US3307484A - Fluid moving machine - Google Patents

Fluid moving machine Download PDF

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US3307484A
US3307484A US434986A US43498665A US3307484A US 3307484 A US3307484 A US 3307484A US 434986 A US434986 A US 434986A US 43498665 A US43498665 A US 43498665A US 3307484 A US3307484 A US 3307484A
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valve
plunger
partition
conduit
fluid
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Hammelmann Paul
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/1095—Valves linked to another valve of another pumping chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
    • F01L25/02—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means
    • F01L25/04—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means by working-fluid of machine or engine, e.g. free-piston machine
    • F01L25/06—Arrangements with main and auxiliary valves, at least one of them being fluid-driven
    • F01L25/063—Arrangements with main and auxiliary valves, at least one of them being fluid-driven the auxiliary valve being actuated by the working motor-piston or piston-rod
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/22—Reciprocating-piston liquid engines with movable cylinders or cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/102—Disc valves
    • F04B53/1022—Disc valves having means for guiding the closure member axially
    • F04B53/1025—Disc valves having means for guiding the closure member axially the guiding means being provided within the valve opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/164—Stoffing boxes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/111—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
    • F04B9/115—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by two single-acting liquid motors, each acting in one direction

Definitions

  • HAMMELMANN -FLUID MOVING MACHINE Filed Feb. 24, 1965 4 Sheets-Sheet 2 March 7, 1967k P.
  • the present invention relates to a fluid moving machine, and more particularly to a double acting plunger pump and hydraulic motor combination with a pair of pump chambers.
  • water pumps are required which combine a very low weight with easy adjustability of the pumped Iamount and of the water pressure. Due to -the fact that very great energy amounts are involved, great efficiency of the pumps is required. Furthermore, the pumps serving these purposes should require very little service.
  • Pressure water pumps of high efficiency are known.
  • Multistage rotary pumps operate at lower efliciency, but serves the purpose. Both pump types are adjustable to ya certain extent, but when the pump is adjusted to a different output, the efficiency is reduced.
  • Piston pumps require very heavy crank drives with cross heads, and the comparatively low rotary speed of this type of pumps necessitates the use of reduction gears, and the great torques involved yrequire very heavy constructions.
  • Another object of the invention is to provide a fluid moving machine constructed of simple parts and having a low weight per unit of pump fluid and pressure.
  • Another object -of the invention is to provide a fluid movingmachine operable free of vibrations in all positions.
  • vthe present invention relates ⁇ to a fluid moving machine in which plunger means are operated by a driving fluid to pump another fluid.
  • One embodiment of the invention includes a double plunger pump with la pair of pump chambers, and having a double plunger in the form of cylindrical piston means and slida'bly guided on a stationary part for reciprocating movement during which a valve controlling the supply and discharge of a driving fluid to the interior of the plunger is operated.
  • a preferred embodiment of the invention comprises housing means formed wit-h an inner cavity for a pumped fluid, and including a partition means dividing the cavity into two rooms which have first inlet and outlet means; plunger means including a pair of pistons located on opposite sides of the partition means and a tubular member connecting the pistons and being guided in the partition means; secondinlet and outlet means for driving fluid which preferably passes through a conduit in a tubular support which extends through the partition means and passes through the pistons; and valve means for connecting the second inlet and outlet means with the motor chambers.
  • the plunger means define in each room of the housing means a pump chamber communicating with first inlet and outlet means, and -the pistons and tubular member defining with the partition means a pair of motor chambers located on opposite sides of the partition means.
  • the valve means are movable between first and second positions for supplying the driving fluid to the first motor chamber while discharging the same from the same motor chamber, and for supplying the driving fluid to the second motor chamber while discharging the same from the first motor chamber.
  • This causes reciprocation of the plunger means since the driving fluid exerts pressure on the pistons, and the reciprocating plunger means, and more particularly the pistons, engage a control means which causes shifting of the valve means so that thereciprocation of the plunger is automatically continued.
  • the valve means are mounted in the partition means communicating with the conduit of the tubular support so that driving fluid supplied to, or discharged from the conduit passes through the valve means into the motor chambers.
  • the valve means comprise preferably a main valve which distributes the driving fluid, and a valve control member which is shifted by the moving plunger means and hydraulically controls lthe main valve which has a piston portion moving in a control chamber to which pressure fluid is admitted under the control of the valve control member.
  • the valve control member is mounted in the partition means and has end portions projecting into the motor chambers so as to be engaged by the inner surfaces of the pist-ons during the reciprocating movement of the plunger means.
  • the main valve is turnable in the partition means, and in another embodiment of the invention the main valve is mounted in the partition means for translatory movement.
  • the turnable main valve is preferably controlled by a pair of valve control members which, when shifted by the reciprocating plunger means, open and close ducts in the partitioning means for supplying pressure fluid to the control chamber in which the piston portion of the main valve is located.
  • the main valve is hydraulically locked, and cannot turn to a position reversing the flow of the driving fluid to the motor chambers until the valve control member is actuated by the reciprocating plunger means at the end of a reciprocating stroke.
  • FIG. l is a longitudinal sectional view of a fluid moving machine according to one embodiment of the invention provided with 'a turnable main valve;
  • FIG. 2 is a fragmentary longitudinal sectional View illustrating the center portion of FIG. l on a larger scale, the section being taken on line II-II in FIG. 3;
  • FIG. 3 is a cross-sectional View taken on line III-III in FIG. 2;
  • FIG. 4 is a cross-sectional view taken on line IV-IV in FIG. 2; j
  • FIG. 5 is a fragmentary longitudinal sectional view illustrating the center portion of another embodiment of the invention in which the main valve is shiftable in a 3 translatory movement, the section being taken on line V-V in FIG. ⁇ 6;
  • FIG. 6 is a longitudinal sectional view taken on line VI-VI in FIG. and
  • FIG. 7 is a cross-sectional view taken on line VII-VII in FIG. 5.
  • a housing has two head portions 1 and 2 with inlet conduit means 3 through which a iiuid to be pumped is supplied.
  • Check valve means 50 and 51 cover inlets 3b in walls 3a, and open when the corresponding pump chambers 5 and 6 are expanded and suction is applied to valves 50 and 51.
  • a pair of cylindrical housing portions 1a and 2a connect the heads 1 and 2 and form outlets communicating with pump chambers 5 and 6 and closed by valves 52 and 53 from which pumped iiuid is discharged when the corresponding pump chambers 5 and 6 are reduced in volume.
  • outlets 1b and 2b'V are connected by a tube 4 into which pressure iluid is pumped.
  • a tie rod 4a connects the outlet means 1b and 2b.
  • a pair of aligned tubular supports 12 and 13 are respectively mounted inthe heads 1 and 2 and secured to the same by nuts 17 and 18 which engage threaded portions of tubular supports 12 and 13.
  • the inner ends of the tubular supports 12 and 13 are threaded at 9a, see FIG. 2, to sleeve portions 9b of la partition means 9.
  • An annular member 7 surrounds the adjacent ends of the tubular members 1a and 2a and has inner sealing means 7a of annular configuration which form a circular gap with annular sealing means 7b which :are secured to partitioning means 9.
  • a tubular member 8 is mounted in this gap for sliding movement and is divided by partitioning means 9.
  • Pistons 19 and 11 are secured to the ends of tubular member 8 and surround the tubular supports 12 and 13. Sealing rings 14 are provided between the tubular supports tand the pistons 10 and 11.
  • the partition means 9, and pistons 10 and 11 form in the tubular member 8 a pair of motor chambers 26 and 28.
  • Pump chambers 5 and 6 are formed in the pump housing 'between the heads 1 and 2 and pistons 111 and 11.
  • Tubular supports 12 and 13 have inner conduits 1S and 16 4for a driving uid which is supplied to the inlet of conduit at the end of tubular support 13, and which is discharged from the outlet of conduit 16 at the end of tubular support 13.
  • tubular supports 12 and 13 have inner cylindrical surfaces 13a and 13b in which a main valve 19 is mounted lfor turning movement.
  • the end portions of main valve 19 abut roller bearing means 20 and 21 so that the main valve 19 cannot be axially displaced.
  • main valve 19 has valve channels 24 and 31) which open at the ends of valve 19 into conduits 15 and 16.
  • Valve channel 3) has two ports 47 and 47a, and valve channel 24 has two ports 46 and 46a.
  • port 47a communicates with an -opening 29 in tubular support 13 which leads to the motor chamber 28 within the plunger 8, 11i, 11.
  • Port 46a communicates with an opening 25 which leads to the motor chamber 26.
  • ports 47 and 46 are closed, but when main valve 19 is turned, ports 46 and 47 respectively communicate with openings 29 and 25 in tubular supports 13 and 12, respectively, so that driving Huid entering channel 24 from conduit 15 passes into motor chamber 28, while the driving liquid is discharged from motor chamber 26 ⁇ and channel 3d into the conduit 16 for reversing the stroke of -plunger 8, 10, 11.
  • Piston portion 35 has a shorter axial length than the main valve, and is located in a corresponding control chamber 34 which extends through an angle of 270 to the end faces of a segmentshaped stationary member 36 which is secured to the main part of the partition means 9 by a screw 45a.
  • valve control members 22 and 23 which are mounted for sliding movement in axial direction in corresponding bores of partition means 9.
  • the ends of control members 22, 23 are connected by arcuate links 39 :and 38 best seen in FIG. 4. In the position shown in FIG. 2, link 39 abuts an end face of partition means 9 so that valve control members 22, 23 cannot move farther to the right as viewed in FIG. 2.
  • Valve control members 22, 23 were -placed in this position by piston 11 moving to the right as viewed in FIG. 1, and when the plunger moves in the opposite direction, piston 111 engages with its inner surface the other ends of valve control members 22, 23 and pushes the same to the left until link 38 abuts a surface of partition means 9.
  • Control valve member 23 has a thinner central portion forming an annular room 32 which communicates with duct 31.
  • Valve control member 22 has two thinner portions surrounded yby annular rooms 44 and 44a. In the illustrated position, annular room 44a communicates with duct 42. In the shifted position of valve control member 22, annular room 44 communicates with duct 42.
  • Main valve 19 has two bores 33 and 41 respectively communicating With channels 24 and 30.
  • Annular channels 43 ⁇ and 411 are provided in tubular supports 13 and 12, respectively and cooperate with bores 33 and 41.
  • F our bores 39a are provided in partition means 9 Afor connecting the annular channels 40 and 43 with the annular rooms 32, 44, 44a.
  • pump chamber 5 expands, and fluid to be pumped is sucked through inlet 3 and valve 51 into pump chamber 5 while valve 52 closes.
  • valve control members 22 and 23 When the inner surface of piston 19 engages the ends of valve control members 22 and 23, the same are pushed to the left as Viewed in FIGS. 1 and 2 until link 38 abuts an end face of partition means 9. In this position of valve control members 22, 23, 4bore 42 communicates with annular room 4d of valve control member 22, and bore 33 is separated from annular room 32 of valve control member 23 and thereby from bore 31 and valve control chamber 34.
  • Pressure duid is discharged ⁇ from control chamber 34 through bore 31, annular room 32, bore 39a in sleeve 39b, annular channel 40, and bore 41 into valve channel 30 which communicates through conduit 16 with the outlet for the driving fluid.
  • valve 19 turns with the piston portion through 180 so that in the new position of the Valve, pressure fluid enters from conduit 15 into valve channel 34 and passes through port 46 and opening 29 into motor chamber 28 to drive piston 10 to the right as Viewed in FIG. 1 whereby the volume of pump chamber 5 is reduced and tluid toV be pumped is discharged through valve 52 and outlet means 2b, 4 and 1b.
  • the main valve is not turned but shifted in a translatory movement by a valve control member operated by the pistons of the plunger.
  • the general arrangement ofthe vpump component is the same as shown in FIG. l, and the plunger means 50 has two pistons 67 and 82 guided on tubular suppolts 12' and 13 and a tubular portion 8' which slides on a partition means 9.
  • a ringshaped member with inner sealing means surrounds the tubular portion l8 of plunger means 5ft, but is not shown in FIGS. 5 and 6.
  • Partitioning means 8 has an axial bore in which a valve control member 69 is mounted for axial movement between two control posirions determined, respectively by abutment of the heads 68 and 83 on end faces of partition means 9', as shown in FIG. 6.
  • Drive ilui-d under pressure is supplied through conduit 53a and ows into valve chamber 55, through chamber portion 56, bore 57 and conduit 58 into motor chamber 59 to move plunger means 8 to the left in the direction of the arrow 60 in FIG. 5.
  • the contracting motor chamber 61 discharges drive uid through conduit 62, bore 63, and valve channel 64 into the discharge conduit 65 of the tubular support 13.
  • pump chamber 6 is reduced in velu-me, and pump chamber 5 is increased in volume so that fluid is pumped out of outlet 1b, and 'sucked into inlet 3 as described with reference to FIG. 1.
  • Valve control member 69 has a thinner central portion surrounded by an annular room 72 in partition means 9'.
  • a bore 73 in tubular support 13 connects annular room 72 with an annular control chamber 70 provided between a portion of the main valve 54 and a corresponding face of tubular support 13.
  • On the other side of main valve 54 a corresponding annular control chamber 74 is provided.
  • Main Valve 54 has a slot 87 into which the end portion 86 of the stop screw 85 projects to limit translatory movement of main valve 54 into end positions, one of which is illustrated in FIGS. 5 and 6.
  • a bore 71 in tubular support 12 and partition means 9 communicates with annular room 72 so that pressure duid flows from conduit 53a, bore 71, annular room 72, and bore 73 into the annular control chamber 70 to move main valve 54 to the left to its other end position.
  • the other control chamber 74 discharges duid through bores 75, 76, FIG. 5, in the body of main body 54 into valve channel 64- which communicates with the discharge conduit 65 in tubular support 13.
  • valve channel 64 registers with a bore 77 communicating with a conduit 58a which opens into motor chamber 59 so that the same is connected to the discharge conduit 65 in tubular support 13.
  • valve channel 55 Drive fluid under pressure ows through valve channel 55, 56, a bore 78, and a conduit 79 into mot-or chamber 61 to urge plunger means 8 to the right.
  • Conduit 79 and bore 78 are circumferentially spaced from conduit 58 an-d bore 57, and valve channel 55 has a wider portion 56 covering in circumferential direction the two bores 57 and 78.
  • plunger means 8 moves to the right, the volume of pump chamber 5 is reduced, and uid is discharged through outlet 2b.
  • the volume of pump chamber 6 increases, an-dizid is sucked into inlet 3 and passes through valve 5t), as described with reference to FIG. l.
  • valve control chamber 70 is connected by bore 73, annular room 72, and bore S4 with discharge conduit 65 in tubular support 13. The pressure of the drive fluid entering into valve channel 55 from conduit 53a is sufficient to urge main valve 54 to the right hand end position when control chamber 70 is relieved of pressure.
  • the pump housing 1, 1a, 2 has an inner'cavity which is divided by the partition means 9, 9 into two rooms.
  • the plunger means 8, 10, 11 forms pump chambers 5 and 6 in their respective rooms, and motor chambers 26, 28 in the interior of the plunger.
  • the tubular member 8 is sealed from the pump chambers only in the region of the partition means 9, 9 so that thin annular portions of pump charnbers extend between housing portion 1a and tubular member 8, 8 to the partition. No sealing means .are required between pistons 10, 11 and the tubular housing portion 1a.
  • a fluid moving machine comprising, in combination, housing means formed with an inner cavity for a pumped fiuid, and including a partition means dividing said cavity into two rooms, each room having first inlet and first outlet means; plunger means including a pair of pistons located on opposite sides of said partition means in said rooms, and a tubular member connecting said pistons having an axis and being guided in said partition means, said plunger means defining in each room a pump chamber communicating with said first inlet and outlet means, and said pistons and tubular member defining with said partition means a pair of motor chambers located on opposite sides of said partition means; second inlet and outlet means for a driving fluid; and valve means mounted in said partition means for connecting said second inlet and outlet means and with said motor chambers, said valve means being formed with first and second conduits and being located centered in said axis, said valve means having first and second positions for supplying said driving fluid through said first conduit to said first motor chamber while discharging the same from said second motor chamber through said second conduit, and for supplying said driving fluid
  • control means include two Control members having ends projecting in axial direction from said partition means, arcuate links connecting said ends and extending about said valve means, and a piston in a chamber in said partition means connected with said valve means, -said control members controlling the flow of fluid in said chamber for turning said valve means.
  • a machine according to claim 1 and including antiriction bearings supporting the ends of said valve means in said partition means.
  • valve means includes a stepped axially movable piston having a surface subjected to fiuid pressure, and a control chamber means in said partition means receiving said piston and having an hydraulically effective annular surface having a greater area than said surface of said piston, said control chamber being hydraulically connected by said control means with said second inlet and outlet means, respectively.
  • a machine wherein said piston has a circular surface in said second inlet means subjected to uid pressure, and wherein said annular surface has an area substantially twice the area of said circular surface; and wherein said valve means closes a chamber -connected by a bore in said partition means with said second outlet means.
  • a uid moving machine comprising, in combination, housing means formed with an inner cavity having first inlet and outlet means, and including a partition means dividing said cavity; tubular support means supported on said housing means and on said partition means and located in said cavity; cylindrical plunger means located in said cavity and mounted on said partition means and said tubular support means for reciprocating movement, said plunger means defining in said cavity a pair of pump chambers, and defining in the interior thereof with said partition means a pair of motor chambers; valve means mounted in said partition means for turning movement between two positions for Connecting one or the other of said motor chambers to the interior of said tubular support means so that a driving fiuid supplied through the same causes reciprocation of said plunger means; a valve control member mounted on said partition means and operated by said reciprocating plunger means to shift said valve means between said positions, said valve control member being hydraulically connected with said valve means for shifting the latter between said two positions when said valve control member is shifted by said reciprocating plunger means.
  • a fiuid moving machine comprising, in combination, housing means formed with an inner cavity for a pumped fluid, and including a partition means dividing said cavity into two rooms, each room having first inlet and first outlet means; plunger means including a pair of pistons located on opposite sides of said partition means in said rooms, and a tubular member connecting said pistons and being guided in said partition means, said plunger means defining in each room a pump chamber communicating with said first inlet and outlet means, and said pistons and tubular member defining with said partition means a pair of motor chambers located on opposite sides of said partition means; a tubular support having an axis secured to said housing means extending through said partition means and said pump chambers and motor chambers and passing through said pistons movably sup porting the same, said tubular support being formed with an inner conduit having a second inlet means at one end of said tubular support and a second outlet means at the other end of said tubular support for admitting and discharging a driving fluid; and valve means mounted in said partition means communicating W
  • a iiuid moving machine comprising, in combination,
  • housing means formed with an inner cavity having first inlet and outlet means, and including a partition means dividing said cavity; tubular support means supported on said housing means and on said partition means and located in said cavi-ty; cylindrical plunger means located in said cavity and mounted on said partition means and said tubular support means for reciprocating movement, said plunger means defining in said cavity a pair of pump chambers, and defining in the interior thereof with said partition means a pair of motor chambers; and valve means mounted in said partition means for turning movement between two positions for connecting one or the other of said motor chambers to the interior of said tubular support means so that a driving fiuid supplied through the same causes reciprocation of said plunger means; and a valve control member mounted on said partition means and operated -by said reciprocating plunger means to shift said valve means between said positions, said valve control means including two valve control members mounted for translatory movement on said partition means, and being interconnected with each other for simultaneous movement, said valve control members being hydraulically connected with said valve means for shifting the latter between said two positions when said valve control members are
  • a machine as set forth in claim 8 wherein said main valve has valve channels communicating with the interior of said tubular support means to receive a driving fluid from the same, and wherein said partition means is formed With ducts -controlled by said valve control means for connecting said valve channels with said motor chambers.
  • a 'luid moving machine comprising, in combination, housing means formed with an inner cavity having first inlet and outlet means, and including a partition means dividing said cavity; tubular support means supported on said housing means and on said partition means and located in said cavity; cylindrical plunger means located in said cavity and mounted on said partition means and said tubular support means for reciprocating movement, said plunger means dening in said cavity a pair of pump chambers, and defining in the interior thereof with said partition means a pair of motor chambers; valve means mounted in said partition means and having two positions for connecting one or the other of said motor chambers to the interior of said tubular support means so that a driving fluid supplied through the same causes reciprocation of said plunger means; and a valve control member mounted on said partition means and operated by said reciprocating plunger means to shift said valve means between said positions; first sealing means 4on the periphery of said partitioning means in sliding engagement with the inner surface of said cylindrical plunger means; and a ring mounted on said housing means and surrounding said cylindrical plunger means in the region of said partition means and having
  • a iluid moving machine comprising, in combination, housing means formed with an inner cavity having first inlet and outlet means, and including a partition means dividing said cavity; tubular support means supported on said housing means and on said partition means and located in said cavity; cylindrical plunger means located .in said cavity and mounted on said partition means and said tubular support means for reciprocating movement, said plunger means dening in said cavity a pair of pump chambers, and defining in the interior thereof with said partition means a pair of motor chambers; valve means mounted -in said parti-tion means for turning movement between two positions for connecting one or the other of said motor chambers to the interior of said tubular support means so that a driving fluid supplied through the same causes reciproeation of said plunger means; a valve control member mounted on said partition means and operated by said reciprocating plunger means to shift said valve means between said positions; and antifriction bearing means at the end of said valve means supporting the same against axial movement.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
US434986A 1964-02-27 1965-02-24 Fluid moving machine Expired - Lifetime US3307484A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEH0051860 1964-02-27
DEH52745A DE1279468B (de) 1964-02-27 1964-05-21 Druckmittelgetriebene Schubkolbenpumpe

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US3307484A true US3307484A (en) 1967-03-07

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US434986A Expired - Lifetime US3307484A (en) 1964-02-27 1965-02-24 Fluid moving machine

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US (1) US3307484A (de)
BE (1) BE660303A (de)
CH (1) CH419841A (de)
DE (1) DE1279468B (de)
DK (1) DK124623B (de)
FR (1) FR1426535A (de)
GB (1) GB1090392A (de)
NL (1) NL6502358A (de)
SE (1) SE319385B (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4069747A (en) * 1976-06-28 1978-01-24 Towmotor Corporation Cylinder constructions
WO1986003262A1 (en) * 1984-11-23 1986-06-05 John Dawson Watts Hydraulically driven downhole pump
US4624628A (en) * 1984-11-06 1986-11-25 Flotronics Ag Double-diaphragm pumps
CN105569941A (zh) * 2015-12-28 2016-05-11 中国煤炭科工集团太原研究院有限公司 一种液压能转化高压水能的装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2150646A (en) * 1983-11-30 1985-07-03 Terry Blackler A pump

Citations (4)

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US1164926A (en) * 1914-01-29 1915-12-21 Edwin W Clark Pump.
US1448486A (en) * 1921-09-15 1923-03-13 George C Garraway Pump
US1487946A (en) * 1922-04-03 1924-03-25 George W Johnston Combined fluid-pressure motor and pump
US3152016A (en) * 1962-09-20 1964-10-06 Allis Chalmers Mfg Co Pressure powered pump

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE319051C (de) * 1918-05-11 1920-02-21 Froelich & Kluepfel Pressluftmotor zum Antrieb von Schuettelrutschen
DE363973C (de) * 1920-10-29 1922-11-16 Wilhelm Kettler Schwungradlose Kolbenmaschine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1164926A (en) * 1914-01-29 1915-12-21 Edwin W Clark Pump.
US1448486A (en) * 1921-09-15 1923-03-13 George C Garraway Pump
US1487946A (en) * 1922-04-03 1924-03-25 George W Johnston Combined fluid-pressure motor and pump
US3152016A (en) * 1962-09-20 1964-10-06 Allis Chalmers Mfg Co Pressure powered pump

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4069747A (en) * 1976-06-28 1978-01-24 Towmotor Corporation Cylinder constructions
US4624628A (en) * 1984-11-06 1986-11-25 Flotronics Ag Double-diaphragm pumps
WO1986003262A1 (en) * 1984-11-23 1986-06-05 John Dawson Watts Hydraulically driven downhole pump
CN105569941A (zh) * 2015-12-28 2016-05-11 中国煤炭科工集团太原研究院有限公司 一种液压能转化高压水能的装置

Also Published As

Publication number Publication date
SE319385B (de) 1970-01-12
BE660303A (de)
CH419841A (de) 1966-08-31
NL6502358A (de) 1965-08-30
FR1426535A (fr) 1966-01-28
GB1090392A (en) 1967-11-08
DK124623B (da) 1972-11-06
DE1279468B (de) 1968-10-03

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