JP6387870B2 - Torsional vibration reduction device - Google Patents

Description

  The present invention relates to a vibration reducing device configured to reduce vibration of an input torque by an inertia torque generated with the vibration of the torque.

  The torsional vibration damper described in Patent Document 1 includes a planetary gear mechanism, and its sun gear is used as an input element and its ring gear is used as an output element. A first fly mass body is coupled to the sun gear, and a second fly mass body is coupled to the ring gear. Between the sun gear and the ring gear, there is provided a spring device that generates an elastic force that counteracts a torque that allows the relative rotation and relative rotation of the sun gear and the ring gear.

  Further, the damper device described in Patent Document 2 includes a first ring gear connected to the engine via a spring, a carrier that holds the pinion gear meshing with the first ring gear so that the pinion gear can rotate and revolve, and is connected to the engine. And a second ring gear connected to the transmission. A first inertia body is attached to the first ring gear, and the first ring gear is connected to the second inertia body via a clutch mechanism. The second inertial body is attached to the housing via a bearing.

JP 9-196122 A JP 2014-177958 A

  In the device described in Patent Document 1 described above, when the torque varies, the sun gear and the ring gear rotate relative to each other, and the carrier rotates accordingly. The carrier generates an inertia torque according to its mass as a resistance force against the torque fluctuation. However, since the mass of the carrier is constant, the vibration characteristics that can be reduced by the inertia torque according to the mass of the carrier are limited.

  Moreover, in the structure described in patent document 2, since a 2nd inertia body is selectively connected to a 1st ring gear via a clutch mechanism, an inertial mass changes and the vibration characteristic according to each can be acquired. . However, in the configuration described in Patent Document 2, since the clutch mechanism is provided, the overall configuration of the device is complicated, such as an increase in the number of parts and the need for a device for controlling the clutch mechanism. There is a possibility of becoming.

  The present invention has been made paying attention to the above technical problem, and an object of the present invention is to provide a torsional vibration reducing device capable of changing the vibration damping performance with a simple configuration.

In order to achieve the above object, the present invention includes a differential mechanism that performs a differential action by at least three rotating elements, and an input to which torque is input to the first rotating element among the at least three rotating elements. The second rotating element is an output element that outputs the torque, the third rotating element is an inertia mass body, and the input element and the output element are connected to each other via an elastic body so as to be relatively rotatable. In the torsional vibration reduction device, an additional inertial body is attached to the third rotating element with a predetermined gap in the rotation direction of the third rotating element, and the gap is formed by the torque of the third rotating element. When the rotation angle is smaller than a predetermined rotation angle, the third rotation element rotates relative to the additional inertia body without the additional inertia body, and the rotation angle of the third rotation element is Predetermined times If the angle is greater than the said gap is filled with the third rotary element and the additional inertial body, characterized in that it is configured to reciprocally rotate in response to the vibration of the torque together Is .
In the present invention, the differential mechanism can transmit torque to at least one of the sun gear, the ring gear arranged concentrically with the sun gear, and the sun gear and the ring gear as the three rotating elements. A planetary gear mechanism having a plurality of pinion gears engaged with the carrier and capable of rotating and revolving, wherein the first rotating element is constituted by one of the sun gear and the ring gear. The second rotating element may be constituted by the carrier, and the third rotating element may be constituted by the other of the sun gear and the ring gear.

According to the present invention, the first rotating element and the second rotating element compress the elastic body relative to each other due to the vibration of the input torque, and the third rotating element, which is an inertial mass body, reciprocally rotates. In the state where the rotation angle is small, the gap between the additional inertial body and the additional rotation body is not blocked, and therefore the third rotation element reciprocates independently without the additional rotation body. Therefore, the moment of inertia in this case is the moment of inertia corresponding to the mass of the third rotating element. Further, when the rotation angle of the third rotary body element is large, the third rotating element clogged the gap and additional inertial body are integrated. Accordingly, the moment of inertia in this case is the moment of inertia corresponding to the sum of the mass of the third rotating element and the mass of the additional inertial body. According to the present invention, it is possible to obtain a vibration reducing device having at least two types of vibration damping characteristics by changing the equivalent inertia for vibration damping with a simple configuration.

It is a front view of the planetary gear mechanism which comprises the principal part of 1st Example of the torsional vibration reduction apparatus which concerns on this invention. It is a skeleton figure which shows the state which integrated the vibration reduction apparatus shown in FIG. 1 in the predetermined power transmission device. It is a figure for demonstrating operation | movement of 1st Example of the torsional vibration reduction apparatus shown in FIG. It is a front view of the planetary gear mechanism which comprises the principal part of 2nd Example of the torsional vibration reduction apparatus of this invention. FIG. 5 is a skeleton diagram showing a state in which the torsional vibration reducing device shown in FIG. 4 is incorporated in a predetermined power transmission device. It is a front view of the planetary gear mechanism which comprises the principal part of 3rd Example of the torsional vibration reduction apparatus of this invention. It is a skeleton figure which shows the state which incorporated the torsional vibration reduction apparatus shown in FIG. 6 in the predetermined power transmission device. It is a front view of the planetary gear mechanism which comprises the principal part of 4th Example of the torsional vibration reduction apparatus of this invention. It is a figure which expands and shows the meshing part of the sun gear and mass increase part in 4th Example shown in FIG. It is a front view of the planetary gear mechanism which comprises the principal part of 5th Example of the torsional vibration reduction apparatus of this invention.

  FIG. 1 is a front view of a planetary gear mechanism constituting the main part of a first embodiment of the torsional vibration reducing device of the present invention. The planetary gear mechanism 1 is a sun gear 2 that is an external gear, a ring gear 3 that is an internal gear arranged concentrically with the sun gear 2, and an external gear that meshes with the sun gear 2 and the ring gear 3. A plurality of pinion gears 4 and a carrier 5 holding the pinion gears 4 so as to be capable of rotating and revolving are provided. An additional inertial body 7 is attached to the sun gear 2 with a predetermined gap in the rotational direction of the sun gear 2. Specifically, a plurality of pins 6 are provided on the side surface of the sun gear 2, and a long hole 8 into which the pins 6 are movably inserted is formed in the additional inertial body 7.

  The additional inertial body 7 is formed in a fan shape as an example, and has a pair of long holes 8 penetrating in the plate thickness direction. Each elongated hole 8 is formed at the same position from the center of the additional inertial body 7 in the length direction, extending in the circumferential direction of the sun gear 2 and curved along the shape of the additional inertial body 7. The pins 6 are inserted into the long holes 8 so as to be movable. When the magnitude of vibration of the torque is smaller than the magnitude of vibration of torque determined in advance, the pin 6 contacts the inner surfaces 8a and 8b in the length direction of the slot 8. It is not long. Therefore, when the magnitude of the torque vibration is larger than the predetermined magnitude of the torque vibration, the inner surfaces 8a, 8b in the length direction of the long hole 8 and the pin 6 come into contact with each other.

  FIG. 2 is a skeleton diagram showing a state in which the vibration reducing device shown in FIG. 1 is incorporated in a predetermined power transmission device. In the example shown in FIG. 2, the ring gear 3 is connected to the engine 9 and the ring gear 3 is used as an input element, and the carrier 5 is connected to the transmission 10 and the carrier 5 is used as an output element. The ring gear 3 and the carrier 5 are connected via a spring damper 11 corresponding to the elastic body in the first embodiment, and the spring damper 11 is subjected to torque that causes relative rotation between the ring gear 3 and the carrier 5. The elastic force acts as a reaction force.

  When the torque of the engine 9 is transmitted to the ring gear 3, the torque for rotating the transmission 10 acts on the carrier 5 as a reaction force. Along with this, a load that compresses a spring (not shown) acts on the spring damper 11, and a displacement corresponding to the load occurs. As a result, the ring gear 3 and the carrier 5 rotate relative to each other by a predetermined angle. Along with this, the sun gear 2 rotates at an angle corresponding to the relative rotation angle between the ring gear 3 and the carrier 5. When the torque transmitted from the engine 9 is stable, that is, when there is no or slight torque vibration, the entire planetary gear mechanism 1 in which such relative rotation occurs is integrated. The engine 9 rotates and torque is transmitted from the engine 9 to the transmission 10. When the planetary gear mechanism 1 rotates, a centrifugal force is generated in the additional inertial body 7 and is moved outward in the radial direction by the centrifugal force. As will be described later, the outer peripheral surface of the pin 6 and the additional inertial body 7 Of the inner surface of the long hole 8, the inner surface 8 c contacts with the inner surface 8 c in the radial direction of the sun gear 2.

  When the torque transmitted to the ring gear 3 vibrates, the load acting on the spring damper 11, that is, the compression force changes, and the ring gear 3 and the carrier 5 rotate relative to each other by a predetermined angle. Accordingly, the sun gear 2 reciprocates within a rotation angle range corresponding to the magnitude of the torque vibration. In the first embodiment, when the magnitude of torque vibration is larger than the predetermined torque vibration magnitude, that is, when the rotation angle of the sun gear 2 is larger than the predetermined rotation angle, the additional inertial body together with the sun gear 2 is used. The length of the long hole 8 is designed so that 7 reciprocates. The rotational angle at which the sun gear 2 and the additional inertial body 7 are reciprocated integrally, or the length of the long hole 8 in the circumferential direction can be determined by design for each number of cylinders of the engine 9 and vehicle type.

  Next, the operation of the torsional vibration reducing device having the above configuration will be described. When the torque transmitted from the engine 9 to the planetary gear mechanism 1 is stable, as described above, the spring of the spring damper 11 is bent, and the entire planetary gear mechanism 1 is integrated in a state where the bending is maintained. Turns and turns. The additional inertial body 7 generates a centrifugal force according to its mass and the number of rotations, and the additional inertial body 7 is moved to the farthest radial direction from the rotation center of the sun gear 2 by this centrifugal force. As a result, the inner surface 8 c on the inner side of the pin 6 and the inner surface of the long hole 8 in the radial direction of the sun gear 2 comes into contact. Since each long hole 8 is formed at the same position from the central portion in the length direction of the additional inertial body 7 as described above, each pin 6 is disposed at the same position from the central portion in each long hole 8. Is done. This state is maintained when the torque transmitted to the planetary gear mechanism 1 is stable. Such a state is a so-called neutral state.

  FIG. 3 is a diagram for explaining the operation of the first embodiment of the torsional vibration reducing apparatus shown in FIG. FIG. 3A shows an example of the above-described neutral state. In the example shown here, the pins 6 are respectively arranged at the center portions of the long holes 8 in the length direction. When the torque vibrates, the compressive force acting on the spring damper 11 changes, and the ring gear 3 and the carrier 5 relatively rotate within an angle range corresponding to the magnitude of torque vibration. Accordingly, the sun gear 2 reciprocates within an angle range corresponding to the magnitude of the torque vibration.

  When the magnitude of the vibration of the torque is smaller than the magnitude of the predetermined torque vibration, the rotation angle of the sun gear 2 is smaller than the rotation angle corresponding to the magnitude of the predetermined torque vibration. 3 (b) and 3 (c) show the state, and FIG. 3 (b) and FIG. 3 (c) show the magnitude and direction of the vibration of the torque acting on the sun gear 2 as vector V1 or vector V2. It is marked with. That is, when the sun gear 2 is rotated by the vibration of the torque indicated by the vector V1 in FIG. 3B, the additional inertial body 7 apparently moves in the direction opposite to the sun gear 2. In the example shown in FIG. 3B, the rotation angle of the sun gear 2 is smaller than the rotation angle corresponding to the magnitude of the predetermined torque vibration, so the other of the pin 6 and the long hole 8 in the length direction is the other. The inner surface 8b does not contact. The same applies to the case where the sun gear 2 is rotated by the vibration of the torque indicated by the vector V2 in FIG. 3C, and the pin 6 and one inner surface 8a in the length direction of the long hole 8 are in contact with each other. Do not touch. As described above, when the magnitude of the torque vibration is smaller than the predetermined magnitude of the torque vibration, the gap between the sun gear 2 and the additional inertial body 7 is not blocked. As a result, the additional inertial body 7 and the sun gear 2 move relative to each other, and the sun gear 2 generates an inertia torque according to its mass (moment of inertia) and rotational angular acceleration. The inertia torque of the sun gear 2 acts as a load for reducing the vibration of the torque, and the vibration of the torque is reduced.

  On the other hand, when the magnitude of vibration of the torque is larger than the magnitude of vibration of the predetermined torque, the rotation angle of the sun gear 2 becomes larger than the rotation angle corresponding to the magnitude of vibration of the predetermined torque. 3 (d) and 3 (e) show the state, and FIG. 3 (d) and 3 (e) show the magnitude and direction of the vibration of the torque acting on the sun gear 2 as vector V3 or vector V4. It is marked with. That is, when the sun gear 2 is rotated by the vibration of the torque indicated by the vector V3 in FIG. 3D, the pin 6 and the other inner surface 8b of the long hole 8 abut due to the large rotation angle of the sun gear 2. The same applies to the case where the sun gear 2 is rotated by the vibration of the torque indicated by the vector V4 in FIG. Thus, when the magnitude of torque vibration is larger than the magnitude of the predetermined torque vibration, the gap between the sun gear 2 and the additional inertial body 7 is clogged, and these reciprocate and rotate together. As a result, an inertia torque according to the mass (moment of inertia) obtained by adding the mass of the sun gear 2 and the mass of the additional inertial body 7 and the rotational angular acceleration is generated, and the vibration of the torque is reduced by the inertia torque.

  FIG. 4 is a front view of the planetary gear mechanism constituting the main part of the second embodiment of the torsional vibration reducing device of the present invention, and FIG. 5 shows the torsional vibration reducing device shown in FIG. 4 as a predetermined power transmission device. It is a skeleton figure which shows the assembled state. The example shown in FIGS. 4 and 5 is an example in which the sun gear 2 is connected to the engine 9 as an input element, and the carrier 5 is connected to the transmission 10 as an output element. Further, the sun gear 2 and the carrier 5 are connected via a spring damper 11. An additional inertial body 7 is attached to the ring gear 3 with a predetermined gap. Specifically, a pin 6 is provided on the ring gear 3, and the pin 6 is inserted into the long hole 8 of the additional inertial body 7. When the transmitted torque vibrates, the compressive force acting on the spring damper 11 changes, and the sun gear 2 and the carrier 5 rotate relative to each other within an angle range corresponding to the magnitude of vibration of the transmitted torque. Accordingly, the ring gear 3 reciprocates within an angle range corresponding to the magnitude of the torque vibration. In the second embodiment, when the magnitude of torque vibration is larger than the predetermined torque vibration magnitude, that is, when the rotation angle of the ring gear 3 is larger than the predetermined angle, the additional inertial body 7 is coupled with the ring gear 3. The length of the long hole 8 in the circumferential direction is designed so as to reciprocate. The length of the long hole 8 in the circumferential direction can be determined by design for each cylinder number and vehicle type of the engine 9 as in the first embodiment described above.

  4 and 5, when the magnitude of the transmitted torque vibration is smaller than the predetermined torque vibration magnitude, the same principle as in the first embodiment is used. The ring gear 3 rotates reciprocally. Therefore, the vibration of the torque is reduced by the inertia torque according to the mass of the ring gear 3 and the rotational angular acceleration. On the other hand, if the magnitude of the vibration of the torque is larger than the magnitude of the predetermined vibration of the torque, the ring gear 3 and the additional inertial body 7 are reciprocally rotated integrally by the same principle as in the first embodiment. The vibration of the torque is reduced by the inertia torque according to the mass obtained by adding the masses and the rotational angular acceleration.

  FIG. 6 is a front view of a planetary gear mechanism that constitutes a main part of a third embodiment of the torsional vibration reducing device of the present invention. FIG. 7 shows the torsional vibration reducing device shown in FIG. 6 as a predetermined power transmission device. It is a skeleton figure which shows the assembled state. 6 and 7 are examples in which the sun gear 2 is connected to the engine 9 as an input element, and the ring gear 3 is connected to the transmission 10 as an output element. Further, the sun gear 2 and the ring gear 3 are connected via a spring damper 11. An additional inertial body 7 is attached to the carrier 5 with a predetermined gap. Specifically, the carrier 5 is provided with a pin 6, and the pin 6 is inserted into the elongated hole 8 of the additional inertial body 7. When the torque transmitted to the sun gear 2 vibrates, the compressive force acting on the spring damper 11 changes, and the sun gear 2 and the ring gear 3 rotate relative to each other within an angle range corresponding to the magnitude of vibration of the transmitted torque. . As a result, the carrier 5 reciprocates within an angle range corresponding to the magnitude of the torque vibration. In the third embodiment, when the magnitude of torque vibration is larger than the predetermined magnitude of torque vibration, that is, when the rotation angle of the carrier 5 is larger than the predetermined rotation angle, the additional inertial body 7 together with the carrier 5 is used. The length of the long hole 8 in the circumferential direction is designed so as to reciprocate. The length of the long hole 8 in the circumferential direction can be determined by design for each cylinder number and vehicle type of the engine 9 as in the first and second embodiments described above.

  6 and 7, even if the magnitude of the transmitted torque vibration is smaller than the predetermined torque vibration magnitude, the first and second embodiments are used. The carrier 5 reciprocates on the same principle as in FIG. Therefore, the vibration of the torque is reduced by the inertia torque according to the mass of the carrier 5 and the rotational angular acceleration. On the other hand, when the magnitude of the torque vibration is larger than the predetermined magnitude of the torque vibration, the carrier 5 and the additional inertial body 7 are united according to the same principle as in the first and second embodiments. Therefore, the vibration of the torque is reduced by the inertia torque according to the mass obtained by adding the masses and the rotational angular acceleration.

  FIG. 8 is a front view of the planetary gear mechanism constituting the main part of the fourth embodiment of the torsional vibration reducing apparatus of the present invention. The example shown here is an example in which a part of the first embodiment shown in FIG. 1 is changed, and the additional inertial body 7 is provided with a predetermined gap in the circumferential direction on the inner side in the radial direction of the sun gear 2. It is an attached example. The additional inertial body 7 shown in FIG. 8 is formed in an annular shape, and external teeth are formed on the outer peripheral surface thereof at regular intervals. Internal teeth that mesh with these external teeth are formed on the inner side in the radial direction of the sun gear 2. FIG. 9 is an enlarged view showing a meshing portion between the sun gear 2 and the additional inertial body 7. As shown in FIG. 9, a predetermined gap C is formed between the tooth surface of the inner tooth 2 a of the sun gear 2 and the tooth surface of the outer tooth 7 a of the additional inertial body 7. This gap C functions in the same way as the long hole 8 in the first to third embodiments, and when the magnitude of torque vibration is larger than the predetermined magnitude of torque vibration, the sun gear 2 And the additional inertial body 7 are designed to reciprocate together. That is, the length is the same as the moving length of the sun gear 2 according to the magnitude of the predetermined torque vibration. The sun gear 2 and the additional inertial body 7 may be configured to be spline-fitted with the gap C in place of the so-called meshing of the dog teeth. In short, the gap is formed. Just do it. As in the first embodiment, the engine 9 is connected to the ring gear 3, the transmission 10 is connected to the carrier 5, and the ring gear 3 and the carrier 5 are connected via a spring damper 11. Yes.

  FIG. 10 is a front view of the planetary gear mechanism constituting the main part of the fifth embodiment of the torsional vibration reducing apparatus of the present invention. The example shown here is an example in which a part of the fourth embodiment shown in FIG. 8 is changed, and an example in which an additional inertial body 7 is provided so as to mesh with the outer teeth of the sun gear 2 with a predetermined gap. It is. Although not shown in detail, the additional inertial body 7 is formed in an annular shape, and external teeth that mesh with the external teeth of the sun gear 2 are formed on the outer peripheral surface thereof at a constant interval. Further, a gap C is formed between the tooth surface of the external tooth of the sun gear 2 and the tooth surface of the external tooth of the additional inertial body 7 as in the fourth embodiment.

  Even in the fourth embodiment shown in FIG. 8 and the fifth embodiment shown in FIG. 10, when the transmitted torque vibrates, the ring gear 3 and the carrier 5 cause a large amount of torque vibration as in the first embodiment. Relative rotation within a range of angles according to the height. As a result, the sun gear 2 reciprocates within an angle range corresponding to the magnitude of the torque vibration. Since the gap C described above functions in the same way as the long hole 8, when the magnitude of the torque vibration is smaller than the predetermined torque vibration magnitude, the additional inertial body is applied according to the same principle as in the first embodiment. 7 external teeth and the internal or external teeth of the sun gear 2 do not mesh with each other, and only the sun gear 2 reciprocates. Torque vibration is reduced by an inertia torque according to the mass of the sun gear 2 and the rotational angular acceleration. On the other hand, when the magnitude of the vibration of the torque is larger than the magnitude of the predetermined torque vibration, the external teeth of the additional inertial body 7 and the internal teeth or external teeth of the sun gear 2 according to the same principle as in the first embodiment. Meshing with each other, they reciprocate together, and torque vibration is reduced by inertia torque according to the sum of the masses and the rotational angular acceleration.

  Thus, in the vibration reducing device according to the present invention, the inertial mass body has a planetary gear mechanism that performs differential action by three rotating elements, and reduces the torsional vibration of one of the three rotating elements. To function as. Further, since the additional inertial body 7 is attached to the inertial mass body with a predetermined gap, if the magnitude of vibration of the input torque is larger than the magnitude of the predetermined torque vibration, the inertial mass 7 The mass body and the additional inertial body 7 can be reciprocated together. Therefore, according to the present invention, it is possible to obtain a vibration reduction device having a simple configuration and having at least two types of vibration damping characteristics.

  DESCRIPTION OF SYMBOLS 1 ... Planetary gear mechanism, 2 ... Sun gear, 3 ... Ring gear, 5 ... Carrier, 6 ... Pin, 7 ... Additional inertia body, 8 ... Long hole, 11 ... Spring damper

Claims (2)

A differential mechanism that performs a differential action by at least three rotating elements, wherein the first rotating element of the at least three rotating elements is an input element to which torque is input, and the second rotating element outputs the torque; A torsional vibration reduction device in which the third rotating element is an inertial mass body, and the input element and the output element are connected to each other via an elastic body so as to be relatively rotatable.
An additional inertial body is attached to the third rotating element with a predetermined gap in the rotational direction of the third rotating element ,
When the rotation angle of the third rotation element due to vibration of the torque is smaller than a predetermined rotation angle, the third rotation element does not accompany the additional inertial body and the additional inertial body When the relative rotation is performed and the rotation angle of the third rotation element is larger than the predetermined rotation angle, the clearance is closed and the third rotation element and the additional inertial body are integrated with each other. A torsional vibration reducing device configured to reciprocate in response to vibration.   The torsional vibration reducing device according to claim 1,
  The differential mechanism is engaged with at least one of a sun gear, a ring gear concentrically arranged with respect to the sun gear, and at least one of the sun gear and the ring gear as the three rotating elements so as to transmit torque. A planetary gear mechanism including a carrier holding a plurality of pinion gears so as to be capable of rotating and revolving,
  The first rotating element is constituted by one of the sun gear and the ring gear,
  The second rotating element is constituted by the carrier;
  The third rotating element is constituted by the other of the sun gear and the ring gear.
A torsional vibration reduction device characterized by that.

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