EP0899231B1 - Dispositif de freinage à double action - Google Patents

Dispositif de freinage à double action Download PDF

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Publication number
EP0899231B1
EP0899231B1 EP19980114970 EP98114970A EP0899231B1 EP 0899231 B1 EP0899231 B1 EP 0899231B1 EP 19980114970 EP19980114970 EP 19980114970 EP 98114970 A EP98114970 A EP 98114970A EP 0899231 B1 EP0899231 B1 EP 0899231B1
Authority
EP
European Patent Office
Prior art keywords
guide rail
braking
disc
safety brake
brake shoe
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP19980114970
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German (de)
English (en)
Other versions
EP0899231A1 (fr
Inventor
Gerhard Schlosser
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.)
Aufzugstechnologie Schlosser GmbH
Original Assignee
Aufzugstechnologie Schlosser GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by Aufzugstechnologie Schlosser GmbH filed Critical Aufzugstechnologie Schlosser GmbH
Priority to EP19980114970 priority Critical patent/EP0899231B1/fr
Publication of EP0899231A1 publication Critical patent/EP0899231A1/fr
Application granted granted Critical
Publication of EP0899231B1 publication Critical patent/EP0899231B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • B66B5/20—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 by means of rotatable eccentrically-mounted members

Definitions

  • the present invention relates to a brake safety device for Elevators, consisting of one, one guide rail each for encompassing an elevator car, in the transverse direction to the Guide rail arranged console, on which there are two to Brake shoes arranged on both sides of the guide rail support, of which one as a passive brake shoe and the other than active brake shoe works, the active Brake shoe is supported by a work eccentric and the Work cam is rotatably connected to a rolling disc, and the rolling disc and the work eccentric around a common Center are rotatable.
  • a safety gear of the aforementioned type is known from DE 21 39 056 known.
  • This safety gear is blocked by the Limiter rope actuates a release lever on the safety gear, which the clamping eccentric connected to the bearing eccentric in Rotation, whereupon the clamping eccentric in contact with the Guide rail comes. That has because of the still moving Elevator cabin result that the clamping eccentric through the Frictional contact with the guide rail automatically continues to rotate and the active brake shoe through the bearing eccentric to the braking position is moved.
  • the bearing cam In the braking position, the bearing cam has the End position before the greatest deflection towards the guide rail achieved because of the shape of the outer contour of the clamping eccentric in this position its frictional contact with the guide rail reduced or lost so that it is no longer rotated.
  • Another safety device that works with an eccentric is the BFx3 safety brake from East German elevator construction (lift report, issue 5, 1991).
  • This safety gear two are triggered Cam discs with rolling and sliding surfaces depending on the direction of travel of the elevator turned left or right and is a strong one in the downward direction and in the upward direction a weaker braking deceleration of the elevator car generated. It is triggered by a from the governor rope wrapped separate role, which in turn has a Roll-off transmission, depending on the direction of travel, one or the other Direction of rotation of the eccentric determined.
  • braking in the Upward travel direction is the roll angle and the radius Sliding surface in the braking position is smaller than when braking in the downward direction of travel. This results in the different deflections of the brake springs and accordingly the desired different braking forces for the two Driving directions.
  • the brake safety device has a simple one Setup is inexpensive to manufacture and easy to assemble.
  • the invention is characterized inter alia by from the fact that after the Engaging the safety gear still existing frictional contact Rolling disc with the guide rail an easy release of the Safety gear allows.
  • the passive brake shoe is able to provide a vertical free travel braking and pulling out of the catch. The facilitates pulling out of the catch by an initial one Reduction of friction.
  • angles alpha and beta between the zero point of the next to the track of a rolling disc in the Standby position and the top dead center of the work eccentric, or the smaller ones dependent on these two angles Determine the working angle up to the braking position together with the Shape of the rolling contour of the rolling disc the ratio of Braking forces in downward direction and upward direction.
  • the rolling disc can also be used for certain applications have a circular outer contour, with or without a flat spot, which simplifies and cheapens their manufacture.
  • the circular contour of the rolling disc results for both Driving directions the same curve when rolling on the Guide rail, which is why only the roll angle up to Braking position (working angle) and partly the angular position between rolling disc and work eccentric for that Determining the braking force ratio between the two directions of travel is.
  • the rolling disc and the work eccentric can be inexpensive to manufacture be carried out as a one-piece part.
  • the rolling disc and the work eccentric can be used as separate and mutually adjustable parts are executed, with which then hereby certain force parameters, or the onset of Braking effect can be influenced.
  • the end position of the safety gear, or the rolling disc at Braking becomes impact-free thanks to a natural adjustment Balance of the contact pressure of the active brake shoe and Rolling disc determined.
  • FIG. 1 denotes a console, on the left outside an abutment 3 and on the right side a bearing journal 2 are inextricably linked to it.
  • An actuating element 21 can be rotated via a slide bearing bush 23 arranged.
  • the actuating element 21 consists of a larger one Rolling disc 4 and a smaller one, with the rolling disc 4 non-rotatably connected work eccentric 5.
  • work eccentric 5 itself consists of two eccentric discs, which are on both sides of the Rolling disc 4 are arranged in the same position to each other.
  • the rolling disc 4 has a flat point, whose center is designated as zero point 4.1 and which in the Ready position parallel to the sliding surface of a Guide rail 8 stands, and a rolling contour 4.2, the shape controls the braking force.
  • the flat spot is here essential part of the shape of the rolling contour 4.2, because with it a accelerated application of the braking effect after triggering the Safety gear is reached.
  • a rolling disc 4 without Flat point is the zero point 4.1 of the guide rail 8 on next lying point on the circumference of the rolling disc 4 in the Ready position of the safety gear.
  • At the Working eccentric 5 is the greatest distance from the center 12 of the Bearing pin 2 referred to as top dead center 5.1.
  • the zero point 4.1 of the rolling disc 4 and the top dead center 5.1 of the Work eccentrics are at an angle to each other alpha.
  • An active brake shoe 6 is pivotable with the bracket 13 with the Work eccentric 5 connected, with an arcuate Recess on the right side of the active brake shoe 6 on the circular outer surface of the work eccentric 5 can slide.
  • the Active brake shoe 6 has a longitudinal slot for a central one Penetration of the rolling disc 4 by the active brake shoe 6.
  • the passive brake shoe 7 On the left side of the guide rail 8 is to this spaced, the passive brake shoe 7 arranged.
  • As vertical Stops serve a stop jaw 14 at the top and bottom vertical play distance 15 between the end faces of the Passive brake shoe 7 and the inner stop surfaces of the Stop jaws 14 is an important measure and also serves easier release of the safety gear after braking.
  • the passive brake shoe 7 is connected to two guide bolts 10, which are guided in the abutment 3. Compression springs 9 and one not Shown adjustment mechanism for the spring preload on the Guide bolts 10 hold the passive brake shoe 7 in the Ready position and generate the braking force when triggered Safety gear.
  • the brake safety device is in the Ready position shown.
  • the active brake shoe 7, the Passive brake shoe 6 and the rolling disc 4 are not in engagement with the guide rail 8.
  • the dimensions a and b are the distances between the Passive brake shoe 6 and the flat point with the zero point 4.1 Rolling disc 4 to the guide rail 8.
  • the dimension c is the current distance between the geometric center 11 of the Working eccentric and the center 12 of the journal 2.
  • Fig. 3 the safety gear is in the engagement position shown.
  • a trigger device not shown, has that Actuator 21 rotated slightly to the left, whereupon the Rolling disc 4, or its knurled rolling contour 4.2 with the Guide rail 8 frictionally connected and rolling on the guide rail 8, from the elevator still moving is rotated. It will then be the entire safety gear pulled to the left and the passive brake shoe 7 comes through Cancellation of the passage game, in contact with the Guide rail 8.
  • the active brake shoe 6 still has one Distance b to the guide rail 8 and is on the braking not yet involved.
  • the normal force of the The braking device hereby has the defined final value for a Downward braking achieved.
  • the preload and characteristics of the compression springs 9 are the preload and characteristics of the compression springs 9, the Course of the rolling contour 4.2 of the rolling disc 4 and the angle Alpha between the zero point 4.1 on the rolling disc 4 and the top dead center 5.1 of the work eccentric 5, or of these Decisive working angles.
  • the actuator 21, or the top dead center 5.1 of the work eccentric 5 remains in an angle of about 30 ° before the point of contact with the Guide rail 8 stand. That means an angle alpha or beta minus these, for example 30 ° result in the previously mentioned Working angle of the rolling disc 4 to the braking position Safety gear.
  • the elevator car which is now in the brake lock, can pass through Pulling the cabin upwards easily released from the catching position be because the rolling disc 4 frictional contact with the Has guide rail 8 for turning back and because of Passive brake shoe 7 with its upper end face on the upper Stop jaw 14 abuts.
  • the double play distance 15 is available, see above that the passive brake shoe 7 when pulling up the elevator car during this distance does not slow down what the pulling out of the Catch by rolling in the release direction of the rolling disc 4 on the Guide rail 8 facilitated.
  • Figure 5 is comparable to Figure 2 and shows the same Ready position of the safety gear. It will now assumed that the elevator car goes up and one Catch braking is imminent. It is under with this upward braking the angle beta between points 4.1 and 5.1, or the working angle dependent on this angle (e.g. Beta-30 °) for the Decisive braking force.
  • the Roll disc 4 sets in the upward direction up to Force balance with the active brake shoe 6 another Angular path back than in the downward direction.
  • the sum of the horizontal extensions of the radii of the working eccentric 5 and the rolling disc 4 are smaller in this position than in the Downward direction of travel, so that there is also a smaller deflection of the compression springs 9 for the desired smaller braking forces in the Upward direction of travel results.
  • the actuator 21, or the top dead center 5.1 of the work eccentric 5 remains with this exemplary representation at an angle of about 60 ° in front of the Stand in contact with the guide rail 8.
  • the geometric center 11 of the Working eccentric 5 is horizontally by the amount e-x and vertically by shifted the amount e-y to the center 12 of the journal 2.
  • On the left side are on a circular arc with the radius r out the center 12 of the bearing pin 12 has two threaded holes 19 and 20 arranged. These are used to attach a not shown Triggering device.
  • the rolling contour 4.2 of the rolling disc 4 is in this example a calculated, asymmetrical control curve with a flat spot with the center point 4.1. It can be for certain Use cases also a circular rolling contour 4.2 with or can be provided without a flat spot. It can also be seen that the work eccentric 5 with the center 11 a circular Has outer contour with the circular diameter d.
  • the cross section of the actuating element 21 in FIG. 9 shows its one-piece design.
  • FIG. 10 shows this as a further variant Actuator 21 in multi-part and adjustable Execution.
  • Fig. 10 there is a dashed line circular arc-shaped slot 16 shown in the rolling disc 4, which extend over an angle between 30 ° to 60 ° can.
  • a coupling pin 17 With a coupling pin 17, the two parts of the Work eccentric 5 connected so that they always the assume the same position to each other, or only synchronously with each other are angularly displaceable relative to the rolling disc 4.
  • By rotating displacement of the work eccentric 5 relative to the The rolling disc 4 can be in the region of the arcuate slot 16 any angular position can be set.
  • a Tensioning screw 18 can be a set angular position of the Work eccentric can be fixed relative to the rolling disc 4.
  • FIG 11 shows in cross section the clamping screw 18 and the circular slot 16.
  • the one used Plain bearing bush 23 between the journal 2 and the bearing bore the actuator 21 therefore has the task of Bearing friction as low as possible at high specific bearing pressures to keep.
  • the plain bearing bush 23 preferably consists of a special maintenance-free sintered material, which is under high specific pressure still remains smooth. The Use of a plain bearing bush 23 replaces the use of a Needle bearing and takes up less space.
  • the plain bearing bush 23 can, with suitable material pairing, e.g. Different types of steel and degrees of hardness, when using special ones Lubricants and for smaller loads are omitted.
  • the material for the actuating element 21, 22 is preferred a steel grade suitable for hardening is used.
  • the whole safety gear is in a known manner from the Cabin support structure held so that when engaged the safety gear necessary for centering the same to the guide rail 8 is made possible.
  • the inventive Brake safety device On a displaceable mounting of the inventive Brake safety device can be dispensed with in those cases where the Guide devices a vibration-damping connection with the Have cabin construction and thereby a side Push away a few millimeters.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Maintenance And Inspection Apparatuses For Elevators (AREA)

Claims (8)

  1. Parachute à frein pour ascenseurs, composé d'une console (1), qui entoure à chaque fois une barre de guidage (8) pour une cabine d'ascenseur et qui est disposée transversalement à la barre de guidage (8), console sur laquelle prennent appui deux mâchoires de frein (6, 7) disposées des deux côtés de la barre de guidage (8) dont l'une travaille en tant que mâchoire passive (7) et l'autre en tant que mâchoire active (6), la mâchoire active (6) prenant appui par l'intermédiaire d'un excentrique de travail (5), et l'excentrique de travail (5) étant relié solidairement en rotation à un disque roulant (4), le disque roulant (4) et l'excentrique de travail (5) pouvant tourner autour d'un centre commun (12).
       caractérisé en ce que le parachute à frein peut être déclenché dans les deux sens de marche grâce au fait que le disque roulant (4) peut être entraíné en rotation aussi bien dans le sens des aiguilles d'une montre que dans le sens inverse et en ce qu'après l'exécution du freinage, le disque roulant (4) reste en contact avec la barre de guidage (8) correspondante, pour permettre de faire tourner le disque roulant (4) en sens inverse et, par ce moyen, de relâcher le parachute engagé en dégageant la cabine d'ascenseur de la prise.
  2. Parachute à frein selon la revendication 1,
       caractérisé en ce que,
       dans la monture de la mâchoire de frein passive (7), il est prévu un jeu vertical (15) entre la mâchoire de butée et les côtés frontaux de la mâchoire de frein passive (7), de sorte que, lors du relâchement du parachute, la mâchoire de frein passive (7) est entraínée initialement sans frottement dans le sens du relâchement.
  3. Parachute à frein selon la revendication 1,
       caractérisé en ce que
       le rapport entre les forces de freinage dans le sens de freinage ascendant et dans le sens de freinage descendant est essentiellement déterminé par les angles alpha et bêta entre le point mort haut (5.1) de l'excentrique de travail (5) et le point zéro (4.1) de la zone du disque roulant (4) qui est la plus proche de la barre dans la position de veille ou, respectivement, par les angles de travail ou de roulement aboutissant à la position de freinage, qui sont fonction des angles alpha et bêta.
  4. Parachute à frein selon la revendication 1,
       caractérisé en ce que
       le profil de roulement (4.2) du disque roulant (4) présente, pour commander un effet de freinage entrant en jeu rapidement, un méplat qui est dirigé vers la barre de guidage (8) correspondante dans la position de veille.
  5. Parachute à frein selon la revendication 3,
       caractérisé en ce que
       le disque roulant (4) présente qu' un profil de roulement (4.2) circulaire.
  6. Parachute à frein selon la revendication 1,
       caractérisé en ce que
       le disque roulant (4) et l'excentrique de travail (5) sont réalisés sous la forme d'un élément d'actionnement (21) en une seule pièce.
  7. Parachute à frein selon la revendication 1,
       caractérisé en ce que
       un élément d'actionnement (22) est réalisé en plusieurs pièces.
  8. Parachute à frein selon la revendication 1,
       caractérisé en ce que
       l'élément d'actionnement (22) en plusieurs pièces présente un dispositif (16, 17, 18) pour faire varier la position angulaire entre l'excentrique de travail (5) et le disque roulant (4) par une translation circulaire de l'excentrique de travail (5) par rapport au disque roulant (4).
EP19980114970 1997-08-21 1998-08-10 Dispositif de freinage à double action Expired - Lifetime EP0899231B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP19980114970 EP0899231B1 (fr) 1997-08-21 1998-08-10 Dispositif de freinage à double action

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP97810588 1997-08-21
EP97810588 1997-08-21
EP19980114970 EP0899231B1 (fr) 1997-08-21 1998-08-10 Dispositif de freinage à double action

Publications (2)

Publication Number Publication Date
EP0899231A1 EP0899231A1 (fr) 1999-03-03
EP0899231B1 true EP0899231B1 (fr) 2002-10-23

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EP19980114970 Expired - Lifetime EP0899231B1 (fr) 1997-08-21 1998-08-10 Dispositif de freinage à double action

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104203791A (zh) * 2012-03-20 2014-12-10 因温特奥股份公司 电梯设备中的防坠装置
US9714157B2 (en) 2012-05-24 2017-07-25 Inventio Ag Damping unit for an elevator

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE59806027D1 (de) * 1997-08-21 2002-11-28 Aufzugstechnologie Schlosser G Bremsfangvorrichtung
KR100370747B1 (ko) * 2000-09-09 2003-02-06 (주)동광사우 엘리베이터용 비상 제동 장치
JP2015517447A (ja) 2012-05-24 2015-06-22 インベンテイオ・アクテイエンゲゼルシヤフトＩｎｖｅｎｔｉｏ Ａｋｔｉｅｎｇｅｓｅｌｌｓｃｈａｆｔ エレベータ用緩衝ユニット
EP2883826B1 (fr) * 2013-12-16 2018-07-04 Inventio AG Frein d'ascenseur
CN107720478A (zh) * 2017-09-19 2018-02-23 西继迅达（许昌）电梯有限公司 一种电梯紧急制动装置
CN107416638A (zh) * 2017-09-19 2017-12-01 西继迅达（许昌）电梯有限公司 一种电梯制动安全钳
CN107651528A (zh) * 2017-09-19 2018-02-02 西继迅达（许昌）电梯有限公司 一种电梯轿厢制动装置
CN109292698A (zh) * 2018-11-15 2019-02-01 无锡星亿智能环保装备股份有限公司 一种组合式浮动刹车保险装置
RU2718706C1 (ru) * 2019-11-07 2020-04-14 Акционерное общество "Щербинский Лифтостроительный Завод" Ловитель
CN115092789B (zh) * 2022-08-25 2022-11-11 河南起升智能科技有限公司 防意外移动装置、防意外移动组件和电梯

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE805782C (de) * 1949-05-27 1951-05-31 Gustav Hahn Dipl Ing Bremsfangvorrichtung fuer Aufzuege
DE19606861C2 (de) * 1996-02-23 1999-02-04 Gerhard Schlosser Bremsfangvorrichtung für Aufzüge

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104203791A (zh) * 2012-03-20 2014-12-10 因温特奥股份公司 电梯设备中的防坠装置
CN104203791B (zh) * 2012-03-20 2016-10-26 因温特奥股份公司 电梯设备中的防坠装置
US9919898B2 (en) 2012-03-20 2018-03-20 Inventio Ag Safety brake device for an elevator installation
US9714157B2 (en) 2012-05-24 2017-07-25 Inventio Ag Damping unit for an elevator

Also Published As

Publication number Publication date
EP0899231A1 (fr) 1999-03-03

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