JP6331585B2 - Centrifugal pendulum vibration absorber - Google Patents

Description

  The present invention provides a support member that rotates integrally with a rotating element that is rotated by power from a drive device, and a support member that moves the center of gravity along a predetermined swinging track as the support member rotates. The present invention relates to a centrifugal pendulum type vibration absorber provided with a mass body that is swingably supported.

2. Description of the Related Art Conventionally, a rotational speed adaptive vibration absorber for a shaft that can rotate around an axis includes a hub portion provided with at least one inertial mass member, and the at least one inertial mass member is a hub along a predetermined motion trajectory. What makes it reciprocate with respect to a part is known (for example, refer patent document 1). In this rotational speed adaptive vibration absorber, the motion trajectory has a central position adjusted such that the at least one inertial mass member has the largest spacing from the axis, and from the central position of the at least one inertial mass member. As the displacement increases, it has a radius of curvature that decreases stepwise or monotonically. The radius of curvature of the motion trajectory at the center position is a range from “L” to the distance from the center of curvature, “x” to the excitation vibration order, and “K” from 0.8 to 1.2. Is defined by the equation: R = kL / x ² .

Patent Document 1 discloses that
(1) The motion trajectory is formed by a part of the cycloid.
(2) The motion trajectory has a radius of curvature (R) at the center position on the other hand, with a circle (K) defined by the equation: R = kL / x ² where the radius of curvature (R) is on the other hand k = 1.2 Is in the area (F) defined by the cycloid (Z) defined by the formula at k = 0.8: R = kL / x ² .
(3) The motion trajectory is in the first region of the section (F) in the first section adjacent to the central position, and the first region has its radius of curvature (R) while k = 1.0: the circle defined by R = kL / x ^2, wherein the k = 1.2 in the other: it is an area defined by a circle defined by ^{R = kL / x 2 (K} ).
(4) The motion trajectory is in the second region of the section (F) in the second section adjacent to the first section, and the second region has its radius of curvature (R) while k = 1.0. : Restricted by the circle defined by R = kL / x ² , while the radius of curvature (R) at the central position is limited by the cycloid (Z) defined by the formula: R = kL / x ^{2 at} k = 0.8 It is an area to be done.
Is described.

Japanese Patent No. 3221866

  As the motion trajectory of an inertial mass member having a radius of curvature that decreases stepwise or monotonously as the displacement from the central position increases as described above, for example, a trochoid curve such as epicycloid, epitrochoid or cycloid is adopted. Can be considered. However, the locus of the drawing points defined on a basic circle such as a trochoidal curve or a rolling circle that rolls on a fixed line has cusps (points). For this reason, when the trochoid curve is adopted as the motion trajectory of the inertial mass member, the swing range of the inertial mass member is limited to a range between two cusps. It becomes difficult to increase the deflection angle.

  Accordingly, the main object of the present invention is to increase the deflection angle of the mass body in the centrifugal pendulum type vibration absorber.

The centrifugal pendulum type vibration absorber according to the present invention is:
A support member that rotates integrally with a rotating element that rotates by the power from the drive device, and a swingable by the support member so that the center of gravity moves along a predetermined swinging orbit as the support member rotates. In a centrifugal pendulum type vibration absorber provided with a plurality of mass bodies supported by
The swing trajectory is configured by a trochoid curve and intersects the swing center line of the mass body, and is configured by an arc and connected to a corresponding end point of the first trajectory. And two second tracks located on both sides of one track.

  This centrifugal pendulum type vibration absorber is integrated with the support member by swinging the mass body with respect to the support member so that the center of gravity moves along a predetermined swinging track as the support member rotates. A rotating element having a phase opposite to that of the rotating element is applied to the rotating element. In this centrifugal pendulum type vibration absorber, the rocking trajectory of the mass body is configured by a trochoid curve and intersects with the rocking center line of the mass body, and is configured by an arc and the first trajectory. And two second tracks located on both sides of the first track. In this way, by connecting the second trajectory constituted by the arc to the end points on both sides of the first trajectory constituted by the trochoid curve, the centrifugal pendulum is compared with the case where the swing trajectory is constituted only by the trochoid curve. The deflection angle of the mass body in the type vibration absorber can be further increased.

It is a schematic block diagram which shows the starting apparatus containing the centrifugal pendulum type vibration absorption apparatus by this invention. It is a top view which shows the centrifugal pendulum type vibration absorption apparatus by this invention. It is sectional drawing along the III-III line of FIG. It is an enlarged view which shows the rocking | fluctuation track | orbit of the gravity center of the mass body in the centrifugal pendulum type vibration absorption apparatus by this invention. It is a schematic diagram for demonstrating the procedure which sets the rocking | fluctuation track | orbit of the gravity center of the mass body in the centrifugal pendulum type vibration absorption apparatus by this invention. It is a schematic diagram for demonstrating the other procedure which sets the rocking | fluctuation track | orbit of the gravity center of a mass body in the centrifugal pendulum type vibration absorption apparatus by this invention.

  Next, the form for implementing this invention is demonstrated, referring drawings.

  FIG. 1 is a schematic configuration diagram of a starting device 1 including a centrifugal pendulum vibration absorber 10 according to the present invention. A starting device 1 shown in the figure is mounted on a vehicle equipped with an engine (internal combustion engine) as a prime mover, and power from the engine is transmitted to a transmission which is an automatic transmission (AT) or a continuously variable transmission (CVT). To communicate. In addition to the centrifugal pendulum vibration absorber 10, the starting device 1 includes a front cover (input member) 3 connected to the crankshaft of the engine, and a pump impeller (input side fluid transmission element) 4 fixed to the front cover 3. A turbine runner (output-side fluid transmission element) 5 that can rotate coaxially with the pump impeller 4, a stator 6 that rectifies the flow of hydraulic fluid (working fluid) from the turbine runner 5 to the pump impeller 4, and an input of the transmission For example, a single plate friction lockup clutch (starting) having a damper hub (output member) 7 fixed to the shaft IS, a damper mechanism 8 connected to the damper hub 7, and a lockup piston (not shown) connected to the damper mechanism 8. Clutch) 9.

  The pump impeller 4 and the turbine runner 5 face each other, and a stator 6 is disposed between them so as to rotate coaxially with the pump impeller 4 and the turbine runner 5. The rotation direction of the stator 6 is set to only one direction by the one-way clutch 60. The pump impeller 4, the turbine runner 5, and the stator 6 are a torus that circulates hydraulic oil (fluid) in a fluid transmission chamber (liquid chamber) 2 defined by the front cover 3 and the pump shell of the pump impeller 4. (Annular flow path) is formed and functions as a torque converter having a torque amplification function. In the starting device 1, the stator 6 and the one-way clutch 60 may be omitted, and the pump impeller 4 and the turbine runner 5 may function as a fluid coupling.

  The damper mechanism 8 includes a drive member (input element) 81, an intermediate member (intermediate element) 82, and a driven member (output element) 83 as rotating elements. Further, the damper mechanism 8 is higher than the plurality of first coil springs SP1 disposed between the drive member 81 and the intermediate member 82 as a torque transmission element (torque transmission elastic body), for example, the first coil spring SP1. A plurality of second coil springs (second elastic bodies) SP2 having rigidity (spring constant) and disposed between the intermediate member 82 and the driven member 83 are included.

  The drive member 81 has a plurality of abutting portions that abut against one end of the corresponding first coil spring SP1. The respective contact portions of the drive member 81 are in contact with each other between the first coil springs SP1 adjacent to each other when the damper mechanism 8 is attached. The intermediate member 82 includes a plurality of first contact portions that contact the other end of the corresponding first coil spring SP1, and a plurality of second contact portions that contact the end portion of the corresponding second coil spring SP2. Have Each first contact portion of the intermediate member 82 contacts both of the first coil springs SP1 adjacent to each other when the damper mechanism 8 is attached. The second coil spring SP2 is disposed between two adjacent second contact portions of the intermediate member 82 in the attached state of the damper mechanism 8, and one of the two second contact portions is the second coil. One end of the spring SP2 is in contact with the other end, and the other is in contact with the other end of the second coil spring SP2. The driven member 83 has a plurality of contact portions that contact the corresponding end portions of the second coil springs SP <b> 2, and is fixed to the damper hub 7. The second coil spring SP2 is disposed between two adjacent contact portions of the driven member 83 in the mounted state of the damper mechanism 8, and one of the two contact portions is in contact with one end of the second coil spring SP2. The other is in contact with the other end of the second coil spring SP2.

  In the starting device 1 of the present embodiment, the turbine runner 5 is connected to the driven member 83 that is an output element of the damper mechanism 8 via a plurality of third coil springs (third elastic bodies) SP3. The third coil spring SP3 and the turbine runner 5 constitute a dynamic damper 20. As a result, when the lockup clutch 9 is engaged (including slip control), the vibration of the entire damper mechanism 8 can be satisfactorily absorbed by both the centrifugal pendulum vibration absorber 10 and the dynamic damper 20. Become.

  The lock-up clutch 9 is operated by hydraulic pressure from a hydraulic control device (not shown). By directly connecting the front cover 3 and the drive member 81, the front cover 3 and the damper hub 7, that is, the transmission of the transmission are connected via the damper mechanism 8. Lock-up for connecting the input shaft IS and release of the lock-up are selectively executed. Further, when a predetermined slip control execution condition is satisfied, the rotational speed difference (actual slip speed) between the engine, that is, the front cover 3 and the input shaft IS, that is, the damper hub 7 is matched with the target slip speed (engine ( By executing slip control for controlling the lock-up clutch 9 (so as to cause a difference in rotational speed between the crankshaft) and the drive member 81, the transmission efficiency of the power via the lock-up clutch 9 and the engine (prime engine) Fuel consumption can be improved. Note that the slip control execution condition is satisfied, for example, when lockup is executed by the lockup clutch 9, during acceleration or deceleration of the vehicle, or during transmission shift.

  A lockup piston (not shown) constituting the lockup clutch 9 is supported by the damper hub 7 so as to be movable and rotatable in the axial direction. An annular friction material is attached to the outer peripheral side of the lockup piston and the front cover 3 side, and the drive member 81 is connected to, for example, the outer peripheral portion of the lockup piston. The starting device 1 may be configured to include a multi-plate friction lock-up clutch instead of the single-plate friction lock-up clutch 9.

  As shown in FIGS. 2 and 3, the centrifugal pendulum vibration absorber 10 is connected (fixed) coaxially to a driven member 83 that is a rotating element of the damper mechanism 8 and is supported so as to rotate integrally with the driven member 83. A member (flange) 11 is supported by a support member 11 so that the center of gravity moves along a predetermined swinging track 100 (see FIG. 4), and a plurality of (main) In the embodiment, four mass bodies 12 are included. Further, the centrifugal pendulum type vibration absorber 10 is disposed inside a fluid transmission chamber 2 (liquid chamber) that is defined by the front cover 3 and the pump shell of the pump impeller 4 and accommodates hydraulic oil. The centrifugal pendulum vibration absorber 10 has a plurality of mass bodies 12 with respect to the support member 11 in the fluid transmission chamber 2 filled with hydraulic oil as the support member 11 (driven member 83) rotates. By swinging in the same direction, a vibration having a phase opposite to the vibration of the driven member 83 is applied to the driven member 83 of the damper mechanism 8. As a result, vibration can be absorbed (damped) by the centrifugal pendulum vibration absorber 10 between the lock-up clutch 9 and the damper hub 7 (transmission).

  In the present embodiment, each mass body 12 includes two weights 120 that face each other in the axial direction of the starting device 1 through the support member 11 and are connected to each other by a rivet (not shown) and the two guide rollers 15. Have. As shown in FIG. 2, each weight 120 is a metal plate that extends in a generally arcuate shape along the outer periphery of the support member 11 when viewed from the axial direction of the support member 11, and has a bilaterally symmetric shape. As shown in FIG. 3, the guide roller 15 is obtained by integrating two small diameter rollers 151 and a large diameter roller 152. The small diameter roller 151 protrudes from the both end surfaces in the axial direction of the large diameter roller 152 to the opposite sides.

  The support member 11 is formed with a plurality of first guide notches (first guide portions) 11g so as to correspond to one mass body 12 two (one pair at a time). The pair of first guide cutout portions 11g are formed as, for example, left-right asymmetrical or left-right symmetric elongated holes having a curved line protruding outward in the radial direction of the support member 11 as an axis, and the support member 11 (driven member 83). ) Of the mass body 12 including the center of rotation (axial center) RC of the mass body 12 (symmetrical center line). The large-diameter roller 152 of the corresponding guide roller 15 is rotatably inserted into the first guide notch 11g, and the large-diameter roller 152 of each guide roller 15 is the inner circumference of the corresponding first guide notch 11g. Roll on a surface (basically, the radially outer circumferential surface).

  Further, each weight 120 of the mass body 12 is formed with two (a pair) of second guide cutout portions (second guide portions) 120g. The pair of second guide cutouts 120g is formed as, for example, a left-right asymmetrical or left-right symmetric elongated hole whose axis is a convex curve toward the center of the support member 11, and is symmetrical with respect to the oscillation center line of the mass body 12. Placed in. The small diameter roller 151 of the corresponding guide roller 15 is rotatably inserted into the second guide notch 120g, and the small diameter roller 151 of each guide roller 15 has an inner peripheral surface ( Basically, it rolls on the inner peripheral surface of the radially inner side.

  Thereby, in the centrifugal pendulum type vibration absorber 10, the mass bodies 12 guided by the first and second guide notches 11 g and 120 g are rotated around the pendulum fulcrum as the support member 11 rotates. It can be rotated around the center of gravity of the mass body 12 as it swings within the range. Therefore, according to the centrifugal pendulum type vibration absorber 10, the vibration transmitted to the support member 11 is attenuated not only by swinging around the pendulum fulcrum of the mass body 12 but also by using the rotational moment around the center of gravity of the mass body 12. It becomes possible to do. The first guide cutouts 11g may be formed on the support member 11 so as to correspond to one mass body 12 one by one, and the second guide cutouts 120g are formed on each weight 120 one by one. May be. Further, the centrifugal pendulum type vibration absorber may be configured as a so-called bifilar type device including two arm members that support one mass body so as to be swingable as the support member 11.

  FIG. 4 is an enlarged view showing the swinging orbit 100 of the center of gravity of the mass body 12 in the centrifugal pendulum vibration absorber 10, and FIG. 5 is a schematic diagram for explaining a procedure for setting the swinging orbit 100. As shown in these drawings, the swing track 100 has a first track 101 extending symmetrically with respect to the swing center line L about the swing center line L of the mass body 12, and masses on both sides of the first track 101. And two second trajectories 102 positioned symmetrically with respect to the rocking center line L of the body 12.

  The first track 101 is a trochoidal curve such as an epicycloid, epitrochoid or cycloid that protrudes on the opposite side (radially outward) of the rotation center RC of the support member 11 or the like, that is, a rolling rolling on a basic circle or a constant straight line. A mass of a drawing point defined in a circle (see a broken line in FIG. 5) (in this embodiment, an epicycloid) intersects the oscillation center line L of the mass body 12 at the center in the circumferential direction. Twelve small amplitude regions are defined. In the present embodiment, the intersection between the locus of the center of the rolling circle that draws the trochoidal curve constituting the first trajectory 101 and the oscillation center line L is the pendulum fulcrum PF1 of the first trajectory 101, and the center of gravity is the first trajectory 101. When reciprocating along, the mass body 12 is assumed to swing around the pendulum fulcrum PF1 while changing the radius of rotation.

Further, the trochoid curve forming the first track 101 is such that the mass body 12 swings so that the center of gravity reciprocates within the range of the first track 101 as the support member 11 rotates. It is selected according to the order q _in of vibration from the engine so that the vibration transmitted from the engine as the drive device to the drive member 81 can be damped at the time of lockup (direct connection). Incidentally, the order q _in the vibration of the engine is essentially becomes one corresponding to the number of cylinders of the engine, for example, in the case of three-cylinder engine, in the case of q _in = 1.5,4-cylinder engine, q _in = 2.0.

  On the other hand, the two second tracks 102 are configured by arcs (part of the circumference indicated by a two-dot chain line in FIG. 5) that are convex on the opposite side (radially outward) from the rotation center RC. As shown in FIG. 5, each second track 102 is connected to a corresponding one of the two end points 101 e of the first track 101. Accordingly, the two second tracks 102 are located on both sides of the first track 101 and define a large amplitude region of the mass body 12. Further, the end point 101 e of the first track 101 to which the second track 102 is connected is a cusp of the trochoidal curve that constitutes the first track 101.

  Further, the arc constituting the second trajectory 102 is centered on the intersection IP of the normal line SN perpendicular to the tangent T at the end point 101e (cusp C) of the first trajectory 101 (trochoid curve) and the oscillation center line L. The distance between the intersection point IP and the end point 101e is a radius r. The pendulum fulcrum PF2 of the second trajectory 102 coincides with the intersection IP of the normal line SN perpendicular to the tangent line T of the first trajectory 101 at the end point 101e and the oscillation center line L, and as shown in the figure, the first trajectory 101 Is closer to the rotation center RC of the support member 11 than the pendulum fulcrum PF1.

  The shapes of the first guide cutout portion 11g of the support member 11 and the second guide cutout portion 120g of the mass body 12 (weight 120) are determined based on the swing track 100 set as described above. That is, the first guide notch portion 11g and the second guide notch portion 120g are formed so that the swinging track 100 includes the first and second tracks 101 and 102 as described above. When the mass body 12 does not rotate around the center of gravity as the mass body 12 swings within the swing range, the first guide notch portion 11g and the second guide notch portion 120g What is necessary is just to be made into the long hole which makes a similar curve an axis.

  In the starting device 1 configured as described above, the mass body 12 of the centrifugal pendulum vibration absorber 10 is configured so that the center of gravity moves within the range of the swinging track 100 when the lockup clutch 9 is locked up. Further, the driven member 83 is oscillated with respect to the driven member 83, and a vibration having a phase opposite to the vibration transmitted from the engine to the drive member 81 via the lockup clutch 9 is applied to the driven member 83. Thus, when the lockup clutch 9 is locked up, vibration can be satisfactorily absorbed (damped) between the lockup clutch 9 and the transmission.

  In the centrifugal pendulum type vibration absorber 10, the swinging trajectory 100 of the mass body 12 is configured by a trochoid curve and a first trajectory 101 intersecting the swinging center line L of the mass body 12, respectively. And two second tracks 102 connected to corresponding end points 101e of the first track 101 and positioned on both sides of the first track 101. Furthermore, the end point 101 e of the first track 101 to which each second track 102 is connected coincides with the cusp of the trochoidal curve constituting the first track 101. This makes it possible to increase the deflection angle of the mass body 12 of the centrifugal pendulum type vibration absorber 10 while effectively utilizing the entire range between the two cusps C of the trochoid curve as the oscillation track 100 of the mass body 12. It becomes possible.

  In addition, by connecting the second track 102 formed of an arc to the end points on both sides of the first track 101 that coincides with the cusp C of the trochoidal curve, as shown in FIG. The end point on the opposite side of one orbit) can be brought closer to the oscillation center line L. This makes it possible to bring the end of the mass body 12 closer to the rotation center RC of the support member 11 when the mass body 12 swings most to one side (at the maximum amplitude). Therefore, in the centrifugal pendulum vibration absorber 10, it is possible to satisfactorily prevent the mass bodies 12 that are adjacent to each other and shake in the same direction from colliding with each other while increasing the deflection angle of each mass body 12.

  Furthermore, the arc constituting the second trajectory 102 is centered on the intersection point IP of the normal line SN perpendicular to the tangent line T of the first trajectory 101 at the end point 101e and the oscillation center line L, and the intersection point IP and the end point 101e. Let the distance be radius r. Thereby, the first track 101 and the two second tracks 102 are smoothly continued, and the mass body 12 of the centrifugal pendulum vibration absorber 10 is more smoothly swung with respect to the support member 11 and the driven member 83. Is possible.

FIG. 6 is a schematic diagram for explaining another procedure for setting the swing trajectory of the center of gravity of the mass body in the centrifugal pendulum vibration absorber. Also in the swinging orbit 100B shown in the figure, the first orbit 101B has a trochoidal curve such as epicycloid, epitrochoid, or cycloid that protrudes on the opposite side (radially outward) from the rotation center RC of the support member 11 or the like (see FIG. In the example of FIG. 6, it is constituted by an epicycloid), and as shown in the drawing, the small amplitude region of the mass body is defined by intersecting the oscillation center line L of the mass body at the center in the circumferential direction. The trochoid curve forming the first track 101 also reduces the vibration order transmitted from the engine to the drive member 81 when the lockup clutch 9 is locked up (directly coupled). It is selected according to q _in . In addition, the two second tracks 102B are configured by an arc (part of a circumference indicated by a two-dot chain line in FIG. 6) that protrudes on the side opposite to the rotation center RC (outside in the radial direction). The large amplitude region of the mass body is defined on both sides of the mass body.

  On the other hand, in the swinging track 100B shown in FIG. 6, the two end points 101e of the first track 101 to which each second track 102 is connected are from the cusp C of the trochoidal curve constituting the first track 101 as shown in the figure. Is also determined to be close to the oscillation center line L. The arc constituting the second track 102B is defined by the normal SN and the swing center line L perpendicular to the tangent line T of the first track 101B at the end point 101e located on the swing center line L side of the cusp C. The distance between the intersection point IP and the end point 101e with the intersection point IP as the center is defined as a radius r. Thereby, when the trochoid curve which comprises the 1st track | orbit 101B is the same as what comprises the 1st track | orbit 101 of the above-mentioned rocking track 100, the pendulum fulcrum PF2 of the 2nd track 102B is It is closer to the pendulum fulcrum PF1 of the first track 101B than that of the second track 102 (see the dotted line in FIG. 6).

Here, if the distance from the rotation center of the support member of the centrifugal pendulum type vibration absorber to the pendulum fulcrum is “R”, and the distance (average value) from the pendulum fulcrum to the center of gravity of the mass is “r”, the mass The vibration order q of can generally be expressed as q≈√ (R / r). Therefore, the two end points 101e of the first track 101 to which the second track 102B is connected are moved closer to the oscillation center line L than the cusp C, and the pendulum fulcrum PF2 of the second track 102B is moved to the pendulum fulcrum PF1 of the first track 101B. , The vibration center of the mass body when the center of gravity reciprocates within the range of the first track 101B, and the center of gravity within the entire range of the swing track 100B including the first track 101B and the second track 102B. The deviation from the vibration order of the mass body when reciprocating can be reduced. Therefore, according to the swinging trajectory 100B, while increasing the deflection angle of the mass body, the vibration order of the mass body when the center of gravity moves along the second trajectory 102B is the target vibration order, that is, from the engine. The vibration absorption performance of the centrifugal pendulum vibration absorber 10 can be further improved by approaching the vibration order q _in .

  The starting device 1 described above is configured as a so-called wet starting device, but the starting device according to the present invention is a so-called dry starting device in which a fluid transmission device including a pump impeller, a turbine runner, a stator and the like is omitted. It may be configured as. Furthermore, the dynamic damper 20 of the starting device 1 may be configured to have a dedicated mass body, and may be connected to the intermediate member 82 (intermediate element) and the drive member 81 (input element) of the damper mechanism 8. The starting device 1 may be omitted. Further, the rotating element to which the centrifugal pendulum vibration absorber 10 is connected is not limited to the driven member 83 (output element) of the damper mechanism, but may be the intermediate member 82 or the drive member 81 (input element) of the damper mechanism. Furthermore, the damper mechanism included in the starting device 1 may be, for example, a parallel damper mechanism configured such that a plurality of springs (elastic bodies) spaced apart in the radial direction act in parallel. It may have an intermediate element.

  As described above, the support member that rotates integrally with the rotating element that is rotated by the power from the driving device, and the center of gravity moves along a predetermined swinging track as the support member rotates. In the centrifugal pendulum vibration absorber provided with a plurality of mass bodies swingably supported by a support member, the swing trajectory is configured by a trochoid curve and intersects a swing center line of the mass body. The track includes a track, and two second tracks each formed by an arc and connected to a corresponding end point of the first track and positioned on both sides of the first track.

  This centrifugal pendulum type vibration absorber is integrated with the support member by swinging the mass body with respect to the support member so that the center of gravity moves along a predetermined swinging track as the support member rotates. A rotating element having a phase opposite to that of the rotating element is applied to the rotating element. In this centrifugal pendulum type vibration absorber, the rocking trajectory of the mass body is configured by a trochoid curve and intersects with the rocking center line of the mass body, and is configured by an arc and the first trajectory. And two second tracks located on both sides of the first track. In this way, by connecting the second trajectory constituted by the arc to the end points on both sides of the first trajectory constituted by the trochoid curve, the centrifugal pendulum is compared with the case where the swing trajectory is constituted only by the trochoid curve. The deflection angle of the mass body in the type vibration absorber can be further increased.

  The end point of the first track may be a cusp of the trochoidal curve. This makes it possible to further increase the deflection angle of the mass body while effectively utilizing the entire range between the two cusps of the trochoidal curve as the swing trajectory. In this case, since the tip of the second track (the end point opposite to the first track) can be brought closer to the swing center line, when the mass body swings most to one side (at the maximum amplitude). The end of the mass body can be brought closer to the rotation center of the support member. Therefore, in such a centrifugal pendulum type vibration absorber, the mass bodies that are adjacent to each other and shake in the same direction can be satisfactorily suppressed while increasing the deflection angle of each mass body.

  Further, the end point of the first trajectory may be determined on the swing center line side of the cusp of the trochoidal curve. Thereby, the pendulum fulcrum of the mass body when the center of gravity reciprocates along the second track can be brought closer to the pendulum fulcrum of the mass body when the center of gravity moves back and forth within the range of the first track. As a result, while increasing the deflection angle of the mass body, the vibration order of the mass body when the center of gravity reciprocates within the range of the first trajectory, and the oscillation trajectory including the first trajectory and the second trajectory. The deviation from the vibration order of the mass body when reciprocating within the entire range can be reduced.

  The arc is centered on the intersection of the normal line perpendicular to the tangent at the end point of the first trajectory and the swing center line, and the distance between the intersection and the end point is a radius. Also good. As a result, the first track and the two second tracks can be smoothly continued, and the mass body of the centrifugal pendulum vibration absorber can be swung more smoothly with respect to the support member.

  Further, the trochoidal curve constituting the first trajectory may be an epicycloid.

  Further, the trochoidal curve constituting the first trajectory may be determined according to the order of vibration from the driving device.

  Furthermore, at least one of the support member and the mass body of the centrifugal pendulum vibration absorber is configured to swing the mass body with respect to the support member so that the center of gravity of the mass body moves along the swing track. You may have a guide part which guides.

  And this invention is not limited to the said embodiment at all, and it cannot be overemphasized that a various change can be made within the range of the extension of this invention. Furthermore, the mode for carrying out the invention described above is merely a specific embodiment of the invention described in the column for solving the problem, and is described in the column for means for solving the problem. It is not intended to limit the elements of the invention.

  The present invention can be used in the manufacturing industry of centrifugal pendulum vibration absorbers.

  DESCRIPTION OF SYMBOLS 1 Start device, 2 Fluid transmission chamber, 3 Front cover, 4 Pump impeller, 5 Turbine runner, 6 Stator, 7 Damper hub, 8 Damper mechanism, 9 Lock-up clutch, 10 Centrifugal pendulum type vibration absorber, 11 Support member, 11g 1st Guide notch, 12 mass, 120 weight, 120g Second guide notch, 15 guide roller, 151 small diameter roller, 152 large diameter roller, 20 dynamic damper, 60 one-way clutch, 81 drive member, 82 intermediate member, 83 driven member , 100, 100B swinging track, 101, 101B first track, 101e end point, 102, 102B second track, IS input shaft, PF1, PF2 pendulum fulcrum, RC rotation center, SP1 first coil spring, SP2 second coil spring , SP3 Third Coils Ring.

Claims (7)

A support member that rotates integrally with a rotating element that rotates by the power from the drive device, and a swingable by the support member so that the center of gravity moves along a predetermined swinging orbit as the support member rotates. In a centrifugal pendulum type vibration absorber provided with a plurality of mass bodies supported by
The oscillating trajectory is configured by a trochoid curve and intersects with the oscillating center line of the mass body, and is configured by a part of the circumference and connected to a corresponding end point of the first trajectory. And a centrifugal pendulum type vibration absorber, comprising two second orbits positioned on both sides of the first orbit. The centrifugal pendulum type vibration absorber according to claim 1,
The end point of the first track is a cusp of the trochoidal curve. The centrifugal pendulum type vibration absorber according to claim 1,
The centrifugal pendulum type vibration absorber according to claim 1, wherein the end point of the first track is defined on the swing center line side of the cusp of the trochoidal curve. The centrifugal pendulum type vibration absorber according to claim 2 or 3,
The circumference is centered on an intersection of a normal line perpendicular to a tangent at the end point of the first trajectory and the swing center line, and a distance between the intersection and the end point is a radius. Centrifugal pendulum type vibration absorber. In the centrifugal pendulum type vibration absorber according to any one of claims 1 to 4,
The centrifugal pendulum vibration absorber according to claim 1, wherein the trochoid curve constituting the first trajectory is an epicycloid. In the centrifugal pendulum type vibration absorber according to any one of claims 1 to 5,
The centrifugal pendulum vibration absorber according to claim 1, wherein the trochoid curve constituting the first trajectory is determined according to an order of vibration from the driving device. The centrifugal pendulum vibration absorber according to any one of claims 1 to 6,
At least one of the support member and the mass body has a guide portion that guides the swing of the mass body with respect to the support member so that the center of gravity of the mass body moves along the swing track. A centrifugal pendulum type vibration absorber.

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