JP3144774B2 - Exciting force generator - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibrating force generating device provided in a pile driving machine or the like for driving or pulling out a steel pipe pile or the like, and more particularly to a vibration generating device using an unbalanced weight. The present invention relates to a vibrating force generating device capable of arbitrarily adjusting a vibrating force within a range from a minimum vibrating force to a maximum vibrating force in an operation state in which is generated.

[0002]

2. Description of the Related Art Conventionally, a vibratory pile driving machine has been used in civil engineering work for driving steel sheet piles, steel pipe piles, etc. (hereinafter referred to as "pile") into the ground and for pulling out the driven pile. I have.
As one type of means for generating the vibrating force in such a vibrating pile driver, a linear vibrating force is generated by a reaction force of centrifugal force generated by rotating an unbalanced weight provided in a casing. There is a weight-type vibrating force generator for generating the force. For example, in a two-axis type vibrating force generating device, a centrifugal force in the horizontal direction is canceled by rotating unbalanced weights disposed substantially horizontally in opposite directions, and a straight line is formed only by the centrifugal force in the vertical direction. The pile is driven or pulled out by vibrating only in the vertical direction by generating a vibrating force in a shape.

[0003] An example of a vibratory pile driving machine provided with a vibrating force generating device will be described. When a pile driving operation is performed by the vibratory pile driving machine, a chuck provided at a lower portion of the vibrating pile driving machine is used. The pile is gripped by the device, the whole is lifted to a predetermined position by a hanging machine such as a pile driver, and the pile is vibrated in the vertical state by vibrating the vibrating pile driving machine in this state, and the pile is driven into the ground.

However, this type of vibratory pile driver passes through the natural frequency of the hanging machine and the natural frequency of the ground from the start of operation until reaching the rated operation state. Resonance occurs when these natural frequencies match. For example, a crane or the like holding such a vibrating pile driver usually suspends the vibrating pile driver by a spring in order to absorb vibration, and therefore, the starting operation passing through the resonance point of the spring is performed. Large vibrations occur when stopped. The resonance is a resonance or noise of the surrounding ground that occurs only when the natural frequency is passed, but may adversely affect the surrounding environment.

In the case of such a vibrating pile driving machine, there is a case where the pile is driven halfway and stopped. In this case, a large load acts when the driving is started again. As this load, the starting load acts together with the frictional resistance between the pile and the ground in contact with the pile, so that a large load acts on the drive motor. At this time, since the drive motor requires a large starting torque, a large starting power is required, which may cause an overload, and may cause a start failure of the electric motor. In particular, when the ground is hard, the motor may seize due to overload and the operation may not be possible.

In such a case, if the eccentric moment of the unbalanced weight can be adjusted, it is possible to disassemble and adjust the amount of eccentric moment, and assemble the assembly. It takes down the ground and disassembles it, requiring a lot of time and effort. In addition, the operation must be performed with the eccentric moment lowered, and the work for adjusting the eccentric moment and the reduction of the moment cause a large delay in the construction period.

Further, when determining a stop position at which a pile is driven into a predetermined position to stop the motor, it is necessary to stop the motor in consideration of the driving amount until the vibratory pile driver is completely stopped. Because of this, the vehicle is often stopped before reaching the predetermined position. In this case, position control is performed by repeatedly stopping and driving just before the predetermined position, which causes problems such as start-up failure due to a high load at the time of restart, and generation of vibration in the surroundings due to resonance when the spring passes through the resonance point. And accurate position control is also difficult.

As a prior art for preventing such an adverse effect, there is an invention described in Japanese Patent Application Laid-Open No. 9-78579. In this invention, as shown in a sectional view in plan view of FIG. Two-system eccentric weight rotating drive system 51,
52 is provided, and the weight 53 provided in one eccentric weight rotating drive system 51 is replaced with the other eccentric weight rotating drive system 52.
Are provided so as to be rotatable with a relative rotational phase difference. By switching these rotational phase differences to a state of 0 degree or a state of 180 degrees or less, the driving force at the time of starting / stopping is reduced, and the pile driving operation can be performed with the maximum driving force at the time of rated operation. (Conventional example 1).

Another conventional technique is disclosed in Japanese Patent Application Laid-Open No. 9-3
No. 891, there is a fixed eccentric weight and a movable eccentric weight, and these weights are symmetrically positioned with respect to the rotation axis, and a reference state of zero excitation force and movable The eccentric weight can be adjusted from the reference state to the state where the maximum vibrating force is rotated by an acute angle θ. Work can be performed (conventional example 2).

[0010]

However, in the above-mentioned prior art example 1, since it can be operated only by a selected vibrating force of 0 degree or 180 degrees or less, one of the two drive motors is used. The change in the excitation force between the minimum excitation force when rotating while pushing the other and the maximum excitation force when rotating while pulling the other with the other drive motor is controlled only by the drive motor. It is difficult to perform, and it is difficult to change the vibrating force smoothly. In addition, since the excitation force cannot be adjusted from the minimum to the maximum excitation force, the work is performed only with the maximum excitation force determined in advance by the pile driving operation conditions such as the soil type and the pile type. Depending on the conditions, large vibrations may occur.

In the second prior art, since the weight is to be adjusted within an acute angle range, the adjustment range of the vibrating force is narrow. It is difficult to respond to the demand for driving force. Moreover, means for rotating the movable eccentric weight to adjust the vibrating force is not clearly described.

[0012]

Therefore, in order to solve the above-mentioned problems, the invention according to the present application provides a constant-speed weight and an adjustment weight on a drive shaft and a driven shaft. Operate with the weights facing each other and minimize the vibrating force (moment), and adjust the relative angle of the adjusting weight to the constant-speed weight in normal operation to minimize the vibrating force. To the maximum vibration force.

As described above, the vibrating force of the weight can be arbitrarily adjusted from a minimum to a maximum so that the weight can be started quietly with the vibrating force minimized, and the rated rotation speed of the driving machine can be reduced. When the work reaches the maximum vibrating force, the work can be performed by arbitrarily adjusting the vibratory force up to the maximum vibrating force. At the end of the work, the vibrating force can be minimized to stop the operation quietly. Thereby, the work which does not generate a large vibration at the time of starting / stopping can be performed. In addition, it is possible to arbitrarily adjust the vibrating force according to the load.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The invention according to this application relates to a drive shaft that is driven to rotate by a predetermined drive unit, a driven shaft that is driven by the drive shaft via a link device that transmits the rotation drive, A fixed first unbalanced weight, a second unbalanced weight rotatably provided around the drive shaft in the axial direction, and driven to rotate by the driven shaft; and a third unbalanced weight fixed to the driven shaft.
An unbalanced weight, and a fourth unbalanced weight rotatably provided around the driven shaft in the axial direction and being rotationally driven by the drive shaft, wherein the link device is provided on the drive shaft. Input gear, an output gear provided on the driven shaft, a first intermediate gear meshed with the input gear, a second intermediate gear meshed with the first intermediate gear and the output gear, and an input gear and a first intermediate gear. A first link member rotatably supporting the rotating shaft and connecting them, a second link member rotatably supporting the rotating shafts of the first intermediate gear and the second intermediate gear and connecting them, A third shaft in which the rotation shafts of the output gear and the second intermediate gear are rotatably supported and connected to each other.
By rotating the link member and the third link member along the rotation direction of the output gear to rotate the driven shaft,
Link angle adjusting means for generating a phase difference of a relative rotation angle between the unbalanced weight and the second unbalanced weight with respect to the fourth unbalanced weight and the first unbalanced weight, respectively. Thereby, the adjusting weight constituted by the second and third unbalanced weights is rotated to a position opposed to the constant speed weight constituted by the first and fourth unbalanced weights, and both the weights are moved. If you start in a balanced state, there will be no large vibration,
If the relative weight of the adjusting weight is adjusted so that the adjusting weight becomes the maximum centrifugal force by gradually rotating the adjusting weight after reaching the rated rotation speed, the vibration of the maximum vibrating force can be generated. Since the adjustment weight is rotated by the link mechanism, by controlling the link mechanism, if the fixing weight is fixed at an arbitrary vibration force position, an arbitrary value between the minimum vibration force and the maximum vibration force can be obtained. Vibration force can be generated. If this minimum vibrating force can be adjusted to a state of zero vibrating force, starting and stopping of zero vibrating force can also be performed.

The link device is connected to an input gear provided on a drive shaft to which a constant speed weight is fixed, an intermediate gear meshing with the input gear, and a driven shaft meshing with the intermediate gear and fixing an adjustment weight. The output gear provided, a link member connecting these gears, and link angle adjusting means for rotating the link member can easily adjust the relative angle of the rotating adjustment weight with respect to the constant speed weight. A link device that can be changed can be configured.

The constant-speed weight is composed of an unbalanced weight fixed to the drive-side shaft and an unbalanced weight provided on the driven-side shaft driven by the unbalanced weight. If the weight is composed of an unbalanced weight fixed to the driven-side shaft and an unbalanced weight provided on the drive-side shaft driven by the unbalanced weight, the weight is rotating. A two-axis type that can adjust the relative angle between the constant weight and the adjustable speed weight by rotating the adjusting weight, and can adjust the centrifugal force arbitrarily within the range of the maximum vibrating force due to all unbalanced weights Can be configured.

An approximately 90-degree unbalanced weight, which is fixed to the drive-side shaft, and an approximately 90-degree, unbalanced weight provided to the driven-side shaft driven by the unbalanced weight. Consisting of
The adjusting weight is composed of an approximately 90-degree unbalanced weight fixed to the driven-side shaft and an approximately 90-degree unbalanced weight provided on the driving-side shaft driven by the unbalanced weight, The adjusting weight adjusting rotation angle of the link device is in a range of approximately 90 degrees between a position where the constant speed weight and the adjusting weight face each other and a position where the constant speed weight and the adjusting weight are adjacent to each other. If configured to be arbitrarily adjustable with
In a shaft-type vibrating force generator, any range from the minimum vibrating force with both weights facing each other to the maximum vibrating force with an unbalanced weight of approximately 180 degrees with both weights adjacent to each other The vibrating force can be adjusted.

[0018]

[0019]

Furthermore, if the link device is provided with control means for detecting a load acting on the driving machine and adjusting the rotation angle of the adjusting weight according to the load, the load acting on the driving machine can be improved. Therefore, the vibrating force of the unbalanced weight can be adjusted according to the above, so that a stable operation can be performed while avoiding an overload of the driving machine.

[0021]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the invention according to the present application will be described below with reference to the drawings. FIG. 1 shows a first embodiment of the invention according to this application.
FIG. 3 is a cross-sectional view in plan view showing a main configuration of the vibration generating device according to the embodiment, and a driving machine is shown on a side portion for explanation. FIG. 2 is a side view showing a link device of the vibrating force generator, FIG. 3 is a schematic diagram showing an example of an unbalanced weight rotating position of the vibratory force generating device, and FIG. FIG. 4B is a schematic diagram illustrating zero force, (b) a maximum vibration force, and (c) an intermediate vibration force. This first
The embodiment shows a two-axis vibrating force generator.

As shown, a first support shaft 2 serving as a drive shaft and a second support shaft 3 serving as a driven shaft are provided side by side on a casing 1, and unbalanced weights 4A and 5B are provided on the first support shaft 2. The second support shaft 3 is provided with unbalanced weights 4B and 5A. These unbalanced weights 4A, 4B, 5A, 5B rotate left and right in opposite directions, and as shown in FIG.
A maximum excitatory force (eccentric moment) is generated when A and 5B and 4B and 5A are adjacent to each other and are directed vertically, and are canceled when turned to the left and right.
A first gear 6 and a second gear 7 provided on both support shafts 2 and 3;
The third gear 8 and the fourth gear 9 mesh with each other to rotate the unbalanced weights 4A, 5B and 4B, 5A in opposite directions.

In this embodiment, the unbalanced weights 4A, 4B,
5A and 5B are all formed in a substantially 90-degree sector shape,
It is configured to balance the weight at the opposing position, and to form a semicircular unbalanced weight at the adjacent position.
These unbalanced weights 4A, 4B, 5A, 5B are rotatable around the second support shaft 3 and the unbalanced weight 4A in which the central mounting portion 4a is fixed to the first support shaft 2 with the key 2a. And an unbalanced weight 4B provided on the second support shaft 3 constitutes a constant-speed weight, and the mounting portion 5a is formed on the second support shaft 3 so as to sandwich the mounting portion 4a.
An unbalanced weight 5A fixed by a key 3a and an unbalanced weight 5B rotatably provided around the first support shaft 2 constitute an adjustment weight. These unbalanced weights 4A, 4B
The first gear 6 fixed to the first support shaft 2 with the key 2b and the second gear 7 provided on the unbalanced weight 4B mesh with each other to transmit power, and the unbalanced weights 5A and 5B The third gear 8 and the unbalanced weight 5B fixed to the second support shaft 3 by the key 3b
The power is transmitted by meshing with a fourth gear 9 provided on the second gear.

Therefore, the constant speed weight 4A and the adjustment weight 5
B, the constant speed weight 4B and the adjustment weight 5A rotate in the same direction, and the weights 4A and 5B and the weights 4B and 5A are rotated in opposite directions.

The first and second support shafts 2 and 3 are driven by driving a pulley 10 provided on the first support shaft 2 around a pulley 12 of a drive motor 11 provided on the casing 1. It has been carried out by driving a belt 13, from the first support shaft 2 driven by the drive motor 11, the second supporting shaft 3 via the linkage L ₁ is driven.
In this embodiment, it is driven by one drive motor 11.

[0026] The linkage L _1, as shown in FIG. 2, a plurality of gears, a plurality of link members arranged between these gears is composed of the link member with the link angle adjusting means for rotating ing. The gear includes an input gear 14 provided on the support shaft 2 protruding from the casing 1, a first intermediate gear 15 meshed with the input gear 14, and a second intermediate gear 16 meshed with the first intermediate gear 15. And an output gear 17 provided on the support shaft 3 that meshes with the second intermediate gear 16 and protrudes from the casing 1. The link member includes the input gear 14 and the first intermediate gear 1.
5, a first link member 18 provided between the first intermediate gear 15 and the second intermediate gear 16, a second link member 19 provided between the first intermediate gear 15 and the second intermediate gear 16, And the third link member 20 provided therebetween. A cylinder 21 serving as a link angle adjusting means is provided at a predetermined position of the third link member 20. By expanding and contracting the cylinder 21, the first to third link members 18, 19, and 20 are moved to predetermined positions. It is configured to rotate in the direction.

In the case of this embodiment, each unbalanced weight 4A, 4
Since B, 5A, and 5B are formed in a substantially 90-degree sector shape, if the adjustments 5A and 5B are rotated at a relative angle of approximately 90 degrees with respect to the constant-speed weights 4A and 4B, the sector shapes face each other. An arbitrary relative angle difference (rotational phase difference) can be generated between the position and the position where the sector is adjacent to and substantially at 180 degrees. This relative angle difference is caused by extending the cylinder 21 and
The rotation of the link member 20 causes the axial centers of the second intermediate gear 16 and the first intermediate gear 15 to move. In the case of this embodiment, if the rotation angle α of the first link member 18 on the input side is rotated by an angle of about 30 degrees, the output gear 17 has a relative angle difference β of about 160 degrees with respect to the input gear 14. Is configured to occur.

Therefore, by expanding and contracting the cylinder 21, the axial positions of the first intermediate gear 15 and the second intermediate gear 16 are changed, and the output gear 17 with respect to the input gear 14 is changed.
And a phase difference of "advance" or "lag" in the relative rotation angle of the second support shaft 3 with respect to the first support shaft 2 rotating at a fixed position.

Moreover, according to this configuration, the first support shaft 2
, Input gear 14, intermediate gears 15, 16 and output gear 17
While power is being transmitted to the second support shaft 3 via
If the third link member 20 is rotated by expanding and contracting the cylinder 21, a phase difference occurs in the relative rotation angle between the support shaft 2 and the support shaft 3. It is possible to cause the weights 5A and 5B to “lead” or “delay”. In other words, even during power transmission, the cylinder 2
1 by controlling the amount of expansion and contraction of the weights 4A and 4B.
The relative rotation angle (rotational phase difference) between the control weights 5A and 5B can be arbitrarily adjusted.

At this time, when the cylinder 21 is fixed and the link members 18, 19, 20 are restrained, the constant speed weights 4A, 4
The phase between B and the adjustment weights 5A and 5B does not change, and only when the cylinder 21 is extended and contracted to rotate the link members 18, 19 and 20, the adjustment weights for the constant speed weights 4A and 4B are adjusted. The phases of 5A and 5B will change.

By adjusting the relative rotation angle of the second support shaft 3 to adjust the phase difference between the constant-speed weights 4A, 4B and the adjustment weights 5A, 5B in this manner, all the unbalanced weights 4A, 4A, 4B, 5
The vibrating force by A and 5B can be adjusted arbitrarily.

The configuration of the gears 14 to 17 may be appropriately determined according to the specifications of the vibrating force generator. The first intermediate gear 15 and the second intermediate gear 16 are configured to be swingable along a guide groove provided in a casing (not shown). Reference numeral 22 denotes a bearing that supports the support shafts 2 and 3 on the casing 1.

The vibrating force generator V configured as described above
According to ₁ , as shown in FIGS. 3 (a) to 3 (c), a schematic diagram showing an example of the unbalanced weight rotating position is shown. Vibration force can be generated.

[0034] That is, when startup, (a), the linkage L ₁ of the third link member in the cylinder 21 2
By turning 0, the adjustment weights 5A and 5B are turned to the counter-constant weight side to be in a state of facing the constant-speed weights 4A and 4B. By driving the driving motor 11 in this state, the first support shaft 2 via the V-belt 13 is driven, the second supporting shaft 3 via a linkage L ₁ from the first support shaft 2 opposite Rotated in the direction. At this time, the force for rotating the constant-speed weights 4A, 4B and the adjustment weights 5A, 5B in the opposite direction is substantially zero in the vibrating force when both weights are balanced at the opposing positions (the “minimum vibrating force” in this embodiment). Force)), all unbalanced weights 4A, 4B,
5A and 5B can be driven. In addition, since it can be rotated without generating vibration, there is no adverse effect on the surrounding environment.

When the drive motor 11 reaches the rated rotation speed, the third link member 20 is rotated in a predetermined direction by the cylinder 21 so that the state shown in FIG.
As shown in the figure, the adjustment weights 5A and 5B and the constant speed weights 4A and 4
B is rotated to be adjacent. That is, by adjusting the amount of expansion and contraction of the cylinder 21, the weights 5A and 5A are adjusted.
B is made to be adjacent to the constant speed weights 4A, 4B so that the unbalanced weights 4A, 4B, 5A, 5B having a semicircular shape as a whole exert the maximum vibrating force.

The constant-speed weight 4 rotated in this manner
Since the first support shaft 2 and the second support shaft 3 are rotated in opposite directions to each other, the unbalanced weights 4A, 5B and 4B, 5A are in the same direction. A large vertical vibrating force is generated in the vertical direction facing the.

Moreover, in the invention according to this application, the advance or delay angle of the second support shaft 3 is arbitrarily adjusted by adjusting the amount of expansion and contraction of the cylinder 21 of the link device L ₁ , so that Since the relative angle can be arbitrarily maintained, for example, as shown in FIG.
It is also possible to easily stop 5B at approximately the middle position of the adjustment range and make the excitation force approximately half of the maximum excitation force. That is, anywhere between the maximum excitation force the linkage L ₁ in regulating weight 5A, and 5B constant speed Jutsumu 4A, Keeping adjusted to 4B and any relative angle, from the state of the minimum exciting force It is possible to easily adjust the vibrating force.

If the vibrating force can be adjusted arbitrarily as described above, even if the ground into which the pile is to be driven changes from a soft ground to a hard ground, as in a vibrating pile driving machine, for example, The driving operation can be continued by adjusting the vibrating force so that the load of the motor 11 is not overloaded, and the pile driving operation can be continued with high work efficiency without interrupting the operation.

In this case, a detector for detecting the load from the current of the drive motor 11 and the like is provided, and if the third link member 20 is rotated by the cylinder 21 in accordance with the signal of the detector, the overdrive of the drive motor 11 It is also possible to easily perform control so as to prevent the load, and by performing such feedback control, it is possible to perform a pile driving operation in which a stable operation of the driving machine can be performed.

At the time of stop, the relative angle of the second support shaft 3 is adjusted by rotating the third link member 20 with the cylinder 21 from the state shown in (b) or (c).
As shown in (a), the adjusting weights 5A and 5B are
A and 4B are turned to face each other. In this state, the unbalanced weights 4A and 5B, 4B and 5
A is for a minimum vibratory force of approximately vibratory force zero balanced, it is possible to stop the vibratory force generator V ₁ without causing vibration.

FIG. 4 shows a reference relating to the first embodiment described above .
It is a side view which shows the link apparatus of the vibrating-force generator which concerns on an example . This reference example shows a four-axis type vibrating force generator, which is provided in the same casing as that of the first embodiment, but explains only the configuration relating to the link device and the unbalanced weight, Descriptions of other configurations are omitted. The same components as those of the first embodiment will be described with the same reference numerals.

As shown in the figure, in this embodiment , a first support shaft 23 serving as a drive shaft and a second support shaft 24 serving as a driven shaft are arranged side by side in the upper part, and these two lower support shafts serve as driven shafts. third support shaft 25 and the fourth support shaft exciting force generating device V ₂ of 26 is juxtaposed 4-shaft is constituted. The first and second support shafts 23 and 24 are provided with constant speed weights 27 and 28, respectively, and the third and fourth support shafts 25 and 26 are provided with adjustment weights 29 and 30, respectively. These unbalanced weights 2
7, 28, 29, 30 are formed in a semicircular shape of approximately 180 degrees, and the respective unbalanced weights 27, 28, 29,
30 is fixed by keys 23a, 24a, 25a, 26a provided on the support shafts 23, 24, 25, 26.

The first gear 31 provided on the first support shaft 23
And the second gear 32 provided on the second support shaft 24 mesh with each other, and the third gear 33 provided on the third support shaft 25 and the fourth gear 34 provided on the fourth support shaft 26 mesh with each other. The left and right unbalanced weights 27, 30 and 28, 29 are configured to rotate in opposite directions. Then, the second gear 32
If the link device L ₂ is provided between the third gear 33.

The link device L ₂ includes a fifth gear 35 meshing with the second gear 32, a sixth gear 36 meshing with the fifth gear 35 and meshing with the third gear 33, and a second gear 32. A first link member 37 for connecting the axes of the fifth gear 35, a second link member 38 for connecting the axes of the fifth gear 35 and the sixth gear 36, and an axis of the sixth gear 36 and the third gear 33. It comprises a third link member 39 for connecting between them, and a cylinder 21 as link angle adjusting means for rotating the third link member 39 around the third support shaft 25. The rear end of the cylinder 21 is supported by the casing 1.

Therefore, the V-belt 1 is
When the first support shaft 23 is driven via the third gear 3, the first gear 31 provided on the first support shaft 23, the second gear 32, the fifth gear 35, the sixth gear 36, the third gear 33, 4 gears 3
4 is transmitted to the first support shaft 23 to the fourth support shaft 2.
The vibrating force can be generated in the vertical direction by the unbalanced weights 27, 28, 29, 30 provided in 6.

In the case of this reference example , since it has a four-axis configuration,
Since the upper unbalanced weights 27 and 28 can be separately configured as a constant speed weight and the lower unbalanced weights 29 and 30 can be separately configured as an adjustment weight, the link device L ₂ can be compared with the first embodiment. The number of gears can be reduced to cause "advance" or "lag" in the rotation angle of the adjusting weights 29, 30 with respect to the constant-speed weights 27, 28, within the range from the minimum vibration force to the maximum vibration force. the vibratory force generator V ₂ that can adjust the vibratory force to any can be a simple configuration in.

In this embodiment , the fifth gear 3
5, the guide groove in which the shaft of the sixth gear 36 swings
And may be configured to support it.

With the vibrating force generator V _{2 of} the reference example configured as described above, the third link member 39 is rotated by the cylinder 21 at the time of start-up or the like, as in the first embodiment. The first link member 37 is rotated at a predetermined rotation angle α by moving the axis positions of the fifth gear 35 and the sixth gear 36, and a predetermined relative angle difference β is generated by the third gear 33. Is configured to occur. Accordingly, the relative rotation angle of the third gear 33 with respect to the second gear 32 is “lagged” or “advanced”.
And the constant speed weights 27 and 28 and the adjustment weights 29 and 30
Are positioned so as to face each other, the total weights 27, 28,
With the minimum vibrating force ("zero vibrating force" in this embodiment) due to 29 and 30, it is possible to start and stop without generating vibration in the surroundings.

When the drive motor 11 reaches the rated speed, the third link member 39 is rotated by the cylinder 21 so that the adjusting weights 29, 30 are directed in the same direction as the constant speed weights 27, 28. By adjusting, the total unbalanced weight 27,
Large vibration can be generated by the maximum vibrating force generated by 28, 29, 30. When adjusting the vibrating force, if the cylinder 21 is fixed and the link members 37, 38, 39 are restrained, the phases of the constant-speed weights 27, 28 and the adjustment weights 29, 30 do not change, and the cylinder 21 The link member 3
Only when rotating 7, 38, 39, the constant speed weight 2
Since the phases of the adjustment weights 29 and 30 with respect to the positions 7 and 28 are changed, an arbitrary excitation force can be generated by stopping at an arbitrary position between the minimum excitation force and the maximum excitation force. Moreover, the adjusting weights 29, 3 by the cylinder 21
0 of rotation, since it is possible to rotate in the state of rotating the unbalanced weight 27, 28, 29, 30, without stopping the vibratory force generator V _2, any excitation Can be set to power.

Also in this embodiment , a detecting means for detecting the load from the current value of the drive motor 11 and the like is provided, and the rotation angle of the third link member 39 is controlled by a control device or the like in accordance with a signal from the detecting means. By adjusting the vibrating force, it is possible to control the vibrating force according to the load so that the drive motor 11 is not always overloaded, and to protect the drive motor by controlling the load of the drive motor 11 constantly. Becomes possible. This means that, for example, in the case of a stakeout operation, preferable output control can be performed according to a change in the ground, and a stable stakeout operation can be performed.

In the embodiment and the reference example , the two-axis type vibrating force generator V ₁ and the four-axis type vibrating force generator V _{2 are used.}
Although the embodiment has been described, the invention according to this application can be applied to a vibrating force generating device having another shaft configuration, and is not limited to the shaft configuration.

In the above embodiment and the reference example , the minimum vibrating force is substantially zero, but may be determined as appropriate according to the use conditions, the machine used, and the like.

[0053]

The invention according to this application is implemented in the form described above, and has the following effects.

If the adjustment weight is started by rotating the adjustment weight to a position facing the constant-speed weight and maintaining the balance, no large vibration is generated, and the adjustment weight is gradually moved after reaching the rated rotation speed. By rotating to the maximum centrifugal force position, vibration of the maximum vibrating force can be generated, and since the rotation of this adjusting weight is performed by the link device, if this link device is controlled, It is possible to work with any vibrating force from the state of the minimum vibrating force to the maximum vibrating force, and to generate any vibrating force according to changes in working conditions, etc. It is possible to provide a force generator. This makes it possible to easily perform a work in which the vibrating force is arbitrarily adjusted according to a change in work conditions or the like.

The link device includes an input gear provided on a drive shaft, an intermediate gear meshing with the input gear, an output gear meshing with the intermediate gear, a link member connecting these gears, and rotating the link member. With the link angle adjusting means, it is possible to configure a link device that can easily change the phase angle with the constant speed weight by rotating the rotating adjusting weight at an arbitrary angle. By controlling, it is possible to easily adjust to an arbitrary vibration generating force.

Further, the constant-speed weight is composed of an unbalanced weight fixed to the drive-side shaft and an unbalanced weight provided to the driven-side shaft.
If the adjusting weight is composed of an unbalanced weight fixed to the driven side shaft and an unbalanced weight provided to the driving side shaft, the adjusting weight is rotated while the weight is rotating. Thus, it is possible to configure a two-axis type vibrating force generating device capable of arbitrarily adjusting the vibrating force.

The constant-speed weight is composed of an approximately 90-degree unbalanced weight fixed to the drive-side shaft and an approximately 90-degree unbalanced weight provided to the driven-side shaft. An unbalanced weight of approximately 90 degrees fixed to the driven side shaft and an unbalanced weight of approximately 90 degrees provided on the drive side shaft. If it is configured to be arbitrarily adjustable in a range of approximately 90 degrees between the opposing position and the adjacent position, 2
It is possible to configure a vibrating force generating device that is axial and has a wide range of adjusting the vibrating force.

[0058]

[0059]

Further, if these link devices are provided with control means for adjusting the turning angle of the adjusting weight according to the load acting on the driving machine, stable operation can be performed while avoiding overload of the driving machine. Therefore, it is possible to configure a vibrating force generating device with high working efficiency.

[Brief description of the drawings]

FIG. 1 is a sectional view in plan view showing a main configuration of a vibrating force generating device according to a first embodiment of the present invention.

FIG. 2 is a side view showing a link device of the vibration generating device shown in FIG.

FIGS. 3A and 3B are schematic diagrams illustrating an example of a rotational position of the unbalanced weight of the vibrating force generating device illustrated in FIG. 1; FIG. 3A is a vibrating force of zero, FIG. FIG. 3 is a schematic diagram showing an intermediate vibrating force.

FIG. 4 is a side view showing a link device of the vibration generating device according to the reference example of the invention according to the present application.

FIG. 5 is a cross-sectional view in plan view showing a conventional vibrating force generator.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Casing 2 1st support shaft 3 2nd support shaft 4A, 4B Constant-speed weight 4a Attachment part 5A, 5B Adjustable weight 5a Attachment part 6 1st gear 7 2nd gear 8 3rd gear 9 4th gear 11 Drive motor Reference Signs List 14 input gear 15 first intermediate gear 16 second intermediate gear 17 output gear 18 first link member 19 second link member 20 third link member 21 cylinder 23 support shaft 23 first support shaft 24 second support shaft 25 third support Shaft 26 Fourth support shaft 27, 28 Constant speed weight 29, 30 Adjusting weight 31 First gear 32 Second gear 33 Third gear 34 Fourth gear 35 Fifth gear 36 Sixth gear 37 First link member 38 First 2 link member 39 3rd link member α Rotation angle β Relative angle difference L ₁ , L ₂ link device V ₁ , V ₂ Exciting force generator

Continuation of front page (56) References JP-A-61-245876 (JP, A) JP-A-56-28932 (JP, A) JP-A-8-131952 (JP, A) JP-A-7-145605 (JP, A) JP-A-4-108913 (JP, A) JP-A-7-31934 (JP, A) JP-A-4-9437 (JP, U) JP-A-6-14209 (JP, U) Field surveyed (Int.Cl. ⁷ , DB name) B06B 1/16

Claims (3)

(57) [Claims] A driving shaft rotatably driven by a predetermined driving machine; a driven shaft driven by the driving shaft via a link device for transmitting the rotation driving; and a first unbalanced weight fixed to the driving shaft. A second unbalanced weight provided rotatably around the drive shaft in the axial direction and driven to rotate by the driven shaft; a third unbalanced weight fixed to the driven shaft; A fourth unbalanced weight that is rotatably provided around the axial direction and that is rotatably driven by the drive shaft, wherein the link device is provided on an input gear provided on the drive shaft and on a driven shaft. The output gear, the first intermediate gear meshed with the input gear, the second intermediate gear meshed with the first intermediate gear and the output gear, and the rotation shafts of the input gear and the first intermediate gear are rotatably supported. And a first link member connecting these, a first intermediate gear and A second link member rotatably supporting the rotating shaft of the second intermediate gear and connecting them, and a third link rotatably supporting the rotating shafts of the output gear and the second intermediate gear and connecting them. The third unbalanced weight and the second unbalanced weight are respectively rotated by rotating the driven shaft by rotating the member and the third link member along the rotation direction of the output gear, and the fourth unbalanced weight and the third unbalanced weight are respectively rotated. First
A vibrating force generator comprising: link angle adjusting means for generating a phase difference of a relative rotation angle with respect to the unbalanced weight. 2. The vibration generating device according to claim 1, wherein the first unbalanced weight, the second unbalanced weight, the third unbalanced weight, and the fourth unbalanced weight have an angle of about 90 degrees. The link angle adjusting means includes a first unbalanced weight and a second unbalanced weight, and a third unbalanced weight and a fourth unbalanced weight. The position, the first unbalanced weight and the second unbalanced weight are adjacent to each other,
The third link member can be rotated so as to be arbitrarily adjusted within a range of approximately 90 degrees between the position where the unbalanced weight and the fourth unbalanced weight are adjacent to each other. Exciting force generator. 3. The vibrating force generating device according to claim 1, wherein a load acting on the driving device is detected in the link device, and the second unbalanced weight and the third unbalanced weight are determined according to the load. A vibrating force generating device comprising a control means for adjusting a rotation angle of a weight.