JPS6014940B2 - Sliding clutch device for small electric hoisting machines, etc. - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a slip clutch device, and more particularly to a submerged clutch device for use in a small electric hoist.

[Conventional technology]

A hollow shaft rotatably driven from the outside of the motor, a first clutch plate fixed to one end of the hollow shaft, a drive shaft inserted into the hollow shaft, and a drive shaft supported slidably in the direction of the shaft. and a second clutch plate facing the first clutch plate, a clutch lining interposed between opposing surfaces of the first and second clutch plates, and a clutch lining provided adjacent to the second clutch plate. , a 4-shaped electric hoist having a pressure device that presses a second clutch plate against the first clutch plate via the clutch lining and enables power transmission by friction from the hollow shaft to the drive shaft. Sliding clutch devices for this purpose are known (see East German Patent No. 78074).

In this known slipping clutch device, if the friction coupling force through the clutch linings of the first and second clutch plates decreases due to wear or damage to the clutch lining or damage to the compression device, the load on the hoist will decrease. Due to the weight, the drive shaft rotates rapidly in the direction of unloading the load, causing an accident.In order to prevent this, in the known sliding clutch device for hoisting rock, the rotation of the second clutch plate connected to the drive shaft is controlled. It is equipped with a braking device that applies braking to prevent the load from dropping. It is composed of a brake bar pivotally mounted at one end and pivotably displaceable with respect to the circumference of the second clutch plate.

In a braking device having such a structure, in a non-braking state, the friction shoe is located with a relatively large gap between it and the second clutch plate circumference, and therefore the brake lever is moved so as to eliminate this large gap. In order to cause the rotational displacement around the pivot axis, the power plant that operates the braking device must have a fairly large capacity.

Furthermore, since the motion of the brake lever that presses the arc-shaped friction shoe against the periphery of the second clutch plate for braking is rotation around the pivot point, uneven wear occurs on the friction shoe and the braking The function of the device is likely to deteriorate.Furthermore, as mentioned above, due to the relatively large gap between the friction shoe and the edge of the second clutch plate, especially in the case of efficient hoisting with a small moment of inertia, the power There is a time delay between when the device starts operating and when the brake is applied, and during that time the hoisting load drops and the hoisting machine accelerates.This is very disadvantageous for braking. A large braking torque is required to stop something, and it is not possible to obtain uniform braking action as a whole.By the way,
In order to apply braking to the second clutch plate with a small time delay and small braking torque through a uniform and small gap, a braking member that acts on the disc brake principle is placed on the surface of the second clutch plate. However, if a braking method is adopted in which a pressure force is applied to the surface of the second clutch plate, the first and second clutches constituting the slipping clutch will slip when a certain torque is exceeded. This disc brake system cannot be used as is because the pressure force between the two clutch plates constantly fluctuates, which affects the normal function of the slipping clutch.

[Problem that the invention seeks to solve]

The present invention was made in view of the above-mentioned problems.
The purpose is to make the braking gap small and uniform,
The braking time can be shortened, uneven wear of the lining can be prevented, and the braking torque can be reduced, and the braking does not affect the pressure force between the first and second clutch plates. To obtain a slip clutch device for a small electric hoisting rock, etc., in which the normal function of the slip clutch is not impaired.

[Means to solve the problem]

In the present invention, a system similar to a disc brake is explored in order to apply braking to the second clutch plate of the known slipping clutch device mentioned at the beginning to prevent the load from falling. The pressing force is first transmitted to the pressing plate.

A brake ring movable in the hammer direction is provided behind the pressing plate between the press plate and the housing, and the brake ring is located near the circumference of the second clutch plate and is in engagement with the second clutch plate,
Both are arranged to be displaced together in the direction of rotation. The brake ring has brake linings on both sides. Further, in order to apply a braking pressing force to the pressing plate, a pivot lever whose one end is in contact with the pressing plate is provided,
A spring acts on the other end of the lever, and the force of the spring causes one end of the lever to apply a pressing force to the pressing plate, while a power device is provided that has a force that overcomes the force of the spring. [Operation] When the power unit is turned off during emergency braking, the force of the spring acts on the pressing plate via the lever bar.

At this time, the force acting on the press plate presses the brake ring through the brake lining between the housing and the press plate, and locks the brake ring unrotatably. At this time, even if the brake ring is displaced in the marring direction, the displacement is not transmitted to the second clutch plate. However, since the second clutch plate is engaged with the brake ring so as to be interlocked with respect to the direction of rotation,
When the brake ring is locked, the rotation of the second clutch plate is stopped instantaneously, and the drive shaft of the hoisting rock, etc. is also stopped instantaneously.
[Example] Hereinafter, an example of the present invention will be described with reference to the drawings.

In Fig. 1, reference numeral 25 denotes a drive motor for the electric hoisting rock, which has a rotor 25', and this rotor 25' has a hollow shaft 1.
is fixed.

A first clutch plate 2 is fixed to one end of the hollow shaft 1 (the right end in the figure) by bolts or the like, and a drive shaft 3 for a hoisting mechanism, which will be described later, is inserted inside the hollow shaft 1. .At the right end of this drive shaft in the diagram, there is a first
A second clutch plate 4 faces the clutch plate 2 of
is supported. The second clutch plate 4 is freely movable in a direction relative to the drive shaft 3, but is supported by means such as a key so as not to rotate relative to the drive shaft 3. 1st
An annular clutch lining 5 is interposed between the opposing surfaces of the second clutch plates 2 and 4.

Portrait recesses 23 are provided in the first and second clutch plates 2 and 4.
and an inclined surface 24 are formed, and the clutch lining 5 is received in the wide cut recess 23. A hub is formed on the opposite side of the second clutch plate 4 from the clutch lining 5, and a coil spring 19 constituting an elastic device is formed on the outer periphery of the hub.
is provided. The coil spring 19 is interposed between the second clutch plate 4 and a backing plate 27 that is supported behind an adjustment nut 20' that is adjustably screwed into a screw shaft 26 that protrudes from the end of the drive shaft 3. This presses the second clutch plate 4 against the first clutch plate 2 via the clutch lining 5. Therefore, the first and second clutch plates 2
, 4 are in frictional contact, and the rotation of the hollow shaft 1 is caused by the clutch plates 2, 4.
is transmitted to the drive wheel 3 via a clutch. As shown in FIG. 6, a chain wheel 30 constituting a hoisting rock foundation is connected to the left end 3a of the drive shaft 3 in a known manner via an electric gear device 31, and the rotation of the drive shaft 3 As a result, the load supported by the chain 32 wound around the three chain wheels is moved up and down. Note that in FIG. 6, a part of the gear that connects the drive shaft end 3a and the electric gear device 31 is omitted. Furthermore, since FIG. 6 is a horizontal sectional view, the load moves in a direction perpendicular to the plane of the paper. The electric hoisting rock main body 33 incorporating these mechanisms is suspended from a ceiling beam or a ceiling rail, and the load below is lifted and lowered using a hanging hook supported by a chain. As shown in FIG. 1, a brake ring 6 is provided near the outer periphery of the second clutch plate 4, and this brake ring 6 has a cylindrical shape as shown in FIG. It engages with the second clutch plate 4 via rollers 7.

Recesses are formed in the second clutch plate 4 and the brake ring 6 to receive the rollers 7, respectively. Note that the above-mentioned inclined portion 24 of the second clutch plate 4 makes it easy to install the roller 7 in the recess between the brake ring cover and the clutch plate 4. An annular brake lining 8,g is provided on both sides of the brake lining 8.One brake lining 9 is inserted into an annular groove 2 formed separately from the hoist housing i. On the one hand, the other brake lining 8
A pressing plate 14 is provided between the clutch plate 4 and the second clutch plate 4.

The pressing plate wing 4 has a closing opening in the center thereof through which the coil spring 19 passes, and is provided with an annular holder 22 on one side thereof for receiving the brake lining 8. Further, the press plate 14 is supported so as not to rotate by a pin 6' protruding from the housing turtle 5, but is guided by a pin 161 and can be freely displaced in the scale direction. In a normal state, a small gap 17, 17 is formed between both surfaces of the brake ring 6 and the brake lining 899. A power device such as an electromagnetic solenoid is supported below the housing 15, and its output member is connected to the lower end of the lever 13.

The lever 13 extends upward, and its upper end has a forked shape as shown in FIG.
At the tip of the pressure plate (Fig. 5), adjust the adjustment bolt 18 toward the
is screwed in and its tip is in contact with the surface of the pressure plate turtle.
Also, on the side of the housing unit 6, there is provided a fulcrum part back 2 for pivotally supporting the lever 13, and the fulcrum pin 2a (Fig. 5) is connected to the adjustment bolt of the bifurcated shaft 3a as shown in the figure. The lever turtle 3 is pivotally supported at a position separated from the lever 8 by a distance a.
A spring device 0 is provided around the output shaft of the power device.
It applies a rightward force to the lower end of . Therefore, with the force of this spring device turtle 8, the lever force S tries to rotate counterclockwise in the figure, around the branch pin turtle 2a, and the tip 1 of the adjustment bolt 1 moves the pressing plate 14 to the left in the figure. The brake ring 6 is pressed through the brake linings 8 and 9 to lock it. On the other hand, when the power bag Hawk Wing River is energized, its output member compresses the mimic device and is pulled toward the left, so the force exerted by the spring device 8 on the lever turtle 3 is removed. The pressing force of the pressing plate Tomimo disappears,
The brake ring 6 is unlocked and the aforementioned slight gap 17 is removed.
, 17 occurs.

Incidentally, the gap wings 7, 17 can be finely adjusted by the adjustment bolt group 81. Next, the effect will be explained.

During normal operation of the hoisting rock, the power unit turtle 1 is energized and the brake ring S and the second clutch plate turtle are not locked, so the hollow shaft 1 rotates by the forward and reverse rotation of the motor 26. The friction transmission of the clutch plates 2 and 4 causes the drive shaft 3 to rotate, and the winding machine connected to the drive shaft 3 moves forward and backward to move the load up and down.

At this time, the transmission force below the constant torque of the clutch plates 2 and 4 is provided by the compression device g. ``In an overload state that exceeds a certain torque, the clutch plates 2 and 4 slip relative to each other, and even if the hollow shaft turtle rotates, the drive shaft 3 does not rotate, so the load does not move up or down.This slipping state It continues until the motor 2 zero is cut off. By the way, if the slipping clutch fails due to wear or other damage to the clutch lining due to long-term use or use under overload conditions, or even if there is no failure, the overload may occur. When a load is applied, the drive shaft 3 rotates due to the action of the load, and the load lowers or falls.

When this happens, turn off the power unit, such as a solenoid.

As a result, the spring device IQ instantly presses the pressing plate 14 with the force increased by the lever turtle 3, locking the brake ring 6 between the brake linings 8 and 9. Because of its small size, it can be done instantly without any delay. Therefore, the second clutch plate 4 is also stopped instantly via the roller 7, the drive shaft 8 is also stopped instantly, and the hoisting iso-yoko is stopped before it is accelerated. It stops in a short time and with a small amount of braking torque.Therefore, the load does not drop or drop.Also, since all members are displaced in the same axial direction, uneven wear of the lining does not occur.In this case, the power By repeatedly turning on the device 11 for short periods of time, the load can be lowered little by little.In the case of the present invention, by applying a pressing force in the rutting direction to the pressing plate base 4, the brake ring 6 is The brake ring 6 is depressurized and locked between the housing S and the press plate 4 via the brake lining 9, thereby performing braking.

However, even if the brake ring 6 receives a force and is displaced in the axial direction, the second clutch plate 4 does not receive any substantial force in the axial direction, so that both the first and second clutch plates 4 are displaced in the axial direction. clutch plate 2
. braking is performed reliably. FIG. 3 shows a modified embodiment of the invention.

In this example, the second clutch plate 4 and the brake ring 6 are engaged with each other by a pin 7. And brake ring 6
An axial sliding displacement of is made along the pin 7. Otherwise, this embodiment is similar to the previous embodiment.
Note that the present invention can also be applied to similar devices other than small electric hoisting rocks.

〔Effect of the invention〕

As described above, according to the present invention, by pinching and locking the brake ring by the parallel movement of the pressing plate, the second clutch plate that engages with the brake ring is also locked. Since the gap between both sides of the clutch and the brake linings on both sides is extremely small, the second sliding clutch can be instantly removed without directly affecting the slipping clutch itself.
can lock the clutch plate and prevent acceleration of the load drop.

Further, since locking is performed by friction caused by parallel movement in the ball direction, wear between the friction members becomes uniform, and the braking function is less likely to deteriorate. Furthermore, by turning off the power unit, the force of the copying device is increased and instantly transmitted to the pressing plate, thereby ensuring reliable braking. As in the case of the prior art example, a compact structure can be obtained by inserting the drive shaft into the hollow shaft.

[Brief explanation of the drawing]

1 is a longitudinal horizontal sectional view of a slip clutch device according to the invention, FIG. 2 is a side view of the slip clutch device of FIG. 1, and FIG. 3 is a partial longitudinal sectional view of a modified embodiment of the invention; Fig. 4 is a side view showing the relationship between the second clutch plate and the brake ring, Fig. 5 is a partially omitted sectional view of a different cross section from Fig. 1, and Fig. 6 is a 4-type electric hoisting rock. It is a horizontal sectional view showing the whole. 1...Hollow shaft, 2...First clutch plate, 3...
... Drive shaft, 4... Second clutch plate, 5.
...Clutch lining, 6...Brake ring, 7
... Cylindrical roller, 8, 9 ... Brake lining, 1
0... Spring device (compression spring), 11... Power device, 12
...Fulcrum part, 12a...Fulcrum pin, 13.
...Lever, 14...Press plate, i5...Housing 16...Guide pin, 17...Gap, 18...Adjustment bolt, 19...・・・・Pressure device (compression spring), 20 ・・・Adjustment bolt, 21, 2
2... Annular groove, 23... Cutting recess, 24...
...Troubled slope, a...Gap. Fig. 3Fig. 4 F;9.1 Fig5 Fig. 6 Fig. 2

Claims (1)

[Claims] 1. A hollow shaft 1 rotationally driven by a motor 25, a first clutch plate 2 fixed to one end of the hollow shaft 1, and a drive for driving the hoisting machine inserted into the hollow shaft 1. shaft 3 and drive shaft 3
a second clutch plate 4 supported slidably in its axial direction and facing the first clutch plate 2;
a clutch lining 5 interposed between opposing surfaces of the clutch plates 2 and 4; A pressure device 19 that presses the second clutch plate 4 and enables power transmission from the hollow shaft 1 to the drive shaft 3 by friction; a brake ring 6 which is in engaged relationship and is axially movable and radially stationary with respect to the second clutch plate 4;
and annular brake linings 8 and 9, which are provided on both sides of the brake ring 6, and one of which is sandwiched between the housing 15 and the brake ring 6; A press plate 14 which is movable in the axial direction but cannot rotate and which sandwiches the other brake lining 8 between the two, and a press plate 14 whose one end is in contact with the surface of the press plate 14 opposite to the brake ring 6, and which is close to the one end. a lever 13 which is pivotally connected to the housing 15 at a portion thereof and which extends in a direction transverse to the drive shaft 3; 6 and apply a force to the lever 13 of such magnitude as to lock the brake ring 6 between the housing 15 and the pressure plate 14 via the brake linings 8, 9. A small electric winding having a spring device 10 acting on it and a power device 1 which removes the force of the spring device 10 acting on the lever 13 to allow the brake ring 6 to rotate together with the second clutch plate 4. Slip clutch device for upper machines, etc. 2. Claim 1, in which the second clutch plate and the brake ring engage with each other via a plurality of cylindrical rollers 7 between the outer circumference of the second clutch plate 4 and the inner circumference of the brake ring 6. Slip clutch device as described. 3. The outer circumference of the second clutch plate 4 and the inner circumference of the brake ring 6 are connected by an axial pin 7, and the brake ring 6 is slidable relative to the pin 7. Sliding clutch device as described in section. 4. One end of the lever 13 is formed into a bifurcated shape near the drive shaft 3, and adjustment bolts 18 are inserted into the tips of the forks, respectively, so that these come into contact with the pressing plate 14. Sliding clutch device as described in section. 5 Pressing plate 1 to receive brake linings 8 and 9
4 and the housing 15 are provided with annular brocade grooves 21, 22, and a cut recess 23 is formed in the first clutch plate 2 for receiving the clutch lining 5. A slip clutch device according to paragraph 3.