EP0086127B1 - Dispositif hydraulique de ralentissement et de verrouillage et ensemble d'alimentation automatique de canon comportant un tel dispositif - Google Patents

Dispositif hydraulique de ralentissement et de verrouillage et ensemble d'alimentation automatique de canon comportant un tel dispositif 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)
English (en)
French (fr)
Other versions
EP0086127A1 (fr
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
Original Assignee
Delegation Generale pour lArmement
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Delegation Generale pour lArmement filed Critical Delegation Generale pour lArmement
Publication of EP0086127A1 publication Critical patent/EP0086127A1/fr
Application granted granted Critical
Publication of EP0086127B1 publication Critical patent/EP0086127B1/fr
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.

Landscapes

  • 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)
EP19830400135 1982-01-21 1983-01-20 Dispositif hydraulique de ralentissement et de verrouillage et ensemble d'alimentation automatique de canon comportant un tel dispositif Expired EP0086127B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8200867A FR2520452A1 (fr) 1982-01-21 1982-01-21 Dispositif hydraulique de ralentissement et de verrouillage et ensemble d'alimentation automatique de canon comportant un tel dispositif
FR8200867 1982-01-21

Publications (2)

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

Family

ID=9270179

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19830400135 Expired EP0086127B1 (fr) 1982-01-21 1983-01-20 Dispositif hydraulique de ralentissement et de verrouillage et ensemble d'alimentation automatique de canon comportant un tel dispositif

Country Status (3)

Country Link
EP (1) EP0086127B1 (enrdf_load_stackoverflow)
DE (1) DE3365750D1 (enrdf_load_stackoverflow)
FR (1) FR2520452A1 (enrdf_load_stackoverflow)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2729130A1 (fr) * 1995-01-11 1996-07-12 Otis Elevator Co Dispositif de guidage et d'entrainement des portes palieres et des portes de cabine d'un ascenseur
SE9800207L (sv) * 1998-01-27 1998-11-16 Bofors Ab Granatmagasin för grövre självgående artilleripjäser

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 (enrdf_load_stackoverflow) * 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

Publication number Publication date
DE3365750D1 (en) 1986-10-09
FR2520452B1 (enrdf_load_stackoverflow) 1984-04-27
FR2520452A1 (fr) 1983-07-29
EP0086127A1 (fr) 1983-08-17

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