JPH09323068A - Method for controlling phase difference of eccentric weight for excitation and mechanism for controlling the same phase - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make it possible to execute the adjustment of the phase difference of a movable eccentric weight to a stationary eccentric weight by improving an exciting machine of a structure obtd. by fixing the stationary eccentric weight to a common revolving shaft and mounting the movable eccentric weight turnably relative to the common revolving shaft. SOLUTION: The movable eccentric weight 51 is pressed in the direction where its phase is advanced by pressing a phase difference control spring 53 as shown in Fig. A. Its phase advance angle is limited by a stopper 61 and the overall eccentric moment of both eccentric weights is zero in the Fig. If the movable eccentric weight 51 is lightly braked while the stationary eccentric weight 49 is rotationally driven in an arrow R direction as shown in Fig. B, the movable eccentric weight deflects the phase difference control spring 53 to delay the phase and attains the max. state of the overall eccentric moment, thereby generating exciting force.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a phase difference control method created for controlling the phase difference between a fixed eccentric weight and a movable eccentric weight provided in a rotary exciter for driving a pile. The present invention relates to a phase difference control mechanism and can be applied to rotary exciters other than those for pile driving.

[0002]

2. Description of the Related Art A vibration device (vibrator) used for civil engineering construction generally has a structure in which a plurality of pairs of rotary shafts having eccentric weights are arranged in parallel. According to such a configuration, the centrifugal excitation force of the eccentric weight rotating in the opposite direction can be added in the desired direction and can be canceled in the unnecessary direction. When the pile driving work is performed using the above-described vibrator, the prevention of vibration pollution and the prevention of noise pollution are important problems. Next, technical problems relating to vibration pollution will be described with reference to FIGS.

FIG. 4 is a schematic diagram for explaining vibration pollution in a pile driving operation. This figure shows a state in which the vibration device 6 is suspended by the crane boom 5, the upper end of the pile 7 is grasped by the chuck 6a of the vibration device 6, and the pile 7 is vibrated and placed in the ground. Is drawn. When the lower end of the pile 7 is brought into contact with the ground surface and the pile driving work is started, when the vibrating device 6 is fully operated from the beginning, the surface wave a generated on the ground surface at the pile driving point is hardly attenuated and the neighboring private house 8 Because it reaches to, it causes the problem of vibration pollution. Here, if the exciting force of the vibration device 6 can be arbitrarily adjusted, the pile driving work may be started while giving a slight vibration in addition to the weight of the pile 7, and the vibration may be gradually strengthened after driving for several meters. .

If the hypocenter position corresponding to the lower end of the pile 7 becomes deeper, the ground wave b is attenuated while reaching the private house 8, so that vibration pollution is slight.

FIG. 5 is a table showing changes in the vibration frequency at the time of starting and stopping the operation of the vibration device. The horizontal axis represents time. Start of operation time t _0, between time t ₁ to reach the rated operating state, frequency rises sharply as shown by arrow c. During the above-mentioned frequency increase, the natural frequency n ₁ of the ground and the natural frequency n ₂ of the crane boom are passed. However, since the rotation speed increasing period T ₁ at the start of operation is generally short (for example, about 3 seconds), the problem of resonance when the vibration frequency of the vibration device matches the natural frequency can be usually ignored. it can. However, from the time point t ₂ when the motor (not shown) of the vibration device 6 is stopped to the time point t ₃ when the rotation shaft stops, the rotation shaft continues to rotate due to inertia and gradually decelerates as shown by the arrow d. .

Since the rotation speed reduction period T ₂ is a relatively long time (for example, about 50 seconds), when the natural frequency n ₂ of the crane boom is passed on the way, the crane boom resonates and is damaged. There is a risk of suffering. Further, when passing through the natural frequency n ₁ of the ground, vibration of the ground may cause vibration pollution. It stops the energization of the motor in said time t _2, the if it is possible to zero the vibratory force by changing the rotation phase of the rotary weight of the vibration device, issues resonance during shutdown operation of the vibration device Can be prevented.

Next, looking at the amount of energy supplied to the vibrating device, the vibrating device 6 from the time t ₀ to t ₁ described above.
If the speed is increased while the vibration is generated by the eccentric weight (not shown) of the vibration device while the rotation speed of the vibration device increases, a large-capacity motor and a large-capacity power supply facility are required to drive this. . In this case, if the eccentric weight of the vibration device is changed to a zero phase to start the operation in a state where the vibration force is zero, and if the vibration force can be exerted after reaching the rated rotation speed,
It is economical because the motor capacity and power supply capacity can be reduced.
This is because after the rated speed is reached, it is not necessary to store further rotational energy in the rotary member, and the operation can be continued by supplementing the energy for compensating for the vibration damping.

[0008] In view of the above circumstances, an adjustment technique for increasing or decreasing the vibrating force of a vibrator has been developed and is known. Next, the principle of increasing or decreasing the exciting force of the exciter will be described. FIG. 6 is a view for explaining a known technique of changing an exciting force by a combination of two eccentric weights, and (A) shows two eccentric weights exhibiting maximum exciting force. A schematic diagram showing a state, (B) a schematic diagram showing a state where the exciting force is medium, (C) a schematic diagram showing a state where the exciting force is slightly small, (D) a state where the exciting force is zero It is a schematic diagram showing. Of the two eccentric weights shown in FIG. 6A, 9 is a fixed eccentric weight fixed to the rotating shaft 2B ', and 10 is rotatable relative to the rotating shaft 2C'. It is a movable eccentric weight. In the present invention, the fixed eccentric weight is an eccentric weight that is locked to rotate relative to the rotary shaft, and is a member that rotates together with the rotary shaft, so fixing does not mean stationary. . The relative positions of the two eccentric weights 9 and 10 in FIG. 6A are in a state where the phase difference is zero. Therefore, in the state of FIG. 6A, the two eccentric weights 9 and 10 are
When they are synchronously rotated at B 'and 4C', a vibrating force is generated. In the state shown in FIG. 6D, the center of gravity of each of the two eccentric weights 9 and 10 is always the reference line MM (the two rotation shafts 2 and 10).
Since it is located symmetrically with respect to the perpendicular bisector of the line connecting B 'and 2C', the vertical excitation force is zero. For convenience of description, a state in which the phase difference between the two eccentric weights is 180 degrees and the total eccentric moment of the two eccentric weights is zero as shown in FIG. 6D is named a reference state. FIG. 6 (B),
Since (C) is an intermediate state between the above (A) and (D), a vertical vibration force smaller than that in the case of FIG. (A) and larger than that in the case of (D) is generated. And (B)
Since the figure is closer to the state of FIG. (A) than the figure of (C), if the vibrating force is listed in descending order, (A), (B),
(C) and (D). In order to show the principle of the vibration force increase / decrease control in FIG. 6 described above, the two rotary shafts 2B ′ and 2C ′ are depicted as being synchronously rotated by the synchronous rotary gears 4B ′ and 4C ′, but the structure is simple. Therefore, it is possible to dispose two eccentric weights on one rotating shaft. FIG. 7 is a schematic view of a mechanism in which a fixed eccentric weight is fixed to a common rotation shaft and a movable eccentric weight can adjust a relative rotation angle position with respect to the common rotation shaft.

The fixed eccentric weight 9 is fixed to the rotary shaft 2 and rotates together. The movable eccentric weight 10 can be adjusted by changing the mounting angle position with respect to the rotary shaft 2 as indicated by the arc arrows α-β, and can maintain the adjusted state. The state depicted in FIG. 7 is shown in FIG.
The excitation force is moderate, corresponding to the state shown in (B).
From this state, if the movable eccentric weight is rotated and fixed in the direction of the arrow α, the state becomes closer to the state of FIG. Further, when it is rotated in the direction of the arrow β, the state of FIG. 6 (A) is approached and the excitation force increases. The exciting force is adjusted as described above. 8 shows the principle as shown in FIG. 7 above.
FIG. 11 is a perspective view showing a conventional example of a vibration oscillating machine in which a fixed eccentric weight and a movable eccentric weight are arranged with respect to a common one axis so that an oscillating force can be increased or decreased. The two rotating shafts 2A and 2B are arranged in the horizontal direction and are synchronously rotated in the opposite direction (clockwise and counterclockwise) by the drive pulley 11 and the synchronous rotation transmission gears 4A and 4B. This is to offset the vibration force. The fixed eccentric weight 9A is fixed to the rotary shaft 2A. The movable eccentric weight 10A is rotatably supported by the rotary shaft 2A, and the rotation of the fixed eccentric weight 9A can be adjusted and fixed. That is, the movable eccentric weight 10A has a plurality of adjusting female screw holes (only one is shown in this figure) 12
Is being worn. Insert the set bolt 14 into the female screw hole 12
Screw it in and tighten it with a hexagon wrench 15.
When the rotation stop is applied, the angular position of the movable eccentric weight 10A is fixed. FIG. 9 is a view for explaining the relationship between the rotary shaft, the fixed eccentric weight, and the movable eccentric weight in the vibration oscillating machine including the conventional adjusting mechanism shown in FIG. 8 (A). FIG. 3A is an external perspective view drawn by partially cutting, and FIG. 3B is a schematic view drawn as seen in a direction parallel to the rotation axis.
Reference numerals 23a, 23b, and 23c shown in FIG. 9A are scales, and the unit is kg · cm. By aligning the scale and screwing the set bolt, as shown in Fig. 9 (B),
The movable eccentric weight has three angular positions, 10a, 10b,
As shown in 10c, the vibration force is changed by relatively rotating.
The exciter according to the related art shown in FIGS. 7 to 9 can increase / decrease the exciting force as described above.

[0010]

If an attempt is made to increase / decrease the exciting force in the conventional exciter described with reference to FIGS. 7 to 9, it will be easily understood from the structure shown in FIG. As described above, the operation is stopped, the knock pin 13 is pulled out, the set bolt 14 is pulled out, and the movable eccentric weight 10 is manually turned to make a scale (indicated by 23a to 2 in FIG. 9).
3c), the set bolt 14 must be screwed again and tightened, and the knock pin 13 must be used to prevent rotation.
In the conventional technique, the above-described operation is required to increase / decrease the exciting force. As already described with reference to FIG. 4, since the vibration generator 6 is attached to the upper end of the pile 7, after it is suspended by the crane boom 5 for adjustment,
The work of hoisting the crane again with the crane boom 5 and attaching it to the upper end of the pile 7 requires a lot of time and labor. 1
A fixed eccentric weight and a movable eccentric weight are attached to the central axis of rotation of the book, and in order to increase or decrease the excitation force while continuing the operation without stopping the operation, the configuration shown in FIG. Is effective. This technology was created by the present inventor and applied for separately, and is not known (Japanese Patent Application No. 7-236695).
Hereinafter, the invention is referred to as a prior invention.

FIG. 10 shows an exciter equipped with an embodiment of an eccentric weight oscillating force control mechanism according to the invention of the prior application, which is configured to carry out the oscillating force control method of the invention of the earlier application. FIG. 3 is a horizontal sectional view shown and schematically drawn. Depending on the case 1, two horizontal axes, that is, the A-system rotation shaft 21 and the B-system rotation shaft 2
2 are rotatably supported. An A system drive gear 23 is fixed to the A system rotary shaft 21 via a key 24. In FIG. 10, seven keys are drawn.
Although only one symbol is attached, the drawing of the key indicates that the key is fitted so that it cannot rotate relative to the rotation axis. And, the part where the figure of the key is not drawn shows that it is fitted so as to be relatively rotatable.

The A system driven gear 25 has the same number of teeth as the A system drive gear 23, and is rotatably fitted to and supported by the B system rotary shaft 22. Similarly, of the pair of gears of the B system having the same number of teeth, the B system drive gear 34 is fixed to the B system rotary shaft 22 so as not to be rotatable, and the B system driven gear 31 is the A system rotary shaft 21. Is rotatably fitted to and supported by. The A-system fixed eccentric weight 26 cannot rotate relative to the A-system rotation shaft 21,
The B-system movable eccentric weights 27 are relatively rotatably fitted and supported, and the B-system movable eccentric weights 27 are synchronously connected to the B-system driven gear 31.
They are integrally connected via 3 and rotate together. As a result, the B system movable eccentric weight 27 is rotated at the same rotational speed in the direction opposite to the B system rotary shaft 22. The B-system fixed eccentric weight 28 is fitted in and supported relative to the B-system rotary shaft 22 such that the B-system fixed eccentric weight 28 is relatively unrotatable and the A-system movable eccentric weight 29 is relatively rotatable. The A system movable eccentric weight 29 is integrally connected to the A system driven gear 25 via a synchronous connecting rod 30 and rotates together. As a result, the A system movable eccentric weight 29 is rotated at the same rotational speed in the direction opposite to the A system rotary shaft 21. The A system driven pulley 35 is attached to the A system rotary shaft 21.
And the A system drive pulley 38 is fixed to the A system drive motor Ma, and the winding transmission means 37 is wound around the A system driven pulley 35 and the A system drive pulley 38 to be transmitted. There is. A B-system driven pulley 36 is fixed to the B-system rotating shaft 22, and a B-system driving pulley 39 is fixed to the B-system driving motor Mb.
A winding transmission means 37 is wound around and is transmitted.

In order to perform a pile driving work using the apparatus of FIG. 10, (see also FIG. 5) at the work starting point o,
The B system drive motor Mb is actuated to start rotation at the minimum eccentric moment (minimum vibration force, vibration acceleration of about g), while increasing the rotation speed as indicated by arrow c, the ground peculiar ground motion number n ₁ and the crane. Passes the boom natural frequency n ₂ with the minimum eccentric moment. When the passage is completed, the B system drive motor Mb is de-energized or de-energized to
The system drive motor Ma is operated. In this case, the rotation speed (rotation speed) of the eccentric weight is equal to the vibration frequency of the generated vibration. When the number of rotations reaches the rated number of rotations (point i), the operation shifts to steady operation. In this state, the A system leads the maximum eccentric moment by advancing a certain angle as compared with the reference state, and the pile driving work is performed while exhibiting the maximum vibration force. This steady operation is
In the form in which the system pulls the system B, the system B follows with a certain angle delay. During this period of operation in the stationary state, the B system drive motor Mb may be deenergized. Also, B system is A
The electric energy may be supplied to the B-system drive motor Mb to the extent that it cannot catch up with the system. When the pile driving work is completed (point j), drive motors Ma and Mb of both A and B systems
And the electric braking is applied to the A-system drive motor Ma. As a result, the eccentric moment is minimized, and sequentially passes through the crane boom natural frequency n ₂ and the ground natural frequency n ₁ , decelerates as indicated by an arrow d, and stops (point m).

The present inventor applied for the invention of the earlier application shown in FIG. 10 and then carried out the industrial production of the invention, and further improved researches, particularly, repeated practical application tests, and as a result, the earlier application was completed. It was confirmed that the invention of (1) has a desired effect under practical conditions and contributes to the prevention of vibration pollution, and that there is still room for improvement. That is, (a) In order to control the drive motors of the A system and the B system, the operating states of both the A and B systems must be detected in detail. Moreover,
(B) Since the A-system drive motor and the B-system drive motor have to be controlled in association with each other based on the detection result, the control mechanism becomes complicated. If the control mechanism is complicated, the manufacturing cost is high, maintenance is difficult, and it is not easy to increase the operational reliability.

The present invention has been made in view of the above-mentioned circumstances, and is an improvement of the invention of the above-mentioned prior application, in which "the total eccentric moment of the eccentric weight is increased or decreased while operating continuously. To provide a technique capable of reliably and stably controlling the phase difference between a fixed eccentric weight and a movable eccentric weight with a simple mechanism without impairing the advantage of being able to control vibration force. With the goal.

[0016]

The basic principle of the present invention created to achieve the above object will be briefly described with reference to FIG. 1 corresponding to the first embodiment. (A) Rotating shaft 41 The fixed eccentric weight 49 and the movable eccentric weight 51 are attached to the
Rotatively driven in the direction (this is a known configuration). (B) As shown in (A) of the same figure, between the fixed eccentric weight 49 and the movable eccentric weight 51, the “movable eccentric weight 51
Is provided with a phase difference control spring 53 "that pushes in the direction of rotation.
As a result, the movable eccentric weight 51 is given a force in the phase advance direction as compared with the fixed eccentric weight 49. (C) The advance of the movable eccentric weight 51 is limited by the stopper 61. In the state shown in FIG. 7A, the stopper is effective and the reference state (the eccentric moment is zero) is reached. (D) As shown in FIG. 1B, when the fixed eccentric weight 49 is rotated in the direction of the arc arrow R, and the movable eccentric weight 51 is lightly braked (resistance to rotation), the phase difference control spring 53 is moved. And the movable eccentric weight 51 is delayed to increase the total eccentric moment.

FIG. 1 is one embodiment of the present invention, and is not limited to this configuration, but means (for example, a spring) for advancing the phase of the movable eccentric weight with respect to the fixed eccentric weight, and the above The basic principle of the present invention is to combine the means for limiting the phase difference (for example, a stopper) and the means for giving a resistance to the rotation of the movable eccentric weight (for example, a brake).

Based on the principle described above, claim 1
In the invention, the fixed eccentric weight is attached to the common rotation shaft so as not to be rotatable relative to the common rotation shaft, and the movable eccentric weight is attached to the common rotation shaft to be rotatable relative to the common rotation shaft. By controlling the phase difference between the weights, the "excitation force zero state in which the total eccentric moment of both eccentric weights with respect to the rotation axis becomes almost zero" and "the total eccentricity of both eccentric weights with respect to the rotation axis In the method of adjusting the oscillating force between the maximum oscillating force and the maximum moment, the rotational force that acts in the direction that advances the phase of the movable eccentric weight with respect to the phase of the fixed eccentric weight is applied. A means is provided to advance the phase of the movable eccentric weight to make the excitation force zero state, and the rotational drive of the rotary shaft is started in the state where the excitation force is zero, and the rotation speed is the rotation of steady operation. Up to speed and the above rotation speed is After passing through the rotation speed range corresponding to the frequency, a resistance is given to the rotation of the movable eccentric weight, and the rotational force imparting means is bent to delay the phase of the movable eccentric weight so that the excitation force becomes maximum. , Performing the work as the exciter in the maximum state of the exciter force, and / or releasing the resistance applied to the rotation of the movable eccentric weight at the rotation speed of the steady operation to apply the rotation force. A means for advancing the phase of the movable eccentric weight to make the excitation force zero state, cancel the rotational drive of the rotary shaft, and reduce the rotation speed in the excitation force zero state to stop. And According to the invention of claim 1 described above, the vibration force is adjusted while continuing the operation by increasing or decreasing the phase difference between the fixed eccentric weight and the movable eccentric weight using a simple control mechanism. In particular, it is only the fixed eccentric weight that has to be rotationally driven, and it suffices to give rotational resistance to the movable eccentric weight, and also give rotational resistance due to some circumstances (such as failure). If it becomes impossible to do so, the vibration force will automatically disappear, which is safe.

According to the structure of the invention of claim 2, in addition to the structure of the invention of claim 1, the relative rotatable angle of the movable eccentric weight with respect to the fixed eccentric weight is restricted to about 30 degrees, and the operation is started. Occasionally, a rotary driving force is applied to the fixed eccentric weight without applying a special operating force to the movable eccentric weight.
By rotating the movable eccentric weight by the fixed eccentric weight via the turning force applying means, the rotational speed is increased while reaching the rated rotational speed while maintaining the state of zero excitation force, and the rotational speed is the rated rotational speed. When the speed is reached or before and after the speed is reached, a braking force is applied to the movable eccentric weight, and the magnitude of the braking force is set to "the bending force imparting means is bent to move the movable eccentric weight to the maximum within the rotatable range. It is characterized in that the maximum excitation force is maintained by setting the delay phase to a level that is sufficient to tighten it. According to the invention of claim 2 described above, among the rotational drive energy given to the fixed eccentric weight when carrying out the invention of claim 1, the energy lost due to the braking of the movable eccentric weight is minimized. It is possible,
Moreover, since the range of change of the phase angle is limited to about 30 degrees, the responsiveness of the change of the excitation force due to the phase change is good, and moreover, the eccentric moment sufficient for practical use can be generated, and the sufficient vibration is generated. Power is gained.

According to the structure of the invention of claim 3, in addition to the structure of the invention of claim 1, the magnitude of the resistance given to the rotation of the movable eccentric weight is defined as "the movable eccentric weight bends the turning force applying means. The force required to generate a zero excitation force state is smaller than that, and by performing an operation to generate an excitation force in a state between the zero excitation force state and the maximum excitation force state. It is characterized in that the exciting force is increased / decreased within a range within the maximum exciting force. According to the invention of claim 3 described above, when the invention of claim 1 is carried out, a stepless vibration is generated so as to generate an exciting force of an arbitrary magnitude within the range of the maximum exciting force. Swing force can be adjusted.

According to a fourth aspect of the present invention, the fixed eccentric weight is attached to the common rotation shaft such that the fixed eccentric weight cannot rotate relatively, and the movable eccentric weight rotates relatively to the common rotation shaft. The eccentric weight is attached to the rotary shaft so that the phase difference between the both eccentric weights is controlled, and the "excitation force zero state in which the total eccentric moment of both eccentric weights with respect to the rotary shaft becomes substantially zero" and "with respect to the rotary shaft In the method of adjusting the excitation force between the maximum eccentric moment of both eccentric weights and the maximum eccentric moment, the phase of the movable eccentric weight is advanced relative to the phase of the fixed eccentric weight. By providing a turning force applying means that acts in the direction to make it move, the phase of the movable eccentric weight is advanced by the force of the above-mentioned turning power applying means to bring the vibration force to the maximum state when no special operation force is applied. , It is possible to rotate the fixed eccentric weight. Giving resistance to rotation of the eccentric weight, characterized in that occupied become vibratory force zero state by delaying the phase of the movable eccentric weight. According to the invention of claim 4 described above, the exciting force can be increased or decreased by using a simple control mechanism and while the operation is continued. In particular, the maximum exciting force is generated. Therefore, the energy loss due to the braking of the movable eccentric weight is not generated, and the rotational driving force of the fixed eccentric weight can be assisted by applying the rotational driving force to the movable eccentric weight.

According to a fifth aspect of the invention, in addition to the configuration of the fourth aspect of the invention, when the phase of the movable eccentric weight with respect to the eccentric weight is advanced to the maximum excitation force state, the movable eccentric weight is increased. Of the fixed eccentric weight so that the phase of the fixed eccentric weight does not advance further with respect to the phase of the fixed eccentric weight. It is characterized in that a rotational driving force in a direction is applied. According to the invention of claim 5 described above, claim 4
In carrying out the invention of (1), the driving means for the fixed eccentric weight can be assisted in a stable state by the rotational driving means for the movable eccentric weight to generate the maximum oscillating force. No additional control is required to maintain the operating conditions that generate force.

The structure of the invention of claim 6 is the same as that of claims 1 and 4 above.
In addition to the configuration of the invention described above, one pair of vibration generating units each including the rotary shaft, the fixed eccentric weight, and the movable eccentric weight are used to form the above-mentioned pair of vibration generating units. Of the fixed eccentric weight is synchronized with the rotation of the two movable eccentric weights forming the pair of vibration generating units, and the pair of vibration generating units is formed. One of the two rotary shafts is connected so as to be synchronized with the fixed eccentric weight, and the other of the two rotary shafts is connected so as to be synchronized with the movable eccentric weight. The rotary shaft connected to the rotary eccentric weight is rotationally driven, and the rotary shaft connected to the movable eccentric weight is braked so as to be adjustable and controllable. According to the sixth aspect of the invention described above, the two fixed eccentric weights forming the pair of vibration oscillating units are driven by one rotation driving means, and the two movable eccentric weights are moved. Since resistance can be applied to rotation by one braking means, the control system is further simplified, and vibration component force in a desired direction can be added and vibration component force in an unnecessary direction can be canceled. it can.

According to a seventh aspect of the invention, in addition to the configuration of the sixth aspect of the invention, the rotary shaft connected to the fixed eccentric weight is driven to rotate, and the rotary shaft connected to the movable eccentric weight is connected to the rotary shaft. It is characterized by adjustable braking. According to the invention of claim 7 described above, when carrying out the invention of claim 6, the magnitude of the exciting force is adjusted steplessly without impairing the action and effect of the invention of claim 6. be able to.

According to the structure of the eighth aspect of the present invention, a fixed eccentric weight and a movable eccentric weight having the same or substantially the same eccentric moment amount are attached to a common rotating shaft. The movable eccentric weight is restricted in a range in which the movable eccentric weight can relatively rotate around the rotation axis, and is elastic in a direction for advancing the phase of the movable eccentric weight with respect to the phase of the fixed eccentric weight. A means for imparting turning power is provided,
When the phase of the movable eccentric weight is the most advanced within the range in which the relative rotation is restricted with respect to the phase of the fixed eccentric weight,
The total eccentric moment of both eccentric weights becomes zero and the excitation force becomes zero, and while the fixed eccentric weight is rotationally driven, resistance is given to the rotation of the movable eccentric weight, and By delaying the phase of the movable eccentric weight against the force, braking means is provided to bring the total eccentric moment into the maximum state of the exciting force. According to the invention of claim 8 described above, the eccentric moment is increased by applying a braking force to the movable eccentric weight, and the exciting force can be adjusted up or down without the need to control the two system drive motors in conjunction. You can
Particularly, it is safe because the vibration force automatically becomes zero when the braking force disappears due to an abnormality in the braking means.

According to a ninth aspect of the present invention, a fixed eccentric weight and a movable eccentric weight having the same or substantially the same eccentric moment amount are attached to a common rotary shaft, and the fixed eccentric weight and The movable eccentric weight is restricted in a range in which the movable eccentric weight can relatively rotate around the rotation axis, and is elastic in a direction for advancing the phase of the movable eccentric weight with respect to the phase of the fixed eccentric weight. When the phase of the movable eccentric weight is delayed most relative to the phase of the fixed eccentric weight within the range in which the relative rotation is restricted, the means for applying the turning power is provided. The total eccentric moment of the eccentric weight becomes almost zero, and the movable eccentric weight reaches the most advanced position within the range in which relative rotation is restricted by the turning force applying means. When the eccentric moment is the maximum, the maximum excitation force Next, and characterized in that the braking means for delaying the phase by giving a resistance to the rotation of the movable eccentric weight against the force of the turning force applying means. According to the invention of claim 9 described above, the eccentric moment is reduced by applying the braking force to the movable eccentric weight, and the exciting force can be adjusted up or down without the need to control the two system drive motors in conjunction. You can Particularly, since the braking force is not applied in the operating state in which the maximum excitation force is generated, the energy efficiency is good.

The structure of the invention of claim 10 is the same as that of claim 8,
In addition to the configuration of the ninth aspect of the invention, two sets of an oscillating unit composed of the rotary shaft, the fixed eccentric weight, and the movable eccentric weight are arranged such that the respective rotary axes are parallel, and A motor for rotationally driving one of the two rotary shafts constituting each of the vibrating units, and a braking means for giving resistance to the rotation of the other of the two rotary shafts. One of the two fixed eccentric weights provided and constituting each of the two sets of vibrating units is locked to rotate relative to the drive-side rotary shaft, and two of them are locked. The other one of the movable eccentric weights is locked in relative rotation with respect to the rotation shaft on the braking side. According to the tenth aspect of the invention described above, both the two sets of vibration generating units are rotationally driven by one motor, and resistance is given to the rotation by one braking means, so that the drive / braking mechanism is simple. Therefore, a mechanism for controlling the drive / braking mechanism described above is simple and sufficient. Moreover, the vibrations of the two sets of vibration generating units can be added to each other in the desired vibration direction and can be canceled in the unnecessary vibration direction, which is highly versatile.

The structure of the invention of claim 11 is the same as that of claim 9,
In addition to the tenth aspect of the invention, the braking means is an electric motor including a variable resistor in an electric circuit. According to the eleventh aspect of the invention described above, the variable resistor in the electric motor circuit can be operated to arbitrarily adjust the braking force to increase / decrease the exciting force, and further, to use it as a brake. Since the electric motor that is used can be switched to a rotary drive, the application range is expanded.

The configuration of the invention of claim 12 is the same as that of claim 9,
In addition to the tenth aspect of the invention, the braking means is a fluid pressure motor having a variable orifice in a fluid circuit. According to the twelfth aspect of the invention described above, the braking force can be arbitrarily adjusted by operating the variable orifice, and the circuit of the fluid pressure motor installed as a brake is switched to generate the rotational driving force. Therefore, the versatility of the vibration device can be expanded. Furthermore, it is safe because there is no need to use high voltage current.

The structure of the invention of claim 13 is the same as that of claim 9,
In addition to the structure of the tenth aspect of the invention, the braking means is an electromagnetic brake or a friction brake having a structure capable of increasing / decreasing the braking force. According to the invention of claim 13 described above, it is convenient to use an off-the-shelf braking machine, and moreover, it is possible to precisely and easily adjust the braking force to increase / decrease the exciting force with high accuracy. .

The structure of the invention of claim 14 is the same as that of claim 10.
In addition to the configuration of the invention, a drive motor composed of a fluid pressure motor or an electric motor for rotationally driving the fixed eccentric weight via the rotary shaft to which the fixed eccentric weight is attached is provided, and rotation of the drive motor is provided. An automatic control device is provided which inputs performance characteristics representing the relationship between speed and output torque, and the automatic control device controls the braking means based on the input characteristics of the drive motor. It is characterized by According to the invention of claim 14 described above, it is possible to smoothly perform the increase / decrease adjustment of the excitation force without requiring the worker to have a high degree of knowledge or skill.
There is no risk of vibration pollution due to operation error.

[0032]

BEST MODE FOR CARRYING OUT THE INVENTION Next, an embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a schematic diagram for explaining the operation of one embodiment of a phase difference control mechanism for an eccentric weight for vibration according to the present invention, where (A) shows a zero vibration force state, and (B) shows Represents the maximum excitation force state. 41 is a common rotating shaft, 49 is a fixed eccentric weight, and 51 is a movable eccentric weight. The fixed eccentric weight 49 is fixed to the rotating shaft 41 and is rotationally driven in the direction of the arrow R. With respect to the fixed eccentric weight 49,
A phase difference control spring 53 is provided so as to advance the phase of the movable eccentric weight 51, that is, as a means for applying a turning force in the direction of the arc arrow r, and the phase difference control spring 5 is provided.
A stopper 61 is provided as a means for restricting the advance angle by 3. This FIG. 1 is schematically illustrated, and the phase difference control spring 53 is represented by a contraction type spring symbol, but its substantial shape is a torsion coil type spring as described later with reference to FIG.

As shown in FIG. 1A, the fixed eccentric weight 4
When 9 is rotated in the direction of the arrow R, the movable eccentric weight 51 is rotated by the phase difference control spring 53 in the direction of the arrow r. In this state, both eccentric weights are
Since they are located symmetrically with respect to each other, the total eccentric moment of both eccentric weights is zero, and no vibrating force is generated even when rotating. As shown in FIG. 1B, when the movable eccentric weight 51 is given a light braking force while the fixed eccentric weight 49 is rotationally driven in the direction of the arc arrow R, the phase difference control spring 53 is bent. The phase of the movable eccentric weight 51 is delayed, and the total eccentric moment of both the eccentric weights becomes maximum in the state shown in the figure, and an exciting force is generated. By rotating in the state of FIG. 1B (maximum vibration force), the function as a vibration exciter is exhibited. In this case, the braking force applied to the movable eccentric weight 51 is the movable eccentric weight. It is desirable that the retardation of 51 should not be so much larger than the minimum braking force that can be obtained by maximizing the excitation force. For this purpose, the braking means needs to be capable of adjusting the magnitude of the braking force, and the specific method and configuration thereof will be described later with reference to FIG.

As shown in FIG. 1, the rotatable angle of the movable eccentric weight 51 with respect to the fixed eccentric weight 49 (that is, the angle range in which the phase difference can be changed) is set to about 30 degrees. . It is not preferable to set the angle larger than 30 degrees because the responsiveness of the vibration force change due to the phase difference change is delayed. Further, if it is set to less than 30 degrees, the value of the maximum excitation force becomes small, which is not preferable. Although the improvement of the responsiveness and the increase of the vibrating force are contradictory to each other in design, it is most suitable to set it to about 30 degrees according to the experience and experiment of the present inventor. When the braking force applied to the movable eccentric weight 51 is set to an intermediate value between (A) and (B) in FIG.
The phase difference by which the movable eccentric weight is advanced with respect to 9 compared to the reference state is in an intermediate state between the two figures (A) and (B).
In this way, the magnitude of the exciting force can be changed arbitrarily and steplessly within the range smaller than the maximum exciting force.

FIG. 2 is a schematic sectional view showing an embodiment of a phase difference control mechanism for an eccentric weight for vibration according to the present invention. Two rotary shafts 41 and 42 are arranged in parallel, and the rotary shaft 41 includes a driven pulley 43 and a winding transmission means 4
4, and is driven to rotate by the drive motor 46 via the drive pulley 45. The driven pulley 43 is fitted to the rotating shaft 41 by a key k so as not to be relatively rotatable. In FIG. 2, four keys are drawn, and these four parts are fitted so as not to rotate relative to each other. Key k
The portion in which the bush B is drawn without being drawn indicates that the relative rotation is possible.

A fixed eccentric weight 49 and a movable eccentric weight 51 are attached to the rotary shaft 41 to form a set of vibration generating units. When this vibrating unit is viewed in the direction of arrow I, it becomes as shown in FIG. The phase difference control spring 53 schematically depicted in FIG. 1 is a torsion coil spring as shown by a spring symbol in FIG. Similar to the above, the rotary shaft 4
A fixed eccentric weight 50 and a movable eccentric weight 52 are attached to 2 to form a set of vibration generating units, and a phase difference control spring 53 is attached.

The fixed eccentric weights 49 and 50, which constitute the two sets of vibration generating units, are integrally connected to the fixed eccentric weight gears 47 and 48, respectively, through these gears. Are forcibly synchronized with each other. Similarly, the movable eccentric weights 51 and 52 are the movable eccentric weights 5
They are forcibly synchronized with each other via 4, 55. The member M ₂ attached to the rotary shaft 42 is a brake. As this brake, the oil motor 5
A known braking device such as a fluid pressure motor such as No. 6, an electric motor, an electromagnetic brake, or a friction brake can be applied. When the oil motor 56 is used as the brake M ₂ , a variable orifice 57 is provided to enable adjustment of the braking force. Further, when the electric motor 58 is provided as a brake, the variable electric resistor 5 is
9 is provided so that the braking force can be adjusted. An electromagnetic brake 60 or a friction brake may be used as the braking device. In this way, it is possible to drive one of the two sets of vibration generating units by the driving device M ₁ and perform phase difference control by the one braking device M ₂ .

When an oil motor or an electric motor is used as the braking device, it can be used not only as a braking device but also as a rotary driving device. This Figure 2
As is clear from the configuration shown in FIG. 5, when the member M ₂ acts as a rotary drive machine, the movable eccentric weight 52
Is driven to rotate. Next, an embodiment will be described in which the movable eccentric weight is braked or rotationally driven. 3A and 3B show an embodiment of a phase difference control mechanism for an eccentric weight for vibration according to the present invention, FIG. 3A is a schematic diagram showing a state in which vibration force is zero, and FIG. It is a schematic diagram showing the maximum state. Also in the embodiment of FIG. 3, the phase difference control spring 53 acts so that the phase of the movable eccentric weight 51 advances more than the fixed eccentric weight 49. And this Figure 3
When the fixed eccentric weight 49 is rotationally driven in the direction of the arrow R as shown in (A) and the movable eccentric weight 51 is lightly braked, the phase of the movable eccentric weight 51 is delayed. The phase delay angle is limited by the stopper 61, and the stopper 61 is set so that the exciting force becomes zero when the stopper is opened.

After starting the operation in the state of zero excitation force shown in FIG. 3A to increase the speed and pass through the rotational speed range corresponding to the harmful resonance frequency, or before and after reaching the rated rotational speed. When the light braking applied to the movable eccentric weight is released, the state becomes as shown in FIG. 3 (B). That is, the phase of the movable eccentric weight 51 with respect to the fixed eccentric weight 49 advances to the maximum within the allowable range, and the excitation force becomes maximum. In the state of FIG. 3 (B), while the fixed eccentric weight 49 is rotationally driven in the direction of the arc arrow R, the movable eccentric weight 51 can be given auxiliary rotational drive in the same direction (arc arrow r). The reason is that even if a rotational driving force in the direction of the arc arrow r is applied to the movable eccentric weight 51, the phase relationship does not change any more. (Refer to FIG. 2) As described above, in order to rotationally drive the movable eccentric weight, the device M ₂ provided as a brake is configured by a fluid pressure motor such as an oil motor 56 or an electric motor 58. Made possible by When the illustrated device M ₂ is operated as a rotary drive machine, the rotational drive of the drive motor M ₁ is assisted.
As a result, a larger exciting force can be obtained by the drive motor having the same capacity, and the capacity of the drive motor M ₁ required to generate the same exciting force can be small. As described above, when operating the device M ₂ as a brake or as a rotary drive, an automatic control device (not shown) that stores the characteristic curve of the driving device M ₁ is used. Automatically controlling the brake / driving machine M ₂ is convenient because it enables reliable operation without requiring the operator to have a high level of knowledge and skill, and there is no risk of operating errors. .

[0040]

As described above, the configuration and operation of the present invention have been clarified by the embodiments, and according to the invention of claim 1, a fixed eccentric weight and a movable eccentric weight are used by using a simple control mechanism. By increasing or decreasing the phase difference with the weight, the exciting force can be adjusted while continuing the operation. In particular, it is only the fixed eccentric weight that must be driven to rotate, and the movable eccentric weight. It is enough to give rotation resistance to
If the rotation resistance cannot be given due to some circumstances (such as a failure), the vibration force will automatically disappear, which is safe. According to the invention of claim 2, among the rotational drive energy given to the fixed eccentric weight when carrying out the invention of claim 1, the energy lost due to the braking of the movable eccentric weight can be minimized. Moreover, since the range of change of the phase angle is limited to about 30 degrees, the responsiveness of the change of the excitation force due to the phase change is good, and moreover, the eccentric moment sufficient for practical use can be generated, and the sufficient vibration is generated. Power is gained. According to the invention of claim 3, when carrying out the invention of claim 1, the excitation force is adjusted steplessly so as to generate the excitation force of any magnitude within the range of the maximum excitation force. can do.

According to the fourth aspect of the present invention, the exciting force can be increased or decreased by using a simple control mechanism and while the operation is continued. Especially, in the state where the maximum exciting force is generated. Energy loss due to braking of the movable eccentric weight is not caused, and moreover, a rotational driving force can be applied to the movable eccentric weight to assist the rotational driving means of the fixed eccentric weight. According to the invention of claim 5, when carrying out the invention of claim 4, the drive means for the fixed eccentric weight is supported in a stable state by the rotary drive means for the movable eccentric weight, and the maximum excitation force is generated. It can be generated and in particular does not require any additional control in order to maintain the operating conditions in which the maximum excitation force is generated.

According to the sixth aspect of the present invention, the two fixed eccentric weights forming the pair of vibration generating units are driven by one rotation driving means, and the two movable eccentric weights rotate. Since the resistance can be applied by one braking means, the control system is further simplified, and the vibration component force in the desired direction can be added and the vibration component force in the unnecessary direction can be canceled. . According to the invention of claim 7, when carrying out the invention of claim 6, it is possible to continuously increase or decrease the magnitude of the exciting force without impairing the action and effect of the invention of claim 6.

According to the invention of claim 8, the braking force is applied to the movable eccentric weight to increase the eccentric moment,
It is possible to increase / decrease the exciting force without the need to control the drive motors of the two systems in conjunction with each other. Particularly, it is safe because the vibration force automatically becomes zero when the braking force disappears due to an abnormality in the braking means. According to the invention of claim 9,
By applying a braking force to the movable eccentric weight, the eccentric moment is reduced, and the exciting force can be adjusted up or down without the need to control the two system drive motors in conjunction. Especially,
Since the braking force is not applied in the operating state in which the maximum excitation force is generated, energy efficiency is good.

According to the tenth aspect of the present invention, both of the two sets of vibration generating units are rotationally driven by one motor, and resistance is given to the rotation by one braking means, so that the driving / braking mechanism is simple. The mechanism for controlling the drive / braking mechanism described above is simple and sufficient. Moreover, the vibrations of the two sets of vibration generating units can be added to each other in the desired vibration direction and can be canceled in the unnecessary vibration direction, which is highly versatile.

According to the invention of claim 11, the variable resistor in the electric motor circuit can be operated to arbitrarily adjust the braking force to increase / decrease the exciting force, and further, to use as a braking device. Since the existing electric motor can be switched to a rotary drive, the application range is expanded. According to the invention of claim 12, the braking force can be arbitrarily adjusted by operating the variable orifice, and the rotational driving force can be generated by switching the circuit of the fluid pressure motor installed as a braking device. The versatility of the vibration device can be expanded. Furthermore, it is safe because there is no need to use high voltage current.

According to the thirteenth aspect of the present invention, it is convenient to use an off-the-shelf braking machine, and moreover, it is possible to precisely and easily adjust the braking force to control the exciting force with high accuracy. According to the fourteenth aspect of the invention, the vibration force can be smoothly increased / decreased and adjusted without requiring the worker to have a high level of knowledge or skill, and there is no risk of vibration pollution due to an operation error.

[Brief description of drawings]

FIG. 1 is a schematic diagram for explaining the operation of one embodiment of a phase difference control mechanism for an eccentric weight for vibration according to the present invention, in which (A) shows a state in which vibration force is zero, ) Indicates the maximum excitation force state.

FIG. 2 is a schematic sectional view showing an embodiment of a phase difference control mechanism for an eccentric weight for vibration according to the present invention.

3A and 3B show one embodiment of a phase difference control mechanism for an eccentric weight for vibration according to the present invention, FIG. 3A is a schematic diagram illustrating a zero vibration force state, and FIG. It is a schematic diagram showing the maximum state.

FIG. 4 is an explanatory diagram showing transmission of ground waves and underground waves in pile driving work using a vibration device.

FIG. 5 is a diagram showing time-rotation speed for explaining a resonance phenomenon in a vibrating pile driving work.

FIG. 6 is a view for explaining a known technique of changing an exciting force by a combination of two eccentric weights, and (A) shows that two eccentric weights generate a maximum exciting force. Is a schematic diagram showing a state in which the exciting force is medium, a schematic diagram showing a state in which the exciting force is medium, a schematic diagram showing a state in which the exciting force is a little small, and a schematic diagram showing a state in which the exciting force is zero. It is a schematic diagram showing a state.

FIG. 7 is a schematic view of a mechanism in which a fixed eccentric weight is fixed to a common rotation shaft and a movable eccentric weight can be adjusted in a rotational angle position relative to the common rotation shaft.

8] As shown in FIG. 7 above, a fixed eccentric weight and a movable eccentric weight are arranged on a common single axis so that the exciting force can be adjusted to be increased or decreased. It is a perspective view which shows the conventional example of a shaker.

9 is a view for explaining the relationship between the rotary shaft, the fixed eccentric weight, and the movable eccentric weight in the vibration oscillating machine including the conventional adjusting mechanism shown in FIG. () Is an external perspective view drawn by partially cutting, and (B) is a schematic view drawn as seen in a direction parallel to the rotation axis.

FIG. 10 is a schematic diagram showing a vibration exciter including one embodiment of a vibration force control mechanism for an eccentric weight according to the invention of the prior application, which is configured to carry out the vibration control method of the invention of the previous application. It is the horizontal sectional view drawn typically.

[Explanation of symbols]

1 ... Exciter case, 2, 2A-2D ... Rotating shaft, 4, 4
A to 4D ... Transmission gears for synchronous transmission, 5 ... Crane boom, 6 ... Vibration device (vibrator), 7 ... Pile, 8 ... Private house, 4
1, 42 ... Rotating shaft, 43 ... Driven pulley, 44 ... Winding transmission means, 45 ... Drive pulley, 46 ... Drive motor, 47, 4
8 ... Fixed eccentric weight gear, 49, 50 ... Fixed eccentric weight, 5
1, 52 ... Movable eccentric weight, 53 ... Phase difference control spring, 5
4, 55 ... Movable eccentric weight gear, 56 ... Oil motor, 5
7 ... Variable orifice, 58 ... Electric motor, 59 ... Variable electric resistor, 60 ... Electromagnetic brake, 61 ... Stopper as rotation angle regulating means.

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[Procedure amendment]

[Submission date] September 4, 1996

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] Figure 3

[Correction method] Change

[Correction contents]

FIG. 3 is an operation explanatory view of the phase difference control mechanism of the eccentric weight for the vibration exciter according to the present invention.

Claims (14)

[Claims] 1. A fixed eccentric weight is attached to a common rotation shaft so as not to be rotatable relative to it, and a movable eccentric weight is attached to the common rotation shaft to be rotatable relative to the common rotation shaft. By controlling the phase difference between the eccentric weights, the "excitation force zero state in which the total eccentric moment of both eccentric weights with respect to the rotating shaft becomes almost zero" and "the total eccentric weight with respect to the rotating shaft are combined. In the method of adjusting the oscillating force between the maximum eccentric moment and the maximum oscillating force state, the rotational force acting in the direction that advances the phase of the movable eccentric weight with respect to the phase of the fixed eccentric weight. Providing means is provided to advance the phase of the movable eccentric weight so as to make the exciting force zero state, and in the state where the exciting force is zero, the rotational drive of the rotary shaft is started, and the rotation speed of the steady operation is Increase the rotation speed to the above value, After passing through the speed range corresponding to Do resonance frequency, giving resistance to rotation of the movable eccentric weight,
Flexing the turning force applying means to delay the phase of the movable eccentric weight to bring the maximum oscillating force, and perform the work as the oscillating machine in the maximum oscillating force state, and / or , The resistance applied to the rotation of the movable eccentric weight at the rotational speed of the steady operation is released, and the phase of the movable eccentric weight is advanced by the turning force applying means to make the exciting force zero state. It is characterized by eliminating the rotational drive of, and reducing the rotation speed in the state of zero excitation force to stop.
Phase difference control method for eccentric weight for vibration. 2. A relative rotatable angle of the movable eccentric weight with respect to the fixed eccentric weight is regulated to about 30 degrees, and at the time of starting the operation, the movable eccentric weight is not given a separate operation force. A rotational driving force is applied to the fixed eccentric weight, and the movable eccentric weight is rotationally driven by the fixed eccentric weight via the turning force applying means to increase the rotational speed while maintaining the state of zero exciting force. When the rated rotation speed is reached and the rotation speed reaches the rated rotation speed, or before and after the rotation speed reaches the rated rotation speed, a braking force is applied to the movable eccentric weight, and the magnitude of the above braking force is set to "the flexural force applying means is bent to move. The eccentric weight for oscillating force according to claim 1, wherein a maximum oscillating force is maintained by setting the eccentric weight to such an extent that the eccentric weight has a phase that is most delayed in the rotatable range. Weight difference phase difference control method. 3. The magnitude of the resistance given to the rotation of the movable eccentric weight is made smaller than "the force sufficient for the movable eccentric weight to bend the turning force applying means to bring about a state of zero excitation force". By performing an operation to generate an exciting force in a state between the state where the exciting force is zero and the state where the exciting force is maximum, it is possible to increase or decrease the exciting force within the range of the maximum exciting force. Characteristic,
The method for controlling a phase difference of an eccentric weight for vibration according to claim 1. 4. A fixed eccentric weight is attached to a common rotation shaft so as not to be rotatable relative to it, and a movable eccentric weight is attached to the common rotation shaft to be rotatable relative to the common rotation shaft. By controlling the phase difference between the eccentric weights, the "excitation force zero state in which the total eccentric moment of both eccentric weights with respect to the rotating shaft becomes almost zero" and "the total eccentric weight with respect to the rotating shaft are combined. In the method of adjusting the oscillating force between the maximum eccentric moment and the maximum oscillating force state, the rotational force acting in the direction that advances the phase of the movable eccentric weight with respect to the phase of the fixed eccentric weight. Provided with an applying means, when the operation force of another stage is not applied, the phase of the movable eccentric weight is advanced by the force of the above-mentioned power applying means to bring the vibration force to the maximum state, and at the start of operation, the fixed eccentric weight is rotated. Drives and resists rotation of the movable eccentric weight Is applied to delay the phase of the movable eccentric weight so that the exciting force is brought to a zero state. 5. When the phase of the movable eccentric weight with respect to the eccentric weight is advanced to the state of maximum excitation force, the phase of the movable eccentric weight does not advance further than the phase of the fixed eccentric weight. 5. The rotating eccentric weight is restrained to rotate and drive the fixed eccentric weight, and the movable eccentric weight is also given a rotational driving force in the same direction as that of the fixed eccentric weight. For controlling the phase difference of the eccentric weight for vibration. 6. A fixed eccentric unit comprising a pair of oscillating units each comprising the rotating shaft, a fixed eccentric weight and a movable eccentric weight. The rotations of the weights are synchronized, and the rotations of the two movable eccentric weights forming the pair of vibration generating units are synchronized, and the two rotations forming the pair of vibration generating units. Connect one of the shafts to synchronize with the fixed eccentric weight,
Moreover, the other of the two rotary shafts is connected so as to be synchronized with the movable eccentric weight, and the rotary shaft connected to the fixed eccentric weight is rotationally driven, and the rotary shaft connected to the movable eccentric weight is The method for controlling the phase difference of the eccentric weight for vibration excitation according to claim 1 or 4, wherein the braking is performed so as to be adjustable and controllable. 7. A rotary shaft connected to the fixed eccentric weight is rotationally driven by a motor, and a rotary shaft connected to the movable eccentric weight is braked by a motor or a brake, and the fixed eccentric weight is provided. 7. The vibration eccentricity according to claim 6, wherein a motor or a brake that brakes the movable eccentric weight is automatically controlled by an automatic control device that stores the operating characteristics of a motor that rotationally drives the motor. Weight difference phase difference control method. 8. A fixed eccentric weight and a movable eccentric weight having equal or substantially equal eccentric moment amounts are attached to a common rotating shaft, and the fixed eccentric weight and the movable eccentric weight are A means for restricting the range of relative rotation around the rotation axis and for giving an elastic turning force in the direction of advancing the phase of the movable eccentric weight with respect to the phase of the fixed eccentric weight is provided. It is provided, and when the phase of the movable eccentric weight is the most advanced within the range in which the relative rotation is restricted with respect to the phase of the fixed eccentric weight,
The total eccentric moment of both eccentric weights becomes almost zero, and the excitation force becomes zero, and while the fixed eccentric weight is driven to rotate, resistance is given to the rotation of the movable eccentric weight and By virtue of delaying the phase of the movable eccentric weight against the force, a braking means is provided for keeping the total eccentric moment to the maximum state of the motive force. Eccentric weight phase difference control mechanism. 9. A fixed eccentric weight and a movable eccentric weight having equal or substantially equal eccentric moment amounts are attached to a common rotating shaft, and the fixed eccentric weight and the movable eccentric weight are While restricting the range of relative rotation around the rotation axis,
Means are provided to apply elastic rotational force in the direction that advances the phase of the movable eccentric weight with respect to the phase of the fixed eccentric weight. When the relative rotation is delayed most within the restricted range,
The total eccentric moment of both eccentric weights becomes zero, and the movable eccentric weight is the most within the range in which relative rotation is restricted by the turning force applying means. When it advances, the braking force is in the maximum state where both eccentric moments are maximum, and the braking means for delaying the phase against the force of the turning force applying means by giving resistance to the rotation of the movable eccentric weight. A phase difference control mechanism for an eccentric weight for vibration is provided. 10. Two sets of vibration generating units, each of which has the rotating shaft, a fixed eccentric weight, and a movable eccentric weight, are arranged such that the respective rotating shafts are parallel to each other, and the two vibration generating units are provided. A motor for rotationally driving one of the two rotary shafts constituting each of the two rotary shafts, and a braking means for providing resistance to the rotation of the other of the two rotary shafts. One of the two fixed eccentric weights forming each of the two sets of vibrating units is locked to rotate relative to the drive-side rotation shaft, and two movable eccentric weights are attached. 10. The other of the weights is locked for relative rotation with respect to the rotation shaft on the braking side.
A phase difference control mechanism for an eccentric weight for vibration described in any one of 1. 11. The phase difference of the eccentric weight for oscillation according to claim 9 or 10, wherein the braking means is an electric motor having a variable resistor in an electric circuit. Control mechanism. 12. The phase difference of an eccentric weight for oscillation according to claim 9 or 10, wherein the braking means is a fluid pressure motor having a variable orifice in a fluid circuit. Control mechanism. 13. The vibration generating apparatus according to claim 9, wherein the braking means is an electromagnetic brake or a friction brake, and has a structure capable of increasing / decreasing a braking force. Eccentric weight phase difference control mechanism. 14. A drive motor comprising a fluid pressure motor or an electric motor for rotationally driving a fixed eccentric weight via a rotary shaft to which the fixed eccentric weight is attached, and a rotation speed and an output of the drive motor. An automatic control device is provided which inputs a performance characteristic representing a relationship with torque, and the automatic control device controls the braking means based on the input characteristic of the drive motor. The phase difference control mechanism for an eccentric weight for vibration according to claim 10.