EP0225834A1 - Piston and barrel rotary machine with a fixed central swivel member - Google Patents

Piston and barrel rotary machine with a fixed central swivel member 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
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Granted
Application number
EP86420172A
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German (de)
French (fr)
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EP0225834B1 (en
Inventor
Michel Drevet
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Individual
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Individual
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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)
  • Soil Working Implements (AREA)
  • Rotational Drive Of Disk (AREA)
  • Hydraulic Motors (AREA)

Abstract

L'invention concerne une pompe à barillet (1) et à plateau oscillant (67), avec rotule centrale fixe (70).The invention relates to a barrel pump (1) and a swash plate (67), with a fixed central ball joint (70).

Le plateau (67) a en son centre, un palier sphérique (68,69) dont la section méridienne circulaire correspond à un angle an centre supérieur à 180°, alors qu'à l'intérieur de ce palier sphérique (68,69) est disposée une rotule sphérique fixe (70) solidaire d'un bras (71) ancré axialement dans le centre du barillet (61).The plate (67) has in its center, a spherical bearing (68,69) whose circular meridian section corresponds to an angle in the center greater than 180 °, while inside this spherical bearing (68,69) is arranged a fixed spherical ball joint (70) secured to an arm (71) anchored axially in the center of the barrel (61).

La rotule (70) peut être solidaire de deux demi-arbres (71,72) dont on peut régler la précontrainte axiale par des écrous (77,80) et par une cale d'épaisseur (87).

Figure imgaf001
The ball joint (70) can be secured to two half-shafts (71,72) of which the axial preload can be adjusted by nuts (77,80) and by a shim (87).
Figure imgaf001

Description

La présente invention est relative à une machine ro­tative à pistons du type à barillet, plus particulièrement prévue pour refouler des fluides à haute pression, et notamment des li­quides chargés.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.

On sait que des pompes de ce type sont couramment utilisées dans l'industrie minière ou dans l'industrie pétrolière, pour pomper des liquides chargés, tels que du pétrole, des boues liquides, des fluides de fracturation, ou analogues. Les pompes de ce type sont couramment de grandes dimensions et prévues pour refouler le liquide avec un débit important, sous des pressions élevées, couramment supérieures à 200 bars.It is known that 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.

Dans le cas particulier des exploitations pétroliè­res, il est en outre nécessaire qu'une pompe de ce type reste de dimensions relativement réduites, suffisamment pour permettre de la charger et de la transporter avec son moteur d'entraînement en une seule fois sur un camion. Le problème étant ainsi posé, on cmprend que la tendance soit à réduire le poids et les dimensions hors tout de la pompe, tout en augmentant la pression à laquelle elle refoule le liquide. Les solutions connues à ce jour consis­tent à utiliser une pompe à piston à barillet, l'embiellage des pistons étant commandé à partir d'un plateau incliné rotatif. Les techniques connues à ce jour consistent à faire reposer le plateau incliné rotatif sur des butées que porte le fond du carter de la pompe, lequel carter entoure l'embiellage, pour remonter jusqu'au barillet auquel il est lié.In the particular case of petroleum operations, it is also necessary for a pump of this type to remain relatively small, sufficient to allow it to be loaded and transported with its drive motor all at once on a truck. The problem being thus posed, it is understood that the tendency is to reduce the weight and the overall dimensions of the pump, while increasing the pressure at which it delivers the liquid. The solutions known to date consist in using a barrel piston pump, the connecting rods of the pistons being controlled from a rotary inclined plate. The techniques known to date consist in resting the rotary inclined plate on stops carried by the bottom of the pump casing, which casing surrounds the crankshaft, to go up to the barrel to which it is linked.

En pratique, on constate que cette technique connue présente un grave inconvénient. En effet, le carter extérieur de la pompe assure la transmission des efforts de poussée entre les butées arrière du plateau rotatif oscillant, et le barillet dans les cylindres duquel le liquide est refoulé par les pistons. Au­trement dit, plus la pression de refoulement du liquide est éle­vée, plus les efforts transmis par le carter sont importants et plus ce carter doit donc être largement dimensionné et lourd. Les pompes connues à ce jour ont ainsi atteint une limite au-­delà de laquelle il n'est plus possible d'augmenter la pression du liquide sans augmenter le poids et l'encombrement de l'ensem­ble qui devient alors intransportable par camion.In practice, it is found that this known technique has a serious drawback. Indeed, the external casing of the pump ensures the transmission of the thrust forces between the rear stops of the oscillating rotary plate, and the barrel in the cylinders from which the liquid is discharged by the pistons. In other words, the higher the discharge pressure of the liquid, the greater the forces transmitted by the casing and the more this casing must therefore be large and heavy. The pumps known to date have thus reached a limit beyond which it is no longer possible to increase the pressure of the liquid without increasing the weight and size of the assembly which then becomes untransportable by truck.

La présente invention a pour but d'éviter ces in­convénients, en réalisant une machine rotative à barillet et à plateau incliné rotatif, dont l'embiellage d'un type nouveau permet d'augmenter la pression de refoulement du liquide, tout réduisant le poids d'ensemble de l'appareil.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.

Une machine rotative selon l'invention comprend un barillet fixe, dans les alésages cylindriques duquel coulissent des crosses directement reliées à des pistons de refoulement, dont cha­cune est reliée par une bielle à un plateau incliné à mouvement rotatif louvoyant, dont la face arrière estéquipée d'un tourillon central d'entraînement orienté perpendiculairement à la face de poussée avant du plateau, et elle est caractérisée en ce que la face avant du plateau comporte, en son centre, un palier sphérique, dont la section méridienne circulaire correspond à un angle au cen­tre supérieur à 180 °, préférablement de l'ordre de 240 ° ou davan­tage, alors qu'à l'intérieur de ce palier sphérique, est disposée une rotule sphérique fixe, solidaire d'un bras ancré axialement dans le centre du barillet, si bien que la poussée du plateau en cours de fonctionnement est transmise directement au barillet par l'intermédiaire du palier sphérique travaillant à l'arrachement, et ceci sans faire intervenir la résistance des parois du carter, notamment dans sa partie arrière.A rotary machine according to the invention 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.

Suivant une autre caractéristique de l'invention, le tourillon arrière du plateau louvoyant est placé dans un palier solidaire du voile d'un pignon sur lequel il occupe une position excentrique. Le pignon en question est entraîné en rotation à par­tir d'un engrenage latéral motorisé, sur lequel il engrène.According to another characteristic of the invention, 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.

Suivant une autre caracteristique de l'invention, le tourillon arrière pour la commande du platteau à mouvement lou­voyant est monté dans le voile du pignon par une articulation sphé­rique.According to another characteristic of the invention, the rear trunnion for the control of the platter with wiggling movement is mounted in the veil of the pinion by a spherical joint.

Suivant une autre caractéristique de l'invention, l'articulation sphérique en question est portée par un plateau excentré, dont on peut choisir à volonté l'orientation angulaire par rapport au voile du pignon qui le porte. Ainsi, on choisit au montage l'excentricité du palier sphérique par rapport au voile du pignon, ce qui permet de régler l'amplitude de la course réelle des pistons de la pompe, et par conséquent, la valeur maxima du couple moteur à la pression de refoulement désirée pour le fluide pompé.According to another characteristic of the invention, 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. Thus, when mounting, 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.

Suivant une autre caractéristique de l'invention, le plateau incliné à mouvement louvoyant est immobilisé en rotation par une bielle latérale le reliant au carter.According to another characteristic of the invention, the tilting platform with a weaving movement is immobilized in rotation by a lateral connecting rod connecting it to the casing.

Suivant une autre caractéristique de l'invention, le plateau incliné à mouvementlouvoyant est immobilisé en rotation par un couple d'engrenages coniques dont l'un est porté par la périphérie de la face arrière du plateau louvoyant, alors que l'au­tre, sur lequel il engrène, est solidaire du carter de la pompe.According to another characteristic of the invention, 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.

Suivant une autre caractéristique de l'invention, on prévoit, entre la face avant du plateau louvoyant, et la face en regard du barillet fixe, les organes à mouvement alternatif d'une pompe de graissage à pistons axiaux.According to another characteristic of the invention, provision is made, between the front face of the tacking plate, and the opposite face of the fixed barrel, for the reciprocating members of a greasing pump with axial pistons.

Suivant une autre caractéristique de l'invention, la lubrification du palier sphérique central de la face avant du pla­teau est assurée à partir d'un canal principal disposé longitudi­nalement dans le bras, pour déboucher à l'intérieur de la sphère où il se ramifie en plusieurs canaux radiaux débouchant sur la périphie de la sphère fixe, notamment dans la zone annulaire, où celle-ci travaille à l'arrachement.According to another characteristic of the invention, 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.

Suivant une autre caractéristique de l'invention, le réducteur d'entraînement du plateau incliné à mouvement lou­voyant est fixé au carter de la partie mécanique de la pompe au moyen d'une bride et d'une contrebride coaxiales avec l'axe de sortie du réducteur et avec l'axe du barillet donnant ainsi l'a­vantage de pouvoir orienter à volonté l'axe du pignon d'entrée du réducteur.According to another characteristic of the invention, 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.

Suivant une caractéristique de l'invention, la ro­tule sphérique centrale est par ailleurs solidaire d'un second demi-arbre rigide, situé à l'opposé du premier avec lequel il est aligné, ce second demi-arbre étént par son extrémité opposée, ri­gidement ancré sur la partie arrière du carter de la machine. Il est à noter que ces deux demi-arbres peuvent dans certains mon­tages ne former qu'un seul arbre monobloc.According to a characteristic of the invention, 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.

Suivant une autre caractéristique de l'invention, des moyens de précharge du palier sphérique sont disposés entre l'arrière du carter et l'extrémité correspondante du second demi-­arbre qui y prend appui. Cette précharge de la rotule sphérique soumet celle-ci à des charges opposées à celles qu'elle subit du fait de la poussée des pistons sur le plateau.According to another characteristic of the invention, 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.

Suivant une autre caractéristique de l'invention, l'extrémitégauche du second demi-arbre est constituée par une tige filetée qui traverse le fond du carter fixe, derrière lequel on y visse un écrou de mise sous tension en vue de rigidifier parfai­tement le carter.According to another characteristic of the invention, 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.

Suivant une autre caractéristique de l'invention, les moyens de mise en précharge du palier sphérique sont consti­tués parl'utilisation d'une cale d'épaisseur, convenablement choisie, qu'on intercale entre un couvercle amovible et l'arrière du carter dont il constitue le fond en vue de comprimer une butée à rouleaux.According to another characteristic of the invention, 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.

Suivant une autre caractéristique de l'invention, les moyens de précharge utilisée sont constitués par l'interposi­tion entre le fond fixe de l'arrière du carter et une butée à rou­leaux sur laquelle prend appui l'arrière du plateau oscillant incliné, d'un vérin hydraulique annulaire coaxial.According to another characteristic of the invention, 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.

Suivant une autre caractéristique de l'invention, l'alimentation du vérin de précharge du palier sphérique est assu­rée en fluide sous pression, par une canalisation qui le relie à la pression de refoulement fournie par la machine dans le cas où celle-ci est une pompe.According to another characteristic of the invention, 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.

Suivant une autre caractéristique de l'invention, le plateau oscillant incliné est réalisé par assemblage de deux pla­teaux superposés,ayant chacun un profil en coin, des moyens, étant prévus pour fixer l'un sur l'autre, de facon amovible, les deux demi-plateaux en coin dont l'orientation angulaire relative a été choisie en fonction de la course désirée pour les pistons de la machine à barillet.According to another characteristic of the invention, 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.

Le dessin annexé, donné à titre d'exemple non limi­tatif, permettra de mieux comprendre les caractéristiques de l'invention.

  • Figure 1 est en vue en coupe axiale d'une pompe à barillet selon l'invention.
  • Figure 2 est en vue en bout, montrant le palier sphérique excentrique du tourillon commandant le plateau.
  • Figure 3 est une coupe suivant III -III (figure 1).
  • Figure 4 correspond à la figure 1, pour une variante de réalisation où le plateau est immobilisé en rotation par un couple d'engrenages coniques.
  • Figure 5 est une vue en coupe axiale d'une pompe hy­ draulique à barillet selon l'invention.
  • Figure 6 est une vue analogue, montrant à grande échelle, le détail de l'embiellage dont les deux demi-plateaux inclinés sont assemblés à la position qui confére aux pistons la course maxima.
  • Figure 7 est une coupe analogue, les deux demi-pla­teaux étant assemblés, cette fois, à la position de course nulle.
  • Figure 8 montre une variante où un vérin hydraulique annulaire équipe l'arrière du carter, pour la mise sous précon­trainte de tension du second demi-arbre supportant la rotule cen­trale.
The appended drawing, given by way of nonlimiting example, will allow a better understanding of the characteristics of the invention.
  • Figure 1 is a view in axial section of a barrel pump according to the invention.
  • Figure 2 is an end view, showing the eccentric spherical bearing of the journal controlling the plate.
  • Figure 3 is a section along III -III (Figure 1).
  • Figure 4 corresponds to Figure 1, for an alternative embodiment where the plate is immobilized in rotation by a pair of bevel gears.
  • Figure 5 is an axial sectional view of a hy pump barrel hydraulics according to the invention.
  • Figure 6 is a similar view, showing on a large scale, the detail of the connecting rod assembly of which the two inclined half-plates are assembled in the position which gives the pistons the maximum stroke.
  • Figure 7 is a similar section, the two half-plates being assembled, this time in the zero stroke position.
  • Figure 8 shows a variant where an annular hydraulic cylinder equips the rear of the casing, for the tensioning of the second half-shaft supporting the central ball joint.

On a représenté sur les dessins, une pompe à barillet qui comprend :
- un barillet fixe 1, dans les alésages 2 duquel des crosses ou des pistons 3 coulissent suivant un mouvement alternatif ;
- un plateau incliné 4, dont l'axe géométrique 5 forme un angle aigu 6 avec l'axe géométrique 7 du barillet 1 ;
- des bielles 8, dont chacune possède deux extrémités sphériques 9 et 10, pour assurer la liaison entre chaque crosse ou piston 3, et le plateau à mouvement louvoyant 4 ;
- un maneton arrière 11, solidaire du plateau 4, et co-linéaire avec l'axe 5 ;
- unpignon de commande 12, axé sur l'axe géométrique 7 autour du­quel il tourne, tandis que, dans son voile 13, est prévu un palier excentré 14, pour le maneton 11 ;
- un engrenage latéral 15, qui engrène sur la denture du pignon 12, et dont l'arbre 16 est entraîné par un moto-réducteur non re­présenté.There is shown in the drawings, 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.

La partie centrale de la face avant du plateau 4 por­te, en creux, un palier sphérique 17, à l'intérieur duquel est ar­ticulée une rotule sphérique 18. Cette dernière est solidaire d'un bras 19.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.

Ce bras 19 est monté à poste fixe dans la partie cen­trale du barillet 1, le long de l'axe géometrique 7.This arm 19 is mounted in a fixed position in the central part of the barrel 1, along the geometric axis 7.

On voit, notamment sur les figures 1 et 4, que la rotule sphérique 18 est emprisonné dans le palier sphérique 17, suivant un angle au centre 20, qui est nettement supérieur à 180°. Autrement dit, le bord 21 du palier sphérique 17 se referme derriè­re le grand diamètre de la rotule 18. Dans le cas particulier du du dessin, l'angle au centre 20 est de l'ordre de 260°, si bien que lorsque le plateau 4 est soumis par la réaction des pistons 3 à une poussée orientée dans le sens de la flèche 22, le palier 17 travaille à l'arrachement, autour de larotule fixe 18.It can be seen, in particular in FIGS. 1 and 4, that 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 °. In other words, the edge 21 of the spherical bearing 17 closes behind the large diameter of the ball joint 18. In the particular case of in the drawing, 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.

Le tourillon 11 est préférablement monté dans un manchon de palier 23, qui est sphérique. La section méridienne sphérique 24 du manchon 23 permet à l'axe géométrique 5 du plateau 4 et du maneton 11, d'osciller lègérement lorsqu'on fait varier l'angle d'inclinaison 6 du plateau 4, pour régler la course des pistons 3 et la pression de refoulement du liquide.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.

L'excentricité du palier 14 permet, en faisant tour­ner celui-ci d'une position angulaire à une autre, autour de l'a­xe géométrique 7, de faire varier l'excentration de celui-ci, par rapport au manchon 23, ce qui a pour effet de faire varier l'ex­centration de celui-ci, par rapport au manchon 23, ce qui a pour effet de faire varier l'angle d'inclinaison 6. Dans l'exemple il­lustré sur la figure 2, le palier excentré 14 possède huit perça­ges 25, répartis sur sa périphérie. Ainsi, par mise en place de boulons de fixation dans les perçages 25, on peut choisir à 1/8ème de tour prés, la position angulaire du manchon 23 dans le palier 14 du voile 13.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. In the example illustrated in Figure 2, 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.

Dans l'exemple illustré sur les figures 1 à 3, une bielle latérale 26 à extrémités sphériques articulées 27 et 28, relie la périphérie du plateau louvoyant 4, à une partie fixe 29 du carter 30 de la pompe. Cette bielle 26 a pour but d'immobiliser en rotation le plateau 4, au cours de son mouvement louvyant com­mandé par la rotation sur lui-même du pignon 13.In the example illustrated in FIGS. 1 to 3, 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.

Dans la variante illustrée sur la figure 4, le pla­teau louvoyant 4 est immobilisé en rotation, non plus par la bielle latérale 26, mais par un couple de deux engrenages coniques 31 et 32, ayant chacun le mêne nombre de dents, à savoir :
- un engrenage conique 31, prévu sur la face arrière à la péri­phérie du plateau 4 ;
- un engrenage conique 32, solidaire du carter fixe 30 de la pom­pe, et axé sur l'axe géométrique 7.In the variant illustrated in FIG. 4, 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.

La rotation du pignon 12 commandant le mouvement louvoyant du plateau incliné 4, le pignon mobile 31 roule sur le pignon fixe 32, ce qui immobilise en rotation le plateau oscil­lant 4.The rotation of the pinion 12 controlling the swinging movement of the inclined plate 4, the movable pinion 31 rolls on the fixed pinion 32, which immobilizes in rotation the oscillating plate 4.

Suivant une autre caractéristique de l'invention, le bras fixe 19 est percé d'un canal axial 33 relié à une source d'alimentation en huile de graissage sous pression. Le canal 33 se ramifie dans la partie centrale de la rotule 18, en plusieurs canaux radiaux 34 qui débouchent dans le palier sphérique 17, par des ouvertures 35 situées notamment dans la partie en contre-dé­pouille du palier 17, c'est-à-dire dans la partie où celui-ci travaille à l'arrachement, sur la rotule 18, autour du bras fixe 19.According to another characteristic of the invention, 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.

Le canal 33 peut également se ramifier suivant un ou plusieurs canaux 36, lubrifiant la partie arrière du palier 17.The channel 33 can also branch along one or more channels 36, lubricating the rear part of the bearing 17.

La lubrification du palier sphérique 17 peut être effectuée dans certaines applications par une pompe à huile à pis­ton axial à mouvement alternatif.The lubrication of the spherical bearing 17 can be carried out in certain applications by an oil pump with axial piston with reciprocating movement.

Il s'agit d'une pompe constituée par un alésage fixe 37 localisé dans le barillet 1 et à l'intérieur duquel coulisse un piston 38 qu'une biellette à paliers sphériques relie à la face avant du plateau louvoyant 4. La biellette 39 est percée d'un ca­nal 41. Cette pompe à huile possède un clapet 42. Elle est ali­mentée par un orifice 43. Au cours du mouvement du plateau lou­voyant 4, le piston 38 est animé d'un mouvement alternatif lui permettant de refouler l'huile à la manière connue dans une cana­lisation 40 grâce à l'action du clapet antiretour 42. Notons que l'alimentation des canaux de graissage 33 et/ou 43 peut être effec­tuée à partir de toute pompe de graissage extérieure de type connu. Il est important de noter que la lubrification peut se faire soit en hydrostatique, soit en hydrodynamique selon les applications.It is 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. During the movement of the swinging plate 4, 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. Note that 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.

Le fonctionnement est le suivant :The operation is as follows:

Lorsqu'on entraîne en rotation l'arbre moteur 16, l'axe géométrique 5 du plateau 4 constitue une génératrice décri­vant une surface conique de demi-angle au sommet 6 autour de l'a­xe fixe 7 de la machine. On a vu que la valeur exacte de ce demi-­angle au sommet 6 peut être réglée par un choix judicieux de la position angulaire du palier excentré 14 dans le manchon 23.When the drive shaft 16 is rotated, 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. We have seen that the exact value of 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.

Le plateau 4 étant par ailleurs immobilisé en ro­tation par la bielle 26 ou par les pignons coniques 31, 32, il décrit autour de l'axe fixe 7, un mouvement louvoyant, qui agit à la manière connue sur les pistons 3, pour les animer d'un mou­vement alternatif de pompage. Les réactions développées par les pistons 3 du fait de la pression du liquide refoulé se combi­nent en une résultante qui tend à arracher le plateau 4 hors de la rotule fixe18, suivant la direction de la flèche 22. La forme en contre-dépouille du palier 17 qui se referme autour du bras fixe 19 s'oppose à cet arrachement, en provoquant un frottement principalement dans la zone annulaire lubrifiée par les orifices 35. Les efforts ainsi supportés par le plateau 4 se transmettent donc à la rotule sphérique 18 qui les reporte, par le bras 19, directement sur le barillet fixe 1. Autrement dit, les efforts développés par la poussée des pistons 3 sur le plateau 4 sont encaissés directement par la réaction du ba­rillet 1 au niveau du bras 19, sans avoir à passer par le car­ter 30 de la pompe. Ce dernier peut donc être réalisé suivant une structure particulièrement légère. De plus, on voit que si l'on augmente la pression de refoulement du fluide pompé par les pistons 3, cela n'a pratiquement aucune incidence sur les efforts auxquels est soumis le carter fixe 30.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. In other words, the forces developed by the pushing of the pistons 3 on the plate 4 are collected directly by the reaction of the barrel 1 at the level of the arm 19, without having to pass through the casing 30 of the pump. The latter can therefore be produced according to a particularly light structure. In addition, it can be seen that if the discharge pressure of the fluid pumped by the pistons 3 is increased, this has practically no effect on the forces to which the fixed casing 30 is subjected.

En fonction des nécessités du montage de la pompe dans une installation, le positionnement de l'arbre d'entraî­nement 16 peut se faire à volonté grâce à l'orientation de la bride 44 par rapport à la contrebride 45, ces deux brides é­tant en effet coaxiales avec l'axe géométrique 7 du barillet.Depending on the requirements for mounting the pump in an installation, 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.

A noter que l'axe 46 coaxial avec l'axe 7 soli­daire du pignon 13, peut servir à l'entraînement d'un tachy­mètre ou peut aussi être utilisé pour acheminer le lubrifiant du manchon 23.Note that the 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.

L'invention s'applique en particulier aux compres­seurs, pompes ou moteurs hydrauliques à pistons axiaux soit pour des fluides chargés.The invention applies in particular to compressors, pumps or hydraulic motors with axial pistons either for loaded fluids.

Suivant une variante illustrée sur la Figure 5, le carter 30 de la pompe est partagé en deux parties munies l'­une 57 d'une bride 58, l'autre 59 d'une contrebride 60 pour les raccorder l'une à l'autre, ces deux brides étant circu­laires et centées sur l'axe 7 de la machine, ce qui permet de décaler par crans leur positionnement angulaire relatif. On peut ainsi choisir à volonté la position angulaire de l'arbre d'entraînement 32 autour de l'axe géometrique 7 de la machine. Dans la variante des figures 5 à 8, on a représenté une ma­chine tournante, par exemple une pompe, comportant un barillet fixe 61, dans lequel sont disposés des alésages 62 parllèles entre eux, et répartis autour de l'axe géométrique 7 de l'en­semble. Dans chaque alésage 62, coulisse un piston 64, dont la bielle 65 prend appui, par un coussinet 66, sur un plateau in­cliné oscillant 67. Ce plateau porte, en son centre, un palier sphérique 68, 69, est engagé autour de la sphère d'une rotule fixe 70.According to a variant illustrated in Figure 5, 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. We can thus choose at will the angular position of the drive shaft 32 around the geometric axis 7 of the machine. In the variant of FIGS. 5 to 8, there is shown 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. In each bore 62, 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.

Selon l'invention, la rotule fixe 70 est solidai­re d'un premier demi-arbre 71, et d'un second demi-arbre 72, entre lesquels elle se trouve. Les deux demi-arbres 71 et 72 sont alignés l'un avec l'autre, de part et d'autre de la rotu­le 70, tous deux centrés sur l'axe longitudinal 7 de la machi­ne. Les deux demi-arbres 71 et 72 peuvent quelquefois ne former qu'un seul arbre rigide et monobloc.According to the invention, 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.

Le premier demi-arbre 71 est encastré dans la par­tie centrale du barillet 61.The first half-shaft 71 is embedded in the central part of the barrel 61.

Le second demi-arbre 72 est solidaire de la partie arrière 59 du carter fixe 30 de la machine.The second half-shaft 72 is integral with the rear part 59 of the fixed casing 30 of the machine.

Plus particulièrement, le second demi-arbre 72 se prolonge vers l'arrière, par une tige filetée 74, qui traverse librement un orifice central 76 du couvercle arrière 75. Un écrou 77 vissé sur la tige filetée 74 à l'extérieur du couver­cle 75 permet de fixer le second demi-arbre 72 en vue de rigi­difier le carter 30.More particularly, 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.

De même, on prévoit sur le premier demi-arbre 71, à proximité de la rotule 70, un épaulement 78 qui prend appui sur la face intérieure du barillet 61, alors qu'à l'avant de ce même barillet, le demi-arbre 71 se prolonge par une tige filetée 79, sur laquelle on peut visser plus ou moins un écrou 80. La périphérie de cet écrou prenant appui sur la face avant du barillet 61, on comprend qu'en agissant sur l'acrou 80, on puisse reprendre sur la face avant du barillet les efforts de traction auxquels le premier demi-arbre 71 sera, lui aussi, soumis.Likewise, 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.

La partie centrale du demi-arbre 71 est disposée dans un alésage central 81 du barillet 61, où elle peut li­brement coulisser dans le sens longitudinal.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.

La face avant de poussée du plateau 67 est per­pendiculaire à un axe géométrique 82 qui forme avec l'axe géométrique 7, un angle aigü 83. Ces deux axes géometriques 7 et 82 convergent vers le centre 90 de la rotule sphérique 70. Le plateau 67 tourne antour de l'axe géométrique 82 et, pour cela, sa face arrière prend appui par une butée à rouleaux co­nique 84 sur un transmetteur de mouvement 85. Ce dernier prend à son tour appui par une butée à rouleaux 86, sur le couvercle arrière 75 du carter 30. Ce couvercle arrière 75 du carter 30 est vissé sur le carter 30, avec interposition d'une cale d'­épaisseur annulaire 87, dont l'épaisseur 88 peut être choisie à volonté, en fonction des précharges désirées.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.

Le transmetteur de mouvement 85 est traversé, dans sa partie centrale, par un alésage longitudinal 89, à l'­intérieur duquel peut librement se déplacer le second demi-ar­bre 72.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.

Sur sa périphérie, le transmetteur de mouvement 85 est équipé d'un pignon denté 90, centré sur l'axe géométri­que 7. Ce pignon 90 engrène sur un pignon de commande 91, de plus petit diamètre, qui est situé latéralement dans le carter 30, solidaire d'un arbre de sortie tournant 92, disposé à l'ex-­térieur. L'axe géométrique 93 de cet arbre de sortie 92 est pa­rallèle à l'axe géométrique 7. Une masselote d'équilibrage 94 est fixée sur le pignon 90 par des vis 95.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.

Enfin, une biellette latérale 96 est articulée par l'une de ses extrémités 97 (figure 5), dans un palier 98, solidaire du plateau 67 qui est ainsi immobilisé en rotation.Finally, 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.

On comprend que l'embiellage ainsi représenté, et notamment la structure du transmetteur de mouvement 85, pré­sentent l'avantage de permettre la mise en compression axiale des butées à rouleaux 84 et 86, grâce à la cale d'épaisseur 87 qui est comprimée par le couvercle arrière 75, lui-même fixé sur le fond du carter 30, par des vis 99, et par l'écrou 77. En particulier, on étudie soigneusement l'épaisseur 88 de la cale 87, en vue d'appliquer sur les butées 84 et 86, une pré­charge qui sera encaissée par la partie des demi-coussinets 68 et 69 située à gauche du plan diamétral transversal théorique 100 défini par la rotule sphérique 70. Cette préchange vien­dra donc soulager l'autre partie des demi-coussinets 68 et 69, qui est située à droite du plan théorique 100, et reçoit des effots de poussée exercés par les pistons 64. Ainsi, on garan­ tit tout autour de la calotte sphérique des demi-coussinets 68 et 69, une bonne répartition des pressions spécifiques qui ap­paraissent au cours du fonctionnement de la machine. Un choix judicieux sera par exemple, de calculer l'épaisseur 88 de la cale 87, de sorte que les contraintes à droite et à gauche du plan transversal 100 induisent des pressions égales sur la ca­lotte sphérique du palier centrale 68, 69. Si cette condition est réalisée, on dira que la machine comporte en son centre, une "butée fottante", étant donné qu'à cette position d'équili­bre, la butée sphérique (palier 68, 69, sur la rotule 70) est en charge axiale nulle.It is understood that 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. In particular, 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. This prechange will therefore relieve the other part of the half-bearings 68 and 69, which is located to the right of the theoretical plane 100, and receives thrusting forces exerted by the pistons 64. Thus, we guarantee tit all around the spherical cap of the half-bearings 68 and 69, a good distribution of the specific pressures which appear during the operation of the machine. A judicious choice will be, for example, to calculate the thickness 88 of the wedge 87, so that the stresses to the right and to the left of the transverse plane 100 induce equal pressures on the spherical cap of the central bearing 68, 69. If this condition is carried out, it will be said that the machine has in its center, a "floating stop", since at this position of equilibrium, the spherical stop (bearing 68, 69, on the ball 70) is in zero axial load.

Dans la variante de la figure 8, la précharge de compression axiale des butées 84, 86, s'effectue, non plus l'­intermédiaire de la cale d'épaisseur 87 et du chapeau 75 (fi­gure 5), mais en utilisant un chapeau de retenue 101, qui vient se fixer sur le carter 30, par les vis 99, mais à l'intérieur duquel peut coulisser un piston hydraulique annulaire 102. Ce dernier est pourvu de deux joints d'étanchéité annulaires, à savoir un joint intérieur coulissant 103 et un joint extérieur 104, également coulissant. L'espace moteur 105 qui reste situé entre piston annulaire 102, et le fond du chapeau 101, reçoit, par une ouverture d'alimentation 106, un fluide hydraulique sous pression schématisé par la flèche 107. L'ensemble est calculé de façon que la course minima du vérin 101, 105, corresponde à un point de serrage mécanique minimum permanent sur la rotule de la butée 86.In the variant of FIG. 8, 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.

Cette variante permet de relier la pression d'uti­lisation de la pompe ou du compresseur que constitue la machi­ne à barillet, à la pression exercée par l'espace 105 sur le piston 102. Un choix judicieux de la surface utile de ce pis­ton 102 permettra de contrôler l'effort appliqué sur les bu­tées 84 et 86, et donc sur le coussinet sphérique 68 , 69, de manière à obtenir en permanence :
- soit la condition précitée de "butée flottante" pour la re­tule 70 ;
- soit tout rapport désiré entre les poussées exercées sur cet­te rotule 70 de part et d'autre du plan théorique 100.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.

Dans la variante illustré sur les figures 6 et 7, le transmetteur de mouvement 25 est réalisé sous la forme de deux demi-transmetteurs 108 et 109, chacun à profil en coin. Autrement dit, la face d'appui plane 100 suivant laquelle ils sont en contact l'un avec l'autre, est perpendiculaire à un axe théorique 111 passant par le centre géométrique 112 de la ro­tule 70, cet axe 111 formant avec l'axe géométrique 7, un angle 113 égal à la moitié de l'angle 23 précité, et qui correspond à l'axe 22. Des vis 114, régulièement réparties en cercle au­tour de l'axe 111, permettent d'assembler des deux demi-trans­metteurs 108 et 109.In the variant illustrated in FIGS. 6 and 7, the movement transmitter 25 is produced in the form of two half-transmitters 108 and 109, each with a corner profile. In other words, 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.

On comprend, qu'en choississant leurs positions angulaires relatives autour de l'axe 111, avant de les visser à l'aide des vis 114, on puisse définir la longueur de la cour­se désormais imposée aux pistons 4, 64, pour toute valeur in­termédiaire entre :
- la course maxima correspondant à la position illustrée sur la figure 6 (la zone la plus mince 115 du demi-transmetteur 109 est alors en appui sur la zone du demi-transmetteur 108 qui est situé le plus en arrière le long de l'axe 3) ;
- à la position de course nulle, obtenue par décalage de 180° par rapport à la position de la figure 6, de façon à orienter la face avant 116 du plateau de poussée 4, perpendiculairement à l'axe géométrique longitudinal 7.
- Dans une version plus élaborée on utilise un dispositif de contrôle continu, avec commande extérieure, de la position des deux demi-transmetteurs de mouvement 108 et 109.We understand that by choosing their relative angular positions around the axis 111, before screwing them with screws 114, we can define the length of the stroke now imposed on the pistons 4, 64, for any intermediate value Between :
the maximum stroke corresponding to the position illustrated in FIG. 6 (the thinnest zone 115 of the half-transmitter 109 is then supported on the zone of the half-transmitter 108 which is located furthest back along the axis 3);
- at the zero stroke position, obtained by 180 ° offset from the position in FIG. 6, so as to orient the front face 116 of the thrust plate 4, perpendicular to the longitudinal geometric axis 7.
- In a more elaborate version, a continuous control device is used, with external control, of the position of the two half-movement transmitters 108 and 109.

Claims (21)

1 - Pompe à barillet comprenant un barillet fixe (1), (61) dans les alésages cylindriques (2), (62) duquel cou­lissent des pistons de refoulement (3), (64) dont chacun est re­lié par une bielle (8), (65) à un plateau incliné (4), (67) à mouvement rotatif louvoyant, dont la face arrière est équipée d'un tourillon central d'entraînement (11), orienté suivant un axe (5) perpendiculaire à la face de poussée avant du plateau comporte, en son centre, un palier sphérique (17), (67) dont la section méridienne circulaire correspond à un angle au cen­tre (20) supérieur à 180°, alors qu'à l'intérieur de ce palier sphérique (17),(67) est disposée une rotule sphérique fixe (18), (70) solidaire d'un bras (19), (71) ancré axialement dans le centre du barillet (1), (61), si bien que la poussée du plateau (4), (61) en cours de fonctionnement est transmise directement au barillet (1), (61) par l'intermédiaire du palier sphérique (17), (67) travaillant à l'arrachement, et ceci sans faire in­tervenir la résistance des parois du carter (30), notamment dans sa partie arrière.1 - Barrel pump comprising a fixed barrel (1), (61) in the cylindrical bores (2), (62) of which slide delivery pistons (3), (64) each of which is connected by a connecting rod (8) , (65) to an inclined plate (4), (67) with a swiveling rotary movement, the rear face of which is equipped with a central drive pin (11), oriented along an axis (5) perpendicular to the face of front thrust of the plate comprises, in its center, a spherical bearing (17), (67) whose circular meridian section corresponds to an angle at the center (20) greater than 180 °, while inside this spherical bearing (17), (67) is arranged a fixed spherical ball joint (18), (70) integral with an arm (19), (71) anchored axially in the center of the barrel (1), (61), so that the thrust of the plate (4), (61) during operation is transmitted directly to the barrel (1), (61) via the spherical bearing (17), (67) working in tearing, and this without involve r resistance of the walls of the casing (30), in particular in its rear part. 2 - Pompe à barillet suivant la revendication 1, caractérisée en ce que l'angle au centre (20) est supérieur à 250° .2 - Barrel pump according to claim 1, characterized in that the angle at the center (20) is greater than 250 °. 3. - Pompe à barillet suivant l'une quelconque des revendications précédentes, caractérisée en ce que le tourillon arrière (11) du plateau louvoyant (4) est placé dans un palier (14) solidaire du voile (13) d'un pignon (12) sur lequel il oc­cupe une position excentrique, le pignon (12) étant entraîné en rotation à partir d'un engrenage latéral mptorisé (15) sur le­quel il engrène.3. - Barrel pump according to any one of the preceding claims, characterized in that the rear pin (11) of the tacking plate (4) is placed in a bearing (14) integral with the web (13) of a pinion ( 12) in which it occupies an eccentric position, the pinion (12) being driven in rotation from a side gear mptorized (15) on which it meshes. 4 - Pompe à barrillet suivant l'une quelconque des revendications précédentes, caractérisée en ce que le tourillon arrière (11) pour la commande du plateau à mouvement louvoyant (4) est monté dans le voile (13) du pignon (12), par une articulation sphérique (24).4 - Barrel pump according to any one of the preceding claims, characterized in that the rear pin (11) for the control of the movement plate (4) is mounted in the web (13) of the pinion (12), by a spherical joint (24). 5 - Pompe à barillet suivant la revendication 4, caractérisée en ce que l'articulation sphérique (24) est portée par un manchon (23) placé dans un palier excentré (14) dont on peut choisir à volonté l'orientation angulaire par rapport au voile (13) du pignon qui le porte, si bien qu'on choisit au montage l'excentricité du palier (14) supportant le manchon sphérique (23), par rapport au voile (13) du pignon (12), ce qui permet de régler l'amplitude de la course réelle des pis­tons (3) de la pompe, et par conséquent, la valeur maxima de la pression de refoulement pour le liquide pompé par rapport au couple du moteur d'entraînement.5 - Barrel pump according to claim 4, characterized in that the spherical joint (24) is carried by a sleeve (23) placed in an eccentric bearing (14) which one can choose at will the angular orientation relative to the veil (13) of the pinion which carries it, so that one chooses mounting the eccentricity of the bearing (14) supporting the spherical sleeve (23), relative to the web (13) of the pinion (12), which makes it possible to adjust the amplitude of the real stroke of the pistons (3) of the pump , and therefore the maximum value of the discharge pressure for the pumped liquid in relation to the torque of the drive motor. 6 - Pompe à barillet suivant l'une quelconque des revendications précédentes, caractérisée en ce que le plateau incliné (4) à mouvement louvoyant est immobilisé en rotation par une bielle latérale (26) le reliant au carter (30).6 - Barrel pump according to any one of the preceding claims, characterized in that the inclined plate (4) with swaying movement is immobilized in rotation by a lateral connecting rod (26) connecting it to the casing (30). 7 - Pompe à barillet suivant l'une quelconque des revendications 1 à 5, caractérisée en ce que le plateau incli­né (4) à mouvement louvoyant est immobilisé en rotation par un couple d'engrenages coniques (31) et (32), dont l'un (31) est porté par la périphérie de la face arrière du plateau louvoyant (4), alors que l'autre (32), sur lequel il engrène, est soli­daire du carter (30) de la pompe.7 - Barrel pump according to any one of claims 1 to 5, characterized in that the inclined plate (4) with swaying movement is immobilized in rotation by a pair of bevel gears (31) and (32), of which l 'one (31) is carried by the periphery of the rear face of the tacking plate (4), while the other (32), on which it meshes, is integral with the casing (30) of the pump. 8 - Pompe à barillet suivant l'une quelconque des revendications précédentes, caractérisée en ce qu'on prévoit, entre la face avant du plateau louvoyant (4) et la face en re­gard du barillet fixe (1), les organes à mouvement alternatif (38), (39), d'une pompe de graissage (37), (38), (39), (42) per­mettant d'apporter un lubrifiant dans un canal (40) débouchant dans la zone annulaire travaillant à l'arrachement du palier sphérique (17).8 - Barrel pump according to any one of the preceding claims, characterized in that provision is made, between the front face of the swinging plate (4) and the opposite face of the fixed barrel (1), for reciprocating members ( 38), (39), a greasing pump (37), (38), (39), (42) making it possible to supply a lubricant in a channel (40) opening into the annular zone working at tearing of the spherical bearing (17). 9 - Pompe à barillet suivant l'une quelconque des revendications précédentes, caractérisée en ce que la lubrifi­cation du palier sphérique central (17) de la face avant du pla­teau (4) est assurée à partir d'un canal principal (33) disposé lon­gitudinalement dans le bras (19), pour déboucher à l'intérieur de la sphère (18) où il se ramifie en plusieurs canaux radiaux (34) débouchant en (35) sur la périphérie de la sphère fixe (18), notamment dans la zone annulaire où celle-ci travaille à l'arrachement.9 - Barrel pump according to any one of the preceding claims, characterized in that the lubrication of the central spherical bearing (17) of the front face of the plate (4) is ensured from a main channel (33) arranged longitudinally in the arm (19), to open into the interior of the sphere (18) where it branches into several radial channels (34) opening into (35) on the periphery of the fixed sphere (18), in particular in the area annular where it works with the tearing. 10 - Pompe à barillet suivant l'une quelconque des revendications précédentes, caractérisée en ce que le position­nement de l'arbre d'entraînement (16) peut se faire à volonté grâce à l'orientation de la bride (44) par rapport à la con­trebride (45), ces deux brides coaxiales avec l'axe géométrique (7) faisant partis intégrantes du carter (30).10 - Barrel pump according to any one of the preceding claims, characterized in that 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 coaxial with the geometric axis (7) forming integral parts of the casing (30). 11 - Pompe à barillet suivant l'une quelconque des revendications précédentes, caractérisée en ce que la rotule (70) est par ailleurs solidaire d'un second demi-arbre rigide (72) situé à l'opposé du premier (71) avec lequel il est ali­gné sur l'axe (7), ce second demi-arbre (72) étant par son ex­trémité opposée, rigidement ancré sur la partie arrière du car­ter (30) de la machine.11 - Barrel pump according to any one of the preceding claims, characterized in that the ball joint (70) is also integral with a second rigid half-shaft (72) located opposite the first (71) with which it is aligned with the axis (7), this second half-shaft (72) being by its opposite end, rigidly anchored on the rear part of the casing (30) of the machine. 12 - Machine rotative suivant la revendication 11, caractérisée en ce que des moyens de précharge du palier sphé­rique sont disposés entre l'arrière du carter (30) et les bu­tées à rouleaux (84) et (86) qui prennent appui sur le palier sphérique par l'intermédiaire du transmetteur de mouvement (67).12 - rotary machine according to claim 11, characterized in that the preloading means of the spherical bearing are arranged between the rear of the casing (30) and the roller thrust bearings (84) and (86) which bear on the spherical bearing through the motion transmitter (67). 13 - Machine rotative suivant l'une quelconque des revendications 11 et 12, caractérisée en ce que les deux demi-arbres (71) et (72) équipés respectivement des écrous (74) et (79) permettent la reprise des efforts de traction sur la face avant du barillet (61) et donc contribuent à la parfaite rigidité du carter (30) pendant le fonctionnement de la machine.13 - Rotary machine according to any one of claims 11 and 12, characterized in that the two half-shafts (71) and (72) equipped with nuts (74) and (79) respectively allow the recovery of the traction forces on the front face of the barrel (61) and therefore contribute to the perfect rigidity of the casing (30) during the operation of the machine. 14 - Machine rotative suivant l'une quelconque des revendications 11 et 13 caractérisée en ce que les moyens de précharge de la butée sphérique sont constitués par l'utilisa­tion d'une cale d'épaisseur (87) dont on choisit l'épaisseur (88) et qu'on interclae entre un couvercle amobible (75) et l'­arrière du carter (30) en vue d'exercer une compression pré­déterminé sur la butée à rouleaux (86).14 - Rotary machine according to any one of claims 11 and 13 characterized in that the preloading means of the spherical stop are constituted by the use of a thickness shim (87) whose thickness is chosen (88 ) and interclae between a removable cover (75) and the rear of the housing (30) in order to exert a predetermined compression on the roller stop (86). 15 - Machine rotative suivant l'une quelconque des revendications 11 à 14, caractérisée en ce que les moyens de précharge de la butée sphérique utilisés sont constitués par l'interposition entre le fond fixe de l'arrière du carter (30) et une butée à rouleaux (86), sur laquelle prend appui l'­arrière du plateau rotatif incliné (67), d'un vérin hydrauli­que annulaire coaxial (101), (105).15 - rotary machine according to any one of claims 11 to 14, characterized in that the preloading means of the spherical stop used are constituted by the interposition between the fixed bottom of the rear of the housing (30) and a stop with rollers (86), on which the rear of the inclined rotary plate (67) is supported, with a coaxial annular hydraulic cylinder (101), (105). 16 - Machine rotative suivant la revendication 15, caractérisée ence que l'alimentation du vérin de précontrainte (101), (105) est assurée en fluide sous pression (107) par une canalisation (106) qui le relie à la pression de refoulement fournie par la machine, dans le cas où celle-ci est une pompe ou un compresseur.16 - rotary machine according to claim 15, characterized in that the supply of the prestressing cylinder (101), (105) is ensured in pressurized fluid (107) by a pipe (106) which connects it to the delivery pressure supplied by the machine, if it is a pump or a compressor. 17 - Machine rotative suivant l'une quelconque des revendications 11 à 16 caractérisée en ce que le plateau rotatif incliné (67) prend appui sur un transmetteur de mouve­ment (25) réalisé par assemblage de deux demi-transmetteurs (108) et (109) superposés, ayant chacun un profil en coin, des moyens étant prévus pour fixer l'un sur l'autre, de façon amo­vible, les deux demi-transmetteurs en coin (108) et (109) dont l'orientation angulaire relative a été choisie en fonction de la course désirée pour les pistons (64) de la manche à baril­let, le reglage pouvant aller de la course maxima (Figure 6) à la course nulle ( Figure 7).17 - Rotary machine according to any one of claims 11 to 16 characterized in that the inclined rotary plate (67) is supported on a movement transmitter (25) produced by assembling two half-transmitters (108) and (109) superimposed, each having a wedge profile, means being provided for removably fixing one on the other, the two wedge half-transmitters (108) and (109) whose relative angular orientation has been chosen depending on the desired stroke for the pistons (64) of the barrel handle, the adjustment can range from the maximum stroke (Figure 6) to the zero stroke (Figure 7). 18 - Machine rotative suivant l'une quelconque des revendications 11 à 17, caractérisée en ce que le demi-arbre avant (71) traverse librement un alésage axial longitudinal (81) du barillet (61) sur la face inférieure duquel il prend appui par un épaulement (78), alors que son extrémité avant se termine par une tige filetée (79) sur laquelle est vissé un écrou (80) permettant de régler la charge de traction à laquel­le le demi-arbre (71) est soumis quand l'écrou (80) est en ap­pui sur la face avant du barillet (61).18 - Rotary machine according to any one of claims 11 to 17, characterized in that the front half-shaft (71) freely crosses a longitudinal axial bore (81) of the barrel (61) on the underside of which it is supported by a shoulder (78), while its front end ends in a threaded rod (79) on which is screwed a nut (80) making it possible to adjust the tensile load to which the half-shaft (71) is subjected when the nut (80) is supported on the front face of the barrel (61). 19 - Machine rotative suivant l'une quelconque des revendications 11 à 18, caractérisée en ce que les deux demi-­arbres (71) et (72) sont fabriqués séparément, puis assemblés.19 - Rotary machine according to any one of claims 11 to 18, characterized in that the two half-shafts (71) and (72) are produced separately, then assembled. 20 - Machine rotative suivant l'une quelconque des revendications 11 à 18, caractérisée en ce que les deux demi-arbres (71) et (72) sont fabriqués d'une seule pièce.20 - Rotary machine according to any one of claims 11 to 18, characterized in that the two half-shafts (71) and (72) are made in one piece. 21 - Machine rotative suivant l'une quelconque des revendications prédédentes, caractérisée en ce que le car­ter (30) de la machine est partagé en deux parties (57) et (59) munies, d'une bride (58) l'autre d'une contre-bride (60), pour les raccorder l'une à l'autre, ces deux brides (58), (60) é­tant circulaires, centrées sur l'axe (7) (Figure 1), ce qui permet de décaler par crans leur positionnement angulaire re­latif pour choisir à volonté la position angulaire de l'arbre d'entraînement (32) autour de l'axe (7).21 - Rotary machine according to any one of the preceding claims, characterized in that the casing (30) of the machine is divided into two parts (57) and (59) provided with a flange (58) the other d '' a counter-flange (60), to connect them to each other, these two flanges (58), (60) being circular, centered on the axis (7) (Figure 1), which allows offset by relative notches their relative angular positioning to choose at will the angular position of the drive shaft (32) around the axis (7).
EP86420172A 1985-10-14 1986-06-26 Piston and barrel rotary machine with a fixed central swivel member Expired EP0225834B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8515604A FR2588617B1 (en) 1985-10-14 1985-10-14 ROTARY PISTON AND BARREL MACHINE WITH FIXED CENTERING BALL JOINT.
FR8515604 1985-10-14

Publications (2)

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

Family

ID=9324045

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86420172A Expired EP0225834B1 (en) 1985-10-14 1986-06-26 Piston and barrel rotary machine with a fixed central swivel member

Country Status (8)

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

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WO1998051905A1 (en) * 1997-05-14 1998-11-19 Ahto Anttila Axial piston engine

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FR2619166B2 (en) * 1985-10-14 1990-02-02 Drevet Michel ROTARY PISTON AND BARREL MACHINE WITH FIXED CENTERING BALL
DE3861077D1 (en) * 1987-08-06 1990-12-20 Michel Drevet ROTATING DRUM PISTON MACHINE WITH A FIXED, CENTERING JOINT.
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 (en) * 1997-02-26 2008-01-16 株式会社日立製作所 Axial piston machine
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 (en) * 2008-09-08 2010-09-10 Michel Drevet ROTATING MACHINE WITH PISTONS AND BARREL
MD309Y (en) * 2010-02-23 2010-12-31 Артур НИКИШОВ Axial-piston machine

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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
FR2588617A1 (en) 1987-04-17
DK486286D0 (en) 1986-10-10
DK486286A (en) 1987-04-15
NO864069L (en) 1987-04-15
DK165063C (en) 1993-02-15
DE3665905D1 (en) 1989-11-02
NO165508C (en) 1991-02-20
NO864069D0 (en) 1986-10-13
NO165508B (en) 1990-11-12
EP0225834B1 (en) 1989-09-27
DK165063B (en) 1992-10-05
FR2588617B1 (en) 1989-11-24
CA1307163C (en) 1992-09-08
SU1514246A3 (en) 1989-10-07
US4815327A (en) 1989-03-28

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