EP0195983B1 - Cabestan à tambour unique - Google Patents

Cabestan à tambour unique Download PDF

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Publication number
EP0195983B1
EP0195983B1 EP86103392A EP86103392A EP0195983B1 EP 0195983 B1 EP0195983 B1 EP 0195983B1 EP 86103392 A EP86103392 A EP 86103392A EP 86103392 A EP86103392 A EP 86103392A EP 0195983 B1 EP0195983 B1 EP 0195983B1
Authority
EP
European Patent Office
Prior art keywords
capstan
load
head
cable
windings
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
Application number
EP86103392A
Other languages
German (de)
English (en)
Other versions
EP0195983A1 (fr
Inventor
Peter Bechmann
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to AT86103392T priority Critical patent/ATE39676T1/de
Publication of EP0195983A1 publication Critical patent/EP0195983A1/fr
Application granted granted Critical
Publication of EP0195983B1 publication Critical patent/EP0195983B1/fr
Expired legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/60—Rope, cable, or chain winding mechanisms; Capstans adapted for special purposes
    • B66D1/74—Capstans
    • B66D1/7442—Capstans having a horizontal rotation axis
    • B66D1/7447—Capstans having a horizontal rotation axis driven by motor only

Definitions

  • the invention relates to a single-head capstan winch of the type specified by the preamble of claim 1.
  • the clamping force required in the capstan winch for holding the load rope on the capstan head is generated by means of a synchronously driven clamping disc.
  • the clamping disc has a clamping groove in the transition from two disc parts axially preloaded against each other by compression springs, in which the rope length running from the capstan head is guided over a deflection roller arranged parallel to the axis after a preferably provided deflection, before it is only then forwarded without load to a rope storage device.
  • the deflection roller is always required to generate the necessary frictional connection between the multiple wrapping of the load rope and the jacket of the capstan head if the capstan winch is designed for a higher load transmission.
  • a multi-head capstan winch with a motor-driven capstan head and at least one axially parallel deflection pulley is known, by means of which a load-transmitting frictional engagement between a multiple looping of the load rope and the jacket of the capstan head is also generated. Furthermore, in this capstan winch there are pressure rollers that are biased by springs, each pressing only one turn of the load rope firmly anchored with its two rope ends to the capstan head and to the or each further provided deflection roller for mere guiding purposes.
  • the invention characterized by claims 1 or 2 solves the problem of designing a single-head capstan winch of the type specified in such a way that the clamping force required in the drive of the capstan head to hold the load rope on its jacket is load-dependent and at the same time translated without access to a by a clamping disc arrangement Spring force is provided, a safety factor comparable to that of the multi-head capstan winches for holding a load of the same order of magnitude attached to the load rope should be achievable on the basis of the same motor drive power.
  • the complementary and at the same time rotationally symmetrical design of the contact surface of the or each cable pressure roller for all cable turns complements the envelope surface of the multiple wrapping of the load cable, and the same throughput speed is obtained through the gap which is formed between the capstan head and each cable pressure roller.
  • This same throughput speed of all rope turns prevents any excessive deformation of the load rope, even taking into account the likelihood of axial migration of the multiple wrap, which is always present in such single-head capstan winches, which is typically caused by foreign substances adhering to the load rope and therefore changing its load-transmitting frictional connection with the jacket of the capstan head is caused.
  • the capstan winch shown in the drawing for a mobile embodiment including a drive motor with a power of 4 hp (2.9 kW) and a commercially available planetary gear change load bearing total weight of only about 16 kilograms comprises a support frame 1 welded together from individual carriers, which at its upper End is provided with an abutment formed by an eyelet 2.
  • the lower end of the support frame 1 is formed with two parallel beams 3 and 4, to each of which a guide rail 5 or 6 of a parallel guide provided for the capstan winch is attached.
  • the main beams of the support frame 1 can have a rectangular hollow profile 7.
  • the multiple wrap 28 has an arrangement axially displaced towards the annular flange 22.
  • the two rope lengths 30 and 31 are then functionally interchanged, which again ensures that one rope length 31 then runs onto the larger diameter area 27 so that the other rope length 30 can run from a smaller diameter area.
  • the output shaft 13 of the planetary gear change transmission results in the coupling of a drive motor, not shown in the drawing, to the drive shaft 12 of the drive shaft for the capstan head 15 when a claw coupling 32 provided for a drive connection is engaged.
  • the dog clutch 32 consists of a driver part 33, which is connected in a rotationally fixed manner to the output shaft 13 by means of a wedge 34 and is axially movable in the direction of the double arrow 35.
  • the claw coupling 32 comprises two claws 36 and 37, which can be seen in the illustration in FIG. 1, and which are fastened to the jacket 8 of the capstan head 15 at a distance of 180 degrees from one another by screws 38.
  • two somewhat larger engagement recesses 39 and 40 are formed corresponding to the claws 36 and 37, claws and engagement recesses also having complementary friction surfaces which, as shown in FIG. 2, at an inclination angle 1) obliquely to the axis of rotation 14 of the Capstan head 15 are aligned.
  • the parallel guide formed with the two guide rails 5, 6 of the support frame 1 is oriented at an angle y obliquely to the line of action of the tensile force Si, so that there is a corresponding to the tensile force Si for a guide flange 42 provided on the housing 11 for guidance by these guide rails results in an angular displacement guide in the direction of the double arrow 43.
  • a force component acting in the direction of arrow 44 is thus obtained for the counterforce acting in the direction of arrow 41 to the tensile force S 1 , which force component is therefore subject to the input and output shafts 12 and 13 of the planetary gear change transmission arranged in the axis of rotation 14 of the capstan head 15.
  • the force component acting in the direction of arrow 44 is further divided along two lines of action, which are indicated by arrows 45 and 46 and are spaced apart by more than 90 degrees.
  • the axes of rotation 47 and 48 of two rope pressure rollers 49 are arranged, which are rotatably mounted on the support frame 1 by a welded-on U-shaped support 50.
  • the axes of rotation 47, 48 are aligned at an angle to the axis of rotation 14 of the capstan head 15 such that for a rotationally symmetrical contact surface of the two rope pressure rollers 49, which is complementary to the envelope surface of the multiple loop 28 of the load rope, a frictional contact is simultaneously applied to all windings of the multiple loop 28 results, which are located on the assigned axial partial length of the jacket 8.
  • the force component acting in the direction of the arrow 44 thus becomes a load-dependent clamping force for this frictional engagement of the two rope pressure rollers 49 exerted on all turns of the multiple wrap 28.
  • the different angular orientation results from the different envelopes of the multiple looping of the load rope, respectively. from the different course of the curvature of the jacket 8 of the capstan head formed with the radii of curvature R.
  • the opposite to the direction of arrow 29 direction of rotation of capstan 15 and. its jacket 8 requires disengagement of the dog clutch 32 or alternatively the use of a reversing motor to be switched over for this purpose as the drive motor for the capstan head.
  • the support frame 1 When working with the capstan winch described above, for example in forestry, the support frame 1 is first anchored in place by means of a belt attached to the eyelet 2. Then, with the claw coupling 32 disengaged and the jacket 8 freely rotatable in the opposite direction to the arrow 29, the accruing rope length 30 is pulled with its free end towards the load which is to be brought to the anchorage location of the capstan winch.
  • the running rope length 31 is pulled from a rope storage device, which can either be attached to the support frame 1 to accommodate any desired rope length or is more appropriately separated so that the load rope can also be transported separately from the capstan winch.
  • the capstan head 15 is driven in the arrow direction 29 after the drive motor is switched on, the multiple looping 28 of the load rope without any hindrance to the throughput speed of the individual rope turns during the pulling of the load experiences load-dependent jamming between the rope pressure rollers 49 and the jacket 8.
  • the frictional surfaces which are complementary on the claws 36, 37 and the engagement recesses 39, 40 of the claw clutch 32 prevent the claw clutch from being disengaged for safety reasons.
  • FIG. 2 also shows a braking device 54 for the drive shaft 12 of the planetary gear changing mode, with which a rotation of the casing 8 opposite to the arrow direction 29 when the claw clutch 32 is disengaged can be braked.
  • This braking option then supplements the braking force exerted on the multiple wrap 28 in a load-dependent manner by means of the rope pressure rollers 51, which can be important in individual cases if the capstan winch is not only used for horizontal, but also for inclined and, in extreme cases using a hoist as an example, also vertical movement is used by loads.
  • the above-described single-head capstan winch can transmit a pulling force of up to 1200 kg.
  • the principle of load-dependent influencing of the clamping force exerted on the multiple looping of the load rope can also be applied to the transmission of significantly higher tensile forces.
  • a bearing that can be pivoted relatively to the rope pressure rollers can then be discussed for the capstan head instead of being supported by a sliding guide, but the implementation thereof is more complex.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Tension Adjustment In Filamentary Materials (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)
  • Crystals, And After-Treatments Of Crystals (AREA)
  • Jib Cranes (AREA)
  • Earth Drilling (AREA)
  • Types And Forms Of Lifts (AREA)
  • Storing, Repeated Paying-Out, And Re-Storing Of Elongated Articles (AREA)

Claims (11)

1. Cabestan à tambour unique, à une cloche de cabestan (15) entraînée par moteur et comprenant une chemise polie sous forme de tambour (8) pour l'enroulement multiple (28) d'un câble porteur qui est maintenu, le long d'une section partielle axiale de la chemise, par un effort de serrage contre la force de traction exercée par une charge dans le mécanisme de commande du cabestan, qui est accrochée au brin (30) du câble porteur s'enroulant sur une extrémité axiale de la chemise au diamètre supérieur, et se déroulant, en état non chargé, d'une partie à diamètre inférieur formé entre les deux extrémité axiales de la chemise, caractérisé en ce que ladite cloche de cabestan (15) comprend une glissière de translation (5, 6, 42) orienté à un angle aigu (y) à un bâti de support (1) auquel au moins un galet-presseur de câble (49, 51) est pivotant et pourvu afin d'exercer ledit effort de serrage pour un contact par friction aux tous les tours dudit enroulement multiple (28), ledit galet-presseur de câble comprenant une face de contact à symétrie de révolution et complémentaire à la surface enveloppante dudit enroulement multiple (28).
2. Cabestan à tambour unique, à une cloche de cabestan (15) entraînée par moteur et comprenant une chemise polie sous forme de tambour (8) pour l'enroulement multiple (28) d'un câble porteur qui est maintenu, le long d'une section partielle axiale de la chemise, par un effort de serrage contre la force de traction exercée par une charge dans le mécanisme de commande du cabestan, qui est accrochée au brin (30) du câble porteur s'enroulant sur une extrémité axiale de la chemise au diamètre supérieur, et se déroulant, en état non chargeé, d'une partie à diamêtre inférieur formé entre les deux extrémie axiales de la chemise, caractérisé en ce que ladite cloche de cabestan (15) est pivotant à un bâti de support (1), relativement à au moins un galet-presseur de câble (49, 51) pivotant et pourvu afin d'exercer ledit effort de serrage pour un contact par friction aux tous les tours dudit enroulement multiple (28), ledit galet-presseur de câble comprenant une face de contact à symétrie de révolution et complémentaire à la surface enveloppante dudit enroulement multiple (28) du câble porteur.
3. Cabestan à tambour unique selon la revendication 1 ou 2, caractérisé en ce qu'au bâti de support (1) au moins deux galets-presseurs du câble (49, 51) sont pivotants afin de porter, en alternance selon les deux sens de rotation de ladite cloche de cabestan (15), respecivement aux tous les tours dudit enroulement multiple (28) du câble porteur qui se déplace axialement au changement du sens de rotation.
4. Cabestan à tambour unique selon les revendications 1, 2 ou 3, caractérisé en ce que pour chaque sens de rotation de la cloche de cabestan (15), deux galets-presseurs de câble (49, 51) sont pourvus qui sont séparés l'un de l'autre par 90 degrés d'arc.
5. Cabestan à tambour unique selon la revendication 1, caractérisé en ce que la glissière de translation (5, 6, 42) de ladite cloche de cabestan (15) comprend une butée éventuellement déplaçable, à un bâti de support (1) afin de limiter ledit effort de serrage exercé sur les tours dudit enroulement multiple (28) du câble porteur à une force de serrage maximale admissible.
6. Cabestan à tambour unique selon la revendication 1, caractérisé en ce que ledit bâti de support (1) est joint par soudage des supports individuels (3, 4) auxquels sont montées deux glissières (5, 6) d'un système de glissières parallèles et de coussinet de pivotement (50) pour le ou les galets-presseurs de câble (49, 51), lequel système est pourvu pour un collet de guidage (42) de ladite cloche de cabestan (15).
7. Cabestan à tambour unique selon la revendication 6, caractérisé en ce que ledit bâti de support (1) comprend un oeil (2) pourvu comme butée pour la force de traction, disposée dans le même alignement.
8. Cabestan à tambour unique selon quelconque des revendications 1 à 7, dans lesquel ladite cloche de cabestan (15) est entraînable par l'arbre de sortie (13) accouplable d'un engrenage à changement de vitesses, caractérisé en ce que la chemise (8) de ladite cloche de cabestan (15) est pivotante à un boîtier (11) dudit engrenage à changement de vitesses, à déplacement ou pivotement audit bâti de support (1), en étant accouplable à l'arbre de sortie (13) dudit engrenage par un élément d'entraînement (33) d'un manchon à endentures (32), ledit élément d'entraînement étant relié audit arbre à résistance contre torsion et à flexibilité axiale.
9. Cabestan à tambour unique selon quelconque des revendications 1 à 8, caractérisé en ce qu'un dispositif étrangloir (54) est disposé pour freiner le mouvement rotatif de ladite cloche de cabestan (15) ou de sa chemise (8).
10. Cabestan à tambour unique selon la revendication 8, caractérisé en ce que ledit manchon à endentures (32) est constitué d'au moins deux crabots (36, 37) montés à la chemise (8) de ladite cloche de cabestan (15) et des évidements à engrènement (39, 40) dudit élément d'entraînement (33), qui sont complémentaires auxdits crabots.
11. Cabestan à tambour unique selon la revendication 10, caractérisé en ce que lesdits crabots (36, 37) et les évidements à engrènement (39, 40) sont pourvus des surfaces à friction complémentaires qui s'étendent angulairement, relativement à l'axe de rotation (14) de ladite cloche de cabestan (15).
EP86103392A 1985-03-21 1986-03-13 Cabestan à tambour unique Expired EP0195983B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86103392T ATE39676T1 (de) 1985-03-21 1986-03-13 Einkopf-spillwinde.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3510282 1985-03-21
DE3510282A DE3510282C2 (de) 1985-03-21 1985-03-21 Einkopf-Spillwinde

Publications (2)

Publication Number Publication Date
EP0195983A1 EP0195983A1 (fr) 1986-10-01
EP0195983B1 true EP0195983B1 (fr) 1989-01-04

Family

ID=6265935

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86103392A Expired EP0195983B1 (fr) 1985-03-21 1986-03-13 Cabestan à tambour unique

Country Status (6)

Country Link
US (1) US4666128A (fr)
EP (1) EP0195983B1 (fr)
JP (1) JPS61221093A (fr)
AT (1) ATE39676T1 (fr)
CA (1) CA1234093A (fr)
DE (2) DE3510282C2 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5090666A (en) * 1988-10-13 1992-02-25 May Marvin M Hoist apparatus
US5092646A (en) * 1989-06-20 1992-03-03 Smallridge Bruce B Double capstan winch drive
US5215272A (en) * 1991-01-30 1993-06-01 Sauber Charles J Winding device having a tilting table and method
US5309997A (en) * 1992-10-22 1994-05-10 Shell Oil Company Well fluid for in-situ borehole repair
DE202004013841U1 (de) * 2004-09-06 2006-01-19 Skysails Gmbh & Co. Kg Wasserfahrzeug mit einem drachenartigen Element
US7850146B2 (en) * 2008-06-13 2010-12-14 Production Resource Group, Llc Lineset winch with braking parts

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE375170A (fr) *
US600729A (en) * 1898-03-15 Island
DE639790C (de) * 1934-05-20 1936-12-12 I G Farbenindustrie Akt Ges Winde
US2221903A (en) * 1937-07-31 1940-11-19 Greenlee Bros & Co Cable puller
US2628813A (en) * 1948-12-04 1953-02-17 Philip S Arnold Rope puller
DE872987C (de) * 1951-04-08 1953-04-09 Yale & Towne Mfg Co Hebezeug mit Seil als Lastorgan
GB1035652A (en) * 1962-01-04 1966-07-13 Coal Industry Patents Ltd Rope drums or pulleys
DE6602636U (de) * 1967-12-21 1969-06-12 Pohlig Heckel Bleichert Abseilgeraet
US3608389A (en) * 1969-12-05 1971-09-28 George C Christian Load responsive gripping device for flexible cable drives and the like
DE2307370C3 (de) * 1973-02-15 1979-03-29 Carl 5291 Kupferberg Kaeufer Seilwinde, insbesondere für Hängegerüste
US3841606A (en) * 1973-10-26 1974-10-15 M Declercq Self-tailing winch
FR2268742A1 (en) * 1974-04-24 1975-11-21 Collavet Jacques Handling equipment using endless cable - has drive with cable winding system and automatic brake
FR2307761A1 (fr) * 1975-04-18 1976-11-12 Dressler Bruno Palan auto-elevateur
DE2517796A1 (de) * 1975-04-22 1976-11-04 Rotzler Ohg Durchlaufwinde
US4026525A (en) * 1975-04-24 1977-05-31 Declercq Maurice G Self-tailing winch
FR2414470A1 (fr) * 1978-01-13 1979-08-10 Mittler Michel Debiteur d'ecoute pour treuil
US4225118A (en) * 1978-11-20 1980-09-30 Barient Company Direct drive deck winch
CH656600A5 (de) * 1981-09-24 1986-07-15 Rotzler Gmbh Co Mobile seilwinde.
DE3138034C2 (de) * 1981-09-24 1985-01-10 Rotzler GmbH + Co Spezialfabrik für Seilwinden und Hebezeuge, 7853 Steinen Seilwinde
DE3240345C3 (de) * 1982-10-30 1993-12-02 Mannesmann Ag Seiltrommelantrieb
US4557465A (en) * 1984-03-19 1985-12-10 The Boeing Company Cable drive mechanism

Also Published As

Publication number Publication date
DE3510282C2 (de) 1987-02-19
JPS61221093A (ja) 1986-10-01
CA1234093A (fr) 1988-03-15
ATE39676T1 (de) 1989-01-15
DE3661621D1 (en) 1989-02-09
EP0195983A1 (fr) 1986-10-01
DE3510282A1 (de) 1986-10-02
US4666128A (en) 1987-05-19

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