber 82 formed between the inner surface of the working member 70 and the outer periphery of the core section 44, fluid passage or slot 46 formed in the core section 44, the fluid passage 34 formed in the front plate 6 and the fluid conduit 26 extending therefrom.
  • FIGS. 10-13 illustrate link positions at intervals and fluid machine operation for one complete revolution of thedrive shaft 14 or cycle of fluid machine operation.
  • each of the fluid passages orslots 46 and 48 in the core section 44 will be uncovered by the working member-70 and will thus be in fluid flow communication with the inner fluid working chamber 83. Fluid flow communication between therespective right and left-hand portions of the inner working chamber 83 will be prevented, however, by the sealing action of the sealing member 50 against the respective inner surfaces of the link members 74 and 76; Accordingly, as the drive shaft 14 rotates 90- in the counterclockwise direction from the position thereof depicted in FIG. 10 to the position thereof depicted in FIG.
  • the left-hand portion of the inner fluid working chamber 82 will be substantially decreased in volume by the pivotal movement of the link 78 from contact with the face of the aperture 36 and the sealing member 58 to contact with the periphery of the core section 44 whereby may be understood that the liquid present in this inner working chamber portion will be forced therefrom through fluid passage or slot 46 in core section 44 and therefrom through passage 34 in front plate 6 for discharge through discharge conduit 26. This liquid flow will, of course, continue, until closure of the slot 46 by thelink 78 as seen in FIG. 11.
  • the right-hand portion of the inner working chamber 83 will commence to increase in volume as the link 74 moves towardthe sealing member 56, whereupon liquid will be drawn thereinto through inlet conduit 24, fluid passage 32, and slot 48.
  • this pivotal movement of the link 74 will function to substantially decrease the volume of the right-hand portion of the outer working chamber 84 to displace the fluid therefrom to the left-hand portion of the said outer working chamber.
  • the pivotal movement of the link 78 will have uncovered slot 40, whereby the discharge of liquid from he left-hand portion of outer working chamber 84 through slot 40, connected passage 30 and fluid conduit 22 will commence.
  • the fluid machine of the invention when operated as a liquid pump with rotational power supplied thereto through drive shaft 14, will be double acting in comprising two simultaneously operative working sections, namely, an outer working section which includes slot 38, the outer working chamber 84 and slot 40, respectively, and an inner working section which includes slot 48, the inner working chamber 83 and the slot 46, respectively.
  • the fluid machine of the invention would be eminently suitable for use as a motor driven pump complete in itself. More specifically, it may be understood that under such operational conditions, no rotational power need be applied to the drive shaft 14 and that the introduction of this higher pressure fluid to, for example, the inner working chamber through slot 48, would cause the inner working section to act as a fluid motor and move the working member 70 through repeated cycles of operation thereof as depicted in FIGS. l through 13 to effect the pumping of a liquid by the outer working section in the same manner as described in detail hereinabove as resulting from the driven rotation of the drive shaft 14.
  • staging may readily be effected in the fluid machine of the invention as depicted in FIGS, 2, 3 and 5.
  • suitable connection of outlet conduit 22 to inlet conduit 24 will, of course, result in the formation of a single action, two-stage pump with the higher pressure being maintained in the inner working chamber 83.
  • suitable connection of outlet conduit 26 to inlet conduit will result in the formation of a single acting, two-stage fluid motor with the higher pressure being maintained in the inner working chamber 83.
  • FIG. 14 A more detailed understanding of the manner in which the respective links 72, 74, 76 and 78 cooperate with he respective sealing members 50, 56 and 58 to provide the desired sealing function may be acquired from FIG. 14 wherein a portion of the link 78 is depicted in operative, sealing relationship with a portion to the sealing member 58 during an intermediate point in a cycle of fluid machine operation. More specifically, FIG. 14 may be understood to depict the link sealing member relationship at the point in a cycle of operation of the fluid machine intermediate those depicted in FIGS. 13 and 10.
  • the link 78 would, of course, be disposed in the left-hand portion of the outer working chamber 84 and would bear against the flexible sealing member 58 to displace the latter from the position thereof depicted by the dashed line to the position thereof depicted by the solid line, with the resultant tensile force functioning to provide the desired sealing force.
  • this left-hand portion of the outer working chamber 84 is the high pressure or pump discharge zone, it may be understood that the pressure of the liquid would create a force on the sealing member 58, as indicated by the arrows 110, with the reaction that the tensile force exerted by the sealing member 58 at the point contact thereof with the link 78, as indicated by the arrow 112, would be increased slightly to thus increase the effectiveness of the sealing member-link seal as desired at the high pressure ordischarge side.
  • sealing members 50, 56 and 58 it may be understood that extremely careful machining of the contour of the housing aperture 36, and similar care in the formation of the respective links 72, 74, 76 and 78 may be utilized to provide for minimum gaps or spaces therebetween during fluid machine operation,
  • substantially frictionless seals would be provided throughout it being readily apparent, however, that such would also entail the acceptance of the controlled fluid leakage that would, of course, occur through the said minimum gaps or spaces.
  • steels of high tensile strength and hardness ratings may be understood to have proven particularly satisfactory for working member link construction with, for example, any one'of a wide variety of far less sophisticated steels, or plastics proving satisfactory, in such application, for use in the construction of the respective housing, core section, and front and back plates.
  • the respective links 72, 74, 76 and 78 may readily be constructed from a relatively inert plastic material in the nature of fiberglass, and the respective housing, core and front and back plates from inert materials in the nature of somewhat reinforced ceramics.
  • the weight of material selected for utilization in the construction of the working member 70 will not be a significant factor, it having been determined that no more than percent of the input power is required to overcome mechanical friction and drive the said working member through its cycle of operation.
  • the width and diameter of the working member 70 can be chosen in almost any ration commensurate with practical overall fluid machine dimensions without disadvantageous influence upon the basic principle of fluid machine operation.
  • the running speed of the fluid machine of the invention can be substantially higher than that of state-of-the-art positive displacement fluid machines because, in the former, the working member 70 is moved through a relatively short path of movement with the speed of movement thereof decreasing from a maximum at the drive pin 68 to a minimum at the attached extremities of the links 72 and 78.
  • a particular advantage of the fluid machine of this invention resides in the eminent suitability thereof for high pressure applications in high pressure pumps, high torque fluid motors and/or a self-driven high pressure pump and high torque fluid motor combination. More specifically, it may be understood that since the respective links 72, 74, 76 and 78 are constructed of substantially rigid, or substantially nonflexible, materials as discussed-hereinabove, the application of high pressure loadings thereto will not be effective to change the respective paths of movement thereof during fluid machine operation.
  • a fluid machine comprising a casing having a space formed therein, core means fixedly disposed within said space and spaced at least in part from said casing to form a generally annular chamber therebetween, a working member means disposed in said chamber to surround said core means at least in part and form at least one generally annular working chamber therein, said working member means comprising a plurality of pivotally interconnected parts, spaced fluid inlet and outlet means communicating with different portions of said working chamber, holding means fixedly holding at least one portion of said working member means at a first position, and drive means connected to a second portion of said working member means spaced from said first portion for moving said second portion in a predetermined path for pivotally moving said parts of said working member meansrelative to each other to contract and expand said working member means about said core means to alternately expand and contract said different portions of said working chamber and concomitantly alternately open and close said space fluid inlet and outlet means to move fluid between said inlet and outlet means 2.
  • said one working chamber is
  • a second generally annular working chamber is formed between the opposite face of said working'member means and the face of said casing space, and said fluid machine further comprises second, spaced inlet and outlet means communicating with different portions of said second working chamber whereby, said movement of said working member means will be concomitantly effective to alternately expand and contract said different portions of said second working chamber and altemately open and close said second inlet and outlet means whereby, the movement of fluid between said second inlet and outlet means may be concomitantly effected.
  • a fluid machine comprising a casing having a spaced formed therein, core means disposed within said space and spaced at least in part from said casing to form a generally annular chamber therebetween, pivotal working member means having opposed faces and disposed in said chamber to surround said core means at least in part and form at least one generally annular working chamber therein, spaced fluid inlet and outlet means communicating with different portions of said working chamber, said one working chamber being formed between one face of said working member means and said core means, said inlet and outlet means extending at least in part through said core means, and means for pivotally moving said working member means to alternately expand and contract said different portions of said working chamber and concomitantly alternately open and close said spaced fluid inlet and outlet means, whereby the movement of fluid between said inlet and outlet means may be effected.
  • a fluid machine comprising a casing having a space formed therein, core means disposed within said space and spaced at least-in part from said casing to form a generally annular chamber therebetween, pivotal working member means having opposed faces and disposed in said chamber to surround said core means at least in part and form at least one generally annular working chamber therein, spaced fluid inlet and outlet means communicating with different portions of said one working chamber, said one working chamber being formed between one face of said working member means and said core means, said inlet and outlet means extending at least in part through said core means, means for pivotally moving said working means to alternately expand and contract said different portions of said working chamber and concomitantly alternately open and close said spaced fluid inlet and outlet means whereby the movement of fluid between said inlet and outlet means may be effected, a second generally annular working chamber formed between the opposite face of said working member means and the face of said casing space, and
  • said second inlet and outlet means extend at least in part through said casing.
  • a fluid machine comprising a casing having a space formed therein, core means disposed within said space and spaced at least in part from said casing to form a generally annular chamber therebetween, pivotal working member means having opposed faces and disposed in said chamber to surround said core means at least in part and form at least one generally annular working chamber therein, said pivotal working member means comprising a plurality of pivotally interconnected links, spaced fluid inlet and outlet means communicating with different portions of said working chamber, and means for pivotally moving said working member means to alternately expand and contract said different portions of said working chamber and concomitantly alternately open and close said spaced fluid inlet and outlet means, whereby the movement of fluid between said inlet and outlet means may be effected.
  • a second generally annular working chamber is formed between the opposite face of said working member means and the face of the said casing space, and said fluid machine further comprises second, spaced inlet and outlet means communicating with different portions of said second working chamber whereby said movement of said working member means will be concomitantly effective to alternately expand and contract said different portions of said second working chamber and alternately open and close said second inlet and outlet means so that the movement of fluid between said second inlet and outlet means may be concomitantly effected.
  • said means for pivotally moving said pivotal working member means comprise means pivotally connected to a generally central portion thereof to pivotally interconnect two of said links and operative to move said generally central portion in a generally circular path.
  • said means for pivotally moving said pivotal working member means comprise means pivotally connected to a generally central portion thereof to pivotally interconnect two of said links and operative to move said generally central portion in a generally circular path.
  • said means for pivotally moving said pivotal working member means comprise means pivotally connected to a generally central portion thereof to pivotally interconnect two of said links and operative to move said generally central portion in a generally circular path.
  • sealing means disposed in said generally annular chamber for sealing contact therewith by said pivotally interconnected links during the pivotal movement of the latter to prevent the backflow of fluid from said outlet means to said inlet means
  • sealing means comprise flexible band means disposed within each of said one generally annular working chamber and said second generally annular working chamber within the respective paths of movement of said pivotally interconnected links within said working chambers.
  • said plurality of pivotally interconnected links is constituted by first, second, third and fourth links, respectively
  • said means for pivotally moving said pivotal working member means comprise a drive pin which extends through first extremities of said second and third links to pivotally interconnect the same
  • said means pivotally connecting two of said links to said housing at spaced points on the latter comprise pin means pivotally connecting first extremities of said first and fourth links to said housing, and the respective second extremities of said first and second links
  • said third and fourth links comprise means pivotally interconnecting the second extremities of said first and second links, and the second extremities of said third and fourth links.
  • said plurality of pivotally interconnected links is constituted by first, second, third and fourth links, respectively
  • said means for pivotally moving said pivotal working member means comprise a drive pin which extends through first extremities of said second and third links to pivotally interconnect the same
  • said means pivotally connecting two of said links to said housing at spaced points on the latter comprise pin-means pivotally connecting first extremities of said first and fourth links to said housing, and the respective second extremities of said first and second links
  • said third and fourth links comprise means pivotally interconnecting the second extremities of said first and second links, and the second extremities of said third and fourth links.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Details Of Reciprocating Pumps (AREA)
US797415A 1969-02-07 1969-02-07 Fluid machine especially adapted for high pressure applications Expired - Lifetime US3574494A (en)

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JP (1) JPS5118644B1 (enrdf_load_stackoverflow)
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US5004409A (en) * 1988-03-22 1991-04-02 Nakhmanson Raoul S Displacement machine
US5419292A (en) * 1992-02-21 1995-05-30 Antonov; Roumen Positive-displacement machine with reciprocating and rotating pistons, particularly four-stroke engine
US5895421A (en) * 1996-08-07 1999-04-20 Nakhmanson; Raoul S. Artificial heart
US6065289A (en) * 1998-06-24 2000-05-23 Quiet Revolution Motor Company, L.L.C. Fluid displacement apparatus and method
WO2007065976A1 (en) * 2005-12-08 2007-06-14 Maraplan Oy Pump or motor
EP3615772A4 (en) * 2017-04-28 2021-01-13 Quest Engines, LLC VARIABLE VOLUME BEDROOM SYSTEM

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US1974225A (en) * 1932-07-27 1934-09-18 Varley Pumps And Enginecring L Rotary pump
US2784902A (en) * 1953-07-20 1957-03-12 Ashley C Glenn Pumps or compressors
US3050013A (en) * 1960-08-18 1962-08-21 Griffith Company Rotary duplex pump
US3196854A (en) * 1963-04-08 1965-07-27 Novak Andrew Rotary engine

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US716970A (en) * 1902-05-26 1902-12-30 Edward H Werner Rotary engine.
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US1516107A (en) * 1923-02-24 1924-11-18 Leiman Bros Pump
US1780109A (en) * 1927-05-11 1930-10-28 Vacuum Compressor Ab Rotary machine
DE529406C (de) * 1928-07-31 1933-02-15 Alfred Bachert Drehkolben-Dampfmaschine
US1974225A (en) * 1932-07-27 1934-09-18 Varley Pumps And Enginecring L Rotary pump
US2784902A (en) * 1953-07-20 1957-03-12 Ashley C Glenn Pumps or compressors
US3050013A (en) * 1960-08-18 1962-08-21 Griffith Company Rotary duplex pump
US3196854A (en) * 1963-04-08 1965-07-27 Novak Andrew Rotary engine

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5004409A (en) * 1988-03-22 1991-04-02 Nakhmanson Raoul S Displacement machine
US5419292A (en) * 1992-02-21 1995-05-30 Antonov; Roumen Positive-displacement machine with reciprocating and rotating pistons, particularly four-stroke engine
US5895421A (en) * 1996-08-07 1999-04-20 Nakhmanson; Raoul S. Artificial heart
US6065289A (en) * 1998-06-24 2000-05-23 Quiet Revolution Motor Company, L.L.C. Fluid displacement apparatus and method
WO2007065976A1 (en) * 2005-12-08 2007-06-14 Maraplan Oy Pump or motor
EP3615772A4 (en) * 2017-04-28 2021-01-13 Quest Engines, LLC VARIABLE VOLUME BEDROOM SYSTEM

Also Published As

Publication number Publication date
JPS5118644B1 (enrdf_load_stackoverflow) 1976-06-11
DE2004936A1 (de) 1970-09-24
GB1303131A (enrdf_load_stackoverflow) 1973-01-17

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