JPH04330972A - Vibration generator - Google Patents

Abstract

PURPOSE:To arbitrarily and continuously change vibromotive force by forcedly and relatively moving a phase regulation shaft in the axial direction and inserting a pin erected to this phase regulation shaft into the spiral long holes of phase regulation gears and relatively rotating these gears in the reverse directions, and rotating the gears integrally with the phase regulation shaft in a state wherein the phases thereof are shifted. CONSTITUTION:A phase regulation shaft 80 is forcedly and relatively moved in the axial direction. Thereby, since a pin 82 erected to this phase regulation shaft 80 is inserted into the spiral long holes of phase regulation gears 35, 36, these gears 35, 36 are relatively rotated in the reverse directions with each other and rotated integrally with the phase regulation shaft 80 in a state wherein the phases are shifted. Therefore, the phases of both the rotary shafts 21, 22 to which rotation of the gears 35, 36 is transferred and stationary eccentric weights 51A, 52A are shifted. Further, movable transmission gears 32, 34 are relatively rotated for the rotary shafts 21, 22. The phases of movable eccentric weights 51B, 52B are shifted in the direction reverse to the stationary eccentric weights 51A, 52A. Thereby the horizontal component force of the respective eccentric weights is canceled but the vertical component force is changed in accordance with the phase difference.

Description

[Detailed description of the invention]

0001

[Industrial Application Field] The present invention relates to a vibration generator applied to vibrating pile drivers, various shakers, sieving devices, etc. It relates to something that can be changed arbitrarily and steplessly.

0002

[Prior Art] A vibration generator that utilizes centrifugal force generated by rotating an eccentric weight has a vibration generating device that uses a pair of even-numbered rotating shafts to which eccentric weights are attached, which are parallel to each other in a casing member. At the same time, by attaching a transmission gear to each rotating shaft and meshing adjacent gears, and rotating one group of rotating shafts and the other group of rotating shafts in opposite directions, the eccentricity attached to each rotating shaft can be reduced. In general, a device that cancels the horizontal component of the centrifugal force generated in the weight and adds the vertical component of the centrifugal force, and uses this vertical component to apply an excitation force in the vertical direction to the casing member, for example, is well-suited. Are known.

In such a vibration generator, by supporting the casing member via a spring or a damper, the entire vibration generator is caused to vibrate at a frequency corresponding to the rotational speed of the rotating shaft. Therefore, by supporting a pile such as a steel sheet pile on the casing member through a chuck or the like and activating the vibration generator, pile driving and pile pulling operations can be performed. By incorporating it into a device, stirring and sifting operations can be performed.

0004

[Problems to be Solved by the Invention] In the conventional vibration generator as described above, since an eccentric weight is fixed to the rotating shaft, it is not easy to arbitrarily change the excitation force or amplitude during operation. . However, in such a vibration generator, the driving force required to rotate the stationary eccentric mass at the start of operation is significantly larger than that after the eccentric mass reaches the rated rotational speed. If the driving force required for the eccentric weight to reach the rated rotational speed can be reduced, the drive source such as the motor can be downsized, and the efficiency of energy use such as power consumption can be significantly improved. can. Therefore, there is a need for a measure that can easily reduce the driving force required for rotation at the beginning of rotation of the rotating shaft.

[0005] Also, for example, in a vibration generator applied to a vibrating pile driver, in order to improve the workability of driving piles and pulling out piles, it is necessary to measures to easily change the excitation force or amplitude,
There is also a need for measures to prevent resonance phenomena that occur during startup and braking.

[0006] In order to meet the above-mentioned demands, several vibration generators with variable excitation force or amplitude are currently being considered, but all of them have a complicated structure, a large number of parts, and a significant increase in cost. . In view of these points, the present invention provides a vibration generator that can arbitrarily and steplessly change the excitation force or amplitude even during operation, and that has a simple, rational, and easy-to-manufacture structure. With the goal.

[0007]

[Means for Solving the Problems] In order to achieve the above-mentioned object, a vibration generator according to the present invention basically includes a first fixed transmission gear and a first fixed eccentric, which is pivotally supported by a casing member. A first rotary shaft on which a weight is fitted and fixed on the outside, and a first movable transmission gear and a first movable eccentric weight coupled to the gear are fitted on the outside so as to be relatively rotatable, and the casing member. A second fixed transmission gear and a second fixed eccentric weight that are supported in parallel with the first rotating shaft and mesh with the first fixed transmission gear are externally fitted and fixed, and the first movable a second movable transmission gear that meshes with the transmission gear; a second rotating shaft on which a second movable eccentric weight coupled to the gear is fitted so as to be relatively rotatable; and the first and second rotating shafts. at least one of the phase adjustment shafts is disposed parallel to the phase adjustment shaft so as to be rotatable and movable in the axial direction; A pair of phase adjustment gears, one of which meshes with either of the first and second movable transmission gears, the other of which meshes with either of the first and second movable transmission gears; A pin protruding in the radial direction is provided on the phase adjustment shaft, and an extension boss portion is provided on at least one of the pair of phase adjustment gears, and the extension boss portion is provided on at least one of the pair of phase adjustment gears. A feature is that the boss portion is formed with a spiral elongated hole into which the pin is inserted.

As one aspect of the present invention, a pair of phase adjustment gears is provided with a small diameter extension boss portion and a large diameter extension boss portion, one of which is inserted into the other, and the pin is inserted into each of these extension boss portions. It is also possible to form spiral elongated holes with opposite phases.

[0009]

[Operation] In the vibration generator according to the present invention having the above-described configuration, when the phase adjustment shaft is forcibly moved relatively in the axial direction by the driving means, the pin provided upright on the phase adjustment shaft changes the phase. By being fitted into the spiral elongated hole provided in the adjustment gear, the pair of phase adjustment gears rotate relative to each other in opposite directions according to the moving distance of the phase adjustment shaft.
They rotate together with the phase adjustment shaft with their phases advanced or delayed by equal angles.

When the phase of the pair of phase adjustment gears changes in this way, the rotation of one of the pair of phase adjustment gears is transmitted to the first and second rotation shafts and the first and second rotation shafts attached thereto. The phase of the fixed eccentric weight also changes by the same angle, and the first and second movable transmission gears to which the rotation of the other of the pair of phase adjustment gears is transmitted are rotated relative to the first and second rotating shafts. The phases of the first and second movable eccentric masses connected to the first and second movable transmission gears rotate relative to each other, and the phases of the first and second movable eccentric masses are opposite to the first and second fixed eccentric masses at the same angle. It changes gradually. As a result, the horizontal component force generated on each eccentric weight is always canceled out, while the total value of the vertical component force generated on each eccentric weight is the relative rotation angle of the pair of phase adjustment gears with respect to the phase adjustment shaft. As a result, the excitation force or amplitude applied to the casing member via the first and second rotating shafts is changed.

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. 1 and 2 are a perspective view and a developed view showing the main parts of an embodiment of the vibration generator according to the present invention, and FIG. 6 shows an example in which the vibration generator of the embodiment shown in FIGS. 1 and 2 is applied. FIG. 2 is a front view showing an example of a vibrating pile driver.

In FIG. 6, the vibratory pile driver 1 includes a hanger 5 provided with a hook 2 on which a hook 2 of a lifting means such as a crane is hooked, and four guides hanging from the hanger 5. A shock absorber 7 having a rod 6 and a pair of upper and lower coil springs 8 and 9 compressed therein, an electric motor 14 as a drive source supported by the hanger 5 via the shock absorber 7, a casing member 20, The vibration generator 10 of this embodiment includes an excitation force generator disposed inside the casing member 20, a belt 17 for power transmission, pulleys 18, 25, etc., and a vibration generator 10 provided below the vibration generator 10. It also includes a chuck 12 for holding piles such as steel sheet piles. This vibratory pile driver 1 is conventionally known except for a vibratory force generating section which will be described later, and can use any means such as not only an electric motor but also a hydraulic motor as a drive source, and a shock absorber is also shown in the figure. Any suitable material other than the above may be used.

As shown in detail in FIGS. 1 and 2, the vibration force generating section provided in the casing member 20 has a first section to which the rotational driving force from the electric motor 14 is transmitted via a pulley 25. a rotating shaft 21; a second rotating shaft 22 disposed substantially right beside and parallel to the first rotating shaft 21;
A phase adjustment shaft 80 is provided below the first and second rotation shafts 21 and 22, parallel to them and rotatably arranged. In addition, although the phase adjustment shaft 80 is shown as being located below the first and second rotation shafts 21 and 22 in this embodiment, the phase adjustment shaft 80 is located below the first and second rotation shafts 21 and 22. It will be clear that the position is not limited to being below 22, as long as it is parallel to and rotatably arranged.

As shown in FIG. 2, the first rotating shaft 21 has both ends connected to the side walls 20a, 20 of the casing member 20.
b via bearings 26 and 27, and this first
The first fixed transmission gear 31 is externally fitted onto the rotating shaft 21 and fixed by a key 43, and the divided first
Fixed eccentric weights 51Aa and 51Ab (51Aa and 51A
51A) is externally fitted and fixed near the side walls 20a and 20b of the casing member 20 by spline connection, and rotates integrally with the first movable transmission gear 32 and a connecting pin 37 thereto. A first movable eccentric weight 51B is fitted onto the outside via bearings 45 and 53 so as to be relatively rotatable.

The second rotating shaft 22 is supported by the side walls 20a, 20b of the casing member 20 via bearings 28, 29, and the second rotating shaft 22 is provided with a first fixed transmission gear 31. The second fixed transmission gear 33 that meshes with is fitted onto the outside and fixed by the key 44, and the divided second fixed eccentric weights 52Aa and 52Ab (52Aa and 52Ab are collectively referred to as 52A). A second movable transmission gear 34 is externally fitted and fixed near the side walls 20a and 20b of the casing member 20 by spline connection, and is coupled to a second movable transmission gear 34 and a connecting pin 38 so as to be able to rotate integrally therewith. Eccentric weights 52B are fitted onto the outside via bearings 46 and 54, respectively, so that they can rotate relative to each other.

It should be noted that the first and second rotating shafts 21, 22 and the fixed eccentric weights 51A, 52A are fixed by fixing means, or the first
, the means for fixing the second movable transmission gears 32, 34 and the first and second movable eccentric weights 51B, 52B are not limited to spline coupling and coupling using connecting pins, as shown here. It will be clear that any means may be used as long as it functions as a fixing means.

Furthermore, one end side of the phase adjustment shaft 80 is connected to the tip of a piston rod 65 of a hydraulic cylinder 50, which will be described later, through a bearing 69 in a rotatable state and in a state in which relative movement in the axial direction is prevented. ing. Further, the other end side is connected to the side wall 20b of the casing member via the bearing 42.
is rotatably supported. As shown in detail in FIG. 3, the phase adjustment shaft 80 has an insertion hole 81 that penetrates in the radial direction near the center thereof, and a pin 82 projects from both ends of the insertion hole 81 by a predetermined length. It is press-fitted in this position.

A double-acting hydraulic cylinder 50 with an automatic locking device is attached to a wall portion 20c attached to the casing member 20 as a driving means for moving the phase adjustment shaft 80 in the axial direction. ing. hydraulic cylinder 5
0 has supply and discharge ports 66 and 68 for supplying and discharging hydraulic oil from an externally arranged hydraulic unit, and is adapted to move its piston rod 65 forward and backward according to the amount of hydraulic oil supplied and discharged. In order to control the amount of movement of the piston rod 65, a position detector, such as a differential transformer type, is provided, although not shown.

The phase adjustment shaft 80 has a first phase adjustment gear 35 that meshes with the second fixed transmission gear 33 and a second phase adjustment gear 36 that meshes with the second movable transmission gear 34. It is fitted externally so that movement in the axial direction is prevented. The first phase adjustment gear 35 is rotatable relative to the phase adjustment shaft 80.
5 is provided with a large-diameter extension boss part 84, and a pair of spiral elongated holes 86 are formed in the large-diameter extension boss part 84 so as to face each other in the same direction with a phase difference of 180 degrees. Further, the second phase adjustment gear 36 is provided with a small diameter extension boss part 85 inserted into the large diameter extension boss part 84, and the small diameter extension boss part 85 has a pair of spiral elongated holes 86 having opposite phases. The spiral elongated holes 87 are formed facing each other in the same direction with a phase difference of 180°. These spiral elongated holes 86 and 87 have pins 82 that are press-fitted into the insertion holes 81 formed in the phase adjustment shaft 80.
Both ends of are inserted. A sleeve-shaped rotating ring 88 is loosely fitted to both ends of the pin 82 to reduce the sliding resistance between the pin and the spiral elongated holes 86 and 87, and a washer 89 is inserted to prevent the pin from coming off.

[0020] Furthermore, the above-mentioned first and second fixed eccentric weights 51A, 52A and first and second movable eccentric weights 51B
, 52B are approximately fan-shaped with a center angle of 180°, and the first and second fixed eccentric weights 51A,
One thickness of 52A is the first and second movable eccentric weights 51
B, 52B, and the first and second fixed eccentric weights 51A, 52A and the first and second movable eccentric weights 51B, 52B (including pins 37, 38, etc.) are: Their weight and shape are determined so that their eccentric moments are the same, and they are positioned so that they are balanced in the left-right direction.

However, the first and second fixed eccentric weights 51A, 52A and the first and second movable eccentric weights 51
The shape, thickness, etc. of B and 52B are not limited to those described above, and their weight, shape, or position may be determined so that the eccentric moments are the same and are balanced in the left and right directions. One thing is clear.

In the vibration generator 10 of this embodiment having the above-described configuration, the rotational driving force of the motor 14 is transmitted via the belt 17 from the first rotation shaft 21 to the first fixed transmission gear 31 to the second transmission gear. The signal is transmitted to the phase adjustment shaft 80 via the fixed transmission gear 33 → first phase adjustment gear 35 → pin 82 in order, and the first rotation shaft 21, second rotation shaft 22, and phase adjustment shaft 80 are synchronized. At the same time, the phase adjustment shaft 80
The rotation is sequentially transmitted to → pin 82 → second phase adjustment gear 36 → second movable transmission gear 34 → first movable transmission gear 32.

Here, when the phase adjustment shaft 80 is forcibly moved in the axial direction by the cylinder 50, the pin 82 installed on the phase adjustment shaft 80 moves between the first phase adjustment gear 35 and the second phase adjustment gear 35. Since the first phase adjustment gear 35 and the second phase adjustment gear 36 are fitted into the spiral elongated holes 86 and 87 of opposite phase provided in the gear 36, respectively, the first phase adjustment gear 35 and the second phase adjustment gear 36 are aligned in the circumferential direction of the spiral elongated holes 86 and 87. The component forces cause the phase adjustment shafts 80 to rotate in opposite directions according to the moving distance, and their phases are advanced or delayed by equal angles, and in this state, the first phase adjustment gear 35 and the second phase adjustment The gear 36 rotates together with the phase adjustment shaft 23.

[0024] In this way, the first phase adjustment gear 3
5 and the second phase adjustment gear 36 occurs,
The first and second movable transmission gears 32 and 34 are
rotates relative to the rotation axes 21 and 22 of the
a rotating shaft, first and second fixed eccentric weights 51A, 52A attached thereto, and first and second movable eccentric weights 5 coupled to the first and second movable transmission gears 32, 34.
1B and 52B, and thereby the excitation force or amplitude applied to the casing member 20 via the first and second rotating shafts 21 and 22 is changed.

In this case, the first and second rotating shafts 21, 2
Each eccentric weight 51A, 52A, 51B attached to 2
, 52B are canceled out, and the vertical component of the centrifugal force is added to the casing member 20. This vertical component gives the casing member 20 an excitation force in the vertical direction. Now, as shown in FIG. 7A, the positions of the first and second fixed eccentric weights 51A, 52A and the first and second movable eccentric weights 51B, 52B, which are arranged on the same axis, are The phase difference is 180° (for example, the pin 82 is the spiral long hole 86,
87), the excitation forces obtained therefrom cancel each other out and become 0, as shown by curves a and b in FIG. 8A. On the other hand, the phase adjustment shaft 80 is moved by one stroke from the above state (for example, the pin 82 is moved through the spiral elongated holes 86, 8
7), the first phase adjustment gear 35 rotates clockwise, and the second phase adjustment gear 36 rotates 90 degrees counterclockwise, as shown in FIG. 7C. The phase difference between the first and second fixed eccentric weights 51A, 52A and the first and second movable eccentric weights 51B, 52B, which are arranged on the same axis, is 0, and the curve c in FIG. 8C
As shown, an excitation force twice the amplitude or the excitation force obtained with only one eccentric weight can be obtained.

Note that FIG. 8B shows a case where the phase difference is 90°, and as in the case of FIGS. 8A and 8C, the amount as the sum of the excitation force or amplitudes a and b, that is, the curve in FIG. 8B. The amount of excitation force or amplitude indicated by c is obtained.

Therefore, for example, when starting up the vibration generator 10, the first and second fixed eccentric weights 51A, 5
If the phase difference between the coaxial weights 2A and the first and second movable eccentric weights 51B and 52B is set to 180° as shown in FIG. 7A, a balanced flywheel can be activated. If the phase adjustment shaft 80 is moved so that the phase difference between them gradually decreases from 180° to 0 during the period after startup until the electric motor 14 reaches the rated rotational speed, a large It becomes possible to smoothly rotate each eccentric weight without the need for additional driving force, and therefore, the electric motor 14 can sufficiently fulfill its role even if it is small, resulting in energy savings. .

In the above example, the first phase adjustment gear 35 and the second phase adjustment gear 36 each have spiral elongated holes 86 and 8 for rotating them in opposite directions by about 90 degrees.
7, but the spiral elongated hole may be formed only on one side. In that case, the shape of the spiral elongated hole should be changed so that only one side can be rotated relative to the phase adjustment axis from 0° to 180°. Just choose. Further, although the hydraulic cylinder 50 is used as a driving means for the phase adjustment shaft 80, a driving means composed of a motor, a worm gear, a thrust shaft, etc. may be used instead.

Furthermore, the first and second movable transmission gears 3
2, 34 and first and second movable eccentric weights 51B, 52B
may be integrally manufactured or combined, and it goes without saying that the arrangement of each eccentric weight and gear, as well as the arrangement of the first rotation shaft 21, second rotation shaft 22, and phase adjustment shaft 80, can be changed as appropriate. It is.

[0030]

As is clear from the above description, the vibration generator according to the present invention has the advantage that when the first adjustment shaft is forcibly moved relative to the second adjustment shaft in the axial direction by the driving means, When the phase adjustment shaft is forcibly moved relatively in the axial direction by the driving means, the pin installed upright on the phase adjustment shaft is inserted into the spiral elongated hole provided in the phase adjustment gear, so that the phase The pair of phase adjustment gears rotate relative to each other in opposite directions according to the moving distance of the adjustment shaft, and the phase of either the first and second fixed transmission gears or the first and second movable transmission gears accordingly changes. It is made to rotate integrally with the phase adjustment shaft while being advanced or delayed relative to the other. Therefore, when the phase of the pair of phase adjustment gears changes in this way, the rotation of one of the pair of phase adjustment gears is transmitted to the first and second fixed eccentric weights attached to the first and second rotating shafts. A phase difference is created between the weight and the first and second movable eccentric weights coupled to the first and second movable transmission gears to which the rotation of the other of the pair of phase adjustment gears is transmitted, so that each While the horizontal component forces generated on the eccentric weights are always canceled out, the total value of the vertical component forces generated on each eccentric weight is the sum of the vertical component forces generated on the first and second fixed eccentric weights and the first and second movable weights. The excitation force is changed according to the phase difference with the eccentric weight, and as a result, the excitation force applied to the casing member via the first and second rotating shafts is changed. It can be changed arbitrarily and steplessly, and
It has the advantage that the structure is extremely simple, rational, and easy to manufacture.

[Brief explanation of drawings]

FIG. 1 is a perspective view showing the main parts of an embodiment of a vibration generator according to the present invention.

FIG. 2 is a developed view showing the main parts of an embodiment of the vibration generator according to the present invention.

FIG. 3 is a detailed view of the main parts of the embodiment shown in FIGS. 1 and 2;

FIG. 4 is a diagram used to explain the operation of the embodiment shown in FIGS. 1 and 2;

FIG. 5 is a diagram used to explain the operation of the embodiment shown in FIGS. 1 and 2;

[Fig. 6] A front view showing an example of a vibrating pile driver to which the vibration generator of the embodiment shown in Figs. 1 and 2 is applied.

FIG. 7 is a diagram used to explain the operation of the embodiment shown in FIGS. 1 and 2;

FIG. 8 is a diagram used to explain the operation of the embodiment shown in FIGS. 1 and 2;

[Explanation of symbols]

10-Vibration generator 14─Motor 20─Casing member 21--first rotation axis 22-Second rotation axis 31, 33 - Fixed transmission gear 32, 34─Movable transmission gear 35, 36─Phase adjustment gear 51A, 52A - Fixed eccentric weight 51B, 52B─Movable eccentric weight 50-Hydraulic cylinder 80-Phase adjustment axis 82-pin 84, 85-Extension boss part 86,87-Spiral long hole

Claims (2)

[Claims] Claim 1: A first fixed transmission gear and a first fixed eccentric weight are pivotally supported on a casing member, and a first fixed transmission gear and a first fixed eccentric weight are fitted and fixed on the outside, and a first movable transmission gear and a first a first rotating shaft on which a movable eccentric weight is fitted so as to be relatively rotatable; and a second rotating shaft that is supported by the casing member in parallel with the first rotating shaft and meshes with the first fixed transmission gear. A fixed transmission gear and a second fixed eccentric weight are externally fitted and fixed, and a second movable transmission gear that meshes with the first movable transmission gear and a second movable eccentric weight coupled to the gear are provided. a second rotating shaft fitted externally so as to be relatively rotatable;
and a phase adjustment shaft arranged to be rotatable and movable in the axial direction parallel to the second rotation axis, and at least one of the shafts is fitted externally so as to be relatively rotatable with the phase adjustment shaft being prevented from moving in the axial direction. a pair of phase adjustment gears, one of which meshes with either of the first and second fixed transmission gears and the other meshes with either of the first and second movable transmission gears; and the phase adjustment shaft. a driving means for forcibly moving the phase adjustment gear in the axial direction, a pin protruding in the radial direction is provided on the phase adjustment shaft, and an extension boss portion is provided on at least one of the pair of phase adjustment gears. . A vibration generator characterized in that the extension boss portion is formed with a spiral elongated hole into which the pin is inserted. 2. A pair of phase adjustment gears each having a small-diameter extension boss portion and a large-diameter extension boss portion, one of which is inserted into the other, and a spiral with opposite phases in which the pin is inserted into each of these extension boss portions. The vibration generator according to claim 1, characterized in that a long hole is formed.