JP2019066008A - Torsional vibration reduction device - Google Patents

Abstract

An object of the present invention is to provide a torsional vibration reducing device whose strength can be improved and inexpensive materials can be selected or whose manufacturing cost can be suppressed. A plate (50) is provided in a torque converter (10) and rotates under torque, and a rolling element (46) swingably accommodated in a rolling chamber (48) in the plate (50) and swinging according to a fluctuation of torque. And the first cover 54 and the second cover 56 that rotate by receiving torque and shield the rolling element 46 and the plate 50 from the hydraulic oil in the torque converter 10; The first cover 54 and the second cover 56 are deformed toward the rolling element 46 in the direction of the rotation center line C by the hydraulic pressure of the hydraulic fluid in the torque converter 10 when the rotational speed is equal to or higher than the predetermined rotational speed. And flat portions 54 a and 56 a which are pressing portions for pressing the rolling elements 46. [Selected figure] Figure 5

Description

  The present invention relates to improvement in strength of a torsional vibration reduction device provided inside a torque converter.

  A rotating body, for example, a plate, provided in a torque converter and rotated by receiving a torque, and a rolling element accommodated swingably in a rolling chamber in the plate and swinging according to a fluctuation of the torque, and the torque There is known a torsional vibration reducing device configured to receive and rotate, and to have a cover that shields rolling elements and plates from hydraulic oil in a torque converter. The torsional vibration reduction device of Patent Document 1 is that. In the torsional vibration reducing device of Patent Document 1, when a torque fluctuation occurs, the rolling element is swung in the rolling chamber, whereby the energy of the torque fluctuation is absorbed by the swing of the rolling element. However, in such a torsional vibration reduction device, since there is a gap between the plate and the cover at the outer peripheral portion in the radial direction of the rotation center line of the torque converter, when the torque converter rotates at high speed around the rotation center line. Since a large centrifugal force is applied to the rolling elements and a large load is applied to the rolling chamber that accommodates the rolling elements, that is, the plate, it is necessary to increase the strength of the plate.

  On the other hand, as in the torsional vibration reducing device described in Patent Document 2, it has been proposed to increase the strength by welding the plate and the cover.

JP, 2015-102115, A Unexamined-Japanese-Patent No. 2017-057884

  However, when welding the plate and the cover as in the torsional vibration reduction device described in Patent Document 2, the plate must be made of a material suitable for welding, or the manufacturing cost may be increased. There were issues such as

  The present invention has been made against the background described above, and the object of the present invention is to select inexpensive materials or suppress manufacturing costs in a torsional vibration reducing device provided in a torque converter. Accordingly, it is an object of the present invention to provide a torsional vibration reducing device in which the strength of a rotating body accommodating rolling elements is improved.

  The gist of the present invention resides in a rotating body provided in a torque converter, which receives torque and rotates, and is accommodated in a rolling chamber in the rotating body so as to be able to swing, and swings according to the fluctuation of the torque A torsional vibration reducing device comprising: a rolling element; and a cover that rotates in response to the torque and shields the rolling element and the rotating body from hydraulic oil in the torque converter, the cover being When the speed is equal to or higher than a predetermined rotational speed, the pressure converter has a pressing portion that deforms toward the rolling element in the rotation center line direction of the rotating body by the hydraulic pressure of the hydraulic fluid in the torque converter and presses the rolling element. It is in.

  According to the torsional vibration reducing device of the present invention, when the rotational speed is equal to or higher than a predetermined rotational speed, the cover is rotated in the rotational center line direction of the rotating body by the hydraulic pressure of the hydraulic oil in the torque converter. It has a pressing part which is deformed to the moving body side and presses the rolling element. Therefore, when the rotational speed becomes high, the cover is automatically deformed to press the rolling elements to resist the centrifugal force, and therefore the strength of the rotating body accommodating the rolling elements is not increased more than necessary. good. Therefore, inexpensive materials can be selected, and the manufacturing cost can be suppressed.

It is sectional drawing of the torque converter to which the torsional vibration reduction apparatus which is one Example of this invention was applied. It is the external view which looked at the torsional vibration reduction apparatus of FIG. 1 from the arrow A direction. It is the figure which looked at the torsional vibration reduction apparatus of FIG. 1 from the arrow A direction, Comprising: It is a figure which removed the 1st cover. It is sectional drawing which cut | disconnected the torsional vibration reduction apparatus of FIG. 2 by the cutting plane line IV. It is sectional drawing when the torsional vibration reduction apparatus of FIG. 4 rotates at high speed. FIG. 6 is a characteristic diagram showing the relationship between torque fluctuation and rotational speed of a torque converter. It is sectional drawing of the torsional vibration reduction apparatus which is another Example of this invention. It is sectional drawing when the torsional vibration reduction apparatus of FIG. 7 rotates at high speed. It is sectional drawing of the torsional vibration reduction apparatus which is another Example of this invention. It is sectional drawing when the torsional vibration reduction apparatus of FIG. 9 rotates at high speed.

  In one embodiment of the present invention, the pressing portion is a flat portion facing the rolling surface of the rolling element.

  In one embodiment of the present invention, the pressing portion is a sloped stepped portion facing the outer edge portion of the rolling element.

  In one embodiment of the present invention, a stay is provided between an outer edge portion of the rolling element and an outer peripheral portion of the cover, and the pressing portion acts on the stay to have a diameter of a rotation center line C of the rolling element. It is to press from the outer peripheral side to the inner peripheral side in the direction.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the following embodiments, the drawings are appropriately simplified or modified, and the dimensional ratios and shapes of the respective parts are not necessarily drawn accurately.

  FIG. 1 is a cross-sectional view of a torque converter 10 mounted on a vehicle according to an embodiment of the present invention. The torque converter 10 is a fluid transmission that is provided between an engine (not shown) and a transmission, amplifies the torque of the engine, and transmits the amplified torque to the transmission. The torque converter 10 is rotationally driven about the rotation center line C by transmitting power from the engine.

  The torque converter 10 has a front cover 12 to which power of the engine is input, a pump impeller 14 connected to the front cover 12, and a turbine runner 16 disposed opposite to the pump impeller 14 in the rotation center line C direction. , A lockup clutch 18, and a torsional vibration reducing device 20 provided between the turbine runner 16 and the lockup clutch 18 in the direction of the rotation center line C.

  The front cover 12 is formed in a cylindrical shape with a bottom and is connected to a crankshaft (not shown) of the engine. The open end of the front cover 12 is connected to the outer peripheral end of the pump impeller 14 with respect to the rotation center line C by welding. The pump impeller 14 is configured to include a pump shell 22 formed in an annular shape having an arc cross section, and a plurality of pump blades 24 attached to the pump shell 22. The hydraulic oil is enclosed in a space surrounded by the front cover 12 and the pump shell 22.

  The turbine runner 16 is disposed at a position facing the pump impeller 14 in the rotation center line C direction. The turbine runner 16 is configured to include a turbine shell 28 formed in an annular shape having an arc cross section, and a plurality of turbine blades 30 attached to the turbine shell 28. An inner circumferential portion of the turbine shell 28 is connected to the clutch hub 32 by a rivet 34. The inner peripheral portion of the clutch hub 32 is connected to the input shaft 33 of the transmission by spline fitting so that power can be transmitted.

  A stator 35 is disposed between the pump impeller 14 and the turbine runner 16 opposed to each other in the rotation center line C direction. The inner peripheral portion of the stator 35 is connected to a case which is a non-rotational member (not shown) via a one-way clutch 36 and an intermediate member 38.

  When the pump impeller 14 is rotationally driven by the engine through the front cover 12, a fluid flow of hydraulic fluid in the torque converter 10 is generated, and the fluid flow rotates the turbine runner 16 to transmit power. The stator 35 is disposed to control the fluid flow of the hydraulic fluid.

  The lockup clutch 18 is provided between the front cover 12 and the clutch hub 32 such that power can be transmitted. The lockup clutch 18 includes a lockup piston 40 and a friction material 42 fixed to the outer peripheral side of the lockup piston 40. The lockup piston 40 is disposed adjacent to the front cover 12 in the direction of the rotation center line C. The inner peripheral end of the lockup piston 40 is fitted on the outer peripheral surface of the cylindrically formed portion of the clutch hub 32 so as to be relatively movable in the rotation center line C direction. The friction material 42 is fixed at a position in contact with the front cover 12 when the lockup piston 40 moves toward the front cover 12 in the direction of the rotation center line C.

  The outer peripheral portion of the lockup piston 40 is coupled to the clutch hub 32 via a torsional damper 44 so as to be able to transmit power. The torsional damper 44 is a well-known vibration reduction device that reduces engine torque fluctuations transmitted from the front cover 12 through the lockup clutch 18. The outer peripheral portion of the lockup piston 40 is formed in a cylindrical shape, and a plurality of notches extending in the circumferential direction are formed at an end portion thereof. At the outer peripheral end of the torsional damper 44, a protrusion fitted with the notch is formed. Therefore, the torsional damper 44 can not rotate relative to the lockup piston 40 and can move relative to the rotation center line C direction.

  The lockup clutch 18 moves in the direction of the rotation centerline C in accordance with the pressure difference of the hydraulic pressure acting on both sides in the direction of the rotation centerline C of the lockup piston 40. For example, when the hydraulic pressure on the front cover 12 side of the lockup piston 40 in the rotation center line C direction is higher than the hydraulic pressure on the torsional damper 44 side of the lockup piston 40 in the rotation center line C direction, the lockup piston 40 Is moved in the direction away from the front cover 12 in the direction of the rotation center line C. At this time, since the friction material 42 of the lockup clutch 18 is not pressed against the front cover 12, the lockup clutch 18 is released.

  On the other hand, when the hydraulic pressure on the torsional damper 44 side of the lock-up piston 40 in the rotation center line C direction is higher than the hydraulic pressure on the front cover 12 side in the rotation center line C direction, the lock-up piston 40 has a rotation center line It is moved to the front cover 12 side in the C direction. At this time, since the friction material 42 of the lockup clutch 18 is pressed against the front cover 12, part or all of the power input to the front cover 12 is transmitted through the lockup clutch 18 and the torsional damper 44 to the clutch hub 32. Transmitted to Also, torque fluctuations transmitted through the lockup clutch 18 are reduced by the torsional damper 44.

  A torsional vibration reducing device 20 is provided between the turbine runner 16 and the torsional damper 44 in the direction of the rotation center line C. The torsional vibration reducing device 20 is provided in the torque converter 10 and provided to reduce torque fluctuation of the engine transmitted through the lockup clutch 18 or torsional vibration of a rotating shaft (for example, the clutch hub 32 etc.). It is done. 2 is an external view of the torsional vibration reducing device 20 of FIG. 1 as viewed from the direction of arrow A, and FIG. 3 is a view of the torsional vibration reducing device 20 of FIG. 1 as viewed from the direction of arrow A It shows a state in which the first cover 54 is removed. FIG. 4 is a cross-sectional view of the torsional vibration reducing device 20 of FIG. 2 taken along the cutting line IV, and is a cross-sectional view when the torsional vibration reducing device 20 is not rotating. FIG. 5 is a cross-sectional view when the torsional vibration reducing device 20 of FIG. 4 is rotated at high speed.

  Hereinafter, FIG. 4 which shows the state when the torsional vibration reduction apparatus 20 is not rotating is demonstrated. In the torsional vibration reducing device 20, a plurality of rolling elements 46 (eight in this embodiment) disposed at equal angular intervals in the circumferential direction are formed, and a rolling chamber 48 for swingingly accommodating the rolling elements 46 is formed. And a cover 52 that accommodates the rolling element 46 and the plate 50.

  The cover 52 is configured to include a first cover 54 and a second cover 56 facing each other in the rotation center line C direction.

  The first cover 54 is formed in a disk shape. The second cover 56 has a disc-shaped portion and a cylindrical portion extending from the outer peripheral end of the disc-shaped portion toward the first cover 54 in the direction of the rotation center line C. With the inner peripheral surface of the end of the cylindrical portion of the second cover 56 in contact with the outer peripheral end face of the first cover 54, the entire surface of the second cover 56 and the first cover 54 (full circumference) Are joined by welding across. Therefore, an annular space 62 is formed between the first cover 54 and the second cover 56, and the plate 50 and the rolling elements 46 are accommodated in the annular space 62.

  The plate 50 is formed in a disk shape. The plate 50 is separated from the first cover 54 and the second cover 56 at the outer peripheral end relative to the rotation center line C of the plate 50. Further, the length in the direction of the rotation center line C between the first cover 54 and the second cover 56 on the inner peripheral side of the position where the rolling elements 46 are accommodated in the plate 50 is viewed from the rotation center line C direction. And the length in the direction of the rotation center line C between the first cover 54 and the second cover 56 at a position overlapping the rolling element 46 is shorter. The inner peripheral portions of the first cover 54 and the second cover 56 are fastened and fixed to the clutch hub 32 by rivets 34 inserted into the rivet holes 51 in a state in which the inner peripheral portion of the plate 50 is sandwiched. A first seal member 70 is interposed between the inner periphery of the first cover 54 and the inner periphery of the plate 50, and the first seal member 70 is interposed between the inner periphery of the second cover 56 and the inner periphery of the plate 50. The annular space 62 which is interposed between the second seal member 72 and the first cover 54 and the second cover 56 is isolated from the hydraulic oil in the torque converter 10.

  The plate 50 is formed with a rolling chamber 48 that accommodates the rolling elements 46 in a swingable manner. The rolling chamber 48 is a fan-shaped space formed in the plate 50, and the rolling element 46 is accommodated in this space. The rolling element 46 is a substantially cylindrical member having a thickness in the direction of the center line C of rotation than the plate 50. The rolling element 46 has a circular first surface 46a, a second surface 46b, and a cylindrical outer peripheral surface 46c between the first surface 46a and the second surface 46b, which face each other. A fitting groove 64 for fitting the wall surface of the rolling chamber 48 is formed on the outer peripheral surface 46 c of the rolling element 46. The rolling element 46 can be swung in the circumferential direction along the wall surface of the rolling chamber 48 by the engagement groove 64 engaging the inner circumferential wall surface and the outer circumferential wall surface of the rolling chamber 48. ing. That is, the rolling element 46 can swing along the rolling surface Pr perpendicular to the rotation center line C through the center of the plate 50 in the thickness direction. Further, the fitting groove 64 of the rolling element 46 is engaged with the wall surface of the rolling chamber 48 to prevent the rolling element 46 from coming off the rolling chamber 48. The first surface 46 a of the rolling element 46 faces the first cover 54 and is parallel to the rolling surface Pr. Further, the second surface 46 b of the rolling element 46 is opposed to the disc-like formed portion of the second cover 56 and is parallel to the rolling surface Pr.

  When torque fluctuation is transmitted to the torsional vibration reducing device 20, the rolling element 46 accommodated in the rolling chamber 48 rolls (rocks) along the peripheral wall surface of the rolling chamber 48 according to the torque fluctuation. By doing this, vibration (torsional vibration) due to torque fluctuation is suppressed.

  The first cover 54 has a flat portion 54 a which is a pressing portion facing the first surface 46 a of the rolling element 46. The second cover 56 also has a flat portion 56 a which is a pressing portion facing the second surface 46 b of the rolling element 46. The length between the flat portion 54a of the first cover 54 and the first surface 46a of the rolling element 46 in the direction of the rotation center line C and between the flat portion 56a of the second cover 56 and the second surface 46b of the rolling element 46 The length in the direction of the center line C of rotation is the length L1.

  FIG. 6 is a characteristic diagram showing the relationship between torque fluctuation T (dB) of torque converter 10 and rotational speed N (rpm). In terms of vibration characteristics, as shown in FIG. 6, the torque fluctuation T is large when the rotation speed N of the torque converter 10 is low, and is small when the rotation speed N is high. When the required performance for the torque fluctuation T is T1, the torque fluctuation needs to be reduced when the rotational speed N is lower than the predetermined rotational speed N1, and the rotational speed N is higher than the predetermined rotational speed N1. In the case of high speed, less torque fluctuation reduction is required. Therefore, in the case where rotational speed N of torque converter 10 at which torque fluctuation is relatively small is higher than predetermined rotational speed N1, vibration reduction due to torque fluctuation is not required to a high speed although it is not necessary. Since the centrifugal force of the rolling element 46 generated accompanying it is applied to the plate 50, the plate 50 is required to have a strength that can withstand the centrifugal force.

  Hereinafter, FIG. 5 which shows the state when the torsional vibration reduction apparatus 20 rotates at high speed is demonstrated. The hydraulic pressure of the hydraulic fluid in the torque converter 10 becomes higher on the outer peripheral side in the radial direction of the rotation center line C due to the centrifugal force as the rotation speed N of the torque converter 10 increases. Therefore, the first cover 54 and the second cover 56 are deformed toward the rolling elements 46 by the hydraulic pressure of the hydraulic fluid in the torque converter 10 as the rotation speed N of the torque converter 10 increases. When the rotational speed N of the torque converter 10 is equal to or higher than the predetermined rotational speed N1, as shown in FIG. 5, the flat portion 54a which is the pressing portion of the first cover 54 has a length L1 on the rolling element 46 side. Thus, the first surface 46a of the rolling element 46 is pressed toward the rolling surface Pr. The flat portion 56a, which is a pressing portion of the second cover 56, is deformed toward the rolling element 46 by the length L1 to press the second surface 46b of the rolling element 46 toward the rolling surface Pr. The rolling element 46 is restrained in its movement due to the frictional force due to the flat portion 54a of the first cover 54 and the flat portion 56a of the second cover 56 which are pinched from both sides. That is, since the increase of the centrifugal force applied to the rolling element 46 is reduced by the above-described frictional force, the force applied from the rolling element 46 to the plate 50 is suppressed.

  In the first cover 54 and the second cover 56, when the rotational speed N of the torque converter 10 reaches a predetermined rotational speed N1, the flat portion 54a of the first cover 54 and the flat portion 56a of the second cover 56 The first surface 46 a and the second surface 46 b of the rolling element 46 are pressed by being deformed by the length L 1 toward the rolling element 46 in the rotation center line C direction, ie, the thickness direction of the rolling element 46. The material of the first cover 54 and the second cover 56, the shape (for example, the length L1 of the surface on which the flat portion 54a and the rolling element 46 face each other), etc. are determined in advance by experiments etc. .

  According to the torsional vibration reducing device 20 of the present embodiment, when the rotational speed N of the torque converter 10 is equal to or higher than the predetermined rotational speed N1, the first cover 54 and the second cover 56 The flat portions 54a and 56a are deformed toward the rolling element 46 in the direction of the center line C of rotation by the hydraulic pressure of the above to press the rolling element 46. Therefore, when the rotational speed N of the torque converter 10 is equal to or higher than the predetermined rotational speed N1, the first cover 54 and the second cover 56 are automatically deformed to press the rolling elements 46 to resist the centrifugal force. It is not necessary to increase the strength of the plate 50 that accommodates the rolling elements 46 more than necessary because such a frictional force acts. Therefore, inexpensive materials can be selected, and the manufacturing cost can be suppressed.

  FIG. 7 is a cross-sectional view of a torsional vibration reducing device 80 according to another embodiment of the present invention, which is a cross-sectional view when the torsional vibration reducing device 80 is not rotating. FIG. 8 is a cross-sectional view when the torsional vibration reducing device 80 of FIG. 7 is rotated at high speed. The torsional vibration reducing device 80 is disposed in the torque converter 10 as in the first embodiment described above. In the following description, the same parts as those in the first embodiment described above are denoted by the same reference numerals, and the description will be appropriately omitted.

  Hereinafter, FIG. 7 which shows the state when the torsional vibration reduction apparatus 80 is not rotating is demonstrated. The first cover 54 has a sloped stepped portion 54 b opposed to one outer edge portion 46 d of the rolling element 46. In addition, the second cover 56 has a sloped stepped portion 56 b facing the other outer edge portion 46 d of the rolling element 46. The outer edge portion 46 d of the rolling element 46 is the boundary between the first surface 46 a or the second surface 46 b of the rolling element 46 and the outer circumferential surface 46 c and is the most radial in the radial direction based on the rotation center line C. It is a part on the outer peripheral side. The length in the rotation center line C direction between the first cover 54 and the first surface 46 a of the rolling element 46 and the length in the rotation center line C direction between the second cover 56 and the second surface 46 b of the rolling element 46 In all cases, the length is L1 at a position near the center of the rolling element 46 when viewed from the direction of the rotation center line C, but the length L2 is shorter than the length L1 at the position of the outer edge portion 46d of the rolling element 46 . That is, both the first cover 54 and the second cover 56 gradually come closer to the rolling surface Pr at a position slightly opposite to the outer circumferential position from the position slightly inner circumferential than the outer edge portion 46 d of the rolling element 46. The sloped portion is a step portion 54 b of the first cover 54 and a step portion 56 b of the second cover 56.

  Hereinafter, FIG. 8 which shows the state when the torsional vibration reduction apparatus 80 rotates at high speed is demonstrated. As described above, the hydraulic pressure of the hydraulic fluid in the torque converter 10 increases on the outer circumferential side due to the centrifugal force as the rotation speed N of the torque converter 10 increases. Therefore, the first cover 54 and the second cover 56 are deformed toward the rolling elements 46 by the hydraulic pressure of the hydraulic fluid in the torque converter 10 as the rotation speed N of the torque converter 10 increases. When the rotational speed N of the torque converter 10 is equal to or higher than the predetermined rotational speed N1, as shown in FIG. 8, the step portion 54b which is the pressing portion of the first cover 54 has a length L2 on the rolling element 46 side. Thus, the outer edge 46d of the rolling element 46 is pressed. Further, the stepped portion 56b, which is the pressing portion of the second cover 56, is deformed toward the rolling element 46 by the length L2 to press the other outer edge 46d of the rolling element 46. Therefore, the step portion 54b, which is the pressing portion of the first cover 54, and the step portion 56b, which is the pressing portion of the second cover 56, sandwich the outer edge portion 46d of the rolling element 46 from both sides. It is pressed to the inner peripheral side in the radial direction of the line C. At this time, the rolling element 46 is pressed by the force in the direction opposite to the centrifugal force from the step portion 54 b of the first cover 54 and the step portion 56 b of the second cover 56. The force by the force is weakened by the force by this pressure.

  In the first cover 54 and the second cover 56, when the rotational speed N of the torque converter 10 reaches a predetermined rotational speed N1, the stepped portion 54b of the first cover 54 and the stepped portion 56b of the second cover 56 The first cover 54 and the first cover 54 are configured to be deformed by the length L2 toward the rolling element 46 in the direction of the rotation center line C, ie, the thickness direction of the rolling element 46 to press the outer edge 46 d of the rolling element 46 respectively. The material of the second cover 56, the shape (for example, the length L2 in the direction of the rotation center line C between the first cover 54 and the rolling element 46 at the position of the outer edge 46d of the rolling element 46), etc. And based on this.

  According to the torsional vibration reducing device 20 of the present embodiment, when the rotational speed N of the torque converter 10 is equal to or higher than the predetermined rotational speed N1, the first cover 54 and the second cover 56 In the direction of the center line C of rotation, there are stepped portions 54b and 56b that are deformed toward the rolling element 46 and press the outer edge 46d of the rolling element 46 by the hydraulic pressure of. Therefore, when the rotational speed N of the torque converter 10 is equal to or higher than the predetermined rotational speed N1, the first cover 54 and the second cover 56 are automatically deformed to rotate the outer edge portion 46 d of the rolling element 46 at the rotation center line C. It resists the centrifugal force by pressing to the inner peripheral side in the radial direction of. In the present embodiment, since the first cover 54 and the second cover 56 directly press the outer edge portion 46 d of the rolling element 46 to the inner peripheral side in the radial direction of the rotation center line C, as in the first embodiment described above. It is possible to resist the centrifugal force more stably than the conventional frictional force. Therefore, the strength of the plate 50 that accommodates the rolling elements 46 may not be increased more than necessary. Therefore, inexpensive materials can be selected, and the manufacturing cost can be suppressed.

  FIG. 9 is a cross-sectional view of a torsional vibration reducing device 90 according to still another embodiment of the present invention, which is a cross-sectional view when the torsional vibration reducing device 90 is not rotating. FIG. 10 is a cross-sectional view when the torsional vibration reducing device 90 of FIG. 9 is rotated at high speed. The torsional vibration reducing device 90 is disposed in the torque converter 10 as in the first and second embodiments described above. In the following description, the same reference numerals are given to parts common to the first embodiment and the second embodiment described above, and the description will be appropriately omitted.

  Hereinafter, FIG. 9 which shows the state when the torsional vibration reduction apparatus 90 is not rotating is demonstrated. In the present embodiment, the stay 74 is disposed in the space between the outer edge portion 46 d of the rolling element 46 and the inner peripheral surface of the cylindrical portion of the second cover 56 in the annular space 62. The stay 74 is, for example, a stainless steel stay. In the stay 74, four arm portions are connected by three joint portions 74a, 74b and 74c. The central joint portion 74 a among the three joint portions is fixed to the inner peripheral surface of the cylindrical portion of the second cover 56. At the outer end portions 74d and 74e of the arm portions at both ends of the stay 74, metal fittings 74f and 74g having L-shaped cross sections are attached to face the outer edge portion 46d of the rolling element 46, respectively. The metal fittings 74 f and 74 g face the outer edge portion 46 d of the rolling element 46 in the circumferential direction of the rotation center line C within the range in which the rolling element 46 is swung in the rolling chamber 48. When the torsional vibration reduction device 90 is rotating at a relatively low speed, a centrifugal force is applied to the stay 74 on the outer peripheral side, so as shown in FIG. 9, the non-fixed joint portion 74b and joint portion 74c are shown in FIG. The joint portion 74 b contacts the inner surface of the first cover 54 and the joint portion 74 c contacts the inner surface of the second cover 56 under the upper force. Along with this, the arm portions at both ends of the stay 74 also receive an upper force in the drawing in FIG. 9, and a gap is provided between the outer edge portion 46d of the rolling element 46 and the metal fittings 74f and 74g.

  The first cover 54 has a pressing portion 54 c facing the joint portion 74 b of the stay 74. Further, the second cover 56 has a pressing portion 56 c facing the joint portion 74 c of the stay 74.

  Hereinafter, FIG. 10 which shows the state when the torsional vibration reduction apparatus 90 rotates at high speed is demonstrated. As described above, the hydraulic pressure of the hydraulic fluid in the torque converter 10 increases on the outer circumferential side due to the centrifugal force as the rotation speed N of the torque converter 10 increases. Therefore, the first cover 54 and the second cover 56 are deformed toward the rolling elements 46 by the hydraulic pressure of the hydraulic fluid in the torque converter 10 as the rotation speed N of the torque converter 10 increases. When the rotational speed N of the torque converter 10 is equal to or higher than the predetermined rotational speed N1, as shown in FIG. 10, the pressing portion 54c of the first cover 54 contacts the joint 74b of the stay 74 on the rolling surface Pr side. Press it. The pressing portion 56c of the second cover 56 presses the joint portion 74c of the stay 74 toward the rolling surface Pr. Therefore, the pressing portion 54c of the first cover 54 and the pressing portion 56c of the second cover 56 sandwich and press the joint 74b and the joint 74c of the stay 74 from both sides in the direction of the rotation center line C. Therefore, the joint 74b and the joint 74c of the stay 74 are moved so as to slide inward in the radial direction of the rotation center line C. As a result, the arm portions at both ends of the stay 74 have the rotation center line C. Receiving a force toward the inner circumferential side in the radial direction of The metal fittings 74f and 74g attached to the arm portions at both ends of the stay 74 press the rolling element 46 from the outer peripheral side to the inner peripheral side in the radial direction of the rotation center line C. That is, the pressing portion 54 c of the first cover 54 and the pressing portion 56 c of the second cover 56 press the rolling element 46 from the outer peripheral side to the inner peripheral side in the radial direction of the rotation center line C via the stay 74. At this time, the rolling elements 46 are pressed by the force opposite to the centrifugal force by the brackets 74 f and 74 g attached to the arm portions at both ends of the stay 74, so the centrifugal force applied to the plate 50 from the rolling elements 46 The force is weakened by this pressing force.

  In the first cover 54 and the second cover 56, when the rotational speed N of the torque converter 10 reaches a predetermined rotational speed N1, the pressing portion 54c of the first cover 54 and the pressing portion 56c of the second cover 56 It is deformed toward the rolling element 46 in the rotation center line C direction, that is, in the thickness direction of the rolling element 46, and presses the rolling element 46 from the outer periphery to the inner periphery in the radial direction of the rotation center line C via the stay 74. As a structure, materials, shapes, and the like of the first cover 54 and the second cover 56 are determined in advance by experiments and the like, and are manufactured based on this.

  According to the torsional vibration reducing device 90 of the present embodiment, when the rotational speed N of the torque converter 10 is equal to or higher than the predetermined rotational speed N1, the first cover 54 and the second cover 56 The pressing portions 54c and 56c are deformed toward the rolling element 46 in the direction of the rotation center line C by the hydraulic pressure and press the rolling element 46 from the outer peripheral side to the inner peripheral side in the radial direction of the rotation center line C via the stay 74. Each has. Accordingly, when the rotational speed N of the torque converter 10 is equal to or higher than the predetermined rotational speed N1, the first cover 54 and the second cover 56 are automatically deformed and the rolling elements 46 in the radial direction of the rotation center line C. It resists the centrifugal force by being pressed to the inner peripheral side. In the present embodiment, since the stay 74 is used to reduce the concern of wear between the first cover 54 and the second cover 56 and the rolling elements 46, stability is maintained while maintaining performance over a long period of time It can resist the centrifugal force. Therefore, the strength of the plate 50 that accommodates the rolling elements 46 may not be increased more than necessary. Therefore, inexpensive materials can be selected, and the manufacturing cost can be suppressed.

  Although the embodiments of the present invention have been described in detail with reference to the drawings, the present invention is also applicable in other aspects.

  In the above-described first, second, and third embodiments, the dimensional relationship between the pressing portions 54a, 54b, 54c of the first cover 54 and the rolling elements 46 and the pressing portions 56a, 56b, 56c of the second cover 56 Although the dimensional relationship with the moving body 46 is the same as each other, it is not limited thereto. The shapes of the first cover 54 and the second cover 56 may be determined independently so as to press the rolling element 46. For example, the flat portions 54a and 56a in the first embodiment, the step portions 54b and 56b in the inclined surface shape in the second embodiment, and the pressing portions 54c and 56c in the third embodiment are all either the first cover 54 or the second cover 56. It may be provided in only one or the other.

  In the first, second, and third embodiments described above, the first seal member 70 is interposed between the inner peripheral portion of the first cover 54 and the inner peripheral portion of the plate 50, and the inside of the second cover 56 is Although the second seal member 72 intervenes between the peripheral portion and the inner peripheral portion of the plate 50, the first seal member 70 and the second seal member 72 are not essential components. For example, the inner peripheral portion of the plate 50 is fixed to either the inner peripheral portion of the first cover 54 or the inner peripheral portion of the second cover 56, and the inner portion of the first cover 54 is included so as to enclose the fixed portion. Even if the annular space 62 inside the first cover 54 and the second cover 56 is blocked from the hydraulic oil in the torque converter 10 by welding the circumference and the inner circumference of the second cover 56. good.

  Note that what has been described above is merely an embodiment, and the present invention can be implemented in variously modified and improved forms based on the knowledge of those skilled in the art.

10: Torque converter 20, 80, 90: Torsional vibration reduction device 46: rolling element 48: rolling chamber 50: plate (rotary body)
54: 1st cover (cover)
56: Second cover (cover)

Claims (1)

A rotating body provided in a torque converter, which receives torque and rotates, and a rolling element accommodated swingably in a rolling chamber in the rotating body and swinging according to fluctuation of the torque, and receiving the torque A torsional vibration reduction device comprising: a cover that rotates and rotates the rolling element and the rotating body from hydraulic oil in the torque converter,
When the rotational speed of the cover is equal to or higher than a predetermined rotational speed, the cover is deformed toward the rolling element in the direction of the rotation center line of the rotating body by the hydraulic pressure of the hydraulic fluid in the torque converter to press the rolling element. A torsional vibration reducing device characterized by having a pressing portion.

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