JPH0565437B2 - - Google Patents

Abstract

The invention relates to a control system with which the rope (3), drawn off from a cable drum (4) by a ramming weight (5), can be braked essentially without shocks within a predetermined overrun travel while avoiding a slack rope formation and while maintaining the selected drop height during subsequent blows, the winch drum being driven with adjustable torque by a motor (12) via a slip clutch. The torque when lifting over the height of the overrun travel is set to a threshold value which is matched to the weight of the rope and the load suspension device in such a way that the latter, but not the ramming weight (5), is lifted. After the threshold value is reached, the tensile force of the rope activates a measuring device (15) before or during the lifting of the ramming weight, which measuring device (15) measures the sectional length up to the desired drop height. When the threshold value is reached, the clutch is switched from the lower torque of the overrun travel to the torque for lifting the ramming weight or to the rated torque. The clutch is switched to free running after a rope length corresponding to the drop height is wound onto the winch, and the winch brake is engaged as soon as a rope length corresponding to the drop height has run off the winch drum. <IMAGE>

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides a drum operating device for a winch having the following configuration, namely, a winch rope is pulled out by a free-falling ramming weight connected to the rope, and then the winch Drum operation of a winch configured to momentarily rest the ramming weight on an object to be struck, move it away from the object, and raise it to a desired falling height, wherein the load take-up means located at a height or connected to the ramming weight;
The rope can be braked within an overrun distance before colliding with the ramming weight to prevent the rope from being pulled out in a loose state, and the rope can be braked before, simultaneously or at the same time as the ramming weight collides with the object to be hit. The present invention relates to a drum operating device for a winch, which is configured to be immediately braked within an overrun distance via the winch drum.

Such ramming weights are used, for example, for compacting soil and other materials and for driving solid or tubular piles, and have a falling height of, for example, 3 to 10 m. The ramming weight falls virtually without any hindrance (the ramming weight is braked only by the inertia of the entrained mass and in special cases may even rotate due to friction).
This means that the rope pulled out from the winch drum is accelerated to a considerable speed, so that after the ramming weight hits the object to be struck, the rope is pulled out in a slack state ( (unwound). Further, if the rope is not braked when the ramming weight collides with the object to be hit, the rope may remain taut and become entangled with the winch and wound up. Furthermore, if the rope is braked prematurely, a portion of the impact force due to the ramming weight will react on the rope drum, causing an undesirable large dynamic load to act on the rope drum. On the other hand, if the timing of braking the rope is too late, the rope may be pulled out in a slack state and may bounce out of the groove of the rope drum.

As a general principle, the rope drum should be braked based on the impact of the ramming weight on the object to be struck. As a technique that has been proposed so far, there is a technique in which noise generated at the time of impact is detected by a sensor, and the brake of the rope drum is started after a predetermined delay time has elapsed after the sensor responds. Another technique that has been proposed is
Some devices are configured to detect the vibration waves of the rope caused by the impact using a sensor, and apply the brake simultaneously with the detection or after a predetermined delay time. However, neither of these devices is preferred, since neither noise nor vibration waves traveling backwards along the rope can be used as a sufficiently accurate control signal.

One object of the invention is therefore a rope drum operating device of the type mentioned at the outset, which allows the rope being pulled out by the ramming weight to be moved within a predetermined overrun distance essentially without jerking. To provide a rope drum operating device configured to prevent a rope from unwinding in a loose state by controlling the rope to maintain a set falling height at the time of the next impact.

According to the present invention, the above object is achieved by a winch drum operating device according to the present invention as follows: the winch drum is driven by a prime mover via a sliding clutch with an adjustable torque, the torque being: is set to a certain threshold when raised to the height of the overrun distance, and this threshold is
related to the weight of the rope and the load take-up means, such that the load take-up means rather than said ramming weight can be pulled up, and once said threshold is reached, before or when said ramming weight is pulled up; An increase in the tensile stress occurring in the rope can actuate a measuring device, which measures the length of the rope up to the desired fall height and, when said threshold is reached, causes the clutch to after the small torque at the overrun distance has been switched to a torque or rated torque capable of raising the ramming weight and a length of rope corresponding to the fall height has been hoisted onto the winch, the clutch is switched to freewheel mode; This is achieved by a winch drum operating device characterized in that the brake of the winch is activated as soon as a rope length corresponding to the falling height is pulled out from the winch drum.

The operating device according to the invention accurately sets the point of impact of the ramming weight by measuring the length of the rope without the need for a sensor that detects the sound waves and shock waves transmitted by the rope and is prone to failure. can do. The point in time for lifting the ramming weight from the object to be struck can be set very precisely based on the increase in rope tension up to a threshold value. This threshold value is greater than the tension required to raise the load take-up means, but less than the tension required to raise the ramming weight. Once this threshold is reached, the rope pulling up the ramming weight is pulled out taut, allowing the exact length of rope to be set until the ramming weight is pulled up to the selected stroke height. and measured. For the next collision (which occurs due to the free fall of the ramming weight from a given height), the point of impact of the ramming weight is a length of rope corresponding to the measured ram stroke height. It is precisely measured by pulling the weight out of the winch drum.

Therefore, the previously measured rope length (which is
The ramming weight (corresponding to the point of impact) is withdrawn from the winch drum and the winch brake is activated to brake the rope and the load take-up means within the overrun distance. In the operating device according to the invention, it is provided that the downward movement of the upper point of the stroke, which occurs, for example, when driving a pile into the ground, takes place automatically.

Therefore, in the operating device according to the invention, the load take-up means, after the movement along the overrun distance, are raised by the height of the overrun distance with a small tension until the front ramming weight acts on the pull-out rope. As a result, the tension initially increases and at the same time the clutch slips until a threshold is reached. This indicates the position of the ramming weight at the moment of impact on the object to be struck in the case of the next strike. This load threshold is stored and serves as a zero point for measuring the rope as it is pulled up to the selected stroke height.

Precise setting of the point of impact and setting of the impact of the ramming weight, which acts on the object to be struck in the case of the next ram blow, reduces wear on the ram, since the negative effects of impact loads can be avoided altogether. I can do it. In addition, the load acting on the rope can be reduced and diagonal winding caused by the rope coming off the groove of the rope drum and becoming jammed is prevented, so the operating life of the rope can be considerably extended. Further, by preventing the rope from being pulled out in a loose state and by preventing the ram from being pulled up unnecessarily rapidly, work can be performed more safely and easily. Furthermore, the overall operation and economy of the ramming operation can be improved.

After raising the load take-up means along the overrun distance, it is desirable to continuously increase the rope tension up to the rated torque of the winch when a threshold value is reached. This continuous increase in the tension of the rope makes it possible, on the one hand, to avoid sudden pulling up of the rope and shock loads, and on the other hand, to increase the effectiveness of the ramming device.

When the rope or load take-up means is hoisted (ie pulled up) from the position set by the threshold, the clutch is automatically switched from hoisting to free fall.

The rope or drum is preferably braked by a sliding clutch which can be set to a suitable braking moment. In this regard, as already mentioned, the moment of braking is determined by the length of the rope corresponding to the previously measured stroke height (this rope length is the length of the winch drum up to the point of impact of the ramming weight on the object to be struck). (the length being drawn from) is set accurately.

According to a characteristic feature of the invention, after braking the rotational moment due to inertia of the winch drum and other cooperating rotating masses comprising the rope, the load take-up means and the rotating masses, the sliding clutch is
It is designed to switch the load take-up means up. This switching of the clutch allows, on the one hand, to automatically raise the load take-up means until a threshold value is reached, and then, by increasing the tension appropriately, the ramming weights are raised, thereby speeding up the ramming operation. As a result, you can finish your work without wasting time. On the other hand, when driving a ramming weight into a cavity in the ground, the required length of rope is pulled out from the winch drum due to clutch slippage, so that the ramming weight can be emptied without sudden movement of the ramming weight. Fall into the premises.

According to a further feature of the invention, the load take-up means consist of or are of a large mass of such a size as to prevent the rope from being pulled loose during braking and overruns. An additional square of a certain size is provided. If the mass of the load take-up means is not large enough, an additional mass may be provided to keep the rope taut and to allow the rope to travel loose during braking and overrun distances. can be prevented. The mass with only the load take-up means (or with additional mass) can be of the order of 200Kg.

Still another feature of the present invention is that the load take-up means is braked after a length of rope corresponding to the falling height is pulled out from the winch drum, and the length of the rope corresponding to the falling height is It is designed to be reduced by a certain reserve distance associated with the moving and rotational mass to be braked. This operation type is effective when the fall height is high, such as exceeding 3 to 5 m.
In this case, the rotating drum and the parts rotating with it are accelerated to a rotational speed that generates a large rotational moment.

Preferably, the sliding clutch is a fluid-operated disk clutch which has a very low wear rate. By using such a disc clutch, the force generated using the fluid cylinder or the discharge passage of the spring-loaded disc clutch is
Since the torque varies as a substantially linear function of its magnitude, it is possible to quickly and reliably set the required variable torque.

A further feature of the invention is that the rope drum is driven via a planetary gear system (i.e. a differential drive with planetary gears), the two outputs of these planetary gears or differential gears being The shafts are connected to each other via the sliding clutch. With this design according to the invention, the slip clutch can be set in a simple manner so that the respective torque can be controlled with respect to the slip limit, and the rope drum can easily be brought into freewheeling condition. A stop brake can be additionally provided on the drive side and configured to be activated when the prime mover is stopped.

The load take-up means can be constructed as a plate and attached via ropes or chains, serving to compact the soil.

Said ramming weight may consist of a cylindrical ram, said ram being provided with an essentially cylindrical chamber, the length of said chamber being greater than the overrun distance, said load take-up means or A target weight is disposed within the chamber and connected to the hoisting rope extending through a hole formed in the top wall of the chamber.

According to a further feature of the invention, said ramming weight may be formed by a single rope excavator grab, in which case the upper point of the stroke is such that the stationary bell member is located It is necessary to configure the glove so that it can be moved to a location and opened.

Hereinafter, one embodiment of the present invention will be described in detail with reference to the accompanying drawings. The attached drawing schematically shows the operating device for the rope drum of a winch for free-falling ramming weights.

A hoisting rope 3 is hung on a pulley 1 above a crane or excavator (only the jib 2 is schematically shown for simplicity). A driving weight in the form of a ram 5 is suspended from this rope 3. The lifting rope 3 is
It is wound around the winch drum 4 in the usual way. The ram 5 is composed of a cylindrical member with a long chamber 6 inside. The top wall 7 of the ram 5 is provided with a hole 8 through which the lifting rope 3 passes. A load take-up means 9 is fixed to the lower free end of the pulling rope 3, and the load take-up means 9 is constituted by a cylindrical weight of, for example, 200 kg. This load take-up means 9
can be lowered within the cylindrical chamber 6 of the ram 5. However, when the lifting rope 3 is pulled up, the top of the load take-up means 9 (the diameter of which is larger than the diameter of the hole 8) comes into contact with the edge of the hole 8, and the load take-up means 9 and the lifting rope 3 cause the ram to It is now possible to raise the

The ram 5 is guided in a vertical reciprocating movement within the tubular pile 10. To drive pile 5,
Raising the ram 5 to a predetermined height and then switching the winch drum 4 to freewheel mode allows the ram 5 to fall.
The winch drum 4 is driven by a lifting fluid motor 12 via a planetary gear system. The two output shafts of the planetary gear system are connected to the disk clutch 13.
are connected to each other via. The disc clutch 13 is engaged by a compression spring and disengaged by relaxing the compression spring by a fluid piston-cylinder actuator (not shown). The engaged disc clutch produces a braking force or torque of 20, corresponding to a tension of 20 tons in the hoisting rope. In this case, for example, the maximum
Under a pressure of 80 bar, the braking force or tension is
A fluid piston-cylinder actuator can be used that reduces the pressure from 20t to virtually zero.

A stop brake 14 is provided on the input side of the winch. This stop brake 14 is also constituted by a disc clutch, and is activated when the pulling motor 12 is stopped.

The respective length of the rope wound around the winch (winch drum) 4 can be measured by a measuring sensor 15, which can be configured, for example, in the form of an incremental pickup. disk clutch 1
3, a proportioning valve 16 is provided. The disc clutch 13 is switched into freewheeling mode by means of an additional switching valve 17, in which the freely falling ram 5
However, the winch drum 4 moves in freewheel motion.
It is designed to pull out a rope from. The fluid circuit schematically shown in the drawings includes fluid pumps 19, 2.
0 supplies fluid oil. fluid pump 1
9 and 20 are driven by a diesel engine 22 via a gear transmission 21.

At the start of pile driving, the lower driving surface 24 of the ram 5 rests on a counterbore abutment surface 25 formed at the bottom of the tubular pile 10. In this state, the load take-up means 9
is located, for example, in the lower part of the chamber 6, so that the rope 3 is kept taut and thus prevented from being pulled up loose.

When starting in this initial state, the pile driving machine operator initiates automatic control operation by, for example, pressing down on a knob.

The automatic control now sets the disc clutch 13 to a limited rope tension that allows the load take-up means 9 to be raised. At the same time, the pump 19 of the lifting motor 12 is set to maximum displacement. As soon as the load take-up means 9 impinge on the top wall 7 of the ram 5, the system pressure in the pump circuit increases and acts on the clutch, thereby setting the maximum rope tension. As soon as the pressure exceeds the threshold value (the pressure value at which the disc clutch 13 is switched from the limited rope tension and the rope tension gradually increases to the maximum value), the rope length measuring means (i.e. the measuring sensor) 15 reaches zero. is set to This ensures that the point of impact of the ram 5 is precisely set for the next blow.

When the preselected free fall height is reached, the displacement of the pump 20 is locked to zero and the disc clutch 13 is set via the switching valve 17 to the free fall condition. Downward running counter of measurement sensor 15
As soon as the counter) reaches zero count,
The disk clutch 13 is engaged and the rope tension is reduced so that the load take-up means 9, which constitutes an additional weight, is moved over the overrun distance (approx.
braking within 0.7m).

At the moment when the ram 5 hits the bottom of the tubular pile 10, the lower end of the additional weight (load take-up means) 9 is at the level indicated by the number 30.
This level 30 thus indicates the braking point, at which point the disc clutch 13 becomes operational as an overrun brake.

If the free fall height is high, e.g. more than 3 m, the switching point (level) 30 may be reset to brake the load take-up means 9 or an additional upward reserve distance may be required. It is preferable to brake to minimize the winch overrun distance. This preliminary distance can be freely selected based on the free fall height and is generally selected in the range of 50 to 90 cm.

When braking the loaded weight or load take-up means 9, the disk clutch 13 is only partially engaged, even if it does not encounter any resistance, for example when falling into an underground cavity. Therefore, the rope 3 is sufficiently pulled out from the winch 4 by the ram 5.

As soon as the additional weight 9 stops, the disc clutch 13 instantly pulls up the additional weight 9 due to the tension increased by the braking moment, so that a new lifting/shock cycle is started as soon as the ram 5 hits.

[Brief explanation of drawings]

The accompanying drawings schematically show a rope drum operating device for a winch for free-falling ramming weights. 1... Pulley, 2... Jib, 3... Pulling rope, 4... Winch drum, 5... Ram, 6...
...Chamba, 7...Top wall of ram, 8...Hole, 9...
...load take-up means (additional weight), 1
0...Pile, 12...Fluid motor, 13...Disc clutch, 14...Stop brake, 15...
... Measurement sensor, 16 ... Proportional valve, 17 ... Switching valve, 19, 20 ... Fluid pump, 21 ... Gear transmission, 22 ... Diesel engine, 24 ... Driving surface, 25 ... Spot facing abutment Face, 30...level.

Claims (1)

Claims: 1. A winch rope is pulled out by a free-falling ramming weight connected to the rope, and then the winch momentarily pauses the ramming weight on the object to be struck,
A winch drum operating device configured to lift the winch away from the object to a desired fall height, the winch drum operating device being configured to lift the winch away from the object to a desired fall height, the winch drum operating device being configured to lift the winch away from the object to a desired drop height, the load take-up means being located at a height above the ramming weight or connected to the ramming weight. The rope can be braked within an overrun distance before colliding with the ramming weight to prevent the rope from being pulled out in a loose state, and the rope can be braked before the ramming weight collides with the object to be hit. , the winch drum operating device is configured to be braked within an overrun distance via said winch drum simultaneously or immediately thereafter, said winch drum being driven with adjustable torque by a prime mover via a sliding clutch. , this torque is
A threshold is set when the overrun distance is raised to a height, this threshold being related to the weight of the rope and the load take-up means, such that the load take-up means can be pulled up instead of said ramming weights. and once said threshold value is reached, a measuring device can be actuated by an increase in the tensile stress created in the rope before or during lifting of said ramping weight, said measuring device being able to reach the desired When said threshold is reached, said clutch is switched from a small torque at the overrun distance to a torque capable of raising the ramming weight or to a rated torque corresponding to the falling height. After a length of rope has been hoisted onto the winch, the clutch is switched to freewheel mode so that the brake of the winch is activated as soon as a length of rope corresponding to the fall height is pulled out of the winch drum. A winch drum operating device characterized by comprising: 2. The apparatus of claim 1, wherein the rope tension is continuously increased to the winch's rated torque when the threshold is reached. 3. Device according to claim 1 or 2, characterized in that the rope or drum is braked by a sliding clutch which can be switched to the appropriate braking moment. 4. After braking the rotational moment due to inertia of the load take-up means, the winch drum and other cooperating rotating masses, the sliding clutch is configured to switch to an overrun torque capable of lifting the load take-up means. The device according to any one of claims 1 to 3, characterized in that: 5. The load take-up means has a mass that is large enough to prevent the rope from being pulled out in a slack state along the overrun distance during braking, or is provided with an additional mass. The device according to any one of claims 1 to 4, characterized in that: 6. After a rope of a length corresponding to the falling height is pulled out from the winch drum, the load tape up means is braked, and the length of the rope corresponding to the falling height is linearly and rotatably moved. Claim 1 characterized in that the distance is reduced by a certain reserve distance associated with the square to be
6. The device according to any one of . 7. A device according to any one of claims 1 to 6, characterized in that the sliding clutch is a fluid actuated disc clutch. 8. that said rope drum is driven via a planetary gearing or a differential gearing, and that the two output shafts of said planetary gearing or differential gearing are connected to each other via said sliding clutch; 8. A device according to any one of claims 1 to 7, characterized in that: 9. Claim 1, wherein a plate for compacting the soil is attached to the load take-up means via a rope or a chain.
9. The device according to any one of items 1 to 8. 10. said ramming weight consists of a cylindrical ram, said ram being provided with an essentially cylindrical chamber, the length of said chamber being greater than the overrun distance, said load take-up means or addition; a target weight is disposed within said chamber, and said load take-up means or additional weight is connected to said lifting rope extending through a hole formed in a top wall of said chamber. Claim 1
9. The device according to any one of items 1 to 8. 11. Apparatus according to any one of claims 1 to 8, characterized in that the ramming weight is formed by a single rope excavator grab.