Lever hoist

Abstract

To provide a lever hoist that allows for manipulation of an operating lever even if a power transmission mechanism is provided to transmit drive power from external drive means.SOLUTION: A lever hoist comprises an operating lever 50 that is manually rotated, a load sheave 33 that is rotated by the power from the operating lever 50, a pair of frames 31 and 32 that rotatably support the load sheave 33, a drive shaft 35 that transmits the driving force from the operating lever 50 to the load sheave 33, and a quick-turning grip 70 to be used to fast-forward a chain C1 that is passed around the load sheave 33 and also to quickly rotate the load sheave 33 located at one end of the drive shaft 35. Also included is a power transmission mechanism 100 comprising a sliding joint 170 and a shaft joint 180 that are connected to the other end of the drive shaft 35, and a deceleration mechanism that outputs the driving force from an external electric driver 300 in a decelerated state to the sliding joint 170 and the shaft joint 180.SELECTED DRAWING: Figure 6

Description

Technical Field

[0001] The present invention relates to a lever hoist.

Background Art

[0002] Lever hoists are widely used for operations such as lifting and pulling loads, and fixing (securing) loads with chains, belts, etc. By operating the operating lever by hand, such a lever hoist can wind up and unwind a chain. In recent years, in such a lever hoist, for example, there is one that enables operation of the lever hoist by using the driving force of an electric driver so that even a relatively weak operator can easily perform load lifting and securing operations. As an example related to such a lever hoist, there is one shown in Patent Document 1.

[0003] In Patent Document 1, a separate power transmission device (100) for a lever hoist is attached to the lever hoist (10). This power transmission device (100) for a lever hoist includes an input shaft (140) to which the driving force from an electric driver (300) is input, and the driving force transmitted to the input shaft (140) is transmitted to an output shaft (180) via a first reduction gear mechanism (150) and a second reduction gear mechanism (170). The output shaft (180) transmits the driving force to a coupling portion (190), and the coupling portion (190) is configured to mesh with a free ratchet (60) and rotate integrally.

Prior Art Documents

Patent Documents

[0004]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0005] Incidentally, the power transmission device (100) for a lever hoist disclosed in Patent Document 1 described above is configured to be connected to the rotating gripper (60). Therefore, when the power transmission device (100) for a lever hoist is attached to the lever hoist (10), there is a problem that the operation lever (40) cannot be operated.

[0006] Also, in order to improve workability, the rotating gripper (60) is pulled in a direction away from the hoist body (30) to switch to the rotating state of the load sheave (33), and the chain (C1) is quickly loosened by hand-pulling or the chain (C1) is quickly wound up to a predetermined position. Generally, this is performed. Here, the rotating state means a state in which drive is not transmitted from the operation lever (40) to the drive shaft for driving the load sheave.

[0007] However, in the configuration disclosed in Patent Document 1, when the power transmission device (100) for a lever hoist is attached to the lever hoist (10) and the coupling portion (190) is connected to the rotating gripper 70, it is difficult to switch to the rotating state. Further, even if the power transmission device (100) for a lever hoist is attached to the lever hoist (10) and switched to the rotating state, when the chain (C1) is hand-pulled, the first reduction gear mechanism (150) and the second reduction gear mechanism (170) are also driven via the drive shaft, the coupling portion (190), etc. Therefore, there is a problem that the hand-pulling force of the chain (C1) becomes heavy.

[0008] The present invention has been made in view of the above circumstances, and an object thereof is to provide a lever hoist capable of operating an operation lever even when a power transmission mechanism for transmitting a driving force from a driving means such as an external electric driver is provided. Further, it is preferable that a lever hoist capable of reducing the hand-pulling force of the chain in the rotating state can be provided even when a power transmission mechanism for transmitting a driving force from an external electric driver is provided.

Means for Solving the Problems

[0009] According to a first aspect of the present invention, in order to solve the above problems, there is provided a lever hoist comprising: an operation lever manually rotated; a load sheave rotated by power from the operation lever; a pair of frames rotatably supporting the load sheave; a drive shaft transmitting a driving force from the operation lever to the load sheave; a quick-pull for quickly feeding a chain wound around the load sheave and quickly rotating the load sheave disposed at one end of the drive shaft. The lever hoist is characterized in that it is provided with a power transmission mechanism including a connecting means connected to the other end of the drive shaft and a speed reduction mechanism for outputting the driving force from an external drive means to the connecting means in a decelerated state.

[0010] In another aspect of the present invention, in the above-described invention, it is preferable that the power transmission mechanism includes a connection-disconnection mechanism for switching between a connected state in which the driving force is transmitted from the speed reduction mechanism to the drive shaft and a non-connected state in which the transmission of the driving force from the speed reduction mechanism to the drive shaft is made impossible.

[0011] In another aspect of the present invention, in the above-described invention, the connection-disconnection mechanism preferably includes a shaft coupling that rotates integrally with the drive shaft and is attached to the drive shaft, and a sliding coupling that transmits the driving force from the speed reduction mechanism and transmits the driving force of the driving means from the speed reduction mechanism in an engaged state with the shaft coupling. The connection-disconnection mechanism can preferably release the engagement between the shaft coupling and the sliding coupling by manual operation.

[0012] In another aspect of the present invention, in the above-described invention, the connection-disconnection mechanism preferably includes a blocking plate that presses the sliding coupling toward the other side in the axial direction of the drive shaft, is disposed in a state where rotation with respect to the drive shaft and the speed reduction mechanism is impossible, and has a cam projection protruding toward the outer peripheral side, and a cam ring disposed on the outer peripheral side of the blocking plate and having a cam groove into which the cam projection enters on the inner peripheral surface. The cam ring releases the engagement between the shaft coupling and the sliding coupling by being relatively rotated with respect to the power transmission mechanism.

[0013] In another aspect of the present invention, in the above-described invention, the connection and disconnection mechanism includes a shaft coupling that rotates integrally with the drive shaft and is attached to the drive shaft, and a sliding coupling that transmits the driving force from the reduction mechanism and engages with the shaft coupling to transmit the driving force of the driving means from the reduction mechanism. The power transmission mechanism transmits the driving force to the shaft coupling when the sliding coupling rotates in the normal rotation direction, which is the specified rotation direction, while when rotating in the reverse rotation direction opposite to the normal rotation direction, it does not transmit the driving force from the sliding coupling to the shaft coupling by releasing the engagement between the sliding coupling and the shaft coupling, and preferably includes a one-way clutch mechanism.

[0014] In another aspect of the present invention, a friction clutch mechanism including a first sliding member and a second sliding member that are relatively slidable is provided between the driving means and the reduction mechanism. When a torque equal to or greater than a predetermined torque is input from the driving means, the friction clutch mechanism blocks the transmission of torque to the reduction mechanism by sliding between the first sliding member and the second sliding member, which is preferable.

Effects of the Invention

[0015] According to the present invention, it is possible to provide a lever hoist capable of operating the operation lever even when a power transmission mechanism for transmitting the driving force from a driving means such as an external electric driver is provided. Also, even when a power transmission mechanism for transmitting the driving force from an external electric driver is provided, it is preferable that a lever hoist capable of reducing the manual pulling force of the chain in the free rotation state can be provided.

Brief Description of the Drawings

[0016]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Figure 8

Figure 9

Figure 10

Figure 11

Figure 12

Mode for Carrying Out the Invention

[0017] Hereinafter, the lever hoist 10 according to an embodiment of the present invention will be described with reference to the drawings.

[0018] <Regarding the lever hoist> In the following description, the X direction is the axial direction of the drive shaft 35 disposed between the gear case 40 and the fast-rotating nipping member 70 (hereinafter referred to as the "idle nipping member"). The X1 side is the side where the idle nipping member 70 is attached, and the X2 side is the opposite gear case 40 side. Further, the Z direction is the vertical direction (suspension direction; hoisting and lowering direction) in the suspended state of the lever hoist 10. The Z1 side is the upper side in the suspended state, and the Z2 side is the lower side in the suspended state.

[0019] FIG. 1 is a front view showing the configuration of the lever hoist 10 according to the present embodiment. FIG. 3 is a rear view showing the configuration of the lever hoist 10. FIG. 3 is a side view showing the configuration of the lever hoist 10. As shown in FIGS. 1 to 3, the lever hoist 10 includes an upper hook 20, a lower hook 25, a hoist body 30, an operation lever 50, a switching knob 60, a freewheel gripper 70, and a power transmission mechanism 100. The upper hook 20 is a portion for hooking on a hooking portion such as a ring-shaped fitting or an annular wire.

[0020] Also, the upper hook 20 is connected to the hoist body 30, and the lower hook 25 is connected to the end side of the chain C1. These upper hook 20 and lower hook 25 are portions for hooking on other members.

[0021] The hoist body 30 has a hollow load sheave 33 around which a chain C1 is wound between a pair of frames 31, 32 connected by four stay bolts B1 and socket nuts N1. This load sheave 33 rotates as the shaft-shaped drive shaft 35 along the axial direction (X direction) rotates. Note that a gear case 40 incorporating a reduction gear is also attached to the hoist body 30, and the gear case 40 is provided on the other side (X2 side) in the axial direction (X direction) than the frame 32. Further, a brake mechanism (not shown) is incorporated in the hoist body 30. Depending on the rotation direction of the load sheave 33 and the drive shaft 35, the chain C1 is wound up or, conversely, the chain C1 is wound down.

[0022] Note that on the other end side (X2 side) in the axial direction (X direction) of the drive shaft 35, there is provided an other end recess 35a into which a cylindrical portion 181 of a shaft joint 180 described later is inserted. Also, the gear case 40 is provided with an insertion hole (not shown). This insertion hole 41 penetrates the gear case 40 along the axis of the drive shaft 35 and enables the shaft joint 180 described later to be inserted.

[0023] Further, the operation lever 50 is a long portion that an operator grips by hand and rotates to wind up or unwind the chain C1. When the chain C1 is being wound up, when the operation lever 50 is rotated, the operation lever 50 and the load sheave 33 described later rotate integrally while a brake mechanism (not shown) remains in a tightened state. On the other hand, when the chain C1 is being wound down, when the operation lever 50 is rotated, the brake mechanism loosens by the amount of operation of the operation lever 50, and the chain C1 is wound down by that loosened amount. However, when the operation of the operation lever 50 is stopped during winding down, the rotation of the load sheave 33 is immediately stopped by the action of the brake mechanism.

[0024] Also, the switching knob 60 is attached to a portion of the operation lever 50 close to the rotating grip 70. Further, as shown in FIG. 1, a pair of engaging protrusions 61 are provided on the upper side (Z1 side) of the switching knob 60. This switching knob 60 is interlocked with a ratchet mechanism built into the rotating grip 70 and inside the hoist body 30. That is, the switching knob 60 rotates integrally with a switching claw that meshes with a switching gear screw-coupled to the drive shaft 35. This switching claw has a form in which a ratchet claw for winding up and a ratchet claw for winding down are integrated.

[0025] For example, when the lower side (Z2 side) of the switching knob 60 is tilted to the left, the ratchet claw for winding up meshes with the switching gear. As a result, when the operation of rotating the operation lever 50 is repeated, the switching gear rotates in the winding-up direction but does not rotate in the winding-down direction. At this time, it corresponds to the wound-up state of the chain C1. In addition, by one of the engaging protrusions 61 engaging with the flange portion 72 of the rotating grip 70, the rotating grip 70 is prevented from being pulled out to one side (X1 side) in the axial direction (X direction). For this reason, a biasing spring (not shown) can maintain a state of pressing the brake mechanism.

[0026] On one hand, for example, when the lower side (Z2 side) of the switching knob 60 is tilted to the right, the ratchet claw for unwinding engages with the switching gear. As a result, when the operation lever 50 is repeatedly rotated, the switching gear rotates in the unwinding direction but not in the winding direction. At this time, it corresponds to the unwound state of the chain C1. In addition, when the other engaging protrusion 61 engages with the flange portion 72 of the rotating nipper 70, the rotating nipper 70 cannot be pulled out to one side (X1 side) in the axial direction (X direction). Therefore, a biasing spring (not shown) can maintain the state of pressing the brake mechanism.

[0027] Also, when the lower side (Z2 side) of the switching knob 60 is positioned at the neutral position, which is a position between the winding direction and the unwinding direction (in this case, the switching knob 60 is positioned along the longitudinal direction of the operation lever 50), neither the ratchet claw for winding nor the ratchet claw for unwinding engages with the switching gear. As a result, even if the operation lever 50 is rotated, neither the winding nor the unwinding operation of the chain C1 is executed, and it is in a free (rotating) state. At this time, neither of the pair of engaging protrusions 61 engages with the flange portion 72 of the rotating nipper 70. Therefore, the rotating nipper 70 can be pulled out to one side (X1 side) in the axial direction (X direction), and the biasing spring (not shown) can loosen the state of pressing the brake mechanism.

[0028] Also, the rotating nipper 70 is a substantially circular handle-shaped portion that can rotate together with the drive shaft 35. The rotating nipper 70 is provided with a gripping portion 71 that repeats concavities and convexities along the circumferential direction, and a flange portion 72 that protrudes to the outer diameter side from the concave portion of the gripping portion 71. When either one of the pair of engaging protrusions 61 described above engages with the flange portion 72, the rotating nipper 70 cannot be pulled out to one side (X1 side) in the axial direction (X direction). Therefore, a biasing spring (not shown) can maintain the state of pressing the brake mechanism.

[0029] Further, when the rotating nipper 70 is being wound up or down, as shown in FIG. 2, it is pushed toward the other side (X2 side) in the axial direction (X direction). However, in the neutral position (neutral state), it can be pulled out toward one side (X1 side) in the axial direction (X direction). When the rotating nipper 70 is pulled out toward one side (X1 side) in the axial direction (X direction), the pressing force of the biasing spring that biases a brake mechanism (not shown) weakens, resulting in a brake release state, and it can be freely pulled out in either the winding-up or winding-down direction while gripping the chain C1 with a hand or the like.

[0030] However, in the above-described neutral position (neutral state), if the state where the rotating nipper 70 is pushed into the other side (X2 side) without being pulled out toward one side (X1 side) in the axial direction (X direction) is maintained, the chain C1 can only be pulled out in the winding-up direction.

[0031] <Regarding the power transmission device for the lever hoist> Next, the power transmission mechanism 100, which is fixed to the above-described lever hoist 10, will be described below. This power transmission mechanism 100 is a device for transmitting the driving force given from an electric driver 300, which is an electric tool, to the drive shaft 35.

[0032] FIG. 4 is a side view showing the configuration of the power transmission mechanism 100 provided in the lever hoist 10. FIG. 5 is a cross-sectional view showing the configuration of the power transmission mechanism 100. FIG. 6 is an exploded perspective view showing the configuration of the power transmission mechanism 100.

[0033] As shown in FIGS. 4 to 6, the power transmission mechanism 100 is provided on the side of the gear case 40 (X2 side) rather than on the side of the rotating nipper 70 (X1 side) in the axial direction (X direction) of the lever hoist 10. A fixed plate 220, which will be described later, of this power transmission mechanism 100 is fixed to the frame 32 together with the gear case 40 by fixing means such as a stay bolt B1 and a socket nut N1.

[0034] The power transmission mechanism 100 includes an input section 110, a friction clutch mechanism 120, a first reduction gear mechanism 130, a second reduction gear mechanism 150, a one-way clutch mechanism W1, and a connection / disconnection mechanism D1.

[0035] The input section 110 includes an input shaft 111 and a shaft holder 112. The input shaft 111 is a shaft-shaped member to which the driving force of the electric driver 300 is transmitted. Specifically, the input shaft 111 has a fitting recess 111a and a fixed plate portion 111b (see FIG. 7). The fitting recess 111a is a recess having a shape corresponding to the shape of the tip of a tool, and is a portion into which the tip of the tool is inserted in a state where rotation is prevented. For example, when the tool attached to the electric driver 300 is a hexagon wrench, the fitting recess 111a is a hexagon hole corresponding to the hexagon wrench. The fixed plate portion 111b is a plate-shaped portion fixed to a cylindrical support member 122 described later, for example, via a screw or the like. By fixing the fixed plate portion 111b to the cylindrical support member 122, the driving force from the electric driver 300 can be transmitted to the friction clutch mechanism 120 side.

[0036] Also, the shaft holder 112 is a plate-shaped member that holds the input shaft 111. The shaft holder 112 holds the input shaft 111 so that the shaft holder 112 does not come off on the other side (X2 side) in the axial direction (X direction).

[0037] The friction clutch mechanism 120 is a mechanism that blocks the transmission of torque when a torque greater than a predetermined torque larger than the rated value is applied from the electric driver 300. The friction clutch mechanism 120 has, for example, a configuration as shown in FIG. 7. FIG. 7 is a cross-sectional view showing the configuration of the friction clutch mechanism 120. The friction clutch mechanism 120 includes a support spacer 121, a cylindrical support member 122, a pressing screw member 123, a disc spring 124, and a friction wheel 125.

[0038] The support spacer 121 is a spacer provided in a ring shape. This support spacer 121 is locked to the inner cylindrical step portion 112a of the shaft holder 112 and is also locked to the outer peripheral step portion 122a of the cylindrical support member 122. Thereby, the support spacer 121 is in a state of being sandwiched between the shaft holder 112 and the cylindrical support member 122, and positioning can be performed on the other side (X2 side) in the axial direction (X direction) of the cylindrical support member 122 through this support spacer 121.

[0039] Further, the cylindrical support member 122 is a member that rotates integrally with the input shaft 111 by being fixed to the input shaft 111 described above, for example, by a screw or the like. This cylindrical support member 122 is a cylindrical member fitted into the inner hole of the support spacer 121, and is provided with an outer peripheral step portion 122a on the outer peripheral side thereof to which the support spacer 121 is locked. Further, a pressing screw member 123, a disc spring 124, and a friction wheel 125 are arranged in the inner cylindrical portion 122b of the cylindrical support member 122, and a female screw portion 122c that meshes with the male screw portion 123a of the pressing screw member 123 is formed in the inner cylindrical portion 122b.

[0040] Furthermore, an inner peripheral step portion 122d that protrudes in a flange shape on the inner diameter side is provided on one side (X1 side) of the inner cylindrical portion 122b, and the friction wheel 125 is locked to the inner peripheral step portion 122d. Thereby, the movement of the pressing screw member 123, the disc spring 124, and the friction wheel 125 in one direction (X1 side) in the axial direction (X direction) is restricted.

[0041] Also, the pressing screw member 123 is provided with a male screw portion 123a that meshes with the female screw portion 122c on the outer peripheral surface thereof. Therefore, when the input shaft 111 and the cylindrical support member 122 rotate in the winding-up direction, the male screw portion 123a can be screwed into the female screw portion 122c toward one side (X1 side) in the axial direction (X direction). Further, a friction surface 123b is provided on one side (X1 side) in the axial direction (X direction) of the pressing screw member 123, and the friction surface 123b is a portion that generates a frictional force while exerting a biasing force with the disc spring 124.

[0042] Also, the disc spring 124 is disposed between the pressing screw member 123 and the friction wheel 125 in the inner cylinder portion 122b, and by being sandwiched between them, it applies a biasing force to both of them.

[0043] Further, one side (X1 side) in the axial direction (X direction) of the friction wheel 125 is received by the inner peripheral stepped portion 122d, and the other side (X2 side) in the axial direction (X direction) is a member that receives the disc spring 124. This friction wheel 125 is provided in a cylindrical shape, and a gear portion 125b that meshes with an input shaft 131a, which will be described later, is provided in its inner cylinder portion. Also, a friction surface 125c is provided on the other side (X2 side) in the axial direction (X direction) of the friction wheel 125, and the friction surface 125c is a portion that generates a frictional force while applying a biasing force to the disc spring 124.

[0044] Note that the pressing screw member 123 and the friction wheel 125 correspond to the first sliding member, and the disc spring 124 corresponds to the second sliding member. However, it is also possible that the disc spring 124 corresponds to the first sliding member, and the pressing screw member 123 and the friction wheel 125 correspond to the second sliding member.

[0045] In the friction clutch mechanism 120 configured as described above, when a torque smaller than the rated value in the winding-up direction acts from the electric driver 300, the input shaft 111 and the cylindrical support member 122 rotate integrally. However, the friction surface 123b of the pressing screw member 123 is biased by the disc spring 124. When a driving force in the winding-up direction is applied from the electric driver 300, the male screw portion 123a is restricted from being screwed into the female screw portion 122c toward one side (X1 side) in the axial direction (X direction) by the above-described biasing force, and the torque is transmitted to the friction wheel 125 by the action of the frictional force between the friction surface 123b and the disc spring 124 and the frictional force between the disc spring 124 and the friction surface 125c. Then, the torque is transmitted to the first reduction gear mechanism 130 by the meshing between the gear portion 125b of the friction wheel 125 and the input shaft 131a of the input-side carrier 131 of the first reduction gear mechanism 130.

[0046] Further, in the above-described friction clutch mechanism 120, when a torque exceeding the rated value acts, the male screw portion 123a is screwed into the female screw portion 122c by a predetermined amount so as to move toward one side (X1 side) in the axial direction (X direction). However, when it is screwed in by a predetermined amount or more, slipping occurs between the friction surface 123b and the disc spring 124, and / or between the disc spring 124 and the friction surface 125c, and a state is reached where a torque exceeding the rated value is not transmitted. As a result, an overload exceeding the rated value is prevented from being transmitted to the friction wheel 125 and the first reduction gear mechanism 130 side.

[0047] Also, in the present embodiment, the first reduction gear mechanism 130 is a planetary gear mechanism including an input-side carrier 131 (see FIG. 7), a sun gear (not shown), a planetary gear (not shown), and an internal gear formed on the inner peripheral surface of a ring-shaped member (not shown). An input shaft 131a that meshes with the gear portion 125b of the friction wheel 125 is provided on the input-side carrier 131.

[0048] For example, when a driving force is applied from the electric driver 300 to the sun gear while the ring-shaped member is in a non-rotating state, the planetary gear rotates around the sun gear while revolving around the sun gear and the internal gear due to the meshing therewith. At this time, a large reduction ratio is obtained.

[0049] Further, an output-side carrier (not shown) that supports the planetary gear has a meshing portion in which a gear portion is formed on the inner peripheral surface of a concave portion similar to the above-described meshing portion 121a. The gear portion 141 of the output shaft 140 meshes with the meshing portion. The output shaft 140 is integrally provided with a sun gear (not shown) that constitutes the second reduction gear mechanism 150.

[0050] In addition, in the present embodiment, the second reduction gear mechanism 150 has the same configuration as the above-described first reduction gear mechanism 130. Specifically, the second reduction gear mechanism 150 is a planetary gear mechanism including an input-side carrier, a sun gear, a planetary gear (not shown), an internal gear formed on the inner peripheral surface of a ring-shaped member (not shown), and the like. For example, when the driving force from the output-side carrier of the first reduction gear mechanism 130 is transmitted to the output shaft 140 in a state where the ring-shaped member does not rotate, the sun gear of the second reduction gear mechanism 150 rotates. Then, although the planetary gear of the second reduction gear mechanism 150 rotates around the sun gear while rotating by meshing with the sun gear and the internal gear, a large reduction ratio is obtained in this case.

[0051] In addition, the output-side carrier of the second reduction gear mechanism 150 has an engagement portion in which a gear portion is formed on the inner peripheral surface of a concave portion similar to the above-described engagement portion 121a, and the gear portion 161 of the output shaft 160 meshes with the engagement portion.

[0052] In addition, the output shaft 160 has a gear portion 161 that meshes with the above-described engagement portion and a cylindrical portion 162 that is provided in a cylindrical shape. A plurality (for example, two at 180-degree intervals) of slits 163 that are cut out so as to have a predetermined length along the axial direction (X direction) are provided in the cylindrical portion 162. The outer peripheral protrusion 172 of the sliding joint 170 is inserted into the slit 163 in a state where it can slide in the axial direction (X direction).

[0053] Also, the sliding joint 170 is a component of the one-way clutch mechanism W1 as shown in FIG. 8. FIG. 8 is a cross-sectional view showing a schematic configuration of the one-way clutch mechanism W1. This one-way clutch mechanism W1 includes the above-described sliding joint 170, a shaft joint 180, and a biasing spring 190. Further, the sliding joint 170 is also a component of the connection / disconnection mechanism D1 as shown in FIGS. 9 and 10. FIG. 9 is a cross-sectional view showing a schematic configuration of the connection / disconnection mechanism D1, and shows a state where the sliding joint 170 and the shaft joint 180 are connected. Also, FIG. 10 is a cross-sectional view showing a schematic configuration of the connection / disconnection mechanism D1, and shows a state where the sliding joint 170 and the shaft joint 180 are disconnected. This connection / disconnection mechanism D1 has the above-described sliding joint 170, a shaft joint 180, a biasing spring 190, a blocking plate 200, and a cam ring 210.

[0054] The sliding joint 170 has a cylindrical tubular portion 171, and an outer peripheral protrusion 172 that protrudes from the tubular portion 171 to the outer diameter side is provided on the outer peripheral side of the tubular portion 171. The outer peripheral protrusion 172 is a portion that is inserted into the above-described slit 163 and slides in the slit 163. FIG. 11 is a perspective view showing the configuration of the sliding joint 170. In the configuration shown in FIG. 11, a pair of outer peripheral protrusions 172 are provided, but three or more outer peripheral protrusions 172 may be provided. Although the outer peripheral protrusion 172 is inserted into the slit 163, it is provided so that the outer peripheral protrusion 172 does not come off from the slit 163 during assembly. Therefore, although the sliding joint 170 rotates integrally with the output shaft 160, due to the sliding of the sliding joint 170 in the axial direction (X direction), the outer peripheral protrusion 172 of the sliding joint 170 moves in the axial direction within the slit 163 of the output shaft 160.

[0055] Note that a gap S1 for positioning a blocking plate 200, which will be described later, is provided between the outer peripheral protrusion 172 and the input pressing plate portion 173.

[0056] Further, the sliding joint 170 is provided with a disc-shaped input pressing plate portion 173. The input pressing plate portion 173 is provided coaxially with the cylindrical portion 171 and is a portion facing the output pressing plate portion 182 of the shaft joint 180 described later. An engaging convex portion 174 is provided on the outer peripheral side of the input pressing plate portion 173. The engaging convex portion 174 is a portion protruding from the surface (contact surface) of the input pressing plate portion 173 rather than the inner peripheral side of the engaging convex portion 174.

[0057] On one end side in the circumferential direction of the engaging convex portion 174, a tapered convex wall portion 174a is provided, and on the other end side in the circumferential direction of the engaging convex portion 174, a rising wall portion 174b is provided. The tapered convex wall portion 174a is a wall surface slightly inclined with respect to the axial direction (X direction) and is a wall surface that contacts the tapered concave wall portion 183a described later. Further, the rising wall portion 174b is a wall surface provided along the axial direction (X direction) and is a wall surface that collides with the regulating wall portion 183b described later.

[0058] Note that the sliding joint 170 is also provided with an insertion hole (reference numeral omitted) along the axial direction (X direction). The pin shaft 184 of the shaft joint 180 is inserted into the insertion hole. Therefore, the sliding joint 170 can move in the axial direction (X direction) with respect to the shaft joint 180, but its movement in directions other than the axial direction (X direction) is restricted.

[0059] FIG. 12 is a perspective view showing the configuration of the shaft joint 180. The shaft joint 180 includes a cylindrical portion 181, and this cylindrical portion 181 is inserted into the other end recess 35a of the drive shaft 35 described above. A key groove 181a is provided in the cylindrical portion 181. On the other hand, a key inserted into the key groove 181a is provided in the other end recess 35a of the drive shaft 35. By the fitting of these keys and the key groove 181a, the shaft joint 180 rotates integrally with the drive shaft 35.

[0060] In addition, the shaft joint 180 is provided with an output pressing plate portion 182 that is integral with the above-described cylindrical portion 181. The output pressing plate portion 182 is provided coaxially with the cylindrical portion 181 and is a portion that faces the above-described input pressing plate portion 173. An engaging concave portion 183 is provided on the outer peripheral side of the output pressing plate portion 182. This engaging concave portion 183 is a portion that is recessed from the surface (contact surface) of the output pressing plate portion 182 rather than the inner peripheral side of the output pressing plate portion 182.

[0061] A tapered concave wall portion 183a is provided on one end side in the circumferential direction of the engaging concave portion 183, and a regulating wall portion 183b is provided on the other end side in the circumferential direction of the engaging concave portion 183. The tapered concave wall portion 183a is a wall surface that is slightly inclined with respect to the axial direction (X direction) and is a wall surface that contacts the above-described tapered convex wall portion 174a. The inclination angle of this tapered concave wall portion 183a is approximately the same as that of the above-described tapered convex wall portion 174a. The regulating wall portion 183b is a wall surface provided along the axial direction (X direction) and is a wall surface that collides with the above-described rising wall portion 174b.

[0062] Therefore, normally, the engaging convex portion 174 is fitted into the engaging concave portion 183. However, when a rotational torque in the reverse direction (opposite to the predetermined rotational direction) acts from the electric driver 300, the tapered convex wall portion 174a moves along the tapered concave wall portion 183a while resisting the biasing force of the biasing spring 190, so that the sliding joint 170 moves to the other side (X2 side) in the axial direction (X direction). Thereby, it is possible to release the rotational torque in the reverse direction from the electric driver 300.

[0063] On the other hand, normally, when a rotational torque in the predetermined rotational direction (forward rotation direction) acts from the electric driver 300 with the engaging convex portion 174 fitted into the engaging concave portion 183, the rotational torque is transmitted from the sliding joint 170 to the shaft joint 180 due to the collision between the rising wall portion 174b and the regulating wall portion 183b. Thereby, the chain C1 can be wound up via the power transmission mechanism 100 by the rotational torque in the forward rotation direction applied from the electric driver 300.

[0064] Note that a pin shaft 184 is also provided on the shaft coupling 180. The pin shaft 184 is a shaft-shaped portion inserted into an insertion hole (not shown) of the sliding coupling 170, and by this insertion, it prevents the sliding coupling 170 and the shaft coupling 180 from shifting in the axial direction (X direction).

[0065] In addition, the biasing spring 190 is inserted into the inner cylinder portion (reference numeral omitted) of the cylindrical portion 171 of the sliding coupling 170 and protrudes from the inner cylinder to the other side (X2 side) in the axial direction (X direction). The biasing spring 190 is, for example, a compression spring, and the other side (X2 side) thereof is inserted into the inner cylinder portion (reference numeral omitted) of the output shaft 160 in a compressed state. Therefore, due to the biasing force of the biasing spring 190, the engaged convex portion 174 is maintained in a state of being fitted into the engaged concave portion 183, and when a rotational torque in the forward rotation direction acts from the electric driver 300, a collision state between the rising wall portion 174b and the regulating wall portion 183b is realized.

[0066] In addition, the blocking plate 200 constituting the connection disconnecting mechanism D1 is a ring-shaped plate having a ring hole 201 at the center in the radial direction. This blocking plate 200 is normally located in the gap S1 between the outer peripheral protrusion 172 and the input pressing plate portion 173. Moreover, the radius of the ring hole 201 is provided to be larger than the radius of the cylindrical portion 171 at the portion where the gap S1 is located. However, the radius of the ring hole 201 is provided to be smaller than the distance from the center in the radial direction of the cylindrical portion 171 to the tip of the outer peripheral protrusion 172. Therefore, in a normal state, when the blocking plate 200 moves to the other side (X2 side) in the axial direction (X direction), the sliding coupling 170 is pushed into the other side (X2 side) in the axial direction (X direction) by the blocking plate 200 while resisting the biasing force of the biasing spring 190.

[0067] In addition, from the outer peripheral side of the blocking plate 200, cam protrusions 202 protrude toward the outer diameter side. The cam protrusions 202 are convex portions that enter the cam grooves 211 of a cam ring 210 described later. These cam protrusions 202 protrude from the outer periphery thereof a plurality of times (for example, two at 180-degree intervals) in the circumferential direction of the blocking plate 200.

[0068] Note that the rotation of the blocking plate 200 is prevented relative to the lever hoist 10 and other parts of the power transmission mechanism 100. To prevent such rotation of the blocking plate 200, for example, appropriate holes are provided in the blocking plate 200, and convex portions (not shown) are inserted into the holes from, for example, the side of the second reduction gear mechanism 150 or the fixed plate 220 side.

[0069] In addition, the cam ring 210 constituting the connection disengagement mechanism D1 is a ring-shaped member that can be rotated from the outside in the power transmission mechanism 100, and is located on the outer peripheral side of the blocking plate 200. A cam groove 211 into which the above-mentioned cam projection 202 enters is provided on the inner peripheral surface of this cam ring 210. As shown in FIG. 5, the cam groove 211 is provided so as to be inclined with respect to the axial direction (X direction). Therefore, when an operator relatively rotates the cam ring 210 with a finger with respect to the lever hoist 10 and other parts of the power transmission mechanism 100, the blocking plate 200 moves in the axial direction (X direction).

[0070] Due to the rotation of such a cam ring 210, the fitting between the engaging convex portion 174 of the sliding joint 170 and the engaging concave portion 183 of the shaft joint 180 is released. For this reason, for example, when pulling the chain C1 by hand, it is possible to prevent the rotation from being transmitted from the drive shaft 35 to the second reduction gear mechanism 150 and the first reduction gear mechanism 130 side. Thereby, when pulling the chain C1 by hand, it is not necessary to rotate the second reduction gear mechanism 150 and the first reduction gear mechanism 130 together with the drive shaft 35, so that the pulling force of the chain C1 can be reduced.

[0071] In addition, grip projections 212 are provided on the outer peripheral side of the cam ring 210. The grip projections 212 are protruding portions that protrude to the outer diameter side more than other parts of the power transmission mechanism 100 in order for an operator to easily rotate the cam ring 210 with a finger.

[0072] Note that a spacer SP1 is disposed between the cam ring 210 and the second reduction gear mechanism 150. An annular flange portion SP1a projects toward the inner diameter side on the inner peripheral side of the spacer SP1, and the other end side (X2 side) in the axial direction (X direction) of the split spacer SP2 is attached to the flange portion SP1a. The split spacer SP2 is a curved plate-like member that forms an arc shape in plan view, and is provided, for example, in a predetermined number (three in FIG. 6) in the circumferential direction. One end side (X1 side) in the axial direction (X direction) of the split spacer SP2 is attached to the fixed plate 220. The presence of these spacers SP1 and split spacers SP2 secures a space for arranging the connection disconnecting mechanism D1 and the output shaft 160.

[0073] Further, in order to hold the rotational position of the cam ring 210, a rotational position holding member may be provided. As such a rotational position holding member, for example, a plunger having a pin projecting from its tip may be provided, and a recess (for example, a recess forming a circular shape in plan view) into which the pin of the plunger can enter may be provided at a portion of the spacer SP1 or the fixed plate 220 facing the plunger.

[0074] The fixed plate 220 is a member fixed to the above-described frame 32 via fixing means such as stay bolts and nuts, for example. Further, other members of the power transmission mechanism 100 are fixed to the fixed plate 220, and the entire power transmission mechanism 100 is supported.

[0075] <Regarding the operation> In the power transmission mechanism 100 configured as described above, the driving force from the electric driver 300 is transmitted to the input shaft 111, and further transmitted to the friction clutch mechanism 120, and then transmitted to the first reduction gear mechanism 130. Here, when a torque equal to or greater than a predetermined torque larger than the rated value is input from the electric driver 300, the male screw portion 123a is screwed into the female screw portion 122c by a predetermined amount or more against the biasing force of the disc spring 124, and then slippage occurs between the friction surface 123b and the disc spring 124, and / or between the disc spring 124 and the friction surface 125c. Therefore, transmission of an overload from the friction clutch mechanism 120 to the output shaft 140 is prevented.

[0076] The driving force transmitted to the first reduction gear mechanism 130 is decelerated at a predetermined reduction ratio and then transmitted from the output shaft 140 to the second reduction gear mechanism 150. Also in this second reduction gear mechanism 150, it is decelerated at a predetermined reduction ratio, and then transmitted from the output shaft 160 to the sliding joint 170.

[0077] Here, when a driving force in the forward rotation direction is applied from the electric driver 300, due to the collision between the rising wall portion 174b of the sliding joint 170 and the regulating wall portion 183b of the shaft joint 180, the driving force is transmitted from the sliding joint 170 to the shaft joint 180, and it becomes possible to rotate the drive shaft 35. Therefore, the electric driver 300 can be operated to perform the hoisting operation of the lever hoist 10.

[0078] However, when a driving force in the reverse rotation direction is applied from the electric driver 300, the sliding joint 170 slides (rides up) against the biasing force of the biasing spring 190, and the tapered convex wall portion 174a of the sliding joint 170 slides against the tapered concave wall portion 183a of the shaft joint 180, thereby blocking the transmission of the driving force from the sliding joint 170 to the shaft joint 180. Thereby, damage to the lever hoist 10 due to an operation error of the electric driver 300 is prevented.

[0079] Also, when pulling the chain C1 by hand, the cam ring 210 is rotated in a specified direction. Then, the blocking plate 200 moves to the other side (X2 side) in the axial direction (X direction), thereby releasing the fitting between the engaging recess 183 of the shaft joint 180 and the engaging projection 174 of the sliding joint 170. Therefore, even if the drive shaft 35 and the shaft joint 180 rotate when pulling the chain C1 by hand, the rotational force is not transmitted to the sliding joint 170. Therefore, when pulling the chain C1 by hand, it is not necessary to rotate the first reduction gear mechanism 130 and the second reduction gear mechanism 150 having a relatively large reduction ratio, and the force required for pulling the chain C1 can be reduced.

[0080] <Regarding the effect> The lever hoist 10 having the above-described configuration includes an operation lever 50 that is manually rotated, a load sheave 33 that rotates by the power from the operation lever 50, a pair of frames 31 and 32 that rotatably support the load sheave 33, a drive shaft 35 that transmits the driving force from the operation lever 50 to the load sheave 33, a quick-feed claw 70 for quickly feeding the chain C1 wound around the load sheave 33 and quickly rotating the load sheave 33 disposed at one end (X1 side) of the drive shaft 35. Further, the lever hoist 10 includes a sliding joint 170 and a shaft joint 180 (connecting means) connected to the other end (X2 side) of the drive shaft 35, and a power transmission mechanism 100 including a first reduction gear mechanism 130 and a second reduction gear mechanism 150 (reduction mechanism) that output the driving force from an external electric driver 300 (driving means) to the sliding joint 170 and the shaft joint 180 (connecting means) in a decelerated state.

[0081] In the lever hoist 10 configured as described above, since the power transmission mechanism 100 is arranged at the end on the other side (X2 side) in the axial direction (X direction), even if the power transmission mechanism 100 for transmitting the driving force from the external electric driver 300 (driving means) is provided in the lever hoist 10, it is possible to operate the operation lever 50. Therefore, for example, after performing the winding operation of the chain C1 using the electric driver 300 (driving means), it becomes easier to perform operations such as winding the chain C1 while operating the operation lever 50 to check the tension of the chain C1 and the like, and it is possible to improve the work convenience for the operator.

[0082] Further, in the present embodiment, the power transmission mechanism 100 includes a connection / disconnection mechanism D1 that switches between a connected state in which the driving force is transmitted from the first reduction gear mechanism 130 and the second reduction gear mechanism 150 (reduction mechanism) to the drive shaft 35, and a non-connected state in which the transmission of the driving force from the first reduction gear mechanism 130 and the second reduction gear mechanism 150 (reduction mechanism) to the drive shaft 35 is disabled.

[0083] Therefore, by switching to the non-connected state in which the driving force is not transmitted to the drive shaft 35, when pulling the chain C1 by hand, it is not necessary to rotate the second reduction gear mechanism 150 and the first reduction gear mechanism 130 (reduction mechanism) together with the drive shaft 35, so it is possible to reduce the pulling force of the chain C1.

[0084] Further, in the present embodiment, the connection / disconnection mechanism D1 includes a shaft coupling 180 that rotates integrally with the drive shaft 35 and is attached to the drive shaft 35, and a sliding coupling 170 that transmits the driving force from the first reduction gear mechanism 130 and the second reduction gear mechanism 150 (reduction mechanism) and meshes with the shaft coupling 180 to transmit the driving force of the electric driver 300 (driving means) from the first reduction gear mechanism 130 and the second reduction gear mechanism 150 (reduction mechanism). The connection / disconnection mechanism D1 enables the engagement between the shaft coupling 180 and the sliding coupling 170 to be released by manual operation.

[0085] In the lever hoist 10 configured as described above, by using the connection disconnecting mechanism D1 to release the engagement between the shaft coupling 180 and the sliding coupling 170, that is, when pulling the chain C1 with the drive shaft in a free rotation state by operating the free rotation grip, it is not necessary to rotate the second reduction gear mechanism 150 and the first reduction gear mechanism 130 (reduction mechanism) together with the drive shaft 35. Therefore, it is possible to reduce the pulling force of the chain C1.

[0086] Further, in the present embodiment, the connection disconnecting mechanism D1 presses the sliding coupling 170 toward the other side in the axial direction (X direction) of the drive shaft 35, and is arranged in a state where rotation with respect to the drive shaft 35, the first reduction gear mechanism 130, and the second reduction gear mechanism 150 (reduction mechanism) is impossible. It includes a blocking plate 200 having a cam projection 202 protruding toward the outer peripheral side, and a cam ring 210 disposed on the outer peripheral side of the blocking plate 200 and having a cam groove 211 into which the cam projection 202 enters on the inner peripheral surface. Then, the cam ring 210 is relatively rotated with respect to the power transmission mechanism 100 to release the engagement between the shaft coupling 180 and the sliding coupling 170.

[0087] With such a configuration, the operator can release the engagement between the shaft coupling 180 and the sliding coupling 170 only by rotating the cam ring 210 from the outside. Therefore, when pulling the chain C1, it is possible to easily reduce the pulling force of the chain C1.

[0088] Further, in the present embodiment, the connection disconnecting mechanism D1 includes a shaft coupling 180 that rotates integrally with the drive shaft 35 and is attached to the drive shaft 35, and a drive force from the first reduction gear mechanism 130 and the second reduction gear mechanism 150 (reduction mechanism) is transmitted, and the drive force of the electric driver 300 (driving means) from the first reduction gear mechanism 130 and the second reduction gear mechanism 150 (reduction mechanism) is transmitted in an engaged state with the shaft coupling 180. And a sliding coupling 170. In addition, when the sliding joint 170 rotates in the forward rotation direction, which is the specified rotation direction, the power transmission mechanism 100 transmits the driving force to the shaft joint 180. On the other hand, when it rotates in the reverse rotation direction, which is opposite to the forward rotation direction, the one-way clutch mechanism W1 is provided to cut off the transmission of the driving force from the sliding joint 170 to the shaft joint 180 by releasing the engagement between the sliding joint 170 and the shaft joint 180.

[0089] In this way, by providing the one-way clutch mechanism W1, when a driving force in the reverse rotation direction is applied from the electric driver 300 (driving means), the transmission of the driving force from the sliding joint 170 to the shaft joint 180 is blocked. Thereby, it is possible to prevent damage to the lever hoist 10 due to an operation error of the electric driver 300.

[0090] Further, in the present embodiment, between the electric driver 300 (driving means) and the first reduction gear mechanism 130 and the second reduction gear mechanism 150 (reduction mechanism), there are provided a pressing screw member 123 (first sliding member) and a disc spring 124 (second sliding member) that are relatively slidable, and a friction wheel 125 (first sliding member) and a disc spring 124 (second sliding member) that are relatively slidable. A friction clutch mechanism is provided. When a torque greater than a predetermined torque greater than the rated value is input from the electric driver 300 (driving means), the friction clutch mechanism 120 causes slippage between the pressing screw member 123 (first sliding member) and the disc spring 124 (second sliding member), and / or between the friction wheel 125 (first sliding member) and the disc spring 124 (second sliding member), thereby blocking the transmission of torque to the first reduction gear mechanism 130 and the second reduction gear mechanism 150 (reduction mechanism).

[0091] In this way, by providing the one-way clutch mechanism W1, even if a torque greater than a predetermined torque larger than the rated torque is input from the driving means (electric driver 300), slipping occurs between the pressing screw member 123 (first sliding member) and the disc spring 124 (second sliding member), and / or between the friction wheel 125 (first sliding member) and the disc spring 124 (second sliding member). Therefore, transmission of an overload (torque) from the friction clutch mechanism 120 to the output shaft 140 is prevented, so that breakage of the lever hoist 10 can be prevented.

[0092] <Modification example> As described above, each embodiment of the present invention has been described, but the present invention can be variously modified in addition to this. This will be described below.

[0093] In the above-described embodiment, two reduction gear mechanisms, i.e., the first reduction gear mechanism 130 and the second reduction gear mechanism 150, are provided. However, only one reduction gear mechanism may be present, or three or more reduction gear mechanisms may be present.

Explanation of reference numerals

[0094] 10…Lever hoist, 20…Upper hook, 25…Lower hook, 30…Hoist body, 31, 32…Frames, 33…Load sheave, 35…Drive shaft, 40…Gear case, 41…Insertion hole, 50…Operating lever, 60…Switch knob, 61…Engaging projection, 70…Rotating gripper, 71…Grip portion, 72…Flange portion, 100…Power transmission mechanism, 110…Input portion, 111…Input shaft, 111a…Fitting recess, 111b…Fixed plate portion, 112…Shaft holder, 120…Friction clutch mechanism, 121…Support spacer, 121a…Meshing portion, 122…Cylindrical support member, 122a…Outer peripheral step portion, 122b…Inner cylinder portion, 122c…Female screw portion, 122d…Inner peripheral step portion, 123…Pressing screw member (corresponding to the first sliding member), 123a…Male screw portion, 123b…Friction surface, 124…Dish spring, 125…Friction wheel, 125b…Gear portion, 125c…Friction surface, 130…First reduction gear mechanism (corresponding to a part of the reduction mechanism), 131…Input side carrier, 131a…Input shaft, 140…Output shaft, 141…Gear portion, 150…Second reduction gear mechanism (corresponding to a part of the reduction mechanism), 160…Output shaft, 161…Gear portion, 162…Cylindrical portion, 163…Slit, 170…Sliding joint (corresponding to a part of the connecting means), 171…Cylindrical portion, 172…Outer peripheral projection, 173…Input pressing plate portion, 174…Engaging convex portion, 174a…Tapered convex wall portion, 174b…Rising wall portion, 180…Shaft joint (corresponding to a part of the connecting means), 181…Cylindrical portion, 181a…Key groove, 182…Output pressing plate portion, 183…Engaging recess, 183a…Tapered concave wall portion, 183b…Regulating wall portion, 184…Pin shaft, 190…Biasing spring, 200…Blocking plate, 201…Ring hole, 202…Cam projection, 210…Cam ring, 211…Cam groove, 212…Protrusion for grip, 220…Fixed plate, 300…Electric driver (corresponding to the driving means), B1…Stay bolt (corresponding to a part of the connecting means), C1…Chain, D1…Connecting separation mechanism, N1…Cap nut, S1…Gap, SP1…Spacer, SP1a…Flange portion, SP2…Split spacer, W1…One-way clutch mechanism

Claims

1. An operation lever that is manually rotated, A load sheave that rotates by the power from the operation lever, A pair of frames that rotatably support the load sheave, A drive shaft that transmits the driving force from the operation lever to the load sheave, A lever hoist comprising a quick-feed for quickly feeding a chain wound around the load sheave and a quick-rotation pinch for quickly rotating the load sheave disposed at one end of the drive shaft, A power transmission mechanism is provided that includes a connecting means connected to the other end of the drive shaft and a speed reduction mechanism that outputs the driving force from an external driving means to the connecting means in a decelerated state. A lever hoist characterized by the above.

2. The lever hoist according to Claim 1, The power transmission mechanism, A connection / disconnection mechanism is provided that switches between a connected state in which the driving force is transmitted from the speed reduction mechanism to the drive shaft and a non-connected state in which the transmission of the driving force from the speed reduction mechanism to the drive shaft is disabled. A lever hoist characterized by the above.

3. The lever hoist according to Claim 2, The connection / disconnection mechanism, A shaft coupling that rotates integrally with the drive shaft and is attached to the drive shaft, A sliding coupling that transmits the driving force from the speed reduction mechanism and meshes with the shaft coupling to transmit the driving force of the driving means from the speed reduction mechanism, Comprising, the connection / disconnection mechanism, The meshing between the shaft coupling and the sliding coupling can be released by manual operation. A lever hoist characterized by the above.

4. The lever hoist according to Claim 3, The connection / disconnection mechanism, A blocking plate that presses the sliding coupling toward the other side in the axial direction of the drive shaft, is arranged in a state where rotation with respect to the drive shaft and the speed reduction mechanism is impossible, and has a cam projection protruding toward the outer peripheral side, A cam ring disposed on the outer peripheral side of the blocking plate and having a cam groove into which the cam projection enters on the inner peripheral surface, Comprising, the cam ring is rotated relative to the power transmission mechanism to release the meshing between the shaft coupling and the sliding coupling. A lever hoist characterized by the above.

5. The lever hoist according to Claim 2, The connection / disconnection mechanism, A shaft coupling that rotates integrally with the drive shaft and is attached to the drive shaft, A sliding joint that transmits the driving force from the speed reduction mechanism and meshes with the shaft joint to transmit the driving force of the driving means from the speed reduction mechanism, and is provided with The power transmission mechanism includes a one-way clutch mechanism that transmits the driving force to the shaft joint when the sliding joint rotates in the forward rotation direction, which is the specified rotation direction, and does not transmit the driving force from the sliding joint to the shaft joint by releasing the engagement between the sliding joint and the shaft joint when rotating in the reverse rotation direction, which is opposite to the forward rotation direction. The lever hoist is characterized by this.

6. The lever hoist according to claim 1, A friction clutch mechanism including a first sliding member and a second sliding member that are relatively slidable is provided between the driving means and the speed reduction mechanism. When a torque of a predetermined torque or more is input from the driving means, the friction clutch mechanism blocks the transmission of the torque to the speed reduction mechanism by sliding between the first sliding member and the second sliding member. The lever hoist is characterized by this.

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