EP1072791B1 - Radialkolbenmotor mit einer einzigen Koppelauswahlvorrichtung - Google Patents

Radialkolbenmotor mit einer einzigen Koppelauswahlvorrichtung Download PDF

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Publication number
EP1072791B1
EP1072791B1 EP20000401985 EP00401985A EP1072791B1 EP 1072791 B1 EP1072791 B1 EP 1072791B1 EP 20000401985 EP20000401985 EP 20000401985 EP 00401985 A EP00401985 A EP 00401985A EP 1072791 B1 EP1072791 B1 EP 1072791B1
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EP
European Patent Office
Prior art keywords
cylinder
selector
cylinders
ducts
group
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP20000401985
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English (en)
French (fr)
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EP1072791A3 (de
EP1072791A2 (de
Inventor
Louis Martin
Jean-Marie Rouillard
Jean-Pierre Souply
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Poclain Hydraulics Industrie
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Poclain Hydraulics Industrie
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Publication of EP1072791A2 publication Critical patent/EP1072791A2/de
Publication of EP1072791A3 publication Critical patent/EP1072791A3/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0447—Controlling
    • F03C1/045—Controlling by using a valve in a system with several pump or motor chambers, wherein the flow path through the chambers can be changed, e.g. series-parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0425—Disconnecting the pistons from the actuated cam

Definitions

  • An engine of this type is known from the document FR 2 710 111.
  • all cylinders are periodically supplied with fluid under pressure. he is known to suppress the periodic fluid supply of all the cylinders to make them inactive so the engine does not deliver no couple. It is also known to not delete the supply of fluid that some cylinders, the other cylinders continuing to be periodically supplied with fluid, so that the motor operates in partial displacement.
  • the invention applies equally well to an engine for which all the cylinders belong to the first group and are therefore likely to be rendered all inactive, only to an engine further comprising a second group of cylinders which continue to be active when the cylinders of the first group are rendered inactive.
  • FR 2 710 111 recommends the use of selection means which include a selector individual for each of the cylinders of the first group, this selector individual being controlled so that it can not be activated for disengage or engage the sliding piston in the cylinder to which it is associated only when the axis of this cylinder passes, during the relative rotation of the cylinder block and the cam, by a position in which it is near the top of a ripple of the cam.
  • the document FR 2 677 409 discloses a circuit hydraulic system for disengaging the pistons of an engine hydraulic.
  • This circuit includes a shuttle valve interposed on the conduits that connect the pump ports to the main ports power and exhaust of the engine.
  • This system is external, and it is reported on the engine, which increases its size.
  • the walkout applies indiscriminately to all engine pistons. Finally, the problems of shock during the disengagement and re-clutch are not avoided.
  • the present invention aims to propose a system simple, arranged inside the engine, to allow the disengagement pistons sliding in the cylinders of the first group, in substantially avoiding the shock phenomena of these pistons against the cam during the phases of disengagement and re-clutching pistons concerned, even at relatively fast rotational speeds high, for example of the order of 100 rpm and more.
  • the means of selection include a single clutch selector, integral with the cylinder block vis-à-vis the rotation around the axis of rotation and having a communication conduit for each cylinder of the first group of cylinders, this selector being susceptible to occupy a first position, corresponding to said first configuration, in which the communication conduits allow the connection of cylinder ducts of cylinders from the first group to the distribution ducts, a second position corresponding to said disengagement configuration and a interim transitional position between said first and second positions, in which the cylinder ducts of the cylinders of the first group are interconnected by an isolated enclosure.
  • the ducts of cylinder cylinders of the first group are normally connected to the distribution ducts and are therefore alternately connected to the fluid supply and exhaust, so that the pistons sliding in these cylinders are active.
  • the cylinder ducts of cylinders of the first group are all connected to the fluid discharge, so that the pistons sliding in these cylinders are inactive and can be returned to said cylinders, that is, they are disengaged.
  • the enclosure of fluid discharge is just a part of the space inside of the engine that is connected to a return duct of leaks.
  • the cylinder of the first group cylinders are all interconnected by an isolated enclosure.
  • isolated enclosure it is necessary to understand a part of the inner space of the engine casing which is isolated from different "functional" ducts of the motor, ie the ducts which are connected to a pipe external to the engine, such as a supply or exhaust pipe, or a pipe auxiliary, connected to the engine charging circuit to ensure an auxiliary function of this motor (brake control .).
  • the isolated enclosure is not connected to the power supply, neither the exhaust nor any auxiliary pressure outside the engine.
  • the pistons of the cylinders of the first group can move in their respective cylinders according to their positions on the cam. In other words, they do not do not get stuck in a given position inside their cylinders, but they can follow the ripples of the cam, the volumes of fluid displaced by the reentry movement of some pistons offsetting the volumes of fluid displaced by the output movement of other pistons, the engine being CV.
  • the invention makes it possible to avoid a putting in direct communication the fluid discharge chamber with the engine power supply or exhaust, which would be detrimental to smooth operation of the latter.
  • the cylinder ducts of the cylinders of the first group are not isolated from each other, which avoids blocking pistons sliding in these cylinders.
  • the disengagement selector is formed by a slide slidably mounted in a bore of the cylinder block, the communication conduits comprising grooves of communication formed on the surface of this drawer.
  • the conduits of cylinders of the first group then have openings which are open in said bore of the cylinder block and which are each permanently connected to a groove of communication; the bore of the cylinder block has a throat intercommunication system to which the communication grooves are connected in the transient position of the selector.
  • the communication grooves are arranged axially or substantially axially to the surface of the drawer. Their machining is so extremely simple. In the first position of the selector, these communication grooves make it possible to connect the conduits of cylinders of the first group cylinders with the ducts of distribution, so that the pistons of the cylinders of the first group are active. By an axial displacement of the selector towards its second position, this connection of the cylinder ducts cylinders of the first group with the distribution ducts ceases, and the communication grooves are all connected to the throat intercommunication of the cylinder block.
  • the assembly formed by the cylinder ducts cylinders of the first group, the communication grooves and the intercommunication groove constitutes the isolated enclosure through which the cylinder ducts of the cylinders of the first group communicate with each other in the transient position of the selector.
  • the motor it is advantageous for the motor to present for each cylinder duct of the cylinders of the first group, a distribution passage formed by a conduit which presents a first open port in the bore of the cylinder block and a second port open on a communication face of the cylinder block to be connected to the distribution ducts during the relative rotation of the cylinder block and distributor and, for each cylinder duct cylinders of the first group, the first orifice of the duct forming the dispensing passage, the orifice of the cylinder duct and the intercommunication groove are successively arranged in the bore of the cylinder block in the direction of movement of the drawer of the selector from his first to his second position.
  • the passage of communication is permanently connected to the face of cylinder block communication and is therefore likely to be alternately connected to each of the distribution ducts.
  • the communication groove realizes, for each conduit of cylinder cylinder of the first group, the communication between the cylinder duct and this dispensing passage, this in the first position of the selector. When this selector is moved in its second position, the communication between the passage of distribution and the cylinder duct stops, while said duct cylinder is connected to the intercommunication groove, always by the communication groove.
  • the engine comprises means for controlling the movement of the selector which comprise elastic return means capable of soliciting permanently said selector towards one of its first and second positions and means of counter-effort likely to be controlled to solicit the movement of the selector towards the other of his first and second positions.
  • the elastic return means seek the selector to its first position and the means of counter-force comprise a control piston cooperating with a control cylinder integral with a stator portion of the motor, said control piston being able to be moved to against the return force of said return means for push the selector towards its second position.
  • control piston cooperates with the selector via spherical stop means, or well by means of rolling means, or else by via hydrostatic stop means using a fluid confined.
  • the control cylinder is integral with a part of stator of the motor, while the selector is integral in rotation with the cylinder block. Therefore, the part of the selector with which cooperates the control piston rotates relative to the cylinder of ordered.
  • the choice of spherical stop means, means of bearing or means of hydrostatic abutment makes it possible to avoid a premature wear of parts in relative rotation.
  • This zone is preferably aligned with the axis of rotation of the engine, the bore of the cylinder block in which is disposed the disengagement selector, as well as the control cylinder, preferably being centered on the motor axis. So the speed between the fixed part and the rotating part is small, so that at most a very weak couple is generated in this zone. he as a result of which the friction, and therefore the heating of the parts in contact are limited.
  • the means of counter-effort include a control chamber arranged between the selector and a reference piece fixed relative to the cylinder block, as well as a control line suitable for connecting said control chamber to a source of fluid.
  • the elastic return means seek the selector to its second position and that the means of counter-effort are likely to be ordered to solicit the selector to its first position.
  • the disengagement configuration is obtained at rest, by the elastic return means.
  • This is advantageous example when the engine is used to drive a vehicle.
  • a failure in the control of the means of counter-effort happens while the vehicle is traveling in configuration engaged pistons (thus at low speed and high engine torque)
  • this failure puts the selector in the configuration of disengagement, which decreases the displacement and therefore the engine torque.
  • the driver can then easily control the speed in controlling the flow of the pump.
  • This variant is also advantageous in the case of a hydraulic motor equipped with a parking brake and safety.
  • the braking torque needed to avoid a accidental drive of the engine and the vehicle that it equips must simply be able to overcome the couple developed by the motor in its disengagement configuration (so small displacement), which is that of rest.
  • This braking torque is lower to that which would be necessary if the rest position of the selector was its first position (in which the pistons are engaged), this which allows to choose a brake less bulky and less expensive.
  • a chamber of decompression is provided at the end of the selector located downstream side of the latter in the direction of his moving his first in its second position, and in the second position of that selector, the cylinder ducts are connected to this chamber.
  • the decompression chamber When changing the selector from its first position in its second position, the decompression chamber is powered by the fluid that is in the cylinder ducts of the cylinders of the first group.
  • the decompression chamber is thus “put in “pressure”, which opposes a resistance force to the continuation of movement of the selector to its second position. In other words, moving the selector between its position transient and its second position is slowed down, so that the declutching takes place smoothly.
  • This decompression chamber is advantageously communication with a return line of leaks, connected to a tank without pressure.
  • This communication takes place advantageously via at least one passage of low section, which causes, between the room of decompression and driving back leaks, a loss of load which prevents the selector from moving too fast from his first position to his second position.
  • passage section of the passage (s) of small section determines the pressure drop between the chamber of decompression and fluid return pipe, which conditions the speed of movement of the selector between its transient position and his second position.
  • the invention can be applied to the motors of which it is desired all pistons are disengageable. It can also apply to engines having two or more separate displacements operating system which we wish to disengage only pistons cylinders that are inactive in small displacement (s).
  • the cylinder block presents a second group of cylinders arranged radially relative to the axis of rotation, each cylinder of this second group being connected to a cylinder duct that is directly connected to a face of communication of the cylinder block cooperating with a face of distribution of the distributor, in order to be connected to distribution during the relative rotation of the cylinder block and the distributor, regardless of the position of the selector.
  • Figure 1 shows a hydraulic piston engine radial, with fixed housing.
  • the housing has several parts, know a first part 1A, called distribution cover, a part 1B whose inner periphery is corrugated so as to forming a reaction cam, and a portion 1C. These different parts are assembled by screws 2.
  • the corrugated cam is itself made in two parts, 4A and 4B, juxtaposed axially.
  • the engine comprises a cylinder block 6 which is rotatably mounted relative to an axis of rotation 10 with respect to the cam and which has a plurality of radial cylinders inside which are sliding mounted radial pistons.
  • the axes 13A of the cylinders 12A (axes arranged radially with respect to the axis of rotation 10) define a first radial plane PA, while the axes 13B of the cylinders of the second group 12B define a second radial plane PB distinct from the plane PA.
  • the pistons 14A which slide in the cylinders 12A of the first group cooperate with the first part 4A of the cam, while the pistons 14B which slide in the cylinders 12B of the second group cooperate with the second part 4B of the cam.
  • the cylinder block 6 rotates a shaft 5 which cooperates with him by grooves 7.
  • the end of the shaft 5 opposite the distributor cover 1A carries an outlet flange 9.
  • the shaft 5 is supported relative to the part 1C of the housing by bearing means, for example 8A tapered roller bearings and 8B.
  • the engine still has an internal distributor of fluid 16 which, by a system with pawns and notches 17, is rendered integral in rotation of the dispensing cover 1A.
  • the distributor 16 has an external axial face 18 staged, cooperating with an internal axial face 19 staged from distribution cover 1A. Between faces 18 and 19, are three grooves respectively designated by the references 20, 21 and 22.
  • the engine still has two main ducts, know a main supply line and a main line exhaust. These main ducts are not found in the sectional plan of Figure 1 but, for ease of understanding, indicated their positions by broken lines. So the first main duct 24 is permanently connected to the first groove 20, while the second main conduit 26 is permanently connected at the third throat 22. As will be seen later, the second groove 21 may, depending on the position of a displacement selector not shown in FIG. 1, be connected to one or other of the grooves 20 and 22.
  • the invention also applies to an engine having, as the only group of cylinders, the group 12A, and also to a engine for which only two distribution grooves, respectively permanently connected to each of the ducts are provided between the distributor and the distribution cover.
  • Distribution ducts are practiced in the distributor and open into a radial distribution face 28 of the latter, in support against a radial face of communication 30 of the cylinder block. Distribution ducts connect selectively the grooves 20, 21 and 22 at the distribution face. In the example shown, only a dispensing duct 31 has been shown which connects the groove 21 to the distribution face 28, and a conduit of distribution 32 which connects the groove 22 to the distribution face.
  • Each cylinder is associated with a cylinder duct, which connects it to the communication face 30 of the cylinder block, in order to put it in communication alternately with each of the conduits of distribution during the relative rotation of the cylinder block by compared to the cam.
  • a cylinder duct 15B directly puts this cylinder into communication with the communication face 30.
  • the communication of the 15A cylinder ducts with the communication face 30 takes place via a disengagement selector 34.
  • the selector 34 is formed by an axially movable drawer in a central bore 36 of the cylinder block.
  • the selector is integral with the cylinder block with respect to the rotation about the axis 10. It has in fact a flange portion 34 'provided with holes through which the screw rods pass 38. These rods have, each, a threaded end portion 39A screwed into a tapping of the cylinder block, and a smooth intermediate portion 39B, with which cooperates the drilling of the flange 34 'in which the rod is engaged considered.
  • the selector 34 can slide relative to the screws 38.
  • the outer cylindrical face 34A of the cooperating selector 34 with the bore 36 of the cylinder block has as many ducts of communication in the form of grooves 40 that the first group of cylinders comprises cylinders, each groove 40 being associated with a cylinder duct 15A.
  • Each cylinder duct 15A comprises one end connected to the cylinder 12A and another end forming an orifice 15'A which is open in the bore 36 of the cylinder block. This orifice 15'A is in permanent communication with the groove of communication 40 associated with the cylinder duct 15A considered.
  • Each cylinder duct 15A is associated with a passage of distribution formed by a duct 42 which presents a first port 42A open in the bore 36 of the cylinder block and a second port 42B open on the communication face 30 of the cylinder block. As can be seen in Figure 1, this allows connect the distribution passage 42 to the distribution ducts such as conduit 32.
  • the cylinder duct 15A and the dispensing passage 42 both open in bore 36 and, as can be seen in FIG. 1, this makes it possible to communicate the conduit of 15A cylinder with distribution ducts when selector 34 occupies his first position.
  • the whole formed by the duct 15A, the communication groove 40 and the passage of distribution 42 forms a substantially U-shaped duct, connected to the face of communication 30 of the cylinder block.
  • the communication groove 40 extends substantially axially and its length is sufficient to connect the orifices 15'A and 42A in the first position of the selector.
  • the end of the dispensing passage 42 located on the side of the cylinder 12A is closed by a plug 42C.
  • An annular intercommunication groove 44 is made in the bore 36 of the cylinder block 6. Depending on the displacement of the selector, this groove 44 can be put into communication with the communication grooves 40. Indeed, considered in the sense moving the selector from its first position to its second position, the orifice 42A, the orifice 15'A and the groove 44 are arranged one after another.
  • this seal is placed in a groove in the bore 36. It aims to prevent leakage that may occur between communication grooves 40 and an engine space 80 which, as will be seen in the following, is connected to a conduct of return of leaks 48.
  • the motor of FIG. 1 further comprises a system of braking 100 comprising two sets of brake disks respectively integral with the rotor and the stator, and a device brake piston 102 controlled between a configuration of braking, in which he presses the discs against each other others, and a brake release configuration.
  • a system of braking 100 comprising two sets of brake disks respectively integral with the rotor and the stator, and a device brake piston 102 controlled between a configuration of braking, in which he presses the discs against each other others, and a brake release configuration.
  • FIG. 2A shows, in partial axial section, the slide of the selector 34 in its first position, ports 15'A and 42A of the cylinder duct 15A and distribution passage 42 considered being interconnected by the communication groove 40.
  • Figure 3A shows, in strong lines, a part of the developed of the bore 36 and, in fine lines, a corresponding part of the development of the outer cylindrical face 34A of the drawer 34.
  • the orifice 15'A of cylinder duct 15A and the first port 42A of the passage of distribution 42 we also see the position of the intercommunication groove 44.
  • Communication grooves 40 respectively associated with each of the cylinder ducts taken into account on the Figure 3A are shown in fine lines.
  • the orifices 15'A and 42A communicate with the communication groove 40, but are isolated from the throat 44. Communication between the passage of distribution 42 and the communication groove 40 is then ensured by a maximum section S1.
  • FIGS. 2B and 3B the drawer 34 has begun moving to his second position.
  • the orifice 42A of the distribution passage 42 does not communicate with the communication groove 40 only by a weaker section S1 while the communication groove 40 starts to communicate with the groove 44 by a section S2.
  • cylinders of the first group continue to be connected to dispenser distribution, but only through section S1. By therefore, the pistons of these cylinders only contribute weakly to the engine torque.
  • this compression chamber constitutes an advantageous variant, but which must also be provided, in the second position of the selector, to communicate directly the communication grooves 40 with a conduit of return of leaks or, in general, with an enclosure of fluid discharge.
  • the graph in Figure 4 shows the evolution of the sections S1, S2 and S3 during the movement of the drawer 34 from its first position (displacement 0) to its second position (X displacement). It can be seen that the passage section S1 decreases regularly until it becomes zero for an X2 move. The section S2 has begun to take a non-zero value from a displacement X1 less than the displacement X2.
  • the Figures 2B and 3B correspond to a displacement value intermediate between the values X1 and X2. Then, when the continuous displacement, section S2 continues to increase, and the section S3 begins to take a non-zero value from a displacement X3 greater than displacement X2.
  • the minimum distance d (see Figure 3A), measured in the direction of movement of the selector 34, between the first orifice 42A of the duct forming the dispensing passage 42 associated with a given cylinder duct 15A and the intercommunication throat 44 is less than the length L of the communication groove 40 associated with this cylinder duct. This allows to obtain the situation Figures 2B and 3B.
  • the 15A cylinder ducts are therefore, possibly by via the decompression chamber 46, connected to a fluid discharge chamber. Therefore, the pistons of cylinders of the first group cease to be solicited in the tending to move them away from the axis of rotation 10 of the motor. This last on the contrary, provides means for, in this situation, to return these pistons in their respective cylinders, that is to say for the bring back to the axis of rotation 10. At this moment, the pistons are disengaged and stop cooperating with the cam.
  • the disengaged pistons do not tend to come out of their cylinders to come into contact with the hollows of the cam, it is expected advantageously of having some pressure in the region 50 of the interior space of the engine in which is located the cam 4A. It is known to connect said interior space to a conduit for returning leaks such as conduit 48.
  • the invention provides for not allowing this connection only through a calibrated check valve 52 located in a connecting line between the space 50 and the return duct 48.
  • control means of the moving the selector 34 between its first and second position The selector 34 is disposed in the bore 36 of the cylinder block and it is preferably coaxial with the axis of rotation 10.
  • means for controlling its movement include resilient return means such as a spring 54 able to solicit Permanently selector 34 to its first position.
  • this spring 54 is supported, on the one hand, on the radial face 5A of the shaft 5 which is located on the side of the distributor 16 and, on the other hand, on a radial surface 34C of the drawer 34 opposite to said radial face 5A.
  • the spring 54 is partially housed in a central recess 56 of the drawer 34, of which an end portion forms said surface 34C.
  • the means for controlling the movement of the selector 34 further comprise a control piston 58 cooperating with a control cylinder 60 integral with a stator portion of the motor, in this case the distribution cover 1A.
  • the cylinder 60 is formed in the stator of the engine, and the piston 58 is also fixed with respect to the rotation about the axis 10.
  • the selector 34 is integral in rotation with the cylinder block.
  • the contact between the piston 58 and the selector 34 is operated by surfaces in relative rotation. It should be noted that these surfaces do not under high stresses only when, under the action of the piston 58, the selector is moved to its second position.
  • FIGS. 5A to 5B show various variants of realization of the zones in contact with the selector piston, of a nature to limit the premature wear that might result from this relative rotation.
  • the active head 58A of the piston 58 that is to say the part of this piston which cooperates with the selector 34, is equipped with a spherical stop means.
  • a ball 59 set in a recess 59A practiced at the end of the piston.
  • this ball cooperates directly with the radial face 34'A of the selector that faces him.
  • the ball 59 may be replaced by a screw or the like whose head has a surface constituting a sphere portion.
  • the spherical surface is formed on the face 34'A of the selector.
  • control piston 58 ' has a active head 58'A which is connected to the body of this piston by rolling means 70.
  • the head 58'A cooperates with the selector 34 via a piece of contact 72 formed for example by the head of a screw screwed into this selector 34.
  • the head 58'A and this piece 72 may have a hardness superior to that of other parts and / or a clean coating to limit friction.
  • the control piston 58 "cooperates with the selector 34 via hydrostatic abutment using a confined fluid.
  • the active head 58 "A of the hollow piston 58" is formed by an additional piece, held in position by relative to the piston by the fluid pressure prevailing in a chamber Hydrostatic stop 74.
  • This chamber is connected to the control chamber 62 mentioned above by a passage having a restriction 76 made at the end of the hollow piston 58 "which is opposed to the head 58 "A and by a bore 79 made in the head 58 "To which connects the enclosure 74 to the recess of the piston 58".
  • the head 58 "A cooperates with the selector 34 by via an additional contact piece 72 'fixed to said selector.
  • the decompression chamber 46 is provided in the end 34B of the selector which is on the downstream side of the latter in the direction of his moving from his first position to his second position. This room is thus arranged between the selector 34, the cylinder block 6 and the shaft 5A, the connections between these parts being made substantially watertight. In the second selector position 34, cylinder ducts 15'A cylinders of the first group are connected to this chamber of decompression.
  • the communication grooves 40 are in communication with the chamber 46 in the second selector position. So, when, during the shift of the selector from its first position to its second position, the cylinder ducts 15'A start to be connected to room 46, it is fed by the fluid contained in these ducts. Therefore, the fluid pressure in the chamber 46 increases, and this pressure opposes, to the control of the displacement operated by the piston 58, a antagonistic hydraulic force. Thus, from this implementation communication between the ducts 15'A and the chamber 46, the moving the selector 34 to its second position is slowed, so that section S3 increases very gradually, and that the pistons of the cylinders of the first group are disengaged "in softness ".
  • the decompression chamber 46 is in communication with the aforementioned leakage return line 48. advantageously, this communication is carried out through at least one passage of small section.
  • Passage of small section it is necessary understand a passage through which the flow of fluid is relatively small, so as to cause a difference in pressure (pressure drop) between the chamber 46 and the pipe of return of leaks 48.
  • the low section passage (s) are formed by holes 78 axially passing through the selector 34.
  • the ends of these holes are in the bearing area of the spring 54 on the bottom of the recess 56, they can be machined without particular precaution as to their section, and it is the presence of springs that decreases their section of passage.
  • the passages 78 open into a space 80 of the motor formed between the piston 58 and an internal bore 16A of the distributor, space 80 to which is connected the return line of leaks 48.
  • the decompression chamber 46 is in communication with the interior space 50 of the engine located under the reaction member 4A via a check valve 82 which allows only the fluid circulation in the direction of draining this bedroom.
  • a check valve 82 which allows only the fluid circulation in the direction of draining this bedroom.
  • the leak return duct 48 has a first section 48A which is connected to the space 80, and therefore, through passages 78, to the chamber of decompression 46, a second section 48B in which is located the non-return valve 82, a third section 48C in which found the calibrated flap 52 which when pressure in space 50 is greater than its calibration pressure, allows fluid circulation only in the direction from space 50 to line 48.
  • the engine comprises the cylinders 12B belonging to a second group, cylinders in which pistons 14B slide.
  • the conduits of cylinder 15B of these cylinders 14B open in the face of communication 30 of the cylinder block 6 to be alternately put in communication with the distribution ducts such as ducts 31 and 32, during the relative rotation of the cylinder block and of the distributor.
  • FIG. engine has a cylinder capacity selection device separate from the selector 34.
  • This device is located in the distribution cover 1A, in the zone Z indicated in FIG. 1, but it is not shown in Figure 1 to the extent that it is not in the cutting plane of this figure.
  • this selection device the cubic capacity does not cooperate with the cylinder ducts, but with the distribution grooves 20, 21 and 22. It has in effect a axial bore 88 in which are performed three grooves 90, 91 and 92 who are respectively in permanent communication with each of the three distribution grooves 20, 21 and 22.
  • a drawer 94 is movable within this bore 88 and has a groove or analogous 96. In a first position of the drawer, the throat 96 is communicate throats 90 and 91 (so it is also communicate between them the throats 20 and 21) while, in the second position of the drawer, its throat 96 communicates the throats 91 and 92 (and thus the throats 21 and 22).
  • the distribution ducts are divided into three groups respectively connected to each of three grooves 20, 21 and 22.
  • the number of conduits in the third group, which are connected to throat 22 is equal to the sum of the number of ducts of the first group and the number of ducts of the second group.
  • the first position of the drawer 94 shown in FIG. 6 is a position of large displacement, in which the ducts of the first and second groups are connected to the duct 24 and isolated from the ducts of the third group, while the ducts of the third group are connected to the main duct 26 and isolated from those of the other two groups.
  • the cylinder ducts 15B and the ends 42B of the distribution passages 42 pass alternatively opposite a distribution pipe belonging to the third group and next to a distribution pipe belonging to one of the first and second groups.
  • the pistons of the cylinders of the first group are disengaged.
  • the holes of the cylinder ducts 15B cylinders of the second group continue to be put alternatively in communication with a distribution conduit connected to the power supply and then with a distribution duct connected to the fluid escapement, so that all cylinder pistons of the second group are active.
  • the engine then works with a partial displacement, equal to the cylinder capacity of the cylinders of the second group.
  • the groove 90 In the second position of the drawer 94, the groove 90 is isolated, while the gorges 91 and 92 communicate with each other. Thus, among the distribution ducts, only those of the first group that are connected to the groove 20 continue to be connected to the 24.
  • the distribution ducts of the second and third groups are all connected to driving principal 26, by putting in communication grooves 91 and 92. Therefore, only the cam lobes that correspond to the distribution ducts 20 of the first group are active, since the pistons which, at a given moment, cooperate with these cam lobes are alternately connected to a distribution duct of the first group connected to the groove 20, then to a distribution duct of the second to third groups that is connected to the main conduit 26.
  • the motor has four separate operating cylinders.
  • the drawer 94 is controlled between its two positions by control means comprising a control chamber 98 capable of being connected to a control conduit through an orifice 100, and a spring 102 of antagonistic effect to that of the increase volume of the room.
  • control means comprising a control chamber 98 capable of being connected to a control conduit through an orifice 100, and a spring 102 of antagonistic effect to that of the increase volume of the room.
  • the chamber 98 is delimited by a closure washer 104 reported in bore 88.
  • the engine according to the invention may comprise a tachometer 106 comprising a sensor 108 which counts the number of passages, the right of its end, of 110 marks made at regular intervals on the radial face of the cylinder block located on the side of the distribution cover 1A.
  • Figure 7 also shows a device for selecting the displacement, which is distinct from the clutch disengagement switch and which comprises a slide 124 movable inside a bore 118. drawer is shown in each of its two positions, respectively on either side of the axis A118 of this bore.
  • the distribution ducts are divided into four groups, respectively connected to each of the four grooves 120 to 123 of the distributor 116, themselves respectively in permanent communication with each of the four grooves 130 to 133 of bore 118.
  • Drawer 124 presents two throats 125 and 126 which, according to its position, communication or isolate the grooves 130 to 133 and thus the conduits of distribution.
  • the grooves 130 and 131 are interconnected and isolated grooves 132 and 133, themselves connected to each other.
  • the distribution ducts connected to the grooves 120 and 121 are connected to the same pressure (power or exhaust), while distribution connected to grooves 122 and 123 are at the other pressure main (exhaust or feed).
  • the grooves 130 and 133 are each isolated from the other grooves of the bore 118, while the throats 131 and 132 are connected.
  • Distribution ducts connected to 120 and 123 grooves are respectively placed at each of the two main pressures and correspond to an active displacement. In however, the distribution ducts connected to grooves 121 and 122 are at the same pressure and correspond to an inactive displacement.
  • the slide 124 has an internal bore 134 in which is arranged a shuttle 135. Holes 136 to 139 of the drawer communicate with this internal bore 134.
  • the shuttle 135 allows to order a communication of these holes 136 to 139 for, in small displacement, automatically connect the grooves 131 and 132 (and therefore the grooves 121 and 122 corresponding to an inactive displacement) to that of grooves 130 or 133 which contains the fluid at lower pressure.
  • the selector 234 may, depending on whether it occupies one or the other of its first and second positions, put the ducts of cylinder 15A in communication with the passages of communication 42 or isolate them from these passages.
  • the selector 234 is formed by a hollow drawer, inside which extends a rod 250 which, in this case, is centered on the axis 10 the engine on which is also centered the selector 234.
  • the rod 250 constitutes a "reference piece” which is fixed in translation by relative to the cylinder block 6.
  • a retaining flange 252 is fixed to the cylinder block 6 by screws 253 and the rod 250 crosses this flange and is wedged relative to it by a shoulder and an elastic locking ring.
  • the selector 234 is constantly recalled to its second position (visible below the axis 10) by a spring 254 which is supported on the flange 252. It is solicited towards its first position (visible above the axis 10) by means of counter-effort which include a controlled control chamber 262 between said selector 234 and the rod 250. More precisely, the rod carries a closure ring 264 at its opposite end to the flange 252 and the chamber 262 is formed between a recess 266 of the inner periphery of the selector 234, the rod 250 and the ring 264.
  • the selector movement control duct 234 includes a first section 268 which is formed in the stem 250 so as to debouch in room 262, and a second section 270 which is formed in a portion 1'A of the motor housing.
  • the sections 268 and 270 are connected by the arrangement of the rod 250 in correspondence with section 270 and are isolated from the rest of the motor by a seal 272 disposed between the tail 250A of the rod and the housing portion 1'A, against which this seal is maintained supported by a spring 274.
  • This seal is of the "rotary joint" type, providing a rotational seal between two rotating parts relative.
  • the decompression chamber 46 is connected to the space 280, which is provided between the flange 252 and the housing portion 1'A and to which is connected the leak return line 248.
  • the selector 234 comprises at least one axial bore 278 which connects the chamber 46 at the end of the selector located on the side of the flange 252 and the latter comprises at least one piercing or slot 282 which opens on space 280.
  • it is an axial slit 282 which cooperates with a key 284 to guide the displacement selector 234 between its two positions.
  • selectors 34 and 234 differ by the means of control of their movement. For the rest, their operation is analogous.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)

Claims (20)

  1. Hydraulikmotor, umfassend:
    einen Zylinderblock (6), der mindestens eine erste Gruppe von Zylindern (12A) umfaßt, die radial in bezug auf eine Drehachse (10) angeordnet ist, wobei jeder Zylinder (12A) mit einer Zylinderleitung verbunden ist und mit einem Kolben (14A) zusammenwirkt, der in diesem Zylinder gleiten kann,
    ein Reaktionselement (4A), das in relativer Drehung zu dem Zylinderblock (6) um die Drehachse (10) angeordnet ist,
    einen internen Fluidverteiler (16; 116), der mit dem Reaktionselement (4A) in bezug auf die Drehung um die Drehachse (10) fest verbunden ist und Verteilungsleitungen (31, 32) umfaßt, die mit den Zylinderleitungen verbunden werden können, um diese Leitungen mit Leitungen (24, 26) zur Zuund Ableitung des Fluids des Motors in Verbindung zu bringen,
    Auswahlmittel (34; 234), die in einer ersten Konfiguration den Anschluß der Zylinderleitungen (15A) der Zylinder (12A) der ersten Gruppe an die Verteilungsleitungen (31, 32) ermöglichen können, und die in einer zweiten Konfiguration, "Kolbenentkopplung" genannt, die Zylinderleitungen (15A) mit einem Fluidableitungsraum (46, 48) in Verbindung bringen können, wobei die Kolben (14A), die mit den Zylindern (12A) der ersten Gruppe zusammenwirken, in der genannten Entkopplungskonfiguration in die Zylinder zur Drehachse (10) zurückgeführt werden können,
    dadurch gekennzeichnet, daß die Auswahlmittel einen einzigen Entkopplungswähler (34; 234) umfassen, der bezüglich der Drehachse (10) drehfest mit dem Zylinderblock (6) verbunden ist und eine Verbindungsleitung (40; 240) für jeden Zylinder (12A) der ersten Gruppe von Zylindern umfaßt, wobei dieser Wähler eine erste Position, die der ersten Konfiguration entspricht und in der die Verbindungsleitungen (40; 240) den Anschluss der Zylinderleitungen (15A) der Zylinder (12A) der ersten Gruppe an die Verteilungsleitungen (31, 32) ermöglichen, eine zweite Position, die der Entkopplungskonfiguration entspricht, und eine Zwischenposition zwischen der ersten und der zweiten Position einnehmen kann, in der die Zylinderleitungen (15A) der Zylinder (12A) der ersten Gruppe miteinander durch einen getrennten Raum (15A, 40, 44; 15A, 240, 44) verbunden sind.
  2. Motor nach Anspruch 1, dadurch gekennzeichnet, daß der Entkopplungswähler von einem Schieber (34; 234) gebildet ist, der gleitend in einer Bohrung (36) des Zylinderblocks (6) befestigt ist, wobei die Verbindungsleitungen Verbindungsrillen (40; 240) umfassen, die auf der Oberfläche (34A) dieses Schiebers (34; 234) vorgesehen sind, und daß die Zylinderleitungen (15A) der Zylinder (12A) der ersten Gruppe Öffnungen (15'A) aufweisen, die in der Bohrung (36) des Zylinderblocks (6) offen sind und jeweils ständig an eine Verbindungsrille (40; 240) angeschlossen sind, und daß die Bohrung (36) des Zylinderblocks (6) eine Zwischenverbindungsnut (44) aufweist, mit der die Verbindungsrillen (40; 240) in der Zwischenposition des Entkopplungswählers (34; 234) verbunden sind.
  3. Motor nach Anspruch 2, dadurch gekennzeichnet, daß er für jede Zylinderleitung (15A) der Zylinder (12A) der ersten Gruppe einen Verteilungsdurchgang aufweist, der von einer Leitung (42) gebildet ist, die eine erste Öffnung (42A), die in der Bohrung (36) des Zylinderblocks (6) offen ist, und eine zweite Öffnung (42B) aufweist, die auf einer Verbindungsfläche (30) des Zylinderblocks (6) offen ist, um mit den Verteilungsleitungen (31, 32) während der relativen Drehung des Zylinderblocks (6) und des Verteilers (16) zueinander verbunden zu werden, und daß für jede Zylinderleitung (15A) der Zylinder der ersten Gruppe (12A) die erste Öffnung (42A) der den Verteilungsdurchgang (42) bildenden Leitung, die Öffnung (15'A) der Zylinderleitung (15A) und die Zwischenverbindungsnut (44) nacheinander in der Bohrung (36) des Zylinderblocks (6) in Verschieberichtung des Schiebers des Entkupplungswählers (34) von ihrer ersten in ihre zweite Position verstellt werden.
  4. Motor nach Anspruch 3, dadurch gekennzeichnet, daß für jede Zylinderleitung (15A) der Zylinder (12A) der ersten Gruppe der Minimalabstand (d), der in Verschieberichtung des Entkopplungswählers (34; 234) gemessen wird, zwischen der ersten Öffnung (42A) der den Verteilungsdurchgang (42) bildenden Leitung, die mit der Zylinderleitung (15A) verbunden ist, und der Zwischenverbindungsnut (44) kleiner als die Länge (L) der Verbindungsrille (40; 240) ist, die mit dieser Zylinderleitung (15A) verbunden ist.
  5. Motor nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß er Steuermittel für die Verschiebung des Entkopplungswählers (34; 234) zwischen seiner ersten und seiner zweiten Position umfaßt, wobei diese Steuermittel elastische Rückstellmittel (54; 254) umfassen, die den Wähler (34; 234) ständig in seine erste oder seine zweite Position bringen können, und Gegenbelastungsmittel (58, 58', 58", 60; 262, 268, 270) umfaßt, die derart gesteuert werden können, daß sie die Verschiebung des Wählers (34; 234) in die jeweils andere seiner ersten oder zweiten Position bewirken.
  6. Motor nach Anspruch 5, dadurch gekennzeichnet, daß die elastischen Rückstellmittel (54) den Wähler (34) in seine erste Position bringen, und daß die Gegenbelastungsmittel einen Steuerkolben (58, 58', 58'') umfassen, der mit einem Steuerzylinder (60) zusammenwirkt, der mit einem Teil (1A) eines Stators des Motors fest verbunden ist, wobei der Steuerkolben (58, 58', 58'') gegen die Rückstellkraft der Rückstellmittel (54) verschoben werden kann, um den Wähler in seine zweite Position zu bringen.
  7. Motor nach Anspruch 6, dadurch gekennzeichnet, daß der Steuerkolben (58) mit dem Entkopplungswähler (34) über kugelförmige Anschlagmittel (59) zusammenwirkt.
  8. Motor nach Anspruch 6, dadurch gekennzeichnet, daß der Steuerkolben (58') mit dem Entkopplungswähler (34) über Wälzlagermittel (70) zusammenwirkt.
  9. Motor nach Anspruch 6, dadurch gekennzeichnet, daß der Steuerkolben (58'') mit dem Entkopplungswähler (34) über hydrostatische Anschlagmittel (58''A, 74, 76, 79) zusammenwirkt, die ein eingeschlossenes Fluid verwenden.
  10. Motor nach Anspruch 5, dadurch gekennzeichnet, daß die Gegenbelastungsmittel eine Steuerkammer (262), die zwischen dem Wähler und einem festen Bezugsstück (250) in bezug auf den Zylinderblock (6) vorgesehen ist, und eine Steuerleitung (268, 270) umfassen, die die Steuerkammer an eine Fluidquelle anschließen kann.
  11. Motor nach Anspruch 5 oder 10, dadurch gekennzeichnet, daß die elastischen Rückstellmittel (254) den Wähler (234) in seine zweite Position bringen und daß die Gegenbelastungsmittel derart gesteuert werden können, daß sie den Wähler (234) in seine erste Position bringen.
  12. Motor nach Anspruch 10 oder den Ansprüchen 10 und 11, dadurch gekennzeichnet, daß die Steuerleitung (268, 270) einen ersten Abschnitt (268), der in dem Bezugsstück (250) vorgesehen ist, und einen zweiten Abschnitt (270) umfassen, der in einem Gehäuseteil (1'A) des Motors vorgesehen ist, wobei der erste und der zweite Abschnitt durch Drehdichtungsmittel (272) aneinander angeschlossen sind.
  13. Motor nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, daß eine Druckminderungskammer (46) am Ende (34B) des Entkopplungswählers (34) vorgesehen ist, die sich auf der stromabwärtigen Seite dieses letztgenannten in die Richtung seiner Verschiebung von seiner ersten in seine zweite Position befindet, und daß in der zweiten Position des Wählers (34) die Zylinderleitungen (15'A) der Zylinder der ersten Gruppe (12A) an diese Kammer (46) angeschlossen sind.
  14. Motor nach Anspruch 13, dadurch gekennzeichnet, daß die Druckminderungskammer (46) mit einer Leckagerückleitung (48), die mit einem drucklosen Behälter verbunden ist, in Verbindung steht.
  15. Motor nach Anspruch 14, dadurch gekennzeichnet, daß die Druckminderungskammer (46) mit der Leckagerückleitung (48) über mindestens einen Durchgang mit geringem Querschnitt (78) verbunden ist.
  16. Motor nach einem der Ansprüche 13 und 14, dadurch gekennzeichnet, daß die Druckminderungskammer (46) mit dem Innenraum (50) des Motors, der sich unter dem Reaktionselement (4A) befindet, über eine Rückschlagklappe (82) in Verbindung steht, die nur die Fluidzirkulation in die Richtung der Entleerung der Kammer (46) gestattet.
  17. Motor nach einem der Ansprüche 1 bis 16, dadurch gekennzeichnet, daß der Innenraum (50) des Motors, der sich unter dem Reaktionselement (4A) befindet, mit einer Leckagerückleitung (48) in Verbindung steht, die mit einem drucklosen Behälter über ein Rückschlagventil (52) verbunden ist.
  18. Motor nach einem der Ansprüche 1 bis 17, dadurch gekennzeichnet, daß der Zylinderblock (6) eine zweite Gruppe von Zylindern (12B) aufweist, die radial in bezug auf die Drehachse (10) angeordnet sind, wobei jeder Zylinder dieser zweiten Gruppe mit einer Zylinderleitung (15B) verbunden ist, die direkt mit einer Verbindungsfläche (30) des Zylinderblocks (6) verbunden ist, die mit einer Verteilungsfläche (28) des Verteilers (16) zusammenwirkt, um mit den Verteilungsleitungen (31, 32) während der relativen Drehung des Zylinderblocks (6) und des Verteilers (16) zueinander unabhängig von der Position des Entkopplungswählers (34) verbunden zu werden.
  19. Motor nach Anspruch 18, dadurch gekennzeichnet, daß die Achsen (13A) der Zylinder (12A) der ersten Zylindergruppe in einer ersten Radialebene (PA) enthalten sind, während die Achsen (13B) der Zylinder (12B) der zweiten Zylindergruppe in einer zweiten Radialebene ((PB), die sich von der ersten Ebene unterscheidet, enthalten sind.
  20. Motor nach einem der Ansprüche 1 bis 19, dadurch gekennzeichnet, daß er eine Auswahlvorrichtung (88, 94) für den Anschluss der Verteilungsleitungen (31, 32) an die Fluidzu- und -ableitungen (24, 26) umfaßt, wobei diese Vorrichtung mit dem Verteiler (16) zusammenwirkt und eine erste Konfiguration aufweist, in der alle Verteilungsleitungen aktiv sind, sowie eine zweite Konfiguration, in der gewisse Verteilungsleitungen inaktiv sind, so daß, wenn eine Zylinderleitung (15A, 15B) mit einer dieser Verteilungsleitungen in Verbindung steht, der Druck des Fluids in Zuleitungsrichtung und/oder in Ableitungsrichtung des mit der Zylinderleitung verbundenen Zylinders derart ist, daß die von dem Kolben dieses Zylinders während eines Zyklus verrichtete Arbeit gleich Null ist.
EP20000401985 1999-07-27 2000-07-10 Radialkolbenmotor mit einer einzigen Koppelauswahlvorrichtung Expired - Lifetime EP1072791B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9909714 1999-07-27
FR9909714A FR2796992B1 (fr) 1999-07-27 1999-07-27 Moteur hydraulique a pistons radiaux et a selecteur de debrayage unique

Publications (3)

Publication Number Publication Date
EP1072791A2 EP1072791A2 (de) 2001-01-31
EP1072791A3 EP1072791A3 (de) 2001-04-11
EP1072791B1 true EP1072791B1 (de) 2004-06-09

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US (1) US6347572B1 (de)
EP (1) EP1072791B1 (de)
JP (1) JP4657425B2 (de)
DE (1) DE60011352T2 (de)
FR (1) FR2796992B1 (de)

Families Citing this family (11)

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Publication number Priority date Publication date Assignee Title
FR2819024B1 (fr) * 2000-12-28 2003-08-15 Poclain Hydraulics Ind Dispositif de moteur hydraulique ayant un selecteur de cylindree et un systeme de freinage
FR2834012B1 (fr) 2001-12-24 2004-03-19 Poclain Hydraulics Ind Moteur hydraulique a pistons radiaux
FR2846381B1 (fr) * 2002-10-29 2005-01-28 Poclain Hydraulics Ind Mecanisme hydraulique ayant des cylindres a communications multiples
FR2891593B1 (fr) * 2005-10-03 2007-12-21 Poclain Hydraulics Ind Soc Par Dispositif de gestion de la cylindree d'un moteur hydraulique
WO2010052743A1 (en) * 2008-11-10 2010-05-14 S.A.I. Società Apparecchiature Idrauliche S.p.A. Hydraulic motor with radial cylinders provided with rotation speed detection
WO2013160145A2 (de) 2012-04-28 2013-10-31 Robert Bosch Gmbh Radialkolbenmotor mit bremse
US10344827B2 (en) * 2012-06-25 2019-07-09 Volvo Lastvagnar Ab Dual clutch transmission
US9175563B2 (en) 2012-07-18 2015-11-03 Eaton Corporation Combined motor and brake with rotating brake-release piston
WO2014014985A2 (en) * 2012-07-18 2014-01-23 Eaton Corporation Freewheel hydraulic motor
US20170363192A1 (en) * 2014-11-17 2017-12-21 Eaton Corporation Hydraulic device with sleeve insert
US10781816B2 (en) 2017-04-13 2020-09-22 Eaton Intelligent Power Limited Hydraulic motor brake

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GB1603116A (en) * 1977-04-29 1981-11-18 Massey Ferguson Services Nv Hydrostatic transmissions
FR2481755A1 (fr) * 1980-04-30 1981-11-06 Poclain Hydraulics Sa Moteur a fluide sous pression muni d'un dispositif de selection de sa vitesse de rotation
US4401182A (en) * 1980-12-10 1983-08-30 Sundstrand Corporation Variable displacement hydraulic drive with disconnect
US4461188A (en) * 1981-12-23 1984-07-24 Ford Motor Company Dual clutch multiple countershaft transmission
JP2716543B2 (ja) * 1989-09-18 1998-02-18 株式会社クボタ 車輌の走行駆動構造
FR2677409B1 (fr) * 1991-06-10 1993-10-15 Poclain Hydraulics Circuit hydraulique d'alimentation d'au moins un moteur hydraulique a pistons "debrayables".
FR2710111B1 (fr) * 1993-09-15 1995-12-01 Poclain Hydraulics Sa Moteur hydraulique muni d'un dispositif de sélection de sa cylindrée active.
FI104014B1 (fi) * 1994-05-18 1999-10-29 Valmet Voimansiirto Oy Radiaalimäntähydraulimoottori ja menetelmä radiaalihydraulimoottorin säätämiseksi

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DE60011352T2 (de) 2005-06-30
US6347572B1 (en) 2002-02-19
EP1072791A3 (de) 2001-04-11
JP2001107836A (ja) 2001-04-17
DE60011352D1 (de) 2004-07-15
FR2796992B1 (fr) 2001-10-19
EP1072791A2 (de) 2001-01-31
JP4657425B2 (ja) 2011-03-23
FR2796992A1 (fr) 2001-02-02

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