EP0524104B1 - Hydraulic motor with reciprocating differential piston - Google Patents

Hydraulic motor with reciprocating differential piston Download PDF

Info

Publication number
EP0524104B1
EP0524104B1 EP92402066A EP92402066A EP0524104B1 EP 0524104 B1 EP0524104 B1 EP 0524104B1 EP 92402066 A EP92402066 A EP 92402066A EP 92402066 A EP92402066 A EP 92402066A EP 0524104 B1 EP0524104 B1 EP 0524104B1
Authority
EP
European Patent Office
Prior art keywords
flap
chamber
fluid
moving assembly
exhaust
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
EP92402066A
Other languages
German (de)
French (fr)
Other versions
EP0524104A1 (en
Inventor
Philippe Cloup
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Civile De Recherche S A M Ste
Original Assignee
Civile De Recherche S A M Ste
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Civile De Recherche S A M Ste filed Critical Civile De Recherche S A M Ste
Publication of EP0524104A1 publication Critical patent/EP0524104A1/en
Application granted granted Critical
Publication of EP0524104B1 publication Critical patent/EP0524104B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L21/00—Use of working pistons or pistons-rods as fluid-distributing valves or as valve-supporting elements, e.g. in free-piston machines
    • F01L21/04—Valves arranged in or on piston or piston-rod
    • 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
    • F03C1/007—Reciprocating-piston liquid engines with single cylinder, double-acting piston
    • F03C1/0073—Reciprocating-piston liquid engines with single cylinder, double-acting piston one side of the double-acting piston being always under the influence of the liquid under pressure
    • F03C1/0076—Reciprocating-piston liquid engines with single cylinder, double-acting piston one side of the double-acting piston being always under the influence of the liquid under pressure the liquid under pressure being continuously delivered to one cylinder chamber through a valve in the piston for actuating the return stroke
    • 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
    • F03C1/08—Distributing valve-gear peculiar thereto
    • F03C1/10—Distributing valve-gear peculiar thereto actuated by piston or piston-rod
    • F03C1/12—Distributing valve-gear peculiar thereto actuated by piston or piston-rod mechanically

Definitions

  • the present invention relates to reciprocating hydraulic motors with differential piston which use the energy of the main fluid to generate their movement.
  • the basic principle of these engines is to transfer the inlet fluid, at pressure P1, into an intermediate chamber of variable volume, which, after closing the inlet valves and opening the exhaust valves, empties at the outlet in a fluid of the same flow rate but of pressure P2 lower than the pressure P1.
  • the overall energy used by these hydraulic motors is a function of the flow rate of the fluid and the difference between the pressures P1 and P2.
  • One of the very important constituent elements in this type of device is the assembly constituted by the inlet and exhaust valves and their control system.
  • the object of the present invention is to provide a simplified alternative hydraulic motor.
  • the alternative hydraulic motor proposed comprises a single valve which makes it possible to manage, by itself, the filling and emptying of the volumes concerned.
  • Said motor makes it possible to automatically transfer at each operating cycle a volume of fluid from said inlet duct to said intermediate chamber, then to transfer the same volume of fluid from said intermediate chamber to the exhaust duct under the action of the difference pressure P1-P2, and said control means.
  • the motor is characterized in that said control means comprise a single valve disposed in said cavity and mounted to pivot about a pivot axis located in the general plane of said valve and substantially perpendicular to the general plane of said conduits, and means for actuating said valve carried by said mobile assembly and actuating said valve so that the latter can take two positions in each operating cycle: a first position in which said inlet chamber communicates with said intermediate chamber, the exhaust chamber being isolated, a second position in which the intermediate chamber communicates with the exhaust chamber, the inlet chamber being isolated.
  • the valve mounted on the mobile assembly thus behaves like a two-position valve of a three-way valve.
  • said valve is in support, in each of said positions, on two wall portions of said movable assembly, said two wall portions being located on either side of the general plane of said valve.
  • One of said wall portions is arranged, relative to the general plane of said valve, on the side of the fluid at pressure P1, and the other of said wall portions is disposed on the side of the fluid at pressure P2.
  • the wall portion located on the side of the fluid at the pressure P2 is farther from the pivot axis than the other wall portion so that the fluid pressures exerted on the two faces of the valve create a torque of positive closure.
  • the means for actuating said valve comprise: a trigger rod slidingly mounted on said movable element parallel to the directions of movement of said pistons, said trigger rod being capable of being displaced relative to the movable element when it abuts on the walls of said stepped cylinder, a link secured to the pivot axis of said valve and, a spring interposed between said link and said trigger rod and, intended to tilt the valve during movement of the trigger rod.
  • said link is pivotally mounted on said pivot axis, so that the torque exerted by the spring after tilting of the link is greater than the positive closing torque exerted by fluid pressures.
  • the cavity of said movable element has two walls parallel to each other and perpendicular to the pivot axis, the wall portions cooperating with the valve are substantially parallel to the pivot axis.
  • the reciprocating hydraulic motor 1 shown in the drawing comprises a stepped cylinder 2 consisting of two concentric sleeves 3 and 4 delimiting between them an annular space 5 into which an inlet conduit 6 opens with a fluid at a pressure P1.
  • the outer sleeve 4 is extended by a cylindrical bell 7 fixed to the outer sleeve 4 by a ring 8.
  • the bell 7 has an inner diameter greater than the inner diameter of the inner sleeve 3.
  • the inner sleeve 3 and the bell 7 constitute the inner wall of the stepped cylinder 2.
  • a movable assembly 9 having two pistons 10 and 11 of different diameter connected together by a body 12.
  • the smaller diameter piston 10 is mounted sliding and sealed in the sleeve internal 3 with interposition of a seal 13.
  • the larger diameter piston 11 is slidably and sealed in the bell 7 with interposition of a seal 14a.
  • the exhaust pipe 14 of the fluid at pressure P2 opens, through the end wall 15 of the inner sleeve 3 which is opposite the bell 7, into an exhaust chamber 16 of variable volume located between the piston of smaller section 10 and the end face 15.
  • the annular space 5 is in permanent communication with an inlet chamber 17 of variable volume located in the stepped cylinder 2 between the pistons 10 and 11.
  • An intermediate chamber 18 of variable volume is delimited by the end wall 19 of the bell 7 and the larger diameter piston 11.
  • a cavity 20 is formed in the body 12 of the movable assembly 8. This cavity 20 communicates with the inlet chamber 17 by a first conduit 21. It also communicates with the exhaust chamber 16 by a second conduit 22 passing through the piston 10, and with the intermediate chamber 18 by a third conduit 23 passing through the piston 11.
  • a valve 25 In the cavity 20 is pivotally mounted around a pivot axis 24 a valve 25.
  • the pivot axis 24 is located in the general plane of the valve 25 and is substantially perpendicular to the general plane defined by the three conduits 21, 22 and 23.
  • the valve 25 can take two extreme positions: on the one hand, a first position, shown in FIG. 1, in which the inlet chamber 17 is in communication with the intermediate chamber 18 via the conduits 21 and 23 and in which the exhaust chamber 16 is isolated, and, on the other hand, a second position shown in FIG. 2, in which the inlet chamber 17 is isolated and in which the exhaust chamber 16 is in communication with the intermediate chamber 18 via the conduits 22 and 23.
  • valve 25 In the first position, shown in FIG. 1, the valve 25 is supported on two wall portions 26 and 27 to isolate the exhaust chamber 16.
  • the wall portions 26 and 27 are located on either side of the pivot axis 24 and on either side of the general plane of the valve 25.
  • the wall portion 26 is located relative to the valve 25 on the side of the face subjected to the pressure P1; the wall portion 27 is located on the contrary on the side of the face of valve subject to pressure P2 which is less than P1.
  • the distance separating the wall portion 27 from the pivot axis 24 is greater than the distance separating the wall portion 26 from the pivot axis 24.
  • the pressures P1 and P2 being exerted on the two faces of the valve 25 , therefore generate on the valve a resulting torque, represented by arrow 28, which tends to positively hold the valve 25 in the first position.
  • valve 25 In the second position, shown in Figure 2, the valve 25 is also supported on two wall portions 29 and 30 arranged on either side of the pivot axis 24 and on either side of the general plane of the valve 25.
  • One of the faces of the valve 25 is also subjected to the pressure P1 and the other face to the pressure P2.
  • the wall portion 29 located on the side of the pressure P2 is further from the pivot axis 24 than the wall portion 30 on which the face of the valve 25 subjected to the pressure P1 is supported.
  • the valve 25 is also in this case subjected to a torque resulting from positive closure, represented by the arrow 31.
  • the cavity 20 has two walls 20a and 20b perpendicular to the pivot axis 24, and the wall portions 26, 27, 29 and 30 are straight and parallel to the pivot axis 24.
  • the valve 25 then has a substantially rectangular shape and has on its edges seals cooperating with the walls 20a and 20b.
  • the valve 25 is produced in a conventional manner by elastic membranes interposed between stiffening plates.
  • the valve 25 is carried by the pivot axis 24 which passes through at least one of the walls, 20a for example, of the body 12 of the mobile assembly 9.
  • the valve 25 is actuated by actuating means which comprise a trigger rod 32, a link 33 secured to the pivot axis 24 and a spring 34 interposed between the trigger rod 32 and the free end of the link 33 .
  • the trigger rod 32 is slidably mounted on the mobile assembly 9 and is parallel to the directions of movement of the mobile assembly 9 in the stepped cylinder 2.
  • the trigger rod 32 is moved relative to the mobile assembly 9 when one of its ends abuts on the walls of the stepped cylinder 2, the end walls 15 and 19 for example. This movement causes the spring 34 to pivot about the free end of the link 33, and creates an opposing torque which causes the valve 25 to tilt when it is greater than one of the couples 28 or 31 described above.
  • the link 33 is pivotally mounted on the pivot axis 24.
  • the pivot axis 24 comprises two opposite lugs 35 accommodating in two openings 36 in the form of sectors, so as to allow free movement of the rod 33 relative to the pivot axis 24, when the spring 34 pivots as a result of the displacement of the trigger rod 32.
  • the valve 25 is in the first position, shown in Figure 1; the mobile assembly 9 is in the low position, and the trigger rod 32 is in the high position relative to the mobile assembly 9.
  • the inlet chamber 17 and the intermediate chamber 18 are at pressure P1.
  • the exhaust chamber 16 is at pressure P2. Due to the difference in the cross sections of the pistons 10 and 11, the movable assembly 9 moves upward in the direction of arrow 37. A volume of fluid is transferred from the inlet duct 6 to the intermediate chamber 18. A same volume of fluid is expelled from the exhaust chamber 16 to the exhaust duct 14.
  • the force used to move the movable assembly is the product of the section of the piston 10 by the difference in pressures (P1-P2).
  • the rod 33 finally pivots around the pivot axis 24, which causes a shock of the lugs 35 against the side walls of the openings 36 and a frank tilting of the valve 25 from the first position to the second position, shown in FIG. 2
  • the trigger rod 32 is now in the low position on the mobile assembly 9.
  • the exhaust chamber 16 and the intermediate chamber 18 now contain a fluid at pressure P2.
  • the inlet chamber 17 contains a fluid at pressure P1.
  • the movable assembly 9 moves downward in the direction of arrow 38. The force used in this movement to move the engine is equal to the product of the difference in the cross sections of the pistons 10 and 11 by the difference in pressures P1- P2. A volume of fluid is transferred from the intermediate chamber 18 to the exhaust chamber 16.
  • the mobile assembly 9 can be equipped with a rod 40 sealingly passing through the end wall 19 and making it possible to actuate a member external to the engine, a metering device for example.
  • valve actuation means in particular the rod 33 and the spring 34 are located outside the body 12 connecting the pistons 10 and 11, so as to make them directly accessible for repair after removal of the bell 7 .

Landscapes

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

Description

La présente invention concerne les moteurs hydrauliques alternatifs à piston différentiel qui utilisent l'énergie du fluide principal pour générer leur mouvement.The present invention relates to reciprocating hydraulic motors with differential piston which use the energy of the main fluid to generate their movement.

Le principe de base de ces moteurs est de transférer le fluide d'arrivée, à la pression P1, dans une chambre intermédiaire de volume variable, qui, après fermeture de clapets d'arrivée et ouverture de clapets d'échappement, se vide à la sortie en un fluide de même débit mais de pression P2 inférieure à la pression P1.The basic principle of these engines is to transfer the inlet fluid, at pressure P1, into an intermediate chamber of variable volume, which, after closing the inlet valves and opening the exhaust valves, empties at the outlet in a fluid of the same flow rate but of pressure P2 lower than the pressure P1.

L'énergie globale utilisée par ces moteurs hydrauliques est fonction du débit du fluide et de la différence entre les pressions P1 et P2.The overall energy used by these hydraulic motors is a function of the flow rate of the fluid and the difference between the pressures P1 and P2.

Un des éléments constitutifs très important dans ce type de dispositif est l'ensemble constitué par les clapets d'arrivée et d'échappement et leur système de commande.One of the very important constituent elements in this type of device is the assembly constituted by the inlet and exhaust valves and their control system.

En général, les dispositifs actuels utilisent des soupapes circulaires ou des tiroirs de manoeuvre. Il en résulte des systèmes complexes. (Voir US-A-4 031 812 et FR-A-2 205 361).In general, current devices use circular valves or operating drawers. The result is complex systems. (See US-A-4,031,812 and FR-A-2,205,361).

Le but de la présente invention est de proposer un moteur hydraulique alternatif simplifié.The object of the present invention is to provide a simplified alternative hydraulic motor.

Le but est atteint selon l'invention par le fait que le moteur hydraulique alternatif proposé comporte un seul clapet qui permet de gérer, à lui seul, le remplissage et la vidange des volumes concernés.The object is achieved according to the invention by the fact that the alternative hydraulic motor proposed comprises a single valve which makes it possible to manage, by itself, the filling and emptying of the volumes concerned.

L'invention concerne donc un moteur hydraulique à piston différentiel interposé entre un conduit d'arrivée de fluide à une pression P1 et un conduit d'échappement de fluide à une pression P2 inférieure à P1, du type comprenant :

  • un cylindre étagé,
  • un ensemble mobile comportant deux pistons de section différente, liés entre eux et montés coulissant et étanches dans ledit cylindre étagé, ledit ensemble mobile délimitant avec la paroi interne dudit cylindre étagé, trois chambres de volume variable : une chambre d'arrivée interposée entre lesdits deux pistons et dans laquelle débouche ledit conduit d'arrivée, une chambre d'échappement disposée de l'autre côté du piston de plus faible section par rapport à ladite chambre d'arrivée et dans laquelle débouche le conduit d'échappement, et une chambre intermédiaire située de l'autre côté du cylindre de plus grande section par rapport à ladite chambre d'arrivée,
  • un premier passage permettant de mettre temporairement en communication ladite chambre d'arrivée et ladite chambre intermédiaire,
  • un deuxième passage permettant de mettre temporairement en communication ladite chambre intermédiaire et ladite chambre d'échappement, et,
  • des moyens de commande pour ouvrir et fermer en alternance ledit premier et ledit deuxième passages à chaque cycle de fonctionnement,
ledit premier passage et ledit deuxième passages étant formés par une cavité ménagée dans ledit ensemble mobile et trois conduits mettant respectivement en communication ladite cavité avec ladite chambre d'arrivée, ladite chambre d'échappement et ladite chambre intermédiaire,The invention therefore relates to a differential piston hydraulic motor interposed between a fluid inlet pipe at a pressure P1 and a fluid exhaust pipe at a pressure P2 lower than P1, of the type comprising:
  • a stepped cylinder,
  • a mobile assembly comprising two pistons of different cross-section, linked to each other and mounted to slide and seal in said stepped cylinder, said mobile assembly delimiting with the inner wall of said stepped cylinder, three chambers of variable volume: an inlet chamber interposed between said two pistons and into which opens said inlet duct, an exhaust chamber disposed on the other side of the piston of smaller cross section by relative to said inlet chamber and into which the exhaust duct opens out, and an intermediate chamber situated on the other side of the cylinder of larger cross section relative to said inlet chamber,
  • a first passage making it possible to temporarily connect said arrival chamber and said intermediate chamber,
  • a second passage making it possible to temporarily connect said intermediate chamber and said exhaust chamber, and,
  • control means for alternately opening and closing said first and said second passages at each operating cycle,
said first passage and said second passage being formed by a cavity formed in said movable assembly and three conduits respectively placing said cavity in communication with said inlet chamber, said exhaust chamber and said intermediate chamber,

Ledit moteur permet de transférer automatiquement à chaque cycle de fonctionnement un volume de fluide dudit conduit d'arrivée vers ladite chambre intermédiaire, puis de transférer le même volume de fluide de ladite chambre intermédiaire vers le conduit d'échappement sous l'action de la différence de pression P1-P2, et desdits moyens de commande.Said motor makes it possible to automatically transfer at each operating cycle a volume of fluid from said inlet duct to said intermediate chamber, then to transfer the same volume of fluid from said intermediate chamber to the exhaust duct under the action of the difference pressure P1-P2, and said control means.

Selon L'invention, le moteur est caractérisé en ce que lesdits moyens de commande comportent un clapet unique disposé dans ladite cavité et monté pivotant autour d'un axe de pivotement situé dans le plan général dudit clapet et sensiblement perpendiculaire au plan général desdits conduits, et des moyens d'actionnement dudit clapet portés par ledit ensemble mobile et actionnant ledit clapet afin que ce dernier puisse prendre deux positions à chaque cycle de fonctionnement :
   une première position dans laquelle ladite chambre d'arrivée communique avec ladite chambre intermédiaire, la chambre d'échappement étant isolée, une deuxième position dans laquelle la chambre intermédiaire communique avec la chambre d'échappement, la chambre d'arrivée étant isolée.According to the invention, the motor is characterized in that said control means comprise a single valve disposed in said cavity and mounted to pivot about a pivot axis located in the general plane of said valve and substantially perpendicular to the general plane of said conduits, and means for actuating said valve carried by said mobile assembly and actuating said valve so that the latter can take two positions in each operating cycle:
a first position in which said inlet chamber communicates with said intermediate chamber, the exhaust chamber being isolated, a second position in which the intermediate chamber communicates with the exhaust chamber, the inlet chamber being isolated.

Le clapet monté sur l'ensemble mobile se comporte ainsi comme un clapet à deux positions d'un robinet à trois voies.The valve mounted on the mobile assembly thus behaves like a two-position valve of a three-way valve.

De manière à assurer la stabilité du clapet dans chacune desdites positions, ledit clapet est en appui, dans chacune desdites positions, sur deux portions de paroi dudit ensemble mobile, lesdites deux portions de paroi étant situées de part et d'autre du plan général dudit clapet. L'une desdites portions de paroi est disposée, par rapport au plan général dudit clapet, du côté du fluide à la pression P1, et l'autre desdites portions de paroi est disposée du côté du fluide à la pression P2. La portion de paroi située du côté du fluide à la pression P2 est plus éloignée de l'axe de pivotement que l'autre portion de paroi de telle manière que les pressions de fluide s'exerçant sur les deux faces du clapet créent un couple de fermeture positif.In order to ensure the stability of the valve in each of said positions, said valve is in support, in each of said positions, on two wall portions of said movable assembly, said two wall portions being located on either side of the general plane of said valve. One of said wall portions is arranged, relative to the general plane of said valve, on the side of the fluid at pressure P1, and the other of said wall portions is disposed on the side of the fluid at pressure P2. The wall portion located on the side of the fluid at the pressure P2 is farther from the pivot axis than the other wall portion so that the fluid pressures exerted on the two faces of the valve create a torque of positive closure.

Avantageusement, les moyens d'actionnement dudit clapet comportent :
   une tige de déclenchement montée coulissante sur ledit élément mobile parallèlement aux directions de déplacement desdits pistons, ladite tige de déclenchement étant susceptible d'être déplacée par rapport à l'élément mobile lorsqu'elle vient en butée sur des parois dudit cylindre étagé,
   une biellette solidaire de l'axe de pivotement dudit clapet et,
   un ressort interposé entre ladite biellette et ladite tige de déclenchement et, destiné à basculer le clapet lors du déplacement de la tige de déclenchement.
   De préférence, ladite biellette est montée pivotante sur ledit axe de pivotement, de telle manière que le couple exercé par le ressort après basculement de la biellette soit supérieur au couple de fermeture positif exercé par les pressions de fluide.Advantageously, the means for actuating said valve comprise:
a trigger rod slidingly mounted on said movable element parallel to the directions of movement of said pistons, said trigger rod being capable of being displaced relative to the movable element when it abuts on the walls of said stepped cylinder,
a link secured to the pivot axis of said valve and,
a spring interposed between said link and said trigger rod and, intended to tilt the valve during movement of the trigger rod.
Preferably, said link is pivotally mounted on said pivot axis, so that the torque exerted by the spring after tilting of the link is greater than the positive closing torque exerted by fluid pressures.

Avantageusement, la cavité dudit élément mobile présente deux parois parallèles entre elles et perpendiculaires à l'axe de pivotement, les portions de paroi coopérant avec le clapet sont sensiblement parallèles à l'axe de pivotement.Advantageously, the cavity of said movable element has two walls parallel to each other and perpendicular to the pivot axis, the wall portions cooperating with the valve are substantially parallel to the pivot axis.

D'autres avantages et caractéristiques de l'invention ressortiront à la lecture de la description suivante faite à titre d'exemple et en référence aux dessins annexés dans lesquels :

  • la figure 1 représente une coupe longitudinale du moteur hydraulique alternatif de la présente invention pendant la phase de remplissage de la chambre intermédiaire,
  • la figure 2 représente une coupe longitudinale du moteur de la figure 1 pendant la phase de vidange de la chambre intermédiaire,
  • la figure 3 est une coupe transversale du même moteur selon la ligne III-III de la figure 2.
Other advantages and characteristics of the invention will emerge on reading the following description given by way of example and with reference to the appended drawings in which:
  • FIG. 1 represents a longitudinal section of the alternative hydraulic motor of the present invention during the filling phase of the intermediate chamber,
  • FIG. 2 represents a longitudinal section of the motor of FIG. 1 during the emptying phase of the intermediate chamber,
  • FIG. 3 is a cross section of the same engine along the line III-III of FIG. 2.

Le moteur hydraulique alternatif 1 représenté sur le dessin comporte un cylindre étagé 2 constitué de deux manchons concentriques 3 et 4 délimitant entre eux un espace annulaire 5 dans lequel débouche un conduit d'arrivée 6 d'un fluide à une pression P1. Le manchon extérieur 4 est prolongé par une cloche cylindrique 7 fixée au manchon extérieur 4 par une bague 8. La cloche 7 a un diamètre intérieur supérieur au diamètre intérieur du manchon intérieur 3. Le manchon intérieur 3 et la cloche 7 constituent la paroi interne du cylindre étagé 2. Dans le cylindre étagé 2 est monté coulissant et étanche un ensemble mobile 9 présentant deux pistons 10 et 11 de diamètre différent reliés entre eux par un corps 12. Le piston de plus petit diamètre 10 est monté coulissant et étanche dans le manchon interne 3 avec interposition d'un joint d'étanchéité 13. Le piston de plus grand diamètre 11 est monté coulissant et étanche dans la cloche 7 avec interposition d'un joint d'étanchéité 14a.The reciprocating hydraulic motor 1 shown in the drawing comprises a stepped cylinder 2 consisting of two concentric sleeves 3 and 4 delimiting between them an annular space 5 into which an inlet conduit 6 opens with a fluid at a pressure P1. The outer sleeve 4 is extended by a cylindrical bell 7 fixed to the outer sleeve 4 by a ring 8. The bell 7 has an inner diameter greater than the inner diameter of the inner sleeve 3. The inner sleeve 3 and the bell 7 constitute the inner wall of the stepped cylinder 2. In the stepped cylinder 2 is mounted sliding and sealed a movable assembly 9 having two pistons 10 and 11 of different diameter connected together by a body 12. The smaller diameter piston 10 is mounted sliding and sealed in the sleeve internal 3 with interposition of a seal 13. The larger diameter piston 11 is slidably and sealed in the bell 7 with interposition of a seal 14a.

Le conduit d'échappement 14 du fluide à la pression P2 débouche, par la paroi d'extrémité 15 du manchon intérieur 3 qui est opposée à la cloche 7, dans une chambre d'échappement 16 de volume variable située entre le piston de plus faible section 10 et la face d'extrémité 15.The exhaust pipe 14 of the fluid at pressure P2 opens, through the end wall 15 of the inner sleeve 3 which is opposite the bell 7, into an exhaust chamber 16 of variable volume located between the piston of smaller section 10 and the end face 15.

L'espace annulaire 5 est en communication permanente avec une chambre d'arrivée 17 de volume variable située dans le cylindre étagé 2 entre les pistons 10 et 11.The annular space 5 is in permanent communication with an inlet chamber 17 of variable volume located in the stepped cylinder 2 between the pistons 10 and 11.

Une chambre intermédiaire 18 de volume variable est délimitée par la paroi d'extrémité 19 de la cloche 7 et le piston de plus grand diamètre 11.An intermediate chamber 18 of variable volume is delimited by the end wall 19 of the bell 7 and the larger diameter piston 11.

Une cavité 20 est ménagée dans le corps 12 de l'ensemble mobile 8. Cette cavité 20 communique avec la chambre d'arrivée 17 par un premier conduit 21. Elle communique également avec la chambre d'échappement 16 par un deuxième conduit 22 traversant le piston 10, et avec la chambre intermédiaire 18 par un troisième conduit 23 traversant le piston 11.A cavity 20 is formed in the body 12 of the movable assembly 8. This cavity 20 communicates with the inlet chamber 17 by a first conduit 21. It also communicates with the exhaust chamber 16 by a second conduit 22 passing through the piston 10, and with the intermediate chamber 18 by a third conduit 23 passing through the piston 11.

Dans la cavité 20 est monté pivotant autour d'un axe de pivotement 24 un clapet 25. L'axe de pivotement 24 est situé dans le plan général du clapet 25 et est sensiblement perpendiculaire au plan général défini par les trois conduits 21, 22 et 23.In the cavity 20 is pivotally mounted around a pivot axis 24 a valve 25. The pivot axis 24 is located in the general plane of the valve 25 and is substantially perpendicular to the general plane defined by the three conduits 21, 22 and 23.

Le clapet 25 peut prendre deux positions extrêmes : d'une part, une première position, représentée sur la figure 1, dans laquelle la chambre d'arrivée 17 est en communication avec la chambre intermédiaire 18 par l'intermédiaire des conduits 21 et 23 et dans laquelle la chambre d'échappement 16 est isolée, et, d'autre part, une deuxième position représentée sur la figure 2, dans laquelle la chambre d'arrivée 17 est isolée et dans laquelle la chambre d'échappement 16 est en communication avec la chambre intermédiaire 18 par les conduits 22 et 23.The valve 25 can take two extreme positions: on the one hand, a first position, shown in FIG. 1, in which the inlet chamber 17 is in communication with the intermediate chamber 18 via the conduits 21 and 23 and in which the exhaust chamber 16 is isolated, and, on the other hand, a second position shown in FIG. 2, in which the inlet chamber 17 is isolated and in which the exhaust chamber 16 is in communication with the intermediate chamber 18 via the conduits 22 and 23.

Dans la première position, représentée sur la figure 1, le clapet 25 est en appui sur deux portions de paroi 26 et 27 pour isoler la chambre d'échappement 16.In the first position, shown in FIG. 1, the valve 25 is supported on two wall portions 26 and 27 to isolate the exhaust chamber 16.

Les portions de paroi 26 et 27 sont situées de part et d'autre de l'axe de pivotement 24 et de part et d'autre du plan général du clapet 25. La portion de paroi 26 est située par rapport au clapet 25 du côté de la face soumise à la pression P1 ; la portion de paroi 27 est située au contraire du côté de la face de clapet soumise à la pression P2 qui est inférieure à P1. La distance séparant la portion de paroi 27 de l'axe de pivotement 24 est supérieure à la distance séparant la portion de paroi 26 de l'axe de pivotement 24. Les pressions P1 et P2, s'exerçant sur les deux faces du clapet 25, engendrent donc sur le clapet un couple résultant, représenté par la flèche 28, qui tend à maintenir positivement le clapet 25 dans la première position.The wall portions 26 and 27 are located on either side of the pivot axis 24 and on either side of the general plane of the valve 25. The wall portion 26 is located relative to the valve 25 on the side of the face subjected to the pressure P1; the wall portion 27 is located on the contrary on the side of the face of valve subject to pressure P2 which is less than P1. The distance separating the wall portion 27 from the pivot axis 24 is greater than the distance separating the wall portion 26 from the pivot axis 24. The pressures P1 and P2, being exerted on the two faces of the valve 25 , therefore generate on the valve a resulting torque, represented by arrow 28, which tends to positively hold the valve 25 in the first position.

Dans la deuxième position, représentée sur la figure 2, le clapet 25 est également en appui sur deux portions de paroi 29 et 30 disposées de part et d'autre de l'axe de pivotement 24 et de part et d'autre du plan général du clapet 25. L'une des faces du clapet 25 est également soumise à la pression P1 et l'autre face à la pression P2. La portion de paroi 29 située du côté de la pression P2 est plus éloignée de l'axe de pivotement 24 que la portion de paroi 30 sur laquelle la face du clapet 25 soumise à la pression P1 est en appui. Le clapet 25 est également dans ce cas soumis à un couple résultant de fermeture positif, représenté par la flèche 31.In the second position, shown in Figure 2, the valve 25 is also supported on two wall portions 29 and 30 arranged on either side of the pivot axis 24 and on either side of the general plane of the valve 25. One of the faces of the valve 25 is also subjected to the pressure P1 and the other face to the pressure P2. The wall portion 29 located on the side of the pressure P2 is further from the pivot axis 24 than the wall portion 30 on which the face of the valve 25 subjected to the pressure P1 is supported. The valve 25 is also in this case subjected to a torque resulting from positive closure, represented by the arrow 31.

De préférence, la cavité 20 présente deux parois 20a et 20b perpendiculaires à l'axe de pivotement 24, et les portions de paroi 26, 27, 29 et 30 sont rectilignes et parallèles à l'axe de pivotement 24. Le clapet 25 a alors une forme sensiblement rectangulaire et présente sur ses bords des joints d'étanchéité coopérant avec les parois 20a et 20b. Le clapet 25 est réalisé de manière classique par des membranes élastiques interposées entre des plaques de rigidification.Preferably, the cavity 20 has two walls 20a and 20b perpendicular to the pivot axis 24, and the wall portions 26, 27, 29 and 30 are straight and parallel to the pivot axis 24. The valve 25 then has a substantially rectangular shape and has on its edges seals cooperating with the walls 20a and 20b. The valve 25 is produced in a conventional manner by elastic membranes interposed between stiffening plates.

Le clapet 25 est porté par l'axe de pivotement 24 qui traverse au moins l'une des parois, 20a par exemple, du corps 12 de l'ensemble mobile 9.The valve 25 is carried by the pivot axis 24 which passes through at least one of the walls, 20a for example, of the body 12 of the mobile assembly 9.

Le clapet 25 est actionné par des moyens d'actionnement qui comportent une tige de déclenchement 32, une biellette 33 solidaire de l'axe de pivotement 24 et un ressort 34 interposé entre la tige de déclenchement 32 et l'extrémité libre de la biellette 33.The valve 25 is actuated by actuating means which comprise a trigger rod 32, a link 33 secured to the pivot axis 24 and a spring 34 interposed between the trigger rod 32 and the free end of the link 33 .

La tige de déclenchement 32 est montée coulissante sur l'ensemble mobile 9 et est parallèle aux directions de déplacement de l'ensemble mobile 9 dans le cylindre étagé 2. La tige de déclenchement 32 est déplacée par rapport à l'ensemble mobile 9 lorsque l'une de ses extrémités vient en butée sur les parois du cylindre étagé 2, les parois d'extrémité 15 et 19 par exemple. Ce déplacement provoque un pivotement du ressort 34 autour de l'extrémité libre de la biellette 33, et crée un couple antagoniste qui provoque le basculement du clapet 25 lorsqu'il est supérieur à l'un des couples 28 ou 31 décrits ci-dessus.The trigger rod 32 is slidably mounted on the mobile assembly 9 and is parallel to the directions of movement of the mobile assembly 9 in the stepped cylinder 2. The trigger rod 32 is moved relative to the mobile assembly 9 when one of its ends abuts on the walls of the stepped cylinder 2, the end walls 15 and 19 for example. This movement causes the spring 34 to pivot about the free end of the link 33, and creates an opposing torque which causes the valve 25 to tilt when it is greater than one of the couples 28 or 31 described above.

De manière à provoquer un basculement franc du clapet 25, la biellette 33 est montée pivotante sur l'axe de pivotement 24. Comme on le voit sur les figures 1 et 2, l'axe de pivotement 24 comporte deux ergots opposés 35 logeant dans deux ouvertures 36 en forme de secteurs, de manière à permettre un débattement libre de la biellette 33 par rapport à l'axe de pivotement 24, lorsque le ressort 34 pivote par suite du déplacement de la tige de déclenchement 32.So as to cause a frank tilting of the valve 25, the link 33 is pivotally mounted on the pivot axis 24. As can be seen in FIGS. 1 and 2, the pivot axis 24 comprises two opposite lugs 35 accommodating in two openings 36 in the form of sectors, so as to allow free movement of the rod 33 relative to the pivot axis 24, when the spring 34 pivots as a result of the displacement of the trigger rod 32.

Le fonctionnement du moteur 1 va maintenant être expliqué pour un cycle de fonctionnement.The operation of the motor 1 will now be explained for an operating cycle.

Le clapet 25 se trouve dans la première position, représentée sur la figure 1 ; l'ensemble mobile 9 est dans la position basse, et la tige de déclenchement 32 est dans la position haute par rapport à l'ensemble mobile 9. La chambre d'arrivée 17 et la chambre intermédiaire 18 sont à la pression P1. La chambre d'échappement 16 est à la pression P2. Du fait de la différence des sections des pistons 10 et 11, l'ensemble mobile 9 se déplace vers le haut dans le sens de la flèche 37. Un volume de fluide est transféré du conduit d'arrivée 6 vers la chambre intermédiaire 18. Un même volume de fluide est chassé de la chambre d'échappement 16 vers le conduit d'échappement 14. La force utilisée pour mouvoir l'ensemble mobile est le produit de la section du piston 10 par la différence des pressions (P1-P2).The valve 25 is in the first position, shown in Figure 1; the mobile assembly 9 is in the low position, and the trigger rod 32 is in the high position relative to the mobile assembly 9. The inlet chamber 17 and the intermediate chamber 18 are at pressure P1. The exhaust chamber 16 is at pressure P2. Due to the difference in the cross sections of the pistons 10 and 11, the movable assembly 9 moves upward in the direction of arrow 37. A volume of fluid is transferred from the inlet duct 6 to the intermediate chamber 18. A same volume of fluid is expelled from the exhaust chamber 16 to the exhaust duct 14. The force used to move the movable assembly is the product of the section of the piston 10 by the difference in pressures (P1-P2).

Finalement, la tige de déclenchement 32 vient buter sur la paroi 15, provoquant le pivotement du ressort 34 autour de l'extrémité libre de la biellette 33. L'ensemble mobile 9 continu encore de monter.Finally, the trigger rod 32 abuts on the wall 15, causing the spring 34 to pivot about the free end of the link 33. The movable assembly 9 continues yet to go up.

La biellette 33 pivote enfin autour de l'axe de pivotement 24, ce qui provoque un choc des ergots 35 contre les parois latérales des ouvertures 36 et un basculement franc du clapet 25 de la première position vers la deuxième position, représentée sur la figure 2. La tige de déclenchement 32 est maintenant en position basse sur l'ensemble mobile 9.The rod 33 finally pivots around the pivot axis 24, which causes a shock of the lugs 35 against the side walls of the openings 36 and a frank tilting of the valve 25 from the first position to the second position, shown in FIG. 2 The trigger rod 32 is now in the low position on the mobile assembly 9.

La chambre d'échappement 16 et la chambre intermédiaire 18 contiennent maintenant un fluide à la pression P2. La chambre d'arrivée 17 contient un fluide à la pression P1. L'ensemble mobile 9 se déplace vers le bas dans le sens de la flèche 38. L'effort utilisé dans ce mouvement pour mouvoir le moteur est égal au produit de la différence des sections des pistons 10 et 11 par la différence des pressions P1-P2. Un volume de fluide est transféré de la chambre intermédiaire 18 vers la chambre d'échappement 16.The exhaust chamber 16 and the intermediate chamber 18 now contain a fluid at pressure P2. The inlet chamber 17 contains a fluid at pressure P1. The movable assembly 9 moves downward in the direction of arrow 38. The force used in this movement to move the engine is equal to the product of the difference in the cross sections of the pistons 10 and 11 by the difference in pressures P1- P2. A volume of fluid is transferred from the intermediate chamber 18 to the exhaust chamber 16.

Finalement, la tige de délenchement 32 vient buter sur la paroi 19, ce qui provoque le pivotement inverse du ressort 34 autour de l'exrémité libre de la biellette 33, puis le pivotement inverse de la biellette 33 autour de l'axe de pivotement 24 et le basculement franc du clapet 25 de la deuxième position vers la première position.Finally, the release rod 32 abuts on the wall 19, which causes the reverse pivoting of the spring 34 around the free end of the link 33, then the reverse pivoting of the link 33 around the pivot axis 24 and the frank tilting of the valve 25 from the second position to the first position.

Il faut noter que l'ensemble mobile 9 peut être équipé d'une tige 40 traversant de manière étanche la paroi d'extrémité 19 et permettant d'actionner un organe extérieur au moteur, un dispositif de dosage par exemple.It should be noted that the mobile assembly 9 can be equipped with a rod 40 sealingly passing through the end wall 19 and making it possible to actuate a member external to the engine, a metering device for example.

De préférence, les moyens d'actionnement du clapet, notamment la biellette 33 et le ressort 34 sont situés à l'extérieur du corps 12 reliant les pistons 10 et 11, de manière à les rendre directement accessibles pour réparation après enlèvement de la cloche 7.Preferably, the valve actuation means, in particular the rod 33 and the spring 34 are located outside the body 12 connecting the pistons 10 and 11, so as to make them directly accessible for repair after removal of the bell 7 .

Claims (6)

  1. Reciprocating hydraulic motor having a differential piston interposed between an inlet duct (6) for fluid at a pressure P1 and an exhaust duct (14) for fluid at a pressure P2 lower than P1, the motor being of the type comprising:
    a stepped cylinder (2);
    a moving assembly (9) comprising two pistons (10, 11) of different sections, the pistons being interconnected and mounted to slide in sealed manner inside said stepped cylinder (2), said moving assembly (9) defining with the inside wall of said stepped cylinder (2) three variable-volume chambers: an inlet chamber (17) interposed between said two pistons (10, 11) and into which said inlet pipe (6) opens out, an exhaust chamber (16) disposed on the opposite side of the smaller section piston (10) relative to said inlet chamber (17) and into which the exhaust pipe (14) opens out, and an intermediate chamber (18) situated on the opposite side of the larger diameter piston (11) relative to said inlet chamber (17);
    a first passage allowing said inlet chamber (17) to be put temporarily into communication with said exhaust chamber (18);
    a second passage enabling said intermediate chamber (18) to be put temporarily into communication with said exhaust chamber (16); and,
    control means for opening and closing said first and second passages in alternation during each operating cycle;
    said first passage and said second passage being formed by a cavity (20) located in said moving assembly (9) and by three ducts (21, 22, 23) putting said cavity (20) into communication respectively said inlet chamber (17), with said exhaust chamber (16), and with said intermediate chamber (18), characterized in that
    said control means comprise a single flap (25) disposed in said cavity (20) and pivotally mounted on a pivot shaft (24) situated in the general plane of said flap (25) and extending substantially perpendicularly to the general plane of said ducts (21, 22, 23), and actuator means (32, 33, 34) for said flap (25) carried by said moving assembly(9) and actuating said flap (25) so as to enable it to take up two positions during each operating cycle:
    a first position in which said inlet chamber (17) communicates with said intermediate chamber (18) while said exhaust chamber (16) is isolated,
    a second position in which the intermediate chamber (18) communicates with the exhaust chamber (16), said inlet chamber (17) being isolated.
  2. Motor according to claim 1, characterized in that said flap bears in each of said positions against two wall portions (26, 27; 29, 30) of said moving assembly (9), said two wall portions being situated on opposite sides of the general plane of said flap (25). One of said wall portions (26, 30) is disposed relative to the general plane of said flap (25), on the side of the fluid at the pressure P1, while the other of said wall portions (27, 29) is disposed on the side of the fluid at the pressure P2 and,
       in that the wall portion (27, 29) situated on the side of the fluid at the pressure P2 is further from the pivot shaft (24) than is the other wall portion (26, 30) such that the fluid pressures acting on the two faces of the flap (25) create a positive closure torque.
  3. Motor according to claim 2, characterized in that the actuator means for said flap (25) comprise:
    a trip rod (32) slidably mounted on said moving assembly (9) to slide parallel to the displacement directions of said pistons (10, 11), said trip rod (32) being adapted to be displaced relative to the moving assembly (9) when it comes into abutment against the walls of said stepped cylinder (2),
    a crank (33) secured to the pivot shaft (24) of said flap (25), and
    a spring (34) interposed between said crank (33) and said trip rod (32) and designed to toggle the flap (25) during displacement of the trip rod (32).
  4. Motor according to claim 3, characterized in that said crank (33) is pivotally mounted on said pivot shaft (24) in such a manner that the torque exerted by the spring (34) after the crank has toggled is greater than the positive closure torque exerted by the fluid pressures.
  5. Motor according to any one of claims 1 to 4, characterized in that the cavity (20) of said moving assembly (9) has two mutually parallel walls (20a, 20b) extending perpendicularly to the pivot shaft (24), the wall portions (26, 27, 29, 30) which cooperate with the flap (25), being substantially parallel to the pivot shaft (24).
  6. Motor according to any one of claims 1 to 5, characterized in that the means for actuating the flap (25), in particular the crank (33) and the spring (34) are situated outside the body (12) interconnecting the pistons (10, 11) so as to make them directly accessible for maintenance and repair purposes after removal of the bell (7).
EP92402066A 1991-07-18 1992-07-17 Hydraulic motor with reciprocating differential piston Expired - Lifetime EP0524104B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9109105 1991-07-18
FR9109105A FR2679298B1 (en) 1991-07-18 1991-07-18 DIFFERENTIAL PISTON RECIPROCATING HYDRAULIC MOTOR.

Publications (2)

Publication Number Publication Date
EP0524104A1 EP0524104A1 (en) 1993-01-20
EP0524104B1 true EP0524104B1 (en) 1996-03-20

Family

ID=9415275

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92402066A Expired - Lifetime EP0524104B1 (en) 1991-07-18 1992-07-17 Hydraulic motor with reciprocating differential piston

Country Status (4)

Country Link
US (1) US5261311A (en)
EP (1) EP0524104B1 (en)
DE (1) DE69209176T2 (en)
FR (1) FR2679298B1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6626079B1 (en) * 2002-03-28 2003-09-30 Rehco, Llc Pneumatic motor
TWI684705B (en) * 2016-12-21 2020-02-11 黃進添 Low energy high steam pressure, oil pressure, steam engine

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US119076A (en) * 1871-09-19 Improvement in liquid-meters
US437097A (en) * 1890-09-23 Peter t
US245310A (en) * 1881-08-09 Water-meter
US2987051A (en) * 1958-10-22 1961-06-06 Lodding Engineering Corp Water-operated oscillator
FR2205361A1 (en) * 1972-11-09 1974-05-31 Cloup Philippe Automatic injection of an additive into a liquid - using a differential piston assembly, the displacement of piston being controlled by liq. under pressure
US4031812A (en) * 1974-03-08 1977-06-28 Nikolai Vasilievich Koshelev Hydraulic vibrator for actuator drive
FR2602282B1 (en) * 1986-07-31 1988-09-23 Cloup Jean IMPROVEMENT IN DEVICES FOR INJECTING AN ADDITIVE DOSE INTO A MAIN FLUID
US5137435A (en) * 1991-03-25 1992-08-11 Frank And Robyn Walton 1990 Family Trust Compression spring fluid motor

Also Published As

Publication number Publication date
DE69209176D1 (en) 1996-04-25
FR2679298A1 (en) 1993-01-22
US5261311A (en) 1993-11-16
DE69209176T2 (en) 1996-11-07
FR2679298B1 (en) 1993-11-26
EP0524104A1 (en) 1993-01-20

Similar Documents

Publication Publication Date Title
EP0462874B1 (en) Aircraft shock absorber
EP0805278B1 (en) Pneumatic actuating device
EP0088017B1 (en) Hydraulic directional spool valve
EP0524104B1 (en) Hydraulic motor with reciprocating differential piston
EP0217699B1 (en) Motor device of the piston liquid meter type, especially for a dosing pump
EP0396479B1 (en) Spherical plug valve
FR2893379A1 (en) COAXIAL INTERCEPTION VALVE FOR USE IN COMPRESSED AIR FACILITIES
EP0173625A1 (en) Fluid pressure-actuated device with wear compensation, especially for friction clutch mechanisms
FR2731071A1 (en) DIFFERENTIAL PRESSURE INDICATOR
FR2715437A1 (en) Device for measuring and recycling of exhaust gas, particularly for exhaust gas of diesel engine
FR2545906A1 (en) GUIDE VALVE VALVE FOR A PIPING NETWORK FOR LIQUIDS
FR2695861A1 (en) Hydraulic power and speed selector for press mfr. - has hydro-electric detector connected to primary actuator chamber to sense changes in press closure speed and power.
EP0790412B1 (en) Hydraulic circuit selector
EP0165281B1 (en) Compressed air flow rate limiter
FR2536810A1 (en) CYLINDER DEVICE AND FLUID DAMPENING PISTON
FR2524580A1 (en) Distributor for compressed air circuit - has drive chambers cross connected to reduce air consumption
EP0343051A1 (en) Bellows valve
FR2647208A1 (en) DEVICE FOR DOSING A LIQUID CONTAINED IN A FIRST CHAMBER AND FOR TRANSFERRING IN SMALL DOSES IN A FLUID FLOWING IN A SECOND CHAMBER
EP0294296B1 (en) Compact slide-valve
BE1011007A3 (en) VALVE ONLINE self-locking.
FR2625786A1 (en) COMBINATION OF A VALVE AND A PNEUMATIC CYLINDER
CH596483A5 (en) Constant volume valve for fluid
FR2591659A1 (en) Distribution system for reciprocating pneumatic motor
EP0526274A1 (en) Tandem brake booster
EP0528718A1 (en) Reciprocating hydraulic motor

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): BE DE ES GB IT

17P Request for examination filed

Effective date: 19930720

17Q First examination report despatched

Effective date: 19940329

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): BE DE ES GB IT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19960320

Ref country code: ES

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 19960320

REF Corresponds to:

Ref document number: 69209176

Country of ref document: DE

Date of ref document: 19960425

ITF It: translation for a ep patent filed

Owner name: PROROGA CONCESSA IN DATA: 13.08.96;BUZZI, NOTARO&A

GBV Gb: ep patent (uk) treated as always having been void in accordance with gb section 77(7)/1977 [no translation filed]

Effective date: 19960320

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20080715

Year of fee payment: 17

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20080726

Year of fee payment: 17

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 20080814

Year of fee payment: 17

BERE Be: lapsed

Owner name: SOC. CIVILE DE RECHERCHE *S A M

Effective date: 20090731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100202

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090717