US3266639A - Overhead ropeway having an automatic clamping device and a lockable load lifter - Google Patents

Overhead ropeway having an automatic clamping device and a lockable load lifter Download PDF

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Publication number
US3266639A
US3266639A US305158A US30515863A US3266639A US 3266639 A US3266639 A US 3266639A US 305158 A US305158 A US 305158A US 30515863 A US30515863 A US 30515863A US 3266639 A US3266639 A US 3266639A
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Prior art keywords
crab
tube
cable
load
load lifter
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Expired - Lifetime
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US305158A
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English (en)
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Koller Josef
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C21/00—Cable cranes, i.e. comprising hoisting devices running on aerial cable-ways
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C2700/00—Cranes
    • B66C2700/01—General aspects of mobile cranes, overhead travelling cranes, gantry cranes, loading bridges, cranes for building ships on slipways, cranes for foundries or cranes for public works
    • B66C2700/011—Cable cranes

Definitions

  • the invention relates to a combined overhead ropeway for conveying loads, comprising a traveling crab equipped with a clamping device and a load lifter interlocked with the crab, in which a reversal of the motion of the traveling crab causes the clamping mechanism to fix the position of the traveling crab on the suspension cable while the release mechanism liberates the load lifter.
  • the invention is characterized in that the clamping and release device can be actuated after reversal of the motion of the traveling crab by energy accumulated in a reservoir by the motion of the traveling crab along the ropeway; this actuation of the clamping and release device is obtained by forcing gear wheels by means of the reservoir into engagement with a countershaft driven by the rollers of the traveling crab and by providing a hammer shifted by these gear wheels when the motion of the crab is reversed in order to control a changeover valve actuating the blocking and release mechanism, the reservoir being preferably charged by a pump driven by a countershaft.
  • the invention makes it possible that the switching elements effecting the blocking of the traveling crab and the release of the load lifter can be brought to a preparatory position by means of control elements actuated by the motion of the crab along the ropeway from which the blocking and release can be effected by the switching elements when the motion of the traveling crab is reversed.
  • the switching members are brought into a position, preparing the switching, by means of the respective control elements. Only when the motion of the crab is reversed, do the switching elements effect the blocking or release.
  • FIGURE 1 is a perspective side view of the overhead ropeway
  • FIGURE 2 shows the overhead ropeway as seen from the opposite side in FIG. 1;
  • FIGURE 3 is a perspective view in section showing the guide pulley disposed on the traveling crab above the load lifter;
  • FIGURE 4 shows the portion of FIG. 3 turned through 90 in a position in which the load hook is retracted
  • FIGURE 5 is a perspective view of the load lifter in longitudinal section
  • FIGURE 6 is a sectional view through the load lifter of FIG. 5;
  • FIGURE 7 is a perspective view of a switching mechanism
  • FIGURE 8 is a view in longitudinal section of a hydraulic reservoir
  • FIGURE 9 shows a first preferred embodiment of a clamping mechanism
  • FIGURE 10 shows another preferred embodiment of a clamping mechanism
  • FIGURES 11 and 12 show details of the clamping jaws acting on the suspension cable.
  • the traveling crab 1 is provided with the usual rollers 2. Through the rollers, by means of a V-belt drive 5 a countershaft 6 is driven when the traveling cr-ab moves, independent-1y of the direction of this motion.
  • the countershaft drives via an adjustable eccentric 12 an oil pump 7. Above the oil pump 7 an oil tank 11 is provided.
  • This oil pump is connected by a feed line 31 containing a control valve 10 with a hydraulic reservoir 8.
  • a further oil line 32 connects reservoir 8 with a changeover valve 20 from which hydraulic lines 33 and 34 lead to respective clamping and release cylinders the operation of which will be discussed in greater detail hereinafter.
  • a further line 35 connects the changeover valve 20 with the oil tank 11 which in turn communicates through a separate line 36 with the control valve 10.
  • a shaft 30 is disposed above the changeover valve 20 in parallel relation with shaft 6.
  • a lever 14 is supported on shaft 30 and carries a gear wheel 17. Gear wheel 17 is in continuous engagement with a further gear wheel 16, which is rigidly mounted on the shaft 30.
  • a cable line 15 is coupled to and displaced by the cylinder 9 of the reservoir 8 to cause the lever 14 to be swiveled about shaft 30 until the gear wheel 17 engages a gear wheel provided on the countershaft 6.
  • a sleeve 28 (FIG. 6) is mounted which can rotate and slide on the shaft. The sleeve is equipped at both ends with jaws. This sleeve is rigidly connected by a lever with a hammer or weight 18.
  • the changeover valve comprises a cylindrical housing in which a valve stem 22 can be displaced against the force of a spring. By means of this stem the oil lines 32, 34 and 35 are connected with each other. The top part of this stern projects beyond the valve housing.
  • a circular guideway 25 On the top face of this valve and concentrically with the valve is a circular guideway 25 on which a circular ring 21 rests and can rotate.
  • On the circular ring 21 two diametrically opposite horn-shaped brackets 19 are supported. The brackets 19 rotate with the ring 21.
  • a spring 26 acts on the circular ring 21 and maintains the same in an initial position, the function of which will be described hereinafter.
  • the load lifter comprises essentially a cylindrical tube 23 which is suspended for swivelling movement in the plane of the traveling crab.
  • a hoisting cable 4 carries the load hook 24 and passes along the central axis through the load lifter tube 23.
  • a weight 37 (FIG. 3) is rigidly connected with the cable.
  • a helical spring 58 is arranged which is suspended with its upper end in suitable guide bars 59 provided inside the tube. The lower part of this spring moves freely and carries a spring plate 60.
  • Below the weight 37 (with retracted load hook) two diametrically opposite apertures are provided through which two cams 43 and 44 project into the tube.
  • cams can be displaced against the force of two springs 45 and 46 which urge the cams into the apertures.
  • the earns 43 and 44 are displaced by means of two pegs 47 and 48 which are actuated by a hydraulic cylinder 49. Through a linkage 51 these pegs together with the cylinder 49 arranged between them, can be displaced in a direction away from the tube 23 in a manner as will be described hereinafter.
  • the pegs 47 In the locked position of the hook 24, i.e., when the earns 43, 44 project through the apertures in the tube 23 and support weight 37, the pegs 47,
  • lever arm 55 which is supported for swiveling movement on the tube 23.
  • This lever arm has an enlarged bottom end 56 which projects through an opening 57 into the tube.
  • the lever arm 55 and the linkage 51 are interconnected by a coupling rod 54.
  • a further lever 38 In the above-mentioned plane, at the opposite side of the tube 23 there is provided a further lever 38, the bottom end of which is formed as a guide rail 39 for a sliding body 40.
  • the sliding body 40 has a nose-shaped boss directed toward the tube 23 and is connected by means of a cable line 27 via guide pulleys with the circular ring 21 mounted on the changeover valve 20.
  • In the tube 23 is formed a slot-shaped axial recess 50 for the nose of the sliding body 40.
  • a spring 61 is positioned between the lever 38 and the tube 23 and due to the force of the spring 61, the lever 38 is urged away from the tube 23.
  • a coupling rod 42 connects via a spring 41 the' lever 38 with the arm 55.
  • a guide pulley 13 for the hoisting cable 4 is supported in the traveling crab on a shaft 62.
  • two disks 63 and 64 are located in spaced relation, the disk 64 having a flange or collar which encircles the disk 63.
  • a helical spring 65 one end of which is attached to the disk 64, while the other end is fixed to the disk 63. Both disks can be rotated with respect to each other.
  • the disk 63 On the face opposite the guide pulley the disk 63 has a groove into which is engaged a pawl 66 which is loaded by a spring 67, said pawl being attached movably to the guide pulley 13.
  • the other disk 64 is provided with grooves 71 at its circumference (FIG.
  • On the traveling crab 1 a pawl 70 is supported which is pressed by the force of a spring 69 into these grooves 71 (FIG. 2).
  • the hydraulic reservoir 8 (see FIG. 7) consists of a double-walled cylinder.
  • the inner cylinder 73 guides a piston 75.
  • a sliding sleeve cylinder 9 is supported which can be displaced outward against the force of the spring 74. This sleeve 9 is connected with the piston 75.
  • FIG. 8 the construction of a simple suitable clamping device will be explained.
  • the clamping device enables the traveling crab 1 to selectively engage cable 3 and thus be locked.
  • the clamping device comprises two jaws 76 and 77 supported on the traveling crab which are urged apart by means of a hydraulic cylinder 79 such that the clamping jaws are clamped against the suspension cable 3.
  • a hydraulic cylinder 79 When the cylinder 79 is relieved, the jaws are spaced from the suspension cable by the force of a spring 78 which is interposed between jaws 76 and 77.
  • This construction is suflicient for light overhead ropeways.
  • a construction which proves more suitable is shown in detail in FIG. 9.
  • the clamping device shown therein comprises two tong arms 92 and 93 supported for swivelling movement on the traveling crab 1. Between the top end parts of these two tong arms a hydraulic cylinder 87 is situated. In their lower parts the tong arms 92 and 93 have two rails 82 and 83 provided for the clamping jaws 80 and 81. These rails have at their tops nose-shaped extensions 84 and 85. Above the clamping jaws a toothed rack 86 is arranged at right angles to the cable. Two rams 90 connected with this toothed rack are guided in a rail 94 attached to the traveling crab 1 and are urged upwards by the force of the two springs 91.
  • a further hydraulic cylinder 89 is provided the cross-sectional area of which is only a fraction of that of the cylinder 87.
  • the clamping jaws 80 and 81 are kept separated from the suspension cable by the two springs 88 when the cylinder is hydraulically relieved.
  • the rails 82 and 83 diverge in the direction of the cable winch and the clamping jaws and 81 are constructed in the form of wedges.
  • the sleeve On its outward movement, the sleeve moves the cable line 15 therewith, thus swiveling the lever 14, together with the gear Wheel 17, toward the countershaft 6 until the gear wheel 17 engages the gear wheel provided on the countershaft 6.
  • the gear wheel 17 and hence also the gear wheel 16 mounted rigidly on the shaft 30 are driven by the countershaft.
  • the hammer 18 is in the position shown in FIG. 1 and FIG. 6 and is pressed by one of the brackets 19 under the action of spring 26 against the upper jaw 29. Since the upper jaw rotates clockwise owing to the downward motion of the crab, the jaws undergo ratchet action and freely rotate past each other.
  • the hammer is lifted and falls down by its own weight at the other side of the shaft 30, striking the second bracket 19. Thereby the bracket is pressed downward and also presses the valve stem 22 downward. Thereby, the lines 32, 33 and 34 are connected with each other and the oil pressurized by the spring 74 passes through the changeover valve 20 into the cylinders 49, and 79 (cylinders 87 and 89 of the embodiment in FIG. 9).
  • the cylinder 49 actuates the release mechanism of the load lifter by forcing apart the two pegs 47 and 48. Thereby the cams 43 and 44 are retracted from the corresponding apertures in the tube 23 (see FIG. 4) and the weight 37 is free of its support. Owing to the force of the spring 58 the weight 37 is urged downwards out of the tube 23. On its downward course the weight 37 contacts the lever arm 55 and displaces arm 55 away from the tube which takes along in this movement the linkage 51 via the coupling rod 54, thus drawing the pegs 47 and 48 away from the cams 43 and 44. Owing to the force of the springs 45 and 46 these cams spring back into their initial position.
  • the cylinders 87 and 89 are equally pressurized at the same time and the two jaws 80 and 81 are pressed against the cable.
  • the toothed rack 86 is pressed down against the force of the two springs 91 and the noses 84 and 85 are engaged in the teeth of the toothed rack 86. If the load hook would be loaded, the traveling crab would be lifted as soon as the load lifter is released.
  • the rails 82, 83 which are arranged diverging in the direction of the cable winch and are provided as guides for the clamping jaws 80 and 81, these jaws are pressed tightly against the cable due to the wedge effect of the rails (see FIGS. and 11).
  • the load lifter is released and may be lowered.
  • the hoisting cable 4 is hauled in. This produces the following effects: the weight 37 enters the tube 23 from below and exerts an outward pressure on the lever arm 55 owing to the conically shaped top part of the weight 37.
  • the lever 38 together with the sliding body 40 is urged against the tube by the linkage 42 so that the nose of the sliding body 40 projects through the slots 50 into the tube 23.
  • the rising weight carries the sliding body upwardly therewith.
  • the spring 58 is compressed.
  • the bottom side of the weight is situated above the cams 43 and 44, the latter are pressed again into the interior of the tube by the springs 45 and 46.
  • the enlarged end of the lever arm 55 can again project into the tube, since the spring 52 draws the linkage 51 toward the tube 23 by the coupling rod 54. Since the cylinder 49 is still under pressure, the pegs 47 and 48 are forced apart. The sliding body 40 lifted by the weight 37 actuates the cable line 27, whereby the circular ring 21 of the changeover valve is rotated against the force of the spring 26. Thereby the bracket 19 is withdrawn from below the weight 18, the weight 18 falls further downward and the stem 22 of the valve 20 moves upward. Now, the path is free for the flow of compressed oil from the cylinders 49 and 79 (or the cylinders 87 and 89 in the embodiment of FIG.
  • the function of the helical spring 65 will be briefly explained.
  • the disk 63 is rotated via the guide pulley 13 and the pawl 66, whereby the helical spring is wound up.
  • the spring 69 is dimensioned such that it yields only when the helical spring is completely wound up so that only then is the second disk 64 able to join in the rotation; thus, breaking or overwinding of the helical spring is prevented.
  • An overhead ropeway for conveying loads comprising a cable, a traveling crab supported for travel in opposite directions along said cable, said crab including clamping means for engaging the cable to lock the crab therewith, said clamping means having engaged and re leased positions, load lifter means supported from said crab for raising and lowering a load, said load lifter means having retracted and extending positions, and control means for the clamping means and the lifter means to cause the clamping means to assume the engaged position thereof and the load lifter means to move to extended position when the direction of travel of the crab is reversed, said control means comprising power means which is energized by the movement of the traveling crab and switching means for coupling the thus energized power means with both the clamping means and the load lifter means when the direction of travel of the crab is reversed, said control means further comprising a gear wheel driven by the crab as it travels, gear means supported for movementbetween engaged and disengaged positions with respect to the gear wheel, said gear means being driven by the gear wheel when engaged therewith, hammer means controlling said switching means and
  • said switching means comprises a changeover valve includinga housing and a stem displaceable on said housing, two swiveling brackets supported for rotation at the end of the stem, the load lifter means comprising a cylindrical tube, a lever pivotally mounted on said tube and having a lower end constituted as a guide rail, a sliding body having a nose-shaped extension supported for movement in said guide rail and a cable connecting said swiveling brackets and said sliding body.
  • said load lifter means comprises a hoisting cable, a rotatable guide pulley for said cable, two rotatable disks arranged in spaced facing relation, a pawl coupling one of said disks with the guide pulley, a spring loaded pawl coupled to the crab and preventing rotation of the other.
  • one of said disks including a collar encircling the other of the two disks and a helical spring between the two disks, one end of said spring being fixed to the first disk and the other end to the second disk.
  • the reservoir comprises a double-walled cylinder having internal and external walls, a spring-loaded sleeve supported for sliding movement between the cylinder walls, a piston slidably supported within the inner cylinder and engaged with the sleeve to move the same, said control means further comprising a pivotal lever coupled to the piston of the hydraulic reservoir and supporting said gear means for movement between the engaged and disengaged positions thereof, said gear means comprising a first gear which can engage the gear wheel and a second gear in continuous mesh with the first gear and adapted for driving the hammer means.
  • control means further comprises a rotatable sleeve having jaws at opposite ends and connected to said hammer means and jaw members coupled to said second gear and engageable with the jaws of the sleeve to drive the same and the hammer means therewith.
  • said switching means comprises a changeover valve actuated by the hammer means, said changeover valve comprising a cylinder housing, a stern displaceable in said cylinder housing and projecting beyond the housing, two opposite brackets supported for swiveling movement about the axis of the valve, the changeover valve being hydraulically connected with the reservoir and with the clamping means and the load lifter means.
  • said load lifter means comprises a cylindrical tube supporting said weight and pivotally movable in the direction of travel of the crab, a helical spring in said tube above said weight and having a displaceable lower end which rests upon the weight when the latter is raised.
  • the means for supporting the weight in raised position comprises at least two cams projecting through openings provided in the tube when the weight is raised; said cams being supported for retractable swiveling movement in a plane perpendicular of the tube to be drawn out of their respective openings in the tube, said means for releasing the weight comprising two pegs actuated by said displaceable hydraulic cylinder for retracting the cams from the tube.
  • said means .for releasing the weight comprises a pivotally mounted lever on said tube extending lengthwise thereof and having a lower end constituted as a guide rail, a sliding body in said guide rail having a nose-shaped extension, said tube having an axial slot for the nose extension of said sliding body.
  • said load lifter means comprises a further pivotally mounted lever arm on an opposite side of the tube as that of said lever, said arm having a lower end with an enlargement which projects through a corresponding opening provided in the tube into the .interior of the tube, said lever arm being coupled to the said lever opposed thereto.
  • said means for releasing the weight comprises a supporting arm carrying said pegs, a pivotable lever on said tube having a lower end with an enlargement projecting into the interior of the tube, said latter lever being coupled to said supporting arm for common pivotable movement therewith.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Load-Engaging Elements For Cranes (AREA)
US305158A 1962-09-08 1963-08-28 Overhead ropeway having an automatic clamping device and a lockable load lifter Expired - Lifetime US3266639A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT717662A AT237678B (de) 1962-09-08 1962-09-08 Kranseilbahn zur Lastbeförderung

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US3266639A true US3266639A (en) 1966-08-16

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US305158A Expired - Lifetime US3266639A (en) 1962-09-08 1963-08-28 Overhead ropeway having an automatic clamping device and a lockable load lifter

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US (1) US3266639A (de)
AT (1) AT237678B (de)
CH (1) CH418563A (de)
ES (1) ES291210A1 (de)
GB (1) GB1056047A (de)
NO (1) NO115399B (de)
SE (1) SE302345B (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103231995A (zh) * 2013-04-28 2013-08-07 杭州国电大力机电工程有限公司 一种双轮自行式承马
CN116835456A (zh) * 2023-08-30 2023-10-03 贵州省公路工程集团有限公司 一种缆索吊装***的防损伤跑车结构

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT387558B (de) * 1986-08-29 1989-02-10 Stuefer Heinz Fa Kabelkranwagen
AT402060B (de) * 1991-02-08 1997-01-27 Josef Werlberger Führungseinrichtung für das hubseil eines kabelkranwagens
CN114394535B (zh) * 2022-03-28 2022-06-10 南通德众科技发展有限公司 一种高安全克令吊吊装***及方法

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US528297A (en) * 1894-10-30 Hoisting mechanism
US1069722A (en) * 1912-03-01 1913-08-12 Ney Mfg Company Hay-carrier.
US1530244A (en) * 1923-03-15 1925-03-17 Lidgerwood Mfg Co Attachment for hoisting devices
US2429908A (en) * 1943-12-11 1947-10-28 Benoto Sa Electric control means for selfacting buckets
US2790561A (en) * 1950-06-21 1957-04-30 Wyssen Jakob Hoisting and conveying apparatus
US3058601A (en) * 1960-03-09 1962-10-16 Wyssen Jakob Transportation system
US3079008A (en) * 1960-08-15 1963-02-26 Ernest O Naud Hoisting and conveying apparatus

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US528297A (en) * 1894-10-30 Hoisting mechanism
US1069722A (en) * 1912-03-01 1913-08-12 Ney Mfg Company Hay-carrier.
US1530244A (en) * 1923-03-15 1925-03-17 Lidgerwood Mfg Co Attachment for hoisting devices
US2429908A (en) * 1943-12-11 1947-10-28 Benoto Sa Electric control means for selfacting buckets
US2790561A (en) * 1950-06-21 1957-04-30 Wyssen Jakob Hoisting and conveying apparatus
US3058601A (en) * 1960-03-09 1962-10-16 Wyssen Jakob Transportation system
US3079008A (en) * 1960-08-15 1963-02-26 Ernest O Naud Hoisting and conveying apparatus

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103231995A (zh) * 2013-04-28 2013-08-07 杭州国电大力机电工程有限公司 一种双轮自行式承马
CN116835456A (zh) * 2023-08-30 2023-10-03 贵州省公路工程集团有限公司 一种缆索吊装***的防损伤跑车结构
CN116835456B (zh) * 2023-08-30 2023-11-03 贵州省公路工程集团有限公司 一种缆索吊装***的防损伤跑车结构

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Publication number Publication date
CH418563A (de) 1966-08-15
ES291210A1 (es) 1963-12-16
AT237678B (de) 1964-12-28
NO115399B (de) 1968-09-30
GB1056047A (en) 1967-01-25
SE302345B (de) 1968-07-15

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