WO2015198413A1 - Drum for load handling machine, and load handling machine - Google Patents

Abstract

The present invention provides a drum for a load handling machine, the drum allowing a rope to be wound therearound in multiple layers such that the windings are parallel to each other. Convex-shaped guide sections (12) for supporting and guiding a rope are arranged at predetermined intervals on the surface of a circular cylindrical drum body (11) so as to extend in the circumferential direction thereof. The guide sections (12) are formed to have a circular arc cross-sectional shape having a curvature radius greater than or equal to the radius of the rope. Supports (13) for supporting the rope are provided between the guide sections (12).

Description

Drum for cargo handling machine and cargo handling machine

The present invention relates to a technology of a device for raising and lowering a load using a rope wound around a drum such as a hoist or a winch.

Conventionally, as this type of apparatus, for example, a system called parallel winding is known in Japan, and a system called a balanced cable spooling system (see, for example, Patent Document 1) is known in Europe and the United States.
If the rope is wound in multiple layers on the drum by this type of device, it is possible to perform aligned winding without generating turbulent winding. However, in this conventional technique, there is a constraint condition such as fleet angle. It is necessary to give tension to the sag without slack.

However, the fleet angle is large, the unwinding speed of the rope and the followability of the load are bad, and when the rope speed is high and the acceleration / deceleration is repeated, the rebound (bounce) phenomenon due to the spring action of the rope occurs, The rope may come out of the groove and jump to the adjacent groove or the groove ahead.
In addition, in the prior art, the rope is guided by the guide groove provided in the drum. Therefore, when the rope comes off the groove, the rope is damaged and the life of the rope is shortened. There are challenges.

U.S. Pat. No. 2,734,695

The present invention has been made to solve the above-described problems of the prior art. The object of the present invention is to damage the rope when winding and unwinding the rope wound around the drum. Therefore, it is to provide a drum that can be handled safely and to provide a technique for extending the life of the rope.

In order to achieve the above object, the present invention is a drum for a cargo handling machine capable of winding a rope in multiple stages by parallel winding, for supporting and guiding the rope on the surface of a cylindrical drum body. The plurality of convex curved guide portions are cargo handling machine drums provided at predetermined intervals along the circumferential direction of the drum main body portion.
The present invention is also effective when the guide portion is formed in a circular arc shape having a radius of curvature equal to or greater than the radius of the rope.
In this invention, it is effective also when the support part for supporting the said rope is provided between the said guide parts.
In the present invention, the drum main body portion has a concave rope accommodating portion for accommodating and fixing the tip end portion of the rope, and a portion for guiding the rope when the rope is pulled out from the rope accommodating portion. It is also effective in the case where a rope whose end is bent so as to correspond to the shape is accommodated and fixed in the rope accommodating portion of the drum main body.
Further, the present invention is a cargo handling machine including any of the above-described drums for a cargo handling machine, a drum drive mechanism that rotationally drives the drum for a cargo handling machine, and a control unit that controls the operation of the drum drive mechanism.
The present invention further includes a rope feeding mechanism for guiding or moving the rope wound around or around the drum of the cargo handling machine in the direction of the axis of rotation of the drum. A rod-shaped rope reciprocating feed screw which is provided in parallel with the rotation axis and is rotatable with the drum for cargo handling machine, and a threaded portion of the rope reciprocating feed screw are mounted, and with the rotation of the rope reciprocating feed screw A block-shaped moving body configured to move in the longitudinal direction of the rope reciprocating feed screw and having a rope guide portion for guiding a rope unwound from the drum for a cargo handling machine, and the rope reciprocating feed screw; A rod-shaped guide shaft that is provided in parallel and guides the movable body in contact with the movable body, the guide shaft being rotatable If you have been made it is also effective.
The present invention further includes a rope reverse winding detection mechanism for detecting a reverse winding state of the rope unwound from the cargo handling machine drum, wherein the reverse winding detection mechanism is a rope unwound from the cargo handling machine drum. And a limit lever unit that is rotatably attached to the movable body and that operates a limit switch by the rotational movement. The limit lever unit is a rope that is unwound from the drum for a cargo handling machine. This is also effective when the limit switch is operated by rotating according to the displacement of the path.
In the present invention, it further has a no-load detection mechanism for detecting an unloaded state of the rope unwound from the drum for the cargo handling machine, and the no-load detection mechanism is provided on the rope unwound from the drum for the cargo handling machine. And a loadless lever unit that is attached to the movable body so as to be able to rotate and that operates a limit switch by the rotational movement. The loadless lever unit is unwound from the drum for cargo handling machinery. This is also effective when the limit switch is operated by rotating in accordance with the change in the tension of the rope.
The present invention further includes a rope presser mechanism for pressing a rope wound around the drum for a cargo handling machine, wherein the rope presser mechanism is connected to a rope wound around a central portion of a drum body portion of the drum for a cargo handling machine. It is also effective in the case of having a rope presser roller formed in a shape that does not come into contact with the rope wound around both ends of the drum main body of the cargo handling machine drum while making contact and pressing.
In the present invention, the drum drive mechanism includes a DC or AC motor, and the control unit includes a rotation control unit that sets acceleration time and deceleration time of the motor, and an addition set in the rotation control unit. An acceleration / deceleration waveform control unit that determines a soft acceleration waveform and a soft deceleration waveform of the motor based on a deceleration signal, and a PWM generation unit that generates a PWM waveform based on a drive waveform signal from the acceleration / deceleration waveform control unit. Even when the cargo handling machine drum is lowered, the motor is driven by PWM control using the rotation control unit, the acceleration / deceleration waveform control unit, and the PWM generation unit. It is effective.

According to the present invention, it is possible to provide a drum that can be safely handled without damaging the rope when the rope wound around the drum is wound up and down, and the life of the rope can be extended.

(A): Front view showing an external configuration of an embodiment of a hoist that is a cargo handling machine according to the present invention (b): Side view showing an external configuration of the hoist Front view showing an external configuration of a drum in the present embodiment (A) (b): It is the front view which shows the external appearance structure of the drum main-body part in the same drum, FIG.3 (a) is the figure seen from one side, FIG.3 (b) is the figure seen from the other side. Development view of the drum body Side view for explaining a straight portion and an intersecting portion of the drum main body Explanatory drawing which shows the arrangement structure of the support part of the drum main-body part FIGS. 7A to 7C are explanatory views showing the configuration and dimensional relationship of the guide portion and the support portion in the drum main body, and FIGS. 7D and 7E are the configurations of the first and second guide portions. Explanatory drawing showing (A)-(d): The figure which shows typically the cross-sectional structure of the drum main-body part of a prior art. (A)-(c): The figure which shows typically the principle of the drum main-body part of this invention. The block diagram which shows the structure of the control part of this Embodiment (A) (b): The structure of the drive system of this Embodiment is shown, FIG. 11 (a) is an internal front view, FIG.11 (b) is an internal side view. FIGS. 12A to 12C show an embodiment of a rope feeding mechanism used in the present invention. FIG. 12A is a partial cross-sectional view showing the overall configuration, and FIG. 12B is a configuration of a shifter block. FIG. 12C is a side view showing the configuration of the main part of the rope feeding mechanism. (A)-(d): Explanatory drawing which shows operation | movement which winds the rope in this Embodiment around a drum main-body part (the 1) (A)-(c): Explanatory drawing which shows operation | movement which winds the rope in this Embodiment around a drum main-body part (the 2) Schematic configuration diagram of an embodiment of a rope reverse winding detection mechanism and no-load detection mechanism used in the present invention (A) (b): The limit lever unit of the rope reverse winding detection mechanism of this embodiment is shown, FIG. 16 (a) is a side view, and FIG. 16 (b) is a front view. (A)-(c): Shows the configuration of the rope reverse winding detection mechanism, FIG. 17 (a) is a front view showing the overall configuration, and FIG. 17 (b) shows the main configuration of the rope reverse winding detection mechanism. FIG. 17 (c) is a side view showing the overall configuration of the rope reverse winding detection mechanism. (A) (b): Explanatory drawing which shows operation | movement of a rope reverse winding detection mechanism. FIGS. 19A to 19C show the no-load detection lever unit of the no-load detection mechanism used in the present invention. FIG. 19A is a partial cross-sectional view seen from the no-load detection guide sheave side. b) is a side view, and FIG. 19 (c) is a partial sectional view as seen from the guide sheave side. (A)-(c): Shows the configuration of the no-load detection mechanism, FIG. 20 (a) is a front partial sectional view showing the overall configuration, and FIG. 20 (b) shows the main configuration of the no-load detection mechanism. FIG. 20C is a side view showing the entire configuration of the no-load detection mechanism. (A) (b): Explanatory drawing which shows operation | movement of the no-load detection mechanism. (A) (b): The figure which shows the structure of a rope presser mechanism Explanatory drawing which shows the dimensional relationship of the rope presser roller of the rope presser mechanism (A) (b): This shows a mechanism for preventing the rope end portion from lifting up in the present embodiment. FIG. 24 (a) is a side view showing the main part of the drum, and FIG. 24 (b) is FIG. AA line cross section (A) to (d): showing a mechanism for preventing the rope end portion from rising in the present embodiment. FIG. 25 (a) is an explanatory view showing the configuration of the tip of the conventional rope, and FIG. 25 (b). FIG. 25 is an explanatory view showing a case where a conventional rope is fixed to a drum main body, FIG. 25C is an explanatory view showing a configuration of a tip portion of the rope of the present embodiment, and FIG. 25D is a present embodiment. Explanatory drawing showing the case of fixing the rope to the drum body

Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings.
Fig.1 (a) is a front view which shows the external appearance structure of embodiment of the hoist which is a cargo handling machine based on this invention, FIG.1 (b) is a side view which shows the external appearance structure of the hoist.
As shown in FIGS. 1 (a) and 1 (b), the hoist 1 of the present embodiment is used in a factory or the like. For example, the hoist 1 is hung by a support hook 3 on a support shaft 2 provided at a high place. It is configured.

The hoist 1 has an apparatus main body 4 in which a drum 10 and the like to be described later are accommodated. A rope 20 unwound from the drum 10 is led downward from a main body frame 4a at the lower part of the apparatus main body 4, and the rope 20 The hook 6 provided at the front end portion is moved upward or downward.

Here, a hollow weight 5 for adjusting the tension of the rope 20 is detachably mounted on the hook 6.
A DC or AC motor 7 for rotating the drum 10 is provided on one side of the apparatus body 4, and the rotation speed of the drum 10 is controlled on the other side of the apparatus body 4. A drive mechanism unit 8 is provided.

In the drive mechanism unit 8, a reduction gear, a clutch mechanism, a brake mechanism, and the like (not shown) are provided.
On the other hand, a control unit 9 is provided on the front surface of the main body frame 4a.
The control unit 9 controls the driving of the motor 7, and controls the rotation of the motor 7 by an operation switch 9 a connected to the control unit 9.

FIG. 2 is a front view showing an external configuration of the drum in the present embodiment.
3 (a) and 3 (b) are front views showing the external configuration of the drum body of the drum, FIG. 3 (a) is a view from one side, and FIG. 3 (b) is a view from the other side. It is a figure.

4 is a development view of the drum main body, FIG. 5 is a side view for explaining a straight portion and an intersection of the drum main body, and FIG. 6 is an arrangement configuration of support portions of the drum main body. It is explanatory drawing which shows.

As shown in FIG. 2, a drum (handling machine drum) 10 of the present embodiment has a cylindrical drum body 11, and first and second flanges are provided at both ends of the drum body 11. 10a and 10b are provided in parallel.
The rope 20 is wound around the drum main body 11 in multiple layers in parallel.

As shown in FIGS. 3A and 3B, the drum body 11 has a plurality of convex curved guide portions 12 provided on the surface thereof at predetermined intervals along the circumferential direction.
In the case of the present embodiment, each guide portion 12 is formed in an arc shape in cross section, and a planar support portion 13 is provided between the guide portions 12, for example.

As shown in FIGS. 3 to 6, the surface area of the drum main body 11 includes a first straight portion 14, a second straight portion 15, a first intersecting portion (crossover portion) 16, and a second intersecting portion. It is divided into regions (crossover portions) 17.
In the first and second linear portions 14 and 15, the guide portion 12 and the support portion 13 are formed in a straight line and parallel along the circumferential direction of the drum body portion 11, that is, the direction orthogonal to the rotation axis. Yes.

On the other hand, at the first and second intersecting portions 16 and 17, the guide portion 12 and the support portion 13 are inclined at a predetermined angle in the same direction with respect to the circumferential direction of the drum body portion 11, that is, the rotation axis, as will be described later. Are formed in parallel in a straight line.

Here, the first and second straight portions 14 and 15 and the first and second intersecting portions 16 and 17 are provided so as to be symmetrical on the surface of the drum main body 11, respectively. The first straight portion 14, the first crossing portion 16, the second straight portion 15, and the second straight portion 14 in the winding direction K of the rope 20 with reference to the rope outlet 11 a provided at the crossing portion 17. Are provided in the order of the intersections 17 (see FIGS. 4 and 5).
In addition, the 1st and 2nd linear parts 14 and 15 are formed in the same length, and the length of the 1st and 2nd intersection parts 16 and 17 is also formed in the same length.

Further, the first and second straight portions 14 and 15 are set to be longer than the lengths of the first and second intersecting portions 16 and 17, respectively.
In the first and second intersecting portions 16 and 17 of the drum main body 11, the guide portions 12 and the support portions 13 are respectively in the direction of the rotation axis of the cylinder by ½ pitch P between the starting point and the ending point. Inclined so as to be displaced in the (width direction).
Here, the pitch P of the guide part 12 and the support part 13 means the distance between the top parts of each guide part 12 (refer FIG. 6, FIG. 7 (a)).

With such a configuration, as shown in FIGS. 4 to 6, for example, when moving from the first straight portion 14 to the second straight portion 15 via the first intersecting portion 16, each guide portion 12 and support portion Each guide 13 shifts in the rotational axis direction of the cylinder by ½ pitch P, and further moves from the second straight portion 15 to the first straight portion 14 via the second intersecting portion 17. When the part 12 and the support part 13 are displaced by 1/2 pitch P in the rotation axis direction of the cylinder and make a round of the drum main body part 11, each guide part 12 and the support part 13 are in the rotation axis direction of the cylinder. Are arranged so as to be shifted by one pitch P.

As shown in FIG. 6, in the present embodiment, the rope 20 is smoothly wound around the first and second straight portions 14 and 15 of the drum main body portion 11, and the end portion thereof will be described later. The 1st guide part 12a and the 2nd guide part 12b are provided.
The first and second guide portions 12 a and 12 b are provided at opposite positions in the first straight portion 14 and the second straight portion 15 of the drum main body portion 11.

FIGS. 7A to 7C are explanatory views showing the configuration and dimensional relationship of the guide part and the support part in the drum main body part in the present invention, and FIGS. 7D and 7E show the first and first parts. It is explanatory drawing which shows the structure of 2 guide parts.

In the present invention, the lower portion of the rope 20 wound around the drum main body 11 is supported at two points by a pair of adjacent guide portions 12 formed in a convex shape (see FIG. 7A).
In the present invention, the pitch P of the guide portion 12 is set to be slightly larger than the diameter φ of the rope 20 (see FIG. 7A).

The reason for this is to provide a slight gap between the adjacent first layer ropes 20 wound around the drum main body 11 so that the ropes 20 can be smoothly wound in multiple layers.
In this case, the preferable pitch P of the guide portion 12 is 1.03 to 1.05 times the diameter φ of the rope 20.

Further, the curvature radius R, width D and height H of the guide portion 12 and the width d of the support portion 13 between the guide portions 12 are the first layer when the rope 20 is wound around the drum body portion 11. The distance between the rope 20 and the support portion 13 is set in consideration.
In this case, the preferred curvature radius R of the guide portion 12 is ½ of the diameter φ of the rope 20.

The height H of the guide portion 12 (distance from the support portion 13) is the distance h between the lower portion of the rope 20 and the support portion 13 when the rope 20 is supported by a pair of adjacent guide portions 12. (See FIGS. 7B and 7C).

On the other hand, as described above, the first guide portion 12a and the second guide portion 12b are provided at the ends of the first and second linear portions 14 and 15 of the drum main body portion 11 (see FIG. 6).
As described below, the first guide portion 12a and the second guide portion 12b are formed so as to have different shapes and sizes (see FIG. 7D).

The first guide portion 12a is formed continuously with the support portion 13 at one end portion of the drum main body portion 11, and has a shape such that the guide portion 12 is divided into two with respect to the central portion, and the height of the end portion is increased. Is configured to be the highest.
The end portion of the first guide portion 12a is flush with the inner surface of the first or second flange 10a, 10b (see FIG. 6).

The first guide portion 12a supports the rope 20 at the end of the first layer together with the adjacent guide portion 12. Therefore, from the viewpoint of reliably guiding and supporting the rope 20, the first guide portion 12a The guide portion 12a is preferably formed in the same shape as the inclined surface of the guide portion 12.

Further, the width and height of the first guide portion 12a are determined so that the first guide portion 12a and the adjacent guide portion 12 support the first layer of rope 20 on the flange side of the rope 20. It is preferable to set so that the portion is supported in contact with the first or second flange 10a, 10b.

On the other hand, the second guide portion 12b includes a lower guide portion 12b ₁ formed continuously with the support portion 13 at the other end of the drum body portion 11, and an upper portion continuous with the lower guide portion 12b _1. and a upper guide portion 12b ₂ formed in (see FIG. 7 (e)).

The lower guide portion 12b ₁ of the second guide portion 12b supports the rope 20 at the end of the first layer together with the adjacent guide portion 12, and therefore the viewpoint of reliably guiding and supporting the rope 20 From the above, it is preferable that the shape of the lower guide portion 12b ₁ is the same as the inclined surface of the guide portion 12, that is, the same radius of curvature R as that of the guide portion 12.

On the other hand, the upper guide portion 12b ₂ of the _second guide portion 12b supports the rope 20 at the end of the second layer together with the rope 20 at the end of the first layer, as will be described later. From the viewpoint of reliably guiding and supporting the rope 20, the shape of the upper guide portion 12 b ₂ is preferably formed with the same radius of curvature R as the guide portion 12.
The end portion of the upper guide portion 12b ₂ of the _second guide portion 12b is flush with the inner surface of the first or second flange 10a, 10b (see FIG. 6).

The width and height of the second guide portion 12b are such that when the second layer rope 20 is supported by the upper guide portion 12b ₂ and the rope 20 at the end of the first layer, the second layer rope 20 is provided. It is preferable to set the side of the flange side so as to contact the first or second flange 10a, 10b.

In the present embodiment, specifically, the diameter φ of the rope 20 is 5.2 mm.
The pitch P of the guide portion 12 is 5.4 mm, the curvature radius R of the guide portion 12 is 2.5 to 2.6 mm, and the width D of the guide portion 12 is about 4 mm. The height H of 12 is about 1 mm.

Next, the principle of the drum according to the present invention will be described in comparison with the prior art.
FIGS. 8A to 8D are diagrams schematically showing a cross-sectional configuration and principle of a drum main body according to the prior art.

FIGS. 9A to 9C are diagrams schematically showing the principle of the drum main body of the present invention.
As shown in FIG. 8A, in the case of the conventional technique, a guide groove 113 is provided on the surface of the drum main body 111. Here, between the adjacent guide grooves 113, an acute-angle protrusion 112 having a small curvature is formed.

The guide groove 113 is formed in a circular arc shape having a radius of curvature r ₁ slightly larger than the radius r _{0 of the} rope 120 having a diameter d ₀ , and is provided along the circumference of the drum body 111.

Here, the radius of curvature r ₁ of the guide groove 113 is 0.535 d ₀ or more and 0.56 d ₀ or less.
The depth H ₀ of the guide groove 113 is 0.28d ₀ or more and 0.45d ₀ or less.

In the drum main body 111, the guide grooves 113 are shifted from each other by ½ pitch in the first and second linear portions 14, 15 and the first and second intersecting portions 16, 17 in the same manner as in the present invention. When the drum main body 111 is made a round, the guide grooves 113 are provided so as to be continued with a shift of one pitch.

Then, the rope 120 is wound along the guide groove 113 by the same method as the present invention, and the rope 120 is inclined in the direction opposite to the inclination direction of the lower rope 120 at the first and second intersecting portions 16 and 17. It is designed to be wound up by riding it.

In such a conventional technique, the load F acts on the cross section of the rope 120 wound around the drum main body 111 from the bottom of the guide groove 113 to the bottom of the guide groove 113 with respect to the cross section. The reaction force f acts on the cross section at one point on the drawing (see FIG. 8B).

In this case, since the rope 120 is an elastic body, a force does not act at one point, but in order to make the explanation easy to understand, it will be described as a rigid body.
As described above, in the prior art, the radius of curvature r ₁ of the guide groove 113 is configured to be larger than the radius r _{0 of the} rope 120 (see FIG. 8A). When a load F ₀ from obliquely above acts, the rope 120 rotates on the guide groove 113 by the horizontal component force of the load F ₀ and moves laterally, and a gap is formed between the edge 113a of the guide groove 113. a ₁ is generated (see FIG. 8C).

As a result, when the second layer rope 120c is wound on the first layer adjacent ropes 120a and 120b, the second layer rope 120c with respect to the first layer adjacent ropes 120a and 120b. By the horizontal component force of the loads F ₁ and F ₂ , the adjacent ropes 120a and 120b of the first layer supporting the rope 120c of the second layer rotate on the guide groove 113 and move away from each other, these adjacent ropes 120a, a gap a ₂ occurs during 120b.

In the case of the prior art, such a phenomenon often occurs at the moment when the load that winds up the rope 120 is cut off. At this time, the rope 120 of the first layer is only about 10% of the load by the hook with the initial weight. Since the rope 120, which is an elastic body, is stretched and thinned by a sudden increase in tension, the above phenomenon tends to be promoted.

In addition, since the gap between the ropes 120 generated in this manner easily causes the rope 120 to bite and disturbs the alignment of the ropes 120, in the related art, it is necessary to reduce the pitch interval between the guide grooves 113. It was happening.
However, if the pitch interval between the guide grooves 113 is too small, there is a problem that the ropes 120 that have expanded at the time of no load rub against each other.

In addition, in the prior art, when a load is applied to the rope 120 and the rope 120 is pulled obliquely, the rope 120 is detached from the guide groove 113, passes over the acute protrusion 112, and is adjacent to the guide groove 113. The guide groove 113 may be pushed out.

As a result, the rope 120 in contact with the protrusion 112 may be damaged, sometimes ruptured, and the load may fall. This is a very dangerous situation for safety.
In addition, when such a situation occurs, even if the rope 120 is not broken, it is necessary to replace it with a new rope 120, which requires much time and cost.

In the conventional technique, the guide groove 113 described above is used, and the rope 120 is wound only on the first layer and then used as a multi-layer winding. However, in this case, the first layer rope 120 is useless and the environment Causes load.
Further, when the rope 120 is unwound, the rope 120 may be unwound by mistake, resulting in a dangerous state.

Furthermore, for example, when a rope 120 having a length of several thousand meters is rolled down on the seabed, it is considered that most of the rope 120 is unwound and breaks off the groove in the last first layer.
In this case, most of the rope 120 may sink in the sea, and it may be impossible to collect the measuring instrument or the exploration device attached to the tip of the rope 120.

Even when the hoist used in a general factory is out of the groove, the rope 120 may be broken, and if this happens, a great loss (time and cost) will occur. become.

On the other hand, in the present invention, since the convex arcuate guide portion 12 is adopted, for example, when the load is pulled diagonally or wound with no load, a turbulence is generated and the load is lifted as it is. In this case, even when the rope 20 is out of the row and is displaced to the next row or beyond, the cross-sectional shape of the guide portion 12 is close to the radius of the rope 20 and is not a sharp shape as in the prior art. Will not cause damage.

On the other hand, in the present invention, as shown in FIG. 9A, when a load is applied to the rope 20, the pair of adjacent convex guide portions 12A and 12B that are in contact with the lower portion of the rope 20 are in contact. Thus, the loads F ₁₀ and F _{11 in} the tangential direction of the contact portion, that is, the diagonal direction on both sides of the rope 20 are applied.
As a result, the reaction forces f ₁₀ and f ₁₁ act on the rope 20 at two points with respect to the cross section from the guide portions 12A and 12B.

According to the drum 10 of the present invention having such a configuration, the first layer rope 20 is supported at two points with respect to the cross section, so that the centering function works on each rope 20. The distance between the rows of the ropes 20 of the layer can be stabilized.

Further, in the present invention, as shown in FIG. 9B, when the second layer rope 20c is wound on the adjacent ropes 20a and 20b of the first layer, the second layer rope is wound. The horizontal component force of loads f ₁ and f ₂ from 20c causes a force to move away from the adjacent ropes 20a and 20b in the first layer, but the adjacent ropes 20a and 20b in the first layer On the other hand, loads f _a and f _b having horizontal component forces in the direction approaching each other from the guide portions 12A and 12B on both sides act on each other, so that the interval between the adjacent ropes 20a and 20b in the first layer is widened. This can stabilize the spacing between rows of the first layer of ropes 20.

In addition, according to the drum 10 of the present invention, the load acting on the drum main body 11 from the rope 20 can be distributed and received at two points with respect to the cross section, thereby reducing the stress concentration in the rope 20. it can.

Further, the force acting on the rope 20 from the drum main body 11 can be distributed and received at two points with respect to the cross section, whereby the stress concentration in the rope 20 can be relaxed.
As a result, according to the present invention, wear of the drum main body 11 can be reduced and the life of the rope 20 can be extended.

Further, for example, when an overload is applied to the rope 20 such as at the time of ground cutting (separation from the ground), the rope 20 is a pair of convex guide portions 12A and 12B adjacent to the drum main body portion 11. The rope 20 is mainly compressed and deformed, so that the portion of the rope 20 on the drum main body 11 side comes into contact with and is supported by the support portion 13 between the guide portions 12A and 12B of the drum main body 11. (See FIG. 9C).

As a result, the loads F ₁₂ and F _{13 in} the tangential direction of the contact portion from the rope 20 to the guide portions 12A and 12B, that is, slanting directions on both sides of the rope 20, and the tangential direction of the contact portion to the support portion 13 A vertical load F ₁₄ is applied to the support portion 13, while reaction forces f ₁₂ and f ₁₃ are applied to the rope 20 from the respective guide portions 12 A and 12 B of the drum main body portion 11. From 13, a reaction force f ₁₄ acts.

As a result, according to the drum 10 of the present invention, the load acting on the drum body 11 from the rope 20 can be distributed and received at three points with respect to the cross section. In addition, since the force acting on the rope 20 from the drum body 11 can be distributed and received at three points with respect to the cross section, stress concentration in the rope 20 can be reduced.

According to the present invention as described above, even when an overload is applied to the rope 20, the wear of the drum body 11 can be reduced and the life of the rope 20 can be extended.
In the case of the present invention, the shape of the support portion 13 is not limited to the above-described plane, but may be a convex shape or a concave shape.

FIG. 10 is a block diagram showing the configuration of the control unit of the present embodiment.
As shown in FIG. 10, the control unit 9 of the present embodiment has a rotation control unit 101 for controlling the rotation of the DC motor 7 described above, and the rotation control unit 101 includes the operation described above. An up or down instruction signal is input from the switch 9a.

The rotation control unit 101 sets the acceleration time and deceleration time of the motor 7 and the subsequent constant speed conditions, and outputs an instruction signal based on these settings.
The rotation control unit 101 is connected to the acceleration / deceleration waveform control unit 102 and the constant velocity waveform control unit 103.

The acceleration / deceleration waveform control unit 102 receives the acceleration / deceleration signal from the rotation control unit 101, sets the acceleration waveform (soft start) and deceleration waveform (soft stop) of the motor 7, and sets the set drive waveform signal at a predetermined timing. Output to the PWM generator 104.

The constant speed waveform control unit 103 receives the constant speed signal from the rotation control unit 101, determines the constant speed waveform of the motor 7, and outputs the determined drive waveform signal to the PWM generation unit 104 at a predetermined timing.

The PWM generation unit 104 generates a PWM waveform at a low voltage based on the drive waveform signals from the acceleration / deceleration waveform control unit 102 and the constant velocity waveform control unit 103, and outputs the PWM waveform signal to the motor drive circuit 105.

The motor drive circuit 105 converts the PWM waveform signal from the PWM generation unit 104 into a motor output waveform signal, and outputs this signal to the motor 7.
With such a configuration, the motor 7 can perform a soft start when starting and a soft stop when stopping.

Further, in the present embodiment, the motor 7 is provided with a sensor (not shown) that detects its rotational position and the like, and a position detector 106 that reads the state of the sensor based on a signal from this sensor. It has been.
Thereby, the position detection part 106 outputs a stop signal also to the state detection part 107, when the operation | movement of the above-mentioned preset sensor is detected.

The state detection unit 107 monitors the state operation of the motor 7, and when receiving a stop signal from the position detection unit 106, outputs a signal to the rotation control unit 101 that all operation instructions should be prohibited. To do.
As a result, the rotation control unit 101 stops outputting instruction signals to the acceleration / deceleration waveform control unit 102 and the constant velocity waveform control unit 103. As a result, the rotation operation of the motor 7 is stopped.

In the present embodiment described above, when the drum 10 is lowered, the acceleration signal set in the rotation control unit 101 is changed to a predetermined soft waveform in the acceleration / deceleration waveform control unit 102, and the low voltage is generated in the PWM generation unit 104. After the PWM waveform is generated, the motor 7 is started (soft start).

Controlling the operation of the motor 7 in this way prevents the occurrence of relative slip between the upper layer portion and the lower layer rope 20 wound around the drum main body portion 11 when the drum 10 is lowered. As a result, the rope 20 can be prevented from being lifted or jumped to the adjacent guide portion 12.

FIGS. 11A and 11B show the configuration of the drive system of the present embodiment. FIG. 11A is an internal front view and FIG. 11B is an internal side view.
As shown in FIGS. 11A and 11B, in the present embodiment, the driving gear 21 is connected to the second flange 10 b on the motor side of the drum 10 provided in the apparatus main body 4. It is attached concentrically with the rotation axis O and is configured to rotate with the drum 10.

A first transmission gear 23 that rotates about a support shaft 22 provided in the apparatus main body 4 is provided below the drive gear 21, and the first transmission gear 23 meshes with the drive gear 21. It is provided as follows.

The gear ratio of the first transmission gear 23 is set to be equivalent to that of the driving gear 21.
Further, a pinion gear 24 having a smaller number of teeth than the first transmission gear 23 is integrally and concentrically fixed to the first transmission gear 23.

A rope reciprocating feed screw 30 is provided below the drum 10 in the apparatus body 4.

The rope reciprocating feed screw 30 is made of an engineering resin (for example, polyacetal, high density polyethylene, nylon resin, carbon fiber, or the like).
The rope reciprocating feed screw 30 is formed in a straight line and is arranged in parallel with the rotation axis O of the drum 10, and the rotation shaft 31 is rotatably supported by bearings 32 provided on both sides of the main body frame 4 a.

The rope reciprocating feed screw 30 has a thread groove portion 33 in the middle part thereof, and a shifter block 50 described later meshes with the screw groove portion 33 so that the rope reciprocating feed screw 30 reciprocates at a predetermined speed along the direction in which the rope reciprocating feed screw 30 extends. It is like that.
A second transmission gear 25 is fixed to the rotary shaft 31 of the rope reciprocating feed screw 30, and the second transmission gear 25 is disposed so as to mesh with the pinion gear 24 described above.

Here, the number of teeth of the second transmission gear 25 is set to be larger than the number of teeth of the pinion gear 24.
A rod-shaped guide shaft 40 for guiding a shifter block 50 described later is provided obliquely below the rope reciprocating feed screw 30.

The guide shaft 40 is formed in a straight line and is arranged in parallel with the rope reciprocating feed screw 30, and both ends thereof are rotatably supported by bearings 43 provided on both sides of the main body frame 4a.
The driven gear 26 is fixed to the guide shaft 40, and the driven gear 26 is disposed so as to mesh with the second transmission gear 25 described above.
Here, the number of teeth of the driven gear 26 is set to be smaller than the number of teeth of the second transmission gear 25.

12 (a) to 12 (c) show an embodiment of the rope feeding mechanism used in the present invention. FIG. 12 (a) is a partial sectional view showing the entire configuration, and FIG. 12 (b) is a shifter. FIG. 12C is a side view showing the configuration of the main part of the rope feed mechanism.

As shown in FIGS. 12A to 12C, this rope feed mechanism has a shifter block 50 that is mounted across the rope reciprocating feed screw 30 and the guide shaft 40 described above.
The shifter block 50 has a main body 51 formed in a rectangular parallelepiped shape, for example.

The shifter block 50 is configured such that the above-described rope reciprocating feed screw 30 penetrates at one end of the main body 51 and the above-described guide shaft 40 penetrates at the other end of the main body 51. Has been.

In the main body 51 of the shifter block 50, a top 52 having a projection that meshes with the thread groove 33 of the rope reciprocating feed screw 30 is provided, and the top 52 and the thread groove 33 of the rope reciprocating feed screw 30 are engaged with each other. The shifter block 50 is configured to reciprocate in the rotational axis direction of the rope reciprocating feed screw 30 as the rope reciprocating feed screw 30 rotates.

Since the hoist 1 of the present embodiment performs parallel multi-layer winding by supporting the rope 20 by the convex guide portion 12 provided in the drum main body portion 11 as described above, a conventional parallel grooved drum is used. As in the case of use, the fleet angle is set to be 90 ° ± 1.5 ° or less with respect to the rotation axis O of the drum 10, and particularly in the vicinity of the first and second flanges 10 a and 10 b. It is necessary to set the fleet angle to be 90 degrees ± about 1.0 to 1.5 degrees so that the transfer of the rope 20 to the road becomes smooth.

Therefore, in the present embodiment, when the drum 10 makes one rotation, the screw at the central portion of the rope reciprocating feed screw 30 is moved so that the shifter block 50 moves at a slightly smaller pitch than the pitch P of the guide portion 12 described above. The angle and speed ratio of the groove 33 are set.

Then, when the rope 20 reaches the end of the drum body 11, 90 ° ± about 1.0 to 1.5 ° of the fleet angle of 90 ° ± about 1.5 to 1.5 ° can be secured on the inner side. The angle and speed ratio of the thread groove portion 33 are set.

A guide sheave 53 is provided at the other end of the main body 51 of the shifter block 50.
The guide sheave 53 moves the rope 20 fed from the drum 10 so as to come to the center position of the hoist 1, and is attached to a position inside the shifter block 50.

In this case, a ball bearing 54 is attached to the guide sheave 53, and a slide bearing 55 is attached inside the ball bearing 54 (see FIG. 12A).
The slide bearing 55 is attached so as to penetrate in the width direction of the guide sheave 53, and both ends thereof are fixed to the shifter block 50 in a state in which the slide sheave cannot be rotated by, for example, a stop screw (not shown). A guide shaft 40 is inserted and arranged concentrically with the guide shaft 40.

The rope 20 is inserted into a through hole 51 a provided in the middle part of the main body 51 of the shifter block 50, and is engaged with the sheave groove 53 a of the guide sheave 53 to guide the rope 20. (See FIGS. 12A and 12B).

In the present embodiment having such a configuration, when the motor 10 is driven to rotate the drum 10, the rotational power of the drive gear 21 attached concentrically with the rotation axis O of the drum 10 is the first. It is transmitted via the transmission gear 23, the pinion gear 24, and the second transmission gear 25, whereby the rope reciprocating feed screw 30 rotates at a predetermined speed, and the shifter block 50 extends along the direction in which the rope reciprocating feed screw 30 extends. Moving.

Further, the rotational power of the second transmission gear 25 is transmitted to the driven gear 26 fixed to the guide shaft 40, so that the guide shaft 40 rotates.
Here, in the rope feed mechanism of the present embodiment, the number of teeth of the second transmission gear 25 fixed to the rotary shaft 31 of the rope reciprocating feed screw 30 is the number of teeth of the driven gear 26 fixed to the guide shaft 40. The rotational speed of the guide shaft 40 is set to be larger than the rotational speed of the rope reciprocating feed screw 30.

FIGS. 13 (a) to 13 (d) and FIGS. 14 (a) to 14 (c) are explanatory views showing the operation of winding the rope in the present embodiment around the drum body. Here, the cross-sectional configuration of the first straight portion 14 is schematically shown.

In the present embodiment, the tip of the rope 20 is fixed to the rope outlet 11a (see FIG. 4) of the drum main body 11, and the drum 10 is rotated and the shifter block 50 is operated to wind the rope 20 in parallel winding. As the body portion 11 is wound, first, the first layer of rope 20A includes a first guide portion 12a on the first flange 10a side, a guide portion 12C adjacent to the first guide portion 12a, 1 (see FIG. 13A).

Then, when the rotation of the drum 10 and the operation of the shifter block 50 are continued, the first layer of rope 20A is sequentially applied to the pair of adjacent guide portions 12 toward the second guide portion 12b on the second flange 10b side. will be supported, the first layer of the rope 20A in the final stage, the lower guide portion 12b ₁ of the second guide portion 12b, is supported by a guide section 12D adjacent to the second guide portion 12b ( (Refer FIG.13 (b)).

After that, at the end of the drum main body 11 on the second guide portion 12b side, the second layer rope 20B is connected to the first layer rope 20A at the end on the second guide portion 12b side and the second layer. It rides on the guide portion 12b and is supported by the first layer rope 20A, the upper guide portion 12b2 of the _second guide portion 12b, and the second flange 10b (see FIG. 13C).

Further, when the rotation of the drum 10 and the operation of the shifter block 50 are continued, the second-layer rope 20B is sequentially supported by the adjacent first-layer rope 20A toward the first flange 10a ( (Refer FIG.13 (d)).

In this case, in the first and second intersections 16 and 17 described above, the second layer rope 20B is inclined in the direction opposite to the inclination direction of the first layer rope 20A, and the first layer It rides on the rope 20A and is wound.

Then, at the end of the drum body 11 on the first flange 10a side, the third layer rope 20C is supported by the first flange 10a, and the second layer at the end of the first flange 10a side. It rides on the rope 20B of the eye and is supported by the rope 20B of the second layer and the first flange 10a (see FIG. 14A).

Further, when the rotation of the drum 10 and the operation of the shifter block 50 are continued, the third layer rope 20C is sequentially supported by the adjacent second layer rope 20B toward the second flange 10b ( (Refer FIG.14 (b)).
In this case, in the first and second intersections 16 and 17 described above, the rope 20C of the third layer is inclined in the direction opposite to the inclination direction of the rope 20B of the second layer, and the second layer It rides on the rope 20B and is wound.

Then, at the end on the second flange 10b side of the drum body 11, the fourth layer rope 20D is supported by the second flange 10b, and the third layer on the second flange 10b side end. It rides on the rope 20C of the eye and is supported by the rope 20C of the third layer and the second flange 10b (see FIG. 14C).

Hereinafter, multilayer winding of the rope 20 around the drum body 11 is performed by the same procedure.
In addition, as mentioned above, in the 1st and 2nd cross | intersection parts 16 and 17, it winds by making the rope 20 in winding incline in the direction opposite to the inclination direction of the rope 20 one layer below, and run.

Further, as shown in FIGS. 13 (a) to 13 (d) and FIGS. 14 (a) to (c), in the present embodiment, at the end of the drum main body 11 on the first guide portion 12a side, The odd-numbered layer (here, the first and third layers) ropes 20A and 20C are supported in contact with the first flange 10a, and the drum body portion 11 has an even-numbered end on the second guide portion 12b side. Layers (here, second and fourth layers) of ropes 20B and 20D are supported in contact with the second flange 10b.

In the present embodiment described above, the gear ratio of the driven gear 26 and the second transmission gear 25 is set so that the rotational speed of the guide shaft 40 is 2 to 3 times the rotational speed of the rope reciprocating feed screw 30. As a result, the dust splashes off with the rotation of the guide shaft 40 to prevent the dust from adhering to the guide shaft 40, and the static friction coefficient at the start of the operation is changed to the dynamic friction coefficient to reduce the friction. The coefficient is reduced.

That is, in the prior art, the slide may not go smoothly due to the presence of dust and the lack of lubrication of the guide shaft 40, which may cause a self-lock and stop moving, but according to this embodiment, Such inconvenience does not occur, and the length of the slide bearing 55 of the guide shaft 40 can be shortened as the friction coefficient is reduced, so that a more compact rope feeding mechanism can be provided. It was.

Moreover, although the rope reciprocating feed screw used for the conventional hoist and winch was made of a steel material including stainless steel, in this embodiment, by configuring the rope reciprocating feed screw 30 with the above-described engineering resin, Because of its self-lubricating property, oil and grease are not required, and dust can be made difficult to adhere.

In addition, in a conventional apparatus, when a rope close to an unloaded state is unwound, if the acceleration or speed of the rope is large, the rope may not be unwound smoothly due to the rotational resistance of the guide sheave.
That is, the guide sheave that normally slides in the axial direction uses a sliding bearing, but smooth low-friction rotation cannot be obtained.

On the other hand, in the present embodiment, by combining the ball bearing 54 with the slide bearing 55, low friction rotation of the guide sheave 53 is realized, whereby the rope 20 can be smoothly unwound.

FIG. 15 is a schematic configuration diagram of an embodiment of a rope reverse winding detection mechanism and a no-load detection mechanism used in the present invention.
In this invention, it has a rope reverse winding detection mechanism and a no-load detection mechanism so that it may mention later.

Here, below the drum 10 in the main body frame 4a, the reverse of the rope constituted by the above-described shifter block 50, the limit lever unit 60 assembled to the shifter block 50, the limit dog 71, the limit cam 73, and the limit switch 75. A winding detection mechanism is provided.

Further, below the drum 10 in the main body frame 4a, the shifter block 50, a no-load detection lever unit 80 assembled to the shifter block 50, a limit dog 71, a limit cam 73, and a limit switch 75 are included. A load detection mechanism is provided.

Furthermore, rope regulating rollers 41 and 42 are provided below the rope reverse winding detection mechanism and the no-load detection mechanism in the main body frame 4a.
Hereinafter, embodiments of the rope reverse winding detection mechanism and the no-load detection mechanism will be described in detail.

16 (a) and 16 (b) show a limit lever unit of the rope reverse winding detection mechanism of the present embodiment. FIG. 16 (a) is a side view and FIG. 16 (b) is a front view.
FIGS. 17 (a) to 17 (c) show the configuration of the rope reverse winding detection mechanism, FIG. 17 (a) is a front view showing the entire configuration, and FIG. 17 (b) is the rope reverse winding detection. The side view which shows the principal part structure of a mechanism, FIG.17 (c) is a side view which shows the whole structure of the rope reverse winding detection mechanism.

The rope reverse winding detection mechanism according to the present embodiment includes a limit lever unit 60 attached to the shifter block 50 described above.
As shown in FIGS. 16A and 16B, the limit lever unit 60 includes a pair of limit levers 61 having the same shape, and a detection roller 62 and a drive roller 63 attached to the pair of limit levers 61. Yes.

The limit lever 61 is formed, for example, by bending an elongated plate-like member at right angles twice in different directions almost at the middle part, and by making these two limit levers 61 face each other, the drive unit 61a having a small interval between the levers A mounting portion 61b having a larger interval between the levers than the driving portion 61a is provided.

Here, the interval between the mounting portions 61 b of the pair of limit levers 61 is set to be slightly larger than the width of the shifter block 50.
The drive part 61a of each limit lever 61 is formed in a straight line shape, and a drive roller 63 is attached to the tip of the limit lever 61 with the drive part 61a sandwiched between the drive parts. Here, the drive roller 63 is configured to rotate about a support shaft 64 orthogonal to a straight line in the extending direction of the drive unit 61a.

On the other hand, the mounting portion 61b of each limit lever 61 is formed such that its middle portion is curved in one direction, for example, in a boomerang shape on the same plane, and the radius of curvature of the edge portion 61c inside the curve is the rope reciprocating feed screw. It is set to be slightly larger than the radius of 30.
And the detection roller 62 is attached to the front-end | tip part of the mounting part 61b of each limit lever 61 in the state pinched | interposed into a pair of mounting part 61b.

Here, the detection roller 62 is configured to rotate around a support shaft 65 parallel to the support shaft 64 of the drive roller 63 described above.
Moreover, the detection roller 62 is comprised from the edge part roller 62a provided in the both ends, and the inner side press roller 62b provided inside these edge part rollers 62a.

Here, the outer diameter of the end roller 62a is set to be slightly larger than the outer diameter of the inner pressing roller 62b.
In this case, the end roller 62a is made of stainless steel, for example.
The inner pressing roller 62b is made of, for example, stainless steel or resin, and is configured to rotate independently of the end roller 62a.

The limit lever unit 60 having such a configuration is rotatable around, for example, support shafts 56 provided on both sides of the shifter block 50 in a state where the shifter block 50 is sandwiched between the mounting portions 61b of the pair of limit levers 61. It is attached.

The support shaft 56 is located in the vicinity of the through hole 51a for the rope reciprocating feed screw 30 of the shifter block 50 (see FIGS. 12A and 12B), and on the inner edge of the curved portion of the mounting portion 61b of each limit lever 61 It is provided in the vicinity of the portion 61c (see FIG. 16A).

The limit lever unit 60 is configured such that the drive portion 61a is reciprocated by the rope of the shifter block 50 by a tension coil spring 58 having one end attached to a mounting bracket 57a fixed to the end of the shifter block 50 on the rope reciprocating feed screw 30 side. It is comprised so that it may be pulled by the feed screw 30 side edge part (refer FIG.17 (b)).

On the other hand, for example, a projecting locking portion 59 is provided on the upper portion of the main body 51 of the shifter block 50, that is, on the detection roller 62 side of the limit lever unit 60.
In this case, the locking portion 59 is provided at a position facing the end roller 62a of the detection roller 62 (see FIG. 16B), and the tension coil spring 58 is in a state where no external force acts on the limit lever unit 60. The end roller 62a of the detection roller 62 abuts against the locking portion 59 and is locked by the elastic force.

In the case of the present embodiment, the limit lever unit 60 is attached such that the detection roller 62 is on the upper side with respect to the rope reciprocating feed screw 30 (shifter block 50).
On the other hand, below the rope reciprocating feed screw 30 and on the opposite side of the rope reciprocating feed screw 30 from the guide shaft 40, a limit dog 71 fixed to the linear rotary support shaft 70 is provided.
Here, the rotation support shaft 70 is arranged in parallel with the rope reciprocating feed screw 30 and is attached to the main body frame 4a in a rotatable state.

The limit dog 71 is made of, for example, a plate-like member extending in the direction of the rotation support shaft 70, and the limit lever unit is configured such that one surface (here, the upper surface) is in contact with the drive roller 63 of the limit lever unit 60 described above. The dimension (length) of the drive part 61a of 60, the position of the rotation spindle 70, and the size and shape of the limit dog 71 are set (see FIGS. 17A and 17C).

For example, a torsion coil spring 72 is connected to the limit dog 71, and the end roller 62 a of the detection roller 62 is engaged with the locking portion 59 by the elastic force of the torsion coil spring 72 when no external force is applied to the limit dog 71. Are configured to come into contact with the driving roller 63 of the limit lever unit 60 (see FIG. 17C).

Further, a limit cam 73 is provided at, for example, one end of the rotation support shaft 70 (see FIG. 17A), and a limit switch is provided at a position facing the arc-shaped cam surface of the limit cam 73, for example. 75 is provided.

The limit switch 75 is turned off when the limit dog 71 shown in FIG. 17C faces obliquely upward and contacts the driving roller 63 of the limit lever unit 60, and is turned on when the limit dog 71 is pushed down. It is configured.

18A and 18B are explanatory views showing the operation of the rope reverse winding detection mechanism.
In the apparatus for performing multi-layer winding as in the present invention, if the row groove of the rope 20 collapses during lowering, a gap is generated between the rows, and the rope 20 is likely to bite into the gap.

When the rope 20 bites into such a gap, the rope 20 is not only damaged, but the rope 20 that has bitten cannot be removed, so that the rope 20 is fixed to the other rope 20 during unwinding and unwound. As a result, it falls into a hoisting state (referred to as “reverse winding state” in this specification).
Such a reverse winding state occurs even when the rope 20 is completely unwound from the drum 10.

In the rope reverse winding detection mechanism of the present embodiment, when the reverse winding of the rope 20 occurs in the normal lowering state shown in FIG. 18 (a), the rope 20 is attached to the shifter block 50 as shown in FIG. 18 (b). The inner pressing roller 62b of the detection roller 62 of the limit lever unit 60 is pushed by the rope 20 whose direction of winding is reversed to operate.

That is, the rope 20 whose path is displaced from the guide shaft 40 side to the rope reciprocating feed screw 30 side pushes the inner pressing roller 62b of the detection roller 62 toward the rope reciprocating feed screw 30, and thereby the limit lever unit 60 is pulled by the tension coil. The drive roller 63 provided at the front end of the drive portion 61a of the limit lever unit 60 pushes down the limit dog 71 downward, and the limit switch 75 is turned off. Turn on. Thereby, the lowering operation of the motor 7 is stopped.

When the operation of the motor 7 is stopped, the motor 7 is operated in the winding direction to return the rope 20 in the reverse winding state to the original position, so that the rope 20 is pressed against the inner pressing roller 62b of the detection roller 62. Since the force no longer acts, the limit lever unit 60 rotates around the support shaft 56 by the elastic force of the tension coil spring 58, returns to the original state shown in FIG. 18A, and the end roller 62a of the detection roller 62 Are brought into contact with the locking portions 59 and locked.

Even in this case, in this embodiment, the inner pressing roller 62b of the detection roller 62 has a smaller roller diameter than the end roller 62a of the detection roller 62, and the end roller 62a is pressed against the locking portion 59 of the shifter block 51. Even if it is a case, it is freely rotatable. For this reason, the inner pressing roller 62b does not rotate with respect to the rope 20, and the sliding rope 20 is not damaged.

As described above, according to the present embodiment, when an excessive load is applied during the lowering and the rope 20 bites between the rows and the reverse winding of the rope 20 occurs, the entire rope 20 is unwound from the drum 10. Even in this case, the operation can be stopped immediately.
As a result, abnormalities during operation can be detected, so that random winding of the rope 20 can be prevented.

Further, in the present embodiment, even when the limit switch 75 is operated and stopped after the rope 20 is completely unwound, the rope outlet is arranged so that the tip end portion of the rope 20 does not fall out of the drum body 11. The female thread portion 11c connected to 11a is fixed by a rope stopper 11e (this point will be described later, see FIGS. 24A and 24B).

And by such a structure, even if it is a case where all the ropes 20 are unwound from the drum 10, the rope 20 can be wound up again without a problem.
Even if the rope 20 is removed from the guide portion 12 of the drum main body portion 11, as described above, the guide portion 12 of the drum main body portion 11 is formed in a convex curved surface shape. There will be no damage.

19 (a) and 19 (b) show the no-load detection lever unit of the no-load detection mechanism used in the present invention. FIG. 19 (a) is a partial sectional view as seen from the guide sheave side for no-load detection. 19 (b) is a side view, and FIG. 19 (c) is a partial sectional view as seen from the guide sheave side.
20 (a) to 20 (c) show the configuration of the no-load detection mechanism, FIG. 20 (a) is a front partial sectional view showing the entire configuration, and FIG. 20 (b) is the no-load detection mechanism. The side view which shows the principal part structure of a mechanism, FIG.20 (c) is a side view which shows the whole structure of the no-load detection mechanism.

As shown in FIGS. 19A to 19C, the no-load detection mechanism includes the no-load detection lever unit 80 attached to the shifter block 50 described above.
The no-load detection lever unit 80 includes a pair of no-load detection levers 81 having the same shape, and a no-load detection guide sheave 82 and a driving roller 83 attached to the pair of no-load detection levers 81.

The no-load detection lever 81 has, for example, an elongated plate-like main body portion 81a, and has a drive projection 81b formed so as to extend obliquely to one side of the main body portion 81a.
The pair of no-load detection levers 81 is provided inside the shifter block 50.

The guide sheave 53 used in the rope feed mechanism and the rope reverse winding detection mechanism described above is sandwiched between the pair of no-load detection levers 81 at one end of the main body 81 a of the no-load detection lever 81. A no-load detection guide sheave 82, which will be described later, is provided at the other end of the main body 81a of the no-load detection lever 81 (the end on the side where the drive protrusion 81b is provided). 81 so as to be sandwiched by 81.

Here, a collar 54a is provided on both sides of the ball bearing 54 provided in the guide sheave 53, and the no-load detection lever 81 is configured to rotate around the collar 54a.

On the other hand, a no-load detection guide sheave 82 is provided between the end portions of the main body 81a of the no-load detection lever 81 on the side where the drive protrusion 81b is provided.
Here, the no-load detection guide sheave 82 includes a pair of no-load detection levers 81 through which a cylindrical pin 84 provided in parallel with the guide shaft 40 passes, and the pin 84, collar 85, and shaft retaining ring ( It is rotatably mounted via a ball bearing 86 fixed by a not-shown).

A driving roller 83 is attached to the outer portion of the tip of the driving protrusion 81b of each no-load detection lever 81 so as to be rotatable around a support shaft 87 parallel to the guide shaft 40.

The no-load detection lever unit 80 having such a configuration is rotatably mounted around the rotation axis of the guide shaft 40 described above at a position inside the shifter block 50 (see FIG. 20B).
In this case, the no-load detection guide sheave 82 and the drive roller 83 of the no-load detection lever unit 80 are positioned below the main body 51 of the shifter block 50, and the drive roller 83 is on the rope reciprocating feed screw 30 side. It is arranged to be located.

Then, the drive roller 63 of the limit lever 61 described above is arranged and configured so as to enter the inner portion of the tip of the drive protrusion 81b of the no-load detection lever 81 of the no-load detection lever unit 80 (FIGS. 15 and 15). 19 (a)).

In the no-load detection lever unit 80, one end is attached to the mounting bracket 57b fixed to the end of the shifter block 50 on the guide shaft 40 side, and the other end is a pin 84 of the no-load detection lever unit 80 (FIG. 19). The driving protrusion 81b is configured to be pulled to the end of the shifter block 50 on the side of the guide shaft 40 by the elastic force of the tension coil spring 58 attached to (a) and (b).

Then, as shown in FIG. 20 (c), the rope 20 unwound from the drum body 11 passes through the body 51 from above the body 51 of the shifter block 50 and enters the sheave groove 53 a of the guide sheave 53. One side is in contact, passes between the pair of no-load detection levers 81 of the no-load detection lever unit 80, and the other side of the rope 20 contacts the sheave groove 82a of the no-load detection guide sheave 82. Is configured to do.

In the present embodiment, the rope 20 hangs directly under the long rollers 41 and 42. In this case, the rope 20 has the long roller 41 on the side of the guide sheave 53 by the elastic force of the tension coil spring 58 attached to the pin 84 of the no-load detection guide sheave 82 located substantially at the center between the guide sheave 53 and the long roller 41. It is pressed against.

In the present embodiment, the spring force is set as follows.
In other words, when the tension of the rope 20 during the lowering is larger than a predetermined set value (for example, 8% of the rated load), there is almost no deflection of the rope 20 and no load is detected by the elastic force of the tension coil spring 58. The force applied to the rope 20 from the guide sheave 82 and the force applied from the rope 20 to the no-load detection guide sheave 82 based on the tension of the rope 20 are set to be balanced.

In this state, as shown in FIG. 20 (c), the drive roller 83 of the no-load detection lever unit 80 comes in contact with the upper surface of the limit dog 71 of the limit switch 75 turned diagonally upward. It is configured.

It should be noted that the weights of the hook and weight are adjusted so that the tension of the rope 20 is, for example, 8 to 10% so that the limit switch 75 is not turned on when the load is not suspended.

FIGS. 21A and 21B are explanatory diagrams showing the operation of the no-load detection mechanism.
In the no-load detection mechanism having such a configuration, when the drum 10 is rotated while being hanged on the rope 20 to perform the lowering, the tension of the rope 20 becomes equal to or higher than the set value. The force applied to the rope 20 from the no-load detection guide sheave 82 by the elastic force of the tension coil spring 58 and the force applied from the rope 20 to the no-load detection guide sheave 82 based on the tension of the rope 20 in a state where there is almost no deflection. Therefore, as shown in FIG. 21A, the limit switch 75 is turned off.

When the load reaches the ground in this state, the tension applied to the no-load detection guide sheave 82 disappears because the tension of the rope 20 is lost.
As a result, as shown in FIG. 21 (b), the no-load detection lever 81 rotates about the rotation axis of the guide shaft 40 counterclockwise by the elastic force of the tension coil spring 58, thereby driving roller Since 83 pushes down the limit dog 71 downward and the limit switch 75 is turned on, the operation of the motor 7 is stopped.

In this case, when a tension equal to or higher than the set value described above is applied to the rope 20, the rope 20 becomes almost a straight line, and the limit switch 75 is restored, so that the lowering operation can be performed.

In a device for performing parallel winding as in the present invention, when a load lands and the rope loses a certain level of tension, the rope wound around the drum jumps and causes turbulence when the rope is subsequently lowered. However, according to the present embodiment, when the tension of the rope 20 becomes, for example, 8% or less of the rated load during the lowering, it can be automatically stopped, so that such inconvenience does not occur. .

Furthermore, many conventional hoists have two or more ropes, and in the no-load state, it was possible to easily detect the load by using the fixed side rope. It becomes larger as a device, such as attaching a fixed pulley separately.

However, according to the present embodiment, a compact configuration can be obtained by combining the shifter block 50 and the no-load detection lever unit 80.

22A and 22B are diagrams showing the configuration of the rope presser mechanism, and FIG. 23 is an explanatory diagram showing the dimensional relationship of the rope presser roller of the rope presser mechanism.
As shown in FIGS. 22A and 22B, the rope presser mechanism 90 presses the surface of the rope 20 by the rope presser roller 91 when the rope 20 is wound up and down.

Here, the rope presser roller 91 is formed in a cylindrical shape, and is attached to the end of one long side of two L-shaped arms 92, for example, so as to be rotatable around the rotation shaft 93.
An end portion on the short side of each arm 92 is provided so as to be rotatable about a support shaft 94 provided on the upper portion of the apparatus main body 4 of the hoist 1, for example.

Here, the support shafts 94 provided at both ends of the arm 92 are respectively arranged in parallel with the rotation axis O of the drum 10, so that the rope presser roller 91 is arranged in parallel with the drum main body 11. ing.

The rope pressing roller 91 is configured to press the rope 20 against the drum body 11 by urging the arm 92 toward the drum body 11 by the elastic force of the torsion coil spring 97 provided on the support shaft 94, for example. Has been.

A limit cam 95 is attached to the end portion of the arm 92 on the support shaft 94 side, and a limit switch 96 provided in the vicinity thereof is turned on / off in accordance with the operation of the arm 92.

As shown in FIG. 23, the rope presser roller 91 is slightly shorter than the width of the drum main body 11, and narrows from the central portion 91a toward the both end portions 91b in the axial direction via the tapered portions 91c. Thus, the diameter φD of both end portions 91b of the rope presser roller 91 is configured to be smaller than the diameter φA of the central portion 91a.

The reason is as follows.
That is, when a rope is wound on a drum having a conventional parallel groove, when the rope is transferred to a layer on one layer and the rope is pressed by means such as a roller, the ropes are stacked in multiple stages.
When such a phenomenon occurs, the rope is wound in a random manner. Therefore, when transferring to the upper layer of the rope, it is necessary to make the rope free from contact with other members.

Further, in the drum that performs parallel winding, because of the characteristic, the pitch is shifted by 0.5 pitch for each layer of the rope. For the reason described above, for example, in this embodiment, the drum main body portion is represented by reference numeral B in FIG. It is necessary not to contact the rope 20 for 1.5 pitches of the 11 guide portions 12.

Therefore, in the present embodiment, in consideration of such circumstances, the size and the inclination angle of the tapered portion 91c are set.
On the other hand, in the drum 10 of the present embodiment, the rope 20 being wound is inclined on the first and second intersecting portions 16 and 17 in a direction opposite to the inclination direction of the rope 20 that is one layer below. Wound by.

In this case, the first and second straight portions 14 and 15 and the first and second intersecting portions 16 and 17 are provided so as to be symmetrical on the surface of the drum main body 11 (see FIG. Therefore, the rope 20 wound around the drum main body 11 has an elliptical cross-sectional shape in each layer, and the relative position is also the same.

Therefore, the difference between the diameter φA of the central portion 91a of the rope pressing roller 91 and the diameter φD of both end portions 91b of the rope pressing roller 91 can be expressed by the following equation.
(ΦA-φD) / 2 = C
This relationship can be minimized as compared with the spiral groove drum and the cylindrical drum.

Actually, in consideration of a slight change s of the rope diameter φ due to wear of the rope presser roller 91 and tension of the rope 20, it can be expressed by the following equation.
C = φ + s
It is a condition that the rope 20 passing through the rope presser roller 91 described above is always given a minimum tension (about 8 to 10%).

The reason for this is that when the rope 20 is wound around the drum main body 11 in a completely unloaded state, the rope 20 does not reliably contact the guide portion 12 of the drum main body 11, and is in a so-called crumpled (loosely wound) state. Because it will end up.

And according to this Embodiment which has such a structure, when winding the rope 20 around the drum main-body part 11, the center part 91a of the rope presser roller 91 over the perimeter of the drum main-body part 11 WHEREIN: The rope 20 in the central portion can be surely pressed so as not to float, and the rope 20 should not be brought into contact with the rope presser roller 91 when transferring to the upper layer of the rope 20 at both ends of the drum body 11. As a result, it is possible to reliably prevent random winding when the rope 20 is wound.

24 (a), 24 (b) and FIGS. 25 (a) to 25 (d) show a mechanism for preventing the rope end portion from lifting up in the present embodiment.
Here, FIG. 24A is a side view showing the main part of the drum, and FIG. 24B is a cross-sectional view taken along line AA of FIG.

FIG. 25 (a) is an explanatory view showing the configuration of the tip of the conventional rope, FIG. 25 (b) is an explanatory view showing a case where the conventional rope is fixed to the drum body, and FIG. 25 (c). FIG. 25 is an explanatory view showing the configuration of the tip of the rope of the present embodiment, and FIG. 25D is an explanatory view showing a case where the rope of the present embodiment is fixed to the drum body.

In the present embodiment, a concave rope housing portion 11b for housing the distal end portion of the rope 20 is provided in the vicinity of the first flange 10a of the drum main body portion 11, and the distal end of the rope 20 is placed in the rope housing portion 11b. It is comprised so that a rope 20 may be pulled out from the rope outlet 11a by inserting a part.

The rope outlet 11a is formed in, for example, an oval shape extending in the circumferential direction of the drum main body 11, and a cylindrical female screw portion 11c is provided at the rear end portion so as to be connected to the rope outlet 11a. ing. The female threaded portion 11c is configured such that a rope stopper 11e, which is a male threaded plug, meshes with the hole to close the hole (see FIG. 24B).

The rope accommodating portion 11b is provided with a convex curved rope guide portion 11d along the rope outlet 11a. The rope guide portion 11d extends from the rope accommodating portion 11b to the tip of the rope outlet 11a. It is formed so that the depth becomes shallower.

Generally, a wire rope used in a cargo handling machine such as the present invention is provided with a bump-shaped lock pipe at its end.
Conventionally, when such a rope 120 is inserted into the rope outlet 11a of the drum body 11 and then fixed with the rope stopper 11e, and the rope 120 is wound around the drum body 11, the lock 120a of the rope 120 is A phenomenon occurs in which the adjacent drawn portion 120b slightly floats from the curved surface of the drum main body 11 due to the rigidity of the rope 120 (see FIGS. 25A and 25B).

If this lift is large, the rope presser roller 91 is pushed up when the above-described rope presser roller 91 is provided, so that the ropes 120 of the other rows cannot be pressed uniformly, causing a turbulence.

In addition, since the slack portion of the rope 120 that is pressed by the rope wound on the bulge is stretched to several lines ahead, the rope that is entirely wound around the drum body 11 when no load is applied. The tension of 120 decreases, and slipping between the lower layer and upper layer ropes 120 is likely to occur, resulting in turbulence.
Therefore, in the present embodiment, such a problem is prevented from occurring by the following means.

As shown in FIG. 25 (c), the rope 20 of the present embodiment has a distal end portion corresponding to the shape of the portion that guides the rope 20 when the rope 20 is pulled out from the accommodating portion 11b of the drum main body portion 11. Bending is applied.

That is, for example, bending of an equivalent radius of curvature is performed so that the drawn-out portion 20b on the rear end side in the vicinity of the lock tube 20a at the tip end portion of the rope 20 corresponds to the curved surface shape of the rope guide portion 11d of the drum main body portion 11. In addition, the routing portion 20c on the rope rear end side of the drawing portion 20b is bent so as to have the same radius of curvature as the surface of the drum body portion 11.

In such a configuration, when the rope 20 is attached to the drum body 11, the lock tube 20 a at the tip of the rope 20 is disposed in the rope housing portion 11 b of the drum body 11, and the rear end of the rope 20. The portion on the side is pulled toward the tip end side of the rope outlet 11 a and is wound around the surface of the drum main body 11 as it is.

Thus, as shown in FIGS. 24B and 25D, the lock tube 20a of the rope 20 is locked and fixed by the protruding portion of the rope accommodating portion 11b and the rope stopper 11e.

As described above, the drawn portion 20b of the rope 20 is subjected to, for example, bending processing with an equivalent curvature radius so as to correspond to the curved surface shape of the rope guide portion 11d of the rope 20 of the drum main body portion 11, and further, the drawn portion 20b. Since the bending portion 20c on the rear end portion side of the rope 20 is bent so as to have the same radius of curvature as the surface of the drum body portion 11, the drawing portion 20b of the rope 20 is provided with the drum body portion 11. The rope guide portion 11d is in close contact with each other, and the routing portion 20c of the rope 20 is in close contact with the surface of the drum main body portion 11, that is, the pair of guide portions 12.

As described above, according to the present embodiment, the rope 20 attached to the drum 10 does not float at all from the drum main body 11, and as a result, the diameter φD of the both ends 91b of the rope pressing roller 91 is increased to the limit. It became possible.

This means that the difference in diameter between the central portion 91a and both end portions 91b of the rope pressing roller 91 (the portion indicated by the symbol C in FIG. 23) can be reduced, and the length of the tapered portion 91c can be reduced. The length of the central portion 91a, which is an effective pressing portion of the roller 91, can be made relatively large, and thereby, it is possible to more reliably prevent turbulent winding when the rope 20 is wound.

Moreover, according to this Embodiment, when the rope 20 is wound in multiple layers, it can prevent that the tension | tensile_strength inside the lower layer rope 20 weakens.
That is, in the conventional configuration, the tension inside the ropes 120 in the plurality of lower layers is weakened by a so-called extending effect when the ropes 120 are wound in a multi-layered manner with the extended portion 120b of the end of the rope 120 raised, and the upper layer The rope 120 becomes easier to bite.
In such a state, it is dangerous and the row is disturbed and turbulence is generated. However, according to the present embodiment, such a situation can be avoided.

1 ... Hoist (handling machine)
4 ... Device body 7 ... Motor 10 ... Drum (Drum for cargo handling machine)
DESCRIPTION OF SYMBOLS 10a ... 1st flange 10b ... 2nd flange 11 ... Drum main-body part 12 ... Guide part 13 ... Support part 20 ... Rope 30 ... Rope reciprocating feed screw 40 ... Guide shaft 50 ... Shifter block (moving body)
60 ... Limit lever unit 75 ... Limit switch 80 ... No load detection lever unit 81 ... No load detection lever 90 ... Rope presser mechanism 91 ... Rope presser roller 120 ... Conventional rope

Claims (10)

1. It is a drum for a cargo handling machine that can wind a rope in multiple stages with parallel winding,
   Cargo handling in which a plurality of convex curved guide portions for supporting and guiding the rope are provided on the surface of the cylindrical drum main body portion at predetermined intervals along the circumferential direction of the drum main body portion. Machine drum.
2. The drum for a cargo handling machine according to claim 1, wherein the guide portion is formed in a circular arc shape having a radius of curvature equal to or larger than a radius of the rope.
3. The drum for a cargo handling machine according to any one of claims 1 and 2, wherein a support portion for supporting the rope is provided between the guide portions.
4. A concave rope housing portion for housing and fixing the tip of the rope to the drum body portion;
   When a rope is pulled out from the rope housing portion, a rope having a bending process at the tip so as to correspond to the shape of the portion that guides the rope is housed and fixed in the rope housing portion of the drum main body portion. The drum for a cargo handling machine according to any one of claims 1 to 3, wherein the drum is configured.
5. A drum for a cargo handling machine according to any one of claims 1 to 4,
   A drum driving mechanism for rotating the drum for cargo handling machine;
   A cargo handling machine having a control unit for controlling the operation of the drum driving mechanism.
6. A rope feeding mechanism for guiding and moving the rope wound around the drum for the cargo handling machine or in the direction of the rotation axis of the drum;
   The rope feed mechanism
   A rod-shaped rope reciprocating feed screw which is provided in parallel with the rotation axis of the cargo handling machine drum and is rotatable together with the cargo handling machine drum;
   The rope reciprocating feed screw is mounted so as to mesh with the rope reciprocating feed screw, and is configured to move in the longitudinal direction of the rope reciprocating feed screw as the rope reciprocating feed screw rotates. A block-shaped moving body having a rope guide for guiding the rope that has been taken out;
   A rod-shaped guide shaft that is provided in parallel with the rope reciprocating feed screw and contacts the moving body to guide the moving body;
   The cargo handling machine according to claim 5, wherein the guide shaft is configured to be rotatable.
7. A rope reverse winding detection mechanism for detecting a reverse winding state of the rope unwound from the cargo handling machine drum;
   The reverse winding detection mechanism is
   A limit lever unit that contacts the rope unwound from the drum for the cargo handling machine and is rotatably attached to the movable body, and operates a limit switch by the rotational movement;
   The said limit lever unit is comprised so that the said limit switch may be operated by rotating according to the displacement of the path | route of the rope unwound from the said drum for cargo handling machines. The cargo handling machine described in the section.
8. Further comprising a no-load detection mechanism for detecting an unloaded state of the rope unwound from the drum for the cargo handling machine;
   The no-load detection mechanism is
   A load detecting lever unit that contacts the rope unwound from the drum for the cargo handling machine and is rotatably attached to the movable body, and operates a limit switch by the rotational movement;
   The non-load detection lever unit is configured to operate the limit switch by rotating in accordance with a change in tension of a rope unwound from the drum for cargo handling machinery. The cargo handling machine according to claim 1.
9. A rope presser mechanism for pressing a rope wound around the drum for the cargo handling machine;
   The rope presser mechanism is
   While contacting and pressing against the rope wound around the central portion of the drum body of the cargo handling machine drum, it does not contact with the rope wound around both ends of the drum body of the cargo handling machine drum The cargo handling machine according to any one of claims 5 to 8, further comprising a rope presser roller formed in a shape.
10. The drum drive mechanism has a DC or AC motor,
    The control unit determines a soft acceleration waveform and a soft deceleration waveform of the motor based on a rotation control unit that sets acceleration time and deceleration time of the motor, and an acceleration / deceleration signal set in the rotation control unit. A waveform control unit, and a PWM generation unit that generates a PWM waveform based on a drive waveform signal from the acceleration / deceleration waveform control unit,
    10. The motor is configured to be driven by PWM control using the rotation control unit, the acceleration / deceleration waveform control unit, and the PWM generation unit when the cargo handling machine drum is lowered. The cargo handling machine according to any one of the above.

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