JP2019086009A - Inertia adjustment method of inertia rotor in torque transmission device, and torque transmission device - Google Patents

Abstract

To correct inertia of an inertia rotor so that it is not dispersed, in a torque transmission device in which at least one damper is disposed, and a dynamic damper including the inertia rotor and a dynamic damper spring is provided on a torque transmission passage between a torque input member and a torque output member.SOLUTION: A weight member 80 for adjusting inertia is fixed to an inertia rotor 41 or a recessed portion 81 for adjusting inertia is formed by mechanical processing to the inertia rotor 41 on the basis of a result of execution of inertia measurement of the inertia rotor 41, to adjust the inertia of the inertia rotor 41.SELECTED DRAWING: Figure 1

Description

  The present invention relates to an inertial rotation in a torque transmission device in which at least one damper is interposed in a torque transmission path between a torque input member and a torque output member, and a dynamic damper including an inertial rotating body and a dynamic damper spring is attached. The present invention relates to a method of adjusting the inertia of a body, and a torque transmission device that can suitably execute the method of adjusting the inertia.

  Patent Document 1 discloses a torque converter in which one damper is interposed in a torque transmission path between a clutch piston of a lockup clutch and an output shaft, and a dynamic damper is attached to the torque transmission path.

JP, 2009-293671, A

  In the torque converter disclosed in Patent Document 1 above, the damping performance is improved in the working region of the dynamic damper at the time of torque transmission between the clutch piston and the output shaft as the lockup clutch is engaged. However, due to the inertia variation of the inertial rotating body, which is one component of the dynamic damper, the operating frequency of the dynamic damper may vary, and the originally desired performance may not be sufficiently exhibited.

  The present invention has been made in view of the above circumstances, and an inertia adjustment method of an inertia rotating body in a torque transmission device, which can be corrected so that inertia of the inertia rotating body does not vary, and the inertia adjustment thereof It is an object of the present invention to provide a torque transfer device which is adapted to carry out the method preferably.

  In order to achieve the above object, according to a method of adjusting inertia of an inertial rotating body in a torque transfer device of the present invention, at least one damper is interposed in a torque transfer path between a torque input member and a torque output member In a torque transmission device to which a dynamic damper including a rotary body and a dynamic damper spring is attached, adhesion of a weight member for inertia adjustment to the inertial rotary body or formation of a recess for mechanical inertia adjustment to the inertial rotary body is performed The first feature is to adjust the inertia of the inertial rotating body.

  Further, in addition to the configuration of the first feature, the present invention performs the inertia measurement of the inertial rotating body manufactured aiming to be lower in inertia than the target inertia, and the measurement result based on the measurement result. And a step of fixing the inertia adjusting weight member to the inertia rotating body.

  In the present invention, in addition to the configuration of the first feature, the step of performing the inertia measurement of the inertial rotating body manufactured aiming to become higher inertia than the target inertia, and the inertia based on the measurement result A third feature is to execute the step of forming the inertia adjustment recess on the rotating body by machining.

  The present invention includes the step of measuring the spring constant of the dynamic damper spring in addition to any one of the configurations of the first to third features, and considering the measurement result of the spring constant, the appropriateness of the inertial rotating body The fourth feature is to calculate the amount of inertia.

  According to the present invention, in addition to any one of the configurations of the first to fourth features, the rotational balance of a unit under test assembled including at least the dynamic damper of the torque transfer device or the rotational balance of the inertial rotating body A fifth feature of the present invention is to determine the position of the inertia adjusting weight member or the inertia adjusting recess with respect to the inertial rotating body in consideration of the rotational balance measurement result.

  A torque transfer device according to a sixth aspect of the present invention is the torque transfer device used when performing the inertia adjustment method of the inertial rotating body in the torque transfer device having the configuration according to the fourth aspect, wherein the inertial rotating body is An inertia plate interposed between the dynamic damper spring and a torque transmission rotary member constituting a part of the torque transmission path, and a mass ring fixed to an outer periphery of the inertia plate; The plate is characterized in that notches in which jigs used in the step of measuring the spring constant of the dynamic damper spring are inserted and engaged are formed at a plurality of locations on the outer periphery of the plate.

  Further, according to a seventh torque transmitting device of the present invention, in addition to the configuration of the sixth feature, the torque transmitting device is characterized in that it is attached to the torque converter so as to transmit torque in a connected state of a lockup clutch included in the torque converter. I assume.

  The output hub 29 of the embodiment corresponds to the torque output member of the present invention, the clutch piston 43 of the embodiment corresponds to the torque input member of the present invention, and the holding plates 50 and 51 of the embodiment correspond to the present invention. The fixing jig 90 of the embodiment corresponds to the jig of the present invention, corresponding to the torque transmission rotation member.

  According to the above feature of the present invention, the inertia adjusting weight member is fixed to the inertial rotating body or the inertia adjusting recess is formed on the inertial rotating body by machining based on the inertia measurement result of the inertial rotating body Therefore, it can be corrected so that the inertia of the inertial rotating body does not vary.

  In particular, according to the second feature of the present invention, an inertial rotating body is manufactured with the aim of becoming an inertia lower than the target inertia, and the inertia adjusting weight member is fixed to the inertial rotating body based on the inertia measurement result. Therefore, it suffices to fix only the inertia adjustment weight member in the inertia adjustment, and the inertia adjustment process can be simplified and the cost can be reduced.

  In particular, according to the third feature of the present invention, an inertial rotating body is manufactured aiming at inertia higher than the target inertia, and a recess for inertia adjustment is formed on the inertial rotating body by machining based on the inertia measurement result. Therefore, only the formation of the inertia adjustment recess may be performed in the inertia adjustment, and the inertia adjustment process can be simplified and the cost can be reduced.

  In particular, according to the fourth feature of the present invention, since the appropriate amount of inertia of the inertial rotating body is calculated in consideration of the measurement result of the spring constant of the dynamic damper spring, the dispersion of the damping performance due to the dispersion of the spring constant of the dynamic damper spring It is possible to suppress the occurrence, and to improve the damping performance of the dynamic damper reliably in the necessary region.

  In particular, according to the fifth aspect of the present invention, the position of the inertia adjusting weight member or the inertia adjusting recess relative to the inertial rotating body is determined in consideration of the measurement result of the rotational balance of the unit to be measured including the dynamic damper or the inertial rotating body. As it is determined, inertia correction can be performed simultaneously with rotation balance correction, and inertia correction and rotation balance correction can be performed while avoiding an increase in cost.

  In particular, according to the sixth aspect of the present invention, the inertia plate includes the inertia plate and a mass ring fixed to the outer periphery of the inertia plate, and the notches formed at a plurality of locations on the outer periphery of the inertia plate In addition, since the jig used for measuring the spring constant of the dynamic damper spring is inserted and engaged, simplification of the jig in measuring the spring constant can be achieved, which can contribute to cost reduction.

FIG. 2 is a longitudinal sectional view taken along line 1-1 of FIG. 2 of the torque converter in a state in which the inertia adjusting weight member is fixed to the inertial rotating body. It is the 2-2 line sectional drawing of FIG. 1 in the state which abbreviate | omitted the transmission cover. It is a figure which shows the frequency characteristic of the torque transmission apparatus containing a dynamic damper. It is a longitudinal cross-sectional view which shows the measuring apparatus which measures the inertia of an inertial rotation body. It is a longitudinal cross-sectional view corresponding to FIG. 1 of the torque converter in the state in which the recessed part for inertia adjustment was formed in the inertial rotation body. It is a longitudinal cross-sectional view which shows the measuring apparatus which measures the spring constant of a dynamic damper spring. FIG. 7 is a view on arrow 7 of FIG. 6;

  Hereinafter, an embodiment of the present invention will be described with reference to the attached FIGS. 1 to 7. First, in FIG. 1, the torque converter 10 is disposed to face the pump impeller 11 and the pump impeller 11. A turbine runner 12 and a stator 13 disposed between the pump impeller 11 and the inner peripheral portion of the turbine runner 12, and an arrow 14 is drawn between the pump impeller 11, the turbine runner 12 and the stator 13. As shown, a circulation circuit 15 is formed to circulate the working oil.

  The pump impeller 11 includes a bowl-shaped pump shell 16, a plurality of pump blades 17 provided on the inner surface of the pump shell 16, a pump core ring 18 connecting the pump blades 17, and the inside of the pump shell 16. An oil pump (not shown) for supplying a working oil to the torque converter 10 is interlocked and coupled to the pump hub 19 at a periphery thereof, for example, by a pump hub 19 fixed by welding.

  Further, a wedge-shaped transmission cover 20 covering the turbine runner 12 from the outside is connected to the outer peripheral part of the pump shell 16 by welding, and a ring gear 21 is fixed to the outer peripheral part of the transmission cover 20 by welding. The drive plate 22 is fastened to the ring gear 21. Further, a crankshaft 23 of a vehicle engine E is coaxially fastened to the drive plate 22, and rotational power is input to the pump impeller 11 from the vehicle engine E.

  The turbine runner 12 has a bowl-shaped turbine shell 24, a plurality of turbine blades 25 provided on the inner surface of the turbine shell 24, and a turbine core ring 26 connecting the turbine blades 25.

  The end of the output shaft 27 for transmitting the rotational power from the vehicle engine E to the transmission not shown is a bearing bush 28 in a cylindrical cylindrical support cylinder 20a with the transmission cover 20 integrated in its center. Be supported through. The output shaft 27 is splined to an output hub 29 disposed at a position spaced apart from the pump hub 19 in the axial direction, and a needle thrust bearing 30 is interposed between the output hub 29 and the transmission cover 20. Be disguised.

  The stator 13 includes a stator hub 31 disposed between the pump hub 19 and the output hub 29, a plurality of stator blades 32 provided on the outer periphery of the stator hub 31, and a stator core ring 33 connecting the outer peripheries of the stator blades 32. The thrust bearing 34 is interposed between the pump hub 19 and the stator hub 31, and the thrust bearing 35 is interposed between the output hub 29 and the stator hub 31.

  A one-way clutch 37 is interposed between the stator hub 31 and a stator shaft 36 that rotatably surrounds the output shaft 27 that rotates with the output hub 29. The stator shaft 36 is a transmission case (Not shown) is rotatably supported.

  A clutch chamber 38 communicating with the circulation circuit 15 is formed between the transmission cover 20 and the turbine shell 24. In the clutch chamber 38, the lockup clutch 40, the inertial rotating body 41, and the inertial rotating body A spring holder 42 is accommodated which enables relative rotation within a limited range with respect to 41 and which sandwiches the inner peripheral portion of the inertial rotating body 41 from both sides.

  The lockup clutch 40 has a clutch piston 43 that can be frictionally connected to the transmission cover 20 and switches between a connected state in which the clutch piston 43 is frictionally connected to the transmission cover 20 and a disconnected state in which the frictional connection is released. The inner periphery of the clutch piston 43, which is formed in a disc shape, is slidably supported on the output hub 29 so as to allow axial movement.

  The inside of the clutch chamber 38 is divided by the clutch piston 43 into an inner chamber 38 a on the turbine runner 12 side and an outer chamber 38 b on the transmission cover 20 side, and adjacent to the needle thrust bearing 30. An oil groove 44 formed in the output hub 29 is in communication with the outer chamber 38 b, and the oil groove 44 is in communication with the cylindrical output shaft 27. Further, an oil passage 45 communicating with the inner circumferential portion of the circulation circuit 15 is formed between the pump hub 19 and the stator shaft 36. The oil pump and the oil reservoir (not shown) are alternately connected to the oil groove 44 and the oil passage 45.

  When the vehicle engine E is idling or in a very low speed operating range, hydraulic oil is supplied from the oil groove 44 to the outer chamber 38b, and hydraulic oil is drawn from the oil passage 45. In this state, the outer chamber 38b is Is higher than the pressure in the inner chamber 38a, the clutch piston 43 is pushed to the side away from the inner surface of the transmission cover 20, and the lockup clutch 40 is in the non-connected state. In this state, relative rotation of the pump impeller 11 and the turbine runner 12 is allowed, and the pump impeller 11 is rotationally driven by the vehicle engine E, whereby the hydraulic oil in the circulation circuit 15 is indicated by the arrow 14. Thus, the pump impeller 11, the turbine runner 12 and the stator 13 are circulated in this order in the circulation circuit 15, and the rotational torque of the pump impeller 11 is output via the turbine runner 12, the spring holder 42 and the output hub 29. It is transmitted to the shaft 27.

  In a state in which the torque amplification action is generated between the pump impeller 11 and the turbine runner 12, the reaction force associated therewith is borne by the stator 13, and the stator 13 is fixed by the locking action of the one-way clutch 37. When the torque amplification operation is finished, the stator 13 rotates in the same direction together with the pump impeller 11 and the turbine runner 12 while idling the one-way clutch 37 due to the reversal of the torque direction received by the stator 13.

  When such a torque converter 10 is in the coupling state or approaches the coupling state, the hydraulic oil is supplied from the oil passage 45 to the inner chamber 38a, and the hydraulic oil is derived from the oil groove 44. As a result, the connection between the oil groove 44 and the oil passage 45 and the oil pump and the oil reservoir is switched. As a result, in the clutch chamber 38, the pressure in the inner chamber 38a becomes higher than that in the outer chamber 38b, and the pressure difference causes the clutch piston 43 to be pressed toward the transmission cover 20, and the outer peripheral portion of the clutch piston 43 is the transmission cover. The friction cover 20 is in pressure contact with the inner surface of the bearing 20 and frictionally connected to the transmission cover 20, and the lockup clutch 40 is in a connected state.

  The torque transmitted from the vehicle engine E to the transmission cover 20 when the lockup clutch 40 is in the connected state is the clutch piston 43 as a torque input member and the output hub 29 as a torque output member. Mechanically transmitted to the output shaft 27 via a torque transmission device 39 having a torque transmission device 39. The torque transmission device 39 transmits torque from the clutch piston 43 via the spring holder 42 and the output hub 29. At least one damper, in this embodiment, first and second dampers 47 and 48, is interposed in the torque transfer path 46, and a dynamic damper 49 is attached to the torque transfer path 46. .

  The spring holder 42 is configured such that a pair of holding plates 50, 51, which are spaced apart in the axial direction of the output shaft 27 and arranged coaxially with the output hub 29, are mutually non-rotatably connected to each other. A part of the torque transmission path 46 is formed so as to be sandwiched between the pair of holding plates 50 and 51 and to project radially inward from the holding plates 50 and 51. An inner peripheral portion of the ring plate shaped driven plate 52 and an inner peripheral portion of the turbine shell 24 in the turbine runner 12 rotate together with the output hub 29 so that a plurality of first rivets are formed on the output hub 29. It is fixed at 53.

  In the first damper 47, a plurality of coil-shaped first damper springs 55 held by the clutch piston 43 and arranged at equal intervals in the circumferential direction are the clutch piston 43 and the spring holder. It is interposed between 42.

  An annular accommodation recess 56 is formed on the surface of the outer peripheral portion of the clutch piston 43 opposite to the transmission cover 20, and is accommodated in the accommodation recess 56 at equal intervals in the circumferential direction. A spring holding member 54 for holding the first damper spring 55 with the clutch piston 43 is fixed to the clutch piston 43.

  The spring holding member 54 has a ring plate portion 54 a having an outer periphery substantially corresponding to the inner periphery of the accommodation recess 56 and arranged coaxially with the clutch piston 43, and the second one along the radial direction of the clutch piston 43. It is formed in a circular arc shape in cross section so as to cover the inward side of the first damper spring 55, and is continuously provided at four places spaced equally in the circumferential direction of the outer periphery of the ring plate portion 54a. A spring cover portion 54b which is formed long along the circumferential direction, and the ring plate portion 54a so as to be disposed between the spring cover portions 54b and to project radially outward from the spring cover portion 54b. And the ring plate portion 54 a is integrally formed with the plurality of second rivets 5. In is fixed to the clutch piston 43.

  The spring contact portion 54c is disposed between the plurality of first damper springs 55, and when the lockup clutch 40 is in the disconnected state, the spring contact portion 54c is disposed on both sides thereof. The end of the first damper spring 55 abuts.

  Referring also to FIG. 2, the dynamic damper 49 includes a plurality of, for example, six coils interposed between the spring holder 42, the inertial rotating body 41, the spring holder 42 and the inertial rotating body 41. And a dynamic damper spring 58.

  Spring holding portions 50 a and 51 a for holding the dynamic damper spring 58 are provided at a plurality of, for example, six places spaced equally in the circumferential direction of the pair of holding plates 50 and 51. It is formed to expose the part to the outside. On the other hand, a spring receiving recess 64 for receiving the dynamic damper spring 58 is formed in the inner peripheral portion of the inertia plate 61 corresponding to the spring holding portions 50a and 51a so as to open to the inner peripheral portion of the inertia plate 61. When the lockup clutch 40 is not connected, both ends of the spring accommodation recess 64 along the circumferential direction of the inertia plate 61 abut the both ends of the dynamic damper spring 58.

  The pair of holding plates 50, 51 constituting the spring holder 42 are connected in a relatively non-rotatable manner by a plurality of, for example, six connecting means 59. The connecting means 59 is interposed between the holding plates 50, 51. A cylindrical first spacer 65 to be mounted, and a fourth rivet 66 penetrating the first spacer 65 so as to connect the pair of the holding plates 50 and 51 in a non-rotatable manner. . On the inner peripheral portion of the inertia plate 61, a plurality of connection means accommodation concave portions 67 for accommodating the connection means 59 while allowing relative rotation of the inertia plate 61 and the pair of holding plates 50, 51 are the inertia plate The spring receiving recesses 64 are disposed between the spring receiving recesses 64 in the circumferential direction 61 and formed so as to open to the inner periphery of the inertia plate 61.

  The inertial rotating body 41 has a ring plate-like inertia plate 61 sandwiched between the outer peripheral portions of the pair of holding plates 50 and 51, and a ring-like inertia plate 61 fixed to the inertia plate 61 by a plurality of third rivets 63. It consists of the massing 62. The inertia plate 61 is formed such that its outer peripheral portion protrudes outward in the radial direction from the pair of holding plates 50 and 51, and the mass ring 62 is fixed to the outer peripheral portion of the inertia plate 61. .

  Further, the dynamic damper spring 58 is held by the pair of holding plates 50 and 51, and constitutes the inertia plate 61 which constitutes a part of the inertial rotating body 41 and a part of the torque transmission path 46. It is interposed between a pair of the holding plates 50 and 51 as a torque transmitting and rotating member.

  Further, both end portions of the connection means accommodating concave portion 67 along the circumferential direction of the inertia plate 61 are in contact with the first spacer 65 of the connection means 59 to make the inertia plate 61 and the pair of holding plates 50 and 51 Restrict relative rotation limit.

  The first damper spring 55 of the first damper 47 includes the spring contact portion 54c of the spring holding member 54 fixed to the clutch piston 43 and the pair of holding plates constituting the spring holder 42. 50 and 51, which in this embodiment is interposed between the lockup clutch 40 and the holding plate 50 on the opposite side of the clutch piston 43, the holding plate 50 includes A plurality of claws 68 are integrally provided to be engaged with the plurality of first damper springs 55 so as to sandwich the damper spring 55 with the spring contact portion 54c of the spring holding member 54.

  The claw portion 68 is formed in a bifurcated shape, and the inertia plate 61 is formed with a long hole 69 extending in the circumferential direction of the inertia plate 61 by inserting the claw portion 68. Moreover, the outer peripheral portion of the holding plate 50 is formed to be bent so as to expand to the opposite side to the first damper spring 55, and the claw portion 68 has the same number as the number of the first damper springs 55. Are integrally provided on the holding plate 50 so as to extend from the outer peripheral bent portion of the holding plate 50 in a direction along the axis of the output shaft 27.

  The second damper 48 is interposed between the pair of holding plates 50 and 51 and the driven plate 52 that rotates with the output shaft 27, and a part of the second damper 48 is A plurality of, for example, six second damper springs 70 are held between the pair of holding plates 50 and 51.

  Spring holding portions 50b and 51b for holding the second damper spring 70 are provided at a plurality of, for example, six positions spaced equally in the circumferential direction of the pair of holding plates 50 and 51, the second damper It is formed in such a manner that a part of the spring 70 is exposed to the outside. On the other hand, a spring receiving hole 71 for receiving the second damper spring 70 is formed in the inner peripheral portion of the driven plate 52 corresponding to the spring holding portions 50b and 51b.

  In the inner side of the spring accommodation hole 71 along the radial direction of the pair of holding plates 50, 51, the circumferential direction of the driven plate 52 is equally spaced between the pair of holding plates 50, 51. A cylindrical second spacer 73 is provided, which is provided at a plurality of locations, for example, six locations, and which is inserted into the elongated holes 72 extending in the circumferential direction, and the pair of holding plates 50 and 51 are the second spacers 73. Are connected by a plurality of fifth rivets 74 respectively penetrating the That is, the driven plate 52 can rotate relative to the spring holder 42 within a limited range in which the second spacer 73 moves in the long hole 72.

The setting frequency f (Hz) of the dynamic damper 49 attached to the torque transmission device 39 is k (Nm / deg) as the spring constant of the dynamic damper spring 58, and the inertia of the inertial rotating body 41 is I. When (kgm ² ), it is calculated by the following equation (1): f = (1 / 2π) × (k / I) ^1/2 (1)

  As apparent from the above-mentioned equation (1), when the inertia I of the inertial rotating body 41 changes due to the production variation of the inertial rotating body 41, the setting frequency f of the dynamic damper 49 varies. Therefore, when it is intended that the attenuation factor changes as indicated by the solid line in FIG. 3 according to the engine speed, variations in the attenuation factor occur as indicated by the broken line and the two-dot chain line in FIG. A predetermined damping rate can not be obtained at a predetermined engine speed.

  Therefore, in order to measure the inertia of the inertial rotating body 41 and appropriately adjust the weight of the inertial rotating body 41 according to the measurement result, for example, a measuring device 75 as shown in FIG. 4 is used.

  The measuring device 75 installed on a fixed base 76 includes a movable jig 77 having a fitting protrusion 77 a fitted on the inner periphery of the inertia plate 61 in the inertial rotating body 41 at the upper end, The inertia plate 61 of the inertial rotating body 41 is fixed to the movable jig 77 by a plurality of pressing members 78 provided on the fitting projection 77a, and the movable jig 77 rotates alternately in forward and reverse directions. The inertia of the inertial rotating body 41 is measured.

  The weight adjustment of the inertial rotating body 41 is performed based on the measurement result by the measuring device 75, and as shown in FIG. 1, the weight member 80 for inertia adjustment to the mass ring 62 in the inertial rotating body 41. The inertia adjustment concave portion 81 is formed by mechanical processing on the mass ring 61 in the inertia rotation 41 as shown in FIG. 5, or the inertia rotation of the inertial rotating body 41 is adjusted.

  At this time, a step of executing the inertia measurement of the inertial rotating body 41 manufactured to aim at an inertia lower than the target inertia, and the inertia adjusting weight member on the inertial rotating body 41 based on the measurement result Performing the step of fixing 80, or performing the inertia measurement of the inertial rotating body 41 manufactured for aiming at a higher inertia than the target inertia, and the inertial rotating body based on the measurement result The step of forming the inertia adjustment recess 81 in 41 may be performed.

  By the way, according to the above-mentioned equation (1), the setting frequency f of the dynamic damper 49 is also changed by the spring constant k of the dynamic damper spring 58 in addition to the inertia I of the inertial rotating body 41 If the inertia I is adjusted in consideration of the spring constant k of the dynamic damper spring 58, the inertia I for obtaining the set frequency F can be determined more accurately.

  Therefore, it is desirable to measure the spring constant k of the dynamic damper spring 58 by the spring constant measuring device 85 shown in FIGS. 6 and 7 and adjust the inertia I in consideration of the measurement result.

  In the measurement of the spring constant k in the measuring device 85, at least the dynamic damper 49 of the torque transfer device 39 is assembled to prepare the unit to be measured 84, and the measurement unit 84 is prepared in this embodiment. The unit to be measured 84 excludes the clutch piston 43 to which the spring holding member 54 is fixed and the first damper spring 55 from the torque transmission device 39, and the turbine of the inertia plate 61 and the output hub 29. The runner 12 is fixed and the spring constant k of the dynamic damper spring 58 is measured by the measuring device 85 using the unit to be measured 84.

  The measuring device 85 installed on the fixed base 86 has the length of the inertia plate 61 of the unit to be measured 84 in a posture in which the holding plate 51 of the spring holder 42 is directed to the base 86 side. Movable jig installed on the base 86 having a plurality of fitting holding parts 87a on the outer periphery, which are inserted into the holes 69 and fit on the tip parts of the claws 68 projecting to the base 86 side 87, a support base 88 provided on the base 86 with a stepped portion 88a for mounting the outer peripheral portion of the inertia plate 61 of the unit to be measured 84 on the inner peripheral side upper portion; A plurality of holding jigs 89 provided on the support base 88 so as to suppress floating from the step 88a, and notches 82 formed in a plurality of, for example, four places on the outer periphery of the inertia plate 61 , And a fixing jig 90 protrudingly provided on the step portion 88a so as to be engaged, insertion of the fixing jig 90 into the notch 82, engagement with the inertia plate 61 and thus the inertial rotating body The rotation of the step 41 on the step 88a is prevented.

  In such a measuring device 85, the movable jig 87 raises and lowers and rotates so as to engage and disengage the tip end portion of the claw portion 68 with the fitting holding portion 87a. The spring constant k of the damper spring 58 can be measured, and the proper inertia I of the inertial rotating body 41 is determined in consideration of the measurement result, whereby the inertia adjusting weight member 80 is fixed to the mass ring 62, Alternatively, as shown in FIG. 5, by forming the inertia adjustment recess 81 by machining the mass ring 61 in the inertial rotation 41, the inertia of the inertial rotating body 41 can be adjusted more accurately. .

  When determining the position where the inertia adjusting weight member 80 is fixed to the inertial rotating body 41 or the position where the inertia adjusting recess 81 is formed on the inertial rotating body 41, the rotational balance of the inertial rotating body 41 is set. It is desirable that the rotational balance of the unit to be measured 84 or the inertial rotating body of the torque transmission device 39, which is preferably assembled to include at least the dynamic damper 49 of the torque transmission device 39, be used when measuring the spring constant k. It is desirable to measure the rotational balance of 41 and determine the position of the inertia adjusting weight member 80 or the inertia adjusting recess 81 with respect to the inertial rotating body 41 in consideration of the rotational balance measurement result. That is, as a result of measuring the rotation balance, the inertia adjusting weight member 80 is disposed at a position determined to be a light point in the circumferential direction of the inertial rotating body 41, and the emphasis is on the circumferential direction of the inertial rotating body 41. The inertia adjustment recess 81 may be disposed at a position determined as

  Next, the operation of this embodiment will be described. The inertia adjustment to the inertia rotating body 41 is performed based on the result of performing the inertia measurement of the inertia rotating body 41 in the torque transmission device 39 attached to the torque converter 10. Since the inertia of the inertial rotating body 41 is adjusted by fixing the weight member 80 or forming the inertia adjustment recess 81 by machining on the inertial rotating body 41, the inertia of the inertial rotating body 41 does not vary. It can be corrected as.

  Further, the inertia adjusting weight member 80 is mounted on the inertial rotating body 41 based on the step of performing the inertia measurement of the inertial rotating body 41 manufactured aiming to become lower in inertia than the target inertia and the measurement result. When the step of fixing is performed, only the fixing of the inertia adjusting weight member 80 may be performed in the inertia adjustment, and the inertia adjusting step can be simplified and the cost can be reduced.

  In addition, based on the step of performing the inertia measurement of the inertial rotating body 41 manufactured to aim at an inertia higher than the target inertia, and based on the measurement result, machine the recess 81 for inertia adjustment in the inertial rotating body 41 When the forming process is performed, only the formation of the inertia adjustment recess 81 may be performed in the inertia adjustment, and the inertia adjustment process can be simplified and the cost can be reduced.

  Further, the step of measuring the spring constant of the dynamic damper spring 58 is executed, and the proper inertia amount of the inertial rotating body 41 is calculated in consideration of the measurement result of the spring constant. The occurrence of variations in performance can be suppressed, and the damping performance of the dynamic damper 49 can be reliably improved in the necessary region.

  Further, the rotational balance of the unit under test 84 assembled including the dynamic damper 49 in the torque transfer device 39 or the rotational balance of the inertial rotating body 41 is measured, and the inertial rotation is taken into consideration in consideration of the measurement result of the rotational balance. If the position of the inertia adjusting weight member 80 or the inertia adjusting recess 81 with respect to the body 41 is determined, the inertia correction can be performed simultaneously with the rotation balance correction, and the inertia correction and the rotation balance can be performed while avoiding an increase in cost. You can make corrections.

  In addition, the inertia rotating body 41 is fixed to the outer periphery of the inertia plate 61 and the inertia plate 61 in which the dynamic damper spring 58 is interposed between the holding plates 50 and 51 forming a part of the torque transmission path 46. And a mass jig 62, and a fixing jig 90 used in the step of measuring the spring constant of the dynamic damper spring 58 is inserted and engaged at a plurality of locations on the outer periphery of the inertia plate 61. Since the notched portion 82 is formed, the jig in the measurement of the spring constant can be simplified, which can contribute to cost reduction.

DESCRIPTION OF SYMBOLS 10 ... Torque converter 29 ... Output hub 39 which is a torque output member ... Torque transmission apparatus 40 ... Lockup clutch 41 ... Inertia rotation body 43 ... Clutch piston 46 which is a torque input member ... Torque transmission path 47, 48 ... Damper 49 ... Dynamic damper 50, 51 ... Holding plate 58 which is a torque transmission rotating member ... Dynamic damper spring 61 ... Inertia plate 62 ... Mass ring 80 ···· Weight member 81 for inertia adjustment ···· Recession adjustment portion 82 ··· Notch 84 ··· Unit to be measured 90 ··· Fixing jig

Claims (7)

  At least one damper (47, 48) is interposed in a torque transmission path (46) between the torque input member (43) and the torque output member (29), and an inertial rotating body (41) and a dynamic damper spring ( 58. In a torque transmission device provided with a dynamic damper (49) including the 58), a weight member for adjusting inertia to the inertial rotating body (41) based on the result of performing the inertia measurement of the inertial rotating body (41). A torque characterized in that the inertia of the inertial rotating body (41) is adjusted by executing the fixation of (80) or the formation of the inertia adjusting recess (81) by machining on the inertial rotating body (41). Method of adjusting inertia of inertial rotating body in transmission device.   The step of performing the inertia measurement of the inertial rotating body (41) manufactured so as to obtain an inertia lower than the target inertia and the weight member for inertia adjustment on the inertial rotating body (41) based on the measurement result 2. The method for adjusting the inertia of the inertial rotating body in a torque transfer device according to claim 1, further comprising the steps of: (80) fixing.   The step of performing the inertia measurement of the inertial rotating body (41) manufactured so as to obtain an inertia higher than the target inertia, and the inertia adjustment recess (in the inertial rotating body (41) based on the measurement result) The method of adjusting the inertia of the inertial rotating body in a torque transfer device according to claim 1, wherein the step of forming 81) by machining is performed.   4. The method according to claim 1, further comprising the step of measuring a spring constant of the dynamic damper spring (58), wherein an appropriate inertia amount of the inertial rotating body (41) is calculated in consideration of the measurement result of the spring constant. The inertia adjustment method of the inertial rotating body in the torque transfer device according to any one of 3.   Measuring the rotational balance of the unit to be measured (84) assembled including at least the dynamic damper (49) or the rotational balance of the inertial rotating body (41), taking into account the result of the measurement of the rotational balance, The torque transmission according to any one of claims 1 to 4, wherein the position of the inertia adjusting weight member (80) or the inertia adjusting recess (81) with respect to the inertial rotating body (41) is determined. Method of adjusting inertia of inertial rotating body in device.   A torque transfer device used when performing the inertia adjustment method of an inertial rotating body in a torque transfer device according to claim 4, wherein the inertial rotating body (41) is a part of the torque transfer path (46). The inertia plate (61), in which the dynamic damper spring (58) is interposed between the torque transmission and rotation member (50, 51) constituting the body, and the mass ring (61) fixed to the outer periphery of the inertia plate (61) 62), and jigs (90) used in the step of measuring the spring constant of the dynamic damper spring (58) are inserted and engaged at a plurality of locations on the outer periphery of the inertia plate (61) A torque transmission device characterized in that the notched portion (82) is formed.   The torque transmission device according to claim 6, characterized in that the torque converter (10) is attached to the torque converter (10) so as to transmit torque in a connected state of a lockup clutch (40) provided in the torque converter (10).

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