EP0165281B1 - Compressed air flow rate limiter - Google Patents

Compressed air flow rate limiter Download PDF

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Publication number
EP0165281B1
EP0165281B1 EP85900124A EP85900124A EP0165281B1 EP 0165281 B1 EP0165281 B1 EP 0165281B1 EP 85900124 A EP85900124 A EP 85900124A EP 85900124 A EP85900124 A EP 85900124A EP 0165281 B1 EP0165281 B1 EP 0165281B1
Authority
EP
European Patent Office
Prior art keywords
movable element
flow rate
rate limiter
limiter according
cylindrical
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
Application number
EP85900124A
Other languages
German (de)
French (fr)
Other versions
EP0165281A1 (en
Inventor
André Legris
Yves Levenez
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.)
Legris SA
Original Assignee
Legris SA
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Filing date
Publication date
Application filed by Legris SA filed Critical Legris SA
Publication of EP0165281A1 publication Critical patent/EP0165281A1/en
Application granted granted Critical
Publication of EP0165281B1 publication Critical patent/EP0165281B1/en
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the output member

Definitions

  • the present invention relates to a compressed air flow limiter arranged between a conventional compressed air distributor and a pneumatic cylinder.
  • the exhaust flow being limited only, the starting of the cylinders is slow, due to the large volume of air to be evacuated by the restriction and it can be accompanied by jolts. Pressure drop sensors tend to deliver end-of-travel signals that are all the more delayed as the passage restriction is important.
  • the device for adjusting the speed of a double-acting cylinder therefore consists of at least two flow restrictors, either intake or exhaust.
  • Hydraulic distributors are also known in which the drawer is self-piloting and subjected on its two faces to the action of springs.
  • this device due to the fact that it is used with incompressible liquids has passages which provide flow rates and do not allow, as in the present application where it is a matter of compressible gases, to limit the speed of a jack by controlling the air flow.
  • this known device does not allow easy adjustment of the position of the drawer by means of movable stops.
  • the device according to the present invention makes it possible to eliminate the drawbacks associated with the use of limiters and known devices for adjusting the speed of the pneumatic actuation means such as the jacks.
  • the air flow limiter comprises a body having a cylindrical housing bounded by two bottoms and in which is slidably mounted axially a movable member of revolution whose stroke is limited at each end of the housing by a member adjustable stop, said body being traversed perpendicularly to said cylindrical housing by two passage conduits supplying the actuator, said passage conduits each opening into a chamber delimited by the bottom, the cylindrical housing and the movable member, said movable member comprising a means of '' central seal ensuring the isolation between the two chambers defined at the two ends of the bistable housing, ensuring the adjustment of the opening of the passage conduits according to the position of the stop members located at the two ends of the housing, so that 'this results in an adjustment of the supply air and purge flow rates of the two air volumes of the double ef cylinder fet and this, in each direction of movement of the cylinder piston.
  • the device according to the invention makes it possible to adjust for each of the two directions of travel, both the intake flow and the exhaust air flow using a single adjustment for each direction.
  • This flow limiter arranged between a compressed air distributor and a pneumatic cylinder makes it possible to adjust the speed of the piston of a cylinder in each direction.
  • the flow limiter according to the invention is connected by its two inlet ports to the two outlet ports of a distributor and by its two outlet ports to the two inlet ports of a double-acting cylinder.
  • the reversal of the movement of the piston of the jack is a function of a sufficient pressure difference between the chambers of the regulator and the starting. of the cylinder with the double adjuster is much faster in setting for the purge than with conventional adjusters.
  • FIGS 1 and 2 there is shown an embodiment of a flow limiter which is arranged between a compressed air distributor 15 and a double-acting cylinder 5.
  • the flow limiter comprises a body 1 having a bore or housing cylindrical 1a limited by two bottoms and in which is slidably mounted an axially movable member 2 of revolution whose stroke is limited at each end of the housing by a stop member constituted by a screw 3, 4, engaged in a tapped hole 32b of a plug 32 closing off the two ends of the cylindrical housing 1a, said plug being forcibly engaged in the housing 1a with the interposition of an annular seal 32a disposed in a groove in the plug 32.
  • the head of the screws 3, 4 is engaged in a blind hole 32c provided in the plugs 32, with the interposition of an annular seal 3a, 4a.
  • the body 1 is crossed perpendicularly to the housing 1a by two passage conduits 11, 12 and 13, 14 supplying the jack 5, said conduit 11, 12 opening into a chamber 1b and said conduit 13, 14 opening into a chamber 1c.
  • the chambers 1b and 1c are delimited by the plug 32, the cylindrical housing 1a and the movable member 2, said movable member comprising a central annular seal 10, disposed in a groove 2g of said movable member and ensuring the isolation between the two chambers 1b and 1c.
  • the movable member 2 consists of a single cylindrical part (Fig. 1, 2) having a central partition 2f, delimiting on each side a recess 2c, and against which the screws 3 and 4 are likely to abut to limit the stroke of the movable member 2.
  • the body 1 of the flow limiter is connected by its half-ducts 11, 13 to the jack 5 and by its half-ducts 12, 14 to the compressed air distributor which is connected to a source P of compressed air and to exhausts EA and EB linked to the atmosphere.
  • the dispenser drawer When the dispenser drawer is in the position shown in FIGS. 1 and 2, it supplies compressed air to the semi-duct 12 thus pushing the movable member 2 which acts like a piston to the left and feeding through the housing 1 a and the half-duct 11 one of the sides of the jack 5.
  • the movable member is in abutment against the end of the screw 4 which has been adjusted beforehand to more or less close the passage orifice corresponding to the conduit 13, 14 which is connected to the chamber of the jack 5 which is located at the exhaust through the distributor 15.
  • the air flow rate escaping from the jack 5 is regulated by the orifice. delimited between the circular edge 34 of the movable member and the orifices of the half-ducts 13, 14, the position of the movable member 2 being determined by the position of the screw 4.
  • the speed of movement of the piston 5a in the jack 5 is also controlled, since this speed is a function of the resistance opposed by the air escaping from the jack by the conduit 13, 14, the orifice of which is more or less closed.
  • the adjuster of Figure 1 allows the adjustment of the flow rate on the exhaust, the intake being wide open and this in each direction.
  • the movable member 2 bi-stable in abutment to the right or to the left according to the cylinder cycle, more or less closes depending on the adjustment of the abutment screws 3, 4, the orifices for passage of the conduits 11, 12 and 13, 14 regulating thus the purge air flows in each direction.
  • the seal 10 ensuring the seal between the chambers 1b and 1c is mounted in a groove 1 formed in the body and in contact with the cylindrical outer surface of the movable member 2.
  • FIGS 3 and 4 there is shown another embodiment of the movable member 2 which consists of two identical elements 2a, 2b or complementary assembled by means of a rivet 2d or a screw, said elements delimiting between them a housing in which is disposed a seal 2e disposed around the rivet 2d. Outside the two elements 2a, 2b and on their joint plane there is provided a groove 2g intended to receive a seal 10.
  • the assembly of the elements 2a, 2b facilitates the passage of the seal 10 opposite the passage conduits 11, 12 and 13, 14, inside the housing 1a of the body 1.
  • the body 1 of Figure 2 can be made in two symmetrical or complementary parts.
  • the stop screws 3 and 4 are mounted in the plugs 32, so that their head extends outside.
  • the screws 3 and 4 are provided with locknuts 3b and 4b preventing these from unscrewing under the action of vibrations and the plugs 32 extended inside the housing 1a have grooves in which are arranged seals tightness. 3a, 4a, surrounding the rods of screws 3 and 4.
  • the caps 32 are fitted into the housing 1a with a shoulder 35 and they are held by a crimped edge 36.
  • FIG. 5 there is shown another embodiment of the movable member 2 which has in its cylindrical part holes 6, 6a and 8, 8a located on each side of the central partition 2f, said holes which move opposite orifices of the half-conduits 11 and 13, the section of which is substantially equal to that of the holes 6, 6a and 8, 8a.
  • the spacing between the holes 6, 6a and 8, 8a makes it possible to vary the proportion of the flow rates between the purge and the feed.
  • the movable member 2 includes notches 37 for the passage of the fluid towards the half-conduits 12, 14 and it is immobilized in rotation in order to maintain the holes along the same longitudinal axis.
  • FIGS 6 and 7 there is shown another embodiment of the flow limiter in which housing la is closed on one side by a plug 32 screwed into the body 1 and on the other side by a partition of the body 1.
  • the screws 3 and 4 are provided with locknuts 3b and 4b having a circular housing in which is disposed a seal 3a and 4a.
  • the movable member 2 consists of a solid cylindrical body in which are provided channels 6 and 8 which more or less seal the orifices of the half-conduits 11, 12 and 13, 14 according to the adjustment of the stop screws 3 and 4.
  • FIG. 8 represents another mobile member 2 in the body 1 of a flow limiter.
  • the movable member has two annular grooves 2h and 2i, arranged on either side of the seal 10, said grooves being arranged so that the movable member 2 is in the middle position of the housing 1a the conduits 11, 12 and 13, 14 are at their maximum opening.
  • the width of the grooves 2h, 2i is such that only the passage of the intake duct 11, 12 is reduced while the passage of the exhaust duct 13-14 remains fully open, whatever the setting of the screw stop 4. It is the same for the other alternation.
  • FIG. 9 another embodiment of the movable member 2 has been shown in which the annular grooves 2h and 2i ensure maximum opening of the conduits 11, 12 and 13, 14 when the movable member 2 occupies a middle position in housing 1a.
  • the width of the grooves 2h and 2i is such that the orifices for passage of the intake and exhaust ducts are reduced simultaneously.
  • Figure 10 there is shown another embodiment of the movable member 2, which comprises two annular grooves 2h, 2i, arranged so that the movable member occupying a middle position in the housing 1a. the conduits 11, 12 and 13, 14 are completely closed.
  • the width of the grooves is such that the two passage conduits, 11, 12 and 13, 14 are partially open, as in the previous example, for any adjustment the sections of the orifices of passage are equal or unequal according to their center distance relative to that of the conduits.
  • FIG. 11 shows a flow limiter in which the head of the screws 3 and 4 is arranged in a blind hole 32c, plugs 32, said blind hole being closed by a shutter member 31 which is force fitted and which is held by a seal 31a engaged in a groove 32d, formed in the plug 32.
  • This arrangement makes it possible to prohibit access to the screws 3 and 4 when the adjustment is made.
  • Figure 12 shows the same movable member as in Figure 8 abutting on the screw 4 and in this case only the conduit 11, 12 corresponding to the intake represents a reduced section, and therefore the speed of the cylinder piston 5 is regulated by this only restriction.
  • Figure 13 shows the same movable member as previously in abutment on the screw 4 which has been moved back from its position of Figure 12.
  • the passage section of the intake duct 11, 12 is now completely closed while the section passage of the exhaust duct 13, 14 is completely open.
  • the speed of the cylinder piston is zero.
  • FIG. 14 represents the same movable member 2 on the stop screw 4 which has been moved back with respect to the position of FIG. 13. This greater freedom of travel given to the slide causes both partial closings in the following variable proportions adjusting the screw of the ducts 11, 12 and 13, 14.
  • FIG. 15 represents the movable member 2 in abutment on the screw 4 which has been moved back to the maximum allowing the total travel of the movable member. In this position the piston of the jack 5 stops by completely closing the exhaust duct 13, 14.
  • This device therefore makes it possible, by simply adjusting the screws 3 and 4, to choose in a progressive and continuous manner the mode of adjustment of the speed of the piston of the jack in each of the half-cycles.
  • FIGs 16 to 21 there is shown another embodiment of a flow limiter in which the movable member 2 has holes 6, 6a and 8, 8a which are previously drilled on the same generator with a diameter ⁇ . Then the holes 8 and 6a are angularly enlarged by a positive value a with respect to the common drilling axis p (fig. 19) and the holes 8a, and 6 are angularly enlarged by a negative value ⁇ with respect to this same axis 13 (fig. 21).
  • a flange 48 which has slots 38, 39, in which are engaged screws 28, 29 fixed in the body 1, said flange 48 being able to pivot along the axis of the movable member 2 on the body 1 at the angles a + and a-, and be locked in the chosen position by means of the screws 28, 29.
  • the flange 48 has a finger 27 which is slidably mounted in a hole 40 in the movable member 2 in order to drive the latter in rotation when the flange 48 is acted on.
  • FIG. 18 shows under these conditions the position of the hole 8a, and of the half-duct 13 as well as that of the hole 6a and the orifice 11, these positions. being determined longitudinally by the adjustment of the stop screw 4, the intake and exhaust passages then being equal.
  • a rotation of the flange 48 by an angle a + drives the movable member 2 by means of the finger 27.
  • FIG. 20 For the same adjustment of the screw 4 it is shown in FIG. 20 that there is a preponderance of the exhaust passage 13- 8a on the admission passage 6a-11.
  • a rotation of the flange 48 and of the movable member 2 by an angle a- causes, as shown in FIG. 22, an inversion of the preponderance.
  • the geometric shape of the holes in the movable member 2 can be arbitrary and different from the circular section for better progressiveness in adjusting the opening of the passages.
  • the flow restrictors described above have the form of a double connector which is reversible as regards the orientation of its connections with a distributor and a jack.
  • a flow restrictor comprising a movable member 2 of the type shown in Figure 1 and in which are provided oblong holes 8b, 8c and 6b, 6c, the geometric centers of the holes 8b , 8c located on the same side with respect to the seal 10 are diametrically opposite, as for the holes 6b, 6c located on the other side of the seal 10.
  • the geometric centers of the holes 8b and 6b are on the same generatrix and therefore holes 8c and 6c are on the diametrically opposite generator.
  • These oblong holes extend along an axis forming with their generatrix a positive angle for the holes 8b, 8c and a negative angle for the holes 6b and 6c.
  • the distance between the geometric centers of the holes 8b, 8c and 6b, 6c is equal to the distance between the axes of the conduits 11, 12 and 13, 14.
  • the housing 1a is closed at one of its ends by a plug 32 and at the other end by a plug 26 which has at one of its ends a lug 46 perpendicular to its axis which is engaged in a groove 47 formed in the movable member 2, on a generator different from that of the holes and open at one of its ends.
  • the plug 26 has an external element 26b in the form of a hexagon for driving the plug in rotation and consequently of the movable member 2, by means of the lug 46 engaged in the groove 47 of the movable member. This arrangement makes it possible to maintain the mobile member 2 in a determined angular position, without preventing its longitudinal displacement.
  • FIG. 29 the movable member 2 is shown in a neutral angular position and in abutment against the stop screw 4, while in FIG. 30, it is abut against the abutment screw 3. In this case, the through holes are equal.
  • Figures 31 and 32 the movable member 2 which has been moved in rotation by an angle a + and for the two alternations to the left and to the right, priority is given to intake flow over exhaust.
  • FIGS. 35 to 40 Another embodiment of a flow limiter shown in FIGS. 35 to 40 comprises, as in the previous example, a rotary plug 26a, which is extended on one side by a part of hexagonal section 26c, engaged in a hole 41, of corresponding section provided at one end of the movable member 2 so that the latter can be driven in rotation and in axial translation.
  • the plug 26a is extended externally by a part 26b, in the form of a hexagon for driving the plug 26a (FIGS. 35-36 and 40).
  • the movable member 2 shown in Figure 40 has on each side of the seal 10 two grooves 8d, and 6d which are extended by two longitudinal grooves extending in opposite directions, the grooves 8e and 8f corresponding to the groove 8d and the grooves 6e and 6f corresponding to the groove 6d.
  • the grooves 8e and 8f are located on the same generator different from that mentioned above. With respect to an average generator, the axes of these grooves are offset by an angle a + and a-.
  • the width of the grooves is substantially equal to that of the diameter of the passage conduits 11,12 and 13,14 when they exit into the housing 1a of the movable member and the distance which separates them on the circle is also equal to this diameter.
  • FIG. 37 represents the movable member in abutment on the screw 4 which regulates the speed of retraction of the rod of the jack 5. In the neutral angular position shown, the values of the orifices for passage of the outward and return flow rates are equal.
  • FIG 41 there is shown a flow limiter which is identical to that of Figure 6 but which comprises two return springs 22, 23 which act on both sides of the movable member 2.
  • the springs 22, 23 which are very weak have no influence during the pressure cycles on the movable member 2; however, when the device is stopped under pressurized fluid, they allow manual actuation of the jack, particularly in the event of an accident.
  • FIG 42 there is shown an alternative embodiment of a flow limiter in which the housing 1a comprises two throttling members 33 comprising an orifice having double cones 8 and 7 which cooperate with conical parts 42, 43 and 42a , 43a of the movable member 2 and regulate the passages and therefore the flow rates.
  • the two chambers 1b, and 1c, are isolated by the seal 10 mounted on the central part of the movable member.
  • the throttling members 33 are disposed respectively between the orifices of the half-conduits 11 and 12 and between the orifices of the half-conduits 13 and 14.
  • the plugs 32 each have a blind hole 44 in which is mounted each end 45 of the movable member for guiding the latter.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Sliding Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Actuator (AREA)
  • Lift Valve (AREA)
  • Safety Valves (AREA)

Abstract

Improvement to compressed air flow rate limiters arranged between a conventional compressed air dispenser and a pneumatic jack, in order to regulate the speed of a jack piston in each direction. It comprises a body (1) having a cylindrical housing (1a) limited by two bottoms (32) and wherein is axially and slidingly mounted a movable revolution member (2) of which the travel is limited at each end of the housing by an adjustable stop member, said body (1) being traversed perpendicularly to said cylindrical housing (1a) by two passage conduits (11, 12 and 13, 14) supplying the jack (5), said passage conduits (11, 12 and 13, 14) opening each into a chamber (1b, 1c) delimited by the bottom. The invention is intended to regulate the speed of a jack.

Description

La présente invention a pour objet un limiteur de débit d'air comprimé disposé entre un distributeur classique d'air comprimé et un vérin pneumatique.The present invention relates to a compressed air flow limiter arranged between a conventional compressed air distributor and a pneumatic cylinder.

Pour réduire la vitesse des vérins pneumatiques il est connu d'utiliser des limiteurs de débit qui comportent un passage réduit réglable pour limiter le débit dans un sens et en dérivation sur ce passage réduit, un clapet qui, fermé par la pression dans ce même sens, s'ouvre dans l'autre pour permettre le plein débit. Les limiteurs de débit sont utilisés soit pour limiter le débit d'admission dans la chambre motrice du vérin, soit pour limiter le débit évacué vers l'atmosphère à partir de l'autre chambre en vidange. Le débit d'admission étant seul limité, le démarrage du vérin est très rapide, la chambre à l'échappement se vidant très vite. Cette solution présente l'inconvénient, quand la charge du vérin tend à l'entraîner, de nuire au contrôle de la vitesse qui devient très grande. Lorsque des capteurs à chute de pression sont utilisés, ils peuvent émettre leurs signaux de fin de course prématurément par rapport à la fin de course réelle, en raison de la disparition rapide de la contre-pression d'échappement. Le débit d'échappement étant seul limité, le démarrage des vérins est lent, du fait de l'important volume d'air à évacuer par la restriction et il peut s'accompagner d'à-coups. Des capteurs à chute de pression ont tendance à déliver des signaux de fin de course d'autant plus retardés que la restriction de passage est importante. Le dispositif pour le réglage de la vitesse d'un vérin à double effet est donc constitué d'au moins deux limiteurs de débit soit d'admission soit d'échappement.To reduce the speed of pneumatic cylinders it is known to use flow limiters which have an adjustable reduced passage to limit the flow in one direction and bypass on this reduced passage, a valve which, closed by pressure in the same direction , opens in the other to allow full flow. The flow limiters are used either to limit the admission flow into the drive chamber of the jack, or to limit the flow discharged to the atmosphere from the other draining chamber. The admission flow being limited only, the starting of the cylinder is very fast, the exhaust chamber emptying very quickly. This solution has the disadvantage, when the load of the jack tends to drive it, to interfere with speed control which becomes very large. When pressure drop sensors are used, they can issue their limit switch signals prematurely compared to the actual limit switch, due to the rapid disappearance of the exhaust back pressure. The exhaust flow being limited only, the starting of the cylinders is slow, due to the large volume of air to be evacuated by the restriction and it can be accompanied by jolts. Pressure drop sensors tend to deliver end-of-travel signals that are all the more delayed as the passage restriction is important. The device for adjusting the speed of a double-acting cylinder therefore consists of at least two flow restrictors, either intake or exhaust.

Toutefois pour bénéficier des avantages inhérents à chacun des deux procédés, on est parfois amené à monter quatre limiteurs et les réglages deviennent très compliqués. On connaît également des distributeurs hydrauliques dans lesquels le tiroir est auto-piloté et soumis sur ses deux faces à l'action de ressorts. Toutefois, ce dispositif du fait qu'il est utilisé avec des liquides incompressibles comporte des passages qui fournissent des débits et ne permettent pas comme dans la présente demande où il s'agit de gaz compressibles de limiter la vitesse d'un vérin en contrôlant le débit d'air.However, to benefit from the advantages inherent in each of the two methods, it is sometimes necessary to mount four limiters and the adjustments become very complicated. Hydraulic distributors are also known in which the drawer is self-piloting and subjected on its two faces to the action of springs. However, this device due to the fact that it is used with incompressible liquids has passages which provide flow rates and do not allow, as in the present application where it is a matter of compressible gases, to limit the speed of a jack by controlling the air flow.

Par ailleurs la faible viscosité de l'air engendrerait des phénomènes de vibration inacceptables pour des équilibres entre les deux ressorts.Furthermore, the low viscosity of the air would generate vibration phenomena that are unacceptable for equilibria between the two springs.

Enfin, ce dispositif connu ne permet pas un réglage facile de la position du tiroir au moyen de butées mobiles. Le dispositif suivant la présente invention permet d'éliminer les inconvénients liés à l'usage des limiteurs et des dispositifs connus pour régler la vitesse des moyens d'actionnement pneumatiques tels que les vérins.Finally, this known device does not allow easy adjustment of the position of the drawer by means of movable stops. The device according to the present invention makes it possible to eliminate the drawbacks associated with the use of limiters and known devices for adjusting the speed of the pneumatic actuation means such as the jacks.

Conformément à la présente invention, le limiteur de débit d'air comprend un corps présentant un logement cylindrique limité par deux fonds et dans lequel est monté coulissant axialement un organe mobile de révolution dont la course est limitée à chaque extrémité du logement par un organe de butée réglable, ledit corps étant traversé perpendiculairement audit logement cylindrique par deux conduits de passage alimentant le vérin, lesdits conduits de passage débouchant chacun dans une chambre délimitées par le fond, le logement cylindrique et l'organe mobile, ledit organe mobile comportant un moyen d'étanchéité central assurant l'isolement entre les deux chambres délimitées aux deux extrémités du logement bistable, assurant le réglage de l'ouverture des conduits de passage en fonction de la position des organes de butée situés aux deux extrémités du logement, de telle sorte qu'il en résulte un réglage des débits d'air d'alimentation et de purge des deux volumes d'air du vérin à double effet et ce, dans chaque sens de déplacement du piston de vérin.According to the present invention, the air flow limiter comprises a body having a cylindrical housing bounded by two bottoms and in which is slidably mounted axially a movable member of revolution whose stroke is limited at each end of the housing by a member adjustable stop, said body being traversed perpendicularly to said cylindrical housing by two passage conduits supplying the actuator, said passage conduits each opening into a chamber delimited by the bottom, the cylindrical housing and the movable member, said movable member comprising a means of '' central seal ensuring the isolation between the two chambers defined at the two ends of the bistable housing, ensuring the adjustment of the opening of the passage conduits according to the position of the stop members located at the two ends of the housing, so that 'this results in an adjustment of the supply air and purge flow rates of the two air volumes of the double ef cylinder fet and this, in each direction of movement of the cylinder piston.

Le dispositif suivant l'invention permet de régler pour chacun des deux sens de la course, à la fois, le débit d'admission et le débit d'échappement d'air à l'aide d'un réglage unique pour chaque sens. Ce limiteur de débit disposé entre un distributeur d'air comprimé et un vérin pneumatique permet de régler la vitesse du piston d'un vérin dans chaque sens.The device according to the invention makes it possible to adjust for each of the two directions of travel, both the intake flow and the exhaust air flow using a single adjustment for each direction. This flow limiter arranged between a compressed air distributor and a pneumatic cylinder makes it possible to adjust the speed of the piston of a cylinder in each direction.

Il ne comporte aucun clapet de retour. Pour une valeur de réglage donnée, les sections des orifices de passage offertes aux débits aller et retour peuvent être égales ou inégales ou présenter entre elles un rapport variable,. et dans ce dernier cas on peut utiliser un réglage unique pour les deux alternances permettant de favoriser le passage d'admission au détriment du passage d'échappement, et inversement. Le limiteur de débit suivant l'invention se raccorde par ses deux orifices d'entrée aux deux orifices de sortie d'un distributeur et par ses deux orifices de sortie aux deux orifices d'entrée d'un vérin à double effet.There is no return valve. For a given setting value, the sections of the passage openings offered at the outward and return flow rates can be equal or unequal or have a variable relationship between them. and in the latter case, it is possible to use a single adjustment for the two half-cycles enabling the intake passage to be favored to the detriment of the exhaust passage, and vice versa. The flow limiter according to the invention is connected by its two inlet ports to the two outlet ports of a distributor and by its two outlet ports to the two inlet ports of a double-acting cylinder.

Avec le dispositif suivant l'invention, du fait que l'on utilise un organe mobile obturateur à l'échappement, l'inversion du mouvement du piston du vérin est fonction d'une différence de pression suffisante entre les chambres du régleur et le démarrage du vérin avec le régleur double est beaucoup plus rapide en réglage pour la purge qu'avec des régleurs classiques.With the device according to the invention, due to the fact that a movable shutter member is used on the exhaust, the reversal of the movement of the piston of the jack is a function of a sufficient pressure difference between the chambers of the regulator and the starting. of the cylinder with the double adjuster is much faster in setting for the purge than with conventional adjusters.

D'autres caractéristiques et avantages de l'invention seront mieux compris à la lecture de la description qui va suivre de plusieurs modes de réalisation et en se référant aux dessins annexés sur lesquels :

  • La figure 1 est une vue en coupe axiale d'un limiteur de débit d'air comprimé suivant l'invention relié à un distributeur et à un vérin.
  • La figure 2 est une même vue d'un limiteur de débit avec un autre mode d'étanchéité de l'organe mobile.
  • La figure 3 est une vue en coupe d'un autre mode de réalisation d'un organe mobile.
  • La figure 4 est une vue en coupe axiale d'un limiteur de débit avec un autre mode de réalisation des butées.
  • La figure 5 est une vue en coupe axiale d'un limiteur de débit comportant un autre mode de réalisation d'un organe mobile.
  • La figure 6 est une vue en coupe axiale d'un limiteur de débit avec un organe mobile en une seule pièce.
  • La figure 7 est une vue en coupe suivant la ligne VII-VII de la figure 6.
  • Les figures 8 à 15 sont des vues en coupe axiale de limiteurs de débit comportant des organes mobiles munis de gorges pour le contrôle des orifices de passage d'air.
  • La figure 16 est une vue en coupe axiale d'un limiteur de débit comportant un organe mobile à déplacement angulaire et axial.
  • La figure 17 est une vue de l'une des extrémités du limiteur de débit montrant un flasque de réglage.
  • La figure 18 est une vue de l'organe mobile et les orifices pour la position médiane du flasque à la figure 17.
  • Les figures 19 et 20 sont des vues de l'organe mobile en coupe et en élévation pour une position a+ du flasque.
  • Les figures 21 et 22 sont des vues de l'organe mobile en coupe et en élévation pour une position α­ du flasque.
  • Les figures 23 et 24 sont des vues schématiques de montage du limiteur de débit.
  • La figure 25 est une vue en coupe axiale d'un limiteur de débit avec un moyen de commande de l'organe mobile.
  • La figure 26 est une vue en coupe suivant la ligne XXVI-XXVI de la figure 25.
  • La figure 27 est une vue en coupe axiale du limiteur de débit décalée de 90° par rapport à la figure 25.
  • .La figure 28 est une vue en bout du limiteur de débit représenté à la figure 27.
  • Les figure 29 à 34 sont des vues de l'organe mobile dans différentes positions pàr rapport au corps.
  • La figure 35 est une vue en coupe axiale d'un autre mode de réalisation d'un limiteur de débit avec un moyen de manoeuvre de l'organe mobile.
  • La figure 36 est une vue en coupe suivant la ligne XXXVI-XXXVI de la ligne 35.
  • Les figures 37 à 39 sont des vues de l'organe mobile dans différentes positions.
  • La figure 40 est une vue en perspective de l'organe mobile représenté aux figures 37 à 39.
  • La figure 41 est une vue en coupe axiale d'un limiteur de débit muni de ressorts de rappel.
  • La figure 42 est une vue en coupe axiale d'un autre mode de réalisation d'un limiteur de débit suivant l'invention.
Other characteristics and advantages of the invention will be better understood on reading the following description of several embodiments and with reference to the appended drawings in which:
  • Figure 1 is an axial sectional view of a compressed air flow limiter according to the invention connected to a distributor and a cylinder.
  • Figure 2 is the same view of a flow limiter with another sealing mode of the movable member.
  • Figure 3 is a sectional view of another embodiment of a movable member.
  • Figure 4 is an axial sectional view of a flow restrictor with another embodiment of the stops.
  • Figure 5 is an axial sectional view of a flow restrictor comprising another embodiment of a movable member.
  • Figure 6 is an axial sectional view of a flow restrictor with a movable member in one piece.
  • Figure 7 is a sectional view along line VII-VII of Figure 6.
  • Figures 8 to 15 are views in axial section of flow restrictors comprising movable members provided with grooves for controlling the air passage orifices.
  • Figure 16 is an axial sectional view of a flow restrictor comprising a movable member with angular and axial movement.
  • Figure 17 is a view of one end of the flow limiter showing an adjustment flange.
  • FIG. 18 is a view of the movable member and the orifices for the middle position of the flange in FIG. 17.
  • Figures 19 and 20 are views of the movable member in section and in elevation for a position a + of the flange.
  • Figures 21 and 22 are views of the movable member in section and in elevation for an α position of the flange.
  • Figures 23 and 24 are schematic views of mounting the flow restrictor.
  • Figure 25 is an axial sectional view of a flow limiter with a control means of the movable member.
  • Figure 26 is a sectional view along line XXVI-XXVI of Figure 25.
  • FIG. 27 is a view in axial section of the flow limiter offset by 90 ° relative to FIG. 25.
  • .Figure 28 is an end view of the flow limiter shown in Figure 27.
  • Figures 29 to 34 are views of the movable member in different positions relative to the body.
  • FIG. 35 is a view in axial section of another embodiment of a flow limiter with means for maneuvering the movable member.
  • Figure 36 is a sectional view along line XXXVI-XXXVI of line 35.
  • Figures 37 to 39 are views of the movable member in different positions.
  • FIG. 40 is a perspective view of the movable member shown in FIGS. 37 to 39.
  • Figure 41 is an axial sectional view of a flow restrictor provided with return springs.
  • FIG. 42 is a view in axial section of another embodiment of a flow limiter according to the invention.

Aux figures 1 et 2 on a représenté un mode de réalisation d'un limiteur de débit qui est disposé entre un distributeur d'air comprimé 15 et un vérin à double effet 5. Le limiteur de débit comprend un corps 1 présentant un alésage ou logement cylindrique 1a limité par deux fonds et dans lequel est monté coulissant axialement un organe mobile 2 de révolution dont la course est limitée à chaque extrémité du logement par un organe de butée constitué par une vis 3, 4, engagée dans un trou taraudé 32b d'un bouchon 32 obturant les deux extrémités du logement cylindrique 1a, ledit bouchon étant engagé à force dans le logement 1a avec interposition d'un joint d'étanchéité annulaire 32a disposé dans une gorge du bouchon 32.In Figures 1 and 2 there is shown an embodiment of a flow limiter which is arranged between a compressed air distributor 15 and a double-acting cylinder 5. The flow limiter comprises a body 1 having a bore or housing cylindrical 1a limited by two bottoms and in which is slidably mounted an axially movable member 2 of revolution whose stroke is limited at each end of the housing by a stop member constituted by a screw 3, 4, engaged in a tapped hole 32b of a plug 32 closing off the two ends of the cylindrical housing 1a, said plug being forcibly engaged in the housing 1a with the interposition of an annular seal 32a disposed in a groove in the plug 32.

La tête des vis 3, 4 est engagée dans un trou borgne 32c prévu dans les bouchons 32, avec interposition d'un joint annulaire d'étanchéité 3a, 4a.The head of the screws 3, 4 is engaged in a blind hole 32c provided in the plugs 32, with the interposition of an annular seal 3a, 4a.

Le corps 1 est traversé perpendiculairement au logement 1a par deux conduits de passage 11, 12 et 13, 14 alimentant le vérin 5, ledit conduit 11, 12 débouchant dans une chambre 1 b et ledit conduit 13, 14 débouchant dans une chambre 1c. Les chambres 1 b et 1 c sont délimitées par le bouchon 32, le logement cylindrique 1a et l'organe mobile 2, ledit organe mobile comportant un joint d'étanchéité annulaire central 10, disposé dans une gorge 2g dudit organe mobile et assurant l'isolement entre les deux chambres 1 b et 1c.The body 1 is crossed perpendicularly to the housing 1a by two passage conduits 11, 12 and 13, 14 supplying the jack 5, said conduit 11, 12 opening into a chamber 1b and said conduit 13, 14 opening into a chamber 1c. The chambers 1b and 1c are delimited by the plug 32, the cylindrical housing 1a and the movable member 2, said movable member comprising a central annular seal 10, disposed in a groove 2g of said movable member and ensuring the isolation between the two chambers 1b and 1c.

L'organe mobile 2 est constitué d'une seule pièce cylindrique (Fig. 1, 2) présentant une cloison centrale 2f, délimitant de chaque côté un évidement 2c, et contre laquelle sont susceptibles de venir en butée les vis 3 et 4 pour limiter la course de l'organe mobile 2.The movable member 2 consists of a single cylindrical part (Fig. 1, 2) having a central partition 2f, delimiting on each side a recess 2c, and against which the screws 3 and 4 are likely to abut to limit the stroke of the movable member 2.

Le corps 1 du limiteur de débit est relié par ses demi-conduits 11, 13 au vérin 5 et par ses demi-conduits 12, 14 au distributeur d'air comprimé qui est relié à une source P d'air comprimé et à des échappements EA et EB reliés à l'atmosphère.The body 1 of the flow limiter is connected by its half-ducts 11, 13 to the jack 5 and by its half-ducts 12, 14 to the compressed air distributor which is connected to a source P of compressed air and to exhausts EA and EB linked to the atmosphere.

Lorsque le tiroir du distributeur se trouve dans la position représentée aux figures 1 et 2, il alimente en air comprimé le demi-conduit 12 repoussant ainsi l'organe mobile 2 qui agit comme un piston vers la gauche et alimentant à travers le logement 1 a et le demi-conduit 11 l'un des côtés du vérin 5.When the dispenser drawer is in the position shown in FIGS. 1 and 2, it supplies compressed air to the semi-duct 12 thus pushing the movable member 2 which acts like a piston to the left and feeding through the housing 1 a and the half-duct 11 one of the sides of the jack 5.

L'organe mobile est en butée contre l'extrémité de la vis 4 qui a été réglée préalablement pour obturer plus ou moins l'orifice de passage correspondant au conduit 13, 14 qui est relié à la chambre du vérin 5 qui se trouve à l'échappement par le distributeur 15. Il en résulte que le débit d'air s'échappant du vérin 5 est réglé par l'orifice. délimité entre le bord circulaire 34 de l'organe mobile et les orifices des demi-conduits 13, 14, la position de l'organe mobile 2 étant déterminé par la position de la vis 4.The movable member is in abutment against the end of the screw 4 which has been adjusted beforehand to more or less close the passage orifice corresponding to the conduit 13, 14 which is connected to the chamber of the jack 5 which is located at the exhaust through the distributor 15. As a result, the air flow rate escaping from the jack 5 is regulated by the orifice. delimited between the circular edge 34 of the movable member and the orifices of the half-ducts 13, 14, the position of the movable member 2 being determined by the position of the screw 4.

En contrôlant le débit de l'air s'échappant par le conduit 13, 14 on contrôle également la vitesse de déplacement du piston 5a dans le vérin 5, puisque cette vitesse est fonction de la résistance opposée par l'air s'échappant du vérin par le conduit 13, 14, dont l'orifice est plus ou moins obturé.By controlling the flow rate of the air escaping through the duct 13, 14, the speed of movement of the piston 5a in the jack 5 is also controlled, since this speed is a function of the resistance opposed by the air escaping from the jack by the conduit 13, 14, the orifice of which is more or less closed.

Le régleur de la figure 1 permet le réglage du débit sur l'échappement, l'admission étant grande ouverte et ceci dans chaque sens.The adjuster of Figure 1 allows the adjustment of the flow rate on the exhaust, the intake being wide open and this in each direction.

De la même manière la vis 3 est réglée pour obturer plus ou moins les orifices des conduits 11, 12 lorsque l'admission s'effectue par le conduit 13, 14, et que l'organe mobile 2 est repoussé vers la droite.In the same way the screw 3 is adjusted for close more or less the orifices of the conduits 11, 12 when the admission takes place via the conduit 13, 14, and when the movable member 2 is pushed to the right.

L'organe mobile 2 bi-stable en butée à droite ou à gauche suivant le cycle du vérin, obture plus ou moins suivant le réglage des vis de butée 3, 4, les orifices de passage des conduits 11, 12 et 13, 14 réglant ainsi les débits d'air de purge dans chaque sens.The movable member 2 bi-stable in abutment to the right or to the left according to the cylinder cycle, more or less closes depending on the adjustment of the abutment screws 3, 4, the orifices for passage of the conduits 11, 12 and 13, 14 regulating thus the purge air flows in each direction.

A la figure 2 le joint 10 assurant l'étanchéité entre les chambres 1b et 1c est monté dans une gorge 1 ménagée dans le corps et en contact avec la surface extérieure cylindrique de l'organe mobile 2.In FIG. 2, the seal 10 ensuring the seal between the chambers 1b and 1c is mounted in a groove 1 formed in the body and in contact with the cylindrical outer surface of the movable member 2.

Aux figures 3 et 4 on a représenté un autre mode de réalisation de l'organe mobile 2 qui est constitué de deux éléments identiques 2a, 2b ou complémentaires assemblés au moyen d'un rivet 2d ou d'une vis, lesdits éléments délimitant entre eux un logement dans lequel est disposé un joint d'étanchéité 2e disposé autour du rivet 2d. A l'extérieur des deux éléments 2a, 2b et sur leur plan de joint il est prévu une gorge 2g destinée à recevoir un joint d'étanchéité 10.In Figures 3 and 4 there is shown another embodiment of the movable member 2 which consists of two identical elements 2a, 2b or complementary assembled by means of a rivet 2d or a screw, said elements delimiting between them a housing in which is disposed a seal 2e disposed around the rivet 2d. Outside the two elements 2a, 2b and on their joint plane there is provided a groove 2g intended to receive a seal 10.

L'assemblage des éléments 2a, 2b, facilite le passage du joint 10 en regard des conduits de passage 11, 12 et 13, 14, à l'intérieur du logement 1a du corps 1.The assembly of the elements 2a, 2b, facilitates the passage of the seal 10 opposite the passage conduits 11, 12 and 13, 14, inside the housing 1a of the body 1.

Comme représenté à la figure 3 et décrit ci-dessus le corps 1 de la figure 2 peut être réalisé en deux pièces symétriques ou complémentaires.As shown in Figure 3 and described above the body 1 of Figure 2 can be made in two symmetrical or complementary parts.

Dans le mode de réalisation de la figure 4 les vis de butée 3 et 4 sont montées dans les bouchons 32, de telle sorte que leur tête s'étend à l'extérieur. Les vis 3 et 4 sont munies de contre-écrous 3b et 4b empêchant celles-ci de se dévisser sous l'action des vibrations et les bouchons 32 prolongés à l'intérieur du logement 1a comportent des gorges dans lesquelles sont disposés des joints d'étanchéité.3a, 4a, entourant les tiges des vis 3 et 4.In the embodiment of Figure 4 the stop screws 3 and 4 are mounted in the plugs 32, so that their head extends outside. The screws 3 and 4 are provided with locknuts 3b and 4b preventing these from unscrewing under the action of vibrations and the plugs 32 extended inside the housing 1a have grooves in which are arranged seals tightness. 3a, 4a, surrounding the rods of screws 3 and 4.

Les bouchons 32 sont emmanchés dans le logement la avec un épaulement 35 et ils sont maintenus par un bord serti 36.The caps 32 are fitted into the housing 1a with a shoulder 35 and they are held by a crimped edge 36.

A la figure 5 on a représenté un autre mode de réalisation de l'organe mobile 2 qui comporte dans sa partie cylindrique des trous 6, 6a et 8, 8a situés de chaque côté de la cloison centrale 2f, lesdits trous qui se déplacent en regard des orifices des demi-conduits 11 et 13 dont la section est sensiblement égale à celle des trous 6, 6a et 8, 8a. L'écartement entre les trous 6, 6a et 8, 8a, permet de faire varier la proportion des débits entre la purge et l'alimentation.In Figure 5 there is shown another embodiment of the movable member 2 which has in its cylindrical part holes 6, 6a and 8, 8a located on each side of the central partition 2f, said holes which move opposite orifices of the half-conduits 11 and 13, the section of which is substantially equal to that of the holes 6, 6a and 8, 8a. The spacing between the holes 6, 6a and 8, 8a makes it possible to vary the proportion of the flow rates between the purge and the feed.

Bien entendu l'organe mobile 2 comporte des échancrures 37 pour le passage du fluide vers les demi-conduits 12, 14 et il est immobilisé en rotation afin de maintenir les trous suivant le même axe longitudinal.Of course, the movable member 2 includes notches 37 for the passage of the fluid towards the half-conduits 12, 14 and it is immobilized in rotation in order to maintain the holes along the same longitudinal axis.

Aux figures 6 et 7 on a représenté un autre mode de réalisation du limiteur de débit dans lequel logement la est obturé d'un côté par un bouchon 32 vissé dans le corps 1 et de l'autre côté par une cloison du corps 1. Les vis 3 et 4 sont munies de contre-écrous 3b et 4b présentant un logement circulaire dans lequel est disposé un joint d'étanchéité 3a et 4a.In Figures 6 and 7 there is shown another embodiment of the flow limiter in which housing la is closed on one side by a plug 32 screwed into the body 1 and on the other side by a partition of the body 1. The screws 3 and 4 are provided with locknuts 3b and 4b having a circular housing in which is disposed a seal 3a and 4a.

L'organe mobile 2 est constitué d'un corps cylindrique plein dans lequel sont prévus des canaux 6 et 8 qui viennent obturer plus ou moins les orifices des demi-conduits 11, 12 et 13, 14 suivant le réglage des vis de butée 3 et 4.The movable member 2 consists of a solid cylindrical body in which are provided channels 6 and 8 which more or less seal the orifices of the half-conduits 11, 12 and 13, 14 according to the adjustment of the stop screws 3 and 4.

L'action du fluide moteur s'exerce sur l'organe mobile à travers des canaux 16, 17 débouchant dans les canaux 6 et 8 et dans les chambres 1a et 1b.The action of the working fluid is exerted on the movable member through channels 16, 17 opening into channels 6 and 8 and into chambers 1a and 1b.

On peut remarquer : a) Que si l'entr'axe des canaux 6-8 est le même que celui des conduits 11-13 et 12-14, dans chaque alternance la valeur des passages d'admission et d'échappement est identique. b) Si l'entr'axe des canaux 6-8 est plus petit que celui des conduits 11-13 et 12-14 dans chaque alternance la valeur du passage d'admission est plus petite que celle du passage d'échappement. c) Si l'entr'axe des canaux 6-8 est plus grand que celui des conduits 11-13 et 12-14, dans chaque alternance la valeur du passage d'admission est plus grande que celle du passage d'échappement.It can be noted: a) That if the distance between the axes of channels 6-8 is the same as that of the ducts 11-13 and 12-14, in each alternation the value of the intake and exhaust passages is identical. b) If the distance between the channels 6-8 is smaller than that of the ducts 11-13 and 12-14 in each alternation, the value of the intake passage is smaller than that of the exhaust passage. c) If the distance between the channels 6-8 is greater than that of the ducts 11-13 and 12-14, in each alternation the value of the intake passage is greater than that of the exhaust passage.

La figure 8 représente un autre organe mobile 2 dans le corps 1 d'un limiteur de débit. L'organe mobile comporte deux gorges annulaires 2h et 2i, disposées de part et d'autre du joint 10, lesdites gorges étant disposées de telle sorte que l'organe mobile 2 étant dans la position médiane du logement 1a les conduits 11, 12 et 13, 14 sont à leur ouverture maximum. Dans ce dispositif la largeur des gorges 2h, 2i est telle que seul le passage du conduit d'admission 11, 12 est réduit alors que le passage du conduit d'échappement 13-14 reste pleinement ouvert, quel que soit le réglage de la vis de butée 4. Il en est de même pour l'autre alternance.FIG. 8 represents another mobile member 2 in the body 1 of a flow limiter. The movable member has two annular grooves 2h and 2i, arranged on either side of the seal 10, said grooves being arranged so that the movable member 2 is in the middle position of the housing 1a the conduits 11, 12 and 13, 14 are at their maximum opening. In this device the width of the grooves 2h, 2i is such that only the passage of the intake duct 11, 12 is reduced while the passage of the exhaust duct 13-14 remains fully open, whatever the setting of the screw stop 4. It is the same for the other alternation.

A la figure 9 on a représenté un autre mode de réalisation de l'organe mobile 2 dans lequel les gorges annulaires 2h et 2i assurent une ouverture maximum des conduits 11, 12 et 13, 14 lorsque l'organe mobile 2 occupe une position médiane dans le logement 1a. Dans la position représentée à la figure 9, la largeur des gorges 2h et 2i est telle que les orifices de passage des conduits d'admission et d'échappement sont réduits simultanément.In FIG. 9 another embodiment of the movable member 2 has been shown in which the annular grooves 2h and 2i ensure maximum opening of the conduits 11, 12 and 13, 14 when the movable member 2 occupies a middle position in housing 1a. In the position shown in Figure 9, the width of the grooves 2h and 2i is such that the orifices for passage of the intake and exhaust ducts are reduced simultaneously.

Suivant que l'entr'axe des deux gorges 2h, 2i de l'organe mobile et des conduits 11, 12 et 13, 14 est égal ou non, les restrictions des orifices de passage seront pour tout réglage égales ou inégales.Depending on whether the distance between the two grooves 2h, 2i of the movable member and of the conduits 11, 12 and 13, 14 is equal or not, the restrictions of the passage orifices will be for all adjustments equal or unequal.

A la figure 10 on a représenté un autre mode de réalisation de l'organe mobile 2, qui comporte deux gorges annulaires 2h, 2i, disposées de telle sorte que l'organe mobile occupant une position médiane dans le logement 1a. les conduits 11, 12 et 13, 14 sont complètement obturés. Dans le mode de réalisation représenté à la figure 10, la largeur des gorges est telle que les deux conduits de passage, 11, 12 et 13, 14 sont partiellement ouverts, comme dans l'exemple précédent, pour tout réglage les sections des orifices de passage sont égales ou inégales suivant leur entr'axe par rapport à celui des conduits.In Figure 10 there is shown another embodiment of the movable member 2, which comprises two annular grooves 2h, 2i, arranged so that the movable member occupying a middle position in the housing 1a. the conduits 11, 12 and 13, 14 are completely closed. In the embodiment shown in Figure 10, the width of the grooves is such that the two passage conduits, 11, 12 and 13, 14 are partially open, as in the previous example, for any adjustment the sections of the orifices of passage are equal or unequal according to their center distance relative to that of the conduits.

Cet organe mobile permet la réduction des deux passages dans chaque alternance. A la figure 11 on a représenté un limiteur de débit dans lequel la tête des vis 3 et 4 est disposée dans un trou borgne 32c, des bouchons 32, ledit trou borgne étant fermé par un organe d'obturation 31 qui est emmanché à force et qui est maintenu par un joint 31a engagé dans une gorge 32d, ménagé dans le bouchon 32. Cette disposition permet d'interdire l'accès aux vis 3 et 4 lorsque le réglage est effectué.This movable member allows the reduction of the two passages in each alternation. FIG. 11 shows a flow limiter in which the head of the screws 3 and 4 is arranged in a blind hole 32c, plugs 32, said blind hole being closed by a shutter member 31 which is force fitted and which is held by a seal 31a engaged in a groove 32d, formed in the plug 32. This arrangement makes it possible to prohibit access to the screws 3 and 4 when the adjustment is made.

La figure 12 représente le même organe mobile qu'à la figure 8 en butée sur la vis 4 et dans ce cas seul le conduit 11, 12 correspondant à l'admission représente une section réduite, et de ce fait la vitesse du piston du vérin 5 est réglée par cette seule restriction.Figure 12 shows the same movable member as in Figure 8 abutting on the screw 4 and in this case only the conduit 11, 12 corresponding to the intake represents a reduced section, and therefore the speed of the cylinder piston 5 is regulated by this only restriction.

La figure 13 représente le même organe mobile que précédemment en butée sur la vis 4 qui a été reculée par rapport à sa position de la figure 12. La section de passage du conduit d'admission 11, 12 est maintenant totalement fermée tandis que la section de passage du conduit d'échappement 13, 14 est totalement ouverte. La vitesse du piston du vérin est nulle.Figure 13 shows the same movable member as previously in abutment on the screw 4 which has been moved back from its position of Figure 12. The passage section of the intake duct 11, 12 is now completely closed while the section passage of the exhaust duct 13, 14 is completely open. The speed of the cylinder piston is zero.

La figure 14 représente le même organe mobile 2 sur la vis de butée 4 qui a été reculée par rapport à la position de la figure 13. Cette plus grande liberté de course donnée au coulisseau provoque à la fois les fermetures partielles dans les proportions variables suivant le réglage de la vis des conduits 11, 12 et 13, 14.FIG. 14 represents the same movable member 2 on the stop screw 4 which has been moved back with respect to the position of FIG. 13. This greater freedom of travel given to the slide causes both partial closings in the following variable proportions adjusting the screw of the ducts 11, 12 and 13, 14.

La figure 15 représente l'organe mobile 2 en butée sur la vis 4 qui a été reculée au maximum permettant la course totale de l'organe mobile. Dans cette position le piston du vérin 5 s'arrête par la fermeture totale du conduit d'échappement 13, 14.FIG. 15 represents the movable member 2 in abutment on the screw 4 which has been moved back to the maximum allowing the total travel of the movable member. In this position the piston of the jack 5 stops by completely closing the exhaust duct 13, 14.

Ce dispositif permet donc par le simple réglage des vis 3 et 4 de choisir de façon progressive et continue le mode de réglage de la vitesse du piston du vérin dans chacune des alternances.This device therefore makes it possible, by simply adjusting the screws 3 and 4, to choose in a progressive and continuous manner the mode of adjustment of the speed of the piston of the jack in each of the half-cycles.

Aux figures 16 à 21 on a représenté un autre mode de réalisation d'un limiteur de débit dans lequel l'organe mobile 2 présente des trous 6, 6a et 8, 8a qui sont préalablement percés sur une même génératrice d'un diamètre β. Ensuite les trous 8 et 6a sont agrandis angulairement d'une valeur positive a par rapport à l'axe commun de perçage p (fig. 19) et les trous 8a, et 6 sont agrandis angulairement d'une valeur négative α par rapport à ce même axe 13 (fig. 21).In Figures 16 to 21 there is shown another embodiment of a flow limiter in which the movable member 2 has holes 6, 6a and 8, 8a which are previously drilled on the same generator with a diameter β. Then the holes 8 and 6a are angularly enlarged by a positive value a with respect to the common drilling axis p (fig. 19) and the holes 8a, and 6 are angularly enlarged by a negative value α with respect to this same axis 13 (fig. 21).

A l'une des extrémités du corps 1 est monté pivotant un flasque 48 qui présente des lumières 38, 39, dans lesquelles sont engagées des vis 28, 29 fixées dans le corps 1, ledit flasque 48 pouvant pivoter suivant l'axe de l'organe mobile 2 sur le corps 1 suivant les angles a+ et a-, et être bloqué dans la position choisie au moyen des vis 28, 29.At one end of the body 1 is pivotally mounted a flange 48 which has slots 38, 39, in which are engaged screws 28, 29 fixed in the body 1, said flange 48 being able to pivot along the axis of the movable member 2 on the body 1 at the angles a + and a-, and be locked in the chosen position by means of the screws 28, 29.

Par ailleurs le flasque 48 comporte un doigt 27 qui est monté coulissant dans un trou 40 de l'organe mobile 2 afin d'entraîner en rotation ce dernier lorsqu'on agit sur le flasque 48.Furthermore, the flange 48 has a finger 27 which is slidably mounted in a hole 40 in the movable member 2 in order to drive the latter in rotation when the flange 48 is acted on.

Dans la position médiane du flasque 48 indiquée à la figure 17, l'organe mobile 2 occupe, en rotation une position telle que l'axe p est confondu avec les axes des demi-conduits 11 et 13. La figure 18 montre dans ces conditions la position du trou 8a, et du demi-conduit 13 ainsi que celle du trou 6a et de l'orifice 11, ces positions . étant déterminées longitudinalement par le réglage de la vis de butée 4, les passages d'admission et d'échappement étant alors égaux. Une rotation du flasque 48 d'un angle a+ entraîne au moyen du doigt 27 l'organe mobile 2. Pour le même réglage de la vis 4 il est montré à la figure 20 qu'il y a prépondérance du passage d'échappement 13-8a sur le passage d'admission 6a-11.In the middle position of the flange 48 indicated in FIG. 17, the movable member 2 occupies, in rotation, a position such that the axis p coincides with the axes of the half-conduits 11 and 13. FIG. 18 shows under these conditions the position of the hole 8a, and of the half-duct 13 as well as that of the hole 6a and the orifice 11, these positions. being determined longitudinally by the adjustment of the stop screw 4, the intake and exhaust passages then being equal. A rotation of the flange 48 by an angle a + drives the movable member 2 by means of the finger 27. For the same adjustment of the screw 4 it is shown in FIG. 20 that there is a preponderance of the exhaust passage 13- 8a on the admission passage 6a-11.

Une rotation du flasque 48 et de l'organe mobile 2 d'un angle a- provoque comme représenté à la figure 22 une inversion de la prépondérance. La forme géométrique des trous dans l'organe mobile 2 peut être quelconque et différente de la section circulaire pour une meilleure progressivité du réglage de l'ouverture des passages. Les limiteurs de débit décrits ci-dessus présentent la forme d'un raccord double qui est réversible quant à l'orientation de ses branchements avec un distributeur et un vérin.A rotation of the flange 48 and of the movable member 2 by an angle a- causes, as shown in FIG. 22, an inversion of the preponderance. The geometric shape of the holes in the movable member 2 can be arbitrary and different from the circular section for better progressiveness in adjusting the opening of the passages. The flow restrictors described above have the form of a double connector which is reversible as regards the orientation of its connections with a distributor and a jack.

A la figure 23 on a représenté des corps de limiteurs disposés suivant quatre positions dans lesquelles les branchements sont parallèles. Alors qu'à la figure 24 on a représenté les corps de limiteurs disposés suivant quatre positions dont les branchements sont croisés.In Figure 23 there are shown bodies of limiters arranged in four positions in which the connections are parallel. While in Figure 24 there is shown the limiter bodies arranged in four positions whose connections are crossed.

Aux figures 25, 26, 27, 28 on a représenté un limiteur de débit comportant un organe mobile 2 du type représenté à la figure 1 et dans lequel sont prévus des trous oblongs 8b, 8c et 6b, 6c, les centres géométriques des trous 8b, 8c situés du même côté par rapport au joint 10 sont diamétralement opposés, de même que pour les trous 6b, 6c situés de l'autre côté du joint 10. Les centres géométriques des trous 8b et 6b sont sur une même génératrice et par conséquent les trous 8c et 6c sont sur la génératrice diamétralement opposée. Ces trous oblongs s'étendent suivant un axe formant avec leur génératrice un angle positif pour les trous 8b, 8c et un angle négatif pour les trous 6b et 6c.In Figures 25, 26, 27, 28 there is shown a flow restrictor comprising a movable member 2 of the type shown in Figure 1 and in which are provided oblong holes 8b, 8c and 6b, 6c, the geometric centers of the holes 8b , 8c located on the same side with respect to the seal 10 are diametrically opposite, as for the holes 6b, 6c located on the other side of the seal 10. The geometric centers of the holes 8b and 6b are on the same generatrix and therefore holes 8c and 6c are on the diametrically opposite generator. These oblong holes extend along an axis forming with their generatrix a positive angle for the holes 8b, 8c and a negative angle for the holes 6b and 6c.

Là distance entre les centres géométriques des trous 8b, 8c et 6b, 6c est égale à l'entr'axe des conduits 11, 12 et 13, 14. Le logement 1a est obturé à l'une de ses extrémités par un bouchon 32 et à l'autre extrémité par un bouchon 26 qui comporte à l'une de ses extrémités un ergot 46 perpendiculaire à son axe qui est engagé dans une rainure 47 ménagée dans l'organe mobile 2, sur une génératrice différente de celle des trous et ouverte à l'une de ses extrémités. Le bouchon 26 présente un élément externe 26b en forme de six pans pour l'entraînement en rotation du bouchon et par suite de l'organe mobile 2, au moyen de l'ergot 46 engagé dans la rainure 47 de l'organe mobile. Cette disposition permet de maintenir l'organe mobile 2 dans une position angulaire déterminée, sans empêcher son déplacement longitudinal.The distance between the geometric centers of the holes 8b, 8c and 6b, 6c is equal to the distance between the axes of the conduits 11, 12 and 13, 14. The housing 1a is closed at one of its ends by a plug 32 and at the other end by a plug 26 which has at one of its ends a lug 46 perpendicular to its axis which is engaged in a groove 47 formed in the movable member 2, on a generator different from that of the holes and open at one of its ends. The plug 26 has an external element 26b in the form of a hexagon for driving the plug in rotation and consequently of the movable member 2, by means of the lug 46 engaged in the groove 47 of the movable member. This arrangement makes it possible to maintain the mobile member 2 in a determined angular position, without preventing its longitudinal displacement.

A la figure 29 l'organe mobile 2 est représenté dans une position angulaire neutre et en appui contre la vis de butée 4, alors qu'à la figure 30, il est en appui contre la vis de butée 3. Dans ce cas, les orifices de passage sont égaux. Avec le même réglage des vis 3 et 4 on a représenté aux figures 31 et 32, l'organe mobile 2 qui a été déplacé en rotation d'un angle a+ et pour les deux alternances à gauche et à droite, il y a priorité au débit d'admission sur celui d'échappement.In FIG. 29 the movable member 2 is shown in a neutral angular position and in abutment against the stop screw 4, while in FIG. 30, it is abut against the abutment screw 3. In this case, the through holes are equal. With the same adjustment of the screws 3 and 4 there is shown in Figures 31 and 32, the movable member 2 which has been moved in rotation by an angle a + and for the two alternations to the left and to the right, priority is given to intake flow over exhaust.

Avec le même réglage des vis 3 et 4 on a représenté aux figures 33 et 34, l'organe mobile 2 qui a été déplacé en rotation d'un angle a- et pour les deux alternances à gauche et à droite, il y a priorité au débit d'échappement sur celui d'admission.With the same adjustment of the screws 3 and 4 there is shown in Figures 33 and 34, the movable member 2 which has been moved in rotation by an angle a- and for the two alternations to the left and to the right, there is priority at the exhaust flow on that of admission.

Un autre mode de réalisation d'un limiteur de débit représenté aux figures 35 à 40 comprend comme dans l'exemple précédent un bouchon rotatif 26a, qui est prolongé d'un côté par une partie de section hexagonale 26c, engagée dans un trou 41, de section correspondante prévu à l'une des extrémités de l'organe mobile 2 de telle sorte que ce dernier peut être entraîné en rotation et en translation axiale.Another embodiment of a flow limiter shown in FIGS. 35 to 40 comprises, as in the previous example, a rotary plug 26a, which is extended on one side by a part of hexagonal section 26c, engaged in a hole 41, of corresponding section provided at one end of the movable member 2 so that the latter can be driven in rotation and in axial translation.

A l'autre extrémité le bouchon 26a est prolongé extérieurement par une partie 26b, en forme de six pans pour l'entraînement du bouchon 26a (fig. 35-36 et 40).At the other end, the plug 26a is extended externally by a part 26b, in the form of a hexagon for driving the plug 26a (FIGS. 35-36 and 40).

L'organe mobile 2 représenté à la figure 40 comporte de chaque côté du joint d'étanchéité 10 deux gorges 8d, et 6d qui sont prolongées par deux rainures longitudinales s'étendant dans des sens opposés, les rainures 8e et 8f correspondant à la gorge 8d et les rainures 6e et 6f correspondant à la gorge 6d. Les rainures 8e et 8f, sont situées sur une même génératrice différente de celle mentionnée ci-dessus. Par rapport à une génératrice moyenne les axes de ces rainures sont décalées d'un angle a+ et a-. La largeur des rainures est sensiblement égale à celle du diamètre des conduits de passage 11,12 et 13,14 à leur sortie dans le logement 1a de l'organe mobile et la distance qui les sépare sur le cercle est aussi égale à ce diamètre.The movable member 2 shown in Figure 40 has on each side of the seal 10 two grooves 8d, and 6d which are extended by two longitudinal grooves extending in opposite directions, the grooves 8e and 8f corresponding to the groove 8d and the grooves 6e and 6f corresponding to the groove 6d. The grooves 8e and 8f are located on the same generator different from that mentioned above. With respect to an average generator, the axes of these grooves are offset by an angle a + and a-. The width of the grooves is substantially equal to that of the diameter of the passage conduits 11,12 and 13,14 when they exit into the housing 1a of the movable member and the distance which separates them on the circle is also equal to this diameter.

La figure 37 représente l'organe mobile en butée sur la vis 4 qui règle la vitesse de rentrée de la tige du vérin 5. Dans la position angulaire neutre représentée, les valeurs des orifices de passage des débits aller et retour sont égales.FIG. 37 represents the movable member in abutment on the screw 4 which regulates the speed of retraction of the rod of the jack 5. In the neutral angular position shown, the values of the orifices for passage of the outward and return flow rates are equal.

A la figure 38 pour un même réglage de la vis 4, l'organe mobile 2 a subi une rotation d'un angle a+ et seul le débit de retour est réduit.In FIG. 38, for the same adjustment of the screw 4, the movable member 2 has been rotated by an angle a + and only the return flow is reduced.

A la figure 39 pour un même réglage de la vis 4, l'organe mobile 2 a subi une rotation d'un angle a- et seul le débit aller est réduit.In FIG. 39, for the same adjustment of the screw 4, the movable member 2 has been rotated by an angle a- and only the outward flow is reduced.

A la figure 41 on a représenté un limiteur de débit qui est identique à celui de la figure 6 mais qui comporte deux ressorts de rappel 22, 23 qui agissent des deux côtés de l'organe mobile 2. Les ressorts 22, 23 qui sont très faibles n'ont aucune influence pendant les cycles de pression sur l'organe mobile 2 ; toutefois lorsque le dispositif est à l'arrêt sous fluide sous pression, ils permettent la manoeuvre manuelle du vérin notamment dans le cas d'un accident.In Figure 41 there is shown a flow limiter which is identical to that of Figure 6 but which comprises two return springs 22, 23 which act on both sides of the movable member 2. The springs 22, 23 which are very weak have no influence during the pressure cycles on the movable member 2; however, when the device is stopped under pressurized fluid, they allow manual actuation of the jack, particularly in the event of an accident.

A la figure 42 on a représenté une variante de réalisation d'un limiteur de débit dans lequel le logement 1a comporte deux organes d'étranglement 33 comportant un orifice présentant des doubles cônes 8 et 7 qui coopèrent avec des parties côniques 42, 43 et 42a, 43a de l'organe mobile 2 et règlent les passages et donc les débits. Les deux chambres 1 b, et 1 c, sont isolées par le joint 10 monté sur la partie centrale de l'organe mobile.In Figure 42 there is shown an alternative embodiment of a flow limiter in which the housing 1a comprises two throttling members 33 comprising an orifice having double cones 8 and 7 which cooperate with conical parts 42, 43 and 42a , 43a of the movable member 2 and regulate the passages and therefore the flow rates. The two chambers 1b, and 1c, are isolated by the seal 10 mounted on the central part of the movable member.

Les organes d'étranglement 33 sont disposés respectivement entre les orifices des demi-conduits 11 et 12 et entre les orifices des demi-conduits 13 et 14.The throttling members 33 are disposed respectively between the orifices of the half-conduits 11 and 12 and between the orifices of the half-conduits 13 and 14.

Les bouchons 32 présentent chacun un trou borgne 44 dans lequel est montée chaque extrémité 45 de l'organe mobile pour le guidage de celui-ci.The plugs 32 each have a blind hole 44 in which is mounted each end 45 of the movable member for guiding the latter.

Claims (20)

1. Compressed air flow rate limiter situated between a conventional compressed air distributor (15) and a pneumatic ram (5), for the purpose of controlling the speed of a ram piston (5a) in each direction, characterised in that it comprises a body (1) incorporating a cylindrical bore (1a) delimited by two bases (32) and wherein is installed in an axially slidable manner a movable element of revolution (2) of which the displacement is delimited at each extremity of the bore by means of an adjustable stop element (3, 4), the said body (1) being traversed at right angles to the said cylindrical bore (1a) by two passage ducts (11, 12 and 13, 14) which supply the ram (5), the said passage ducts (11, 12 and 13, 14) each leading into a chamber (1b, 1c) delimited by the base, the cylindrical bore (1a) and the movable element (2), the said movable element (2) comprising a central sealing device (10) assuring separation between the two chambers (1 b, 1 c) delimited at the two extremities of the cylindrical bore (1a), the said movable bistable element (2) effecting the adjustment of the aperture of the passage ducts (11, 12 and 13, 14) as a function of the position of the stop elements (3, 4) situated at the two extremities of the bore, in such a manner that this results in a regulation of the supply and outlet airflows of the two air volumes of the ram (5) of the double-acting type and this in each direction of displacement of the ram piston.
2. Flow rate limiter according to claim 1, characterised in that the body (1) comprises at least two members.
3. Flow rate limiter according to claim 1, characterised in that the setting of the stroke of the movable element (2) is performed by means of stop screws (3, 4) provided with an annular sealing joint (3a and 4a).
4. Flow rate limiter according to claim 3, characterised in that the stop screws (3, 4) are secured against vibration by means of lock nuts (3b and 4b).
5. Flow rate limiter according to claim 1, characterised in that the movable element (2) provided with an annular sealing joint (10) forms a piston exposed to the motive force of the fluid under pressure directed alternately against the two opposed surfaces of the movable element, since one of the chambers 1b, 1c is under pressure and the other chamber (1c, 1b) is under decreasing air venting pressure.
6. Flow rate limiter according to claim 1, characterised in that the movable element (2) comprises a single recessed cylindrical unit (2c), comprising a central partition (2f) and an annular groove (2g) wherein is situated a sealing joint (10) separating the two individual chambers (1 and 1c).
7. Flow rate limiter according to claim 1, characterised in that the movable element (2) comprises two identical or complementary elements (2a, 2b), assembled by means of a rivet or screw (2d), the said elements between them delimiting a recess in which is situated a sealing joint (2e) arranged around the rivet or the screw, the said assembly of elements facilitating the passing of the joint (10) in front of the passage ducts (13, 14 and 11, 12) within the bore (1a) of the body (1).
8. Flow rate limiter according to claim 1, characterised in that the movable element (2) is formed by a single recessed unit (2c) incorporating a central partition (2f) and that sealing is assured on its external diameter by an annular joint (10) situated in a groove (1 d) of the barrel (1).
9. Flow rate limiter according to claim 1, characterised in that the movable element (2) causes a greater or lesser degree of obstruction of the passage ducts (11, 12 and 13, 14) as a function of the setting of the stops (3, 4) by means of its circular rim (34) which is dislaced in alignment with the passage orifices, the length of the cylindrical portion of the said element with respect to the distance between the passage ducts (11, 12 and 13, 14) making it possible to control the supply with respect to the venting or to decelerate the flow rate solely on the venting of the ram.
10. Flow rate limiter according to claim 1 characterised in that the movable element (2) comprises in its cylindrical surface situated at either side of the central partition (2f), at least on the hole (6, 8) having a cross-section substantially equal to that of the orifices of the passage ducts (11, 12 and 13, 14), the spacing of the holes of the movable element making it possible to cause a variation of the proportion of the flow rates between the venting and feedsides, the said movable element (2) being immobilised in rotation.
11. Flow rate limiter according to claim 1, characterised in that the movable element (2) comprises two grooves (2h, 2i) on its cylindrical part, of which the one (2h) corresponds to one of the chambers (1c) and of which the other (2i) corresponds to the other chamber (1 b), the widths of the said grooves (2h, 2i) and their mutual spacing making it possible as a function of their values to effect variation of the feed and discharge flow rates whilst favouring the discharge or the feed.
12. Flow rate limiter according to claim 1, characterised in that the movable element (2) comprises, in its cylindrical part, elongated rectilinear grooves (8e and 6e) leading into grooves (8d, 6d) with circulation grooves (8f and 6f), the said movable element (2) being able besides its axial movement limited by the stops to be entrained in rotation by means of an operating element (26a) having six external flats slidably installed in a recess (41) of corresponding shape situated at the one extremity of the movable element (2).
13. Flow rate limiter according to claim 1, characterised in that the movable element (2) comprises elongated ports (8b, 6b and 8c, 6c) in its cylindrical part, which are inclined with respect to the axis of the movable element, the said movable element (2) being able besides its axial displacement to be entrained in rotation by means of an operating device comprising a pin (46) slidably installed in a groove (47) of the movable element (2) permitting rotation of this latter and its axial displacement.
14. Flow rate limiter according to claim 1, characterised in that the movable element (2) comprises elongated orifices (8, 8a) and, apart from its axial displacement, is able to be entrained in rotation by means of an operating element formed by an operating plate (48) comprising a pin (27) slidably installed in a hole (40) formed in the movable element (2), the said place (48) being installed on the barrel 1 by means of screws (28, 29) engaged in openings (38, 39) provided in the plate (48) and allowing its angular displacement.
15. Flow rate limiter according to claim 1, characterised in that the screws (3, 4) for setting the stroke of the movable element (2) have their heads engaged in a cylindrical hole (32c) formed in a plug (32) secured to at least one of the extremities of the bore (1a) provided in the body 1, the said head of the screw having a groove wherein is engaged a sealing joint (3, 4a) equally assuring locking of the screw against rotation under the action of vibrations.
16. Flow rate limiter according to claims 1 and 15, characterised in that the cylindrical holes (32c) receiving the screw heads (3, 4) are able to receive closure elements (31) provided with a sealing joint (31 a) which is engaged in a groove (32d) of the plugs (32).
17. Flow rate limiter according to claim 1, characterised in that the cylindrical bore (1a) provided in the body (1) is closed off at one of its extremities by a plug (32) and at the other extremi- . ty by a partition formed in the body (1).
18. Flow rate limiter according to claim 1, characterised in that the cylindrical bore (1a) formed in the body (1) is closed off at both of its extremities by means of identical plugs (32) which are either engaged by a force fit in the bore (1a), or inserted into abutement within a short stepped recess, or engaged into abutement and secured by swaging over, or screwed to the body (1), the said plugs (32) comprising a sealing joint (32a) disposed between these latter and the barrel (1).
19. Flow rate limiter according to claim 1, characterised in that the cylindrical bore (1a) has engaged in it within a force fit two restrictor elements (33) of which the orifice presents two tapers (7, 8) which co-operate with two tapers (42, 43) formed on the movable element (2) thereby controlling the passage orifices and the flow rates of the two chambers (1 b and 1 c), the said movable element having guiding elements situated at its two extremities which are engaged in holes provided in the plugs (32).
20. Flow rate limiter according to claim 1, characterised in that the movable element (2) which is bistable under the action of the motive force is equally exposed at both of its extremities to the action of two return springs (22, 23) which are very weak and have no effect on the pressure cycles, and which return the movable element (2) to the central position, thus assuring a passage towards the orifices of the ram when the device is stopped and pressureless, thus allowing manual operation of the ram.
EP85900124A 1983-11-29 1984-11-26 Compressed air flow rate limiter Expired EP0165281B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8319059 1983-11-29
FR8319059A FR2555703B1 (en) 1983-11-29 1983-11-29 IMPROVEMENT TO COMPRESSED AIR FLOW LIMITERS

Publications (2)

Publication Number Publication Date
EP0165281A1 EP0165281A1 (en) 1985-12-27
EP0165281B1 true EP0165281B1 (en) 1988-03-02

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US (1) US4745845A (en)
EP (1) EP0165281B1 (en)
JP (1) JPS61500624A (en)
DE (1) DE3469582D1 (en)
ES (1) ES538102A0 (en)
FR (1) FR2555703B1 (en)
IT (2) IT1179837B (en)
WO (1) WO1985002446A1 (en)

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CH372931A (en) * 1959-10-27 1963-10-31 Schindler Werner Piston control valve for at least partially continuous speed change in a pressure medium drive
US3119306A (en) * 1960-08-01 1964-01-28 Onsrud Machine Works Inc Contouring and profiling machines
GB968268A (en) * 1960-09-15 1964-09-02 Telehoist Ltd Improvements in or relating to fluid flow control valves
FR1533221A (en) * 1967-01-06 1968-07-19 Dba Sa Digitally Controlled Flow Valve
US3509968A (en) * 1968-03-01 1970-05-05 Jered Ind Inc Overspeed control valve assembly for a hydrostatic elevator engine
US3532119A (en) * 1968-04-01 1970-10-06 Kershaw Mfg Co Inc Pressure compensated control valve
NL6915281A (en) * 1969-10-09 1971-04-14
US3974742A (en) * 1974-10-31 1976-08-17 Caterpillar Tractor Co. Lock valve assembly

Also Published As

Publication number Publication date
ES8603984A1 (en) 1986-01-01
WO1985002446A1 (en) 1985-06-06
FR2555703B1 (en) 1986-08-14
IT8454099V0 (en) 1984-11-29
DE3469582D1 (en) 1988-04-07
IT1179837B (en) 1987-09-16
IT8468186A0 (en) 1984-11-29
ES538102A0 (en) 1986-01-01
IT8468186A1 (en) 1986-05-29
EP0165281A1 (en) 1985-12-27
FR2555703A1 (en) 1985-05-31
JPS61500624A (en) 1986-04-03
US4745845A (en) 1988-05-24

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