JP2014114862A - Connection structure of torsional vibration attenuation device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a connection structure of a torsional vibration attenuation device that can maintain the damper characteristic of a torsional vibration reduction device connected on the input side of a fluid coupling in a good state regardless of deformation of the case of the fluid coupling.SOLUTION: In a connection structure of a torsional vibration attenuation device in which in a case 5 of a fluid coupling 2, a pendulum type damper 1 having an inertial mass body reciprocating in the rotation direction of the case 5 by fluctuation of torque input in the case 5 is provided, the pendulum type damper 1 is connected to the outer wall surface of the case 5 through an annular retainer 6 having higher rigidity than that of the case 5.

Description

  The present invention relates to an apparatus for attenuating torsional vibration of a rotating body that receives torque, and more particularly to a torsional vibration damping apparatus configured to attenuate torsional vibration of a rotating body by reciprocating motion of an inertial mass body. The present invention relates to a structure for connecting to a rotating body.

  An example of a torsional vibration damping device is described in Patent Document 1. The apparatus described in Patent Document 1 includes a rotating body that rotates integrally with an output shaft of an engine, and a plurality of rolling chambers that rotatably accommodate inertia mass bodies are formed on the outer periphery of the rotating body. Yes. Of the inner wall surfaces of these rolling chambers, a rolling surface is formed on the outer inner wall surface in the radial direction of the rotating body. When torque fluctuation occurs in the rotating body, the above-described torque fluctuation is attenuated by the inertial mass body reciprocating on the rolling surface according to the torque fluctuation.

JP 2002-340097 A

  As described above, the torque fluctuation can be attenuated by providing the damper mechanism between the engine and the rotating body. However, when a damper mechanism is provided between the engine and a fluid coupling such as a torque converter, the case of the fluid coupling is slightly deformed by the pressure of the fluid that is transmitting torque. For this reason, when the housing of the damper mechanism is directly attached to the case of the fluid coupling, even if there is no initial assembly error, if the case is deformed by fluid pressure, the center axis of the damper mechanism and the output shaft of the engine There is a possibility that a deviation occurs from the central axis, and a change in damper characteristics due to the deviation may occur.

  The present invention has been made paying attention to the above technical problem, and maintains the damper characteristics of the torsional vibration reducing device connected to the input side of the fluid coupling in a good state regardless of deformation of the case of the fluid coupling. It is an object of the present invention to provide a connection structure for a torsional vibration damping device.

  In order to achieve the above object, the invention according to claim 1 is a pendulum type damper having a rolling element that reciprocates in the rotation direction of the case when a torque input to the case fluctuates in the case of the fluid coupling. In the connection structure of the torsional vibration damping device, the pendulum damper is connected to the outer wall surface of the case via a retainer that has a higher rigidity than the case and is formed in an annular shape. It is what.

  According to a second aspect of the present invention, in the first aspect of the present invention, the retainer is connected to the outer wall surface inside the outer peripheral edge in the radial direction of the case. Structure.

  According to the invention of claim 1, since the pendulum damper is attached to the annular retainer having higher rigidity than the case, even if the case is deformed by the centrifugal hydraulic pressure of the fluid coupling, It is possible to prevent or suppress the pendulum damper from being inclined and the center axis thereof deviating from the center axis of the fluid coupling. In other words, since the rolling posture of the inertial mass body in the pendulum damper can be stabilized, when the inertial mass body reciprocates, the inertial mass body collides with other members to generate noise or wear. It is possible to prevent or suppress such a situation. As a result, the durability of the pendulum damper can be improved and the desired vibration damping performance can be obtained. Moreover, since a retainer functions as a rib which reinforces the part to which this is attached, the deformation | transformation of the part which attached the retainer in a case can be prevented or suppressed.

  According to the invention of claim 2, in addition to the same effect as that of the invention of claim 1, the inner portion of the fluid coupling in the radial direction of the case is easily deformed in the direction of its central axis, and in the radial direction. Is difficult to deform. Therefore, if the retainer is connected to the inner side of the outer peripheral edge in the radial direction of the case, even if the retainer moves in the central axis direction along with the deformation of the case, it can be difficult to deform in the radial direction. And this

It is a fragmentary sectional view for explaining an example of the connection structure of the torsional vibration damping device according to the present invention. It is sectional drawing which shows typically the state which the torque converter shown in FIG. 1 is expanding. It is a fragmentary sectional view for explaining other examples of connection structure of a torsional vibration damping device concerning this invention. It is a fragmentary sectional view for explaining other examples of connection structure of a torsional vibration damping device concerning this invention. It is a fragmentary sectional view for explaining other examples of the connection structure of the torsional vibration damping device concerning this invention. It is sectional drawing which shows typically the state which the torque converter shown in FIG. 5 is expanding.

  Next, the present invention will be described more specifically. The torsional vibration damping device according to the present invention is a so-called dynamic damper, which rotates by receiving a torque and reciprocating the inertial mass body with respect to the rotating body that vibrates by the torque fluctuation. It is configured to reduce or dampen vibration. The pendulum motion is generated by slidably connecting the inertial mass body to the rotator by a support shaft or a support pin, or rolls the inertial mass body along a predetermined rolling surface provided on the rotator. It can comprise so that it may produce by doing.

  FIG. 1 is a partial cross-sectional view for explaining an example of a connection structure of a torsional vibration damping device according to the present invention, in which a dynamic damper 1 is interposed between an engine (not shown) and a torque converter 2 which is a fluid coupling. Is provided. The torque converter 2 has a conventionally known structure, and is joined so that the front cover 4 is integrated with the front side of the pump shell 3 with the pump blade attached to the inner peripheral surface, that is, the right side in FIG. The pump shell 3 and the front cover 4 constitute a liquid-tight case 5. Although not shown in detail, the torque converter 2 may include a direct coupling clutch that directly transmits torque from the front cover 4 to the turbine or transmission input shaft by frictional contact with the inner surface of the front cover 4.

  In the example shown in FIG. 1, the dynamic damper 1 is attached to the outer wall surface on the engine side near the center in the radial direction of the front cover 4 via an annular retainer 6. The front cover 4 is deformed as the centrifugal hydraulic pressure of the torque converter 2 increases as will be described later. On the other hand, the retainer 6 is configured to have sufficient strength and rigidity to maintain its shape even when the front cover 4 is deformed. As an example, the retainer 6 includes an annular attachment portion 6A to which the dynamic damper 1 is attached, and a flange 6B that is joined to an outer wall surface on the engine side of the front cover 4. The attachment portion 6A is formed by, for example, a key, a spline, or a serration, and is configured to connect the retainer 6 and the dynamic damper 1 by fitting a part of the dynamic damper 1 thereto. . Thus, since the attaching part 6A of the retainer 6 is formed in three dimensions, the strength and rigidity of the retainer 6 are enhanced by the three-dimensional shape. Moreover, the rigidity and intensity | strength are high compared with the front cover 4 in the example shown here. In addition, you may make the rigidity high by forming the retainer 6 using a material with high rigidity. When the above-described key, spline, serration, or the like is used as the attachment portion 6A, the dynamic damper 1 can be made detachable. The flange 6B is joined to the outer wall surface of the front cover 3 by welding, for example.

  Next, the operation of the torsional vibration damping device having the configuration shown in FIG. 1 will be described. Torque output from the engine is transmitted to the dynamic damper 1 via a crankshaft and a drive plate (not shown). Since the dynamic damper 1 is attached to the retainer 6, torque is transmitted to the front cover 4 of the torque converter 2 through the retainer 6, and the dynamic damper 1 is attached to the pump shell 3 integrated with the front cover 4 and the inner peripheral surface thereof. The pump blade rotates. Oil is supplied to the inside of the case 5, and the pump shell 4 and the pump blade are rotated to generate a spiral flow of oil, which flows toward a turbine (not shown), so that the turbine rotates.

  In the torque converter 2, when the rotational speed difference between the pump and the turbine is large, that is, the speed ratio is small, the direction of the oil flowing out from the turbine is changed by a stator (not shown), and this is supplied to the pump. Torque amplification occurs. Further, when the hydraulic pressure between the direct coupling clutch and the front cover 4 is lower than the hydraulic pressure on the turbine side, the direct coupling clutch moves to the front cover 4 side and the friction material is pressed against the inner surface of the front cover 4. The friction clutch comes into contact and the direct clutch is engaged. When the direct clutch is engaged, the front cover 4, the pump of the torque converter 2 and the turbine rotate integrally, so that the rotational speed of the pump of the torque converter 2 and the rotational speed of the turbine change according to the engine rotational speed. To do. Since the pump and the turbine generate a centrifugal hydraulic pressure corresponding to their rotational speed, the centrifugal hydraulic pressure increases when the engine rotational speed increases.

  When the centrifugal hydraulic pressure is small due to the low engine speed, the case 5 is difficult to expand. When the torque fluctuates in such a state, the inertial mass body in the dynamic damper 1 reciprocates to reduce or attenuate the torque fluctuation, and the dynamic damper 1 eventually attenuates the torsional vibration. On the other hand, when the engine speed increases and the centrifugal hydraulic pressure increases, the case 5 expands somewhat. FIG. 2 shows this state. Since the retainer 6 has higher rigidity than the front cover 4, even if the front cover 4 is deformed, the retainer 6 is hardly deformed. Specifically, even if the retainer 6 moves in the axial direction along with the deformation of the front cover 4 in the axial direction, it is difficult to deform in the radial direction of the central axis. That is, the retainer 6 maintains its own ring shape. Therefore, the deformation of the front cover 4 does not reach the dynamic damper 1, or the deformation of the dynamic damper 1 accompanying the deformation of the front cover 4 is extremely small. That is, the retainer 6 can prevent or suppress the center axis of the dynamic damper 1 from being inclined with respect to the center axis of the engine crankshaft.

  Even if a shock is generated when the direct clutch is operated and engaged with the inner wall surface of the front cover 4, the shock is not directly input to the dynamic damper 1. As a result, it is possible to prevent or suppress a decrease in durability caused by the inertial mass body colliding with another member to generate an abnormal noise, or being damaged or worn. Therefore, even if the torque fluctuates while the case 5 is inflated, the inertial mass body in the dynamic damper 1 can be reciprocated as expected, and the desired vibration damping performance can be obtained. Moreover, in the present invention, since the dynamic damper 1 is detachable from the torque converter 2 via the retainer 6, the workability can be improved when the dynamic damper 1 is assembled or replaced. Can be improved. Further, the productivity of the torsional vibration damping device provided with the dynamic damper 1 can be improved.

  The deformation of the inner portion of the front cover 4 due to the increase in the centrifugal hydraulic pressure described above is large in the central axis direction and small in the radial direction. On the other hand, the deformation of the outer portion of the front cover 4 is small in the central axis direction and large in the radial direction. Therefore, if the highly rigid retainer 6 is attached to the outer peripheral side of the front cover 4, there is a possibility that deformation of the front cover 4 in the radial direction can be prevented or suppressed. FIG. 3 shows an example. A retainer 6 is attached to the outer wall surface on the engine side outside the front cover 4 in the radial direction. Other configurations are the same as those shown in FIG. 1, and therefore, the same reference numerals as those in FIG.

  As described above, since the retainer 6 has higher rigidity than the case 5, when the engine speed increases and the case 5 expands, the retainer 6 functions as a so-called rib that reinforces the front cover 4. As a result, even if the centrifugal hydraulic pressure increases, the deformation of the front cover 4 is suppressed, so that the stress generated at the connecting portion between the front cover 4 and the retainer 6 can be reduced. That is, it is possible to prevent or suppress the occurrence of cracks due to stress concentration at the above-mentioned connection locations. Further, since the retainer 6 has high rigidity and is difficult to deform, even if the front cover 4 is deformed, the deformation of the dynamic damper 1 can be extremely reduced. As a result, the center axis of the dynamic damper 1 and the center axis of the crankshaft can be prevented from being suppressed due to the deformation of the front cover 4, and the desired vibration damping performance of the dynamic damper 1 can be obtained. Can do.

  FIG. 4 is an example in which the retainer 6 is attached to the inside of the front cover 4 in the radial direction. Other configurations are the same as the configuration shown in FIG. 1, and therefore, the same reference numerals as those in FIG. As described above, the deformation of the front cover 4 in the radial direction is large in the central axis direction and small in the radial direction. Therefore, as shown in FIG. 4, if the retainer 6 is attached to the inner peripheral side of the front cover 4, strength and rigidity required for the retainer 6 can be reduced in order to resist stress generated in the front cover 4. . As a result, there is a possibility that the component cost and processing cost of the retainer 6 can be suppressed. In addition, the installation space of the dynamic damper 1 in the radial direction can be expanded, and thereby the degree of freedom in designing the dynamic damper 1 can be improved.

  FIG. 5 shows an example in which a clearance is provided between the front cover 4 and the retainer 6. A groove 7 is formed in the center of the front cover 4 in the radial direction along the shape of the retainer 6, and the retainer 6 is attached to the upper portion of the groove 7 in FIG. 5. The width of the groove 7 in the vertical direction in FIG. 5 is the same as or slightly wider than the width or height of the retainer 6 in the vertical direction in FIG. The depth of the groove 7 in the left-right direction in FIG. 5 is a clearance between the front cover 4 and the retainer 6. Other configurations are the same as those shown in FIG. 1, and therefore, the same reference numerals as those in FIG.

  FIG. 6 is a diagram schematically showing a state in which the case 5 shown in FIG. 5 has expanded. When the centrifugal oil pressure increases and the case 5 expands, the groove 7 enters the lower side of the retainer 6 in FIG. 6 as shown in FIG. That is, by providing the groove 7, the deformation of the case 5 acting as stress on the retainer 6 can be released to the groove 7. Therefore, it is possible to prevent or suppress the retainer 6 from being deformed integrally with the front cover 4. In other words, since a clearance may be provided between the front cover 4 and the retainer 6, the degree of freedom in selecting a method for fixing the retainer 6 can be improved. 5 and FIG. 6, the effect of attaching the dynamic damper 1 to the torque converter 2 via the retainer 6 by providing the clearance as described above, that is, the desired vibration damping performance of the dynamic damper 1 is achieved. You can get enough.

  DESCRIPTION OF SYMBOLS 1 ... Dynamic damper, 2 ... Torque converter, 4 ... Front cover, 6 ... Retainer.

Claims (2)

In the connection structure of the torsional vibration damping device, the case in the fluid coupling is provided with a pendulum type damper having a rolling element that reciprocates in the rotation direction of the case when the torque input to the case varies.
The torsional vibration damping device according to claim 1, wherein the pendulum damper is connected to an outer wall surface of the case via a retainer having a higher rigidity than the case and formed in an annular shape.   The torsional vibration damping device according to claim 1, wherein the retainer is connected to an outer wall surface inside the outer peripheral edge in the radial direction of the case.

Images