JP2017048895A - Torsional vibration reduction device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vibration reduction device which can improve vibration resistance by increasing centrifugal forces acting on rolling bodies arranged at a rotating body, and can improve the mountability of the rotating body.SOLUTION: In a torsional vibration reduction device in which a rotating body 5 which rotates by receiving torque is arranged at an output side of an engine, and a plurality of rolling bodies 11 which reciprocate in a circumferential direction of the rotating body 5 by a variation of the torque are arranged in the circumferential direction of the rotating body 5 with constant intervals, the torsional vibration reduction device comprises a speed increase mechanism 8 which is constituted of an annular drive gear 4 being an inner tooth gear, and a driven gear 7 which is smaller than the drive gear 4 in diameter, inserted into the drive gear 4, offset to a radial direction with respect to the drive gear 4, and engaged with the drive gear 4. The drive gear 4 is arranged on the same axial line of an input shaft 1 which is connected to the engine, and integrated to the input shaft 1, and the driven gear 7 is integrated to the rotating body 5 on the same axial line of the rotating body 5.SELECTED DRAWING: Figure 1

Description

  The present invention relates to an apparatus for reducing torsional vibration by reciprocating motion or pendulum motion of an inertial mass body.

  An example of this type of device is described in Patent Document 1. The apparatus includes a carrier disk that is a rotating body, rolling chambers are formed at regular intervals in the circumferential direction of the carrier disk, and a roller is disposed in each rolling chamber. The roller reciprocates when the torque of the carrier disk fluctuates, and the torsional vibration of the carrier disk is reduced by the reciprocation of the roller. This device is connected to the end of the crankshaft via a speed increasing mechanism, and the crankshaft, speed increasing mechanism, and torsional vibration reducing device are arranged coaxially. The speed increasing mechanism is constituted by a single pinion type planetary gear mechanism, in which a crankshaft is connected to a carrier, a carrier disk is connected to a sun gear, and a ring gear is fixed to a casing. That is, by increasing the rotation speed of the carrier disk relative to the rotation speed of the crankshaft, the centrifugal force acting on the roller is increased, thereby improving the vibration damping performance.

Japanese Patent Laid-Open No. 10-184799

  In a device that reduces vibrations by reciprocating motion of the rolling element, the rotational speed of the rotating body on which the rolling element is disposed is increased, or the diameter of the rotating body is increased to the distance from the rotation center axis to the center of the rolling element. By increasing the length, the centrifugal force acting on the rolling elements can be increased, and the vibration damping performance due to the reciprocating motion of the rolling elements can be improved. In the apparatus described in Patent Document 1, the rotational speed of the carrier disk is increased with respect to the rotational speed of the crankshaft by the speed increasing mechanism, so that the centrifugal force acting on each roller can be increased. However, since the crankshaft, the speed increasing mechanism, the carrier disk, and the like are arranged coaxially, the carrier disk and other devices arranged radially outward of the carrier disk may interfere with each other or between them. As a result, there is a possibility that inconveniences arise such that the space for mounting is generated, the size of the carrier disk is limited, and the mountability of the carrier disk is deteriorated.

  The present invention has been made paying attention to the above technical problem, and can increase the centrifugal force acting on the rolling elements arranged in the rotating body to improve the vibration damping performance and improve the mountability of the rotating body. The object is to provide a vibration reducing device.

  In order to achieve the above object, according to the present invention, a rotating body that rotates in response to torque output from an engine is disposed on the output side of the engine in the torque transmission direction, and the torque fluctuates to change the torque. In the torsional vibration reduction device in which a plurality of rolling elements that reciprocate in the circumferential direction of the rotating body are arranged at regular intervals in the circumferential direction of the rotating body, an annular drive gear that is an internal gear, and A speed increasing mechanism comprising a driven gear that is smaller in diameter than the drive gear, is inserted inside the drive gear, and is radially offset with respect to the drive gear and meshes with the drive gear; Is arranged on the same axis as the input shaft connected to the engine and integrated with the input shaft, and the driven gear is the same as the rotating body. And it is characterized in that it is integrated with the rotary body on the axis.

  According to the present invention, since the input shaft coupled to the output side of the engine and the rotating body are connected via the speed increasing mechanism, the rotational speed of the rotating body can be increased with respect to the rotational speed of the input shaft. . Therefore, the centrifugal force acting on the plurality of rolling elements arranged in the rotating body can be increased, and the vibration damping performance due to the reciprocating motion of each rolling element can be improved. The speed increasing mechanism described above is constituted by an annular drive gear that is an internal gear and an external gear that is a driven gear having a smaller diameter than the drive gear, and the drive gear is disposed on the same axis as the input shaft. And it is integrated with the input shaft, and the driven gear is integrated with the rotating body on the same axis as the rotating body. Therefore, when the input shaft and the rotating body are connected via the speed increasing mechanism, the rotation center axis of the input shaft and the rotation center axis of the rotating body are offset. That is, the rotating body can be arranged in a specific direction in the radial direction of the input shaft, and a space can be formed on the opposite side of the rotating body from the rotational center axis of the input shaft. For this reason, the space between the rotating body and other devices arranged outside in the radial direction of the rotating body is enlarged by the space so that the rotating body and other devices interfere with each other, It is possible to avoid or suppress inconveniences such as occurrence of a mounting space between the two. Thereby, the mountability of the rotating body and the entire apparatus can be improved. In addition, since the drive gear that is the external gear is arranged inside the annular drive gear that is the internal gear, when the speed increasing mechanism is configured by arranging the driven gear outside the drive gear in the radial direction. In comparison, the speed increasing mechanism in the present invention can be reduced in size, and the mountability of the speed increasing mechanism can be improved. If the above-described inconvenience such as mounting space does not occur, the diameter of the rotating body can be increased by the space. When the diameter of the rotating body is increased, each rolling element can be arranged on the outer peripheral side in the radial direction of the rotating body, so that the centrifugal force acting on each rolling element as the rotating body rotates can be further increased. The vibration control performance due to the reciprocating motion can be further improved.

It is sectional drawing which shows the torsional vibration reduction apparatus which concerns on one Embodiment of this invention. It is sectional drawing which follows the II-II line | wire shown in FIG. It is sectional drawing which shows the torsional vibration reduction apparatus which concerns on other embodiment of this invention.

  Next, the present invention will be described based on embodiments. FIG. 1 is a cross-sectional view showing a torsional vibration reducing device according to an embodiment of the present invention, and the example shown here is configured to reduce vibration of torque transmitted from an engine (not shown) to a transmission (not shown). This is an example. A disk-shaped connecting plate 2 is fixed to the input shaft 1 of the transmission. In place of the input shaft 1 of the transmission, a crankshaft of an engine (not shown), or a rotating shaft such as a propeller shaft or an axle that transmits driving force to wheels (not shown) may be used. A cylindrical portion 3 extending in the direction of the rotation axis X1 of the input shaft 1 is integrally formed at the outer peripheral end of the connecting plate 2. A drive gear 4, which is an internal gear, is formed over the entire circumference of the inner peripheral surface of the end portion of the cylindrical portion 3 opposite to the connection plate 2.

  A guide plate 5 corresponding to a rotating body in the embodiment of the present invention is disposed adjacent to the connection plate 2 so as to be rotatable relative to the input shaft 1. The guide plate 5 is a member formed in a disc shape as a whole, and a cylindrical shaft portion 6 is provided at the center portion thereof, and the input shaft 1 can be relatively rotated in the shaft portion 6. Has been inserted. Further, the outer diameter of the shaft portion 6 is smaller than that of the cylindrical portion 3 described above, and a driven gear 7 that is an external gear that meshes with the drive gear 4 described above on the outer peripheral surface of the shaft portion 6 on the connecting plate 2 side. Is formed. The driven gear 7 is a gear having a smaller diameter than the drive gear 4. Therefore, a speed increasing mechanism 8 is constituted by these gears 4 and 7. That is, the rotational speed of the guide plate 5 is increased according to these gear ratios with respect to the rotational speed of the input shaft 1. Since the input shaft 1 and the guide plate 5 are connected via the speed increasing mechanism 8, the rotation center axis X1 of the input shaft 1 and the rotation center axis X2 of the guide plate 5 are offset, and the input shaft 1 A space ΔR, which will be described later, is formed on the opposite side of the guide plate 5 from the rotation center axis line X2. A configuration for holding the drive gear 4 and the driven gear 7 in a meshed state will be described later.

  A flange portion 9 extending outward in the radial direction is formed at an end portion of the shaft portion 6 opposite to the connection plate 2. A plurality of guide holes 10 are formed in the flange portion 9 at regular intervals in the circumferential direction of the guide plate 5. Each guide hole 10 is formed through the flange portion 9 in the plate thickness direction, and a rolling element 11 is disposed in each guide hole 10. First, the configuration of the guide hole 10 will be described, and then the configuration of the rolling element 11 will be described.

  FIG. 2 is a cross-sectional view taken along the line II-II shown in FIG. The guide hole 10 described above has an appropriate shape and size that allows the rolling elements 11 disposed therein to reciprocate within a predetermined range. The shape of the guide hole 10 is an elliptical shape or an oval shape shown in FIG. It may be a round shape or a simple circle. Of the inner wall surface of the guide hole 10, the inner wall surface on the outer side in the radial direction of the guide plate 5 is pressed by the rolling element 11 by centrifugal force, and the rolling element 11 reciprocates due to torque fluctuation of the guide plate 5, that is, torsional vibration. It is made into the rolling surface 12 made to be made. The shape of the rolling surface 12 is an arc surface having a radius smaller than the dimension from the rotation center axis X2 of the guide plate 5 to the rolling surface 12 or a curved surface approximating the arc surface. In FIG. 2, each root circle and each tooth tip circle of the drive gear 4 and the driven gear 7 described above are indicated by solid lines, and each pitch circle is indicated by an alternate long and short dash line.

  A portion of the rolling element 11 that contacts the rolling surface 12 is configured to have a circular cross section. Therefore, the rolling element 11 may be a simple columnar or cylindrical member, or the cross-sectional shape having a flange portion provided at both ends of the columnar or cylindrical main body portion forms an “H” shape. It may be configured. FIG. 1 shows a rolling element 11 having a cross-sectional shape of “H” shape. With such a configuration, the outer peripheral surface of the main body portion is in contact with the rolling surface 12 and rolls along the rolling surface 12, and each flange portion is caught so as to contact both side surfaces of the guide plate 5. The rolling element 11 can be prevented from coming out of the guide hole 10 in the axial direction. The outer diameter of the rolling element 11 is set slightly smaller than the dimension of the narrowest opening width in the guide hole 10. This is because the rolling element 11 can roll on the rolling surface 12 without slidingly contacting the inner wall surface of the guide hole 10. Therefore, a gap or a so-called play exists between the outer peripheral surface of the rolling element 11 and the inner wall surface of the guide hole 10.

  A configuration in which the drive gear 4 and the driven gear 7 described above are held in mesh will be described. As shown in FIG. 1, a projecting portion 6 </ b> A extending inward in the radial direction is formed on the inner peripheral surface of the shaft portion 6, and contacts the side surface of the projecting portion 6 </ b> A and the inner peripheral surface of the shaft portion 6. Thus, the outer ring of the bearing 13 is fitted. A cylindrical connecting portion 14 is arranged inside the shaft portion 6. A boss portion 14A extending in the direction of the rotation center axis X2 is formed at one end portion of the connecting portion 14 on the guide plate 5 side. The boss portion 14A and one end portion of the connecting portion 14 come into contact with the inner ring of the bearing 13. Are fitted. That is, the shaft portion 6 and the connecting portion 14 of the guide plate 5 are connected via the bearing 13 so as to be relatively rotatable. Furthermore, a stay 15 extending outward in the radial direction is formed at the end of the connecting portion 14 opposite to the boss portion 14A in the direction of the rotation center axis X2, and the stay 15 is formed on a fixed portion 16 such as a casing. It is supposed to be fixed. The drive gear 4 and the driven gear 7 are engaged with the fixed portion 16 with the bearing 13, the connecting portion 14, the stay 15, and the like.

  Therefore, in the embodiment shown in FIG. 1, the shaft portion 6 and the coupling portion 14 of the guide plate 5 are connected via the bearing 13, and the drive gear 4 and the driven gear 7 are engaged with each other. In this state, the stay 15 is fixed to the fixing portion 16. By doing so, the rotation center axes X1 and X2 of the gears 4 and 7 are offset to be parallel to each other. As a result, as shown in FIG. 1, a space ΔR is formed on the side opposite to the rotation center axis X2 of the guide plate 5 with the input shaft 1 interposed therebetween. Specifically, the space ΔR described above is formed on the outer peripheral side of the guide plate 5, and the guide plate 5 and other devices and members arranged on the outer peripheral side of the guide plate 5 interfere with each other by the space ΔR. Or inconveniences such as having the mounting space for each other can be avoided or suppressed. More specifically, for example, a case where the guide plate 5 is attached to the input shaft in a transmission having an input shaft and an output shaft arranged in parallel to each other will be described. In this case, by adopting the configuration shown in FIG. 1, the distance between the guide plate 5 and the output shaft can be increased by the space ΔR. Therefore, the interference between the guide plate 5 and the output shaft and the mounting space can be avoided or suppressed. As a result, the mountability of the guide plate 5 and the transmission can be improved, and the distance between the input shaft and the output shaft in the transmission can be reduced as much as possible.

  Further, in the embodiment shown in FIG. 1, the speed increasing mechanism 8 is configured by disposing the driven gear 7 that is an external gear inside the drive gear 4 that is an internal gear, and therefore, the outer side of the drive gear in the radial direction. The speed increasing mechanism 8 can be downsized as compared with the case where the speed increasing mechanism is configured by arranging the driven gear. Therefore, the mountability of the speed increasing mechanism 8 can be improved. Further, in the embodiment shown in FIG. 1, the guide plate 5 can be arranged offset with respect to the input shaft 1, so that the diameter of the guide plate 5 can be increased by the space ΔR. In this case, as compared with the case where the diameter of the guide plate 5 is not increased, each rolling element 11 can be arranged on the outer side in the radial direction of the guide plate 5, and the centrifugal force acting on each rolling element 11 can be increased. The width of the space ΔR in the vertical direction in FIG. 1 is twice the length between the rotation center axis X1 of the input shaft 1 and the rotation center axis X2 of the guide plate 5, that is, the offset amount.

  When the input shaft 1 rotates, the drive gear 4 connected to the input shaft 1 via the connection plate 2 rotates, and the driven gear 7 meshed with the drive gear 4 rotates. That is, the speed increasing mechanism 8 increases the rotational speed of the guide plate 5 with respect to the rotational speed of the input shaft 1. Each rolling element 11 rotates together with the guide plate 5, and a centrifugal force corresponding to the number of rotations of the guide plate 5 acts on each rolling element 11. A greater centrifugal force acts on each rolling element 11 than when the guide plate 5 is not accelerated. When the torque does not fluctuate, each rolling element 11 moves to a position farthest from the rotation center axis X2 of the guide plate 5 in the rolling surface 12 by the centrifugal force, and is pressed against the rolling surface 12. . If the torque of the guide plate 5 fluctuates in this state, the guide plate 5 vibrates in the rotational direction (torsional vibration), so that the relative acceleration in the rotational direction occurs in each rolling element 11, and each rolling element 11 is caused by inertial force. Roll along the rolling surface 12. The inertial force of the rolling element 11 acts in a direction to suppress the vibration of the guide plate 5, and torsional vibration is reduced. As described above, in the embodiment shown in FIG. 1, the rotational speed input to the guide plate 5 is increased by the speed increasing mechanism 8, so that the centrifugal force acting on each rolling element 11 arranged on the guide plate 5 is increased. Thus, the vibration control performance due to the reciprocating motion of each rolling element 11 can be improved.

  FIG. 3 is a sectional view showing a torsional vibration reducing device according to another embodiment of the present invention. The example shown here is an example in which a plurality of rollers 17 are arranged in place of the bearing 13 between the shaft portion 6 and the connecting portion 14 of the guide plate 5. In the example shown in FIG. Four rollers 17 are arranged on the surface at regular intervals along the circumferential direction. Each roller 17 is attached to the stay 15 via a support member 18 such as a pin or a bearing that rotatably supports the roller 17. Other configurations are the same as those in the embodiment shown in FIG. 1 and FIG. 2 described above, and a description thereof will be omitted.

  In the example shown in FIG. 3, the roller 17 can be easily replaced as compared with the case where the bearing 13 is used. The offset amount of the guide plate 5 can be easily changed. Furthermore, since it is comprised so that the some roller 17 may be rotatably arrange | positioned between the axial part 6 and the connection part 14, it is easy to manufacture compared with the case where the bearing 13 is used, and it concerns on manufacture and a process. Cost can be reduced. Also in the example shown in FIG. 3, the rotation center axes X1 and X2 are offset from each other, so that the above-described space ΔR is formed, and the guide plate 5 and the outer peripheral side of the guide plate 5 are arranged by the space ΔR. It is possible to avoid or suppress interference with other devices and members and mounting space. Moreover, since the rotational speed of the guide plate 5 is increased with respect to the rotational speed of the input shaft 1 by the speed increasing mechanism 8, the centrifugal force acting on each rolling element 11 can be increased. Thereby, the damping performance by the reciprocating motion of each rolling element 11 can be improved.

  DESCRIPTION OF SYMBOLS 1 ... Input shaft, 5 ... Guide plate (rotating body), 4 ... Drive gear, 7 ... Driven gear, 8 ... Speed increasing mechanism, 11 ... Rolling body.

Claims (1)

A rotating body that rotates in response to the torque output by the engine is disposed on the output side of the engine in the torque transmission direction, and a rolling element that reciprocates in the circumferential direction of the rotating body when the torque fluctuates. In the torsional vibration reduction device that is arranged in a plurality at a constant interval in the circumferential direction of the rotating body,
An annular drive gear that is an internal gear, and a driven gear that is smaller in diameter than the drive gear, is inserted inside the drive gear, and is radially offset with respect to the drive gear and meshes with the drive gear. It has a speed increasing mechanism configured,
The drive gear is disposed on the same axis as the input shaft connected to the engine and integrated with the input shaft;
The torsional vibration reducing device, wherein the driven gear is integrated with the rotating body on the same axis as the rotating body.

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