EP0169202A1 - Dispositif de freinage agissant sur un tambour - Google Patents

Dispositif de freinage agissant sur un tambour

Info

Publication number
EP0169202A1
EP0169202A1 EP19840901444 EP84901444A EP0169202A1 EP 0169202 A1 EP0169202 A1 EP 0169202A1 EP 19840901444 EP19840901444 EP 19840901444 EP 84901444 A EP84901444 A EP 84901444A EP 0169202 A1 EP0169202 A1 EP 0169202A1
Authority
EP
European Patent Office
Prior art keywords
drum
brake
speed
brake body
gear
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.)
Ceased
Application number
EP19840901444
Other languages
German (de)
English (en)
Inventor
Peter Torsten Johan TÖRNQVIST
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.)
CAVOTEC AB
Original Assignee
CAVOTEC AB
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.)
Filing date
Publication date
Application filed by CAVOTEC AB filed Critical CAVOTEC AB
Publication of EP0169202A1 publication Critical patent/EP0169202A1/fr
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D59/00—Self-acting brakes, e.g. coming into operation at a predetermined speed
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
    • B65G13/00—Roller-ways
    • B65G13/075—Braking means

Definitions

  • the present invention relates to a brake device acting directly or indirectly on a drum in order to automatically brake the drum in the event of the drum exceeding a specific speed
  • the said brake device consisting of a gear driven by the drum and gearing up its speed, which gear in its turn is arranged to rotate a pivotably suspended brake body in one end with an inherent weight adapted to the said speed, the said brake body being pretensed for instance by means of a spring or similar device adapted to the said inherent weight and said speed so that at a speed that is lower than the said speed is prevented from braking via direct or indirect contact with the drum and at a speed that is higher than the said speed is unable to prevent the brake body from making direct or indirect contact with the drum and thus braking the drum through the centrifugal force exercised on account of rotation.
  • This prior art type of brake device is used in roller conveyors, among other things, on which the speed of entering goods is to be retarded or braked.
  • Such gears are relatively expensive to produce and also have the inherent disadvantage that the braking weight or weights are placed further from the ends of the drum and thus from the bearing points of the drum, whereby the drum shaft and more specifically its downhang can influence the braking action.
  • the drum shaft and more specifically its downhang can influence the braking action.
  • it is necessary to eliminate the downhang for example by also introducing one or more support bearings for the shaft of the drum. Apart from this a higher torque is also obtained in idling on account of friction between the included parts of the gears, which circumstance negatively influences the ability of the roll to roll easily at low speed.
  • One object of the present invention is to provide in a braking device of the type mentioned in the preamble a significantly improved braking action without it being necessary per se to use further, expensive gears and support bearings and without it being necessary to increase the masses or rotational speeds of the brake weights.
  • This task is solved in the type of brake device mentioned in the preamble in that the braking action generated by the rotating weight directly or indirectly against the drum in accordance with the present invention is utilized in principle also to generate or trigger an additional braking force as defined in closer detail in the accompanying main claim.
  • This generation or triggering of an additional braking force can be carried out by various means, for example by generating in accordance with the accompanying claim 2 an additional braking force on the actual brake weight apart from the braking force that is due to the influence of centrifugal force on the brake weight or by using according to the accompanying claims 4 and 5 separate brake devices, the braking action of which is triggered by the braking action of the brake weights.
  • Fig. 1 shows a cross-section through a brake device for a roller conveyor
  • Fig. 2 shows a cross-section through the brake device according to Fig. 1 but with only certain parts drawn for the sake of clarity
  • Fig. 3 shows a cross-section through a brake device with a different design. It should be noted that the same referens numerals are used throughout in the figures for equivalent parts.
  • a seat 22 is fixed in the stationary shaft and comprises a seat for, say, three shafts which rotatably support toothed rollers 9, 10, 11 mounted on the said shafts, the teeth of which rollers interact with the inner teeth of the intermediate part 19.
  • the said three toothed rollers 9, 10, 11 are preferably symmetrically disposed around the stationary shaft 2.
  • a second body 16 is rotatably mounted on the stationary shaft 2 and is driven via teeth 12 by the teeth rollers 9, 10, 11.
  • the second body 16 on account of the selected gear ratio rotates at a significantly higher speed than the drum 1 does in itself.
  • the other body 2 is in the vicinity of its periphery fitted with a bearing trunnion en which a roller 13 is rotatably disposed.
  • This roller 13 is in turn arranged to drive and thus to rotate a brake body 4 around the stationary shaft 2 through contact against the brake body 4, preferably close to its other end 14.
  • the brake body 4 is also rotatably suspended in a bearing journal 15, which is fixed in a first body 3 which in turn is rotatably mounted on the stationary shaft 2.
  • the brake body 4 is pretensed away from the inside of the drum 1 by means of, for example, a spring 5 and is provided on its outer side with a wear and brake lining 7.
  • This wear lining 7 is preferably sited closer to one end of the brake body 4 than the ohter end 14 of the brake body 4 and has an extent in the direction of rotation of the drum that is significantly shorter than a ⁇ uarter of a revolution.
  • the location of the wear lining 7 on the outer surface of the brake body 4 and the extent of the wear lining 7, and the choice of the material in the wear lining 7, must be made with great care.
  • the inherent weight of the brake body 4 and the tensile force of the spring 5 must be selected so that braking occurs at the intended speed of the drum 1.
  • brake bodies 4a can be driven by one or a plurality of drive members 13a, indicated in the drawing with broken lines.
  • the brake device according to Fig. 1 and Fig. 2 works in the following manner. Goods with a higher speed than can be accepted by the braking device contact the peripheral surface of the drum 1 and the drum
  • the brake body 4 In that the brake body 4 is forced to rotate with constant contact in its other end 14 with the drive member 13 the latter, upon this initial braking contact with the inner surface of the drum 1, will act as a pushing lever for this initial, braking contact. Since the distance between the point of contact of the drive member 13 with the brake body 4 and the wear lining 7 is selected relatively large, a large lever is attained, whereby the initial braking action accomplished solely on account of the centrifugal force is amplified to a significant degree.
  • FIG. 3 A second embodiment of the invention is shown in Fig. 3.
  • the parts fulfilling the same function as in the embodiment according to Fig. 1 and 2 have been allocated the same reference numerals and are consequently not described further hereinafter.
  • a drive and braking device 18 is wound around this stationary body 7 and may, for example, comprise a relatively soft belt, the said belt 18 being fixed at one end to a pin 23 which in turn is fixed in the second body 16 and in its other end fixed at the pin 15. It should be observed that the brake body 4 and the first body 3 in this embodiment have changed places in comparison with the embodiment according to Fig. 1 and Fig. 2.
  • This second embodiment works in the following manner: the drum 1 is caused to rotate by goods which at a certain motional speed contact the peripheral surface of the drum 1. Via gears 20, 10, 11, 12, 16 the pin 23 is caused to rotate at a higher speed and is accompanied by the belt 18 wound around the stationary body 17, the drive and braking device, which belt 18 slides on the surface of the stationary body 17 and drive the bearing pin 15 which is thereby caused to rotate the first body 3 rotatably mounted on the shaft 2 and the brake body 4.
  • the wear lining 7 of the brake body 4 contacts the inner surface of the drum 1, i.e.
  • the belt 18 tightens around the stationary body 17 and in this way increases the total braking force exerted on the drum 1 significantly.
  • the number of turns the belt 18 is wound around the stationary body 17 and thus the total friction-generating surface can naturally vary within wide limits in order thus to vary the total braking force exerted on the drum 1.
  • the lengths of the opposingly directed bearing pin 15 and the pin 23, viewed in the direction of extension of the shaft 2, are so selected that the mutual displacement of these pins 15 and 23 is limited, they can for example strike against each other, and that the pin 23 and/or 15 also prevents the belt 18 from changing "tracks". There is therefore not risk that the belt 18 will occupy faulty positions on the stationary body 17.
  • the embodiment according to Fig. 3 can be provided with several drive and braking devices 17, 18, if so desired or required and/or a plurality of brake bodies influenced by the centrifugal force.
  • the embodiment according to Fig. 1 and Fig. 2 can obviously be combined in an optional manner with the embodiment according to Fig. 3.

Landscapes

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

Abstract

Dispositif de freinage agissant directement ou indirectement sur un tambour (1) de manière à freiner automatiquement ce tambour en cas de dépassement d'une certaine vitesse du tambour (1). Ce dispositif de freinage comporte un engrenage (9, 10, 11, 12, 16) entraîné par la vitesse du tambour (1) qui l'accélère, engrenage qui lui aussi est conçu pour faire tourner un corps de frein (4) suspendu de manière à pouvoir tourner une extrémité (6) avec un poids inhérent adapté à ladite vitesse. Le corps de frein (4) est prétendu par exemple par un ressort (5) ou autre adapté audit poids inhérent et à ladite vitesse, le ralentissement par contact direct ou indirect avec le tambour (1) étant empêché, à une vitesse inférieure à ladite vitesse et incapable, à une vitesse supérieure à ladite vitesse, d'empêcher le corps de frein (4), par l'intermédiaire de la force centrifuge due à la rotation, d'entrer en contact direct ou indirect avec le tambour (1) et ainsi, de freiner ce dernier. La force d'entraînement que l'engrenage (9, 10, 11, 12) doit appliquer au corps de frein (4) est appliquée au corps de frein (4) via un élément d'actionnement (respectivement 13, 16 et 18) travaillant entre l'engrenage (9-12) et le corps de frein (4), conçu de telle façon que, lorsque le corps de frein (4) entre directement ou indirectement en contact avec le tambour (1), un effet d'asservissement est créé, afin d'augmenter l'action de freinage du corps de frein (4).
EP19840901444 1983-03-16 1984-03-16 Dispositif de freinage agissant sur un tambour Ceased EP0169202A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE8301433A SE437971B (sv) 1983-03-16 1983-03-16 Pa en trumma verkande bromsanordning
SE8301433 1983-03-16

Publications (1)

Publication Number Publication Date
EP0169202A1 true EP0169202A1 (fr) 1986-01-29

Family

ID=20350393

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19840901444 Ceased EP0169202A1 (fr) 1983-03-16 1984-03-16 Dispositif de freinage agissant sur un tambour

Country Status (3)

Country Link
EP (1) EP0169202A1 (fr)
SE (1) SE437971B (fr)
WO (1) WO1984003685A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3890121C2 (de) * 1987-02-20 1996-08-08 Hitachi Construction Machinery Hydraulisches Schnellablaßventil und hydraulischer Fernsteuerungskreis mit einem solchen Schnellablaßventil
GB9423321D0 (en) * 1994-11-18 1995-01-11 Dexion Group Plc A conveyor including a braking device
EP1847485B1 (fr) * 2006-04-21 2009-01-07 Interrroll Holding AG Rouleau avec roue libre et frein
EP2128048A1 (fr) * 2008-05-27 2009-12-02 Werner Langer GmbH & Co. Metall- und Kunststoffverarbeitung Utilisation de tambours de freinage, tambours de freinage et transporteur de rouleaux
TWI381240B (zh) * 2008-06-24 2013-01-01 Aixin Technologies Llc 減速裝置與投影幕捲放機構
DE102010000803A1 (de) * 2010-01-12 2011-07-14 Dürr Systems GmbH, 74321 Vorrichtung mit Rotationselement, insbesondere mit Rolle
KR200470300Y1 (ko) 2011-12-23 2013-12-06 세창엔터프라이즈(주) 속도 자동제어 롤러
DE102014018769B3 (de) * 2014-12-16 2016-03-03 Interroll Holding Ag Rolle mit Innenbaugruppe
RU170875U1 (ru) * 2017-02-17 2017-05-12 федеральное государственное бюджетное образовательное учреждение высшего образования "Московский государственный технический университет имени Н.Э. Баумана (национальный исследовательский университет)" (МГТУ им. Н.Э. Баумана) Ролик тормозной для роликовых гравитационных конвейеров
RU177559U1 (ru) * 2017-04-27 2018-02-28 Закрытое акционерное общество "Инженерно-технический центр "КРОС" Ролик тормозной для роликовых гравитационных конвейеров

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI20284A (fi) * 1939-02-03 1944-10-16 Asea Ab Centrifugalbroms
DE2112894A1 (de) * 1971-03-17 1972-09-28 Anaconda Wire & Cable Co Bremsvorrichtung
US3918561A (en) * 1973-04-02 1975-11-11 Brake Roller Company Conveyor brake roller
DE2717611C3 (de) * 1977-04-20 1979-11-29 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Bremsrolle

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8403685A1 *

Also Published As

Publication number Publication date
SE437971B (sv) 1985-03-25
SE8301433D0 (sv) 1983-03-16
SE8301433L (sv) 1984-09-17
WO1984003685A1 (fr) 1984-09-27

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Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19841114

AK Designated contracting states

Designated state(s): DE FR GB

17Q First examination report despatched

Effective date: 19861009

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN REFUSED

18R Application refused

Effective date: 19880107

RIN1 Information on inventor provided before grant (corrected)

Inventor name: TOERNQVIST, PETER, TORSTEN, JOHAN