JP6707864B2 - Vibration damping device - Google Patents

Description

The present invention relates to a vibration damping device.

Techniques for reducing vibration by providing a vibration damping device in a power transmission path from an engine to a driven member are known (see Patent Documents 1 to 6). The torque transmission device 501 of FIG. 6 disclosed in Patent Document 1 is capable of connecting/disconnecting to/from a transmission via a first bounce mass body 503 that can be coupled to an output shaft of an internal combustion engine. Two bobbin masses 505 are provided. The two flywheel masses are mounted so that they can pivot relative to one another against the action of a damping device 507 arranged between them. The damping device 507 is housed in an annular chamber 511 and includes an elastic damper 509 that is effective in the circumferential direction. The annular chamber 511 houses two segmented attenuator masses (pendulums) 513a, 513b distributed around the entire circumference. The pendulums 513a, 513b are supported by at least one rotor-like component 515 of one of the bobbin masses.
Similarly, the vibration reduction device disclosed in Patent Document 2 is also provided with an elastic damper and a centrifugal pendulum damper that damps vibration by swinging of a swingably supported pendulum.

In the fluid torque converter 517 of FIG. 7 disclosed in Patent Document 3, a pump impeller (not shown) driven by an internal combustion engine drives a turbine runner 519. The turbine runner 519 is connected to the input unit 523 of the turbine damper 521. The output part 525 of the turbine damper 521 is connected to a transmission input shaft (not shown). The turbine damper 521 includes an elastic damper 527 formed by a compression coil spring 531 provided on the intermediate flange 529. A centrifugal pendulum damper 533 having a pair of pendulums 535 is arranged on the intermediate flange 529. The pair of pendulums 535 are arranged radially outside the outer peripheral portion of the intermediate flange 529 in a circumferentially distributed manner.

Similarly to Patent Document 3, the force transmission device disclosed in Patent Document 4 is also provided with a spring unit on the intermediate flange coupled to the hub and a centrifugal pendulum damper on the outer peripheral side of the intermediate flange.

Although not shown in the drawings, the torsional vibration damper including the centrifugal pendulum damper disclosed in Patent Document 5 has pendulums arranged in the circumferential direction on the outer peripheral side of the flange member. The pendulum in this case is a mass member housed in a motion trajectory formed in the flange member, and is movable with respect to the flange member within a limited range in the circumferential direction and the radial direction.
The centrifugal pendulum damper for an automobile transmission disclosed in Patent Document 6 has at least one pendulum movably attached to a rotor-shaped support body that is rotatable about an axis, although not shown.

JP, 2003-4101, A JP, 2011-208774, A JP, 2010-255853, A Special table 2011-504987 gazette Special table 2011-522185 gazette Japanese Patent Publication No. 2015-514941

The vibration damping devices of Patent Documents 1 and 2 have a configuration in which an elastic damper is arranged on the outer side in the radial direction of the rotating body and a pendulum of the centrifugal pendulum damper is arranged on the inner side. Therefore, the pendulum must be placed in a limited space between the elastic damper and the center of rotation, and the pendulum shape and pendulum length (distance from the center of the rotation axis to the center of pendulum) are limited, and the centrifugal pendulum damper Vibration control performance is reduced.
The vibration damping devices of Patent Documents 3 and 4 have a configuration in which the centrifugal pendulum damper is arranged on the outer side in the radial direction of the rotating body and the elastic damper is arranged on the inner side in the radial direction. Therefore, there is a problem in that the elastic damper cannot have a long circumference and the damping performance is low.
The vibration damping devices of Patent Documents 5 and 6 have a configuration in which a centrifugal pendulum damper is arranged on the outer peripheral edge of the rotating body. Therefore, it is only possible to select whether to arrange the elastic damper outside the pendulum or inside the pendulum. If the outer diameter of the vibration damping device is constant, if the elastic damper is placed outside the pendulum, the pendulum must be placed in a limited space, and the vibration damping performance of the centrifugal pendulum damper is reduced as above. . Further, if the pendulum is arranged on the outer peripheral edge, the circumferential length of the elastic damper cannot be increased, and the damping performance is reduced as in the above.

The present invention has been made in view of the above circumstances, and an object thereof is to provide a vibration damping device that can be downsized while improving both the vibration damping performance of a centrifugal pendulum damper and an elastic damper.

The present invention has the following configuration.
A rotating body that receives torque and rotates,
An elastic damper that is provided along the outer peripheral edge of the rotating body, and in which the elastic body expands and contracts in the circumferential direction of the rotating body due to the fluctuation of the torque,
A centrifugal pendulum damper provided on the rotating body, having a pendulum swingable in a rotation direction of the rotating body;
Equipped with
The pendulum, surrounds the outside of the resilient damper, so that the pendulum center of gravity is radially outward of said elastic damper and the resilient damper at least a portion of the pendulum in the direction of the axis of rotation of the rotating body vibration damping device, characterized in that a heavy such so that are arranged in the rotating body.
A support shaft that swingably supports the pendulum may be arranged radially inward of the elastic damper of the rotating body.

According to the vibration damping device of the present invention, it is possible to reduce the size of the centrifugal pendulum damper and the elastic damper while improving both vibration damping performance.

It is a perspective view of the vibration damping device of the first configuration example. It is a perspective view of the pendulum shown in FIG. FIG. 2 is a radial cross-sectional view of the vibration damping device shown in FIG. 1. It is a partially expanded front view seen from the rotating shaft direction of the vibration damping device shown in FIG. It is a perspective view of the vibration damping device of a modification. It is a principal part sectional view of the conventional vibration damper in which an elastic damper is arrange|positioned on the outer side of a centrifugal pendulum damper. It is a principal part sectional view of the conventional vibration damping device by which a centrifugal pendulum damper is arrange|positioned on the outer side of an elastic damper.

Hereinafter, each configuration example of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a perspective view of the vibration damping device of the first configuration example.
The vibration damping device 100 of this configuration is provided in a power transmission path from the engine to a driven member such as a drive wheel. The engine is an internal combustion engine, and examples thereof include a gasoline engine, a diesel engine, and an LPG engine. This engine is provided with a crankshaft, and torque is output to this crankshaft.

A torque converter is connected to the crankshaft of the engine, and a driven member is connected to the output shaft of the torque converter. The vibration damping device 100 is arranged in series in the power transmission path between the crankshaft and the driven member. Hereinafter, as an example, a case where the vibration damping device 100 is provided on the flywheel downstream of the crankshaft will be described.

The vibration damping device 100 includes a rotating body 11, an elastic damper 13, and a centrifugal pendulum damper 15. The vibration damping device 100 functions as a dynamic vibration absorber (DVA).

The dynamic vibration reducer suppresses the resonance phenomenon around the natural frequency of the vibration target by attaching the auxiliary mass body to the vibration target via a spring or the like. The dynamic vibration reducer suppresses the vibration of the vibrating target object by vibrating the auxiliary mass body as a substitute for the vibration of the target object.

A flywheel (flywheel) that generates a moment of inertia is fixed to a crankshaft, which is a cylindrical hub fixed to the outer circumference of the shaft. The vibration damping device 100 can be incorporated in this flywheel, for example.

Generally, a flywheel is composed of a first flywheel and a second flywheel that can rotate relative to each other. The first flywheel is fixed to the hub and is rotationally driven by the rotational torque from the engine. The second flywheel is concentrically mounted so as to be rotatable relative to the first flywheel.

An annular chamber is formed on the inner circumference of the first flywheel, and the annular chamber accommodates a vibration damping device 100 including a pair of compression coil springs 17 that are elastic bodies along the circumferential direction.

A rotating body 11 having a substantially circular outer peripheral edge, which constitutes the vibration damping device 100, is integrally attached to the second flywheel. Legs 21</b>A and 21</b>B protruding outward in the radial direction are formed on the outer circumference of both ends of the rotating body 11 in the radial direction. The leg portions 21A and 21B are arranged to face a spring seat convex portion (not shown) provided on the first flywheel so as to project in the axial direction. The leg portions 21A and 21B press the compression coil spring 17 at the ends of the compression coil spring 17 that come into contact with the spring seat protrusions, according to the rotational torque of the first flywheel. That is, the second flywheel compresses the compression coil spring 17 when rotating relative to the hub.

Thereby, the rotational torque from the crankshaft is transmitted from the first flywheel to the rotating body 11 via the compression coil spring 17. The rotator 11 receives torque to rotate, and rotationally drives the second flywheel. When the engine torque fluctuates, the fluctuation is absorbed or alleviated by expansion and contraction of the compression coil spring 17 due to elasticity.

A plurality of (four in total in this configuration) centrifugal pendulum dampers 15 are provided along the outer peripheral edge 23 of the rotating body 11 at equal intervals in the circumferential direction. Each of the centrifugal pendulum dampers 15 has a pendulum 25, which is rotatably supported by the rotating body 11 according to the rotating method of the rotating body 11.

The pendulum 25 is a metal mass body, and damps the vibration by the swinging motion. At least a part of the pendulum 25 of this configuration is arranged so as to overlap the compression coil spring 17 of the elastic damper 13 in the direction of the rotation axis of the rotating body 11. The pendulum 25 is swingably supported by the outer peripheral edge 23 of the rotating body 11.

FIG. 2 is a perspective view of the pendulum shown in FIG.
The pendulum 25 has a pair of side plate portions 26A and 26B and a bottom plate portion 28 that connects the sides of the side plate portions 26A and 26B. The side plate portions 26A and 26B have a pair of swing support arms 27 at both ends along the circumferential direction of the rotating body 11, respectively. A shaft hole 29 is formed at the tip of each swing support arm 27.

In the pendulum 25, the space between the pair of side plate portions 26A and 26B serves as a spring accommodating recess 31 that accommodates the compression coil spring 17. Further, the bottom plate portion 28 of the pendulum 25 is arranged outside the compression coil spring 17 in the radial direction of the rotating body 11 when assembled to the rotating body 11.

FIG. 3 is a radial cross-sectional view of the vibration damping device shown in FIG.
Both ends of a support shaft 33 are fixed to a pair of swing support arms 27 facing each other with the outer peripheral edge 23 of the rotating body 11 interposed therebetween. Two support shafts 33 are provided on one pendulum 25. The outer peripheral edge 23 of the rotating body 11 is formed with guide holes 35 through which the respective support shafts 33 pass.

A collar 37 that restricts the movement of the pendulum 25 in the thickness direction of the rotating body is provided between the rotating body 11 and each swing support arm 27. The pendulum 25 is positioned so that the center Dc in the thickness direction of the rotating body 11 coincides with the intermediate position of the pair of swing support arms 27 through which the same support shaft 33 is inserted. The compression coil spring 17 is positioned so that the circular center Cc of the coil cross section passes through the center Dc. Thereby, the centrifugal force is stably applied to the centrifugal pendulum damper 15 and the elastic damper 13 attached to the rotating body 11 in the direction orthogonal to the rotation axis.

FIG. 4 is a partially enlarged front view of the vibration damping device shown in FIG. 1 as seen from the rotation axis direction.
The guide hole 35 is formed in an arc shape centered on the rotation axis of the rotating body 11 and in a shape along a cycloid curve or an epicycloid curve. The pendulum 25 is attached to the outer peripheral edge 23 of the rotating body 11 by penetrating the support shaft 33 into the guide hole 35. As a result, the pendulum 25 can swing with respect to the rotating body 11 within a range in which the support shaft 33 moves along the guide hole 35.

In the vibration damping device 100, the center of gravity of the pendulum 25 is arranged outside the compression coil spring 17 in the radial direction, so that the vibration damping performance is improved as compared with the configuration in which the pendulum 25 having the same weight is arranged inside. That is, the torque that cancels the torque fluctuation increases.

This torque Q is obtained by the following equation.
Q=mω ² RLβ
However,
m: Mass ω: Angular velocity β: Swing angle R: Radial distance from the center of the rotating shaft to the swing center L: Distance from the swing center to the center of gravity of the pendulum 25

In the centrifugal pendulum damper 15, even if the pendulum 25 has the same weight, increasing the distances R and L increases the torque that cancels the torque fluctuation. That is, the damping performance of the damper is improved by increasing the distances R and L.

In the vibration damping device 100 of this configuration, the compression coil spring 17 of the elastic damper 13 is arranged between the rotating body 11 and the centrifugal pendulum damper 15, so that both the vibration damping performance of the centrifugal pendulum damper 15 and the elastic damper 13 are improved. To do.

As shown in FIG. 4, since the centrifugal pendulum damper 15 rotates integrally with the rotating body 11, the vibration damping characteristic of the centrifugal pendulum damper 15 changes depending on the mass of the pendulum 25. Therefore, the mass, the number, and the like of the pendulum 25 are determined based on the amplitude of the vibration input to the centrifugal pendulum damper 15.

For example, in a vehicle that uses an engine as a drive source, when fuel is burned in the engine and torque is output from the crankshaft, the torque is transmitted to the torque converter via the elastic damper 13 and the centrifugal pendulum damper 15. . In this case, the torque output from the crankshaft may fluctuate or the torsional vibration about the rotation axis may occur depending on the characteristics of the engine. For example, when the engine is operated in a region where the combustion efficiency is relatively good, the explosive force increases and the torque fluctuation range becomes relatively large.

When such torque fluctuation occurs in the engine, the elastic damper 13 expands and contracts the compression coil spring 17 to absorb or absorb the vibration. The higher the vibration frequency of the elastic damper 13, the higher the vibration absorbing function. Further, since the elastic damper 13 is configured to damp the vibration by the expansion and contraction of the compression coil spring 17, even if the amplitude of the input torque is relatively large, the vibration can be damped by the design of the spring constant.

Further, in the centrifugal pendulum damper 15, when the input torque fluctuates and the rotating body 11 vibrates in the circumferential direction, the pendulum 25 swings along the guide hole 35 later than the vibration of the rotating body 11. . The swinging motion of the pendulum 25 reduces the vibration depending on the rotation speed of the crankshaft. The centrifugal pendulum damper 15 has different vibration absorption characteristics from the elastic damper 13, does not depend on the frequency of torque fluctuation, but depends on the rotation speed of the rotating shaft. Therefore, vibration of a frequency that cannot be absorbed by the elastic damper 13 is absorbed by the centrifugal pendulum damper 15, and high vibration damping performance is obtained.

In this way, the torque output from the engine is transmitted to the torque converter via the elastic damper 13 and the centrifugal pendulum damper 15 in a vibration-damped state. Then, the torque transmitted from the torque converter to the input shaft of the transmission and output from the transmission is transmitted to the drive wheels to generate a stable driving force for the vehicle.

In the vibration damping device 100 of this configuration, the pendulum 25 is arranged so as to overlap the elastic damper 13 in the direction of the rotation axis of the rotating body 11. Since the pendulum 25 is arranged so as to surround the outside of the elastic damper 13, the pendulum 25 is not limited in its shape. That is, since the pendulum 25 covers the outer side of the elastic damper 13, it does not interfere with the elastic damper 13 even if it is displaced outward in the radial direction. As a result, the pendulum 25 has a higher degree of freedom in designing a shape that projects outward in the circumferential direction and the radial direction.

Further, in the case of the same weight, the pendulum 25 of the present configuration can extend the distance from the rotation center axis line, as compared with the pendulum 25 arranged inward in the radial direction, so that the vibration damping performance is improved.

Further, the pendulum 25 is arranged at the same position as the compression coil spring 17 of the elastic damper 13 in the radial direction of the rotating body 11. However, the pendulum 25 of this configuration is provided so as to surround the compression coil spring 17 and has a concave shape (cradle shape) inside. Therefore, the elastic damper 13 does not interfere in the circumferential direction of the rotating body 11. Therefore, the compression coil spring 17 can be arranged along the outer peripheral edge 23 of the rotating body 11 in an arc shape over a long range. Therefore, the elastic damper 13 can easily improve the damping performance of the elastic damper 13 due to the long compression coil spring 17 along the outer peripheral edge 23 of the rotating body 11.

As described above, the vibration damping device 100 can increase the arc length of the elastic damper 13 while disposing the pendulum 25 outside the elastic damper 13. Moreover, the pendulum 25 and the elastic damper 13 can be housed together in a small space, and the outer shape can be reduced.

Therefore, according to the vibration damping device 100 of the present configuration, it is possible to improve the damping performance of both the centrifugal pendulum damper 15 and the elastic damper 13 while achieving downsizing. In other words, the centrifugal pendulum damper 15 and the elastic damper 13 can both function in an optimal state without sacrificing the damper function of either one, even though they are arranged in a space-saving manner.

Next, a modified example of the vibration damping device 100 described above will be described.
FIG. 5 is a perspective view of a vibration damping device of a modified example.
In the vibration damping device 100A of the modified example, the centrifugal pendulum damper 15A has a pair of swing support plates 39. The pair of swing support plates 39 are formed in an arc shape along the outer peripheral edge 23 of the rotating body 11. The swing support plate 39 includes a base portion 41 fixed to the outer peripheral edge 23 of the rotating body 11 and a support plate portion 43 protruding from the base portion 41 to the outer peripheral edge 23 in the radial direction. The support plate portion 43 is formed thinner than the base portion 41 and avoids interference with the compression coil spring 17.

A guide hole 35 similar to the above is formed in the support plate portion 43. The pendulum 25 is swingably attached to the rotating body 11 with the support shaft 33 penetrating the guide hole 35 of the support plate portion 43. The support shaft 33 is a back surface that penetrates the support plate portion 43 and is prevented from coming off from the support plate portion 43. That is, the support shaft 33 is not penetrated through the pair of swing support plates 39. Accordingly, the pendulum 25 can be arranged at the position where the support shaft 33 overlaps the compression coil spring 17 in the radial direction of the rotating body 11.

According to this vibration damping device 100A, since the support plate portions 43 arranged on both sides of the compression coil spring 17 support the swing support arm 27, contact between the swing support arm 27 and the compression coil spring 17 is avoided. it can. As a result, the pendulum 25 of the centrifugal pendulum damper 15A can be further extended without interfering with the compression coil spring 17 and the vibration damping performance can be further improved.

The swing support plate 39 described above is an example, and the above-described distances R and L can be appropriately changed by using members having other shapes.

The present invention is not limited to the above-described embodiments, and the configurations of the embodiments may be combined with each other, or may be modified and applied by those skilled in the art based on the description in the specification and well-known techniques. The invention is planned and is included in the scope of protection required.

For example, the pendulum 25 is not limited to a configuration including two pairs of swing support arms 27 that face each other with the outer peripheral edge 23 of the rotary body 11 interposed therebetween, and is supported by the rotary body 11 by one set of swing support arms 27. The configuration may be different.
Further, in the above configuration example, the case where the vibration damping device is provided on the flywheel has been described as an example, but the configuration is not limited to this. In addition, the vibration damping device may integrally rotate the rotating body 11 including the elastic damper 13 and the centrifugal pendulum damper 15 on the power transmission path from the engine to the driven member, for example, the front cover and the power transmission shaft of the torque converter. It may be provided in.

As described above, the following items are disclosed in this specification.
(1) A rotating body that receives torque to rotate,
An elastic damper that is provided along the outer peripheral edge of the rotating body, and in which the elastic body expands and contracts in the circumferential direction of the rotating body due to the fluctuation of the torque,
A centrifugal pendulum damper provided on the rotating body, having a pendulum swingable in the rotation direction of the rotating body;
Equipped with
At least a part of the pendulum is arranged so as to overlap the elastic damper in a direction of a rotation axis of the rotating body.
According to this vibration damping device 100, the pendulum 25 of the centrifugal pendulum damper 15 and the elastic damper 13 are both arranged on the outer peripheral edge 23 of the rotating body 11. Therefore, the pendulum 25 extends the distance from the center axis of rotation of the rotating body 11, and the elastic damper 13 can be arranged long along the outer peripheral edge 23 of the rotating body 11. As a result, both vibration damping effects can be enhanced.

(2) In the vibration damping device according to (1), the centrifugal pendulum damper includes at least a pair of rocking members that are rockably supported by the outer peripheral edge of the rotating body so as to sandwich both surfaces in the rotation axis direction. Have supporting arms,
The vibration damping device, wherein the elastic damper is arranged between the pair of swing support arms.
According to this vibration damping device 100, the pendulum 25 of the centrifugal pendulum damper 15 has a pair of swing support arms 27 extending inward in the radial direction of the rotating body 11, and the swing support arms 27 are The outer peripheral edge 23 of the rotating body 11 is swingably supported by the outer peripheral edge 23 so as to sandwich the outer peripheral edge 23 from both sides in the axial direction. That is, the pendulum 25 is formed in a shape with a concave inside (cradle shape), and the elastic damper 13 is included in the space inside the pendulum 25. Therefore, the pendulum 25 has no limitation on its shape and has a high degree of freedom in design. Accordingly, the pendulum 25 and the elastic damper 13 can be accommodated in a small space, and the vibration damping device 100 can be downsized.

11 rotating body 13 elastic damper 15 centrifugal pendulum damper 17 compression coil spring (elastic body)
23 Outer peripheral edge 25 Pendulum 27 Swing support arm 100 Vibration damping device

Claims (2)

A rotating body that receives torque and rotates,
An elastic damper that is provided along the outer peripheral edge of the rotating body, and in which the elastic body expands and contracts in the circumferential direction of the rotating body due to the fluctuation of the torque,
A centrifugal pendulum damper provided on the rotating body, having a pendulum swingable in the rotation direction of the rotating body;
Equipped with
The pendulum, surrounds the outside of the resilient damper, so that the pendulum center of gravity is radially outward of said elastic damper and the resilient damper at least a portion of the pendulum in the direction of the axis of rotation of the rotating body vibration damping device, characterized in that a heavy such so that are arranged in the rotating body. The vibration damping device according to claim 1, wherein a support shaft that swingably supports the pendulum is arranged radially inward of the elastic damper of the rotating body.

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