EP0225834B1 - 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 PDFInfo
- Publication number
- EP0225834B1 EP0225834B1 EP86420172A EP86420172A EP0225834B1 EP 0225834 B1 EP0225834 B1 EP 0225834B1 EP 86420172 A EP86420172 A EP 86420172A EP 86420172 A EP86420172 A EP 86420172A EP 0225834 B1 EP0225834 B1 EP 0225834B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- barrel
- rotary machine
- machine according
- housing
- shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- 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
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- 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]
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- 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.
- FR A 2 572 774 published on 9.5.1986, made known an embodiment avoiding certain drawbacks, by making a rotary machine with barrel and rotary inclined plate, the linkage of which makes it possible to increase the discharge pressure of the liquid, while reducing the overall weight of the device.
- a barrel pump comprising a fixed barrel in the cylindrical bores from which slide delivery pistons, each of which is connected by a connecting rod to an inclined plate with a rotary swiveling movement, the rear face of which is fitted with a central journal.
- a drive oriented along an axis perpendicular to the front thrust face of the plate and comprises, at its center, a spherical bearing whose circular meridian section corresponds to an angle at the center greater than 180 ° while inside this spherical bearing is arranged a fixed spherical ball joint secured to an arm axially anchored in the center of the barrel, so that the thrust of the plate during operation is transmitted directly to the barrel via the spherical bearing working at tearing, and this without involving the resistance of the walls of the casing, in particular in its rear part.
- FR-A 2 211 090 has made known a barrel mechanism comprising, inside a casing, a motor shaft driven in rotation about its axis, journalling in two bearings supported respectively by two perpendicular casing bottoms to the axis, and on which is fixed an oblique plate with respect to the axis, a barrel resting on the oblique plate and centered, around an axis intersecting the journal axis, on a cylindrical inclined bearing provided on the shaft, perpendicular to the plate, and a means for blocking the rotation of the barrel, characterized in that the two bases of the casing are connected by a tie rod extending along the axis of the journal, in an axial bore of the motor shaft.
- the new arrangement according to the invention eliminates the cantilevered position of the central ball joint, which prevents the rupture of the support shaft of this ball joint, a rupture which can be caused by the influence of fatigue due to high rotating loads. .
- the rotary piston and barrel machine comprising a thrust plate inclined with respect to its geometric axis of rotation which coincides with the geometric axis of the barrel, the central part of the inclined plate comprising a spherical bearing which rotates freely around a fixed central ball joint integral with a first half-shaft anchored directly in the central part of the barrel, while the latter is connected to a rigid peripheral casing which covers the rear of the crankshaft behind which it closes, is characterized in that the central ball joint is also integral with a second rigid half-shaft situated opposite the first with which it is aligned on the axis, this second half-shaft being, by its opposite end , rigidly anchored on the rear part of the machine housing.
- the invention applies in particular to compressors, pumps or hydraulic motors with axial pistons for charged 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. We can thus choose at will the angular position of the drive shaft around the geometric axis 7 of the machine.
- a rotary machine for example a pump, comprising a fixed barrel 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 oscillating inclined plate 67.
- This plate carries, in its center, a spherical bearing 68, 69 and is engaged around the sphere a fixed ball joint 70.
- the fixed ball 70 is integral with a first half-shaft 71 and 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.
- first half-shaft 71 there is provided on the first half-shaft 71, near the ball joint 70, a shoulder 78 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, on which one can more or less screw a nut 80.
- a threaded rod 79 on which one can more or less screw a nut 80.
- the periphery of this nut bearing on the front face of the barrel 61 it is understood that by acting on the nut 80, one can 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 geometric axis 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 tapered roller stop 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 the interposition of a block of annular thickness 87, the thickness of which 88 can be chosen at will, as a function of 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. 1) 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 a preload on the stops 84 and 86 which will be collected by the part of the half-bearings 68 and 69 situated to the left of the theoretical transverse diametral plane 100 defined by the spherical ball joint 70.
- This preload 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 thrust forces exerted by the pistons 64.
- everything is guaranteed 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 fulfilled we say that the machine has in its center a "floating stop" since at this position to balance the spherical stop (bearing 68, 69 on the ball 70) is under zero axial load.
- the axial compression preload of the stops 84, 86 is carried out, no longer via the shim 87 and the cap 75 (fig. 1) but using a retaining cap 101, which comes fix 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 interior seal 103 and an exterior seal 104, also sliding .
- the engine space 105 which remains located between the annular piston 102 and the bottom of the cap 101 receives, via 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 jack 102, 105 corresponds to a minimum permanent mechanical tightening point on the ball of the stop 86.
- the motion transmitter 85 of FIG. 1 is produced in the form of two half-transmitters 108 and 109, each with a corner profile.
- the plane bearing face 110 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 the 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 the two half-transmitters 108 and 109.
- a continuous control device is used, with external control of the position of the two half-movement 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)
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 exploitation 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 comprend 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.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 understandable 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.
Les solutions connues à ce jour sont décrites notamment dans FR-A 2 251 220, US-A 3 223 042 et FR A 2 211 090.The solutions known to date are described in particular in FR-A 2 251 220, US-A 3 223 042 and FR A 2 211 090.
FR A 2 572 774, publié le 9.5.1986, a fait connaître une réalisation évitant certains inconvénients, en réalisant une machine rotative à barillet et à plateau incliné rotatif, dont l'embiellage permet d'augmenter la pression de refoulement du liquide, tout en réduisant le poids d'ensemble de l'appareil. A cette fin, il décrit une pompe à barillet comprenant un barillet fixe dans les alésages cylindriques duquel coulissent des pistons de refoulement dont chacun est relié par une bielle à un plateau incliné à mouvement rotatif louvoyant dont la face arrière est équipée d'un tourillon central d'entraînement orienté suivant un axe perpendiculaire à la face de poussée avant du plateau et comporte, en son centre, un palier sphérique dont la section méridienne circulaire correspond à un angle au centre supérieur à 180° 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.FR A 2 572 774, published on 9.5.1986, made known an embodiment avoiding certain drawbacks, by making a rotary machine with barrel and rotary inclined plate, the linkage of which makes it possible to increase the discharge pressure of the liquid, while reducing the overall weight of the device. To this end, it describes a barrel pump comprising a fixed barrel in the cylindrical bores from which slide delivery pistons, each of which is connected by a connecting rod to an inclined plate with a rotary swiveling movement, the rear face of which is fitted with a central journal. drive oriented along an axis perpendicular to the front thrust face of the plate and comprises, at its center, a spherical bearing whose circular meridian section corresponds to an angle at the center greater than 180 ° while inside this spherical bearing is arranged a fixed spherical ball joint secured to an arm axially anchored in the center of the barrel, so that the thrust of the plate during operation is transmitted directly to the barrel via the spherical bearing working at tearing, and this without involving the resistance of the walls of the casing, in particular in its rear part.
Une machine similaire a été divulguée par FR-A 2 251 220. En pratique, on constate que cette technique connue présente encore des inconvénients. 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 augmen-ter le poids et l'encombrement de l'ensemble qui devient alors intransportable par camion.A similar machine has been disclosed by FR-A 2 251 220. In practice, it is found that this known technique still has drawbacks. 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.
Par ailleurs, FR-A 2 211 090 a fait connaître un mécanisme à barillet comprenant, à l'intérieur d'un carter, un arbre moteur entraîné en rotation autour de son axe, tourillonnant dans deux paliers supportés respectivement par deux fonds du carter perpendiculaires à l'axe, et sur lequel est fixé un plateau oblique par rapport à l'axe, un barillet s'appuyant sur le plateau oblique et centré, autour d'un axe coupant l'axe de tourillonnement, sur une portée cylindrique inclinée ménagée sur l'arbre, perpendiculairement au plateau, et un moyen de blocage en rotation du barillet, caractérisé par le fait que les deux fonds du carter sont reliés par un tirant s'étendant le long de l'axe de tourillonnement, dans un alésage axial de l'arbre moteur.Furthermore, FR-A 2 211 090 has made known a barrel mechanism comprising, inside a casing, a motor shaft driven in rotation about its axis, journalling in two bearings supported respectively by two perpendicular casing bottoms to the axis, and on which is fixed an oblique plate with respect to the axis, a barrel resting on the oblique plate and centered, around an axis intersecting the journal axis, on a cylindrical inclined bearing provided on the shaft, perpendicular to the plate, and a means for blocking the rotation of the barrel, characterized in that the two bases of the casing are connected by a tie rod extending along the axis of the journal, in an axial bore of the motor shaft.
Dans cette réalisation, il n'est cependant pas possible d'obtenir les avantages du FR-A 2 251 220.In this embodiment, it is however not possible to obtain the advantages of FR-A 2 251 220.
Il en est de même de la réalisation suivant US-A 3 223 042 qui montre un axe logé dans la partie avant et arrière du carter et sur lequel est montée une rotule. En effet, dans cette publication, la rotule est coulissante.It is the same for the embodiment according to US-A 3,223,042 which shows an axis housed in the front and rear part of the casing and on which a ball joint is mounted. Indeed, in this publication, the ball joint is sliding.
La nouvelle disposition selon l'invention supprime la position en porte à faux de la rotule centrale, ce qui empêche la rupture de l'arbre de support de cette rotule, rupture pouvant être causée par l'influence de la fatigue due aux fortes charges tournantes.The new arrangement according to the invention eliminates the cantilevered position of the central ball joint, which prevents the rupture of the support shaft of this ball joint, a rupture which can be caused by the influence of fatigue due to high rotating loads. .
Conformément à l'invention, la machine rotative à pistons et à barillet comprenant un plateau de poussée incliné par rapport à son axe géométrique de rotation qui coïncide avec l'axe géométrique du barillet, la partie centrale du plateau incliné comportant un palier sphérique qui tourne librement autour d'une rotule centrale fixe solidaire d'un premier demi-arbre ancré directement dans la partie centrale du barillet, alors que celui-ci est relié à un carter périphérique rigide qui coiffe l'arrière de l'embiellage derrière lequel il se referme, est caractérisée en ce que la rotule centrale est par ailleurs solidaire d'un second demi-arbre rigide situé à l'opposé du premier avec lequel il est aligné sur l'axe, ce second demi-arbre étant, par son extrémité opposée, rigidement ancré sur la partie arrière du carter de la machine.According to the invention, the rotary piston and barrel machine comprising a thrust plate inclined with respect to its geometric axis of rotation which coincides with the geometric axis of the barrel, the central part of the inclined plate comprising a spherical bearing which rotates freely around a fixed central ball joint integral with a first half-shaft anchored directly in the central part of the barrel, while the latter is connected to a rigid peripheral casing which covers the rear of the crankshaft behind which it closes, is characterized in that the central ball joint is also integral with a second rigid half-shaft situated opposite the first with which it is aligned on the axis, this second half-shaft being, by its opposite end , rigidly anchored on the rear part of the machine housing.
Le dessin annexé, donné à titre d'exemple non limitatif permettra de mieux comprendre les caractéristiques de l'invention.
- La fig. 1 est une coupe axiale d'une pompe hydraulique à barillet selon l'invention.
- La fig. 2 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 confère aux pistons la course maxima.
- La fig. 3 est une coupe analogue, les deux demi- plateaux étant assemblés, cette fois, à la position de course nulle.
- La fig. 4 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.
- Fig. 1 is an axial section of a hydraulic barrel pump according to the invention.
- Fig. 2 is a similar view, showing on a large scale, the detail of the connecting rod assembly, the two inclined half-plates of which are assembled in the position which gives the pistons the maximum stroke.
- Fig. 3 is a similar section, the two half-plates being assembled, this time in the zero stroke position.
- Fig. 4 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 61 dans les
alésages 62 duquel des crosses ou des pistons 64 coulissent suivant un mouvement alternatif; - - un plateau incliné 67 dont l'axe géométrique 82 forme un un angle aigu 83 avec l'axe géométrique 7 du bariiiet 61 ;
- - des
bielles 65 dont chacune possède deux extrémités sphériques 9 et 10 pour assurer la liaison entre chaque crosse ou piston 64 et le plateau à mouvement louvoyant 67; - - un pignon de commande 90 axé sur l'axe géométrique 7 autour duquel il tourne;
- - un engrenage latéral 91 qui engrène avec la de- riture du un pignon 90 et dont l'arbre 92 est entraîné par un motoréducteur non représenté.
- - A fixed barrel 61 in the
bores 62 of which sticks or pistons 64 slide in an alternating movement; - - an
inclined plate 67 whose geometric axis 82 forms an acute angle 83 with the geometric axis 7 of the bariiiet 61; - - connecting
rods 65, each of which has two spherical ends 9 and 10 for ensuring the connection between each stock or piston 64 and the plate withswaying movement 67; - - A control gear 90 centered on the geometric axis 7 around which it rotates;
- - A lateral gear 91 which meshes with the gear of a pinion 90 and the
shaft 92 of which is driven by a gearmotor not shown.
L'invention s'applique en particulier aux compresseurs, pompes ou moteurs hydrauliques à pistons axiaux pour des fluides chargés.The invention applies in particular to compressors, pumps or hydraulic motors with axial pistons for charged fluids.
Suivant la fig. 1, 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 centrées 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 autour de l'axe géométrique 7 de la machine.According to fig. 1, the
Aux fig. 1 à 4, on a représenté une machine tournante, par exemple une pompe, comportant un barillet fixe 61, dans lequel sont disposés des alésages 62 parallèles 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 et est engagé autour de la sphère d'une rotule fixe 70.In fig. 1 to 4, a rotary machine is shown, for example a pump, comprising a fixed barrel 61, in which are arranged
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
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-
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-
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'écrou 80, on puisse reprendre sur la face avant du barillet les efforts de traction auxquels le premier demi-arbre 71 sera, lui aussi, soumis.Similarly, there is provided on the first half-shaft 71, near the
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 aigu 83. Ces deux axes géométriques 7 et 82 convergent vers le centre 90 de la rotule sphérique 70. Le plateau 67 tourne autour 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
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
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'extérieur. 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
Enfin, une biellette latérale 96 est articulée par l'une de ses extrémités 97 (fig. 1) dans un palier 98, solidaire du plateau 67 qui est ainsi immobilisé en rotation.Finally, a
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.It is understood that the linkage thus represented, and in particular the structure of the
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 précharge viendra donc soulager l'autre partie des demi-coussinets 68 et 69, qui est située à droite du plan théorique 100 et reçoit des efforts de poussée exercés par les pistons 64. Ainsi, on garantit tout autour de la calotte sphérique des demicoussinets 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 central 68, 69. Si cette condition est réalisée on dira que la machine comporte en son centre une "butée flottante" étant donné qu'à cette position d'équilibre la butée sphérique (palier 68, 69 sur la rotule 70) est en charge axiale nulle.In particular, the
Dans la réalisation de la fig. 4, la précharge de compression axiale des butées 84, 86 s'effectue, non plus par l'intermédiaire de la cale d'épaisseur 87 et du chapeau 75 (fig. 1) 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 le 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 102, 105 corresponde à un point de serrage mécanique minimum permanent sur la rotule de la butée 86.In the embodiment of FIG. 4, the axial compression preload of the
Cette réalisation 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 de "butée flottante" pour la rotule 70;
- - soit tout rapport désiré entre les poussées exercées sur cette rotule 70 de part et d'autre du
plan théorique 100.
- - either the condition of "floating stop" for the
ball 70; - - or any desired ratio between the thrusts exerted on this
ball 70 on either side of thetheoretical plane 100.
Dans la vue partielle des fig. 2 et 3, le transmetteur de mouvement 85 de la fig. 1 est réalisé sous la forme de deux demi-transmetteurs 108 et 109, chacun à profil en coin. Autrement dit, la face d'appui plane 110 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, et qui correspond à l'axe 22. Des vis 114, régulièrement réparties en cercle autour de l'axe 111, permettent d'assembler les deux demi-transmetteurs 108 et 109.In the partial view of figs. 2 and 3, the
On comprend qu'en choisissant 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 64, pour toute valeur intermédiaire entre:
- - la course maxima correspondant à la position illustrée sur la fig. 2 (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); - - la position de course nulle, obtenue par décalage de 180° par rapport à la position de la fig. 2, de façon à orienter la
face avant 116 du plateau de poussée 4, perpendiculairement à l'axe géométrique longitudinal 7.
- - the maximum stroke corresponding to the position illustrated in fig. 2 (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); - - the zero stroke position, obtained by 180 ° offset from the position of fig. 2, so as to orient the
front face 116 of the thrust plate 4, perpendicular to the longitudinal geometric axis 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.In a more elaborate version, a continuous control device is used, with external control of the position of the two half-
Claims (10)
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 EP0225834A1 (en) | 1987-06-16 |
EP0225834B1 true 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) |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2619166B2 (en) * | 1985-10-14 | 1990-02-02 | Drevet Michel | ROTARY PISTON AND BARREL MACHINE WITH FIXED CENTERING BALL |
ATE58416T1 (en) * | 1987-08-06 | 1990-11-15 | Michel Drevet | ROTATING DRUM PISTON MACHINE WITH FIXED, CENTERING BELLY 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 |
WO1998051905A1 (en) * | 1997-05-14 | 1998-11-19 | Ahto Anttila | Axial piston engine |
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 |
Family Cites Families (23)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US27844A (en) * | 1860-04-10 | Bed-cord tightener | ||
US2022290A (en) * | 1935-11-26 | Tool holder | ||
US1331035A (en) * | 1918-04-01 | 1920-02-17 | Joseph C Soemer | Mechanical movement |
US2127773A (en) * | 1935-12-27 | 1938-08-23 | Foreign Rights Prec Meters Ltd | Liquid meter |
FR885831A (en) * | 1942-05-15 | 1943-09-27 | Control device for reciprocating piston pump or compressor | |
US2737894A (en) * | 1952-08-15 | 1956-03-13 | Oilgear Co | Axial type pump with stationary cylinders |
FR1104109A (en) * | 1954-04-28 | 1955-11-16 | Rech S Etudes | Further development of piston fluid pumps or motors |
US2955475A (en) * | 1957-01-10 | 1960-10-11 | Gen Motors Corp | Variable pressure fluid pump |
US2940325A (en) * | 1957-02-15 | 1960-06-14 | Nakesch Michael | Internal combustion engine with swash plate drive |
US3010339A (en) * | 1958-03-17 | 1961-11-28 | Densmore Richard M | Cam mechanical movement |
US3069913A (en) * | 1960-05-11 | 1962-12-25 | Battelle Development Corp | Crankless motion mechanism |
FR1295451A (en) * | 1961-04-25 | 1962-06-08 | Lubrication method for barrel mechanisms | |
FR1332574A (en) * | 1962-04-12 | 1963-07-19 | Barrel machine mechanism | |
FR1303796A (en) * | 1962-10-01 | 1962-09-14 | Adjustable variable flow piston rotary pump | |
US3223042A (en) * | 1963-06-14 | 1965-12-14 | Frank Wheatley Corp | Multi-piston variable stroke pump |
US3663122A (en) * | 1970-11-25 | 1972-05-16 | Mcneil Corp | Axial plunger pump |
FR2211090A5 (en) * | 1972-12-14 | 1974-07-12 | Creusot Loire | |
US3911791A (en) * | 1973-06-15 | 1975-10-14 | Robert Cecil Clerk | Swash-plate drive for axial piston pumps/motors |
FR2251220A5 (en) * | 1973-11-09 | 1975-06-06 | Girodin Marius | |
FR2271459B1 (en) * | 1973-11-09 | 1977-01-07 | ||
FR2510698A1 (en) * | 1981-07-30 | 1983-02-04 | Creusot Loire | MOVEMENT TRANSFORMATION MECHANISM |
FR2548284B1 (en) * | 1983-07-01 | 1987-10-23 | Creusot Loire | OBLIQUE PLATE MECHANISM FOR THE CONTROL OF A PUMP |
FR2572774B1 (en) * | 1984-11-06 | 1989-05-19 | Drevet Michel | BARREL PISTON PUMP, ESPECIALLY FOR HIGH PRESSURE FLUIDS |
-
1985
- 1985-10-14 FR FR8515604A patent/FR2588617B1/en not_active Expired
-
1986
- 1986-06-26 EP EP86420172A patent/EP0225834B1/en not_active Expired
- 1986-06-26 DE DE8686420172T patent/DE3665905D1/en not_active Expired
- 1986-10-10 DK DK486286A patent/DK165063C/en not_active IP Right Cessation
- 1986-10-11 SU SU864028435A patent/SU1514246A3/en active
- 1986-10-13 NO NO864069A patent/NO165508C/en unknown
- 1986-10-14 US US06/918,466 patent/US4815327A/en not_active Expired - Lifetime
- 1986-10-14 CA CA000520416A patent/CA1307163C/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
DE3665905D1 (en) | 1989-11-02 |
FR2588617A1 (en) | 1987-04-17 |
EP0225834A1 (en) | 1987-06-16 |
DK486286D0 (en) | 1986-10-10 |
FR2588617B1 (en) | 1989-11-24 |
DK165063B (en) | 1992-10-05 |
CA1307163C (en) | 1992-09-08 |
NO165508B (en) | 1990-11-12 |
NO165508C (en) | 1991-02-20 |
SU1514246A3 (en) | 1989-10-07 |
DK486286A (en) | 1987-04-15 |
US4815327A (en) | 1989-03-28 |
DK165063C (en) | 1993-02-15 |
NO864069L (en) | 1987-04-15 |
NO864069D0 (en) | 1986-10-13 |
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