JP4272982B2 - Hoisting and towing machine - Google Patents

Description

  The present invention relates to a hoisting and towing machine, and more particularly to a hoisting and towing machine provided with a driving force switching means for switching the rotational speed of a load sheave.

It has already been proposed to provide power transmission switching means for transmitting the driving force of the handwheel to the load sheave in the hoisting and towing machine. (For example, see Patent Document 1 and Patent Document 2)
In Patent Document 1, a spline having a slight torsion angle in the direction opposite to the winding rotation direction of the drive shaft is engraved on a part of the shaft, and the spline is engaged by the axial thrust generated by the torsion angle. A pinion clutch that reciprocates on the shaft is provided, and a pawl clutch that engages with the pinion clutch is provided at one end of a load lifting wheel or a steel cable, and the pinion clutch is pressed against the pawl clutch. A spring is inserted into the end of the drive shaft on the opposite side of the claw clutch and combined with a known reduction gear mechanism, so that a high speed is automatically obtained when no load is applied and a low speed is automatically obtained when a load is applied. Then, the drive shaft is provided with a spline, the gear can be moved with respect to the spline, and when a load is applied, the load sheave (ring wheel) is rotated via the reduction gear and the load gear, When the load is shifted gear, it is intended to enable high-speed driving by driving the Rodogiya directly from the gear.

Patent Document 2 describes a manual chain block including a hand wheel that is rotated by a hand chain, and a load sheave that winds and lowers the load chain in conjunction with the rotation of the hand wheel. A rotation ratio switching means that can be switched to increase the normal rotation ratio of the load sheave relative to the handwheel is provided. The rotation ratio switching means includes a speed increasing gear group and a switching operation section, and the switching operation section A rotational force transmission shaft that is rotatably arranged around the same axis as the input shaft connected to the wheel and transmits rotational force to the pressure contact plate of the brake part, and can be rotated integrally with the rotational force transmission shaft and in the axial direction A sliding member provided so as to be slidable; and a swing operation mechanism that slides the sliding member in the axial direction. The speed increasing gear is integrated with the input shaft. A first gear provided, a second gear meshing with the first gear, a third gear provided to rotate integrally with the second gear, the slide member and the third gear. The third gear and the fourth gear in a large rotation ratio switching state in which the sliding member is slid to the third gear side by the swing operation mechanism. In the normal rotation ratio switching state in which the slide member is slid to the first gear side by the swing operation mechanism, the fourth gear is disengaged from the third gear, and the slide member is moved to the first gear. It is configured to rotate integrally. When there is no load, the input shaft is rotated from the handwheel, the speed is increased by the first gear, the fourth gear is rotated from the third gear, the slide member is rotated, and the pressure contact plate , Load sheave via brake unit output shaft and reduction gear At the time of load, the swing member is operated to move the slide member to the first gear side, the meshing of the fourth gear and the third gear is released, and the rotation of the first gear is directly transmitted to the fourth gear. Then, the load sheave is driven to decelerate via the rotational force transmission shaft.
Japanese Utility Model Publication No. 46-19539 (2 pages, Fig. 2) JP 2000-86168 A (pages 3 to 4, FIGS. 1 and 7)

  However, in the device described in Patent Document 1 described above, the gear itself is a power switching member and can be moved by inserting the gear into a spline. It has become an obstacle to conversion. Further, when the meshing of the gears cannot be performed smoothly, there is a problem that a failure occurs at the time of switching.

  In the device described in Patent Document 2, the speed of the handwheel is increased by the first gear or the like on the speed increasing drive shaft, and the load sheave is driven at a higher speed via the speed reducing gear. Since the transmission mechanism is complicated and the operation at the time of switching is diverse, the switching operation cannot be performed smoothly, and the apparatus is unavoidably large because of the complicated structure described above. It had the problem that.

In order to solve the above-mentioned problem, the invention according to claim 1 of the present invention relates to a driving shaft that drives a load sheave, a brake hook that is externally mounted on the driving shaft, and a driving force from a handwheel. In a hoisting and traction machine having a drive member that transmits to a drive shaft via a brake hook, a drive force deceleration transmission system that transmits a drive force from a handwheel to the drive shaft on the brake side of the load sheave, And a slide member having an engagement portion that is interposed between the drive shafts and engages with the drive shaft on the inside, and a projection portion that engages with the load sheave at the end portion, A hoisting and pulling machine comprising a driving force switching means for switching a driving force high-speed transmission system that transmits to a load sheave without passing through a driving shaft .

The invention according to claim 2 is characterized in that the slide member is fitted to a drive shaft including a power transmission portion and an idling portion, slides in the axial direction, and switches the drive force. Further, the invention according to claim 3 is characterized in that the slide position of the slide member is regulated by a regulating member whose end is rotatably attached to the drive shaft and the other end is fitted to the operation bar. It is what. The invention according to claim 4 is characterized in that, in each of the above-described inventions, a cylindrical projecting portion into which one end of the driving force switching means is fitted is provided on the brake side of the load sheave. The invention according to claim 5 is characterized in that the brake hook is brought into contact with the end portion of the brake side frame to restrict the movement in the axial direction.

  The hoisting and pulling machine of the present invention is provided with a power transmission switching means formed of a slider or the like on the brake side, and the power transmission switching means causes the driving force from the handwheel to be transmitted via a drive shaft linked to the speed reducer. Switching between the power transmission system that drives the load sheave and the power transmission system that transmits the driving force directly from the slider to the load sheave can be performed reliably and smoothly with a simple operation of moving the slider. A speed change device capable of arbitrarily changing the hoisting speed without increasing the size of the device, and a hoisting and pulling machine capable of installing a free-wheeling mechanism can be provided, and a slider which is a main member of the power transmission switching device described above Is interposed between the brake hook and the drive shaft, engages with the drive shaft on the inside, and protrudes at the other end with a protrusion of a protrusion provided on the brake side of the load sheave. Since the slider is interposed between the brake spacer and the drive shaft, the slider can be installed with a size substantially the same as that of the conventional device without increasing the size in the radial direction. Thus, the size can be greatly reduced as compared with the conventional apparatus.

  In addition, a cylindrical projecting portion into which one end of the slider serving as the driving force switching means is fitted is provided on the brake side of the load sheave so that the slider serving as the driving force switching means is fitted inside the load sheave. Since a space for joining can be provided, it is easy to insert the slider, and the power transmission can be easily switched, and the size can be reduced as compared with the conventional device. Since the pressure receiving part engages with the brake side frame end of the frame body, a slider can be built inside the brake hook, providing a hoisting and pulling machine that can downsize the device and easily transmit power it can.

  Further, since the loosening means can be engaged with the slider via a restricting member that can move in the length direction and the rotational direction, and the idle state can be accurately and easily made free via the restricting member. The height can be adjusted freely.

  Embodiments of the present invention will be described below.

  Hereinafter, the hoisting and pulling machine according to the first embodiment of the present invention will be described with reference to FIGS. 1 is a front cross-sectional view of the hoisting and traction machine of the first embodiment, FIG. 2 is a partial cross-sectional view showing a deceleration operation under load in FIG. 1, and FIG. 3 is a cross-sectional view taken along line AA in FIG. ) Is a high speed operation, (b) is a cross-sectional view showing a deceleration operation, FIG. 4 is a BB cross-sectional view, FIG. 5 is a CC cross-sectional view, FIG. 6 is a DD cross-sectional view, and FIG. FIG. 8A is a front view, FIG. 8B is a cross-sectional view, FIG. 8 shows a slider, FIG. 8A is a front view, FIG. 8B is a cross-sectional view along AA, and FIG. FIG. 9 is a sectional view, FIG. 9 shows a regulating member, (a) is a front view, and (b) is a side view. In the figure, 1 is a load sheave that is rotatably supported, 1a is a recess provided in the brake side protrusion of the load sheave, 1b is a protrusion provided on the inner surface of the recess of the brake side protrusion, and 1c is the brake side protrusion. , 2 is a drive shaft, 2a is a serration portion, 2b is an idling portion, 3 is a reduction gear, 4 is a brake pocket, and the end surface is in contact with the main body frame, and movement in the axial direction is restricted. 5 is interposed between the brake spacer 4 and the drive shaft 2, and has a protrusion 5 a that protrudes toward the load sheave, a serration portion 5 b that engages with the serration portion 2 a of the drive shaft 2 on the inside, and an operation margin provided at the tip. 6 is a slider provided with a protrusion 5c that engages with the protrusion 6a. 5 d is a recess of the slider 5, 5 e is a flange of the slider 5, and 5 f is a slide surface that comes into contact with the projection 6 a of the operation limit 6. 6 is an operation limit, 6a is a protrusion provided inside the operation limit 6, 6b is a fitting groove into which a protrusion at the end of the regulating member is inserted, 6c is a locking groove into which a retaining member is fitted, and 7 is One-way clutch plate, 8 is a one-way clutch roller, 9 is a brake plate, 10 is a drive member, 10a is a female screw portion of the drive member, 11 is a belt, 12 is a handwheel, 12a is a fitting portion, 13 is an upper hook, and 14 is Main body frame, 14a is a brake side frame, 14b is a reducer side frame, 14c is a connecting frame, 15a is a brake side cover, 15b is a reducer side cover, 16 is a cover fitting part, 17 is a thick part of the frame, 18 Is a brake spacer cover hole, 19 is a one-way roller joint hole, 20 is a roller support ring locking groove, 21 is a regulating member, and 21a is a first protrusion of the slider. 3a, the second protrusion 23b, and the step 23c are in contact with and engaged with each other. The bottom of the regulating member having a non-circular bottom shown in FIG. 9 is provided, 22 is a retaining member, and 23a is provided inside the slider 5. Similarly, the first protrusion 23b is a second protrusion 23c is a stepped portion 24, a torsion spring 24, a compression spring 25, and a screw 26. As shown in FIG. 1, a brake side frame 14a and a reducer side frame 14b and a connecting frame 14c for connecting and coupling both are provided. Each of the frames 14a and 14b has an overhanging portion, and an outer peripheral edge thereof The cover fitting part 16 with which the brake side cover 15a and the reduction gear side cover 15b are fitted is provided. The brake side frame 14a is provided with a thick portion 17 extending outward from the bearing portion of the load sheave 1, and the thick portion 17 sequentially has a brake pocket bearing hole 18, a brake pocket cover section 18a, A one-way clutch roller joint hole 19 and a roller support ring locking groove 20 are provided. The thick portion 17 is a molten metal flow portion (introduction portion) at the time of molding. By forming the brake cover cover portion as a thick portion, the molten metal is transferred from the thick portion 17 to the brake side frame 14a at the time of molding. Is directly formed on the reduction gear side frame 14b via the connecting frame 14c, so that both the frames 14a, 14b and the connecting frame 14c can be formed to a desired thickness. In the present embodiment, as described above, by providing the thick portion in the brake pocket cover portion of the frame 14a, the molten metal flow can be made smooth, and the entire frame 14a, 14b can be thinned. The casting time can be shortened, and the product strength can be improved with the homogenization of the structure.

  The drive / brake portion of the hoisting and traction machine constitutes a so-called mechanical brake by the drive member 10 connected to the handwheel 12, the brake spacer 4, the one-way clutch plate 7, the one-way clutch roller 8, and the brake plate 9. The one-way clutch mechanism may be configured as the most general mechanical brake including a ratchet wheel (claw wheel) and a locking claw (not shown), but the above-described configuration is small and the one-way clutch mechanism is accommodated in the brake pocket cover. This is a preferred form. During normal operation, the rotational driving force of the handwheel 12 is transmitted to the drive shaft 2 via the drive member 10, the brake spacer 4, and the slider 5, and further loaded from the drive shaft 2 via the speed reduction mechanism including the reduction gear 3. It is transmitted to the sheave 1. As shown in FIG. 5, the brake spacer 4 and the slider 5 are coupled so as to be able to transmit a rotational force, and the slider 5 is fitted to the drive shaft 2 so as to be slidable within a predetermined range in the axial direction. As shown in FIG. 4, a non-circular fitting portion 12a is provided inside the handwheel 12, and the driving member 10 is fitted to the fitting portion 12a so that power can be transmitted. Further, a female screw 10 a is screwed inside the driving member 10, and the female screw 10 a is screwed with a screw provided on the outer periphery of the brake pocket 4. A brake plate 9 is provided on the outer periphery of the brake wall 4 so as to be coaxially rotatable. The brake plates 9 are provided between the pressure receiving portion 4 a formed at one end of the brake wall 4 and the drive member 10 as a pair. The brake pocket 4 is rotatably provided. Similarly, a one-way clutch roller joint hole 19 is provided between the brake plates 9 and 9 in a recess 7a of the clutch plate 7 and a recess 7a of the clutch plate 7 that is provided coaxially on the outer periphery of the brake pocket 4. And a one-way clutch roller 8 inscribed therein.

  Further, as described above, the inside of the brake spacer 4 is concavo-convexly fitted so as to be able to transmit rotation with the slider 5 and to slide in the axial direction, and as shown in FIG. The side end portion is in contact with a protrusion 1b provided on the inner surface of the concave portion 1a of the cylindrical protruding portion 1c protruding toward the brake side of the load sheave 1, and transmits the rotational shaft power of the hand wheel 12 to the load sheave 1. A portion 5a is provided. The protrusion 5a slides in the axial direction with respect to the recess 1a of the protrusion 1c of the load sheave 1, and can be switched between an engaged state and a disengaged state with the protrusion 1b. As shown in FIG. 2, a serration 5 b is provided inside the slider 5, and the serration 5 b is slidably fitted to a serration portion 2 a provided outside the drive shaft 2. The slider 5 slides in the axial direction between the serration portion 2a of the drive shaft 2 and the idling portion 2b having a smaller diameter than the serration portion 2a. When the slider 5 is slid until the projection 5a is completely engaged with the projection 1b, the serration 5b Moves to the idling portion 2b, and the engagement with the serration portion 2a is released. Thus, the switching operation to the high-speed transmission system is facilitated by inserting the end portion of the slider 5 into the cylindrical projecting portion 1c of the load sheave. As shown in FIGS. 3A and 3B, the other end of the slider 5 has a flange 5e provided with a protrusion 5c that abuts the protrusion 6a that protrudes in the axial direction from the inner end surface of the operation end 6. A recess 5d into which the protrusion 6a is fitted is provided on both sides of the protrusion 5c. As shown in FIGS. 1 and 2, the operation limit 6 is rotatably attached to the flange 5e of the slider 5 by a retaining member 22, and the rotatable range is restricted by the protrusion 5c and the protrusion 6a. . Reference numeral 21a denotes a bottom portion of the regulating member 21, which has a bottom portion that abuts and engages with a first projection 23a, a second projection 23b, and a step portion 23c of the slider, which will be described later, and regulates the axial position of the slider. The operation limit 6 is engaged with the slider 5 by a retaining member 22 that is fitted in a locking groove 6c provided in the inner peripheral portion of the protrusion that houses the flange 5e and is provided so as to contact the end flange 5e of the slider 5. The operation limit 6 is restricted from moving in the axial direction by the retaining member 22.

  As shown in FIGS. 8 and 9, the inner periphery of the slider 5 on the operation side has a recess for accommodating the bottom portion of the regulating member 21, and the bottom portion of the regulating member 21 and the slider are disposed on the inner periphery of the recess. 5 is provided with a protrusion for restricting the position in the axial direction. The protrusion is composed of a first protrusion 23a extending from the end face on the side of the loose end 6 to the bottom of the recess, the first protrusion 23a, and a second protrusion 23b having a different depth. The first protrusion 23a or the second protrusion 23b is contacted and engaged to restrict the axial position of the slider 5 and the rotation range of the slider 5 relative to the restricting member 21. Further, the operation limit 6 and the regulating member 21 are movable in the circumferential direction within the range of the stroke in the circumferential direction regulated by the slide surface 5 f provided between the protrusions 5 c of the slider 5. Further, the slider 5 and the regulating member 21 are linked to each other by a torsion spring 24 whose one end is engaged with the projection 5c end surface of the slider 5 and the other end is engaged with the regulating member 21. One end is engaged with the base portion 21a of the restricting member 21, and the other end is linked with a compression spring 25 engaged with the inner end face of the operation end 6. The restricting member 21 is connected to the slider 5 by the torsion spring 24. A rotational urging force is applied in the counterclockwise direction on three sheets of paper, and an urging force in the axial direction is applied to the slider 5 by the compression spring 25 via the operation limit 6. The state shown in FIG. 2 is a state in which the bottom portion 21a of the regulating member 21 is nipped and engaged with the first protrusion 23a and the second protrusion 23b of the slider 5 and is in contact with the step portion 23c. The slider 25 is slid to the operation end 6 side (outside the main body) by the spring 25, and the serration portion 5d engages with the serration portion 2a of the drive shaft 2 to transmit the driving force from the slider 5 to the drive shaft 2, as shown in FIG. When the slider 5 is pushed into the load sheave side through the operation limit 6, the bottom 21a of the restricting member 21 is released from the rotation restriction by the second protrusion 23b, and the rotational biasing force of the torsion spring 24 causes the first one to the other. It rotates until it contacts one protrusion 23a. Even if the operation finger 6 is released in this state, the bottom portion 21a rides on the second protrusion 23b, so that this state is maintained against the compression spring 25. As a result, the slider 5 is fixed at the position of the idling portion 2 b of the driving member 2 and does not engage with the driving member 2. The drive shaft 2 having the serration portion 2a and the idling portion 2b, the slider 5, the restriction member 21 for restricting the position of the slider 5, and the operation limit 6 for operating the restriction member 21 form a power transmission switching device.

  Next, the driving force switching operation according to the present embodiment will be described. During normal operation (when the operation force 6 is in the state shown in FIG. 2), the slider 5 is pushed toward the idle rotation 6 by the compression spring 25, and the serration portion 5b of the slider 5 engages with the serration portion 2a of the drive shaft 2. The rotation of the handwheel 12 is transmitted only to the drive shaft 2 through the drive member 10, the brake spacer 4, and the slider 5, and is transmitted from the drive shaft 2 to the load sheave 1 through the speed reduction mechanism including the reduction gear 3. Drives the load sheave 1 at a reduced speed.

  Next, switching to high speed operation when no load is applied is as follows. When the idle gear 6 is pressed in the axial direction, the slider 5 is pushed in the axial direction of the load sheave 1 as described above, and at the same time, the regulating member 21 is pressed by the torsion spring 24. Rotates a predetermined stroke, and the position of the slider 5 in the axial direction is fixed. The slider 5 moves to the idling portion 2 b of the drive shaft 2, the engagement with the serration portion 2 a is released, and transmission of the driving force to the drive shaft 2 through the slider 5 is interrupted.

  Further, the operation will be described. Switching from the driving force high-speed transmission operation state to the driving force transmission operation state is performed until the projection 6a provided on the inner side of the operation edge 6 contacts the projection 5c at the slider end against the rotational force of the torsion spring 24. When rotated clockwise, the bottom 21a of the restricting member 21 is released from the ride on the second protrusion 23b of the slider 5 by the helical groove 6b of the operation edge 6, and the slider is pushed toward the operation edge 6 by the compression spring 25. Move. During this operation, the slider 5 is urged toward the operation end 6 in the axial direction by the compression spring 25 and pushed, so that the slider 5 is engaged with the serration portion 2a of the drive shaft 2 and the drive shaft 2 is interposed via the slider. Transmit driving force to. To switch from the driving force deceleration transmission operation state to the driving force high speed transmission operation state, when the operation force 6 is pushed against the compression spring 25 in the axial direction, the bottom portion 21a of the regulating member 21 and the bottom portion 21a of the regulating member 21 are Stroke is performed from the rotation restriction by the second protrusion 23 b until it is released, and the restriction member 21 is rotated counterclockwise by the torsion spring 24 with the operation limit 6. At this time, the operation edge 6 is rotated until the protrusion 5 c provided on the inner side of the protrusion 5 c of the slider 5 interferes with the protrusion 6 a on the inner side of the idle rotation 6. At the same time, the regulating member 21 is the first protrusion opposite to the slider 5. It rotates to the position where it abuts against 23a.

  On the other hand, since the slider 5 is pushed toward the load sheave 1, the protrusion 5 a provided on the load sheave side of the slider 5 is inserted inside the protrusion 1 c of the load sheave 1, and inside the protrusion 1 c. The protrusion 5 can be engaged with the provided protrusion 1b, and the rotation of the slider 5 directly rotates the load sheave 1 at a high speed via the protrusion 5a of the slider 5 and the protrusion 1b of the load sheave 1. Therefore, since the load sheave 1 is directly rotated from the handwheel 12 via the drive member 10, the brake spacer 4, and the slider 5 without using the speed reduction device, the load sheave 1 is rotated at a high speed.

  FIG. 10 shows another embodiment in which a power transmission device and an idling device are provided, and FIG. 10 is a cross-sectional view taken along the line DD in FIG. In this embodiment, the protrusion 1c of the load sheave 1 does not have a protrusion 1b for transmitting power. Therefore, at the time of idle rotation, the slider 5 is not locked with the load sheave, that is, in an idle state. Other configurations are exactly the same as those of the first embodiment, and a description thereof is omitted.

  In the above-described embodiment, the power transmission switching means formed of a slider or the like is provided on the brake side, and the drive shaft that links the driving force from the handwheel with the speed reduction device by switching the power transmission by the switching means. Switching between the power transmission system that drives the load sheave and the power transmission system that directly transmits the driving force from the slider to the load sheave can be performed reliably and smoothly with a simple operation of moving the slider. Thus, it is possible to provide a hoisting and pulling machine in which a power switching means, a speed changing device, and an idle rotation mechanism can be installed without increasing the size of the device.

  The slider, which is the main member of the power transmission switching device described above, is interposed between the brake spacer and the drive shaft, engages with the drive shaft on the inner side, and engages with the projection of the load sheave at the other end. Protrusions are provided, and the slider is interposed between the brake spacer and the drive shaft. The slider is installed in the same size as the conventional device without increasing the size in the radial direction to provide the slider. Since it can be installed, it can be significantly reduced in size compared with the conventional apparatus.

  In addition, the slider is externally mounted on the drive shaft inside the brake shaft, and the power transmission is switched by sliding in the axial direction. Therefore, no special space for providing the power transmission switching means is required. The size of the apparatus can be reduced.

  In addition, a cylindrical projection that houses one end of the driving force switching means is provided on the brake side of the load sheave so that a slider that is the driving force switching means is fitted inside the load sheave. Since the space can be provided, the slider can be easily inserted, the power transmission can be easily switched, and the size can be reduced as compared with the conventional device. Furthermore, the pressure receiving portion of the brake wall is engaged with the brake side frame end of the frame body, and is not engaged with the drive shaft as in the conventional device, so that the slider is made inside the brake wall. It is possible to provide a hoisting and pulling machine that can easily reduce the size of the device and transmit power.

  In addition, since the operation limit can be engaged with the slider via a restricting member that can move in the length direction and the rotational direction, and the free-running state can be accurately and easily made via the restricting member. The length can be adjusted freely.

  Further, the operation is moved by moving the slider via the regulating member, so that the load sheave is driven at a low speed via the drive shaft and the reduction gear mechanism, and the idle state where the slider is positioned at the idling portion of the drive shaft, The slider engages with the load sheave, and the load sheave can be switched to high-speed driving.

  In the above-described embodiment, the slider 5 is configured to drive the load sheave 1 through the slider 5 by engaging the protrusion 5a at the tip of the slider 5 with the protrusion of the load sheave 1 at the idle position. However, the present invention is not limited to this configuration, and the idle position where the slider completely idles between the deceleration transmission position where the slider 5 and the drive shaft 2 are engaged and the high speed transmission position where the slider 5 directly drives the load sheave 1. It is naturally possible to provide them.

FIG. 3 is a side cross-sectional view of the hoisting and pulling machine according to the first embodiment. The fragmentary sectional view which shows the time of deceleration operation in FIG. FIGS. 2A and 2B are cross-sectional views taken along the line A-A in FIG. 1, wherein FIG. BB sectional drawing. CC sectional drawing. DD sectional drawing. FIG. 4A is a front view, and FIG. A slider is shown, (a) is a front view, (b) is AA sectional drawing, (c) is BB sectional drawing. A restricting member is shown, (a) is a front view, (b) is a side view. DD sectional drawing of the winding / traction machine of Embodiment 2. FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Load sheave 1a Concave part 1b Protrusion 1c Protrusion part 2 Drive shaft 2a Serration part 2b Sliding part 3 Reduction gear 4 Brake unit 4a Pressure receiving part 5 Slider 5a Protrusion part 5b Serration 5c Protrusion part 5d Concave part 5e Flange 5f Sliding face 6 Projection 6b Fitting groove 6c Locking groove 7 One-way clutch plate 8 One-way clutch roller 9 Brake plate 10 Drive member 10a Female screw 11 Belt 12 Handwheel 12a Fitting portion 13 Upper hook 14 Main body frame 14a Brake side frame 14b Reducer side frame 14c Connecting frame 15a Brake side cover 15b Reducer side cover 16 Cover fitting part 17 Thick part 18 Brake pocket bearing hole 18a Brake pocket cover part 19 One-way clutch roller joint hole 20 Roller support Ring engagement groove 21 regulating member 21a bottom 22 retaining member 23a first protrusion 23b second protrusion 23c stepped portion 24 torsion spring 25 compression spring 26 screw

Claims (5)

A hoisting / winding unit provided with a drive shaft that is linked to the speed reduction mechanism and that drives the load sheave, a brake hook that is externally mounted on the drive shaft, and a drive member that transmits the driving force from the handwheel to the drive shaft via the brake hook. In a traction machine, a drive force deceleration transmission system that transmits the drive force from the handwheel to the drive shaft , a brake spacer, and a drive shaft are interposed between the drive sheave and the inner side of the load sheave. A driving force high-speed transmission system that consists of a sliding member with an engaging part and a protrusion that engages with the load sheave at the end, and that transmits the driving force from the handwheel to the load sheave without going through the drive shaft. A hoisting and pulling machine characterized in that it is provided with a driving force switching means for performing the operation. The hoisting and pulling machine according to claim 1, wherein the slide member is fitted to a drive shaft including a power transmission unit and an idling unit, and slides in the axial direction to switch the drive force. 3. The hoisting and rolling device according to claim 2, wherein the sliding position of the slide member is regulated by a regulating member having an end rotatably attached to the drive shaft and the other end fitted to the operation bar. Traction machine. The hoisting and pulling machine according to any one of claims 1 to 3, wherein a cylindrical projecting portion into which one end of the driving force switching means is fitted is provided on the brake side of the load sheave. The hoisting and pulling machine according to any one of claims 1 to 4, wherein the brake hook is brought into contact with an end portion of the brake side frame to restrict movement in the axial direction.

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