Abstract
The disclosure relates to a winding device for winding a rope onto a rope drum rotatable about a rotation axis. The winding device includes a rope guide for feeding the rope to the rope drum. The rope guide has a pivoting arm having a longitudinal axis and has a deflection element. The pivoting arm is pivotable about a pivot axis. The deflection element is disposed on the pivoting arm. The winding device is conceived such that the rope when being wound onto the rope drum passes the pivoting arm before the deflection element. The rope guide includes a delimitation element. The delimitation element is disposed such that a pivoting movement of the pivoting arm about the pivot axis is limited to a critical angular range (Δ). The deflection element is tiltable about a tilting axis. The tilting axis extends along the longitudinal axis of the pivoting arm.
Claims
1. A winding device for winding a rope onto a rope drum which is rotatable about a rotation axis, comprising: a rope guide for feeding the rope to the rope drum; said rope guide having a pivoting arm defining a longitudinal axis and further having a deflection element; said pivoting arm being pivotable about a pivot axis; said deflection element being disposed on said pivoting arm; wherein the winding device is configured such that the rope when being wound onto the rope drum passes said pivoting arm before said deflection element; said rope guide including a delimitation element disposed such that a pivoting movement of said pivoting arm about the pivot axis is limited to a critical angular range Δ; and, said deflection element being tiltable about a tilting axis extending along the longitudinal axis of said pivoting arm.
2. The winding device of claim 1, wherein said deflection element is tiltable about the tilting axis such that the rope is able to be guided by said deflection element in an angular range ϕ outside the critical angular range Δ.
3. The winding device of claim 1 further comprising: an actuator; said deflection element being disposed in a tilted position in terms of the tilting axis; said pivoting arm being disposed in a pivoted position in terms of the pivot axis; and, wherein said actuator predefines said tilted position as a function of said pivoted position.
4. The winding device of claim 1, wherein said rope guide has a pivot gear for driving by a motor; and, said pivoting arm, via said pivot gear, is movable in a reciprocating manner in said critical angular range Δ.
5. The winding device of claim 4, wherein: said pivot gear has a shaft, a pin, and a connecting rod; said shaft is rotatable about a shaft axis; said pin is disposed eccentrically to the shaft axis and is movable about the shaft axis; said connecting rod connects said pin to said pivoting arm; and, said pivot gear is configured such that a spacing between the shaft axis and the pin varies in a movement of said pin about said shaft axis.
6. The winding device of claim 5, wherein said spacing between said shaft axis and said pin in the movement of said pin about said shaft axis is varied such that a constant rope pitch is achieved when the rope is being wound on the rope drum.
7. The winding device of claim 5, wherein said pivot gear has a cam with a track in which said pin is guided on a path of said pin about said shaft axis.
8. The winding device of claim 1, wherein said deflection element includes a plurality of rollers which are mutually adjacently disposed on a cam track.
9. A rope take-up winding device comprising: a rope drum having two flange discs; a winding device for winding a rope onto said rope drum; said rope drum being rotatable about a rotation axis; said winding device including a rope guide for feeding the rope to said rope drum; said rope guide having a pivoting arm defining a longitudinal axis and further having a deflection element; said pivoting arm being pivotable about a pivot axis; said deflection element being disposed on said pivoting arm; said winding device being configured such that the rope when being wound onto said rope drum passes said pivoting arm before said deflection element; said rope guide including a delimitation element disposed such that a pivoting movement of said pivoting arm about said pivot axis is limited to a critical angular range Δ; said deflection element being tiltable about a tilting axis extending along said longitudinal axis of said pivoting arm; and, said pivoting arm being pivotable about said pivot axis so as to reciprocate between said two flange discs.
10. The rope take-up winding device of claim 9, wherein a pivotable part of said rope guide that is pivotable about said pivot axis in absence of said delimitation element would be pivotable between said two flange discs in a maximum flange angular range Ω; and, said critical angular range Δ is at most 80% of said maximum flange angular range Ω.
11. The rope take-up winding device of claim 9, wherein a pivotable part of said rope guide that is pivotable about said pivot axis in absence of said delimitation element would be pivotable between said two flange discs in a maximum flange angular range Ω; and, said critical angular range Δ is at most 70% of said maximum flange angular range Ω.
12. The rope take-up winding device of claim 9, wherein a pivotable part of said rope guide, proceeding from said pivot axis, has a pivoting length measured perpendicularly to said pivot axis; said two flange discs have a maximum diameter; and, said pivoting length is at most 100% of said maximum diameter.
13. The rope take-up winding device of claim 9, wherein a pivotable part of said rope guide, proceeding from said pivot axis, has a pivoting length measured perpendicularly to said pivot axis; said two flange discs have a maximum diameter; and, said pivoting length is at most 90% of said maximum diameter.
14. The rope take-up winding device of claim 9, wherein said rope guide at a specific rotary position of said rope drum in terms of said rotation axis, as a function of the specific rotary position, assumes a pivoted position in terms of said pivot axis.
15. The rope take-up winding device of claim 9, wherein said pivoting arm at a specific rotary position of said rope drum in terms of said rotation axis, as a function of the specific rotary position, assumes a pivoted position in terms of said pivot axis.
16. The rope take-up winding device of claim 9 further comprising a drum drive for driving the rope drum.
17. The rope take-up winding device of claim 9, wherein said rope drum is a component part of a drum winch; and, all tensile forces are transmitted from the rope to said rope drum.
18. The rope take-up winding device of claim 9, wherein said rope drum is a component part of a storage drum; and, the rope take-up winding device is configured such that only pretension forces are transmitted from the rope to said rope drum.
Description
BRIEF DESCRIPTION OF THE DRAWINGS
[0044] The invention will now be described with reference to the drawings wherein:
[0045] FIG. 1 shows a perspective illustration of a winding device;
[0046] FIG. 2 shows a plan view from below onto the winding device from FIG. 1;
[0047] FIG. 3 shows a view in the direction of the arrow III onto the end side of the pivoting arm of the winding device from FIG. 2;
[0048] FIG. 4 shows a lateral view of the winding device from FIG. 1, having a disassembled flange disc;
[0049] FIG. 5 shows a view in the direction of the arrow V from FIG. 4 onto the winding device from FIG. 4;
[0050] FIG. 6 shows a lateral view of the winding device from FIG. 1 in the direction perpendicular onto the rotation axis of the rope drum and perpendicular onto the pivot axis of the pivoting arm;
[0051] FIG. 7 shows a plan view from above onto the winding device from FIG. 1;
[0052] FIG. 8 shows a schematic illustration of the view of the winding device as per FIG. 2, with the illustration of three different positions of the pivoting arm in a single figure;
[0053] FIG. 9 shows a schematic illustration of the view of the winding device as per FIG. 6, with the illustration of three different positions of the pivoting arm in a single figure;
[0054] FIG. 10 shows a schematic illustration of the view of the winding device as per FIG. 1, with the illustration of three different positions of the pivoting arm in a single figure;
[0055] FIG. 11 shows a sectional illustration of a section along the section plane XI-XI from FIG. 8 through the deflection element;
[0056] FIG. 12 shows a schematic perspective illustration of an alternative embodiment of a winding device having an actuator for setting the tilted position of the deflection element as a function of the pivoted position of the pivoting arm, wherein three different pivoted positions of the pivoting arm are illustrated in a single figure;
[0057] FIG. 13 shows a schematic illustration of a lateral view of the winding device as per FIG. 12, with the illustration of three different positions of the pivoting arm in a single figure;
[0058] FIG. 14 shows a schematic illustration of an alternative pivot gear for the pivoting arm of a pivoting device as per FIGS. 1 to 13; and,
[0059] FIG. 15 shows a schematic illustration of a comparison of the winding device according to the disclosure and a winding device in from the prior art based on a winding arm having a non-tiltable deflection element.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0060] FIG. 1 shows a rope take-up winding device 1. The rope take-up winding device 1 includes a winding device 40 and a rope drum 3 having a rope 2. The winding device 40 serves for winding the rope 2 onto the rope drum 3. To this end, the rope drum 3 is mounted so as to be rotatable about a rotation axis 50. The winding device 40 serves for unwinding the rope 2 from the rope drum 3.
[0061] The rope take-up winding device 1 is suitable for the multi-tier operation. The winding device 40 is suitable for hoisting winches and draw winches. The winding device 40 is conceived for drawing applications using forces of 10 kN to 1000 kN, in the embodiments of 50 kN to 500 kN. The winding device 40 is conceived for hoisting applications using forces of 1 kN to 100 kN, in the embodiments of 10 kN to 50 kN.
[0062] The rope take-up winding device 1 includes a main body 19. The main body 19 is a component part of the rope drum 3. The drum of the rope drum 3 is rotatably mounted on the main body 19. The main body 19 is also referred to as a support bearing.
[0063] The rope drum 3 includes the drum, the two flange discs 4 and the main body 19. The drum has a drum shell. The drum shell extends between the two flange discs 4. The drum shell encircles the rotation axis 50. The drum shell has the shape of the circumferential face of a cylinder.
[0064] The rope take-up winding device 1 has a drum drive. The drum drive serves for driving the rope drum 3 so as to perform a rotating movement about the rotation axis 50. The drum drive in the embodiments includes a motor, not illustrated, having a motor rotation axis 45. The drum drive includes a gearbox (not illustrated). The gearbox is disposed between the motor and the rope drum 3. It can also be provided that the drum drive does not have any such gearbox. The motor rotation axis 45 in the embodiments runs so as to be coaxial with the rotation axis 50 of the rope drum 3. The motor drives the rope drum 3.
[0065] The rope 2 by way of one end is fastened to the rope drum 3. The rope drum 3 has two flange discs 4 illustrated in FIG. 1. The flange discs 4 limit a winding space for the rope 2 in the direction of the rotation axis 50. The winding space in the direction radial to the rotation axis 50 is limited by the drum of the rope drum 3. The rope 2 can be wound onto a drum of the rope drum 3 between the flange discs 4. The rope take-up winding device 4 is conceived such that the rope 2 is wound on the rope drum 3 such that, upon winding, in terms of the direction of the rotation axis 50, one winding is initially placed next to another winding onto the rope drum 3 until the rope 2 impacts a flange disc 4. When the rope 2 impacts the flange disc 4, the rope runs onto the rope drum 3 at a winding angle α illustrated in FIG. 5. The winding angle α is measured in a tangential plane to the rope 2 already wound on the rope drum 3, at the point where the rope 2 runs onto the already wound tiers of the rope 2, in relation to a plane G. The tangential plane is disposed at a spacing in relation to the rotation axis 50, which corresponds to the mean radius of the outermost wound rope tier. The tangential plane in FIG. 5 runs so as to be parallel to the drawing plane. Each flange disc 4 is disposed in a plane G. The plane G runs perpendicularly to the rotation axis 50. The plane G bears on the inside of the flange disc 4. The insides of the flange discs 4 face one another. The inside of the flange disc 4 limits the receptacle space of the rope drum 3 for the rope 2.
[0066] Once the rope 2 has impacted the flange disc 4, the axial winding direction of the rope 2 changes. The rope 2 is now wound from the flange disc 4, impacted by the rope 2, away towards the opposite flange disc 4. A new rope tier in terms of the direction radial to the rotation axis 50 is created in the process. A tidy winding pattern results in this way.
[0067] The rope drum 3 in the embodiments is a component part of a storage drum. The storage drum includes the drum drive. The storage drum includes a controller, not illustrated. The storage drum includes the rope guide 5. A rope winch, not illustrated, is disposed upstream of the rope drum 3. Only pretension forces from the rope 2 are transmitted to the storage drum. However, it can also be provided that the rope drum is a component part of a drum winch. The drum winch includes the drum drive. The drum winch includes a controller. In an embodiment of the rope drum as a component part of a drum winch, all the forces that act on the rope 2 are transmitted from the rope 2 to the rope drum.
[0068] The winding device 40 in the embodiments includes a rope guide 5 (FIG. 1). The rope 2 is fed to the rope drum 3 by way of the rope guide 5. The rope guide 5 includes a pivoting arm 6 and a deflection element 7. The pivoting arm 6 is pivotable about a pivot axis 48. The pivot axis 48 lies in a plane which is oriented perpendicularly to the rotation axis 50 and is disposed between the two flange discs 4, in particular in the centre between the two flange discs 4. The direction of the pivot axis 48 runs perpendicularly to the direction of the rotation axis 50. The pivot axis 48 runs parallel to a tangent that bears on the rope drum 3. The pivot axis 48 can be disposed at a spacing from the drum of the rope drum 3. The pivoting arm 6 is pivotable about the pivot axis 48, in a reciprocating manner between the two flange discs 4. The two flange discs 4 lie in each case in one of the two planes G. The plane G is oriented so as to be perpendicular to the rotation axis 50. The two planes G limit in each case the flange discs 4 to the insides of the flange discs 4 that face one another in terms of the rotation axis 4. The pivoting arm 6 is pivotable in a reciprocating manner between these two planes G of the flange discs 4. The pivoting arm 6 can be positioned in relation to the rope drum 3 such that the pivotable part of the rope guide 5 is arranged partially or, as in the embodiments, completely radially in terms of the rotation axis 50 outside the flange discs 4.
[0069] The pivoting arm 6 has a rope window 34 (FIG. 2). The rope 2 is fed to the pivoting arm 6 through the rope window 34 on the longitudinal end of the pivoting arm 6 that faces away from the deflection element 7. Between the rope window 34 and the deflection element 7, the rope 2 is guided along the longitudinal axis 49 of the pivoting arm 6. The rope window 34 includes two guide rollers 35. The guide rollers 35 are mounted so as to be rotatable on the pivoting arm 6. The guide rollers 35 are rotatable about roller axes 34. The roller axes 34 run so as to be parallel to the pivot axis 48 of the pivoting arm 6. The guide rollers 35 are disposed so as to lie next to one another. The guide rollers 35 limit the rope window 34 on mutually opposite sides of the rope window 34. The rope 2 runs between the two guide rollers 35. The rope 2 bears on both guide rollers 35. The rope 2 is deflected by the guide rollers 35.
[0070] The winding device 40 includes a support element 36 illustrated in FIG. 1 or 2. The support element 35 serves for supporting the pivotable part of the rope guide 5. The support element 36 serves for supporting the pivoting arm 6. The support element 36 is disposed such that the support element 36 supports the pivoting arm 6 on the longitudinal end thereof that faces away from the pivot axis 48. The support element 36 in the direction radial to the rotation axis 50 is disposed between the pivoting arm 6 and the rope drum 3. The support element 36 by way of the longitudinal extent thereof extends in the direction of the rotation axis 50. The support element extends from one flange wall 4 to the other flange wall 4 of the rope drum 3. In the reciprocating movement of the pivoting arm 6, the leverage forces generated by the rotating movement of the rope drum 3 and transmitted via the rope 2 to the pivoting arm 6 by way of the deflection element 7 are at least partially absorbed by the support element 36. The support element 36 in the embodiments is a rail. The support element 36 is fastened to a frame 33 of the winding device 40. The frame 33 of the winding device 40 in the embodiments is formed by the main body 19 of the rope drum 3. However, a winding device having a frame configured separately from the rope drum can also be provided. An embodiment of a winding device without a support element can also be provided.
[0071] The deflection element 7 is disposed on the pivoting arm 6. The deflection element 7 is disposed on that end of the pivoting arm 6 that faces away from the pivot axis 48. The deflection element 7 is disposed such that the rope 2, when being wound onto the rope drum 3, passes the pivoting arm 64 before the deflection element 7. The deflection element 7 is disposed functionally between the pivoting arm 6 and the rope drum 3. The winding device 40 is conceived such that the rope 2 is guided along the pivoting arm 6. The rope 2 is guided from the pivot axis 48 up to a longitudinal end of the pivoting arm 6 that faces the deflection element 7. The rope 2 is guided from the rope window 35 to the deflection element 7 along the pivoting arm 6.
[0072] The deflection element 7 is tiltable about a tilting axis 47. The pivoting arm 6 has a longitudinal axis 49. The tilting axis 47 extends along the longitudinal axis 49 of the pivoting arm 6. The tilting axis 47 runs transversely, in the embodiment perpendicularly, to the pivot axis 48. The tilting axis 47 runs radially to the pivot axis 48. The tilting axis 47 is pivotable about the pivot axis 48.
[0073] Upon passing the pivoting arm 6, the rope 2 is fed to the rope drum 3 by way of the deflection element 7. Rough pre-positioning of the rope guide 5 can take place by pivoting the pivoting arm 6 about the pivot axis 48. Precise positioning can take place in particular in the regions close to the flange disc 4, by tilting the deflection element 7.
[0074] The pivoting arm 6 in FIG. 2 is pivoted such that the deflection element 7 is situated close to the flange disc 4. The pivot axis 48 of the pivoting arm 6, in terms of the rotation axis 50 of the rope drum 3, is disposed in the centre between the flange discs 4. A central plane M runs perpendicularly to the rotation axis 50. The central plane M contains the pivot axis 48. When the longitudinal axis 49 of the pivoting arm 6 is situated in the central plane M, the pivoting arm 6 is disposed in a central position. The pivoting arm 6 in FIG. 2 is pivoted from the central position by a pivoting angle β.
[0075] On its way to the rope drum 3 runs into the rope window 31 in the central plane M. When the pivoting arm 6 is pivoted from a central position, the rope 2 is deflected through the rope window 34. In the embodiments this takes place by virtue of the guide rollers 35.
[0076] The deflection element 7 in FIGS. 1 to 7 in the position of the pivoting arm 6 in which the latter is pivoted by the pivoting angle β is tilted from a basic position. The deflection element 7 in the basic position guides the rope 2 such that the latter in the region of the deflection element runs in a plane E which contains the pivot axis 48 and the tilting axis 47. FIG. 3 shows a view onto the end side of the deflection element 7, in the direction of the tilting axis 47. The rope 2 in the region of the deflection element 7 is guided in a tilting plane F. The deflection element 7, from the basic position thereof, is tilted out of the plane E into the tilting plane F, to the tilted position of the deflection element 7. The deflection element 7 in FIGS. 2 and 3 is tilted by the tilting angle γ. The tilting plane F in relation to the plane E is tilted by the angle γ about the tilting axis 47. The tilting plane F contains the tilting axis 47. The tilting plane F in relation to the plane E is tilted about the tilting axis 47. This tilting of the deflection element 7 in relation to the pivoting arm 6 is also illustrated in FIGS. 5 to 7.
[0077] The deflection element 7 in the embodiment as per FIGS. 1 to 11 is freely movable in relation to the pivoting arm 6. The tilting of the deflection element 7 is caused by the rope 2.
[0078] The schematic illustrations as per FIGS. 8 to 10 show the pivoting arm 6 in the central position. Two further pivoted positions of the single pivoting arm 6, or of the rope guide 5, respectively, are also schematically illustrated. For reasons of improved clarity, the pivoting arm 6 is not plotted in the positions pivoted from the central position.
[0079] The two positions of the pivoting arm 6, schematically plotted in FIGS. 8 to 10, are peripheral positions of the pivoting arm 6. The pivoting arm 6 cannot be pivoted any further about the pivot axis 48. The winding device 1 has a delimitation element 8. The delimitation element 8 is disposed such that a pivoting movement of the pivoting arm 6 about the pivoting axis 48 is limited to a critical angular range Δ. The critical angular range Δ extends in a plane perpendicular to the pivot axis 48. The critical angular range Δ is a single contiguous angular range. The critical angular range Δ is at most 135°, in particular at most 90°, preferably at most 70°, in the embodiment at most 60°. The rope guide 5 has a part which in terms of the main body 19 is pivotable about the pivot axis 48. The pivotable part of the rope guide 5 in the embodiments includes the pivoting arm 6 and the deflection element 7. In the absence of the delimitation element 8, the pivotable part of the rope guide 5 would be pivotable between the flange discs 4 in a maximum flange angular range Ω about the pivot axis 48. The flange angular range Ω is limited by the two flange discs 4. The mutually facing insides of the two flange discs 4 each lie in a plane G. The flange angular range Ω is the range in which the pivotable part of the rope guide 5 is pivotable until the pivotable part impacts the mutually opposite planes G of the flange discs 4. When the pivotable part of the rope guide 5 contacts the plane G, a peripheral region of the flange angular range Ω is defined by the position of the tilting axis 47 in this position. The maximum flange angular range Ω is measured in the basic position of the deflection element 7. In the absence of the delimitation element 8, the pivotable part of the rope guide 5 would be pivotable about the pivot axis 48 in a maximum flange angular range Ω between the planes G of the flange discs 4.
[0080] The critical angular range Δ is smaller than the flange angular range Ω. The critical angular range Δ is at most 80%, in particular at most 75%, in the embodiment at most 70%, of the maximum flange angular range Ω. The critical angular range Δ lies completely within the flange angular range Ω. Those regions of the flange angular range Ω that are not overlapped by the critical angular range Δ are referred to as angular range ϕ. In the embodiments, the angular range ϕ includes two sub-ranges. The critical angular range Δ in the embodiments is disposed so as to be symmetrical in relation to the central plane M. The maximum flange angular range Ω in the embodiments is disposed so as to be symmetrical in relation to the central plane M. The angular range ϕ in the embodiments is disposed so as to be symmetrical in relation to the central plane M. The winding device 40 is conceived such that the deflection element 7 is tiltable about the tilting axis 47 such that the rope 2 is able to be guided into the angular range ϕ outside the critical angular range Δ by the deflection element 7.
[0081] The delimitation element 8 in the embodiments is implemented by a crank mechanism 18. The crank mechanism 18 includes a shaft 11 which is illustrated in FIG. 8. The shaft 11 is rotatable about a shaft axis 46. The shaft 11 in the embodiments, by way of a worm mechanism 20 (FIG. 1), is driven by the motor that drives the rope drum 3. However, it can also be provided that a separate motor is provided for driving the shaft 11. The motor for driving the rope drum 3 is a hydraulic motor. However, this here may also be any other type of motor. The motor drives the rope drum 3. A gearbox, not illustrated, is disposed between the motor and the rope drum 3 in the embodiments. The rope drum 3 is connected to the worm mechanism 20 by way of a chain mechanism 21. A gear wheel of the chain mechanism 21 is connected in a rotationally fixed manner to a worm shaft of the worm mechanism 20. The worm shaft is mounted so as to be rotatable about a worm axis 43 (FIGS. 1 and 4). The worm shaft meshes with a worm wheel which is not illustrated and fixed to the shaft 11. The rope take-up winding device 1 is conceived such that the rope guide 5, in particular the pivoting arm 6 of the rope guide 5, at a specific rotary position of the rope drum 3 in terms of the rotation axis 50, as a function of the rotary position assumes a pivoted position in terms of the pivot axis 48.
[0082] The crank mechanism 18 furthermore includes an eccentric 22 (FIG. 8). The eccentric 22 is connected in a rotationally fixed manner to the shaft 11. The eccentric 22, on the longitudinal end of the eccentric 22 that faces away from the shaft axis 46, has a pin 12. The shaft 11 and the eccentric 22 move the pin 12 about the shaft axis 46. The pin 12 is connected in a rotationally fixed manner to the eccentric 22. A connecting rod 13 is rotatably mounted on the pin 12. The connecting rod 13 connects the pin 12 to a bolt 23 of the pivoting arm 6. The connecting rod 13 is pivotably mounted on the bolt 23. The bolt 23 is connected in a rotationally fixed manner to the pivoting arm 6. The bolt 23 is disposed at a spacing d from the pivot axis 48 (FIG. 2). The spacing d of the bolt 23 from the pivot axis 48 is at least 10%, advantageously at least 20%, in the embodiments at least 25% of a pivoting length 1 of the pivotable part of the rope guide 5, the pivoting length 1 proceeding from the pivot axis 48 and being measured perpendicularly to the pivot axis 48. The bolt 23 is disposed on the longitudinal axis 49 of the pivoting arm 6 (FIG. 8). The lengths of the connecting rod 13 and of the eccentric 22 establish in which angular range the bolt 23, and thus also the pivoting arm 6, are pivotable. In this way, the crank mechanism 18 forms the delimitation element 8.
[0083] However, it may also be provided that the delimitation element 8 is formed by two simple pins which project from the frame 33 (FIG. 8) and in this way limit the pivoting movement of the pivoting arm 6. In one variant of embodiment, the winding device can be implemented completely without positive guiding for the pivoting arm or the rope guide. In this instance, the delimitation element limits only the free pivoting movement of the pivotable part of the rope guide.
[0084] As a result of the pivoting movement of the pivoting arm 6 being limited to the critical angular range Δ and as a result of the tilting capability of the deflection element 7 about the tilting axis 47, the winding device 40 can be of a compact construction and at the same time deliver a positive winding pattern. FIG. 15 shows a comparison between a winding device 40 according to the disclosure and a winding device 41 according to the prior art. The two winding devices 40 and 41 are schematically plotted relative to a single rope drum 3 in a single figure. The winding device 41 has a winding arm 42 with a non-tiltable deflection element 37. The winding arm 42 is illustrated in two different pivoted positions. In the pivoted position of the winding arm 42 close to the flange disc 4, the rope impacts the flange wall 4. The winding angle is 3°. The wrapping angle about the deflection element 37, configured as a single roller, in this pivoted position is 75°.
[0085] The winding device 40 according to the disclosure, likewise illustrated in FIG. 15, likewise has a deflection element 7 configured as a single roller. The diameter of the roller of the winding device 40 in this example corresponds to the diameter of the winding device 41. The pivoting arm 6 in FIG. 15 is in a peripheral position in the peripheral region of the critical angular range Δ. The wrapping angle about the deflection element 7 is likewise 75°. The winding arm 42 of the winding device 41 according to the prior art has a larger spacing from the rotation axis 50 of the rope drum 3 than the pivoting arm 6 of the winding device 40 according to the present disclosure. The deflection element is tilted from the basic position about the tilting axis 47. The rope impacts the flange disc 4. The winding angle is likewise 3°.
[0086] The pivoting arm 6 of the winding device 40 according to the disclosure is significantly shorter than the winding arm 42 of the winding device 41 according to the prior art. Nevertheless, the winding device 40 delivers a positive winding pattern and a winding angle of 3°. By virtue of the present disclosure, the winding device 40 can be of a significantly more compact configuration.
[0087] The winding device 40 in the embodiments as per FIGS. 1 to 14 has a pivot gear 10. The pivot gear 10 is illustrated in FIG. 2 or FIG. 8, for example. The winding device 40 is conceived such that the pivoting arm 6 via the pivot gear 10 is movable in a reciprocating manner in the critical angular range Δ. The pivot gear 10 in the embodiments includes the crank mechanism 18, the worm mechanism 20 and the chain mechanism 21. An embodiment of the winding device in which the pivot gear includes exclusively the crank mechanism may also be provided. An embodiment of the winding device in which the pivot gear is implemented by another type of returning gearbox may also be provided.
[0088] The pivot gear 10 is a component part of a pivot drive. The pivot drive includes a motor. The motor for driving the rope drum 3 in the embodiments is also utilized for driving the pivot gear 10. However, it may also be provided that the pivot drive includes a motor that is configured separately from the motor of the rope drum 3. As a result of the pivot drive 10, the pivoting arm 6 is positively guided. However, it may also be provided that the pivoting arm 6 can move freely in a reciprocating manner in the critical angular range Δ, in particular between the flange discs 4, without a drive. The angular position of the pivoting arm 6 is then this instance determined by the wound position of the rope 2 on the rope drum 3. The pivoting arm 6 follows the rope 2, the latter being wound winding-by-winding in the direction of the rotation axis 50 onto the rope drum 3.
[0089] The pivoting arm 6 in the embodiment as per FIGS. 1 to 11 is positively guided, and the deflection element 7 is freely movable in relation to the pivoting arm 6. The tilting of the deflection element 7 is caused by the rope 2. The rope take-up winding device 1 as per FIGS. 1 to 11 is conceived such that the rope 2, when being wound onto the rope drum 3, in the direction of the rotation axis 50 travels a greater distance than the distance which the free end of the pivotable part of the rope guide 5, by virtue of the pivoting about the pivot axis 48, in the same time travels in the direction of the rotation axis 50. The deflecting element 7, on the way thereof from the central plane M illustrated in FIG. 2 to one of the two peripheral regions of the critical angular range Δ, in particular to one of the two flange discs 4, is tilted by the leading rope 2. The degree of tilting of the deflection element 7 in terms of the basic position in the plane E illustrated in FIG. 3 continually increases in the process. The tilting of the deflection element 7 is at the maximum in the reversal point of the pivoting arm 6. The degree of tilting of the deflection element 7 in terms of the basic position in the plane E decreases on the way of the deflection element 7 from the peripheral region of the critical angular range Δ, in particular from the flange disc 4 to the central plane M. When the rope 2 is being unwound from the rope drum 3, the drum of the rope drum 3 rotates about the rotation axis 50 in the opposite direction. The steps described in the context of winding are performed in the reverse order. The deflection element 7 is tilted by the trailing rope 2.
[0090] The pivot drive 10 in the embodiments includes the crank mechanism 18 already described. Accordingly, the pivot drive 10 has the shaft 11 that is rotatable about the shaft axis 46, the pin 12 which is disposed eccentrically to the shaft axis 46 and is movable about the shaft axis 46, the eccentric 22, the connecting rod 13 and the bolt 23. The pivoting arm 6 is positively controlled by the pivot gear 10, the latter being a component part of the pivot drive. The pivot gear 10 moves the pivoting arm 6 in a reciprocating manner between the peripheries of the critical angular range Δ illustrated in FIG. 8. The shaft axis 46 in the embodiment runs parallel to the pivot axis 48. In the embodiments as per FIGS. 1 to 13, the eccentric 22 guides the pin 12 on an orbit about the shaft axis 46.
[0091] The force of the motor is transmitted to the pivoting arm 6 in particular by way of the gearbox, by way of the rope drum 3, by way of the chain mechanism 21, by way of the worm mechanism 20, and by way of the crank mechanism 18.
[0092] The pivot drive is a returning pivot drive. Two tiers of the rope 2 on the rope drum 3 correspond to one revolution of the crank mechanism 18. The pivot gear 10 includes the worm mechanism 20 and the chain mechanism 21. The total gearing of the worm mechanism 20 and of the chain mechanism 21 corresponds to approximately double the number of rope windings on one rope tier. The total gearing in the embodiments corresponds to a reduction gearing of approximately 20 to 50.
[0093] The total gearing can be adapted to the number of rope windings on one rope tier. In this way, a drum of the rope drum 3 having a larger or smaller length in terms of the direction of the rotation axis 50 can be used. The adaptation of the total gearing in the embodiments takes place by adapting the gearing of the chain mechanism 21. The gearing ratio of the chain mechanism 21 can be varied between 1:1 and 2.5:1. The rotating speed here is reduced by the chain drive 21.
[0094] An alternative embodiment is shown in FIG. 14. The winding device 40 as per FIG. 14 is conceived such that the spacing a between the shaft axis 46 and the pin 12 is varied in the movement of the pin 12 about the shaft axis 46. In the alternative embodiment of the crank mechanism, the crank mechanism instead of the eccentric has a rotating disc 24 and a cam disc 14. The cam disc 14 is fastened in a rotationally fixed manner to the main body 19 of the winding device 40, not illustrated in FIG. 14. The rotating disc 24 is mounted so as to be rotatable in relation to the cam disc 14. The rotating disc 24 is illustrated by dashed lines in FIG. 14. The rotating disc 24 has an elongate bore 25. The elongate bore 25 is an opening which in the direction of the shaft axis 46 completely penetrates the rotating disc 24. The elongate bore 25 has a longitudinal extent. The longitudinal extent of the elongate bore 25 extends in the direction the radial to the shaft axis 46. The length of the longitudinal extent of the elongate bore 25 is a multiple of the diameter of the pin 12. The pin 12 is inserted through the elongate bore 25. The shaft 11, not illustrated in FIG. 14, of the pivot gear 10 is connected in a rotationally fixed manner to the rotating disc 24. The rotating disc 24 is likewise rotated in the rotation of the shaft 11. The pin 12 inserted through the elongate bore 25 here is entrained by the periphery of the elongate bore 25. The pin 12 is established on the connecting rod 13.
[0095] The cam disc 14 has a track 15. The track 15 is an opening which in the direction of the shaft axis 46 completely penetrates the cam disc 14. The track 15 encircles the shaft axis 46 in a closed manner. The pin 12 is inserted through the track 15 in the direction of the shaft axis 46. The track 15 and the elongate bore 25 overlap when viewed in the direction of the shaft axis 46. The bolt 12 in the direction of the shaft axis 46 is inserted through the track 15 as well as through the elongate bore 25. In the rotation of the rotating disc 24 about the shaft axis 46 the pin 12 is entrained by the elongate bore 25 and in the track 15 is guided about the shaft axis 46. The track 15 guides the pin 12 on the path thereof about the shaft axis 46. The spacing a of the pin 12 from the shaft axis 46 is varied in the process. The track 15 is configured such that the track 15 causes the variation of the spacing a of the pin 12.
[0096] The spacing a as a function of the angular position of the rotating disc 24 is varied by the track 15 such that a constant rope pitch results when the rope is being wound on the rope drum 3. The rope take-up winding device 1 is conceived such that the pivoting arm 6 in a rotation of the rope drum 3 about the rotation axis 50 is offset in the direction of the rotation axis 50 of the rope drum 3 by 100% to 110% of the rope diameter c of the rope 2 illustrated in FIG. 6, in particular by 100% to 105% of the rope diameter c, in the embodiment by 100% to 102% of the rope diameter c. This applies in particular when the alternative crank mechanism is used in the winding device 40 as per FIGS. 12 and 13. The crank mechanism as per FIG. 14 can also be used in the embodiments as per FIGS. 1 to 13.
[0097] Irrespective of the specific embodiment of the crank mechanism, the pivotable part of the rope guide 5 in the embodiments as per FIGS. 1 to 13 is pivotable about the pivot axis 48. As mentioned, an embodiment in which the pivotable part of the rope guide 5 is not positively controlled but freely pivotable is also conceivable. As is illustrated in FIG. 2, the pivotable part of the rope guide 5 has a pivoting length l which is measured, proceeding from the pivot axis 48, perpendicularly to the pivot axis 48. The flange discs 4 each have a largest diameter measured perpendicularly to the rotation axis 50. The larger of these two diameters is referred to as the maximum diameter d. The pivoting length l of the pivotable part of the rope guide 5 is at most 100%, in particular at most 95%, in the embodiment at most 90%, of the maximum diameter d.
[0098] FIG. 11 shows the deflection element 7. The deflection element 7 has a rope entry 26. The rope 2 is fed to the deflection element 7 through the rope entry 26. The deflection element 7 has a rope exit 27. The rope 2 exits the deflection element 7 at the rope exit 27. The rope 2 is deflected in the deflection element 7.
[0099] Only a single deflection roller is typically used to this end in the prior art. In a deflection of the rope of approximately 90°, a wrapping angle of the single roller of approximately 90° is also required in this instance. Should the radius of the single roller be chosen to be too small, this can result in excessive and rapid wear of the rope. In contrast, a large radius of the single deflection roller requires a large installation space and prevents the single deflection roller from being able to be disposed at the desired small radial spacing from the rope drum.
[0100] A plurality of rollers 16 are provided in the deflection element 7 as per the embodiments. The rollers 16 are disposed on a cam track 17. The rollers 16 are mounted so as to be rotatable on a basic member 28 of the deflection element 7. The rollers 16 are disposed so as to be directly next to one another on the cam track 17. The wrapping angle of the rope 2 about a single one of the plurality of rollers 16 is in each case less than 30°, in particular less than 20°, in the embodiment less than 10°. Six rollers 16 are provided in the embodiment. The cam track 17 can reproduce a circle. The curvature of the cam track 17 in the embodiment is greater than that of a circle through the rotation axes of the two outermost rollers, the central axis of the circle running parallel to the rotation axes. The mutual spacing of the individual rollers 16 is less than 100%, in particular less than 50%, in the embodiment less than 5%, of the diameter of the smallest roller 16. The diameters of the rollers 16 are identical in the embodiment. The rope 2 in the deflection element 7 is guided on the deflection rollers 16 from the rope entry 26 to the rope exit 27. The basic member 28 on both sides of the rope 2 delimits a guiding space for the rope 2 in the direction of the rotation axes of the rollers 16.
[0101] FIGS. 12 and 13 show an alternative embodiment of the winding device 40, or of the rope take-up winding device 1. The winding device 40 as per FIGS. 12 and 13 differs from the winding device as per FIGS. 1 to 11 only in that an actuation means 9 is additionally provided. The other components of the winding device 40 as per FIGS. 12 and 13 are embodied so as to be identical to the components of the winding device 40 as per FIGS. 1 to 11. Accordingly, identical reference signs are also used.
[0102] The deflection element 7 in terms of the tilting axis 47 is disposed in a tilted position. The pivoting arm 6 in terms of the pivot axis 48 is disposed in a pivoted position. The winding device 40 as per FIGS. 12 and 13 is conceived such that the actuator 9 predefines the tilted position of the deflection element 7 as a function of the pivoted position of the pivoting arm 6. The actuator 9 in the embodiment as per FIG. 12 includes a guide slot 29, a guide slot pin 30 and a tilting element 31. The tilting element 31 is connected in a rotationally fixed manner to the tiltable deflection element 7. The guide slot pin 30 is established on the tilting element 31. The guide slot pin 31 in the direction of the tilting axis 47 projects beyond the tilting element 31. The guide slot pin 30 is disposed eccentrically to the tilting axis 47. The guide slot pin 30 has a spacing from the tilting axis 47 that is measured in the direction of the rotation axis 50. The guide slot pin 30 has a spacing from the deflection element 7 that is measured in the direction of the rotation axis 50. The guide slot pin 30 is inserted through a guide slot track 32 of the guide slot 29. The guide slot track 32 is an opening in the guide slot 29 that completely penetrates the guide slot 29 in the direction of the tilting axis 47.
[0103] As is illustrated in FIG. 13, the tilting axis 47 in a pivoting plane S is pivotable about a pivot axis 48. The pivoting plane S is perpendicular to the pivot axis 48. When the deflection element 7 is situated in the central plane M between the flange discs 4, the guide slot pin 30 by way of the central axis thereof is disposed in the pivoting plane S. The guide slot track 32 runs obliquely to the pivoting plane S. When the deflection element 7 is pivoted from the central plane M, the guide slot pin 30, in particular the central axis of the guide slot pin 30, by virtue of the guide slot pin 30 being guided in the guide slot track 38 of the guide slot 29, is moved out of the pivoting plane S. Since the guide slot pin 30 is fastened on the tilting element 31 so as to be eccentric to the tilting axis 47, the tilting element 31 is tilted when the guide slot pin 30 is deflected from the pivoting plane S. When the pivoting arm 6 is being pivoted about the pivot axis 48, from the central plane M towards one of the two peripheral regions of the critical angular range Δ, in particular towards one of the two flange discs 4, the deflection element 4 is continuously tilted ever more about the tilting axis 47. The guide slot track 32 has a continuous profile. However, a guide slot track which has a discontinuous profile and causes an abrupt change in the tilted position of the deflection element 7 may also be provided.
[0104] The actuator 9 causes a dependency of the tilted position of the deflection element 7 on the pivoted position of the pivoting arm 6. The actuator can also be implemented in any other conceivable manner. For example, a separate drive, which by way of a control unit is tuned to the pivot drive, can be provided for tilting the deflection element 7. It is likewise conceivable that the tilted position of the deflection element 7 is implemented by a gearbox connection to the pivot drive. The positive control of the tilting of the deflection element 7 can also be implemented by way of a thrust member, for example, which is mounted so as to be tiltable about an axis which extends parallel to the line of intersection of the central plane M illustrated in FIG. 13 and of the pivoting plane S. A point at the base of the deflection element here may move only in a plane parallel to the pivoting plane S illustrated in FIG. 13. The length of the thrust member changes when the thrust member is pivoted. The deflection element 7 is pivoted about the pivot axis of the thrust member to the same degree as the thrust member.
[0105] It is understood that the foregoing description is that of the preferred embodiments of the invention and that various changes and modifications may be made thereto without departing from the spirit and scope of the invention as defined in the appended claims.
