JP2004263486A - Vibrator mechanism and vibrating roller - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vibrator mechanism which is of a "horizontal vibration-normal vibration" switchable type, and solves a problem of collision of a movable eccentric weight, and to provide a vibrating roller. <P>SOLUTION: The vibrator mechanism is formed of a central exciting shaft 20 arranged at the center of a roll 1 and having the movable eccentric weight 25 mounted thereon; eccentric exciting shafts 22, 23 arranged across the central exciting shaft 20 and having respective fixed eccentric weights 27A, 27B mounted thereon; a drive transfer mechanism for transferring drive force to the eccentric exciting shafts 22, 23 such that the eccentric exciting shafts 22, 23 are always in the same phase; a first clutch C1 engaged with the central exciting shaft 20 only when the shaft is rotated in one direction, to thereby rotate the eccentric exciting shafts 22, 23; and a second clutch C2 disengaged from the central exciting shaft 20 when the shaft is rotated in the one direction and engaged with the same when it is rotated in the other direction, to thereby rotate the movable eccentric weight 25 together with the central exciting shaft 20. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a vibration mechanism and a vibration roller.
[0002]
[Prior art]
Vibration rollers are mainly used for compaction of embankments at highway and dam construction sites, and for compaction of asphalt pavement on roads. The compaction wheels (rolls) vibrate the ground while vibrating. Therefore, there is an effect that the ground is compacted at high density. As a vibration mechanism built in a roll, a structure of rotating a vibration generating shaft to which an eccentric weight is attached is generally used.
[0003]
Examples of the vibration mode of the roll include a mode in which the roll is vibrated over its entire circumference in the radial direction (this is referred to as “normal vibration” in the present specification) and a mode in which the roll is vibrated along its circumferential direction ( This is referred to as “horizontal vibration” in this specification), and FIGS. 10a and 10b of Patent Document 1 disclose a mechanism for switching between “normal vibration” and “horizontal vibration”. . In addition, in Patent Document 1, FIG. 5 describes an operation explanatory diagram relating to “horizontal vibration”.
[0004]
In FIGS. 10a and b of Patent Document 1, a pair of vibrating shafts are disposed at positions 180 degrees opposite to each other with respect to the center of the roll, and the eccentric weight of one vibrating shaft is located at It is configured as a movable eccentric weight that is rotatably mounted. If the relative phase angle of the movable eccentric weight with respect to the vibration axis when the vibration axis is rotated in one direction is 0 degrees, the movable eccentric weight is raised when the vibration axis is rotated in the other direction. The movable eccentric weight is configured to have a relative phase angle of 180 degrees with respect to the oscillation axis, and the movable eccentric weight is positioned by a stopper fixed to the oscillation axis (the stop body 32 shown in FIG. 33).
[0005]
FIG. 5 shows another conventional example regarding a vibration mechanism of a "horizontal vibration-normal vibration" switching type. In this example, a pair of exciter shafts 51 (51A, 51B) that rotate synchronously in the same direction are arranged with a center of the roll interposed in an exciter case (not shown) in the roll. Is shown. The exciter case is configured to rotate integrally with the roll when the vehicle travels. 5 (a) and (b-1) to (b-4) show the case where the exciter shaft 51A is located above and the exciter shaft 51B is located below the roll rotation position. .
[0006]
A pair of fixed eccentric weights 52A are fixedly mounted on the excitation shaft 51A, and a movable eccentric weight 53A is fitted between the fixed eccentric weights 52A so as to be rotatable with respect to the excitation shaft 51A. Have been. A stopper 54 is provided between the two fixed eccentric weights 52A to abut on the movable eccentric weight 53A to restrict the rotational displacement of the movable eccentric weight 53A. Here, regarding the eccentric moment mr of each eccentric weight (m is the eccentric mass, r is the distance between the axis of the vibrating shaft and the center of gravity of the eccentric weight), the eccentric moment m by the movable eccentric weight 53A ₂ r ₂ Is the total eccentric moment m of the pair of fixed eccentric weights 52A. ₁ r ₁ Shall be greater.
[0007]
A pair of fixed eccentric weights 52B are fixedly mounted on the excitation shaft 51B, and a movable eccentric weight 53B is externally fitted between the fixed eccentric weights 52B so as to be rotatable with respect to the excitation shaft 51B. Have been. Further, a stopper 54 is fixedly provided between the fixed eccentric weights 52B to abut on the movable eccentric weight 53B and regulate the rotational displacement of the movable eccentric weight 53B. Here, the total eccentric moment m of the pair of fixed eccentric weights 52B ₃ r ₃ Is the eccentric moment m of the movable eccentric weight 53A. ₂ r ₂ Eccentric moment m due to the movable eccentric weight 53B ₄ r ₄ Is the total eccentric moment m of the pair of fixed eccentric weights 52A. ₁ r ₁ It is the same size as.
[0008]
FIG. 5A shows a case of normal vibration. When the vibrating shafts 51A and 51B rotate in the S direction, each stopper 54 rotates while pressing one end side of each of the movable eccentric weights 53A and 53B. In this state, the positions of the centers of gravity of the fixed eccentric weights 52A and 52B and the movable eccentric weights 53A and 53B are reversed with respect to the vibrating shafts 51A and 51B. On the vibrating shaft 51A side, the total eccentric moment m of the pair of fixed eccentric weights 52A ₁ r ₁ Eccentric moment m of movable eccentric weight 53A ₂ r ₂ Is set large, the eccentric moment of the entire eccentric weight is “m ₂ r ₂ -M ₁ r ₁ And the direction in which the vibration force acts is in the direction of the right arrow in the figure. On the vibrating shaft 51B side, the total eccentric moment m of the pair of fixed eccentric weights 52B ₃ r ₃ Is the eccentric moment m of the movable eccentric weight 53B. ₄ r ₄ Eccentric moment of the entire eccentric weight is “m ₃ r ₃ -M ₄ r ₄ In this case as well, the direction in which the vibration force acts is the right arrow direction. That is, the value of each eccentric moment “m” ₂ r ₂ -M ₁ r ₁ ”,“ M ₃ r ₃ -M ₄ r ₄ Have the same value, the same vibration force is generated on the vibrating shafts 51A and 51B in the same direction.
[0009]
Of course, the vibrating shafts 51A and 51B rotate in the same direction synchronously, so that the relationship between the directions in which the respective vibrating forces act is maintained. When acting on the vibrating shaft 51B, the vibrating force on the side of the vibrating shaft 51B also acts in the left direction. Works. As described above, the vibrating forces of the vibrating shafts 51A and 51B are combined in the same direction on the roll, and always act as the same value of vibrating force.
[0010]
Next, the case of horizontal vibration will be described with reference to FIGS. 5 (b-1) to 5 (b-4). When the vibrating shafts 51A and 51B rotate in the R direction, each stopper 54 rotates while pressing the other end side of each movable eccentric weight 53, and (b-1) → (b-2) → (b- The state of 3) → (b-4) is repeated. In each of these states, the fixed eccentric weight 52A and the movable eccentric weight 53A rotate while overlapping as shown in (b-1) to (b-4), and the eccentricity of the entire eccentric weight around the excitation shaft 51A. The moment is “m ₁ r ₁ + M ₂ r ₂ ". Similarly, the fixed eccentric weight 52B and the movable eccentric weight 53B also rotate in an overlapping state, and the eccentric moment of the entire eccentric weight around the excitation shaft 51B is “m”. ₃ r ₃ + M ₄ r ₄ ". Of course, the value of each eccentric moment "m ₁ r ₁ + M ₂ r ₂ ”,“ M ₃ r ₃ + M ₄ r ₄ Is the same value.
[0011]
At the position (b-1), a force directed toward the roll center is applied to the excitation shaft 51A, and the excitation shaft 51B located at a position 180 degrees opposite to the roll center has the same size toward the roll center. As the force is applied, the oscillating forces cancel each other out. At the position (b-2), a force directed clockwise in the circumferential direction of the roll is applied to the excitation shaft 51A, and a force directed clockwise in the circumferential direction of the roll is also applied to the excitation shaft 51B. As a result, a horizontal force in a direction from right to left is applied to the ground contact portion on the ground on which the roll is placed. At the position (b-3), a force is applied to the excitation shaft 51A in a direction away from the center of the roll, and a force is also applied to the excitation shaft 51B in the opposite direction, so that the vibration forces cancel each other. At the position (b-4), a force directed in the circumferential direction of the roll in the counterclockwise direction is applied to the excitation shaft 51A, and a force directed in the circumferential direction of the roll in the roll direction is also applied to the excitation shaft 51B. As a result, a horizontal force in a direction from left to right is applied to the ground contact portion on the ground on which the roll is placed. As described above, the state of (b-2) and the state of (b-4) are alternately repeated, so that a horizontal vibration force is applied to the contact portion of the roll.
[0012]
[Patent Document 1]
Japanese Patent Publication No. 4-6805 (pages 8 and 9; Fig. 10)
[0013]
[Problems to be solved by the invention]
The vibration mechanism having the conventional structure shown in FIG. 5 has the following problems. FIG. 6 is an explanatory side view showing a case where the roll is rotated in a state where no vibration is applied (that is, a state where the excitation shafts 51A and 51B are stopped). When the roll rotates counterclockwise in FIG. The pair of vibrating shafts 51A and 51B also revolve counterclockwise around the center of the roll. Focusing on the movement of the movable eccentric weight 53A on the one of the vibrating shaft 51A side, the movable eccentric weight 53A pushed up on one end side by the stopper 54 in the state of FIG. Rotate counterclockwise. Then, the movable eccentric weight 53A is located below the vibrating shaft 51A as in the state of (c), but rotates upward as it is due to the inertial force acting thereon, as shown in (d). The other end collides with the stopper 54. Next, the movable eccentric weight 53A rotates clockwise by the reaction that collides with the stopper 54, while the stopper 54 revolves counterclockwise with the rotation of the roll, so that the movable eccentric weight 53A and the stopper 54 As shown in (e), the collision occurs again at one end side of the movable eccentric weight 53A.
[0014]
Therefore, even during traveling without vibration, for example, during forward traveling of the vehicle, the two collisions between the movable eccentric weight 53A and the stopper 54 shown in FIG. 6 are constantly repeated during traveling, as described above. There have been problems such as the generation of unpleasant noise due to the generation of a collision sound and the generation of abrasion powder. This problem is also applicable to the structure disclosed in Patent Document 1, in which the movable eccentric weight (the eccentric mass 30a shown in FIG. 10 of Patent Document 1) has a stopper (shown in FIG. 10 of Patent Document 1). A similar problem can occur when colliding with the stops 32, 33).
[0015]
Further, the vibration mechanism having the conventional structure has the following problem in addition to the above-mentioned problem at the time of no vibration. When the exciter shaft rotates, the stopper fixed to the exciter shaft abuts (collides) with the movable eccentric weight, but the exciter shaft is normally designed to rotate several thousand times per minute. The rising speed is also high, and therefore, the impact force when the stopper collides with the movable eccentric weight tends to be large. Therefore, a loud collision sound is generated, resulting in unpleasant noise, and abrasion powder is likely to be generated at the time of the collision, so that the abrasion powder may enter a bearing that supports the vibrating shaft. Further, since a large load is applied to the fixing portion of the stopper, for example, it is necessary to take a thorough check of the quality of the fixing strength of the stopper with respect to the vibrating shaft.
[0016]
Further, when the drive source for rotating the vibrating shaft is, for example, a hydraulic motor, immediately after stopping the hydraulic motor, the rotating speed of the vibrating shaft, that is, the stopper is rapidly increased by the braking force based on the stoppage of the flow of the pressure oil. However, since the movable eccentric weight rotates while maintaining the high rotational speed as it is due to the inertial force, the impact force at the time of collision between the movable eccentric weight and the stopper is the same as at the time of the rotation start described above. growing. Particularly, the vibration roller frequently performs ON / OFF operation of the vibration depending on the construction condition, and as described above, a large impact force is generated between the movable eccentric weight and the stopper every time the vibration starts and stops. It is a problem.
[0017]
In order to solve these problems, it is conceivable to provide an impact interference member made of rubber or the like on the movable eccentric weight or the stopper. However, a material having elasticity such as rubber is apt to have insufficient strength and easily peel off. There is a problem, especially in the case of a vibrating roller, since the vibrating mechanism is housed in a room filled with oil, there is a problem that the rubber material is easily deteriorated by this oil, and it is not suitable for long-term use .
[0018]
Further, according to the structure disclosed in Patent Literature 1, there is also a problem of the roll amplitude described below. In each of the normal vibration mode and the horizontal vibration mode, an appropriate roll amplitude is required. FIG. 7 is an explanatory view showing a vibration system of the roll at the time of normal vibration in a roll provided with a biaxial vibration mechanism. Eccentric weights having the same shape are attached to each of the two axes, and the two eccentric weights in this roll are rotated in the same direction and in the same phase by a power transmission mechanism (not shown). The vibration force acts so that the direction of the vibration changes sequentially from the center of the roll to the radial direction. The vibration force is denoted by F, focusing on the component of the vibration force perpendicular to the road surface. Then, the vibration force F becomes “F = 2 · mrω ² The road surface is modeled as a spring with a spring constant of K, acting perpendicular to the ground contact surface of the roll. m is the eccentric mass, r is the distance between the axis of the excitation shaft and the center of gravity of the eccentric weight, and ω is the angular velocity of the excitation shaft. Mass M ₀ The equation of motion when the vibration force F is acting periodically on the roll of the roller is as follows: ignoring the spring constant K as a soft road surface, "2 · mω ² sinωt = M ₀ ・ D ² y / dt ² ". y is the vertical displacement. When this equation of motion is transformed into y, “y = (− 2 · mr / M ₀ ) Sinωt ”, whereby the upper and lower amplitudes a of the roll during normal vibration a ₁ Is represented by the following equation.
a ₁ = 2 · mr (during normal vibration) / M ₀ … Equation (1)
In Equation (1), for convenience, the eccentric moment mr is denoted by “mr (during normal vibration)”.
[0019]
FIG. 8 is an explanatory view showing a vibration system of the roll at the time of horizontal vibration in a roll provided with a biaxial vibration mechanism. An anti-vibration rubber interposed between the frame of the vibration roller (not shown) and the roll acts on the axis O ′ of the roll in the horizontal direction. ₁ It is modeled as a spring having the following spring constant: As for the road surface, it acts horizontally on the contact surface of the roll, K ₂ It is modeled as a spring having the following spring constant: K ₁ , K ₂ The moment of inertia I about the axis O 'of the roll supported by the spring having the following spring constant is given by T (= p · 2 · mrω ² sinωt, where p is the distance between the axis O ′ of the roll and the axis of the vibrating axis), the equation of motion when a periodic torque is acting is represented by a spring constant K ₁ , K ₂ Neglecting that both springs are soft, "p · 2 · mrω ² sinωt = Id ² θ / dt ² ". Assuming that the radius of the roll is R, the horizontal displacement y of the roll in the horizontal direction of the ground contact surface is represented by “y = Rθ” by regarding θ as a minute angular displacement. ² sinωt = (I / R) · (d ² y / dt ² )), And when this equation of motion is transformed into y, it becomes "y =-((R.p.2.mr) / I) sin.omega.t". Thereby, the horizontal amplitude a of the roll at the time of horizontal vibration ₂ Is represented by the following equation.
a ₂ = (R · 2 · p · mr (at horizontal vibration)) / I Equation (2)
In equation (2), the eccentric moment mr is denoted by “mr (for horizontal vibration)” for convenience.
[0020]
The mass M included in the formula (1) or (2) ₀ , The radius R of the roll, and the moment of inertia I about the axis O ′ of the roll are almost determined when the dimensions of the roll are determined. ₁ Is set to a desired value, the condition is that the value of the eccentric moment mr (during normal vibration) has a degree of freedom in setting. Horizontal vibration amplitude a ₂ Is set to a desired value, the distance p between the axis O ′ of the roll and the axis of the vibrating shaft and the eccentric moment mr (at the time of horizontal vibration) are set to one of two factors. The degree of freedom is a condition. However, since the vibrating shaft is disposed inside the roll, the range of the set value of the distance p is structurally limited, and therefore, the amplitude a of the horizontal vibration ₂ Also depends on the value of the eccentric moment mr (at the time of horizontal vibration).
[0021]
Thus, the amplitude a of the normal vibration ₁ And amplitude of horizontal vibration a ₂ Is set to an appropriate value, it is desirable that the eccentric moment mr (during normal vibration) and the eccentric moment mr (during horizontal vibration) take different values. However, according to the technique disclosed in Patent Document 1, although the phase angle of the eccentric weight changes with the forward / reverse rotation of the excitation shaft, the eccentric moment mr (during normal vibration) and the eccentric moment mr (during horizontal vibration) ) Have the same value, so that it is difficult to obtain amplitudes suitable for normal vibration and horizontal vibration, respectively.
[0022]
The present invention has been created in order to solve the above-described problems, and solves the conventional problem of collision and amplitude relating to a movable eccentric weight, and a new “horizontal vibration-normal vibration” switching. It is an object of the present invention to provide a vibrating mechanism and a vibrating roller.
[0023]
[Means for Solving the Problems]
SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention provides a central oscillating shaft disposed at the center of a roll, and a movable eccentric weight attached to the central oscillating shaft and rotatable relative to the central oscillating shaft. A plurality of eccentric vibrating shafts disposed on both sides of the central oscillating shaft, a fixed eccentric weight attached to each of the eccentric vibrating shafts, and the phases of the eccentric vibrating shafts are always A drive transmission mechanism for transmitting a driving force to each of the deflection excitation shafts so as to have the same relationship, and only when the central excitation shaft rotates in one direction, the central deflection shaft side and the deflection A first connecting means for connecting the oscillating shaft side and synchronously rotating each of the eccentric oscillating shafts, and only when the central oscillating shaft rotates in the other direction, the movable eccentric weight and the A second connecting means for integrally connecting the central excitation shaft with the central excitation shaft. By the fixed eccentric weight is vibrated along the roll in its circumferential direction, to constitute a vibration mechanism for vibrating the entire periphery of the roll in the radial direction by the movable eccentric weights when rotating in the other direction.
[0024]
Further, the first connecting means is interposed between the central excitation shaft and each of the eccentric excitation shafts, and is connected only when the central excitation shaft rotates in the one direction. A first clutch for rotating each of the eccentric excitation shafts, wherein the second connecting means is interposed between the central oscillating shaft and the movable eccentric weight; And a second clutch that is connected only when the motor rotates.
[0025]
Further, the first clutch includes an inner ring portion and an outer ring portion with a clutch mechanism interposed therebetween, the inner ring portion being fixed to the central vibrating shaft, a drive gear being fixed to the outer ring portion, and The transmission mechanism has a configuration in which a driven gear attached to each of the deflection excitation shafts meshes with the drive gear.
[0026]
Further, the first clutch and the second clutch are configured to be connected or disconnected from a connected state at a rotational speed higher than a rotational speed at which resonance occurs when the excitation shaft starts and stops.
[0027]
Further, the vibration mechanism is a vibration roller provided inside a roll.
[0028]
BEST MODE FOR CARRYING OUT THE INVENTION
FIG. 1 is a cross-sectional explanatory view of a roll incorporating a vibration mechanism according to the present invention, FIG. 2 is a cross-sectional view taken along the line AA in FIG. 1, (a) shows the case of “horizontal vibration”, and (b) shows “ The case of "normal vibration" is shown.
[0029]
The roll 1 is rotatably supported by, for example, a support plate 2 fixed to a machine frame of a vibration roller (not shown). The roll 1 has a hollow cylindrical shape, and a disk-shaped first head plate 3 and a second head plate 4 having through holes 3a, 4a formed in the center thereof are fixed on the inner peripheral surface of the roll 1 at a distance from each other. . Between the first end plate 3 and the second end plate 4, a hollow cylindrical exciter case 5 is coaxial with the roll 1 so as to be sandwiched over the respective peripheral portions of the through-holes 3a and 4a. It is fixed. Axle shafts 6 and axle shafts 7 are attached to the first end plate 3 and the second end plate 4 so as to close the through holes 3a and the through holes 4a, respectively, and the bolts 8 penetrate the flange portions 6a and 7a respectively. The holes 3a and the through holes 4a are fastened and fixed to the peripheral edges.
[0030]
One axle shaft 6 is pivotally supported by a bearing member 9 via bearings 10 and 10. The bearing member 9 is a member connected to the support plate 2 via the mounting plate 12 and the vibration isolating rubber 11. The other axle shaft 7 is fixed to an output portion 14 a of the traveling motor 14 via a mounting plate 13. The fixed portion 14b of the traveling motor 14 is fixed to the support plate 2 via a mounting plate 15 and an anti-vibration rubber 16. As described above, when the output portion 14 a of the traveling motor 14 rotates, the roll 1 rotates while the axle shaft 6 is configured to be rotatable with respect to the bearing member 9. In addition, the traveling motor 14 is usually composed of a hydraulic motor or the like.
[0031]
A vibration motor 18 is fixed to the bearing member 9 via a vibration motor mounting member 17, and a center vibration shaft 20 is connected to a rotation shaft thereof via a coupling 19. The vibration motor 18 is also usually composed of a hydraulic motor or the like, and is configured to be capable of normal and reverse rotation. The center vibrating shaft 20 is horizontally extended so as to be concentric with the roll 1 by pivotally supporting both ends of the center vibrating shaft 20 via the axle shaft 6 and the axle shaft 7.
[0032]
Displacement excitation shafts 22 and 23 are disposed at positions 180 degrees opposite to each other with respect to the central excitation shaft 20, that is, with respect to the axis of the roll 1. Each of the eccentric excitation shafts 22 and 23 is horizontally extended in the exciter case 5 by each end of each being pivotally supported by the axle shafts 6 and 7 via bearings 24.
[0033]
A movable eccentric weight 25 that is rotatable relative to the central excitation shaft 20 is attached to the central excitation shaft 20. The figure shows a case where the movable eccentric weight 25 is attached via the bearings 26, 26. Fixed eccentric weights 27A and 27B are fixed to the eccentric excitation shafts 22 and 23, respectively. The fixed eccentric weights 27A and 27B are eccentric weights having the same shape as each other. Therefore, the eccentric moment mr of the fixed eccentric weight 27A around the eccentric excitation shaft 22 and the eccentricity of the fixed eccentric weight 27B around the eccentric excitation shaft 23. The moment mr is the same value. Here, m is the eccentric mass, and r is the distance between the axis of the vibrating shaft and the center of gravity of the eccentric weight.
[0034]
As shown in FIG. 2, the positional relationship between the fixed eccentric weight 27A and the fixed eccentric weight 27B is such that the eccentric mass side of the fixed eccentric weight 27A is When located on the right side of the center line 28 connecting the axes of the excitation shaft 22 and the excitation shaft 23, the eccentric mass side of the fixed eccentric weight 27B is located on the left side of the center line 28. .
[0035]
The vibration mechanism according to the present invention connects the center excitation shaft 20 to the eccentric excitation shafts 22 and 23 only when the central oscillating shaft 20 rotates in one direction. First connecting means for enabling synchronous rotation of the central oscillating shaft 22 and the movable eccentric weight 25 and the central oscillating shaft 20 only when the central oscillating shaft 20 rotates in the other direction. 2 connection means. In the present embodiment, as described below, a mode is used in which a clutch is used as each of the first connecting means and the second connecting means.
[0036]
A connection is made between the central excitation shaft 20 and each of the offset excitation shafts 22 and 23 only when the central excitation shaft 20 rotates in one direction. A first clutch (hereinafter, referred to as a first clutch) C1 for rotating the swing shafts 22, 23 is provided. In the present embodiment, the first clutch C1 is constituted by a one-way clutch including an inner ring portion Cb and an outer ring portion Cc with a clutch mechanism Ca interposed therebetween. As an example of the structure of the clutch mechanism Ca, as shown in FIG. 3, a structure in which a large number of sprags S are arranged in a circumferential shape is exemplified. According to this structure, when the first clutch C1 rotates in one direction and its rotation speed increases, the sprags S are erected by centrifugal force and pressed against the outer ring portion Cc, and the outer ring portion Cc is moved by the frictional force to the inner ring portion Cc. It rotates integrally with the portion Cb.
[0037]
The above-described first clutch C1 has its inner ring portion Cb externally fitted and fixed to a portion of the central vibrating shaft 20 near the axle shaft 6, and a driving gear 29 made of a spur gear is fastened to the outer ring portion Cc by bolts 30. Fixed. The boss portion of the drive gear 29 is supported by the central vibration shaft 20 via a bearing 31. Driven gears 32 and 33 are fixedly mounted on the eccentric excitation shafts 22 and 23 near each axle shaft 6, and the driven gears 32 and 33 mesh with the drive gear 29. The driven gears 32 and 33 have the same diameter and the same number of teeth. As can be seen from the above, in the present embodiment, the drive transmission mechanism for transmitting the driving force to each of the deflection excitation shafts 22 and 23 is such that the phases of the respective deflection excitation shafts 22 and 23 always have the same relationship. , A driving gear 29 and driven gears 32 and 33. When the central vibration shaft 20 rotates in one direction and the first clutch C1 is connected, the eccentric vibration shafts 22 and 23 rotate in the same direction via the drive gear 29 and the driven gears 32 and 33 in synchronization with each other. I do.
[0038]
The center vibration shaft 20 is disconnected when the center vibration shaft 20 rotates in the one direction, and is connected when the center vibration shaft 20 rotates in the other direction, and the movable eccentric weight 25 is integrated with the center vibration shaft 20. A second clutch (hereinafter, referred to as a second clutch) C2 for rotating the motor is mounted. In forming the second clutch C2, the same members as those of the first clutch C1 can be used, and the second clutch C2 can be achieved by mounting the first clutch C1 on the center vibration shaft 20 with its front and back reversed. In this case, the inner ring portion Cb is externally fitted to and fixed to the center excitation shaft 20, and the movable eccentric weight 25 is fastened and fixed to the outer ring portion Cc by bolts 34.
[0039]
Hereinafter, the operation of the present invention will be described with reference to FIG. 1 or FIG. First, the case where the roll 1 is horizontally vibrated will be described. When the vibration motor 18 is operated to rotate the center excitation shaft 20 in one direction (clockwise in FIG. 2), the first clutch C1 is connected, and the drive gear 29 fixed to the outer ring portion Cc rotates. As a result, the deflecting vibrating shafts 22 and 23 rotate counterclockwise through the driven gears 32 and 33 meshing with the driving gear 29 as shown in FIG. At this time, since the second clutch C2 is in the disengaged state, the center oscillating shaft 20 is rotating, but the movable eccentric weight 25 fixed to the outer ring portion Cc of the second clutch C2 does not rotate. That is, when the central excitation shaft 20 rotates in one direction, the roll 1 is vibrated only by the fixed eccentric weights 27A and 27B of the eccentric excitation shafts 22 and 23.
[0040]
FIGS. 4A to 4D are side explanatory views showing a state of horizontal vibration. The state shown in FIG. 2A is the same state as FIG. 4B. First, in the position (a), a force directed toward the axis of the roll 1 is applied to the offset excitation shaft 22, and the offset excitation shaft 23 is located 180 ° opposite to the axis of the roll 1. Also, since the same magnitude of force directed toward the axis of the roll 1 is applied, the vibration forces cancel each other. In the position (b), a force directed clockwise in the circumferential direction of the roll 1 is applied to the deflection excitation shaft 22, and a force directed clockwise in the circumferential direction of the roll 1 is also applied to the deflection excitation shaft 23. . As a result, a horizontal force in a direction from right to left is applied to the ground contact portion on the ground on which the roll 1 is placed.
[0041]
In the position (c), a force is applied to the eccentric excitation shaft 22 in a direction away from the axis of the roll 1, and a force is also applied to the eccentric excitation shaft 23 in the opposite direction. Be countered. In the position (d), a force directed in a counterclockwise direction in the circumferential direction of the roll 1 is applied to the eccentric excitation shaft 22, and a force directed in the circumferential direction of the roll 1 is also applied to the eccentric excitation shaft 23. . As a result, a horizontal force in a direction from left to right is applied to the ground contact portion on the ground on which the roll 1 is placed. As described above, the state (b) and the state (d) are alternately repeated, so that the roll 1 vibrates along its circumferential direction, and a horizontal vibration force is applied to the ground portion of the roll 1.
[0042]
Next, in the case of normal vibration, when the rotation of the vibration motor 18 is reversed to rotate the center vibration shaft 20 in the other direction (counterclockwise in FIG. 2), the second clutch C2 is connected. As a result, the movable eccentric weight 25 fixed to the outer ring portion Cc rotates integrally with the central vibration shaft 20. At this time, since the first clutch C1 is in the disengaged state, the deflection excitation shafts 22 and 23 do not rotate. That is, when the center vibration shaft 20 rotates in the other direction, the roll 1 is vibrated only by the movable eccentric weight 25 attached to the center vibration shaft 20. Due to the movable eccentric weight 25, vibration is generated in the roll 1 over the entire circumference in the radial direction.
[0043]
As described above, the central excitation shaft 20 to which the movable eccentric weight 25 is attached, and the eccentric excitation shafts 22 and 23 which are disposed with the central oscillating shaft 20 interposed therebetween and to which the fixed eccentric weights 27A and 27B are fixed, respectively. And a drive transmission mechanism for transmitting a driving force to the eccentric excitation shafts 22 and 23 so that the phases of the eccentric excitation shafts 22 and 23 always have the same relationship, and the central oscillating shaft 20 is moved in one direction. The first connecting means which is connected only when rotated to allow the eccentric excitation shafts 22 and 23 to be synchronously rotatable, and becomes disconnected when the central excitation shaft 20 rotates in the one direction, and And a second connecting means for connecting the movable eccentric weight 25 integrally with the central oscillating shaft 20 only when the central oscillating shaft 20 rotates in the one direction, and rotating the central oscillating shaft 20 in the one direction. When the roll is horizontally vibrated by the fixed eccentric weights 27A and 27B, the roll is rotated in the other direction. If the configuration is such that the movable eccentric weight 25 normally vibrates when the movable eccentric weight 25 is used, the problem that the conventional "normal vibration-horizontal vibration" switching type vibration mechanism has, that is, when the movable eccentric weight collides with the stopper, The problem of the collision noise of the above, the problem of the influence on the bearings (reference numerals 21 and 24) due to the generation of wear powder at the time of the collision, the problem of the fixing strength of the stopper, and the like are solved.
[0044]
In particular, the problem of collision between the movable eccentric weight and the stopper caused by the oscillation shaft revolving around the center of the roll as shown in FIG. , A low-noise traveling vehicle.
[0045]
The eccentric moment mr in the above equation (1) (during normal vibration) is determined only by the eccentric moment mr of the movable eccentric weight 25 around the central vibration axis 20, and the eccentric moment mr in the above equation (2) (horizontal vibration). ) Is determined only by each eccentric moment mr of the fixed eccentric weights 27A and 27B around the eccentric excitation shafts 22 and 23, so that the distance between the movable eccentric weight 25 and the fixed eccentric weights 27A and 27B is determined. By adjusting the values of the eccentric mass m and the distance r, the eccentric moment mr (during normal vibration) and the eccentric moment mr (during horizontal vibration) can be made different from each other. Therefore, the amplitude a of the roll 1 during normal vibration ₁ And amplitude a during horizontal vibration ₂ Can be set to desired values.
[0046]
In addition, by configuring the first clutch C1 and the second clutch C2 as described above as the first connection means and the second connection means, a simple structure is realized, and easy and economical vibration is achieved. Mechanism.
[0047]
Further, the first clutch C1 is a clutch having an inner ring portion Cb and an outer ring portion Cc with a clutch mechanism Ca interposed therebetween, and the inner ring portion Cb is fixed to the central vibration shaft 20 and a driving gear 29 is attached to the outer ring portion Cc. If the driven transmission gears are fixed and the driven gears 32 and 33 attached to the eccentric excitation shafts 22 and 23 are meshed with the driving gear 29, the eccentric excitation shaft 20 and the central excitation shaft 20 can be formed in a simple structure. The synchronous rotation between the displacement excitation shafts 22 and 23 and the synchronous rotation between the displacement excitation shafts 22 and 23 can be compatible.
[0048]
Here, as described in Japanese Patent Application Laid-Open No. H10-165893, a resonance point exists in a rising process of the rotation speed at the time of starting the excitation shaft and a falling process of the rotation speed at the time of stopping the excitation shaft. It is known that when a vibration force is generated at a point, there is a risk of affecting the rolling compaction road surface.
[0049]
Therefore, at the time of startup, the first clutch C1 or the second clutch C2 is connected when the central vibration shaft 20 reaches a rotational speed higher than the rotational speed at which the resonance point is generated. A configuration in which the first clutch C1 or the second clutch C2 is disengaged at a stage before the oscillating shaft 20 decreases to a rotation speed at which the resonance point is generated, that is, at a rotation speed higher than the rotation speed at which the resonance point is generated. This makes it possible to cause the roll 1 to vibrate horizontally or normally without affecting the road surface due to the resonance point. Such a configuration can be easily achieved by connecting the clutch mechanism Ca at a predetermined rotational speed equal to or higher than the resonance point, or by appropriately selecting a clutch having a specification that disconnects from the connected state.
[0050]
Further, by using the vibration mechanism described above as a vibration roller provided in the roll 1, a compact vehicle of low noise type can be obtained. In addition, the problem of the fixing strength of the stopper and the like due to the collision is solved, and the vehicle has excellent long-term quality maintenance performance. In addition, whether to use the normal vibration and the horizontal vibration is normally appropriately determined depending on the material of the ground to be constructed.
[0051]
The preferred embodiments of the present invention have been described above. In the above-described embodiment, the eccentric excitation axis is provided as two axes. However, for example, when viewed from the side surface of the roll, the eccentric excitation axis is further configured to be orthogonal to the two eccentric excitation axes. It is also possible to adopt a configuration in which two eccentric excitation axes are arranged, that is, a configuration in which four eccentric excitation axes are arranged at intervals of 90 degrees around the central excitation axis 20. Further, depending on the design, the fixed eccentric weights 27A and 27B may not be individually provided, but may be formed integrally with the eccentric vibrating shafts 22 and 23, for example. However, in the present invention, the eccentric component formed integrally with the eccentric excitation shaft is also included as the fixed eccentric weight. In addition, the present invention can be appropriately changed in design without departing from the gist of the shape, layout, number, and the like of each component.
[0052]
【The invention's effect】
According to the present invention, a collision sound is not generated as in the past when traveling without vibration, for example, when the vehicle is being forwarded, or when the excitation shaft is started and stopped, so that it can be used when traveling, in a residential area, or the like. In the case of compaction work in the above, a vibration mechanism and a vibration roller having excellent environmental properties are obtained. In addition, the amplitude of the roll suitable for normal vibration and the amplitude of the roll suitable for horizontal vibration can be set, respectively, and the quality related to the compaction of the ground is improved.
[Brief description of the drawings]
FIG. 1 is an explanatory plan sectional view of a roll incorporating a vibration mechanism according to the present invention.
FIGS. 2A and 2B are cross-sectional views taken along line AA in FIG. 1, wherein FIG. 2A shows a case of horizontal vibration, and FIG. 2B shows a case of normal vibration.
FIG. 3 is a structural diagram of a first clutch.
FIG. 4 is an explanatory side view showing an operation of horizontal vibration.
FIGS. 5A and 5B are side views illustrating the operation of a vibration mechanism capable of switching between “normal vibration” and “horizontal vibration” in a two-axis system. FIG. (B-4) shows the case of horizontal vibration.
FIG. 6 is an explanatory diagram of an action when a vibrating shaft revolves around the center of a roll in a state where rotation is stopped in a vibration mechanism capable of switching between “normal vibration” and “horizontal vibration” in a two-axis system. .
FIG. 7 is a principle diagram for obtaining an amplitude in normal vibration.
FIG. 8 is a principle diagram for obtaining an amplitude in horizontal vibration.
[Explanation of symbols]
1 roll
20 Central vibration axis
22, 23 Deflection excitation shaft
25 movable eccentric weight
27A, 27B Fixed eccentric weight
29 Drive gear
32, 33 driven gear
C1 First clutch
C2 Second clutch
Ca clutch mechanism
Cb inner ring
Cc Outer ring

Claims (5)

A central vibration axis disposed in the center of the roll,
A movable eccentric weight attached to the central vibration axis and rotatable relative to the central vibration axis,
A plurality of eccentric excitation shafts disposed on both sides of the central excitation shaft,
A fixed eccentric weight attached to each of the eccentric excitation shafts,
A drive transmission mechanism for transmitting a driving force to each of the deflection excitation shafts so that the phases of the respective deflection excitation shafts always have the same relationship;
Only when the central excitation shaft rotates in one direction, connect the central excitation shaft side and the eccentric excitation shaft side, and rotate each of the eccentric excitation shafts synchronously. Connection means;
Second connection means for integrally connecting the movable eccentric weight and the central excitation shaft only when the central excitation shaft rotates in the other direction,
With
When the center vibration axis is rotated in the one direction, the rolls are vibrated along the circumferential direction by the fixed eccentric weights, and the rolls are rotated by the movable eccentric weights when rotated in the other direction. A vibration mechanism characterized in that it is configured to vibrate over the entire circumference in the radial direction. The first connecting means is interposed between the central excitation shaft and each of the eccentric excitation shafts, and is connected only when the central oscillating shaft rotates in the one direction. A first clutch for rotating the position excitation shaft,
The second connecting means may include a second clutch interposed between the central excitation shaft and the movable eccentric weight and connected only when the central excitation shaft rotates in the other direction. The vibration mechanism according to claim 1, wherein: The first clutch includes an inner ring portion and an outer ring portion with the clutch mechanism portion interposed therebetween,
While the inner ring portion is fixed to the central excitation shaft, a drive gear is fixed to the outer ring portion,
3. The vibration mechanism according to claim 2, wherein the drive transmission mechanism has a configuration in which a driven gear attached to each of the deflection excitation shafts meshes with the drive gear. 4. 3. The first clutch and the second clutch are configured to be connected or disconnected from a connected state at a rotational speed higher than a rotational speed at which resonance occurs at the time of starting and stopping the excitation shaft. 4. Or the vibration mechanism according to claim 3. A vibrating roller comprising the vibrating mechanism according to claim 1 provided inside a roll.

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