EP0438364B1 - Drehantriebsvorrichtung für den Schrankenbaum einer beweglichen Schranke - Google Patents

Drehantriebsvorrichtung für den Schrankenbaum einer beweglichen Schranke Download PDF

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Publication number
EP0438364B1
EP0438364B1 EP91420008A EP91420008A EP0438364B1 EP 0438364 B1 EP0438364 B1 EP 0438364B1 EP 91420008 A EP91420008 A EP 91420008A EP 91420008 A EP91420008 A EP 91420008A EP 0438364 B1 EP0438364 B1 EP 0438364B1
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EP
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Prior art keywords
axis
shaft
motor
driven
bar
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EP91420008A
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English (en)
French (fr)
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EP0438364A1 (de
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Jean-Marc Mignot
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    • E—FIXED CONSTRUCTIONS
    • E06—DOORS, WINDOWS, SHUTTERS, OR ROLLER BLINDS IN GENERAL; LADDERS
    • E06B—FIXED OR MOVABLE CLOSURES FOR OPENINGS IN BUILDINGS, VEHICLES, FENCES OR LIKE ENCLOSURES IN GENERAL, e.g. DOORS, WINDOWS, BLINDS, GATES
    • E06B11/00—Means for allowing passage through fences, barriers or the like, e.g. stiles
    • E06B11/08—Turnstiles; Gates for control of entry or exit of persons, e.g. in supermarkets
    • E06B11/085—Turnstiles; Gates for control of entry or exit of persons, e.g. in supermarkets non-rotary or with a limited angle of rotation, e.g. 90°
    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01F—ADDITIONAL WORK, SUCH AS EQUIPPING ROADS OR THE CONSTRUCTION OF PLATFORMS, HELICOPTER LANDING STAGES, SIGNS, SNOW FENCES, OR THE LIKE
    • E01F13/00—Arrangements for obstructing or restricting traffic, e.g. gates, barricades ; Preventing passage of vehicles of selected category or dimensions
    • E01F13/04—Arrangements for obstructing or restricting traffic, e.g. gates, barricades ; Preventing passage of vehicles of selected category or dimensions movable to allow or prevent passage
    • E01F13/06—Arrangements for obstructing or restricting traffic, e.g. gates, barricades ; Preventing passage of vehicles of selected category or dimensions movable to allow or prevent passage by swinging into open position about a vertical or horizontal axis parallel to the road direction, i.e. swinging gates

Definitions

  • the invention relates to a device for driving the boom of a movable barrier in rotation around an axis perpendicular to this boom, and between two extreme positions, one of which corresponds to the closure of a passage and the other corresponds to the opening of this passage.
  • German patent DE 32 31 720 discloses a heald actuated by an electric motor, placed vertically, and therefore the drive of the shaft carrying the link drive is achieved through a pinion system.
  • an electric motor is generally used, the angular stroke of rotation of which can be less than one revolution, the output shaft of which can remain stationary while the motor is under tension without the latter being damaged, and which can operate in both directions of rotation at will.
  • a motor is known in itself and generally consists of a lockable single-phase motor with constant torque, commonly designated by the expression "torque-motor”.
  • the drive device generally comprises a driven shaft mounted on a frame so as to be able to pivot around the horizontal axis perpendicular to the heald, the heald being driven by one of its ends in rotation by this driven shaft which is itself driven in rotation by a driven rod pivoting about the same horizontal axis.
  • the output shaft of the electric motor is coupled to a connecting rod-crank system, and the crank has its free end connected to the free end of the driven connecting rod.
  • the motor drives the connecting rod of the connecting rod-crank system in rotation substantially through a half-turn between two elastic stops which limit the trajectory of this connecting rod.
  • Such devices have proved difficult to adjust from the point of view of the kinematics, and of the relative positions of the shafts, connecting rods and cranks, so that the arm is effectively driven over 90 ° between the horizontal position and the vertical position.
  • the time required for the beam to pass between its two extreme positions is generally between 1.6 and 1.8 s. Gold, this time is now considered to be too long, especially for modern motorway toll barriers which must allow tolling to be faster and faster, even without stopping vehicles.
  • these known devices include too large a number of moving parts, subject to wear, and noisy.
  • the heddle of such a movable barrier must, for safety reasons, be able to be locked in a horizontal position. It is generally necessary to prevent a user from being able to raise the boom manually. However, the mere resistance of the motor is generally insufficient in this regard. This is why, in known devices, when the heddle is in horizontal position, the connecting rod-crank system is arranged so as to be at one of its top or bottom dead centers, thus effecting mechanical locking of the heddle in horizontal position. . However, it turns out that with such devices, it is difficult in practice to obtain a blocking of the arm in the vertical position, in particular taking into account the problems of space and the other constraints imposed elsewhere. Therefore, in case of strong horizontal wind, the barrier of the barrier in the vertical position can be inadvertently brought back to its horizontal position and thus hinder the free passage of people or vehicles.
  • the elastic stops limiting the rotational stroke of the rod driven by the engine generate phenomena of vibration in the extreme positions of the heddle. These phenomena are obviously undesirable and cause in particular very rapid wear of the shaft mounting bearings and mechanical connections.
  • the invention aims to remedy simultaneously the aforementioned drawbacks of the drive devices of the prior art.
  • the object of the invention is therefore to propose a drive device which is simple to adjust, much faster, in particular allowing a passage of the beam between its two positions. extremes in less than 1 s-, incorporating a minimum number of parts, and which does not include an elastic end-of-travel stop generating untimely vibrations. More particularly, an object of the invention is to provide such a device in which the speeds and the resisting torque tend to be zero in the extreme positions, by geometric construction.
  • Another object of the invention is to provide such a drive device which can not only block the boom in an extreme position, in particular horizontal, but also block the boom in the other extreme position, in particular vertical , in a simple and economical way.
  • Another object of the invention is to provide such a drive device in which the electric motor operates with a rotation stroke of its motor shaft less than 120 °, in particular of the order of 90 °.
  • the invention provides a device for driving the boom of a movable barrier in rotation around an axis perpendicular to this boom, and between two extreme positions, in particular at least partially and at least substantially horizontal respectively vertical , comprising a driven shaft mounted on a frame so as to be able to pivot around the axis of the heald, the heald being driven by one of its ends in rotation by this driven shaft which is itself driven in rotation by a driven connecting rod pivoting about an axis parallel or coincident with the axis of the heald, and comprising an electric motor for driving the driven connecting rod, the driven shaft and the heald in rotation.
  • the motor shaft is parallel to the driven shaft, and connected to the driven connecting rod by means of a driving rod driven in rotation by the motor shaft, the two driven driving rods being associated one with the 'other by association means providing a pivot connection with an axis parallel to the motor shaft and the driven shaft, pivot connection which is capable of sliding in translation radially with respect to the driven connecting rod and the tree led.
  • the motor shaft, the driving rod, the driven rod and the driven shaft have a rotational stroke between the two extreme positions of the arm which is less than half a turn, in particular less than 120 °. In practice, the stroke of the motor shaft can be limited to 90 °.
  • the orientation of the driving rod - defined by the direction passing through the axis of rotation of this driving rod and by the axis of the pivot connection -, and the orientation of the driven rod - defined by the direction passing through the axis of rotation of this driven connecting rod and by the axis of the pivot link, are generally perpendicular to each other in at least one of the two extreme positions of the heddle. In this position where the orientations of the connecting rods are perpendicular to each other, mechanical locking is achieved, since the driven connecting rod cannot rotate the driving connecting rod.
  • the orientations of the driving and driven connecting rods are perpendicular to one another in the two extreme positions of the heddle, namely in particular in the horizontal position and in the vertical position.
  • the driven connecting rod and the arm are mounted on the driven shaft integral in rotation with this shaft
  • the driving connecting rod is mounted on the engine shaft integral in rotation with this shaft of the engine
  • the orientations of the two driving and driven connecting rods are generally at right angles to each other in each of the extreme positions of the arm, and the stroke of the motor shaft is 90 ° between these two positions. extremes.
  • the means of association of the two driving rods and driven to one another consist of a roller mounted free in rotation at the free end of the driving rod around a shaft parallel to the 'motor shaft and the driven shaft, and a radial groove of the driven rod in which the roller is engaged so as to cooperate by contact with the bearing surfaces of the groove.
  • These radial bearing surfaces of the groove allow the roller making the pivot connection to slide radially relative to the rod connected to the driven shaft.
  • the motor shaft extends under and vertically from the driven shaft, and the driving rod is in the form of a flywheel portion whose center of gravity is eccentric relative to the motor shaft and to the orientation of this driving rod, so as to form a return counterweight tending to drive this driving rod in rotation in one direction, in particular in the direction corresponding to the return or the maintenance of the arm in the vertical position - in the absence of an electric power supply to the motor.
  • a return spring drives the driven shaft to assist this motor in the rise of the arm and to return the arm to the vertical position in the event of the power supply to the motor being cut off.
  • the invention also relates to a drive device incorporating the above characteristics, in combination, and more particularly suitable for driving a heald about a horizontal axis.
  • the invention solves the problem mentioned above.
  • the driving and driven connecting rods are perpendicular to each other, that is to say when the groove is perpendicular to the orientation of the driving connecting rod, the engine-resisting torque is , due to the geometry of the mechanism, which is extremely low or even zero when the engine is started. Therefore, the engine can, at startup, have a significant acceleration, acceleration which allows it to quickly take a speed of significant value.
  • the two driving and driven connecting rods are in alignment with each other, that is to say when the resisting torque is, because of the geometry, the most important, the speed of the motor. has already acquired significant value.
  • the invention provides a device essentially incorporating only two connecting rods.
  • the invention relates to a device for driving the boom 1 in rotation of a barrier movable about a horizontal axis 2 perpendicular to this boom 1, and between two extreme positions at least partially and at least substantially horizontal respectively vertical.
  • This drive device comprises a driven shaft 3 mounted on a frame 4 so as to be able to pivot about the horizontal axis 2 of rotation of the heald 1.
  • the heald 1 is driven in rotation by the driven shaft 3 connected to the 'one 5 of the ends of the stringer 1.
  • the smooth 1 can be made of several articulated elements or not.
  • the driven shaft 3 is itself driven in rotation by a driven connecting rod 6 which pivots about a horizontal axis parallel or coincident with the horizontal axis 2 of rotation of the heddle 1.
  • An electric motor 7 rotates the driven connecting rod 6, the driven shaft 3, and the heddle 1.
  • This motor 7 is capable of being able to be stopped by force under tension without undergoing deterioration such as a burnout of its windings.
  • the electric motor 7 is chosen and controlled by an appropriate device so that it can rotate in one or the other direction of rotation depending on whether the heddle 1 must be raised from the horizontal position to the vertical position or lowered from the vertical position to the horizontal position.
  • Such a control device for such an electric motor is known in itself and therefore does not have to be described or shown.
  • the shaft 8 of the engine is arranged to extend parallel to the driven shaft 3.
  • the shaft 8 of the engine is connected to the driven connecting rod 6 by means of a driving connecting rod 9 driven in rotation by the shaft 8 of the engine, the two driving connecting rods 9 and driven 6 being associated with each other by means 10, 13 of association producing a connection of the pivot link type with axis 11 of parallel pivoting to the shaft 8 of the engine and to the driven shaft 3.
  • the pivot connection of the association means 10, 13 is moreover capable of sliding in translation radially with respect to the driven connecting rod 6 and to the driven shaft 3 , that is to say perpendicular to its axis 11.
  • the means 10, 13 of association form a connection between the two connecting rods, 6, 9 with two degrees of freedom: a rotation around the axis 11 of the pivot connection, and a translation perpendicular to this axis 11 and in the stiff direction of the driven shaft 3.
  • the pivot link slides in translation along the driven rod 6 radially while driving this driven rod 6 in rotation around the driven shaft 3.
  • the axis of rotation of the driving rod 9 is parallel or coincident with the horizontal axis of rotation 14 of the shaft 8 of the engine.
  • the direction D2 passing through the axis of rotation of this driving rod 9 and through the axis 11 of the pivot connection of the means 10, 13 of association defines the orientation overall of the driving connecting rod 9.
  • the direction D1 passing through the axis of rotation of the driven connecting rod 6 and through the axis 11 of the pivot connection of the association means 10, 13 defines the overall orientation of the driven rod 6.
  • these two orientations D1, D2 are generally perpendicular to each other in at least one of the extreme positions of the heald 1 -in particular at least in the horizontal position of the heald 1- .
  • these orientations D1, D2 of the connecting rods 6, 9 are perpendicular to each other in the two extreme positions of the heddle 1, that is to say in horizontal position and in vertical position.
  • the driven rod 6 cannot drive the driving rod 9 in untimely rotation.
  • the action of the driven rod 6 on the driving rod 9 can only be done on the pivot link by reaction of the means allowing the radial translation of this pivot link.
  • this reaction is perpendicular to the direction of translation, that is to say perpendicular to the driven connecting rod 6.
  • Reducing devices could be provided between the different elements of the connecting rod mechanism driven by each other. Thanks to such reducers, one could for example use driven rods 6 and driving 9 of different lengths and angular strokes.
  • the driven connecting rod 6 and the heddle 1 are mounted directly on the driven shaft 3 integral in rotation with the driven shaft 3 by means 15, 16 coupling.
  • the coupling 15 of the connecting rod driven on the shaft 3 can be a coupling by tightening, by geared tightening, or by crimping or the like.
  • the coupling 16 of the end 5 of the heddle 1 on the shaft 3 is located at a free end 17 of the shaft 3 opening out of the frame 4.
  • the driven shaft 3 is mounted on the frame 4 thanks to bearings or bearings 18, 19 one of which 18 supports one end 20 of the shaft 3 and the other of which 19 allows the free end 17 of the shaft 3 to exit outside the frame 4.
  • the coupling 16 of the heald 1 on the free end 17 can be made in any suitable manner, for example by means of a set of flanges 21 in the form of a band encircling the end 5 of the heald 1 and clamped to a plate 22 by means of screws or appropriate tensioners, the plate 22 being mounted integral in rotation with the driven shaft 3 and extending perpendicular to the horizontal axis 2 of rotation of this shaft 3.
  • the driving rod 9 is mounted directly on the motor output shaft 8, integral in rotation with the motor shaft 8 by means of a rigid coupling 23 which can be produced by tightening, geared tightening, crimping or the like ... If the motor 7 includes a reduction device which is incorporated therein, the driving rod 9 is then mounted directly on the output shaft of said reduction gear which is considered to be the motor output shaft 8.
  • the orientations D1, D2 of the two driving and driven connecting rods 6, 9 being generally at right angles to one another in these extreme positions of the arm 1, the stroke of the shaft 8 of the engine being 90 ° between these two extreme positions.
  • the drive device according to the invention is particularly simple, incorporates few parts, is reliable, easy to adjust, extremely fast, and optimizes the operating conditions of the electric motor 7.
  • the two connecting rods being at an angle right in each of the extreme positions, the torque resisting starting the engine is zero or almost zero.
  • blocking of the heddle 1 is carried out in the two extreme vertical and horizontal positions.
  • the means 10, 13 of association of the two connecting rods 6, 9 between them consist on the one hand of a roller 10 mounted free in rotation at the free end 24 of the driving rod 9 around a horizontal shaft 12 mounted fixed relative to the driving rod 9 parallel to the motor shaft 8 and to the driven shaft 3, and on the other hand to a radial groove 13 of the driven connecting rod 3 in which the roller 10 is engaged, the radial groove 13 forming bearing surfaces for the roller 10 which cooperates by contact with radial surfaces 25, 26 facing the groove 13.
  • the radial surfaces 25, 26 of the groove 13 are placed parallel to each other, on either side and at equal distance from the radial direction of the axis 2 of the driven shaft 3, that is to say of the orientation D1 of the driven connecting rod 6.
  • the distance between the radial bearing surfaces 25, 26 corresponds, apart from the clearance allowing the rolling of the roller 10, to the external diameter of the roller 10. From the so, for any angular position of the driving rod 9, corresponds, apart from play, one and only one angular position of the driven rod 6, that is to say of the arm 1.
  • the groove 13 is closed at each of its ends, and, according to the invention, at the free end 27 of the driven rod 6 by cylindrical portions of revolution with horizontal axis 28, 29.
  • the cylindrical portions 28, 29 connect the radial bearings 25, 26 continuously at each end of the groove 13. In each extreme position of the heddle 1, the roller 10 comes into contact with the cylindrical portion 28 located at the free end 27 of the driven connecting rod 6.
  • This portion cylindrical 28 is therefore placed at such a distance from the axis 2 of the driven shaft 3 that when the roller 10 comes into contact it is equidistant from the axis 2 of the driven shaft 3 and the axis 14 of the shaft 8 of the engine, the orientations D1 and D2 of the two connecting rods 6, 9 being perpendicular to one another ( Figures 1, 2, 4 and 5).
  • the other cylindrical end portion 29 is located on the internal side close to the driven shaft 3 at a distance sufficient to allow the passage of the two connecting rods 6, 9 in alignment with one another midway between the two extreme positions and between the shafts 3, 8, that is to say when the heald 1 is at 45 ° relative to the horizontal. It should be noted that the other variant in which the groove extends towards the free end of the connecting rod 6 from internal cylindrical portions in the extreme positions, the driving connecting rod 9 rotating under the shaft 8, would be feasible.
  • the roller 10 rolls on one of the bearing surfaces of the groove 13.
  • the roller 10 rolls on the other 26 of the radial bearing surfaces of the groove 13.
  • the bearing surfaces 25, 26 are plane, opposite and located in planes parallel to each other and to a radial plane containing the axis 2 of rotation of the driven connecting rod 6, at equal distance and on each side of this radial plane.
  • the shaft 8 of the motor extends under and vertically from the driven shaft 3.
  • This length L1, L2 is determined according to the gear ratio that we want to give to the device d 'drive, taking into account the characteristics of the motor 7 in particular.
  • the motor 7 is placed on a support 30 rigidly associated with the frame 4 by any suitable means (welding, bolt, etc.).
  • the drive device comprises means making it possible to place the heald 1 in a vertical position and to maintain it in this position in the event of the power supply to the motor being cut off.
  • safety standards require that the arm 1 automatically returns to the vertical position.
  • the drive device according to the invention comprises a return spring 31 driving the driven shaft 3 to bring the arm 1 back to the vertical position in the event of the power supply to the motor being cut off.
  • This spring 31 is for example a linear tension spring, one end of which is mounted on the support 30 of the motor 7, and the other end of which is associated with the free end 32 of a return link rod 33 mounted integral in rotation with the shaft driven 3 by a coupling 34.
  • the connecting rod 33 is angularly oriented relative to the driven shaft 3 and the driven connecting rod 6 to tension the spring 31 in the horizontal position of the arm 1 ( Figure 2) and return this arm 1 in position vertical ( Figure 1).
  • the spring 31 also has the function of compensating for the torque due to the weight of the stringer 1 on the rise by assisting the motor 7.
  • the driving rod 9 is a simple rod.
  • Figure 2 we can see ( Figure 2) that in the horizontal position of the arm 1, if the motor supply comes to be cut, the action 31 of the spring has no effect since, as explained, the driven connecting rod 6 cannot rotate the driving connecting rod 9, the groove 13 extending perpendicular to the direction D2 of the driving rod 9. It suffices for a slight movement of the roller 10 in the groove 13 towards the internal cylindrical portion 29 to exit this blocking point and allow the effective return of the arm 1 under the effect of the spring 31.
  • the driving rod 9 is provided with a counterweight which can be of low value taking into account that the displacement of the roller 10 in the groove 13 from the extreme horizontal position of the heddle 1 requires little effort, thanks to the geometry of the mechanism.
  • This counterweight can be simply achieved by an extension of the driving rod 9 opposite or generally opposite with respect to the shaft 8 of the engine, or even by another connecting rod mounted integral with this shaft 8 of the engine in a appropriate direction, extension or other connecting rod to which a mass of determined value could be suspended.
  • the torque that this counterweight must exert must simply overcome the resistive torque of the motor not supplied with current increased by the torques due to friction in the extreme horizontal position.
  • the driving rod 9 is in the form of a flywheel whose center of gravity is eccentric relative to the shaft 8 of the engine and to the 'orientation D2 of this driving rod 9, so as to form return counterweight tending to cause this driving rod 9 to rotate in one direction in the absence of electrical power to the motor.
  • the driving rod 9 consists of an angular sector of the disc extending generally on one side of the direction D2.
  • the angle formed by this sector is between 90 ° and 180 °, in particular is of the order of 120 °.
  • One of the sides of this angular sector of the flywheel portion is formed by the orientation D2 of the driving rod 9, that is to say by the direction passing through the axis 12 of the roller 10 and through the axis 14 of the motor shaft 8. This side is simply slightly extended beyond the direction D2 to allow the mounting of the driving rod 9 on the shaft 8 thanks to the coupling 23.
  • the curve of the resistive torque undergone by the shaft 8 of the engine in the case of a non-articulated boom 1, and which this engine must therefore overcome, has the general appearance represented in FIG. 6. It can be seen that this torque is zero for extreme positions, especially when the heald 1 is horizontal (angle equal to 0 °). On the ordinate, the value of this resistant torque has been plotted, and on the abscissa, the angle formed by the stringer 1 has been plotted relative to the horizontal. The curve is not necessarily symmetrical with respect to the angular mean portion. We make sure that the maximum torque is near the average position of 45 °.
  • the engine torque supplied to the driven shaft 3 is maximum in the vicinity of the aligned position of the orientations D1 and D2 of the two driven and driving connecting rods corresponding to the position of the beam at 45 °. In this position, the boom rotation speed is also at its maximum.
  • the axis 2 of rotation of the barrier is perpendicular to the heald 1.
  • the heddle 1 pivots horizontally along an axis 2 disposed vertically.
  • the means 10, 13 of association can comprise an elastic stop system.
  • the cylindrical part 28 of the groove 13 is equipped with an elastic stop 280, 281.
  • This stop is such that in the closed closed end position, the motor being supplied, the roller 10 exerts a slight force f1 of compression on the stop, to stress the crushing thereof.
  • the removal of the force f1 causes the release of the stress and the release of the stop which decompresses by causing the displacement along F2 of the roller 10.
  • This displacement has the effect of facilitating lifting of the barrier in the event of a power failure, the movement then being initiated and continued through the shape of the driving rod 9 as has already been explained previously.
  • FIG. 11 shows a variant according to which the return spring is a compression spring whereas in the previous embodiments, the device was equipped with a tension spring.
  • a rod 310 connected to the free end 32 of the connecting rod 33, comprises at its lower end a stop 311 constituted by a nut 312.
  • the compression spring 313 being on the one hand bearing against this lower stop 311 and on the other hand, bearing on an upper stop 314 constituted by the support 30 of the motor 7.

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  • Engineering & Computer Science (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
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  • Auxiliary Devices For And Details Of Packaging Control (AREA)
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Claims (9)

  1. Antriebsvorrichtung zum Drehen des Schrankenbaumes (1) einer beweglichen Schranke um eine Achse (2) zwischen zwei Extremstellungen, umfassend eine derart auf einen Rahmen (4) montierte Abtriebswelle (3), daß sie um die Achse (2) schwenken kann, den Schrankenbaum (1), der von einem seiner Enden (5) aus durch die Abtriebswelle (3) in Drehung versetzt wird, welche selbst durch eine, um eine Parallelachse schwenkbare oder mit der Achse (2) des Schrankenbaumes (1) zusammenfallende, führende Kurbel (6) in Drehung versetzt wird und einen Elektromotor (7), um die geführte Kurbel (6), die Abtriebswelle (3) und den schrankenbaum (1) in Drehung zu versetzen, wobei die geführte Kurbel (6) mit einer führenden Kurbel (9) durch Mittel (10, 13) zum Verbinden, realisiert in einer Vereinigung an der Drehpunktachse (11), verbunden sind, die geeignet sind, bei radialer Parallelverschiebung relativ zu der geführten Kurbel (6) und der Abtriebswelle (3) in einer Führung zu gleiten, dadurch gekennzeichnet, daß die Motorwelle (8) parallel zur Abtriebswelle (3) sitzt, die führende Kurbel (9) direkt durch die Motorwelle (8) in Drehung versetzt wird und der Elektromotor (7) ein Motor des Typs mit konstantem Moment ist.
  2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Stellung der führenden Kurbel (9), definiert durch die, die Rotationsachse dieser Kurbel (9) und die Achse (11) der Drehpunktverbindung schneidende, Richtung D2, und die Stellung der geführten Kurbel (6), definiert durch die, die Rotationsachse dieser Kurbel (6) und die Achse (11) der Drehpunktverbindung schneidende, Richtung D1, wenigstens in einer der Extremstellungen des Schrankenbaumes (1) im ganzen etwa rechtwinklig zueinander sind.
  3. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß die Stellungen der Kurbeln (6, 9) in beiden Extremstellungen des Schrankenbaumes (1) rechtwinklig zueinander sind.
  4. Vorrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die geführte Kurbel (6) und der Schrankenbaum (1) auf der Abtriebswelle (3) montiert sind, drehfest verbunden mit dieser Abtriebswelle (3), daß die führende Kurbel (9) auf der Motorwelle (8) montiert ist, drehfest verbunden mit dieser Motorwelle (8) und daß der Abstand L1 zwischen der Achse (11) der Drehpunktverbindung und der Achse (14) der Motorwelle (8), der Abstand L2 zwischen der Achse (11) der Drehpunktverbindung und der Achse (2) der Abtriebswelle (3) innerhalb der Extremstellungen des Schrankenbaumes (1) und der Abstand d zwischen der Achse (14) der Motorwelle (8) und der Achse (2) der Abtriebswelle (3) ein Verhältnis verwirklichen:
    L1 = L2 = d √2/2 ( d Faktor zur Wurzel 2 dividiert durch 2), derart, daß die Stellungen der beiden führenden und geführten Kurbeln (6, 9) in jeder der Extremstellungen des Schrankenbaumes (1) global etwa in einem rechten Winkel zueinander sind und die Bahn der Motorwelle (8) zwischen diesen beiden Extremstellungen 90° beträgt.
  5. Vorrichtung nach irgendeinem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Mittel (10, 13) zum Verbinden sich zusammensetzen aus einer Laufrolle (10), die frei zum Drehen am freien Ende (24) der führenden Kurbel (9) auf einer zu der Motorwelle (8) und der Abtriebswelle (3) parallelen Welle (12) montiert ist, und einer radialen Nut (13) der geführten Kurbel (6), in der die Rolle (10) derart eingebaut ist, daß sie bei Kontakt mit den Anlageflächen (25, 26) der Nut (13) zusammenwirkt.
  6. Vorrichtung nach irgendeinem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die Motorwelle (8) sich unterhalb der und auf einer Vertikalen zur Abtriebswelle (3) erstreckt, daß die führende Kurbel (9) einen Teil einer Unwucht bildet, deren Schwerpunkt derart exzentrisch zu der Motorwelle (8) und der Stellung dieser führenden Kurbel (9) liegt, daß ein Rückstell-Gegengewicht gebildet wird, welches geeignet ist, diese führende Kurbel (9) in Drehung zu versetzen, wenn die elektrische Versorgung des Motors fehlt.
  7. Vorrichtung nach Anspruch 6, dadurch gekennzeichnet, daß das durch die führende Kurbel (9) gebildete Gegengewicht ein Rückstellmoment in dem Sinne auf diese Kurbel (9) ausübt, daß der Schrankenbaum (1) in die vertikale Position entsprechend zurückgedreht oder gehalten wird.
  8. Vorrichtung nach Anspruch 7, dadurch gekennzeichnet, daß die horizontale Achse (2) des Schrankenbaumes (1) eine die Abtriebswelle (3) in Bewegung versetzende Rückstellfeder (31) umfaßt, um den Motor (7) beim Ansteigen des Schrankenbaumes (1) zu unterstützen und den Schrankenbaum (1) im Fall der Unterbrechung der elektrischen Versorgung des Motors (7) in die vertikale Position zu ziehen.
  9. Vorrichtung nach irgendeinem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Mittel (10, 13) zum Verbinden einen elastischen Anschlag (280, 281) umfassen.
EP91420008A 1990-01-11 1991-01-09 Drehantriebsvorrichtung für den Schrankenbaum einer beweglichen Schranke Expired - Lifetime EP0438364B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9000272A FR2656884B1 (fr) 1990-01-11 1990-01-11 Dispositif d'entrainement en rotation de la lisse d'une barriere mobile.
FR9000272 1990-01-11

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EP0438364A1 EP0438364A1 (de) 1991-07-24
EP0438364B1 true EP0438364B1 (de) 1994-08-10

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EP91420008A Expired - Lifetime EP0438364B1 (de) 1990-01-11 1991-01-09 Drehantriebsvorrichtung für den Schrankenbaum einer beweglichen Schranke

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EP (1) EP0438364B1 (de)
AT (1) ATE109846T1 (de)
DE (1) DE69103287D1 (de)
FR (1) FR2656884B1 (de)

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WO2010133764A1 (en) 2009-05-18 2010-11-25 Pg Effect Oy Apparatus for balancing an object to be reciprocated in a vertical plane along a circular orbit
CN105256739A (zh) * 2015-10-09 2016-01-20 石家庄优创科技股份有限公司 扭簧式电动栏杆机

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AT402311B (de) * 1995-03-20 1997-04-25 Skidata Gmbh Absperreinrichtung
BR9714550A (pt) 1997-07-17 2000-03-21 Magnetic Autocontrol Gmbh Dispositivo de acionamento para uma cancela de bloqueio.
IES991069A2 (en) * 1999-01-21 2000-10-04 Electro Automation Res Ear Ltd A Barrier
AU1551700A (en) 1999-11-06 2001-06-06 Magnetic Autocontrol Gmbh Stop barrier device or a stop or closure device of the kind
FR2854908B1 (fr) * 2003-05-13 2005-08-05 Ero Ind Barriere pour le controle d'acces de vehicules a dispositif de retour automatise, apres degondage
FR2927648B1 (fr) * 2008-02-15 2013-06-28 Jacques Paternoster Structure de pilier associee a un vantail pivotant motorise
CN106638379B (zh) * 2015-11-02 2019-05-03 吉大联合精密机械（厦门）有限公司 一种六杆机构传动的道闸机芯
CN111472302A (zh) * 2019-01-24 2020-07-31 项强 一种新型滑轨式重力自锁的自动道闸传动装置
CN110541348B (zh) * 2019-08-22 2024-07-16 中国船舶重工集团应急预警与救援装备股份有限公司 一种自锁式连接机构

Family Cites Families (3)

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Publication number Priority date Publication date Assignee Title
US4232484A (en) * 1977-12-21 1980-11-11 Zuhlke Engineering Ag Apparatus for moving toll bars or the like
DE3231720C1 (de) * 1982-08-26 1983-11-17 Ewald Berninghaus GmbH & Co, 4100 Duisburg Schranke für Tor- und Parkhauseinfahrten, Eisenbahnübergänge u. dgl.
DE8706868U1 (de) * 1987-05-13 1987-07-09 Magnetic-Elektromotoren GmbH, 7867 Maulburg Antriebsvorrichtung für Schranke od. dgl.

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010133764A1 (en) 2009-05-18 2010-11-25 Pg Effect Oy Apparatus for balancing an object to be reciprocated in a vertical plane along a circular orbit
CN105256739A (zh) * 2015-10-09 2016-01-20 石家庄优创科技股份有限公司 扭簧式电动栏杆机
CN105256739B (zh) * 2015-10-09 2017-07-11 石家庄优创科技股份有限公司 扭簧式电动栏杆机

Also Published As

Publication number Publication date
FR2656884B1 (fr) 1992-07-24
FR2656884A1 (fr) 1991-07-12
ATE109846T1 (de) 1994-08-15
DE69103287D1 (de) 1994-09-15
EP0438364A1 (de) 1991-07-24

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