EP1032536A1 - Method for controlling a screwing spindle - Google Patents

Method for controlling a screwing spindle

Info

Publication number
EP1032536A1
EP1032536A1 EP98956938A EP98956938A EP1032536A1 EP 1032536 A1 EP1032536 A1 EP 1032536A1 EP 98956938 A EP98956938 A EP 98956938A EP 98956938 A EP98956938 A EP 98956938A EP 1032536 A1 EP1032536 A1 EP 1032536A1
Authority
EP
European Patent Office
Prior art keywords
pressure
spindle
piston
screwing
torque
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.)
Granted
Application number
EP98956938A
Other languages
German (de)
French (fr)
Other versions
EP1032536B1 (en
Inventor
Bertrand Gruson
Gérard OLIEVE
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.)
Serac Group SAS
Original Assignee
Serac Group SAS
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 Serac Group SAS filed Critical Serac Group SAS
Publication of EP1032536A1 publication Critical patent/EP1032536A1/en
Application granted granted Critical
Publication of EP1032536B1 publication Critical patent/EP1032536B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B67—OPENING, CLOSING OR CLEANING BOTTLES, JARS OR SIMILAR CONTAINERS; LIQUID HANDLING
    • B67B—APPLYING CLOSURE MEMBERS TO BOTTLES JARS, OR SIMILAR CONTAINERS; OPENING CLOSED CONTAINERS
    • B67B3/00—Closing bottles, jars or similar containers by applying caps
    • B67B3/20—Closing bottles, jars or similar containers by applying caps by applying and rotating preformed threaded caps
    • B67B3/2073—Closing bottles, jars or similar containers by applying caps by applying and rotating preformed threaded caps comprising torque limiting means

Definitions

  • the present invention relates to a method for controlling a screwing spindle such as those used for the fitting by screwing of plugs on packages having threaded necks.
  • Screwing pins are known which comprise a linear cylinder having a piston connected to a pin shaft to drive the latter in rotation.
  • a commonly used method for controlling such pins consists in subjecting the piston to a differential tightening pressure generating the required tightening torque of the plug on the neck of the package.
  • a problem comes from the fact that at the beginning of the screwing of the stopper, there is little friction between the stopper and the neck, so that a weak resistive torque opposes the rotation of the spindle.
  • the spindle shaft then acquires a high rotational speed and, due to the inertia the spindle shaft stores significant kinetic energy.
  • the kinetic energy thus stored causes a rapid screwing of the plug until the latter comes to a stop, which causes the spindle shaft to stop suddenly.
  • the kinetic energy stored is restored by application to the plug in the form of a dynamic torque, greater than the required tightening torque.
  • This dynamic torque may cause deterioration of the cap or neck of the packaging, or force a user of the packaging to use a tool to loosen the cap.
  • An object of the invention is to propose a method for controlling the screwing spindle enabling the required tightening torque to be obtained precisely.
  • a method of controlling a screw spindle comprising a step of supplying the screw spindle with fluid under nominal conditions of pressure and flow generating required torque and previous step during which the screw spindle is supplied under conditions below the nominal conditions in a sufficient proportion so that the spindle shaft has a rotational speed generating kinetic energy producing a torque less than the required tightening torque.
  • the piston is subjected during the previous step to an average differential pressure lower than a differential clamping pressure.
  • the average differential pressure ensures the rotation of the spindle shaft at a low speed resulting in a small accumulation of kinetic energy.
  • the resistive torque opposing the screwing is then sufficient to prevent the spindle rotation speed increasing so that the plug stops as soon as the resistive torque is equal to the engine torque corresponding to the clamping pressure. There is therefore no sudden release of kinetic energy so that the effective tightening torque applied to the plug is equal to the required tightening torque.
  • one face of the piston is subjected in a screwing direction to a constant pressure lower than the differential clamping pressure.
  • the piston is subjected to a constant pressure in a screwing direction, and to a back pressure.
  • the average differential pressure is then equal to the difference between the constant pressure applied to the face of the piston and the back pressure.
  • the constant pressure is equal to the clamping pressure. Only one pressure level, corresponding to the required tightening torque, is then necessary.
  • the regulation of the pressure of the cylinder supply fluid is simplified.
  • the piston is subjected intermittently to a pressure of constant value.
  • the rotation of the spindle is initiated by the pressurization and the kinetic energy is restored during the pressure cut-off times so that it is possible to control the speed of the spindle by acting on the setting times pressure and the pressure cut-off times.
  • the differential pressure has a constant value equal to the clamping pressure.
  • FIG. 1 is a partial perspective view of a screw spindle
  • FIGS. 2, 3 and 4 are schematic representations of the spindle control member corresponding to three embodiments of the method according to one invention.
  • the screw pin controlled by the method of the invention has a structure and an operation known per se and some of its elements have not been shown.
  • the screw pin controlled by the method of the invention has a structure and an operation known per se and some of its elements have not been shown.
  • it comprises a vertical guide tube 1 fixed to a spindle support 2 and sliding vertically in a sleeve 3 secured to a rotary platform 4.
  • the tube 1 rotatably receives a spindle shaft 5 the lower end of which protrudes from the tube 1 and carries a jaw gripping device 6.
  • the upper end of the spindle shaft 5 carries a bevel gear 7 cooperating with a motor assembly generally designated at 11.
  • the spindle support 2 is mounted to slide on a column 9 fixed to the rotary platform 4 and carries a roller 8 intended to cooperate with a cam of a fixed frame to position the support 2 and the parts attached to it in height. associated.
  • a support plate 10 is fixed to the side of the spindle support 2 and carries the motor assembly 11.
  • the motor assembly 11 comprises an intermediate shaft 12 rotatably mounted in a bearing 13 carried by the support plate 10.
  • the shaft 12 has one end carrying, by means of a free wheel 45, a bevel gear 14 whose teeth are in contact with those of the pinion 7, and an opposite end carrying an input pinion 15 whose teeth are at contact with those of a rack 16.
  • the rack 16 is fixed by its lower end to the rod of a jack 17 whose body is fixed to the support plate 10.
  • the jack 17 conventionally comprises a piston
  • the control member 21 comprises a monostable distributor 22 controlled by a control input 24 between a screwing position in which the chamber 19 is exhaust while the chamber 20 is connected to a supply inlet 23 and a return position in which the chamber 19 of the jack 17 is placed in communication with the supply inlet 23 of the distributor 22 while the chamber 20 is exhausted.
  • the control input 24 is connected to a first sensor (not shown) for the position of the screw spindle relative to the fixed frame.
  • a monostable distributor 25 is disposed between the supply inlet 23 and two sources of pressurized air, an air source at the tightening pressure PS corresponding to a required tightening torque and an air source at a pressure P lower than the pressure PS.
  • the distributor 25 is controlled by a control input 26 between a low pressure supply position in which the pressure source P is connected to the supply input 23 while the pressure source PS is closed, and a position d supply at the clamping pressure in which the pressure source P is closed while the pressure source PS is connected to the supply input 23.
  • the control input 26 is connected to a second position sensor of the screw spindle relative to the fixed frame.
  • the platform 4 is rotated relative to the fixed frame by a motor.
  • Packages with threaded necks are brought successively and are held vertically above the jaw gripping device 6 previously provided with a plug.
  • the distributor 22 is brought by the control input 24 to the screwing position while the distributor 25 remains in the low pressure supply position.
  • Air at pressure P is then brought into the chamber 20 of the jack 17 and is exerted on the corresponding face of the piston.
  • the rod of the jack 17 pushes the rack 16 upwards.
  • the rack 16 rotates the input pinion 15 which transmits its opening to the gripping device 6 via the shaft 12, the pinions 14 and 7, and the spindle shaft 5 pivoting in the guide tube 1.
  • the pressure P is lower than the tightening pressure PS in a sufficient proportion so that the spindle shaft 5 has a rotational speed generating kinetic energy producing a torque lower than the required tightening torque.
  • the distributor 25 When passing from a second position of the spindle relative to the frame corresponding for example to an end of screwing the cap, that is to say that the bottom of the cap is in abutment on the neck of the bottle, the distributor 25 is brought by control input 26 to the supply position at the clamping pressure. Air at the clamping pressure PS is then introduced into the chamber 20.
  • the second position determining the start of the supply of the chamber 20 with air at the clamping pressure PS is defined for that the resistive torque opposing then the screwing of the plug on the threaded neck is sufficient to prevent that under the action of the clamping pressure, the speed of rotation of the spindle shaft 5 increases until generating kinetic energy sufficient to produce a torque greater than the required tightening torque.
  • the tightening of the cap on the neck causes a resisting torque having a value equal to that of the motor torque, the spindle shaft 5 stops rotating and the rack 16 stops.
  • the distributor 25 is returned to the low pressure supply position, and the distributor 22 is returned to the return position. Air at pressure P is then introduced into the chamber 19 of the jack 17 so that the jack is retracted.
  • the freewheel 45 associated with the pinion 14 allows retraction of the jack without unscrewing the plug.
  • the jaws of the gripping device 6 can be opened without damage to the plug and the screw spindle is then ready for a new cycle.
  • the control member 21 comprises a bistable distributor 30 disposed between an air source at the clamping pressure PS and the supply inlet 23 of a distributor 22 identical to that of the first embodiment.
  • the distributor 30 is controlled by two control inputs 31 and 32, respectively between a supply position in which the air source at the clamping pressure PS is connected to the supply input 23, and a cut-off position supply in which the air source at the clamping pressure PS is closed.
  • the control input 31 of the distributor 30 is connected to a timing element 33 and the control input 32 is connected to a timing element 34, both of which are connected to the pressure source PS.
  • the control member 21 Before the start of a tightening cycle, the control member 21 is in the position illustrated in FIG. 3, that is to say that the distributor 22 at rest ensures a connection between the supply inlet 23 and the return chamber 19 while the distributor 30 provides a connection between the source at pressure PS and the supply inlet 23.
  • a cam When passing from a first position of the spindle by relative to the frame, a cam simultaneously triggers an action on the control input 24 of the distributor 22 and a commissioning of the timers 33 and 34.
  • the control of the distributor 22 causes the chamber 20 to be supplied with fluid at the clamping pressure PS , which causes the screwing spindle to rotate.
  • the timer element 34 acts on the control input 32 of the distributor 30 to bring the latter into the power cut position.
  • the supply to the chamber 20 is then interrupted and the displacement of the piston 18 continues at a decreasing speed by the expansion of the air contained in the chamber 20.
  • the time delay element 33 acts on the control input 31 of the distributor 30 to return the latter to the supply position . Air at the clamping pressure PS is then again introduced into the chamber 20 so that the required tightening torque is applied to the plug.
  • T1 and T2 are determined so that a sufficient quantity of air is introduced into the chamber 20 so that the screwing of the plug is practically total at the expiration of the time T2 and the spindle then has a sufficiently low speed so that the corresponding kinetic energy generates a dynamic torque lower than the torque generated by the tightening pressure when the stopper is brought to a stop.
  • the re-pressure of chamber 20 at the tightening pressure PS then causes tightening at low speed so that when the spindle rotation stops the required tightening torque is reached but not exceeded.
  • the distributor 22 When the spindle reaches an end of cycle position, the distributor 22 is put to rest and the clamping pressure PS is sent to the chamber 19 of the jack to cause the latter to retract. The jaws of the gripping device 6 are open and the spindle is ready for a new cycle.
  • the supply inlet 23 of the distributor 22 is directly connected to an air source at the clamping pressure PS.
  • An exhaust pipe 40 extends between a monostable distributor 41 and an outlet 43 of the distributor 22 corresponding to the exhaust from the chamber 19 when the distributor 22 is in the screwing position.
  • the distributor 41 is controlled by an inlet 44 between a rest position in which the pipe 40 is connected to an exhaust regulating member 42, itself controlled by the pressure PS, and a regulated exhaust position in which the line 40 is put to free exhaust.
  • the control input 44 of the distributor 41 is connected to a position sensor 50 of the rack 16.
  • the position sensor 50 is arranged to correspond to the end of the screwing of the plug before it is tightened.
  • the distributor 22 When passing from a first position of the spindle relative to the frame, the distributor 22 is brought into the screwing position so that air at the clamping pressure PS is introduced into the chamber 20 while the exhaust from the chamber 19 is subjected to the exhaust regulating member 42.
  • the face of the piston 18 facing chamber 20 is therefore subjected to the clamping pressure PS while the opposite face of the piston 18 is subjected to a back pressure resulting from the restriction of escapement exerted by the regulating member 42.
  • the difference between the pressure and the back pressure is adjusted by means of l 'regulator 42 to avoid runaway of the screw spindle.
  • any actuation means suitable for the installation in question may be used in order to delimit a prior step during which the piston 18 is subjected to a reduced average differential pressure and a final step where it is subjected to the clamping differential pressure.
  • the clamping pressure PS is applied only once during time T2
  • the clamping pressure, or a pressure of different constant value could be applied repeatedly during the time T2 according to pulses of duration appropriate to the type of packaging or to the type of cap used.
  • the invention has been described in relation to a spindle driven in rotation by a linear cylinder, which makes it possible to obtain a tightening torque which is directly proportional to the supply pressure, it is can also implement the method according to the inven ⁇ tion in relation to a powered fluid motor having a motor element connected to the spindle shaft via a torque limiter device, for example a rotary motor equipped a friction clutch.
  • a torque limiter device for example a rotary motor equipped a friction clutch.
  • the method according to the invention makes it possible to avoid overshooting of the tightening torque due to the triggering inertia of the torque limiting device in relation to the kinetic energy stored by the motor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Details Of Spanners, Wrenches, And Screw Drivers And Accessories (AREA)
  • Retarders (AREA)
  • Sealing Of Jars (AREA)

Abstract

The invention concerns a method for controlling a screwing spindle comprising a motor supplied with fluid and having a motor element (18) coupled with the spindle shaft (5) to drive it in rotation, the method comprising the step of supplying the screwing spindle in nominal pressure conditions and flow rate generating the required tightening torque, and a prior step during which the screwing spindle is supplied in conditions less than the nominal conditions in sufficient proportion for the screwing spindle to rotate at a speed generating kinetic energy producing a tightening torque less than the required tightening torque.

Description

Procédé de commande d'une broche de vissage La présente invention concerne un procédé de commande d'une broche de vissage telle que celles utilisées pour la mise en place par vissage de bouchons sur des emballages disposant de goulots filetés . On connaît des broches de vissage qui comportent un vérin linéaire ayant un piston relié à un arbre de broche pour entraîner celui-ci en rotation. Un procédé communément utilisé pour la commande de telles broches consiste à soumettre le piston à une pression différen- tielle de serrage engendrant le couple de serrage requis du bouchon sur le goulot de l'emballage. Un problème vient du fait qu'au début du vissage du bouchon, il y a peu de frottement entre le bouchon et le goulot, de sorte qu'un faible couple résistant s'oppose à la rotation de la broche. L'arbre de broche acquiert alors une vitesse de rotation élevée et, du fait de l'inertie l'arbre de broche emmagasine une énergie cinétique importante. L'énergie cinétique ainsi emmagasinée provoque un vissage rapide du bouchon jusqu'au moment où celui-ci arrive en butée, ce qui provoque l'arrêt brutal de l'arbre de broche. Lors de cet arrêt, l'énergie cinétique emmagasinée est restituée par application au bouchon sous la forme d'un couple dynamique, supérieur au couple de serrage requis . Ce couple dynamique risque de provoquer une détérioration du bouchon ou du goulot de l'emballage, ou d'obliger un utilisateur de l'emballage à recourir à un outil pour desserrer le bouchon. The present invention relates to a method for controlling a screwing spindle such as those used for the fitting by screwing of plugs on packages having threaded necks. Screwing pins are known which comprise a linear cylinder having a piston connected to a pin shaft to drive the latter in rotation. A commonly used method for controlling such pins consists in subjecting the piston to a differential tightening pressure generating the required tightening torque of the plug on the neck of the package. A problem comes from the fact that at the beginning of the screwing of the stopper, there is little friction between the stopper and the neck, so that a weak resistive torque opposes the rotation of the spindle. The spindle shaft then acquires a high rotational speed and, due to the inertia the spindle shaft stores significant kinetic energy. The kinetic energy thus stored causes a rapid screwing of the plug until the latter comes to a stop, which causes the spindle shaft to stop suddenly. During this stop, the kinetic energy stored is restored by application to the plug in the form of a dynamic torque, greater than the required tightening torque. This dynamic torque may cause deterioration of the cap or neck of the packaging, or force a user of the packaging to use a tool to loosen the cap.
Un but de l'invention est de proposer un procédé de commande de la broche de vissage permettant l'obtention précise du couple de serrage requis.An object of the invention is to propose a method for controlling the screwing spindle enabling the required tightening torque to be obtained precisely.
En vue de la réalisation de ce but, on prévoit, selon l'invention, un procédé de commande d'une broche de vissage, comprenant une étape d'alimenter la broche de vissage en fluide dans des conditions nominales de pression et de débit engendrant un couple de serrage requis et une étape préalable au cours de laquelle la broche de vissage est alimentée dans des conditions inférieures aux conditions nominales dans une proportion suffisante pour que l'arbre de broche ait une vitesse de rotation engendrant une énergie cinétique produisant un couple inférieur au couple de serrage requis .In order to achieve this goal, there is provided, according to the invention, a method of controlling a screw spindle, comprising a step of supplying the screw spindle with fluid under nominal conditions of pressure and flow generating required torque and previous step during which the screw spindle is supplied under conditions below the nominal conditions in a sufficient proportion so that the spindle shaft has a rotational speed generating kinetic energy producing a torque less than the required tightening torque.
En particulier, dans le cas d'un vérin linéaire comportant un piston, le piston est soumis au cours de l'étape préalable à une pression différentielle moyenne inférieure à une pression différentielle de serrage.In particular, in the case of a linear cylinder comprising a piston, the piston is subjected during the previous step to an average differential pressure lower than a differential clamping pressure.
Ainsi, la pression différentielle moyenne assure la mise en rotation de l'arbre de broche à une vitesse faible entraînant une faible accumulation d'énergie cinétique. Lorsque la pression de serrage est appliquée au piston, le couple résistant s 'opposant au vissage est alors suffisant pour empêcher que la vitesse de rotation de la broche augmente de sorte que le bouchon s'arrête dès que le couple résistant est égal au couple moteur correspondant à la pression de serrage. Il n'y a donc pas de restitution brutale d'énergie cinétique de sorte que le couple de serrage effectif appliqué au bouchon est égal au couple de serrage requis.Thus, the average differential pressure ensures the rotation of the spindle shaft at a low speed resulting in a small accumulation of kinetic energy. When the clamping pressure is applied to the piston, the resistive torque opposing the screwing is then sufficient to prevent the spindle rotation speed increasing so that the plug stops as soon as the resistive torque is equal to the engine torque corresponding to the clamping pressure. There is therefore no sudden release of kinetic energy so that the effective tightening torque applied to the plug is equal to the required tightening torque.
Selon un premier mode de mise en oeuvre de l'invention, pendant l'étape préalable, une face du piston est soumise dans un sens de vissage à une pression constante inférieure à la pression différentielle de serrage.According to a first embodiment of the invention, during the prior step, one face of the piston is subjected in a screwing direction to a constant pressure lower than the differential clamping pressure.
Deux pressions différentes sont utilisées. Ainsi, une fois l'opération de vissage terminée, la pression constante inférieure à la pression de serrage peut être utilisée pour le retour du vérin de sorte qu'une économie significative de fluide est réalisée.Two different pressures are used. Thus, once the screwing operation is finished, the constant pressure lower than the clamping pressure can be used for the return of the jack so that a significant saving of fluid is achieved.
Selon un deuxième mode de mise en oeuvre, le piston est soumis à une pression constante dans un sens de vissage, et à une contre-pression. La pression dif érentielle moyenne est alors égale à la différence entre la pression constante appliquée à la face du piston et la contre-pression. De préférence, la pression constante est égale à la pression de serrage. Un seul niveau de pression, correspondant au couple de serrage requis, est alors nécessaire. La régulation de la pression du fluide d'alimentation du vérin est simplifiée. Selon un troisième mode de mise en oeuvre, le piston est soumis de façon intermittente à une pression de valeur constante. Ainsi, la rotation de la broche est amorcée par la mise sous pression et l'énergie cinétique est restituée pendant les temps de coupure de la pression de sorte qu'il est possible de commander la vitesse de la broche en agissant sur les temps de mise en pression et les temps de coupure de la pression.According to a second embodiment, the piston is subjected to a constant pressure in a screwing direction, and to a back pressure. The average differential pressure is then equal to the difference between the constant pressure applied to the face of the piston and the back pressure. Preferably, the constant pressure is equal to the clamping pressure. Only one pressure level, corresponding to the required tightening torque, is then necessary. The regulation of the pressure of the cylinder supply fluid is simplified. According to a third embodiment, the piston is subjected intermittently to a pressure of constant value. Thus, the rotation of the spindle is initiated by the pressurization and the kinetic energy is restored during the pressure cut-off times so that it is possible to control the speed of the spindle by acting on the setting times pressure and the pressure cut-off times.
Avantageusement dans cette variante, la pression différentielle a une valeur constante égale à la pression de serrage .Advantageously in this variant, the differential pressure has a constant value equal to the clamping pressure.
Comme dans le cas précédent, un seul niveau de pression, correspondant au couple de serrage requis, est alors employé de sorte que la régulation de la pression du fluide d'alimentation est simplifiée.As in the previous case, a single pressure level, corresponding to the required tightening torque, is then used so that the regulation of the pressure of the supply fluid is simplified.
D'autres caractéristiques et avantages de l'invention ressortiront à la lecture de la description qui suit de variantes particulières non limitatives de l'invention.Other characteristics and advantages of the invention will emerge on reading the following description of particular non-limiting variants of the invention.
Il sera fait référence aux dessins annexés parmi lesquels :Reference will be made to the accompanying drawings, in which:
- la figure 1 est une vue partielle en perspec- tive d'une broche de vissage,FIG. 1 is a partial perspective view of a screw spindle,
- les figures 2, 3 et 4 sont des représentations schématiques de l'organe de commande de la broche correspondant à trois modes de mise en oeuvre du procédé selon 1 ' invention. En référence aux figures, la broche de vissage commandée selon le procédé de l'invention a une structure et un fonctionnement connus en soi et certains de ses éléments n'ont pas été représentés. Dans le mode de réalisation illustré, elle comporte un tube de guidage vertical 1 fixé à un support de broche 2 et coulissant verticalement dans un manchon 3 solidaire d'une plate- forme rotative 4. Le tube 1 reçoit à rotation un arbre de broche 5 dont l'extrémité inférieure dépasse du tube 1 et porte un dispositif de préhension à mâchoires 6. L'extrémité supérieure de l'arbre de broche 5 porte un pignon conique 7 coopérant avec un ensemble moteur généralement désigné en 11.- Figures 2, 3 and 4 are schematic representations of the spindle control member corresponding to three embodiments of the method according to one invention. With reference to the figures, the screw pin controlled by the method of the invention has a structure and an operation known per se and some of its elements have not been shown. In the illustrated embodiment, it comprises a vertical guide tube 1 fixed to a spindle support 2 and sliding vertically in a sleeve 3 secured to a rotary platform 4. The tube 1 rotatably receives a spindle shaft 5 the lower end of which protrudes from the tube 1 and carries a jaw gripping device 6. The upper end of the spindle shaft 5 carries a bevel gear 7 cooperating with a motor assembly generally designated at 11.
Le support de broche 2 est monté pour coulisser sur une colonne 9 fixée à la plate- forme rotative 4 et porte un galet 8 destiné à coopérer avec une came d'un bâti fixe pour positionner en hauteur le support 2 et les pièces qui lui sont associées.The spindle support 2 is mounted to slide on a column 9 fixed to the rotary platform 4 and carries a roller 8 intended to cooperate with a cam of a fixed frame to position the support 2 and the parts attached to it in height. associated.
Une plaque support 10 est fixée sur le côté du support de broche 2 et porte l'ensemble moteur 11. L'ensemble moteur 11 comprend un arbre intermédiaire 12 monté à rotation dans un palier 13 porté par la plaque support 10. L'arbre 12 a une extrémité portant, par l'intermédiaire d'une roue libre 45, un pignon de renvoi conique 14 dont les dents sont au contact de celles du pignon 7, et une extrémité opposée portant un pignon d'entrée 15 dont les dents sont au contact de celles d'une crémaillère 16. La crémaillère 16 est fixée par son extrémité inférieure à la tige d'un vérin 17 dont le corps est fixé à la plaque support 10. Le vérin 17 comprend de façon classique un pistonA support plate 10 is fixed to the side of the spindle support 2 and carries the motor assembly 11. The motor assembly 11 comprises an intermediate shaft 12 rotatably mounted in a bearing 13 carried by the support plate 10. The shaft 12 has one end carrying, by means of a free wheel 45, a bevel gear 14 whose teeth are in contact with those of the pinion 7, and an opposite end carrying an input pinion 15 whose teeth are at contact with those of a rack 16. The rack 16 is fixed by its lower end to the rod of a jack 17 whose body is fixed to the support plate 10. The jack 17 conventionally comprises a piston
18 monté pour coulisser dans le corps du vérin et définir deux chambres 19, 20 à l'intérieur de celui-ci. Le vérin 17 est relié à un organe de commande généralement désigné en 21. On comprendra que dans ce type d'installation le couple appliqué à la broche lorsque celle-ci est bloquée dépend directement de la pression différentielle à laquelle le piston 18 est soumis.18 mounted to slide in the cylinder body and define two chambers 19, 20 inside thereof. The jack 17 is connected to a control member generally designated at 21. It will be understood that in this type of installation the torque applied to the spindle when the latter is blocked depends directly from the differential pressure to which the piston 18 is subjected.
En référence plus particulièrement à la figure 2, et selon le premier mode de mise en oeuvre du procédé, l'organe de commande 21 comprend un distributeur monostable 22 commandé par une entrée de commande 24 entre une position de vissage dans laquelle la chambre 19 est mise à l'échappement tandis que la chambre 20 est reliée à une entrée d'alimentation 23 et une position de retour dans laquelle la chambre 19 du vérin 17 est mise en communication avec l'entrée d'alimentation 23 du distributeur 22 tandis que la chambre 20 est mise à l'échappement. L'entrée de commande 24 est reliée à un premier capteur (non représenté) de position de la broche de vissage par rapport au bâti fixe.Referring more particularly to FIG. 2, and according to the first embodiment of the method, the control member 21 comprises a monostable distributor 22 controlled by a control input 24 between a screwing position in which the chamber 19 is exhaust while the chamber 20 is connected to a supply inlet 23 and a return position in which the chamber 19 of the jack 17 is placed in communication with the supply inlet 23 of the distributor 22 while the chamber 20 is exhausted. The control input 24 is connected to a first sensor (not shown) for the position of the screw spindle relative to the fixed frame.
Un distributeur monostable 25 est disposé entre l'entrée d'alimentation 23 et deux sources d'air sous pression, une source d'air à la pression de serrage PS correspondant à un couple de serrage requis et une source d'air à une pression P inférieure à la pression PS. Le distributeur 25 est commandé par une entrée de commande 26 entre une position d'alimentation basse pression dans laquelle la source de pression P est reliée à l'entrée d'alimentation 23 tandis que la source de pression PS est obturée, et une position d'alimentation à la pression de serrage dans laquelle la source de pression P est obturée tandis que la source de pression PS est reliée à l'entrée d'alimentation 23. L'entrée de commande 26 est reliée à un deuxième capteur de position de la broche de vissage par rapport au bâti fixe.A monostable distributor 25 is disposed between the supply inlet 23 and two sources of pressurized air, an air source at the tightening pressure PS corresponding to a required tightening torque and an air source at a pressure P lower than the pressure PS. The distributor 25 is controlled by a control input 26 between a low pressure supply position in which the pressure source P is connected to the supply input 23 while the pressure source PS is closed, and a position d supply at the clamping pressure in which the pressure source P is closed while the pressure source PS is connected to the supply input 23. The control input 26 is connected to a second position sensor of the screw spindle relative to the fixed frame.
En fonctionnement, la plate- forme 4 est entraînée en rotation par rapport au bâti fixe par un moteur. Des emballages à goulots filetés sont amenés successivement et sont maintenus à l'aplomb du dispositif de préhension à mâchoires 6 préalablement pourvu d'un bouchon. Au passage d'une première position de la broche par rapport au bâti, le distributeur 22 est amené par l'entrée de commande 24 dans la position de vissage tandis que le distributeur 25 demeure dans la position d'alimenta- tion basse pression. De l'air à la pression P est alors amené dans la chambre 20 du vérin 17 et s'exerce sur la face correspondante du piston. La tige du vérin 17 pousse la crémaillère 16 vers le haut. La crémaillère 16 entraîne en rotation le pignon d'entrée 15 qui transmet son ouve- ment au dispositif de préhension 6 par l'intermédiaire de l'arbre 12, des pignons 14 et 7, et de l'arbre de broche 5 pivotant dans le tube de guidage 1. On notera que la pression P est inférieure à la pression de serrage PS dans une proportion suffisante pour que l'arbre de broche 5 ait une vitesse de rotation engendrant une énergie cinétique produisant un couple inférieur au couple de serrage requis.In operation, the platform 4 is rotated relative to the fixed frame by a motor. Packages with threaded necks are brought successively and are held vertically above the jaw gripping device 6 previously provided with a plug. When passing from a first position of the spindle relative to the frame, the distributor 22 is brought by the control input 24 to the screwing position while the distributor 25 remains in the low pressure supply position. Air at pressure P is then brought into the chamber 20 of the jack 17 and is exerted on the corresponding face of the piston. The rod of the jack 17 pushes the rack 16 upwards. The rack 16 rotates the input pinion 15 which transmits its opening to the gripping device 6 via the shaft 12, the pinions 14 and 7, and the spindle shaft 5 pivoting in the guide tube 1. It will be noted that the pressure P is lower than the tightening pressure PS in a sufficient proportion so that the spindle shaft 5 has a rotational speed generating kinetic energy producing a torque lower than the required tightening torque.
Pendant le vissage la broche continue à se déplacer par rapport au bâti par rotation de la plate- formeDuring screwing the spindle continues to move relative to the frame by rotation of the platform
4. Au passage d'une deuxième position de la broche par rapport au bâti correspondant par exemple à une fin de vissage du bouchon, c'est-à-dire que le fond du bouchon est en butée sur le goulot de la bouteille, le distributeur 25 est amené par l'entrée de commande 26 dans la position d'alimentation à la pression de serrage. De l'air à la pression de serrage PS est alors introduit dans la chambre 20. On notera que la deuxième position déterminant le commencement de l'alimentation de la chambre 20 par de l'air à la pression de serrage PS, est définie pour que le couple résistant s 'opposant alors au vissage du bouchon sur le goulot fileté soit suffisant pour empêcher que sous l'action de la pression de serrage, la vitesse de rotation de l'arbre de broche 5 augmente jusqu'à engendrer une énergie cinétique suffisante pour produire un couple supérieur au couple de serrage requis . Lorsque le serrage du bouchon sur le goulot provoque un couple résistant ayant une valeur égale à celle du couple moteur, l'arbre de broche 5 cesse de tourner et la crémaillère 16 s'immobilise.4. When passing from a second position of the spindle relative to the frame corresponding for example to an end of screwing the cap, that is to say that the bottom of the cap is in abutment on the neck of the bottle, the distributor 25 is brought by control input 26 to the supply position at the clamping pressure. Air at the clamping pressure PS is then introduced into the chamber 20. It will be noted that the second position determining the start of the supply of the chamber 20 with air at the clamping pressure PS, is defined for that the resistive torque opposing then the screwing of the plug on the threaded neck is sufficient to prevent that under the action of the clamping pressure, the speed of rotation of the spindle shaft 5 increases until generating kinetic energy sufficient to produce a torque greater than the required tightening torque. When the tightening of the cap on the neck causes a resisting torque having a value equal to that of the motor torque, the spindle shaft 5 stops rotating and the rack 16 stops.
Pour une troisième position de la broche corres- pondant à la fin du cycle de vissage, le distributeur 25 est ramené dans la position d'alimentation basse pression, et le distributeur 22 est ramené en position de retour. De l'air à la pression P est alors introduit dans la chambre 19 du vérin 17 de sorte que le vérin est rétracté. La roue libre 45 associée au pignon 14 permet une rétraction du vérin sans dévissage du bouchon. Une fois le vérin rétracté, les mâchoires du dispositif de préhension 6 peuvent être ouvertes sans dommage pour le bouchon et la broche de vissage est alors prête pour un nouveau cycle. Les éléments identiques ou analogues à ceux précédemment décrits porteront dans la suite de la description la même référence numérique.For a third position of the spindle corresponding to the end of the screwing cycle, the distributor 25 is returned to the low pressure supply position, and the distributor 22 is returned to the return position. Air at pressure P is then introduced into the chamber 19 of the jack 17 so that the jack is retracted. The freewheel 45 associated with the pinion 14 allows retraction of the jack without unscrewing the plug. Once the cylinder retracted, the jaws of the gripping device 6 can be opened without damage to the plug and the screw spindle is then ready for a new cycle. The elements identical or analogous to those previously described will bear in the following description the same reference numeral.
En référence à la figure 3, dans le deuxième mode de mise en oeuvre, l'organe de commande 21 comprend un distributeur bistable 30 disposé entre une source d'air à la pression de serrage PS et l'entrée d'alimentation 23 d'un distributeur 22 identique à celui du premier mode de mise en oeuvre. Le distributeur 30 est commandé par deux entrées de commande 31 et 32, respectivement entre une position d'alimentation dans laquelle la source d'air à la pression de serrage PS est reliée à l'entrée d'alimentation 23, et une position de coupure d'alimentation dans laquelle la source d'air à la pression de serrage PS est obturée. L'entrée de commande 31 du distributeur 30 est reliée à un élément de temporisation 33 et l'entrée de commande 32 est reliée à un élément de temporisation 34, tous les deux reliés à la source de pression PS.Referring to Figure 3, in the second embodiment, the control member 21 comprises a bistable distributor 30 disposed between an air source at the clamping pressure PS and the supply inlet 23 of a distributor 22 identical to that of the first embodiment. The distributor 30 is controlled by two control inputs 31 and 32, respectively between a supply position in which the air source at the clamping pressure PS is connected to the supply input 23, and a cut-off position supply in which the air source at the clamping pressure PS is closed. The control input 31 of the distributor 30 is connected to a timing element 33 and the control input 32 is connected to a timing element 34, both of which are connected to the pressure source PS.
Avant le démarrage d'un cycle de vissage l'organe de commande 21 est dans la position illustrée sur la figure 3, c'est-à-dire que le distributeur 22 au repos assure une liaison entre l'entrée d'alimentation 23 et la chambre de retour 19 tandis que le distributeur 30 assure une liaison entre la source à la pression PS et l'entrée d'alimentation 23. Au passage d'une première position de la broche par rapport au bâti une came déclenche simultanément une action sur l'entrée de commande 24 du distributeur 22 et une mise en service des temporisateurs 33 et 34. La commande du distributeur 22 entraîne une alimentation de la chambre 20 en fluide à la pression de serrage PS, ce qui provoque une mise en rotation de la broche de vissage.Before the start of a tightening cycle, the control member 21 is in the position illustrated in FIG. 3, that is to say that the distributor 22 at rest ensures a connection between the supply inlet 23 and the return chamber 19 while the distributor 30 provides a connection between the source at pressure PS and the supply inlet 23. When passing from a first position of the spindle by relative to the frame, a cam simultaneously triggers an action on the control input 24 of the distributor 22 and a commissioning of the timers 33 and 34. The control of the distributor 22 causes the chamber 20 to be supplied with fluid at the clamping pressure PS , which causes the screwing spindle to rotate.
Au bout d'un temps Tl, l'élément de temporisation 34 agit sur l'entrée de commande 32 du distributeur 30 pour amener celui-ci dans la position de coupure d'alimentation. L'alimentation de la chambre 20 est alors interrompue et le déplacement du piston 18 se poursuit à une vitesse décroissante par la détente de l'air contenu dans la chambre 20.At the end of a time Tl, the timer element 34 acts on the control input 32 of the distributor 30 to bring the latter into the power cut position. The supply to the chamber 20 is then interrupted and the displacement of the piston 18 continues at a decreasing speed by the expansion of the air contained in the chamber 20.
Au bout d'un temps T2 , supérieur à Tl , qui détermine la fin de l'étape préalable, l'élément de temporisation 33 agit sur l'entrée de commande 31 du distributeur 30 pour ramener celui-ci dans la position d'alimentation. De l'air à la pression de serrage PS est alors à nouveau introduit dans la chambre 20 pour que le couple de serrage requis soit appliqué au bouchon.At the end of a time T2, greater than T1, which determines the end of the prior step, the time delay element 33 acts on the control input 31 of the distributor 30 to return the latter to the supply position . Air at the clamping pressure PS is then again introduced into the chamber 20 so that the required tightening torque is applied to the plug.
En raison de l'interruption d'alimentation du vérin pendant la différence de temps entre Tl et T2 , la pression différentielle moyenne sur le piston pendant l'étape préalable est inférieure à la pression de serrage. Tl et T2 sont déterminés pour qu'une quantité d'air suffisante soit introduite dans la chambre 20 afin que le vissage du bouchon soit pratiquement total à l'expiration du temps T2 et que la broche ait alors une vitesse suffisamment faible pour que l'énergie cinétique correspondante génère au moment de la mise en butée du bouchon un couple dynamique inférieur au couple engendré par la pression de serrage. La remise en pression de la chambre 20 à la pression de serrage PS provoque alors un serrage à vitesse lente de sorte qu'au moment de l'arrêt de la rotation de la broche le couple de serrage requis est atteint mais non dépassé . Lorsque la broche atteint une position de fin de cycle, le distributeur 22 est mis au repos et la pression de serrage PS est envoyée dans la chambre 19 du vérin pour provoquer la rétraction de celui-ci. Les mâchoires du dispositif de préhension 6 sont ouvertes et la broche est prête pour un nouveau cycle.Due to the interruption of supply to the cylinder during the time difference between T1 and T2, the average differential pressure on the piston during the previous step is lower than the clamping pressure. T1 and T2 are determined so that a sufficient quantity of air is introduced into the chamber 20 so that the screwing of the plug is practically total at the expiration of the time T2 and the spindle then has a sufficiently low speed so that the corresponding kinetic energy generates a dynamic torque lower than the torque generated by the tightening pressure when the stopper is brought to a stop. The re-pressure of chamber 20 at the tightening pressure PS then causes tightening at low speed so that when the spindle rotation stops the required tightening torque is reached but not exceeded. When the spindle reaches an end of cycle position, the distributor 22 is put to rest and the clamping pressure PS is sent to the chamber 19 of the jack to cause the latter to retract. The jaws of the gripping device 6 are open and the spindle is ready for a new cycle.
En référence à la figure 4, et selon le troisième mode de mise en oeuvre, l'entrée d'alimentation 23 du distributeur 22 est directement raccordée à une source d'air à la pression de serrage PS. Une conduite d'échappe- ment 40 s'étend entre un distributeur monostable 41 et une sortie 43 du distributeur 22 correspondant à l'échappement de la chambre 19 lorsque le distributeur 22 est dans la position de vissage.Referring to Figure 4, and according to the third embodiment, the supply inlet 23 of the distributor 22 is directly connected to an air source at the clamping pressure PS. An exhaust pipe 40 extends between a monostable distributor 41 and an outlet 43 of the distributor 22 corresponding to the exhaust from the chamber 19 when the distributor 22 is in the screwing position.
Le distributeur 41 est commandé par une entrée 44 entre une position de repos dans laquelle la conduite 40 est reliée à un organe de régulation d'échappement 42, lui- même commandé par la pression PS, et une position d'échappement régulé dans laquelle la conduite 40 est mise à l'échappement libre. L'entrée de commande 44 du distribu- teur 41 est reliée un capteur de position 50 de la crémaillère 16. Le capteur de position 50 est disposé pour correspondre à la fin de vissage du bouchon avant serrage de celui-ci.The distributor 41 is controlled by an inlet 44 between a rest position in which the pipe 40 is connected to an exhaust regulating member 42, itself controlled by the pressure PS, and a regulated exhaust position in which the line 40 is put to free exhaust. The control input 44 of the distributor 41 is connected to a position sensor 50 of the rack 16. The position sensor 50 is arranged to correspond to the end of the screwing of the plug before it is tightened.
Au passage d'une première position de la broche par rapport au bâti, le distributeur 22 est amené en position de vissage de sorte que de l'air à la pression de serrage PS est introduit dans la chambre 20 tandis que l'échappement de la chambre 19 est soumis à l'organe de régulation d'échappement 42. La face du piston 18 en regard de la chambre 20 est donc soumise à la pression de serrage PS tandis que la face opposée du piston 18 est soumise à une contre-pression résultant de la restriction d'échappe¬ ment exercée par l'organe de régulation 42. La différence entre la pression et la contre-pression est réglée au moyen de l'organe de régulation 42 pour éviter un emballement de la broche de vissage.When passing from a first position of the spindle relative to the frame, the distributor 22 is brought into the screwing position so that air at the clamping pressure PS is introduced into the chamber 20 while the exhaust from the chamber 19 is subjected to the exhaust regulating member 42. The face of the piston 18 facing chamber 20 is therefore subjected to the clamping pressure PS while the opposite face of the piston 18 is subjected to a back pressure resulting from the restriction of escapement exerted by the regulating member 42. The difference between the pressure and the back pressure is adjusted by means of l 'regulator 42 to avoid runaway of the screw spindle.
Lorsque la crémaillère 16 atteint le capteur 50, celui-ci actionne l'entrée de commande du distributeur 41 dans la position d'échappement non régulé libérant ainsi l'échappement de la chambre 19. Le piston 18 est alors soumis à la pression de serrage PS et le couple de serrage requis est appliqué au bouchon.When the rack 16 reaches the sensor 50, the latter actuates the control input of the distributor 41 in the unregulated exhaust position thereby releasing the exhaust from the chamber 19. The piston 18 is then subjected to the clamping pressure PS and the required tightening torque is applied to the cap.
Bien entendu l'invention n'est pas limitée au mode de réalisation décrit et on peut y apporter des variantes de réalisation sans sortir du cadre de l'invention tel que défini par les revendications .Of course, the invention is not limited to the embodiment described and it is possible to make variant embodiments without departing from the scope of the invention as defined by the claims.
En particulier, bien que les entrées de commande des distributeurs aient été décrites en relation avec des moyens particuliers d' actionnement , on pourra utiliser tout moyen d' actionnement approprié à l'installation considérée afin de délimiter une étape préalable au cours de laquelle le piston 18 est soumis à une pression différentielle moyenne réduite et une étape finale où il est soumis à la pression différentielle de serrage. Bien que dans le deuxième mode de mise en oeuvre décrit, la pression de serrage PS ne soit appliquée qu'une seule fois au cours du temps T2 , la pression de serrage, ou une pression de valeur constante différente, pourrait être appliquée à plusieurs reprises pendant le temps T2 selon des impulsions de durée appropriée au type d'emballage ou au type de bouchon utilisé.In particular, although the distributor control inputs have been described in relation to particular actuation means, any actuation means suitable for the installation in question may be used in order to delimit a prior step during which the piston 18 is subjected to a reduced average differential pressure and a final step where it is subjected to the clamping differential pressure. Although in the second embodiment described, the clamping pressure PS is applied only once during time T2, the clamping pressure, or a pressure of different constant value, could be applied repeatedly during the time T2 according to pulses of duration appropriate to the type of packaging or to the type of cap used.
Bien que l'invention ait été décrite en relation avec une broche entraînée en rotation par un vérin linéaire, ce qui permet d'obtenir un couple de serrage qui est directement proportionnel à la pression d'alimentation, on peut également mettre en oeuvre le procédé selon l'inven¬ tion en relation avec un moteur alimenté en fluide ayant un organe moteur lié à l'arbre de broche par l'intermédiaire d'un dispositif limiteur de couple, par exemple un moteur rotatif équipé d'un embrayage à friction. Dans ce cas, le procédé selon l'invention permet d'éviter un dépassement de couple de serrage dû à l'inertie de déclenchement du dispositif limiteur de couple en relation avec l'énergie cinétique emmagasinée par le moteur. Although the invention has been described in relation to a spindle driven in rotation by a linear cylinder, which makes it possible to obtain a tightening torque which is directly proportional to the supply pressure, it is can also implement the method according to the inven ¬ tion in relation to a powered fluid motor having a motor element connected to the spindle shaft via a torque limiter device, for example a rotary motor equipped a friction clutch. In this case, the method according to the invention makes it possible to avoid overshooting of the tightening torque due to the triggering inertia of the torque limiting device in relation to the kinetic energy stored by the motor.

Claims

REVE.NDICATIONS 1. Procédé de commande d'une broche de vissage comportant un moteur alimenté en fluide et ayant un organe moteur (18) relié à un arbre de broche (5) pour entraîner celui-ci en rotation, le procédé comprenant l'étape d'alimenter la broche de vissage dans des conditions nominales de pression et de débit engendrant un couple de serrage requis, caractérisé en ce que le procédé comprend une étape préalable au cours de laquelle la broche de vissage est alimentée dans des conditions inférieures aux conditions nominales dans une proportion suffisante pour que l'arbre de broche ait une vitesse de rotation engendrant une énergie cinétique produisant un couple inférieur au couple de serrage requis. REVE.NDICATIONS 1. Method for controlling a screw spindle comprising a motor supplied with fluid and having a motor member (18) connected to a spindle shaft (5) to drive the latter in rotation, the method comprising step of feeding the screw spindle under nominal pressure and flow conditions generating a required tightening torque, characterized in that the method comprises a prior step during which the screw spindle is supplied under conditions below the conditions nominal in a sufficient proportion for the spindle shaft to have a rotational speed generating kinetic energy producing a torque less than the required tightening torque.
2. Procédé selon la revendication 1, caractérisé en ce que le moteur est un vérin linéaire et l'organe moteur est un piston, et en ce que dans l'étape préalable le piston est soumis à une pression différentielle moyenne inférieure à une pression différentielle de serrage. 2. Method according to claim 1, characterized in that the motor is a linear cylinder and the motor member is a piston, and in that in the prior step the piston is subjected to an average differential pressure less than a differential pressure Clamping.
3. Procédé selon la revendication 2, caractérisé en ce que, dans l'étape préalable, une face du piston est soumise à une pression constante dans un sens de vissage.3. Method according to claim 2, characterized in that, in the prior step, one face of the piston is subjected to a constant pressure in a screwing direction.
4. Procédé selon la revendication 3, caractérisé en ce que la pression constante est inférieure à la pression différentielle de serrage.4. Method according to claim 3, characterized in that the constant pressure is less than the differential clamping pressure.
5. Procédé selon la revendication 3, caractérisé en ce que le piston est soumis à une contre-pression.5. Method according to claim 3, characterized in that the piston is subjected to a back pressure.
6. Procédé selon la revendication 5, caractérisé en ce que la pression constante est égale à la pression différentielle de serrage.6. Method according to claim 5, characterized in that the constant pressure is equal to the differential clamping pressure.
7. Procédé selon la revendication 2, caractérisé en ce que, dans l'étape préalable, le piston est soumis de façon intermittente à une pression.7. Method according to claim 2, characterized in that, in the prior step, the piston is subjected intermittently to a pressure.
8. Procédé selon la revendication 7, caractérisé en ce que la pression est une pression différentielle de valeur constante égale à la pression différentielle de serrage . 8. Method according to claim 7, characterized in that the pressure is a differential pressure of constant value equal to the differential clamping pressure.
EP98956938A 1997-11-17 1998-11-03 Method for controlling a screwing spindle Expired - Lifetime EP1032536B1 (en)

Applications Claiming Priority (3)

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FR9714364A FR2771040B1 (en) 1997-11-17 1997-11-17 METHOD FOR CONTROLLING A TIGHTENING SPINDLE
FR9714364 1997-11-17
PCT/FR1998/002346 WO1999025638A1 (en) 1997-11-17 1998-11-03 Method for controlling a screwing spindle

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FR2771040A1 (en) 1999-05-21
FR2771040B1 (en) 2000-01-07
PT1032536E (en) 2002-07-31
JP2001523626A (en) 2001-11-27
DK1032536T3 (en) 2002-05-13
EP1032536B1 (en) 2002-01-30
DE69803699D1 (en) 2002-03-14
US6263742B1 (en) 2001-07-24
CN1278777A (en) 2001-01-03
ES2171049T3 (en) 2002-08-16
DE69803699T2 (en) 2002-10-17
CN1105676C (en) 2003-04-16
WO1999025638A1 (en) 1999-05-27
BR9814206A (en) 2000-10-03

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