EP0086127B1 - Hydraulic deceleration and blocking arrangements, and automatic gun ammunition feeding apparatus including the same - Google Patents

Hydraulic deceleration and blocking arrangements, and automatic gun ammunition feeding apparatus including the same Download PDF

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Publication number
EP0086127B1
EP0086127B1 EP19830400135 EP83400135A EP0086127B1 EP 0086127 B1 EP0086127 B1 EP 0086127B1 EP 19830400135 EP19830400135 EP 19830400135 EP 83400135 A EP83400135 A EP 83400135A EP 0086127 B1 EP0086127 B1 EP 0086127B1
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EP
European Patent Office
Prior art keywords
piston
cylinder
inlet
braking
flow
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
EP19830400135
Other languages
German (de)
French (fr)
Other versions
EP0086127A1 (en
Inventor
Jean-Claude Lasfargues
Pierre-Alain Dubedat
Jacques Debesset
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.)
Cessione giat Industries
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Direction General pour lArmement DGA
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Publication of EP0086127A1 publication Critical patent/EP0086127A1/en
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Publication of EP0086127B1 publication Critical patent/EP0086127B1/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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/046—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed depending on the position of the working member
    • F15B11/048—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed depending on the position of the working member with deceleration 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • F15B11/0445—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out" with counterbalance valves, e.g. to prevent overrunning or for braking
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F41—WEAPONS
    • F41A—FUNCTIONAL FEATURES OR DETAILS COMMON TO BOTH SMALLARMS AND ORDNANCE, e.g. CANNONS; MOUNTINGS FOR SMALLARMS OR ORDNANCE
    • F41A9/00—Feeding or loading of ammunition; Magazines; Guiding means for the extracting of cartridges
    • F41A9/01—Feeding of unbelted ammunition
    • F41A9/06—Feeding of unbelted ammunition using cyclically moving conveyors, i.e. conveyors having ammunition pusher or carrier elements which are emptied or disengaged from the ammunition during the return stroke
    • F41A9/09—Movable ammunition carriers or loading trays, e.g. for feeding from magazines
    • F41A9/20—Movable ammunition carriers or loading trays, e.g. for feeding from magazines sliding, e.g. reciprocating
    • F41A9/22—Movable ammunition carriers or loading trays, e.g. for feeding from magazines sliding, e.g. reciprocating in a horizontal direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F41—WEAPONS
    • F41A—FUNCTIONAL FEATURES OR DETAILS COMMON TO BOTH SMALLARMS AND ORDNANCE, e.g. CANNONS; MOUNTINGS FOR SMALLARMS OR ORDNANCE
    • F41A9/00—Feeding or loading of ammunition; Magazines; Guiding means for the extracting of cartridges
    • F41A9/50—External power or control systems
    • 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
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3127—Floating position connecting the working ports and the return line
    • 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
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40576—Assemblies of multiple valves
    • F15B2211/40584—Assemblies of multiple valves the flow control means arranged in parallel with a check 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
    • F15B2211/415—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
    • F15B2211/46—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
    • F15B2211/40—Flow control
    • F15B2211/47—Flow control in one direction only
    • F15B2211/473—Flow control in one direction only without restriction in the reverse direction
    • 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
    • F15B2211/7058—Rotary 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
    • 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
    • F15B2211/77—Control of direction of movement of the output member
    • F15B2211/7741—Control of direction of movement of the output member with floating mode, e.g. using a direct connection between both lines of a double-acting cylinder

Definitions

  • the present invention relates to a hydraulic slowing and locking device and an automatic barrel feed assembly comprising such a device.
  • Known automatic loading devices generally include a storage magazine with two compartments placed on either side of the breech corner and behind it.
  • the two compartments can include either ammunition of a single type, or on one side the shells and on the other the gargoyles or loads.
  • Such a device is described in patent FR-A-2 048 095 and it comprises two mobile carriages ensuring the transfer of ammunition from a compartment to the barrel. No means of slowing down and locking is provided in this document and it is easily understood that it is not possible to obtain high firing rates while maintaining the reliability of the system.
  • Hydraulic retarders are used when mobile assemblies are driven by hydraulic motors or jacks, for example on rail, at high speeds and it is desired to avoid a sudden impact at the end of the stroke.
  • latches are used to ensure precise positioning of the assembly.
  • the devices known hitherto for fulfilling these functions generally use oil flow rate variators or throttles.
  • Some chokers more particularly adopt the solution of the conical needle which more or less blocks a hole.
  • Patent PR-A-2 009 707 describes a system of this kind in which the movable element is constituted by a movable clamp connected to a piston and a cam bar. This piston is in relation to a system fixed to the frame, with fluid flow, ensuring both the movement of the element and the damping of its stroke. The result is a complex system whose end-of-travel locking is not provided.
  • the present invention aims to overcome these drawbacks by providing a hydraulic device ensuring both the slowing down and the locking of a mobile element which does not require complex adjustment and which is reliable whatever the environment.
  • the subject of the invention is a hydraulic device for slowing down and locking a movable member with respect to a support capable of being driven in one direction or the other using a hydraulic assembly.
  • a hydraulic device for slowing down and locking a movable member with respect to a support capable of being driven in one direction or the other using a hydraulic assembly.
  • a bidirectional drive member with two inlets and a pressure distributor capable of directing a pressurized fluid towards one or the other of the inlets of the drive member via two conduits
  • means being designed to ensure the free or constricted flow of fluid from the distributor to the drive member so as to be able to take a first configuration in which they allow the free flow of fluid from the drive member to the distributor and a second configuration in which they allow the constricted flow
  • a cam follower cooperating with a cam to control the passage from one configuration to another, characterized in that it comprises two locks available each located on one of said conduits and connected by a first inlet to the pressure distributor and by a second inlet to the
  • one of the retarder locks is located upstream of this member, that is to say on the high pressure side and that the other retarder lock is located downstream ie on the low pressure side.
  • the retarder lock located downstream of the drive member is at this instant in its first configuration, it only opposes a low resistance to the flow of the low pressure fluid so that the movement caused by the member d training can take place at high speed. If the downstream retarder lock is then placed in its second configuration, it opposes the flow of the fluid much greater resistance so that the pressure downstream of the drive member rises and the movement is slowed down. Locking can then be achieved using the downstream retarder lock, the device then being ready to be driven in the opposite direction after reversing the pressure distributor.
  • the means for ensuring the flow of fluid consist of a cylinder in which is arranged to move a stepped piston, pierced with orifices arranged to selectively match the annular grooves formed on the interior surface of the cylinder and connected at the inputs of the retarder lock.
  • the piston has a relatively small cross-sectional area and a relatively large cross-sectional area, and the cylinder has corresponding cross-sectional areas, the annular groove corresponding to the inlet connected to the pressure distributor being formed in the small cross-sectional area of the cylinder. and the annular groove corresponding to the inlet connected to the drive member being formed in the region of large cross section of the cylinder.
  • the flow of the fluid can be carried out practically without limitation from the entry of the retarder lock connected to the pressure distributor towards its entry connected to the drive member if the piston is positioned in the cylinder. , so that it is its relatively small cross-sectional area which is located in the cylinder between the two annular grooves corresponding to the two inputs of the retarder lock.
  • This relative arrangement of the piston and of the cylinder can therefore correspond to that of the retarder lock located upstream of the drive member.
  • the piston may include an axial bore and three sets of radial bores opening into the axial bore, the first set of radial bores having a relatively large section and opening into the annular groove corresponding to the inlet connected to the drive member for a first relative position of the piston and of the cylinder corresponding to the first configuration of the retarder lock, the second set of radial bores having a relatively small section and opening into the same annular groove for a second relative position of the piston and of the cylinder corresponding to the second configuration of the retarder lock, and the third set of radial bores being of relatively large section and opening into the other annular groove for the two relative positions of the piston and of the cylinder.
  • this arrangement makes it possible to match the two inputs of the retarder lock so that for the first relative position of the piston and of the cylinder a low resistance is opposed to the flow of fluid from the input corresponding to the member of drive towards the inlet corresponding to the pressure distributor, while for the second relative position of the piston and the cylinder a higher resistance is opposed to this flow.
  • the first relative position of the cylinder and the piston can therefore correspond to the first configuration of the retarder lock located downstream of the drive member while the second relative position of the cylinder and the piston can correspond to the second configuration of the retarder lock located downstream of the drive member.
  • the device according to the invention also advantageously comprises a locking finger connected to one of the ends of the piston, capable of cooperating with the locking notch.
  • the locking notch is of course provided in the part of the mobile device relative to the retarder lock.
  • the device according to the invention comprises at least two cams each arranged to cooperate with one of the retarder latches, each of the retarder latches comprising a cam follower controlling its passage from one configuration to another.
  • this second retarder lock arrives at the second cam it is then placed in its second configuration so that the movement is slowed down and that it can then be stopped, the second retarder lock ensuring locking.
  • each cam has a locking notch and the cam follower of the retarder lock forms a locking finger capable of cooperating with this notch.
  • the device comprises a plurality of cams arranged to cooperate with at least retarder latches, spaced longitudinally and circumferentially on a shaft capable of being angularly positioned to place one of the cams in the path of relative movement of the retarder lock along said shaft.
  • the present invention also relates to an automatic barrel feed assembly, characterized in that it comprises combination of at least one shell storage basket, gripping means for these shells, these means being mounted on a mobile carriage, and a hydraulic device as described above for slowing down and blocking the mobile carriage.
  • the turret 1 shown in Figure 1 has a shell storage basket 2 and a shell storage basket 3 arranged side by side.
  • the storage baskets are divided into columns in front of which movable carriages 4 move, each guided on a lower rail 5 and an upper rail 6.
  • Each mobile carriage 4 carries a clamp 7 and can be moved longitudinally on the rails 5 and 8 by means of a feed mechanism 8.
  • the feed device shown in Figure 1 allows the routing of ammunition stored in the two baskets 2 and 3 to the barrel placed in front of the turret and not shown.
  • the ammunition is removed one by one by the clamp 7 which moves in a vertical movement relative to the mobile carriage 4.
  • This mobile cart 4 moves itself in a horizontal movement from the center of the turret to a previously selected column where the clamp 7 grasps an ammunition to bring it back to the center of the turret or it is supported to be transported to the barrel.
  • each mobile carriage 4 in front of the selected column is carried out using a hydraulic assembly 10 mounted on the carriage 4.
  • This hydraulic assembly 10 comprises two retarder latches 11 each carrying a locking finger 12 capable of cooperating with cams 13 circumferentially spaced on a cam-carrying shaft 14 and disposed longitudinally on this shaft in front of each column of ammunition.
  • the angular position of the shaft 14 is determined by means 15 so as to select that of the cams 13 which cooperate with the hydraulic assembly 10.
  • Each cam 13 comprises, starting from its end oriented towards the center of the turret, an inclined plane 16 then a surface 17 connected to the plane 16 and parallel to the generatrices of the shaft 14 and finally a locking notch 18.
  • Another cam 19 with circular section is formed at the end of the shaft 14 located in the center of the turret.
  • This cam 19 has the same profile as the cams 13, but inverted, that is to say it comprises successively starting from the center of the turret an annular locking groove 20 then a cylindrical part 21 coaxial with the shaft 14 and finally a frusto-conical part 22 which is connected to the cylindrical part 21.
  • Each retarder lock 11 is formed of two sub-assemblies, namely a lock 23 and a retarder 24 joined by a coupling 25 (FIG. 5).
  • the lock 23 comprises the locking finger 12 mentioned above which moves in an anti-friction bearing 28 itself mounted on an elastomer damper 27 to absorb the end of stroke shock due to the locking. This locking is achieved by engagement of the locking finger 12 either in the annular groove of the cam 19 or in the notch 18 of one of the cams 13.
  • the hydraulic retarder 24 comprises a stepped piston 28 sliding in a cylinder 29 the interior of which is connected to the exterior by three radial bores 30, 31 and 32 whose function will be described below.
  • the cylinder 29 has at its upper part a zone 33 of diameter smaller than the diameter of the lower zone 34.
  • the bore 30 opens into an annular groove 35 located between the zones 33 and 34 while the bore 31 opens into an annular groove 36 formed in zone 34.
  • the bore 32 opens completely at the bottom of the cylinder 29.
  • the cylinder 29 is closed at its lower part by a screwed cap 37, a compression spring 38 bearing on the one hand at the bottom of the cap 37 and on the other hand at the lower part of the piston 28.
  • the piston 28 itself comprises a zone 39 whose diameter corresponds to that of zone 33 of the cylinder and a zone 40 whose diameter corresponds to that of zone 34 of the cylinder.
  • the piston 28 has at its lower part a flange 41 which can cooperate by its upper surface with a shoulder 42 of the cylinder and by its lower surface with the upper part 43 of the plug 37.
  • An axial bore 44 is produced in the piston 28 and corresponds with the outside by a plurality of sets of radial bores.
  • a first set of radial bores has the two bores 45 and is disposed at the bottom of the axial bore 44.
  • the bores 45 have a relatively large diameter.
  • a second set of radial holes has the single hole 46 formed slightly above the holes 45 and of very small diameter.
  • a third set of radial bores comprises four bores 47 of relatively large diameter formed at the upper part of the axial bore 44.
  • the radial holes 47 open onto the outer surface of the piston 28 above the shoulder formed between the parts 39 and 40 of different diameters of the piston 28 while the radial holes 45 and 48 are located below this shoulder.
  • the piston 28 can move in the cylinder 29 from a high position, shown in FIGS. 5 and 8, in which the flange 41 is in abutment on the shoulder 42 to a low position shown in FIG. 7 in which the flange 41 is in abutment on the surface 43 of the plug 37.
  • the piston 28 and the cylinder 29 are dimensioned so that the following conditions are satisfied.
  • FIG. 4 represents the hydraulic diagram of the device on which the bidirectional drive motor 49 of the carriage 4 is seen.
  • This motor has two inlets 50 and 51 which are selectively connected to a high pressure source 52 and the other to a reservoir of fluid 53 at atmospheric pressure. This selective connection is carried out using two conduits 54 and 55 respectively via a distributor 58 which can also connect the two inputs of the motor 49 to the reservoir 53.
  • FIG. 4 also shows the unit 10 with its two retarder latches 11 each mounted on one of the conduits 54 and 55.
  • the inputs 30 of the two retarder latches are connected to the distributor 56 and the two inputs 31 are connected to the inputs 50 and 51 of the motor 49. Finally the orifices 32 of the retarder latches are brought back to the reservoir 53.
  • the high pressure is then brought to the inlet 30 of the left retarder lock.
  • the carriage 4 is therefore driven by the motor.
  • the right retarder lock of Figure 2 which is downstream of the engine receives the fluid leaving the engine on its inlet 31.
  • This retarder lock is in the configuration of Figure 6 with its inputs 30 and 31 corresponding by the radial holes 47, the axial bore 44 and the radial boreholes of large diameters 45. In this configuration, the retarder lock provides only a small resistance to the passage of the fluid so that the motor drives the carriage at high speed.
  • the distributor is then returned to the neutral position.
  • the ammunition gripping members are then actuated to grasp the shell or the corresponding socket after which the distributor is inverted to bring the high pressure to the inlet 30 of the right retarder lock which has the effect of unlocking the carriage and d '' drive it at high speed until the finger 12 of the left retarder lock comes on the cylindrical part 21 of the cam 19 where the movement continues at low speed as explained above until the finger 12 of the left retarder lock engages in the locking groove of the cam 19.
  • the clamp 7 is then taken care of as explained above in order to be brought to the loading means proper.
  • the invention makes it possible to ensure rapid movement of the carriage 4 while avoiding violent shocks when the movement is stopped by virtue of a prior slowing down.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)
  • Transmission Of Braking Force In Braking Systems (AREA)

Description

La présente invention concerne un dispositif hydraulique de ralentissement et de verrouillage et un ensemble d'alimentation automatique de canon comportant un tel dispositif.The present invention relates to a hydraulic slowing and locking device and an automatic barrel feed assembly comprising such a device.

Les dispositifs de chargement automatiques connus comportent généralement un magasin de stockage à deux compartiments placés de part et d'autre du coin de culasse et en arrière de celui-ci. Les deux compartiments peuvent comporter soit des munitions d'un seul type, soit d'un côté les obus et de l'autre les gargousses ou chargements. Un tel dispositif est décrit dans le brevet FR-A-2 048 095 et il comporte deux chariots mobiles assurant le transfert des munitions d'un compartiment vers le canon. Aucun moyen de ralentissement et de verrouillage n'est prévu dans ce document et on comprend aisément qu'il n'est pas possible d'obtenir des cadences de tir élevées tout en maintenant la fiabilité du système.Known automatic loading devices generally include a storage magazine with two compartments placed on either side of the breech corner and behind it. The two compartments can include either ammunition of a single type, or on one side the shells and on the other the gargoyles or loads. Such a device is described in patent FR-A-2 048 095 and it comprises two mobile carriages ensuring the transfer of ammunition from a compartment to the barrel. No means of slowing down and locking is provided in this document and it is easily understood that it is not possible to obtain high firing rates while maintaining the reliability of the system.

Des ralentisseurs hydrauliques sont utilisés lorsque des ensembles mobiles sont entraînés par des moteurs hydrauliques ou des vérins, par exemple sur rail, à de grandes vitesses et que l'on souhaite éviter un choc brutal en fin de course. De plus, lorsque ces ensembles ne sont pas bloqués hydrauliquement par le moteur ou le vérin en fin de course on utilise des verrous permettant d'assurer un positionnement précis de l'ensemble.Hydraulic retarders are used when mobile assemblies are driven by hydraulic motors or jacks, for example on rail, at high speeds and it is desired to avoid a sudden impact at the end of the stroke. In addition, when these assemblies are not hydraulically blocked by the motor or the actuator at the end of the travel, latches are used to ensure precise positioning of the assembly.

Les dispositifs connus jusqu'à présent pour remplir ces fonctions utilisent généralement des variateurs de débits d'huile ou des étrangleurs. Certains étrangleurs adoptent plus particulièrement la solution de l'aiguille conique qui obture plus ou moins un trou.The devices known hitherto for fulfilling these functions generally use oil flow rate variators or throttles. Some chokers more particularly adopt the solution of the conical needle which more or less blocks a hole.

Toutefois, tous les dispositifs connus sont difficiles à régler et relativement fragiles de sorte qu'ils ne peuvent pas être utilisés dans des environnements hostiles.However, all known devices are difficult to adjust and relatively fragile so that they cannot be used in hostile environments.

On connaît par ailleurs un système hydraulique de ralentissement appliqué dans le façonnage d'une bande de tôle. Le brevet PR-A-2 009 707 décrit un système de ce genre dans lequel l'élément mobile est constitué par une pince mobile liée à un piston et une barre à came. Ce piston est en relation avec un système fixé au bâti, à écoulement de fluide, assurant à la fois le déplacement de l'élément et l'amortissement de sa course. Il en résulte un système complexe dont le verrouillage en fin de course n'est pas prévu.There is also known a hydraulic slowdown system applied in the shaping of a sheet metal strip. Patent PR-A-2 009 707 describes a system of this kind in which the movable element is constituted by a movable clamp connected to a piston and a cam bar. This piston is in relation to a system fixed to the frame, with fluid flow, ensuring both the movement of the element and the damping of its stroke. The result is a complex system whose end-of-travel locking is not provided.

La présente invention vise à pallier ces inconvénients en fournissant un dispositif hydraulique assurant à la fois le ralentissement et le verrouillage d'un élément mobile qui ne nécessite pas de réglage complexe et qui soit fiable quel que soit l'environnement.The present invention aims to overcome these drawbacks by providing a hydraulic device ensuring both the slowing down and the locking of a mobile element which does not require complex adjustment and which is reliable whatever the environment.

A cet effet, l'invention a pour objet un dispositif hydraulique de ralentissement et de verrouillage d'un organe mobile par rapport à un support susceptible d'être entraîné dans un sens ou dans l'autre à l'aide d'un ensemble hydraulique comportant un organe d'entraînement bidirectionnel à deux entrées et un distributeur de pression susceptible de diriger un fluide sous pression vers l'une ou l'autre des entrées de l'organe d'entraînement par l'intermédiaire de deux conduits, des moyens étant prévus pour assurer l'écoulement libre ou étranglé du fluide du distributeur à l'organe d'entraînement pour pouvoir prendre une première configuration dans laquelle ils permettent l'écoulement libre du fluide de l'organe d'entraînement vers le distributeur et une seconde configuration dans laquelle ils permettent l'écoulement étranglé, un suiveur de came coopérant avec une came pour commander le passage d'une configuration à l'autre, caractérisé en ce qu'il comprend deux verrous ralentisseurs disposés chacun sur un desdits conduits et reliés par une première entrée au distributeur de pression et par une deuxième entrée à l'organe d'entraînement, les moyens assurant l'écoulement du fluide étant intégrés aux verrous ralentisseurs, chaque verrou ralentisseur étant muni d'un doigt de verrouillage soumis à l'action d'un ressort coopérant avec une encoche de verrouillage, chaque verrou ralentisseur étant agencé pour assurer le déverrouillage de l'organe mobile et le libre écoulement du fluide du distributeur de pression à l'organe d'entraînement lorsqu'il reçoit la pression sur son entrée reliée au distributeur de pression, et pour pouvoir prendre, en l'absence de pression appliquée à la première entrée les deux configurations où il permet l'écoulement libre ou étranglé du fluide.To this end, the subject of the invention is a hydraulic device for slowing down and locking a movable member with respect to a support capable of being driven in one direction or the other using a hydraulic assembly. comprising a bidirectional drive member with two inlets and a pressure distributor capable of directing a pressurized fluid towards one or the other of the inlets of the drive member via two conduits, means being designed to ensure the free or constricted flow of fluid from the distributor to the drive member so as to be able to take a first configuration in which they allow the free flow of fluid from the drive member to the distributor and a second configuration in which they allow the constricted flow, a cam follower cooperating with a cam to control the passage from one configuration to another, characterized in that it comprises two locks available each located on one of said conduits and connected by a first inlet to the pressure distributor and by a second inlet to the drive member, the means ensuring the flow of the fluid being integrated into the retarder locks, each retarder lock being provided with a locking finger subjected to the action of a spring cooperating with a locking notch, each retarder lock being arranged to ensure the unlocking of the movable member and the free flow of fluid from the pressure distributor to the drive when it receives the pressure on its inlet connected to the pressure distributor, and to be able to take, in the absence of pressure applied to the first inlet, the two configurations where it allows the free or constricted flow of the fluid.

On comprend par conséquent que, quel que soit le sens de fonctionnement de l'organe d'entraînement, l'un des verrous ralentisseurs est situé en amont de cet organe c'est à dire du côté haute pression et que l'autre verrou ralentisseur est situé en aval c'est à dire du côté basse pression.It is therefore understood that, whatever the direction of operation of the drive member, one of the retarder locks is located upstream of this member, that is to say on the high pressure side and that the other retarder lock is located downstream ie on the low pressure side.

Si le verrouillage est assuré par le verrou ralentisseur situé en amont de l'organe d'entraînement, lorsque la haute pression est appliquée par le distributeur de pression à ce verrou ralentisseur le déverrouillage est réalisé et le fluide à haute pression est amené à l'entrée de l'organe d'entraînement. Si le verrou ralentisseur situé en aval de l'organe d'entraînement est à cet instant dans sa première configuration il n'oppose qu'une faible résistance à l'écoulement du fluide basse pression de sorte que le mouvement provoqué par l'organe d'entraînement peut avoir lieu à grande vitesse. Si le verrou ralentisseur aval est alors placé dans sa seconde configuration, il oppose à l'écoulement du fluide une beaucoup plus grande résistance de sorte que la pression en aval de l'organe d'entraînement s'élève et que le mouvement est ralenti. Le verrouillage peut alors être réalisé à l'aide du verrou ralentisseur aval le dispositif étant alors prêt pour être entraîné dans le sens contraire après inversion du distributeur de pression.If the locking is ensured by the retarder lock located upstream of the drive member, when the high pressure is applied by the pressure distributor to this retarder lock the unlocking is carried out and the high pressure fluid is brought to the input of the drive member. If the retarder lock located downstream of the drive member is at this instant in its first configuration, it only opposes a low resistance to the flow of the low pressure fluid so that the movement caused by the member d training can take place at high speed. If the downstream retarder lock is then placed in its second configuration, it opposes the flow of the fluid much greater resistance so that the pressure downstream of the drive member rises and the movement is slowed down. Locking can then be achieved using the downstream retarder lock, the device then being ready to be driven in the opposite direction after reversing the pressure distributor.

Dans un mode particulier de réalisation de l'invention, les moyens pour assurer l'écoulement de fluide sont constitués par un cylindre dans lequel est disposé pour se déplacer un piston étagé, percé d'orifices agencés pour faire correspondre sélectivement des gorges annulaires ménagées à la surface intérieure du cylindre et reliées aux entrées du verrou ralentisseur.In a particular embodiment of the invention, the means for ensuring the flow of fluid consist of a cylinder in which is arranged to move a stepped piston, pierced with orifices arranged to selectively match the annular grooves formed on the interior surface of the cylinder and connected at the inputs of the retarder lock.

Le piston comporte une zone de section relativement faible et une zone de section relativement importante, et le cylindre comporte des zones de sections correspondantes, la gorge annulaire correspondant à l'entrée reliée au distributeur de pression étant ménagée dans la zone de section faible du cylindre et la gorge annulaire correspondant à l'entrée reliée à l'organe d'entraînement étant ménagée dans la zone de section importante du cylindre.The piston has a relatively small cross-sectional area and a relatively large cross-sectional area, and the cylinder has corresponding cross-sectional areas, the annular groove corresponding to the inlet connected to the pressure distributor being formed in the small cross-sectional area of the cylinder. and the annular groove corresponding to the inlet connected to the drive member being formed in the region of large cross section of the cylinder.

On comprend que dans ce cas, l'écoulement du fluide puisse s'effectuer pratiquement sans limitation de l'entrée du verrou ralentisseur reliée au distributeur de pression vers son entrée reliée à l'organe d'entraînement si le piston est positionné dans le cylindre, de sorte que ce soit sa zone de section relativement faible qui se trouve dans le cylindre entre les deux gorges annulaires corrrespondant aux deux entrées du verrou ralentisseur.It is understood that in this case, the flow of the fluid can be carried out practically without limitation from the entry of the retarder lock connected to the pressure distributor towards its entry connected to the drive member if the piston is positioned in the cylinder. , so that it is its relatively small cross-sectional area which is located in the cylinder between the two annular grooves corresponding to the two inputs of the retarder lock.

Cette disposition relative du piston et du cylindre peut donc correspondre à celle du verrou ralentisseur situé en amont de l'organe d'entraînement.This relative arrangement of the piston and of the cylinder can therefore correspond to that of the retarder lock located upstream of the drive member.

Le piston peut comporter un perçage axial et trois ensembles de perçages radiaux débouchant dans le perçage axial, le premier ensemble de perçages radiaux ayant une section relativement élevée et débouchant dans la gorge annulaires correspondant à l'entrée reliée à l'organe d'entraînement pour une première position relative du piston et du cylindre correspondant à la première configuration du verrou ralentisseur, le deuxième ensemble de perçages radiaux ayant une section relativement faible et débouchant dans la même gorge annulaire pour une deuxième position relative du piston et du cylindre correspondant à la deuxième configuration du verrou ralentisseur, et le troisième ensemble de perçages radiaux éetant de section relativement élevée et débouchant dans l'autre gorge annulaire pour les deux positions relatives du piston et du cylindre.The piston may include an axial bore and three sets of radial bores opening into the axial bore, the first set of radial bores having a relatively large section and opening into the annular groove corresponding to the inlet connected to the drive member for a first relative position of the piston and of the cylinder corresponding to the first configuration of the retarder lock, the second set of radial bores having a relatively small section and opening into the same annular groove for a second relative position of the piston and of the cylinder corresponding to the second configuration of the retarder lock, and the third set of radial bores being of relatively large section and opening into the other annular groove for the two relative positions of the piston and of the cylinder.

On constate que cet agencement permet de faire correspondre les deux entrées du verrou ralentisseur de sorte que pour la première position relative du piston et du cylindre une faible résistance est opposée à l'écoulement du fluide de l'entrée correspondant à l'organe d'entraînement vers l'entrée correspondant au distributeur de pression, alors que pour la deuxième position relative du piston et du cylindre une résistance plus élevée est opposée à cet écoulement.It is found that this arrangement makes it possible to match the two inputs of the retarder lock so that for the first relative position of the piston and of the cylinder a low resistance is opposed to the flow of fluid from the input corresponding to the member of drive towards the inlet corresponding to the pressure distributor, while for the second relative position of the piston and the cylinder a higher resistance is opposed to this flow.

La première position relative du cylindre et du piston peut donc correspondre à la première configuration du verou ralentisseur situé en aval de l'organe d'entraînement alors que la deuxième position relative du cylindre et du piston peut correspondre à la deuxième configuration du verrou ralentisseur situé en aval de l'organe d'entraînement.The first relative position of the cylinder and the piston can therefore correspond to the first configuration of the retarder lock located downstream of the drive member while the second relative position of the cylinder and the piston can correspond to the second configuration of the retarder lock located downstream of the drive member.

Le dispositif selon l'invention comporte par ailleurs avantageusement un doigt de verrouillage reliée à une des extrémités du piston, susceptible de coopérer avec l'encoche de verrouillage.The device according to the invention also advantageously comprises a locking finger connected to one of the ends of the piston, capable of cooperating with the locking notch.

L'encoche de verrouillage est bien entendu ménagée dans la partie du dispositif mobile par rapport au verrou ralentisseur.The locking notch is of course provided in the part of the mobile device relative to the retarder lock.

Dans un mode de réalisation parliculier, le dispositif selon l'invention comprend au moins deux cames disposées pour coopérer chacune avec un des verrous ralentisseurs, chacun des verrous ralentisseurs comportant un suiveur de came commandant son passagc d'une conriguration à une autre.In a particular embodiment, the device according to the invention comprises at least two cams each arranged to cooperate with one of the retarder latches, each of the retarder latches comprising a cam follower controlling its passage from one configuration to another.

Un tel agencemcnt permet d'assurer un déplacement du dispositif en va et vient d'une came à l'autre.Such an arrangement ensures movement of the device back and forth from one cam to another.

En effet si l'on suppose qu'un des verrous ralentisseurs assure le verrouillage sur une des cames on constate qu'il suffit d'appliquer à l'aide du distributeur de pression la haute pression sur ce verrou ralentisseur pour qu'il se trouve déverrouillé et que le mouvement se produise en direction de l'autre came à grande vitesse si le deuxième verrou ralentisseur est dans sa première configuration.In fact, if we assume that one of the retarder locks ensures locking on one of the cams, we see that it suffices to apply the high pressure on this retarder lock using the pressure distributor so that it is located unlocked and movement occurs towards the other high speed cam if the second retarder lock is in its first configuration.

Lorsque ce deuxième verrou ralentisseur arrive au niveau de la deuxième came il est alors placé dans sa deuxième configuration de sorte que le mouvement est ralenti et qu'il peut ensuite être arrêté, le deuxième verrou ralentiaseur assurant le verrouillage.When this second retarder lock arrives at the second cam it is then placed in its second configuration so that the movement is slowed down and that it can then be stopped, the second retarder lock ensuring locking.

Si la haute pression est alors appliquée par l'intermédiaire du distributeur de pression au deuxième verrou ralentisseur celui-ci assure le déverrouillage et l'ensemble mobile peut repartir dans l'autre sens en direction de la première came où le processus se répète.If the high pressure is then applied via the pressure distributor to the second retarder latch, this ensures the unlocking and the mobile assembly can set off again in the other direction towards the first cam where the process is repeated.

Avantageusement chaque came comporte une encoche de verrouillage et le suiveur de came du verrou ralentisseur forme un doigt de verrouillage susceptible de coopérer avec cette encoche.Advantageously, each cam has a locking notch and the cam follower of the retarder lock forms a locking finger capable of cooperating with this notch.

Dans un mode de réalisation de l'invention le dispositif comporte une pluralité de cames disposées pour coopérer avec au moins des verrous ralentisseurs, espacées longitudinalement et circonférentiellement sur un arbre susceptible d'être positionné angulairement pour placer une des cames dans le trajet du mouvement relatif du verrou ralentisseur le long dudit arbre.In one embodiment of the invention the device comprises a plurality of cams arranged to cooperate with at least retarder latches, spaced longitudinally and circumferentially on a shaft capable of being angularly positioned to place one of the cams in the path of relative movement of the retarder lock along said shaft.

On peut ainsi en choisissant la position angulaire de l'arbre porteur de came choisir le point d'arrêt longitudinal du dispositif lorsque le mouvement se produit dans la direction de cette came.It is thus possible by choosing the angular position of the cam-carrying shaft to choose the longitudinal stopping point of the device when the movement occurs in the direction of this cam.

La présente invention a également pour objet un ensemble d'alimentation automatique de canon, caractérisé par le fait qu'il comprend en combinaison au moins un panier de stockage d'obus, des moyens de préhension pour ces obus, ces moyens étant montés sur un chariot mobile, et un dispositif hydraulique tel que décrit ci-dessus pour le ralentissement et le blocage du chariot mobile.The present invention also relates to an automatic barrel feed assembly, characterized in that it comprises combination of at least one shell storage basket, gripping means for these shells, these means being mounted on a mobile carriage, and a hydraulic device as described above for slowing down and blocking the mobile carriage.

On décrira maintenant un mode de réalisation particulier de l'invention à titre d'exemple non limitatif en référence aux dessins schématiques annexés dans lesquels:A particular embodiment of the invention will now be described by way of nonlimiting example with reference to the appended schematic drawings in which:

la figure 1 est une vue partielle en perspective éclatée de la tourelle d'un canon automoteur comportant un ensemble d'alimentation automatique selon l'invention,

  • - la figure 2 est une vue de derrière à plus grande échelle d'une partie de ce dispositif,
  • - la figure 3 est une vue en coupe selon la ligne III-III de la figure 2,
  • - la figure 4 est un schéma hydraulique du dispositif,
  • - la figure 5 est une vue à plus grande échelle partiellement en coupe selon la ligne V-V de la figure 6 du dispositif représenté à la figure 2,
  • - la figure 6 est une vue en coupe selon la ligne VI-VI de la figure 5.
  • - la figure 7 est une vue similaire à la figure 6 dans une autre configuration du dispositif et,
  • - la figure 8 est une autre vue similaire à la figure 6 dans encore une autre configuration du dispositif.
FIG. 1 is a partial exploded perspective view of the turret of a self-propelled gun comprising an automatic feed assembly according to the invention,
  • FIG. 2 is a rear view on a larger scale of part of this device,
  • FIG. 3 is a sectional view along line III-III of FIG. 2,
  • FIG. 4 is a hydraulic diagram of the device,
  • FIG. 5 is an enlarged view partially in section along the line VV in FIG. 6 of the device shown in FIG. 2,
  • - Figure 6 is a sectional view along line VI-VI of Figure 5.
  • FIG. 7 is a view similar to FIG. 6 in another configuration of the device and,
  • - Figure 8 is another view similar to Figure 6 in yet another configuration of the device.

La tourelle 1 représentée à la figure 1 comporte un panier de stockage d'obus 2 et un panier de stockage de douilles 3 disposés côte à côte.The turret 1 shown in Figure 1 has a shell storage basket 2 and a shell storage basket 3 arranged side by side.

Les paniers de stockage sont divisés en colonnes devant lesquelles se déplacent des chariots 4 mobiles et guidés chacun sur un rail inférieur 5 et un rail supérieur 6.The storage baskets are divided into columns in front of which movable carriages 4 move, each guided on a lower rail 5 and an upper rail 6.

- Chaque charriot mobile 4 porte une pince 7 et peut être déplacé longitudinalement sur les rails 5 et 8 par l'intermédiaire d'un mécanisme d'avance 8.- Each mobile carriage 4 carries a clamp 7 and can be moved longitudinally on the rails 5 and 8 by means of a feed mechanism 8.

Le dispositif d'alimentation représenté à la figure 1 permet l'acheminement des munitions stockées dans les deux paniers 2 et 3 vers le canon placé à l'avant de la tourelle et non représenté.The feed device shown in Figure 1 allows the routing of ammunition stored in the two baskets 2 and 3 to the barrel placed in front of the turret and not shown.

Les munitions sont prélevées une à une par la pince 7 qui se déplace suivant un mouvement vertical par rapport au charriot mobile 4.The ammunition is removed one by one by the clamp 7 which moves in a vertical movement relative to the mobile carriage 4.

Ce charriot mobile 4 se déplace lui-même suivant un mouvement horizontal depuis le centre de la tourelle vers une colonne sélectionnée au préalable où la pince 7 saisie une munition pour la ramener vers le centre de la tourelle ou elle est prise en charge pour être transportée jusqu'au canon.This mobile cart 4 moves itself in a horizontal movement from the center of the turret to a previously selected column where the clamp 7 grasps an ammunition to bring it back to the center of the turret or it is supported to be transported to the barrel.

Le positionnement de chaque charriot mobile 4 devant la colonne sélectionnée s'effectue à l'aide d un enscmble hydraulique 10 monté sur le charriot 4.The positioning of each mobile carriage 4 in front of the selected column is carried out using a hydraulic assembly 10 mounted on the carriage 4.

Cet ensemble hydraulique 10 comprend deux verrous ralentisseurs 11 portant chacun un doigt de verrouillage 12 susceptible de coopérer avec des cames 13 espacées circonférentiellement sur un arbre porteur de cames 14 et disposé longitudinalement sur cet arbre devant chacune des colonnes de munitions.This hydraulic assembly 10 comprises two retarder latches 11 each carrying a locking finger 12 capable of cooperating with cams 13 circumferentially spaced on a cam-carrying shaft 14 and disposed longitudinally on this shaft in front of each column of ammunition.

La position angulaire de l'arbre 14 est déterminée par des moyens 15 de façon à sélectionner celle des cames 13 qui coopèrent avec l'ensemble hydraulique 10.The angular position of the shaft 14 is determined by means 15 so as to select that of the cams 13 which cooperate with the hydraulic assembly 10.

Chaque came 13 comporte en partant de son extrémité orientée vers le centre de la tourelle un plan incliné 16 puis une surface 17 raccordée au plan 16 et parallèle aux génératrices de l'arbre 14 et enfin une encoche de verrouillage 18.Each cam 13 comprises, starting from its end oriented towards the center of the turret, an inclined plane 16 then a surface 17 connected to the plane 16 and parallel to the generatrices of the shaft 14 and finally a locking notch 18.

Une autre came 19 à section circulaire est formée à l'extrémité de l'arbre 14 situé au centre de la tourelle.Another cam 19 with circular section is formed at the end of the shaft 14 located in the center of the turret.

Cette came 19 possède le même profil que les cames 13, mais inversé, c'est-à-dire qu'elle comporte successivement en partant du centre de la tourelle une gorge annulaire de verrouillage 20 puis une partie cylindrique 21 coaxiale à l'arbre 14 et enfin une partie tronconique 22 qui est raccordée à la partie cylindrique 21.This cam 19 has the same profile as the cams 13, but inverted, that is to say it comprises successively starting from the center of the turret an annular locking groove 20 then a cylindrical part 21 coaxial with the shaft 14 and finally a frusto-conical part 22 which is connected to the cylindrical part 21.

Chaque verrou ralentisseur 11 est formé de deux sous-ensembles à savoir un verrou 23 et un ralentisseur 24 réunis par un accouplement 25 (Fig. 5).Each retarder lock 11 is formed of two sub-assemblies, namely a lock 23 and a retarder 24 joined by a coupling 25 (FIG. 5).

Le verrou 23 comporte le doigt de verrouillage 12 mentionné ci-dessus qui se déplace dans un pallier antifriction 28 monté lui-même sur un amortisseur en élastomère 27 pour amortir le choc de fin de course dû au verrouillage. Ce verrouillage est réalisé par engagement du doigt de verrouillage 12 soit dans la gorge annulaire de la came 19 soit dans l'encoche 18 d'une des cames 13.The lock 23 comprises the locking finger 12 mentioned above which moves in an anti-friction bearing 28 itself mounted on an elastomer damper 27 to absorb the end of stroke shock due to the locking. This locking is achieved by engagement of the locking finger 12 either in the annular groove of the cam 19 or in the notch 18 of one of the cams 13.

Le ralentisseur hydraulique 24 comprend un piston étagé 28 coulissant dans un cylindre 29 dont l'intérieur est relié à l'extérieur par trois perçages radiaux 30, 31 et 32 dont la fonction sera décrite ci-après.The hydraulic retarder 24 comprises a stepped piston 28 sliding in a cylinder 29 the interior of which is connected to the exterior by three radial bores 30, 31 and 32 whose function will be described below.

Le cylindre 29 comporte à sa partie supérieure une zone 33 de diamètre plus petit que le diamètre de la zone inférieure 34. Le perçage 30 débouche dans une gorge annulaire 35 située entre les zones 33 et 34 alors que le perçage 31 débouche dans une gorge annulaire 36 formée dans la zone 34.The cylinder 29 has at its upper part a zone 33 of diameter smaller than the diameter of the lower zone 34. The bore 30 opens into an annular groove 35 located between the zones 33 and 34 while the bore 31 opens into an annular groove 36 formed in zone 34.

Le perçage 32 débouche complètement à la partie inférieure du cylindre 29.The bore 32 opens completely at the bottom of the cylinder 29.

Le cylindre 29 est fermé à sa partie inférieure par un bouchon 37 vissé, un ressort de compression 38 prenant appui d'une part au fond du bouchon 37 et d'autre part à la partie inférieure du piston 28.The cylinder 29 is closed at its lower part by a screwed cap 37, a compression spring 38 bearing on the one hand at the bottom of the cap 37 and on the other hand at the lower part of the piston 28.

Le piston 28 comporte lui-même une zone 39 dont le diamètre correspond à celui de la zone 33 du cylindre et une zone 40 dont le diamètre correspond à celui de la zone 34 du cylindre. Le piston 28 comporte à sa partie inférieure une collerette 41 qui peut coopérer par sa surface supérieure avec un épaulement 42 du cylindre et par sa surface inférieure avec la partie supérieure 43 du bouchon 37. Un perçage axial 44 est réalisé dans le piston 28 et correspond avec l'extérieur par une pluralité d'ensembles de perçages radiaux.The piston 28 itself comprises a zone 39 whose diameter corresponds to that of zone 33 of the cylinder and a zone 40 whose diameter corresponds to that of zone 34 of the cylinder. The piston 28 has at its lower part a flange 41 which can cooperate by its upper surface with a shoulder 42 of the cylinder and by its lower surface with the upper part 43 of the plug 37. An axial bore 44 is produced in the piston 28 and corresponds with the outside by a plurality of sets of radial bores.

Un premier ensemble de perçages radiaux comporte les deux perçages 45 et est disposé à la partie inférieure du perçage axial 44. Les perçages 45 ont un diamètre relativement important.A first set of radial bores has the two bores 45 and is disposed at the bottom of the axial bore 44. The bores 45 have a relatively large diameter.

Un deuxième ensemble de perçages radiaux comporte le perçage unique 46 formé légèrement au-dessus des perçages 45 et de très faible diamètre.A second set of radial holes has the single hole 46 formed slightly above the holes 45 and of very small diameter.

Enfin un troisième ensemble de perçages radiaux comporte quatre perçages 47 de relativement grand diamètre formé à la partie supérieur du perçage axial 44.Finally, a third set of radial bores comprises four bores 47 of relatively large diameter formed at the upper part of the axial bore 44.

Les perçages radiaux 47 débouchent à la surface extérieure du piston 28 au-dessus de l'épaulement formé entre les parties 39 et 40 de diamètres différents du piston 28 alors que les perçages radiaux 45 et 48 se trouvent en dessous de cet épaulement.The radial holes 47 open onto the outer surface of the piston 28 above the shoulder formed between the parts 39 and 40 of different diameters of the piston 28 while the radial holes 45 and 48 are located below this shoulder.

Le piston 28 peut se déplacer dans le cylindre 29 d'une position haute, représentée aux figures 5 et 8, dans laquelle la collerette 41 est en butée sur l'épaulement 42 à une position basse représentée à la figure 7 dans laquelle la collerette 41 est en butée sur la surface 43 du bouchon 37.The piston 28 can move in the cylinder 29 from a high position, shown in FIGS. 5 and 8, in which the flange 41 is in abutment on the shoulder 42 to a low position shown in FIG. 7 in which the flange 41 is in abutment on the surface 43 of the plug 37.

Le piston 28 et le cylindre 29 sont dimensionnés de telle sorte que les conditions suivantes soient satisfaites.The piston 28 and the cylinder 29 are dimensioned so that the following conditions are satisfied.

Lorsque le piston est dans sa position haute des figures 5 et 6 les perçages radiaux 47 débouchent dans la gorge annulaire 35 et au moins les perçages radiaux 45 débouchent dans la gorge annulaire 38. L'épaulement formé entre les parties 39 et 40 de diamètres différents du piston 28 se trouve entre les gorges annulaires 35 et 36.When the piston is in its high position in FIGS. 5 and 6, the radial holes 47 open into the annular groove 35 and at least the radial holes 45 open into the annular groove 38. The shoulder formed between the parts 39 and 40 of different diameters of the piston 28 is located between the annular grooves 35 and 36.

Lorsque le piston est dans sa position basse représentée à la figure 7 l'épaulement formé entre les parties 39 et 40 du piston 28 se trouve en dessous de la partie supérieure de la gorge annulaire 36 de sorte qu'un conduit annulaire 48 est formé entre les gorges 35 et 36, le conduit annulaire 48 étant délimité entre une surface radialement intérieure formée par la surface du piston dans sa zone de petit diamètre et une surface radialement extérieure formée par la surface du cylindre dans sa zone de grand diamètre.When the piston is in its low position shown in FIG. 7, the shoulder formed between the parts 39 and 40 of the piston 28 is located below the upper part of the annular groove 36 so that an annular conduit 48 is formed between the grooves 35 and 36, the annular conduit 48 being delimited between a radially inner surface formed by the surface of the piston in its zone of small diameter and a radially outer surface formed by the surface of the cylinder in its zone of large diameter.

Enfin dans une position intermédiaire du piston 28 dans le cylindre 29, représentée à la figure 8, les perçages radiaux 47 sont toujours en communication avec la gorge annulaire 35 mais seul le perçage radial 46 de faible diamètre débouche dans la gorge annulaire 36.Finally, in an intermediate position of the piston 28 in the cylinder 29, shown in FIG. 8, the radial holes 47 are always in communication with the annular groove 35 but only the radial bore 46 of small diameter opens into the annular groove 36.

La figure 4 représente le schéma hydraulique du dispositif sur lequel on voit le moteur bidirectionnel d'entraînement 49 du chariot 4. Ce moteur comporte deux entrées 50 et 51 qui sont sélectivement reliées une source de haute pression 52 et l'autre à un reservoir de fluide 53 à la pression atmosphérique. Cette liaison sélective est effectuée à l'aide de deux conduits 54 et 55 respectivement par l'intermédiaire d'un distributeur 58 pouvant également relier les deux entrées du moteur 49 au réservoir 53.FIG. 4 represents the hydraulic diagram of the device on which the bidirectional drive motor 49 of the carriage 4 is seen. This motor has two inlets 50 and 51 which are selectively connected to a high pressure source 52 and the other to a reservoir of fluid 53 at atmospheric pressure. This selective connection is carried out using two conduits 54 and 55 respectively via a distributor 58 which can also connect the two inputs of the motor 49 to the reservoir 53.

On voit également sur la figure 4 l'unité 10 avec ses deux verrous ralentisseurs 11 montés chacun sur un des conduits 54 et 55.FIG. 4 also shows the unit 10 with its two retarder latches 11 each mounted on one of the conduits 54 and 55.

Les entrées 30 des deux verrous ralentisseurs sont reliées au distributeur 56 et les deux entrées 31 sont reliées aux entrées 50 ét 51 du moteur 49. Enfin les orifices 32 des verrous ralentisseurs sont ramenés au réservoir 53.The inputs 30 of the two retarder latches are connected to the distributor 56 and the two inputs 31 are connected to the inputs 50 and 51 of the motor 49. Finally the orifices 32 of the retarder latches are brought back to the reservoir 53.

Le fonctionnement du dispositif est le suivant. On suppose que le chariot 4 est dans la position représentée à la figure 2 où il est positionné par l'engagement du doigt de verrouillage 12 du verrou ralentisseur 11 de gauche engagé dans la gorge annulaire 20 de la came 19. Le distributeur de pression 56 est dans la position représentée à la figure 4 de sorte qu'aucune pression ne s'exerce à l'entrée des verrous ralentisseurs. Par conséquent, du fait de la force exercée par le ressort 38, les pistons des deux verrous ralentisseurs sont dans la position des figures 5 et 6.The operation of the device is as follows. It is assumed that the carriage 4 is in the position shown in FIG. 2 where it is positioned by the engagement of the locking finger 12 of the retarder lock 11 on the left engaged in the annular groove 20 of the cam 19. The pressure distributor 56 is in the position shown in Figure 4 so that no pressure is exerted at the input of the retarder latches. Consequently, due to the force exerted by the spring 38, the pistons of the two retarder latches are in the position of FIGS. 5 and 6.

On suppose maintenant que l'on souhaite amener le chariot 4 devant la colonne correspondant à la butée 13a de la figure 2. Pour cela l'arbre porteur de came 14 est tourné de telle sorte que la came 13a se trouve dans le plan de l'unite 10 et du côté de cette unité par rapport à l'axe de l'arbre 14.We now assume that we want to bring the carriage 4 in front of the column corresponding to the stop 13a in Figure 2. For this the cam carrier shaft 14 is rotated so that the cam 13a is in the plane of l unit 10 and on the side of this unit with respect to the axis of the shaft 14.

La haute pression est alors amenée à l'entrée 30 du verrou ralentisseur de gauche.The high pressure is then brought to the inlet 30 of the left retarder lock.

La pression s'exerce alors sur la différence de section du piston 28 entre ses zones 39 et 40 de sorte que le piston est enfoncé contre l'action du ressort pour venir dans la position représentée à la figure 7. Deux fonctions sont réalisées dans ce mouvement. D'une part le doigt 12 est extrait de la gorge de verrouillage 20 et le chariot 4 est par conséquent déverrouillé. Par ailleurs le conduit annulaire 48 est ouvert permettant le passage du fluide à plein débit dans le sens de la flèche 57 de la rigure 7 du distributeur vers le moteur sans perte de charge.The pressure is then exerted on the difference in cross section of the piston 28 between its zones 39 and 40 so that the piston is pressed against the action of the spring to come into the position represented in FIG. 7. Two functions are performed in this movement. On the one hand, the finger 12 is extracted from the locking groove 20 and the carriage 4 is consequently unlocked. Furthermore, the annular duct 48 is open allowing the fluid to pass at full flow in the direction of arrow 57 in FIG. 7 from the distributor to the engine without pressure drop.

Le chariot 4 est par conséquent entraîné par le moteur.The carriage 4 is therefore driven by the motor.

Le verrou ralentisseur de droite de la figure 2 qui se trouve en aval du moteur reçoit le fluide sortant du moteur sur son entrée 31. Ce verrou ralentisseur se trouve dans la configuration de la figure 6 avec ses entrées 30 et 31 correspondant par les perçages radiaux 47, le perçage axial 44 et les perçages radiaux de grands diamètres 45. Dans cette configuration le verrou ralentisseur n'oppose qu'une faible résistance au passage du fluide de sorte que le moteur entraîne le chariot à grande vitesse.The right retarder lock of Figure 2 which is downstream of the engine receives the fluid leaving the engine on its inlet 31. This retarder lock is in the configuration of Figure 6 with its inputs 30 and 31 corresponding by the radial holes 47, the axial bore 44 and the radial boreholes of large diameters 45. In this configuration, the retarder lock provides only a small resistance to the passage of the fluid so that the motor drives the carriage at high speed.

Lorsque le doigt 12 du verrou ralentisseur de droite arrive sur la partie 17 de la came 13a on se trouve alors dans la configuration de la figure 8. Le piston 28 est légèrement enfoncé dans le cylindre 29 de sorte que les entrées 30 et 31 du verrou ralentisseur ne sont plus en communication que par les perçages radiaux 47, le perçage radial 44 et le perçage radial 46 de faible diamètre. Du fait du faible diamètre de ce perçage 46 une forte résistance est opposée au passage du fluide ce qui a pour effet d'augmenter la pression en aval du moteur 49 et par conséquent de ralentir celui-ci.When the finger 12 of the right retarder lock arrives on the part 17 of the cam 13a, we are then in the configuration of FIG. 8. The piston 28 is slightly depressed in the cylinder 29 so that the inputs 30 and 31 of the lock retarder are no longer in communication except by radial holes 47, radial bore 44 and radial bore 46 of small diameter. Due to the small diameter of this drilling 46 a strong resistance is opposed to the passage of the fluid which has the effect of increasing the pressure downstream of the motor 49 and consequently of slowing the latter.

Le mouvement se poursuit alors à petite vitesse jusqu'à ce que le doigt 12 vienne s'engager dans l'encoche 18 de la came 13a.The movement then continues at low speed until the finger 12 comes to engage in the notch 18 of the cam 13a.

Le distributeur est alors ramené à la position neutre.The distributor is then returned to the neutral position.

Les organes de préhension de munitions sont alors actionnés pour saisir l'obus ou la douille correspondante après quoi le distributeur est inversé pour amener la haute pression à l'entrée 30 du verrou ralentisseur de droite ce qui a pour effet de déverrouiller le chariot et d'entraîner celui-ci à grande vitesse jusqu'à ce que le doigt 12 du verrou ralentisseur de gauche vienne sur la partie cylindrique 21 de la came 19 où le mouvement se poursuit à petite vitesse comme expliqué ci-dessus jusqu'à ce que le doigt 12 du verrou ralentisseur de gauche s'engage dans la gorge de verrouillage de la came 19. La pince 7 est alors prise en charge comme expliqué ci-dessus pour être amenée aux moyens de chargement proprement dits.The ammunition gripping members are then actuated to grasp the shell or the corresponding socket after which the distributor is inverted to bring the high pressure to the inlet 30 of the right retarder lock which has the effect of unlocking the carriage and d '' drive it at high speed until the finger 12 of the left retarder lock comes on the cylindrical part 21 of the cam 19 where the movement continues at low speed as explained above until the finger 12 of the left retarder lock engages in the locking groove of the cam 19. The clamp 7 is then taken care of as explained above in order to be brought to the loading means proper.

On constate par conséquent que l'invention permet d'assurer un déplacement rapide du chariot 4 tout en évitant les chocs violents au moment de l'arrêt du mouvement grâce à un ralentissement préalable.It can therefore be seen that the invention makes it possible to ensure rapid movement of the carriage 4 while avoiding violent shocks when the movement is stopped by virtue of a prior slowing down.

On remarquera de plus que l'accouplement 25 entre le piston 28 et le doigt de verrouillage 12 évite tous les efforts radiaux dûs au verrouillage qui pourraient rompre le film d'huile nécessaire au niveau de l'ajustement et entraîner ainsi un grippage.It will also be noted that the coupling 25 between the piston 28 and the locking finger 12 avoids all the radial forces due to locking which could break the oil film necessary at the level of the adjustment and thus cause seizure.

Par ailleurs un minimum de pièces sont en mouvement puisque le piston assure à la rois une fonction de clapet anti-retour et d'étrangleuret commande le doigt de verrouillage.In addition, a minimum of parts are in motion since the piston provides the kings with a non-return valve and throttle function and controls the locking finger.

Enfin la mise en place de l'unité 10 sur le chariot 4 ne demande ni montage particulier ni réglage.Finally, the installation of the unit 10 on the carriage 4 does not require any particular mounting or adjustment.

Claims (8)

1 - Hydraulic device for slowing down and locking moving component (4) with respect to a support (5, 6, 14), which can be driven in one direction or the other by hydraulic assembly (10) including bidirectional drive component (49) with two inputs and one directional control valve (56) directing a fluid under pressure to one or the other input (50, 51) of the drive component (49) through two pipes (54, 55), with circuits (28, 29) to allow free or restricted flow of the fluid from the flow control valve (56) to the drive component (49) to assume a first configuration allowing the free flow of the fluid from the drive component (49) to the flow control valve (35) and a second configuration allowing restricted flow, a cam follower (12) driven by cam (15, 19) to control the change from one configuration to the other, in which said system includes two braking latches (11), each on onepf the said pipes (44, 45) and connected by one inlet (30) to the flow control valve (56) and by a second inlet (31) to the drive component (49), circuits (28, 29) that carry the flow being integral with the braking latches, each braking latch (11) being fitted with a latch bolt (12), loaded by spring (38), operating in notch (18), and also being arranged to ensure the unlatching of moving component (4) and the free flow of fluid from the control valve (56) to drive component (49) when it receives the pressure at its inlet (30) connected to the flow control valve and capable of adopting, in the absence of pressure of the first inlet (30), both configurations, allowine free or restricted flow of the fluid.
2 - Device as claimed in claim 1, wherein the circuit (29, 29) controlling the flow consists of a cylinder (29) carrying a piston in stages (28) with all of the orifices (45,46,47) arranged to correspond selectively to annular groves (35, 35) on the inner surface of the cylinder (29) and connected to inlets (30, 31) of the braking latch 1).
3 - Device as claimed in claim 2, in which piston (28) includes one area (39) of relatively small cross section and one area (40) of relatively large cross section, and where cylinder (29) includes corresponding sections in areas (33, 34), the annular grove (35) corresponding to the inlet (30) connected to the flow control valve (56) beine fitted into the small-section area (33) of the cylinder (29), and the annular groove (36) corresponding to the inlet (31) connected to the drive component (49) being fitted into the large- section area (34) of the cylinder (29).
4 - Device as claimed in either claim 2 or 3, wherein the fact that the piston (28) includes one axial bore (44) and three sets of radial bores (45, 45,47) arriving at the axial bore, with the first set of radial bores (45) having a relatively large sectional area and coming out into the annular grove (35) corresponding to inlet (31) connected to drive component (49) for the first relative position of the piston (28) and cylinder (29) corresponding to the first configuration of the braking latch (11), the second set of radial bores (26) having a relatively small section and coming out in the same annular groove (36) at a second relative position of the piston and cylinder corresponding to the second configuration of the braking latch, and the third set of radial bores (47) having a relatively large sectional area and coming out in the other annular groove (25) for both relative positions of the piston and cylinder.
5 - Device as claimed in any one of the claims 2 to 4, wherein latch bolt (12) is connected to piston (28).
6 - Device as claimed in claim 5, wherein the fact that spring (38) is subjected to the fluid pressure and presses the latch bolt (12) into the correspondine notch (18, 20) in the absence of pressure at the inlet (20, 31) of braking latch (11).
7 - Device as claimed in any one of the claims 1 to 6, wherein said device includes several cams (13) arranged to work together with at least one of the braking latches (11), spaced longitudinally and circumferentially around a shaft (14) that can be positioned at an angle to place one of the cams in the path of relative motion of the braking latch along the said shaft.
8 - Automatic gun feed assembly including a combination of at least one shell storage rack (2), shell gripping systems (7) mounted on a mobile cart (4), and a hydraulic device (10) as claimed in any one of the claims 1 to 9 for braking and locking the moving cart (4).
EP19830400135 1982-01-21 1983-01-20 Hydraulic deceleration and blocking arrangements, and automatic gun ammunition feeding apparatus including the same Expired EP0086127B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8200867A FR2520452A1 (en) 1982-01-21 1982-01-21 HYDRAULIC DOWNLINK AND LATCHING DEVICE AND AUTOMATIC CANON FEEDING ASSEMBLY HAVING SUCH A DEVICE
FR8200867 1982-01-21

Publications (2)

Publication Number Publication Date
EP0086127A1 EP0086127A1 (en) 1983-08-17
EP0086127B1 true EP0086127B1 (en) 1986-09-03

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Application Number Title Priority Date Filing Date
EP19830400135 Expired EP0086127B1 (en) 1982-01-21 1983-01-20 Hydraulic deceleration and blocking arrangements, and automatic gun ammunition feeding apparatus including the same

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EP (1) EP0086127B1 (en)
DE (1) DE3365750D1 (en)
FR (1) FR2520452A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2729130A1 (en) * 1995-01-11 1996-07-12 Otis Elevator Co Support for hanging elevator cables to prevent lateral movement
SE508923C2 (en) * 1998-01-27 1998-11-16 Bofors Ab Garnet magazine for coarser self-propelled artillery pieces

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3122967A (en) * 1964-03-03 Ammunition handling- and loading system for major caliber guns
GB1268452A (en) * 1968-05-31 1972-03-29 Wilhelmsburger Maschinenfabric Metal strip feed device
FR2048095A5 (en) * 1969-06-04 1971-03-19 Applic Tech Et
US3628463A (en) * 1970-02-20 1971-12-21 Interlake Steel Corp Speed-control device

Also Published As

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DE3365750D1 (en) 1986-10-09
EP0086127A1 (en) 1983-08-17
FR2520452B1 (en) 1984-04-27
FR2520452A1 (en) 1983-07-29

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