EP1323660B1 - Frein de securité pour système d'ascenceur - Google Patents

Frein de securité pour système d'ascenceur Download PDF

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Publication number
EP1323660B1
EP1323660B1 EP02027158.1A EP02027158A EP1323660B1 EP 1323660 B1 EP1323660 B1 EP 1323660B1 EP 02027158 A EP02027158 A EP 02027158A EP 1323660 B1 EP1323660 B1 EP 1323660B1
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EP
European Patent Office
Prior art keywords
force
piston
braking
safety brake
brake
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.)
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EP02027158.1A
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German (de)
English (en)
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EP1323660A1 (fr
Inventor
Peter Hitz
Josef Muff
Roger Martinelli
Philipp Angst
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Inventio AG
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Inventio AG
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Priority to EP02027158.1A priority Critical patent/EP1323660B1/fr
Publication of EP1323660A1 publication Critical patent/EP1323660A1/fr
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Publication of EP1323660B1 publication Critical patent/EP1323660B1/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B5/00—Applications of checking, fault-correcting, or safety devices in elevators
    • B66B5/02—Applications of checking, fault-correcting, or safety devices in elevators responsive to abnormal operating conditions
    • B66B5/16—Braking or catch devices operating between cars, cages, or skips and fixed guide elements or surfaces in hoistway or well
    • B66B5/18—Braking or catch devices operating between cars, cages, or skips and fixed guide elements or surfaces in hoistway or well and applying frictional retarding forces

Definitions

  • the invention relates to a safety brake for elevator systems according to the preamble of the first claim.
  • a brake safety device for an elevator car is known in which a braking device acts on the guide rail of the elevator car.
  • the braking force exerted by the braking device on the guide rail is controlled by a control device so that the deceleration values remain in a tolerable for the passengers measure.
  • the braking device is actuated substantially hydraulically by means of a pressure pump and a pressure accumulator, wherein the braking force is adjusted via a control device engaging on a control valve.
  • US 6193026 B1 and US 5353895 disclose a brake for an elevator system in which a prestressed spring is provided to a brake element against a guide rail of an elevator car to squeeze.
  • a device is provided with which a counterforce acting counter to the force of the spring can be exerted on the brake element.
  • This counterforce is generated hydraulically by generating a force on a piston by means of an electromagnet and transmitting this force to the brake element with a pressure medium in a pressure medium volume between the piston and the brake element, the pressure medium volume being shaped on the brake element in such a way that that the force thus transmitted counteracts the force of the spring.
  • the piston is dimensioned such that the counterforce acting on the brake element is greater than the force exerted on the piston force.
  • the pressure medium therefore has the function of a power amplifier for the forces acting on the piston.
  • the construction of this brake is complicated, in particular with regard to the shape of the brake element and the housing which surrounds the brake element, since on the one hand the spring is coupled directly to the brake element and on the other hand a counterforce to the force of the spring must be hydraulically transmitted to the brake element.
  • the efficiency of such a brake in operation is not optimal when the brake should be designed for large braking forces or when the brake should generate different levels of braking forces in different operating conditions. The latter would be the case if the brake is to be designed both for operation as a safety brake of an elevator car and for operation as a holding brake of the elevator car.
  • the invention has for its object to provide a structurally simple, operable with high efficiency safety brake for elevator systems.
  • this object is achieved by a safety brake having the features of the first claim.
  • This safety brake comprises a braking device with one or more movable brake elements, each of which - applied with a braking force - can be brought into contact with a suitable reference surface in order to achieve a braking effect.
  • actuating the braking device is understood below to mean a measure which generates a finite braking force or contributes to increasing the braking force.
  • releasing the braking device is understood below to mean a measure which contributes to a reduction of the braking force.
  • the braking force acting on a brake element is generated by a force acting on a movable piston being transmitted to the respective brake element with a pressure medium in a pressure medium volume between the piston and the brake elements, for example hydraulically.
  • force which acts on a movable piston may also be understood below to mean the resultant of a plurality of partial forces which are generated independently of one another by different means and which act directly or indirectly on the piston.
  • a device for generating a force acting on the piston, which comprises means for generating a first force acting on the piston for actuating the braking device and means for generating a second force acting on the piston, which counteracts the first force, includes.
  • the force acting on the piston is therefore the resultant of all Partial forces related to the first and second forces.
  • the first force In order for the first force to actuate the brake device, the first force must be directed with respect to the direction of movement of the piston in such a way that the piston acts compressively on the pressure medium.
  • the second force is intended to counteract the first force and serves to release the brake device.
  • a functional separation between "actuating the brake device” and “releasing the brake device” is realized. This is accomplished by generating the first and second forces independently by different means. This functional separation provides a starting point for optimizing the safety brake in terms of its efficiency, since the means for generating the first force and the means for generating the second force can be optimized independently.
  • the piston is dimensioned such that the pressure means acts as a booster, i. the braking force acting on a brake element is greater than the force acting on the piston.
  • the pressure means acts as a booster
  • the braking force acting on a brake element is greater than the force acting on the piston.
  • the advantages of the invention can be seen in the fact that, in order to produce the forces acting on the piston, means are available with which sufficiently large forces can be generated with a comparatively small expenditure of energy.
  • energy storage for example on the basis of springs or permanent magnets.
  • Such systems typically require little power during operation because they can store energy and only little energy is needed to control the conversion of the stored energy into mechanical work.
  • a preloaded spring for example, even in the event of a power failure, a force can still be exerted on the piston.
  • the state of stress of the spring can be controlled with simple means and low energy consumption, for example, with electromechanical means, the spring in current flow keep it taut and allow it to relax automatically in the event of a power failure.
  • This principle is also transferable to other energy storage, for example, on permanent magnets which are arranged relative to each other movable at a distance such that they attract each other or repel.
  • the piston is dimensioned so that the pressure medium acts as a booster, then energy accumulators, which interact with the piston, could be designed to be relatively small and the moving masses, for example the pistons, can also be made small. Under these conditions, the means used to release the braking device, such as electromagnets and / or power storage and / or lever systems can be designed to be relatively small. Furthermore, for example, components from vehicle technology can be adopted, which can be produced in large quantities and therefore cost. Reliability and safety are ensured, since the vehicle technology has similar demands on safety and reliability as in elevator technology.
  • means for generating a force acting on the piston force to actuate the braking device may be designed so that different braking forces are generated depending on the situation under different circumstances.
  • a means for generating a third force which acts in addition to the first force on the piston is provided.
  • a variation of the braking force can be controlled by selectively transmitting the third force generating means with a predetermined force or no force to the piston. This is feasible by a controlled establishment or release of a mechanical connection between the means for generating the third force and the piston.
  • braking forces of different magnitude can also be realized, for example, with a plurality of prestressable springs whose effects are combined with each other by combining one or more preloaded springs alone or in combination in parallel and / or serial arrangement with the Pistons are brought.
  • An advantage of this concept is that a control over which of the springs is brought into connection with the piston, can be made possible with simple means and low energy consumption.
  • the relaxation of a spring with movable mechanical means such as lever elements and devices that control the instantaneous orientation of the lever elements, initiated or blocked and thus controlled.
  • the lever elements be formed reinforcing force.
  • the orientation of the lever elements can be controlled electromechanically, for example with springs and electromagnets, such that automatically the operation of the braking device is triggered in the event of a power failure.
  • Another variant for the embodiment of the inventive safety brake as an integrated holding and safety brake is based on the use of an additional (second) movable piston.
  • two pistons can alternatively and independently be acted upon by one or more forces.
  • the action of one of the pistons can be controlled controlled on the pressure medium. This can be achieved by means of a valve which, in the closed state, separates a piston from the part of the pressure medium which acts on the brake elements to generate the braking force, so that the respective braking force can be influenced exclusively by the other piston.
  • a controllable blocking means is provided, with which a movement of a piston during a controllable period in a predetermined position can be blocked, wherein blocking of the movement by means of a control signal can be canceled.
  • a blocking means may serve a movable mechanical means, such as an electromechanically actuated lever or bolt.
  • both pistons By a suitable dimensioning of the pistons and a suitable timing of the forces acting on the individual piston forces of different sizes can be generated with the same braking device in this way.
  • FIG. 1 and Fig. 2 an elevator shaft 1 with a movable along guide rails 2 elevator car 3 is shown.
  • the elevator car is in a support frame 4, which consists of an upper yoke 5, side plates 6 and a not shown lower yoke.
  • brake devices 7 are arranged, which enclose a free leg 8 of the guide rails 2 by means of a recess 9.
  • the free leg 8 may be coated according to the engagement of the braking device and to improve the braking behavior.
  • the braking device 7 can be attached to the upper yoke 5 as shown, but it is also possible, for example, to attach it to the lower yoke or both.
  • the braking device is supplied via a pressure medium device 10 and pressure medium lines 11a and 11b with pressure medium.
  • a first and a second pressure medium line 11a and 11b are used and the two brake devices 7 are addressed by two pressure medium lines in each case.
  • the braking devices are designed so that in case of failure of the pressure medium lines 11a or 11b, the elevator car 3 can still be stopped safely by means of the remaining pressure medium line.
  • a control device 12 suitably an electronic control, via the pressure means device 10 and the Pressure medium lines 11a, 11b supplied amount of pressure medium can be adjusted.
  • the pressure medium device 10 is designed so that in case of failure of the control device 12 or other disorders, the elevator car is stopped.
  • Fig. 3 Another possibility for the arrangement of the braking device 7 is shown.
  • the braking device 7 acts directly on an elevator motor 13, which drives the elevator via a shaft 14 and not shown means such as ropes.
  • the braking device 7 engages via the recess 9 on a brake disk 15 which is connected via the shaft 14 to the elevator drive 13 and the elevator motor brakes and optionally stops when the brake device is actuated.
  • Fig. 4 the braking device 7 is shown schematically in cross section.
  • a brake cylinder 16 a with a cylinder chamber 17 and a piston 18 is arranged.
  • a brake element 19 in the form of a brake plate or a brake lining is arranged on the brake disk 15 or the free leg 8 side facing.
  • Other known per se elements such as seals, etc. are not shown.
  • the braking device 7 after Fig. 4 includes a further brake cylinder 16b, which is constructed according to the brake cylinder 16a.
  • the brake cylinder 16b is now supplied with pressure medium via the pressure medium line 11a of the brake cylinder 16a and the pressure medium line 11b, then the pistons 18 and thus the brake elements 19 with a defined braking force against the brake disk 15 or the free one are pressed by the pressure medium pressed into the cylinder space 17 Leg 8 pressed and it created by friction, a braking effect.
  • a braking device 7 In this example, only one brake cylinder 16 a is arranged in the brake device 7. On the opposite side, a brake element 19a is directly connected to the supporting structure of the brake device 7, a so-called outer shoe brake is formed. The braking device 7 is slidably suspended by means not shown. If pressure medium is now pressed into the cylinder space 17 via the pressure medium line 11a, then the piston 18 is moved until the brake elements 19 contact the brake disk 15 or the free leg 8.
  • the brake device 7 Due to the effect of the braking force exerted by the brake member 19 on the brake disc 15 and the free leg, the brake device 7 is displaced in the opposite direction to the direction of movement of the piston 18 until the brake member 19a also touches the brake disc 15 or the free leg 8. When releasing the brake, the braking device 7 is released again because of their movable arrangement.
  • FIG. 6 an embodiment of the inventive safety brake with a variant of the pressure means device 10 is shown schematically.
  • a master cylinder 20 is connected to a reservoir 21 which supplies the master cylinder 20 with pressure medium and compensates for any losses of pressure medium.
  • a piston 22a is actuated in the master cylinder 20, which presses in a movement of the piston rod 22 in the direction of the master cylinder 20 pressure medium in the leading from the master cylinder 20 pressure medium lines 11a and 11b.
  • the cylinder chamber 17 and the interior of the master cylinder 20 and the Pressure medium lines 11a and 11b define a pressure medium volume that is filled with the pressure medium.
  • an electromagnetic attraction device 23 is arranged, whose operation is known for example from speakers.
  • a plate 26 is fixedly fixed, on which a spring 27 surrounding the piston rod is supported.
  • the spring 27 is supported on the outside of the electromagnetic attraction device 23, which is arranged stationary with respect to the master cylinder 21.
  • the spring 27 is compressed in its longitudinal direction compared to its relaxed state and exerts a force F1 on the plate 26 and thus on the piston 22a.
  • F1 the force required to press the piston rod 22 in the direction of the master cylinder 20 and pressure medium in the leading from the master cylinder 20 pressure medium lines 11a and 11b pressed.
  • the pistons 18 are then moved toward the brake disk 15 or the free leg 8 and the brake elements 19 - acted upon by the braking force - pressed against the brake disk 15 or the free leg 8 to decelerate the elevator car.
  • the area of the piston 22a acting on the pressure medium in the master brake cylinder 20 is dimensioned such that the braking force acting on one of the brake elements 19 is greater than the force F1.
  • the electromagnetic tightening device 23 comprises an electromagnet with a coil 25 and an armature 24, which is attached to the end remote from the master cylinder 20 and along the central axis of the coil 25 together with the piston rod 22 is movable.
  • a Current flow through the coil 25 are directed such that on the armature 24 and thus on the piston rod 22, a counterforce F2 to the force F1 of the spring 27 acts to move the piston rod 22 in the direction of the electromagnetic attraction device 23.
  • the current flow through the coil 25 is effected in response to signals from the control device 12. By controlling the current flowing through the coil 25 thus the braking device 7 can be solved.
  • the coil 25 does not generate any electromagnetic force on the armature 24 and the piston rod 22 is pressed by the spring force F1 in the direction of the master cylinder 20. As a result, the braking device 7 is actuated. Thus, in case of accidents at any time a safe deceleration of the elevator car is guaranteed.
  • the spring 27 can also be replaced by another power storage, this under the condition that it is ensured in case of failure that the braking force is exerted by the energy storage on the master cylinder.
  • an acceleration sensor not shown, can be arranged, which cooperates with the control device 12. This allows the control device 12 to set the braking force so that no high, unpleasant for the users of the elevator car accelerations occur.
  • FIGS. 7 and 8th show by way of example how an integrated holding and catching brake can be realized within the scope of the invention.
  • Fig. 7 shows an embodiment of the safety brake, which is operable as an integrated holding and catch brake.
  • the safety brake according to Fig. 7 differs from the safety brake according to Fig. 6 merely a few additional components which introduce additional functionality: a spring 40 which extends like the spring 27 in the longitudinal direction of the piston rod 22 and is supported between the electromagnetic attraction device 23 and a movable plate 41; a two-armed lever 45 which is rotatably supported about a pivot 46; an electromagnet 49 with which an electromagnetic force can be exerted on one end of the lever 45; a spring 47, with the one end of the lever 45 - as indicated by an arrow - another force can be exercised.
  • a spring 40 which extends like the spring 27 in the longitudinal direction of the piston rod 22 and is supported between the electromagnetic attraction device 23 and a movable plate 41
  • a two-armed lever 45 which is rotatably supported about a pivot 46
  • an electromagnet 49 with which an electromagnetic force can be exerted on one end of the lever 45
  • the spring 40 is in the arrangement according to Fig. 7 compressed in its longitudinal direction and exerts on the plate 41 a force F3 in the direction of the master cylinder 20 (as indicated by the in Fig. 7 indicated arrow indicated). Under the action of the force F3, the plate 41 would be accelerated toward the master cylinder 20 unless prevented from doing so by additional measures.
  • the lever 45 is controlled by means of the electromagnetic force generated by the electromagnetic force 49 against the action of the force of the spring 47 within a limited angular range rotatable about the pivot point 46 and stably stable in at least two extreme angular positions.
  • One of these extreme positions of the lever 45 is in Fig. 7
  • the solenoid 49 is activated, ie supplied with power, and the solenoid 47 near the end of the lever 45 held such that the other end of the lever 45 is in contact with the plate 41 and the plate 41 - against the action of the force F3 of the spring 40 - in a stable position at a distance from the plate 26 holds.
  • the spring 40 and the plate 41 is aligned with respect to the spring 27 and the plate 26, that the braking device 7 by means of the forces F1 and F2, mediated by the spring 27 and the electromagnetic attraction device 23, can be actuated.
  • the other extreme stable angular position which can assume the lever 45, is characterized in that the electromagnet 49 is de-energized and the lever 45 assumes a certain position of the spring 47 equilibrium position.
  • this equilibrium position is determined by a suitable choice of the bias of the spring 47 so that the lever 47 does not touch the plate 41 or the plate 41 is unable to hold against the action of the force F3 of the spring 40 in a stable position. Consequently, the plate 41 is released and moved in the direction of the master cylinder 20.
  • the lengths of the springs 27 and 40 are matched to one another and the plates 26 and 41 are shaped such that the spring 40 expands in the direction of the master cylinder 20 until the plate 41 is finally blocked by the plate 26. In this position, the forces F1 and F3 of the springs 27 and 40 additively act on the piston 22a in the master cylinder 20.
  • the control device 12 is designed such that the electromagnet 49 and the electromagnetic attraction device 23 can be controlled independently of each other, such that the currents of the electromagnet 49 and the coil 25 flowing through currents to predetermined values be managed.
  • the time course of these currents it can thus be achieved that the piston 22a is acted on by the force F1 or by the resultant of the forces F1 and F3, provided that the coil 25 is de-energized and thus the force F2 is equal to zero.
  • By a suitable choice of the current intensity of the coil 25 flowing through the current generated by the springs 27 and 40 forces can be compensated in whole or in part.
  • an integrated holding and catch brake can be realized by the springs 27 and 40 are dimensioned appropriately.
  • the spring constant and the bias of the spring 27 is selected so that by the action of the force F1 on the piston 22a for the operation as, holding brake desired braking force is transmitted to the brake elements 19.
  • the spring constant and the bias of the spring 40 is selected so that by the action of forces F1 and F3 on the piston 22a the desired braking force for operation as a safety brake is transmitted to the brake elements 19.
  • An integrated holding and safety brake based on the safety brake according to Fig. 7 is designed so that in a general power failure, the operation is activated as a safety brake, under this condition, the force F2 is equal to 0 and also the lever 45 is oriented so that the expansion of the spring 40 is enforced in the longitudinal direction.
  • the plate 41 To the safety brake according to Fig. 7 to operate again as a holding brake after operation as a safety brake, the plate 41 must against the force F3 of the spring 40 of the plate 26th are removed, so that only the forces F1 and F2 act on the piston 22a and the spring 40 without influence on the piston 22a. To achieve this is one in the Fig. 7 not shown device provided - the plate 41 is activated in such a stable position - activated by signals of the control device 12, in which they from the lever 45 after a suitable activation of the electromagnet 49 and a corresponding orientation of the lever 45 at a distance to the plate 26th can be held.
  • Such a device can also be dispensed with, since under realistic conditions during the operation of an elevator relatively few situations occur in which the function of a safety brake must be activated. It is therefore acceptable to have the resetting of the safety brake in service as a holding brake by service personnel.
  • the spring 40 is according to Fig. 7 dimensioned so that it surrounds the spring 27 without touching it.
  • the spring 40 is guided around the piston rod 22 like the spring 27.
  • the plate 41 has - as in Fig. 7 is indicated - a central opening through which the piston rod 22 and the spring 27 are movable.
  • the springs 27 and 40 could also be arranged side by side without one of the springs surrounding the other.
  • the means for coupling the springs to the piston rod 22 - i. the plates 26 and 41 - could be replaced by other variants with the same function.
  • Fig. 8 shows a further embodiment of the safety brake, which is operable as an integrated holding and catch brake.
  • the safety brake according to Fig. 8 differs from the safety brake according to Fig. 6 through some additional components that add extra functionality.
  • the safety brake includes in addition to the already associated with Fig. 6 described piston 22a another piston 55a, which is in the master cylinder 20 with the pressure medium in interaction and is arranged on a movable piston rod 55 in its longitudinal direction.
  • the the master cylinder 20 remote from the end of the piston rod 55 is connected via a spring 60 with a (in Fig. 8 connected by a vertical line), wherein the spring 60 is biased such that the spring 60 acts on the piston rod 55 with a force F3, which is directed along the piston rod 55 in the direction of the master cylinder 20.
  • the safety brake according to Fig. 8 has with the springs 27 and 60 thus two means for generating a force which can be used independently to increase the pressure in the pressure medium volume and thus to produce a force acting on one of the brake elements 19 braking force.
  • a partial region of the pressure medium volume is delimited by means of a chamber 50 in the environment of the piston 22a.
  • the chamber 50 has an opening 50a which can be opened or tightly closed by means of an electromagnetically actuatable valve 51.
  • the valve 51 comprises a closing flap 53 and an electromagnet 52 interacting electromagnetically with the closing flap 53 for opening or closing the opening 50a.
  • an electromagnetic advancing device 65 is provided which, as in FIG Fig. 8 indicated by an arrow - is in communication with the control device 12.
  • the electromagnetic propulsion device 65 includes, inter alia, an electromagnet 65 which acts electromagnetically on the piston rod 55 to exert on this a force F4, which counteracts the force F3. If necessary, the electromagnet 65 can be supplied with power to compensate for the effect of the force F3 in whole or in part.
  • a two-armed blocking lever 70 is provided which is rotatably mounted about a pivot point 71.
  • One end of the blocking lever 70 is coupled to a spring 82 which is held stationary at the end remote from the blocking lever 70 (by means not shown).
  • the blocking lever 70 can be pivoted about the pivot point 71 with the aid of an electromagnet 81 over an angular range between two stable extreme positions.
  • Fig. 8 One of these extreme locations is in Fig. 8 is shown and is taken when the solenoid 81 is supplied with a predetermined minimum amount of power. Under this condition, the blocking lever 70 is deflected such that one of its ends engages in a groove 69 on the blocking lever 70, wherein the blocking lever 55 is arranged so that the piston rod 55 is fixed in a stable position despite the action of force F3. The force F3 is then absorbed by the blocking lever 70 or its bearing.
  • the safety brake according to Fig. 8 can be operated as a holding brake and as a safety brake as follows.
  • the Fig. 8 shows the safety brake in a characteristic of the operation as a holding brake state: the opening 50a is open; the solenoid 81 is energized and thus the piston rod 55 is locked in a stable position.
  • the piston 55a is immobile and without influence on the pressure in the pressure medium.
  • the electromagnet 66 can be de-energized because the forces F4 and F3 are without influence on the size of the braking forces acting on the brake elements 19.
  • the pressure in the pressure medium volume - controlled by the control device 12 - can be controlled with the piston 22a in response to the forces F1 and F2. Accordingly, the operation of the safety brake in this state corresponds to the operation of the in Fig. 6 illustrated safety brake.
  • valve 51 closes the opening 50a and the braking forces acting on the brake elements 19 are determined by the magnitude of the force F3, if the electromagnet 66 is de-energized, or the magnitude of the forces F3 and F4, if the electromagnet 66 of a Electricity is flowing through.
  • the safety brake according to Fig. 8 could also be operated without the locking lever as an integrated holding and catch brake. However, then the size of the force F4 would have to be regulated accordingly to partially compensate for the force F3 in operation as a holding brake. This mode of operation is less efficient in terms of efficiency, since the electromagnet 66 would have to be constantly powered, although during operation of an elevator relatively rarely occur situations that require the operation of the safety brake.
  • the operation of the blocking lever 70 can be very efficient, since the two arms of the Blocking lever 70 can be dimensioned so that an exerted by the solenoid 81 on an arm of the blocking lever 70 force is amplified by any factor.
  • the propulsion device 65 can also be dispensed with.
  • the safety brake could still be used as a safety brake, the resetting of the safety brake in the operation as a holding brake can also be made by the intervention of service personnel.
  • the safety brake according to Fig. 8 is designed so that it is automatically switched to the operation as a safety brake in the event of a general power failure. In this case, the piston rod 55 would no longer be blocked by the blocking lever 70 and the solenoid 66 de-energized, ie F4 equal to zero.
  • the pressure medium lines can also respond in each case only one braking device.
  • the springs need not be biased to pressure. You could also be biased on train. In the latter case, their support to stationary or movable parts of the safety brake would have to be suitably modified differently from the illustrated examples.
  • Fig. 6 the pressure medium lines 11a and 11b are shown in dashed lines in pieces, to indicate that these lines can be performed along any routes.
  • Fig. 6 Further developed device to a more compact form, it would also be conceivable to one to dispense with spatial separation between the master cylinder 20 and the brake device 7. Such a configuration could be realized without special pressure medium lines between the master cylinder 20 and the brake cylinders 16a and 16b.
  • the master brake cylinder 20 and the brake device 7 are connected to a particularly compact unit when the pressure medium volume between the piston 18 and the piston 22a and 55a is designed so that it does not form a plurality of separate, interconnected only through openings chambers is divided. In this way, it is possible to form the safety brake so compact that all components of the safety brake including the pressure means device 10 can be arranged on the elevator car 3, if necessary even directly next to the brake elements 19, 19a.
  • the control device 12 can be integrated into the control of the elevator installation and be arranged stationary at a suitable place in the elevator installation. But it is also possible to realize the functions of the control device 12 by means of a separate device which is arranged on the elevator car. It is conceivable, for example, to form the control device 12 as an electronic circuit fixed to the car. This circuit may have a communication link to the elevator control, for example, to send and / or receive control signals and / or send and / or receive status information regarding the elevator installation and / or the safety brake.
  • safety brake springs and electromagnets could of course be replaced by other means of generating a force.
  • these means should be controllable to allow the operation or release of the safety brake at predetermined times and, if necessary, to adapt the size of the force to be generated to the respective requirements.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Claims (18)

  1. Frein de sécurité pour installations d'ascenseur, avec un dispositif de freinage (7) qui comprend un ou plusieurs éléments de freinage (19) mobiles et aptes à être sollicités chacun par une force de freinage, avec un piston mobile (22a, 55a), avec un dispositif pour actionner et/ou desserrer le dispositif de freinage (7) à l'aide d'au moins une force (F1, F2, F3, F4) qui agit sur le piston (22a, 55a) et qui est apte à être transmise aux éléments de freinage (19) à l'aide d'un agent de pression dans un volume d'agent de pression (20, 17, 11a, 11b) entre les éléments de freinage (19) et le piston (22a, 55a), pour produire la force de freinage, le dispositif comprenant également :
    - des moyens (27, 40, 60) pour produire une première force (F1, F3) qui agit sur le piston (22a, 55a), en vue d'actionner le dispositif de freinage (7), et
    - des moyens (23, 65) pour produire une deuxième force (F2, F4) qui agit sur le piston (22a, 55a) et qui agit à l'encontre de la première force (F1, F3).
  2. Frein de sécurité selon la revendication 1, caractérisé en ce que le piston (22a, 55a) est conçu de telle sorte que la force de freinage soit plus grande que la force (F1, F3) qui agit sur le piston.
  3. Frein de sécurité selon l'une des revendications 1 ou 2, caractérisé en ce que la valeur de la deuxième force (F2, F4) est variable, et il est prévu des moyens (12) pour le contrôle de la valeur de la deuxième force.
  4. Frein de sécurité selon l'une des revendications 1 à 3, caractérisé en ce que le moyen pour produire la première force (F1, F3) est conçu de telle sorte que la valeur de la première force soit variable de manière commandée.
  5. Frein de sécurité selon l'une des revendications 1 à 3, caractérisé en ce que le dispositif comprend un moyen (40) pour produire une troisième force (F3) qui agit en plus de la première force (F1) sur le piston (22a, 55a).
  6. Frein de sécurité selon la revendication 5, caractérisé en ce qu'il est prévu des moyens aptes à être commandés (41, 45, 49) pour réaliser ou supprimer une liaison mécanique entre le moyen (40) pour produire la troisième force (F3) et le piston (22a), afin de commander une action de la troisième force (F3) sur ledit piston (22a).
  7. Frein de sécurité selon l'une des revendications 1 à 3, caractérisé en ce qu'il est prévu un deuxième piston mobile (55a) et un moyen (60) pour produire une troisième force (F3) qui agit sur le deuxième piston (55a), le deuxième piston (55a) étant relié au volume d'agent de pression (20, 17, 11a, 11b), et la troisième force (F3) étant apte à être transmise par l'intermédiaire de l'agent de pression aux éléments de freinage (19) afin d'actionner le dispositif de freinage (7).
  8. Frein de sécurité selon la revendication 7, caractérisé en ce qu'il est prévu un moyen (65) pour produire une quatrième force (F4) qui agit sur le deuxième piston (55a) et qui est dirigée de manière à agir à l'encontre de la troisième force (F3).
  9. Frein de sécurité selon l'une des revendications 7 ou 8, caractérisé en ce qu'il est prévu des moyens de blocage (69, 70) pour bloquer le deuxième piston (55a) pendant une durée apte à être contrôlée par des signaux de commande (12).
  10. Frein de sécurité selon l'une des revendications 7 à 9, caractérisé en ce que le premier piston (22a) est apte à être séparé, à l'aide d'une soupape (51), de l'agent de pression qui agit sur les éléments de freinage (19), la pression de l'agent de pression étant apte à être influencée avec le deuxième piston (55a).
  11. Frein de sécurité selon l'une des revendications 7 à 10, caractérisé en ce que le dispositif de freinage (7) est apte à être actionné par l'action de l'un des pistons (22a, 55a), sélectivement, les deux pistons étant conçus de telle sorte que la force de freinage adopte des valeurs différentes, respectivement.
  12. Frein de sécurité selon l'une des revendications 1 à 11, caractérisé en ce que le moyen (27) pour produire la première force (F1) comporte un ressort (27, 40, 60) ou un accumulateur d'énergie d'un autre type, et/ou le moyen (23) pour produire la deuxième force (F2) comprend un électro-aimant (25).
  13. Frein de sécurité selon l'une des revendications 5 à 11, caractérisé en ce que le moyen pour produire la troisième force (F3) comporte un ressort apte à être précontraint (40, 60) ou un accumulateur d'énergie d'un autre type.
  14. Frein de sécurité selon la revendication 13, caractérisé en ce que le ressort (40, 60) est apte à être maintenu dans un état tendu sans agir sur le piston (22a, 55a) ou déplacer celui-ci, et en ce que le ressort (40, 60) est apte à être détendu de manière commandée afin de déplacer ledit piston (22a, 55a) et de produire la force de freinage.
  15. Frein de sécurité selon la revendication 14, caractérisé en ce que le ressort (40, 60) est apte à être maintenu avec des moyens mécaniques (45, 70) dans l'état tendu.
  16. Frein de sécurité selon l'une des revendications 1 à 15, caractérisé en ce que le piston (22a) est relié à l'agent de pression qui se trouve à l'intérieur d'un maître-cylindre de frein (20), et ledit maître-cylindre de frein est relié par l'intermédiaire d'au moins une conduite d'agent de pression (11a, 11b) au dispositif de freinage (7).
  17. Installation d'ascenseur avec un frein de sécurité selon l'une des revendications 1 à 16, caractérisée en ce que le dispositif de freinage (7) est disposé de telle sorte que les éléments de freinage (19), lors d'un actionnement du dispositif de freinage (7), soient aptes à venir en contact avec un rail de guidage (2) d'une cabine d'ascenseur (3) ou en contact avec un disque de frein (15) d'un entraînement d'ascenseur (13).
  18. Installation d'ascenseur selon la revendication 17, caractérisée en ce que le frein de sécurité est conçu comme un frein d'arrêt et de blocage intégré.
EP02027158.1A 2001-12-24 2002-12-05 Frein de securité pour système d'ascenceur Expired - Lifetime EP1323660B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP02027158.1A EP1323660B1 (fr) 2001-12-24 2002-12-05 Frein de securité pour système d'ascenceur

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP01811270 2001-12-24
EP01811270 2001-12-24
EP02027158.1A EP1323660B1 (fr) 2001-12-24 2002-12-05 Frein de securité pour système d'ascenceur

Publications (2)

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EP1323660A1 EP1323660A1 (fr) 2003-07-02
EP1323660B1 true EP1323660B1 (fr) 2017-01-04

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FI118850B (fi) 2003-11-24 2008-04-15 Kone Corp Hissi ja menetelmä hissikorin lukitsemiseksi
JP4890246B2 (ja) * 2004-05-20 2012-03-07 三菱電機株式会社 エレベータの非常止め装置
EP2070860A1 (fr) * 2007-12-11 2009-06-17 Inventio Ag Système d'ascenseur doté de cabines d'ascenseur mobiles verticalement et horizontalement
DE102011000720A1 (de) * 2011-02-14 2012-08-16 Klaus-Peter Kapp Reibungsbremse für Aufzüge mit verbesserten Dämpfungseigenschaften
US9663327B2 (en) 2011-03-22 2017-05-30 Otis Elevator Company Elevator braking system
JP5761742B2 (ja) 2011-03-31 2015-08-12 Ｎｅｃエナジーデバイス株式会社 電池パック
DE102014206461A1 (de) 2014-04-03 2015-10-08 Thyssen Krupp Elevator Ag Aufzug mit einer Bremsvorrichtung
WO2015177228A1 (fr) * 2014-05-20 2015-11-26 Wittur Holding Gmbh Unité de frein de cabine d'ascenseur hydraulique avec puissance de freinage pouvant être commandée
DE202014103702U1 (de) * 2014-05-20 2015-08-26 Wittur Holding Gmbh Sicherheitseinrichtung zum Betrieb eines Aufzugs
US20170291794A1 (en) * 2014-09-24 2017-10-12 Inventio Ag Elevator brake
EP3587324A1 (fr) * 2018-06-22 2020-01-01 Otis Elevator Company Système d'ascenseur
US11203510B2 (en) * 2018-07-31 2021-12-21 Otis Elevator Company Electrohydraulic damper for elevator system
PL4313831T3 (pl) 2021-03-31 2025-06-23 Inventio Ag Układ hamulcowy windy
CN114084771B (zh) * 2021-11-25 2023-06-09 菱王电梯有限公司 电梯导轨制动装置和电梯

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GB9004643D0 (en) * 1990-03-01 1990-04-25 Alphatrad Sa Braking apparatus
CA2072187C (fr) * 1992-06-23 1996-09-03 Dermot Camack Systeme de freinage de secours pour treuil
ATE175946T1 (de) * 1993-10-18 1999-02-15 Inventio Ag Bremssicherheitseinrichtung für eine aufzugskabine
US6193026B1 (en) * 1997-12-22 2001-02-27 Otis Elevator Company Elevator brake
US6105738A (en) * 1998-02-12 2000-08-22 Inventio Ag Elevator brake

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