EP1783371B1 - Electric pump unit - Google Patents

Electric pump unit Download PDF

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Publication number
EP1783371B1
EP1783371B1 EP06291732A EP06291732A EP1783371B1 EP 1783371 B1 EP1783371 B1 EP 1783371B1 EP 06291732 A EP06291732 A EP 06291732A EP 06291732 A EP06291732 A EP 06291732A EP 1783371 B1 EP1783371 B1 EP 1783371B1
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EP
European Patent Office
Prior art keywords
pumps
pump unit
electric pump
manifold
motors
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EP06291732A
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German (de)
French (fr)
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EP1783371A1 (en
Inventor
Nicaïse Lesther
François Fischer
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JTEKT HPI SAS
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JTEKT HPI SAS
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Publication of EP1783371A1 publication Critical patent/EP1783371A1/en
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Classifications

    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms

Definitions

  • the invention relates to an electric pump unit, of the type comprising two hydraulic pumps, in particular geared, driven in rotation by a motor device as described in JP 07-243393 disclosing the preamble of claim 1.
  • Electro-pumps of this type which are known and in particular used by the power steering of a motor vehicle, have the major disadvantage that the power of the group is limited although the vehicles to be equipped with a power steering are becoming heavier and the powers necessary to ensure the power steering are higher and higher.
  • the power of the electric pump units is limited for technological reasons, in particular because the power supply and the connectors do not accept a sufficient intensity, as the technology of high power engines (> 1.5 kW ) is almost non-existent for a voltage of 12V and that the development of such motors is limited to low series and has a high cost.
  • the invention aims to overcome the drawback of known systems.
  • the electro-pump unit according to the invention is characterized in that it comprises two hydraulic pumps and two electric motors which are arranged so that the power of the group can be obtained by adding the powers of the two. engines.
  • the electropump is characterized in that it comprises a discharge manifold which comprises a discharge channel common to both pumps.
  • the electric pump unit is characterized in that the two pumps are integrated in a common pump body.
  • the electro-pump unit is characterized in that comprises a suction manifold having a suction channel common to both pumps.
  • the electric pump unit is characterized in that the pump body is sandwiched between the suction manifold and the discharge manifold, each manifold bearing on its outer face one of the two motors.
  • the electric pump unit is characterized in that the pump body comprises, inside an outer casing wall, a high pressure volume common to the two pumps, which communicates with the working chambers of the two pumps and a common high pressure volume provided in the discharge manifold, which is in communication with the common discharge channel.
  • the electro-pump unit is characterized in that at least one of the pumps comprises, in its discharge path a non-return valve so that this pump can be selectively stopped.
  • the electric pump unit is characterized in that it comprises an engine control device adapted to control one engine from the outside and that engine controls the speed of the other.
  • the electric pump unit is characterized in that the two motors rotate in the same direction or in opposite directions.
  • the electro-pump unit is characterized in that the two pumps are adapted to rotate with an angular offset of a few degrees to provide a decrease in the pressure pulsations produced by the electro-pump unit.
  • the electric pump unit is characterized in that the two pumps are capable of operating in phase opposition.
  • the electric pump unit is characterized in that the pumps operate at different speeds of rotation.
  • the electric pump unit is characterized in that the presence of two motors constitutes a redundancy security means.
  • the figure 1 is the overview of an electric pump unit according to the invention, which comprises two electric motors and two hydraulic pumps, each driven by one of the two motors.
  • references 1 and 2 designate the two electric motors
  • the reference B the pump body which encloses two hydraulic gear pumps, A manifold inlet or suction pumps and C the manifold outlet or discharge.
  • the pump body B is sandwiched between the inlet manifolds A and outlet C.
  • Each motor has a base portion respectively 4 and 5 which carries the electrical connections 6 of the motors and encloses the electrical circuits.
  • the figure 15 gives the synoptic diagram of the system according to the figure 1 .
  • the engine 1 drives a first pump designated by the reference 8 and the second the engine 2 a second pump 9.
  • the two pumps 8 and 9 draw the hydraulic fluid into a reservoir 10.
  • the discharge paths of the two pumps are met at the junction point 14 and thus supply the user with high-pressure hydraulic fluid, generally in oil.
  • a check valve 12 In the discharge line of each pump upstream of the junction point 14 is provided a check valve 12.
  • a pressure limiter 11 and a feed valve 13 are mounted in parallel between the junction point 14 and the reservoir.
  • the figure 3 illustrates the structure of the suction manifold A and also shows the gears of the gear trains of the two pumps 8 and 9, noted for the pump 8 and 16 for the pump 9, the gears being shown with their lower bearings 17 and higher 18.
  • the presentation of the manifold or suction support A is supplemented by the two views in section 6 and 7 which are taken along the lines VI-VI and VII-VII indicated on the figure 2 .
  • the suction manifold A has a suction channel 20 which opens out into the side face 21.
  • This channel 20 which is straight as seen on the Figures 6 and 7 communicates with low pressure capacitive cavities 23, 24 dug in the manifold from the inner face 25 intended to receive the pump body B.
  • This suction channel 20 is connected to a reservoir 10 according to Figure 19, outside the group electro-pump.
  • the cavity 23 near the pinions 16 of the pump 9 is wider and deeper than the cavity 24 on the side of the other pump, which is in the form of an arcuate groove.
  • the cavity 23 has a raised bottom intermediate zone 23 'which delimits a cavity 26 for receiving the spring 27 of the pressure limiter 11 (FIG. 19).
  • the suction channel 20 opens directly into the cavity 23 and communicates with the cavity 24 by a vertical channel 28, that is to say perpendicular to the section plane.
  • the figure 7 further indicates at 30 grooves in which are placed unrepresented seals.
  • the reference 25 designates the installation face of the pump body B.
  • the figures 4 , 8 and 9 show that the pump body B has a bottom wall 32 which rests on the installation face 25 of the suction manifold A and on which rises an outer casing wall 33, and inside this casing there are presqu'Ilots 35, 36 which delimit chambers 37, 38 for housing the gear trains 15, 16 and bearings 17, 18, parts in the form of peduncles 39 for attaching the presqu'Ilots to the envelope wall 33 configured for producing two cylindrical housings 40, 41 of the two nonreturn valves 12 ( figure 15 ) and the housing 39 in alignment with the cavity 26 for receiving the pressure limiter 11 (Figure 19).
  • the envelope wall 33 has a boss which delimits a cavity 43 intended to receive the feedback valve 13 ( figure 15 ).
  • the remainder of the space inside the envelope wall 33 constitutes a capacitive volume comprising four cavities 45, 46, 47, 48 separated from each other only by the peduncle-shaped portions and two narrow ribs 49 of attachment of the penlets to the envelope wall.
  • the front face and the surfaces of the presqu'Ilots, peduncles and ribs constitute the exposure face 34 for manifold C.
  • FIG. 8 and 9 show the inlet channels 50 and 51 of the chambers 37 and 38 for housing the gear trains with the bearings of the two pumps and the outlet channels 53 and 54.
  • the inlet channel 51 communicates with the low pressure cavity 23 into which the suction channel 20 opens.
  • the inlet channel 50 is connected to the suction channel 20 in a corresponding manner, not shown specifically.
  • the figure 12 also shows that the outlet channel 54 communicates with the housing 41 of one of the two check valves 12, through the orifice 52 of the seat of the ball 55 of the valve.
  • the ball 55 is pushed back onto its seat by a return spring 57 resting at its other end on a bearing base 58 being guided by a member in the form of a rod 59 of the valve, disposed in the center of the housing 41.
  • the outlet channel 53 communicates in the same way with the housing 40 of the other non-return valve 12.
  • FIG. 5 and the sectional views of Figures 10 and 11 illustrate the structure of the manifold or pressure support C.
  • the discharge manifold C comprises a bottom wall 60 on which is raised perpendicularly an outer casing wall 61 which encloses a common capacitive volume 63.
  • the front face 62 of this wall is intended to bear on the front face of installation of the pump body 34.
  • the volume 63 surrounds two islands 65, 66 for supporting the upper bearings 18 of the two gear trains, these islands are connected to each other by a relatively thin bar 67 and, at the of this bar, to the casing wall 61 by a raised area 68.
  • This area has two circular projections 69 to the level of the laying plane of the manifold. These zones 69 are intended to serve as a bearing surface, each at the base of a base 58 of spring support of a nonreturn valve 12.
  • housing cavities 40, 41 of the pump body B communicate with the volume 63 of the discharge manifold C, by passages indicated at 72 on either side and around the projections 69 for supporting the anti-backflow valves. -return.
  • the sectional view of the figure 10 shows that the capacitive volume 63 is in communication with a high pressure outlet channel 75 which opens out into the side wall 76 of the discharge manifold C.
  • a high pressure outlet channel 75 which opens out into the side wall 76 of the discharge manifold C.
  • the opening towards the outside of the outlet channel that is to say of repression, is not visible, but one recognizes at the bottom of the volume 63 in 77 the opening of the channel 75 in the volume 63.
  • the discharge outlet manifold C comes, in the assembled state, by its upper face 62 bearing on the upper face 34 of the pump body B, the cavities 45, 46, 47 and 48 of the body B and the volume 63 of the discharge manifold C constitute a single volume filled with the high-pressure oil discharged by the pumps 8 and 9 through the discharge channels 53 and 54 ( figure 9 ) through the check valves 12 arranged in the chambers 40, 41.
  • the pressure limiter 11 ( figure 15 ) it is placed in the cavity 26 of the suction manifold A ( figures 3 , 6, 7 ) and the cavity 39 of the pump body B ( figures 4 , 8, 9 ).
  • the bottom of the cavity 26 is in communication with the low pressure suction space 23, by a not shown channel and the cavity 39 of the pump body B communicates via a visible channel 75 Figures 8 and 9 with the high pressure cavity 48 and thus with the discharge channel 75 via the volume 63 of the discharge manifold C.
  • the refilling valve 13 it is housed in the cavity 43 of the pump body B ( figures 4 , 8, 9 ) that communicates, as we see on the figure 13 with the low-pressure groove 24 of the suction manifold A on the one hand and the volume 63 of the discharge manifold C on the other hand.
  • the two motors 1 and 2 are arranged on either side of the assembly formed by the two pumps and comprising the suction manifolds A and discharge C and sandwiched between these two manifolds , the pump body B.
  • the driving shaft of the motor 2 which is intended to pass through the bore 81 visible in the island 66 of the delivery manifold C, is represented at 80.
  • Concerning the drive of the gear train 15 of the pump 8, it is driven by the engine 1 whose shaft will then cross the bottom wall of the suction manifold A.
  • the invention therefore consists in using two motors which are controlled to be able to add the available powers of the two pumps.
  • the invention also makes it possible to drive two different and uncoupled pumps to increase the difference between the minimum and maximum flow of the electropump. Pumps are generally limited in minimum flow because it is necessary to operate them at a minimum speed, the use of two pumps and two motors allows during low flow requests, not operate a motor and reduce power consumption. Thanks to the presence of a non-return valve at the outlet of the pumps, one of the two pumps can be stopped.
  • the invention makes it possible to use engines that are widely used in series and to provide redundancy between the two motors, which makes it possible to avoid stopping power assistance in the event of a failure of one of the engines.
  • the engine control it is performed from the instructions of the vehicle that the electro-pump group team.
  • the steering could be provided by one of the two engines which would then drive the speed of the second.
  • each pump generates pulsations of a frequency equal to the number of teeth multiplied by the rotation frequency of the pump.
  • the motor control could be carried out to obtain a functioning of the pumps in opposition of phase. We could also drive the engines at different speeds.
  • the invention makes it possible, by integrating the functions of the two pumps into a common pump body, to reduce the size of the group, while providing a large common high pressure volume, which provides, despite the presence of two pump units, a considerable improvement in damping pulsations produced by these pumps.

Description

L'invention concerne un groupe électro-pompe, du type comprenant deux pompes hydrauliques, notamment à engrenage, entraînées en rotation par un dispositif moteur tel que décrit dans JP 07-243393 divulgant le préambule de la revendication 1.The invention relates to an electric pump unit, of the type comprising two hydraulic pumps, in particular geared, driven in rotation by a motor device as described in JP 07-243393 disclosing the preamble of claim 1.

Des groupes électro-pompes de ce type, qui sont connus et notamment utilisés par la direction assistée de véhicule automobile, présentent l'inconvénient majeur que la puissance du groupe est limitée bien que les véhicules à équiper d'une direction assistée sont de plus en plus lourds et les puissances nécessaires pour assurer la direction assistée sont de plus en plus élevées. Or, actuellement la puissance moteur des groupes électro-pompe est limitée pour des raisons technologiques, notamment du fait que l'alimentation et la connectique n'acceptent pas une intensité suffisante, que la technologie des moteurs de forte puissance (> 1,5 kW) est quasi inexistante pour une tension de 12V et que le développement de tels moteurs se limite à des faibles séries et présente un coût élevé.Electro-pumps of this type, which are known and in particular used by the power steering of a motor vehicle, have the major disadvantage that the power of the group is limited although the vehicles to be equipped with a power steering are becoming heavier and the powers necessary to ensure the power steering are higher and higher. However, currently the power of the electric pump units is limited for technological reasons, in particular because the power supply and the connectors do not accept a sufficient intensity, as the technology of high power engines (> 1.5 kW ) is almost non-existent for a voltage of 12V and that the development of such motors is limited to low series and has a high cost.

L'invention a pour but de pallier l'inconvénient des systèmes connus.The invention aims to overcome the drawback of known systems.

Pour atteindre ce but, le groupe électro-pompe selon l'invention est caractérisé en ce qu'il comprend deux pompes hydrauliques et deux moteurs électriques qui sont agencés de façon à ce que la puissance du groupe puisse être obtenue par additionnement des puissances des deux moteurs.To achieve this goal, the electro-pump unit according to the invention is characterized in that it comprises two hydraulic pumps and two electric motors which are arranged so that the power of the group can be obtained by adding the powers of the two. engines.

Selon l'invention, le groupe électro-pompe est caractérisé en ce qu'il comprend un manifold de refoulement qui comporte un canal de refoulement commun aux deux pompes.According to the invention, the electropump is characterized in that it comprises a discharge manifold which comprises a discharge channel common to both pumps.

Toujours selon l'invention, le groupe électro-pompe est caractérisé en ce que les deux pompes sont intégrées à un corps de pompe commun.Still according to the invention, the electric pump unit is characterized in that the two pumps are integrated in a common pump body.

Encore selon l'invention, le groupe électro-pompe est caractérisé en ce qu'il comprend un manifold d'aspiration comportant un canal d'aspiration commun aux deux pompes.Still according to the invention, the electro-pump unit is characterized in that comprises a suction manifold having a suction channel common to both pumps.

Enfin, selon l'invention, le groupe électro-pompe est caractérisé en ce que le corps de pompe est disposé en sandwich entre le manifold d'aspiration et le manifold de refoulement, chaque manifold portant sur sa face extérieure un des deux moteurs.Finally, according to the invention, the electric pump unit is characterized in that the pump body is sandwiched between the suction manifold and the discharge manifold, each manifold bearing on its outer face one of the two motors.

Selon une autre caractéristique de l'invention, le groupe électro-pompe est caractérisé en ce que le corps de pompe comporte, à l'intérieur d'une paroi d'enveloppe extérieure un volume haute pression commun aux deux pompes, qui communique avec les chambres de travail des deux pompes et un volume haute pression commun prévu dans le manifold de refoulement, qui est en communication avec le canal de refoulement commun.According to another characteristic of the invention, the electric pump unit is characterized in that the pump body comprises, inside an outer casing wall, a high pressure volume common to the two pumps, which communicates with the working chambers of the two pumps and a common high pressure volume provided in the discharge manifold, which is in communication with the common discharge channel.

Selon encore une autre caractéristique de l'invention, le groupe électro-pompe est caractérisé en ce qu'au moins une des pompes comporte, dans sa voie de refoulement un clapet anti-retour si bien que cette pompe puisse être arrêtée sélectivement.According to yet another characteristic of the invention, the electro-pump unit is characterized in that at least one of the pumps comprises, in its discharge path a non-return valve so that this pump can be selectively stopped.

Selon encore une autre caractéristique de l'invention, le groupe électro-pompe est caractérisé en ce qu'il comprend un dispositif de pilotage des moteurs adapté pour assurer le pilotage d'un moteur de l'extérieur et en ce que ce moteur pilote la vitesse de l'autre.According to yet another characteristic of the invention, the electric pump unit is characterized in that it comprises an engine control device adapted to control one engine from the outside and that engine controls the speed of the other.

Selon encore une autre caractéristique de l'invention, le groupe électro-pompe est caractérisé en ce que les deux moteurs tournent dans le même sens ou dans les sens opposés.According to yet another characteristic of the invention, the electric pump unit is characterized in that the two motors rotate in the same direction or in opposite directions.

Selon encore une autre caractéristique de l'invention, le groupe électro-pompe est caractérisé en ce que les deux pompes sont adaptées pour tourner avec un décalage angulaire de quelques degrés pour procurer une diminution des pulsations de pression produites par le groupe électro-pompe.According to yet another characteristic of the invention, the electro-pump unit is characterized in that the two pumps are adapted to rotate with an angular offset of a few degrees to provide a decrease in the pressure pulsations produced by the electro-pump unit.

Selon encore une autre caractéristique de l'invention, le groupe électro-pompe est caractérisé en ce que les deux pompes sont susceptibles de fonctionner en opposition de phases.According to yet another characteristic of the invention, the electric pump unit is characterized in that the two pumps are capable of operating in phase opposition.

Selon encore une autre caractéristique de l'invention, le groupe électro-pompe est caractérisé en ce que les pompes fonctionnent à des vitesses de rotation différentes.According to yet another characteristic of the invention, the electric pump unit is characterized in that the pumps operate at different speeds of rotation.

Selon encore une autre caractéristique de l'invention, le groupe électro-pompe est caractérisé en ce que la présence de deux moteurs constitue un moyen de sécurité par redondance.According to yet another characteristic of the invention, the electric pump unit is characterized in that the presence of two motors constitutes a redundancy security means.

L'invention sera mieux comprise, et d'autres buts, caractéristiques, détails et avantages de celle-ci apparaîtront plus clairement dans la description explicative qui va suivre faite en référence aux dessins schématiques annexés donnés uniquement à titre d'exemple illustrant deux modes de réalisation de l'invention et dans lesquels :

  • la figure 1 est une vue en perspective d'un premier mode de réalisation d'un système de groupe électro-pompe selon l'invention ;
  • la figure 2 est une vue latérale du système représenté sur la figure 1,
  • la figure 3 est une vue en perspective du manifold d'aspiration indiqué en A sur la figure 1 du système selon l'invention, certaines parties du module pompe étant représentés supplémentairement ;
  • la figure 4 est une vue en perspective du corps de pompe B de la figure 1, disposé sur le module d'aspiration A ;
  • la figure 5 est une vue en perspective du manifold de refoulement indiqué en C sur la figure 1 ;
  • la figure 6 est une vue en coupe le long de la ligne VI-VI de la figure 2 ;
  • la figure 7 est une vue en coupe le long de la ligne VII-VII de la figure 2 ;
  • la figure 8 est une vue en coupe selon la ligne VIII-VIII de la figure 2 ;
  • la figure 9 est une vue en coupe selon la ligne IX-IX de la figure 2 ;
  • la figure 10 est une vue en coupe selon la ligne X-X de la figure 2 ;
  • la figure 11 est une vue en coupe selon la ligne XI-XI de la figure 2 ;
  • la figure 12 est une vue en coupe de l'ensemble formé par le corps de pompe B et des manifolds A et C à l'état assemblé selon la ligne XII-XII de la figure 8 ;
  • la figure 13 est une vue en coupe de cet ensemble selon la ligne XIII-XIII des figures 8 et 9 ;
  • la figure 14 est une vue en coupe de cet même ensemble selon la ligne XIV-XIV des figures 5 et 9 ;et
  • la figure 15 donne le schéma synoptique du système selon l'invention, comportant deux moteurs électriques d'entraînement de deux pompes hydrauliques.
The invention will be better understood, and other objects, features, details and advantages thereof will appear more clearly in the explanatory description which follows, with reference to the appended schematic drawings given solely by way of example illustrating two modes of embodiment of the invention and in which:
  • the figure 1 is a perspective view of a first embodiment of an electro-pump system according to the invention;
  • the figure 2 is a side view of the system shown on the figure 1 ,
  • the figure 3 is a perspective view of the suction manifold indicated in A on the figure 1 of the system according to the invention, some parts of the pump module being represented additionally;
  • the figure 4 is a perspective view of the pump body B of the figure 1 , arranged on the suction module A;
  • the figure 5 is a perspective view of the discharge manifold indicated in C on the figure 1 ;
  • the figure 6 is a sectional view along the line VI-VI of the figure 2 ;
  • the figure 7 is a sectional view along line VII-VII of the figure 2 ;
  • the figure 8 is a sectional view along line VIII-VIII of the figure 2 ;
  • the figure 9 is a sectional view along the line IX-IX of the figure 2 ;
  • the figure 10 is a sectional view along line XX of the figure 2 ;
  • the figure 11 is a sectional view along the line XI-XI of the figure 2 ;
  • the figure 12 is a sectional view of the assembly formed by the pump body B and manifolds A and C in the assembled state along the line XII-XII of the figure 8 ;
  • the figure 13 is a sectional view of this set along line XIII-XIII of Figures 8 and 9 ;
  • the figure 14 is a sectional view of this same ensemble according to line XIV-XIV of figures 5 and 9 ;and
  • the figure 15 gives the block diagram of the system according to the invention, comprising two electric motors for driving two hydraulic pumps.

La figure 1 est la vue d'ensemble d'un groupe électro-pompe selon l'invention, qui comporte deux moteurs électriques et deux pompes hydrauliques, chacune entraînée par un des deux moteurs. Sur la figure 1, les références 1 et 2 désigne les deux moteurs électriques, la référence B le corps de pompe qui enferme deux pompes hydrauliques à engrenages, A le manifold d'entrée ou d'aspiration des pompes et C le manifold de sortie ou de refoulement. Comme le montre les figures, le corps de pompe B est monté en sandwich entre les manifolds d'entrée A et de sortie C. Ces pièces forment ainsi un bloc compact disposé entre les deux moteurs. Chaque moteur comporte une partie d'embase respectivement 4 et 5 qui porte les connexions électriques 6 des moteurs et renferme les circuits électriques.The figure 1 is the overview of an electric pump unit according to the invention, which comprises two electric motors and two hydraulic pumps, each driven by one of the two motors. On the figure 1 , references 1 and 2 designate the two electric motors, the reference B the pump body which encloses two hydraulic gear pumps, A manifold inlet or suction pumps and C the manifold outlet or discharge. As shown in the figures, the pump body B is sandwiched between the inlet manifolds A and outlet C. These parts thus form a compact block disposed between the two motors. Each motor has a base portion respectively 4 and 5 which carries the electrical connections 6 of the motors and encloses the electrical circuits.

La figure 15 donne le schéma synoptique du système selon la figure 1. On constate que le moteur 1 entraîne une première pompe désignée par la référence 8 et le deuxième le moteur 2 une seconde pompe 9. Les deux pompes 8 et 9 aspirent le fluide hydraulique dans un réservoir 10. Les voies de refoulement des deux pompes sont réunies au point de jonction 14 et alimentent ainsi en parallèle l'utilisateur en fluide hydraulique haute pression, en général en huile. Dans la voie de refoulement de chaque pompe en amont du point de jonction 14 est prévue un clapet anti-retour 12. Un limiteur de pression 11 et une soupape de réalimentation 13 sont montées en parallèle entre le point de jonction 14 et le réservoir.The figure 15 gives the synoptic diagram of the system according to the figure 1 . It can be seen that the engine 1 drives a first pump designated by the reference 8 and the second the engine 2 a second pump 9. The two pumps 8 and 9 draw the hydraulic fluid into a reservoir 10. The discharge paths of the two pumps are met at the junction point 14 and thus supply the user with high-pressure hydraulic fluid, generally in oil. In the discharge line of each pump upstream of the junction point 14 is provided a check valve 12. A pressure limiter 11 and a feed valve 13 are mounted in parallel between the junction point 14 and the reservoir.

En se reportant aux figures 3 à 11 on décrira ci-après la structure du corps de pompe B et des manifolds d'aspiration A et de refoulement C d'un mode de réalisation de l'invention.Referring to Figures 3 to 11 the structure of the pump body B and the suction manifolds A and discharge C of an embodiment of the invention will be described below.

La figure 3 illustre la structure du manifold d'aspiration A et montre également les pignons des trains d'engrenage des deux pompes 8 et 9, noté 15 pour la pompe 8 et 16 pour la pompe 9, les pignons étant montrés avec leurs paliers inférieur 17 et supérieur 18. La présentation du manifold ou support d'aspiration A est complétée par les deux vues en coupe 6 et 7 qui sont faites le long des lignes VI-VI et VII-VII indiquées sur la figure 2.The figure 3 illustrates the structure of the suction manifold A and also shows the gears of the gear trains of the two pumps 8 and 9, noted for the pump 8 and 16 for the pump 9, the gears being shown with their lower bearings 17 and higher 18. The presentation of the manifold or suction support A is supplemented by the two views in section 6 and 7 which are taken along the lines VI-VI and VII-VII indicated on the figure 2 .

Le manifold d'aspiration A comporte un canal d'aspiration 20 qui débouche à l'extérieur dans la face latérale 21. Ce canal 20 qui est rectiligne comme on le voit sur les figures 6 et 7 communique avec des cavités capacitives basse pression 23, 24 creusées dans le manifold à partir de la face interne 25 destinée à recevoir le corps de pompe B. Ce canal d'aspiration 20 est relié à un réservoir 10 selon la figure 19, extérieur au groupe électro-pompe.The suction manifold A has a suction channel 20 which opens out into the side face 21. This channel 20 which is straight as seen on the Figures 6 and 7 communicates with low pressure capacitive cavities 23, 24 dug in the manifold from the inner face 25 intended to receive the pump body B. This suction channel 20 is connected to a reservoir 10 according to Figure 19, outside the group electro-pump.

On constate que la cavité 23 à proximité des pignons 16 de la pompe 9 est plus large et plus profonde que la cavité 24 du côté de l'autre pompe, qui est réalisé sous forme d'une rainure arquée. La cavité 23 présente une zone intermédiaire à fond surélevé 23' qui délimite une cavité 26 de réception du ressort 27 du limiteur de pression 11 (figure 19). Le canal d'aspiration 20 débouche directement dans la cavité 23 et communique avec la cavité 24 par un canal vertical 28, c'est-à-dire perpendiculaire au plan de coupe. La figure 7 indique en outre en 30 des gorges dans lesquelles sont placées des garnitures d'étanchéité non représentées. La référence 25 désigne la face de pose du corps de pompe B.It can be seen that the cavity 23 near the pinions 16 of the pump 9 is wider and deeper than the cavity 24 on the side of the other pump, which is in the form of an arcuate groove. The cavity 23 has a raised bottom intermediate zone 23 'which delimits a cavity 26 for receiving the spring 27 of the pressure limiter 11 (FIG. 19). The suction channel 20 opens directly into the cavity 23 and communicates with the cavity 24 by a vertical channel 28, that is to say perpendicular to the section plane. The figure 7 further indicates at 30 grooves in which are placed unrepresented seals. The reference 25 designates the installation face of the pump body B.

Il ressort des figures 3, 6 et 7 que le fluide hydraulique, c'est-à-dire l'huile, après avoir été aspiré du réservoir remplit les cavités basse pression 23, 24 pour alimenter indépendamment les deux trains d'engrenage 15, 16 comme l'illustre la figure en perspective du corps de pompe B et les vues en coupe 8 et 9.It emerges figures 3 , 6 and 7 that the hydraulic fluid, that is to say the oil, after being sucked from the tank fills the low pressure cavities 23, 24 to independently feed the two gear trains 15, 16 as shown in the figure in perspective of the pump body B and the sectional views 8 and 9.

Les figures 4, 8 et 9 montrent que le corps de pompe B comporte une paroi de fond 32 qui repose sur la face de pose 25 du manifold d'aspiration A et sur laquelle s'élève une paroi extérieure d'enveloppe 33, et à l'intérieur de cette enveloppe des presqu'îlots 35, 36 qui délimitent des chambres 37, 38 de logement des trains d'engrenage 15, 16 et des paliers 17, 18, des parties en forme de pédoncules 39 de rattachement des presqu'îlots à la paroi d'enveloppe 33 configurés pour la réalisation de deux logements cylindriques 40, 41 des deux clapets anti-retour 12 (figure 15) ainsi que du logement 39 en alignement avec la cavité 26 pour la réception du limiteur de pression 11 (figure 19). La paroi d'enveloppe 33 comporte un bossage qui délimite une cavité 43 destinée à recevoir la soupape de réalimentation 13 (figure 15). Le restant de l'espace à l'intérieur de la paroi d'enveloppe 33 constitue un volume capacitif comportant quatre cavités 45, 46, 47, 48 séparées les unes des autres seulement par les parties en forme de pédoncule et deux étroites nervures 49 de rattachement des presqu'îlots à la paroi d'enveloppe. La face frontale et les surfaces des presqu'îlots, des pédoncules et des nervures constituent la face de pose 34 pour le manifold C.The figures 4 , 8 and 9 show that the pump body B has a bottom wall 32 which rests on the installation face 25 of the suction manifold A and on which rises an outer casing wall 33, and inside this casing there are presqu'Ilots 35, 36 which delimit chambers 37, 38 for housing the gear trains 15, 16 and bearings 17, 18, parts in the form of peduncles 39 for attaching the presqu'Ilots to the envelope wall 33 configured for producing two cylindrical housings 40, 41 of the two nonreturn valves 12 ( figure 15 ) and the housing 39 in alignment with the cavity 26 for receiving the pressure limiter 11 (Figure 19). The envelope wall 33 has a boss which delimits a cavity 43 intended to receive the feedback valve 13 ( figure 15 ). The remainder of the space inside the envelope wall 33 constitutes a capacitive volume comprising four cavities 45, 46, 47, 48 separated from each other only by the peduncle-shaped portions and two narrow ribs 49 of attachment of the penlets to the envelope wall. The front face and the surfaces of the presqu'Ilots, peduncles and ribs constitute the exposure face 34 for manifold C.

Les vues en coupe parallèles au plan du corps de pompe des figures 8 et 9 montrent les canaux d'entrée 50 et 51 des chambres 37 et 38 de logement des trains d'engrenage avec les paliers des deux pompes et les canaux de sortie 53 et 54. Comme on le voit sur la vue en coupe perpendiculaire au plan du corps B, de la figure 12, le canal d'entrée 51 communique avec la cavité basse pression 23 dans laquelle s'ouvre le canal d'aspiration 20. Le canal d'entrée 50 est connecté au canal d'aspiration 20 d'une manière correspondante, non représentée spécifiquement.The sectional views parallel to the plane of the pump body Figures 8 and 9 show the inlet channels 50 and 51 of the chambers 37 and 38 for housing the gear trains with the bearings of the two pumps and the outlet channels 53 and 54. As seen in the sectional view perpendicular to the plane of the body B, from figure 12 the inlet channel 51 communicates with the low pressure cavity 23 into which the suction channel 20 opens. The inlet channel 50 is connected to the suction channel 20 in a corresponding manner, not shown specifically.

La figure 12 montre également que le canal de sortie 54 communique avec le logement 41 d'un des deux clapets anti-retour 12, à travers l'orifice 52 du siège de la bille 55 du clapet. La bille 55 est repoussée sur son siège par un ressort de rappel 57 prenant appui à son autre extrémité sur un socle d'appui 58 en étant guidée par un élément en forme d'une tige 59 du clapet, disposé au centre du logement 41. Le canal de sortie 53 communique de la même manière avec le logement 40 de l'autre clapet anti-retour 12.The figure 12 also shows that the outlet channel 54 communicates with the housing 41 of one of the two check valves 12, through the orifice 52 of the seat of the ball 55 of the valve. The ball 55 is pushed back onto its seat by a return spring 57 resting at its other end on a bearing base 58 being guided by a member in the form of a rod 59 of the valve, disposed in the center of the housing 41. The outlet channel 53 communicates in the same way with the housing 40 of the other non-return valve 12.

La figure en perspective 5 et les vues en coupe des figures 10 et 11 illustrent la structure du manifold ou support de refoulement C.The perspective figure 5 and the sectional views of Figures 10 and 11 illustrate the structure of the manifold or pressure support C.

Le manifold de refoulement C comporte une paroi de fond 60 sur laquelle s'élève perpendiculairement une paroi extérieure d'enveloppe 61 qui enferme un volume capacitif commun 63. La face frontale 62 de cette paroi est destinée à venir en appui sur la face frontale de pose du corps de pompe 34. Le volume 63 entoure deux îlots 65, 66 de support des paliers supérieurs 18 des deux trains d'engrenage, ces îlots sont reliés l'un à l'autre par une barrette relativement mince 67 et, au niveau de cette barrette, à la paroi d'enveloppe 61 par une zone surélevée 68. De cette zone s'élève deux saillies circulaires 69 jusqu'au niveau du plan de pose du manifold. Ces zones 69 sont destinées à servir de surface d'appui, chacune à la base d'un socle 58 d'appui de ressort d'un clapet anti-retour 12. Celles-ci sont isolées si bien que ces portions et la zone surélevée 68 rétrécissent, mais n'empêchent pas que l'huile remplissant la cavité puisse passer par-dessus la zone 68 en s'écoulant autour des saillies 69. On constate encore en 70 des gorges dans la face libre des îlots 65, 66 pour la réception de joints de compensation à coeur qui entourent les zones de support des paliers 18 des trains d'engrenage, les parties 73 en creux étant remplies de l'huile basse pression de lubrification. A l'état assemblé du corps de pompe B et des manifolds A et C, les îlots 65 et 66 du manifold C sont en appui sur les presqu'îlots 35, 36 du corps de pompe B.The discharge manifold C comprises a bottom wall 60 on which is raised perpendicularly an outer casing wall 61 which encloses a common capacitive volume 63. The front face 62 of this wall is intended to bear on the front face of installation of the pump body 34. The volume 63 surrounds two islands 65, 66 for supporting the upper bearings 18 of the two gear trains, these islands are connected to each other by a relatively thin bar 67 and, at the of this bar, to the casing wall 61 by a raised area 68. This area has two circular projections 69 to the level of the laying plane of the manifold. These zones 69 are intended to serve as a bearing surface, each at the base of a base 58 of spring support of a nonreturn valve 12. These are isolated so that these portions and the raised area 68 shrink, but do not prevent the oil filling the cavity can pass over the area 68 by flowing around the projections 69. There are still 70 grooves in the free face of the islands 65, 66 for the receiving core compensating gaskets surrounding the bearing regions 18 of the gear trains, the recessed portions 73 being filled with the low pressure lubricating oil. In the assembled state of the pump body B and the manifolds A and C, the islands 65 and 66 of the manifold C rest on the presqu'Ilots 35, 36 of the pump body B.

En se reportant aux vues en coupe perpendiculaires, des figures 13 et 14, on constate que les cavités de logement 40, 41 du corps de pompe B communiquent avec le volume 63 du manifold de refoulement C, par des passages indiqués en 72 de part et d'autre et autour des saillies 69 d'appui des clapets anti-retour.Referring to perpendicular sectional views, figures 13 and 14 it is found that the housing cavities 40, 41 of the pump body B communicate with the volume 63 of the discharge manifold C, by passages indicated at 72 on either side and around the projections 69 for supporting the anti-backflow valves. -return.

La vue en coupe de la figure 10 montre que le volume capacitif 63 est en communication avec un canal de sortie haute pression 75 qui s'ouvre à l'extérieur dans la paroi latérale 76 du manifold de refoulement C. Sur la figure 5 l'ouverture vers l'extérieur du canal de sortie, c'est-à-dire de refoulement, n'est pas visible, mais on reconnaît au fond du volume 63 en 77 l'ouverture du canal 75 dans le volume 63.The sectional view of the figure 10 shows that the capacitive volume 63 is in communication with a high pressure outlet channel 75 which opens out into the side wall 76 of the discharge manifold C. On the figure 5 the opening towards the outside of the outlet channel, that is to say of repression, is not visible, but one recognizes at the bottom of the volume 63 in 77 the opening of the channel 75 in the volume 63.

Etant donné que le manifold de sortie de refoulement C vient, à l'état assemblé, par sa face supérieure 62 en appui sur la face supérieure 34 du corps de pompe B, les cavités 45, 46, 47 et 48 du corps B et le volume 63 du manifold de refoulement C constituent un seul volume rempli de l'huile haute pression refoulé par les pompes 8 et 9 par les canaux de refoulement 53 et 54 (figure 9) en passant par les clapets anti-retour 12 disposés dans les chambres 40, 41.Since the discharge outlet manifold C comes, in the assembled state, by its upper face 62 bearing on the upper face 34 of the pump body B, the cavities 45, 46, 47 and 48 of the body B and the volume 63 of the discharge manifold C constitute a single volume filled with the high-pressure oil discharged by the pumps 8 and 9 through the discharge channels 53 and 54 ( figure 9 ) through the check valves 12 arranged in the chambers 40, 41.

Concernant le limiteur de pression 11 (figure 15) il est placé dans la cavité 26 du manifold d'aspiration A (figures 3, 6, 7) et la cavité 39 du corps de pompe B (figures 4, 8, 9). Le fond de la cavité 26 est en communication avec l'espace d'aspiration basse pression 23, par un canal non représenté et la cavité 39 du corps de pompe B communique par un canal 75 visible aux figures 8 et 9 avec la cavité haute pression 48 et ainsi avec le canal de refoulement 75 par l'intermédiaire du volume 63 du manifold de refoulement C.Concerning the pressure limiter 11 ( figure 15 ) it is placed in the cavity 26 of the suction manifold A ( figures 3 , 6, 7 ) and the cavity 39 of the pump body B ( figures 4 , 8, 9 ). The bottom of the cavity 26 is in communication with the low pressure suction space 23, by a not shown channel and the cavity 39 of the pump body B communicates via a visible channel 75 Figures 8 and 9 with the high pressure cavity 48 and thus with the discharge channel 75 via the volume 63 of the discharge manifold C.

En ce qui concerne la soupape de réalimentation 13, elle est logée dans la cavité 43 du corps de pompe B (figures 4, 8, 9) qui communique, comme on le voit sur la figure 13, avec la rainure basse pression 24 du manifold d'aspiration A, d'une part, et, d'autre part, le volume 63 du manifold de refoulement C.Regarding the refilling valve 13, it is housed in the cavity 43 of the pump body B ( figures 4 , 8, 9 ) that communicates, as we see on the figure 13 with the low-pressure groove 24 of the suction manifold A on the one hand and the volume 63 of the discharge manifold C on the other hand.

Dans ce mode de réalisation, les deux moteurs 1 et 2 sont disposés de part et d'autre de l'ensemble formé par les deux pompes et comprenant les manifolds d'aspiration A et de refoulement C et, disposé en sandwich entre ces deux manifolds, le corps de pompe B. Sur la figure 3 on a représenté en 80 l'arbre d'entraînement du moteur 2, qui est destiné à passer à travers l'alésage 81 visible dans l'îlot 66 du manifold de refoulement C. Concernant l'entraînement du train d'engrenage 15 de la pompe 8, il est entraîné par le moteur 1 dont l'arbre =traversera alors la paroi de fond du manifold d'aspiration A.In this embodiment, the two motors 1 and 2 are arranged on either side of the assembly formed by the two pumps and comprising the suction manifolds A and discharge C and sandwiched between these two manifolds , the pump body B. On the figure 3 the driving shaft of the motor 2, which is intended to pass through the bore 81 visible in the island 66 of the delivery manifold C, is represented at 80. Concerning the drive of the gear train 15 of the pump 8, it is driven by the engine 1 whose shaft = will then cross the bottom wall of the suction manifold A.

Il ressort de la description de l'invention et des figures, que celle-ci résout le problème d'augmentation de la puissance d'un système électro-pompe tout en utilisant les technologies connues. L'invention consiste donc à utiliser deux moteurs qui sont pilotés pour pouvoir additionner les puissances disponibles des deux pompes. L'invention permet également en entraînant deux pompes différentes et non couplées d'augmenter la différence entre le débit minimum et maximum du groupe électro-pompe. Les pompes étant généralement limitées en débit minimum du fait qu'il est nécessaire de les faire fonctionner sous un régime minimum, l'utilisation de deux pompes et de deux moteurs permet lors de faibles demandes de débit, de ne faire fonctionner qu'un moteur et de diminuer la consommation de courant. Grâce à la présence d'un clapet anti-retour à la sortie des pompes, l'une des deux pompes peut être arrêtée. L'invention permet d'utiliser des moteurs largement utilisés en série et d'assurer une redondance entre les deux moteurs, ce qui permet d'éviter l'arrêt d'assistance à la conduite en cas de panne d'un des moteurs.It is apparent from the description of the invention and the figures, that it solves the problem of increasing the power of an electro-pump system while using the known technologies. The invention therefore consists in using two motors which are controlled to be able to add the available powers of the two pumps. The invention also makes it possible to drive two different and uncoupled pumps to increase the difference between the minimum and maximum flow of the electropump. Pumps are generally limited in minimum flow because it is necessary to operate them at a minimum speed, the use of two pumps and two motors allows during low flow requests, not operate a motor and reduce power consumption. Thanks to the presence of a non-return valve at the outlet of the pumps, one of the two pumps can be stopped. The invention makes it possible to use engines that are widely used in series and to provide redundancy between the two motors, which makes it possible to avoid stopping power assistance in the event of a failure of one of the engines.

Concernant le pilotage des moteurs, celui-ci est effectué à partir de consignes du véhicule que le groupe électro-pompe équipe. Le pilotage pourrait être assuré par un des deux moteurs qui piloterait alors la vitesse du second.Regarding the engine control, it is performed from the instructions of the vehicle that the electro-pump group team. The steering could be provided by one of the two engines which would then drive the speed of the second.

A l'avantage indiqué plus haut de la réduction du bruit et des pulsations hydrauliques grâce au grand volume de l'espace haute pression, s'ajoute que le bruit et les pulsations peuvent encore être réduits grâce à la coopération des deux pompes. En effet, chaque pompe génère des pulsations d'une fréquence égale au nombre de dents multiplié par la fréquence de rotation de la pompe. En faisant que les deux pompes tournent avec un calage de quelques degrés, il se produit une diminution des pulsations de pression, en même temps qu'une augmentation de la fréquence. Selon l'invention le pilotage moteur pourrait être effectué pour obtenir un fonctionnement des pompes en opposition de phase. On pourrait également piloter les moteurs à des vitesses différentes.To the advantage indicated above of the reduction of the noise and the hydraulic pulsations thanks to the large volume of the high-pressure space, is added that the noise and the pulsations can be further reduced thanks to the cooperation of the two pumps. Indeed, each pump generates pulsations of a frequency equal to the number of teeth multiplied by the rotation frequency of the pump. By making the two pumps turn with a setting of a few degrees, there is a decrease in the pressure pulsations, at the same time as an increase in the frequency. According to the invention the motor control could be carried out to obtain a functioning of the pumps in opposition of phase. We could also drive the engines at different speeds.

Il ressort de la description du mode de réalisation de l'invention, qui n'a été donné qu'à titre d'exemple, que l'invention permet, par une intégration des fonctions des deux pompes à un corps de pompe commun, de réduire l'encombrement du groupe, tout en prévoyant un volume haute pression commun important, qui apporte, malgré la présence de deux unités de pompe, une amélioration considérable de l'amortissement des pulsations produites par ces pompes.It emerges from the description of the embodiment of the invention, which has been given by way of example only, that the invention makes it possible, by integrating the functions of the two pumps into a common pump body, to reduce the size of the group, while providing a large common high pressure volume, which provides, despite the presence of two pump units, a considerable improvement in damping pulsations produced by these pumps.

Claims (9)

  1. An electric pump unit, of the type comprising two hydraulic pumps (8, 9), in particular gear pumps, and two electric motors (1, 2) driving the pumps, characterized in that the pumps (8, 9) are arranged so that the power of the unit can be obtained by adding the powers of both motors, that both pumps (8, 9) are incorporated into a shared pump body (B) and that the electric pump unit comprises a delivery manifold (C, 3) provided with a delivery channel (75) shared by both pumps (8, 9), and a suction manifold (A) comprising a suction channel (20) shared by both pumps, and in that the pump body (B) is sandwiched between the suction manifold (A) and the delivery manifold (C), each manifold carrying on the external face thereof one of the two motors.
  2. The electric pump unit according to claim 1, characterized in that the pump body (B) comprises within an exterior casing wall (33) a high pressure volume shared by both pumps and communicating with the compressed air chamber of both pumps, and a shared high pressure volume provided in the delivery manifold (C) and communicating with the shared delivery channel (75).
  3. The electric pump unit according to any of claims 1 or 2, characterized in that at least one of the pumps comprises, in the delivery path thereof, a check valve (12) so that this pump can be stopped selectively.
  4. The electric pump unit according to any of claims 1 to 3, characterized in that it comprises a device for driving the motors (1, 2), adapted to ensure driving of one motor externally, and in that this motor drives the speed of the other one.
  5. The electric pump unit according to any of claims 1 to 4, characterized in that both motors are running in the same direction or in opposite directions.
  6. The electric pump unit according to any of claims 1 to 5, characterized in that both pumps (8, 9) are adapted for running with an angular offset of several degrees in order to provide a decrease of pressure pulsations generated by the electric pump unit.
  7. The electric pump unit according to any of claims 1 to 6, characterized in that both pumps (8, 9) can operate in phase opposition.
  8. The electric pump unit according to any of claims 1 to 7, characterized in that the pumps operate at different rotational speeds.
  9. The electric pump unit according to any of claims 1 to 8, characterized in that the availability of two motors (1, 2) is a safety measure by redundancy.
EP06291732A 2005-11-08 2006-11-07 Electric pump unit Active EP1783371B1 (en)

Applications Claiming Priority (1)

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FR0511333A FR2893092B1 (en) 2005-11-08 2005-11-08 ELECTRO-PUMP GROUP, OF THE TYPE COMPRISING AT LEAST ONE HYDRAULIC PUMP, IN PARTICULAR A GEAR, DRIVEN IN ROTATION BY A MOTOR DEVICE

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EP1783371B1 true EP1783371B1 (en) 2009-08-05

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Publication number Publication date
EP1783371A1 (en) 2007-05-09
US7942649B2 (en) 2011-05-17
FR2893092A1 (en) 2007-05-11
US20070122298A1 (en) 2007-05-31
FR2893092B1 (en) 2008-10-10
DE602006008244D1 (en) 2009-09-17

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