JPH05208798A - Hoist tow machine - Google Patents

Abstract

PURPOSE:To reduce the number of parts and to reduce a cost by holding a drive shaft in an idling state and constituting a regulating member, which regulates the slip load of an overload preventing mechanism, by utilizing the parts of an idling mechanism capable of holding idling. CONSTITUTION:A hoisting tow car is formed such that a mechanical brake 9 is mounted around a drive shaft 5 for driving a load sheave 3 and an overload preventing mechanism 15 having friction discs 11 and 12 and a regulating member 14 is located between the mechanical brake and a drive member 10 for the outer periphery of a brake retainer 8. In this case, a stopper 60 is arranged to the end part of the drive shaft 5 and an idling operation handle 40 is axially movably located between the stopper and the brake retainer 8. An idling holding means which comprises an idling holding surface 22 and an engaging protrusion 44 and holds the idling state of the load sheave 3 by suppressing relative rotation between the brake retainer 8 and the drive shaft 5 by bringing the handle 40 into resilient contact with the regulating member 14 through energization of the brake 40 to the brake retainer 8 side is situated between the handle 40 and the regulating member 14.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hoisting traction machine, and more specifically, a mechanical brake mounted around a drive shaft for driving a load sheave, a brake presser of the mechanical brake, and a support on the outer peripheral portion of the brake presser. The present invention relates to a hoisting traction machine having an overload preventing mechanism including a friction plate, an elastic member, and an adjusting member between the driving member and the driving member.

[0002]

2. Description of the Related Art Conventionally, this type of hoisting traction machine is described, for example, in Japanese Utility Model Laid-Open No. 61-80791 and drives a load sheave A via a reduction gear mechanism B as shown in FIG. A mechanical brake H composed of a brake receiver D, a brake presser E, a braking ratchet F and braking plates G, G is mounted around the drive shaft C, and the brake presser E and an outer peripheral portion of the brake presser E are mounted. Drive member I supported on
An overload prevention mechanism M including friction plates J, J, an elastic member K, and an adjusting member L is provided between the friction plate J and the friction plate J. In addition to prohibiting lifting, the adjusting member L
The rated load at which the overload prevention mechanism M starts to operate can be adjusted by adjusting the axial position. Also,
The fourth gear N of the reduction gear mechanism B is moved against the urging force of the spring O by an external operation to cut off the interlocking between the drive shaft C and the load sheave A, so that the load sheave A is free to move. The chain held on the load sheave A can be pulled out freely while being held in the rolled state.

[0003]

However, in such a conventional hoisting and traction machine, the adjusting member L for adjusting the rated load at which the overload preventing mechanism M starts the slipping operation causes the load sheave A to move freely. Only the function of adjusting the slip load of the overload prevention mechanism, which is provided separately from the idling mechanism for holding the rolling state, that is, the mechanism that allows the fourth gear N to move axially to allow idling It is built in as a dedicated part with. For this reason, it is necessary to separately provide the adjusting member for adjusting the slip load of the overload prevention mechanism M with respect to the idling mechanism that holds the idling state of the load sheave A, and the parts cannot be shared. Therefore, there is a problem that not only the number of parts increases, the cost also increases, but also the weight increases.

The present invention has been made in view of the above problems, and an object of the present invention is to prevent overload by operating an overload preventing mechanism, and to drive a drive shaft without requiring skill. Provided is a hoisting traction machine capable of reducing the number of parts by using an adjusting member for adjusting a slip load of an overload preventing mechanism as a part of a free-wheeling mechanism capable of holding a free-wheeling while maintaining the rolling state. Especially.

[0005]

To achieve the above object, the present invention provides a mechanical brake 9 mounted around a drive shaft 5 for driving a load sheave 3 and a brake presser 8 of the mechanical brake 9. The friction plates 11 and 12 are provided between the brake presser 8 and the drive member 10 which is supported on the outer periphery of the brake presser 8.
A hoisting traction machine provided with an overload prevention mechanism 15 including an elastic member 13 and an adjusting member 14, wherein a stopper 60 is provided at the shaft end of the drive shaft 5, and the stopper 60 and the brake presser are provided. 8, an idling operation handle 40, which cannot rotate relative to the drive shaft 5, is interposed so as to be axially movable, and the idling operation handle 40 is urged toward the brake presser 8 side. Between the adjusting member 14 and the operation handle 40, when the operation handle 40 is in the non-idle operation, the relative rotation of the brake presser 8 with respect to the drive shaft 5 at a predetermined angle or more is restricted so that the rotation angle is within a predetermined angle. Rotation restricting means for allowing the brake presser 8 to advance and retract with respect to the brake receiver 7 by relative rotation; and the operation handle 4.
At the time of free rotation operation of 0, the operation handle 40 is elastically brought into contact with the adjusting member 14 by urging the operation handle 40 toward the brake retainer 8 side to suppress the relative rotation of the brake retainer 8 with respect to the drive shaft 5. A free rotation holding means for holding the free rotation state of the load sheave 3 is provided.

Further, the idling holding means includes the idling holding surface 22 and the engaging projections 4 elastically contacting the idling holding surface 22 for idly holding.
4, one of the idle holding surface 22 and the engaging protrusion 44 is provided on one of the facing surfaces of the adjusting member 14 and the idle operating handle 40, and the other is provided on the adjusting member 14 and the idle operating handle 40. It is preferable to provide it on the other side.

The restriction means for restricting the relative rotation of the brake retainer 8 with respect to the drive shaft 5 includes a first restriction surface 21a and a second restriction surface 21b with which the engagement protrusions 44 of the free-wheel holding means are engaged.
The idle holding surface 22 is provided continuously with the second restriction surface 21b, and the surface of the engagement protrusion 44 facing the second restriction surface 21b and the second restriction surface 21b.
It is preferable to provide an inclined guide surface 44a that guides the engaging projection 44 to the free rotation holding surface 22 when the free rotation operation handle 40 rotates in the free rotation operation direction.

Further, between the brake retainer 8 and the drive member 10, the drive member 10 can be freely rotated with respect to the brake retainer 8 when the drive member 10 rotates in the drive rotation direction.
A unidirectional rotation mechanism is provided which enables the drive member 10 to rotate integrally with the brake retainer 8 when rotating in the non-drive rotation direction, and the unidirectional rotation mechanism is provided on the opposing surface of the brake retainer 8 and the drive member 10. And an engaging groove 19 with which the engaging body 86 engages when the drive member 10 rotates in the non-drive rotation direction.
It is preferable that a plurality of the engaging grooves 19 are provided.

[0009]

In the non-idling operation of the idling operation handle 40, the brake presser 8 is screwed into and out of the brake receiver 7 to operate the mechanical brake 9, and the adjusting member 14 is used to adjust the rating. The overload prevention mechanism 15 capable of adjusting the load can also be operated. In addition, when the operation handle 40 is rotated, the operation handle 40
Is relatively rotated with respect to the brake presser 8, the operation handle 40 is elastically contacted with the adjusting member 14, and this elastic contact suppresses relative rotation of the brake presser 8 with respect to the drive shaft 5, and the load sheave. By maintaining the idle state of 3, the load sheave 3 can be easily idle.

Therefore, while the overload prevention mechanism 15 can be operated to prevent overload, the idle operation handle 40 does not require skill to drive the drive shaft 5.
Can be held in an idle state, and the adjusting member 14
A member for adjusting the rated load of the overload prevention mechanism 15,
Since the drive shaft 5 can be shared as a member for holding the drive shaft 5 in an idling state, the number of parts can be reduced accordingly.

It should be noted that, when the drive shaft 5 rotates freely, the protrusion 44 of the operation handle 40 is only in elastic contact with the free rotation holding surface 22 of the adjusting member 14, so that the overload prevention mechanism 15 is not provided. Since the drive shaft 5 can be held in the idling state without changing the rated load for starting the operation, the adjusting member 14 can be used as a common component.

When the idling holding means is composed of the idling holding surface 22 and the engaging protrusions 44, a desired idling holding force can be obtained by elastically contacting the idling holding surface 22 with the protrusions 44. Therefore, it is possible to appropriately control the idle rotation.

In addition, the second restricting surface 2 of the engaging projection 44
By providing the inclined guide surface 44a on one of the facing surface facing 1b and the second restricting surface 21b, it is possible to pull the handle 40 in the axial direction only by rotating the operating handle 40 during idling operation. The operation for moving the adjusting member 14 to a position away from the adjusting member 14 is not necessary, and the idling operation can be improved accordingly.

Further, between the brake retainer 8 and the drive member 10, the drive member 10 can be freely rotated with respect to the brake retainer 8 when the drive member 10 rotates in the drive rotation direction.
A unidirectional rotation mechanism is provided which enables the drive member 10 to rotate integrally with the brake retainer 8 when rotating in the non-drive rotation direction, and the unidirectional rotation mechanism is provided on the opposing surface of the brake retainer 8 and the drive member 10. And an engaging groove 19 with which the engaging body 86 engages when the drive member 10 rotates in the non-drive rotation direction.
When a plurality of engagement grooves 19 are provided, when the drive member 10 is rotated in the non-drive rotation direction, that is, the reverse rotation is performed, the brake presser 8 is reversely rotated to unwind or pull the traction. Since the engaging body 86 can be engaged with the engaging groove 19 with a slight angle of rotation without rotating the member 10 once, lowering and pulling release can be started more quickly.

[0015]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The lever type hoisting and traction machine shown in FIG. 1 has first and second side plates 1 and 2 which are arranged facing each other at a predetermined interval.
In between, a cylinder shaft 4 having a load sheave 3 is rotatably supported, a drive shaft 5 is supported in a central hole of the cylinder shaft 4 so as to be relatively rotatable, and the drive shaft 5 projects toward the second side plate. A reduction gear mechanism 6 including a plurality of reduction gears is interposed between an end portion and the load sheave 3, and the reduction gear mechanism 6 reduces the rotational power of the drive shaft 5 to the load sheave 3 side. I am trying to communicate.

A brake receiver 7 and a brake retainer 8 are screwed onto the first side plate side protrusion of the drive shaft 5, and a brake plate 9 is provided on the outer periphery of the boss of the brake receiver 7.
1, 92 and a braking claw wheel 94 with which the braking claw 93 engages, and these braking plates 91, 92 and the braking claw wheel 94 are supported.
Are interposed between the brake receiver 7 and the brake presser 8, and a mechanical brake 9 is constituted by these members. The brake receiver 7 is restrained from moving in the axial direction by a stop ring 71 provided on the drive shaft 5.

Further, on the outer peripheral portion of the brake presser 8,
A drive member 1 rotated by a swinging operation of a lever 30 described later.
0 via a one-way rotation mechanism, and a pair of friction plates 11 and 12 are provided between the brake presser 8 and the drive member 10.
An overload preventing mechanism 15 including an elastic member 13 and an adjusting member 14 is provided.
Has a large-diameter portion 81 having a pressing side surface facing one braking plate 92, and a medium-diameter portion 82 and a small-diameter portion 83 continuous with the large-diameter portion 81. Is provided with a groove 84 for preventing rotation of the holding plate 16 that receives the pressing force of the elastic member 13 and transmits the pressing force to the entire one friction plate 12, and the small diameter portion 83 has the elastic member The adjusting member 14 for adjusting the pressing force of 13 to adjust the rated load at which the overload preventing mechanism 15 starts to operate is screwed.

The drive member 10 has a vertical portion 10a.
And a cylindrical portion 10b having a tooth portion 32 to be described later,
An annular recessed portion 17 that opens toward the adjustment member 14 is formed at the center in the radial direction, and one of the friction plate 12 and the pressing plate 16 on one side is housed in the recessed portion 17 to provide the elasticity. The pressing force of the member 13 is transmitted to the drive member 10, and is interposed between the large diameter portion 81 of the brake retainer 8 and the vertical portion 10b of the drive member 10 via the drive member 10. The other friction plate 11 can also be pressed so that when the load greater than the rated load is applied to the drive shaft 5, the drive member 10 and the brake retainer 8 can rotate relative to each other by slippage to prevent overload. I am trying to do it. In addition, the inner peripheral surface of the pressing plate 16 is provided with a protruding portion 18 that protrudes inward and is fitted into the recessed groove 84 to enable the pressing plate 16 to move in the axial direction.
Relative rotation with respect to the brake presser 8 is prohibited.

As the one-way rotating mechanism, as shown in FIG. 5, a concave portion 85 is formed on the outer peripheral surface of the medium diameter portion 82 of the brake presser 8, and the engaging body 86 is provided with the spring 8 in the concave portion 85.
7, while holding it so as to always urge it outward in the radial direction, the engaging member 86 can enter the inner peripheral surface of the drive member 10 and has a plurality of engaging grooves 19 extending in a wedge shape in the peripheral direction. (8 places in the drawing), and the drive member 10 is
When it is rotated in the lowering direction shown by the arrow in FIG. 5, the drive member 10 and the brake presser 8 are integrally connected, and a rotational torque larger than the transmission torque of the overload prevention mechanism 15 is required at the time of lowering. And if so, we can deal with it.

The lever 30 is provided at a position corresponding to the radially outer portion of the drive member 10 on the outer side of the brake cover 31 which covers the outer peripheral portion of the mechanical brake 9, and the lever 30 is provided in the drive member 10. The tubular portion 10
It is provided with a claw body 33 having a forward / reverse claw capable of meshing with a tooth part 32 provided on the outer peripheral part of b, and an operating part 34 for engaging and disengaging the claw body 33 with the tooth part 32. , The nail body 3
The drive member 10 can be rotated normally or reversely by switching 3 of the above.

In the lever type hoisting traction machine constructed as described above, a stopper 60 is provided at the shaft end of the drive shaft 5, and the brake is provided between the stopper 60 and the brake presser 8. Protrusion 44 protruding toward the presser foot 8 side
The idle operation handle 40, which is not rotatable relative to the drive shaft 5, is interposed so as to be movable in the axial direction, and the idle operation handle 40 is urged toward the brake presser 8 while the adjustment is performed. When the idling operation handle 40 is not idling operation, the member 14 restricts relative rotation of the brake retainer 8 with respect to the drive shaft 5 at a predetermined angle or more, and the relative rotation within the predetermined angle causes the brake retainer 8 to rotate. A rotation restricting means that allows the brake receiver 7 to be screwed forward and backward, and the tip end surface of the protrusion 44 is urged toward the brake retainer 8 side of the operation handle 40 during the idling operation of the operation handle 40. There is provided an idling holding means for holding the idling state of the load sheave 3 by elastically contacting and suppressing the relative rotation of the brake presser 8 with respect to the drive shaft 5.

That is, a serration portion 51 is formed on the outer side of the brake retainer 8 on the drive shaft 5, and the serration portion 51 has a large diameter portion 62 having an engaging groove 61 on the outer peripheral portion and the serration portion. The stopper 60 having a cylindrical portion 63 that can be connected to the portion 51 is serrated and fixed by fastening the nut 64 to the drive shaft 5.

Further, the boss portion 41 of the operation handle 40 is attached to the tubular portion 63, and the fitting hole 42 formed in the boss portion 41.
By fitting the operating handle 40 with the drive shaft 5
Of the stopper 60 is interposed between the large diameter portion 62 of the stopper 60 and the driving member 10 in a state of being movable in the axial direction and rotatable. The extending ridge 43 is provided, and the ridge 43 is engaged with the engaging groove 61 provided on the outer peripheral portion of the large diameter portion 62 of the stopper 60 as shown in FIG. The operation handle 40 is made unable to rotate relative to the drive shaft 5.

Also, the boss portion 41 of the operation handle 40.
An elastic pressing member 70 composed of a coil spring that comes into contact with each of the side surfaces of the stopper 60 is provided between the outer side surface of the stopper 60 and the inner side surface of the large diameter portion 62 of the stopper 60 facing the boss 41. The protrusion 44 which is biased in the direction of moving away from the stopper 60, that is, the brake presser 8 side, and which is protruded in the biasing direction of the operation handle 40 at the rear end of the boss 41 in the radial direction is symmetrical. The pair is provided in a shape.

Further, the adjusting member 14 is shown in FIGS.
As shown in FIG. 5, a pair of notches 21 are provided at symmetrical positions with a phase shift of 180 degrees, and one side face in the circumferential direction of the notches 21 is a first regulation face 21a, and the other side face is 21b. When the non-idling operation of 40, the projection 44
Is located in the notch 21, and relative rotation of the brake presser 8 with respect to the drive shaft 5 within the range of the first and second restricting surfaces 21a and 21b is allowed. When the lever 30 is swung, the drive member 10 can rotate relative to the operation handle 40, and the brake presser 8 can be screwed forward and backward with respect to the brake receiver 7. -The drive shaft 5 can be rotated following the rotation of the drive member 10 by the operation of the mechanical brake 9 caused by the screwing of the presser foot 8, and the operation of hoisting or lowering the luggage or releasing the towing can be performed. It becomes.

Further, the adjusting member 14 has a free-wheeling structure in which the tip end surface of the protrusion 44 is elastically contacted when the operation handle 40 is operated in the forward rotation direction side shown by the arrow in FIG. The holding surface 22 is provided symmetrically continuously to the second restriction surface 21b so that the holding surface 22 can be brought into the idling state by the operation of the operation handle 40 and the idling state can be held. That is, the drive member 10 is connected to the lever 30.
The operating handle 40 is pulled out to the stopper 60 side and is rotated relative to the driving member 10 in a state where the operating handle 40 is rotationally fixed via the claw 33 of the operating member 40, so that the operating handle 40 moves relative to the driving member 10. The drive shaft 5 rotates integrally with this relative rotation, and the brake retainer 8 screwed to the drive shaft 5 is screwed back from the brake receiver 7. The shaft 5 can be brought into an idling state, and at this time, the tip end surface of the protrusion 44 is biased by the elastic pressing member 70 so that the idling holding surface 22 as shown in FIGS.
The operation handle 40 is contacted by the elastic contact.
Can be restrained from rotating relative to the brake presser 8, and this restraint can maintain the idling state of the load sheave 3.

In FIG. 3, reference numeral 23 indicates that when the operation handle 40 is rotated with respect to the brake retainer 8 and the drive member 10, the operation handle 40 is rotated more than necessary by the contact of the protrusion 44. This is a rotation restricting portion that prevents

Further, as shown in FIG. 5, the driving member 1
By forming the engagement grooves 19 at eight locations or more at equal intervals of 45 degrees on the inner peripheral surface of 0, rotation of the drive member 10 in the non-drive rotation direction by the operation of the lever 30, that is, reverse rotation When the brake presser 8 is rotated in the reverse direction by rotation, the engagement body 86 can be surely engaged with the engagement groove 19 by the rotation within at least 45 degrees, and the lowering and the pulling release can be performed promptly.

Next, the operation of the lever-type hoisting and traction machine constructed as described above will be described.

First, when hoisting or pulling, the claw body 3 is operated by operating the operation portion 34 provided on the operation lever 30.
The brake presser 8 is rotated in the forward rotation direction together with the drive member 10 by engaging the feed claw 3 of FIG. 3 with the tooth portion 32 of the drive member 10 and performing the swinging operation of the lever 30. .. In this case, since the protrusion 44 is located in the cutout portion 21 as shown by the dotted line in FIG. 3, during this forward rotation, the brake presser 8 is screwed toward the brake receiver 7 side, and the mechanical brake 9 is moved. Upon operation, the rotational power of the drive member 10 is transmitted to the drive shaft 5 via the overload prevention mechanism 15 and the mechanical brake 9, and this rotational power is transmitted from the drive shaft 5 to the reduction gear mechanism 6 and the cylinder shaft. It is transmitted to the load sheave 3 side via 4 and can be wound or pulled. In this state, when a load equal to or higher than the rated load adjusted by the adjusting member 14 is applied to the load sheave 3, the overload prevention mechanism 15 slips to regulate winding or towing above the rated value. is there.

When lowering or releasing the tow,
By engaging the reversing claw of the claw body 33 in the operating portion 34 with the tooth portion 32 of the driving member 10 and swinging the lever 30, the brake presser 8 and the driving member 10 rotate in the reverse direction. Also in this case, since the protrusion 44 is located in the cutout portion 21 in this case as well, the brake retainer 8 rotates relative to the drive shaft 5 and moves relative to the brake receiver 7. The drive shaft 5 can be screwed back and rotated, and the drive shaft 5 can be rotated by a predetermined angle following the rotation of the drive member 10 by the operation of the mechanical brake 9. By this rotation, the lowering and the pulling release can be performed.

In this case, the brake retainer 8 is rotated in the reverse direction by the rotation of the drive member 10 in the non-drive rotation direction by the swinging operation of the lever 30, that is, the reverse rotation, as shown in FIG. Since the inner peripheral surface of the drive member 10 is provided with a plurality of engagement grooves 19 with which the engagement bodies 86 engage at equal intervals of 45 degrees, it is not necessary to rotate the drive member 10 at least 45 degrees. The engaging body 86 can be engaged with the engaging groove 19 by the rotation of the angle of, and the lowering and the pulling release can be started more quickly.

Next, a case will be described in which the drive shaft 5 is allowed to freely rotate and the chain is freely extended or shortened toward the load side.

First, when the reversing claw of the claw body 33 is engaged with the tooth portion 32 of the driving member 10, the driving member 10 causes the operating handle 40 to rotate when the operating handle 40 rotates in the forward direction. Do not turn with 40. Then, in this state, the operation handle 40 is pulled out to the stopper 60 side against the elastic pressing member 70, that is, the operation handle 40 is moved in the separating direction with respect to the brake presser 8, and the operation handle 40 is moved. Is operated to rotate in the forward direction. At this time, the drive member 10 in which the reverse rotation claw of the claw body 33 is locked to the tooth portion 32 cannot rotate normally, whereas the drive shaft 5 that rotates together with the operation handle 40 through the stopper 60. Can rotate in the normal rotation direction, that is, in the normal rotation direction with respect to the brake presser 8 and the drive member 10 and beyond the range of the cutout portion 21, and the relative rotation causes the brake presser 8 to move.
In FIG. 1, the brake operation by the mechanical brake 9 can be released by axially moving in a direction away from the brake receiver 7, and the drive shaft 5, and by extension, the load sheave 3 can be put into an idle state. .. When the elastic pressing member 70 is urged, the protruding tip end surface of the protrusion 44 is, as shown in FIGS.
Since the operation handle 40 can be restrained from rotating relative to the brake retainer 8 and the drive member 10 by this elastic contact, the idle state of the load sheave 3 can be maintained. It will be possible. Therefore, in this state, pulling the chain toward the load side allows rapid extension, and pulling toward the unloaded side allows rapid shortening of the load side chain.

During the idling of the load sheave 3, the protrusion 44 makes elastic contact with the idling holding surface 22 and the adjusting member 1
4 is only pressed in the axial direction, the projection 4
The pressing member 4 does not rotate the adjustment member 14 to move it in the axial direction, does not change the rated load at which the overload prevention mechanism 15 starts operating, and further, the free end surface of the protrusion 44 does not move. Even if the rotational torque is transmitted to the adjusting member 14 through the elastic contact portion with the rolling holding surface 22, the rotational resistance of the adjusting member 14 whose axial movement is restricted by the elastic member 13 is equal to the protrusion. Since 44 is larger than the rotation resistance due to elastic contact with the free rotation holding surface 22, the adjusting member 14 is not rotated by the rotation torque transmitted through the elastic contact portion. Therefore, the overload prevention mechanism 1 previously adjusted by the adjusting member 14
The rated load at which 5 starts operating does not change. As a result, the adjusting member 14 can be used as a common component for a member that adjusts the rated load of the overload prevention mechanism 15 and a member that holds the load sheave 3 in an idle state.

Further, since the adjusting member 14 is provided with the rotation restricting portion 23, the brake presser 8 is moved by the drive member 10 with the tip end surface of the protrusion 44 elastically contacting the idle holding surface 22. At the same time, when rotating relative to the drive shaft 5, the rotation of the protrusion 44 against the rotation restricting portion 23 in the rotating direction can be restricted. Therefore, when the operation handle 40 is rotated relative to the brake retainer 8 and the drive member 10 in order to allow the load sheave 3 to rotate freely, the front of the rotation direction of the protrusion 44 contacts the rotation restricting portion 23. Thus, the rotation angle can be limited, and the distance between the brake presser 8 and the brake receiver 7 can be prevented from becoming wider than necessary for the load sheave 3 to rotate freely. As a result, during the idling operation of rotating the operation handle 40 relative to the brake presser 8 and the drive member 10, the idling operation can be performed without rotating the operation handle 40 more than necessary.

Further, as described above, the load sheave 3 is held in an idle state to increase the tensile force of the chain,
When a strong force in the reverse direction is applied to the drive shaft 5,
The elastic contact of the tip end surface of the projection 44 with the free rotation holding surface 22 is released, the projection 44 returns to the notch 21, and the mechanical brake 9 is ready to operate. That is, in the idle state, the load sheave 3
When a strong force in the reverse direction acts on the brake presser 8
Is screwed to the drive shaft 5, and its rotational inertial force is larger than that of the drive shaft 5, so that the operating handle 4
The rotation starts a little after the 0 rotation,
The protrusion 44 slides in the rotational direction with respect to the idle holding surface 22, and as a result, the projecting tip end surface of the protrusion 44 and the idle holding surface 22 are released from elastic contact with each other so that the protrusion 44 is shown by a dotted line in FIG. It returns to the inside of the cutout portion 21 as shown in FIG.

In this case, the operation handle 40 overcomes the relative rotational resistance due to the elastic contact of the tip end surface of the projection 44 with the idle holding surface 22, and the brake presser 8
In addition, the rotation of the drive member 10 in the reverse rotation direction is relatively wide, and the relative rotational resistance due to the elastic contact of the protrusions 44 widens the input range of the chain pulling force during idling, thus improving the skill of idling operation. It can be done without any need.

When the load acting in the reverse direction is applied to the drive shaft 5 from the load sheave 3 by the load acting on the chain, when the idling operation is performed by the operation handle 40, the operation is performed by the load. The handle 40 rotates together with the drive shaft 5 in the reverse rotation direction with respect to the brake retainer 8, and the elastic contact between the tip end surface of the protrusion 44 and the free rotation holding surface 22 is immediately released, so that the mechanical brake 9 can be braked. As a result, the drive shaft 5 cannot be held in the idling state, so that the safety thereof can be improved.

As described above, the idling operation handle 40
In the non-idling operation, the brake presser 8 is screwed and retracted with respect to the brake receiver 7 to operate the mechanical brake 9 to perform the operation of hoisting and lowering the luggage, pulling, and releasing the tow. At this time, the overload prevention mechanism 15 can also be operated, and when the operation handle 40 is idling, the operation handle 40 is relatively rotated with respect to the brake presser 8, and the operation handle 40 is operated. The load sheave 3 can be idled by elastically contacting the protrusion 44 with the idle holding surface 22 to easily hold the idle state of the drive shaft 5.

Therefore, while the overload prevention mechanism 15 can be operated to prevent overload, the idle operation handle 40 does not require any skill to drive the drive shaft 5.
Can be held in an idling state, and further, the adjusting member 14 provided with the notch portion 21 having the first and second regulating surfaces 21a and 21b and the idling holding surface 22 can prevent the overload. Since it can be used not only as a component for adjusting the rated load of the mechanism 15 but also as a component for holding the drive shaft 5 in an idle state, the number of components can be reduced accordingly.

In the above embodiment, the engaging groove 61 is formed.
The operation handle 40 is rotationally fixed to the drive shaft 5 by the engagement between the operation handle 40 and the protrusion 43, but the operation handle 40 is provided with serrations on the outer peripheral surface of the cylindrical portion 63 of the stopper 60. The boss portion 41 may be serrated. Further, although the stopper 60 having the cylindrical portion 63 that can be coupled to the serration portion 51 and the large diameter portion 62 is used, the cylindrical portion 63 may be formed separately from the large diameter portion 62, Further, in this case, the tubular portion 63
Is composed of two short sleeves, and the brake presser 8
A flange may be provided at an end of the sleeve disposed on the side closer to the stopper 60, and the boss portion 41 of the operation handle 40 may be brought into contact with the flange.

Further, as shown in FIG. 5, the engaging body 86 is inserted into the concave portion 85 provided in the medium diameter portion 82 of the brake presser 8.
Is held so as to engage with the engaging groove 19 provided on the inner peripheral surface of the driving member 10, but the engaging body 86 is held on the driving member 10 side, and the medium diameter portion 82 is held. You may make it engage with the engaging groove provided in the outer peripheral surface.

In the embodiment described above, when the idle operation is performed by the operation handle 40, first, the operation handle 4 is moved.
Although 0 was pulled out in the axial direction and then rotated so that the engagement protrusion 44 is elastically contacted with the idling holding surface 22, as shown in FIGS. 6 and 8, as shown in FIGS. By forming an inclined guide surface 44a that guides the free rotation holding surface 22 of the operation handle 40 on the surface facing the second restriction surface 21b, it is possible to pull out the operation handle 40 axially outward. , The engaging projection 44 is moved to a position away from the adjusting member 14 only by rotating.
Is guided to the idle holding surface 22.

Therefore, the operation of pulling the operation handle 40 outward in the axial direction is not necessary, and the operability in the idling operation can be improved accordingly.

In the embodiment described above, the engaging projection 44 is provided on the surface of the operating handle 40 facing the adjusting member 14, and the adjusting member 14 is provided with the first and second restricting surfaces 21a, 21a. 21b is provided, and the second restricting surface 21b is provided on the surface facing the operation handle 40.
The idling holding surface 22 continuous with the engaging projection 3 is provided.
1 may be provided on the adjusting member 14, and the first and second regulating surfaces 21a and 21b and the idling holding surface 22 may be provided on the operation handle 40.

Furthermore, when the inclined guide surface is provided,
The second restricting surface 21b other than that provided on the engaging protrusion 44
It may be provided on both sides or both sides.

[0048]

As described above, in the hoisting and traction machine according to the present invention, the mechanical brake 9 mounted around the drive shaft 5 for driving the load sheave 3, the brake presser 8 of the mechanical brake 9, and the mechanical brake 9 are provided. In the hoisting and traction machine, an overload preventing mechanism 15 provided with friction plates 11 and 12, an elastic member 13 and an adjusting member 14 is provided between a drive member 10 supported on the outer peripheral portion of the brake presser 8 and the drive member 10. A stopper 60 is provided at the shaft end of the shaft 5, and an idling operation handle 40, which cannot rotate relative to the drive shaft 5, is interposed between the stopper 60 and the brake retainer 8 so as to be movable in the axial direction. Then, while the idling operation handle 40 is biased toward the brake presser 8 side, between the adjusting member 14 and the operating handle 40, the non-idle operation of the operating handle 40 causes the brake to move. Rotation restricting means for restricting relative rotation of the presser foot 8 with respect to the drive shaft 5 at a predetermined angle or more, and allowing the brake presser 8 to be screwed into and out of the brake receiver 7 with relative rotation within a predetermined angle; Handle 4
At the time of idling operation of 0, the operation handle 40 is elastically brought into contact with the adjusting member 14 by urging the operation handle 40 toward the brake retainer 8 side, and the drive shaft 5 of the brake retainer 8
Since a relative rotation means for suppressing the relative rotation with respect to the load sheave 3 is provided for holding the idle state of the load sheave 3, the brake presser 8 and the brake receiver 7 are operated when the idle operation handle 40 is not idle. On the other hand, the mechanical brake 9 is actuated by being screwed and unwound to actuate the operation of hoisting and lowering the luggage, towing and releasing the towing, and at the same time operating the overload prevention mechanism 15. Yes, and in addition, during the idling operation of the operation handle 40,
The operation handle 40 is rotated relative to the brake presser 8, and the operation handle 40 is elastically brought into contact with the adjusting member 14 to maintain the idle state of the drive shaft 5 to idle the load sheave 3. You can also let it.

Therefore, while the overload can be prevented by operating the overload prevention mechanism 15, the load sheave 3 can be held in the idle state by the idle operation handle 40 without requiring skill. Moreover, since the adjusting member 14 can be used not only as a component for adjusting the rated load of the overload prevention mechanism 15 but also as a component for holding the load sheave 3 in an idle state, the number of components can be increased accordingly. Can be reduced.

Further, when the idling holding means is constituted by the idling holding surface 22 and the engaging projection 44, the desired idling holding force can be obtained by elastically contacting the projection 44 with the idling holding surface 22. Therefore, it is possible to appropriately control the idle rotation.

In addition, the second restricting surface 2 of the engaging projection 44
By providing the inclined guide surface 44a on one of the facing surface facing 1b and the second restricting surface 21b, it is possible to adjust the handle 40 by pulling the handle 40 in the axial direction only by rotating the handle 40 during idling operation. The operation for moving the member 14 to a position away from the member 14 is not necessary, and the idling operation can be improved accordingly.

Between the brake retainer 8 and the drive member 10, the drive member 10 can be freely rotated with respect to the brake retainer 8 when the drive member 10 rotates in the drive rotation direction.
By providing a one-way rotation mechanism that enables the drive member 10 to rotate integrally with the brake presser 8 when rotating in the non-drive rotation direction, the drive member 10 rotates in the non-drive rotation direction, that is, reverse rotation, When the brake presser 8 is reversely rotated to lower or lower the tow, the engaging member 86 is rotated by a slight angle without rotating the drive member 10 once.
Can be engaged with the engagement groove 19, so that the lowering and the pulling release can be started more quickly.

[Brief description of drawings]

FIG. 1 is a longitudinal side view of a lever-type hoisting and traction machine showing an embodiment of the present invention.

FIG. 2 is a sectional view of an essential part showing a free rotation state.

3 is a cross-sectional view taken along the line AA of FIG.

FIG. 4 is an explanatory view showing the engagement between the idling operation handle and the stopper.

FIG. 5 is an explanatory diagram of a one-way rotation drive mechanism.

FIG. 6 is a view showing the other side of the operation handle in which the engagement protrusion is changed, and is an inner view seen from the surface facing the adjustment member.

FIG. 7 is a front view of only an adjusting member.

8 is an explanatory view showing the action of the engagement protrusion of the operation handle shown in FIG. 6 being guided by the free rotation holding surface.

FIG. 9 is a cross-sectional view showing a conventional example.

[Explanation of symbols]

 3 load sheave 5 drive shaft 7 brake receiver 8 brake retainer 9 mechanical brake 10 drive member 11, 12 friction plate 13 elastic member 14 adjusting member 15 overload prevention mechanism 19 engaging groove 21a first restricting surface 21b second restricting surface 22 free Roll holding surface 40 Idling operation handle 44 Engagement protrusion 44a Inclined guide surface 60 Stopper 86 Engagement body

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[Procedure amendment]

[Submission date] December 2, 1992

[Procedure Amendment 1]

[Document name to be amended] Statement

[Correction target item name] 0016

[Correction method] Change

[Correction content]

A brake receiver 7 and a brake retainer 8 are screwed onto the first side plate side protrusion of the drive shaft 5, and a brake plate 9 is provided on the outer periphery of the boss of the brake receiver 7.
1, 92 and a braking claw wheel 94 with which the braking claw 93 engages, and these braking plates 91, 92 and the braking claw wheel 94 are supported.
Are interposed between the brake receiver 7 and the brake presser 8, and a mechanical brake 9 is constituted by these members. The brake receiver 7 is restrained from moving in the axial direction by a stop ring 71 provided on the drive shaft 5. A coil spring is used instead of the stop ring 71.
May be used or the cotter pin can be driven in the axial direction.
Movement may be restricted.

[Procedure Amendment 2]

[Document name to be amended] Statement

[Correction target item name] 0017

[Correction method] Change

[Correction content]

Further, on the outer peripheral portion of the brake presser 8,
A drive member 1 rotated by a swinging operation of a lever 30 described later.
0 is supported via a negative direction rotation mechanism, and a pair of friction plates 11 and 12 are provided between the brake presser 8 and the drive member 10.
Since the overload prevention mechanism 15 including the elastic member 13 and the overload setting adjusting member 14 is provided, the brake presser 8 has a large diameter portion having a pressing side surface facing one braking plate 92. 81 and a medium-diameter portion 82 and a small-diameter portion 83 that are continuous with the large-diameter portion 81 are formed. The outer peripheral surface of the medium-diameter portion 82 receives the pressing force of the elastic member 13 and applies the pressing force to one of the two. A groove 84 for preventing rotation of the pressing plate 16 that transmits to the entire friction plate 12 is provided, and the small diameter portion 83 is provided.
The adjusting member 14 that adjusts the pressing force of the elastic member 13 to adjust the rated load at which the overload prevention mechanism 15 starts to operate is screwed on. In this case, the adjusting member 14
May be screwed only, but is generally used for overload prevention devices.
Use a lock washer that is used, or use a lock nut.
May be used. In the embodiment shown in the figure,
One rubbing plate 12 and one pressing plate 16 are provided.
However, a plurality of other sheets may be provided.

Claims (4)

[Claims] 1. A mechanical brake 9 mounted around a drive shaft 5 for driving a load sheave 3, a brake presser 8 of the mechanical brake 9, and a drive member 10 supported on an outer peripheral portion of the brake presser 8. , Friction plates 11, 12
A hoisting traction machine provided with an overload prevention mechanism 15 including an elastic member 13 and an adjusting member 14, wherein a stopper 60 is provided at the shaft end of the drive shaft 5, and the stopper 60 and the brake presser are provided. 8, an idling operation handle 40, which cannot rotate relative to the drive shaft 5, is interposed so as to be axially movable, and the idling operation handle 40 is urged toward the brake presser 8 side. Between the adjusting member 14 and the operation handle 40, when the operation handle 40 is in the non-idle operation, the relative rotation of the brake presser 8 with respect to the drive shaft 5 at a predetermined angle or more is restricted so that the rotation angle is within a predetermined angle. Rotation restricting means for allowing the brake presser 8 to advance and retract with respect to the brake receiver 7 by relative rotation; and the operation handle 4.
At the time of free rotation operation of 0, the operation handle 40 is elastically brought into contact with the adjusting member 14 by urging the operation handle 40 toward the brake retainer 8 side to suppress the relative rotation of the brake retainer 8 with respect to the drive shaft 5. A hoisting and traction machine, which is provided with an idling holding means for holding the idling state of the load sheave 3. 2. The idling holding means comprises an idling holding surface 22 and an engaging protrusion 44 which elastically contacts the idling holding surface 22 to hold the idling holding surface 22, and the idling holding surface 22 and the engaging protrusion 44. On one side of the facing surfaces of the adjusting member 14 and the idling operation handle 40, and on the other side the adjusting member 14 and the idling operating handle 4
The hoisting and traction machine according to claim 1, wherein the hoisting and traction machine is provided on the other side of 0. 3. The restricting means for restricting the relative rotation of the brake presser 8 with respect to the drive shaft 5 is the engaging projection 4 of the idle holding means.
4 is provided with a first regulation surface 21a and a second regulation surface 21b, and the idling holding surface 22 is provided continuously to the second regulation surface 21b and at the When the idling operation handle 40 is rotated in the idling operation direction, the engaging protrusion 44 is provided on at least one of the surface facing the second regulating surface 21b and the second regulating surface 21b.
3. An inclined guide surface 44a for guiding to the inner side is provided.
The hoisting and pulling machine described. 4. The drive member 10 is freely rotatable with respect to the brake presser 8 during rotation of the drive member 10 in the drive rotation direction between the brake presser 8 and the drive member 10, and the drive member 10 is free to rotate in the non-drive rotation direction. At the time of rotation, a one-way rotation mechanism that allows the drive member 10 to rotate integrally with the brake presser 8 is provided. And an engaging groove 86 with which the engaging body 86 engages when the drive member 10 rotates in the non-drive rotation direction.
The hoisting traction machine according to claim 1, wherein a plurality of the engaging grooves 19 are provided.