EP1877669B1 - Entrainement hydraulique de catapulte - Google Patents

Entrainement hydraulique de catapulte Download PDF

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Publication number
EP1877669B1
EP1877669B1 EP06722537A EP06722537A EP1877669B1 EP 1877669 B1 EP1877669 B1 EP 1877669B1 EP 06722537 A EP06722537 A EP 06722537A EP 06722537 A EP06722537 A EP 06722537A EP 1877669 B1 EP1877669 B1 EP 1877669B1
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EP
European Patent Office
Prior art keywords
pressure
hydraulic cylinder
catapult drive
drive according
catapult
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.)
Not-in-force
Application number
EP06722537A
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German (de)
English (en)
Other versions
EP1877669A1 (fr
Inventor
Sander Leonard Boeijen
Marten Fluks
Maarten Rik Leo Kuijpers
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Bosch Rexroth AG
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Bosch Rexroth AG
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Publication of EP1877669A1 publication Critical patent/EP1877669A1/fr
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    • A—HUMAN NECESSITIES
    • A63—SPORTS; GAMES; AMUSEMENTS
    • A63G—MERRY-GO-ROUNDS; SWINGS; ROCKING-HORSES; CHUTES; SWITCHBACKS; SIMILAR DEVICES FOR PUBLIC AMUSEMENT
    • A63G7/00—Up-and-down hill tracks; Switchbacks
    • 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
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • 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"
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • 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
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • 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
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source 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
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F15B2211/7054—Having equal piston areas
    • 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
    • F15B2211/755—Control of acceleration or deceleration of the output member

Definitions

  • the invention relates to a hydraulic catapult drive according to the preamble of claim 1.
  • Such hydraulic catapult drives are used for accelerating an object, for example an aircraft along a launcher or a passenger train of a roller coaster or the like.
  • a catapult drive is shown, via which a vehicle of a ride along an acceleration route can be accelerated.
  • the catapult drive has a driven by a hydraulic motor and a traction mechanism carrier car, on which the vehicle to be accelerated is supported.
  • the hydraulic engine drives a winch, which is wrapped in opposite directions by two tension cables, both of which attack the vehicle. When accelerating one of the traction means is wound onto the winch, while the other traction means unwinds accordingly.
  • the traction mechanism is tensioned during acceleration and recovery via a tensioning cable of another traction mechanism.
  • the US Pat. No. 6,837,166 B1 discloses a catapult drive for a ride, in which the driver is accelerated via a traction mechanism and a hydraulic cylinder over which a movable pulley set of the traction mechanism is axially displaceable.
  • this catapult drive is additionally a pull rope on the driver fastened another Switzerlandstoffgetriebes whose end portions - similar to the above embodiment - be wound on a winch or unwound from this, so that the provision of the driver is carried out in the basic position by appropriate control of the winch, in which case the hydraulic cylinder with the movable pulley set in his basic position will be reversed.
  • WO 2004/024562 A1 discloses a catapult drive, in which the acceleration of the driver via a traction mechanism and a hydraulic cylinder designed as a differential cylinder takes place, the bottom-side cylinder space can be acted upon extension of the piston rod with the pressure in a high-pressure accumulator.
  • the piston rod of the differential cylinder carries two movable pulley sets, which are wrapped by a common pull rope to which the driver is attached.
  • Further catapult drives are in US-A-1, 777, 167 and US-A-1,960,264 disclosed.
  • catapult drives described above require comparatively high equipment complexity, since different actuating elements are used for the acceleration and return of the driver, each of which must be controlled in a suitable manner.
  • the invention has for its object to provide a simply constructed catapult drive on the one to be accelerated Accelerated object attacking driver and is moved back to its basic position.
  • the hydraulic catapult drive has a driver which can be moved in the direction of acceleration and in the return direction via a traction mechanism transmission and a hydraulic cylinder driving it.
  • the traction mechanism has two of the hydraulic cylinder movable, at least one traction means partially wrapped pulley sets, so that depending on the control of the hydraulic cylinder via a pulley and the traction means is a tensile force for accelerating or over the other pulley a tensile force for resettable transferable.
  • the driver can be delayed or accelerated in both directions of movement.
  • the acceleration and the return movement takes place with the aid of a single hydraulic cylinder, on which two movable pulley sets of the traction mechanism are arranged.
  • a single hydraulic cylinder on which two movable pulley sets of the traction mechanism are arranged.
  • each pulley set may be assigned a traction means, which is then deflected in each case on the driver. Consequently, engage in this embodiment, the driver at least two traction means or tension cables.
  • both disc sets of the traction mechanism are wrapped by a common traction means, is attached to the central region of the driver.
  • the free end of the or the traction means are anchored rigidly or displaceably.
  • a spring element or a clamping cylinder can be arranged between the end of the traction means and the anchoring in order to avoid a loose coming of the traction means and to compensate for changes in length.
  • clamping cylinders When using clamping cylinders they can be acted upon by the pressure in the associated pressure chamber of the hydraulic cylinder, or be controlled by a separate system.
  • the movable sheaves and the associated fixed deflection pulleys of the traction mechanism can be arranged approximately in extension of the hydraulic cylinder or laterally thereof.
  • the hydraulic cylinder is designed as a synchronous cylinder or with two piston rods of different diameters, wherein one of the disc sets is arranged on each piston rod.
  • a differential cylinder at the single piston rod both pulley sets are arranged. This Koblenstange is then in a direction of movement (Accelerate or reset) pressurized.
  • the hydraulic cylinder can be designed with a cushioning integrated into or separate from the hydraulic cylinder.
  • the control of the hydraulic cylinder via a control arrangement wherein in one embodiment, an increase in acceleration pressure chamber of the hydraulic cylinder via the control arrangement with a high-pressure accumulator and / or a high-pressure pump and the resetting magnifying pressure chamber of the hydraulic cylinder with a low pressure accumulator and / or a low pressure pump is connectable.
  • the high pressure pump is a variable displacement pump.
  • a proportionally adjustable control valve is arranged in the inlet to the pressure chamber of the hydraulic cylinder which increases during acceleration and in the course of the pressure chamber decreasing during acceleration, via which the inlet and outlet can be shut off and / or in dependence
  • An opening cross section for the pressure medium connection of the respective pressure chamber with a pressure medium source or a pressure medium sink can be opened by the weight to be accelerated.
  • control arrangement additionally has a continuously adjustable return control valve, on the resetting of the driver of the increasing pressure chamber the hydraulic cylinder with the low-pressure pump and the decreasing pressure chamber with the pressure medium sink are connectable. Since this return movement is relatively slow, the continuously adjustable return valve can be designed with a smaller nominal size than the aforementioned proportionally adjustable control valves.
  • control arrangement is designed with a check valve, via which a pressure fluid flow path can be controlled from the flow to the pressure chamber enlarging during acceleration when the driver is decelerating after the acceleration phase, whereby the associated proportionally adjustable control valve is bypassed.
  • a pilot-operated logic valve is arranged in the pressure medium flow path between each control valve and the associated pressure chamber, which allows a leak-free sealing of the pressure chambers.
  • the hydraulic cylinder is preferably arranged in an open hydraulic circuit.
  • FIG. 1 shows a circuit diagram of a hydraulic catapult drive 1 for a car or a passenger train of a roller coaster or the like.
  • This car is accelerated by a driven by the catapult drive 1 driver 2.
  • a traction mechanism 4 which is driven by a hydraulic cylinder 6.
  • This is executed in the illustrated embodiment as a synchronous cylinder.
  • the pressure medium supply of the hydraulic cylinder 6 via a control arrangement 8, via the two pressure chambers 10, 12 of the hydraulic cylinder 6 with a pressure medium source 14 or a pressure medium sink are connectable, the at illustrated embodiment is formed by a tank T.
  • the control arrangement 8 is designed as an open circuit. Further details of the catapult drive are described below with reference to the enlarged illustrations in FIGS Figures 2 and 3 explained.
  • FIG. 2 shows the traction mechanism 4 with the hydraulic cylinder 6 for moving the driver 2, wherein it is moved to accelerate in the direction of care and the return takes place in the opposite direction.
  • the hydraulic cylinder 6 is executed in this embodiment as a synchronous cylinder, is divided by the piston with the two piston rods 16, 18 of the cylinder in the two pressure chambers 10, 12, which are each designed as an annular space.
  • the piston is in the illustration according to FIG. 1 moved to the right, so that the pressure chamber 10 increases, while the right ( FIG. 2 ) Pressure chamber 12 is reduced accordingly.
  • the diameter of the piston rods 16, 18 executed the same. In principle, these can also be designed with different diameters.
  • a movable pulley 20 and 22 of the traction mechanism 4 is fixed in each case, which is correspondingly movable by the retraction and extension of the piston rods 16, 18.
  • Each pulley set 20, 22 is associated with a Umlenkumblensatz 24 and 26 respectively.
  • Each of these Umlenkemian instruments 24, 26 is fixedly mounted on the frame of the roller coaster or on a foundation.
  • the mutually associated pulley sets 22, 26 and 20, 24 are each of a traction means, for example a traction cable 28, 30 entwined, each engaging with an end portion on the driver 2, so that is moved over the traction cable 28 of the driver 2 in the acceleration direction, while the provision is made by means of the traction cable 30.
  • a traction means for example a traction cable 28, 30 entwined, each engaging with an end portion on the driver 2, so that is moved over the traction cable 28 of the driver 2 in the acceleration direction, while the provision is made by means of the traction cable 30.
  • It can also be a single continuous pull rope 28 are used, in which case the driver 2 is releasably secured thereto. The traction cable 28 can then be pulled through the driver 2, so that the rope change is simplified.
  • the respective other end portions of the two traction cables 28, 30 are in turn anchored to the frame / foundation.
  • this anchoring takes place via a respective clamping cylinder 32, 34, which is designed as a differential cylinder.
  • This clamping cylinder 32, 34 can be compensated for changes in length of the traction cables 28, 30 and a constant voltage can be adjusted.
  • the clamping cylinder 32, 34 has an annular space 38 and 36, which are connected via a tension line 40 and 42 respectively to the adjacent pressure chamber 10 (tension line 40) and 12 (tension line 42). This ensures that the pulling cable 28, 30 exerting a pulling force on the driver 2 when accelerating or returning is stretched in each case by the pressure in the pressure chamber 10, 12 which increases in the process.
  • clamping elements such as pneumatic clamping cylinders, tension springs, etc. may be used.
  • tension springs etc.
  • a "rigid”, but adjustable, anchoring of the respective hawser is possible.
  • the two movable pulley sets 20, 22 four pulleys 44, and the fixed pulley sets 24, 26 each have 4 sheaves 46, so that correspondingly there is an 8-fold translation. Consequently, the stroke of the piston rods 16, 18 is translated via the traction mechanism 4 so that the driver 2 covers 8 times the distance along the trajectory. Accordingly, the transmitted from the driver 2 on the car to be accelerated traction is only 1/8 of the force applied by the hydraulic cylinder 6.
  • two further stationary guide discs 48, 50 are provided between the driver 2 and the Umlenkusionnsatz 26, via which the traction cable 30 is aligned with respect to the trajectory of the driver 2.
  • the pull rope 28 which acts in the direction of acceleration, only a fixed guide plate 52 is provided.
  • the movable pulley sets 20, 22 can be suitably guided or supported.
  • the movable disc sets 22, 20 are mounted on a common, dash-dotted lines indicated traverse 54 and 56, which in turn are attached to the respectively associated piston rod 16 and 18 respectively.
  • the discs 44 of the movable disc sets 20, 22 can also be arranged coaxially next to one another, in which case the deflecting discs 46 are aligned accordingly.
  • the piston of the hydraulic cylinder 6 is moved to the right, so that according to the movable pulley 20 is also moved to the right and the distance between the movable pulley 20 and the Umlenkusionnsatz 24 increases and corresponding to the driver 2 in the arrow direction is accelerated.
  • the movable pulley set 44 is shifted to the right to Umlenkusionnsatz 26 out, wherein the pull cable 30 moves over the moving carrier 2, and is held by the cylinder 32 to voltage.
  • the piston rods 16, 18 are mounted via a hydrostatic bearing 58, 60 in the cylinder bottom of the cylinder 6. Since such hydrostatic bearings are known in the art, can be dispensed with explanations.
  • the hydraulic cylinder 6 is preferably also designed with end position damping devices which are either integrated in the hydraulic cylinder 6 or arranged externally.
  • the pressure medium source 14 by a pump assembly with a variable displacement pump 62, a constant displacement pump 64 and a high pressure accumulator 66 is formed.
  • the fixed displacement pump 64 and the variable displacement pump 62 are preferably driven by a common motor M.
  • the pressure connection of the fixed displacement pump 64 is followed by a check valve 67.
  • a pilot-operated pressure relief valve 68 or 69 with Directional valve relief connected at each pressure port.
  • the pressure connections of the variable displacement pump 62 and of the high-pressure accumulator 66 are connected via an HP pump line 70 to a pressure port P1 of a control block 72 receiving the control arrangement 8 (indicated by dash-dotted lines).
  • the pressure connection of the fixed displacement pump 64 is connected via an LP pump line 74 to a further pressure port P2 of the control block 72.
  • This also has a tank connection T, which is connected via a tank line 76 and a congestion valve 78 to the tank T.
  • a tank connection T which is connected via a tank line 76 and a congestion valve 78 to the tank T.
  • FIG. 3 can still be provided 71 in the tank line 76, a cooler.
  • a low-pressure hydraulic accumulator 80 is connected, can be compensated by the pressure fluctuations in the tank line 76.
  • the damper valve 78 ensures that the tank line 76 is slightly biased.
  • control port X and a drain port Y are provided on the control block 72, the latter being connected to the tank T.
  • the control port X is connected to the HP pump line 70, so that the pressure prevailing therein acts as a control pressure.
  • an external control pressure can also be given up.
  • the pressure port P1 is connected via a supply line 82 to the input port A of a proportionally adjustable control valve 84, which is referred to below as the acceleration control valve 84.
  • This is precontrolled electro-hydraulically, wherein the control pressure is tapped via a control line 86 from the control terminal X. The leaked oil can flow off via a drain line 87 to the drain port Y.
  • This acceleration control valve 84 may, for example, as a pilot-operated, proportionally adjustable Logic valve be executed.
  • a port B of the acceleration control valve 84 is connected via a feed line 88 and a logic valve 90 to the pressure chamber 10 of the hydraulic cylinder 6.
  • the acceleration control valve 84 closes off the pressure medium connection to the supply line 88 in a leak-tight manner.
  • a pressure medium volume flow determining inlet orifice is opened.
  • the arranged in the flow line 88 logic valve 90 is also carried out pilot-controlled, wherein in a cover 92 of the logic valve 90, a shuttle valve 94 is arranged, the two inputs are acted upon by the pressures at port A and B of the logic valve 90, so that the each larger pressure is forwarded.
  • the output of the shuttle valve 94 is connected to the input of a pilot valve 96.
  • This is designed as a 4/2-way switching valve and connects in its spring-biased home position, the output of the shuttle valve 94 with a spring chamber 98 of the logic valve 90 so that it is biased in the closed position and shuts off the pressure fluid flow path to the annulus 10.
  • a drain line 104 is connected, the pressure over a another pressure sensor 106 can be detected and in which a further logic valve 108 is provided, which has virtually the same structure as the logic valve 90.
  • D. h. The greater pressure at the terminals A, B of the logic valve 108 is tapped via a shuttle valve 110 and reported in a basic position of a pilot valve 112 in a spring chamber 114 of the logic valve 108.
  • the pilot valve 112 By switching the pilot valve 112, the spring chamber 114 is connected to the control oil tank line 87 and thus relieved of pressure, so that the logic valve 108 can be opened by the pressure applied to the pressure port B or A pressure.
  • the port A of the logic valve 108 is connected to an output port B of another continuously variable control valve, hereinafter called discharge control valve 116, whose construction is similar to that of the acceleration control valve 84, so that further explanations are unnecessary.
  • discharge control valve 116 a continuously variable control valve
  • pilot-operated pressure relief valves 120, 122 To avoid pressure increases in the flow line 88 and the return line 104, these are connected to each other via two pilot-operated pressure relief valves 120, 122, wherein the maximum pressure by appropriate adjustment of a pilot valve 124, 126 takes place.
  • the control arrangement is the return movement of the driver, ie, the axial displacement of the piston of the hydraulic cylinder 6 to the left by means of a continuously adjustable remindstellregelventils 128.
  • This has four ports, wherein a pressure port P via a return line 130 to the second pressure port P2 of the control block 72 and a Tank connection T is connected via a return tank line 132 to the drain line 118.
  • Two work connections A, B are connected via a return flow line 134 to the return line 104 and via a return return line 136 to the flow line 88, wherein the valves 84, 116; 90, 108 are bypassed.
  • a pilot-operated check valve 138, 140 is provided in each case.
  • the reset control valve 128 In its spring-biased home position, the reset control valve 128 connects its two working ports A, B to the return tank line 182, with the check valves 138, 140 blocking fluid flow from the return line 104 or from the flow line 88 to the working ports A, B of the reset control valve 128.
  • the illustrated control assembly 8 further includes a check valve 142 which is in a return tank line 132 is arranged with the supply line 88 filling line 144 is arranged.
  • This check valve 142 is also executed in the illustrated embodiment as a logic valve, wherein in its spring chamber 146, the pressure in the flow line 88 is reported.
  • the acceleration control valve 84 and the drain control valve 116 are controlled controlled, the controlled cross section depending on the weight of the passenger car, which can vary due to the number of passengers to set a predetermined acceleration profile.
  • the variable displacement pump 62 is driven via the motor M and promoted pressure medium in the HP pump line 70.
  • the two pilot valves 96 and 112 of the logic valves 90, 108 are switched, so that the pressure medium is conveyed via the opening logic valve 90 and the supply line 88 into the pressure chamber 10, so that the piston of the hydraulic cylinder 6 is moved to the right and - explained - by increasing the distance between the movable pulley set 20 and the associated Umlenkusionnsatz 24 of the driver 2 by the pull rope 28 in the arrow direction ( FIG.
  • the pressure medium from the decreasing annulus 12 flows via the return line 104 to the logic valve 108, wherein the pressure in the return line 104 acts on the annular surface of the piston of the logic valve 108 and brings it into its open position, so that the pressure medium via the up-flow control valve 116, the drain line 118, the tank line 76 and the congestion valve 78 flows toward the tank T.
  • the control valves 84, 116 are controlled in such a way that the desired speed or acceleration profile is established.
  • the acceleration control valve 84 is closed and the flow control valve 116 controlled controlled that a predetermined Abbrems effetsprofil is met.
  • the speed of movement of the piston of the hydraulic cylinder 6 is reduced accordingly, whereby the volume of the pressure chamber 10 (acceleration pressure chamber) further increases - the pressure medium required to fill this pressure chamber 10 can then flow via the opening check valve 142 from the drain line 118, so that the filling takes place in the braking phase despite closed or almost closed acceleration control valve 84.
  • the energy consumption from the high-pressure accumulator 66 is minimal.
  • the hydraulic accumulator 66 can be charged relatively slowly via the variable displacement pump 62, since sufficient time is available. During the waiting time until the next acceleration of the driver 2, the drive side of the control arrangement is virtually unloaded, so that no separate locking device is required.
  • the traction mechanism 4 is executed with two traction cables 28, 30, wherein the driver 2, two additional deflecting discs 148, 150 are provided which serve to deflect each of the traction cables 28, 30.
  • This facilitates the replacement of the traction cables 28 or 30, since they no longer have to be released from the driver 2.
  • the two movable pulley sets 20, 22 are each implemented with 6 pulleys 44, so that a corresponding 6-fold translation results.
  • the respectively associated Umlenkiminsatz 24, 26 is carried out accordingly, wherein the Glasseil Insert is designed so that the piston rod 18 is loaded symmetrically and that the two end portions of the strips 28, 30 each end in the axial region of the piston rod 16, 18.
  • each traction cable 28, 30 are then anchored in this embodiment via a tension spring 152, 154, via which the traction cables 28, 30 are kept under tension.
  • the tension springs 152, 154 are designed so that they can transmit the required tensile forces to accelerate the driver 2.
  • the cable guide is made by additional stationary guide discs 48, 50, 52 and 156th
  • the traction mechanism 4 is designed so that the movable pulley 20, 22 and the fixed Umlenkusionnsatz 24, 26 arranged in extension of the hydraulic cylinder 6 are so that in the axial direction comparatively much space is needed.
  • the cable guide of the traction mechanism 4 can also be made so that the cable guide is located laterally of the hydraulic cylinder 6.
  • the two associated Umlenkrawn accounts 24, 26 are then inwardly, each zuvermine so that they lie on both sides of the cylinder jacket.
  • the stationary deflection pulleys 24, 26 may be supported on the cylinder or on the frame of the roller coaster.
  • the two end portions of the - in this case - common traction cable 28 are in turn anchored stationary.
  • the traction cable 28 is then guided to the driver 2 (not shown) and fastened to the traction cable 28.
  • the driver 2 not shown
  • fastened to the traction cable 28 can also be done with two tension cables.
  • a hydraulic cylinder 6 with two piston rods 16, 18 is used, which preferably have the same diameter.
  • a differential cylinder with a single piston rod 16 instead of such a synchronous cylinder, to which the movable pulley sets 20, 22 are then fastened.
  • the two Umlenkharin accounts 24, 26 are in turn mounted stationary.
  • the disc assembly is wrapped by a common pull cable 28 to which the driver 2 is attached.
  • the two end portions of the pull rope 28 are anchored.
  • the entire traction mechanism 4 looping around Switzerlandseils 28 also a variant with two separate traction cables 28, 30 according to FIG. 4 be used.
  • FIG. 3 explained control arrangement allows operation of a roller coaster with minimal energy losses, but the control arrangement does not necessarily have to be designed as complex as shown.
  • the minimum requirements for this control arrangement are in FIG. 7 shown. Accordingly, the operation of the traction mechanism 4, not shown, via a hydraulic cylinder 6 (synchronous cylinder, cylinder with two piston rods, differential cylinder), via which all movements of the driver 2 are controlled.
  • the two pressure chambers 10, 12 of the hydraulic cylinder 6 can be connected in the simplest case via a control valve assembly 158 with a high pressure side HDS and / or a low pressure side NDS.
  • high-pressure side HDS is understood to mean, for example, a high-pressure accumulator 66 and a high-pressure pump (variable-displacement pump 62).
  • low pressure side NDS stands in principle for the return side to the tank T. In this area, a low-pressure accumulator can be provided to compensate for pressure fluctuations.
  • the control valve assembly 158 may be implemented by one or more control valves.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Friction Gearing (AREA)
  • Braking Arrangements (AREA)

Claims (16)

  1. Entraînement hydraulique de catapulte pour l'accélération d'un objet, en particulier d'un wagon de montagnes russes, avec un entraîneur (2) mobile le long d'une trajectoire, agissant sur l'objet pour son accélération, qui peut être déplacé par un engrenage de moyen de traction (4) et un vérin hydraulique (6) propulsant celui-ci dans le sens d'accélération ou dans le sens de rappel, sachant qu'au moins un espace de pression du vérin hydraulique (6) peut être relié par un ensemble de commande (8) à une source de moyen de pression (14) ou à un puits de moyen de pression (T), sachant que l'engrenage de moyen de traction (4) présente deux jeux de poulies (20, 22) mobiles enroulés par section par au moins un moyen de traction (28, 30) de l'entraînement de catapulte, pouvant être déplacés par le vérin hydraulique (6), sachant qu'une force de traction peut être transmise à l'entraîneur (2) selon la commande du vérin hydraulique (6) par un jeu de poulies (20, 22) et le moyen de traction (28, 30) pour l'accélération et par l'autre jeu de disques (22, 20) et le moyen de traction (28, 30) pour le rappel, caractérisé en ce que le vérin hydraulique (6) est réalisé comme un vérin à double tige ou avec deux tiges de piston de diamètre différent, sachant que l'un des jeux de poulies (20, 22) est disposé sur chaque tige de piston (16, 18) de telle manière que les tiges de piston ne soient sollicitées qu'en traction.
  2. Entraînement de catapulte selon la revendication 1, sachant qu'un moyen de traction (28, 30) de l'entraînement de catapulte est associé à chaque jeu de poulies (20, 22), lequel est renvoyé respectivement sur l'entraîneur (2).
  3. Entraînement de catapulte selon la revendication 1, sachant que les deux jeux de poulies mobiles (20, 22) sont enroulés par un moyen de traction commun (28) de l'entraînement de catapulte, sur la zone médiane duquel est fixé l'entraîneur (2).
  4. Entraînement de catapulte selon la revendication 2 ou 3, sachant que des sections d'extrémité libres du moyen de traction (28, 30) sont ancrées de manière rigide ou mobile.
  5. Entraînement de catapulte selon la revendication 4, sachant qu'un élément de ressort (152, 154) est disposé entre l'extrémité du moyen de traction (28, 30) et l'ancrage.
  6. Entraînement de catapulte selon la revendication 4, sachant qu'un cylindre de serrage (32, 43) est disposé entre l'extrémité du moyen de traction (28, 30) et l'ancrage.
  7. Entraînement de catapulte selon la revendication 6, sachant que les cylindres de serrage (32, 34) sont sollicités respectivement par une pression dans l'espace de pression associé (10, 12) du vérin hydraulique (6).
  8. Entraînement de catapulte selon l'une quelconque des revendications précédentes, sachant que les jeux de poulies de renvoi (24, 26) associés aux jeux de poulies mobiles (20, 22) de l'entraînement de catapulte sont disposés à peu près dans le prolongement du vérin hydraulique (6) ou latéralement à celui-ci.
  9. Entraînement de catapulte selon l'une quelconque des revendications précédentes, avec un amortissement de fin de course du vérin hydraulique (6).
  10. Entraînement de catapulte selon l'une quelconque des revendications précédentes, sachant qu'un espace de pression (10) s'agrandissant lors de l'accélération du vérin hydraulique (6) peut être relié par l'ensemble de commande (8) à un réservoir à haute pression (66) et/ou à une pompe à haute pression (62) de l'entraînement de catapulte et l'espace de pression (12) s'agrandissant lors du rappel du vérin hydraulique (6) peut être relié à une source de basse pression et/ou une pompe à basse pression (64) de l'entraînement de catapulte.
  11. Entraînement de catapulte selon la revendication 10, sachant que la pompe à haute pression est une pompe à cylindrée variable (62) et la pompe à basse pression est une pompe à cylindrée constante (64).
  12. Entraînement de catapulte selon la revendication 10 ou 11, sachant que respectivement une soupape de régulation (84, 116) réglable proportionnellement est disposée dans l'alimentation menant à l'espace de pression (10) s'agrandissant lors de l'accélération et dans l'évacuation de l'espace de pression (12) se réduisant, par laquelle soupape l'alimentation et l'évacuation peuvent être obturées ou une section transversale d'ouverture peut être activée pour la liaison du moyen de pression de l'espace de pression respectif (10, 12) avec la source de moyen de pression (14) ou le puits de moyen de pression (10).
  13. Entraînement de catapulte selon la revendication 12, sachant que l'ensemble de commande (8) présente une soupape de régulation de rappel réglable en permanence (128), par laquelle lors du rappel de l'entraîneur (2), l'espace de pression s'agrandissant (12) du vérin hydraulique (2) peut être relié à une pompe à basse pression (64) et l'espace de pression se réduisant (10) peut être relié au puits de moyen de pression (T).
  14. Entraînement de catapulte selon la revendication 12 ou 13, avec un clapet antiretour (142), par lequel lors d'un freinage de l'entraîneur (2), une voie d'écoulement de moyen de pression (144) de l'évacuation à l'espace de pression (10) s'agrandissant lors de l'accélération peut être activée lors du contournement de la soupape de régulation (84) réglable en permanence disposée dans l'alimentation.
  15. Entraînement de catapulte selon l'une quelconque des revendications 12 à 14, sachant qu'une soupape logique (90, 108) précommandée est disposée entre chaque espace de pression (10, 12) et la soupape de régulation (84, 116) associée réglable en permanence.
  16. Entraînement de catapulte selon l'une quelconque des revendications précédentes, sachant que le vérin hydraulique (6) est disposé dans un circuit ouvert.
EP06722537A 2005-04-28 2006-02-27 Entrainement hydraulique de catapulte Not-in-force EP1877669B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102005020187 2005-04-28
DE102006002921A DE102006002921A1 (de) 2005-04-28 2006-01-20 Hydraulischer Katapultantrieb
PCT/DE2006/000366 WO2006114070A1 (fr) 2005-04-28 2006-02-27 Entrainement hydraulique de catapulte

Publications (2)

Publication Number Publication Date
EP1877669A1 EP1877669A1 (fr) 2008-01-16
EP1877669B1 true EP1877669B1 (fr) 2012-04-18

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EP06722537A Not-in-force EP1877669B1 (fr) 2005-04-28 2006-02-27 Entrainement hydraulique de catapulte

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US (1) US8028521B2 (fr)
EP (1) EP1877669B1 (fr)
CN (1) CN101166905B (fr)
AT (1) ATE554292T1 (fr)
DE (1) DE102006002921A1 (fr)
WO (1) WO2006114070A1 (fr)

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CN101676174B (zh) * 2008-09-19 2013-06-26 胡宣哲 ***冷弹射方法及装置
DK2342129T3 (en) * 2008-10-20 2016-11-07 Aai Corp Aircraft launch ramp with slide frame as well as related approach
CN101920785A (zh) * 2009-06-10 2010-12-22 马世强 电动磨擦牵引带式弹射器
CN102398683A (zh) * 2011-03-01 2012-04-04 刘卫峰 电磁弹射器
CN102689698B (zh) * 2012-05-22 2014-11-26 北京航空航天大学 一种固液动力飞行器地面发射控制装置
CN102785396A (zh) * 2012-07-27 2012-11-21 四川航空工业川西机器有限责任公司 高精度超高压压力曲线控制***
CN103863571B (zh) * 2012-12-12 2016-11-23 中航商用航空发动机有限责任公司 飞机弹射装置和飞机弹射方法
CN105346729B (zh) * 2015-11-16 2017-08-04 中国航天时代电子公司 一种无人机发射装置动力控制的气液压***
CN106956903B (zh) * 2017-04-12 2023-06-30 奥美森智能装备股份有限公司 一种加速装置
FR3105173B1 (fr) * 2019-12-20 2022-01-07 Univ De Technologie De Compiegne Utc Drone hydraulique multi-rotor
CN111746791B (zh) * 2020-06-12 2024-07-23 陕西飞机工业（集团）有限公司 一种飞行器载荷释放装置
CN112937900A (zh) * 2021-02-10 2021-06-11 张志刚 一种飞行器发射***、发射方法及飞行器
CN113339335B (zh) * 2021-06-16 2022-11-22 海南浙江大学研究院 一种增压弹射的伺服作动***

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Also Published As

Publication number Publication date
DE102006002921A1 (de) 2006-11-02
US8028521B2 (en) 2011-10-04
EP1877669A1 (fr) 2008-01-16
CN101166905A (zh) 2008-04-23
WO2006114070A1 (fr) 2006-11-02
CN101166905B (zh) 2012-02-01
ATE554292T1 (de) 2012-05-15
US20090100829A1 (en) 2009-04-23

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