JPH0938575A - Rotary vibration generator and control method therefor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the strength balance of a bearing support by providing two transmission systems installed on the upper and lower sides and constituting each system by being made to have a pair of eccentric weight shafts to which an eccentric weight is fixed respectively and a driving motor. SOLUTION: In a rotary vibration generator equipped with two systems A, B having a pair of eccentric weights shafts S1 S2 ,; S3 , S4 to which eccentric weights W1 , W2 , W3 , W4 are fixed respectively and which rotate synchronously in the opposite direction to each other, the shaft arrangement is made upper and lower three step constitution in a vibration generator casing. The eccentric weights S1 , S2 of the system A are installed in the lower step, the eccentric weights S3 , S4 of the system B are installed in the intermediate step, and driving shafts equipped with motors M1 , M2 are installed horizontally in parallel respectively in the upper step. The driving shaft of the system A installed in the upper step and either one of the eccentric weight shafts S1 , S2 installed in the lower step age connected through an intermediate gear installed in the intermediate step.

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, the present invention can be applied to a rotary type vibration exciter other than a pile driving application, and a practical effect can be obtained in a non-piling driving application.

[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. 5 is a schematic explanatory view of this type of rotary type vibration exciter, in which four rotating shafts 2A, 2B, 2C, 2D are arranged for a case 1, and eccentric weights 3A, 3B, 3C and 3D are attached,
Gears 4A, 4B, 4C, and 4D are attached to each other and restrained so as to mesh with each other and rotate synchronously.

[0003]

When the pile driving work is performed using the above-mentioned vibration oscillating machine, prevention of vibration pollution and prevention of noise pollution are important problems. Next, a technical problem relating to vibration pollution will be described with reference to FIGS. Drawing 6 is a mimetic diagram for explaining vibration pollution in pile driving work. 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.

[0004] When starting the pile driving operation by bringing the lower end of the pile 7 into contact with the ground surface, when 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, which causes a 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 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. 7 is a chart showing the change 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 rotational state, frequency rises rapidly as indicated by the arrow c. During the above frequency rise, the natural frequency n ₁ of the ground,
And the natural frequency n ₂ of the crane boom. However, it because revolutions increase time T ₁ at the start operation is generally short (e.g., about 3 seconds), the problem of resonance when the frequency of the vibration device matches the natural frequency of practically negligible In some cases, it may be as minor as possible. However, at the time t ₂ when the energization of the motor (not shown) of the vibration device is stopped.
From between time t ₃ when the rotary shaft is stopped is gradually decelerated as indicated by the arrow d while continuing to rotate at a rotational axis of inertia.
Rotational speed reducing period T ₂ of the above, because it is a relatively long time unless added otherwise braking operation (e.g., about 50 seconds), passing through the natural frequency n ₂ of the crane boom on its way, the crane The boom may resonate and suffer damage. In addition, when passing through the natural frequency n ₁ of the ground, there is a possibility that vibration pollution may be supported by resonance of the ground. If it is possible to stop the energization of the motor at the time t ₂ and change the rotational phase of the eccentric weight of the vibration device to make the exciting force zero, the operation at the time of starting or stopping the operation of the vibration device can be performed. Problems with resonance 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.
When the rotation speed of the vibration device is increased, the speed is increased while generating vibrations by an eccentric weight (not shown) of the vibration device, and a large-capacity motor or a large-capacity power supply equipment (the motor , A large-scale hydraulic power source device is required. In this case, the operation is started in a state in which the oscillating force is reduced to zero by changing the rotation phase of the eccentric weight of the vibration device, and if the oscillating force can be exerted after reaching the rated rotational speed, the motor capacity is increased. It is economical because the power source capacity (or hydraulic power source capacity) can be reduced. After reaching the rated speed,
There is no need to store any more rotational energy in the rotating member, and operation can be continued by replenishing enough energy to compensate for vibration damping.

In order to increase or decrease the vibrating force while the operation is continued, there is a technique of providing two systems of eccentric weight rotation drive systems and controlling the two systems with the eccentric weight rotation drive system connected to each other. It has been proposed (for example, Japanese Patent Application No. 5-79797).
issue). However, there are technical difficulties described below regarding the arrangement of the eccentric weight shaft to which the eccentric weight is fixed and driven to rotate, and the dynamic support balance. FIG. 8 shows an eccentric weight shaft to which the eccentric weight is fixed, a synchronous transmission gear fixed to the eccentric weight shaft, a driving gear meshed with the synchronous transmission gear, and a motor for rotating and driving the driving gear. (A) is a case where the number of eccentric weights is one, (b) is a case where the number of eccentric weights is a pair, (c) ) Indicates the case where the number of eccentric weights is two pairs,
(D), (e) and (f) show that the number of eccentric weights is 2
It represents a pair and the case where the drive gear is disposed above or below the synchronous transmission gear, respectively.

If only vibration is to be generated, a single eccentric weight 9 is provided as shown in FIG. 8 (a), and a driving gear 10 rotated and driven by a motor M is meshed with a driven gear 11 '. Although it is sufficient to rotate it, it vibrates up and down and left and right, so it is difficult to put it to practical use. Therefore, when the two eccentric weights 9 and 9 'are arranged as shown in FIG. 9B, the two eccentric weights 9 and 9' rotate synchronously in the opposite direction at the same rotational speed, so that the right and left vibrating forces are canceled and vertical vibration occurs. I do. In this case, the illustrated gear 11 is a member similar to the above-described driven gear 11 ', but functions not as a mere transmission gear but as a synchronous transmission gear that also functions as a synchronous gear.

In the configuration shown in FIG. 1B, it is impossible to increase or decrease the vibrating force without changing the rotation speed of the motor M. Therefore, as shown in FIG. 8C, the eccentric weights W ₁ and W ₂ are fixed to the pair of eccentric weight shafts S ₁ and S ₂ , respectively,
As well as rotated by the motor M ₁ via a synchronous transmission gear 11, the same components as those described above for (c) diagram and disposed below the upper and lower two-stage structure, a pair of eccentric weight by fixing the shaft S _3, S ₄ of the eccentric to each weight W _3, W _4, when rotated by the motor M ₂ via the synchronous transmission gear 11, the rotational speed of the two motors M _1, M ₂ Can be adjusted to control the rotational phase difference between the eccentric weights W ₁ and W _{2 of} the upper system and the eccentric weights W ₃ and W ₄ of the lower system. For example, when a phase difference of 180 degrees is given from the state drawn by the solid line in FIG. 10C, the lower eccentric weights W ₃ and W ₄ are set to the positions W ₃ ′ and W ₄ ′ shown by the broken lines. Vibration force becomes almost zero. As described above, according to the configuration of FIG. 9C, the operation of increasing or decreasing the excitation force can be performed while continuing the operation of the excitation device without interruption.

However, in the configuration shown in FIG. 1C, the width Lx of the apparatus becomes large, so that the width Lx may be increased even if the height is increased, depending on the construction conditions of the construction using the vibration exciter.
In such a case, it may be necessary to reduce the length of the line. In this case, the structure shown in FIG. The components depicted in FIG. (D) are the same as those in FIG.
Only the arrangement is different. It can be easily understood that the width dimension can be reduced by using such an upper and lower three-stage structure (FIG. 8C).

However, according to the structure shown in FIG. 3C, the eccentric weight shafts S ₁ and S ₂ to which the eccentric weight is fixed and which receives a large centrifugal load are arranged in the upper stage and are similarly large. Since the eccentric weight shafts S ₃ and S ₄ that receive the centrifugal load are arranged in the lower stage, these four eccentric weight shafts S ₁ , S ₂ ,
S _3, (not shown) bearing the S ₄ it is difficult to take the strength balance of the structure supporting the entire exciter is large, a large weight in order to increase the rigidity of the structure.

The present invention has been made in view of the above circumstances, and is composed of two transmission systems, each system having a pair of eccentric weight shafts to which eccentric weights are fixed and a drive system. By improving the vibration exciter equipped with a motor, the bearing support has a good balance of strength, and a rotary exciter with a reduced lateral width is provided, and vibration pollution is prevented by using the rotary exciter. It aims at providing the control method for doing.

[0013]

FIG. 8 (e) and FIG. 8 corresponding to one embodiment of the basic principle of the rotary vibration exciter according to the present invention created to achieve the above object.
Brief description with reference to (f) is as follows. 1
The two transmission systems constituting the basic exciter will be named A system and B system for convenience of explanation. FIG. 8F illustrates the A system, and FIG. 8E illustrates the B system. When the configurations of these figures (e) and (f) are combined, 4
It functions as a single exciter composed of two eccentric weights, and by changing the rotational phase difference between both A and B systems, it is possible to reduce the excitatory force while continuing operation without interruption. Can be increased or decreased.

FIG. 8 (f), which depicts the A system, shows the positions of the main constituent members of the B system by broken lines, and FIG.
In (e), the positions of the main components of the A system are indicated by broken lines. Components of the B lineage drawn by the solid line in FIG. 8 (e) in FIG. 8 described as tentative above (d), be the same as component surrounded by a chain line, respectively eccentric weight W ₃ , W ₄ are attached to the pair of eccentric weight shafts S ₃ , S ₄ , respectively, and the synchronous transmission gears G ₃ , G ₄ are attached to each other, and the pair of synchronous transmission gears G ₃ , G ₄ mesh with each other. To rotate synchronously at the same rotational speed in the opposite direction,
It is adapted to be rotated by the motor M ₂ through b. In this way, the vibration generating mechanism portion of the B system is arranged in the middle stage and the drive motor thereof is arranged in the upper stage.

The system A drawn by a solid line in FIG. 8F has a pair of eccentric weights W ₁ and W ₂ , a pair of eccentric weight shafts S ₁ and S ₂ ,
A vibration generating mechanism portion including a pair of synchronous transmission gears G ₁ and G ₂ is arranged at a lower stage. Then, it is disposed in the upper and the drive motor M ₁ and the driving gear 10a. Then, the drive gear 10 a arranged in the upper stage and the synchronous transmission gear G ₁ arranged in the lower stage are transmitted via the intermediate gear 12. FIG. 8 (f) is a by the operating principle that schematically illustrates the eccentric rotational output of the upper motor M ₁ lower weight shaft S ₁
The transmission means is not necessarily limited to the intermediate gear 12, and for example, a transmission member such as a chain or a toothed belt (also known as a timing belt) can be used.

FIGS. 8 (e) and 8 (f) show a specific configuration of a rotary vibration exciter according to the present invention created on the basis of the principle described above. 3, the eccentric weights (W ₁ , W ₂ ) are fixed, and a pair of eccentric weight axes (S ₁ , S ₂ ) of the A-system that rotate synchronously in opposite directions to each other are respectively horizontal. And eccentric weights (W
₃ , W ₄ ) is fixed and rotates synchronously in opposite directions to each other 1
Arranged parallel to each other horizontally eccentric weight shafts of the pairs of B lineage (S _3, S ₄₎ respectively, and said drive shaft having a motor (M ₁₎ for rotating the A line (13a) and A drive shaft (13) provided with a motor (M ₂ ) for rotating the B system
In the rotary type exciter provided with b), the exciter casing (13) has a vertically arranged three-stage configuration, and a pair of eccentric weight shafts (S _1, S ₂₎
Are disposed, and a pair of eccentric weight shafts (S ₃ , S ₄ ) of the B system are disposed in a middle stage, and the two drive shafts (13a, 13b) are disposed in an upper stage, respectively. A system drive shaft (13a) arranged horizontally and parallel to each other and arranged in the upper stage, and a pair of eccentric weight shafts (S ₁ , S ₁ ) of the system A arranged in the lower stage One of the eccentric weight shafts in S ₂ ) is connected via a transmission member (12) arranged in the middle stage.

On the premise of the configuration of the rotary vibration exciter according to the present invention described above, the control method of the rotary vibration exciter according to the present invention created for using the rotary vibration exciter is a stationary method. As a preparatory operation for generating the maximum vibratory force,
The rotational phase of the eccentric weights (W ₁ , W ₂ ) of the system A and B
The phase difference between the rotational phase of the eccentric weights (W ₃ , W ₄ ) of the system is set to the maximum angle within the adjustable range, and the state of the vibrating force is minimized. Are rotated in synchronization with each other to increase the number of rotations thereof, and the above A, B
After the rotation speeds of both systems increase, the steady-state operation is performed in a state where the rotational phase difference between the eccentric weight of the A system and the eccentric weight of the B system is reduced to zero to generate the maximum vibrating force. And

The "adjustable range" in the operation of "making the phase difference the maximum angle within the adjustable range" has the following meaning. That is, the method of the present invention requires the use of the rotary vibration exciter according to the present invention as an essential requirement.
In the rotary vibration exciter according to the present invention, the rotational phase difference between the A and B systems may be restricted by the stopper means, and the adjustment of the rotational phase difference is not necessarily limited. is not. Further, even when the phase difference adjustment is not restricted, the phase difference cannot be set to a minus value equal to or less than zero. On the other hand, when the angle exceeds 180 degrees, the eccentric moment substantially increases, so that a meaningful phase difference of 180 degrees or more cannot be given. The adjustable range in the method of the present invention is:
It is intended to mean a range that is technically possible and allows for significant adjustment.

According to the configuration of the rotary vibration exciter according to the present invention described above, a pair of eccentric weight shafts to which the eccentric weights of the A system are fixed are arranged in the lower stage, and the eccentric weights of the B system are connected to Since the fixed pair of eccentric weight shafts is arranged in the middle stage, the eccentric weight shafts receiving a large centrifugal acceleration are positioned in the middle and lower stages so as to correspond to the vertices of substantially squares. Therefore, the bearing of the eccentric weight shaft and the structure supporting the bearing have good strength balance. In addition, since the two motors for rotating and driving the vibration generating mechanisms of the A, B and both systems are arranged in the upper stage to form a three-stage structure, the width of the exciter can be reduced. Thus, according to the configuration of the present invention, the A-system vibration generation mechanism located at the lower stage can be driven via the transmission member even if the A-system rotational drive motor is arranged at the upper stage. .

Although various types of mechanical elements can be used as the transmission member, the use of an intermediate gear is advantageous because the structure of the transmission system is simple and the structure of the support structure for the intermediate gear is easy. In this case, since the intermediate gear is necessarily located at the middle stage, the intermediate gear can be rotatably supported by the eccentric weight shaft of the B system arranged at the middle stage. When the middle eccentric weight shaft is also used as the intermediate gear shaft, the number of components can be reduced. The intermediate gear and the synchronous transmission gear rotating in the same direction as the intermediate gear among the two synchronous transmission gears arranged in the middle stage are opposed to each other, and the rotational phase difference between the opposed two gears is regulated. With such a means, the rotational phase difference between the eccentric weight of the system A and the eccentric weight of the system B can be controlled in a limited manner, so that operation control for preventing vibration pollution can be easily performed. When the rotary exciter according to the present invention described above is operated, according to the control method according to the present invention, the eccentric weight of the A system and the eccentric weight of the B system are used as a preparation operation for starting operation. Since the rotational speed is increased after the vibrating force is minimized by maximizing the rotational phase difference within the adjustable range, it may resonate with the ground or crane boom during the increase in the rotational speed. After increasing the rotation speed, the rotational phase difference between the eccentric weight of the A system and the eccentric weight of the B system is reduced to zero, and the maximum vibration force is exerted at the rated rotation speed. Steady-state operation can be performed.

[0021]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, a preferred embodiment of a rotary vibration exciter and a control method thereof according to the present invention will be described with reference to FIGS. FIG. 1 shows one embodiment of a rotary vibration exciter of the present invention having a three-tiered structure.
It is a top view of the upper part in an example. The power source mechanism of the exciter is arranged in the upper part, and 14 is a casing of the exciter. Exciter casing 1 described above
Reference numeral 4 is attached to a hanger box 16 via an anti-vibration rubber 15. The hanger box is a member that accommodates and supports the exciter casing 14 and is hung by a crane. A stopper rubber 17 is provided so that the exciter casing 14 limits the amount of torsional displacement around a vertical axis (perpendicular to the paper) with respect to the hanger box 16 and buffers the hanger box 16.

A drive shaft 13a to which a drive gear 10a for driving a system A vibration generating mechanism (to be described in detail later with reference to FIG. 3) is fixed, and a system B vibration generating mechanism (see FIG. 2). A drive shaft 13b to which a drive gear 10b for driving the drive shaft (described later) is fixed is rotatably supported on the exciter casing 14 horizontally and parallel to each other. The member denoted by reference numeral “k” in the drawing is a key. In FIGS. 1 to 3, regardless of the presence or absence of the reference numeral “k” in the drawings, the fact that the key is illustrated indicates that the shaft member and the rotating member are fixed to each other. The hydraulic motor M ₁ is mounted on one end of the drive shaft 13a of system A (details rotating output of the hydraulic motor is connected) Rutotomoni, rotary encoder 18a is mounted on the other end, similar to this to, together with the hydraulic motor M ₂ is attached to one end of the drive shaft 13b of the B lineage,
The rotary encoder 18b is mounted on the other end. In this embodiment, the hydraulic motors M ₁ ,
Was used M _2, the driving source is not necessarily limited to the hydraulic motor, it is possible to use the hydraulic pressure motor, such as a hydraulic motor. Hydraulic motors have disadvantages such as difficulty in maintaining lubrication compared to hydraulic motors and require special consideration for rust prevention, but water also has advantages such as better cooling efficiency and lower cost than oil. In particular, it has practical value in a vibration exciter for underwater pile driving work. Further, it is possible and useful to use an electric motor instead of the hydraulic motor. When a hydraulic motor is used, a hydraulic motor having a control mechanism capable of synchronously rotating the pair of hydraulic motors and adjusting the phase difference between the pair of hydraulic motors is used. When an electric motor is used, an electric motor provided with a control circuit having the same functions (synchronous rotation and phase difference adjustment) as the above control mechanism is used.

[0023] As represented in FIG. 1, a pair of drive shafts 13a, face h ₁ of the two vertical imaginary perpendicular to 13b,
assuming h _2, named a space sandwiched between the two vertical faces and the transmission space. This transmission space is divided into two in the thickness direction, one of which is referred to as an A-system transmission space and the other is referred to as a B-system transmission space. These transmission spaces are assumed not only in the upper part shown in FIG. 1 but also in FIG. 2 showing the middle part and FIG. 3 showing the lower part as shown in FIG. First,
The drawing reference symbols and the names of the constituent members shown in FIGS. 8 (e) and 8 (f), which are shown as a principle diagram, that is, the motors M ₁ and M ₂ , the eccentric weights W ₁ , W ₂ , W ₃ and W ₄ , Eccentric weight shafts S ₁ , S ₂ , S ₃ , S ₄ , and synchronous transmission gears G ₁ , G ₂ , G
₃ , G ₄ and the intermediate gear 12 are shown in FIG.
Corresponding to the drawing reference numerals and component member names written in FIGS.

As described above, the eccentric weight shaft receiving a large eccentric load is not provided in the upper part of this embodiment, and the hydraulic motor and the rotary encoder, which are relatively lightweight components, are provided. Has been established.

FIG. 2 is a plan view of the middle stage portion of an embodiment of the rotary exciter of the present invention having a three-stage configuration of upper and lower stages. In the middle stage, a pair of eccentric weight shafts S ₃ , S ₄ to which a pair of eccentric weights W ₃ , W ₄ of the B system are respectively fixed are arranged horizontally and parallel to each other. As represented in the figures, a pair of eccentric weight W _3, W _4, each have been divided into two for axial, divided two eccentric weight W _3, and the W ₃ , The two divided eccentric weights W ₄ , W ₄
, And a total of four eccentric weights are provided. Each of the divided eccentric weights is fixed to the vicinity of both ends of the eccentric weight shaft avoiding the transmission space and close to the bearing. The synchronous transmission gears G ₃ and G ₄ of the B system are meshed with each other to
It is installed in the transmission space of the system. 19 is a spacer for determining the positions of the gear and the eccentric weight. As can be easily understood in comparison with FIG. 1 depicting the upper stage and FIG. 2 depicting the middle stage, the drive gear 10 disposed in the transmission space of the B system is easily understood.
meshes b and the synchronous transmission gear G ₃ is caused to rotate at a constant speed in the direction opposite to the same G ₄ and the synchronous transmission gear G _3. The meshing relationship of these gears is exactly the same as that shown in FIG. Is transmission by the gears, the eccentric weight shaft S ₃ two eccentric secured to the weight W _3, the W ₃ and the eccentricity of the two secured to the weight shaft S ₄ eccentric weight W ₄ , it is rotated at the same rotational speed in the opposite direction to the same W _4.

As shown in this embodiment, the configuration in which the eccentric weight is divided and disposed near both ends of the eccentric weight shaft and disposed between the two divided eccentric weights is a rotary type. The present invention has been created based on technical conditions specific to an exciter. In the prior art, in general, it has been common sense to support the vicinity of the gear with a bearing in order to maintain the meshing state of the gear with high accuracy. However, in a rotary vibration exciter that must support the reaction force of the large centrifugal acceleration of the eccentric weight, the eccentric weight is mainly deflected by the eccentric weight shaft. By supporting the vicinity of the eccentric weight with a bearing, it is possible to reduce the bending of the shaft, and to maintain the meshing accuracy of the gear. Furthermore, in the rotary exciter, the rotational energy that the gear must transmit is
It is mainly the amount of energy for compensating for the damping of vibration, and the load on the gear is relatively light. In addition, as can be understood from an overall view of FIG. 2, the loads of the four bearings are evenly and symmetrically distributed. The strength balance of the machine casing 14 is also advantageous.

The intermediate gear 12 shown in FIG. 2 depicting the middle stage is the intermediate gear 12 described with reference to FIG. 8 (f), which is the principle diagram, and is a transmission member of the A system. The intermediate gear 12 is arranged in the A system transmission space, via the intermediate gear bearing 20, is rotatably supported by the eccentric weight shaft S _4. The synchronous transmission gear G ₄ and the intermediate gear 12 is configured to rotate in the same direction, and are rotated at the same rotational speed in the steady operating state, the phase difference within approximately an angle of 180 degrees as described later Controlled as given. Therefore, while projecting the stopper projection 12a to the intermediate gear 12, is provided an arc-shaped stopper groove Wa to be engaged with the stopper projection 12a, the synchronous transmission gear G ₄ and A strains of B lineage of the intermediate gear 12 The phase difference is restricted to within approximately 180 degrees, and as a result, the phase difference between the eccentric weight of the A system and the eccentric weight of the B system is restricted to within approximately 108 degrees.

FIG. 3 is a plan view of a lower portion of the rotary vibration exciter according to the embodiment of the present invention having a three-stage configuration of upper and lower stages. In the lower stage, a pair of eccentric weight shafts S ₁ , S ₂ to which a pair of eccentric weights W ₁ , W ₂ of the A system are fixed are arranged horizontally and parallel to each other. The fact that each eccentric weight is divided into two and fixed near both ends of the eccentric weight shaft is similar to the configuration of the middle stage shown in FIG. 2 described above. The synchronous transmission gears G ₁ and G ₂ of the A system are fixed to the eccentric weight shafts S ₁ and S ₂ , respectively, and meshed with each other to be disposed in the A system transmission space. One synchronous transmission gear G ₁ of said pair of synchronous transmission gear, an intermediate gear 12 meshes with the A strains are located in the middle of FIG. 2, are arranged in the upper stage shown in FIG. 1 It is rotated by the hydraulic motor M ₁ of system a via the drive gear 10a of system a to have. The meshing relationship of these gears is as shown in FIG. 8 (f), which is the principle diagram and is shown above.

The width of the transmission space in the embodiment shown in FIGS. 1 to 3 is set to be two to three times the tooth width of the synchronous transmission gears G _{1 to} G ₄ . The reason is as follows. A and B
Since the transmission energy and the consumed energy are almost equal to those of the system, it is reasonable that the transmission gears of both the A and B systems have the same tooth width and the same module.

As shown in FIG. 1 to FIG. 3, the transmission space is divided into two sections each having a width dimension, and an A-system transmission space and a B-system transmission space are assumed. disposing a synchronous transmission gear G ₁ ~G ₄ into the space. Therefore,
The width of the transmission space needs to be at least twice the tooth width of the synchronous transmission gear. Although the synchronous transmission gears can be arranged no less than twice or any number of times, if the width of the transmission space is made unnecessarily large, the lateral width of the exciter will be increased unnecessarily. In consideration of these circumstances, it divided two eccentric weight (eg W ₁ and W _1, W ₂
It is appropriate that the distance between W ₂ ) and W ₂ ) is set to be twice or more and three times or less the tooth width of the synchronous transmission gear.

In order to further reduce the width of the rotary vibration exciter of the embodiment described with reference to FIGS. 1 to 3, teeth which can function as a part of a synchronous transmission gear are provided on the outer periphery of the eccentric weight. It is effective to form the synchronous transmission gear and the eccentric weight on a plate. FIG. 4 is a perspective view illustrating a synchronous transmission gear and an eccentric weight in an embodiment different from the above. A part of the outer periphery of the eccentric weight W ₁ ′ of the present example is provided with teeth having the same shape and dimensions as the synchronous transmission gear G ₁ ′ to make the modules equal to each other, so that the tooth is synchronized with the eccentric weight W ₁ ′. The transmission gear G ₁ ′ is integrally connected.

This figure illustrates a member in which a synchronous transmission gear G ₁ ′, an eccentric weight W ₁ ′ and an eccentric weight shaft S ₁ ′ are connected. By replacing this member (FIG. 4) with the “assembly of the eccentric weight W ₁ , the synchronous transmission gear G ₁ and the eccentric weight shaft S ₁ ” in the embodiment (FIGS. 1 to 3), The width dimension of can be shortened. However, all of the four eccentric weights W _{1 to} W ₄ , the four synchronous transmission gears G _{1 to} G _4, and the four eccentric weight shafts S _{1 to} S ₄ in the embodiment are shown in FIG. It is necessary to replace it with a single-body member shown in FIG. The reason is that even if the width of three or less of the four vibration generating members is reduced, the actual effect is not exerted, and the vibration is generated only when the width of the front of the four vibration generating members is reduced. This is because the shape and dimensions of the machine casing can be reduced.

Next, one example in which the rotary exciter of the embodiment shown in FIGS. 1 to 3 is constructed and the control method according to the present invention is carried out is shown in FIG. , Fig. 8
Explaining with reference to (f), it is uncertain what position the eccentric weights W ₁ and W ₂ and the eccentric weights W ₃ and W ₄ are located immediately before the work is started. Due to the fact that it is subjected to gravity, it is usually in a downward posture as shown by the solid lines in FIGS. 8 (e) and 8 (f). From the above state, by rotating the motor M ₁ relatively slowly, the figure 8
As shown by the dotted line in (e), the eccentric weight of the A system is set at the position of W ₁ ″ and W ₂ ″. That is, a phase difference of half a rotation (180 degrees) is given to the eccentric weights W ₃ and W _{4 of} the B system. In such a state, the system A and the system B are driven to rotate by the motors M ₁ and M ₂ , respectively, while maintaining the above-mentioned phase difference, thereby increasing the speed. When this operation is applied to FIG. 7 described above, at the point o of zero rotation speed (zero frequency) immediately before the start, the phase difference between the A and B systems is 180 degrees.
Vibration does not occur because the vibrating forces of both systems A and B cancel each other. In this state, the rotational speed is increased as indicated by arrow C and reaches the rated rotational speed (point i). When this point i is reached,
A difference is given to the rotations of the motors M ₁ and M ₂ of both the A and B systems, and A
When the phase difference between the eccentric weights W ₁ , W ₂ of the system and the eccentric weights W ₃ , W ₄ of the B system is set to zero (the state drawn by a solid line in FIGS. 8E and 8F), The total eccentric moment becomes maximum,
The operation shifts to rated operation while constantly exhibiting the maximum vibrating force.

According to the operation described above with reference to FIG. 7, the point o to the point i in a state where the phase difference is 180 degrees (excitation force is zero).
(Arrow c), the resonance point n ₁ ,
the n ₂ fear is not that or the crane boom or cause vibration pollution by resonating damage from passing through.

As described above, the phase difference between the A and B systems is 1
The operation of setting the angle to 80 degrees or zero is performed by the rotary encoders 18a and 18b shown in FIG.
This can be implemented by controlling the rotations of the motors M ₁ and M ₂ while detecting the rotation phases of both B systems. In this case, if the rotational phase difference between A and B and both systems is restricted to 0 degree or more and 108 degrees or less by the stopper protrusion 12a and the stopper groove Wa shown in FIG. be able to.

In the embodiment of the control method described above with reference to FIG. 7, the operation is started from the point o with no vibrating force,
After passing through the resonance frequencies n ₁ and n ₂ , the driving force was maximized at the point i and the operation was constantly performed with the maximum driving force. This is a basic operation, there are various application examples as described below,
Each application has a unique effect. (A) The vibrating force at the start of the operation at the point o is not necessarily required to be zero, but rather, it may be necessary to exert a slight vibrating force. The reason is that, for example, when the pile 7 is hung upright on the ground and the casting is started as shown by a solid line in FIG. 6, under normal working conditions, the pile 7 is buried under the ground only by gravity load. It is impossible to sink, and the ground wave a starts the operation from the point o (or from the vicinity of the point o) by giving a slight vibration within a range that does not damage the private house 8, and the underground wave This is because the pile 7 must be driven to a depth where b does not cause pollution. In such a case, the present invention considers the gravitational acceleration g as a guide for setting the magnitude of vibration applied to the pile from the exciter. If the vibration acceleration given to the vibration system including the exciter and the load member (pile, chuck, etc.) is equal to or less than the gravitational acceleration g, the pile does not generate any apparent vibration. Therefore, the vibrating force is set to substantially g, or g
By starting operation in the following manner, it is possible to prevent pollution at the beginning of operation. The range of “substantially” in the case of “substantially g” is a range where no pollution occurs when the lower end of the pile is located near the ground surface. (B) In the case where the frequency (rotational speed) is increased as indicated by arrow c in FIG. 7, even if the frequency does not reach point i in the figure, if n ₁ and n ₂ corresponding to the resonance frequency are passed, Even if the vibrating force is increased before reaching the point i, no problem occurs. If the timing for increasing the excitation force is accelerated in this way, the capacity of the pile driving work is increased. In this case, as a specific method of setting the timing for increasing the excitation force, the excitation force is increased when a predetermined time has elapsed since the operation was started at point o using a timer device (not shown). Alternatively, the rotational speed may be detected by the rotary encoders 18a and 18b shown in FIG. 1 and the vibrating force may be increased when the rotational speed reaches a predetermined rotational speed less than the rated rotational speed.

(C) In FIG. 7, after the pile driving work is performed in a state where the vibrating force is maximum from the point i to the point j, the driving of the motor is stopped at the point j to enter an inertial rotation state, or the motor is braked. Also, when the number of rotations is decreased (arrow d) and stopped at the point m, the procedure is the reverse of the operation at the time of starting and increasing the speed (arrow c). That is, a phase difference is generated between the A-system and the B-system rotating at the rated speed at the point j, a rotation phase difference of approximately 180 degrees is given, the vibrating force is almost zero, and deceleration operation is started. . As a result, the vibrating force can pass through the points n ₂ and n ₁ corresponding to the resonance frequency in a state where the vibrating force is minimized, thereby preventing the vibration pollution and the crane boom breakage.

(D) The structure of the ground is generally irregular,
Construction conditions change. Therefore, it is desirable to generate as large a vibration as possible within a range where the vibration does not cause actual harm, in order to improve the efficiency of the pile driving work. From such a viewpoint, the rotational phase difference θ between the eccentric weight of the A system and the eccentric weight of the B system during the speed-up operation of the arrow c or the deceleration operation of the arrow d in FIG. 180 ° ……… (1) Maintaining a constant value in the range of (1) and setting the exciting force to a moderate value between the maximum and minimum to perform pile driving work in order to achieve both pollution prevention and efficiency improvement. It is effective for Controlling the vibrating force to either the maximum or the minimum, that is, setting the rotational phase difference between the eccentric weights of both the A and B systems to the maximum or the minimum is shown in FIG. Stopper protrusion 12a
However, in order to maintain the rotational phase difference at an arbitrary angle as in the above equation 1, the rotary encoders 18a, 18b (or 18b) shown in FIG. (A member corresponding to this) to detect the rotation angle position, and the hydraulic motor M ₁ and the hydraulic motor M ₂ can increase or decrease the rotational speed respectively, and the hydraulic motors M ₁ and M ₂ are the same. It is necessary to have a hydraulic control mechanism capable of rotating at a rotational speed.

[0039]

According to the rotary vibration exciter of the present invention, A
Since a pair of eccentric weight shafts to which the eccentric weights of the system are fixed are arranged in the lower stage, and a pair of eccentric weight shafts to which the eccentric weights of the B system are fixed are arranged in the middle stage, the size is large. The eccentric weight axes receiving the centrifugal acceleration are positioned at the middle and lower stages so as to correspond to the vertices of substantially squares. Therefore, the bearing of the eccentric weight shaft and the structure supporting the bearing have good strength balance. In addition, since the two motors for rotating and driving the vibration generating mechanisms of the A, B and both systems are arranged in the upper stage to form a three-stage structure, the width of the exciter can be reduced. Thus, according to the configuration of the present invention, the A-system vibration generation mechanism located at the lower stage can be driven via the transmission member even if the A-system rotational drive motor is arranged at the upper stage. .

Various mechanical elements can be applied as the above-mentioned transmission member. However, the use of an intermediate gear is convenient because the structure of the transmission system is simple and the structure of the support structure for the intermediate gear is easy. In this case, since the intermediate gear is necessarily located at the middle stage, the intermediate gear can be rotatably supported by the eccentric weight shaft of the B system disposed at the middle stage. When the middle eccentric weight shaft is also used as the intermediate gear shaft, the number of components can be reduced. The intermediate gear and the synchronous transmission gear that rotates in the same direction as the intermediate gear among the two synchronous transmission gears arranged in the middle are opposed to each other, and the rotational phase difference between the opposing gears is regulated. By providing the means for controlling, the rotational phase difference between the eccentric weight of the A system and the eccentric weight of the B system can be controlled in a restricted manner, so that operation control for preventing vibration pollution can be easily performed. When operating the rotary shaker according to the device of the present invention described above,
According to the control method of the present invention, as a preparatory operation for starting operation, the rotational phase difference between the eccentric weight of the A system and the eccentric weight of the B system is maximized within an adjustable range to minimize the vibrating force. Since the rotation speed is increased after the state is maintained, there is no danger that trouble will occur due to resonance with the ground or the crane boom during the rotation speed increase. An excellent practical effect is achieved in that the rotational phase difference between the eccentric weight and the eccentric weight of the B-system can be reduced to zero and steady operation can be performed at the rated rotation speed while exhibiting the maximum vibrating force.

[Brief description of drawings]

FIG. 1 is a plan view of an upper portion of a rotary vibration exciter according to an embodiment of the present invention having a three-stage configuration of upper and lower parts.

FIG. 2 is a plan view of a middle portion of the rotary vibration exciter according to the embodiment of the present invention having a three-tiered structure.

FIG. 3 is a plan view of a lower portion of the rotary vibration exciter according to the embodiment of the present invention having a three-stage configuration of upper and lower stages.

FIG. 4 is a perspective view illustrating a synchronous transmission gear and an eccentric weight in an embodiment different from the above.

FIG. 5 is an explanatory view of a rotary type vibration exciter in which an eccentric weight is attached to each of four rotating shafts.

FIG. 6 is an explanatory diagram showing transmission of ground waves and underground waves in a pile driving work using a vibration device.

FIG. 7 is a chart showing time-rotation speed for explaining a resonance phenomenon in a vibrating pile driving work.

FIG. 8 shows an eccentric weight shaft to which the eccentric weight is fixed, a synchronous transmission gear fixed to the eccentric weight shaft, a drive gear meshed with the synchronous transmission gear, and a motor for rotating the drive gear. FIGS. 4A and 4B are front views schematically illustrating the arrangement of (a), (a) shows a case where the number of arranged eccentric weights is one, (b) shows a case where the number of arranged eccentric weights is one pair, c) shows the case where the number of eccentric weights is two pairs, (d), (e) and (f) show the case where the number of eccentric weights is two pairs and the drive gear is located above the synchronous transmission gear or The case where it is arranged below is shown.

[Explanation of symbols]

1: Exciter case, 2A-2D: Rotating shaft, 3A-3D
... Eccentric weights, 4A-4D ... Transmission gears for synchronous rotation, 5 ...
Crane boom, 6… vibration device (vibrator), 7… pile, 8
.., Private houses, 9, 9 'eccentric weights, 10a, 10b drive gears, 11 synchronous transmission gears, 12 intermediate gears, 12a stopper protrusions, 13a, 13b drive shafts, 14 exciter casings, 15 ... vibration isolation rubber, 16 ... hanger box,
17 ... rubber stopper, 18a, 18b ... rotary encoder 19 ... _{spacer, W 1 ~W 4, W 1} '~W 4' ... eccentric weight, W ₁ ", W _2" is given a phase difference of ... 180 A type of eccentric weight, Wa ... stopper groove, G _{1 to} G ₄ ,
G ₁ '~G _4' ... synchronous transmission gear, k ... key, M _1, M ₂ ... hydraulic motor, h _1, h ₂ ... vertical plane of a virtual, Lx ... width dimension,
_{S 1 ~S 4, S 1 '} ~S 4 ... eccentric weight shaft.

Claims (14)

[Claims] 1. A pair of eccentric weight shafts (S ₁ , S ₂ ) of a system A having fixed eccentric weights (W ₁ , W ₂ ) and synchronously rotating in opposite directions to each other, respectively, horizontally A pair of eccentric weight shafts (S ₃ , S ₄ ) of the B system which are arranged in parallel, fixed with eccentric weights (W ₃ , W ₄ ) different from the above, and synchronously rotate in opposite directions to each other are provided. A drive shaft (13a) that is horizontally and parallel to each other and has a motor (M ₁ ) that rotationally drives the A-system and a drive shaft (13) that has a motor (M ₂ ) that rotationally drives the B-system 13b), the shaft arrangement in the shaker casing (13) has a three-stage configuration in the upper and lower parts, and a pair of eccentric weight shafts (S ₁ , S ₂ ), and a pair of eccentric weight shafts (S ₃ , S ₄ ), and the two drive shafts (13 a, 13 b) are arranged horizontally and parallel to each other in the upper stage, and the A-system is arranged in the upper stage. A drive shaft (13a);
A pair of eccentric weight shafts (S ₁ ,
A rotary vibration exciter characterized in that any one of the eccentric weight shafts of S ₂ ) is connected via a transmission member (12) arranged in the middle stage. 2. The transmission member (12) is an intermediate gear, and the intermediate gear is a pair of eccentric weight shafts (S) of a B system.
_3, S ₄₎ either is fitted on one, characterized in that it is relatively rotatably supported with該何Re or the other of the eccentric weight shaft, rotary force as claimed in claim 1 Shaker. 3. A stopper means for limiting a relative rotation angle between said intermediate gear (12) and an eccentric weight shaft of a B system supporting said intermediate gear. The rotary vibration exciter according to claim 2, wherein 4. The eccentric weight shafts (S ₁ , S ₂ ) of the A system and the eccentric weight shafts (S ₃ , S ₄ ) of the B system are supported by bearings near both ends thereof. , And,
Each of the eccentric weights (W ₁ , W ₂ , W ₃ , W ₄ ) fixed to each of the four eccentric weight shafts is divided in the axial direction, and for each eccentric weight shaft, Each of the divided eccentric weights is disposed one by one in proximity to the bearings at both ends, and an interval is provided between the divided eccentric weights. The rotary vibration exciter according to claim 1, wherein a gear that transmits rotation of members of the system and the system B is arranged. 5. The distance between the divided eccentric weights is such that the synchronous transmission gear (G ₁ ) fixed to each of the eccentric weight shafts (S ₁ , S ₂ , S ₃ , S ₄ ). , G ₂ , G ₃ ,
G ₄ ) Two to three times or less of each tooth width dimension,
The space is designed to be divided into two in the axial direction, and the synchronous transmission gears (G ₁ , G ₂ ) of the A system and the synchronous transmission gear are provided in one of the divided spaces. And a drive gear (10a) meshing with the intermediate gear, and a synchronous transmission gear (G) of the B system is provided in the other space of the divided space. _3, G ₄₎ and characterized in that the synchronous transmission gear and meshes with the drive gear (10b) is disposed, rotary exciter according to claim 4. 6. The four eccentric weights (W ₁ , W ₂ , W ₃ ,
W ₄ ), around at least one of the eccentric weights, there are provided teeth for making the module equal to any one of the _four synchronous transmission gears (G ₁ , G ₂ , G ₃ , G ₄ ). The rotary vibration exciter according to claim 5, wherein an eccentric weight provided with teeth and a synchronous transmission gear adjacent to the eccentric weight are integrally connected. 7. Each of the drive shafts (13a, 13b) is supported by bearings near both ends, and a drive gear (10a, 10b) is fixed to a central portion, and one end of each of the drive shafts is provided. the motor (M _1, M ₂₎ is mounted for driving the end portion, characterized in that the other end a rotary encoder (18a, 18b) is mounted, rotatable according to claim 1 Exciter. 8. The two motors (M ₁ , M ₂ ) are hydraulic motors each having a control mechanism capable of controlling the number of revolutions and rotating in synchronization with each other. The rotary vibration exciter according to any one of claims 1 to 7, wherein 9. The electric motor according to claim 1, wherein the two motors (M ₁ , M ₂ ) are electric motors each having a control circuit capable of controlling the number of rotations and rotating synchronously with each other. The rotary vibration exciter according to any one of claims 1 to 7, wherein 10. A pair of A-system eccentric weight shafts (S ₁ , S ₂ ) having respective eccentric weights (W ₁ , W ₂ ) fixed thereto and synchronously rotating in opposite directions to each other, are respectively horizontally separated from each other. The eccentric weights (W
₃ , W ₄ ) is fixed and rotates synchronously in opposite directions to each other 1
Arranged parallel to each other horizontally eccentric weight shafts of the pairs of B lineage (S _3, S ₄₎ respectively, and said drive shaft having a motor (M ₁₎ for rotating the A line (13a) and A drive shaft (13) provided with a motor (M ₂ ) for rotating the B system
b) The method for controlling a rotary vibration exciter provided with b), wherein the shaft arrangement in the vibration exciter casing (13) is configured in three upper and lower stages, and a pair of eccentric weight shafts of the A system is provided in a lower stage. (S ₁ , S ₂ ) are arranged, a pair of eccentric weight shafts (S ₃ , S ₄ ) of the B system are arranged in the middle stage, and the two drive shafts (13a, 13b) are arranged in the upper stage. Are arranged horizontally and parallel to each other, and as a preparatory operation for constantly generating the maximum vibrating force, the rotational phase of the eccentric weights (W ₁ , W ₂ ) of the A system and B The phase difference between the rotational phase of the eccentric weights (W ₃ , W ₄ ) of the system is set to the maximum angle within the adjustable range, and the state of the vibrating force is minimized. Are rotated in synchronization with each other to increase the rotation speed thereof. After the rotation speeds of the synchronous rotation of the A and B systems are increased, Characterized by performing the steady operation in a state of generating Shimete maximum vibratory force if zero rotational phase difference between the eccentric weight heart weight and B strains, a control method of a rotary exciter. 11. When the rotation speed is increased while synchronizing the A system and the B system, when the rotation speed of the synchronous rotation reaches a predetermined value, or when the A system and the B system are synchronized. 11. A method according to claim 10, wherein when a predetermined time has elapsed since the start of acceleration of the rotation speed while rotating, the rotational phase difference between the eccentric weight of the A system and the eccentric weight of the B system is made zero. The described control method of the rotary vibration exciter. 12. When the vibrating force is minimized in preparation for the generation of the steady maximum vibrating force, the minimum value of the vibrating force is determined to be “the rotary vibration exciter is connected to a load member. The phase difference of the eccentric weight is controlled such that the maximum value of the vibration acceleration is substantially equal to or less than the gravitational acceleration in the state. How to control the shaker. 13. A transition to a steady-state operation or a transition to a steady-state operation while reducing the rotational phase difference between the eccentric weight of the A-system and the eccentric weight of the B-system to zero and generating the maximum vibrating force. Later, the rotational phase difference θ between the eccentric weight of system A and the eccentric weight of system B
The rotational vibration excitation according to claim 10, characterized in that a partial load operation is performed while maintaining a constant value within the range of the above equation (1). Machine control method. 14. A normal operation is performed while reducing the rotational phase difference between the eccentric weight of the system A and the eccentric weight of the system B to zero to generate the maximum vibrating force, and then the rotation speed is reduced to stop. At this time, the eccentric weight of the A system and the eccentric weight of the B system are given a rotational phase difference in advance to minimize the vibrating force, and then the eccentricity of the A system is maintained while maintaining the minimum vibrating force. The control method for a rotary vibration exciter according to claim 10, wherein the rotation speed of the weight and the eccentric weight of the B system is reduced and stopped.