JP2002177887A - Apparatus and method for controlling vibromotive force of eccentric plumb-type vibration generator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve an eccentric plumb-type vibration generator comprising an inner shaft-fixed eccentric plumb shaft 16A equipped with a fixed eccentric plumb 9B and a synchronous transmission gear 22b and an outer pipe-movable eccentric plumb shaft 17A equipped with a movable eccentric plumb 10A and a synchronous transmission gear 22c so that the total width size of the oscillation generator is not enlarged in comparison with the width size W1 of the case 18' of the generator. SOLUTION: A drive/control concentric double shaft 25MV is set up in parallel to a shaft supporting the above two kinds of eccentric plumbs; to this shaft, a rotary drive apparatus 19 and a reversible rotation mechanism 20 are connected; and a synchronous drive gear 26M attached to the shaft is engaged with the above synchronous transmission gear 22b, and so is a synchronous control gear 26V with the above synchronous transmission gear 22c.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method and a device for controlling a vibrating force for preventing the occurrence of vibration pollution and noise pollution when a pile is driven into or pulled out of the ground by a vibration exciter. It is.

[0002]

2. Description of the Related Art A vibration-type pile driving device mounts a vibration exciter on the upper end of a pile and applies vertical vibration (specifically, vibration in the longitudinal direction of the pile) to the pile, thereby forming a pile. The pile is settled in the ground by the gravity load with the shaker. In the case of pulling out a pile driven into the ground, the pile is pulled up by a crane using an exciter mounted on the upper end of the pile. Under these circumstances, a pile driving device in which a pile chuck is installed on a shaker is a pile driving device. In the present invention, when simply referred to as a pile driving device, it is an abbreviation for a pile driving device. With the exception of mountainous areas far from homes, it is necessary to pay attention to the prevention of vibration pollution when punching vibrating piles.

FIG. 6 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 gripped by the chuck 6 a of the vibration device 6, and the pile 7 is vibrated and driven into the ground. Is schematically depicted. When the lower end of the stake 7 is brought into contact with the ground surface to start the stakeout operation, if the vibration device 6 is fully operated from the beginning, the surface wave a generated on the stakeout surface surface is hardly attenuated and the nearby private house 8 is not attenuated. , Causing vibration pollution problems. Here, the vibration device 6
If the vibrating force can be adjusted arbitrarily, the pile driving operation is started while giving a slight vibration in addition to the weight of the pile 7, and after driving several meters, the vibration may be gradually increased. Pile 7
If the epicenter corresponding to the lower end of the ground becomes deeper, 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 table showing changes in the vibration frequency at the time of starting and stopping the operation of the vibration device. The horizontal axis represents time. Start of operation time t _0, between time t ₁ to reach the rated operating state, frequency rises sharply as shown by arrow c. During the above-mentioned frequency rise, the natural frequency of the ground n ₁ and the natural frequency of the crane boom n ₂ are passed. However, since the rotational speed increase period T ₁ at the start operation is generally short (e.g., about 3 seconds), the resonance problem when frequency of the vibration device matches the natural frequency, can be usually ignored it can. However, between the time t ₂ of stopping the energization of the motor of the vibrating device 6 (not shown) to the 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 .

[0005] Since the rotational speed decrease period T ₂ of the above is relatively long (e.g. about 50 seconds), the middle when passing through the natural frequency n ₂ of the crane boom, the crane boom resonates damaged There is a risk of suffering. Further, when passing through the natural frequency n ₁ of the ground, possibility there occur vibration pollution by the resonance of the ground. It stops the energization of the motor in said time t _2, the if it is possible to zero the vibratory force by changing the rotation phase of the rotary weight of the vibration device, issues resonance during shutdown operation of the vibration device Can be prevented.

Next, looking at the amount of energy supplied to the vibrating device, while the rotational speed of the vibrating device 6 increases from the time t ₀ to t ₁ , an eccentric weight (not shown) of the vibrating device is used. When the speed is increased while generating vibrations, a large-capacity motor or a large-capacity power supply is required to drive the motor. In this case, the operation is started in a state where the vibration force is reduced to zero by changing the rotation phase of the eccentric weight of the vibration device, and if the vibration force can be exerted after reaching the rated rotation speed, the motor capacity is increased. It is economical because the power supply capacity can be reduced. This is because, after reaching the rated rotation speed, 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 vibration damping.

[0007] In view of the above circumstances, an adjustment technique for increasing or decreasing the vibrating force of a vibrator has been developed and is known. Next, the principle of increasing and decreasing the excitation force of the exciter will be described. FIG. 8 is a view for explaining a known technique for changing a vibrating force by a combination of two eccentric weights. FIG. 8A shows two eccentric weights exhibiting the maximum vibrating force. FIG. 4B is a schematic diagram illustrating a state in which the vibrating force is moderate, FIG. 4C is a schematic diagram illustrating a state in which the vibratory force is slightly small, and FIG. 4D is a state in which the vibratory force is zero. FIG. Of the two eccentric weights shown in FIG. 8A, 9 is a fixed eccentric weight fixed to the rotating shaft 2B, and 10 is a movable eccentric that can rotate relatively to the rotating shaft 2C. It is a weight. In the present invention, the fixed eccentric weight is an eccentric weight that is locked (relatively speaking) relative rotation with respect to the rotation axis, and is a member that rotates together with the rotation axis.
Fixation does not mean stationary. The relative positions of the two eccentric weights 9 and 10 in FIG. 8A are in a state where the phase difference is zero.

Therefore, when the two eccentric weights 9 and 10 are rotated in synchronization with the gears 4B and 4C in the state shown in FIG. 8A, a vibrating force is generated. In the state of FIG. 8D, the center of gravity of each of the two eccentric weights 9 and 10 is always the reference line M−
Since it is located symmetrically with respect to M (vertical bisector of the line connecting the two rotation axes 2B and 2C), the vertical excitation force is zero. For convenience of explanation, a state where the phase difference between the two eccentric weights is 180 degrees and the total eccentric moment of the two eccentric weights is zero as shown in FIG. 8D is referred to as a reference state.

FIGS. 8 (B) and 8 (C) show intermediate states of the above (A) and (D), respectively, so that the vertical direction is smaller than that of FIG. Generates vibratory force. (B) is closer to the state of FIG. (A) than FIG. (C), so that (A), (B), (C), (D) ). In FIG. 8 described above, the principle of the vibrating force increase / decrease control is shown.
Although the rotating shafts 2B and 2C are synchronously rotated by the synchronous rotating gears 4B and 4C, two eccentric weights may be arranged on one rotating shaft to simplify the structure. it can. FIG. 11 is a schematic view of a mechanism in which a fixed eccentric weight is fixed to a common rotating shaft and a movable eccentric weight can adjust a relative rotation angle position with respect to the common rotating shaft.

The fixed eccentric weight 9 is fixed to the rotating shaft 2 and rotates together. The movable eccentric weight 10 can be adjusted by changing the mounting angle position with respect to the rotating shaft 2 as shown by the arc arrows α-β, and can maintain the adjusted state. The state depicted in FIG. 11 is shown in FIG.
Exciting force is moderate, corresponding to the state shown in (B).
When the movable eccentric weight is rotated and fixed in the direction of the arrow α from this state, the state approaches the state of FIG. 8A, the vibrating force increases. The vibrating force is adjusted as described above. It is understood from the principle of the excitation force adjustment described above that “excitation force control technology is a phase difference control technology”. The technique required for the excitation force control is a phase difference control technique. If the phase difference can be controlled, the excitation force can be controlled.

[0011]

In order to prevent vibration pollution of the eccentric weight type pile punching machine, it is desirable to be able to increase and decrease the vibrating force while continuing the operation of the apparatus without interruption. For this purpose, various devices for adjusting the phase difference between the two eccentric weights to increase or decrease the total eccentric moment have been provided as described above with reference to FIG. 8 while rotating the eccentric weight. I have. But mechanical screws,
A device using a helical groove, a link, or the like has poor durability because a mechanical contact portion is hit by vibration. Furthermore, it is not preferable to incorporate a complicated phase control mechanism inside the exciter case, since maintenance is impaired.

Japanese Patent Application No. 2000-304177 discloses an example of an "eccentric weight type vibrator capable of adjusting the vibrating force" which is excellent in durability without incorporating a phase control mechanism in a vibrator case. There is such an invention. This invention is an unknown invention that was created by the inventor of the present application and is separately filed by the present applicant. Since the previously-unknown invention of the prior application is used in the embodiment of the present invention, an outline of its configuration and function is as follows (paragraphs 0013 to 0024).

FIG. 9 is a cross-sectional view showing an embodiment of an eccentric weight-type vibrator of a variable vibrating force type according to an unknown prior application. A fixed eccentric weight shaft 23 is rotatably supported on the exciter case 18 and is rotationally driven by a rotary drive device 19 (for example, a hydraulic motor or an electric motor). On the other hand, an outer tube (reference numeral 17A) is relatively rotatably fitted to the inner shaft (reference numeral 16A) to form a concentric double shaft, and is rotatably supported on the exciter case 18. The outer tube (17A) penetrates through the wall of the exciter case 18.

A fixed eccentric weight 9A is mounted on the fixed eccentric weight 23 with its relative rotation locked by a key k. The means for locking the relative rotation is not limited to the key, but the fitting portion to which the key (symbol k) is attached in FIGS. This indicates that rotation is not possible. On the contrary, it should be read that a portion where the shape of the key is not written in the fitting portion between the shaft and the eccentric weight can be relatively rotated. A fixed eccentric weight 9B is attached to the inner shaft (reference numeral 16A) by a key k so as not to rotate relatively. Thus, the component previously shown as the inner shaft (16A) is more specifically an inner shaft and fixed eccentric weight.

The fixed eccentric weight 9 A is rotated by the rotary drive device 19. The rotation of the fixed eccentric weight 9A is synchronously transmitted to the fixed eccentric weight 9B via the synchronous transmission gears 22a and 22b. For convenience of explanation, the eccentric weight directly connected to the rotary driving device 19 is referred to as a first fixed eccentric weight 9A, and the eccentric weight which is transmitted with the transmission power from the first fixed eccentric weight 9A and rotates synchronously. Is referred to as a second fixed eccentric weight 9B. The centrifugal force of the movable eccentric weight 10A integrally connected to the outer tube (17A) is supported by the inner and fixed eccentric weight shaft 16A so as to be relatively rotatable. For this reason, the outer tube denoted by reference numeral 17A is, in detail, an outer tube and a movable eccentric weight shaft.

The reversible rotation mechanism 20 is constituted by a vane motor in this embodiment. This reversible rotation mechanism is not limited to the vane motor, and may be an electric motor. In short, any device that can generate forward and reverse rotational force is sufficient.
It is not necessary to be able to rotate continuously by 60 degrees, but it is desirable that it has low-speed and high-torque characteristics. The housing 20a of the reversible rotation mechanism 20 is provided with the outer tube and the movable eccentric weight shaft 17 described above.
A, and the rotating shaft 20b is connected to the inner shaft / fixed eccentric weight shaft 16A. As a result, the movable eccentric weight 10A is rotationally driven by the second fixed eccentric weight 9B via the reversible rotation mechanism 20.

The movable eccentric weight 10B is rotatably mounted on the fixed eccentric weight shaft 23, and the rotation of the movable eccentric weight 10A is controlled by the synchronous transmission gears 22c and 22c.
It is synchronously transmitted to the movable eccentric weight 10B via 2d. For convenience of explanation, the eccentric weight rotated by the fixed eccentric weight via the reversible rotation function 20 is connected to the first movable eccentric weight 1.
An eccentric weight that is synchronously rotated by the first movable eccentric weight via a synchronous transmission gear is referred to as a second movable eccentric weight.

As can be understood from FIG. 9, the fixed eccentric weight shaft 23 supports the first fixed eccentric weight 9A and the second movable eccentric weight 10B, and the gravitational load, centrifugal load and Is receiving. In the present invention, the fixed eccentric weight shaft means "irrespective of the type of the eccentric weight supported, does not rotate relative to the fixed eccentric weight, and rotates in synchronization with the fixed eccentric weight and in the same phase. Axis ". In general, the fixed eccentric weight shaft is directly connected to the output shaft of the rotary driving device, or is transmitted at a constant speed ratio. Similarly, the axis of the movable eccentric weight refers to an axis that does not rotate relative to the movable eccentric weight but rotates in synchronization with the movable eccentric weight and in the same phase.

As is clear from the structure described above,
The rotation of the rotation drive device 19 is sequentially transmitted by the synchronous transmission gear to reach the second movable eccentric weight 10 </ b> B.
As for the synchronous transmission gears, the synchronous transmission gears 22
a, 22b, 22c, and 22d. In the present invention, the suffixes attached to the synchronous transmission gear 22 are a, b, c, and d according to the order of the transmission path.

9, the first fixed eccentric weight 9A and the second fixed eccentric weight 9B always rotate synchronously, and the first movable eccentric weight 10A and the second movable eccentric weight 10A. Weight 1
OB always rotates synchronously. And the reversible rotation mechanism 20
When the turning shaft 20b of the movable eccentric weight rotates relative to the housing 20a, the phase difference of the movable eccentric weight with respect to the fixed eccentric weight changes by an angle equal to the rotation angle. Accordingly, as described with reference to FIG. 8 described above, the total eccentric moment of the fixed eccentric weight and the movable eccentric weight changes, and the excitation force is increased or decreased even at the same rotational speed.

FIG. 10 is a cross-sectional view of a vibration exciter according to an unknown prior application capable of adjusting a vibration generating force, which is different from FIG. 9 described above. The naming and reference numerals of the components in FIG. 10 are as described above with reference to FIG.
The difference between the embodiment of FIG. 10 and the embodiment of FIG. 9 described above is as follows. That is, the reversible rotation mechanism 2
The zero housing 20a is connected to the outer tube / fixed eccentric weight shaft 17B, and the rotating shaft 20b is connected to the inner shaft / movable eccentric weight shaft 16B.

As a configuration common to both the embodiment shown in FIG. 9 and the embodiment shown in FIG. Weight 9
B is driven synchronously, and the second fixed eccentric weight 9B is
First movable eccentric weight 10A via reversible rotation mechanism 20
Are driven so that the phase difference can be adjusted, and the first movable eccentric weight 10A synchronously drives the second movable eccentric weight 10B.

However, the connecting member between the inner shaft and the outer tube of the double tube is exchanged between FIG. 9 and FIG. As a difference due to such a difference, the following difference occurs. That is, it is rotatable with respect to the exciter case 18,
In addition, two shafts, which are arranged in parallel and mainly support the gravitational load and the centrifugal load of one fixed eccentric weight and one movable eccentric weight, respectively, are both fixed eccentric in FIG. In contrast to the weight axis, in FIG. 10, the lower axis is a fixed eccentric weight axis, and the upper axis is a movable eccentric weight axis.

Despite the above-mentioned difference, the total eccentric moment of the movable eccentric weight and the fixed eccentric weight is controlled by adjusting the phase difference between the movable eccentric weight and the fixed eccentric weight. The function that can be performed is common to the embodiment of FIG. 9 and the embodiment of FIG.

According to the previously-unknown invention described above with reference to FIGS. 9 and 10, the eccentric weight type vibrator is operated without interruption and its vibrating force is increased or decreased. Vibration pollution could be prevented or reduced. The present applicant has conducted a practical application test after filing a patent application for the above-mentioned unknown prior application, and has confirmed that the desired effect can be exhibited under practical conditions. On the other hand, it has been found that there is room for further improvement depending on special working conditions. The details will be described below.

[0026]

[SUMMARY OF THE INVENTION For example in exciter machine according to the non-known invention shown in FIG. 9, the width dimension of the exciter casing 18 is W _1, laterally from the exciter casing 18 the rotation drive device 19 protrudes by a dimension W ₂ to,
Reversible rotation mechanism 20 protrudes by a dimension W _3. In this example, since W ₃ > W ₂ , the width W of the entire exciter is
₄ becomes W ₁ + W ₃ .

The working conditions for punching piles using an exciter cannot be said unconditionally because they are remarkably varied. However, the overall width of the exciter is sometimes restricted, and the overall height is also restricted. In some cases. The exciter according to the unknown invention illustrated in FIGS. 9 and 10 is suitable when the overall height is restricted, but is not good under working conditions where the overall width is restricted. The present invention has been made in view of the above circumstances, and without increasing the overall width of the exciter, and while continuing the operation of the exciter without interruption, It is an object of the present invention to provide a technique for controlling a vibrating force of an eccentric weight type vibrator capable of increasing and decreasing a vibrating force.

[0028]

The basic principle of the present invention created to achieve the above object will be briefly described with reference to FIG. 1 corresponding to the embodiment. That is, the fixed eccentric weight 9B and the synchronous transmission gear 2
An eccentric weight type vibration exciter comprising an inner shaft / fixed eccentric weight shaft 16A equipped with 2b and an outer tube / movable eccentric weight shaft 17A equipped with a movable eccentric weight 10A and a synchronous transmission gear 22c. than the width W ₁ of the case 18 ', to improve so as not to enlarge the whole entire width exciter, parallel to the axis that supports the above two eccentric weight, the drive and control concentricity A double shaft 25MV is provided, and a rotary driving device 19 and a reversible rotating mechanism 20 are connected to the shaft, and a driving synchronous gear 26M mounted on the shaft is connected to the synchronous transmission gear 22b.
The control synchronous gear 26V is connected to the synchronous transmission gear 22c.
Then, each is engaged.

Based on the principle described above, claim 1
(See FIG. 1), the fixed eccentric weight and the movable eccentric weight are rotatably and rotatably supported by each of the plurality of eccentric weight shafts.
A plurality of fixed eccentric weights are interlocked by a synchronous transmission gear so as to rotate in the same phase, and a plurality of movable eccentric weights are interlocked by a synchronous transmission gear so as to rotate in the same phase. While rotating the fixed eccentric weight and the movable eccentric weight around the eccentric weight axis, the phase difference between the fixed eccentric weight and the movable eccentric weight is changed to change the phase difference between the fixed eccentric weight and the movable eccentric weight. By changing the total eccentric moment of the eccentric weight type vibrator of the type of changing the vibration force while continuing without interrupting the operation, in the vibrating force control device, in parallel with the eccentric weight spindle , A drive axis and a control axis are provided, and the drive / control axis is
A concentric double shaft composed of an inner shaft and an outer tube that are relatively rotatable. One of the inner shaft and the outer tube of the concentric double shaft is interlocked with the fixed eccentric weights. The synchronous transmission gear is connected to the synchronous transmission gear via a synchronous transmission gear similar to or similar to the synchronous transmission gear, and is driven to rotate by a rotary driving device. One of the other outer tubes is connected to a synchronous transmission gear that links the movable eccentric weights with each other via a synchronous transmission gear similar to or similar to the synchronous transmission gear, and The inner shaft and the outer tube of the double tube are connected to the turning shaft and the housing of the reversible turning mechanism, respectively,
The inner shaft and the outer tube are relatively rotated by the reversible rotating mechanism, so that the phase difference between the fixed eccentric weight and the movable eccentric weight is increased or decreased. I do.

According to the apparatus of the first aspect described above, a drive shaft and a control shaft comprising a concentric double shaft are provided separately from the eccentric weight shaft constituting the eccentric weight type vibrator. The above-mentioned concentric double shaft for driving and control requires rotation about the axis, but does not need to be moved in the axial direction. Since the eccentric weight is not mounted, it can be made much shorter than the eccentric weight shaft. In this way, the drive and control concentric double shaft is rotatable with respect to the drive and control concentric double shaft within a range of dimensions shorter than the eccentric weight shaft. By considering the arrangement and connection of the mechanisms (this is a design consideration), the total length of the drive and control shafts connecting the rotary drive device and the reversible rotation mechanism is reduced by the length of the eccentric weight shaft. It can be configured to be shorter than the dimensions. On the other hand, the width dimension (specifically, the dimension in the eccentric weight axis direction) of the exciter case is substantially equal to the length dimension of the eccentric weight axis. In consideration of the above, the overall length of the drive and control shafts according to the configuration of the present invention is not likely to stick out in the width direction of the exciter case even when the rotary drive device and the reversible rotating mechanism are included, and The entire width direction of the entire shaker is not enlarged. The inner shaft and the outer tube of the concentric double shaft rotate synchronously with the fixed eccentric weight via a driving synchronous gear and a synchronous transmission gear, respectively, and move eccentrically via a control synchronous gear and a synchronous transmission gear. Since the rotation is synchronized with the weight, when the reversible rotation mechanism is operated to rotate the rotation shaft with respect to the housing, the inner shaft is relatively rotated with respect to the outer tube. That is, the phase difference between the inner shaft and the outer tube changes. When the phase difference between the inner shaft and the outer tube changes as described above, the phase difference between the fixed eccentric weight and the movable eccentric weight that are rotating synchronously with respect to the inner shaft and the outer tube changes. Therefore, the total eccentric moment of these eccentric weights changes,
The vibrating force can be changed without changing the rotation speed.

In the configuration of the apparatus according to the second aspect of the present invention (see also FIGS. 2 and 3B), the fixed eccentric weight and the movable eccentric weight are rotated by each of the plurality of eccentric weight shafts. The plurality of fixed eccentric weights are supported so as to be freely and relatively rotatable, and the plurality of fixed eccentric weights are interlocked by a synchronous transmission gear so as to rotate in the same phase, and the plurality of movable eccentric weights are mutually synchronized. The plurality of fixed eccentric weights and the movable eccentric weights are rotated around the eccentric weight axis while the phase difference between the fixed eccentric weights and the movable eccentric weights is rotated. By changing the total eccentric moment of the fixed eccentric weight and movable eccentric weight by changing the In the vibrating force control device, In parallel with the weight shaft, two concentric double shafts in which the inner shaft and the outer tube are relatively rotatably fitted are arranged, and one of the two concentric double shafts is An inner shaft drive concentric double shaft with a rotary drive device connected to the inner shaft,
A drive synchronous gear mounted on the inner shaft is meshed with a synchronous transmission gear that interlocks the fixed eccentric weights, and a control synchronous gear mounted on the outer tube is connected to the movable eccentric weight. The other of the two concentric double shafts is meshed with a synchronous transmission gear linking the weights with each other, and the inner shaft is a rotation shaft of a reversible rotation mechanism, and the outer tube is the reversible rotation shaft. An outer tube control concentric double shaft respectively connected to the housing of the rotating mechanism, and a drive synchronous gear mounted on the inner shaft meshes with a drive synchronous gear of the inner shaft drive concentric double shaft. At the same time, the control synchronous gear mounted on the outer tube is meshed with the control synchronous gear of the inner shaft drive concentric double shaft, and the rotational force by the drive of the rotary drive device is transmitted to two systems,
One of the transmission systems rotates a fixed eccentric weight via a driving synchronous gear, and the other transmission system employs a movable eccentric weight via a driving synchronous gear, a reversible rotating mechanism, and a control synchronous gear in order. A structure for rotating, wherein by rotating a rotation shaft of the reversible rotation mechanism with respect to the housing, the control synchronization gear is relatively rotated with respect to the drive synchronization gear, The phase difference between the fixed eccentric weight and the movable eccentric weight is adjusted to increase or decrease.

According to the apparatus of the second aspect described above, the drive shaft and the control shaft, each of which is a concentric double shaft, are provided separately from the eccentric weight shaft constituting the eccentric weight type vibrator. The concentric double shaft for driving and the concentric double shaft for control need to rotate around the axis, but need not be moved in the axial direction. Since the eccentric weight is not attached to the concentric double shaft, it can be configured to be much shorter than the eccentric weight shaft. In this way, the concentric double shaft for driving and the concentric double shaft for control are within a range of dimensions shorter than the eccentric weight shaft,
By providing a rotary drive device and a reversible rotation mechanism for connection and connection to the concentric double shafts for drive and control (this is a design consideration), the rotary drive device is provided. The total length of each of the driving concentric double shaft connected to the shaft and the control concentric double shaft connected to the reversible rotation mechanism can be configured to be shorter than the length of the eccentric weight shaft.
On the other hand, the width of the shaker case (dimension in the axial direction of the eccentric weight)
Is substantially equal to the length dimension of the eccentric weight shaft. In summary, the total length of the driving concentric double shaft and the total length of the concentric double shaft for control according to the configuration of the present invention is the same as that of the vibration exciter case even if it includes a rotary driving device or a reversible rotating mechanism. There is no danger of sticking out in the width direction of the exciter, and the entire width direction of the entire exciter is not enlarged. The inner shaft and the outer tube of the concentric double shaft rotate synchronously with the fixed eccentric weight via a driving synchronous gear and a synchronous transmission gear, respectively.
Since it rotates synchronously with the movable eccentric weight via the synchronous gear for control and the synchronous transmission gear, when the reversible rotating mechanism is operated to rotate the rotating shaft with respect to the housing, the outer pipe is attached to the outer tube. On the other hand, the inner shaft is relatively rotated. That is, the phase difference between the inner shaft and the outer tube changes. When the phase difference between the inner shaft and the outer tube changes as described above, the phase difference between the fixed eccentric weight and the movable eccentric weight that are rotating synchronously with respect to the inner shaft and the outer tube changes. Thus, the total eccentric moment of these eccentric weights changes, and the vibrating force can be changed without changing the rotation speed.

The configuration of the invention device according to claim 3 is as shown in FIG.
(C)), by each of a plurality of eccentric weight spindles,
A fixed eccentric weight and a movable eccentric weight are rotatably and rotatably supported, and a plurality of fixed eccentric weights are interlocked by a synchronous transmission gear so as to rotate in the same phase. The plurality of movable eccentric weights are interlocked by a synchronous transmission gear so as to rotate in the same phase, and the plurality of fixed eccentric weights and the movable eccentric weight are rotated around the eccentric weight axis while being fixed. By changing the phase difference between the eccentric weight and the movable eccentric weight and changing the total eccentric moment of the fixed eccentric weight and the movable eccentric weight, the vibrating force can be continuously maintained without interrupting the operation. In a vibrating force control device for an eccentric weight type vibrator of a varying type, a concentric double shaft in which an inner shaft and an outer tube are fitted rotatably in parallel with the eccentric weight shaft. Two pieces are arranged, and the above two concentric double axis pieces Is an outer tube control concentric double shaft connected to the inner shaft of the reversible turning mechanism and the outer tube of the outer tube to the housing of the reversible turning mechanism, and mounted on the inner shaft. The driven synchronous gear is meshed with the synchronous transmission gear that links the fixed eccentric weights to each other, and the control transmission gear mounted on the outer tube links the movable eccentric weights to each other. And the other of the two concentric double shafts is an inner shaft drive concentric double shaft whose inner shaft is connected to a rotary drive device, and the other of which is connected to the inner shaft. The mounted drive synchronous gear meshes with the drive synchronous transmission gear of the outer tube control concentric double shaft, and the control synchronous gear mounted on the outer tube controls the outer tube control concentric double shaft. The rotational force generated by driving the rotary driving device is transmitted to two systems. , Transmission lines of the one rotates the fixed eccentric weight through the synchronous gear for driving the other of the transmission lines for driving timing gears, reversible rotation mechanism,
A structure in which the movable eccentric weight is sequentially rotated via the control synchronous gear, and the control synchronous gear is driven synchronously by rotating a rotation shaft of the reversible rotation mechanism with respect to the housing. The phase difference between the fixed eccentric weight and the movable eccentric weight is increased or decreased by being relatively rotated with respect to the gear.

According to the apparatus of the third aspect described above, the drive shaft and the control shaft, which are formed as concentric double shafts, are provided separately from the eccentric weight shaft constituting the eccentric weight type vibrator. The concentric double shaft for driving and the concentric double shaft for control need to rotate around the axis, but need not be moved in the axial direction. Since the eccentric weight is not attached to the concentric double shaft, it can be configured to be much shorter than the eccentric weight shaft. In this way, the concentric double shaft for driving and the concentric double shaft for control are within the range of the dimension shortened than the eccentric weight shaft, with respect to the concentric double shaft for driving and control. Considering that a rotary driving device and a reversible rotating mechanism are arranged and connected respectively (this is a design consideration), a concentric double shaft for driving that connects the rotary driving device, and a reversible rotary The total length of each of the control concentric double shafts to which the mechanisms are connected can be configured to be shorter than the length of the eccentric weight shaft.
On the other hand, the width of the shaker case (dimension in the axial direction of the eccentric weight)
Is substantially equal to the length dimension of the eccentric weight shaft. In summary, the total length of the driving concentric double shaft and the total length of the concentric double shaft for control according to the configuration of the present invention is the same as that of the vibration exciter case even if it includes a rotary driving device or a reversible rotating mechanism. There is no danger of sticking out in the width direction of the exciter, and the entire width direction of the entire exciter is not enlarged. The inner shaft and the outer tube of the concentric double shaft rotate synchronously with the fixed eccentric weight via a driving synchronous gear and a synchronous transmission gear, respectively.
Since it rotates synchronously with the movable eccentric weight via the synchronous gear for control and the synchronous transmission gear, when the reversible rotating mechanism is operated to rotate the rotating shaft with respect to the housing, the outer pipe is attached to the outer tube. On the other hand, the inner shaft is relatively rotated. That is, the phase difference between the inner shaft and the outer tube changes. When the phase difference between the inner shaft and the outer tube changes as described above, the phase difference between the fixed eccentric weight and the movable eccentric weight that are rotating synchronously with respect to the inner shaft and the outer tube changes. Thus, the total eccentric moment of these eccentric weights changes, and the vibrating force can be changed without changing the rotation speed.

The configuration of the invention device according to claim 4 is as shown in FIG.
(D)), by each of a plurality of eccentric weight spindles,
A fixed eccentric weight and a movable eccentric weight are rotatably and rotatably supported, and a plurality of fixed eccentric weights are interlocked by a synchronous transmission gear so as to rotate in the same phase. The plurality of movable eccentric weights are interlocked by a synchronous transmission gear so as to rotate in the same phase, and the plurality of fixed eccentric weights and the movable eccentric weight are rotated around the eccentric weight axis while being fixed. By changing the phase difference between the eccentric weight and the movable eccentric weight and changing the total eccentric moment of the fixed eccentric weight and the movable eccentric weight, the vibrating force can be continuously maintained without interrupting the operation. In the vibrating force control device of the eccentric weight type vibrator of the changing type, a drive shaft and a control shaft are provided in parallel with the eccentric weight shaft, and a rotary drive device is connected to the drive shaft. And the drive gear is attached The drive gear is meshed with a synchronous transmission gear that links the fixed eccentric weight, and the control shaft has a concentric double fitting in which an outer tube is rotatably fitted to an inner shaft. A shaft, an inner shaft of the concentric double shaft is connected to a turning shaft of the reversible turning mechanism, and an outer tube is connected to a housing of the reversible turning mechanism, respectively, and A drive synchronous gear mounted on either one of the outer pipe and the driving gear is meshed with a synchronous transmission gear for interlocking the fixed eccentric weights, and mounted on one of the other of the inner shaft and the outer pipe. The synchronized gear for control is meshed with a synchronous transmission gear that links the movable eccentric weights to each other, and by rotating the rotating shaft of the reversible rotating mechanism with respect to the housing,
The inner shaft and the outer tube are relatively rotated, the phase difference between the fixed eccentric weight and the movable eccentric weight changes, and the vibrating force is controlled to increase or decrease. I do.

According to the apparatus of the fourth aspect described above, the drive shaft and the control shaft, each of which is a concentric double shaft, are provided separately from the eccentric weight shaft constituting the eccentric weight type vibrator. The concentric double shaft for driving and the concentric double shaft for control need to rotate around the axis, but need not be moved in the axial direction. Since the eccentric weight is not attached to the concentric double shaft, it can be configured to be much shorter than the eccentric weight shaft. In this way, the concentric double shaft for driving and the concentric double shaft for control are within the range of the dimension shortened than the eccentric weight shaft, with respect to the concentric double shaft for driving and control. Considering that a rotary driving device and a reversible rotating mechanism are arranged and connected respectively (this is a design consideration), a concentric double shaft for driving that connects the rotary driving device, and a reversible rotary The total length of each of the control concentric double shafts to which the mechanisms are connected can be configured to be shorter than the length of the eccentric weight shaft.
On the other hand, the width of the shaker case (dimension in the axial direction of the eccentric weight)
Is substantially equal to the length dimension of the eccentric weight shaft. In summary, the total length of the driving concentric double shaft and the total length of the concentric double shaft for control according to the configuration of the present invention is the same as that of the vibration exciter case even if it includes a rotary driving device or a reversible rotating mechanism. There is no danger of sticking out in the width direction of the exciter, and the entire width direction of the entire exciter is not enlarged. The inner shaft and the outer tube of the concentric double shaft rotate synchronously with the fixed eccentric weight via a driving synchronous gear and a synchronous transmission gear, respectively.
Since it rotates synchronously with the movable eccentric weight via the synchronous gear for control and the synchronous transmission gear, when the reversible rotating mechanism is operated to rotate the rotating shaft with respect to the housing, the outer pipe is attached to the outer tube. On the other hand, the inner shaft is relatively rotated. That is, the phase difference between the inner shaft and the outer tube changes. When the phase difference between the inner shaft and the outer tube changes as described above, the phase difference between the fixed eccentric weight and the movable eccentric weight that are rotating synchronously with respect to the inner shaft and the outer tube changes. Thus, the total eccentric moment of these eccentric weights changes, and the vibrating force can be changed without changing the rotation speed.

The structure of the invention device according to claim 5 is the same as that of the invention device of claims 1 to 4 (see FIGS. 3B, 3C and 3D). For each of the eccentric weight shafts, a fixed eccentric weight and a movable eccentric weight supported rotatably and relatively rotatably are
Each of the eccentric weight shafts is mounted on a synchronous transmission gear, and the number of the eccentric weight shafts is at least four. For each eccentric weight shaft, a synchronous transmission gear mounted on a fixed eccentric weight and a movable eccentric weight are provided. And a synchronous transmission gear mounted on the eccentric weight forming a “synchronous transmission gear pair”, and the center lines of the four eccentric weight shafts are arranged along the ridge line of the virtual square prism, and four sets Of the eight synchronous transmission gears constituting the synchronous transmission gear pair of the first embodiment, four synchronous transmission gears mounted on the fixed eccentric weight, and four synchronous transmissions mounted on the movable eccentric weight. The gears form a square ring gear train.

When the above-described invention of claim 5 is applied to any of the invention devices of claims 1 to 4,
The vibration device according to claim 1, wherein the vibration exciter is increased or decreased without increasing the width of the exciter and without interrupting the operation of the exciter. Vibration pollution during punching work can be suppressed. "
At least four sets of "fixed" which regulate the rotational phase of at least four sets of "fixed eccentric weights and movable eccentric weights" supported by at least four eccentric weight shafts without fear of impairing the effect of The synchronous transmission gear pair of the eccentric weight synchronous transmission gear and the movable eccentric weight transmission gear can be properly meshed with each other, and reliable phase control can be performed. In particular, since the four eccentric weight shafts are arranged along the ridge of the square prism, the four synchronous transmission gears for the fixed eccentric weight and the four synchronous transmission gears for the movable eccentric weight are provided. For any one of the four gears
Even if the gears are picked up, they are in mesh with the two adjacent gears, and the transmission load is equal.

According to a sixth aspect of the present invention, in addition to the constituent elements of the first to fourth aspects of the present invention (see FIGS. 4 and 5), each of the plurality of eccentric weight shafts is provided. The fixed eccentric weight and the movable eccentric weight supported rotatably and relatively rotatably are mounted on the synchronous transmission gear, respectively, and the number of the eccentric weight shafts to be installed is at least four. For each eccentric weight shaft, the synchronous transmission gear mounted on the fixed eccentric weight and the synchronous transmission gear mounted on the movable eccentric weight form a "synchronous transmission gear pair". The center line of the eccentric weight shaft is arranged along the ridge line of a virtual square prism, and constitutes four sets of synchronous transmission gear pairs supported by each of the four eccentric weight shafts. Of the eight synchronous transmission gears mounted on the fixed eccentric weight Synchronous transmission gears and four synchronous transmission gears mounted on the movable eccentric weight form a modified U-shaped gear train, and the synchronous transmission gears at both ends of the gear train mesh with each other. And the drive synchronous gear and the control synchronous gear mesh with one of the synchronous transmission gears constituting the modified U-shaped gear train.

When the above-described invention of claim 6 is applied to any of the above-described invention devices of claims 1 to 4,
The vibration device according to claim 1, wherein the vibration exciter is increased or decreased without increasing the width of the exciter and without interrupting the operation of the exciter. Vibration pollution during punching work can be suppressed. "
At least four sets of "fixed" which regulate the rotational phase of at least four sets of "fixed eccentric weights and movable eccentric weights" supported by at least four eccentric weight shafts without fear of impairing the effect of The synchronous transmission gear pair of the eccentric weight synchronous transmission gear and the movable eccentric weight transmission gear can be properly meshed with each other, and reliable phase control can be performed. In particular, since the four eccentric weight shafts are arranged along the ridge of the square prism, the four synchronous transmission gears for the fixed eccentric weight and the four synchronous transmission gears for the movable eccentric weight are provided. For any one of the four gears
Even if the gears are picked up, they are in mesh with the two adjacent gears, and the transmission load is equal.

According to a seventh aspect of the present invention, in addition to the constituent features of the first to sixth aspects of the present invention, the reversible rotating mechanism is configured to rotate by hydraulic pressure or electromagnetic force. The structure is such that the moving shaft can be rotated forward and backward with respect to the housing, and the housing rotates in the same phase as the fixed eccentric weight and the rotating shaft rotates in the same phase as the movable eccentric weight. Alternatively, the rotating shaft rotates in the same phase as the fixed eccentric weight, and the housing is connected to rotate in the same phase as the movable eccentric weight.

According to the device of the present invention, the power transmission of the reversible rotation mechanism is performed by hydraulic pressure or electromagnetic force, and the wedge action between the metal members is not used unlike the conventional screw means. There is no place where the metal member slides while receiving local pressure. Therefore, durability and reliability are high. The rotation phase of the housing of the reversible rotation mechanism is constrained to match the rotation phase of the fixed eccentric weight, and the rotation phase of the rotation axis of the reversible rotation mechanism matches the rotation phase of the movable eccentric weight. In contrast to this, the rotation phase of the casing of the reversible rotation mechanism is constrained to match the rotation phase of the movable eccentric weight, and the rotation axis of the Is the same as that of the fixed eccentric weight.
The effect is obtained. The device according to the seventh aspect of the present invention has a large degree of freedom in design as understood from the above-mentioned functions, and has a high practical value.

According to an eighth aspect of the present invention, the fixed eccentric weight and the movable eccentric weight are rotatable and relatively rotatable by each of the plurality of eccentric weight shafts. And a plurality of fixed eccentric weights are interlocked by a synchronous transmission gear so as to rotate in the same phase, and a plurality of movable eccentric weights are interlocked by a synchronous transmission gear so that they rotate in the same phase. The fixed eccentric weight and the movable eccentric weight are rotated around the eccentric weight axis while changing the phase difference between the fixed eccentric weight and the movable eccentric weight. The method of controlling the vibration force of an eccentric weight type vibration generator of a type in which the vibration force is changed while the operation is continued without interrupting by changing the total eccentric moment of the eccentric weight and the movable eccentric weight. Drive shaft parallel to the weight shaft In addition to disposing a shaft that also serves as a control shaft, the drive / control shaft is constituted by a concentric double shaft consisting of an inner shaft and an outer tube that are relatively rotatable, and the inner shaft of the concentric double shaft or One of the outer tubes is connected to a synchronous transmission gear that links the fixed eccentric weights through a synchronous transmission gear similar to or similar to the synchronous transmission gear, and is rotated by a rotary driving device. And the other of the inner shaft and the outer tube of the concentric double shaft is similar to or similar to the synchronous transmission gear with respect to the synchronous transmission gear that links the movable eccentric weights to each other. Connected via a synchronous transmission gear, and the inner shaft and the outer tube of the concentric double tube are connected to the turning shaft and the housing of the reversible turning mechanism, respectively. The shaft and the outer tube are relatively rotated, and the fixed Phase difference between the weight and the movable eccentric weight is characterized in that to be increased or decreased regulation.

According to the above-described method of the present invention, a drive shaft and a control shaft comprising a concentric double shaft are provided separately from the eccentric weight shaft constituting the eccentric weight type vibrator. The above-mentioned concentric double shaft for driving and control requires rotation around the axis, but does not need to be moved in the axial direction. Since the eccentric weight is not mounted, it can be configured to be much shorter than the eccentric weight shaft. In this way, the drive and control concentric double shaft is rotatable with respect to the drive and control concentric double shaft within a range of dimensions shorter than the eccentric weight shaft. By considering the arrangement and connection of the mechanisms (this is a design consideration), the total length of the drive and control shafts connecting the rotary drive device and the reversible rotation mechanism is reduced by the length of the eccentric weight shaft. It can be configured to be shorter than the dimensions. On the other hand, the width dimension (specifically, the dimension in the eccentric weight axis direction) of the exciter case is substantially equal to the length dimension of the eccentric weight axis. In consideration of the above, the overall length of the drive and control shafts according to the configuration of the present invention is not likely to stick out in the width direction of the exciter case even when the rotary drive device and the reversible rotating mechanism are included, and The entire width direction of the entire shaker is not enlarged. The inner shaft and the outer tube of the concentric double shaft rotate synchronously with the fixed eccentric weight via a driving synchronous gear and a synchronous transmission gear, respectively, and move eccentrically via a control synchronous gear and a synchronous transmission gear. Since the rotation is synchronized with the weight, when the reversible rotation mechanism is operated to rotate the rotation shaft with respect to the housing, the inner shaft is relatively rotated with respect to the outer tube. That is, the phase difference between the inner shaft and the outer tube changes. When the phase difference between the inner shaft and the outer tube changes as described above, the phase difference between the fixed eccentric weight and the movable eccentric weight that are rotating synchronously with respect to the inner shaft and the outer tube changes. Therefore, the total eccentric moment of these eccentric weights changes,
The vibrating force can be changed without changing the rotation speed.

The configuration of the method according to the ninth aspect is as shown in FIG.
And FIG. 3B), a fixed eccentric weight and a movable eccentric weight are rotatably and rotatably supported by each of the plurality of eccentric weight shafts. The fixed eccentric weights are interlocked so as to rotate in the same phase by a synchronous transmission gear, and the plurality of movable eccentric weights are interlocked so as to rotate in the same phase by a synchronous transmission gear. While rotating the fixed eccentric weight and the movable eccentric weight around the eccentric weight axis, the phase difference between the fixed eccentric weight and the movable eccentric weight is changed so that the fixed eccentric weight and the movable eccentric weight are By changing the total eccentric moment, in the vibrating force control method of the eccentric weight type vibrator of the type of changing the vibrating force while continuing without interrupting the operation, in parallel with the eccentric weight spindle, Inner shaft and outer tube can rotate relatively The two concentric shafts which together arranged two,
One of the two concentric double shafts is constituted by an inner shaft driving concentric double shaft having a rotation driving device connected to the inner shaft, and the driving synchronous gear mounted on the inner shaft is fixed fixed eccentric. In addition to engaging the weights with the synchronous transmission gear
The control synchronous gear mounted on the outer tube is meshed with a synchronous transmission gear that links the movable eccentric weights to each other,
The other of the two concentric double shafts is an outer tube control concentric tube whose inner shaft is connected to the rotation shaft of the reversible rotation mechanism and whose outer tube is connected to the housing of the reversible rotation mechanism. Composed of dual axes,
The drive synchronous gear mounted on the inner shaft is meshed with the drive synchronous gear of the inner shaft drive concentric double shaft, and the control synchronous gear mounted on the outer tube is connected to the inner shaft drive concentric double shaft. And the rotational force generated by the driving of the rotary drive device is transmitted to two systems. One of the transmission systems rotates the fixed eccentric weight via the synchronous gear for drive, and the other transmits the rotational force. The system is configured so that the movable eccentric weight is rotated sequentially through the driving synchronous gear, the reversible rotating mechanism, and the controlling synchronous gear, and the rotating shaft of the reversible rotating mechanism is rotated with respect to the housing. The synchronous gear for control is rotated relative to the synchronous gear for drive by doing so that the phase difference between the fixed eccentric weight and the movable eccentric weight is adjusted to increase or decrease. Features.

According to the ninth aspect of the present invention, the drive shaft and the control shaft are provided separately from the eccentric weight shaft constituting the eccentric weight type vibrator. The concentric double shaft for driving and the concentric double shaft for control need to rotate around the axis, but need not be moved in the axial direction. Since the eccentric weight is not attached to the concentric double shaft, it can be configured to be much shorter than the eccentric weight shaft. In this way, the concentric double shaft for driving and the concentric double shaft for control are within the range of the dimension shortened than the eccentric weight shaft, with respect to the concentric double shaft for driving and control. Considering that a rotary driving device and a reversible rotating mechanism are arranged and connected respectively (this is a design consideration), a concentric double shaft for driving that connects the rotary driving device, and a reversible rotary The total length of each of the control concentric double shafts to which the mechanisms are connected can be configured to be shorter than the length of the eccentric weight shaft.
On the other hand, the width of the shaker case (dimension in the axial direction of the eccentric weight)
Is substantially equal to the length dimension of the eccentric weight shaft. In summary, the total length of the driving concentric double shaft and the total length of the concentric double shaft for control according to the configuration of the present invention is the same as that of the vibration exciter case even if it includes a rotary driving device or a reversible rotating mechanism. There is no danger of sticking out in the width direction of the exciter, and the entire width direction of the entire exciter is not enlarged. The inner shaft and the outer tube of the concentric double shaft rotate synchronously with the fixed eccentric weight via a driving synchronous gear and a synchronous transmission gear, respectively.
Since it rotates synchronously with the movable eccentric weight via the synchronous gear for control and the synchronous transmission gear, when the reversible rotating mechanism is operated to rotate the rotating shaft with respect to the housing, the outer pipe is attached to the outer tube. On the other hand, the inner shaft is relatively rotated. That is, the phase difference between the inner shaft and the outer tube changes. When the phase difference between the inner shaft and the outer tube changes as described above, the phase difference between the fixed eccentric weight and the movable eccentric weight that are rotating synchronously with respect to the inner shaft and the outer tube changes. Thus, the total eccentric moment of these eccentric weights changes, and the vibrating force can be changed without changing the rotation speed.

According to a tenth aspect of the invention, the fixed eccentric weight and the movable eccentric weight are rotatably and relatively rotatably supported by the plurality of eccentric weight shafts. The plurality of fixed eccentric weights are interlocked by a synchronous transmission gear so as to rotate in phase, and the plurality of movable eccentric weights are interlocked by a synchronous transmission gear so as to rotate in phase. While rotating the plurality of fixed eccentric weights and the movable eccentric weight around the eccentric weight axis, the phase difference between the fixed eccentric weight and the movable eccentric weight is changed to change the phase difference between the fixed eccentric weight and the movable eccentric weight. By changing the total eccentric moment with the eccentric weight type vibrator of the method of changing the vibrating force while continuing without interrupting the operation, in the vibrating force control method, To
Two concentric double shafts in which the inner shaft and the outer tube are relatively rotatably fitted are arranged, and one of the two concentric double shafts is connected to the inner shaft by a reversible rotation mechanism. The rotating shaft is constituted by an outer tube controlling concentric double shaft connected to the casing of the reversible rotating mechanism and the outer tube thereof is connected to the casing of the reversible rotating mechanism, and the driving synchronous gear mounted on the inner shaft is provided with the fixed eccentric weight. The weight is meshed with a synchronous transmission gear that is interlocked with each other, and a control transmission gear mounted on the outer tube is meshed with a synchronous transmission gear that is interlocked with the movable eccentric weights, and The other of the two concentric double shafts has an inner shaft constituted by an inner shaft driving concentric double shaft connected to a rotary driving device, and a driving synchronous gear mounted on the inner shaft is provided with the outer tube control concentric double shaft. The synchronous gear for driving of the heavy shaft is meshed with the synchronous gear for driving, and the synchronous gear for control mounted on the outer tube is connected to the external synchronous gear. The concentric double shaft is engaged with the control synchronous gear, and the rotational force generated by driving the rotary drive device is transmitted to two systems. One of the transmission systems rotates the fixed eccentric weight via the drive synchronous gear. The other transmission system is configured to rotate the movable eccentric weight via a driving synchronous gear, a reversible rotating mechanism, and a controlling synchronous gear in order, and the rotating shaft of the reversible rotating mechanism is By rotating the control synchronous gear relative to the drive synchronous gear, the phase difference between the fixed eccentric weight and the movable eccentric weight is increased or decreased. It is characterized by being operated to.

According to the tenth aspect of the present invention, the eccentric weight type vibrator is provided with a drive shaft and a control shaft which are formed separately from the eccentric weight shaft and which are separate from the eccentric weight shaft. The concentric double shaft for driving and the concentric double shaft for control need to rotate around the axis, but need not be moved in the axial direction. Since the eccentric weight is not attached to the concentric double shaft, it can be configured to be much shorter than the eccentric weight shaft. In this way, the concentric double shaft for driving and the concentric double shaft for control are within a range of dimensions shorter than the eccentric weight shaft,
By providing a rotary drive device and a reversible rotation mechanism for connection and connection to the concentric double shafts for drive and control (this is a design consideration), the rotary drive device is provided. The total length of each of the driving concentric double shaft connected to the shaft and the control concentric double shaft connected to the reversible rotation mechanism can be configured to be shorter than the length of the eccentric weight shaft.
On the other hand, the width of the shaker case (dimension in the axial direction of the eccentric weight)
Is substantially equal to the length dimension of the eccentric weight shaft. In summary, the total length of the driving concentric double shaft and the total length of the concentric double shaft for control according to the configuration of the present invention is the same as that of the vibration exciter case even if it includes a rotary driving device or a reversible rotating mechanism. There is no danger of sticking out in the width direction of the exciter, and the entire width direction of the entire exciter is not enlarged. The inner shaft and the outer tube of the concentric double shaft rotate synchronously with the fixed eccentric weight via a driving synchronous gear and a synchronous transmission gear, respectively.
Since it rotates synchronously with the movable eccentric weight via the synchronous gear for control and the synchronous transmission gear, when the reversible rotating mechanism is operated to rotate the rotating shaft with respect to the housing, the outer pipe is attached to the outer tube. On the other hand, the inner shaft is relatively rotated. That is, the phase difference between the inner shaft and the outer tube changes. When the phase difference between the inner shaft and the outer tube changes as described above, the phase difference between the fixed eccentric weight and the movable eccentric weight that are rotating synchronously with respect to the inner shaft and the outer tube changes. Thus, the total eccentric moment of these eccentric weights changes, and the vibrating force can be changed without changing the rotation speed.

According to an eleventh aspect of the present invention, the fixed eccentric weight and the movable eccentric weight are rotatably and rotatably supported by each of the plurality of eccentric weight shafts. A plurality of fixed eccentric weights are interlocked by a synchronous transmission gear so as to rotate in the same phase, and a plurality of movable eccentric weights are interlocked by a synchronous transmission gear so as to rotate in the same phase. The fixed eccentric weight and the movable eccentric weight are rotated around the axis of the eccentric weight, and the phase difference between the fixed eccentric weight and the movable eccentric weight is changed to change the phase difference between the fixed eccentric weight and the movable eccentric weight. By changing the total eccentric moment with the eccentric weight type vibrator of the method of changing the vibrating force while continuing the operation without interruption, the eccentric weight axis is parallel to the eccentric weight axis. To
A drive shaft and a control shaft are provided, a rotary drive device is connected to the drive shaft, and a drive gear is mounted.The drive gear meshes with a synchronous transmission gear that links the fixed eccentric weight, and The control shaft is constituted by a concentric double shaft in which the outer tube is relatively rotatably fitted to the inner shaft. Similarly, an outer tube is connected to the housing of the reversible rotating mechanism, respectively, and
A drive synchronous gear mounted on one of the inner shaft and the outer tube is meshed with a synchronous transmission gear for interlocking the fixed eccentric weights, and any one of the inner shaft and the outer tube. By meshing the control synchronous gear mounted on the other with the synchronous transmission gear that is interlocking the movable eccentric weights, and by rotating the rotating shaft of the reversible rotating mechanism with respect to the housing, The inner shaft and the outer tube are rotated relatively,
The phase difference between the fixed eccentric weight and the movable eccentric weight is changed, and the vibrating force is controlled to increase or decrease.

According to the eleventh aspect of the present invention, the drive shaft and the control shaft are provided separately from the eccentric weight shaft constituting the eccentric weight type vibrator. The concentric double shaft for driving and the concentric double shaft for control need to rotate around the axis, but do not need to be moved in the axial direction. Since the eccentric weight is not attached to the concentric double shaft, it can be configured to be much shorter than the eccentric weight shaft. In this way, the concentric double shaft for driving and the concentric double shaft for control are within a range of dimensions shorter than the eccentric weight shaft,
By providing a rotary drive device and a reversible rotation mechanism for connection and connection to the concentric double shafts for drive and control (this is a design consideration), the rotary drive device is provided. The total length of each of the driving concentric double shaft connected to the shaft and the control concentric double shaft connected to the reversible rotation mechanism can be configured to be shorter than the length of the eccentric weight shaft.
On the other hand, the width of the shaker case (dimension in the axial direction of the eccentric weight)
Is substantially equal to the length dimension of the eccentric weight shaft. In summary, the total length of the driving concentric double shaft and the total length of the concentric double shaft for control according to the configuration of the present invention is the same as that of the vibration exciter case even if it includes a rotary driving device or a reversible rotating mechanism. There is no danger of sticking out in the width direction of the exciter, and the entire width direction of the entire exciter is not enlarged. The inner shaft and the outer tube of the concentric double shaft rotate synchronously with the fixed eccentric weight via a driving synchronous gear and a synchronous transmission gear, respectively.
Since it rotates synchronously with the movable eccentric weight via the synchronous gear for control and the synchronous transmission gear, when the reversible rotating mechanism is operated to rotate the rotating shaft with respect to the housing, the outer pipe is attached to the outer tube. On the other hand, the inner shaft is relatively rotated. That is, the phase difference between the inner shaft and the outer tube changes. When the phase difference between the inner shaft and the outer tube changes as described above, the phase difference between the fixed eccentric weight and the movable eccentric weight that are rotating synchronously with respect to the inner shaft and the outer tube changes. Thus, the total eccentric moment of these eccentric weights changes, and the vibrating force can be changed without changing the rotation speed.

[0051]

DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 is a schematic vertical sectional view showing one embodiment of a vibrating force control device for an eccentric weight type vibrator according to the present invention. FIG. 7 is a diagram in which “installation positions of a rotary drive device and a reversible rotation mechanism in a vibration control device according to the prior art” are indicated by virtual lines.
In this embodiment (FIG. 1), the present invention is applied to and improved from the previously-unknown invention device shown in FIG. 9 according to the prior application. The synchronous transmission gear 22a is fixed to the fixed eccentric weight shaft 23.
Is fixed. The fixed eccentric weight 9B is fixed to the inner shaft / fixed eccentric weight shaft 16A.
A synchronous transmission gear 22b is fixed to 6A. The pair of synchronous transmission gears 22a and 22b are meshed with each other, whereby the pair of fixed eccentric weights 9A and 9B are connected via gears so as to rotate synchronously in phase.

On the other hand, the movable eccentric weight 10B is integrally connected to the synchronous transmission gear 22d and is supported rotatably relative to the fixed eccentric weight shaft 23. Movable eccentric weight 1
Reference numeral 0A is integrally connected to the synchronous transmission gear 22c, and is rotatably supported relative to the inner shaft / fixed eccentric weight shaft 16A. The pair of synchronous transmission gears 22c and 22d are meshed with each other, thereby forming the pair of movable eccentric weights 10c.
A and 10B are connected via gears so that they rotate synchronously with each other in phase.

The components described above with reference to FIG. 1 are essentially the same as the previously-unknown device of the prior application shown in FIG. 9, and the same reference numerals are used in the drawings. However,
The suffixes of the synchronous transmission gears 22a to 22d in the prior art shown in FIG. 9 are given alphabetical letters in the order in which the rotational power is transmitted. The suffixes of the synchronous transmission gears 22a to 22d in FIG. 1 are not in the order of power transmission. Also, in the fixed eccentric weights 9A and 9B and the movable eccentric weights 10A and 10B in the embodiment of the prior art in FIG. This may not always be the case in the embodiment of the invention. Note that the fixed eccentric weight and the movable eccentric weight basically rotate synchronously, and the phase difference is adjusted to prevent resonance. As described above, the fixed eccentric weight and the movable eccentric weight are names that are relatively determined, and may be interchanged and called. In the present invention, the eccentric weight that is constrained in phase with respect to the rotation axis of the rotary drive device is referred to as a fixed eccentric weight,
An eccentric weight whose phase can be changed with respect to the rotation axis of the rotary drive device is called a movable eccentric weight.

Next, the difference between FIG. 1 and FIG. 9 described above, that is, the point of improvement by applying the present invention will be described. A drive / control concentric double shaft 25MV is rotatably supported on the exciter case 18 ', and its inner shaft is protruded to one side (left side in the figure) to rotate the drive device 19'.
(For example, a hydraulic motor or an electric motor)
Be able to drive in rotation. A pair of gears of the same diameter and the same module, a drive synchronous gear 26M, and a control synchronous gear 26M.
And a drive / control synchronous gear pair 26MV composed of V. The drive synchronous gear 26M is fixed to the inner shaft of the drive / control concentric shaft 25MV and meshed with the synchronous transmission gear 22b.

The other end (right side in the figure) of the drive / control concentric double shaft 25MV is projected out of the exciter case 18 'for both the inner shaft and the outer tube, and the reversible rotating mechanism 20 is mounted. I do. That is, the housing 20a of the reversible rotation mechanism is connected and fixed to the outer tube, and the rotation shaft 20b is connected to the inner shaft.
A control synchronous gear 26V is fixed to the outer tube of the drive / control concentric double shaft 25MV, and meshed with the synchronous transmission gear 22c. Thereby, the movable eccentric weight 1 is moved by the relative rotation angle of the rotation shaft 20b with respect to the housing 20a of the reversible rotation mechanism 20.
The rotation phases of 0A and 10B are changed. When the phase difference between the movable eccentric weights 10A and 10B and the fixed eccentric weights 9A and 9B changes, the total eccentric moment changes and the vibrating force is increased or decreased.

When comparing the embodiment shown in FIG. 1 with the previously-unknown invention shown in FIG. 9, the reversible rotation mechanism 20 and the rotary driving device 19 project to the side of the exciter case 18 in FIG. . In FIG. 1, this is as indicated by a virtual line for comparison and reference. Entire width W ₄ of the electromotive exciter shown in FIG. 9,
Compared to the width W ₁ of the exciter case, the rotary drive device 1
The projecting dimension W ₃ of 9 protruding dimension W ₂ or reversible rotation mechanism 20, are enlarged by whichever larger. In FIG. 1 (the present invention), the fixed eccentric weight shaft 23 and the inner shaft / fixed eccentric weight shaft 16A do not protrude to the side of the exciter case, and are rotationally driven on the extension of these shafts. Equipment 1
9, a drive / control concentric double shaft 25MV equipped with a drive / control synchronous gear pair 26MV was provided in parallel with the eccentric weight shaft without disposing the reciprocating rotation mechanism 9 and the reversible rotation mechanism 20.

The drive / control concentric dual shaft 25MV has:
The eccentric weight is not mounted, and the drive / control concentric double shaft 25MV does not move in the axial direction. For this reason, even if the rotary drive device 19 and the reversible rotation mechanism 20 are arranged and connected on an extension of the drive / control concentric double shaft, the overall length including these devices is the same as the exciter case 18. ′ Width dimension W
Not greater than _one . In addition, since the rotary drive device 19 and the reversible rotation mechanism 20 are located outside the exciter case 18 ', inspection and maintenance thereof are easy.

FIG. 2 is a sectional view of an embodiment different from FIG. 1 described above. However, the cut plane is not a simple vertical plane.
The structure below the line hh shown in FIG. 2 is the same as that of FIG. 1 described above. Above the hh line, it looks like a tall device, because it is cut and unfolded at the bent surface. See Figure 3 for the actual arrangement.
This will be described later with reference to FIG. Next, a point of the present embodiment (FIG. 2) that is different from the embodiment (FIG. 1) will be described.

The inner shaft drive concentric double shaft 25M shown in FIG.
Is a similar member corresponding to the drive / control concentric double shaft 25MV in FIG.
8 'is not penetrated, only the control synchronous gear 26V is fixed to the outer shaft of the double shaft, and the outer tube is rotatable relative to the inner shaft. Further, in parallel with the inner shaft drive concentric double shaft 25M, the outer tube control concentric double shaft 25V
And a drive / control synchronous gear pair 26MV is mounted. The drive synchronous gears 26M mounted on the respective concentric double shafts 25M and 25V are meshed with each other, and the control synchronous gears 26V are also meshed with each other. The tube control concentric double shaft 25V is synchronously rotated in the opposite direction, and is transmitted via a gear so that the inner shafts have the same phase and the outer tubes have the same phase.

One end of the outer tube control concentric double shaft 25V penetrates the wall of the exciter case 18 ', and a reversible rotating mechanism 20 is mounted at the end. This embodiment (FIG. 2)
In, the reversible rotation mechanism 20 is disposed on the right side of the drawing, that is, on the opposite side of the rotary driving device 19, but may be disposed on the left side of the drawing (the same side as the rotary driving device 19). It is. By arranging them on the same side, it becomes easy to reduce the width of the entire exciter. When the embodiment of FIG. 2 is adopted, the transmission path becomes complicated and the number of rotating shafts and the number of gears increase as compared with the embodiment of FIG. 1, but the transmission path is dispersed and noise is reduced, which is excellent. Has advantages.

The arrangement, meshing relationship, and transmission path of the synchronous transmission gear according to the present invention will be described below with reference to FIGS. 3, 4, and 5 sequentially. 1 and 2 depict a view seen from a direction perpendicular to the axis of the synchronous transmission gear, and FIGS. 3, 4 and 5 show a view seen in a direction parallel to the axis of the synchronous transmission gear. It is painted. For this reason, there are components that cannot be distinguished by overlapping in FIGS. 1 and 2, and components that cannot be distinguished by overlapping in FIGS. 3, 4, and 5. Since FIG. 1 and FIG. 2 have already been described, in the configurations shown in FIG. 1 and FIG. And a name will be added.

FIG. 3 is a transmission system schematically illustrating the arrangement of the synchronous transmission gear, the eccentric weight, its driving means, and the phase control means in the vibrating force control device of the eccentric weight type vibrator. FIG. 3 is an explanatory view of the structure and function of the present invention. FIG. 3 (A) is provided for convenience of explanation, and shows the invented device according to the previously unknown prior application shown in FIG. In FIG. 3A, FIG.
The synchronous transmission gears 22a and 22d overlap to form a single gear outer shape, and the synchronous transmission gears 22b and 22c overlap to form a single gear outer shape. Instead, the synchronous transmission gears 22a 'to 22d', which are hidden by overlapping with the synchronous transmission gears 22a to 22d in FIG. 9, appear. However,
The synchronous transmission gears 22a 'and 22d' overlap to form one gear outer shape, and the synchronous transmission gears 22b 'and 22c' overlap to form one gear outer shape.

In FIG. 9, the rotary driving device 19 is arranged coaxially with the synchronous transmission gears 22a and 22d. This state is shown in FIG.
(M mark). Further, the reversible rotating mechanism 20 arranged coaxially with the synchronous transmission gears 22b and 22c in FIG. 9 is replaced with the reversible rotating mechanism 20 (V
Mark). This expression method is described below with reference to FIGS.
Used in FIG.

In FIG. 3A, the synchronous transmission gear 22
b 'and the synchronous transmission gear 22c' overlap and are represented as one gear outer shape. These are collectively referred to as a synchronous transmission gear pair 26A as shown in FIG. Similarly, the synchronous transmission gears 22a 'and 22d' are defined as a synchronous transmission gear pair 26B, the synchronous transmission gears 22a and 22d are defined as a synchronous transmission gear pair C, and the synchronous transmission gears 22b and 22c are defined as a synchronous transmission gear pair D. , Name each. FIG. 3 above
The four sets of synchronous transmission gear pairs shown in FIG.
And a pair of the synchronous transmission gears 22b and 22c, and for example, as a pair of the synchronous transmission gears 22a and 22d, "a synchronous transmission gear integrally provided with the fixed eccentric weight". "A synchronous transmission gear integrally provided with the movable eccentric weight". These pairs of synchronous transmission gears need to have the same pitch circle diameter.

Looking at the relationship between the synchronous transmission gears in FIG. 9, four synchronous transmission gears 22a, 2
2b, 22c, and 22d. These four synchronous transmission gears must have the same pitch circle diameter. B. The synchronous transmission gears 22a and 22b and the synchronous transmission gears 22c and 22d must have the same module. C. The synchronous transmission gears 22a and 22d do not necessarily need to have the same module. (However, from the viewpoint of compatibility of components, it is desirable that the modules be equal.)

In FIG. 3A ', the center points of the gear shafts of the four pairs of synchronous transmission gears 26A, 26B, 26C, and 26D are square. Considering this three-dimensionally, the center lines of the four gear shafts are arranged along the ridges of the square prism. With this configuration, any one of the four synchronous transmission gear pairs meshes equally with two adjacent gear pairs. Therefore, the four gear pairs as a whole exhibit a balanced transmission state. Since the synchronous transmission gears in the eccentric weight type vibrator always receive a severe fluctuation load during operation, it is desirable from the viewpoint of durability that four gear pairs constitute an even transmission system.

Therefore, when the embodiment shown in FIG. 1 is expressed as a combination of a pair of synchronous transmission gears, it becomes as shown in FIG. 3 (B). This corresponds to the configuration described in claim 5.
That is, the center lines of the gear shafts of the four sets of synchronous transmission gear pairs 26A, 26B, 26C, and 26D are disposed along the ridge line of the square prism, and any one of the four sets of gear pairs is used. A drive / control synchronous gear pair 26MV is engaged with one set of synchronous transmission gear pairs, and the drive / control concentric double shaft 2
The rotary drive device 19 (marked M and the same hereinafter) and the reversible rotating mechanism 20 (marked V and the same hereinafter) are connected to the 5MV. Thereby, the operation and effect described above with reference to FIG. 1 can be obtained.

Similarly, the embodiment previously shown in FIG.
It is represented as (C). When the configuration of FIG. 3C is compared with the configuration of FIG. 3B, the control shaft gear pair 26V
Is added to the shaft of the rotary drive device 19 and the reversible rotation mechanism 20.
Can be seen as separated from the axis. Although there is a demerit that the number of constituent members is increased, there is an advantage that noise generation can be reduced as described in detail later. Next, the transmission path of the rotational power in the present embodiment will be described with reference to FIG. 2 and FIG. 3 (C).

The transmission path is defined by the rotational drive of the fixed eccentric weight,
The discussion will be divided into the case of rotary driving of the movable eccentric weight. When the rotary driving device 19 rotates, the driving synchronous gear 26M rotates, and the synchronous transmission gear pair 26A meshing with the driving synchronous gear 26M is rotated. Specifically, of the synchronous transmission gears 22b and 22c constituting the synchronous transmission gear pair 26A, the fixed eccentric weight 9B
, The synchronous transmission gear 22b fixed to is rotated.
When the synchronous transmission gear 22b rotates (see FIG. 2), the fixed eccentric weight 9B fixed thereto is rotated, and the synchronous transmission gear 2 meshed with the synchronous transmission gear 22b.
2a and the fixed eccentric weight 9A fixed thereto are rotated.

Below the reference line hh in FIG. 2, eight synchronous transmission gears are provided. However, when viewed in the direction perpendicular to the gear shaft, two synchronous transmission gears overlap and one gear outer shape appears in the figure, so a total of four gear outer shapes are shown. In each of the four synchronous transmission gear pairs in FIG. 3C, two synchronous transmission gears are overlapped in a direction parallel to the gear axis, and the actual number is eight as described above. Four of the eight synchronous transmission gears are integrally connected to the fixed eccentric weight, and the other four are integrally connected to the movable eccentric weight. In this way, the four fixed eccentric weights are synchronously rotated in phase with each other via the synchronous transmission gear, and the four rotating eccentric weights are synchronized with each other in phase via the synchronous transmission gear. It is rotated.

With the above structure, the synchronous transmission gear 22a meshed with the synchronous transmission gear 22b rotates as described in the paragraph 0069, and the fixed eccentric weight 9
B and the state in which the fixed eccentric weight 9A is synchronously rotated in the same phase are considered with reference to FIG. 3 (B). As shown in FIG. It is understood to rotate. The above is the transmission path of the fixed eccentric weight when the rotation driving device 19 rotates in FIG.

In FIG. 2, when the rotary driving device 19 is rotated to rotate the driving synchronous gear 26M, a total of four fixed eccentric weights are synchronously rotated in the same phase as described above. At the same time, the rotation of the driving device 19 is also transmitted to the inner shaft of the outer tube control concentric double shaft 25V via the driving synchronous transmission gears 26M, 26M. The rotation shaft 20b of the reversible rotation mechanism 20 connected to the inner shaft is rotated synchronously with the rotation driving device 19 in the same phase. The housing 20a of the reversible rotation mechanism 20 is basically rotated synchronously with respect to the rotation axis 20b. The phase changes by the angle of the change. Thereby, the outer tube control concentric double shaft 25
The phase of the outer tube is changed with respect to the inner axis of V.

Outer tube control When the outer tube of the concentric double shaft 25V rotates with its phase controlled, the rotation rotates the synchronous transmission gears 22c and 22d, which are integrally connected to these gears. Movable eccentric weights 10A and 10B
Rotate in “phase controlled” state. This allows
The total number of the four movable eccentric weights is rotated “in phase with each other” and “controlled with a phase difference with respect to the fixed eccentric weight”. The reversible rotation mechanism 20 is rotated at the same rotation speed as the rotation shaft of the rotary drive device 19, but the rotation shaft 20b with respect to the housing 20a (FIG. 2).
Can be arbitrarily operated, so that the phase difference between the movable eccentric weight and the fixed eccentric weight can be arbitrarily controlled.

Considering FIG. 3 (C), the transmission path of the fixed eccentric weight is from the rotary drive device 19 to the drive shaft gear pair 2.
6M, four sets of synchronous transmission gear pairs 26A, 26B, 2
Although the power is transmitted directly to 6C and 26D, the transmission path of the movable eccentric weight is complicated as described above. That is, the rotation of the rotary drive device 19 is transmitted to the control shaft gear pair 26V via the drive shaft gear pair 26M. Specifically, the synchronous transmission gear 2 fixed to the inner shaft of the control concentric double shaft 25V
6M (FIG. 2), the rotation transmitted to the reversible rotating mechanism 20 and the phase controlled by the reversible rotating mechanism is transmitted to the synchronous transmission gear 26V (FIG. )
Conveyed to.

The “phase-controlled rotation” transmitted to the control shaft gear pair 26V in FIG.
6M is transmitted to the synchronous transmission gear pair 26A as an idler gear, and further transmitted to the synchronous transmission gear pair 26A.
B, 26D, and transmitted to the synchronous transmission gear pair 26c, and the synchronous transmission gears integrally provided with the movable eccentric weight in these synchronous transmission gear pairs are in a "phase-controlled state".
And rotate synchronously with each other. Thus, the total number of the four movable eccentric weights is phase-controlled with respect to the four fixed eccentric weights, the total eccentric weight moment is adjusted, and the excitation force is increased or decreased.

When FIG. 3 (C) is compared with FIG. 3 (B),
At first glance, the movable eccentric weight is rotationally driven on a detoured transmission path as seemingly useless. However, according to the embodiment of FIG. 10C, the generation of noise is smaller than that of the embodiment of FIG. The reason why the noise is reduced is not completely understood in theory, but is a fact confirmed by experiments. In FIG. 3 (C), the fact that one synchronous transmission gear in the synchronous transmission gear pair 26M acts as an idler seems to contribute to noise reduction in some form.

The rotary drive device 19 (M) shown in FIG.
FIG. 3D shows an example of the arrangement of the reversible rotating mechanism 20 (V mark) and the reversible rotation mechanism 20 (V mark). Even with such a configuration, the same or similar effects as those in the embodiment of FIG. 3C described above (the total eccentric moment can be increased or decreased without increasing the overall width of the exciter, and noise generation can be suppressed). ) Is obtained. (See FIGS. 1 and 2) In the embodiments described above, the housing 20a of the reversible rotating mechanism 20 is restrained in the same phase as the fixed eccentric weight, and the rotating shaft 20b is in the same phase as the movable eccentric weight. Restrained. Although not shown, the above interlocking (same phase constraint) relationship can be replaced.

FIG. 4 is a schematic diagram showing three types of embodiments different from FIG. 3 described above, and is drawn from the same direction as FIG. The embodiment of FIG. 4 is basically different from the embodiment of FIG. 3 in the arrangement and meshing relationship of the four sets of synchronous transmission gear pairs. That is, the four synchronous transmission gear pairs 26A, 26B, 26C, and 26D shown in FIG. 26E, 26F, 26G, 2
When the center points of the gear shafts of 6H are sequentially connected, a U-shape is formed.

The modified U-shape is an indispensable matter in the structure of claim 6, and its details and definition will be described below. For example, when the center point of the synchronous transmission gear pair 26E, the center point of the same 26F, the center point of the same 26G, and the center point of the same 26H in FIG. 4A are sequentially connected, a shape similar to a U-shape is obtained. Since the diameters of the pitch circles of the four pairs of synchronous transmission gears are equal to each other, the lengths of the three sides forming the U-shape are necessarily equal. However, isometric 3
A U-shape whose sides are perpendicular to each other is substantially equal to a square, and FIG. 4A is equal to FIG. 3B. Now, as a modification of FIG. 3 (B), the synchronous transmission gear pair 26B and the synchronous transmission gear pair 26B, the meshing of the synchronous transmission gear pair 26A and the same 26D, and the synchronous transmission gear pair 26D and the same coupling 26C are maintained. When the pair 26B and the pair 26C are slightly separated from each other to cancel the meshing relationship therebetween, a state equivalent to FIG. 4A is obtained. In the present invention, the modified U-shape means that the shape is similar to the U-shape, three sides are equal in length, and at least one of the two corners forms an obtuse angle.

The embodiment of FIG. 4A can be regarded as a modification of the embodiment of FIG. 3B as described above. The following components also change with this deformation. The four sets of synchronous transmission gear pairs 26A, 26B, 26 in FIG.
C and 26D were mutually meshed evenly. Therefore, there was no substantial difference between any of the four sets of the synchronous transmission gear pairs when the drive / control shaft gear pair 26MV was engaged.
However, the four synchronous transmission gear pairs in FIG.
In order from the end, the synchronous transmission gear pair 26E, 26F, 26
Since the gear trains G and 26H are formed, the synchronous transmission gear pair 26E and 26H at the end and the synchronous transmission gear pair 26F and 26G at the center are not equivalent.

In this embodiment (FIG. 4A), the drive / control gear pair 26MV is connected to the synchronous transmission gear pair 26
F. Since the synchronous transmission gear pair 26G is equivalent to the synchronous transmission gear pair 26F in terms of the central synchronous transmission gear pair, the drive / control gear pair 26MV meshes with the synchronous transmission gear pair 26G instead of meshing with the synchronous transmission gear pair 26F. This is substantially the same as in the embodiment of FIG. In FIG. 4A, the drive / control gear pair 26MV meshes with the central synchronous transmission gear pair of the four synchronous transmission gear pairs arranged in a U-shape. The power transmission path is short, and an operation and effect similar to the operation and effect in FIG.

The embodiment shown in FIG. 4B is a modification of the embodiment shown in FIG. 3C, and the modifications are as follows.
The four sets of synchronous transmission gear pairs 26A to 26 in FIG.
FIG. 4 (B) shows that D is arranged in a square shape.
The four pairs of synchronous transmission gears 26E to 26G are arranged in a U-shape. The pair of drive shaft gears 26M and the pair of control shaft gears 26V are respectively connected to a pair of synchronous transmission gears 26F and 2
6G meshed. With this configuration, FIG.
Functions and effects similar to those of the embodiment (C) are obtained. However, as is clear from comparison between the two figures, the transmission path from the control shaft gear pair 26V to the movable eccentric weight in FIG. 4B is shorter than that in FIG. 3C. Therefore, the transmission energy efficiency is excellent. The embodiment of FIG. 4C is the same as that of FIG.
In this embodiment, the "rotary drive device 9 and the drive shaft gear pair 26M" and the "reversible rotation mechanism 20 and the control shaft gear pair 26V" are replaced. However, since the gear trains of the four sets of synchronous transmission gear pairs 26E to 26H are symmetrical left and right in the figure, the embodiment of FIG.
Is substantially the same as that of the first embodiment.

FIG. 5 is a schematic diagram showing three types of embodiments different from those described above as viewed from a direction parallel to the gear shaft. Also in the embodiment of FIG. 5, four sets of synchronous transmission gear pairs are arranged in a modified U-shape “similar to FIG. 3 and different from FIG. 2 described above”. When the four sets of synchronous transmission gear pairs are arranged in a square shape as in the embodiment of FIG. 3, there is an advantage that the meshing state of each of the four sets of synchronous transmission gear pairs becomes uniform.
Accurately engaging the synchronous transmission gear pairs arranged in this manner and accurately adjusting the backlash thereof requires high-precision machining and assembly, and requires a considerable manufacturing cost. On the other hand, it is easy to make a single gear train by arranging four sets of synchronous transmission gear pairs in a U-shape in a modified U-shape, and the manufacturing cost is low.

The embodiment of FIG. 5A is the same as that of FIG.
4A, a drive / control gear meshed with a central synchronous transmission gear among four pairs of synchronous transmission gears arranged in a modified U-shape in FIG. Vs. 26
In FIG. 5 (A), the MV is meshed with a synchronous transmission gear pair 26E located at the end of four synchronous transmission gear pairs arranged in a U-shape. With this configuration, the transmission path for rotating the fixed eccentric weight and the driving path for rotating the movable eccentric weight are also long, but this is effective for noise reduction.

The embodiment shown in FIG. 5B is a modification of the embodiment shown in FIG. 4B, in which the drive shaft control gear pair 26M is meshed with the synchronous transmission gear pair 26E at the end of the U-shape. In addition, the control shaft gear pair 26V meshes only with the drive shaft gear pair 26M, and does not mesh with any of the synchronous transmission gear pairs 26E to 26H. In view of the fact that the control shaft gear pair 26V is not directly engaged with the synchronous transmission gear pair as described above, the embodiment of FIG.
It is similar to the embodiment of (C). However, FIG.
In (B), the transmission path for rotating the fixed eccentric weight via the gear train composed of four synchronous transmission gear pairs is long. Due to the long transmission path, the energy efficiency is slightly reduced, but the noise reduction effect is large.

The embodiment shown in FIG. 5C is a modification of the embodiment shown in FIG. 5B. In this embodiment, the control shaft gear pair 26V is meshed without engaging the drive gear 28 mounted on the drive shaft 27 directly connected to the rotary drive device 19 with the control shaft gear pair 26V. And the synchronous transmission gear pair 26H located at the gear train at the opposite end of the synchronous transmission gear pair 26E. Therefore, focusing on the gear train of the four sets of synchronous transmission gear pairs having a U-shape, the rotary drive device 19 and the reversible rotation mechanism 20 are arranged at opposite ends. For this reason, the transmission path of the movable eccentric weight is the longest as compared with the above-described embodiments.

When the drive gear 28 is driven to rotate, the rotation is "a synchronous transmission gear integrally provided with the fixed eccentric weight of the two gears constituting the synchronous transmission gear pair 26H".
And transmitted to the synchronous transmission gear pair 26E in the same manner. Thus, the four fixed eccentric weights are synchronously rotated in phase with each other. The rotation of the synchronous transmission gear pair 26E is controlled by the control shaft gear pair 26V and the outer tube control concentric double shaft 2.
The power is sequentially transmitted to the reversible rotating mechanism 20 via the inner shaft of 5 V, and the phase is controlled here. The phase-controlled synchronous rotation is performed in the reverse order from the previous one by sequentially passing through the outer tube of the outer tube control concentric double shaft 25V and the control shaft gear pair 26V and the synchronous transmission gear pair 26.
E, the "movable eccentric weight which is integrally connected to one of the gear pairs" is synchronously rotated in a phase-controlled state. This rotation is further performed by the synchronous transmission gear pair 26F,
The signal is transmitted to 26H via 6G, whereby the total number of the four movable eccentric weights is rotated in synchronization with each other and with the phase difference with respect to the fixed eccentric weight controlled. The embodiment of FIG. 5C described above has the longest transmission path as compared with the other embodiments described above. For this reason, the transmission energy efficiency is the lowest, but the noise reduction effect is excellent.

[0088]

As described above, according to the embodiment of the present invention, the structure and function of the eccentric weight type vibrator according to the first aspect of the present invention are clarified. A drive shaft and a control shaft composed of a concentric double shaft are provided separately from the spindle, and the above-mentioned concentric double shaft for driving and controlling requires rotation around the axis, but is moved in the axial direction. No need,
In addition, since the eccentric weight is not mounted on the concentric double shaft for driving and control, it can be configured to be much shorter than the eccentric weight shaft. In this way, the drive
Within the range of the dimension of the concentric double shaft for control being shorter than the eccentric weight shaft, a rotary drive device and a reversible rotating mechanism are arranged and connected to the concentric double shaft for drive and control. (This is a design consideration) so that the total length of the drive and control shafts connecting the rotary drive device and the reversible rotation mechanism is shorter than the length of the eccentric weight shaft. be able to. On the other hand, the width dimension (specifically, the dimension in the eccentric weight axis direction) of the exciter case is substantially equal to the length dimension of the eccentric weight axis. In consideration of the above, the overall length of the drive and control shafts according to the configuration of the present invention is not likely to stick out in the width direction of the exciter case even when the rotary drive device and the reversible rotating mechanism are included, and The entire width direction of the entire shaker is not enlarged. The inner shaft and the outer tube of the concentric double shaft rotate synchronously with the fixed eccentric weight via a driving synchronous gear and a synchronous transmission gear, respectively, and move eccentrically via a control synchronous gear and a synchronous transmission gear. Since the rotation is synchronized with the weight, when the reversible rotation mechanism is operated to rotate the rotation shaft with respect to the housing, the inner shaft is relatively rotated with respect to the outer tube. That is, the phase difference between the inner shaft and the outer tube changes. When the phase difference between the inner shaft and the outer tube changes as described above, the phase difference between the fixed eccentric weight and the movable eccentric weight that are rotating synchronously with respect to the inner shaft and the outer tube changes. Thus, the total eccentric moment of these eccentric weights changes, and the vibrating force can be changed without changing the rotation speed.

According to the device of the second aspect of the present invention, the drive shaft and the control shaft each formed of a concentric double shaft are provided separately from the eccentric weight shaft constituting the eccentric weight type vibrator. The concentric double shaft for driving and the concentric double shaft for control require rotation around the axis, but it is not necessary to move in the axial direction,
In addition, since the eccentric weight is not mounted on these concentric double shafts for driving and control, it can be configured to be much shorter than the eccentric weight shaft. In this way, the concentric double shaft for driving and the concentric double shaft for control are within the range of the dimension shortened than the eccentric weight shaft, with respect to the concentric double shaft for driving and control. Considering that a rotary driving device and a reversible rotating mechanism are arranged and connected respectively (this is a design consideration), a concentric double shaft for driving that connects the rotary driving device, and a reversible rotary The total length of each of the control concentric double shafts to which the mechanisms are connected can be configured to be shorter than the length of the eccentric weight shaft. On the other hand, the width dimension (dimension in the eccentric weight axis direction) of the exciter case is substantially equal to the length dimension of the eccentric weight axis. In summary, the total length of the driving concentric double shaft and the total length of the concentric double shaft for control according to the configuration of the present invention is the same as that of the vibration exciter case even if it includes a rotary driving device or a reversible rotating mechanism. There is no danger of sticking out in the width direction of the exciter, and the entire width direction of the entire exciter is not enlarged. And, the inner shaft and outer tube of the concentric double shaft,
The synchronous rotation with the fixed eccentric weight via the drive synchronization gear and the synchronous transmission gear, and the synchronous rotation with the movable eccentric weight via the control synchronization gear and the synchronous transmission gear, respectively, actuate the reversible rotation mechanism. Then, when the rotating shaft is rotated with respect to the housing, the inner shaft is relatively rotated with respect to the outer tube. That is, the phase difference between the inner shaft and the outer tube changes. When the phase difference between the inner shaft and the outer tube changes as described above, the phase difference between the fixed eccentric weight and the movable eccentric weight that are rotating synchronously with respect to the inner shaft and the outer tube changes. Thus, the total eccentric moment of these eccentric weights changes, and the vibrating force can be changed without changing the rotation speed.

According to the third aspect of the present invention, the eccentric weight type vibrator is provided with a drive shaft and a control shaft, which are formed separately from the eccentric weight shaft, and are formed separately from the eccentric weight shaft. The concentric double shaft for driving and the concentric double shaft for control require rotation around the axis, but it is not necessary to move in the axial direction,
In addition, since the eccentric weight is not mounted on these concentric double shafts for driving and control, it can be configured to be much shorter than the eccentric weight shaft. In this way, the concentric double shaft for driving and the concentric double shaft for control are within the range of the dimension shortened than the eccentric weight shaft, with respect to the concentric double shaft for driving and control. Considering that a rotary driving device and a reversible rotating mechanism are arranged and connected respectively (this is a design consideration), a concentric double shaft for driving that connects the rotary driving device, and a reversible rotary The total length of each of the control concentric double shafts to which the mechanisms are connected can be configured to be shorter than the length of the eccentric weight shaft. On the other hand, the width dimension (dimension in the eccentric weight axis direction) of the exciter case is substantially equal to the length dimension of the eccentric weight axis. In summary, the total length of the driving concentric double shaft and the total length of the concentric double shaft for control according to the configuration of the present invention is the same as that of the vibration exciter case even if it includes a rotary driving device or a reversible rotating mechanism. There is no danger of sticking out in the width direction of the exciter, and the entire width direction of the entire exciter is not enlarged. And, the inner shaft and outer tube of the concentric double shaft,
The synchronous rotation with the fixed eccentric weight via the drive synchronization gear and the synchronous transmission gear, and the synchronous rotation with the movable eccentric weight via the control synchronization gear and the synchronous transmission gear, respectively, actuate the reversible rotation mechanism. Then, when the rotating shaft is rotated with respect to the housing, the inner shaft is relatively rotated with respect to the outer tube. That is, the phase difference between the inner shaft and the outer tube changes. When the phase difference between the inner shaft and the outer tube changes as described above, the phase difference between the fixed eccentric weight and the movable eccentric weight that are rotating synchronously with respect to the inner shaft and the outer tube changes. Thus, the total eccentric moment of these eccentric weights changes, and the vibrating force can be changed without changing the rotation speed.

According to the fourth aspect of the present invention, the drive shaft and the control shaft each formed of a concentric double shaft are provided separately from the eccentric weight shaft constituting the eccentric weight type vibrator. The concentric double shaft for driving and the concentric double shaft for control require rotation around the axis, but it is not necessary to move in the axial direction,
In addition, since the eccentric weight is not mounted on these concentric double shafts for driving and control, it can be configured to be much shorter than the eccentric weight shaft. In this way, the concentric double shaft for driving and the concentric double shaft for control are within the range of the dimension shortened than the eccentric weight shaft, with respect to the concentric double shaft for driving and control. Considering that a rotary driving device and a reversible rotating mechanism are arranged and connected respectively (this is a design consideration), a concentric double shaft for driving that connects the rotary driving device, and a reversible rotary The total length of each of the control concentric double shafts to which the mechanisms are connected can be configured to be shorter than the length of the eccentric weight shaft. On the other hand, the width dimension (dimension in the eccentric weight axis direction) of the exciter case is substantially equal to the length dimension of the eccentric weight axis. In summary, the total length of the driving concentric double shaft and the total length of the concentric double shaft for control according to the configuration of the present invention is the same as that of the vibration exciter case even if it includes a rotary driving device or a reversible rotating mechanism. There is no danger of sticking out in the width direction of the exciter, and the entire width direction of the entire exciter is not enlarged. And, the inner shaft and outer tube of the concentric double shaft,
The synchronous rotation with the fixed eccentric weight via the drive synchronization gear and the synchronous transmission gear, and the synchronous rotation with the movable eccentric weight via the control synchronization gear and the synchronous transmission gear, respectively, actuate the reversible rotation mechanism. Then, when the rotating shaft is rotated with respect to the housing, the inner shaft is relatively rotated with respect to the outer tube. That is, the phase difference between the inner shaft and the outer tube changes. When the phase difference between the inner shaft and the outer tube changes as described above, the phase difference between the fixed eccentric weight and the movable eccentric weight that are rotating synchronously with respect to the inner shaft and the outer tube changes. Thus, the total eccentric moment of these eccentric weights changes, and the vibrating force can be changed without changing the rotation speed.

When the invention of claim 5 is applied to any of the above-described invention devices of claims 1 to 4, it is possible to increase the width of the vibration exciter in the invention of claims 1 to 4. And without interrupting the operation of the exciter, it is possible to reduce or increase the vibrating force to suppress the vibration pollution in the punching operation of the vibrating pile. At least four sets of synchronous transmission gears for fixed eccentric weights and movable eccentrics that regulate the rotational phase of at least four sets of “fixed eccentric weights and movable eccentric weights” supported by the eccentric weight shafts The synchronous transmission gear pair with the weight transmission gear '' is properly meshed with each other,
Reliable phase control can be performed. In particular,
Since the four eccentric weight shafts are arranged along the ridge of the square prism, the four synchronous transmission gears for the fixed eccentric weight and the four synchronous transmission gears for the movable eccentric weight are respectively provided. About any one of the four gears, the gear is meshed with two adjacent gears,
The transmission load is even.

When the invention of claim 6 is applied to any of the above-described invention devices of claims 1 to 4, it is possible to increase the width of the vibrator in the invention of claims 1 to 4. And without interrupting the operation of the exciter, it is possible to reduce or increase the vibrating force to suppress the vibration pollution in the punching operation of the vibrating pile. At least four sets of synchronous transmission gears for fixed eccentric weights and movable eccentrics that regulate the rotational phase of at least four sets of “fixed eccentric weights and movable eccentric weights” supported by the eccentric weight shafts The synchronous transmission gear pair with the weight transmission gear '' is properly meshed with each other,
Reliable phase control can be performed. In particular,
Since the four eccentric weight shafts are arranged along the ridge of the square prism, the four synchronous transmission gears for the fixed eccentric weight and the four synchronous transmission gears for the movable eccentric weight are respectively provided. About any one of the four gears, the gear is meshed with two adjacent gears,
The transmission load is even.

According to the device of claim 7, the power transmission of the reversible rotating mechanism is performed by hydraulic pressure or electromagnetic force, and the wedge action between the metal members is not used unlike the screw means in the prior art. There is no point where the metal member slips while receiving local pressure. For this reason,
High durability and reliability. The rotation phase of the housing of the reversible rotation mechanism is constrained to match the rotation phase of the fixed eccentric weight, and the rotation phase of the rotation axis of the reversible rotation mechanism matches the rotation phase of the movable eccentric weight. Contrary to this, constraining so that the rotation phase of the casing of the reversible rotation mechanism matches the rotation phase of the movable eccentric weight,
Even if the rotation axis of the reversible rotation mechanism is restricted so as to coincide with the rotation phase of the fixed eccentric weight, the same operation and effect can be obtained. The device according to the seventh aspect of the present invention has a large degree of freedom in design as understood from the above-mentioned functions, and has a high practical value.

According to the eighth aspect of the present invention, the eccentric weight type vibrator is provided with a drive shaft and a control shaft composed of a concentric double shaft separately from the eccentric weight shaft. The drive and control concentric double shaft requires rotation around the axis, but does not need to be moved in the axial direction, and furthermore, the drive and control concentric double shaft has an eccentric weight. Is not mounted, so that it can be configured to be much shorter than the eccentric weight spindle. In this way, the drive and control concentric double shaft is rotatable with respect to the drive and control concentric double shaft within a range of dimensions shorter than the eccentric weight shaft. By considering the arrangement and connection of the mechanisms (this is a design consideration), the total length of the drive and control shafts connecting the rotary drive device and the reversible rotation mechanism is reduced by the length of the eccentric weight shaft. It can be configured to be shorter than the dimensions. On the other hand, the width of the exciter case (specifically, the dimension in the axial direction of the eccentric weight) is
The length is substantially equal to the length of the eccentric weight shaft. Taken together, the total length of the drive and control shafts according to the configuration of the present invention is:
Even if a rotary drive device or a reversible rotating mechanism is included, there is no danger of bleeding in the width direction of the exciter case, and the entire width direction of the entire exciter is not enlarged. The inner shaft and the outer tube of the concentric double shaft rotate synchronously with the fixed eccentric weight via a driving synchronous gear and a synchronous transmission gear, respectively, and move eccentrically via a control synchronous gear and a synchronous transmission gear. Since the rotation is synchronized with the weight, when the reversible rotation mechanism is operated to rotate the rotation shaft with respect to the housing, the inner shaft is relatively rotated with respect to the outer tube. That is, the phase difference between the inner shaft and the outer tube changes. When the phase difference between the inner shaft and the outer tube changes as described above, the phase difference between the fixed eccentric weight and the movable eccentric weight that are rotating synchronously with respect to the inner shaft and the outer tube changes. Thus, the total eccentric moment of these eccentric weights changes, and the vibrating force can be changed without changing the rotation speed.

According to the ninth aspect of the present invention, the drive shaft and the control shaft each formed of a concentric double shaft are provided separately from the eccentric weight shaft constituting the eccentric weight type vibrator. The concentric double shaft for driving and the concentric double shaft for control require rotation around the axis, but it is not necessary to move in the axial direction,
In addition, since the eccentric weight is not mounted on these concentric double shafts for driving and control, it can be configured to be much shorter than the eccentric weight shaft. In this way, the concentric double shaft for driving and the concentric double shaft for control are within the range of the dimension shortened than the eccentric weight shaft, with respect to the concentric double shaft for driving and control. Considering that a rotary driving device and a reversible rotating mechanism are arranged and connected respectively (this is a design consideration), a concentric double shaft for driving that connects the rotary driving device, and a reversible rotary The total length of each of the control concentric double shafts to which the mechanisms are connected can be configured to be shorter than the length of the eccentric weight shaft. On the other hand, the width dimension (dimension in the eccentric weight axis direction) of the exciter case is substantially equal to the length dimension of the eccentric weight axis. In summary, the total length of the driving concentric double shaft and the total length of the concentric double shaft for control according to the configuration of the present invention is the same as that of the vibration exciter case even if it includes a rotary driving device or a reversible rotating mechanism. There is no danger of sticking out in the width direction of the exciter, and the entire width direction of the entire exciter is not enlarged. And, the inner shaft and outer tube of the concentric double shaft,
The synchronous rotation with the fixed eccentric weight via the drive synchronization gear and the synchronous transmission gear, and the synchronous rotation with the movable eccentric weight via the control synchronization gear and the synchronous transmission gear, respectively, actuate the reversible rotation mechanism. Then, when the rotating shaft is rotated with respect to the housing, the inner shaft is relatively rotated with respect to the outer tube. That is, the phase difference between the inner shaft and the outer tube changes. When the phase difference between the inner shaft and the outer tube changes as described above, the phase difference between the fixed eccentric weight and the movable eccentric weight that are rotating synchronously with respect to the inner shaft and the outer tube changes. Thus, the total eccentric moment of these eccentric weights changes, and the vibrating force can be changed without changing the rotation speed.

According to the tenth aspect of the present invention, the drive shaft and the control shaft each formed of a concentric double shaft are provided separately from the eccentric weight shaft constituting the eccentric weight type vibrator. The concentric double shaft for driving and the concentric double shaft for control require rotation around the axis, but need not be moved in the axial direction, and furthermore, these concentric double shafts for driving and control. , The eccentric weight is not mounted, so that it can be configured to be much shorter than the eccentric weight shaft. In this way, the concentric double shaft for driving and the concentric double shaft for control are within the range of the dimension shortened than the eccentric weight shaft, with respect to the concentric double shaft for driving and control. Considering that a rotary driving device and a reversible rotating mechanism are arranged and connected respectively (this is a design consideration), a concentric double shaft for driving that connects the rotary driving device, and a reversible rotary The total length of each of the control concentric double shafts to which the mechanisms are connected can be configured to be shorter than the length of the eccentric weight shaft. On the other hand, the width dimension (dimension in the eccentric weight axis direction) of the exciter case is substantially equal to the length dimension of the eccentric weight axis. In summary, the total length of the driving concentric double shaft and the total length of the concentric double shaft for control according to the configuration of the present invention is the same as that of the vibration exciter case even if it includes a rotary driving device or a reversible rotating mechanism. There is no danger of sticking out in the width direction of the exciter, and the entire width direction of the entire exciter is not enlarged. The inner shaft and the outer tube of the concentric double shaft rotate synchronously with the fixed eccentric weight via a driving synchronous gear and a synchronous transmission gear, respectively, and move eccentrically via a control synchronous gear and a synchronous transmission gear. Since the rotation is synchronized with the weight, when the reversible rotation mechanism is operated to rotate the rotation shaft with respect to the housing, the inner shaft is relatively rotated with respect to the outer tube. That is, the phase difference between the inner shaft and the outer tube changes. When the phase difference between the inner shaft and the outer tube changes as described above, the phase difference between the fixed eccentric weight and the movable eccentric weight that are rotating synchronously with respect to the inner shaft and the outer tube changes. Thus, the total eccentric moment of these eccentric weights changes, and the vibrating force can be changed without changing the rotation speed.

According to the eleventh aspect of the present invention, the drive shaft and the control shaft each having a concentric double shaft are provided separately from the eccentric weight shaft constituting the eccentric weight type vibrator. The concentric double shaft for driving and the concentric double shaft for control require rotation around the axis, but need not be moved in the axial direction, and furthermore, these concentric double shafts for driving and control. Since the eccentric weight is not attached to, it can be configured to be much shorter than the eccentric weight shaft. In this way, the concentric double shaft for driving and the concentric double shaft for control are within the range of the dimension shortened than the eccentric weight shaft, with respect to the concentric double shaft for driving and control. Considering that a rotary driving device and a reversible rotating mechanism are arranged and connected respectively (this is a design consideration), a concentric double shaft for driving that connects the rotary driving device, and a reversible rotary The total length of each of the control concentric double shafts to which the mechanisms are connected can be configured to be shorter than the length of the eccentric weight shaft. On the other hand, the width dimension (dimension in the eccentric weight axis direction) of the exciter case is substantially equal to the length dimension of the eccentric weight axis. In summary, the total length of the driving concentric double shaft and the total length of the concentric double shaft for control according to the configuration of the present invention is the same as that of the vibration exciter case even if it includes a rotary driving device or a reversible rotating mechanism. There is no danger of sticking out in the width direction of the exciter, and the entire width direction of the entire exciter is not enlarged. The inner shaft and the outer tube of the concentric double shaft rotate synchronously with the fixed eccentric weight via a driving synchronous gear and a synchronous transmission gear, respectively, and move eccentrically via a control synchronous gear and a synchronous transmission gear. Since the rotation is synchronized with the weight, when the reversible rotation mechanism is operated to rotate the rotation shaft with respect to the housing, the inner shaft is relatively rotated with respect to the outer tube. That is, the phase difference between the inner shaft and the outer tube changes. When the phase difference between the inner shaft and the outer tube changes as described above, the phase difference between the fixed eccentric weight and the movable eccentric weight that are rotating synchronously with respect to the inner shaft and the outer tube changes. Thus, the total eccentric moment of these eccentric weights changes, and the vibrating force can be changed without changing the rotation speed.

[Brief description of the drawings]

FIG. 1 is a view for explaining one embodiment of a vibrating force control device of an eccentric weight type vibrator according to the present invention,
FIG. 4 is a diagram in which “installation positions of a rotary drive device and a reversible rotation mechanism in a vibration control device according to the prior art” are indicated by phantom lines in a schematic vertical sectional view.

FIG. 2 is a cross-sectional view of an embodiment different from FIG. 1 described above.
However, the cut plane is not a simple vertical plane.

FIG. 3 is a structural function of a transmission system schematically illustrating an arrangement of a synchronous transmission gear, an eccentric weight, a drive unit thereof, and a phase control unit in an excitation force control device of an eccentric weight type exciter. FIG.

FIG. 4 shows three different embodiments from FIG. 3 above,
FIG. 4 is a schematic diagram viewed from the same direction as FIG. 3.

FIG. 5 is a schematic view showing three different embodiments from the above, and viewed from a direction parallel to a gear shaft.

FIG. 6 is a schematic diagram for explaining vibration pollution in a pile driving operation. This figure shows a crane boom 5 and a vibration device 6
While the upper end of the pile 7 is gripped by the chuck 6a of the vibrating device 6, and the pile 7 is vibrated to be driven into the ground.

FIG. 7 is a chart showing a change in frequency at the time of starting and stopping the operation of the vibration device, and the horizontal axis is time.

FIG. 8 is a view for explaining a known technique for changing the vibrating force by a combination of two eccentric weights, wherein (A) shows that the two eccentric weights exert the maximum vibrating force; (B) is a schematic diagram showing a state where the vibrating force is medium, (C) is a schematic diagram showing a state where the vibrating force is slightly small, and (D) is a schematic diagram showing a state where the vibrating force is slightly small. It is a schematic diagram showing a state.

FIG. 9 is a cross-sectional view showing an example of an eccentric weight-type vibrator of a variable vibrating force type according to an unknown prior application.

FIG. 10 is a cross-sectional view of an exciter capable of adjusting an excitatory force according to a previously unknown application, which is different from FIG. 9 described above.

FIG. 11 is a schematic diagram of a mechanism in which a fixed eccentric weight is fixed to a common rotation shaft and a movable eccentric weight can adjust a relative rotation angle position with respect to the common rotation shaft.

[Explanation of symbols]

 2 ... Rotating shaft 2B ... Fixed eccentric weight shaft 2C ... Movable eccentric weight shaft 4B, 4C ... Synchronous transmission gear 5 ... Crane boom 6 ... Vibration device (vibrator) 9,9A, 9B ... Fixed eccentric weight 10. 10A, 10B: movable eccentric weight 16A, 16B: inner shaft / fixed eccentric weight shaft 17A, 17B: outer tube / movable eccentric weight shaft 18, 18 '... exciter case 19, 19' ... rotary driving device 20 ... reversible rotation mechanism 20a ... housing 20b ... rotation shaft 22, 22a to 22d ... synchronous transmission gear 22e ... drive synchronous transmission gear 22f ... control synchronous transmission gear 23 ... fixed eccentric weight spindle 25MV ... drive and control concentric. Double shaft 25M: inner shaft drive concentric double shaft 25V: outer tube control concentric double shaft 26A to 26D: synchronous transmission gear pair 26MV: drive / control synchronous gear pair 26M: drive synchronous gear pair 26V: control synchronous Gear pair 27 ... Shaft 28 ... drive gear

Claims (11)

[Claims] 1. A method according to claim 1, wherein each of the plurality of eccentric weight shafts includes:
A fixed eccentric weight and a movable eccentric weight are supported rotatably and relatively rotatably, and a plurality of fixed eccentric weights are interlocked by a synchronous transmission gear so as to rotate in the same phase. The plurality of movable eccentric weights are interlocked so as to rotate in phase with each other by a synchronous transmission gear, and the plurality of fixed eccentric weights and the movable eccentric weights are fixed while rotating about the eccentric weight axis. By changing the phase difference between the eccentric weight and the movable eccentric weight and changing the total eccentric moment of the fixed eccentric weight and the movable eccentric weight, the vibrating force can be continuously maintained without interrupting the operation. In a vibrating force control device for an eccentric weight type vibrator of a changing type, a drive shaft and a control shaft are also provided in parallel with the eccentric weight shaft, and the drive / control shaft is: It consists of an inner shaft and outer tube that can rotate relatively. Either the inner shaft or the outer tube of the concentric double shaft is the same as the synchronous transmission gear with respect to the synchronous transmission gear that links the fixed eccentric weights to each other. It is connected via a similar synchronous transmission gear, and is driven to rotate by a rotary drive device. The other one of the inner shaft and the outer tube of the concentric double shaft is connected to the movable eccentric weight Are connected to the synchronous transmission gear through the same or similar synchronous transmission gear as the synchronous transmission gear, and the inner shaft and the outer pipe of the concentric double pipe are reversibly rotated. The rotating shaft of the mechanism and the housing are connected to each other, and the inner shaft and the outer tube are relatively rotated by the reversible rotating mechanism, so that the fixed eccentric weight and the movable eccentric weight are Characterized in that the phase difference is adjusted to increase or decrease Vibratory force control apparatus of the heart weight-type exciter. 2. Each of the plurality of eccentric weight shafts
A fixed eccentric weight and a movable eccentric weight are supported rotatably and relatively rotatably, and a plurality of fixed eccentric weights are interlocked by a synchronous transmission gear so as to rotate in the same phase. The plurality of movable eccentric weights are interlocked with each other so as to rotate in phase with each other by a synchronous transmission gear. By changing the phase difference between the eccentric weight and the movable eccentric weight and changing the total eccentric moment of the fixed eccentric weight and the movable eccentric weight, the vibrating force can be continuously maintained without interrupting the operation. In a vibrating force control device for an eccentric weight type vibrator having a variable system, a concentric double shaft in which an inner shaft and an outer tube are relatively rotatably fitted in parallel with the eccentric weight shaft. Two are arranged, of the two concentric double shafts One side is an inner shaft driving concentric double shaft with a rotary driving device connected to its inner shaft, and a driving synchronization gear mounted on the inner shaft is a synchronous gear that links the fixed eccentric weights to each other. While being meshed with the transmission gear,
A control synchronous gear mounted on the outer tube is meshed with a synchronous transmission gear for interlocking the movable eccentric weights, and the other of the two concentric double shafts has an inner shaft. Is a rotating shaft of the reversible rotating mechanism, the outer tube is a housing of the reversible rotating mechanism, the outer tube control concentric double shaft respectively connected,
The drive synchronous gear mounted on the inner shaft meshes with the drive synchronous gear of the inner shaft drive concentric double shaft, and the control synchronous gear mounted on the outer tube is driven by the inner shaft drive concentric double shaft. The rotational force generated by the driving of the rotary driving device is transmitted to two systems, and one of the transmission systems rotates the fixed eccentric weight via the driving synchronous gear, and the other transmits the rotational force. The transmission system has a structure in which the movable eccentric weight is rotated sequentially through a driving synchronous gear, a reversible rotating mechanism, and a controlling synchronous gear, and the rotating shaft of the reversible rotating mechanism is rotated with respect to the housing. By moving the control eccentric weight, the control synchronous gear is rotated relatively to the drive synchronous gear, and the phase difference between the fixed eccentric weight and the movable eccentric weight is increased or decreased. An excitation force control device for an eccentric weight-type exciter, characterized in that: 3. Each of the plurality of eccentric weight shafts,
A fixed eccentric weight and a movable eccentric weight are supported rotatably and relatively rotatably, and a plurality of fixed eccentric weights are interlocked by a synchronous transmission gear so as to rotate in the same phase. The plurality of movable eccentric weights are interlocked with each other so as to rotate in phase with each other by a synchronous transmission gear. By changing the phase difference between the eccentric weight and the movable eccentric weight and changing the total eccentric moment of the fixed eccentric weight and the movable eccentric weight, the vibrating force can be continuously maintained without interrupting the operation. In a vibrating force control device for an eccentric weight type vibrator having a variable system, a concentric double shaft in which an inner shaft and an outer tube are relatively rotatably fitted in parallel with the eccentric weight shaft. Two are arranged, of the two concentric double shafts One is an outer tube control concentric double shaft connected to the inner shaft as the rotation shaft of the reversible rotation mechanism, and the outer tube to the casing of the reversible rotation mechanism, respectively. The mounted drive synchronous gear is meshed with the synchronous transmission gear that links the fixed eccentric weights to each other, and the control transmission gear mounted to the outer tube links the movable eccentric weights to each other. And the other of the two concentric double shafts is an inner shaft drive concentric double shaft whose inner shaft is connected to a rotary driving device, and the inner shaft is The drive synchronous gear mounted on the outer tube engages with the drive synchronous transmission gear of the outer tube control concentric double shaft, and the control synchronous gear mounted on the outer tube controls the outer tube control concentric double shaft. And the rotational force generated by driving the rotary drive device is transmitted to two systems. One of the transmission systems rotates a fixed eccentric weight via a driving synchronous gear, and the other transmission system sequentially moves a movable eccentric weight via a driving synchronous gear, a reversible rotating mechanism, and a control synchronous gear. A structure for rotating a weight, wherein the control synchronization gear is relatively rotated with respect to the drive synchronization gear by rotating a rotation shaft of the reversible rotation mechanism with respect to the housing. And a phase difference between the fixed eccentric weight and the movable eccentric weight is adjusted to increase or decrease. 4. Each of the plurality of eccentric weight shafts
A fixed eccentric weight and a movable eccentric weight are supported rotatably and relatively rotatably, and a plurality of fixed eccentric weights are interlocked by a synchronous transmission gear so as to rotate in the same phase. The plurality of movable eccentric weights are interlocked so as to rotate in phase with each other by a synchronous transmission gear, and the plurality of fixed eccentric weights and the movable eccentric weights are fixed while rotating about the eccentric weight axis. By changing the phase difference between the eccentric weight and the movable eccentric weight and changing the total eccentric moment of the fixed eccentric weight and the movable eccentric weight, the vibrating force can be continuously maintained without interrupting the operation. In a vibrating force control device for an eccentric weight type vibrator of a system that varies, a drive shaft and a control shaft are provided in parallel with the eccentric weight shaft, and a rotary drive device is connected to the drive shaft. And the drive gear is attached The drive gear is meshed with a synchronous transmission gear that interlocks the fixed eccentric weight, and the control shaft is a concentric two-piece with an outer tube fitted to the inner shaft so as to be relatively rotatable. A heavy shaft, wherein an inner shaft of the concentric double shaft is connected to a turning shaft of the reversible turning mechanism, and an outer tube is connected to a housing of the reversible turning mechanism, respectively, and And a drive synchronous gear mounted on one of the outer tube and the synchronous transmission gear for interlocking the fixed eccentric weights with each other, and on the other of the inner shaft and the outer tube. The mounted control synchronous gear is meshed with the synchronous transmission gear that links the movable eccentric weights to each other, and by rotating the rotation axis of the reversible rotation mechanism with respect to the housing, The inner shaft and the outer tube are relatively rotated, and the phase difference between the fixed eccentric weight and the movable eccentric weight is However,
A vibrating force control device for an eccentric weight type vibrator, wherein a vibrating force is controlled to increase and decrease. 5. A fixed eccentric weight and a movable eccentric weight, which are rotatably and relatively rotatably supported on each of the plurality of eccentric weight shafts, are respectively mounted on synchronous transmission gears. The number of the eccentric weight shafts is at least four, and for each eccentric weight shaft, a synchronous transmission gear mounted on the fixed eccentric weight and a synchronous transmission gear mounted on the movable eccentric weight are provided. Forming a “synchronous transmission gear pair”, wherein the center lines of the four eccentric weight shafts are arranged along the ridge line of a virtual square prism, and constitute four sets of synchronous transmission gear pairs. Among the eight synchronous transmission gears, four synchronous transmission gears mounted on the fixed eccentric weight and four synchronous transmission gears mounted on the movable eccentric weight form a square ring gear train. The method according to any one of claims 1 to 4, characterized in that it is formed. The described oscillating force control device of the eccentric weight type exciter. 6. A fixed eccentric weight and a movable eccentric weight which are rotatably and relatively rotatably supported for each of the plurality of eccentric weight shafts are respectively mounted on synchronous transmission gears. The number of the eccentric weight shafts is at least four, and for each eccentric weight shaft, a synchronous transmission gear mounted on the fixed eccentric weight and a synchronous transmission gear mounted on the movable eccentric weight are provided. Forming a “synchronous transmission gear pair”, wherein the center lines of the four eccentric weight shafts are arranged along the ridge line of the virtual square prism, and each of the four eccentric weight shafts Of the eight synchronous transmission gears constituting the four pairs of synchronous transmission gears supported, four synchronous transmission gears mounted on the fixed eccentric weight, and mounted on the movable eccentric weight. Four synchronous transmission gears form a modified U-shaped gear train The synchronous transmission gears at both ends of the gear train are not meshed with each other, and the driving synchronous gear and the control synchronous gear are the synchronous transmission gears constituting the modified U-shaped gear train. The vibrating force control device for an eccentric weight type vibrator according to any one of claims 1 to 4, characterized in that the vibrating force control device is engaged with any one of them. 7. The reversible rotation mechanism has a structure in which a rotation axis can be turned forward and reverse with respect to a housing by hydraulic pressure or electromagnetic force, and the housing is in phase with a fixed eccentric weight. Rotate, the rotating shaft is connected so as to rotate in phase with the movable eccentric weight, or the rotating shaft rotates in phase with the fixed eccentric weight, and the housing is in phase with the movable eccentric weight. The vibrating force control device for an eccentric weight type vibrator according to any one of claims 1 to 6, wherein the vibrating force control device is connected to rotate. 8. Each of a plurality of eccentric weight shafts,
The fixed eccentric weight and the movable eccentric weight are rotatably and rotatably supported, and the plurality of fixed eccentric weights are interlocked by a synchronous transmission gear so as to rotate in the same phase. The plurality of movable eccentric weights are interlocked so as to rotate in phase with each other by a synchronous transmission gear, and the plurality of fixed eccentric weights and the movable eccentric weights are fixed while rotating about the eccentric weight axis. By changing the phase difference between the eccentric weight and the movable eccentric weight and changing the total eccentric moment of the fixed eccentric weight and the movable eccentric weight, the vibrating force can be continuously maintained without interrupting the operation. In a vibrating force control method for an eccentric weight type vibrator of a variable type, a drive shaft and a control shaft are provided in parallel with the eccentric weight shaft, and the drive / control shaft is relatively movable. From the inner shaft and outer tube One of the inner shaft and the outer tube of the concentric double shaft is the same as the synchronous transmission gear with respect to the synchronous transmission gear that links the fixed eccentric weights to each other. Or connected via a similar synchronous transmission gear, and driven to rotate by a rotary drive device, and the other of the inner shaft or the outer tube of the concentric double shaft is linked with the movable eccentric weights. The synchronous transmission gear is connected to the synchronous transmission gear through a synchronous transmission gear similar or similar to the synchronous transmission gear, and the inner shaft and the outer tube of the concentric double tube are rotated by a rotation shaft of a reversible rotation mechanism. And the casing, respectively, whereby the inner shaft and the outer tube are relatively rotated by the reversible rotating mechanism, and the phase difference between the fixed eccentric weight and the movable eccentric weight is adjusted. Eccentric weight-type vibrator characterized in that Vibratory force control method. 9. Each of a plurality of eccentric weight spindles,
The fixed eccentric weight and the movable eccentric weight are rotatably and rotatably supported, and the plurality of fixed eccentric weights are interlocked by a synchronous transmission gear so as to rotate in the same phase. The plurality of movable eccentric weights are interlocked with each other so as to rotate in the same phase by a synchronous transmission gear, and the plurality of fixed eccentric weights and the movable eccentric weight are rotated around the eccentric weight axis while being fixed. By changing the phase difference between the eccentric weight and the movable eccentric weight and changing the total eccentric moment of the fixed eccentric weight and the movable eccentric weight, the vibrating force can be continuously maintained without interrupting the operation. In the vibrating force control method of the eccentric weight type vibration generator of the changing type, the concentric double shaft in which the inner shaft and the outer tube are fitted so as to be relatively rotatable in parallel with the eccentric weight shaft. Two of them are arranged, and one of the two concentric double shafts is An inner shaft is constituted by an inner shaft driving concentric double shaft with a rotary driving device connected to the inner shaft, and a driving synchronous gear mounted on the inner shaft is used as a synchronous transmission gear for interlocking the fixed eccentric weights with each other. As well as
A control synchronous gear mounted on the outer tube is meshed with a synchronous transmission gear that links the movable eccentric weights with each other, and the other of the two concentric double shafts has a reversible inner shaft. A rotating shaft of the rotating mechanism, the outer tube of which is connected to the casing of the reversible rotating mechanism, is constituted by an outer tube controlling concentric double shaft, respectively,
The drive synchronous gear mounted on the inner shaft is meshed with the drive synchronous gear of the inner shaft drive concentric double shaft, and the control synchronous gear mounted on the outer tube is connected to the inner shaft drive concentric double shaft. And the rotational force generated by the driving of the rotary drive device is transmitted to two systems. One of the transmission systems rotates the fixed eccentric weight via the driving synchronous gear, and the other transmits the rotational force. The system is configured so that the movable eccentric weight is rotated sequentially through the driving synchronous gear, the reversible rotating mechanism, and the controlling synchronous gear, and the rotating shaft of the reversible rotating mechanism is rotated with respect to the housing. The synchronous gear for control is rotated relative to the synchronous gear for drive by doing so that the phase difference between the fixed eccentric weight and the movable eccentric weight is adjusted to increase or decrease. A method for controlling the vibrating force of an eccentric weight type vibrator. 10. A fixed eccentric weight and a movable eccentric weight are rotatably and relatively rotatably supported by a plurality of eccentric weight shafts, respectively. The plurality of movable eccentric weights are interlocked so as to rotate in the same phase by the synchronous transmission gear while being linked by the synchronous transmission gear so as to rotate in the same phase, and the plurality of fixed eccentric weights and the movable eccentric are Changing the phase difference between the fixed eccentric weight and the movable eccentric weight while rotating the weight around the eccentric weight axis, thereby changing the total eccentric moment of the fixed eccentric weight and the movable eccentric weight. According to the method of controlling the vibrating force of the eccentric weight type vibrator in which the vibrating force is changed while continuing without interrupting the operation, the inner shaft and the outer pipe are parallel to the eccentric weight shaft. Concentric two fitted rotatably Along with disposing two heavy shafts, one of the two concentric double shafts, the inner shaft thereof as a rotating shaft of the reversible rotating mechanism, and the outer tube thereof as a housing of the reversible rotating mechanism, Each connected outer tube control is constituted by a concentric double shaft, and a drive synchronous gear mounted on the inner shaft meshes with a synchronous transmission gear that interlocks the fixed eccentric weights with each other. The mounted control transmission gear is meshed with the synchronous transmission gear that links the movable eccentric weights to each other, and the other of the two concentric double shafts has its inner shaft connected to a rotary drive device. It is constituted by the inner shaft drive concentric double shaft, and the drive synchronous gear mounted on the inner shaft is meshed with the drive synchronous transmission gear of the outer tube control concentric double shaft, and mounted on the outer tube. The synchronous gear for control is engaged with the synchronous gear for control of the outer tube control concentric double shaft. The rotational force generated by the driving of the rotary drive device is transmitted to two systems, one of which transmits a fixed eccentric weight via a driving synchronous gear, and the other transmission system transmits a driving synchronous gear and a reversible rotating gear. A movable mechanism and a movable synchronous eccentric weight are sequentially rotated via a control synchronous gear, and the control synchronous gear is rotated by rotating a rotating shaft of the reversible rotating mechanism with respect to the housing. An eccentric weight type vibrator, which is rotated relative to the driving synchronous gear so as to adjust the phase difference between the fixed eccentric weight and the movable eccentric weight. Exciting force control method of the machine. 11. A fixed eccentric weight and a movable eccentric weight are rotatably and relatively rotatably supported by each of the plurality of eccentric weight shafts, and the plurality of fixed eccentric weights are mutually connected. The plurality of movable eccentric weights are interlocked so as to rotate in the same phase by the synchronous transmission gear while being linked by the synchronous transmission gear to rotate in the same phase, and the plurality of fixed eccentric weights and the movable eccentric are Changing the phase difference between the fixed eccentric weight and the movable eccentric weight while rotating the weight around the eccentric weight axis, thereby changing the total eccentric moment of the fixed eccentric weight and the movable eccentric weight. According to the method of controlling the vibrating force of the eccentric weight type vibrator of the type in which the vibrating force is changed while continuing without interrupting the operation, the drive shaft and the control shaft are parallel to the eccentric weight shaft. And the above drive shaft A rotary drive device is connected and a drive gear is mounted, the drive gear meshes with a synchronous transmission gear that links the fixed eccentric weight, and the control shaft has an outer tube with respect to an inner shaft. A concentric double shaft that is fitted so as to be relatively rotatable, wherein the inner shaft of the concentric double shaft is the rotation shaft of the reversible rotation mechanism, and the outer tube is also the housing of the reversible rotation mechanism, Connected to each other, and a drive synchronous gear mounted on one of the inner shaft and the outer tube is meshed with a synchronous transmission gear that is interlocking the fixed eccentric weights, and A control synchronous gear mounted on one of the outer tube and the other is meshed with a synchronous transmission gear that links the movable eccentric weights to each other, and a rotating shaft of the reversible rotating mechanism is fixed to a housing. By rotating, the inner shaft and the outer tube are relatively rotated, and fixed eccentricity The phase difference between the mass and the movable eccentric weight is changed,
An oscillating force control method for an eccentric weight exciter, wherein the oscillating force is operated so as to increase or decrease the oscillating force.