EP0538237A1 - Entraînement pour tambour double - Google Patents

Entraînement pour tambour double Download PDF

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Publication number
EP0538237A1
EP0538237A1 EP92890223A EP92890223A EP0538237A1 EP 0538237 A1 EP0538237 A1 EP 0538237A1 EP 92890223 A EP92890223 A EP 92890223A EP 92890223 A EP92890223 A EP 92890223A EP 0538237 A1 EP0538237 A1 EP 0538237A1
Authority
EP
European Patent Office
Prior art keywords
gear
motor
gears
drum
power divider
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.)
Granted
Application number
EP92890223A
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German (de)
English (en)
Other versions
EP0538237B1 (fr
Inventor
Josef Werlberger
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=25595403&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0538237(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Priority claimed from AT208391A external-priority patent/AT402061B/de
Priority claimed from AT127992A external-priority patent/AT402062B/de
Application filed by Individual filed Critical Individual
Publication of EP0538237A1 publication Critical patent/EP0538237A1/fr
Application granted granted Critical
Publication of EP0538237B1 publication Critical patent/EP0538237B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61B—RAILWAY SYSTEMS; EQUIPMENT THEREFOR NOT OTHERWISE PROVIDED FOR
    • B61B12/00—Component parts, details or accessories not provided for in groups B61B7/00 - B61B11/00
    • B61B12/10—Cable traction drives

Definitions

  • the invention relates to a double drum drive, in particular for a cable conveyor system, with at least one motor.
  • Such drives are mostly used for rope conveying systems in which a carriage is held movable on a support rope by means of a rope and a counter rope, this carriage being able to be clamped to the support rope by means of a clamping device, which is controlled by the two ropes, and then one of the Ropes can be extended and used as a load rope to hold a load.
  • the aim of the invention is to avoid these disadvantages and to propose a double drum drive of the type mentioned at the outset, which is distinguished by a simple structure and high efficiency and which also permits high speeds.
  • this is achieved in that the motor is connected to two interconnected power divider transmissions, each with at least two outputs, an output of the power distributor transmission closest to the motor being selectively connectable to one or the other output of the second power divider transmission, each having a drum in drive connection .
  • the two drums can be acted upon with different torques, the braking torque introduced into a drum by a cable being transmitted to the second drum as drive torque by driving the two drums via a power divider gear.
  • there is a mechanical transmission connection between the single motor and the drums which generally require considerably less maintenance than hydraulic drives.
  • such a gear arrangement allows high winding speeds, whereby the e.g. when unloading unavoidable timber can be handled in a short time and there is therefore a significant increase in conveying capacity.
  • a reduction gear which can be switched in stages is interposed in each output of the second power divider gear connected to a drum.
  • This measure has the advantage of a very high degree of flexibility in the use of such a drive device with regard to the structure of the conveyor device to be operated.
  • the reduction gear also makes it possible for a cable conveyor device in which the carriage can be moved by means of pulling and returning ropes coming from the same direction and in which a lifting rope, which can also be formed by the pulling rope, is provided over the carriage. which is held together with the return rope at the upper end of the inclined conveyor track on the drums to carry out an active unwinding of the lifting rope.
  • a conveying device can also be used for long and relatively flat conveying paths, in which, due to the weight of the hoisting rope, difficulties may arise when moving the same out of the carriage in the end region of the conveying path remote from the double drum drive.
  • the power divider gear is formed by planetary gears, with a ring gear of the planetary gear closer to the motor either with the planet carrier of the second planetary gear, which is in drive connection with a drum, or with one with the second drum in Drive connection standing ring gear of the second planetary gear is connectable.
  • the ring gear of the planetary gear closer to the motor is slidably held in the axial direction and is provided with a further internal toothing which, depending on the position of this ring gear, has a toothing which is in a rotationally fixed connection with the planet carrier of the second planetary gear or has an external toothing of the ring gear of the second planetary gear can be brought into engagement, the length of the internal toothing meshing with the planet gears of the planetary gear closer to the motor being selected in its axial extent corresponding to the displacement path, the sun gears of the two planetary gears with one another and the planet carriers of the two planetary gears with one each Shaft are non-rotatably connected.
  • the power divider gear are formed by differential gears, the bell of the differential gear closer to the engine either with the bell of the second differential gear, which is connected in a rotationally fixed manner to an output leading to a drum, or with one the second drum in the drive connection driven gear of the second differential gear is rotatably connected.
  • This solution also has the advantage of a simple structure, this solution allowing a very slim design.
  • connection of the two differential gears takes place via an axially displaceable sleeve which engages with the bell of the differential gear closer to the engine and, depending on its position, with the bell or an output gear of the second differential gear in Intervention stands.
  • the two outputs of the one power divider transmission are in drive connection via a freewheel with a brake, preferably a contactless brake, such as an eddy current brake or a hydraulic brake.
  • the power distribution device is formed by a controllable pump delivering a pressure medium with a motor connected to it and operable with the pressure medium.
  • the rope tension can also be changed by changing the pressure supplied by the controllable pump. This results in essentially proportional relationships, which means that the adjustment of the rope tension can be adjusted in particular.
  • the power distribution device is formed by a torque converter.
  • the power distribution device connected to the brake is formed by a planetary gear.
  • the power divider transmissions connected downstream of the motor are formed by spur gear differential transmissions.
  • the double drum drive according to the invention has a motor 1 which drives a first 50 and a second 70 power divider gear via a helical gear 60.
  • the one output of the power divider gear 50 is connected to the input of the power divider gear 70.
  • the two outputs 26 and 44 of the power divider gear 70 are each connected to a drum 42, 43.
  • the second output of the power divider gear 50 is via a switching device 20 'optionally with one of the two Outputs 26, 44 can be coupled, whereby the two drums 42, 43 are acted upon with different torques.
  • Fig. 2 shows a double drum drive according to the invention in greater detail.
  • the motor 1 is connected to a reduction gear 5 via a converter 2 and a powershift transmission 3 and a cardan shaft 4.
  • This reduction gear drives a reversing gear 60 via a shaft 11, the shaft 11 being divisible via a coupling 13 in order to be able to carry out maintenance work more easily.
  • This reversing gear 60 is designed as a planetary gear, the planet carrier 9 being loosely rotatable on the shaft 11 and being selectively connectable to a housing part 8 or to a ring gear 10 which meshes with the planet gears 12 via a switch 7 which can be displaced by means of the lever 6. mesh with the sun gear 12 'connected to the shaft 11 in a rotationally fixed manner.
  • the planet carrier 9 is connected to the housing part 8, as a result of which the planet gears act as intermediate gears and cause a direction of rotation of the ring gear 10 opposite to the direction of rotation of the shaft 11.
  • the reversing gear 60 is connected via a further clutch 13 to two power divider gears 50 and 70 arranged in a common housing, which are also designed as planetary gears.
  • the planet carrier 15 is rotatably connected to the shaft 14.
  • the planet gears 16 mesh with the sun gear 24, which is connected to the shaft 17 in a rotationally fixed manner, and the sleeve-shaped ring gear 20, which is held axially displaceably and is provided with an internal toothing 18, the axial extent of which corresponds to the displacement path of the ring gear 20.
  • the torque supplied via the shaft 14 is divided via the sun gear 24, which is rotatably connected via the shaft 17 to the sun gear 25 of the second power divider gear 70, and the ring gear 20, which simultaneously forms the switching device 20 '.
  • This ring gear 20 can optionally be brought into engagement with a planet carrier 21 or a toothing 22 of the same or a toothing 23 of a ring gear 27 of the second planetary gear 70.
  • the remaining part of the torque supplied via the shaft 14 reaches the planet carrier 21 and thus the shaft 26 via the sun gear 24, the sun gear 25 and the planet gears 16.
  • the switching of the ring gear 20 is possible by means of the lever 19 held in the housing, the length of the internal toothing 18 of the ring gear 20 meshing with the planet gears 16 of the planetary gear 50 being selected in accordance with the length of the displacement path of the ring gear 20 acting as a switching device 20 '.
  • the planet carrier 21 of the planetary gear 70 is rotatably connected via a shaft 26 to spur gears 32 and 35.
  • the gear 32 meshes with a gear 33 connected to a brake shaft 38 via a freewheel 34.
  • the ring gear 27 of the planetary gear 70 is rotatably connected via a hollow shaft 44 surrounding the shaft 26 to gears 28 and 29, of which the gear 29 meshes with a gear 30 connected to the brake shaft 38 via a further freewheel 31.
  • the gears 28 and 35 are in drive connection with further gears 37 and 36, in each of which a reversing gear can be arranged.
  • the gear 36 is connected in a rotationally fixed manner to the drum 43 via a shaft 40 and the gear 37 is connected in a rotationally fixed manner to the drum 42 via a hollow shaft 41 surrounding the shaft 40.
  • the two drums 42, 43 are driven in the same direction of rotation but with different torque.
  • the latter is due to the torque distribution caused by the power divider gear 50.
  • the torque supplied to the unwinding drum is dimensioned so that it is just sufficient to tension the running rope sufficiently.
  • the moment supplied by the running rope to the corresponding drum causes the direction of rotation of the corresponding drum to be reversed, but this moment is supplied to the winding drum via the two power divider gears 50, 70.
  • the double drum drive can also be used for other cable conveyor systems, as has already been explained.
  • Fig. 3 shows the arrangement of the two planetary gears 50, 70 in a practical embodiment in section.
  • the simultaneously acting as a switching device 20 'hollow tube 20 of the planetary gear 50 is displaceable via a pressurizable cylinder 191, which sits on a rigidly connected to the housing 80 carrier 81, which is provided with a piston 82 serving as a projection.
  • This is sealed against the cylinder 191 by means of a seal, as is the cylinder 191 against the carrier 81.
  • the pressure medium is supplied via two channels 83, 84 running in the carrier 81, which open out on both sides of the attachment 82 into the cavity delimited by the cylinder 191.
  • the ring gear 20 is transmitted to the ring gear 20 via a bearing 85 and circlips 86, 87.
  • the planet carriers 15 and 21 are formed in several parts.
  • the shaft 17, which connects the sun gears 24 and 25 of the planetary gears 50, 70 to one another, is supported in rotations of the shafts 14 and 26 by means of roller bearings 88.
  • FIG. 4 shows a further embodiment of power divider transmissions 50, 70. These are designed as differential gears.
  • a bevel gear 151 is connected in a rotationally fixed manner to the shaft 14 and meshes with differential gears 161 held in a bell 100, which in turn mesh with an output gear 241.
  • This driven gear 241 of the power divider gear 50 closer to the engine 1 is connected in a rotationally fixed manner to a bevel gear 251 of the second power divider gear 70 via a shaft 17 on which the bells 100, 101 of the two differential gears are supported via bearings 88.
  • the bevel gear 251 meshes with differential gears 161 held in the bell 101, which in turn mesh with an output ring gear 271 of the hollow shaft 44.
  • This hollow shaft 44 is further provided with a shoulder 231, which is provided with external teeth 23.
  • the bell 101 is rotatably connected to the shaft 26.
  • the switching device 20 ' is formed in this embodiment by a sleeve with internal gears 18 which is engaged with external gears 22 of the bells 100, 101 or the teeth 23 of the projection 231 of the hollow shaft 44, or can be brought into engagement.
  • the changeover again takes place by means of the cylinder 191.
  • part of the torque supplied via the shaft 14 via the bell 100 and the switching device 20 ' is either the bell 101 and thus the shaft 26 connected to it in a rotationally fixed manner, or the toothing 23 and thus supplied to the hollow shaft 44.
  • the further part of the supplied torque reaches the output gear 241 via the differential gears 161 of the power divider gear 50 and further via the bevel gear 251 and the differential gears 161 to the hollow shaft 44.
  • the shaft 14 is rotatably connected to the shaft 11 in operation via the coupling 13.
  • the shaft 17 is held rotatable relative to the shaft 14, and the shaft 26 is designed as a hollow shaft.
  • the brake 39 is detachably coupled to the brake shaft 38 via a clutch 13.
  • a controllable pump 802 is connected to the brake 39 via a further clutch 13. This is connected to the pressure medium, e.g. Pressurized oil, operable motor 801 connected, which is coupled via a clutch 13 to a shoulder 901 of the output shaft 17 of the power transfer gear 50 closer to the engine 1.
  • the two drums can be connected in a particularly advantageous manner hydrodynamically via a torque converter (not shown)
  • the power distribution device 900 connected to the brake 39 is formed by a planetary gear.
  • This power distribution device 900 is coupled to the brake shaft 38 via a clutch 13.
  • the ring gear 906 is driven by the brake shaft 38.
  • the ring gear 906 transmits most of the moment to the planet gears 905 and a smaller part of the required braking torque on the sun gear 907, which is connected to the brake 39 in a rotationally fixed manner. Since the ring gear 906 is driven by the drum unwinding the rope when roping downhill and the brake 39, which is expediently designed as an eddy current brake, forms a counter-torque, the planet carrier 904 is driven and transmits via the gear 903, which is firmly connected to the planet carrier 904 , and the gear 902 the torque on a shoulder 901 of the output shaft 17 of the power transfer mechanism 50 closer to the motor 1. As a result, the torque with which the cable is pulled from the unwinding drum is almost entirely supplied to the winding drum. This results in a very high efficiency of the double drum drive.
  • Fig. 7 shows the arrangement of the two spur gear planetary gear 50, 70 in a practical embodiment in section.
  • the simultaneously acting as a switching device 20 'ring gear 20 of the planetary gear 50 is displaceable via a pressurizable cylinder 191, which is arranged on a rigidly connected to the housing 80 carrier 81, which is provided with a piston 82 serving as an approach is.
  • This is sealed against the cylinder 191 by means of a seal, as is the cylinder 191 against the carrier 81.
  • the pressure medium is supplied via two channels 83, 84 running in the carrier 81, which open out on both sides of the attachment 82 into the cavity delimited by the cylinder 191.
  • the ring gear 20 is transmitted to the ring gear 20 via a bearing 85 and circlips 86, 87.
  • the planet carriers 15 and 21 are formed in several parts.
  • the shaft 17, which connects the sun gears 24 and 25 of the planetary gears 50, 70 to one another, is supported in a turning of the hollow shaft 26 by means of roller bearings 88.
  • an extension 901 of the shaft 17 is mounted in the hollow shaft 26 via a further bearing 88.
  • the further hollow shaft 44 is supported on this hollow shaft 26 via further bearings 88.
  • FIG. 8 shows a further embodiment of power divider gears 50, 70. These are designed as spur gear differential gears.
  • a spur gear 151 is rotatably connected to the shaft 14 and meshes with differential gears 161 held in a bell 100, which in turn mesh with an output gear 241.
  • This output gear 241 of the power divider gear 50 closer to the motor 1 is via a shaft 17 on which the bells 100 , 101 of the two differential gears are supported via bearings 80, rotatably connected to a bevel gear 251 of the second power divider gear 70.
  • the spur gear 251 meshes with differential gears 261 held in the bell 101, which in turn mesh with an output ring gear 271 of the hollow shaft 44.
  • This hollow shaft 44 is further provided with a shoulder 231, which is provided with external teeth 23.
  • the bell 101 is rotatably connected to the hollow shaft 26.
  • the switching device 20 ' is formed in this embodiment by a sleeve with internal teeth 10, which is engaged with external teeth 22 of the bells 100, 101 or the teeth 23 of the projection 231 of the hollow shaft 44, or can be brought into engagement.
  • the changeover again takes place by means of the cylinder 191.
  • part of the torque supplied via the shaft 14 via the bell 100 and the switching device 20 'either the bell 101 and thus the non-rotatably connected hollow shaft 26, or the toothing 23 and thus the hollow shaft 44 is supplied.
  • the further part of the supplied torque reaches the output gear 241 via the differential gears 161 of the power divider transmission 50 and further via the spur gear 251 and the differential gears 261 to the hollow shaft 44.
  • the shaft 17 has a shoulder 901 which is connected in a rotationally fixed manner to the gear 902 (not shown) or the motor 801, the hollow shaft 26 being mounted on the shoulder 901.

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  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Vending Machines For Individual Products (AREA)
  • Transmission Devices (AREA)
  • Gear Transmission (AREA)
  • Tires In General (AREA)
EP92890223A 1991-10-18 1992-10-15 Entraînement pour tambour double Expired - Lifetime EP0538237B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
AT208391A AT402061B (de) 1991-10-18 1991-10-18 Doppeltrommelantrieb
AT2083/91 1991-10-18
AT127992A AT402062B (de) 1992-06-23 1992-06-23 Doppeltrommelantrieb
AT1279/92 1992-06-23

Publications (2)

Publication Number Publication Date
EP0538237A1 true EP0538237A1 (fr) 1993-04-21
EP0538237B1 EP0538237B1 (fr) 1995-08-23

Family

ID=25595403

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92890223A Expired - Lifetime EP0538237B1 (fr) 1991-10-18 1992-10-15 Entraînement pour tambour double

Country Status (5)

Country Link
US (1) US5407398A (fr)
EP (1) EP0538237B1 (fr)
AT (1) ATE126766T1 (fr)
CA (1) CA2080885A1 (fr)
DE (1) DE59203372D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1965096A3 (fr) * 2007-02-28 2010-01-20 LOHMANN & STOLTERFOHT GMBH Engrenage de téléphérique doté de plusieurs étages planétaires

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2518753A1 (de) * 1975-04-26 1976-11-04 Eisenhuette Prinz Rudolph Ag Doppeltrumfoerderanlage fuer schaechte, insbesondere ab- oder weiterteufhaspel
DE3316530A1 (de) * 1983-05-06 1984-11-08 Dr.-Ing. Farkas Ingenieurbüro, 4700 Hamm Seilbahnanlage, insbesondere fuer den transport im untertaegigen berg- und tunnelbau vorgesehene seilbahn

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD30043A (fr) *
US1269524A (en) * 1918-03-18 1918-06-11 Arthur Thomas Collier Change-speed and reversing gear.
GB650327A (en) * 1947-02-05 1951-02-21 Ruston Buoyrus Ltd Improvements in or relating to operating winches for dragline excavators
CH338578A (de) * 1955-12-30 1959-05-31 Inst Foerdertechnik Des Minist Seilwinde mit Motorantrieb
US3092370A (en) * 1961-11-22 1963-06-04 Superior Equipment Company Winch unit
US3460807A (en) * 1967-02-21 1969-08-12 Viktor Ivanovich Prikhodko Winch
JPS54131243A (en) * 1978-03-31 1979-10-12 Komatsu Ltd Two-drum winch device
JPS57500928A (fr) * 1980-07-03 1982-05-27

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2518753A1 (de) * 1975-04-26 1976-11-04 Eisenhuette Prinz Rudolph Ag Doppeltrumfoerderanlage fuer schaechte, insbesondere ab- oder weiterteufhaspel
DE3316530A1 (de) * 1983-05-06 1984-11-08 Dr.-Ing. Farkas Ingenieurbüro, 4700 Hamm Seilbahnanlage, insbesondere fuer den transport im untertaegigen berg- und tunnelbau vorgesehene seilbahn

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1965096A3 (fr) * 2007-02-28 2010-01-20 LOHMANN & STOLTERFOHT GMBH Engrenage de téléphérique doté de plusieurs étages planétaires

Also Published As

Publication number Publication date
ATE126766T1 (de) 1995-09-15
EP0538237B1 (fr) 1995-08-23
DE59203372D1 (de) 1995-09-28
US5407398A (en) 1995-04-18
CA2080885A1 (fr) 1993-04-19

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