EP1877669B1 - Hydraulic catapult drive - Google Patents

Hydraulic catapult drive 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
Authority
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
Other languages
German (de)
French (fr)
Other versions
EP1877669A1 (en
Inventor
Sander Leonard Boeijen
Marten Fluks
Maarten Rik Leo Kuijpers
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.)
Bosch Rexroth AG
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Bosch Rexroth AG
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Publication of EP1877669A1 publication Critical patent/EP1877669A1/en
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Publication of EP1877669B1 publication Critical patent/EP1877669B1/en
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Classifications

    • 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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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
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Abstract

The drive (1) has a traction drive (4) with two disk sets (20, 22) moving through a hydro cylinder (6) and section-wise moved by traction robes in an entangle manner. A traction force is transferred into an actuator (2) depending upon controlling of the hydro cylinder over one of the disk sets and the traction robes for acceleration of an object and over another disk set and the traction robes for resetting the object.

Description

Die Erfindung betrifft einen hydraulischen Katapultantrieb gemäß dem Oberbegriff des Patenanspruchs 1.The invention relates to a hydraulic catapult drive according to the preamble of claim 1.

Derartige hydraulische Katapultantriebe werden zum Beschleunigen eines Objektes, beispielsweise eines Fluggerätes entlang einer Abschussrampe oder eines Personenzugs einer Achterbahn oder dergleichen verwendet. In der WO 01/66210 A1 ist ein Katapultantrieb gezeigt, über den ein Fahrzeug eines Fahrgeschäftes entlang einer Beschleunigungsstrecke beschleunigt werden kann. Der Katapultantrieb hat eine von einem Hydromotor und einem Zugmittelgetriebe angetriebenen Mitnehmerwagen, an dem das zu beschleunigende Fahrzeug abgestützt ist. Der Hydromotor treibt eine Winsch an, die gegenläufig von zwei Zugseilen umschlungen ist, die beide an dem Fahrzeug angreifen. Beim Beschleunigen wird eines der Zugmittel auf die Winsch aufgewickelt, während sich das andere Zugmittel entsprechend abwickelt. Beim Rückstellen des Fahrzeugs in seine Grundposition wird die Drehrichtung des Hydromotors umgekehrt, so dass das erstgenannte Zugseil aufgewickelt und das letztgenannte Zugseil abgewickelt wird. Das Zugmittelgetriebe wird während der Beschleunigung und der Rückstellung über ein Spannseil eines weiteren Zugmittelgetriebes gespannt.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. In the WO 01/66210 A1 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. When returning the vehicle to its basic position, the direction of rotation of the hydraulic motor is reversed, so that the first-mentioned pull rope is wound and the last-mentioned pull rope is unwound. The traction mechanism is tensioned during acceleration and recovery via a tensioning cable of another traction mechanism.

Die US 6,837,166 B1 offenbart einen Katapultantrieb für ein Fahrgeschäft, bei dem der Mitnehmer über ein Zugmittelgetriebe und einen Hydrozylinder beschleunigt wird, über den ein beweglicher Scheibensatz des Zugmittelgetriebes axial verschiebbar ist. Bei diesem Katapultantrieb ist am Mitnehmer zusätzlich ein Zugseil eines weiteren Zugmittelgetriebes befestigt, dessen Endabschnitte - ähnlich wie beim vorbeschriebenen Ausführungsbeispiel - auf einer Winsch aufwickelbar oder von dieser abwickelbar sind, so dass die Rückstellung des Mitnehmers in die Grundposition durch entsprechende Ansteuerung der Winsch erfolgt, wobei dann auch der Hydrozylinder mit dem beweglichen Scheibensatz in seine Grundposition zurückverfahren wird.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. In this catapult drive is additionally a pull rope on the driver fastened another Zugmittelgetriebes 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.

In der WO 2004/024562 A1 ist ein Katapultantrieb offenbart, bei dem die Beschleunigung des Mitnehmers über ein Zugmittelgetriebe und einen als Differentialzylinder ausgeführten Hydrozylinder erfolgt, dessen bodenseitiger Zylinderraum beim Ausfahren der Kolbenstange mit dem Druck in einem Hochdruckspeicher beaufschlagbar ist. Die Kolbenstange des Differentialzylinders trägt zwei bewegliche Scheibensätze, die von einem gemeinsamen Zugseil umschlungen werden, an dem der Mitnehmer befestigt ist. Die Rückstellung des Hydrozylinders in seine Grundposition erfolgt über einen eigenen Rückstellzylinder, der ebenfalls als Differentialzylinder ausgeführt ist und dessen Kolbenstange diejenige des zur Beschleunigung verwendeten Differentialzylinders gegen die vom Hydrospeicher aufgebrachte Kraft in ihre Grundposition zurückverfährt. Weitere Katapultantriebe sind in US-A-1, 777, 167 und US-A-1, 960, 264 offenbart.In the 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. The provision of the hydraulic cylinder in its basic position via its own return cylinder, which is also designed as a differential cylinder and whose piston rod that of the differential cylinder used for acceleration zurückverfährt against the force applied by the hydraulic accumulator force in its basic position. Further catapult drives are in US-A-1, 777, 167 and US-A-1,960,264 disclosed.

Die vorbeschriebenen Katapultantriebe erfordern einen vergleichsweise hohen vorrichtungstechnischen Aufwand, da für die Beschleunigung und Rückstellung des Mitnehmers unterschiedliche Stellelemente eingesetzt werden, die jeweils in geeigneter Weise angesteuert werden müssen.The 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.

Demgegenüber liegt der Erfindung die Aufgabe zugrunde, einen einfach aufgebauten Katapultantrieb zu schaffen, über den ein an einem zu beschleunigenden Objekt angreifender Mitnehmer beschleunigt und in seine Grundposition zurückfahrbar ist.In contrast, 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.

Diese Aufgabe wird durch einen hydraulischen Katapultantrieb gemäß dem Oberbegriff des Patentanspruchs 1 gelöst.This object is achieved by a hydraulic catapult drive according to the preamble of patent claim 1.

Erfindungsgemäß hat der hydraulische Katapultantrieb einen Mitnehmer, der über ein Zugmittelgetriebe und einen dieses antreibenden Hydrozylinder in Beschleunigungsrichtung und in Rückstellrichtung bewegbar ist. Das Zugmittelgetriebe hat zwei vom Hydraulikzylinder bewegbare, von zumindest einem Zugmittel abschnittsweise umschlungene Scheibensätze, so dass je nach Ansteuerung des Hydrozylinders über einen Scheibensatz und das Zugmittel eine Zugkraft zum Beschleunigen bzw. über den anderen Scheibensatz eine Zugkraft zum Rückstellen übertragbar ist. Der Mitnehmer kann in beiden Bewegungsrichtungen verzögert oder beschleunigt werden.According to the invention, 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.

Erfindungsgemäß erfolgt die Beschleunigung und die Rückstellbewegung mit Hilfe eines einzigen Hydrozylinders, an dem zwei bewegliche Scheibensätze des Zugmittelgetriebes angeordnet sind. Bei einer derartigen Lösung ist - im Unterschied zum vorbeschriebenen Stand der Technik - kein eigener Antrieb zur Rückstellung des Mitnehmers erforderlich, so dass der vorrichtungstechnische Aufwand gegenüber diesen Lösungen wesentlich verringert ist.According to the invention, 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. In such a solution - in contrast to the above-described prior art - no separate drive for returning the driver required so that the device complexity is significantly reduced compared to these solutions.

Bei einem Ausführungsbeispiel der Erfindung kann jedem Scheibensatz ein Zugmittel zugeordnet sein, das dann jeweils am Mitnehmer umgelenkt ist. Demzufolge greifen bei diesem Ausführungsbeispiel am Mitnehmer zumindest zwei Zugmittel bzw. Zugseile an.In one embodiment of the invention, 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.

Bei einer alternativen Lösung werden beide Scheibensätze des Zugmittelgetriebes von einem gemeinsamen Zugmittel umschlungen, an dessen mittleren Bereich der Mitnehmer befestigt ist.In an alternative solution, both disc sets of the traction mechanism are wrapped by a common traction means, is attached to the central region of the driver.

Bei beiden Lösungen sind die freien Ende der oder des Zugmittels starr oder verschiebbar verankert. Dabei kann zwischen dem Ende des Zugmittels und der Verankerung ein Federelement oder ein Spannzylinder angeordnet werden, um ein Losekommen des Zugmittels zu vermeiden und Längenänderungen auszugleichen.In both solutions, the free end of the or the traction means are anchored rigidly or displaceably. In this case, 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.

Bei Verwendung von Spannzylindern können diese mit dem Druck im jeweils zugeordneten Druckraum des Hydrozylinders beaufschlagt sein, oder von einem gesonderten System angesteuert werden.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.

Je nach vorhandenem Bauraum können die beweglichen Seilscheiben und die diesen zugeordneten feststehenden Umlenkscheiben des Zugmittelgetriebes etwa in Verlängerung des Hydrozylinders oder seitlich von diesem angeordnet sein.Depending on the available space, 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.

Der Hydrozylinder ist als Gleichgangzylinder oder mit zwei Kolbenstangen unterschiedlichen Durchmessers ausgeführt, wobei an jeder Kolbenstange einer der Scheibensätze angeordnet ist. Der Vorteil einer derartigen Lösung ist, dass die Kolbenstangen eines derartigen Zylinders nur auf Zug belastet werden, so dass einem Ausknicken der Kolbenstange vorgebeugt ist.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. The advantage of such a solution is that the piston rods of such a cylinder are loaded only on train, so that buckling of the piston rod is prevented.

Anstelle eines Zylinder mit zwei Kolbenstangen kann bei nicht erfindungsgemäßen Ausführungsbeispielen auch ein Differentialzylinder verwendet werden, an dessen einziger Kolbenstange beide Scheibensätze angeordnet sind. Diese Koblenstange ist dann in einer Bewegungsrichtung (Beschleunigen oder Rückstellen) auf Druck beaufschlagt.Instead of a cylinder with two piston rods can be used in non-inventive embodiments, 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.

Zur Vermeidung übermäßiger Belastungen des hydraulischen Antriebes kann der Hydrozylinder mit einer Endlagendämpfung ausgeführt sein, die in den Hydrozylinder integriert oder getrennt davon ausgebildet ist.In order to avoid excessive loads on the hydraulic drive, the hydraulic cylinder can be designed with a cushioning integrated into or separate from the hydraulic cylinder.

Die Ansteuerung des Hydrozylinders erfolgt über eine Steueranordnung, wobei bei einem Ausführungsbeispiel ein sich bei der Beschleunigung vergrößernder Druckraum des Hydrozylinders über die Steueranordnung mit einem Hochdruckspeicher und/oder einer Hochdruckpumpe und der sich beim Rückstellen vergrößernde Druckraum des Hydrozylinders mit einem Niederdruckspeicher und/oder einer Niederdruckpumpe verbindbar ist.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.

Dabei ist es bevorzugt, wenn die Hochdruckpumpe eine Verstellpumpe ist.It is preferred if the high pressure pump is a variable displacement pump.

Bei der erfindungsgemäßen Steueranordnung zur Ansteuerung des Hydrozylinders wird im Zulauf zu dem sich beim Beschleunigen vergrößernden Druckraum des Hydrozylinders und im Ablauf von dem sich beim Beschleunigen verkleinernden Druckraum jeweils ein proportional verstellbares Regelventil angeordnet, über das der Zu- und Ablauf absperrbar und/oder in Abhängigkeit von dem zu beschleunigenden Gewicht ein Öffnungsquerschnitt zur Druckmittelverbindung des jeweiligen Druckraums mit einer Druckmittelquelle oder einer Druckmittelsenke aufsteuerbar ist.In the control arrangement according to the invention for controlling the hydraulic cylinder in each case 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.

Bei einem besonders bevorzugten Ausführungsbeispiel hat die Steueranordnung zusätzlich noch ein stetig verstellbares Rückstellregelventil, über das beim Rückstellen des Mitnehmers der sich vergrößernde Druckraum des Hydrozylinders mit der Niederdruckpumpe und der sich verkleinernde Druckraum mit der Druckmittelsenke verbindbar sind. Da diese Rückstellbewegung vergleichsweise langsam erfolgt, kann das stetig verstellbare Rückstellventil mit einer geringeren Nenngröße als die vorgenannten proportional verstellbaren Regelventile ausgelegt werden.In a particularly preferred embodiment, the 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.

Bei einer vorteilhaften Lösung ist die Steueranordnung mit einem Rückschlagventil ausgeführt, über das bei einem Abbremsen des Mitnehmers nach der Beschleunigungsphase ein Druckmittelströmungspfad vom Ablauf zu dem sich beim Beschleunigen vergrößernden Druckraum aufsteuerbar ist, wobei das zugeordnete proportional verstellbare Regelventil umgangen wird. Dadurch ist es möglich, dieses Regelventil zum Abbremsen in eine Schließstellung zu bringen und Druckmittel aus dem Ablauf in den zugeordneten Druckraum nachströmen zu lassen.In an advantageous solution, the 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. This makes it possible to bring this control valve to decelerate in a closed position and to let pressure fluid from the flow into the associated pressure chamber.

Bei einer weiteren bevorzugten Lösung ist im Druckmittelströmungspfad zwischen jedem Regelventil und dem zugeordneten Druckraum jeweils ein vorgesteuertes Logikventil angeordnet, das eine leckagefreie Abdichtung der Druckräume ermöglicht.In a further preferred solution, in each case 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.

Der Hydrozylinder ist vorzugsweise in einem offenen hydraulischen Kreislauf angeordnet.The hydraulic cylinder is preferably arranged in an open hydraulic circuit.

Im folgenden werden bevorzugte Ausführungsbeispiele der Erfindung anhand schematischer Zeichnungen näher erläutert. Es zeigen:

  • Figur 1 ein Schaltschema eines ersten Ausführungsbeispiels eines Katapultantriebes für eine Achterbahn;
  • Figur 2 eine Teildarstellung eines Zugmittelgetriebes des Katapultantriebs aus Figur 1;
  • Figur 3 eine Teildarstellung einer hydraulischen Steueranordnung des Katapultantriebes aus Figur 1;
  • Figur 4 eine Variante des Zugmittelgetriebes aus Figur 1;
  • Figur 5 eine weitere Variante des Zugmittelgetriebes aus Figur 1;
  • Figur 6 ein weiteres Ausführungsbeispiels eines Zugmittelgetriebes, das über eine Steueranordnung gemäß Figur 1 (3) ansteuerbar ist und
  • Figur 7 eine Steueranordnung in einer Minimalkonfiguration.
In the following preferred embodiments of the invention will be explained in more detail with reference to schematic drawings. Show it:
  • FIG. 1 a circuit diagram of a first embodiment of a catapult drive for a roller coaster;
  • FIG. 2 a partial view of a traction mechanism of the catapult drive from FIG. 1 ;
  • FIG. 3 a partial view of a hydraulic control arrangement of the catapult drive FIG. 1 ;
  • FIG. 4 a variant of the traction mechanism of Figure 1;
  • FIG. 5 another variant of the traction mechanism FIG. 1 ;
  • FIG. 6 a further embodiment of a traction mechanism, via a control arrangement according to FIG. 1 (3) is controllable and
  • FIG. 7 a control arrangement in a minimal configuration.

Figur 1 zeigt einen Schaltplan eines hydraulischen Katapultantriebs 1 für einen Wagen oder einen Personenzug einer Achterbahn oder dergleichen. Dieser Wagen wird über einen vom Katapultantrieb 1 angetriebenen Mitnehmer 2 beschleunigt. Bei dem dargestellten Ausführungsbeispiel greift an beiden Seiten des Mitnehmers 2 ein Zugmittelgetriebe 4 an, das von einem Hydrozylinder 6 angetrieben wird. Dieser ist beim dargestellten Ausführungsbeispiel als Gleichgangzylinder ausgeführt. Die Druckmittelversorgung des Hydrozylinders 6 erfolgt über eine Steueranordnung 8, über die zwei Druckräume 10, 12 des Hydrozylinders 6 mit einer Druckmittelquelle 14 oder einer Druckmittelsenke verbindbar sind, die beim dargestellten Ausführungsbeispiel durch einen Tank T gebildet ist. Die Steueranordnung 8 als offener Kreislauf ausgeführt. Weitere Details des Katapultantriebs werden im Folgenden anhand der vergrößerten Darstellungen in den Figuren 2 und 3 erläutert. 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. In the illustrated embodiment engages on both sides of the 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.

Figur 2 zeigt das Zugmittelgetriebe 4 mit dem Hydrozylinder 6 zum Verfahren des Mitnehmers 2, wobei dieser zum Beschleunigen in Pfleilrichtung bewegt wird und das Rückstellen in entgegengesetzter Richtung erfolgt. Wie oben erwähnt, ist der Hydrozylinder 6 bei diesem Ausführungsbeispiel als Gleichgangzylinder ausgeführt, durch dessen Kolben mit den beiden Kolbenstangen 16, 18 der Zylinder in die beiden Druckräume 10, 12 unterteilt wird, die jeweils als Ringraum ausgeführt sind. Zur Beschleunigung des Mitnehmers 2 wird der Kolben in der Darstellung gemäß Figur 1 nach rechts bewegt, so dass sich der Druckraum 10 vergrößert, während der rechts gelegene (Figur 2) Druckraum 12 entsprechend verkleinert wird. Bei dem dargestellten Ausführungsbeispiel sind die Durchmesser der Kolbenstangen 16, 18 gleich ausgeführt. Prinzipiell können diese auch mit unterschiedlichen Durchmessern ausgeführt sein. 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. As mentioned above, 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. To accelerate the driver 2, 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. In the illustrated embodiment, the diameter of the piston rods 16, 18 executed the same. In principle, these can also be designed with different diameters.

An den aus dem Hydrozylinder 6 herausragenden Endabschnitten der Kolbenstangen 16, 18 ist jeweils ein beweglicher Scheibensatz 20 bzw. 22 des Zugmittelgetriebes 4 befestigt, der durch die Ein- und Ausfahrbewegung der Kolbenstangen 16, 18 entsprechend verfahrbar ist. Jedem Scheibensatz 20, 22 ist ein Umlenkscheibensatz 24 bzw. 26 zugeordnet. Jeder dieser Umlenkscheibensätze 24, 26 ist ortsfest am Rahmen der Achterbahn oder an einem Fundament gelagert.At the protruding from the hydraulic cylinder 6 end portions of the piston rods 16, 18 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 Umlenkscheibensatz 24 and 26 respectively. Each of these Umlenkscheibensätze 24, 26 is fixedly mounted on the frame of the roller coaster or on a foundation.

Die einander zugeordneten Scheibensätze 22, 26 und 20, 24 werden jeweils von einem Zugmittel, beispielsweise einem Zugseil 28, 30 umschlungen, die jeweils mit einem Endabschnitt am Mitnehmer 2 angreifen, so dass über das Zugseil 28 der Mitnehmer 2 in Beschleunigungsrichtung bewegt ist, während die Rückstellung mittels des Zugseils 30 erfolgt. Es kann auch ein einziges durchgehendes Zugseil 28 verwendet werden, wobei dann der Mitnehmer 2 an diesem lösbar befestigt wird. Das Zugseil 28 kann dann durch den Mitnehmer 2 hindurch gezogen werden, so dass der Seilwechsel vereinfacht ist.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. 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.

Die jeweils anderen Endabschnitte der beiden Zugseile 28, 30 sind wiederum am Rahmen/Fundament verankert. Beim dargestellten Ausführungsbeispiel erfolgt diese Verankerung über jeweils einen Spannzylinder 32, 34, der als Differentialzylinder ausgeführt ist. Über diese Spannzylinder 32, 34 können Längenänderungen der Zugseile 28, 30 ausgeglichen und eine gleichbleibende Spannung eingestellt werden. Der Spannzylinder 32, 34 hat einen Ringraum 38 bzw. 36, der über eine Spannleitung 40 bzw. 42 mit dem jeweils benachbarten Druckraum 10 (Spannleitung 40) bzw. 12 (Spannleitung 42) verbunden sind. Dadurch ist gewährleistet, dass das beim Beschleunigen oder Rückstellen das eine Zugkraft auf den Mitnehmer 2 ausübende Zugseil 28, 30 jeweils durch den Druck in dem sich dabei vergrößernden Druckraum 10, 12 gespannt ist.The respective other end portions of the two traction cables 28, 30 are in turn anchored to the frame / foundation. In the illustrated embodiment, this anchoring takes place via a respective clamping cylinder 32, 34, which is designed as a differential cylinder. About 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.

Selbstverständlich können auch andere Spannelemente, beispielsweise pneumatische Spannzylinder, Spannfedern etc. verwendet werden. Prinzipiell ist auch eine "starre", jedoch einstellbare, Verankerung des jeweiligen Zugseils möglich.Of course, other clamping elements, such as pneumatic clamping cylinders, tension springs, etc. may be used. In principle, a "rigid", but adjustable, anchoring of the respective hawser is possible.

Durch die Zugseile 28, 30 und die beiden jeweils von diesem umschlungenen Scheibensätze 22, 26; 20, 24 wird jeweils ein Flaschenzug ausgebildet. Beim dargestellten Ausführungsbeispiel haben die beiden beweglichen Scheibensätze 20, 22 jeweils vier Seilrollen 44, und die festen Scheibensätze 24, 26 jeweils 4 Seilrollen 46, so dass entsprechend eine 8-fache Übersetzung vorliegt. Demzufolge wird der Hub der Kolbenstangen 16, 18 über das Zugmittelgetriebe 4 so übersetzt, dass der Mitnehmer 2 die 8-fache Strecke entlang der Bewegungsbahn zurücklegt. Entsprechend beträgt die vom Mitnehmer 2 auf den zu beschleunigenden Wagen übertragene Zugkraft lediglich 1/8 der vom Hydrozylinder 6 aufgebrachten Kraft.By the traction cables 28, 30 and the two each of this looped pulley sets 22, 26; 20, 24, a pulley is formed in each case. In the illustrated embodiment, 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.

Bei dem dargestellten Ausführungsbeispiel sind zwischen dem Mitnehmer 2 und dem Umlenkscheibensatz 26 zwei weitere ortsfeste Führungsscheiben 48, 50 vorgesehen, über die das Zugseil 30 mit Bezug zur Bewegungsbahn des Mitnehmers 2 ausgerichtet ist. Bei dem in Beschleunigungsrichtung wirksamen Zugseil 28 ist lediglich eine feststehende Führungsscheibe 52 vorgesehen. Die beweglichen Scheibensätze 20,22 können in geeigneter Weise geführt oder abgestützt werden.In the illustrated embodiment, two further stationary guide discs 48, 50 are provided between the driver 2 and the Umlenkscheibensatz 26, via which the traction cable 30 is aligned with respect to the trajectory of the driver 2. In the case of 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.

Bei dem dargestellten Ausführungsbeispiel sind die beweglichen Scheibensätze 22, 20 auf einer gemeinsamen, strichpunktiert angedeuteten Traverse 54 bzw. 56 gelagert, die ihrerseits an der jeweils zugeordneten Kolbenstange 16 bzw. 18 befestigt sind. Selbstverständlich können die Scheiben 44 der beweglichen Scheibensätze 20, 22 auch koaxial nebeneinanderliegend angeordnet werden, wobei dann die Umlenkscheiben 46 entsprechend ausgerichtet werden.In the illustrated embodiment, 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. Of course, 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.

Zum Beschleunigen des Mitnehmers 2 wird der Kolben des Hydrozylinder 6 nach rechts verfahren, so dass entsprechend der bewegliche Scheibensatz 20 ebenfalls nach rechts verschoben wird und sich der Abstand zwischen dem beweglichen Scheibensatz 20 und dem Umlenkscheibensatz 24 vergrößert und entsprechend der Mitnehmer 2 in Pfeilrichtung beschleunigt wird. Dabei wird auch der bewegliche Scheibensatz 44 nach rechts zum Umlenkscheibensatz 26 hin verschoben, wobei das Zugseil 30 über den sich bewegenden Mitnehmer 2 mitbewegt, und vom Zylinder 32 auf Spannung gehalten wird.To accelerate the driver 2, 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 Umlenkscheibensatz 24 increases and corresponding to the driver 2 in the arrow direction is accelerated. In this case, the movable pulley set 44 is shifted to the right to Umlenkscheibensatz 26 out, wherein the pull cable 30 moves over the moving carrier 2, and is held by the cylinder 32 to voltage.

Bei dem dargestellten Ausführungsbeispiel sind die Kolbenstangen 16, 18 über eine hydrostatische Lagerung 58, 60 im Zylinderboden des Zylinders 6 gelagert. Da derartige hydrostatische Lagerungen dem Fachmann bekannt sind, kann auf diesbezügliche Erläuterungen verzichtet werden. Der Hydrozylinder 6 wird vorzugsweise auch mit Endlagendämpfungseinrichtungen ausgeführt, die entweder in den Hydrozylinder 6 integriert oder extern angeordnet sind.In the illustrated embodiment, 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.

Bei der in Figur 2 dargestellten Lösung werden alle notwendigen Bewegungen des Mitnehmers 2 über den Hydrozylinder 6 gesteuert - der Katapultantrieb 1 ist demgemäß wesentlich einfacher als der eingangs beschriebenen Stand der Technik aufgebaut.At the in FIG. 2 All necessary movements of the driver 2 are controlled via the hydraulic cylinder 6 - the catapult drive 1 is accordingly constructed much simpler than the prior art described above.

Die Ansteuerung des Hydrozylinders 6 wird anhand Figur 3 erläutert, die einen Schaltplan der Steueranordnung 8 des Hydrozylinders 6 zeigt.The control of the hydraulic cylinder 6 will be explained with reference to Figure 3, which shows a circuit diagram of the control arrangement 8 of the hydraulic cylinder 6.

Bei dem Ausführungsbeispiel gemäß Figur 1 ist wie näher aus Figur 4 ersichtlich, die Druckmittelquelle 14 durch eine Pumpenanordnung mit einer Verstellpumpe 62, einer Konstantpumpe 64 sowie einem Hochdruckspeicher 66 ausgebildet. Die Konstantpumpe 64 und die Verstellpumpe 62 sind vorzugsweise von einem gemeinsamen Motor M angetrieben. Dem Druckanschluss der Konstantpumpe 64 ist ein Rückschlagventil 67 nachgeordnet. Außerdem ist an jedem Druckanschluss ein vorgesteuertes Druckbegrenzungsventil 68 bzw. 69 mit Wegeventilentlastung angeschlossen. Die Druckanschlüsse der Verstellpumpe 62 und des Hochdruckspeichers 66 sind über eine HD-Pumpenleitung 70 mit einem Druckanschluss P1 eines die Steueranordnung 8 aufnehmenden Steuerblocks 72 (strichpunktiert angedeutet) verbunden. Der Druckanschluss der Konstantpumpe 64 ist über eine ND-Pumpenleitung 74 an einen weiteren Druckanschluss P2 des Steuerblocks 72 angeschlossen. Dieser hat des Weiteren noch einen Tankanschluss T, der über eine Tankleitung 76 und ein Stauventil 78 mit dem Tank T verbunden ist. Gemäß Figur 3 kann in der Tankleitung 76 noch ein Kühler 71 vorgesehen sein. Im Bereich zwischen dem Tankanschluss T und dem Stauventil 78 ist ein Niederdruck-Hydrospeicher 80 angeschlossen, über den Druckschwankungen in der Tankleitung 76 ausgeglichen werden können. Das Stauventil 78 sorgt dafür, dass die Tankleitung 76 etwas vorgespannt ist.In the embodiment according to FIG. 1 is like closer FIG. 4 can be seen, 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. In addition, at each pressure port, a pilot-operated pressure relief valve 68 or 69 with Directional valve relief connected. 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. According to FIG. 3 can still be provided 71 in the tank line 76, a cooler. In the area between the tank connection T and the congestion valve 78, 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.

Am Steuerblock 72 sind des Weiteren noch ein Steueranschluss X und ein Leckölanschluss Y vorgesehen, wobei letzterer mit dem Tank T verbunden ist. Bei dem dargestellten Ausführungsbeispiel ist der Steueranschluss X mit der HD-Pumpenleitung 70 verbunden, so dass der darin herrschende Druck als Steuerdruck wirkt. Prinzipiell kann auch ein externer Steuerdruck aufgegeben werden.Furthermore, a control port X and a drain port Y are provided on the control block 72, the latter being connected to the tank T. In the illustrated embodiment, the control port X is connected to the HP pump line 70, so that the pressure prevailing therein acts as a control pressure. In principle, an external control pressure can also be given up.

Innerhalb des Steuerblocks 72 ist der Druckanschluss P1 über eine Zulaufleitung 82 mit dem Eingangsanschluss A eines proportional verstellbaren Regelventils 84 verbunden, das im Folgenden als Beschleunigungsregelventil 84 bezeichnet wird. Dieses ist elektrohydraulisch vorgesteuert, wobei der Steuerdruck über eine Steuerleitung 86 vom Steueranschluss X abgegriffen wird. Das Lecköl kann über eine Leckölleitung 87 zum Leckölanschluss Y abfließen. Dieses Beschleunigungsregelventil 84 kann beispielsweise als vorgesteuertes, proportional verstellbares Logikventil ausgeführt sein. Ein Anschluss B des Beschleunigungsregelventils 84 ist über eine Vorlaufleitung 88 und ein Logikventil 90 mit dem Druckraum 10 des Hydrozylinders 6 verbunden. In seiner federvorgespannten Grundposition schließt das Beschleunigungsregelventil 84 die Druckmittelverbindung zur Vorlaufleitung 88 leckagedicht ab. Durch entsprechende Ansteuerung des Beschleunigungsregelventils 84 wird eine den Druckmittelvolumenstrom bestimmende Zulaufmessblende aufgesteuert.Within the control block 72, 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. In its spring-biased basic position, the acceleration control valve 84 closes off the pressure medium connection to the supply line 88 in a leak-tight manner. By appropriate control of the acceleration control valve 84, a pressure medium volume flow determining inlet orifice is opened.

Das in der Vorlaufleitung 88 angeordnete Logikventil 90 ist ebenfalls vorgesteuert ausgeführt, wobei in einem Deckel 92 des Logikventils 90 ein Wechselventil 94 angeordnet ist, dessen beiden Eingänge mit den Drücken am Anschluss A bzw. am Anschluss B des Logikventils 90 beaufschlagt sind, so dass der jeweils größere Druck weitergeleitet wird. Der Ausgang des Wechselventils 94 ist mit dem Eingang eines Vorsteuerventils 96 verbunden. Dieses ist als 4/2-Wegeschaltventil ausgeführt und verbindet in seiner federvorgespannten Grundposition den Ausgang des Wechselventils 94 mit einem Federraum 98 des Logikventils 90, so dass dieses in Schließstellung vorgespannt ist und den Druckmittelströmungspfad zum Ringraum 10 absperrt. Bei Umschalten des Vorsteuerventils 96 wird der Federraum 98 mit der Steueröltankleitung 87 verbunden, so dass der Federraum 98 druckentlastet ist und das Logikventil 90 öffnen kann. Die Öffnungsbewegung des Kolbens des Logikventils 90 kann über einen Endlagenschalter 100 erfasst werden. In dieser Schaltposition des Vorsteuerventils 96 wird des Weiteren die Verbindung vom Ausgang des Wechselventils 94 zum Federraum 98 des Logikventils 90 abgesperrt. Der Druck in der Vorlaufleitung 88 wird über einen Druckaufnehmer 102 erfasst.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. When switching the pilot valve 96 of the spring chamber 98 is connected to the control oil tank 87, so that the spring chamber 98 is depressurized and can open the logic valve 90. The opening movement of the piston of the logic valve 90 can be detected via a limit switch 100. In this switching position of the pilot valve 96, furthermore, the connection from the outlet of the shuttle valve 94 to the spring chamber 98 of the logic valve 90 is shut off. The pressure in the supply line 88 is detected by a pressure transducer 102.

An den Druckraum 12 des Hydrozylinders 6 ist eine Ablaufleitung 104 angeschlossen, deren Druck über einen weiteren Druckaufnehmer 106 erfassbar ist und in der ein weiteres Logikventil 108 vorgesehen ist, das praktisch den gleichen Aufbau wie das Logikventil 90 hat. D. h., der größere Druck an den Anschlüssen A, B des Logikventils 108 wird über ein Wechselventil 110 abgegriffen und in einer Grundposition eines Vorsteuerventils 112 in einen Federraum 114 des Logikventils 108 gemeldet. Durch Umschalten des Vorsteuerventils 112 wird der Federraum 114 mit der Steueröltankleitung 87 verbunden und somit druckentlastet, so dass das Logikventil 108 durch den am Druckanschluss B oder A anliegenden Druck geöffnet werden kann. Der Anschluss A des Logikventils 108 ist mit einem Ausgangsanschluss B eines weiteren stetig verstellbaren Regelventils, im Folgenden Ablaufregelventil 116 genannt, verbunden, dessen Aufbau demjenigen des Beschleunigungsregelventils 84 gleicht, so dass weitere Erläuterungen entbehrlich sind. An den Anschluss A des Ablaufregelventils 116 ist eine zum Tankanschluss T führende Ablaufleitung 118 angeschlossen.To the pressure chamber 12 of the hydraulic cylinder 6, 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. 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. At the connection A of the drain control valve 116, a leading to the tank port T drain line 118 is connected.

Zur Vermeidung von Drucküberhöhungen in der Vorlaufleitung 88 bzw. der Rücklaufleitung 104 sind diese über zwei vorgesteuerte Druckbegrenzungsventile 120, 122 miteinander verbindbar, wobei der Maximaldruck durch entsprechende Einstellung eines Vorsteuerventils 124, 126 erfolgt.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.

Bei der in Figur 3 dargestellten Steueranordnung erfolgt die Rückstellbewegung des Mitnehmers, d. h., die Axialverschiebung des Kolbens des Hydrozylinders 6 nach links mit Hilfe eines stetig verstellbaren Rückstellregelventils 128. Dieses hat vier Anschlüsse, wobei ein Druckanschluss P über eine Rückstellleitung 130 mit dem zweiten Druckanschluss P2 des Steuerblocks 72 und ein Tankanschluss T über eine Rückstelltankleitung 132 mit der Ablaufleitung 118 verbunden ist. Zwei Arbeitsanschlüsse A, B sind über eine Rückstellvorlaufleitung 134 mit der Rücklaufleitung 104 und über eine Rückstellrücklaufleitung 136 mit der Vorlaufleitung 88 verbunden, wobei die Ventile 84, 116; 90, 108 umgangen werden. In jeder der Leitungen 134, 136 ist jeweils ein entsperrbares Rückschlagventil 138, 140 vorgesehen. In seiner federvorgespannten Grundposition verbindet das Rückstellregelventil 128 seine beiden Arbeitsanschlüsse A, B mit der Rückstelltankleitung 182, wobei die Rückschlagventile 138, 140 eine Druckmittelströmung von der Rücklaufleitung 104 oder von der Vorlaufleitung 88 zu den Arbeitsanschlüssen A, B des Rückstellregelventils 128 sperren. Durch entsprechende Ansteuerung der Vorsteuerung des Rückstellregelventils 128 wird dies in eine seiner mit (a) gekennzeichneten Positionen verschoben, in der der Druckanschluss P mit dem Arbeitsanschluss B und der Arbeitsanschluss A mit dem Tankanschluss T verbunden ist, so dass Druckmittel von der Konstantpumpe 64 über die ND-Pumpenleitung 74, die Rückstellleitung 130, die Rückstellvorlaufleitung 134, die Rücklaufleitung 104 in den Druckraum 12 gefördert wird und entsprechend das aus dem Druckraum 10 verdrängte Druckmittel über die Vorlaufleitung 88, die Rückstellrücklaufleitung 136, das geöffnete Sperrventil 140, den Arbeitsanschluss A, den Tankanschluss T, die Rückstelltankleitung 132, die Ablaufleitung 118, die Tankleitung 76 und das Stauventil 78 zum Tank T abströmt, wobei über das Stauventil 78 die Tankleitung 76 vorgespannt ist.At the in FIG. 3 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 Rückstellregelventils 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. In each of the lines 134, 136, a pilot-operated check valve 138, 140 is provided in each case. 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. By appropriate control of the feedforward control of the reset control valve 128, this is shifted to one of its positions marked with (a), in which the pressure port P is connected to the working port B and the working port A is connected to the tank port T, so that pressure medium from the constant pump 64 via the ND pump line 74, the return line 130, the return flow line 134, the return line 104 is conveyed into the pressure chamber 12 and corresponding displaced from the pressure chamber 10 pressure fluid via the flow line 88, the return return line 136, the open check valve 140, the working port A, the Tank connection T, the return tank line 132, the drain line 118, the tank line 76 and the damper valve 78 flows to the tank T, via the damper valve 78, the tank line 76 is biased.

Durch Verschieben des Rückstellregelventils 128 in eine seiner mit (b) gekennzeichneten Positionen kann der Hydrozylinder 6 über die Konstantpumpe 64 auch in Beschleunigungsrichtung verstellt werden.By moving the reset control valve 128 in one of his (b) marked positions of the hydraulic cylinder 6 can be adjusted via the constant displacement pump 64 in the direction of acceleration.

Die dargestellte Steueranordnung 8 hat des Weiteren noch ein Rückschlagventil 142, das in einer die Rückstelltankleitung 132 mit der Vorlaufleitung 88 verbindenden Füllleitung 144 angeordnet ist. Dieses Rückschlagventil 142 ist beim dargestellten Ausführungsbeispiel ebenfalls als Logikventil ausgeführt, wobei in seinen Federraum 146 der Druck in der Vorlaufleitung 88 gemeldet wird.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.

Zum besseren Verständnis sei die Funktion der in Figur 3 dargestellten Steueranordnung anhand der verschiedenen Bewegungsphasen des Mitnehmers 2 erläutert.For a better understanding, the function of the control arrangement shown in FIG. 3 will be explained on the basis of the different movement phases of the driver 2.

Zum Beschleunigen des Mitnehmers 2 werden das Beschleunigungsregelventil 84 und das Ablaufregelventil 116 geregelt aufgesteuert, wobei der aufgesteuerte Querschnitt in Abhängigkeit von dem Gewicht des Personenwagens, das aufgrund der Anzahl der Mitfahrer variieren kann, um ein vorbestimmtes Beschleunigungsprofil einzustellen. Die Verstellpumpe 62 wird über den Motor M angetrieben und Druckmittel in die HD-Pumpenleitung 70 gefördert. Die beiden Vorsteuerventile 96 und 112 der Logikventile 90, 108 werden umgeschaltet, so dass das Druckmittel über das sich öffnende Logikventil 90 und die Vorlaufleitung 88 in den Druckraum 10 gefördert wird, so dass der Kolben des Hydrozylinders 6 nach rechts bewegt wird und - wie eingangs erläutert - durch die Vergrößerung des Abstands zwischen dem beweglichen Scheibensatz 20 und dem zugeordneten Umlenkscheibensatz 24 der Mitnehmer 2 durch das Zugseil 28 in Pfeilrichtung (Figur 1) beschleunigt wird, um den Wagen auf seine Anfangsgeschwindigkeit zu bringen. Das Druckmittel aus dem sich verkleinernden Ringraum 12 strömt über die Rücklaufleitung 104 zum Logikventil 108, wobei der Druck in der Rücklaufleitung 104 auf die Ringfläche des Kolbens des Logikventils 108 wirkt und diese in seine Öffnungsstellung bringt, so dass das Druckmittel über das aufgesteuerte Ablaufregelventil 116, die Ablaufleitung 118, die Tankleitung 76 und das Stauventil 78 zum Tank T hin abströmt. Die Ansteuerung der Regelventile 84, 116 erfolgt so, dass sich das gewünschte Geschwindigkeits- oder Beschleunigungsprofil einstellt.To accelerate the driver 2, 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 Umlenkscheibensatz 24 of the driver 2 by the pull rope 28 in the arrow direction ( FIG. 1 ) is accelerated to bring the car to its initial speed. 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.

Zum Ende der Beschleunigungsphase wird der Mitnehmer 2 abgebremst. Dazu wird das Beschleunigungsregelventil 84 geschlossen und das Ablaufregelventil 116 geregelt zugesteuert, dass ein vorbestimmtes Abbremsgeschwindigkeitsprofil eingehalten wird. Die Bewegungsgeschwindigkeit des Kolbens des Hydrozylinders 6 wird entsprechend verringert, wobei sich das Volumen des Druckraums 10 (Beschleunigungsdruckkammer) weiter vergrößert - die zum Füllen dieses Druckraums 10 erforderliche Druckmittelmenge kann dann über das sich öffnende Rückschlagventil 142 aus der Ablaufleitung 118 nachströmen, so dass das Befüllen in der Abbremsphase trotz geschlossenem oder nahezu geschlossenem Beschleunigungsregelventil 84 erfolgt. Durch diese Maßnahme ist der Energieverbrauch aus dem Hochdruckspeicher 66 minimal.At the end of the acceleration phase of the driver 2 is decelerated. For this purpose, the acceleration control valve 84 is closed and the flow control valve 116 controlled controlled that a predetermined Abbremsgeschwindigkeitsprofil 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. By this measure, the energy consumption from the high-pressure accumulator 66 is minimal.

Beim Stillstand des Hydrozylinders 6 sind dann beide Ventile 84, 116 geschlossen, das Rückschlagventil 142 befindet sich dann auch wieder in seiner Schließposition. Der Hochdruckspeicher 66 ist somit vom Hydrozylinder 6 getrennt. Die Rückstellung des Mitnehmers 6 erfolgt dann in der vorbeschriebenen Weise durch Verstellen des Rückstellregelventils 128 in eine seiner mit (a) gekennzeichneten Positionen, wobei das für die Rückstellung erforderliche Druckmittel von der Konstantpumpe 64 geliefert wird, die nunmehr vom gemeinsamen Motor angetrieben ist. Während dieser Rückbewegung treten vergleichsweise niedrige Drücke im System auf, die Bewegung erfolgt zudem relativ langsam, so dass das Rückstellregelventil 128 mit vergleichsweise geringer Nenngröße ausgeführt werden kann. Während der Abbremsphase, der Rückstellbewegung und des Stillstandes des Hydrozylinders 6 kann der Hydrospeicher 66 über die Verstellpumpe 62 relativ langsam aufgeladen werden, da genügend Zeit zur Verfügung steht. Während der Wartezeit bis zur nächsten Beschleunigung des Mitnehmers 2 ist die Antriebsseite der Steueranordnung praktisch unbelastet, so dass keine eigene Verriegelungseinrichtung erforderlich ist.When the hydraulic cylinder 6, both valves 84, 116 are then closed, the check valve 142 is then again in its closed position. The high pressure accumulator 66 is thus separated from the hydraulic cylinder 6. The return of the driver 6 then takes place in the manner described above by adjusting the reset control valve 128 in one of his (a) marked positions, wherein the pressure required for the return pressure medium is supplied by the fixed displacement pump 64, which is now driven by the common motor. During this return movement occur comparatively low pressures in the system, the movement also takes place relatively slowly, so that the reset control valve 128 can be performed with a comparatively small nominal size. During the deceleration phase, the return movement and the standstill of the hydraulic cylinder 6, 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.

Bei dem in Figur 4 dargestellten Ausführungsbeispiel ist das Zugmittelgetriebe 4 mit zwei Zugseilen 28, 30 ausgeführt, wobei am Mitnehmer 2 zwei zusätzliche Umlenkscheiben 148, 150 vorgesehen sind, die zur Umlenkung jeweils eines der Zugseile 28, 30 dienen. Dies erleichtert das Auswechseln der Zugseile 28 oder 30, da diese nicht mehr vom Mitnehmer 2 gelöst werden müssen. Bei diesem Ausführungsbeispiel sind die beiden beweglichen Scheibensätze 20, 22 mit jeweils 6 Scheiben 44 ausgeführt, so dass sich entsprechend eine 6-fache Übersetzung ergibt. Der jeweils zugeordnete Umlenkscheibensatz 24, 26 ist entsprechend ausgeführt, wobei die Zugseilführung so ausgelegt ist, dass die Kolbenstange 18 symmetrisch belastet ist und dass die beiden Endabschnitte der Zugeile 28, 30 jeweils im Axialbereich der Kolbenstange 16, 18 enden. Die beiden Endabschnitte jedes Zugseils 28, 30 sind dann bei diesem Ausführungsbeispiel über eine Spannfeder 152, 154 verankert, über die die Zugseile 28, 30 unter Spannung gehalten werden. Die Spannfedern 152, 154 sind so ausgelegt, dass sie die erforderlichen Zugkräfte zur Beschleunigung des Mitnehmers 2 übertragen können. Die Seilführung erfolgt durch zusätzliche ortsfeste Führungsscheiben 48, 50, 52 und 156.At the in FIG. 4 illustrated embodiment, 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. In this embodiment, 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 Umlenkscheibensatz 24, 26 is carried out accordingly, wherein the Zugseilführung 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. The two end portions of 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

Bei den vorbeschriebenen Ausführungsbeispielen ist das Zugmittelgetriebe 4 so ausgelegt, dass der bewegliche Scheibensatz 20, 22 und der feststehende Umlenkscheibensatz 24, 26 in Verlängerung des Hydrozylinders 6 angeordnet sind, so dass in Axialrichtung vergleichsweise viel Bauraum benötigt wird. Wie in Figur 5 dargestellt ist, kann die Seilführung des Zugmittelgetriebes 4 auch so erfolgen, dass die Seilführung seitlich des Hydrozylinders 6 liegt. Dabei wird der bewegliche Scheibensatz 20, 22 - ähnlich wie beim vorbeschriebenen Ausführungsbeispiel - jeweils an einem Ende der zugeordneten Kolbenstange 16 bzw. 18 befestigt, wobei die einzelnen Zugscheiben 44 koaxial zueinander angeordnet sind und in der Draufsicht dargestellt sind. Die beiden zugeordneten Umlenkscheibensätze 24, 26 sind dann nach innen, aufeinander zuversetzt, so dass sie beidseitig des Zylindermantels liegen. Dabei können die feststehenden Umlenkscheiben 24, 26 am Zylinder oder am Rahmen der Achterbahn abgestützt sein. Die beiden Endabschnitte des - in diesem Fall - gemeinsamen Zugseils 28 sind wiederum ortsfest verankert. Über weitere Führungsscheiben 48 wird das Zugseil 28 dann zum Mitnehmer 2 (nicht dargestellt) geführt und dieser am Zugseil 28 befestigt. Selbstverständlich kann eine derartige Zugseilführung auch mit zwei Zugseilen erfolgen.In the above-described embodiments, the traction mechanism 4 is designed so that the movable pulley 20, 22 and the fixed Umlenkscheibensatz 24, 26 arranged in extension of the hydraulic cylinder 6 are so that in the axial direction comparatively much space is needed. As in FIG. 5 is shown, 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. In this case, the movable pulley set 20, 22 - similar to the above-described embodiment - each attached to one end of the associated piston rod 16 and 18, wherein the individual traction sheaves 44 are arranged coaxially to each other and are shown in plan view. The two associated Umlenkscheibensätze 24, 26 are then inwardly, each zuversetzt 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. Via further guide disks 48, the traction cable 28 is then guided to the driver 2 (not shown) and fastened to the traction cable 28. Of course, such Zugseilführung can also be done with two tension cables.

Bei den vorbeschriebenen Ausführungsbeispielen ist ein Hydrozylinder 6 mit zwei Kolbenstangen 16, 18 verwendet, die vorzugsweise gleichen Durchmesser aufweisen. Prinzipiell kann anstelle eines derartigen Gleichgangzylinders auch ein Differentialzylinder mit einer einzigen Kolbenstange 16 verwendet werden, an der dann die beweglichen Scheibensätze 20, 22 befestigt sind. Die beiden Umlenkscheibensätze 24, 26 sind wiederum ortsfest gelagert. Die Scheibenanordnung wird von einem gemeinsamen Zugseil 28 umschlungen, an dem der Mitnehmer 2 befestigt ist. Die beiden Endabschnitte des Zugseils 28 sind verankert. Selbstverständlich kann anstelle des einzigen, das gesamte Zugmittelgetriebe 4 umschlingenden Zugseils 28 auch eine Variante mit zwei getrennten Zugseilen 28, 30 gemäß Figur 4 verwendet werden.In the above-described embodiments, a hydraulic cylinder 6 with two piston rods 16, 18 is used, which preferably have the same diameter. In principle, it is also possible to use 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 Umlenkscheibensätze 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. Of course, instead of the single, the entire traction mechanism 4 looping around Zugseils 28 also a variant with two separate traction cables 28, 30 according to FIG. 4 be used.

Die insbesondere anhand Figur 3 erläuterte Steueranordnung ermöglicht einen Betrieb einer Achterbahn mit minimalen Energieverlusten, wobei die Steueranordnung jedoch nicht notwendigerweise so komplex wie dargestellt ausgeführt sein muss. Die Minimalanforderungen an diese Steueranordnung sind in Figur 7 dargestellt. Demgemäß erfolgt die Betätigung des nicht dargestellten Zugmittelgetriebes 4 über einen Hydrozylinder 6 (Gleichgangzylinder, Zylinder mit zwei Kolbenstangen, Differentialzylinder), über den alle Bewegungen des Mitnehmers 2 gesteuert werden. Die beiden Druckräume 10, 12 des Hydrozylinders 6 können im einfachsten Fall über eine Regelventilanordnung 158 mit einer Hochdruckseite HDS und/oder einer Niederdruckseite NDS verbunden werden. Unter dem Begriff Hochdruckseite HDS wird dabei beispielsweise ein Hochdruckspeicher 66 und eine Hochdruckpumpe (Verstellpumpe 62) verstanden. Der Begriff Niederdruckseite NDS steht im Prinzip für die Rücklaufseite zum Tank T. In diesem Bereich kann ein Niederdruckspeicher zum Ausgleich von Druckschwankungen vorgesehen sein. Die Regelventilanordnung 158 kann durch ein oder mehrere Regelventile ausgeführt sein.The particular based 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. The term high-pressure side HDS is understood to mean, for example, a high-pressure accumulator 66 and a high-pressure pump (variable-displacement pump 62). The term 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.

Bezugszeichenliste:LIST OF REFERENCE NUMBERS

11
Katapultantriebcatapult drive
22
Mitnehmertakeaway
44
Zugmittelgetriebetraction drives
66
Hydrozylinderhydraulic cylinders
88th
Steueranordnungcontrol arrangement
1010
Druckraumpressure chamber
1212
Druckraumpressure chamber
1414
DruckmittelquellePressure medium source
1616
Kolbenstangenpiston rods
1818
Kolbenstangenpiston rods
2020
beweglicher Scheibensatzmovable disc set
2222
beweglicher Scheibensatzmovable disc set
2424
Umlenkscheibensatzdeflection pulleys
2626
Umlenkscheibensatzdeflection pulleys
2828
Zugseilrope
3030
Zugseilrope
3232
Spannzylinderclamping cylinder
3434
Spannzylinderclamping cylinder
3636
Ringraumannulus
3838
Ringraumannulus
4040
Spannleitungclamping line
4242
Spannleitungclamping line
4444
Zugscheibedrawplate
4646
Umlenkscheibedeflection plate
4848
Führungsscheibeguide disc
5050
Führungsscheibeguide disc
5252
Führungsscheibeguide disc
5454
Traversetraverse
5656
Traversetraverse
5858
hydrostatisches Lagerhydrostatic bearing
6060
hydrostatisches Lagerhydrostatic bearing
6262
Verstellpumpevariable
6464
Konstantpumpefixed displacement pump
6666
HochdruckspeicherHigh-pressure accumulator
6767
Rückschlagventilcheck valve
6868
DruckbegrenzungsventilPressure relief valve
6969
DruckbegrenzungsventilPressure relief valve
7171
Kühlercooler
7070
HD-PumpenleitungHD pump line
7272
Steuerblockcontrol block
7474
ND-PumpenleitungND-pump line
7676
Tankleitungtank line
7878
Stauventilbackflow valve
8080
Hydrospeicherhydraulic accumulator
8282
Zulaufleitungsupply line
8484
BeschleunigungsregelventilAcceleration control valve
8686
Steuerleitungcontrol line
8787
LecköltankleitungLeaking oil tank line
8888
Vorlaufleitungsupply line
9090
Logikventillogic valve
9292
Deckelcover
9494
Wechselventilshuttle valve
9696
Vorsteuerventilpilot valve
9898
Federraumspring chamber
100100
EndlagenschalterLimit switches
102102
DruckaufnehmerPressure transducer
104104
RücklaufleitungReturn line
106106
DruckaufnehmerPressure transducer
108108
Logikventillogic valve
110110
Wechselventilshuttle valve
112112
Vorsteuerventilpilot valve
114114
Federraumspring chamber
116116
AblaufregelventilFlow control valve
118118
Ablaufleitungdrain line
120120
vorgesteuertes Druckbegrenzungsventilpilot operated pressure relief valve
122122
vorgesteuertes Druckbegrenzungsventilpilot operated pressure relief valve
124124
Vorsteuerventilpilot valve
126126
Vorsteuerventilpilot valve
128128
RückstellregelventilReset control valve
130130
RückstellleitungReset line
132132
RückstelltankleitungReset tank line
134134
RückstellvorlaufleitungReset advance line
136136
RückstellrücklaufleitungReset return line
138138
Rückschlagventilcheck valve
140140
Rückschlagventilcheck valve
142142
Rückschlagventilcheck valve
144144
Füllleitungfilling line
146146
Federraumspring chamber
148148
zusätzliche Umlenkscheibeadditional deflection disc
150150
zusätzliche Umlenkscheibeadditional deflection disc
152152
Spannfedertension spring
154154
Spannfedertension spring
156156
Führungsscheibeguide disc
158158
RegelventilanordnungRegulating valve arrangement

Claims (16)

  1. A hydraulic catapult drive for accelerating an object, in particular a car of a roller coaster, comprising a driving element (2) acting upon the object to be accelerated and being movable along a motion track, the driving element being movable via a flexible drive (4) and a hydraulic cylinder (6) driving the latter in the direction of acceleration or in the resetting direction, wherein at least one pressure chamber of the hydraulic cylinder (6) can be connected via a control system (8) to a hydraulic medium source (14) or a hydraulic medium sink (T), and wherein the flexible drive (4) has two movable sets of pulleys (20, 22) wrapped in portions by at least one pull means (28, 30) of the catapult drive, wherein depending on the control of the hydraulic cylinder (6) a pulling force can be transmitted to the driving element (2) via one set of pulleys (20, 22) and the pull means (28, 30) for accelerating, and via the other of the sets of pulleys (22, 20) and the pull means (28, 30) for resetting, characterized in that the hydraulic cylinder (6) is implemented as a synchronized speed cylinder or has two piston rods of different diameter, wherein one of the sets of pulleys (20, 22) is disposed on each piston rod (16, 18) such that the piston rods are subjected to tensile load only.
  2. The catapult drive according to claim 1, wherein a pull means (28, 30) of the catapult drive which is deflected by the respective driving element (2) is allocated to each set of pulleys (20, 22).
  3. The catapult drive according to claim 1, wherein both movable sets of pulleys (20, 22) are wrapped by a common pull means (28) of the catapult drive, to the central area of which the driving element (2) is fixed.
  4. The catapult drive according to claim 2 or 3, wherein free end portions of the pull means (28, 30) are anchored rigidly or displaceably.
  5. The catapult drive according to claim 4, wherein a spring element (152, 154) is disposed between the end of the pull means (28, 30) and the free end positions.
  6. The catapult drive according claim 4, wherein a clamping cylinder (32, 43) is disposed between the end of the pull means (28, 30) and the free end positions.
  7. The catapult drive according to claim 6, wherein pressure prevailing in the allocated pressure chamber (10, 12) of the hydraulic cylinder (6) is applied to the respective clamping cylinders (32, 34).
  8. The catapult drive according to any one of the preceding claims, wherein the sets of deflection pulleys (24, 26) of the catapult drive which are allocated to the movable sets of pulleys (20, 22) are arranged approximately in an extension of the hydraulic cylinder (6) or laterally of the latter.
  9. The catapult drive according to any one of the preceding claims, comprising an end-of-travel damping of the hydraulic cylinder.
  10. The catapult drive according to any one of the preceding claims, wherein a pressure chamber (10) of the hydraulic cylinder (6) increasing in size upon acceleration may be connected via the control system (8) to a high-pressure reservoir (66) and/or to a high-pressure pump (62) of the catapult drive, and the pressure chamber (12) of the hydraulic cylinder (6) increasing in size upon resetting to a low-pressure source and/or a low-pressure pump (64) of the catapult drive.
  11. The catapult drive according to claim 10, wherein the high-pressure pump is a variable-displacement pump (62), and the low-pressure pump is a constant-displacement pump (64).
  12. The catapult drive according to claim 10 or 11, wherein in the supply to the pressure chamber (10) increasing in size upon acceleration and in the discharge from the pressure chamber (12) decreasing in size a respective proportionally variable control valve (84, 116) is arranged by which the supply and the discharge may be blocked or an opening cross-section for hydraulic medium connection of the respective pressure chamber (10, 12) to the hydraulic medium source (14) or the hydraulic medium sink (10) may be opened in a controlled manner.
  13. The catapult drive according to claim 12, wherein the control system (8) comprises a continuously variable reset control valve (128) by which upon reset of the driving element (2) the pressure chamber (12) increasing in size of the hydraulic cylinder (2) may be connected to a low-pressure pump (64) and the pressure chamber (10) decreasing in size can be connected to the hydraulic medium sink (T).
  14. The catapult drive according to claim 12 or 13, comprising a check valve (142) whereby, upon deceleration of the driving element (2), a hydraulic medium flow path (144) may be opened in a controlled manner from the discharge to the pressure chamber (10) increasing in size during acceleration while by-passing the continuously variable control valve (84) arranged in the supply line.
  15. The catapult drive according to any one of claims 12 to 14, wherein between each pressure chamber (10, 12) and the allocated continuously variable control valve (84, 116) a pilot-controlled logic valve (90, 108) is disposed.
  16. The catapult drive according to any one of the preceding claims, wherein the hydraulic cylinder (6) is arranged in an open circuit.
EP06722537A 2005-04-28 2006-02-27 Hydraulic catapult drive Not-in-force EP1877669B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102005020187 2005-04-28
DE102006002921A DE102006002921A1 (en) 2005-04-28 2006-01-20 Hydraulic catapult drive for accelerating e.g. car of fairground ride, has disk sets moving through hydro cylinder, where traction force is transferred into actuator depending upon controlling of hydro cylinder
PCT/DE2006/000366 WO2006114070A1 (en) 2005-04-28 2006-02-27 Hydraulic catapult drive

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EP1877669A1 EP1877669A1 (en) 2008-01-16
EP1877669B1 true EP1877669B1 (en) 2012-04-18

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

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US1960264A (en) * 1931-10-11 1934-05-29 Heinkel Ernst Catapult for launching aeroplanes
US2696957A (en) * 1948-04-27 1954-12-14 Brown Owen Landing and launching system for aircraft
US2783004A (en) * 1954-03-29 1957-02-26 Creusot Forges Ateliers Appliance for braking of aircraft on landing or for launching of same
US2926871A (en) * 1957-01-14 1960-03-01 Bless Harold Gas operated wire rope driven catapult
US3534929A (en) * 1969-02-20 1970-10-20 Gulf & Western Ind Prod Co Aircraft launching device
CN2166086Y (en) * 1992-08-03 1994-05-25 叶海 Combustion-gas catapult
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DE20003950U1 (en) * 2000-03-08 2001-07-19 Spieldiener Patrick Towing device for vehicles on amusement devices
US6837166B1 (en) * 2002-07-15 2005-01-04 Joop Roodenburg Rollercoaster launch system
FI113036B (en) 2002-09-16 2004-02-27 Robonic Ltd Oy Arrangement on the catapult
US7152827B2 (en) * 2003-01-17 2006-12-26 The Insitu Group, Inc. Methods and apparatuses for launching, capturing, and storing unmanned aircraft, including a container having a guide structure for aircraft components

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

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