EP0526333B1 - Pressurised fluid mechanism with equalizing enclosures - Google Patents

Description

The invention has its origin in the design of a new hydraulic motor, but more generally of a new pressurized fluid mechanism, such as a hydraulic motor or pump, comprising: a reaction cam; a cylinder block mounted for rotation relative to said reaction cam about an axis of rotation and provided with a planar communication face, perpendicular to said axis of rotation; a plurality of cylinders formed in the cylinder block; a plurality of pistons mounted sliding in said cylinders, at least by a cylinder delimiting inside the cylinder a working chamber of the fluid, which communicates with said communication face by a cylinder duct; at least two main fluid enclosures capable of containing a fluid for supplying the working chambers and an exhaust fluid outside said working chambers; an internal fluid distributor stationary with respect to rotation about said axis of rotation relative to said reaction cam and comprising a distribution face, which is planar, perpendicular to said axis of rotation, and capable of being supported substantially sealed on said communication face, and into which there are distribution conduits capable of being connected, one to one of said main enclosures, the other to the other main enclosure; and balancing chambers of the internal fluid distributor each communicating with some of said distribution conduits. This part of the new mechanism is already known from EP-A-0 223 656 and from FR-A-2 606 092.

More particularly, the invention was originally intended to design a mechanism which could furthermore have two corresponding distinct operating modes, one for the periodic supply of pressurized fluid to all the working chambers. in fluid and the other operating mode, when supplying only the fluid working chambers belonging to a first group of working chambers, the other fluid working chambers no longer being supplied with fluid under pressure: it it was therefore a mechanism having at least two separate displacement. To make such a mechanism, according to a known technique, it was necessary to provide at least three, and sometimes four separate main enclosures, and it was necessary to balance the pressure forces tending to separate the distribution face of the internal fluid distributor d 'with the communication face of the cylinder block, enclosure by enclosure. These enclosures, at least three in number, succeeded one another axially at the periphery of the internal distributor of fluid, separated from each other by a seal, so that the axial length of the internal fluid distributor had a relatively large value, which it was considered desirable to reduce. One proposed solution has consisted in replacing at least one, sometimes two main enclosures by one or two secondary enclosures placed not at the periphery, but inside the internal fluid distributor, which, for a mechanism comprising four enclosures, corresponds an axial size corresponding to the axial succession of only two main speakers.

In this new scheme, if the pressure forces corresponding to the fluid contained in the distribution conduits communicating with two said main enclosures could be balanced, in a manner known per se, by a judicious choice of the shapes of the walls delimiting these main enclosures, it has It has been noted that the pressure forces relative to the fluid contained in the distribution conduits communicating with the one or two internal secondary enclosures could not be balanced by the choice of the shapes of the walls delimiting this or these internal secondary enclosures, which in fact consist by at least some of the distribution pipes themselves.

The invention, which therefore had the primary aim of solving this problem of balancing the pressure forces of the fluid contained in the internal secondary enclosure (s) of such a mechanism comprising two separate operating displacements, has however a greater scope and is not limited to the production only of such multi-displacement operating mechanisms. This invention is indeed also interesting in the case of a mechanism with a single displacement. Because if, in the first case of the two-displacement operating mechanism, the axial length of the internal distributor can be significantly reduced, which improves the mobility of this internal distributor which is less constrained by the various radial bearing surfaces delimiting the main speakers , and which essentially improves the tightness of the contact between the dispensing face and the communication face of this mechanism, it has also been designed from a structure integral with the cam identical to that of the mechanism at least two operating displacements, to provide a mechanism having only one operating displacement. However, this structure integral with the cam is an important and expensive part of the mechanism, and it is obviously advantageous that it can be common to the mechanisms of a production range comprising both mechanisms with several operating displacements and mechanisms with a single operating displacement. And indeed, by adopting a structure integral with the single cam, the pressure forces have been balanced both with regard to the multi-displacement operating mechanisms, as with regard to the mechanisms having only one displacement Operating.

The scope of the invention is therefore not limited to only mechanisms having two operating displacements.

According to the invention, in a mechanism as previously defined, opposite said distribution face, the internal fluid distributor is delimited by an extreme transverse face which is arranged opposite a reaction face belonging to the one of the two parts constituted by the cylinder block and by a structure integral with the reaction cam, while at least one of said balancing chambers is constituted by a chamber formed in the internal fluid distributor and opening into its so-called extreme transverse face and by a sealing device, which is partially received inside this chamber and which takes reaction support on said reaction face.

• ladite enceinte d'équilibrage comprend une gorge annulaire, à parois cylindriques d'axes parallèles audit axe de rotation;
• la chambre de ladite enceinte d'équilibrage est borgne et est reliée en dérivation avec certains desdits conduits de distribution, communiquant seulement avec ceux-ci, sans être traversée par le débit du fluide susceptible d'être véhiculé par lesdits conduits de distribution;
• ladite face de réaction est plane et perpendiculaire audit axe de rotation;
• la partie de ladite face transversale extrême, dans laquelle débouche ladite enceinte d'équilibrage, est plane et perpendiculaire audit axe de rotation;
• le mécanisme comporte des conduits de distribution qui sont ménagés dans le distributeur interne de fluide, qui sont répartis en un premier et un deuxième groupes de paires de conduits de distribution, comprenant chaque paire un premier et un deuxième conduit de distribution, cependant que les formes des parois délimitant les enceintes principales réalisent en outre les équilibrages des forces de pression des fluides contenus dans les premiers et deuxièmes conduits de distribution du premier groupe de paires de conduits de distribution, respectivement, lesdites deux enceintes principales, constituant alors également deux premières enceintes d'équilibrage; et, au moins une deuxième enceinte d'équilibrage, qui est constituée par l'une desdites chambres ménagées dans le distributeur interne de fluide et débouchant dans sa face transversale extrême et par l'un desdits dispositifs d'étanchéité reçu partiellement dans ladite chambre, et qui est reliée par au moins un conduit ménagé dans le distributeur interne de fluide à l'un des deux ensembles de conduits de distribution comprenant, un premier ensemble, les premiers conduits de distribution du deuxième groupe de paires de conduits de distribution, et un deuxième ensemble, les deuxièmes conduits de distribution dudit deuxième groupe de paires de conduits de distribution;
• selon une première variante de réalisation, le mécanisme est du type comportant au moins une grande et au moins une petite cylindrées de fonctionnement et comporte les deux dites enceintes principales qui sont susceptibles de contenir, l'une le fluide d'alimentation, l'autre le fluide d'échappement, lorsque le mécanisme fonctionne avec chacune des deux dites cylindrées de fonctionnement, les formes des parois délimitant lesdites enceintes principales réalisant en outre l'équilibrage des forces de pression du fluide contenu dans des conduits de distribution qui communiquent en permanence avec ces enceintes principales; et, deux enceintes secondaires qui, lorsque le mécanisme fonctionne avec ladite grande cylindrée de fonctionnement, contiennent, l'une le fluide d'alimentation, l'autre le fluide d'échappement, et, lorsque le mécanisme fonctionne avec ladite petite cylindrée de fonctionnement, communiquent l'une avec l'autre; cependant que les deux dites enceintes secondaires sont associées à deux dites deuxièmes enceintes d'équilibrage, respectivement, chacune étant reliée par au moins un conduit interne ménagé dans le distributeur interne de fluide à l'une desdites enceintes secondaires;
• selon une deuxième variante de réalisation, le mécanisme est du type comportant au moins une grande et au moins une petite cylindrée de fonctionnement et comporte les deux dites enceintes principales qui sont susceptibles de contenir, l'une le fluide d'alimentation, l'autre le fluide d'échappement, lorsque le mécanisme fonctionne avec chacune des deux dites cylindrées de fonctionnement, les formes des parois délimitant lesdites enceintes principales réalisant en outre l'équilibrage des forces de pression du fluide contenu dans des conduits de distribution qui communiquent en permanence avec ces enceintes principales; et, une enceinte secondaire unique qui, lorsque le mécanisme fonctionne avec ladite grande cylindrée de fonctionnement, contient l'un des fluides d'alimentation et d'échappement, et, lorsque le mécanisme fonctionne avec ladite petite cylindrée de fonctionnement, contient l'autre desdits fluides; cependant que ladite enceinte secondaire unique est associée à une dite deuxième enceinte unique d'équilibrage reliée par au moins un conduit interne ménagé dans le distributeur interne de fluide à ladite enceinte secondaire unique;
• selon une troisième variante de réalisation, le mécanisme est du type à une cylindrée unique de fonctionnement et comporte les deux enceintes principales susceptibles de contenir, l'une le fluide d'alimentation, l'autre le fluide d'échappement; et deux dites deuxièmes enceintes d'équilibrage, qui sont reliées, par lesdits conduits internes ménagés dans le distributeur interne de fluide, l'une de ces deuxièmes enceintes d'équilibrage étant reliée aux premiers conduits de distribution du deuxième groupe de paires de conduits de distribution, l'autre des deux dites deuxièmes enceintes d'équilibrage étant reliée aux deuxièmes conduits de distribution dudit deuxième groupe de paires de conduits de distribution.

The following advantageous arrangements are also preferably adopted:

• said balancing enclosure comprises an annular groove, with cylindrical walls of axes parallel to said axis of rotation;
• the chamber of said balancing enclosure is blind and is connected in bypass with some of said distribution conduits, communicating only with them, without being traversed by the flow of fluid capable of being conveyed by said distribution conduits;
• said reaction face is plane and perpendicular to said axis of rotation;
• the part of said extreme transverse face, into which opens said balancing enclosure, is plane and perpendicular to said axis of rotation;
• the mechanism comprises distribution conduits which are formed in the internal fluid distributor, which are distributed in a first and a second group of pairs of distribution conduits, each comprising a first and a second distribution conduit, while the forms walls delimiting the main enclosures also balance the pressure forces of the fluids contained in the first and second distribution conduits of the first group of pairs of distribution conduits, respectively, said two main chambers, then also constituting two first balancing chambers; and, at least one second balancing enclosure, which is constituted by one of said chambers formed in the internal fluid distributor and opening out in its extreme transverse face and by one of said sealing devices partially received in said chamber, and which is connected by at least one conduit formed in the internal fluid distributor to one of the two sets of distribution conduits comprising, a first set, the first distribution conduits of the second group of pairs of distribution conduits, and a second set, the second distribution conduits of said second group of pairs of distribution conduits;
• according to a first alternative embodiment, the mechanism is of the type comprising at least one large and at least one small operating displacement and comprises the two said main enclosures which are capable of containing, one the supply fluid, the other the exhaust fluid, when the mechanism operates with each of said two operating displacements, the shapes of the walls delimiting said main enclosures further achieving the balancing of the pressure forces of the fluid contained in distribution conduits which communicate permanently with these main speakers; and, two secondary enclosures which, when the mechanism operates with said large operating displacement, contain, one the supply fluid, the other the exhaust fluid, and, when the mechanism operates with said small operating displacement , communicate with each other; however, that the two said secondary enclosures are associated with two said second balancing enclosures, respectively, each being connected by at least one internal conduit formed in the internal fluid distributor to one of said secondary enclosures;
• according to a second variant embodiment, the mechanism is of the type comprising at least one large and at least one small operating displacement and comprises the two said main enclosures which are capable of containing, one the supply fluid, the other the exhaust fluid, when the mechanism operates with each of said two operating displacements, the shapes of the walls delimiting said main enclosures further achieving the balancing of pressure forces of the fluid contained in distribution conduits which communicate permanently with these main enclosures; and, a single secondary enclosure which, when the mechanism operates with said large operating displacement, contains one of the supply and exhaust fluids, and, when the mechanism operates with said small operating displacement, contains the other said fluids; however, said single secondary enclosure is associated with a said second single balancing enclosure connected by at least one internal conduit formed in the internal fluid distributor to said single secondary enclosure;
• according to a third alternative embodiment, the mechanism is of the type with a single cubic capacity of operation and comprises the two main chambers capable of containing, one the supply fluid, the other the exhaust fluid; and two said second balancing chambers, which are connected by said internal conduits formed in the internal fluid distributor, one of these second balancing chambers being connected to the first distribution conduits of the second group of pairs of conduits distribution, the other of the two said second balancing enclosures being connected to the second distribution conduits of said second group of pairs of distribution conduits.

The main advantages of the invention reside, on the one hand, in the production of pressurized fluid mechanisms having at least two separate operating displacements and comprising an internal fluid distributor axially less bulky than the known prior mechanisms, and consequently better likely to allow the achievement of a good seal between the distribution face and the communication face of the cylinder block, and therefore better able to reduce the leakage of fluid between these two faces in mutual contact, on the other hand, in the possibility of carrying out a production range comprising both mechanisms having several operating displacements and mechanisms having only one operating cubic capacity, by adopting a single model of the most bulky and ultimately the most expensive part , which remains unchanged for these two types of mechanisms.

The invention will be better understood, and secondary characteristics and their advantages will become apparent during the description of embodiments given below by way of example.

It is understood that the description and the drawings are given for information only and are not limiting.

• la figure 1 est une coupe axiale d'un moteur hydraulique selon une première réalisation conforme à l'invention, représenté dans une première configuration de fonctionnement;
• la figure 2 est un agrandissement de la partie de la figure 1 représentant le distributeur interne du fluide du moteur hydraulique;
• les figures 3 et 4 sont des coupes transversales, respectivement suivant III-III et IV-IV, du moteur illustré par la figure 2;
• la figure 5 est un agrandissement des parties des figures 1 et 2 illustrant plus particulièrement la disposition propre à l'invention;
• la figure 6 est une coupe axiale, analogue à celle de la figure 2, mais correspondant à une deuxième configuration de fonctionnement du moteur hydraulique;
• les figures 7 et 8 sont des coupes transversales, respectivement suivant VII-VII et VIII-VIII, du moteur illustré par la figure 6;
• la figure 9 représente le circuit de commande du moteur hydraulique des figures 1 à 8;
• la figure 10 est une coupe axiale, analogue à celle de la figure 2, d'un moteur hydraulique selon une deuxième réalisation conforme à l'invention, représenté dans une première configuration de fonctionnement;
• les figures 11 et 12 sont des coupes, respectivement suivant XI-XI et XII-XII, du moteur illustré par la figure 10;
• la figure 13 est une coupe axiale du moteur de la figure 10, représenté dans une deuxième configuration de fonctionnement;
• les figures 14 et 15 sont des coupes, respectivement suivant XIV-XIV et XV-XV, du moteur illustré par la figure 13;
• la figure 16 est une coupe axiale, analogue à celle de la figure 2, d'un moteur hydraulique selon une troisième réalisation conforme à l'invention, selon XVI-XVI de la figure 17; et,
• les figures 17 et 18 sont des coupes transversales, respectivement suivant XVII-XVII et XVIII-XVIII, du moteur illustré par la figure 16.

Reference will be made to the appended drawings in which:

• Figure 1 is an axial section of a hydraulic motor according to a first embodiment according to the invention, shown in a first operating configuration;
• Figure 2 is an enlargement of the part of Figure 1 showing the internal distributor of the hydraulic motor fluid;
• Figures 3 and 4 are cross sections, respectively along III-III and IV-IV, of the engine illustrated in Figure 2;
• Figure 5 is an enlargement of the parts of Figures 1 and 2 illustrating more particularly the arrangement specific to the invention;
• Figure 6 is an axial section, similar to that of Figure 2, but corresponding to a second operating configuration of the hydraulic motor;
• Figures 7 and 8 are cross sections, respectively along VII-VII and VIII-VIII, of the engine illustrated in Figure 6;
• FIG. 9 represents the control circuit of the hydraulic motor of FIGS. 1 to 8;
• Figure 10 is an axial section, similar to that of Figure 2, of a hydraulic motor according to a second embodiment according to the invention, shown in a first operating configuration;
• Figures 11 and 12 are sections, respectively along XI-XI and XII-XII, of the engine illustrated in Figure 10;
• Figure 13 is an axial section of the motor of Figure 10, shown in a second operating configuration;
• Figures 14 and 15 are sections, respectively along XIV-XIV and XV-XV, of the engine illustrated in Figure 13;
• Figure 16 is an axial section, similar to that of Figure 2, of a hydraulic motor according to a third embodiment according to the invention, according to XVI-XVI of Figure 17; and,
• FIGS. 17 and 18 are cross-sections, respectively along XVII-XVII and XVIII-XVIII, of the engine illustrated in FIG. 16.

• un carter en trois parties 1A, 1B et 1C assemblées par des vis 2;
• un arbre moteur 3 monté à rotation par rapport au carter 1A-1B-1C, autour d'un axe de rotation 4, au moyen de paliers à rouleaux 5, arbre moteur dont une extrémité est contenue à l'intérieur du carter et comporte des cannelures 6;
• un bloc-cylindres 7 représentant un alésage central muni de cannelures 8, qui coopèrent avec les cannelures 6 pour rendre solidaire ledit bloc cylindres 7 de l'arbre moteur 3 vis-à-vis de la rotation d'axe de rotation 4, ce bloc cylindres comportant une face plane de communication 9, perpendiculaire à l'axe de rotation 4;
• une pluralité de cylindres 10 ménagés dans le bloc-cylindres 7, disposés radialement par rapport à l'axe de rotation 4 et angulairement régulièrement espacés;
• une pluralité de pistons 11, reçus dans les cylindres 10, un par cylindre, monté coulissant à l'intérieur du cylindre 10 et définissant à l'intérieur de ce cylindre une chambre de travail du fluide 12 qui communique avec la face de communication 9 par un conduit de cylindre 13;
• des rouleaux 14 montés, chacun, à l'extémité externe d'un piston 11, à rotation par rapport audit piston autour d'un axe 15 parallèle à l'axe de rotation 4, et en appui sur la face interne de la partie intermédiaire 1B du carter, qui constitue une came ondulée de réaction 16;
• un conduit 17, ménagé dans la partie 1C du carter, relie l'enceinte 18 délimitée par ledit carter à un conduit externe 19;
• ladite partie 1C du carter comprend un évidement central de révolution 20 d'axe de révolution confondu avec l'axe de rotation 4;
• un distributeur interne de fluide 21, dont une face périphérique axiale 22 possède une forme sensiblement complémentaire de celle de l'évidement 20 et dont une face plane de distribution 23, perpendiculaire à l'axe de rotation 4, est en appui sensiblement étanche sur la face de communication 9, un dispositif d'encoches et d'ergots associés 24 rendant solidaire, vis-à-vis de la rotation d'axe de rotation 4, le distributeur interne de fluide 21 de la partie 1C du carter;
• deux enceintes principales 25, 26 sont ménagées entre le distributeur interne de fluide 21 et l'évidement 20, et communiquent avec des conduits externes 27, 28 par l'intermédiaire de conduits 29, 30 ménagés dans la partie 1C du carter, respectivement;
• un premier groupe de conduits de distribution 31, 32 correspondant, par paires de conduits 31-32, aux ondulations d'un premier groupe d'ondulations de la came de réaction 16, communiquent en permanence, les conduits de distribution 31 avec l'enceinte principale 25, et, les conduits de distribution 32 avec l'enceinte principale 26, et débouchent dans la face de distribution 23 de manière, au cours de la rotation relative du bloc cylindres 7 par rapport au carter 1A-1B-1C, et par suite par rapport au distributeur interne de fluide 21, à communiquer périodiquement avec les conduits de cylindre 13;
• des conduits de liaison 33, 34 relient au moins l'un des conduits de distribution 31, 32, et par leur intermédiaire les enceintes principales 25, 26 à un alésage 35 ménagé dans le distributeur interne de fluide 21, dans lequel lesdits conduits de liaison débouchent, les conduits de liaison 33 entre deux plans transversaux P1, P2, perpendiculaires à l'axe 4, et, les conduits de liaison 34 entre deux plans transversaux R1, R2 perpendiculaires à l'axe 4;
• un deuxième groupe de conduits de distribution 36, 37 correspondant, par paire de conduits de distribution 36-37, aux ondulations d'un deuxième groupe d'ondulations de la came de réaction 16, communiquent, les conduits de distribution 36 avec l'alésage 35 en y débouchant entre les plans transversaux P1, P2, et, les conduits de distribution 37 avec l'alésage 35 en y débouchant entre les plans transversaux R1, R2, lesdits conduits de distribution 36, 37 débouchant en outre dans la face de distribution 23 de manière, au cours de la rotation relative du bloc-cylindres 7 par rapport au carter 1A-1B-1C, à communiquer périodiquement avec les conduits de cylindre 13; ces conduits 36, 37 constituent, respectivement, deux enceintes secondaires;
• un tiroir 38, monté coulissant, avec étanchéité, à l'intérieur de l'alésage 35, comporte: deux gorges 39, 40 axialement espacées ; des conduits axiaux borgnes 41 et 42, qui s'étendent de part et d'autre de la gorge 40 et communiquent en permanence avec elle et avec l'alésage 35; et un logement 43, axial, de réception à libre coulissement d'un pion 44 d'indexation en rotation par rapport à la partie 1C du carter, fixé sur la partie 1C du carter;
• des joints d'étanchéité 45, 46, 47 et 48, qui sont interposés entre le distributeur interne de fluide 21 et la partie 1C du carter et qui, isolent chaque enceinte principale 25, 26 de l'autre enceinte et de l'intérieur du carter (joints 45, 46, 47) et isolent une chambre de pilotage 49, ménagée dans la partie 1C du carter entre celui-ci, l'extrémité du distributeur interne de fluide opposé à la face de distribution 23, et une extrémité 38A du tiroir 38;
• un conduit 50, ménagé dans le distributeur interne de fluide 21, débouche d'une part dans l'alésage 35, d'autre part dans la chambre 49;
• une butée interne de réaction 53, fixée sur la partie centrale du distributeur interne de fluide 21 par un segment 54 reçu dans une gorge 55 dudit distributeur interne de fluide, assure le maintien d'un ressort 56, qui est interposé entre elle-même et le tiroir 38 et dont l'effet, antagoniste de celui de la pression du fluide contenu dans la chambre 49, tend à placer le tiroir 38 dans une première position (figures 1 à 5) dans laquelle les conduits 33 et 36 communiquent avec la gorge 39, les conduits 34 et 37 communiquent avec la gorge 40, les conduits 41, 42 ne communiquent qu'avec la gorge 40, et le conduit 50 est obturé par le tiroir 38;
• un conduit externe 51 est raccordé à la chambre 49 et est susceptible de véhiculer un fluide sous pression apte à placer le tiroir 38 dans une deuxième position (figure 6), dans laquelle, d'une part, la gorge 40, obturée par l'alésage 35, communique cependant avec les conduits 36 et 37 par l'intermédiaire des conduits borgnes 41, 42, d'autre part, le conduit 50 débouche en regard de cette gorge 40;
• une chambre 52 est délimitée entre le distributeur interne de fluide 21, et la partie 1C du carter, entre les joints d'étanchéité 47 et 48, et communique en permanence avec le conduit 17 par l'intermédiaire d'un conduit 57, également ménagé dans la partie 1C du carter;
• un ressort 58 est interposé entre le distributeur interne de fluide 21 et la partie 1C du carter, et tend à mettre la face de distribution 23 en appui sensiblement étanche sur la face de communication 9 du bloc-cylindres 7;
• un segment 59, reçu dans une gorge 60 ménagée dans l'alésage 35 du distributeur interne 21, constitue une butée de limitation du coulissement du tiroir 38, qui, lorsqu'il est en appui sur ce segment 59, est disposé dans sa première position;
• deux gorges 61, 62, de révolution, d'axe de révolution confondu avec l'axe géométrique 4, débouchent dans la face arrière plane 21A, perpendiculaire à l'axe géométrique 4, du distributeur de fluide 21 et sont délimitées par des parois axiales cylindriques;
• la gorge 61 reçoit un joint d'étanchéité 63, qui délimite avec le fond de cette gorge une chambre 64 communiquant, par au moins un conduit 65, ménagé dans le distributeur interne de fluide 21, avec les conduits 37, un segment 66 étant introduit dans la gorge 61, à la suite du joint d'étanchéité 63, et prenant appui sur une face interne 67, plane et perpendiculaire à l'axe géométrique 4, de la partie 1C du carter;
• la gorge 62 reçoit un joint d'étanchéité 71, qui délimite avec le fond de cette gorge une chambre 68 communiquant, par au moins un conduit 69, ménagé dans le distributeur interne de fluide 21, avec les conduits 36, un segment 70 étant introduit dans la gorge 62, à la suite du joint d'étanchéité 71, et prenant appui sur la face 67 de la partie 1C du cater.

The hydraulic motor shown in FIGS. 1 to 9 is an engine with two distinct displacement displacements, and with so-called "symmetrical" distribution.

• a casing in three parts 1A, 1B and 1C assembled by screws 2;
• a motor shaft 3 rotatably mounted relative to the casing 1A-1B-1C, around an axis of rotation 4, by means of roller bearings 5, a drive shaft of which one end is contained inside the casing and comprises grooves 6;
• a cylinder block 7 representing a central bore provided with grooves 8, which cooperate with the grooves 6 to make integral said cylinder block 7 of the motor shaft 3 with respect to the rotation of the axis of rotation 4, this block cylinders comprising a flat communication face 9, perpendicular to the axis of rotation 4;
• a plurality of cylinders 10 formed in the cylinder block 7, arranged radially with respect to the axis of rotation 4 and angularly regularly spaced;
• a plurality of pistons 11, received in the cylinders 10, one per cylinder, mounted sliding inside the cylinder 10 and defining inside this cylinder a working chamber of the fluid 12 which communicates with the communication face 9 by a cylinder duct 13;
• rollers 14 mounted, each at the outer end of a piston 11, rotating relative to said piston about an axis 15 parallel to the axis of rotation 4, and bearing on the internal face of the intermediate part 1B of the housing, which constitutes a corrugated reaction cam 16;
• a conduit 17, formed in part 1C of the housing, connects the enclosure 18 delimited by said housing to an external conduit 19;
• said part 1C of the casing comprises a central recess of revolution 20 of axis of revolution coincident with the axis of rotation 4;
• an internal fluid distributor 21, of which an axial peripheral face 22 has a shape substantially complementary to that of the recess 20 and of which a flat distribution face 23, perpendicular to the axis of rotation 4, is in substantially sealed abutment on the communication face 9, a device of associated notches and lugs 24 making them integral with respect to the rotation axis of rotation 4, the internal fluid distributor 21 of part 1C of the casing;
• two main enclosures 25, 26 are formed between the internal fluid distributor 21 and the recess 20, and communicate with external conduits 27, 28 by means of conduits 29, 30 formed in part 1C of the casing, respectively;
• a first group of distribution conduits 31, 32 corresponding, by pairs of conduits 31-32, to the undulations of a first group of undulations of the reaction cam 16, permanently communicate, the distribution conduits 31 with the enclosure main 25, and, the distribution conduits 32 with the main enclosure 26, and open into the distribution face 23 so, during the relative rotation of the cylinder block 7 relative to the casing 1A-1B-1C, and by following with respect to the internal fluid distributor 21, to communicate periodically with the cylinder conduits 13;
• connecting conduits 33, 34 connect at least one of the distribution conduits 31, 32, and through them the main enclosures 25, 26 to a bore 35 formed in the internal fluid distributor 21, in which said connecting conduits open, the connecting conduits 33 between two transverse planes P1, P2, perpendicular to the axis 4, and, the connecting conduits 34 between two transverse planes R1, R2 perpendicular to the axis 4;
• a second group of distribution conduits 36, 37 corresponding, by pair of distribution conduits 36-37, to the undulations of a second group of undulations of the reaction cam 16, communicate, the distribution conduits 36 with the bore 35 by opening there between the transverse planes P1, P2, and, the distribution conduits 37 with the bore 35 by opening there between the transverse planes R1, R2, said distribution conduits 36, 37 further opening into the distribution face 23 so as, during the relative rotation of the cylinder block 7 with respect to the casing 1A-1B-1C, to communicate periodically with the cylinder ducts 13; these conduits 36, 37 constitute, respectively, two secondary enclosures;
• a drawer 38, slidably mounted, with sealing, inside the bore 35, comprises: two grooves 39, 40 axially spaced; blind axial ducts 41 and 42, which extend on either side of the groove 40 and communicate permanently with it and with the bore 35; and a housing 43, axial, for free sliding reception of a pin 44 for indexing in rotation relative to part 1C of the casing, fixed to part 1C of the casing;
• seals 45, 46, 47 and 48, which are interposed between the internal fluid distributor 21 and the part 1C of the casing and which isolate each main enclosure 25, 26 from the other enclosure and from inside the casing (seals 45, 46, 47) and isolate a pilot chamber 49, formed in part 1C of the casing between the latter, the end of the internal fluid distributor opposite to the distribution face 23, and one end 38A of the drawer 38;
• a conduit 50, formed in the internal fluid distributor 21, opens on the one hand into the bore 35, on the other hand into the chamber 49;
• an internal reaction stop 53, fixed on the central part of the internal fluid distributor 21 by a segment 54 received in a groove 55 of said internal fluid distributor, ensures the maintenance of a spring 56, which is interposed between itself and the drawer 38 and whose effect, antagonistic to that of the pressure of the fluid contained in the chamber 49, tends to place the drawer 38 in a first position (FIGS. 1 to 5) in which the conduits 33 and 36 communicate with the groove 39, the conduits 34 and 37 communicate with the groove 40, the conduits 41, 42 communicate only with the groove 40, and the conduit 50 is closed by the drawer 38;
• an external conduit 51 is connected to the chamber 49 and is capable of conveying a pressurized fluid capable of placing the drawer 38 in a second position (FIG. 6), in which, on the one hand, the groove 40, closed by the bore 35, however communicates with the conduits 36 and 37 via the blind conduits 41, 42, on the other hand, the conduit 50 opens facing this groove 40;
• a chamber 52 is delimited between the internal fluid distributor 21, and the part 1C of the casing, between the seals 47 and 48, and permanently communicates with the conduit 17 via a conduit 57, also provided in part 1C of the housing;
• a spring 58 is interposed between the internal fluid distributor 21 and the part 1C of the casing, and tends to put the distribution face 23 in substantially sealed abutment on the communication face 9 of the cylinder block 7;
• a segment 59, received in a groove 60 formed in the bore 35 of the internal distributor 21, constitutes a stop for limiting the sliding of the drawer 38, which, when it is supported on this segment 59, is disposed in its first position ;
• two grooves 61, 62, of revolution, of axis of revolution coinciding with the geometric axis 4, open into the flat rear face 21A, perpendicular to the geometric axis 4, of the fluid distributor 21 and are delimited by axial walls cylindrical;
• the groove 61 receives a seal 63, which delimits with the bottom of this groove a chamber 64 communicating, through at least one conduit 65, formed in the internal fluid distributor 21, with the conduits 37, a segment 66 being introduced in the groove 61, following the seal 63, and bearing on an internal face 67, flat and perpendicular to the geometric axis 4, of the part 1C of the casing;
• the groove 62 receives a seal 71, which delimits with the bottom of this groove a chamber 68 communicating, through at least one conduit 69, formed in the internal fluid distributor 21, with the conduits 36, a segment 70 being introduced in the groove 62, following the seal 71, and bearing on the face 67 of the part 1C of the cater.

It should be noted that the constitution of the engine represented in FIGS. 1 to 9 corresponds, for example, to the fixing of the casing 1A-1B-1C on a vehicle chassis, and to the rotation of the cylinder block 7 and of the motor shaft 3, which is integral in rotation and which is coupled to a movement member of said vehicle for the purpose of driving the latter. There are other types of engines, in which the rotary member is constituted by the casing (and by the cam which is integral therewith in rotation), the fixed member then being the cylinder block. In such an engine, the end transverse face 21A of the internal distributor 21 is arranged opposite a transverse face, with which the cylinder block is provided, and which is similar to the face 67 of the engine which has just been described. In these two embodiments, the face 67 of the casing, like said face of the cylinder block constitute a reaction face allowing the support of the segments 66 and 70. The observation which has just been made, valid for the production of FIGS. 1 to 9, is also valid for that of FIGS. 10 to 15, and, for that of FIGS. 16 to 18.

• ledit moteur,
• un réservoir de fluide sans pression 72;
• une pompe principale 73;
• un distributeur principal de fluide 74, à trois positions;
• une pompe secondaire 75;
• un distributeur secondaire de fluide 76, à deux positions;
• deux clapets de décharge 77 et 78, de protection contre les suppressions; et les conduits suivants:
• le conduit d'aspiration 79 de la pompe principale 73, reliant celle-ci au réservoir 72;
• le conduit de refoulement 80 de la pompe principale 73, reliant celle-ci au distributeur principal de fluide 74;
• un conduit 81, qui relie le conduit de refoulement 80 au réservoir 72 et sur lequel est placé le clapet de décharge 77;
• un conduit 82 reliant le distributeur principal de fluide 74 au réservoir 72;
• le conduit d'aspiration 83 de la pompe secondaire 75, reliant celle-ci au réservoir 72;
• le conduit de refoulement 84 de la pompe secondaire 75, reliant celle-ci au distributeur secondaire de fluide 76;
• un conduit 85, qui relie le conduit de refoulement 84 au réservoir 72 et sur lequel est placé le clapet de décharge 78; et,
• un conduit 86 reliant le distributeur secondaire de fluide 76 au réservoir 72.

The hydraulic circuit of FIG. 9 fully incorporates the hydraulic motor which has just been described, in its configuration shown in FIGS. 1 to 5, and comprises:

• said motor,
• a pressureless fluid reservoir 72;
• a main pump 73;
• a main fluid distributor 74, with three positions;
• a secondary pump 75;
• a secondary fluid distributor 76, with two positions;
• two relief valves 77 and 78, for protection against deletion; and the following conduits:
• the suction duct 79 of the main pump 73, connecting the latter to the reservoir 72;
• the discharge pipe 80 of the main pump 73, connecting the latter to the main fluid distributor 74;
• a conduit 81, which connects the discharge conduit 80 to the reservoir 72 and on which the relief valve 77 is placed;
• a conduit 82 connecting the main fluid distributor 74 to the reservoir 72;
• the suction duct 83 of the secondary pump 75, connecting the latter to the reservoir 72;
• the discharge conduit 84 of the secondary pump 75, connecting the latter to the secondary fluid distributor 76;
• a conduit 85, which connects the discharge conduit 84 to the reservoir 72 and on which the relief valve 78 is placed; and,
• a conduit 86 connecting the secondary fluid distributor 76 to the reservoir 72.

Note the connection of conduits 27 and 28 to the main fluid distributor 74; the connection of the duct 51 to the secondary fluid distributor 76; and, the connection of the conduit 19 to the reservoir 72.

• la première position, à la communication des conduits 80 et 27, et, des conduits 28 et 82;
• la deuxième position, aux obturations des conduits 27, 28, 80 et 82; et,
• la troisième position, à la communication des conduits 80 et 28, et, des conduits 27 et 82.

The three positions of the main fluid distributor 74 correspond:

• the first position, at the communication of the conduits 80 and 27, and, of the conduits 28 and 82;
• the second position, to the obturations of the conduits 27, 28, 80 and 82; and,
• the third position, at the communication of the conduits 80 and 28, and, of the conduits 27 and 82.

• la première position, à la mise en communication des conduits 84, 51 et 86, et à la première configuration du moteur hydraulique et de son tiroir 38; et,
• la deuxième position, à la mise en communication des conduits 84 et 51, à l'obturation du conduit 86, et à la deuxième configuration du moteur hydraulique et de son tiroir 38.

The two positions of the secondary fluid distributor 76 correspond:

• the first position, when the conduits 84, 51 and 86 are put into communication, and when the hydraulic motor and its drawer 38 are first configured; and,
• the second position, when the conduits 84 and 51 are placed in communication, when the conduit 86 is closed, and at the second configuration of the hydraulic motor and of its drawer 38.

• un carter en trois parties 1A, 1B et 1C assemblées par des vis 2;
• un arbre moteur 3 monté à rotation par rapport au carter 1A-1B-1C, autour d'un axe de rotation 4, au moyen de paliers à rouleaux 5, arbre moteur dont une extrémité est contenue à l'intérieur du carter et comporte des cannelures 6;
• un bloc-cylindres 7 présentant un alésage central muni de cannelures 8, qui coopèrent avec les cannelures 6 pour rendre solidaire ledit bloc-cylindres 7 de l'arbre moteur 3 vis-à-vis de la rotation 4, ce bloc-cylindres comportant une face plane de communication 9, perpendiculaire à l'axe de rotation 4;
• une pluralité de cylindres 10 ménagés dans le bloc-cylindres 7, disposés radialement par rapport à l'axe de rotation 4 et angulairement régulièrement espacés ;
• une pluralité de pistons 11, reçus dans les cylindres 10, un par cylindre, monté coulissant à l'intérieur du cylindre 10 et définissant à l'intérieur de ce cylindre une chambre de travail du fluide 12 qui communique avec la face de communication 9 par un conduit de cylindres 13;
• des rouleaux 14 montés, chacun, à l'extrémité externe d'un piston 11, à rotation par rapport audit piston autour d'un axe 15 parallèle à l'axe de rotation 4, et en appui sur la face interne de la partie intermédiaire 1B du carter, qui constitue une came ondulée de réaction 16;
• un conduit 17, ménagé dans la partie 1C du carter, relie l'enceinte 18 délimitée par ledit carter à un conduit externe 19.

The hydraulic motor shown in FIGS. 10 to 15 is a motor with two separate displacement and with so-called "asymmetrical" distribution. This engine comprises, like the engine of FIG. 1 to which reference is made:

• a casing in three parts 1A, 1B and 1C assembled by screws 2;
• a motor shaft 3 rotatably mounted relative to the casing 1A-1B-1C, around an axis of rotation 4, by means of roller bearings 5, a drive shaft of which one end is contained inside the casing and comprises grooves 6;
• a cylinder block 7 having a central bore provided with grooves 8, which cooperate with the grooves 6 to make said cylinder block 7 integral with the motor shaft 3 with respect to rotation 4, this cylinder block comprising a flat communication face 9, perpendicular to the axis of rotation 4;
• a plurality of cylinders 10 formed in the cylinder block 7, arranged radially with respect to the axis of rotation 4 and angularly regularly spaced;
• a plurality of pistons 11, received in the cylinders 10, one per cylinder, mounted sliding inside the cylinder 10 and defining inside this cylinder a working chamber of the fluid 12 which communicates with the communication face 9 by a cylinder duct 13;
• rollers 14 mounted, each at the outer end of a piston 11, rotating relative to said piston about an axis 15 parallel to the axis of rotation 4, and bearing on the internal face of the intermediate part 1B of the housing, which constitutes a corrugated reaction cam 16;
• a conduit 17, formed in part 1C of the casing, connects the enclosure 18 delimited by said casing to an external conduit 19.

• la partie 1C du carter comprend un évidement central de révolution 220, d'axe de révolution confondu avec l'axe de rotation 4;
• un distributeur interne de fluide 221, dont une face périphérique axiale 222 possède une forme sensiblement complémentaire de celle de l'évidement 220 et dont une face plane de distribution 223, perpendiculaire à l'axe de rotation 4, est en appui sensiblement étanche sur la face de communication 9, un dispositif d'encoches et d'ergots associés 224 rendant solidaire, vis-à-vis de la rotation d'axe de rotation 4, le distributeur interne de fluide 221 de la partie 1C du carter;
• deux enceintes principales 25, 26 sont ménagées entre le distributeur interne de fluide 221 et l'évidement 220, et communiquent avec les conduits externes 27, 28 par l'intermédiaire de conduits 29, 30 ménagés dans la partie 1C du carter, respectivement;
• un premier groupe de conduits de distribution 31, 32 correspondant, par paires de conduits 31-32, aux ondulations d'un premier groupe d'ondulations de la came de réaction 16, communiquent en permanence, les conduits de distribution 31 avec l'enceinte principale 25, et, les conduits de distribution 32 avec l'enceinte principale 26, et débouchent dans la face de distribution 223 de manière, au cours de la rotation relative du bloc-cylindres 7 par rapport au carter 1A-1B-1C, et par suite par rapport au distributeur interne de fluide 221, à communiquer périodiquement avec les conduits de cylindre 13;
• des conduits de liaison 33, 34 relient au moins l'un des conduits de distribution 31, 32, et par leur intermédiaire les enceintes principales 25, 26, à un alésage 235 ménagé dans le distributeur interne de fluide 221, dans lequel lesdits conduits de liaison 34 débouchent entre deux plans transversaux R1, R2, perpendiculaires à l'axe 4;
• un deuxième groupe de conduits de distribution 236, 237 correspondant, par paires de conduits de distribution 236-237, aux ondulations d'un deuxième groupe d'ondulations de la came de réaction 16, communiquent, les conduits de distribution 236, en permanence, avec l'enceinte principale 25, et, les conduits de distribution 237 avec l'alésage 235 en y débouchant entre les plans transversaux R1, R2, lesdits conduits de distribution 236, 237 débouchant en outre dans la face de distribution 223 de manière, au cours de la rotation relative du bloc-cylindres 7 par rapport au carter 1A-1B-1C, à communiquer périodiquement avec les conduits de cylindre 13;
• un tiroir 238, monté coulissant, avec étanchéité, à l'intérieur de l'alésage 235, comporte: une gorge 240; des conduits axiaux borgnes 242, qui communiquent en permanence avec la gorge 240 et avec l'alésage 235; et un logement 243, axial, de réception à libre coulissement d'un pion 244 d'indexation en rotation par rapport à la partie 1C du carter, fixé sur la partie 1C du carter;
• des joints d'étanchéité 245, 246, 247 et 248, qui sont interposés entre le distributeur interne de fluide 221 et la partie 1C du carter et qui isolent chaque enceinte principale 25, 26 de l'autre enceinte et de l'intérieur du carter (joints 245, 246, 247) et isolent une chambre de pilotage 249, ménagée dans la partie 1C du carter entre celui-ci, l'extrémité du distributeur interne de fluide opposée à la face de distribution 223, et une extrémité 238A du tiroir 238;
• une butée interne de réaction 253, fixée sur la partie centrale du distributeur interne de fluide 221 par un segment 254 reçu dans une gorge 255 dudit distributeur interne de fluide, assure le maintien d'un ressort 256, qui est interposé entre ellemême et le tiroir 238 et dont l'effet, antagoniste de celui de la pression du fluide contenu dans la chambre 249, tend à placer le tiroir 238 dans une première position (figures 10, 11 et 12), dans laquelle les conduits 34 et 237 communiquent avec la gorge 240, les conduits 242 ne communiquant qu'avec la gorge 240;
• un conduit externe 51 est raccordé à la chambre 249 et est susceptible de véhiculer un fluide sous pression apte à placer le tiroir 238 dans une deuxième position (figures 13, 14 et 15), dans laquelle la gorge 240 communique avec les conduits 33 et, par l'intermédiaire des conduits borgnes 242, avec les conduits 237; les conduits 34 étant alors obturés par le tiroir 238;
• une chambre 252 est délimitée entre le distributeur interne de fluide 221, et la partie 1C du carter, entre les joints d'étanchéité 247 et 248, et communique en permanence avec le conduit 17 par l'intermédiaire d'un conduit 257, également ménagé dans la partie 1C du carter;
• un ressort 258 et interposé entre le distributeur interne de fluide 221 et la partie 1C du carter, et tend à mettre la face de distribution 223 en appui sensiblement étanche sur la face de communication 9 du bloc-cylindres 7;
• un segment 259, reçu dans une gorge 260 ménagée dans l'alésage 235 du distributeur interne 221, constitue une butée de limitation du coulissement du tiroir 238, qui, lorsqu'il est en appui sur ce segment 259, est disposé dans sa première position;
• une gorge 261 de révolution, d'axe de révolution confondu avec l'axe géométrique 4, débouche dans la face arrière plane 221A, perpendiculaire à l'axe géométrique 4, du distributeur interne de fluide 221 et est délimitée par des parois axiales cylindriques; la gorge 261 reçoit un joint d'étanchéité 263, qui délimite avec le fond de cette gorge une chambre 264 communiquant, par au moins un conduit 265, ménagé dans le distributeur interne de fluide 221, avec les conduits 237, un segment 266 étant introduit dans la gorge 261, à la suite du joint d'étanchéité 263, et prenant appui sur la face 67 de la partie 1C du carter.

This engine of FIGS. 10 to 15 also has the following provisions, which are new compared to the engine of FIG. 1:

• the part 1C of the casing comprises a central recess of revolution 220, of axis of revolution coincident with the axis of rotation 4;
• an internal fluid distributor 221, of which an axial peripheral face 222 has a shape substantially complementary to that of the recess 220 and of which a flat distribution face 223, perpendicular to the axis of rotation 4, is in substantially sealed abutment on the communication face 9, a device of notches and associated lugs 224 making integral, with respect to the rotation of the axis of rotation 4, the internal fluid distributor 221 of the part 1C of the casing;
• two main enclosures 25, 26 are formed between the internal fluid distributor 221 and the recess 220, and communicate with the external conduits 27, 28 via conduits 29, 30 formed in part 1C of the casing, respectively;
• a first group of distribution conduits 31, 32 corresponding, by pairs of conduits 31-32, to the undulations of a first group of undulations of the reaction cam 16, permanently communicate, the distribution conduits 31 with the enclosure main 25, and, the distribution conduits 32 with the main enclosure 26, and open into the distribution face 223 so, during the relative rotation of the cylinder block 7 with respect to the casing 1A-1B-1C, and consequently with respect to the internal fluid distributor 221, to communicate periodically with the cylinder conduits 13;
• connecting conduits 33, 34 connect at least one of the distribution conduits 31, 32, and through them the main enclosures 25, 26, to a bore 235 formed in the internal fluid distributor 221, in which said conduits link 34 open out between two transverse planes R1, R2, perpendicular to the axis 4;
• a second group of distribution conduits 236, 237 corresponding, by pairs of distribution conduits 236-237, to the undulations of a second group of undulations of the reaction cam 16, communicate, the distribution conduits 236, permanently, with the main enclosure 25, and, the distribution conduits 237 with the bore 235 opening therein between the transverse planes R1, R2, said distribution conduits 236, 237 further opening into the distribution face 223 so as, during the relative rotation of the cylinder block 7 with respect to the casing 1A-1B-1C, to communicate periodically with the cylinder ducts 13;
• a drawer 238, mounted to slide, with sealing, inside the bore 235, comprises: a groove 240; blind axial conduits 242, which communicate permanently with the groove 240 and with the bore 235; and a housing 243, axial, for free sliding reception of a pin 244 for indexing in rotation relative to the part 1C of the casing, fixed to the part 1C of the casing;
• seals 245, 246, 247 and 248, which are interposed between the internal fluid distributor 221 and the part 1C of the casing and which isolate each main enclosure 25, 26 from the other enclosure and from inside the casing (seals 245, 246, 247) and isolate a control chamber 249, formed in the part 1C of the casing between the latter, the end of the internal fluid distributor opposite the distribution face 223, and one end 238A of the drawer 238;
• an internal reaction stop 253, fixed on the central part of the internal fluid distributor 221 by a segment 254 received in a groove 255 of said internal fluid distributor, ensures the maintenance of a spring 256, which is interposed between itself and the drawer 238 and whose effect, antagonistic to that of the pressure of the fluid contained in the chamber 249, tends to place the drawer 238 in a first position (FIGS. 10, 11 and 12), in which the conduits 34 and 237 communicate with the groove 240, the conduits 242 communicating only with the groove 240;
• an external conduit 51 is connected to the chamber 249 and is capable of conveying a pressurized fluid capable of placing the drawer 238 in a second position (FIGS. 13, 14 and 15), in which the groove 240 communicates with the conduits 33 and, via the blind conduits 242, with the conduits 237; the conduits 34 then being closed by the drawer 238;
• a chamber 252 is delimited between the internal fluid distributor 221, and the part 1C of the casing, between the seals 247 and 248, and communicates permanently with the conduit 17 via a conduit 257, also provided in part 1C of the housing;
• a spring 258 and interposed between the internal fluid distributor 221 and the part 1C of the casing, and tends to put the distribution face 223 in substantially sealed abutment on the communication face 9 of the cylinder block 7;
• a segment 259, received in a groove 260 formed in the bore 235 of the internal distributor 221, constitutes a stop for limiting the sliding of the drawer 238, which, when it is supported on this segment 259, is disposed in its first position ;
• a groove 261 of revolution, of axis of revolution coinciding with the geometric axis 4, opens into the flat rear face 221A, perpendicular to the geometric axis 4, of the internal fluid distributor 221 and is delimited by cylindrical axial walls; the groove 261 receives a seal 263, which delimits with the bottom of this groove a chamber 264 communicating, through at least one conduit 265, formed in the internal fluid distributor 221, with the conduits 237, a segment 266 being introduced in the groove 261, following the seal 263, and bearing on the face 67 of the part 1C of the casing.

The motor of FIGS. 10 to 15 can be integrated into the circuit of FIG. 9, without any change concerning this circuit.

The hydraulic motor of Figures 16 to 18 is a motor having only one operating displacement. This engine resembles the engine shown with reference to FIGS. 1 to 9, except as regards the following characteristics: the internal fluid distributor 121 has been modified and replaces the distributor 21, so as to remove the drawer 38, the conduits 36, 37 and 50, and of course the housing 43 and the indexing pin 44.

Thus, the distribution conduits 31-136, 32-137, correspond, by pair of distribution conduits 31-32, 136-137, to the undulations of the reaction cam 16; communicate permanently, the conduits 31 and 136 with the main enclosure 25, and, the conduits 32 and 137 with the main enclosure 26; and open into a distribution face 123, which comprises the internal fluid distributor 121, planar and perpendicular to the geometric axis 4, so, during the relative rotation of the cylinder block 7 with respect to the casing 1A-1B- 1C, and consequently with respect to the internal fluid distributor 121 made integral with respect to said rotation of the part 1C of the casing by means of a device of notches and associated lugs 124, to be communicated periodically with the cylinder ducts 13.

The conduits 31, 32 communicate with the main enclosures 25, 26, the shapes of which, as previously, have been chosen to hydrostatically balance the thrust due to the pressure of the fluid contained in the conduits 31, 32 and acting on the distributor. fluid 121.

On the other hand, the conduits 136, 137, which are placed at the locations of the conduits 36, 37 of the embodiment of FIGS. 1 to 9, and which, numerically, correspond to these conduits 36, 37, generate a hydrostatic thrust, due to the effect of the pressure of the fluids they contain, no more balanced than that generated by the fluids contained in the conduits 36, 37 of the engine of FIGS. 1 to 9, and therefore a thrust not balanced by the chosen shapes of the enclosures 25, 26 For this reason, grooves 161, 162, similar to grooves 61, 62 have been provided and provide the same function with respect to conduits 136, 137 as that of grooves 61, 62 with respect to conduits 36 , 37.

These grooves 161, 162 are formed in the internal fluid distributor 121, open in its rear face 121A, flat, perpendicular to the geometric axis 4, opposite the internal face 67 of the part 1C of the casing.

Seals 163, 171, associated with segments 166, 170 bearing on the face 67, define chambers 164, 168, which communicate, through conduits 165, 169 formed in the internal fluid distributor 121 with the ducts 137, 136, respectively.

A spring 158, interposed between the internal fluid distributor 121 and the part 1C of the casing, tends to put the distribution face 123 in substantially sealed abutment on the communication face 9 of the cylinder block 7.

Finally, a plug 87 is screwed into the tapping 88 for connection of the conduit 51 of the embodiment of FIGS. 1 to 9, tapping 88 formed in the part 1C of the casing.

It should be observed that, apart from the internal fluid distributor 121, and the devices linked to it, the motor of FIGS. 16 to 18 is identical to that of FIGS. 1 to 9, in particular as regards the casing 1A-1B-1C, the cylinder block 7, the motor shaft 3, the reaction cam 16, the geometric axis 4, already defined by the description of the motor in FIGS. 1 to 9.

The operations of the motors described above are described below.

The engine shown in Figures 1 to 9 is an engine with two separate displacements, with "symmetrical" distribution.

When the secondary fluid distributor 76 is placed in its first position, the spring 56 acts alone on the slide 38, which it places in the first configuration shown with reference to FIGS. 1 to 5 and 9. Assuming the main fluid distributor 74 placed in its first position, there is the supply of pressurized fluid, by the main pump 73, of the conduits 80, 27, 29, of the groove 25, and of the conduits 31, 33, of the groove 39, and conduits 36. Similarly, the conduits 32 and 37 (conduits 37 connected to the conduits 32 by the groove 40 and the conduits 34) are connected to the fluid reservoir 72 by the groove 26 and the conduits 30, 28 and 82. The chambers working fluid 12 are each supplied with pressurized fluid, when the rollers 14 are supported on each corrugation of the reaction cam 16. The displacement, which corresponds to all of the working chambers 12, constitutes the large engine displacement.

The shapes of the main speakers 25, 26 are sufficient to balance the thrust due to the pressure of the fluids contained in the conduits 31, 32, directly connected to said grooves, these main speakers 25, 26 therefore also having the function of balancing with respect to the fluids contained in the distribution conduits 31, 32.

On the other hand, the thrust due to the pressure of the fluids contained in the conduits 36, 37, not directly connected to the main speakers 25, 26, is not balanced by the shape of these main speakers. The sets of distribution conduits 36, on the one hand, and distribution conduits 37, on the other hand, in fact constitute two secondary enclosures. The fluid cylinders, constituted by the segments 66, 70, associated with the seals 63, 71, mounted to slide in the grooves 61, 62, which are supplied with fluids contained in the conduits 37, 36 by the conduits 65, 69 , respectively, make it possible to obtain this balancing of the thrust due to the pressure of the fluids contained in the conduits 37, 36, the chambers 64, 68 constituting then balancing chambers with respect to the fluids contained in the distribution conduits 36, 37.

This balancing, directly proportional to the value of the pressures of said fluids, is also carried out automatically.

If now, the main fluid distributor 74 remaining placed in its first position, the secondary fluid distributor 76 is placed in its second position, the configuration of FIGS. 6 to 8 is obtained.

In this configuration, the conduits 36 are no longer connected to the main enclosure 25 by the groove 39 and the conduit (s) 33. Only the working chambers of the fluid 12 corresponding to the rollers 14 bearing on the corrugations corresponding to the conduits 31 are supplied with pressurized fluid. The displacement obtained constitutes the small displacement of the engine.

The conduits 36 and 37, isolated from the conduits 33, 34, and connected to the groove 40 by the blind conduits 41 and 42, which keep their constant angular orientation thanks to the indexing obtained by the combined action of the pin 44 and its housing 43, are placed in communication with the chamber 49 via the conduit 50. Note that the pressure of the fluid contained in the chamber 49 is usually of the order of 5 to 10 bars, while the pressure of the pumped fluid by the main pump 73 is usually of the order of 400 bars. Consequently, not only the working chambers 12 corresponding to said conduits 36, 37 have their supply short-circuited, but also are placed in communication with a fluid under low pressure.

It should also be observed that the thrust of the fluids contained in these conduits 36, 37 is, here again, automatically balanced by the jacks 63-66-61, and, 71-70-62. Of course, the shape of the main speakers 25, 26 continues to ensure automatic balancing of the thrust of the fluids contained in the conduits 31, 32.

The engine shown in FIGS. 10 to 15 is an engine with two separate displacements, with so-called "asymmetric" distribution.

When the secondary fluid distributor 76 is placed in its first position, the spring 256 acts alone on the slide 238, which it places in the first configuration shown with reference to FIGS. 10 to 12. Assuming the main fluid distributor 74 placed in its first position, there is the supply of pressurized fluid, by the main pump 73, of the conduits 80, 27, 29, of the groove 25, and conduits 31 and 236. Similarly, the conduits 32 and 237 are connected to the fluid reservoir 72 by the groove 26 and the conduits 30, 28 and 82, the groove 240 and the conduits 34 communicating the conduits 237 with the conduits 32. The working chambers of the fluid 12 are each supplied with pressurized fluid when the rollers 14 are supported on each undulation of the reaction cam 16. The displacement, which corresponds to all of the working chambers 12, constitutes the large displacement of the engine.

The shapes of the main enclosures 25, 26 are sufficient to balance the thrust due to the pressure of the fluids contained in the conduits 31 and 236, on the one hand, 32, on the other hand, respectively, respectively, directly connected to said grooves. Here again, as in the case of the engine of FIGS. 1 to 9, the main chambers 25, 26 also have a balancing function with respect to the fluids contained in the distribution conduits 31 and 236, and, 32.

On the other hand, the thrust due to the pressure of the fluids contained in the distribution conduits 237, not directly connected to the main speakers 25, 26, is not balanced by the shape of these main speakers. All of these distribution conduits 237 constitute a secondary enclosure. The fluid cylinder constituted by the segment 266 associated with the seal 263, mounted sliding in the groove 261, which is supplied with fluids contained in the conduits 237 by the conduits 265 allows this balancing of the thrust due to the pressure of the fluids contained in the conduits 237. The chamber 264 then constitutes a balancing chamber with respect to the fluids contained in the distribution conduits 237.

This balancing, directly proportional to the value of the pressures of said fluids, is also carried out automatically.

If now, the main fluid distributor 74 remaining placed in its first position, the secondary fluid distributor 76 and placed in its second position, the configuration of FIGS. 13 to 15 is obtained.

In this configuration, the conduits 237 are no longer connected to the main enclosure 26. Only the working chambers of the fluid 12 corresponding to the rollers 14 bearing on the corrugations corresponds to the conduits 31, 32 are periodically supplied with fluid under pressure and put in communication with the reservoir 72. The displacement obtained constitutes the small displacement of the engine.

The conduits 237 connected to the groove 240 by the blind conduits 242, which retain their constant angular orientation thanks to the indexing obtained by the combined action of the pin 244 and its housing 243, are placed in communication with the main enclosure 25 via the conduits 33 and 31, as the conduits 236 already are. The conduits 237 and 236 are therefore in communication with the same main enclosure 25.

It should also be observed that the thrust of the fluids contained in these conduits 237 is, here again, automatically balanced by the jack 263-266-261. Of course, the shapes of the main speakers 25, 26 continue to provide automatic balancing of the thrust of the fluids contained in the conduits 31, 236 on the one hand, 32 on the other hand, respectively.

• la poussée des fluides contenus dans les conduits 31, 32 est équilibrée automatiquement grâce aux choix des formes des enceintes principales 25, 26;
• la poussée des fluides contenus dans les conduits 136, 137 est équilibrée automatiquement au moyen des vérins d'équilibrage 171-170-162, et, 163-166-161.

The motor shown in FIGS. 16 to 18 does not have a displacement selection drawer 38, and therefore has only one displacement. This engine is deduced from the engine of FIGS. 1 to 9 while keeping the important and heavy parts, in particular the casing 1A-1B-1C, the cylinder block 7, etc., and by adopting a new internal distributor of fluid under pressure 121, which is a lighter piece than the others. In this internal fluid distributor 121, the balancing of the thrusts of the fluids is carried out in a manner analogous to what is obtained with the embodiment of FIGS. 1 to 9:

• the thrust of the fluids contained in the conduits 31, 32 is automatically balanced by the choice of the shapes of the main speakers 25, 26;
• the thrust of the fluids contained in the conduits 136, 137 is balanced automatically by means of the balancing cylinders 171-170-162, and, 163-166-161.

Of course, one could also conceive a variant of the engine of FIGS. 16 to 18 in which the hydrostatic thrust of the fluids contained, either of all of the conduits 31 and 136, or of all of the conduits 32 and 137 would be balanced by the shape chosen. of the corresponding main enclosure 25 or 26, but that the hydrostatic thrust of the fluids contained either in the conduits 137 or in the conduits 136 is not balanced by the shape of the corresponding enclosure. In this case, instead of providing two complementary balancing chambers (chambers 164 and 168), it would suffice to provide only one for balancing the part hydrostatic thrust not balanced by the chosen shape of the corresponding main enclosure 25 or 26.

The mechanisms according to the invention, with a single displacement or with several operating displacements, therefore make it possible in all cases to obtain balanced operations of the internal fluid distributor, without, in a manufacturing range, there being place to modify the important parts, the most expensive of these mechanisms.

In addition, the mechanism has several operating displacements, but only two main enclosures 25, 26, which allows excellent axial compactness, balancing remains possible thanks to the small auxiliary cylinders 71-70-62, 63-66-61; 263-266-261; 171-170-162, 163-166-161.

It is also worth noting an important, particularly advantageous arrangement: in each of the embodiments shown the chambers 64, 68, or 264, or 164, 168 are blind chambers, which are connected in derivation, by conduits 65, 69, or 265 , or 165, 169, to conduits 37, 36, or 237, or 137, 136, respectively, and which are therefore not crossed by the flow conveyed by said conduits. However, these flows are significant: if said chambers had to be crossed by these flows, their sections would necessarily have been large. This is not the case with the embodiments described and shown in which said chambers can have small dimensions while, of course, ensuring the balancing function of the internal fluid distributor, in which they participate.

The invention is not limited to the embodiments shown, but on the contrary covers all the variants which could be made to them without departing from the scope of the claims.

Claims (9)

1. Pressure fluid mechanism such as a hydraulic motor or a hydraulic pump, the mechanism comprising:
      a reaction cam (16);
      a cylinder block (7) mounted to rotate relative to said reaction cam about an axis of rotation (4) and provided with a plane communication face (9) perpendicular to said axis of rotation;
      a plurality of cylinders (10) formed in the cylinder block;
      a plurality of pistons (11) slidably mounted in said cylinders, at least one piston per cylinder and delimiting within each cylinder a fluid working chamber (12) which communicates with said communication face (9) via a cylinder duct (13);
      at least two main fluid enclosures (25, 26) suitable for containing a feed fluid for the working chambers (12) and an exhaust fluid from said working chambers;
      an internal fluid distributor (21; 221; 121) which is prevented from rotating (24; 224; 124) about said axis of rotation relative to said reaction cam, and including a distribution face (23; 223;123) which is plane, perpendicular to said axis of rotation (4), and suitable for bearing in substantially fluid-tight manner against said communication face (9), and into which there open out distribution ducts (31, 32, 36, 37; 31, 32, 236, 237; 31, 32, 136, 137) suitable for being connected, some to one of said main enclosures and the others to the other main enclosure; and
      balancing enclosures (25, 26, 64, 68; 25, 26, 264; 25, 26, 164, 168) of the internal fluid distributor each communicating with some (31, 32, 36, 37; 31, 32, 237; 31, 32, 136, 137) of said distribution ducts;
      characterized in that the internal fluid distributor is delimited opposite from said distribution face (23; 223; 123) by a transverse end face (21A; 221A; 121A) which is disposed facing a reaction face (67) belonging to one of the two parts constituted by the cylinder block and by a structure (1C) secured to the reaction cam (16), while at least one (64, 68; 264; 164, 168) of said balancing enclosures is constituted by a chamber (64, 68; 264; 164, 168) formed in the internal fluid distributor (21; 221; 121) and opening out into said transverse end face (21A; 221A; 121A) and by a sealing device (63-66, 71-70; 263-266; 163-166, 171-170) which is received partially inside said chamber and which bears for reaction purposes against said reaction face (67).
2. Mechanism according to claim 1, characterized in that said balancing enclosure comprises an annular groove (64, 68; 264; 164, 168) having cylindrical walls with axes parallel to said axis of rotation (4).
3. Mechanism according to any one of claims 1 and 2, characterized in that the chamber of said balancing enclosure is a blind chamber and is connected in parallel with some of said distribution ducts, communicating with them only, without conveying the flow of fluid that may be conveyed by said distribution ducts.
4. Mechanism according to any one of claims 1 and 3, characterized in that said reaction face (67) is plane and perpendicular to said axis of rotation (4).
5. Mechanism according to any one of claims 1 to 4, characterized in that the portion of said transverse end face (21A; 221A; 121A) into which said balancing enclosure opens out is plane and perpendicular to said axis of rotation (4).
6. Mechanism according to any one of claims 1 to 5, characterized in that it includes:
      distribution ducts which are formed in the internal fluid distributor (21; 221; 121), which are split up into a first group (31, 32) of pairs of distribution ducts and a second group (36, 37; 236, 237; 136, 137) of pairs of distribution ducts, with each pair comprising a first distribution duct and a second distribution duct, whereas the shapes of the walls delimiting the main enclosures (25, 26) also provide the balancing of the pressure forces of the fluid contained in the first (31) and second (32) distribution ducts of the first group of pairs (31, 32) of distribution ducts, respectively, said two main enclosures (25, 26) then also constituting two first balancing enclosures; and
      at least one second balancing enclosure (68, 64; 264; 168, 164) which is constituted by one of said chambers formed in the internal fluid distributor (21; 221; 121) and opening out into its transverse end face (21A; 221A; 121A) and by one of said sealing devices (71-70, 63-66; 263-266; 171-170, 163-166) partially received in said chamber, and which is connected by at least one duct (69, 65; 265; 169, 165) formed in the internal fluid distributor to one (36, 37; 237; 136, 137) of the two sets of distribution ducts comprising a first set, the first distribution ducts (36; 236; 136) of the second group of pairs (36, 37; 236, 237; 136, 137) of distribution ducts, and a second set, the second distribution ducts (37; 237; 137) of said second group of pairs of distribution ducts.
7. Mechanism according to claim 6, characterized in that said mechanism (figures 1 to 9) is of the type including at least one large and at least one small operating cylinder capacity, and including:
      said two main enclosures (25, 26) one of which is suitable for containing the feed fluid and the other the exhaust fluid, when the mechanism is operating with each of said two operating cylinder capacities, the shapes of the walls delimiting said main enclosures also providing balancing of the pressure forces of the fluid contained in distribution ducts (31, 32) which are permanently in communication with said main enclosures; and
      two secondary enclosures (36, 37) one of which contains the feed fluid and the other of which contains the exhaust fluid when the mechanism is operating with said large operating cylinder capacity (figures 1 to 5), and which communicate with each other when the mechanism is operating with said small operating cylinder capacity (figures 6 to 8); and
      in that two said secondary enclosures (36, 37) are associated with respective ones of two said second balancing enclosures (68, 64), each being connected via at least one internal duct (69, 65) formed through the internal fluid distributor to one of said secondary enclosures (36, 37).
8. Mechanism according to claim 6, characterized in that said mechanism (figures 10 to 15) is of the type including at least one large and at least one small operating cylinder capacity, and including:
      said two main enclosures (25, 26) one of which is suitable for containing the feed fluid and the other the exhaust fluid, when the mechanism is operating at each of said two operating cylinder capacities, the shapes of the walls delimiting said main enclosures further providing balancing of the pressure forces contained in the distribution ducts (31-236, 32) which are permanently in communication with said main enclosures; and
      a single secondary enclosure (237) which contains one of the exhaust and feed fluids when the mechanism is operating with said large operating cylinder capacity (figures 10 to 12) and which contains the other one of said fluids when the mechanism is operating with said small operating cylinder capacity (figures 13 to 15); and
      in that said single secondary enclosure (237) is associated with a single one of said second balancing enclosures (264) connected via at least one internal duct (265) formed in the internal fluid distributor to said single secondary enclosure (237).
9. Mechanism according to claim 6, characterized in that it is of the type having a single operating cylinder capacity (figures 16 to 18), and including:
      the two main enclosures (25, 26) one suitable for containing the feed fluid and the other the exhaust fluid; and
      said two second balancing enclosures (168, 164) which are connected via said internal ducts (169, 165) formed in the internal fluid distributor, one (168) of said second balancing enclosures being connected to the first distribution ducts (136) of the second group of pairs (136-137) of distribution ducts, the other one (164) of said second balancing enclosures being connected to the second distribution ducts (137) of said second group of pairs (136-137) of distribution ducts.

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