EP0225834A1 - Rotierende Trommelkolbenpumpe mit festem zentralscharnierpunkt - Google Patents

Rotierende Trommelkolbenpumpe mit festem zentralscharnierpunkt Download PDF

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Publication number
EP0225834A1
EP0225834A1 EP86420172A EP86420172A EP0225834A1 EP 0225834 A1 EP0225834 A1 EP 0225834A1 EP 86420172 A EP86420172 A EP 86420172A EP 86420172 A EP86420172 A EP 86420172A EP 0225834 A1 EP0225834 A1 EP 0225834A1
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EP
European Patent Office
Prior art keywords
barrel
plate
spherical
casing
rotary machine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP86420172A
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English (en)
French (fr)
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EP0225834B1 (de
Inventor
Michel Drevet
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Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0225834A1 publication Critical patent/EP0225834A1/de
Application granted granted Critical
Publication of EP0225834B1 publication Critical patent/EP0225834B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/02—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis with wobble-plate
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/146—Swash plates; Actuating elements
    • F04B1/148—Bearings therefor
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/28—Control of machines or pumps with stationary cylinders
    • F04B1/29—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B1/295—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/16—Alternating-motion driven device with means during operation to adjust stroke
    • Y10T74/1625—Stroke adjustable to zero and/or reversible in phasing
    • Y10T74/1683—Cam and follower drive
    • Y10T74/1692—Axial-type cam [e.g., wabbler type]
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18296—Cam and slide
    • Y10T74/18336—Wabbler type

Definitions

  • the present invention relates to a rotary piston machine of the barrel type, more particularly intended for delivering high-pressure fluids, and in particular charged liquids.
  • pumps of this type are commonly used in the mining industry or in the petroleum industry, for pumping loaded liquids, such as petroleum, liquid sludge, fracturing fluids, or the like. Pumps of this type are commonly of large dimensions and designed to discharge the liquid with a high flow rate, under high pressures, commonly greater than 200 bars.
  • the object of the present invention is to avoid these drawbacks by producing a rotary barrel machine and inclined rotary plate, the crankshaft of a new type allows to increase the discharge pressure of the liquid, while reducing the overall weight of the device.
  • a rotary machine comprises a fixed barrel, in the cylindrical bores from which slide butts directly connected to delivery pistons, each of which is connected by a connecting rod to an inclined plate with rotary swiveling movement, the rear face of which is equipped with '' a central drive pin oriented perpendicular to the front thrust face of the plate, and it is characterized in that the front face of the plate comprises, in its center, a spherical bearing, the circular meridian section of which corresponds to an angle at center greater than 180 °, preferably of the order of 240 ° or more, while inside this spherical bearing, a fixed spherical ball joint is arranged, secured to an arm axially anchored in the center of the barrel, if although the thrust of the plate during operation is transmitted directly to the barrel via the spherical bearing working at tearing, and this without intervening r the resistance of the casing walls, especially in its rear part.
  • the rear journal of the tacking plate is placed in a bearing secured to the web of a pinion on which it occupies an eccentric position.
  • the pinion in question is driven in rotation from a motorized side gear, on which it meshes.
  • the rear trunnion for the control of the platter with wiggling movement is mounted in the veil of the pinion by a spherical joint.
  • the spherical joint in question is carried by an eccentric plate, the angular orientation of which can be chosen relative to the veil of the pinion which carries it.
  • the eccentricity of the spherical bearing is chosen relative to the wall of the pinion, which makes it possible to adjust the amplitude of the real stroke of the pistons of the pump, and therefore the maximum value of the motor torque at pressure desired discharge for the pumped fluid.
  • the tilting platform with a weaving movement is immobilized in rotation by a lateral connecting rod connecting it to the casing.
  • the tilting plate with swaying movement is immobilized in rotation by a pair of bevel gears, one of which is carried by the periphery of the rear face of the swaying plate, while the other, on which it meshes, is secured to the pump housing.
  • the lubrication of the central spherical bearing of the front face of the plate is ensured from a main channel disposed longitudinally in the arm, to open out inside the sphere where it branches out in several radial channels opening onto the periphery of the fixed sphere, in particular in the annular zone, where the latter works for tearing.
  • the drive reduction gear of the inclined plate with a weaving movement is fixed to the casing of the mechanical part of the pump by means of a flange and a counter-flange coaxial with the outlet axis of the reducer and with the axis of the barrel thus giving the advantage of being able to orient at will the axis of the input pinion of the reducer.
  • the central spherical ball joint is also integral with a second rigid half-shaft, located opposite the first with which it is aligned, this second half-shaft is rigidly at its opposite end anchored to the rear of the machine housing. It should be noted that these two half-shafts can, in certain arrangements, form only one single piece shaft.
  • means for preloading the spherical bearing are arranged between the rear of the casing and the corresponding end of the second half-shaft which bears thereon. This preload of the ball joint subjects it to loads opposite to those it undergoes due to the thrust of the pistons on the plate.
  • the left end of the second half-shaft is constituted by a threaded rod which crosses the bottom of the fixed casing, behind which a tensioning nut is screwed there in order to rigidify the casing perfectly.
  • the means for preloading the spherical bearing consist of the use of a shim of thickness, suitably chosen, which is interposed between a removable cover and the rear of the casing. constitutes the bottom in order to compress a roller stop.
  • the preloading means used are constituted by the interposition between the fixed bottom of the rear of the casing and a roller stop on which the rear of the inclined swash plate is supported, of a coaxial annular hydraulic cylinder.
  • the supply of the preload cylinder of the spherical bearing is ensured in pressurized fluid, by a pipe which connects it to the discharge pressure supplied by the machine in the case where this is a pump.
  • the inclined swash plate is produced by assembling two superimposed plates, each having a wedge profile, means being provided to fix one on the other, removably, the two wedge half-plates whose relative angular orientation has been chosen according to the desired stroke for the pistons of the barrel machine.
  • a barrel pump which comprises: - A fixed barrel 1, in the bores 2 of which the butts or pistons 3 slide in an alternating movement; - an inclined plate 4, the geometric axis 5 of which forms an acute angle 6 with the geometric axis 7 of the barrel 1; - connecting rods 8, each of which has two spherical ends 9 and 10, to ensure the connection between each stick or piston 3, and the plate with swaying movement 4; - a rear crank pin 11, integral with the plate 4, and co-linear with the axis 5; - A control pinion 12, centered on the geometric axis 7 around which it rotates, while, in its web 13, an eccentric bearing 14 is provided, for the crank pin 11; - A lateral gear 15, which meshes on the teeth of the pinion 12, and whose shaft 16 is driven by a gear motor not shown.
  • the central part of the front face of the plate 4 carries, in hollow, a spherical bearing 17, inside which is articulated a spherical ball joint 18.
  • the latter is integral with an arm 19.
  • This arm 19 is mounted in a fixed position in the central part of the barrel 1, along the geometric axis 7.
  • the spherical ball joint 18 is trapped in the spherical bearing 17, at an angle at the center 20, which is clearly greater than 180 °.
  • the edge 21 of the spherical bearing 17 closes behind the large diameter of the ball joint 18.
  • the angle at the center 20 is of the order of 260 °, so that when the plate 4 is subjected by the reaction of the pistons 3 to a thrust oriented in the direction of the arrow 22, the bearing 17 works to tearing, around the fixed ball 18.
  • the pin 11 is preferably mounted in a bearing sleeve 23, which is spherical.
  • the spherical meridian section 24 of the sleeve 23 allows the geometric axis 5 of the plate 4 and the pin 11, to oscillate slightly when the angle of inclination 6 of the plate 4 is varied, to adjust the stroke of the pistons 3 and the discharge pressure of the liquid.
  • the eccentricity of the bearing 14 allows, by rotating the latter from one angular position to another, around the geometric axis 7, to vary the eccentricity thereof, relative to the sleeve 23, which has the effect of varying the eccentricity thereof, relative to the sleeve 23, which has the effect of varying the angle of inclination 6.
  • the eccentric bearing 14 has eight holes 25, distributed around its periphery. Thus, by fitting fixing bolts in the holes 25, it is possible to choose within 1 / 8th of a turn, the angular position of the sleeve 23 in the bearing 14 of the web 13.
  • a lateral connecting rod 26 with articulated spherical ends 27 and 28, connects the periphery of the swinging plate 4, to a fixed part 29 of the casing 30 of the pump.
  • the purpose of this connecting rod 26 is to immobilize the plate 4 in rotation, during its weaving movement controlled by the rotation of the pinion 13 on itself.
  • the swinging plate 4 is immobilized in rotation, no longer by the lateral link 26, but by a pair of two bevel gears 31 and 32, each having the same number of teeth, namely: - a bevel gear 31, provided on the rear face at the periphery of the plate 4; - a bevel gear 32, integral with the fixed casing 30 of the pump, and centered on the geometric axis 7.
  • the fixed arm 19 is pierced with an axial channel 33 connected to a source of supply of pressurized lubricating oil.
  • the channel 33 branches in the central part of the ball joint 18, into several radial channels 34 which open into the spherical bearing 17, through openings 35 located in particular in the undercut part of the bearing 17, that is to say say in the part where the latter works for tearing, on the ball joint 18, around the fixed arm 19.
  • the channel 33 can also branch along one or more channels 36, lubricating the rear part of the bearing 17.
  • the lubrication of the spherical bearing 17 can be carried out in certain applications by an oil pump with axial piston with reciprocating movement.
  • a pump constituted by a fixed bore 37 located in the barrel 1 and inside which slides a piston 38 which a rod with spherical bearings connects to the front face of the flapping plate 4.
  • the rod 39 is pierced with a channel 41.
  • This oil pump has a valve 42. It is supplied by an orifice 43.
  • the piston 38 is driven in an alternating movement allowing it to discharge the oil in the known manner in a pipe 40 thanks to the action of the non-return valve 42.
  • the supply of the lubrication channels 33 and / or 43 can be carried out from any external lubrication pump of known type. It is important to note that lubrication can be done either in hydrostatic or in hydrodynamics depending on the applications.
  • the geometric axis 5 of the plate 4 constitutes a generatrix describing a conical surface with a half-angle at the apex 6 around the fixed axis 7 of the machine.
  • this half-angle at the apex 6 can be adjusted by a judicious choice of the angular position of the eccentric bearing 14 in the sleeve 23.
  • the plate 4 being moreover immobilized in rotation by the connecting rod 26 or by the bevel gears 31, 32, it describes around the fixed axis 7, a swaying movement, which acts in the known manner on the pistons 3, to animate them an alternative pumping movement.
  • the reactions developed by pistons 3 due to the pressure of the pumped liquid combine in a resultant which tends to tear off the plate 4 out of the fixed ball joint18, in the direction of arrow 22.
  • the undercut shape of the bearing 17 which closes around the fixed arm 19 opposes this tearing, by causing friction mainly in the annular zone lubricated by the orifices 35.
  • the forces thus supported by the plate 4 are therefore transmitted to the spherical ball joint 18 which transfers them, by the arm 19, directly on the fixed barrel 1.
  • the positioning of the drive shaft 16 can be done at will thanks to the orientation of the flange 44 relative to the counter flange 45, these two flanges being in fact coaxial with the geometric axis 7 of the barrel.
  • axis 46 coaxial with the axis 7 integral with the pinion 13, can be used to drive a tachometer or can also be used to convey the lubricant from the sleeve 23.
  • the invention applies in particular to compressors, pumps or hydraulic motors with axial pistons either for loaded fluids.
  • the casing 30 of the pump is divided into two parts provided one with a flange 58, the other 59 with a counter flange 60 to connect them to each other , these two flanges being circular and centered on the axis 7 of the machine, which makes it possible to shift their relative angular positioning by notches.
  • a rotary machine for example a pump, comprising a barrel fixed 61, in which are arranged bores 62 parallel to each other, and distributed around the geometric axis 7 of the assembly.
  • a piston 64 slides, the rod 65 of which bears, by a pad 66, on an inclined oscillating plate 67.
  • This plate carries, in its center, a spherical bearing 68, 69, is engaged around the sphere a fixed ball joint 70.
  • the fixed ball 70 is integral with a first half-shaft 71, and with a second half-shaft 72, between which it is located.
  • the two half-shafts 71 and 72 are aligned with each other, on either side of the ball joint 70, both centered on the longitudinal axis 7 of the machine.
  • the two half-shafts 71 and 72 can sometimes form only one rigid, one-piece shaft.
  • the first half-shaft 71 is embedded in the central part of the barrel 61.
  • the second half-shaft 72 is integral with the rear part 59 of the fixed casing 30 of the machine.
  • the second half-shaft 72 is extended towards the rear, by a threaded rod 74, which freely passes through a central orifice 76 of the rear cover 75.
  • a nut 77 screwed onto the threaded rod 74 outside the cover 75 used to fix the second half-shaft 72 in order to stiffen the casing 30.
  • a shoulder 78 is provided on the first half-shaft 71, near the ball joint 70, which bears on the inner face of the barrel 61, while at the front of this same barrel, the half-shaft 71 is extended by a threaded rod 79, onto which a nut 80 can be more or less screwed.
  • the periphery of this nut bearing on the front face of the barrel 61 it is understood that by acting on the nut 80, it is possible to resume on the front face of the barrel the tensile forces to which the first half-shaft 71 will also be subjected.
  • the central part of the half-shaft 71 is arranged in a central bore 81 of the barrel 61, where it can freely slide in the longitudinal direction.
  • the thrust front face of the plate 67 is perpendicular to a geometric axis 82 which forms with the axis geometric 7, an acute angle 83. These two geometric axes 7 and 82 converge towards the center 90 of the spherical ball joint 70.
  • the plate 67 rotates around the geometric axis 82 and, for this, its rear face is supported by a stop with tapered roller 84 on a motion transmitter 85. The latter in turn is supported by a roller stop 86 on the rear cover 75 of the casing 30.
  • This rear cover 75 of the casing 30 is screwed onto the casing 30, with interposition a spacer of annular thickness 87, the thickness of which 88 can be chosen at will, according to the desired preloads.
  • the movement transmitter 85 is traversed, in its central part, by a longitudinal bore 89, inside which the second half-shaft 72 can freely move.
  • the movement transmitter 85 On its periphery, the movement transmitter 85 is equipped with a toothed pinion 90, centered on the geometric axis 7.
  • This pinion 90 meshes with a control pinion 91, of smaller diameter, which is located laterally in the casing 30 , secured to a rotating output shaft 92, arranged outside.
  • the geometric axis 93 of this output shaft 92 is parallel to the geometric axis 7.
  • a balancing weight 94 is fixed to the pinion 90 by screws 95.
  • a lateral link 96 is articulated by one of its ends 97 (FIG. 5), in a bearing 98, integral with the plate 67 which is thus immobilized in rotation.
  • the linkage thus represented, and in particular the structure of the motion transmitter 85 have the advantage of allowing the axial thrust of the roller thrust bearings 84 and 86, thanks to the shim 87 which is compressed by the rear cover 75, itself fixed to the bottom of the casing 30, by screws 99, and by the nut 77.
  • the thickness 88 of the shim 87 is carefully studied, with a view to applying to the stops 84 and 86, a preload which will be collected by the part of the half-bearings 68 and 69 located to the left of the theoretical transverse diametral plane 100 defined by the spherical ball joint 70.
  • the axial compression preload of the stops 84, 86 takes place, no longer through the shim 87 and the cap 75 (FIG. 5), but using a cap retainer 101, which is fixed on the casing 30, by the screws 99, but inside which an annular hydraulic piston 102 can slide.
  • the latter is provided with two annular seals, namely a sliding inner seal 103 and an outer seal 104, also sliding.
  • the engine space 105 which remains located between the annular piston 102 and the bottom of the cap 101 receives, by a supply opening 106, a hydraulic fluid under pressure shown diagrammatically by the arrow 107.
  • the assembly is calculated so that the minimum stroke of the cylinder 101, 105, corresponds to a minimum permanent mechanical tightening point on the ball of the stop 86.
  • This variant makes it possible to connect the operating pressure of the pump or of the compressor that constitutes the barrel machine, to the pressure exerted by the space 105 on the piston 102.
  • a judicious choice of the useful surface of this piston 102 will allow check the force applied to the stops 84 and 86, and therefore to the ball bearing 68, 69, so as to obtain permanently: - either the aforementioned condition of "floating stop” for the retule 70; - or any desired ratio between the thrusts exerted on this ball 70 on either side of the theoretical plane 100.
  • the movement transmitter 25 is produced in the form of two half-transmitters 108 and 109, each with a corner profile.
  • the planar bearing face 100 along which they are in contact with each other is perpendicular to a theoretical axis 111 passing through the geometric center 112 of the ball 70, this axis 111 forming with the axis geometric 7, an angle 113 equal to half of the aforementioned angle 23, and which corresponds to the axis 22.
  • Screws 114 regularly distributed in a circle around the axis 111, make it possible to assemble two half-transmitters 108 and 109.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Soil Working Implements (AREA)
  • Rotational Drive Of Disk (AREA)
EP86420172A 1985-10-14 1986-06-26 Rotierende Trommelkolbenpumpe mit festem zentralscharnierpunkt Expired EP0225834B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8515604A FR2588617B1 (fr) 1985-10-14 1985-10-14 Machine rotative a pistons et a barillet avec rotule de centrage fixe.
FR8515604 1985-10-14

Publications (2)

Publication Number Publication Date
EP0225834A1 true EP0225834A1 (de) 1987-06-16
EP0225834B1 EP0225834B1 (de) 1989-09-27

Family

ID=9324045

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86420172A Expired EP0225834B1 (de) 1985-10-14 1986-06-26 Rotierende Trommelkolbenpumpe mit festem zentralscharnierpunkt

Country Status (8)

Country Link
US (1) US4815327A (de)
EP (1) EP0225834B1 (de)
CA (1) CA1307163C (de)
DE (1) DE3665905D1 (de)
DK (1) DK165063C (de)
FR (1) FR2588617B1 (de)
NO (1) NO165508C (de)
SU (1) SU1514246A3 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998051905A1 (en) * 1997-05-14 1998-11-19 Ahto Anttila Axial piston engine

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2619166B2 (fr) * 1985-10-14 1990-02-02 Drevet Michel Machine rotative a pistons et a barillet avec rotule de centrage fixe
ES2018627B3 (es) * 1987-08-06 1991-04-16 Michel Drevet Maquina giratoria de pistones y tambor con rotulo de centrado fijo.
US4885980A (en) * 1988-03-10 1989-12-12 Stirling Thermal Motors, Inc. Hydrodynamic bearing
US4994004A (en) * 1988-11-30 1991-02-19 Stirling Thermal Motors, Inc. Electric actuator for swashplate
US5114261A (en) * 1989-07-31 1992-05-19 Honda Giken Kogyo Kabushiki Kaisha Swashplate type hydraulic device having a ball joint connection
ZA935640B (en) * 1992-08-06 1995-08-08 Hydrowatt Syst Axial piston machine, in particular axial piston pump or axial piston motor
US5493862A (en) * 1994-11-03 1996-02-27 Martin Marietta Corporation Continuously variable hydrostatic transmission
US5535589A (en) * 1995-01-30 1996-07-16 Martin Marietta Corporation Ratio controller for continuously variable hydrostatic transmission
JP4035193B2 (ja) * 1997-02-26 2008-01-16 株式会社日立製作所 アキシャルピストン機械
US6109034A (en) * 1997-04-25 2000-08-29 General Dynamics Land Systems, Inc. Continuously variable hydrostatic transmission ratio controller capable of generating amplified stroking forces
FR2935735B1 (fr) 2008-09-08 2010-09-10 Michel Drevet Machine rotative a pistons et barillet
MD309Y (ro) * 2010-02-23 2010-12-31 Артур НИКИШОВ Maşină cu piston axial

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DE1453650A1 (de) * 1962-10-01 1969-02-06 Hugues Schellenberg Rotierende Trommelkolbenpumpe mit veraenderlicher Foerderleistung
US3663122A (en) * 1970-11-25 1972-05-16 Mcneil Corp Axial plunger pump
FR2211090A5 (de) * 1972-12-14 1974-07-12 Creusot Loire
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FR2271459A1 (de) * 1973-11-09 1975-12-12 Creusot Loire
EP0130912A1 (de) * 1983-07-01 1985-01-09 Framatome Schiefscheibentriebwerk, insbesondere für der Antrieb einer Pumpe
FR2572774A1 (fr) * 1984-11-06 1986-05-09 Drevet Michel Pompe a pistons a barillet, notamment pour des fluides a haute pression

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Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1453650A1 (de) * 1962-10-01 1969-02-06 Hugues Schellenberg Rotierende Trommelkolbenpumpe mit veraenderlicher Foerderleistung
US3223042A (en) * 1963-06-14 1965-12-14 Frank Wheatley Corp Multi-piston variable stroke pump
US3663122A (en) * 1970-11-25 1972-05-16 Mcneil Corp Axial plunger pump
FR2211090A5 (de) * 1972-12-14 1974-07-12 Creusot Loire
FR2251220A5 (de) * 1973-11-09 1975-06-06 Girodin Marius
FR2271459A1 (de) * 1973-11-09 1975-12-12 Creusot Loire
EP0130912A1 (de) * 1983-07-01 1985-01-09 Framatome Schiefscheibentriebwerk, insbesondere für der Antrieb einer Pumpe
FR2572774A1 (fr) * 1984-11-06 1986-05-09 Drevet Michel Pompe a pistons a barillet, notamment pour des fluides a haute pression

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998051905A1 (en) * 1997-05-14 1998-11-19 Ahto Anttila Axial piston engine
US6202606B1 (en) 1997-05-14 2001-03-20 Ahto Anttila Axial-piston engine

Also Published As

Publication number Publication date
DK486286D0 (da) 1986-10-10
CA1307163C (fr) 1992-09-08
DK165063C (da) 1993-02-15
NO165508C (no) 1991-02-20
NO165508B (no) 1990-11-12
FR2588617A1 (fr) 1987-04-17
FR2588617B1 (fr) 1989-11-24
DE3665905D1 (en) 1989-11-02
NO864069D0 (no) 1986-10-13
DK486286A (da) 1987-04-15
NO864069L (no) 1987-04-15
SU1514246A3 (ru) 1989-10-07
EP0225834B1 (de) 1989-09-27
US4815327A (en) 1989-03-28
DK165063B (da) 1992-10-05

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