JP2016216144A - Rope arranging mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rope arranging mechanism for reducing a fleet angle without any trouble.SOLUTION: In a rope arranging mechanism arranging a plurality of ropes R1 to R3 from a working machine body 10 to a boom tip part 24, the ropes R1 to R3 are individually arranged from winch drums 15 to 17 arranged at the working machine body 10 through idler sheaves 31 to 33 arranged at the boom tip part 24, to point sheaves 34 to 36 arranged on the leading end side farther than the idler sheaves 31 to 33. At least one idler sheave 32 or 33 of the idler sheaves 31 to 33 is made into a slide type.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a rope routing mechanism for routing a plurality of ropes from a work machine main body to a boom tip.

  For example, Patent Literature 1 discloses a rope routing mechanism for routing a rope to an auxiliary jib sheave via a boom guide sheave provided at the boom tip of a crane. In this rope routing mechanism, two left and right boom guide sheaves are provided, and only one auxiliary jib sheave is provided. In such a configuration, if the auxiliary jib sheave is arranged so that the fleet angle when passing through one boom guide sheave is reduced, the fleet angle when passing through the other boom guide sheave is increased.

  Therefore, in Patent Document 1, it is configured so that the half-cracked spacer can be attached to and detached from the support shaft to which the auxiliary jib sheave is attached, and the position of the auxiliary jib sheave can be changed by changing the attachment position of the half-cracked spacer. It has become. Accordingly, even when the rope is routed through the left or right boom guide sheave, the fleet angle can be reduced by appropriately positioning the auxiliary jib sheave using the half-break spacer.

JP-A-63-96096

  However, the position of the boom guide sheave described in Patent Document 1 is fixed, and it is not possible to improve the fleet angle between the winch drum and the boom guide sheave. Problems are likely to occur. Furthermore, since it takes time to attach and detach the half-spaced spacer, there is room for improvement in this respect.

  Then, an object of this invention is to provide the rope routing mechanism which can make a fleet angle small without taking an effort.

  To achieve the above object, the present invention provides a rope routing mechanism for routing a plurality of ropes from a work machine main body to a boom tip, wherein each of the plurality of ropes is disposed on the work machine main body. From the winch drum to the second sheave arranged further to the tip side than the first sheave via the first sheave arranged at the tip of the boom. At least one of the first sheaves is slidable with respect to a support shaft that rotatably supports the first sheave.

  In the present invention, a plurality of ropes are provided from the winch drum to the second sheave via the first sheave, and at least one first sheave is of a slide type that can slide with respect to the support shaft. ing. Thus, if the first sheave is a slide type, the fleet angle can be reduced as compared with the case where the first sheave is fixed, without requiring laborious work such as attaching and detaching the spacer. Can do. That is, according to the present invention, the fleet angle can be reduced without taking time and effort.

It is a side view of the crane concerning the embodiment of the present invention. It is a top view which shows a boom front-end | tip part typically. It is a schematic diagram for demonstrating a fleet angle. It is a schematic diagram for demonstrating a fleet angle. It is a graph which shows the improvement rate of a fleet angle.

  Hereinafter, an embodiment of a crane provided with a rope routing mechanism according to the present invention will be described with reference to the drawings. In the embodiment described below, the case where the rope routing mechanism according to the present invention is applied to a mobile crane will be described, but the rope routing mechanism according to the present invention can also be applied to a fixed crane. Furthermore, the rope routing mechanism according to the present invention can be applied to work machines such as a pile driver and a container crane.

  FIG. 1 is a side view of a crane 1 according to an embodiment of the present invention. The crane 1 includes a main body 10 and a boom 20 supported by the main body 10 so as to be able to move up and down, and a plurality of wire ropes (hereinafter simply referred to as “ropes”) R <b> 1 from the main body 10 to the tip of the boom 20. R3 is routed. Suspension tools 37 to 39 are attached to the ends of the ropes R1 to R3, respectively. As the suspenders 37 to 39, necessary ones such as hooks and buckets can be appropriately selected according to work.

  The main body 10 mainly includes an upper swing body 11 and a lower traveling body 12. A cab 13 is provided at the front (right side in FIG. 1) of the upper swing body 11 and a counterweight 14 is provided at the rear (left side in FIG. 1). A base end portion of the boom 20 is swingably attached to the side of the cab 13 (the back side in FIG. 1). The lower traveling body 12 is composed of a crawler, and enables the crane 1 to move. However, it is not essential that the lower traveling body 12 is a crawler, and for example, a wheel or the like may be used.

  Three winch drums 15 to 17 (main drum 15, auxiliary drum 16, and third drum 17) are disposed behind the cab 13 of the upper swing body 11. A main rope R1 is wound around the main drum 15, an auxiliary rope R2 is wound around the auxiliary drum 16, and a third rope R3 is wound around the third drum 17. The winch drums 15 to 17 are connected to a motor (not shown) via a speed reducer, and the rotational output from the motor is decelerated and transmitted to the winch drums 15 to 17.

  The boom 20 includes a lower boom 21 having a lattice structure, an upper boom 22 fixed to the distal end portion of the lower boom 21, and a distal end boom 23 attached to the distal end portion of the upper boom 22. The The tip boom 23 can swing with respect to the upper boom 22 and can be fixed to the upper boom 22 in a state in which the relative posture with respect to the upper boom 22 is changed. In the following description, the upper boom 22 and the tip boom 23 are collectively referred to as a boom tip portion 24.

  FIG. 2 is a top view schematically showing the boom tip 24. As shown in FIG. 2, the upper boom 22 has a configuration in which a pair of plate members 22 a and 22 b that are spaced apart in the left-right direction are connected by support shafts 25 to 27. Similarly, the tip boom 23 has a configuration in which a pair of plate members 23 a and 23 b that are spaced apart in the left-right direction are connected by support shafts 27 and 28. The pair of plate members 23 a and 23 b is disposed outside the pair of plate members 22 a and 22 b in the left-right direction, and these are connected by a common support shaft 27.

  The support shafts 25 to 28 rotatably support the sheaves 31 to 36. An idler sheave 31 that does not slide in the axial direction (hereinafter, such a sheave is referred to as a “fixed type”) is attached to the support shaft 25. The support shaft 26 is attached with idler sheaves 32 and 33 slidable in the axial direction (hereinafter, such sheave is referred to as “sliding type”). A fixed type point sheave 34 is attached to the support shaft 27. Fixed point sheaves 35 and 36 are attached to the support shaft 28.

  The idler sheaves 31 to 33 corresponding to the “first sheave” of the present invention function as a route guide for routing the ropes R1 to R3 from the winch drums 15 to 17 to the point sheaves 34 to 36. The point sheaves 34 to 36 corresponding to the “second sheave” of the present invention are arranged further on the tip side than the idler sheaves 31 to 33, and function as suspension starting points when the suspension tools 37 to 39 are suspended. To do. The idler sheaves 32 and 33 are sheaves having the same shape and the same dimensions. Similarly, the point sheaves 35 and 36 are sheaves having the same shape and size.

  The ropes R1 to R3 are routed in the rope routing mechanism configured as described above. Specifically, the main rope R <b> 1 is routed from the main drum 15 to the point sheave 36 via the slide type idler sheave 33. The auxiliary rope R <b> 2 is routed from the auxiliary drum 16 to the point sheave 35 via the sliding idler sheave 32. The third rope R3 is routed from the third drum 17 through the fixed idler sheave 31 to the point sheave 34. As shown in FIGS. 1 and 2, the rope route of the third rope R <b> 3 is defined so as to pass between the main rope R <b> 1 and the auxiliary rope R <b> 2 between the idler sheave 31 and the point sheave 34.

  The slide ranges of the slide type idler sheaves 32 and 33 are respectively between the position indicated by the solid line and the position indicated by the broken line in FIG. 2 so that the slide ranges do not overlap each other. Specifically, the sliding ranges of the idler sheaves 32 and 33 are adjusted by appropriately adjusting the positions and dimensions of the winch drums 15 and 16 and the point sheaves 35 and 36 that define the rope paths of the main rope R1 and the auxiliary rope R2. Like that.

  The point sheave 34 as the main point is composed of a plurality of sheaves. This is because the heavy rope 37 can be suspended by suspending the third rope R3 around the suspension 37 that is suspended from the point sheave 34 a plurality of times. However, it is not essential to configure the point sheave 34 with a plurality of sheaves.

  Here, the fleet angle will be described. 3A and 3B are schematic diagrams for explaining the fleet angle. Specifically, FIG. 3A shows a case where the idle sheave IS is a fixed type, and FIG. 3B shows a case where the idler sheave IS is a slide type. The width of the winch drum WD is W, the distance from the winch drum WD to the idle sheave IS is D1, and the distance from the idle sheave IS to the point sheave PS is D2. More precisely, the distance D1 is the distance between the central axis of the winch drum WD and the central axis of the idle sheave IS, and the distance D2 is the distance between the central axis of the idler sheave IS and the central axis of the point sheave PS. It is defined as

  As shown in FIG. 3A, when the idler sheave IS is a fixed type, the fleet angle α is determined by the width W of the winch drum WD and the distance D1 from the winch drum WD to the idler sheave IS. On the other hand, as shown in FIG. 3B, when the idler sheave IS is a slide type, the rope R is stretched substantially linearly from the winch drum WD to the point sheave PS by sliding the idler sheave IS. Therefore, the fleet angle β is determined by the width W of the winch drum WD and the distance D1 + D2 from the winch drum WD to the point sheave PS.

  That is, the fleet angle β when the idler sheave IS is a slide type is smaller than the fleet angle α when the idler sheave IS is a fixed type. Incidentally, when the fleet angles α and β are increased, problems such as turbulence are likely to occur. For example, the mobile crane structure standard Article 21 defines that the fleet angle is kept at 4 degrees or less.

  Here, the ratio of the distance D1 from the winch drum WD to the idle sheave IS to the distance D2 from the idle sheave IS to the point sheave PS, and the improvement rate of the fleet angle by changing the idler sheave IS from the fixed type to the slide type The result of investigating the relationship with is shown in FIG. As apparent from the graph of FIG. 4, when D1 / D2 is 10 or less, the improvement rate is approximately 10% or more, and a large effect is obtained. However, when D1 / D2 exceeds 10, the improvement effect is It became clear that it was not so big.

  Here, the distance D1 from the winch drum WD to the idle sheave IS is fixed at 7000 mm, the width W of the winch drum WD is 300 to 1400 mm, and the distance D2 from the idler sheave IS to the point sheave PS is changed from 100 to 7000 mm. However, there was almost no difference depending on the value of the width W of the winch drum WD. That is, in the actual crane 1, it is understood that the influence of the width W of the winch drum WD on the improvement rate of the fleet angle is slight, and D1 / D2 is a dominant factor with respect to the improvement rate of the fleet angle. It was.

(effect)
As described above, in the crane 1 of the present embodiment, at least one idler sheaves 32 and 33 among the plurality of idler sheaves 31 to 33 are slidable. As described above, if the idler sheaves 32 and 33 are slidable, the fleet angle can be reduced as compared with the case where the idler sheaves 32 and 33 are fixed, without requiring troublesome work such as attaching and detaching the spacer. can do. That is, the fleet angle can be reduced without taking time and effort. Further, since the fleet angle can be reduced between the winch drums 15 and 16 and the idler sheaves 32 and 33, the arrangement of the point sheaves 35 and 36 is not limited, and the arrangement of the point sheaves 35 and 36 is free. There is also an effect that the degree can be improved.

  In the present embodiment, among the plurality of idler sheaves 31 to 33, the one having the shortest distance from the corresponding winch drums 15 to 17, specifically the idler sheave 33 on which the main rope R1 is hung. (See FIG. 1) is a slide type. As is apparent from FIGS. 3A and 3B, the smaller the distance between the winch drum WD and the idler sheave IS, the larger the fleet angle, so the effect of reducing the fleet angle when changing from the fixed type to the slide type is large. Become. For this reason, the effect of reducing the fleet angle can be increased by making the idler sheave 33 having the shortest distance from the winch drums 15 to 17 a slide type.

  In the present embodiment, at least one idler sheave 31 among the plurality of idler sheaves 31 to 33 is fixed. When all the idler sheaves 31 to 33 are slidable, the idler sheaves 31 to 33 and the ropes R1 to R3 hung on the idler sheaves 31 to 33 easily interfere with each other. Therefore, by making at least one idler sheave 31 fixed, such interference can be suppressed and the fleet angle can be reduced more reliably.

  In this embodiment, the fixed idler sheave 31 is attached to a support shaft 25 different from the slide type idler sheaves 32 and 33. By doing so, it is possible to reliably prevent the slide type idler sheaves 32 and 33 from interfering with the fixed type idler sheave 31. In addition, the slide range of the slide type idler sheaves 32 and 33 can be secured wider, and the fleet angle can be effectively reduced.

  In the present embodiment, the other rope R3 is configured to pass between the two ropes R1 and R2, and the two ropes R1 and R2 are hung on the slide type idler sheaves 32 and 33. The other rope R3 is hung on a fixed idler sheave 34. In this way, by hanging the rope R3 passing between the two ropes R1 and R2 on the fixed idler sheave 34, the rope path of the middle rope R3 is fixed, and the ropes R1 and R2 existing on both sides thereof are fixed. Interference can be effectively suppressed.

  In this embodiment, the two slide type idler sheaves 32 and 33 on which the two ropes R1 and R2 are respectively hung are attached to the same support shaft 26. For this reason, the number of parts required for constituting the rope routing mechanism can be reduced.

  In the present embodiment, the slide ranges of the plurality of slide type idler sheaves 32 and 33 attached to one support shaft 26 do not overlap each other. For this reason, it can prevent reliably that the idler sheaves 32 and 33 mutually interfere.

  Further, in the crane 1 of the present embodiment, the distance between the sliding idler sheave 32 (33) and the winch drum 16 (15) corresponding thereto is the point corresponding to the idler sheave 32 (33). The distance to the sheave 35 (36) is 10 times or less. For this reason, as apparent from FIG. 4, by changing the idler sheave 32 (33) from the fixed type to the slide type, the improvement rate of the fleet angle can be as great as about 10% or more.

(Other embodiments)
The present invention is not limited to the above embodiment, and the elements of the above embodiment can be appropriately combined or variously modified without departing from the spirit of the present invention.

  In the above embodiment, the idler sheave 31 is fixed and the idler sheaves 32 and 33 are slidable. However, which idler sheave is fixed or slidable can be changed as appropriate. For example, the idler sheave 31 may be a slide type.

  In the above embodiment, the idler sheave 31 is attached to the support shaft 25, and the idler sheaves 32 and 33 are attached to the support shaft 26. However, this can be changed as appropriate. For example, all idler sheaves 31 to 33 may be attached to the same support shaft, or all idler sheaves 31 to 33 may be attached to different support shafts.

  Moreover, although the three ropes R1-R3 shall be routed in the crane 1 of the said embodiment, the number of ropes may be two or four or more.

1 Crane (work machine)
10 Main body (work machine main body)
24 Boom tip 25-28 Support shaft 31 Fixed idler sheave (first sheave)
32, 33 Sliding idler sheave (first sheave)
34-36 point sheave (second sheave)
R1-R3 rope 15-17 winch drum

Claims (8)

A rope routing mechanism for routing a plurality of ropes from the work machine body to the boom tip,
Each of the plurality of ropes is disposed further to the distal end side than the first sheave from the winch drum disposed in the work machine main body via the first sheave disposed at the boom distal end portion. To the second sheave,
A rope routing mechanism characterized in that at least one of the plurality of first sheaves is slidable with respect to a support shaft that rotatably supports the first sheave.   2. The rope routing mechanism according to claim 1, wherein among the plurality of first sheaves, the one having the shortest distance from the winch drum corresponding to each of the plurality of first sheaves is the sliding first sheave.   The rope routing mechanism according to claim 1 or 2, wherein at least one of the plurality of first sheaves is a fixed type that does not slide relative to the support shaft.   4. The rope routing mechanism according to claim 3, wherein the fixed first sheave is attached to the support shaft different from the sliding first sheave.   When the other ropes are configured to pass between the two ropes, the two ropes are hung on the sliding first sheave, and the other ropes are fixed. The rope routing mechanism according to claim 3 or 4, being hung on the first sheave of the formula.   The rope routing mechanism according to claim 5, wherein the two first sliding sheaves on which the two ropes are respectively hung are attached to the same support shaft.   The slide ranges of the plurality of first slide sheaves are configured not to overlap each other when a plurality of the first slide sheaves are attached to one support shaft. 7. The rope routing mechanism according to any one of 6 above.   The distance between the sliding first sheave and the corresponding winch drum is not more than 10 times the distance between the sliding first sheave and the corresponding second sheave. The rope routing mechanism according to any one of claims 1 to 7.

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