JP7046406B1 - Harvester and rope winder for harvester - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a harvester and a rope winder for a harvester, which can be used in various sites and can linearly transport a carrier and a harvester with a simple configuration. SOLUTION: The main rope 14 is reciprocated via a pulley 12 and has first and second winding drums D1 and D2 around which the main rope 14 is wound. A transport vehicle 16 attached to the main rope 14 and for transporting the collecting material 24 is provided. The rotation shafts 21 and 22 of the first and second winding drums D1 and D2 in which both ends of the main rope 14 are wound are composed of a main rotation shaft 26 provided coaxially and integrally. The first take-up drum D1 is rotatably connected to the first drive motor M1 together with the main rotating shaft 26. The second take-up drum D2 can rotate via the main rotating shaft 26 and the planetary gear mechanism, and the sun gear shaft of the planetary gear mechanism is coaxially located at the center of the second take-up drum D2. A second drive motor M2 is connected to the sun gear shaft, and the first and second take-up drums D1 and D2 are differentially rotated via a planetary gear mechanism. [Selection diagram] Fig. 1

Description

The present invention relates to a harvester and a rope winder for a harvester that carry a heavy object such as wood to a harvester by operating a rope stretched in the air.

Conventionally, in the forestry field, various unloading machines have been used for the work of transporting logs felled and sawn on slopes in mountainous areas to forest roads and the like. For example, an H-type logging machine that can collect logging in a range surrounded by four columns is used in a forest area with a long slope in a deep valley. This unloading machine has a large number of overhead wires, and the arrangement of the overhead wires is complicated. In order to secure the transport mass, the loading rope is greatly loosened to suppress the tension, so that a deep valley is the applicable site. This device is called an H-type logging machine because it looks like an H character when viewed from a bird's-eye view.

On the other hand, as shown in FIG. 25, there is a conventional running skyline method in which materials are collected by a linear reciprocating motion between two columns. This is formed in a structure in which a carrier is placed on a main rope 2 folded back at a pair of fulcrums S, the main rope 2 is erected back and forth, and the pulling rope and the pulling back rope of the main rope 2 are operated to collect materials. 3 is to be transferred. This method is a rope tensioning method in which the number of overhead lines is small and it is easy to install and withdraw, but in general, there is a drawback that the material collecting material 3 is not lifted in the air and the material is collected by towing.

Further, as shown in FIG. 25, two types of conventional running skyline systems are arranged in parallel, a connecting rope 4 is provided, a self-propelled carrier 6 is connected between them, and an H-type overhead wire collecting machine 8 is configured. There is also. In this conventional running skyline system, there are an endless winding drum type as shown in FIG. 25 and a type in which the pulling line and the pulling line are operated separately.

The features of the endless take-up drum type are that one take-up drum can pull and pull back the carrier and that the tensions of the ropes can be deducted from each other. However, since the perimeter is fixed, the carrier to be operated draws an elliptical arc centering on the two fulcrums as shown by the broken line locus h shown in FIG. 25. Further, when the two sets are arranged in parallel by this operation, the distance between the ropes 2 changes, and the tension of the connecting rope 4 for the self-propelled carrier connecting the ropes may exceed the safe load.

Further, as in the comparative example shown in FIG. 4 (b), the pulling rope and the pulling back rope of the main rope 14 are operated separately to make the transport vehicle 16 move linearly, and these are arranged in parallel in two sets of the transport vehicles . Unlike the endless cord, the type capable of keeping the distance between the 16s constant has no difference in the tension acting on the cord, and each take-up drum bears all the tension. For this reason, a load is applied to the power source and the deceleration mechanism, the power loss is large, and the tension is insufficient, so that the material is towed to the ground.

In addition, as a speed reducer for a cargo handling device such as a crane, as disclosed in Patent Document 1 and Patent Document 2, there is also one using planetary gears.

In addition to the above problems, the operation of a vast surface (eg, 1,000 m in length and 300 m in width) such as an H-type logging machine exceeds the limit of a visual manual operation machine and enhances the safety of operation. Numerical control is required. Further, in order to improve the carry-out efficiency, it is required to control the tension of a suitable rope (rope). Therefore, a rope random winding prevention device is required.

Conventional rope random winding prevention devices include a traverse cam method as disclosed in Patent Document 3 and a numerical control method in which a ball screw and a servomotor are combined. The traverse cam type traverse cam (shaft with spiral groove processing for reciprocating motion) and shoe (ship-shaped in-groove sliding body: small piece to fit in the groove) have a guide surface at the intersection of the spiral grooves. Since it passes through the area where it decreases, it is not suitable for heavy loads such as H-type overhead wire collectors. If the 4 axes of the rope random winding prevention device, which is a combination of a ball screw and a servo motor, and the 4 axes of rope control are combined, 8-axis control becomes expensive.

JP-A-2002-220189 Japanese Unexamined Patent Publication No. 2010-23375 Japanese Unexamined Patent Publication No. 2018-104108

Even if an H-type overhead wire collector is constructed by combining the above background technologies, the problem that the carrier draws an elliptical arc centering on two fulcrums as described above is a problem, and the spacing between the two sets of parallel lines is large. The problem that the tension of the main rope for the self-propelled carrier that connects between them may exceed the safe load, and the problem that the power loss is large when the pulling rope and the pulling back rope are operated separately cannot be solved. Met. In addition, a rope random winding prevention device is also required.

The present invention has been made in view of the above-mentioned problems of the background technology, and is a harvester and a harvester that can be used in various sites and can linearly transport a carrier and a harvester with a simple configuration. It is an object of the present invention to provide a rope winding device for use.

The present invention includes a single main rope reciprocally arranged via a pulley, a first take-up drum fixed close to a predetermined position, and one end of the main rope fixed and wound. It is provided with a second take-up drum in which the other end of the main rope is fixed and wound, and a transport vehicle attached to the reciprocating main rope to transfer the collected material as the main rope moves. In the material collector, the rotation shafts of the first and second take-up drums around which both ends of the main rope are wound are composed of the main rotation shafts integrally provided coaxially, and the first The take-up drum is rotatably provided integrally with the main rotating shaft and connected to the first drive motor, and the second take-up drum is rotatably provided via the main rotating shaft and the planetary gear mechanism. At the same time, the sun gear shaft of the planetary gear mechanism is coaxially located at the center of the second take-up drum, the second drive motor is connected to the sun gear shaft, and the first and second take-ups are taken. The drum is a material collector provided so as to be differentially rotatable by the first and second drive motors via the planetary gear mechanism.

The main rotating shaft is fixed to the planetary gear carrier of the planetary gear mechanism provided on the second take-up drum, and the internal gear of the planetary gear mechanism is formed on the second take-up drum. An internal gear meshes with a planetary gear pivotally supported by the planetary gear carrier, and the first and second take-up drums are differentially rotated by the first and second drive motors via the planetary gear mechanism. Is.

A pair of mechanisms including the main rope, the first and second take-up drums, and the first and second drive motors is provided, and a connecting rope is erected between the pair of main ropes to connect the main ropes. Both ends of the rope are connected to the transport vehicle, and a self-propelled self-propelled transporter that moves along the connecting rope to transport the collecting material is provided to form an H-type overhead wire collecting machine.

Further, the present invention is a rope winding device for a material collecting machine that winds the main rope around the winding drum of the material collecting machine, and when the main rope is wound around the first and second winding drums. A traverse mechanism for evenly winding the main rope at a predetermined pitch equal to or larger than the diameter of the main rope is provided on the side surface of the take-up drum, the traverse mechanism is provided with a cam mechanism, and the cam mechanism is a winding drum. A moving body that moves in parallel with the rotating shaft, a drive mechanism that has a cam follower provided on the moving body and reciprocates the moving body in parallel with the rotating shaft of the take-up drum, and a drive mechanism provided in the drive mechanism. A roller cam that engages with the cam follower to reciprocate the moving body is provided, and the cam follower guides the roller cam with the moving body moved to both ends of the side surface of the take-up drum. The moving body is moved by 1/2 pitch of the predetermined pitch so that the main rope can be further wound around the outside between the main ropes wound around the winding drum, and the moving body is the main rope. This is a rope winding device for a collecting machine, in which the position of is reciprocated along the side surface of the winding drum, and the main rope is wound around the winding drum at equal intervals in a plurality of layers.

The cam follower is composed of a pair of movable cams, the roller cams are guided by the pair of movable cams at both ends of the side surface of the take-up drum, and the roller cams are guided by one of the movable cams of the cam followers. The moving body is moved to the opposite end side of the take-up drum by 1/2 pitch of the predetermined pitch, and the other movable cam is formed so as to be retractable when the roller cam is moved. ..

The drive mechanism is composed of a chain mechanism provided on the side surface of the take-up drum, the moving body is movably provided by the chain mechanism, and the center of the roller cam is a pair of chains of the chain mechanism. It is located in the center of the pin.

The lumber collector and the rope take-up device for the lumber collector of the present invention have a simple structure and enable accurate transport, can reliably move the timber to be transported, etc., and are mainly arranged in parallel. The spacing between the ropes does not change, and the tension of the connecting ropes connecting the main ropes does not exceed the safe load.

Further, the rope winding device for a harvester of the present invention can reliably wind the main rope to be wound on the winding drum in parallel at equal intervals.

It is a schematic diagram which shows the outline of the structure of the material collecting machine of one Embodiment of this invention. It is a schematic diagram (a) which shows the basic structure of the harvester of this embodiment, and is a schematic diagram (b) which shows the structure of the harvester of a comparative example. It is schematic cross-sectional view (a), (b), (c) explaining the structure and operation of the planetary gear mechanism of the material collector of this embodiment. It is a schematic diagram (a), (b) of the comparative example explaining the transfer of the material collecting by the material collecting machine of this embodiment. It is a schematic diagram explaining the transfer of the material collecting by the material collecting machine of this embodiment. It is a schematic diagram explaining the winding of the main rope by the winding drum of the material collecting machine of this embodiment. It is schematic cross-sectional view explaining the winding of the main rope by the winding drum of the material collecting machine of this embodiment. It is a schematic diagram explaining the tension applied to the wire rope of the material collector of this embodiment. It is a schematic diagram explaining the example of the tension applied to the wire rope of the material collector of this embodiment. It is a top view explaining the outline of one Embodiment of the rope winding apparatus for a harvester of this invention. It is a partial schematic view (a) and a partial enlarged view (b) of the cam mechanism of the traverse mechanism of the rope winding device for a material collector of this embodiment. It is a partial front view (a) which shows the cam mechanism and the chain mechanism of the traverse mechanism of the rope winding device for a lumber collector of this embodiment, and is the enlarged view (b) of the roller cam part. It is a partially enlarged view of the chain mechanism of the traverse mechanism of the rope winding device for a material collector of this embodiment. It is a partial fracture sectional view of the winding drum wound by the rope winding device for a material collector of this embodiment. It is a partial front view which shows the wire moving chain and the roller cam of the traverse mechanism of the rope winding device for a lumber collector of this embodiment. It is a conceptual diagram which shows the cam mechanism and the winding drum of the traverse mechanism of the rope winding device for a material collector of this embodiment. It is explanatory drawing which shows the movement of the main rope position by the cam mechanism of the traverse mechanism of the rope winding device for a material collector of this embodiment. It is a conceptual diagram which shows the cam mechanism of the traverse mechanism of the rope winding device for a material collector of this embodiment. It is a conceptual diagram (a), (b) which shows the operation of the roller cam and the cam follower of the cam mechanism of the traverse mechanism of the rope winding device for a lumber collector of this embodiment. It is a conceptual diagram which shows the operation of the cam follower of the cam mechanism of the traverse mechanism of the rope winding device for a lumber collector of this embodiment. It is a conceptual diagram which shows the winding state of the rope winding apparatus for a material collector of this embodiment. It is a partial fracture plan view which shows the rope winding apparatus for a harvester of this embodiment. It is a front view which shows the rope winding apparatus for a harvester of this embodiment. It is an enlarged side view which shows the winding drum of the rope winding apparatus for a material collector of this embodiment. It is a schematic diagram which shows the arrangement of the main rope etc. of the conventional H type skylogger.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. 1 to 9 show a harvester 10 according to an embodiment of the present invention, and the harvester 10 according to this embodiment is a pulley 12 installed in a timber logging area or the like and installed at a predetermined position. It is provided with one main rope 14 reciprocally arranged via the above, and a first take-up drum D1 and a second take-up drum D2 fixed close to a predetermined position and around which the main rope 14 is wound. .. The reciprocating main rope 14 is provided with a transport vehicle 16 for transporting the lumber collecting 24, which is the timber cut down, as the main rope 14 moves.

The main rope 14 is folded back and reciprocated by the pulley 12, and both ends 14a and 14b are fixed to the first take-up drum D1 and the second take-up drum D2, respectively. Both ends 14a and 14b of the main rope 14 are connected to the first take-up drum by a predetermined length via the pulley 17 near the first take-up drum D1 and the pulley 18 near the second take-up drum D2. It is wound around at least one of D1 and the second take-up drum D2.

A transport vehicle 16 is fixed to an intermediate portion on one side of the reciprocating main rope 14, a transport roller 15 is provided on the transport vehicle 16, and a transport roller 15 is placed on the other side of the reciprocating main rope 14. It is provided so as to be driveable on the main rope 14. Therefore, the transport vehicle 16 is fixed at a predetermined position on one side of the reciprocating main rope 14 and moves integrally at a predetermined distance between the first and second take-up drums D1 and D2 and the pulley 12. , The transport roller 15 is provided so as to be movable along the other main rope 14 on which the transfer roller 15 is placed.

One end 14a of the main rope 14 is fixed to the first take-up drum D1 and wound, and the other end 14b of the main rope 14 is fixed to the second take-up drum D2 and wound. The rotation shafts 21 and 22 of the first take-up drum D1 and the second take-up drum D2 are composed of a main rotation shaft 26 integrally provided coaxially, and the first take-up drum D1 is a main rotation shaft 26. It is integrally rotatably provided and is connected to the first drive motor M1. The second take-up drum D2 is rotatably provided via the main rotating shaft 26 and the planetary gear mechanism 30, and the sun of the sun gear 33 of the planetary gear mechanism 30 is located at the center of the second take-up drum D2. The gear shaft 32 is positioned coaxially with the rotary shaft 22, and the second drive motor M2 is connected to the sun gear shaft 32.

As shown in FIG. 6, the main rope 14 is wound around the first take-up drum D1 and the second take-up drum D2 so as to rotate in opposite directions to each other, and the first and second drive motors M1 and M2 are wound. Driven by. As a result, the first and second take-up drums D1 and D2 are provided so as to be differentially rotatable by the first and second drive motors M1 and M2 via the planetary gear mechanism 30 as described later. There is.

The main rotary shaft 26 is fixed to the planetary gear carrier 34 of the planetary gear mechanism 30 provided on the second take-up drum D2, and the second take-up drum D2 has an internal gear 38 for the planetary gear mechanism 30. It is formed. As a result, the internal gear 38 meshes with the planetary gear 36 pivotally supported by the planetary gear carrier 34, and the first and second take-up drums D1 and D2 are driven by the first and second drive motors M1 and M2. It rotates differentially via the mechanism 30.

In this embodiment, as shown in FIG. 1, a material collector 10 including a main rope 14, first and second take-up drums D1 and D2, and first and second drive motors M1 and M2. A pair of mechanisms is provided, a connecting rope 40 is erected between the pair of main ropes 14, both ends of the connecting rope 40 are connected to each of the transport vehicles 16, and the material collecting 24 is transported along the connecting rope 40. It is equipped with a self-propelled self-propelled carrier 42.

Next, the drive of the main rope 14 by the take-up drums D1 and D2 of the material collector 10 and the operation of the take-up drums D1 and D2 will be described. First, as shown in the comparative example of FIG. 4A, the main rope 14 made of an endless wire rope is hung between the two pulleys 12 and 17 by one take-up drum D , and the main rope 14 is driven by a drive motor. Assuming the operation of the transfer vehicle 16 when driven by M, the transfer vehicle 16 is conveyed in an elliptical orbit as shown by the broken line h in FIG. 4 (a). When such an elliptical orbit is drawn, when an H-type overhead wire collecting machine using a pair of collecting machines 10 is configured as shown in FIG. 1, the tension applied to the connecting rope 40 increases toward both ends in the moving direction. Therefore, it is difficult to accurately adjust the height and position of the self-propelled carrier 42 and the logging material 24, and the connecting rope 40 may be damaged due to excessive tension.

Therefore, as shown in the comparative examples of FIGS. 2 (b) and 4 (b), both end portions 14a and 14b of the main rope 14 are fixed to the first take-up drum D1 and the second take-up drum D2, respectively. Then, the main rope 14 is wound around the first take-up drum D1 and the second take-up drum D2. Then, the first and second drive motors M1 and M2 are differentially rotated so that the first take-up drum D1 and the second take-up drum D2 rotate in opposite directions. As a result, the length of the main rope 14 hung between the pulleys 12 and 17 can be adjusted, and the movement locus of the self-propelled carrier 42 and the material collecting 24 suspended from the main rope 14 is shown in FIG. 4 (b). ) Can be linear like the locus h1 shown by the broken line.

However, in the case of this configuration, the torque applied to the rotation shafts of the first and second drive motors M1 and M2 is independently applied via the first and second take-up drums D1 and D2, so that the first is large. And the load of the second drive motors M1 and M2 becomes large, and a motor having a large torque is required.

On the other hand, in the material collecting machine 10 of this embodiment, as shown in FIGS. 2 (a), 5 and the like, the main rope 14 is wound around the first take-up drum D1 and the second take-up drum D2. At the same time, the rotation shafts 21 and 22 of the first take-up drum D1 and the second take-up drum D2 are coaxially provided and configured by the main rotation shaft 26, and the first and second take-up drums D1 and D2 are By connecting with the first and second drive motors M1 and M2 via the planetary gear mechanism 30, the first and second take-up drums D1 and D2 can be differentially rotated. As a result, the movement locus of the self-propelled carrier 42 and the material collecting material 24 can be made linear like the locus h1 shown by the broken line in FIG. Moreover, since the rotary shafts 21 and 22 of the first and second take-up drums D1 and D2 are connected to the main rotary shaft 26 by the planetary gear mechanism 30, the rotation of the first and second drive motors M1 and M2 The torque applied to the shaft can be canceled out from each other, and the load of the first and second drive motors M1 and M2 can be suppressed so that the motor can be driven by a relatively small output motor.

Next, the operation of the planetary gear mechanism 30 of the material collecting machine 10 of this embodiment will be described. First, as shown in FIG. 3A, the first and second take-up drums D1 and D2 are connected to the first and second drive motors M1 and M2 via the planetary gear mechanism 30, and the sun gear 33 is connected. When the drive motor M1 is connected to the first take-up drum D1 by fixing the speed ratio U, the speed ratio U of the input / output rotation speeds of the planetary gear mechanism 30 is
U = (Z ₁ + Z ₃ ) / Z ₃ ... (1).
Here, the number of teeth Z3 of the internal gear 38 and the _number of teeth Z1 of the sun gear ₃₃ are assumed. Further, as shown in FIG. 3B, when the planetary gear carrier 34 is fixed and the output of the drive motor M2 is connected to the sun gear 33 of the planetary gear mechanism 30, the speed ratio R of the input / output rotation speed becomes.
R = −Z ₁ / Z ₃ ... (2).

Further, the rotation speed control of the first and second take-up drums D1 and D2 will be described with reference to FIGS. 6 and 7. Assuming that the radius of the first take-up drum D1 is r1, the radius of the second take-up drum is r2, the rotation speed of the first drive motor M1 is n1, and the rotation speed of the second drive motor M2 is n2. The rotation speed of the take-up drum D1 of 1 is the rotation speed n1 equal to the rotation speed of the drive motor M1, and the rotation speed nd2 of the second take-up drum D2 is
It is expressed as nd2 = U · n1 + R · n2 ... (3).
Regarding the rope speed of the main rope 14 by the first and second take-up drums D1 and D2, the rope speed V1 by the first take-up drum D1 is
V1 = 2, π, r1, n1 ... (4),
The search speed V2 by the second take-up drum D2 is V2 = 2, π, r2, nd2 = 2, π, r2, (U, n1 + R, n2) ... (5)
Will be.

Therefore, when the above sun gear 33 is fixed, n2 = 0, so that
V2 = 2, π, r2, U, n1 ... (5),
In the case of U = (Z ₁ + Z ₃ ) / Z ₃ = r1 / r2 ... (6)
From the formula (5), the rope speeds V1 and V2 of the main rope 14 by the first and second take-up drums D1 and D2 are equal.

Then, the rotation speed n1 of the first drive motor M1 and the rotation speed n2 of the second drive motor M2 are controlled, and the rope speeds V1 and V2 of the main rope 14 are set to the extension amount of the main rope 14 from the constant speed state. When the rotation speed n1 of the first drive motor M1 and the rotation speed n2 of the second drive motor M2 are adjusted in the direction of increasing the number, the main rope 14 is extended for a long time, and conversely, the rotation speed n1 of the first drive motor M1. If the main rope 14 is controlled to be wound more by either the first or second winding drums D1 or D2 by the difference in the rotation speed n2 of the second drive motor M2, the main rope 14 is unwound. The length becomes shorter. Then, by adjusting the feeding amount of the main rope 14, the self-propelled carrier 42 can be linearly moved in the erection direction of the main rope 14, as shown in FIG.

As a result, as shown in FIG. 1, when the H-type overhead wire collecting machine by the collecting machine 10 of this embodiment is configured, the self-propelled transfer machine 42 and the collecting material 24 are first as shown in FIG. And the second take-up drums D1 and D2 can be linearly moved in parallel with the straight line connecting the pulley 12. Therefore, even when the connecting rope 40 is translated, excessive tension is not applied.

Further, as shown in FIGS. 2 and 8, the tension balance at this time is a load by the self-propelled carrier 42 and the material collecting material 24 by the two main ropes 14 on the pulling side and the pulling side of the main rope 14. Since the tension W is supported, the tensions Ta and Tb applied to the main rope 14 in the figure are represented by the following equations (7) and (8).
Ta ・ sinθa + Tb ・ sinθa + Tb ・ sinθb + Tb ・ sinθb
= Ta · sinθa ++ Tb · sinθa + 2Tb · sinθb = W ... (7)
Ta ・ cosθa + Tb ・ cosθa = Tb ・ cosθb + Tb ・ cosθb
= 2Tb · cosθb
Ta · cosθa + Tb · cosθa-2Tb · cosθb = 0 ... (9)

Here, a calculation example based on FIGS. 9A, 9B, and 9C is shown below. In FIGS. 9A, 9B, and 9C, the hanging height N is 56 m, the weighted W is 6,300 kg, and the distance between fulcrums Lb is 500 m. In (a), a = 450 m, in (b), a = 250 m, in (c), a = 50 m, and the angles θa and θb are as shown in the figure.
From the above, in FIG. 9A,
Ta = 1,300kg
Tb = 3,800 kg
Ta-Tb = -2,500kg
In FIG. 9 (b),
Ta = 7,200kg
Tb = 7,200 kg
Ta-Tb = 0kg
In FIG. 9 (c),
Ta = 5,050kg
Tb = 2,550 kg
Ta-Tb = 2,500kg
Therefore, it can be seen that the material collecting machine 10 of the present embodiment functions effectively. The diameters of the first and second take-up drums D1 and D2 in the take-up state change due to the take-up of the main rope 14, but the diameters of the first and second take-up drums D1 and D2 are relative to the diameters of the first and second take-up drums D1 and D2. Since it is the diameter ratio of the main rope 14, the influence is small. Further, it can be adjusted by the drive control program of the first and second drive motors M1 and M2.

According to the logging machine 10 of this embodiment, the rotating shafts 21 and 22 of the first and second winding drums D1 and D2 are connected to the main rotating shaft 26 by the planetary gear mechanism 30, and the first and second winding drums D1 and D2 are connected. Since the second take-up drums D1 and D2 are differentially rotated to pull or pull back the main rope 14, the self-propelled carrier 42 can be configured even when the H-type overhead wire collector by the logging machine 10 is configured. The logging material 24 can be moved linearly, and excessive tension is not applied to the main rope 14 and the connecting rope 40.

Next, an embodiment of the rope winding device for a harvester used in the harvester 10 of the present invention will be described with reference to FIGS. 10 to 24. In the rope winding device 50 for a material collector of this embodiment, when the main rope 14 is wound around the first and second winding drums D1 and D2, the circumferences of the first and second winding drums D1 and D2 are rotated. A traverse mechanism 52 is provided on the side surface, which is a surface, to evenly wind the main rope 14 at a predetermined pitch P slightly wider than the diameter of the main rope 14.

As shown in FIGS. 10 to 13, the traverse mechanism 52 includes a cam mechanism 51 located on the side surface of the first and second take-up drums D1 and D2 (hereinafter, simply referred to as take-up drum D). The cam mechanism 51 has a moving body 54 that moves in parallel with the main rotation shaft 26 of the take-up drum D, and a cam follower 55 provided on the moving body 54. The moving body 54 is integrally provided with a reciprocating table 59 that supports the cam follower 55. Further, the cam mechanism 51 includes a chain mechanism 60 which is a drive mechanism for reciprocating in parallel with the rotation axis of the take-up drum D. The chain mechanism 60 includes a pair of wire moving chains 62 arranged in parallel, and the pair of wire moving chains 62 are hung between a pair of sprockets 63 provided in a frame or the like (not shown). A joint link 53 is provided in one piece of each wire moving chain 62, and a roller cam 58 that engages with a cam follower 55 to reciprocate the moving body 54 is pivotally supported between the pair of joint links 53. .. The center of the roller cam 58 is arranged at the center of a pair of pins 62a of one piece of the wire moving chain 62.

As shown in FIGS. 12 to 19, the cam follower 55 includes a pair of movable cams 56, 57 arranged axially symmetrically on a reciprocating table 59 of the moving body 54, and the pair of movable cams 56, 57. Is driven by the movement of the roller cam 58, and moves the moving body 54. The pair of movable cams 56 and 57 are located at predetermined intervals so that the roller cam 58 can pass through and can be swung by the movement of the roller cam 58 during passing. Further, movable stoppers 56a and 57a are located outside the pair of movable cams 56 and 57 in the swing direction, respectively. The movable stoppers 56a and 57a are provided on the reciprocating table 59 and are retracted so as to stop the swing of one of the pair of movable cams 56 and 57 when guiding the roller cam 58 and to enable the swing of the other. .. The retracting operation is for preventing interference with the rotation of the roller cam 58 at the positions of the sprockets 63 at both ends of the wire moving chain 62, as will be described later.

As shown in FIGS. 12, 19, 20, 20 and the like, the movable stoppers 56a and 57a are moved back and forth with the movement of the reciprocating table 59 by the stopper protrusions 56b and 57b provided integrally with the movable stoppers 56a and 57a. Guided by the step-shaped guide groove 65a formed in the material 65, it moves up and down in the vertical direction. The base material 65 is a part of a member provided integrally with a main body base material such as a frame (not shown) constituting the rope winding device 50 for a harvester, and is a plate-shaped member.

Here, when this cam mechanism is linearly moved by the chain mechanism 60, the roller cam 58 is located at the upper end or the lower end of the cam follower 55, and the sprocket of the chain mechanism 60 is at the left and right folded ends which are both ends of the drum D. Make a circular motion along 63. On the other hand, in the movable cams 56 and 57 of the pair of point-symmetrical cam followers 55, when the roller cams 58 are linearly moved by the chain mechanism 60, the cam followers 55 are both closed and sandwich the roller cams 58. The table 59 is held in the form in the traveling direction. However, if the roller cam 58 makes a circular motion along the sprocket 63 in the state where both sides are closed as it is, the passing width is insufficient. Therefore, it is necessary to perform a retracting operation to open the movable cams 56 and 57 of the cam follower 55 near the left and right turns. The movable cams 56 and 57 of the cam follower 55 can be opened and closed by holding and releasing the movable stoppers 56a and 57a that move in the vertical direction. Then, the force with which the roller cam 58 pushes the movable cams 56 and 57 increases and decreases with the center in the drum width direction as a boundary, and the pushing force in the counter-progressing direction almost disappears near the turn, so that the movable stoppers 56a and 57a move in the vertical direction. The moving force of is light load.

The chain mechanism 60 includes a drum connecting chain 64, an index device 66, a rotary encoder 68, and a cam drive chain 72, in addition to the wire moving chain 62. The drum connecting chain 64 is provided so as to be driveable by a motor for driving the take-up drum D, and an index device 66 and a rotary encoder 68 are provided coaxially with the sprocket on which the drum connecting chain 64 is wound. The index device 66 is provided so as to be able to drive the cam drive chain 72 by converting the rotational driving force from the drum connecting chain 64 into the rotating shaft 70, and drives the motor that drives the take-up drum D via the drum connecting chain 64. The wire moving chain 62 is formed to be intermittently driveable at a predetermined pitch by rotationally driving the wire moving chain 62 by a predetermined angle by a force.

Further, as shown in FIGS. 12 and 15, the traverse mechanism 52 includes a pair of wire guide rollers 74 pivotally supported by a reciprocating table 59 that moves integrally with the moving body 54. The main rope 14 is located between the pair of wire guide rollers 74, the winding position is intermittently displaced as the moving body 54 moves, and the main rope 14 is placed on the wire winding surface on the side surface of the winding drum D at a predetermined pitch. Wrap while moving with P, and then wrap in multiple layers. As shown in FIG. 14, a wire groove 76 is formed on the wire winding surface which is the side surface of the take-up drum D. The wire groove 76 is an arcuate groove having a width slightly narrower than the diameter of the main rope 14, formed with a slight space between the wire grooves 76, and slightly shallower than the radius of the main rope 14. The wire 14 can be wound around the take-up drum D at a constant pitch P. Further, the pitch Ps of the wire grooves 76 are formed in a direction orthogonal to the rotation axis of the take-up drum D at intervals slightly larger than the diameter of the main rope 14.

Next, the operation of the traverse mechanism 52 that winds the main rope 14 around the take-up drum D will be described below. The traverse mechanism 52 moves the main rope 14 to the adjacent winding position in a state where the main rope 14 is wound around the winding drum D and makes one round. The driving force at the time of movement is the index device 66 and the chain mechanism. The driving force of the driving motor of the drum D is transmitted via 60. The traverse mechanism 52 moves the moving body 54 at a predetermined pitch P slightly larger than the diameter of the main rope 14 so as to be orthogonal to the rotation axis of the take-up drum D, and moves the main rope 14 to the wire groove 76. Wrap around. The movement to the adjacent winding position is a state in which the main rope around the wire groove 76 on the side surface of the winding drum D is sandwiched between a pair of wire guide rollers 74 within a certain narrow range on the side surface of the winding drum D. Move to the adjacent wire groove 76, and repeat this process to wind the main rope 14 around the take-up drum D. When the main rope 14 is wound around the wire groove 76 of the take-up drum D and the winding position reaches one end of the side surface of the take-up drum D, as shown in FIGS. 15 to 17, the cam mechanism 51 The moving body 54 is moved by 1/2 of the pitch P, and the main rope 14 is further wound on the intermediate position between the main ropes 14 previously wound around the take-up drum D.

At the end of the take-up drum D, the roller cam 58 of the chain mechanism 60 guides the cam follower 55 to move the moving body 54 by 1/2 of the pitch P, as shown in FIG. As a result, as shown in FIG. 14, the main rope 14 is placed in the valley between the previously wound main ropes 14 and then wound around the winding drum D at a predetermined pitch P. Then, when the other end is reached, the moving body 54 is moved by the cam follower 55 by 1/2 of the pitch P in the same manner as described above, and the main rope is moved in the valley between the main ropes 14 wound earlier. 14 is wound. By repeating this, the main rope 14 is wound around the take-up drum D over a plurality of layers.

At this time, the operation of the cam follower 55 of the cam mechanism 51 moves the winding position of the wound main wire 14 by 1/2 of the pitch P at both ends of the side surface of the winding drum D, as shown in FIG. However, the roller cam 58 arranged at the center of the pair of pins 62a of the wire moving chain 62 rotates along the sprocket 63 around which the wire moving chain 62 is wound at the end of the wire moving chain 62, and the cam follower. The moving body 54 is moved along the outer cam surface of the pair of movable cams 56, 57 of 55 by 1/2 of the pitch P. As a result, the main rope 14 can be moved by 1/2 of the pitch P and can be accurately wound on the valley between the previously wound main ropes 14.

Further, when the moving body 54 is moved by the roller cam 58 at 1/2 pitch, the pair of movable cams 56 and 57 of the cam followers 55 are provided so as to be swingable with the rotation of the roller cam 58, so that the wire can be moved. When the roller cam 58 rotates along the sprocket 63 of the chain 62, one of the movable stoppers 56a and 57a swings and retracts, the cam follower 55 and the roller cam 58 interfere with each other, and the roller cam 58 rotates. Does not interfere with.

The rope winding device 50 for a harvester of this embodiment is used for the harvester 10 of the present invention as shown in FIG. 21, and the position of the bent end A of the main rope 14 is as shown in FIG. Since it is installed in the center of the width of the drum D, it is equipped with a sighting device 67 for observing the point A.

The force with which the roller cam 58 pushes the cam followers 56 and 57 with respect to the center of the side surface of the drum D in the width direction changes depending on the angle θ which is the direction of the main rope 14. That is, the magnitude of the force F for the pair of wire guide rollers 74 to guide the main rope 14 is obtained from the cross section perpendicular to the axis of the drum D and the rope angle, and the maximum value is obtained from the uniform angle when biased to any end. growing. From this, it is desirable that the rope angle θ is equal on the left and right sides of the center of the drum D. For example, in FIG. 21, assuming that the tension of the main rope 14 is T and the component force of the drum D in the rotation axis direction is F.
F = T · sinθ (10).
When an actual load is applied to Equation 10, for example, assuming that the width of 1/2 of the drum D is 0.6 m, the distance between the drum D and the pulley 17 is 12 m, and the tension T = 7200 kg weight.
F = 7200 · sin (tan ^-1 (0.6 / 12))
= 360 (kg weight)
Will be.

As shown in FIGS. 22 to 24, the material collecting machine rope winding device 50 of this embodiment comprises the material collecting machine 10 of the above-described embodiment, and the material collecting machine 10 winds the rope for the material collecting machine. A device 50 is provided to enable smooth winding and unwinding of the main rope 14.

According to the harvester 10 and the rope winder 50 of this embodiment, it is suitable for various forest areas such as mountain slopes where timber is cut, and the number of overhead lines is small, which saves energy and power. It is possible to form an H-type overhead wire collecting machine that can form a material collecting machine 10 that enables the material to be used, enables linear movement of the material collecting material 24, and enables good drive operation.

10 Material collectors 12, 17 Slippers 14 Main ropes 16 Conveyors 21 and 22 Rotating shafts 24 Collecting materials 26 Main rotating shafts 30 Planetary gears Mechanism 32 Sun gear shafts 33 Sun gears 34 Planetary gear carriers 36 Planetary gears 38 Internal gears 40 Connecting lines 42 Self-propelled carrier 50 Rope take-up device for lumber collector 51 Cam mechanism 52 Traverse mechanism 54 Moving body 56, 57 Movable cam 56a, 57a Movable stopper 58 Roller cam 59 Reciprocating table 60 Chain mechanism 62 Wire moving chain 64 Drum connection chain 74 Wire guide roller 76 Wire groove D, D1, D2 Take-up drum M1, M2 Drive motor

Claims (6)

A single main rope reciprocated via a pulley, a first take-up drum fixed close to a predetermined position, and one end of the main rope fixed and wound, and the main rope. A material collector equipped with a second take-up drum whose other end is fixed and wound, and a transport vehicle which is attached to the reciprocating main rope and transfers the material as the main rope moves. There,
The rotation shafts of the first and second take-up drums around which both ends of the main rope are wound are composed of a main rotation shaft coaxially provided integrally.
The first take-up drum is rotatably provided integrally with the main rotating shaft and is connected to the first drive motor.
The second take-up drum is rotatably provided via the main rotation shaft and the planetary gear mechanism, and the sun gear shaft of the planetary gear mechanism is coaxially located at the center of the second take-up drum. , A second drive motor is connected to the sun gear shaft,
The first and second take-up drums are a material collector provided so as to be differentially rotatable by the first and second drive motors via the planetary gear mechanism. The main rotating shaft is fixed to the planetary gear carrier of the planetary gear mechanism provided on the second take-up drum, and the internal gear of the planetary gear mechanism is formed on the second take-up drum. A claim that the internal gear meshes with a planetary gear pivotally supported by the planetary gear carrier, and the first and second take-up drums are differentially rotated by the first and second drive motors via the planetary gear mechanism. Item 1 The material collecting machine. A pair of mechanisms including the main rope, the first and second take-up drums, and the first and second drive motors is provided, and a connecting rope is erected between the pair of main ropes to connect the main rope. 2. 2 The logging machine described. A rope winder for a harvester that winds the main rope around the take-up drum of the harvester according to any one of claims 1 to 3.
When winding the main rope around the first and second take-up drums, the side surface of the take-up drum is provided with a traverse mechanism for evenly winding the main rope at a predetermined pitch equal to or larger than the diameter of the main rope.
The traverse mechanism includes a cam mechanism.
The cam mechanism has a moving body that moves in parallel with the rotation axis of the winding drum, and a cam follower provided on the moving body.
It is provided with a drive mechanism for reciprocating the moving body in parallel with the rotation axis of the take-up drum, and a roller cam provided in the drive mechanism for engaging with the cam follower to reciprocate the moving body.
The cam follower guides the roller cam in a state where the moving body is moved to both ends of the side surface of the winding drum, and moves the moving body by 1/2 pitch of the predetermined pitch to wind the moving body. The main rope can be further wound around the outside between the main ropes wound around the drum.
The moving body is characterized in that the position of the main rope is reciprocated along the side surface of the take-up drum, and the main rope is wound around the take-up drum in a plurality of layers at equal intervals at the predetermined pitch. Rope winding device for material machines. The cam follower is composed of a pair of movable cams, the roller cams are guided by the pair of movable cams at both ends of the side surface of the take-up drum, and the roller cams are guided by one of the movable cams of the cam followers. 4. Claim 4 in which the moving body is moved to the opposite end side of the take-up drum by 1/2 pitch of the predetermined pitch, and the other movable cam is retractable when the roller cam is moved. The described rope winding device for a lumber collector. The drive mechanism is composed of a chain mechanism provided on the side surface of the take-up drum, the moving body is movably provided by the chain mechanism, and the center of the roller cam is a pair of chains of the chain mechanism. The rope winder for a harvester according to claim 4 or 5, which is arranged at the center of a pin.

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