JPH0733390A - Overload preventing device for hoisting/hauling device - Google Patents

Abstract

PURPOSE:To connect an inner ring and an outer ring with wedge friction force and optionally set transfer torque by applying the pressure by a pressing member to one of both rings coupled between the first and second operating members. CONSTITUTION:The first operating member 18 is screwed to a brake screw 17 provided on a pinion shaft 1, the second operating member 20 is coupled with the outer periphery of a small cylinder section 19, and a ring structural body 26 constituted of an inner ring 24 and an outer ring 25 is inserted between the small cylinder section 19 and the second operating member 20. The outer periphery of the inner ring 24 and the inner periphery of the outer ring 25 are formed into wedgelike taper faces meshed with each other. A transfer torque adjusting pressing member 27 is reciprocatably screwed to the sleeve 28 of the first operating member 18, the outer ring 25 is pressed by the pressing member 27, vertical face pressure is generated on the inner ring 24 and the outer ring 25, and the first and second operating members 18, 20 are connected.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an overload preventing device for preventing overload in a hoisting and traction device.

[0002]

2. Description of the Related Art A conventional overload preventing device for a hoisting and pulling device has a structure in which a pair of friction plates are interposed at a position of an operating member composed of a switching gear and pressure is applied by a disc spring or the like. For example, Japanese Patent Publication No. 4-57591 is known.

[0003]

In the conventional overload preventing device for the hoisting and pulling device, since the friction plate is used at the place where the transmission torque is generated, when oil or the like enters the friction plate, There is a problem that the transmission torque is extremely reduced and it is not possible to wind up a load within the specified load.

Further, since the friction plate, the disc spring, the receiving plate, etc. are assembled, not only the cost becomes high, but also the axial length of the overload preventing mechanism becomes large as a whole, and the center of gravity of the hoisting and traction device is balanced. Collapses, and the inclination when used for hanging increases,
It is difficult to commercialize and there are problems such as.

[0005]

SUMMARY OF THE INVENTION The present invention provides an overload preventing device for a hoisting and traction device that solves the above problems. The first means of the device is a reduction gear group. A pinion shaft for driving a load sheave via a ratchet wheel connectable to the pinion shaft via a brake part, a first actuating member for actuating the brake part, and a manual actuating means for the first actuating member. In a hoisting and traction device including a second actuating member that transmits a driving force, the second actuating member is rotatable with respect to the first actuating member in the hoisting direction and lockable in the hoisting direction. A one-way clutch means is provided, and a ring structure for torque transmission is interposed between the first actuating member and the second actuating member, and the ring constructs are mutually contacted via a tapered surface. Inn Consists of a-ring and the outer ring, the tapered surface is a point made by providing a pressing member for transmitting torque adjusting pressing the inner ring and / or the outer ring in the axial direction in a direction to be pressed.

The present invention is configured as a second means. In addition to the first means, the pressing member is screwed to the first actuating member so as to be movable back and forth, and the pressing member is screwed. Is configured to press the inner ring and / or the outer ring in the axial direction.

Further, the present invention is configured as a third means, in addition to the second means, the pressing member and the first actuating member screwed with the pressing member are not relatively rotatable. It is provided with a loosening prevention means to be fixed to.

According to the present invention, when hoisting or pulling is attempted in an overloaded state, the inner peripheral surface of the inner ring fitted between the first operating member and the second operating member is Since slip occurs between the first actuating member and the outer peripheral surface of the small cylindrical portion, hoisting and pulling in an overloaded state are prevented, and safety can be ensured.

[0009]

Embodiments of the present invention will be described in detail below with reference to the drawings.

1 to 9 show a first embodiment in which an overload preventing device of the present invention is applied to a lever type towing and hoisting machine. FIG. 1 shows the entire lever-type traction hoisting machine, and FIG. 2 shows an enlarged main part thereof, and a pinion 2 is integrally provided at one end of a pinion shaft 1.

A load sheave 3 is rotatably fitted on the pinion shaft 1, and both ends of the load sheave 3 are opposed to each other with a pair of frames 5 with metals 4, 4 interposed therebetween.
5 is pivotally supported.

A gear 6 is fixed to the load sheave 3, and the gear 6 is connected to the pinion 2 via a reduction gear group 7 at all times.

A gear case 8 is fixed to one of the frames 5, and surrounds the entire mechanism including a reduction gear group 7 provided on one side of the frame 5. Further, a brake cover 9 is fixed to the other frame 5 and surrounds the entire brake unit 10 provided on the other side of the frame 5.

An upper hook 1 is provided on top of the frames 5 and 5.
1 is arranged so as to be swingable about a horizontal axis 12 and rotatable about a vertical axis 13.

The load sheave 3 has a load chain 1
4 is suspended and has a lower hook (not shown) at the lower end of the load chain 14 to be loaded.

In the brake unit 10, a hub 15 is fitted on the pinion shaft 1 via serrations 16 so as not to rotate relative to each other. Also, the pinion shaft 1
A first actuating member 18 is screwed onto the brake screw 17 provided on the first actuating member 18, and the first actuating member 18 faces the hub 15.

The first operating member 18 is the brake screw 1
7 is provided with a small cylindrical portion 19, and the second operating member 20 is fitted to the outer periphery of the small cylindrical portion 19.

As shown in FIG. 4, a plurality of recesses 22 for accommodating the rollers 21 are provided on the inner circumference of the second actuating member 20, and the recesses of the recesses 22 have a surface facing the winding direction DN. 21 is formed into an arcuate surface for holding, and a surface facing the winding direction UP is formed into an inclined surface 23 that gently inclines. Therefore, the second operating member 20 moves in the winding direction U.
Although it can rotate in P, it cannot rotate in the winding direction DN. That is, when trying to rotate in the unwinding direction DN, the roller 21 moves between the first operating member 18 and the second operating member 20.
Is configured to bite into the slope 23 and prevent rotation,
It constitutes one-way clutch means.

Between the small cylindrical portion 19 of the first actuating member 18 and the second actuating member 20, a ring structure 26 consisting of an inner ring 24 and an outer ring 25 is interposed. The outer peripheral surface of the inner ring 24 and the outer ring 2
The inner peripheral surface of 5 is formed into a tapered surface whose diameter is gradually reduced toward the axial end of the pinion shaft 1, and both tapered surfaces are fitted so as to mesh with each other in a wedge shape. A pressing member 27 for adjusting the transmission torque is screwed into the sleeve 28 of the first operating member 18 so as to be able to move forward and backward, and the pressing member 27 presses the outer ring 25 against the inner ring 24, that is, the arrow in FIG. Press in the A direction.

Therefore, the pressing member 27 causes the arrow A in FIG.
When pressure is applied in the direction, surface pressure is generated in the inner ring 24 and the outer ring 25 in the directions of arrows P1 and P2, and the first operating member 18 and the second operating member 20 are tightened by the pressing force of the pressing member 27. The transmission torque is proportional to.

When the transmission torque adjustment between the first operating member 18 and the second operating member 20 is completed in this way, the pressing member 2
The pressing member 27 and the first actuating member 18 so as not to loosen 7.
A hole is drilled at the screwing point of and the spring pin 29 (FIG. 2) that prevents the pressing member 27 from rotating is set.

Therefore, when an overload exceeding the set torque is applied, a sliding bearing is formed between the outer peripheral surface of the small cylindrical portion 19 of the first operating member 18 and the inner peripheral surface of the inner ring 24. Slip occurs and overload transmission is prevented.

The inner ring 24 and the outer ring 25 are inserted in a direction opposite to the direction shown in FIGS. 2 and 3, that is, the inner ring 24 and the outer ring 2 are combined.
It is functionally the same even if the tapered surfaces of 5 that are contacted with each other are arranged in a direction in which the diameter gradually increases toward the axial end of the pinion shaft 1 and the pressure of the pressing member 27 is applied to the inner ring 24. .

A fast-turning grip 30 is fitted around the shaft end of the pinion shaft 1 so as to be rotatable and axially movable. A locking member 31 is rotatably fitted over the shaft end of the pinion shaft 1, and an elastic resistance member 32 made of a spring is interposed between the locking member 31 and the pinion shaft 1. ing. The pinion shaft 1 is provided with a threaded rod extending beyond the locking member 31, and a nut 33 is screwed to the threaded rod to form a retaining means for the locking member 31. A spring 34 is interposed between the first actuating member 18 and the quick-turning grip 30 in a compressed state,
As a result, the quick-turn grip 30 is always provided with the locking member 3
It is pressed against 1.

As shown in FIG. 5, the elastic resistance member 32 is made of a thin spring steel spring and has an inner peripheral projection 35 and an outer peripheral projection 36. As shown in FIGS. The inner peripheral projection 35 is locked in the locking groove 37 of the pinion shaft 1 and the outer peripheral projection 3 while the force is accumulated.
6 is locked in the locking groove 38 of the locking member 31.

As shown in FIGS. 2 and 7, the locking member 31
And the quick-turning grip 30 are interlockingly connected to each other through mutual engagement of a plurality of grooves 39 and protrusions 40 provided at intervals in the circumferential direction.

As shown in FIGS. 2 and 8, the pressing member 27 screwed and fixed to the sleeve 28 of the first actuating member 18 and the quick-turn grip 30 are fast-turned to the locking groove 41 of the pressing member 27. By engaging the locking protrusions 42 of the grip 30, they are interlockingly connected in the circumferential direction.

As shown in FIG. 2, a ratchet wheel 44 and a pair of brake linings 45 are externally inserted into a small cylindrical portion 43 of the hub 15 which is non-rotatably fitted to the pinion shaft 1, and a first actuating member. The brake unit 10 is configured together with 18. Pins 46 and 46 are arranged on the frame 5 above and below the ratchet wheel 44, and braking pawls 47 and 47 axially supported by the pins are biased by an engagement spring 48. 44
Is engaged with.

As shown in FIG. 2, a gap θ is formed between the pressing member 27 and the quick-turning grip 30 in the brake operating state.
Is formed. As shown in FIGS. 2 and 9, a switching gear portion 49 is provided on the outer periphery of the second actuating member 20, and the forward rotation claw piece 50A and the reverse rotation of the switching claw metal fitting 50 are reversed with respect to the switching gear portion 49. The claw piece 50B is selectively engageable.
The switching claw fitting 50 is provided with respect to the shaft portion 52 of the handle 51.
It is fixed by a spring pin 53, and the shaft portion 52 is pivotally supported by a lever 54. The lever 54 is provided with a holding shaft 55 that holds the switching claw metal fitting 50, and the holding shaft 55 is pressed against the switching claw metal fitting 50 via a spring 56 and rotated by a handle 51. It defines and holds the forward rotation position, reverse rotation position, and neutral position of. As a result, the lever 54 constitutes a manual drive means in the hoisting and pulling device.

In the unloaded state, the elastic resistance member 32
From the state before incorporation shown in FIG. 6 (A) to FIG. 6 (B).
As in the state after the assembly shown in FIG. 2, the pinion shaft 1 and the locking member 31 are twisted and the elastic force is accumulated.
7 is interposed between the pinion shaft 1 and the pinion shaft 1 to urge the locking member 31 to rotate in the direction of the arrow in FIG. A plurality of grooves 39 provided on the outer periphery of the locking member 31 are engaged with the projections 40 of the quick-turn grip 30, and further, the locking projections 42 of the quick-turn grip 30 are locked by the locking grooves 41 of the pressing member 27. As a result, the pressing member 27 is constantly urged to rotate in the direction of the arrow shown in FIG. 8 to prevent the tightening of the brake portion and release the brake. Quickly pull the load side load chain 14A or the unloaded side load chain 14B
It is possible to perform idling operation to extend and shorten.

FIG. 10 shows a second embodiment and shows a structure in which the overload preventing device of the present invention is incorporated in a chain block. Handwheel 5 rotated by hand chain 57
The inner ring 61 and the outer ring 62 similar to those in the first embodiment are fitted to the inner circumference of the outer ring 8 and the outer circumference of the small cylindrical portion 60 of the actuating member 59, and the outer ring 62 is pressed by the pressing member 63 for adjusting the transmission torque. When an overload exceeding the set torque is applied by applying pressure to the inner ring 61,
Between the inner peripheral surface and the outer peripheral surface of the small cylindrical portion 60 of the actuating member 59, slip serving as a slide bearing is generated to prevent overload.

Therefore, in this embodiment, the handwheel 58 serves as the manual drive means and the second operating member in the first embodiment, and the operating member 59 serves as the first operating member in the first embodiment. Equivalent to.

It is needless to say that the present invention is not limited to the above-mentioned embodiment, and various design changes can be made based on the constitution described in the claims. For example, the transmission mechanism between the pinion shaft 1 and the load sheave 3 and the idling device described above may employ configurations other than those in the above-described embodiment.

[0034]

According to the present invention, by applying pressure from the pressing member 27 to one of the inner ring 24 and the outer ring 25 fitted between the first operating member 18 and the second operating member 20, Both the rings 24 and 25 are connected by a wedge friction force, and the inner and outer radial surface pressures P1 and P2 from the two rings 24 and 25 are applied to connect the first operating member 18 and the second operating member 20. Therefore, there is an effect that the transmission torque can be set only by changing the thrust direction pressure of the pressing member 27.

Then, when winding or pulling is attempted in an overloaded state, that is, when an external force corresponding to an overload acts on the lever 54 and an external force equal to or greater than the set torque acts, the inner ring 24 is Since slip is caused between the peripheral surface and the outer peripheral surface of the first operating member 18, hoisting or pulling in an overloaded state can be preferably prevented.

By the way, in the conventional case where the friction plate is adopted at the transmission torque generating portion, there is a drawback that the transmission torque is extremely lowered when oil or the like enters the friction plate, whereas the present invention According to the inner ring 24
Also, the outer ring 25 made of heat-treated metal has an advantage that the transmission torque does not change even when oil or the like enters.

Further, the above-mentioned friction plate system requires a disc spring and a receiving plate for applying a pressure, which not only causes a high cost, but also increases the axial length of the drive unit as a whole, thereby increasing the winding. While there is a problem that the balance of the center of gravity of the combined traction device is lost and the tilt becomes large, according to the present invention, the number of parts is small, and the cost is low because it can be implemented by simple small parts. Since the axial length of the entire device hardly changes depending on the presence or absence of the overload prevention device, there are advantages such as compactness.

[Brief description of drawings]

FIG. 1 is a vertical sectional view showing a lever type towing and hoisting machine according to a first embodiment of the present invention.

FIG. 2 is an enlarged cross-sectional view showing one embodiment of an overload prevention device in a lever type towing and hoisting machine.

FIG. 3 is an explanatory view showing an operation of an inner ring, an outer ring and a pressing member in an assembled state.

FIG. 4 is a cross-sectional view taken along the line X in FIG. 2, showing the action of rotating in the winding direction but being fixed in the winding direction.

FIG. 5 shows an elastic resistance member, (A) is a front view, (B)
Is a side view.

FIG. 6 shows an elastic resistance member, (A) is a front view showing a state before being assembled, and (B) is a front view showing a state after being assembled.

7 is a cross-sectional view taken along line Z of FIG. 2, showing the engaged state of the locking member, the pinion shaft, the elastic resistance member, and the quick-turn grip.

8 is a cross-sectional view taken along line Y of FIG. 2, showing a state of engagement between the pressing member and the quick-turn grip.

9 is an explanatory view taken along the arrow B of FIG. 2 and showing the action of the switching claw fitting.

FIG. 10 is a vertical sectional view showing a chain block according to a second embodiment of the present invention.

[Explanation of symbols]

 1 Pinion Shaft 3 Load Sheave 10 Brake Part 14 Load Chain 18 First Actuating Member 19 Small Cylindrical Part of First Actuating Member 20 Second Actuating Member 21 Roller (One-way Clutch) 22 Recess (One-way Clutch) 24 Inner Ring 25 Outer Ring 26 Ring structure 27 Pressing member 28 First actuating member sleeve 29 Spring pin 30 Fast-turning grip 31 Locking member 32 Elastic resistance member 49 Switching gear part 50 Switching claw metal fitting 51 Handle 54 Lever (manual driving means)

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[Procedure amendment]

[Submission date] December 14, 1993

[Procedure Amendment 1]

[Document name to be amended] Statement

[Correction target item name] 0018

[Correction method] Change

[Correction content]

As shown in FIG. 4, a plurality of recesses 22 for accommodating the rollers 21 are provided on the inner circumference of the second operating member 20, and the recessed surfaces of the recesses 22 are surfaces facing in the winding direction DN.
Is formed on the slope 23 that gently inclines, and the winding direction UP
The arc-shaped surface that holds the roller 21
There is. Therefore, the second actuating member 20 can rotate in the winding direction UP, but cannot rotate in the winding direction DN.
That is, when trying to rotate in the unwinding direction DN, the roller 21 is configured to bite the slope 23 between the first actuating member 18 and the second actuating member 20 to prevent the rotation. I am configuring.

[Procedure Amendment 2]

[Document name to be amended] Statement

[Name of item to be corrected] 0023

[Correction method] Change

[Correction content]

The inner ring 24 and the outer ring 25 are inserted in the opposite directions to the directions shown in FIGS. 2 and 3, that is, the tapered surfaces of the inner ring 24 and the outer ring 25 that are in contact with each other are arranged on the pinion shaft. The pressing member 27 is arranged in a direction in which the diameter gradually increases toward the shaft end of 1.
Even if the pressure is applied to the inner ring 24, the function is the same. Also, depending on the tightening force of the pressing member 27,
The first operating member 18 and the second operating member 20 come into contact with each other.
However, the frictional resistance is reduced by making the contact surface smaller. Ma
If a large amount of abrasion resistance occurs and it causes a functional problem,
Between the first actuating member 18 and the second actuating member 20, fitted on one side.
Sludge with extremely low frictional resistance consisting of gold-impregnated adherend
You may incorporate the washer 64.

[Procedure 3]

[Document name to be corrected] Drawing

[Name of item to be corrected] Figure 2

[Correction method] Change

[Correction content]

[Fig. 2]

Claims (3)

[Claims] 1. A pinion shaft that drives a load sheave through a reduction gear group, a ratchet wheel that is connectable to a pinion shaft through a brake unit, a first actuating member that actuates the brake unit, and A hoisting and traction device comprising a second actuating member for transmitting a driving force from a manual driving means to the actuating member, wherein the second actuating member is rotatable in the hoisting direction and is wound around the first actuating member. A downwardly lockable one-way clutch means is provided, and a ring structure for torque transmission is interposed between the first operating member and the second operating member, and the ring structures are mutually connected. The transmission ring comprises an inner ring and an outer ring that are opposed to each other via a tapered surface, and that axially presses the inner ring and / or the outer ring in the direction in which the tapered surface is pressed. An overload prevention device for a hoisting and traction device, comprising a pressing member for adjusting the torque. 2. The pressing member is screwed to the first actuating member so as to be able to move forward and backward, and is configured to axially press the inner ring and / or the outer ring by screwing the pressing member. The overload prevention device in the hoisting and traction device according to claim 1. 3. The winding device according to claim 2, further comprising a loosening prevention means for fixing the pressing member and the first actuating member screwed with the pressing member such that they cannot rotate relative to each other. Overload prevention device for upper and traction devices.