JPH089210Y2 - Plate compactor exciter structure - Google Patents

Description

[Detailed Description of the Invention] [Industrial field of application] The present invention relates to a vibrating body structure of a plate compactor used for compacting a road surface or the like in road construction, etc. The present invention relates to a vibrating body structure of a plate compactor that produces a function.

[Conventional technology]

Although various types of plate compactors are used, for example, the type shown in FIG. 4 is commonly used. The outline structure is a main body case in which a compression plate 31 that is in direct contact with a road surface, etc., and a vibrating body (not shown) that is connected to the compression plate 31 and that adds vibration and forward / backward movement force thereto are housed. 7, an engine 32 elastically mounted on the body case 7 side via an engine base 7a, and a steering handle 33 and the like. The rotation of the engine 32 is transmitted to the rotary shaft of the vibrating body, and the rotation of the eccentric weight attached to the rotary shaft gives vibration and forward / backward movement to the pressure plate 31, and the steering wheel 33 steers the entire body. While using it. FIG. 5 shows an example of the internal structure of the vibrator. That is,
The rotation of the drive shaft 6a connected to the engine 32 side of FIG. 4 via the pulley 9a is caused by rotation of the driven shaft 5a arranged in parallel with the gear 3
4,35 (consisting of the same number of teeth).
Two eccentric weights 37, 37, 36a, 36b are fixed to the drive shaft 6a and the driven shaft 5a, respectively. In addition, the driven shaft 5
The shifter 38 is fixed to the a-side gear 35, and the gear 35
Further, the shifter 38 is integrally fixed with claws 39, 40 capable of abuttingly engaging with the upper surfaces of the eccentric weights 36a, 36b.
Further, a shifter fork 41 slidably supported on the main body case 7a side is engaged with the shifter 38 to move the shifter 38,
The claws 39, 40 are adapted to be able to alternately contact the eccentric weights 36a, 36b. The drive shaft 6a and the driven shaft 5a are all housed in the main body case 7.

As shown in FIG. 5 and FIG. 6, the drive shaft 6a and the driven shaft 5 with the pawl 39 in contact with the upper surface of the eccentric weight 36a.
When a rotates, as shown in FIG. 7, centrifugal forces F ₁ and F ₂ are generated, and the resultant force F ₃ acts in the direction of the figure.
In addition, the eccentric weight also rotates to generate a centrifugal force of S ₁ which is equal to the resultant force F ₃ and is directed in the opposite direction. Therefore, total force F ₃ , total force S ₁
As described above, the compression plate 31 vibrates as described above, and
For example, reverse in the direction of S ₁ .

On the other hand, the shifter fork 41 in FIG. 5 is operated, and the gear 35 and the shifter 38 are moved so that the claw 40 is brought into abutting engagement with the eccentric weight 36b side (see FIG. 8). In this state, the driven shaft 5a rotates in the A direction as viewed from the arrow, and the claw 39 contacts the upper surface of the eccentric weight 35b only after rotating 180 ° from the state shown in the figure, so that the drive shaft 6a passes through the gears 35, 34. Comes to a position rotated by 180 °. That is, the relative phase positional relationship between the eccentric weights 36a, 36b and the eccentric weight 37 is as shown in FIG. When the drive shaft 6a and the driven shaft 5a rotate in this state, centrifugal forces F ₄ and F ₅ act as shown in FIG. 9, and the resultant force F ₆ acts in the direction of the figure. Further, the eccentric weight also rotates and generates a centrifugal force of S ₂ which is equal to the resultant force F ₆ and is directed in the opposite direction. Therefore, the compression plate 31 is
While vibrating due to F ₆ and S ₂ , it moves in the S ₂ direction, that is, the forward direction opposite to that in Fig. 7.

[Problems to be solved by the device]

In the case of the prior art plate compactor described above,
The eccentric weights 37, 37 on the side of the drive shaft 6a and the eccentric weights 36a, 36b on the side of the driven shaft 5a are formed so as to transmit the forward or backward moving force to the pressure plate 31 by changing the relative phase positions. And the steering of the entire aircraft is the steering wheel
It was done exclusively by 33.

On the other hand, since the total weight of the plate compactor is quite heavy, steering the entire machine body in a desired direction requires a lot of labor and requires a skillful operation. In addition, the aircraft may move in an unexpected direction due to an operation error or the like, which may be dangerous. Further, in the vibrator structure shown in FIG. 5, the claws 39 and 49 have eccentric weights 36.
Since it collides with a and 36b and receives a large impact force, the claws 39 and 40 suffer abnormal wear and the like, and the impact force causes rattling and slack in each part, causing abnormal vibration and noise. .

The present invention solves the above problems and the like, and the vibrating body itself has a steering function, so that the steering rig of the aircraft can be easily and smoothly performed without using a steering handle or the like, and stability is improved. (EN) Provided is a vibrating body structure of a plate compactor which can be improved and which does not generate an impact force even when the mutual phase positions of eccentric weights are converted, which improves the life of each part and prevents abnormal vibration or noise. The purpose is to

[Means for solving the problem]

In order to achieve the above-mentioned object, the present invention attaches eccentric weights to both rotary shafts of a drive shaft and a driven shaft arranged in parallel with the drive shaft, and vibrates the pressure plate by a centrifugal force generated by the rotation of both shafts. A vibrating body structure of a plate compactor for transmitting, wherein a plurality of eccentric weights arranged facing the both rotary shafts are arranged along an axis line, and a plurality of eccentric weights arranged on one of the both rotary shafts. Is rotatably supported about an axis orthogonal to the axis of the rotation axis, and eccentric weight rotating means for rotating the eccentric weight is attached to the plurality of eccentric weights rotatably supported. And a vibrating body structure of the plate compactor.

[Action]

A plurality of eccentric weights are arranged facing each other on the drive shaft of the vibrating body and the rotary shaft of the driven shaft arranged in parallel with the drive shaft. A plurality of eccentric weights attached to one of the rotation shafts are attached to be rotatable about an axis line orthogonal to the rotation axis line. When the eccentric weights are rotatably supported by the eccentric weight rotating mechanism so as to be rotatable about a plurality of eccentric weights, the relative phase positions of the eccentric weights are changed. The centrifugal force generated on the eccentric weight side is the resultant force in which the size and direction change from the lower rear to the upper front, and the other is the resultant force that changes the size and the direction from the lower front to the upper rear. The horizontal reaction force from is reversed and a turning moment is generated around the center point in the vibrating body. As a result, a swivel force is applied to the compression plate, and the airframe is swung in a desired direction. Of course, for forward and backward movements of the airframe, one and the other eccentric weights should be arranged at the same mutual phase position, and the relative phase position with the eccentric weight attached to the other rotary shaft should be related to the predetermined direction. Done by. Further, since the eccentric weight is formed so as to rotate about the axis line orthogonal to the rotation axis to change the mutual phase position, no impact force is generated at the time of phase conversion.

[Embodiment] An embodiment of the present invention will be described below with reference to the drawings.

1 is an axial sectional view showing the entire structure of an embodiment of the present invention, and FIG. 2 is a sectional view taken along the line II-II of FIG. FIG. 3 is a sectional view taken along line III-III in FIG. The drive shaft 6 is pivotally supported by bearings 8 and 9 on the main body case 7 connected to the tension plate 31, and a pulley 10 connected to the engine side (not shown) is fixed. A gear 11 is fixed to an intermediate portion of the drive shaft 6, and eccentric weights 3 and 4 are fixed by bolts 12 between the gear 11 and both ends of the drive shaft 6, respectively. On the other hand, drive shaft 6
Both ends of the driven shaft 5 arranged in parallel with each other are pivotally supported by the body case 7 via bearings 13 and 14, and a gear 15 having the same number of teeth meshing with the gear 11 is fixed to an intermediate portion thereof. An eccentric weight 1 and an eccentric weight 2 are arranged between the gear 15 and both ends of the driven shaft 5 so as to face the eccentric weights 3 and 4.
The eccentric weight 1 is composed of eccentric weights 1a and 1b, and both eccentric weights 1a and 1b are fixed to a support shaft 16a arranged along an axis orthogonal to the axis of the driven shaft 5 and fixed to the driven shaft 5. It In addition, the eccentric weights 1a and 1b have stopper surfaces 1
Stopper 18a formed with 7a and fixed to the driven shaft 5 side
The abutting engagement with the position of the rotary position is performed. The other eccentric weight 2 is also eccentric weight 2a, 2b
Like the eccentric weights 1a and 1b, the eccentric weights 1a and 1b are fixed to the support shaft 16b and fixed to the driven shaft 5. Further, similarly to the eccentric weight 1 side, the stopper surface 17b, the stopper 18b and the like are formed. Further, pinion gears 19 and 20 are formed at the centers of the support shafts 16a and 16b.

As shown in FIG. 3, the eccentric weight 1 is formed by combining a pair of eccentric weights 1a and 1b having the same shape. That is, flat surfaces 44 and 45 which are parallel to each other are formed in the intermediate portion of the driven shaft 5, and the through hole 46 is formed. The eccentric weights 1a and 1b are attached to the driven shaft 5 by inserting the boss portion 47 into the through hole 46 and bringing the stepped portion 48 into contact with the flat surfaces 44 and 45, and the supporting shaft penetrating the boss portion 47. 16
It is fixed to a by a nut 50 via a key or the like. Also,
A pinion gear 19 is formed at the center of the support shaft 16a.

Both the eccentric weights 1 and 2 are provided with eccentric weight rotating means 21 and 22 shown in FIG. 2, respectively.

According to FIG. 2, the eccentric weight rotating means 21 (22 is the same)
Will be explained.

A sleeve 24 is fixed to the end of the inner hole 23 of the driven shaft 5, and a moving member 25 is slidably supported in the sleeve 24. A rack 26 is fixed to the moving member 25. The rack 26 meshes with the pinion gear 19. The moving member 25 is rotatably supported by the piston rod 27 via a bearing 28. The piston rod 27 is a cylinder 29 fixed to the main body case 7.
Connected to the piston 30 inside. The inside of the cylinder 29 communicates with a drive source (not shown), and the piston 30 reciprocates.

 Next, the operation of this embodiment will be described in more detail.

As shown in FIGS. 1 and 3, the eccentric weights 3 and 4 on the drive shaft 6 are arranged in the same direction. on the other hand,
The eccentric weight 1 on the driven shaft 5 facing the eccentric weight 3 operates the eccentric weight rotating means 21 engaged with the eccentric weight 1, that is, from the drive source (not shown) to the cylinder 29.
From the position shown in FIG. 1, the working medium is introduced into the cylinder, the piston 30 is moved, and the pinion gear 19 is rotated through the rack 26.
It is installed at a position rotated by 180 °. Further, the eccentric weight 2 facing the eccentric weight 4 is left at the position shown in FIG. That is, it is assumed that the eccentric weight 1 and the eccentric weight 2 are arranged so that their relative phase positions are shifted from each other by 180 °, and that the eccentric weights 1 and 2 and the eccentric weights 3 and 4 are shifted from each other by 90 °. When the drive shaft 6 and the driven shaft 5 are rotated in this state, the resultant force of the centrifugal force between the eccentric weight 3 and the eccentric weight 1 and the resultant force of the centrifugal force between the eccentric weight 4 and the eccentric weight 2 are respectively from the lower rear side. The resultant force whose size and direction change to the upper front, the other becomes the resultant force whose size and direction change from the lower front to the upper rear, and the horizontal reaction force from the compression surface acts in the opposite direction, A rotation moment is generated around the center of the body case 7 (indicated by the zero point). As a result, a force that turns the entire body acts. On the contrary, eccentric weight rotation means
When the eccentric weight 1 is rotated in the opposite direction by 21 and the eccentric weight rotating means 22 is simultaneously operated to direct the eccentric weight 2 in the opposite direction, a rotational moment opposite to the above is generated, and the entire body is It can turn in the opposite direction. Since the turning angle is determined by the positional relationship of the relative phases of the eccentric weight 1 and the eccentric weight 2, it is possible to perform a desired steering operation by appropriately operating the eccentric weight rotating means 21, 22.

Eccentric weights 1, 2 when moving forward and backward only
Are directed in the same direction and the relative phase position with respect to the eccentric weights 3 and 4 is changed, so that the same operation as in the conventional method is performed.

Since the eccentric weight rotating means 21 and 22 are independently engaged with the eccentric weights 1 and 2, it is possible to give an arbitrary steering or forward / backward movement to the body.

On the other hand, in the case of the present embodiment, since the eccentric weights 1 and 2 are rotated along the axis line orthogonal to the axis line of the driven shaft 5,
There is no collision due to the claws 39, 40, etc. of the prior art, and no impact force acts on each part.

In this embodiment, two eccentric weights 1 and 2 are arranged on the driven shaft 5, but the invention is not limited to this.

[Effect of device]

 According to the present invention, the following effects can be obtained.

1) By arranging a plurality of eccentric weights, which are rotatably supported by eccentric weight rotating means so as to be rotatable about an axis orthogonal to each other, by changing the relative phase position, a rotational moment is generated in the vibrating body, and a swinging motion is generated in the machine body. Can be given.

2) By adopting an eccentric weight rotation mechanism that rotatably supports the eccentric weight around an axis orthogonal to the rotation axis, the relative phase position of each set of eccentric weights can be freely adjusted, and a desired turning movement can be achieved. Can be given to the aircraft. That is, a steering function can be provided without the need for a steering handle. Further, since the operation handle is unnecessary, a vibration-proof member around the handle is not required, and the cost can be reduced. Further, the operation is automatically performed, requires no skill, and is performed safely.

3) The eccentric weight turning mechanism operates by introducing a working medium into its cylinder, and can be operated remotely. Therefore, it is possible to perform remote control from the ground side even when working in the ditch.

4) The forward and backward movements of the machine body are smoothly and promptly performed by remote control by the eccentric weight rotating means.

5) Since the eccentric weight is structured so as to be pivotally supported about the axis line orthogonal to the rotation axis, no impact force is generated in each part, the life is improved, and rattling and looseness of each part are not generated. Therefore, no abnormal vibration or noise is generated.

[Brief description of drawings]

FIG. 1 is an axial sectional view showing the overall structure of an embodiment of the present invention,
2 is a sectional view taken along line II-II in FIG. 1, and FIG. 3 is II in FIG.
It is a sectional view taken along the line I-III. FIG. 4 is an external view for explaining the overall structure of the plate compactor, FIG. 5 is an axial sectional view showing an example of a conventional vibrating body structure, FIG. 6 is an explanatory view of an eccentric weight, and FIG. Fig. 6 is a vector diagram showing the force generated by the vibrator, Fig. 8 shows that one weight in Fig. 6 is 180
FIG. 9 is an explanatory diagram of the eccentric weight when the degree phase is shifted, and FIG. 9 is a vector diagram showing the force generated by the vibrator in FIG. 1,1a, 1b, 2,2a, 2b, 3,4 …… Eccentric weight, 5 …… Driven shaft, 6 …… Drive shaft, 7 …… Main body case, 8,9,13,14,28…
… Bearing, 10 …… Pulley, 11,15 …… Gear, 16a, 16b …… Support shaft, 17a, 17b …… Stopper surface, 18a, 18b …… Stopper,
19,20 …… Pinion gear, 21,22 …… Eccentric weight rotation means, 23 …… Inner hole, 24 …… Sleeve, 25 …… Movement member, 26
…… Rack, 27 …… Piston rod, 29 …… Cylinder,
30 …… Piston, 31 …… Pressure plate, 32 …… Engine, 33…
… Steering handle.

Claims (1)

[Scope of utility model registration request] 1. A vibrating body structure for a plate compactor, wherein eccentric weights are attached to both rotary shafts of a drive shaft and a driven shaft arranged in parallel with the drive shaft, and the centrifugal force generated by the rotation of both shafts transmits vibration to a pressure plate. There are a plurality of eccentric weights arranged opposite to the rotary shafts along the axis, and a plurality of eccentric weights arranged on either one of the rotary shafts are orthogonal to the rotary shaft axis. An eccentric weight rotating means for rotating the eccentric weights is attached to the plurality of eccentric weights rotatably supported around the eccentric weight rotating means. .