EP0043881B1 - Rotary hydraulic converting and distributing device with multiple synchronized cylinders - Google Patents

Rotary hydraulic converting and distributing device with multiple synchronized cylinders Download PDF

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Publication number
EP0043881B1
EP0043881B1 EP19800401063 EP80401063A EP0043881B1 EP 0043881 B1 EP0043881 B1 EP 0043881B1 EP 19800401063 EP19800401063 EP 19800401063 EP 80401063 A EP80401063 A EP 80401063A EP 0043881 B1 EP0043881 B1 EP 0043881B1
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EP
European Patent Office
Prior art keywords
radius
cubic
pressure
stator
capacities
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EP19800401063
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German (de)
French (fr)
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EP0043881A1 (en
Inventor
Gaston Sauvaget
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Individual
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Priority to EP19800401063 priority Critical patent/EP0043881B1/en
Priority to DE8080401063T priority patent/DE3071830D1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/08—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/356—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C2/3566—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along more than one line or surface

Definitions

  • the invention relates to a hydraulic distributor-distributor device with synchronized multi-displacement intended to transform hydraulic energy into kinetic energy of rotation and vice versa.
  • Hydraulic motors or pumps are already known as described in patents AU-B-443618, FR-A-2 057 272, US-A-3 416 457.
  • the patent AU-B-443 618 describes a hydraulic device (page 3 line 7 - page 5, line 24 and Figures 1-3) distributor converter intended to transform hydraulic energy into kinetic energy of rotation and vice versa, comprising a stator (2), a rotor (13) in which grooves are formed ( 16) equidistant radials, each designed to receive a pallet (20) whose lower face moves on the periphery (11) of the stator which has recesses forming the displacements (18), the thrust of the working fluid ensuring the drive in rotation of the rotor by moving successively in the displacements of the stator, two lateral flanges (14) mounted on a bearing (6, 7) and integral with the rotor, closing the assembly tightly.
  • French patent FR-A-2 057 272 also describes a device for converting hydraulic or pneumatic energy into kinetic energy or vice versa, such as a rotary vane motor or pump.
  • the device comprises, Figure 1, a stator (10), an outer rotor (1, 2, 38) in which are formed recesses (29).
  • the stator comprises pallet housings (69a, 69b, 69c) in FIG. 7 and supply pipes (25, 26) opening out on each side of each pallet; said pipes can be ordered separately and allow a speed variation for an almost constant flow.
  • the device according to the invention aims to overcome these drawbacks.
  • the invention as characterized in the claims solves the problem of creating a hydraulic device making it possible to obtain very large direct torques at low speed, capable of reaching the limits of current technology of transmission means, this that is to say of the order of at least 10,000,000 Nm and this with a mass that is all the more weaker as the torque increases, therefore with increasing mass power. It offers the possibility of self-compensating for dimensional variations, whatever their origin, by generating very few leaks without causing wear or cyclic pulsations. Its overall displacement can range from the fraction of a liter to hundreds of liters with very many gear ratios in both directions of rotation with remarkable efficiency. In addition, it provides total security in the event of very large overloads which can lead to the failure of control or reception components, by instantly coasting. It also allows starting and braking of masses with very high inertia.
  • the device according to the invention comprises four equidistant displacements A, B, C, D, formed in the stator 1 of external radius R.
  • the bottom of each of the displacements is of radius r aI r b , r b , r d .
  • the rotor 2 concentric with the stator 1, has a large clearance J between the radius R and the radius R1 internal to the rotor.
  • the rotor 2 has 24 equidistant and radially oriented grooves 3, in which 24 differential valves slide 4.
  • the closing flanges are assembled by 24 bolts 5.
  • the uncut valves are visible as well as a circular groove 6 supplying the differential chambers 7 at the pressure Pi prevailing inside the casing.
  • the pressure Pi can be controlled and controlled by an external distributor connected to the orifice 8 which, via the pipe 9, distributes said pressure.
  • the Pi inlet pipes can be isolated by displacement. Displacement B is shown inactive.
  • the valves are raised to the bottom of their groove 3, the other displacements A, C, D, are active. They are each limited by a ramp R.
  • each of the ramps has a groove, for the displacement A these grooves are designated by Ru a1 , R Ua2 . etc ... In these grooves lead to the inlet and outlet pipes of the working fluid 10. These pipes act, according to the direction of rotation, as the inlet or outlet function of the fluid. Here the direction of rotation is represented by the arrow F.
  • the lines 10 have been designated by HP for high pressure and BP for low pressure. In the inactive cylinder B, all the pipes are at low pressure BP.
  • the detail of the displacement A is better seen on the enlargement in section (along the plane P of FIG. 1) FIG. 2.
  • the direction of application of the high pressure HP, on the part of the valve 11 being in position active in the displacement in sliding contact on the radius r (r a ), is designated by the arrows S.
  • the thrust of the working fluid on the valve is equal to P bar / cm 2 multiplied by the active surface (R - r) L , L is the width of the valve.
  • a valve 12 is shown descending the ramp R a2, while another valve 13 goes up the ramp R a1 .
  • a displacement is limited by the pre-active valves located on either side thereof. In fig. 1 the displacement is limited by the valves 14 and 15, the valve 16 is no longer tight on R.
  • the two grooves Ru a1 , Ru a2 of each of the displacements are of length equal to that of the ramps or preferably a little longer as in FIG. 2.
  • the edge of the valve 4 is at the end of the cylindrical part r while the edge of the groove Ru a2 is at the end of the cylindrical part r however the edge of the groove Ru a2 is located opposite the pressure exchanger pipe of the valve which is therefore deactivated, that is to say made inactive. This allows the valve to go up the ramps under pressure. It is the same for the valve 12 which descends the ramp. The construction details of the valves will be described later.
  • FIG. 3 there is shown the section along A of FIG. 1.
  • the reference numbers of fig. 1 and 2 were used.
  • This view shows the section of the torus constituting the annular device, the shape of the stator 1, of the rotor 2, of the closing flanges 17, 18 and of the roller bearings 19, 20, as well as their retaining flanges 21, 22, fixed by screws 23 on the flanges 17, 18.
  • the circulation of the fluid at the pressure Pi of the casing is represented by a shading with small points. We also see the differential return chambers 7 of the valves at the bottom of their groove.
  • FIG. 4 shows the section along B of FIG. 1.
  • the circulation of the fluid at the pressure of the casing is also represented by a shading with small points.
  • the pipes 9 which supply the circular grooves (fig. 1) open into the differential chambers 7 ensuring the return of the valves at the bottom of their groove under the action of the pressure Pi of the casing in the absence of high pressure HP in line with the displacement.
  • This view also shows the fixing of the flanges 17, 18 to the rotor 2 by means of the bolts 5.
  • the holes 28 (fig. 3) and 29 (fig. 4) have a centering and a tapping, they are used for fixing on the built on the one hand and on the receiving member on the other.
  • FIG. 5 shows the valve in elevation. It is in the form of a rectangular parallelepiped whose differential section is obtained by making a shoulder 30, 31 on each of the short sides, which has the effect of reducing the active surface 32 of the lower part or valve head by relative to the upper surface 33 on which the working fluid acts to slide the valve in its groove through it through the holes 34, 35, 36, 37 (fig. 8) drilled from the face 33 and opening into a longitudinal groove 38 , of shallow depth, located on the axis of symmetry YY of the surface 32.
  • the valve comprises, on its axis of symmetry XX, a threaded hole 39 which receives a threaded sleeve 40 (valve 12 of FIG. 2) limiting the stroke of the pusher 41 recalled by the spring 42 in the output position.
  • the function of this plunger is to make the valve pre-active on the radius R of the stator in the absence of a defusing pressure in the differential chambers 7, so as to automatically delimit the active displacements when the valves pass.
  • the differential return pressure of the valves in the bottom of their groove must be greater than the thrust of the return springs 42 so that the output end of the pusher 41 is almost completely pressed into the socket 40, which has the effect to prevent the valve from coming into tight contact on the spoke R.
  • the valves are furthermore each provided with a shallow plating clearance 43, located on each of their large parallel faces in the part of the valve always remaining inside the corresponding groove in the rotor; this clearance opens at 44 on the active surface 32.
  • This surface is of concave shape along a radius 45 (FIG. 12) which corresponds to the average radius Rm of the displacements R + r / 2.
  • This radius Rm is connected on the large outer faces by a flat or better by a convex part 46, 47, being in contact with the ramps Ru at the time of the descent or the rise of the valves in the displacements.
  • the valves are furthermore provided with pressure-exchange lines 48, 49, FIG. 10 and 11, each putting one of the surface portions 32 into communication with the clearance 44 located on the opposite face. This arrangement allows the valves to be placed and immobilized when they are in sealed contact with the radius r of the displacement capacity. There is never any friction in the grooves when the valves are active.
  • the pressure Pi acts on the shoulders 30, 31 of the valves, it is always greater than the low pressure BP.
  • the high pressure HP acts on the surface 33 of the valves according to the result of the pressures HP and BP, which forces the valve to come out of its groove and to come into contact with the rays R and r.
  • the pressure variation control Pi may or may not be specific to each of the displacements.
  • the pressure Pi can be calibrated to precisely define the sliding contact pressure of the active surface 32 of the valves on the surface of radius r of the stator.
  • the depth of the displacements R-r is preferably different, in particular when they are three in number or multiples of three or two. They are of equal depth in pairs in diametric opposition, each pair may or may not be different from the others in volume.
  • the cylindrical parts R of the stator, of developed length L and r of developed length I must be of substantially equal length and of a value such that they allow each to receive at least two valves simultaneously.
  • the various reduction ratios of the speed of rotation can be obtained according to an arithmetic progression by successively combining displacements of different or equal volume, the volume of which is calculated as a function of this progression.
  • At least one of the displacements can be used as a pump, compressor or distributor to control or control auxiliary functions or one or more displacements of a second device operating in parallel or in series with the first.
  • the invention applies to all cases of coupling, decoupling, distribution and conversion of power, speeds, torques, for small, medium, large or very large powers.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)

Description

L'invention concerne un dispositif hydraulique convertisseur répartiteur à multi-cylindrées synchronisées destiné à transformer une énergie hydraulique en une énergie cinétique de rotation et réciproquement. On connaît déjà des moteurs ou pompes hydrauliques tels que décrits dans les brevets AU-B-443618, FR-A-2 057 272, US-A-3 416 457. Le brevet AU-B-443 618 décrit un dispositif hydraulique (page 3 ligne 7 - page 5, ligne 24 et figures 1-3) convertisseur répartiteur destiné à transformer une énergie hydraulique en énergie cinétique de rotation et réciproquement, comportant un stator (2), un rotor (13) dans lequel sont ménagées des rainures (16) radiales équidistantes, prévues pour recevoir chacune une palette (20) dont la face inférieure se déplace sur la périphérie (11) du stator laquelle comporte des évidements formant les cylindrées (18), la poussée du fluide moteur assurant l'entraînement en rotation du rotor en se déplaçant successivement dans les cylindrées du stator, deux flasques latérales (14) montées sur roulement (6, 7) et solidaires du rotor, refermant l'ensemble de façon étanche.The invention relates to a hydraulic distributor-distributor device with synchronized multi-displacement intended to transform hydraulic energy into kinetic energy of rotation and vice versa. Hydraulic motors or pumps are already known as described in patents AU-B-443618, FR-A-2 057 272, US-A-3 416 457. The patent AU-B-443 618 describes a hydraulic device (page 3 line 7 - page 5, line 24 and Figures 1-3) distributor converter intended to transform hydraulic energy into kinetic energy of rotation and vice versa, comprising a stator (2), a rotor (13) in which grooves are formed ( 16) equidistant radials, each designed to receive a pallet (20) whose lower face moves on the periphery (11) of the stator which has recesses forming the displacements (18), the thrust of the working fluid ensuring the drive in rotation of the rotor by moving successively in the displacements of the stator, two lateral flanges (14) mounted on a bearing (6, 7) and integral with the rotor, closing the assembly tightly.

Le brevet français FR-A-2 057 272 décrit également un dispositif convertisseur d'énergie hydraulique ou pneumatique en énergie cinétique ou l'inverse, tel que moteur ou pompe rotatifs à palettes. Le dispositif comporte, figure 1, un stator (10), un rotor extérieur (1, 2, 38) dans lequel sont ménagés des évidements (29). Le stator comporte des logements de palettes (69a, 69b, 69c) figure 7 et des canalisations d'alimentation (25, 26) débouchant de chaque côté de chaque palette ; lesdites canalisations peuvent être commandées séparément et permettent une variation de vitesse pour un débit presque constant.French patent FR-A-2 057 272 also describes a device for converting hydraulic or pneumatic energy into kinetic energy or vice versa, such as a rotary vane motor or pump. The device comprises, Figure 1, a stator (10), an outer rotor (1, 2, 38) in which are formed recesses (29). The stator comprises pallet housings (69a, 69b, 69c) in FIG. 7 and supply pipes (25, 26) opening out on each side of each pallet; said pipes can be ordered separately and allow a speed variation for an almost constant flow.

Le brevet US-A-3 416 457 décrit un convertisseur hydraulique dans lequel les palettes (176) se déplacent dans des chambres (178) à pression active, les palettes sont rendues actives au moyen d'une pression de commande agissant sur les pistons (194) en coopération avec des ressorts (84) figure 6.US Pat. No. 3,416,457 describes a hydraulic converter in which the vanes (176) move in chambers (178) at active pressure, the vanes are made active by means of a control pressure acting on the pistons ( 194) in cooperation with springs (84) Figure 6.

Ces différents dispositifs hydauliques ne permettent pas d'obtenir à la fois un nombre élevé de rapports de vitesses et un bon rendement. Leur rapport pression/puissance massique/couple est défavorable. Leur durée de vie est généralement faible du fait des efforts internes importants qu'ils engendrent. Leur rendement est particulièrement faible dans les petits rapports car ils mettent en circulation un important volume de fluide hydraulique inactif.These various hydaulic devices do not make it possible to obtain both a high number of gear ratios and good efficiency. Their pressure / mass power / torque ratio is unfavorable. Their lifespan is generally short due to the significant internal forces which they generate. Their efficiency is particularly low in small reports because they circulate a large volume of inactive hydraulic fluid.

Les utilisations des moteurs hydrauliques de type connu sont actuellement limitées technologi- quement en puissance, la cylindrée maximum développée à ce jour est de l'ordre de vingt litres. Ce type de moteur ne supporte pas les déformations élastiques d'organes, ovalisations, variations dimensionnelles dues aux différences de températures, car elles engendrent des efforts anormaux qui provoquent une usure très rapide ainsi que d'importantes fuites réduisant la puissance et le rendement. Le bon fonctionnement exige des finitions de surfaces très fines ainsi que des masses métalliques très importantes pour limiter les fuites dues aux déformations élastiques.The uses of hydraulic motors of known type are currently technologically limited in power, the maximum displacement developed to date is of the order of twenty liters. This type of engine does not support the elastic deformations of organs, ovalizations, dimensional variations due to temperature differences, because they generate abnormal forces which cause very rapid wear as well as significant leaks reducing power and efficiency. Proper functioning requires very fine surface finishes as well as very large metallic masses to limit leaks due to elastic deformations.

Le dispositif selon l'invention a pour but de pallier ces inconvénients. L'invention telle qu'elle est caractérisée dans les revendications résoud le problème consistant à créer un dispositif hydraulique permettant l'obtention de très grands couples en direct à basse vitesse, pouvant atteindre les limites de la technologie actuelle des moyens de transmission, c'est-à-dire de l'ordre d'au moins 10000000 Nm et cela avec une masse relativement d'autant plus faible que le couple s'accroît, donc avec une puissance massique croissante. Il offre la possibilité d'autocompenser les variations dimensionnelles, quelle qu'en soit l'origine, en n'engendrant que très peu de fuites sans provoquer d'usure ni de pulsations cycliques. Sa cylindrée globale peut aller de la fraction de litre à des centaines de litres avec de très nombreux rapports de vitesses dans les deux sens de rotation avec un rendement remarquable. En outre, il assure une sécurité totale en cas de surcharges très importantes pouvant entraîner la rupture d'organes de commande ou de réception, en se mettant instantanément en roue libre. Il permet également le démarrage et le freinage de masses de très forte inertie.The device according to the invention aims to overcome these drawbacks. The invention as characterized in the claims solves the problem of creating a hydraulic device making it possible to obtain very large direct torques at low speed, capable of reaching the limits of current technology of transmission means, this that is to say of the order of at least 10,000,000 Nm and this with a mass that is all the more weaker as the torque increases, therefore with increasing mass power. It offers the possibility of self-compensating for dimensional variations, whatever their origin, by generating very few leaks without causing wear or cyclic pulsations. Its overall displacement can range from the fraction of a liter to hundreds of liters with very many gear ratios in both directions of rotation with remarkable efficiency. In addition, it provides total security in the event of very large overloads which can lead to the failure of control or reception components, by instantly coasting. It also allows starting and braking of masses with very high inertia.

Aucune puissance inutile n'est absorbée, ce qui contribue à obtenir un rendement global très élevé comparativement aux solutions connues de puissance voisine.No unnecessary power is absorbed, which contributes to obtaining a very high overall efficiency compared to known solutions of neighboring power.

Les avantages obtenus grâce au dispositif selon l'invention consistent essentiellement en ceci que les très grands couples sont obtenus en choisissant un rayon moyen des cylindrées (R + r/2) de l'ordre de plusieurs mètres la section d'application du fluide moteur (section annulaire du dispositif) pouvant rester constante par plages de couples. Le dispositif comporte un stator, un rotor dans lequel sont ménagées des rainures radiales équidistantes, prévues pour recevoir chacune une palette dont la surface active se déplace sur la périphérie du stator lequel comporte des évidements formant les cylindrées (A, B, C, D), la poussée du fluide moteur assurant l'entraînement en rotation du rotor en se déplaçant successivement dans les cylindrées (A, B, C, D) du stator, deux flasques latéraux montés sur roulements et solidaires du rotor referment l'ensemble de façon étanche, chaque cylindrée communiquant par deux canalisations avec les haute et basse pressions, caractérisé :

  • - en ce que le stator comportant les cylindrées est annulaire et ne possède pas de moyeu, et en coopération avec le rotor, des flasques de fermeture et des flasques de retenue, il forme un moteur ou une pompe entièrement annulaire,
  • - en ce que les rayons R du stator et R1 du rotor sont définis par le nombre de cylindrées, par le pas entre les palettes et par l'épaisseur desdites palettes, il en résulte une longueur de la partie cylindrique active de rayon r du fond des cylindrées A, B, C, D, une longueur des rampes d'entrée et de sortie des cylindrées et une longueur des parties cylindriques de rayon R dudit stator, de telle sorte que l'étanchéité desdites cylindrées soit assurée par une palette en aval et une palette en amont sur ledit rayon R,
  • - en ce que la puissance maximale dudit convertisseur est fonction du nombre de cylindrées simultanément actives et donc de la valeur du rayon R,
  • - en ce que le débit du fluide est sensiblement constant à toutes les vitesses de rotation tout en pouvant admettre, pour éviter les à-coups au moment du passage des vitesses, une variation du débit de l'ordre de plus ou moins 15 %,
  • - en ce que l'admission du fluide est pilotée séparément pour chacune des cylindrées A, B, C, D, quand le nombre de cylindrées est impair, le volume des cylindrées pouvant être différent, ou séparément pour chaque paire de cylindrées en opposition diamétrale quand le nombre de cylindrées est pair,
  • - en ce que les cylindrées inactives ne sont pas soumises à un débit de fluide,
  • - en ce que les palettes sont construites en forme de valves différentielles à double effet, qui sont rendues actives, au contact du rayon r du fond des cylindrées actives, ou bien rappelées au fond de leur logement au moyen d'une pression différentielle Pi ou une pression du carter agissant directement sur les valves différentielles,
  • - et en ce que la mise en roue libre instantanée est obtenue en accroissant la pression Pi du carter ou en interrompant l'alimentation de la haute pression dans les cylindrées actives.
  • L'invention est décrite en détail dans le texte qui suit en référence aux dessins annexés donnés à titre d'exemples non limitatifs dans lequels :
The advantages obtained thanks to the device according to the invention essentially consist in that the very large torques are obtained by choosing an average radius of the displacements (R + r / 2) of the order of several meters the section of application of the working fluid. (annular section of the device) which can remain constant by ranges of torques. The device comprises a stator, a rotor in which equidistant radial grooves are provided, each intended to receive a pallet whose active surface moves on the periphery of the stator which comprises recesses forming the displacements (A, B, C, D) , the thrust of the working fluid ensuring the rotational drive of the rotor by moving successively in the displacements (A, B, C, D) of the stator, two lateral flanges mounted on bearings and integral with the rotor seal the assembly tightly , each displacement communicating by two pipes with high and low pressures, characterized:
  • - in that the stator comprising the displacements is annular and does not have a hub, and in cooperation with the rotor, closing flanges and retaining flanges, it forms a fully annular motor or pump,
  • - in that the radii R of the stator and R1 of the rotor are defined by the number of displacements, by the pitch between the pallets and by the thickness of said pallets, this results in a length of the active cylindrical part of radius r at the bottom of displacements A, B, C, D, a length of the entry and exit ramps of displacements and a length of the cylindrical parts of radius R of said stator, so that the sealing of said displacements is ensured by a pallet downstream and a pallet upstream on said radius R,
  • - in that the maximum power of said converter is a function of the number of simultaneously active displacements and therefore of the value of the radius R,
  • - in that the fluid flow rate is substantially constant at all rotational speeds while being able to admit, in order to avoid jolts when shifting gears, a variation in flow rate of the order of plus or minus 15%,
  • - in that the fluid intake is controlled separately for each of the displacements A, B, C, D, when the number of displacements is odd, the volume of the displacements can be different, or separately for each pair of displacements in diametrical opposition when the number of displacements is even,
  • - in that the inactive displacements are not subjected to a fluid flow,
  • - in that the pallets are constructed in the form of differential double-acting valves, which are made active, in contact with the radius r of the bottom of the active displacements, or else recalled to the bottom of their housing by means of a differential pressure Pi or a pressure of the casing acting directly on the differential valves,
  • - And in that the instantaneous freewheeling is obtained by increasing the pressure Pi of the casing or by interrupting the supply of the high pressure in the active displacements.
  • The invention is described in detail in the following text with reference to the accompanying drawings given by way of nonlimiting examples in which:

  • la figure 1 représente une coupe partielle en élévation du dispositif selon l'invention, flasque retiré ;Figure 1 shows a partial sectional elevation of the device according to the invention, flange removed;
  • la figure 2 représente une coupe partielle en élévation du dispositif selon l'invention, agrandie suivant le plan P de la figure 1 ;2 shows a partial section in elevation of the device according to the invention, enlarged along the plane P of Figure 1;
  • la figure 3 est une coupe du dispositif selon l'invention suivant la flèche A de la figure 1 ;Figure 3 is a section of the device according to the invention according to arrow A of Figure 1;
  • la figure 4 est une coupe du dispositif selon l'invention suivant la flèche B de la figure 1 ;Figure 4 is a section of the device according to the invention according to arrow B of Figure 1;
  • les figures 5 à 13 sont des vues montrant la valve différentielle.Figures 5 to 13 are views showing the differential valve.

Tel qu'il est représenté sur la figure 1 en élévation en coupe partielle, le dispositif selon l'invention comporte quatre cylindrées équidistantes A, B, C, D, ménagées dans le stator 1 de rayon extérieur R. Le fond de chacune des cylindrées est de rayon raI rb, rb, rd. Le rotor 2, concentrique au stator 1, présente un jeu important J entre le rayon R et le rayon R1 interne au rotor. Le rotor 2 comporte 24 rainures équidistantes et radialement orientées 3, dans lesquelles coulissent 24 valves différentielles 4. Les flasques de fermeture sont assemblés par 24 boulons 5. Dans la zone où le flasque a été retiré, on aperçoit les valves non coupées ainsi qu'une rainure circulaire 6 alimentant les chambres différentielles 7 à la pression Pi régnant à l'intérieur du carter. La pression Pi peut être contrôlée et pilotée par un distributeur extérieur relié à l'orifice 8 qui, par la canalisation 9, répartit ladite pression. On peut isoler les canalisations d'admission de Pi par cylindrée. La cylindrée B est représentée inactive. Les valves sont remontées au fond de leur rainure 3, les autres cylindrées A, C, D, sont actives. Elles sont limitées chacune par une rampe R.1, Ra2, Rb1, Rb2, Rc1, Rc2, Rd1, Rd2-Chacune des rampes comporte une rainure, pour la cylindrée A ces rainures sont désignées par Rua1, RUa2. etc... Dans ces rainures aboutissent les canalisations d'admission et d'échappement du fluide moteur 10. Ces canalisations font, suivant le sens de rotation, fonction d'admission ou d'échappement du fluide. Ici le sens de rotation est figuré par la flèche F. Les canalisations 10 ont été désignées par HP pour la haute pression et BP pour la basse pression. Dans la'cylindrée inactive B, toutes les canalisations sont en basse pression BP.As shown in Figure 1 in elevation in partial section, the device according to the invention comprises four equidistant displacements A, B, C, D, formed in the stator 1 of external radius R. The bottom of each of the displacements is of radius r aI r b , r b , r d . The rotor 2, concentric with the stator 1, has a large clearance J between the radius R and the radius R1 internal to the rotor. The rotor 2 has 24 equidistant and radially oriented grooves 3, in which 24 differential valves slide 4. The closing flanges are assembled by 24 bolts 5. In the area where the flange has been removed, the uncut valves are visible as well as a circular groove 6 supplying the differential chambers 7 at the pressure Pi prevailing inside the casing. The pressure Pi can be controlled and controlled by an external distributor connected to the orifice 8 which, via the pipe 9, distributes said pressure. The Pi inlet pipes can be isolated by displacement. Displacement B is shown inactive. The valves are raised to the bottom of their groove 3, the other displacements A, C, D, are active. They are each limited by a ramp R. 1 , R a2 , R b1 , R b2 , R c1 , R c2 , R d1 , R d2 -Each of the ramps has a groove, for the displacement A these grooves are designated by Ru a1 , R Ua2 . etc ... In these grooves lead to the inlet and outlet pipes of the working fluid 10. These pipes act, according to the direction of rotation, as the inlet or outlet function of the fluid. Here the direction of rotation is represented by the arrow F. The lines 10 have been designated by HP for high pressure and BP for low pressure. In the inactive cylinder B, all the pipes are at low pressure BP.

On voit mieux le détail de la cylindrée A sur l'agrandissement en coupe (suivant le plan P de la figure 1) figure 2. Le sens d'application de la haute pression HP, sur la partie de la valve 11 se trouvant en position active dans la cylindrée en contact glissant sur le rayon r (ra), est désigné par les flèches S. La poussée du fluide moteur sur la valve est égale à P bar/cm2 multiplié par la surface active (R - r) L, L est la largeur de la valve. Une valve 12 est représentée descendant la rampe Ra2 cependant qu'une autre valve 13 remonte la rampe Ra1. Une cylindrée est limitée par les valves pré-actives se trouvant de part et d'autre de celle-ci. Sur la fig. 1 la cylindrée est limitée par les valves 14 et 15, la valve 16 n'est plus étanche sur R. Les deux rainures Rua1, Rua2 de chacune des cylindrées sont de longueur égale à celle des rampes ou préférablement un peu plus longues comme sur la figure 2. Le bord de la valve 4 se trouve à l'extrémité de la partie cylindrique r cependant que le bord de la rainure Rua2 se trouve à l'extrémité de la partie cylindrique r cependant que le bord de la rainure Rua2 se trouve en face de la canalisation échangeuse de pression de la valve qui de ce fait se trouve désamorcée, c'est-à-dire rendue inactive. Ceci permet à la valve de remonter les rampes en équipression. Il en est de même pour la valve 12 qui descend la rampe. Le détail de réalisation des valves sera décrit plus loin.The detail of the displacement A is better seen on the enlargement in section (along the plane P of FIG. 1) FIG. 2. The direction of application of the high pressure HP, on the part of the valve 11 being in position active in the displacement in sliding contact on the radius r (r a ), is designated by the arrows S. The thrust of the working fluid on the valve is equal to P bar / cm 2 multiplied by the active surface (R - r) L , L is the width of the valve. A valve 12 is shown descending the ramp R a2, while another valve 13 goes up the ramp R a1 . A displacement is limited by the pre-active valves located on either side thereof. In fig. 1 the displacement is limited by the valves 14 and 15, the valve 16 is no longer tight on R. The two grooves Ru a1 , Ru a2 of each of the displacements are of length equal to that of the ramps or preferably a little longer as in FIG. 2. The edge of the valve 4 is at the end of the cylindrical part r while the edge of the groove Ru a2 is at the end of the cylindrical part r however the edge of the groove Ru a2 is located opposite the pressure exchanger pipe of the valve which is therefore deactivated, that is to say made inactive. This allows the valve to go up the ramps under pressure. It is the same for the valve 12 which descends the ramp. The construction details of the valves will be described later.

Sur la figure 3 on a représenté la coupe suivant A de la fig. 1. Les numéros de repère des fig. 1 et 2 ont été utilisés. Cette vue montre la section du tore constituant le dispositif annulaire, la forme du stator 1, du rotor 2, des flasques de fermeture 17, 18 et des roulements à galets 19, 20, ainsi que leurs flasques de retenue 21, 22, fixés par des vis 23 sur les flasques 17, 18. Des joints d'étanchéité statiques 24, 25 et d'étanchéité en rotation 26, assurent l'étanchéité de l'ensemble. La circulation du fluide à la pression Pi du carter est représentée par un ombrage à petits points. On voit également les chambres différentielles 7 de rappel des valves au fond de leur rainure.In Figure 3 there is shown the section along A of FIG. 1. The reference numbers of fig. 1 and 2 were used. This view shows the section of the torus constituting the annular device, the shape of the stator 1, of the rotor 2, of the closing flanges 17, 18 and of the roller bearings 19, 20, as well as their retaining flanges 21, 22, fixed by screws 23 on the flanges 17, 18. Seals static 24, 25 and rotational sealing 26, seal the assembly. The circulation of the fluid at the pressure Pi of the casing is represented by a shading with small points. We also see the differential return chambers 7 of the valves at the bottom of their groove.

- La fig. 4 représente la coupe suivant B de la fig. 1. La circulation du fluide à la pression du carter est également représentée par un ombrage à petits points. Les canalisations 9 qui alimentent les rainures circulaires (fig. 1) débouchent dans les chambres différentielles 7 assurant le rappel des valves au fond de leur rainure sous l'action de la pression Pi du carter en l'absence de haute pression HP au droit des cylindrées. Cette vue montre également la fixation des flasques 17, 18 sur le rotor 2 au moyen des boulons 5. Les trous 28 (fig. 3) et 29 (fig. 4) comportent un centrage et un taraudage, ils servent à la fixation sur le bâti d'une part et sur l'organe récepteur d'autre part.- Fig. 4 shows the section along B of FIG. 1. The circulation of the fluid at the pressure of the casing is also represented by a shading with small points. The pipes 9 which supply the circular grooves (fig. 1) open into the differential chambers 7 ensuring the return of the valves at the bottom of their groove under the action of the pressure Pi of the casing in the absence of high pressure HP in line with the displacement. This view also shows the fixing of the flanges 17, 18 to the rotor 2 by means of the bolts 5. The holes 28 (fig. 3) and 29 (fig. 4) have a centering and a tapping, they are used for fixing on the built on the one hand and on the receiving member on the other.

Sur la planche V on a représenté la valve différentielle sur les figures 5 à 13. La fig. 5 montre la valve en élévation. Elle se présente sous la forme d'un parallélépipède rectangle dont la section différentielle est obtenue en réalisant un épaulement 30, 31 sur chacun des petits côtés, ce qui a pour effet de réduire la surface active 32 de la partie inférieure ou tête de valve par rapport à la surface supérieure 33 sur laquelle agit le fluide moteur pour faire coulisser la valve dans sa rainure en la traversant par les trous 34, 35, 36, 37 (fig. 8) percés depuis la face 33 et débouchant dans une rainure longitudinale 38, de faible profondeur, située sur l'axe de symétrie YY de la surface 32. La valve comporte, sur son axe de symétrie XX, un trou taraudé 39 qui reçoit une douille filetée 40 (valve 12 de la fig. 2) limitant la course du poussoir 41 rappelée par le ressort 42 en position de sortie. La fonction de ce poussoir est de rendre la valve pré-active sur le rayon R du stator en l'absence d'une pression de désamorçage dans les chambres différentielles 7, de façon à délimiter automatiquement les cylindrées actives au passage des valves. La pression différentielle de rappel des valves dans le fond de leur rainure doit être supérieure à la poussée des ressorts de rappel 42 de façon à ce que l'extrémité sortie du poussoir 41 soit presque complètement enfoncée dans la douille 40, ce qui a pour effet d'empêcher la valve d'entrer en contact étanche sur le rayon R. Les valves sont en outre munies chacune d'un dégagement de placage 43 de faible profondeur, situé sur chacune de leurs grandes faces parallèles dans la partie de la valve restant toujours à l'intérieur de la rainure correspondante dans le rotor ; ce dégagement débouche en 44 sur la surface active 32. Cette surface est de forme concave suivant un rayon 45 (fig. 12) qui correspond au rayon moyen Rm des cylindrées R + r/2. Ce rayon Rm se raccorde sur les grandes faces extérieures par un plat ou mieux par une partie convexe 46, 47, se trouvant en contact avec les rampes Ru au moment de la descente ou de la montée des valves dans les cylindrées. Les valves sont en outre munies de canalisations échangeuses de pression 48, 49, fig. 10 et 11, mettant chacune en communication une des portions de surface 32 avec le dégagement 44 situé sur la face opposée. Cette disposition permet le placage des valves et leur immobilisation lorsqu'elles sont en contact étanche avec le rayon r du fond de cylindrée. Il n'y a jamais de frottement dans les rainures lorsque les valves sont actives.On plate V there is shown the differential valve in FIGS. 5 to 13. FIG. 5 shows the valve in elevation. It is in the form of a rectangular parallelepiped whose differential section is obtained by making a shoulder 30, 31 on each of the short sides, which has the effect of reducing the active surface 32 of the lower part or valve head by relative to the upper surface 33 on which the working fluid acts to slide the valve in its groove through it through the holes 34, 35, 36, 37 (fig. 8) drilled from the face 33 and opening into a longitudinal groove 38 , of shallow depth, located on the axis of symmetry YY of the surface 32. The valve comprises, on its axis of symmetry XX, a threaded hole 39 which receives a threaded sleeve 40 (valve 12 of FIG. 2) limiting the stroke of the pusher 41 recalled by the spring 42 in the output position. The function of this plunger is to make the valve pre-active on the radius R of the stator in the absence of a defusing pressure in the differential chambers 7, so as to automatically delimit the active displacements when the valves pass. The differential return pressure of the valves in the bottom of their groove must be greater than the thrust of the return springs 42 so that the output end of the pusher 41 is almost completely pressed into the socket 40, which has the effect to prevent the valve from coming into tight contact on the spoke R. The valves are furthermore each provided with a shallow plating clearance 43, located on each of their large parallel faces in the part of the valve always remaining inside the corresponding groove in the rotor; this clearance opens at 44 on the active surface 32. This surface is of concave shape along a radius 45 (FIG. 12) which corresponds to the average radius Rm of the displacements R + r / 2. This radius Rm is connected on the large outer faces by a flat or better by a convex part 46, 47, being in contact with the ramps Ru at the time of the descent or the rise of the valves in the displacements. The valves are furthermore provided with pressure-exchange lines 48, 49, FIG. 10 and 11, each putting one of the surface portions 32 into communication with the clearance 44 located on the opposite face. This arrangement allows the valves to be placed and immobilized when they are in sealed contact with the radius r of the displacement capacity. There is never any friction in the grooves when the valves are active.

Sur la fig. 13 on a montré le schéma de fonctionnement à double effet des valves différentielles. Elles sont renvoyées dans le fond de leur rainure en absence de haute pression ou lorsque la pression Pi interne au carter est modifiée par une commande extérieure, par exemple par un distributeur hydraulique non représenté.In fig. 13 the double-acting diagram of the differential valves has been shown. They are returned to the bottom of their groove in the absence of high pressure or when the pressure Pi internal to the casing is modified by an external control, for example by a hydraulic distributor not shown.

La pression Pi agit sur les épaulements 30, 31 des valves, elle est toujours supérieure à la basse pression BP. La haute pression HP agit sur la surface 33 des valves selon la résultante des pressions HP et BP, laquelle oblige la valve à sortir de sa rainure et à venir en contact avec les rayons R et r. La commande de variation de pression Pi peut être propre ou non à chacune des cylindrées. La pression Pi peut être tarée pour définir avec précision la pression de contact glissant de la surface active 32 des valves sur la surface de rayon r du stator. La profondeur des cylindrées R-r est préférablement différente, notamment lorsqu'elles sont au nombre de trois ou de multiples de trois ou de deux. Elles sont d'égale profondeur par paires en opposition diamétrale, chaque paire pouvant être ou non différente des autres en volume. Les parties cylindriques R du stator, de longueur développée L et r de longueur développée I doivent être d'une longueur sensiblement égale et d'une valeur telle qu'elles permettent de recevoir simultanément chacune au moins deux valves.The pressure Pi acts on the shoulders 30, 31 of the valves, it is always greater than the low pressure BP. The high pressure HP acts on the surface 33 of the valves according to the result of the pressures HP and BP, which forces the valve to come out of its groove and to come into contact with the rays R and r. The pressure variation control Pi may or may not be specific to each of the displacements. The pressure Pi can be calibrated to precisely define the sliding contact pressure of the active surface 32 of the valves on the surface of radius r of the stator. The depth of the displacements R-r is preferably different, in particular when they are three in number or multiples of three or two. They are of equal depth in pairs in diametric opposition, each pair may or may not be different from the others in volume. The cylindrical parts R of the stator, of developed length L and r of developed length I must be of substantially equal length and of a value such that they allow each to receive at least two valves simultaneously.

Les différents rapports de réduction de la vitesse de rotation peuvent être obtenus suivant une progression arithmétique en combinant successivement des cylindrées de volume différent ou égal, dont le volume est calculé en fonction de cette progression.The various reduction ratios of the speed of rotation can be obtained according to an arithmetic progression by successively combining displacements of different or equal volume, the volume of which is calculated as a function of this progression.

Le démarrage au couple maximum peut être obtenu en laminant le fluide dans le distributeur d'alimentation.Starting at maximum torque can be achieved by laminating the fluid in the feed distributor.

Au moins une des cylindrées peut être utilisée en pompe, compresseur ou répartiteur pour commander ou asservir des fonctions annexes ou une ou plusieurs cylindrées d'un second dispositif fonctionnant en parallèle ou en série avec le premier.At least one of the displacements can be used as a pump, compressor or distributor to control or control auxiliary functions or one or more displacements of a second device operating in parallel or in series with the first.

L'invention s'applique à tous les cas de couplage, découplage, répartition et conversion de puissance, de vitesses, couples, pour des puissances petites, moyennes, grandes ou très grandes.The invention applies to all cases of coupling, decoupling, distribution and conversion of power, speeds, torques, for small, medium, large or very large powers.

Claims (12)

1. Hydraulic converter/distributor device designed to transform hydraulic energy into kinetic rotation energy and reciprocally, containing a stator (1), rotor (2), in which equidistant, radial grooves (3) are provided each designed to house a vane (4) whose active surface moves on the circumference of the stator the which contains recesses forming the cubic capacities (A, B, C, D). two side flanges mounted on bearings (19, 20) and rigidly locked to the rotor (2) enclosing and sealing the assembly, each cubic capacity communicating via two ducts (10) with the high and low pressures (HP, BP), wherein :
- the stator (1) containing the cubic capacities (A, B, C, D) is annular and has no hub, and in cooperation with the rotor (2), closing flanges (17, 18) and retaining flanges (21, 22), it forms a motor or fully annular pump,
- the radii (R) of the stator (1) and (R1) of the rotor (2) are defined by the number of cubic capacities, by the pitch between the vanes (4) and by the thickness of the aforesaid vanes, resulting in a length of the radius r active cylindrical section of the base of the cubic capacities (A, B, C, D), a length of the cubic capacities inlet and outlet ramps (Ra1, Rez, Rb1' Rb2, Rc1, Rc2. Rd1, Rd2) and a length of the radius R cylindrical sections of the aforesaid stator, in such a way that the aforesaid cubic capacities are sealed by one vane upline and one vane downline on the aforesaid radius R,
- the maximum power of the aforesaid converter depends on the number of cubic capacities simultaneously active and hence on the value of radius R,
- the flow of the fluid is practically constant at all speeds of rotation whilst, to avoid jerks when changing gears, accepting a variation in the flow of around ± 15 %,
- the inlet of the fluid is controlled separately for each of the cubic capacities (A, B, C, D) when their number is odd, as their volume may be different, or separately for each diametrically opposite pair of cubic capacities when their number is even,
- the inactive cubic capacities are not subjected to a fluid flow,
- the vanes are constructed in the form of dual effect differential valves (4), which are made active, in contact with radius (r) of the base of their cubic capacities, directly by the high pressure (HP) in the active cubic capacities, or else returned to the bottom of their housing by a differential pressure (Pi) or pressure of the casing acting directly on the differential valves (4)
- and instantaneous free wheeling is obtained by increasing the pressure (Pi) of the casing or cutting off the supply of high pressure (HP) in the active cubic capacities.
2. Device as claimed in claim 1, wherein the active surface (32) of the valve is put into communication with the opposite face (33) by holes (34, 35, 36, 37), wherein the valves are in Tee form, the two small sides each containing a shoulder (31, 32), increasing the surface of the opposite face (33) in relation to the active surface (32), wherein the active surface (32) is divided longitudinally into two equal parts by a shallow groove (38) in which holes (34, 35, 36, 37) emerge, putting the two surfaces (32, 33) into communication,
- wherein the two parts of the active surface (32) together have a concave profile whose radius (45) corresponds to the mean radius (Rm) of the cubic capacities (R + r/2), and
- wherein the two parts of the active surface (32) are connected to the large outside, parallel faces by a flat section or by a convex radius (46, 47).
3. Device as claimed in claim 2 wherein the cubic capacities (A, B, C, D) are defined by the inner radius (R1) of rotor (2), by the two closing flanges (17, 18) and by the recesses machined in the stator (1), these recesses containing a cylindrical portion of radius r limited on each side by a slope ramp and of identical length, connecting to the cylindrical peripheral of radius R, each ramp containing a fluid (HP, LP) duct (10), wherein the radius r cylindrical sections of stator (1) have the same length so that each one can house simultaneously at least two differential valves (4), wherein the radius R cylindrical sections of stator (1) are of a length such that each one houses at least two differential valves (4) in order to seal the cubic capacities located on either side of the aforesaid radius R cylindrical sections,
- wherein the inner radius (R1) of rotor (2) and the radius R of stator (1), placed concentrically, have considerable play (J),
- wherein valves (4) are made pre-active in fluid-tight contact with the radii R,
- wherein for each cubic capacity (A, B, C, D), the length of the distribution grooves (Ru) linking the ducts (10) to the cubic capacities, is equal to or slightly greater than the length of the corresponding ramps,
- wherein, in case of pairs of cubic capacities, the volume can be different from one pair to another,
- wherein the cubic capacities (A, B, C, D) can be of different volume, and wherein the fluid (HP, LP) flow ducts (10) are placed radially and emerge in the internal bore of the stator, their cross section being very high so as to reduce the pressure drops to a minimum.
4. Device as claimed in claim 2, wherein the valves (4) each contain an integrated plunger (41), independent of the groove (3), whose travel is very limited, the plunger (41) being returned by a spring (42), and wherein this plunger (41) normally emerges on the opposite face (33) at a height such that when valve (4) bears on radius R of stator (1) plunger (41) is compressed sufficiently to make valve (4) preactive and seal the contact of the active surface (32) on radius R of the stator, the aforesaid plunger (41) only operating on the radius R sections of the stator.
5. A device as claimed in claim 4, wherein the valves (4) contain at least a pair of pressure exchanger ducts (48, 49) one putting the first part of the active surface (32) into communication with the opening (43) in one of the large outer faces, and the other the second section of the active surface (32) with the opening (43) on the other large outer face.
6. Claim as claimed in claim 3 (wherein the valves (4) are made active by being put into sealed contact with the radius r cylindrical portion through the resultant of the HP and LP pressures operating on the opposite face (3) of the valve (4) through the difference in the surfaces of the active and opposite faces (22, 23) which obliges valve (4) to lower on the ramps to the base of the active cubic capacities until sealing is obtained on cubic capacity base radius (r), and wherein the said sealing is obtained when the corresponding pressure exchange duct (48, 49), emerging on face (32) closes in contact with the cylindrical section (r) after having left the inlet groove (Ru) of the fluid on the outlet of the ramp, wherein the aforesaid valve is applied on the inner face of its groove (3) opposite the fluid inlet, and wherein the deactivation of the aforesaid valves (4) is obtained as soon as the corresponding pressure exchange duct (48, 49) emerging on the active surface (32) leaves radius (r) and arrives in line with the inlet groove (Ru) of the outlet of the cubic capacity, low pressure (LP) outlet side.
7. Device as claimed, in claim 2, wherein one, several or all the cubic capacities (A, B, C, D) can be made inactive, wherein the pressure (Pi) of the casing applies to the shoulders (31, 32) of valves (4) via an annular, differential chamber (7) defined in rotor (2), in the absence of high pressure (HP) flow in the corresponding cubic capacity (B), wherein the differential chamber (7) is always at the pressure (Pi) of the casing, wherein the pressure (Pi) is always higher than the low pressure (LP), wherein the variation in pressure (Pi) of the casing can be specific to each cubic capacity, and wherein the contact pressure slipping on the active surface (32) of the valves against the radius r surface of the stator (1) is adjusted, firstly by a pressure (Pi) operating on the surface of the shoulders (30, 31) and secondly by the resultant of the HP and LP pressures operating on the surface (33) opposite to the active surface (32) subjected to the high pressure (HP).
8. Device as claimed in claims 3 and 7, wherein the different rotation speed ratios of the converter rotor (2) used as motor and the corresponding torque are obtained via a drive fluid delivered by a constant flow rate to pump for all the rotation speeds, and wherein for the slowest speed and the highest torque, the whole of the flow is distributed in all the cubic capacities (A, B, C, D), which are then all active, and progressively, supplying them with the same constant flow rate, of decreasing cubic capacity so as to increase the speed reducing the torque until the whole of the drive fluid is delivered into the lowest volume cubic capacity (A) in order to obtain the highest rotation speed and the lowest motor torque.
9. Device as claimed in claims 3 and 7, wherein at least one of the cubic capacities (A, B, C, D) is used as a pump, distributor or compressor, to control or servo ancillary functions or supply at least one cubic capacity with a second motor device operating in series or in parallel with the first device.
10. Device as claim in claim 3, wherein the depth (Rr) of the cubic capacities (A, B, C, D) increases along a constant ratio per pairs of cubic capacity, each diametrically opposite cubic capacity having the same depth, the device containing at least two pairs of cubic capacities.
11. Device as claim in claim 1, wherein it contains at least three cubic capacities of different depth (R - r).
EP19800401063 1980-07-15 1980-07-15 Rotary hydraulic converting and distributing device with multiple synchronized cylinders Expired EP0043881B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP19800401063 EP0043881B1 (en) 1980-07-15 1980-07-15 Rotary hydraulic converting and distributing device with multiple synchronized cylinders
DE8080401063T DE3071830D1 (en) 1980-07-15 1980-07-15 Rotary hydraulic converting and distributing device with multiple synchronized cylinders

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19800401063 EP0043881B1 (en) 1980-07-15 1980-07-15 Rotary hydraulic converting and distributing device with multiple synchronized cylinders

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EP0043881A1 EP0043881A1 (en) 1982-01-20
EP0043881B1 true EP0043881B1 (en) 1986-11-12

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DE4303115A1 (en) * 1993-02-04 1994-08-11 Bosch Gmbh Robert Vane pump
CN113244741B (en) * 2021-04-27 2022-11-08 湖北灏瑞达环保能源科技有限公司 Liquid collection redistributor for waste gas treatment spray tower

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GB191202340A (en) * 1911-02-25 1912-08-29 Edgar Flygh Girod Improvements in and relating to Steam-engines of the Rotary Type.
US2396316A (en) * 1942-04-02 1946-03-12 Houdaille Hershey Corp Hydraulic pump or motor
US2873683A (en) * 1956-06-05 1959-02-17 Farmingdale Corp Floating non-sticking blades
US3139036A (en) * 1961-09-14 1964-06-30 Daniel F Mcgill Rotary piston action pumps
DE1176952B (en) * 1961-12-23 1964-08-27 Beteiligungs & Patentverw Gmbh Motion converter for converting a reciprocating motion into a rotating motion, and vice versa
US3241456A (en) * 1962-12-26 1966-03-22 Baron C Wolfe Rotary fluid motor
US3416457A (en) * 1966-07-19 1968-12-17 Applied Power Ind Inc Vane type fluid converter
US3450004A (en) * 1967-06-06 1969-06-17 Biasi Charles P De Auto-kinetic wheel or fluid motor
FR2057272A5 (en) * 1969-08-08 1971-05-21 Sauvaget Gaston
AU443618B2 (en) * 1969-05-14 1973-12-10 Leonard Haffner Thomas Rotary motors or pumps

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DE3071830D1 (en) 1987-01-02

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