JPH0938576A - Driving-controlling device of vibration generator and driving-controlling method therefor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve a technique for driving and controlling the rotation of a rotary vibration generator, to prevent vibrational pollution and the resonance breakage of a crane boom by enabling the increase-decrease adjustment of vibromotive force while operation is being continued without being interrupted, and to control with a simple device which does not require servo control over the whole range of the number of revolutions. SOLUTION: A hydraulic pressure system is constituted which can independently rotation-drive and control-decelerate the hydraulic motor 32A of a system A and the hydraulic motor 32B of a system B respectively, a semi-circular-arc- shaped stopper circular arc channel 38Aa fixed to a synchronous transmission gear 38A which is equipped with the eccentric weight of the system A and rotates and a stopper projection 38Ba fixed to a synchronous transmission gear 38B which is equipped with the eccentric weight of the system B and rotates are connected, and the rotational phase difference between the eccentric weights of systems A, B, is restricted to be 0-close-to 180 degree.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method for driving a rotary type exciter for driving a pile and for controlling an exciting function, and an apparatus therefor. However, it can be applied to applications other than pile driving.

[0002]

2. Description of the Related Art Generally, a vibration device used for civil engineering construction has a structure in which a plurality of pairs of rotating shafts having eccentric weights attached thereto 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. FIG. 7 is a schematic explanatory view of this type of rotary exciter, in which four rotating shafts 2A, 2B, 2C, 2D are arranged with respect to the case 1, and eccentric weights 3A, 3B, 3C and 3D are attached, and gears 4A, 4B, 4C and 4D are attached and constrained to mesh with each other and rotate synchronously.

[0003]

When the pile driving work is carried out by using the above-mentioned vibrator, prevention of vibration pollution and prevention of noise pollution are important problems. Next, technical problems relating to vibration pollution will be described with reference to FIGS. 8 and 9, and noise pollution will be described with reference to FIG. FIG. 8 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 1 is brought into contact with the ground surface to start the pile driving operation, the vibration device 6 is fully operated from the beginning.
The surface wave a generated on the ground at the stakeout point reaches the nearby private house 8 with almost no attenuation, so that a problem of vibration pollution occurs.
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 sound source position corresponding to the lower end of the pile 7 is deepened, the underground wave b is attenuated on the way to the private house 8, so that the vibration pollution is negligible.

FIG. 9 is a chart showing changes in the vibration frequency at the time of starting and stopping the operation of the vibration device, and the horizontal axis is 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 vibrating device matches the natural frequency can be practically ignored. It is as slight as possible. 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 rotary shaft stops, the rotary shaft continues to rotate due to inertia and gradually decelerates as shown by the arrow d. To do. The rotation speed reduction period T ₂ is relatively long (for example, about 50
Therefore, the crane boom may resonate and be damaged when passing through the natural frequency n ₂ of the crane boom on the way. 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 rotational phase of the eccentric weight of the vibrating 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 vibrating device starts the operation in a state where the vibrating force is reduced to zero by changing the rotation phase of the eccentric weight, if the vibrating force can be exerted after reaching the rated number of operations,
It is economical because the motor capacity and power supply capacity can be reduced.
This is because, after reaching the rated operation number, there is no need to store any more rotational energy in the rotating member, and the operation can be continued by replenishing energy sufficient to compensate for the attenuation of vibration.

Next, the reduction of gear noise will be described with reference to FIG. In order to rotate the vibration generating mechanism composed of the eccentric weight shown in FIG.
As shown in (A), a structure is used in which _two motors M ₁ and M ₂ are synchronized via gears. 3E, 3F, 3
G and 3H are eccentric weights, 4E, 4F, 4G and 4H, respectively.
Are gears, 9I is a gear attached to the shaft of the motor M ₁ , and 4J is a gear attached to the shaft of the motor M ₂ . Eccentric weight 3 via gears 9I, 4E, 4F
E, 3F rotationally driven series, gears 9J, 4H,
The gears 9I and 9J are meshed with each other in order to synchronize with the train that rotationally drives the eccentric weights 3H and 3G via 4G. Now, assuming that the gear 9I and the gear 9J are not meshed with each other as shown in FIG.
₁ , one series consisting of the eccentric weights 3E and 3F and one series consisting of the motor M ₂ and the eccentric weights 3H and 3G are arranged in parallel, and both of these series are forced by the engagement of the gears 9I and 9J. If the synchronization can be achieved by a method other than the synchronization, the noise component generated by the meshing of the gears 9I and 9J can be completely prevented.

Further, as shown in FIG. 10 (C), the above two series (hereinafter referred to as a vibrating unit for convenience of explanation) are arranged as shown in FIG. 10 (C), and the two vibrating units are arranged. If the phase difference of can be controlled arbitrarily, the exciting force can be adjusted from zero to the maximum, so that the vibration pollution described in FIGS. 8 and 9 can be significantly reduced, and Can significantly reduce the load on the drive motor and the transmission member (both not shown).

Based on the above consideration, a technique is provided in which two systems of vibration generating units are provided with servo mechanisms to control the rotational phases of the two vibration generating units while synchronizing the two vibration generating units over the entire range of the rotational speed in use. Japanese Patent Application No. 579797 is known as the latest one. The above-mentioned invention technique was created by the present inventor and is being applied for by the present applicant, and is hereinafter referred to as the invention of the prior application. Next, the configuration of the invention of the above-mentioned prior application and the technical problem relating to the invention of the above-mentioned prior application will be described with reference to FIGS.

FIGS. 11 (A) and 11 (B) are principle explanatory diagrams of the invention of the prior application. Note that FIGS. 11A and 11B and FIG. 12 described later are schematically illustrated so that the structural function can be easily understood.
It is simplified, and devices such as a safety valve, a pressure regulating valve, and a hydraulic gauge that can be appropriately arranged based on common technical knowledge are omitted. Further, for simplification of the drawing, an oscillating unit in which a plurality of eccentric weights are rotationally driven by an oil motor is represented as shown in FIG. 11C, and an oscillating unit provided with a rotary encoder is shown in FIG. ). Reference numeral 14 is an oil motor, 3 is an eccentric weight, and R / E is a rotary encoder.

As shown in FIG. 11A, the oil pump 15 is rotated by an engine (not shown), and the discharge pressure oil is
When the pair of vibration units are rotatably driven to the oil motor, the upper shell 14a and the oil motor B, 14b, respectively, the two oil motors 14 are logically supplied.
The a and 14b are rotated at the same rotation speed. However, a. As a matter of fact, a slight difference in the volumetric efficiency of the oil motor affects the above two oil motors.
It is not possible to expect complete synchronous rotation for a long time only with the configuration of (A), and a means for correcting this is required. B. Further, in order to intentionally control the phases of the two oil motors to arbitrarily increase or decrease the vibration force, the control means shown in FIG. 11B is provided. That is, the oil pump 15
While splitting the discharged oil into two, the split discharged oils are supplied to the oil motors A, B 14a and 14b through the control valves 23a and 23b. The control valves 23a and 23b are flow rate control valves having a throttle function.

According to the above structure, the control valve 23a
When it is opened more than 3b, the oil motor, instep 1
4a is speeded up compared to 14b, and the phase is advanced. Also,
When it is closed, it is decelerated and the phase is delayed. Since the relative phases of the two oil motors can be controlled in this manner, it is possible to control the phase difference between the two series of vibrating units driven by both oil motors. If the phase difference between the two series of oscillating units can be arbitrarily adjusted, the total oscillating force of the two series of oscillating units can be arbitrarily selected from a minimum value to a maximum value. If the two series of vibration units have the same capacity, the minimum value of the total vibration force can be set to zero. Similarly, it is possible to control a plurality of vibrating units.

FIG. 12 shows the drive of the vibrator according to the invention of the prior application.
One of the control and drive devices configured to carry out the control method
It is explanatory drawing of the hydraulic system and control system which show an Example. The two oil motors 14a and 14b shown in FIG. 12 correspond to the two oil motors 14a and 14b shown in FIG.
Corresponding to the control valve 23a, which is a similar or similar constituent member and which controls the discharge pressure oil of the variable displacement oil pump 16
It is supplied by 23b in two substantially equal parts. FIG.
What has been described above is the basic constituent parts described above with reference to FIG. Further, details of a specific configuration will be described.

The oil pump 16 is connected to one shaft and is rotationally driven by the engine E. On the other hand, each of the two oil motors A and B and the oil motor B B 14b has a rotary encoder R / E.
The output signals of these two rotary encoders R / E are input to the phase difference counter 17, and the phase difference between the two oil motors is calculated. Specifically, the phase difference between the vibration generating unit driven by the two oil motors and the instep 14a and the vibration generating unit driven by the oil motor and the second winding 14b is calculated, and the digital / analog converter D / A Is input to the operational amplifier 18 via
It is compared with the output of the eccentric moment control circuit. The eccentric moment setting circuit includes an eccentric moment zero setting circuit 19 for outputting a signal for equalizing the phase difference of the two series of vibration generating units by 180 °, and an eccentric moment arbitrary setting circuit 20 for arbitrarily adjusting the phase difference. Is connected to the operational amplifier 18 via the changeover switch 28. The output signal of the operational amplifier 18 is the compensation circuits 21a and 21b and the voltage / current converter V.
The control valves 23a and 23b are controlled via / I22a and 22b. As a result, the phase difference between the two vibration generating units is adjusted as described above with reference to FIG. When the drive / control method according to the invention of the prior application described above is used to carry out the drive / control method of the present invention, the two series of vibration generating units are hydraulically interlocked with each other without being mechanically coupled to each other to perform synchronous rotation. In addition, the phase difference can be adjusted arbitrarily. As a result, it is possible to prevent noise generation due to the mechanical coupling member, and
Vibration pollution during pile driving work can be significantly reduced.

After applying for the invention of the earlier application, the present inventor transferred it to industrial production and asked the public about its effect. As a result, it was confirmed that the desired effect was achieved in practical use. The present inventor further conducted an improvement study on the invention according to the prior application, discovered that there was room for improvement as described below, and confirmed this. (A) In the invention of the prior application, since the servo control is performed over the entire range of the number of revolutions used, the excellent effect that the phase difference control can be performed in a wide range with high precision and fine,
For example, since a complicated control mechanism is provided as shown in FIG. 12, the manufacturing cost is high.

(B) Since complicated and sophisticated control is performed as described above, the user needs special knowledge and skill, and it is difficult to maintain the machine.

The present invention has been made in view of the above circumstances, and is improved in the direction of simplifying the invention of the above-mentioned prior application,
Provided is a drive / control technique for a rotary exciter, which has the same level of pollution prevention effect as that of the invention of the earlier application and can be implemented by a simpler and less expensive device than the device of the invention of the earlier application. The purpose is to

[0018]

The basic principle of the present invention created to achieve the above-mentioned object (simplification of the control mechanism) will be outlined below with reference to FIG. 9 mentioned above. . That is, at the start of operation, what is necessary for pollution prevention and crane boom protection is to set the total eccentric moment of the eccentric weight to zero at the point o when the rotation of the exciter is started, and start the steady operation. At the point i, the total eccentric moment should be maximized. In other words, the rotational phase difference between the two series of vibration units is 18
The maximum excitation force may be exerted by setting the rotation phase difference to 0 degrees at a point j at which the operation is started at 0 degree and the excitation force is zero (point o), and then the steady operation is started. Similarly, at the end of operation, what is required for pollution prevention and crane boom protection is that the rotational phase difference is 18 at the point j at which steady operation is changed to inertial operation.
The vibration force may be set to 0 degrees to zero. If say further summarize, the speed range corresponding to the natural frequency n ₂ of the natural frequency n ₁ and a crane boom of the ground, the rotational phase difference 18
You only have to pass at 0 degrees. Needless to say, during the steady operation from the point i to the point j, the rotational phase difference must be maintained at 0 degree to exert the maximum excitation force. What has become clear from the above consideration is that the control of the rotational phase difference between the two series of vibration generating units is sufficient if the switching operation between the 0 degree state and the 180 degree state is performed, and the entire rotation speed range is controlled. It means that precise servo control over can be omitted.

The basis of the present invention is to provide an eccentric weight type vibration generating mechanism for A and B systems so that the rotational phase difference between the rotating members of both A and B systems does not become smaller than 0 degrees and is 180 degrees. It is mechanically constrained within an allowable angle of 180 degrees so that it does not become larger than that, and both the A and B systems are rotationally driven by a hydraulic motor. However, what has been described above is the basic principle, and it is not always necessary to make the exciting force zero when the exciting force is reduced. As a practical matter, the pile will not sink into the ground by its own weight unless there is enough vibration force to prevent vibration pollution and resonance damage of the crane boom.

The above-mentioned A system and B system are names for convenience of explanation, and the names can be interchanged. However, in the present invention, it is possible to relatively advance the phase by about 180 degrees from the state in which the rotational phase difference between the eccentric weights of both the A and B systems is zero, but the above is the same. The system that cannot be delayed from the state is system A, and the system that can be retarded by about 180 degrees from the state where the phase difference is zero as described above is the system B that cannot be advanced from this aligned state. To do. That is, from the state where the rotational phase difference is zero, the A system can be advanced by about 180 degrees and the B system can be delayed by 180 degrees.
It is agreed that system A leads by about 180 degrees relative to system B, and system B lags by about 180 degrees relative to system A. Therefore, when one of the A and B systems is rotating while pushing the other, the phase relationship between the A and B systems is as follows:
It is either 180 degrees ahead of the system and the total eccentric moment is minimum, or (b) the total eccentric moment is maximum when the rotational phase difference between both systems A and B becomes zero, whichever is the case.

Based on the above-mentioned principle, the concrete construction of the drive / control device for the vibrator according to the present invention is as follows (see FIG. 1):
A hydraulic motor (32A) having a drive / transmission system consisting of two systems, an A system and a B system, for rotationally driving a drive gear (36A) of the A system, and a drive gear (36B) of the B system.
A hydraulic motor (32B) for rotating the
Driven gear (37A) that meshes with drive gear (36A) of the system
A) and a synchronous transmission gear (38A) that meshes with the driven gear (37A) and rotates synchronously, and meshes with a driven gear (37B) and the driven gear (37B) that mesh with a B system drive gear (36B). And a synchronous transmission gear (38B) that rotates in synchronization with each other, and a driven gear (37A) of the A system.
And the eccentric weights (39A, 39A ') attached to the synchronous transmission gears (38A), and the eccentric weights (39B) attached to the driven gear (37B) and the synchronous transmission gears (38B) of the B system, respectively. , 39B '), the rotational phase difference between the synchronous transmission gear (38A) of the A system and the synchronous transmission gear (38B) of the B system is between 0 degree and 180 degrees. It is characterized in that a stopper mechanism for limiting the angle within a set allowable angle range is provided.

On the premise that the drive / control device configured as described above is used, the drive / control of the vibration exciter according to the present invention is
The control method is to slowly rotate the hydraulic motor (32A) of the A system to advance the rotation phase of the A system, and to rotate the eccentric weights of the A system (39A, 39A ') and the eccentric weights of the B system (39B, 3A).
9B ′) and the rotational phase difference between them is set to approximately 180 degrees so that the eccentric moment is minimized.
2A) is operated to rotate the A system, and the B system is driven to rotate via the stopper mechanism to accelerate the rotation of both the A and B systems, and then to the hydraulic motor (32A) of the A system. While reducing or stopping the hydraulic energy supply and inertially rotating the A system, the hydraulic motor of the B system (3
2B) is operated to drive the rotation of the B system, and the rotation phase of the B system, which was delayed from the A system, is advanced by approximately 180 degrees to make the rotation phase difference 0 and make the eccentric moment maximum. Further, the rotational drive of the hydraulic motor (32B) of the B system is continued, and the A system and the B system are synchronously rotated by restricting with the stopper mechanism, and the rotational phase difference between the eccentric weights of the A and B systems is 0. In this state, the maximum exciting force is generated and the steady operation is performed.

When the drive / control device for a vibration generator according to the present invention described above is constructed and the drive / control method according to the present invention is applied, a drive / transmission system of system A and a drive / transmission system of system B are applied. With a simple configuration in which a stopper mechanism that limits the rotation phase difference between the rotation angle and the rotation angle within the allowable angle range set between 0 degree and 180 degrees is provided, the rotation speed whole range servo control is not required, and the rotation at the start of operation is performed. When accelerating and decelerating at the end of operation, it passes through the natural frequency range of the ground and the natural frequency range of the crane boom with "minimum vibration force", preventing vibration pollution and preventing damage to the crane boom. It is effective in prevention. Further, since it is not necessary to synchronize the A system hydraulic motor and the B system hydraulic motor by gears, noise pollution due to gear meshing can be reduced.

[0024]

BEST MODE FOR CARRYING OUT THE INVENTION Next, an embodiment of the present invention will be described with reference to FIGS. FIG.
FIG. 1 is a diagram showing an example of an embodiment of a drive / control device for a vibration exciter according to the present invention, in which a hydraulic system is attached to a schematic drawing of a vibration generating mechanism, showing a state before starting operation. ing. The reference line YY shown in FIG. 1 is a virtual line drawn for convenience of description, and the left side of this line is the A system and the right side is the Y system. The drive gear 36A of the A system is connected to the rotary output shaft of the hydraulic motor 32A of the A system,
The drive gears 36B of the B system are fixed to the rotation output shafts of 2B, respectively. Then, the drive gear 36A of the above A system
Is the driven gear 37A of the A system and the drive gear 36B of the B system
Are respectively engaged with the driven gears 37B of the B system. The synchronous transmission gear 38A of the A system is the driven gear 37A.
Has the same number of teeth and is meshed with the driven gear 37A,
It can be rotated in the opposite direction at the same number of rotations. The synchronous transmission gear 38B of the B system has the same number of teeth as the driven gear 37B, is meshed with the driven gear 37B, and is rotated in the opposite direction at the same rotational speed. An eccentric weight 39A is attached to the driven gear 37A of the A system and a synchronous transmission gear 38
Eccentric weights 39A 'are attached to A, and these eccentric weights rotate in synchronization. Driven gear 3 of the B system
An eccentric weight 39B is attached to 7B and an eccentric weight 39B 'is attached to the synchronous transmission gear 38B, and these eccentric weights rotate in synchronization.

The phase difference between the synchronous transmission gear 38A of the A system and the synchronous transmission gear 38B of the B system is limited as indicated by a thick chain line. Specifically, a semicircular stopper arc groove 38A provided on the A transmission gear 38A.
a and the stopper projection 38Ba provided on the synchronous transmission gear 38B of the B system are slidably engaged in the circumferential direction, and the A system cannot advance the phase by more than about 180 degrees than the B system. The B line cannot be delayed later than the A line.

The hydraulic motor 32A of the A system receives supply of pressure oil from the hydraulic pump 31 common to both the A and B systems via the drive / driven switching valve 33A of the A system. The drive / driven switching valve 33A can be appropriately used as long as the valve has a structure that functions as an opening / closing valve. Further, when carrying out the present invention, a hydraulic pump dedicated to the system A (not shown)
Can be provided and is within the technical scope of the present invention. Similarly, the hydraulic motor 32B of the B system is
Pressure oil is supplied from the hydraulic pump 31 common to both the A and B systems via the drive / driven switching valve 33A of the B system. The drive / driven switching valve 33B can be appropriately used as long as it has a structure that functions as an opening / closing valve. Also,
When carrying out the present invention, it is possible to provide a dedicated hydraulic pump (not shown) in the B system, which belongs to the technical scope of the present invention.

A brake circuit 34A, which is a combination of a pressure regulating valve and a check valve, is connected between the suction side pipe line and the discharge side pipe line of the hydraulic pump 32A of the A system, and the brake circuit 34A is connected to the brake circuit. The brake valve 35A is connected in parallel. The brake valve has a function as an on-off valve, and when the brake valve is opened, the brake circuit is short-circuited and the brake function is not fulfilled. When this brake valve is opened, the hydraulic pump 32A of system A
When it is driven to rotate and acts as a hydraulic pump, it applies pressure to the discharged oil to brake the hydraulic pump (original hydraulic motor). Similarly, a brake circuit 34B, which is a combination of a pressure regulating valve and a check valve, is connected between the suction side pipe line and the discharge side pipe line of the hydraulic pump 32B of the B system, and the brake circuit 34B is connected to the brake circuit. The brake valve 35B is connected in parallel. The brake valve has a function as an on-off valve, and when the brake valve is opened, the brake circuit is short-circuited and the brake function is not fulfilled. Further, when the brake valve is closed, when the hydraulic pump 32B of the B system is driven to rotate and acts as a hydraulic pump, pressure is applied to the discharged oil to brake the hydraulic pump (original hydraulic motor). .

Prior to explaining the operation and effect of the drive / control device (FIG. 1) according to the present invention having the above-mentioned structure, the law concerning the operation of this device will be considered. The rotation phase of the eccentric weight of the A system cannot advance more than approximately 180 degrees than the rotation phase of the eccentric weight of the B system, and the rotation phase of the eccentric weight of the B system is the eccentric weight of the A system. The phase cannot be retarded by more than about 180 degrees than the rotational phase of (due to the phase difference limitation represented by the chain line in FIG. 1). This characteristic will be abbreviated as "A system can advance only 180 degrees more than B system" and will be tentatively called the first law for convenience of the following description. Therefore, 180 according to the first law
The degree means about 180 degrees in detail, and as described in more detail below, it is less than 180 degrees (that is, 180 degrees).
180 ° -α, not ° ± α). In addition, this first
In the law, when we say, "System A can only advance 180 degrees", "System B can only delay 180 degrees."
It also means that. As a result, when the system A is rotationally driven in a direction in which the system A is trying to advance the phase by 180 degrees or more than the system B, the system A rotates while pulling the system B delayed by 180 degrees. Looking at this in the B system, the driven state is that the system is rotated by the A system and follows with a delay of 180 degrees.

(2) In the state in which the above first law is working (the system A leads the system B by 180 degrees), the eccentric weights of both the A and B systems are rotated by 180 degrees. Since the phase difference is generated, the total eccentric moment of the eccentric weights of both A and B systems is zero. In this case, if the rotational phase difference is exactly 180 degrees, the total eccentric moment becomes completely zero, but if the rotational phase difference is slightly less than 180 degrees, the total eccentric moment does not become completely zero. In consideration of such matters, it is expressed that "when the first law is working, the total eccentric moment becomes the minimum value", and for convenience of explanation below,
This is tentatively called the second law.

(3) The rotation phase of the eccentric weight of the B system is A
The eccentric weight of the system cannot be advanced even at a small angle, and the rotational phase of the eccentric weight of the system A cannot be delayed from the rotational phase of the eccentric weight of the system B ( (Due to the phase difference limitation shown by the chain line in FIG. 1). This characteristic will be abbreviated as "system A cannot lag behind system B", and will be tentatively called the third law for convenience of the following description. Therefore, in this third law, when saying "system A cannot be delayed more than system B", it also means "system B cannot advance more than system A. As a result, system B is rotationally driven. When it rotates, the A system rotates while pushing the A system so as not to be delayed (even when rotating at a constant speed, rotational energy lost due to friction and vibration is replenished from the B system to the A system). Looking at this with respect to the A system, it is in a driven state in which it is rotated by the B system without being delayed while being pushed.

(4) In the state where the third law is working (the system A is being pushed by the system B so as not to be delayed), the phase difference between both systems A and B is zero. Therefore, the total eccentric moment of the eccentric weights of both systems is in the maximum state. This phenomenon is "when the third law is working, the total eccentric moment becomes the maximum value."
For convenience of description below, this is tentatively called the fourth law.

Considering the state before the start of operation shown in FIG. 1, the eccentric weights 39A and 39 of both the A and B systems are considered.
A ', 39B, and 39B' are in the postures in which their centers of gravity are located directly below the rotation axis for the same reason as that of the pendulum that receives gravity. That is, the eccentric weights of both the A and B systems have no rotational phase difference and are in the maximum eccentric moment. Therefore, if the rotation is started while maintaining this state (rotational phase difference 0), there is a high possibility that the vibration pollution described in FIGS. 8 and 9 above may occur or the crane boom may be damaged. In order to prevent such a problem, as shown in FIG. 1, the B system is stopped (that is, the B system is driven and the driven switching valve 38B is closed), and the A system Drive / driven switching valve 33A
Open. At this time, the brake valves 35 for both A and B systems
Keep A and 35B closed. By the above operation, the eccentric weights 39A and 39B 'of the B system start to rotate while the eccentric weights 39B and 39B' of the B system remain stopped.

FIG. 2 illustrates the apparatus of the present embodiment in a state in which the hydraulic motor of the A system is rotated from the state shown in FIG. 1 to rotate the eccentric weight of the A system to complete the operation preparation. It is a schematic diagram. Since the A system is rotationally driven while the B system is stopped, only the A system starts to rotate, but the phase difference between the synchronous transmission gear 38A of the A system and the synchronous transmission gear 38B of the B system is limited (see FIG. 1). The engagement of the stopper arc groove 38Aa and the stopper projection 38Ba shown in Fig. 2) and the above-mentioned first law work, and as shown in Fig. 2, the rotational phase difference between the eccentric weights of both the A and B systems is approximately 180 degrees. In this state, the system A is rotationally driven by the hydraulic motor 32A, and the system B is driven to rotate via the stopper mechanism. Since the stopper mechanism comes into contact with about half a turn,
It starts to work when the rotation speed is still low. Therefore, there is no risk of impact damage. When the hydraulic motor 32A of system A is rotationally driven, the number of rotations is accelerated, and accordingly, the number of rotations of system B is also accelerated. At this time, the brake valve 35B is opened so that the braking force does not act on the B system. The hydraulic motor 32B of the B system rotates in a driven state and acts as a hydraulic pump to circulate the oil in the B system.
No load is applied because valve 5B is opened.

Although FIG. 2 illustrates the operation ready state, the state in which the vehicle is being accelerated as described above is the same as in FIG. This accelerating state corresponds to the arrow c in FIG. 9 described above. In this way, the point o at 0 rpm
To the point i corresponding to the rated rotation speed, the rotational phase difference between the A and B systems is maintained at 180 degrees by the first law, so that the total eccentric moment of the eccentric weight is determined by the second law. Kept to a minimum. (Refer to FIG. 9) In the state where the total eccentric moment is the minimum, the rotation speed region corresponding to the natural frequency n ₁ of the ground and the rotation speed region corresponding to the natural frequency n ₂ of the crane boom are passed. There is no risk of vibration pollution due to resonance, and there is no risk of resonance damage to the crane boom, and acceleration is reached to point i corresponding to the rated speed.

Next, from point o to point i in FIG.
The total eccentric moment of the eccentric weight in the accelerated state indicated by the arrow c will be considered in detail. When considering only vibration pollution prevention and crane boom damage prevention, point o
From point to point i, accelerate with zero total eccentric moment,
It suffices if the maximum total eccentric moment is set at the point i, but in the actual problem, it is not necessary to make the total eccentric moment zero, and the work cannot be performed at zero eccentric moment. In other words, like the pile 7 drawn with a solid line in FIG. 8, the pile 7 does not penetrate into the ground just by standing the pile to be laid on the ground. Therefore, the pile 7 and the vibrating device 6
In addition to the gravitational load of the crane boom, while giving a weak vibration that does not cause pollution, while passing the ground natural frequency n ₁ of FIG. 9 and giving a weak vibration that does not cause resonance damage to the crane boom 5, the crane boom Must pass the natural frequency n ₂ of. Further, if the resonance frequencies n ₁ and n ₂ are passed, there is no particular inconvenience even if the total eccentric moment is increased before reaching the point i corresponding to the rated speed. From this point of view, the end point of the operation for continuing the operation in the state of the minimum total eccentric moment does not necessarily have to be the time when the rotation speed reaches the rated rotation speed n ₃ , and the predetermined rotation speed set lower than the rated rotation speed. The total eccentric moment may be increased when the rotation speed reaches, and the total eccentric moment may be increased when a predetermined time (2.5 seconds, for example) elapses after the rotation starts at the point o.

Frequency n corresponding to the natural vibration shown in FIG.
The problem of how much the total eccentric moment should be set when passing ₁ and n _{2 is} that the value of "a little less than 180 degrees", which is the allowable angle at which the system A can lead the system B, is more specific. Related to making decisions. As a designing technique in this case, the present invention introduces a comparison setting with the gravitational acceleration g (980 cm / sec ² ). That is, in FIG. 8, when the vertical vibration acceleration applied to the vibration system in which the vibration device 6 and the pile 7 are coupled is less than g, the position of the center of gravity of the vibration system, which is the load of the exciter, is It remains stationary. When the applied vibration acceleration exceeds g, the center of gravity of the vibration system starts to vibrate vertically.

The minimum vibration force to be set depends on the ground condition, the pile specifications, the condition of nearby private houses and the crane boom strength, but the minimum vibration force is almost the same. The allowable phase difference range of the eccentric weights of both the A and B systems is set so that the gravitational acceleration is g. in this case,
The total eccentric moment when the phase difference between both A and B systems is 180 ° -α and the total eccentric moment when the phase difference is 180 ° + α are equal, but the phase difference is 180
180 degrees because there is no rational meaning to making it more than degrees
It is desirable to set it to -α. However, 180 ° + α
Even if it is configured as described above, it is inevitable to belong to the technical scope of the invention.

As described with reference to FIG. 2 above, when the acceleration is finished in the state of the minimum total eccentric moment, the total eccentric moment is maximized and the motor is steadily operated at the rated rotation speed in the state of maximum excitation force. . FIG. 3 is a schematic diagram of a state in which the maximum vibration force is generated by shifting to the steady operation through the state shown in FIG. 2 above. In FIG. 2, when accelerating both the A and B systems, the A system was rotationally driven, but in the steady operation, as shown in FIG. 3, the drive / driven switching valve 33B of the B system is opened and the hydraulic motor of the B system is driven. 32B is rotationally driven, and the drive / driven switching valve 33A of the A system is closed to stop the rotational driving of the hydraulic motor 32A. As a result, the system A is driven by the system B via the stopper mechanism. The brake valve 35A of the A system is opened so as not to brake this driven rotation. In the state of FIG. 3, the third law described above (A does not lag behind B) works, the phase differences of both A and B systems coincide, and the total eccentric moment becomes maximum (fourth law).

In this embodiment (FIG. 3), the entire system is driven by the hydraulic motor 32B of system B, and the hydraulic motor 32A of system A is idle. Although not shown in the drawing, the hydraulic motor 32A of the A system is not left idle, and is connected in series or in parallel with the hydraulic motor 32B of the B system to connect “A”.
It is also possible to generate rotational power also to the hydraulic motor 32A of the A system while the system is being pushed from the B system, that is, while the A system is being assisted by the B system via the stopper mechanism. By doing this, the hydraulic motor 32B of the B system
It is possible to increase the excitation force as compared with the isolated operation (FIG. 3).

As described above (FIG. 3), after carrying out the steady operation while exerting the maximum excitation force, when the operation is stopped, the total eccentric moment is minimized to reduce the excitation force as described below. The speed is reduced to the minimum (for example, approximately equal to the gravitational acceleration g). FIG. 4 is a schematic diagram of a state in which the vibration force is minimized to perform braking / deceleration as the next step of the state shown in FIG. 3 described above. The drive / driven switching valves 33A and 33B of both A and B systems are closed, and the supply of hydraulic energy to the hydraulic motors 32A and 32B of both A and B systems is stopped. At this time, the brake valve 35A of the A system is opened to release the hydraulic braking to the hydraulic motor 32A of the A system, and the brake valve 35B of the B system is closed to operate the hydraulic motor 32B of the B system (at this time, it operates as a hydraulic pump). The discharged oil of (1) is guided to the brake circuit 34B to apply pressure to brake the hydraulic motor 32B. As a result, the braking force is applied only to the B system, but the first law described above acts and the rotational phase difference of the eccentric weights of both the A and B systems becomes approximately 180 degrees, and the total eccentricity is obtained by the second law. Decelerates and stops with the minimum moment. In the example shown in FIG. 4, A
Although the braking force is not applied to the hydraulic motor of the system, as an embodiment different from this, the braking may be applied to the A system, though not shown. In this case, it is necessary to make the braking force applied to the A system weaker than the braking force applied to the B system so as not to prevent the establishment of the first law and the second law.

FIG. 5 is a schematic system diagram showing a modified example of the drive / control device according to the embodiment shown in FIG. The difference from FIG. 1 is that the dedicated drive / driven switching valves 33A and 33B are integrated into both the A and B systems,
The drive / driven switching valve 33 common to both the A and B systems is provided. In the case of such a configuration, the required condition of the drive / driven switching valve 33 is at least a 6-port type and at least a 3-position type. The reason is that there are a total of 6 ports, two ports for connecting to the hydraulic motor of system A, two ports for connecting to the hydraulic motor of system B, and two ports for connecting to the hydraulic pump. What you need. This is because it requires three positions: an operation start (acceleration) operation position, a steady operation position, and an operation end (braking / deceleration) position.

FIG. 6 shows a modified example of the drive / control device according to the embodiment shown in FIG. 1 mentioned above, and a drive provided with a stopper mechanism for limiting the rotational phase difference between the drive gears of both A and B systems. -It is a schematic diagram of a control device. The difference from FIG. 1 is that the drive gear 3 directly connected to the hydraulic motor of system A is not directly limited to the rotational phase difference between the synchronous transmission gears.
6A and the drive gear 36 directly connected to the hydraulic motor of the B system
That is, a stopper mechanism (not shown) is provided so as to limit the rotational phase difference from B. With such a configuration (FIG. 6), the basic operating principle is the same as in the embodiment of FIG. 1, but the following matters should be noted.
That is, the drive gears 36A and 36B and the driven gear 37
Since the reduction gear ratios of A and 37B are not always 1: 1, "As a result, the driven gears are limited to each other within a permissible angular range set between 0 and 180 degrees. The stopper mechanism (not shown) must be configured to limit the rotational phase difference between the drive gears 36A and 36B.

[0043]

When the drive / control device for an exciter according to the present invention as described above is constructed and the drive / control method according to the present invention is applied, the drive / transmission system of the A system and the drive / control system of the B system are operated. With a simple structure of providing a stopper mechanism that limits the rotational phase difference with the transmission system to within an allowable angle range set between 0 and 180 degrees, it does not require servo control over the entire rotational speed,
At the time of rotational acceleration at the start of operation and at the time of rotational deceleration at the end of operation, the ground natural frequency range and crane boom natural frequency range are passed in the state of "minimum vibration force".
It is effective in preventing vibration pollution and crane boom damage. Further, since it is not necessary to synchronize the A system hydraulic motor and the B system hydraulic motor by gears, it is possible to reduce noise pollution due to meshing of the gears, which is an excellent practical effect.

[Brief description of drawings]

FIG. 1 is a diagram showing an example of an embodiment of a drive / control device for a vibration exciter according to the present invention, in which a hydraulic system is attached to a schematic drawing of a vibration generating mechanism. It represents the state.

FIG. 2 is a schematic diagram illustrating the device of the present embodiment in a state in which preparation for operation is completed by rotating the hydraulic motor of the A system from the state shown in FIG. 1 to rotate the eccentric weight of the A system. Is.

FIG. 3 is a schematic diagram of a state in which a maximum vibration force is generated by shifting to a steady operation through the state shown in FIG. 2 above.

FIG. 4 is a schematic diagram of a state in which an exciting force is minimized to perform braking / deceleration as a process subsequent to the state shown in FIG. 3 described above.

5 is a schematic system diagram showing a modified example of the drive / control device according to the embodiment shown in FIG. 1 above.

FIG. 6 shows a modified example of the drive / control device according to the embodiment shown in FIG. 1, and a drive / control device provided with a stopper mechanism for limiting the rotational phase difference between the drive gears of both A and B systems. FIG.

FIG. 7 is an explanatory diagram of a rotary exciter in which an eccentric weight is attached to each of four rotary shafts.

FIG. 8 is an explanatory diagram showing transmission of ground waves and underground waves in pile driving work using a vibration device.

FIG. 9 is a chart showing time-rotation speed for explaining a resonance phenomenon in a vibrating pile driving work.

FIG. 10 (A) is an explanatory view of a drive system of a vibration generator of a conventional example, and (B) and (C) are explanatory views of a drive system in the present invention.

11A and 11B are explanatory views of the basic principle of the invention of the prior application, and FIG. 11C is a symbol mark of the vibration unit.
(D) is a symbol mark of the vibration generating unit with a rotary encoder.

FIG. 12 is a schematic system diagram showing one embodiment of a drive / control device for a vibration exciter according to the invention of the prior application.

[Explanation of symbols]

1: Exciter case, 2A-2D: Rotating shaft, 3A-3H
... Eccentric weights, 4A-4H ... Transmission gears for synchronous rotation, 5 ...
Crane boom, 6… vibration device (vibrator), 7… pile, 8
… Private house, 9I, 9J… Gears, 31… Hydraulic pump, 32
A, 32B ... Hydraulic motor, 33, 33A, 33B ... Drive / driven switching valve, 34A, 34B ... Brake circuit, 35
A, 35B ... Brake valve, 36A, 36B ... Drive gear,
37A, 37B ... Driven gears, 38A, 38B ... Synchronous transmission gears, 39A, 39A ', 39B, 39B' ... Eccentric weights.

Claims (14)

[Claims] 1. A hydraulic motor (32A) having a drive / transmission system consisting of two systems, an A system and a B system, for rotationally driving a drive gear (36A) of the A system, and a drive gear of the B system ( 36B) includes a hydraulic motor (32B) for rotationally driving the driven gear (37A) that meshes with the drive gear (36A) of the A system, and a synchronous transmission gear that meshes with the driven gear (37A) and rotates synchronously. 38A), a driven gear (37B) that meshes with the drive gear (36B) of the B system, and a synchronous transmission gear (38B) that meshes with the driven gear (37B) and rotates synchronously. An eccentric weight (39) attached to each of the gear (37A) and the synchronous transmission gear (38A).
A, 39A '), and an eccentric weight (39B, 39B') attached to each of the driven gear (37B) and the synchronous transmission gear (38B) of the B system, wherein the A system A stopper mechanism is provided for limiting the rotational phase difference between the synchronous transmission gear (38A) of No. 1 and the synchronous transmission gear (38B) of the B system within the allowable angle range set between 0 degree and 180 degrees. The drive / control device for the vibration exciter. 2. A brake circuit for connecting an inflow side and an outflow side of the hydraulic motor to the hydraulic circuit of the hydraulic motor (32A) of the A system and the hydraulic circuit of the hydraulic motor (32B) of the B system, respectively. 34A, 34B) are provided, The drive-control device of the vibration exciter of Claim 1 characterized by the above-mentioned. 3. A brake circuit for both the A and B systems (34)
A, 34B) is provided in parallel with each brake valve (35A, 35B) having a function as a hydraulic on-off valve. Control device. 4. A drive / driven switching valve (33A) having a function as a hydraulic on-off valve is provided between the hydraulic motor (32A) of the A system and the hydraulic pump (31), and the hydraulic pressure of the B system is provided. The drive / driven switching valve (33B) having a function as a hydraulic on-off valve is provided between the motor (32B) and the hydraulic pump (31). The drive / control device for the vibration exciter according to any one of 1. 5. Between the A system hydraulic motor (32A) and the B system hydraulic motor (32B) and the hydraulic pump (31) shared by both the A system and the B system, the system is shared by both the A and B systems. 4. A drive for a vibration exciter according to any one of claims 1 to 3, characterized in that a drive / driven switching valve consisting of at least a 6-port 3-position directional control valve is provided. ·Control device. 6. The stopper mechanism for limiting the phase difference between the A-system synchronous transmission gear (38A) and the B-system synchronous transmission gear (38B) has a structure for limiting the maximum rotational phase difference as follows. The drive / control device for the vibration exciter according to claim 1, wherein When the rotational phase difference is maximized, the eccentric moments of the eccentric weights of both the A and B systems become the minimum values, and the vibration force in the state of the minimum eccentric moment is "The vibration system including the vibration generator and its vibration load receives The “vibration acceleration” is almost equal to the gravitational acceleration g. 7. A synchronous transmission gear (3) for both the A and B systems.
8A, 38B) is provided with a stopper mechanism for limiting the rotational phase difference between the A system drive gear (36A) and the B system drive gear (36B).
The drive / control device for the vibration exciter according to claim 1. 8. A hydraulic motor (32A) having a drive / transmission system comprising two systems, an A system and a B system, for rotationally driving a drive gear (36A) of the A system, and a drive gear (36B) of the B system. ) Is driven to rotate, and a driven gear (37A) that meshes with the drive gear (36A) of the A system and a synchronous transmission gear (38A) that meshes with the driven gear (37A) and rotates synchronously. ), A driven gear (37B) that meshes with the drive gear (36B) of the B system, and a synchronous transmission gear (38B) that meshes with the driven gear (37B) and rotates synchronously, the driven gear of the A system. (37A) and an eccentric weight (39) attached to each of the synchronous transmission gears (38A).
A, 39A ') and an oscillating machine having eccentric weights (39B, 39B') attached to the driven gear (37B) and the synchronous transmission gear (38B) of the B system, respectively. A method for limiting a rotational phase difference between the A-system synchronous transmission gear (38A) and the B-system synchronous transmission gear (38B) within an allowable angle range set between 0 and 180 degrees. A mechanism is provided, and the hydraulic motor (32A) of the A system is slowly rotated to advance the rotation phase of the A system, and the eccentric weights (39A, 39A) of the A system are advanced.
A ') and the eccentric weights (39B, 39B') of the B system are set to approximately 180 degrees to make the eccentric moment minimum, and the hydraulic motor (32A) of the A system is operated to operate the A system. The system B is driven to rotate via the stopper mechanism to accelerate the rotation of both systems A and B, and then the hydraulic energy supply to the hydraulic motor (32A) of the system A is reduced or stopped. While operating the A system inertially, the hydraulic motor (32B) of the B system is driven to drive the rotation of the B system, and the rotation phase of the B system delayed from the A system is almost 180 degrees.
The phase difference is advanced so that the rotational phase difference is 0 to maximize the eccentric moment, and the hydraulic motor of system B (32
By continuing the rotation drive of B) and regulating by the stopper mechanism described above, A system and B
Drive and control of an exciter characterized by performing synchronous rotation with the system and generating a maximum excitation force in a state where the eccentric weights of both systems A and B have a rotational phase difference of 0, and shifting to steady operation. Method. 9. A hydraulic pump (31) shared by both the A and B systems, during which the rotational phase difference between the eccentric weights of the A and B systems is zeroed and a steady operation is performed with the maximum excitation force. The pressure oil discharged from the hydraulic system is supplied to the hydraulic motor (32A) of the A system and the hydraulic motor (32B) of the B system connected in series to these hydraulic motors. The method for driving and controlling the exciter described in. 10. A hydraulic pump (31) shared by both the A and B systems, during which the rotational phase difference between the eccentric weights of the A and B systems is zeroed and the steady operation is performed with the maximum vibration force. The pressure oil discharged from the hydraulic system is supplied to these hydraulic motors in a state where the hydraulic motors (32A) of the A system and the hydraulic motors (32B) of the B system are connected in parallel. The method for driving and controlling the exciter described in. 11. The pressure oil is supplied to the hydraulic motor (32B) of the B system while the rotational phase difference between the eccentric weights of the A and B systems is zeroed and the steady operation is performed with the maximum vibration force. 9. The drive / control method for an exciter according to claim 8, wherein rotational energy is supplied from the B system to the A system via the stopper mechanism while rotationally driving the B system. 12. The hydraulic energy is supplied to the hydraulic motor (32A) of the A system after performing a steady operation while generating the maximum motive force in a state where the rotational phase difference between the eccentric weights of the A and B systems is 0. Stop and rotate the rotating member of the A system inertially, and apply hydraulic braking to the hydraulic motor (32B) of the B system to decelerate the rotational phase of the B system compared to the A system by about 180. To minimize the vibration force and apply the braking force to the A system by the B system via the stopper mechanism, while setting the rotational phase difference of the eccentric weights of the A and B systems to about 180 degrees. The method of driving and controlling a vibration exciter according to claim 8, characterized in that the method is performed by decelerating while maintaining the speed and stopping. 13. The hydraulic energy is supplied to the hydraulic motor (32A) of the A system after performing the steady operation while generating the maximum motive force in the state where the rotational phase difference of the eccentric weights of the A and B systems is 0. And hydraulic braking is applied to the hydraulic motor (32A) of the B system, and hydraulic braking is applied to the hydraulic motor (32B) of the A system more gently than the hydraulic braking of the hydraulic motor of the B system. The system according to claim 8, wherein the stopper means decelerates and stops both the A and B systems while maintaining the rotational phase difference of the eccentric weights of both the A and B systems at about 180 degrees. Drive and control method of shaker. 14. The deceleration force generated by the eccentric weights of both the A and B systems when decelerating while maintaining the rotational phase difference of the eccentric weights of both the A and B systems at about 180 degrees. 14. The drive of the vibration exciter according to claim 12 or 13, wherein the "vibration acceleration applied to the vibration load member to which the vibration force is applied" is controlled to be approximately the gravitational acceleration g.
Control method.