JP3645669B2 - Viscous damper mechanism - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a viscous damper mechanism, and more particularly to a viscous damper mechanism for transmitting torque and damping torsional vibration.
[0002]
[Prior art]
For example, in a vehicle, a damper mechanism for absorbing engine torque fluctuation is provided between an engine-side member and a transmission-side member. The damper mechanism is incorporated in the clutch disc assembly and the flywheel assembly. The damper mechanism includes a first rotating member and a second rotating member that can rotate relative to each other, a coil spring that is disposed so as to restrict rotation when both members rotate relative to each other, and friction when both members rotate relatively. Alternatively, it includes a hysteresis torque generating mechanism that generates hysteresis torque by viscous resistance.
[0003]
Such a damper mechanism requires characteristics of a wide torsion angle, a low rigidity, and a small hysteresis torque in order to absorb minute torsional vibrations caused by engine combustion fluctuations. For this purpose, conventionally, a spring member in which a coil spring or a leaf spring is extended in the circumferential direction has been used.
In the damper mechanism disclosed in Japanese Patent Laid-Open No. 6-174011, a bent leaf spring is used instead of the coil spring. A bent leaf spring is formed by bending a long and narrow plate member having a certain width into a wave shape to form a plurality of series spring elements. The bent leaf spring is disposed in an annular fluid chamber formed by the first rotating member and the second rotating member, and transmits torque from the first rotating member to the second rotating member. When torsional vibration is input and both members rotate relative to each other, the bent leaf spring is compressed in the circumferential direction. At this time, the space between the bent leaf spring and the wall surface of the annular fluid chamber is compressed, and viscous resistance is generated by the fluid passing through the gap between the two members.
[0004]
[Problems to be solved by the invention]
In the conventional viscous damper mechanism, the viscous resistance generated between the bent leaf spring and the wall surface of the annular fluid chamber is not so large. However, on the other hand, the viscous damper mechanism used in the flywheel assembly requires a large viscous resistance in a large range of torsion angles. This is because large torque fluctuations are transmitted to the viscous damper mechanism when passing through the resonance point in the low engine speed range (starting or stopping) of the engine. At this time, the bending angle of the low-rigid bent leaf spring is large, and the relative rotation angle between the first rotating member and the second rotating member is large. In this case, it is preferable to quickly attenuate torsional vibration by generating a large viscous resistance.
[0005]
An object of the present invention is to generate a sufficiently large viscous resistance in a viscous damper mechanism.
[0006]
[Means for Solving the Problems]
  A viscous damper mechanism according to a first aspect includes a first rotating member, a second rotating member, an elastic member, a pair of sheet members, and a viscous resistance generating portion. The first rotating member forms a chamber that extends in the circumferential direction and is filled with fluid, and has a first engaging portion that extends into the chamber. The second rotating member has a second engaging portion disposed in a position displaced in the circumferential direction with respect to the first engaging portion in the chamber, and is rotatable relative to the first rotating member. The elastic member extends between the first engaging portion and the second engaging portion in the chamber. The pair of sheet members are arranged on both sides in the circumferential direction of the elastic member in the chamber to support the elastic member, and form a viscous resistance generation space by sealing both sides in the circumferential direction of the elastic member in the chamber. To do. When the pair of sheet members approach each other and the viscous resistance generating space is reducedIncludes a first choke gap in which fluid can move between the viscous resistance generating space and the space outside thereof.Further, the sheet member is formed with a second choke gap that is wider than the first choke gap and through which a fluid can pass between a space between the pair of sheet members and a space on the outer side in the circumferential direction. The viscous damper mechanism further includes a closing member capable of closing the second choke gap according to a change in pressure on both sides in the circumferential direction of the second choke gap.
[0007]
  2. The viscous damper mechanism according to claim 1, wherein, for example, when the first rotating member rotates, the first engaging portion of the first rotating member pushes the elastic member through the sheet member, and the second engaging portion, that is, the second rotation. Torque is transmitted to the member. When torsional vibration is transmitted to the viscous damper mechanism, the first rotating member and the second rotating member rotate relative to each other, and the elastic member moves in the circumferential direction between the first engaging portion and the second engaging portion. Is compressed. At this time, the pair of sheet members approach each other in the circumferential direction. That is, the viscous resistance generation space is compressed by a pair of sheet members, and pressure is generated. At this time, viscous resistance generator1st choke gapFluid flows and viscous resistance is generated.As a result, the torsional vibration is attenuated. Thus, since the viscous resistance generation space sealed by the pair of sheet members is provided, a large viscous resistance can be obtained.Further, in this viscous damper mechanism, for example, when a minute torque fluctuation caused by engine combustion fluctuation is transmitted, the fluid flows through the second choke gap and does not generate a large viscous resistance. This effect is not affected by the torsional angle between the first rotating member and the second rotating member. Next, for example, when a large torque fluctuation at the time of passing through the resonance point is transmitted, the first rotating member and the second rotating member repeatedly perform relative rotation with a large torsion angle. At this time, when the closing member closes the second choke gap, the fluid passes through the first choke gap and generates a large viscous resistance.
[0009]
  Claim2The viscous damper mechanism described in (1) includes a first rotating member, a second rotating member, a plurality of elastic members, a plurality of sheet members, and a viscous resistance generating unit. The first rotating member forms a chamber that extends in the circumferential direction and is filled with a fluid, and has a plurality of first engaging portions arranged to divide the inside of the chamber into a plurality of arc-shaped spaces. The second rotating member has a plurality of second engaging portions arranged in the chamber corresponding to each of the plurality of first engaging portions, and is rotatable relative to the first rotating member. The plurality of elastic members are disposed in each of the plurality of arc-shaped spaces. The plurality of sheet members are arranged on both sides in the circumferential direction of each elastic member to support the elastic member, and form a viscous resistance generation space by sealing both sides in the circumferential direction of the elastic member in the chamber. The viscous resistance generating portion includes a first choke gap through which fluid flows out to the outside in the circumferential direction of the viscous resistance generating space when the sheet members on both sides in the circumferential direction of each elastic member approach each other to reduce the viscous resistance generating space.Further, in this viscous damper mechanism, the sheet member has a second choke gap that is wider than the first choke gap and through which a fluid can pass between the space between the pair of sheet members and the outer circumferential space. Is formed. The viscous damper mechanism further includes a closing member capable of closing the second choke gap according to a change in pressure on both sides in the circumferential direction of the second choke gap.
[0010]
  Claim2In the viscous damper mechanism described in (1), for example, when the first rotating member rotates, the plurality of first engaging portions respectively press the plurality of elastic members to transmit torque to the second engaging portion, that is, the second rotating member. When torsional vibration is transmitted to the viscous damper mechanism, the first rotating member and the second rotating member rotate relative to each other, and the plurality of elastic members are circular between the first engaging portion and the second engaging portion. Compressed in the circumferential direction. At this time, the sheet members arranged on both sides in the circumferential direction of each elastic member move in directions approaching each other, and the viscous resistance generation space is reduced. At this time, the fluid flows out in the circumferential direction through the first choke gap of the viscous resistance generating portion. As a result, viscous resistance is generated and torsional vibration is attenuated. Here, since the viscous resistance generation space where both ends in the circumferential direction are sealed by the sheet member is formed, a large viscous resistance can be obtained.Further, in this viscous damper mechanism, for example, when a minute torque fluctuation caused by engine combustion fluctuation is transmitted, the fluid flows through the second choke gap and does not generate a large viscous resistance. This effect is not affected by the torsional angle between the first rotating member and the second rotating member. Next, for example, when a large torque fluctuation at the time of passing through the resonance point is transmitted, the first rotating member and the second rotating member repeatedly perform relative rotation with a large torsion angle. At this time, when the closing member closes the second choke gap, the fluid passes through the first choke gap and generates a large viscous resistance.
[0011]
  Claim3The viscous damper mechanism described in (1) includes a first rotating member, a second rotating member, a pair of arc-shaped elastic members, a sheet member, and a viscous resistance generating unit. The first rotating member forms an annular chamber filled with fluid and has a pair of first engaging portions that extend into the chamber and divide the annular chamber into a pair of arcuate spaces. The second rotating member has a pair of second engaging portions disposed in the chamber corresponding to the pair of first engaging portions, and is rotatable relative to the first rotating member. The pair of arcuate elastic members is disposed in each of the pair of arcuate spaces. The sheet member is disposed on both sides of the elastic member in the circumferential direction in the chamber to support the elastic member, and forms a viscous resistance generating space by sealing both sides in the circumferential direction of the elastic member in the chamber. The viscous resistance generating portion includes a first choke gap through which fluid flows out to the outside in the circumferential direction of the viscous resistance generating space when the sheet members on both sides in the circumferential direction of each elastic member approach each other to reduce the viscous resistance generating space.Further, in this viscous damper mechanism, the sheet member has a second choke gap that is wider than the first choke gap and through which a fluid can pass between the space between the pair of sheet members and the outer circumferential space. Is formed. The viscous damper mechanism further includes a closing member capable of closing the second choke gap according to a change in pressure on both sides in the circumferential direction of the second choke gap.
[0012]
  Claim3For example, when the first rotating member rotates, torque is transmitted from the pair of first engaging portions to the second engaging portion of the second rotating member via the elastic member. When torsional vibration is transmitted to the viscous damper mechanism, the first rotating member and the second rotating member rotate relative to each other, and the pair of arcuate elastic members are respectively the first engaging portion and the second engaging portion. Is compressed in the circumferential direction. At this time, the sheet members arranged on both sides of each elastic member move in a direction approaching each other, and the viscous resistance generation space is reduced in the circumferential direction. At this time, the fluid flows out in the circumferential direction through the first choke gap of the viscous resistance generating portion. As a result, viscous resistance is generated and torsional vibration is attenuated. Here, since the viscous resistance generation space where both ends in the circumferential direction are sealed by the sheet member is formed, a large viscous resistance can be obtained.Further, in this viscous damper mechanism, for example, when a minute torque fluctuation caused by engine combustion fluctuation is transmitted, the fluid flows through the second choke gap and does not generate a large viscous resistance. This effect is not affected by the torsional angle between the first rotating member and the second rotating member. Next, for example, when a large torque fluctuation at the time of passing through the resonance point is transmitted, the first rotating member and the second rotating member repeatedly perform relative rotation with a large torsion angle. At this time, when the closing member closes the second choke gap, the fluid passes through the first choke gap and generates a large viscous resistance. According to a fourth aspect of the present invention, in the viscous damper mechanism according to any one of the first to third aspects, the second engagement portion and the seat member each have an engagement portion that can be engaged and disengaged in the circumferential direction. ing. In the viscous damper mechanism according to claim 4, when the first rotating member and the second rotating member rotate relative to each other and the elastic member is compressed in the circumferential direction, one of the pair of sheet members is the second engagement member. The joint is engaged from the circumferential direction. Therefore, the sheet member does not move outward in the radial direction even when centrifugal force is applied. Therefore, even if the sheet member slides on the inner peripheral wall surface of the chamber, it is difficult to generate a large sliding resistance.
[0018]
  Claim5In the viscous damper mechanism according to claim 1,4In any of the above, a pair of arcuate plate seals is further provided. The pair of arcuate plate seals is fixed between one end of the sheet member in the radial direction, extends in an arc toward the sheet member on the opposite side of the elastic member, and is disposed between the sheet members disposed on both sides in the circumferential direction of the elastic member. Seal the inner periphery of.
[0019]
  Claim5In the viscous damper mechanism described in 1), since the pair of arcuate plate seals fixed to the sheet member seal the inner peripheral portion between the pair of sheet members, the viscous resistance formed between the pair of sheet members Fluid is difficult to leak from the generation space.
  Claim6In the viscous damper mechanism according to claim 1,5The other ends of the pair of arcuate plate seals overlap in the radial direction.
[0020]
  Claim6In the viscous damper mechanism described in 1), since the other ends of the pair of arcuate plate seals overlap each other in the radial direction, the fluid hardly leaks from the viscous resistance generating space.
  Claim7In the viscous damper mechanism according to claim 1,5Or6The first rotating member includes a pair of disk-shaped portions forming both side walls of the chamber, and the second rotating member includes an annular portion disposed on the inner peripheral side of the first rotating member, and an annular portion. A second engagement portion extending into the chamber. The viscous damper mechanism further includes a pair of annular seal members on the inner peripheral side of the pair of arcuate seal plate members. The pair of annular seal members are disposed between the annular portion and one pair of disk-shaped inner peripheral portions, and between the annular portion and the other inner peripheral portion of the pair of disk-shaped portions, respectively. Has been.
[0021]
  Claim7In the viscous damper mechanism described in 1), the pair of annular seal members ensures the space between the inner peripheral portion of the pair of disk-shaped portions of the first rotating member and the annular portion of the second rotating member, that is, the inner peripheral portion of the chamber. Is sealed. The pair of arcuate plate seal members are strongly pressed against the pair of annular seal members as the distance between the pair of sheet members is reduced, further improving the sealing performance.
[0022]
  Claim8In the viscous damper mechanism according to claim 1,5In any of the above, the first rotating member includes a pair of disk-shaped portions that form both side walls of the chamber, and the second rotating member includes an annular portion disposed on the inner peripheral side of the first rotating member, and an annular shape A second engaging portion extending from the portion into the chamber. The viscous damper mechanism further includes a pair of annular seal members. The pair of annular seal members are formed between the annular portion and one inner peripheral portion of the pair of disc-shaped portions, and between the annular portion and the other inner peripheral portion of the pair of disc-shaped portions. Each is arranged.
[0023]
  Claim8In the viscous damper mechanism described in 1), since the pair of annular seal members are provided between the inner peripheral portion of the pair of disk-shaped portions of the first rotating member and the annular portion of the second rotating member, Increases the sealing performance at the inner periphery.
  Claim9In the viscous damper mechanism according to claim 1,7Or8The pair of annular seal members is immovable in the radial direction with respect to the first and second rotating members. The viscous damper mechanism further includes a limiting member. The restricting member is locked to the pair of annular seal members and engages the elastic member to restrict the outward movement of the elastic member in the radial direction.
[0024]
  Claim9In the viscous damper mechanism described in 1), since the restricting member locked to the pair of annular seal members restricts the movement of the elastic member outward in the radial direction, the elastic member has a radius even if centrifugal force acts. Difficult to move out of direction. As a result, sliding resistance between the elastic member and the inner peripheral wall surface of the chamber is suppressed.
  Claim10In the viscous damper mechanism according to claim 1,9A pair of annular seal members are formed with a plurality of notches extending in the circumferential direction, and both ends of the engaging member extend into the notches.
[0025]
  Claim10In the viscous damper mechanism described in (1), the engaging member is rotatable relative to the pair of annular seal members. Therefore, the movement of the elastic member in the circumferential direction is hardly restricted, and the amount of deflection of the elastic member in the circumferential direction can be set large.
  Claim11In the viscous damper mechanism according to claim 1,10In any of the above, a fluid passage recess having a circumferential width longer than that of the sheet member is formed on the inner wall surface of the chamber corresponding to the sheet member.
[0026]
  Claim11In the viscous damper mechanism described in (1), when the sheet member is overlapped with the fluid passage recess, the fluid communicates with both sides in the circumferential direction of the sheet member via the fluid passage recess. When the pair of sheet members move relative to each other at a position away from the fluid passage recess in the circumferential direction, the fluid flows from the space between the pair of sheet members to the space on both sides in the circumferential direction through the first choke gap, and the flow increases. Generate viscous resistance. In such a structure, by adjusting the position of the fluid passage recess, a large viscous resistance is not generated in a small range of the torsion angle between the first rotating member and the second rotating member, and the torsion angle In a large range, a large viscous resistance can be generated by allowing the fluid to pass through the first choke gap. In that case, the viscous resistance generating space between the pair of sheet members is compressed in the circumferential direction during relative rotation with a large torsion angle between the first rotating member and the second rotating member when passing through the resonance point. After flowing out, when the sheet member passes the vicinity of the fluid passage recess, the fluid is returned between the pair of sheet members through the fluid passage recess. In this way, it is difficult for the fluid to be insufficient in the viscous resistance generation space between the pair of sheet members, and a large viscous resistance can always be generated.
[0027]
  Claim12In the viscous damper mechanism according to claim 1,11In any of the above, a slider is further provided. The slider is disposed between the elastic member and the inner peripheral wall surface of the chamber, and is slidable in the circumferential direction with respect to the outer peripheral inner wall surface.
  Claim12In the viscous damper mechanism described in (1), the slider rotates relative to the chamber together with the elastic member, and slides on the inner peripheral wall surface of the chamber. Thereby, a large sliding resistance is unlikely to occur.
[0028]
  Claim13In the viscous damper mechanism according to claim 1,12In any of the above, a slider is further provided. The slider is disposed between the sheet member and the outer peripheral side inner wall surface of the chamber, and is slidable in the circumferential direction with respect to the outer peripheral side inner wall surface.
  Claim13In the viscous damper mechanism described in (1), the slider rotates relative to the chamber together with the sheet member, and slides on the outer peripheral side inner wall surface of the chamber. As a result, large sliding resistance is unlikely to occur.
[0029]
  Claim14In the viscous damper mechanism according to claim 1,12Or13The slider includes a slider main body and a rotating body that is rotatably locked to the outer peripheral surface of the slider main body and can contact the inner peripheral wall surface of the chamber.
  Claim14In the viscous damper mechanism described in 1), when the slider body moves relative to the outer peripheral side inner wall surface of the chamber, the rotating body moves on the outer peripheral side inner wall surface of the chamber while rotating. By providing such a rotating body, the sliding resistance between the outer peripheral inner wall surface of the chamber and the slider is reduced.
[0030]
  Claim15In the viscous damper mechanism according to claim 1,14, A groove having a length that allows the rotating body to move in the circumferential direction is formed on the outer peripheral surface of the slider body.
  Claim15When the slider body moves in the circumferential direction with respect to the outer peripheral inner wall surface of the chamber, the rotating body contacts the outer peripheral inner wall surface of the chamber and rotates in the circumferential direction while rotating. Moving. Thereby, the sliding resistance between the outer peripheral side inner wall surface of the chamber and the slider is further reduced. When the rotating body moves to one end in the circumferential direction of the groove of the slider body and further moves relative to the chamber, the rotating body is difficult to rotate and move in the circumferential direction with respect to the slider body. The sliding resistance between the inner wall surface and the slider increases.
[0031]
  Claim16In the viscous damper mechanism according to claim 1,14Or15The rotating body is a columnar member extending in the axial direction.
  Claim17In the viscous damper mechanism according to claim 1,14Or15, The outer peripheral surface of the slider has a shape along the inner peripheral wall surface of the chamber, and a fluid reservoir recess is formed on the outer peripheral surface of the slider body.
[0032]
  Claim17In the viscous damper mechanism described in (1), the fluid accumulates in the fluid reservoir recess formed on the outer peripheral surface of the slider, whereby the sliding surface is lubricated by the fluid, and the sliding between the slider and the inner peripheral wall surface of the chamber is performed. Dynamic resistance is reduced.
  Claim18In the viscous damper mechanism according to claim 1,17In any of the above, the elastic member is a bent leaf spring in which a plurality of leaf spring elements are connected in series.
[0033]
  Claim18In the viscous damper mechanism described in 1), the use of a bent leaf spring makes it possible to obtain a low rigidity characteristic with a wide torsion angle.
  Claim19In the viscous damper mechanism according to claim 1,18The bent leaf spring has a plurality of ring portions and a plurality of lever portions that connect the plurality of ring portions, and the central portion of the plurality of lever portions has a narrower axial width than both ends.
[0034]
  Claim19In the viscous damper mechanism described in (1), since the central portion of the plurality of lever portions has a narrower axial width than both ends, the ability to store elastic energy at the central portion of the lever portion is increased.
[0035]
DETAILED DESCRIPTION OF THE INVENTION
First embodiment
Construction
A flywheel assembly 1 shown in FIGS. 1 to 3 is a device for transmitting torque from a crankshaft 2 on the engine side to a main drive shaft (not shown) on the transmission side. A clutch cover assembly 3 and a clutch disc assembly 14 are attached to the flywheel assembly 1. In the following description, the left side of FIGS. 2 and 3 is the engine side, and the right side is the transmission side.
[0036]
The flywheel assembly 1 mainly includes a first flywheel 4, a second flywheel 5, and a viscous damper 6. The first flywheel 4 is a disk-shaped thick member. The inner peripheral portion of the first flywheel 4 can be fixed to the end surface of the crankshaft 2 by a plurality of crank bolts 12 arranged in the circumferential direction. A bearing 13 is provided on the inner peripheral surface of the first flywheel 4 for rotatably supporting the tip of the main drive shaft of a transmission (not shown). A ring gear 11 is fixed to the outer peripheral surface of the first flywheel 4. Further, an annular projecting portion 4 a projecting toward the transmission side is formed on the outer peripheral portion of the first flywheel 4.
[0037]
The viscous damper 6 is mainly composed of a drive plate 15, a seal plate 16, a driven plate 17, a pair of bent leaf springs 19, and a plurality of sheet members 20. The drive plate 15 is a disk-shaped member that is disposed close to the transmission side of the flywheel 4. The inner peripheral portion of the drive plate 15 is an inner peripheral protruding portion 15a extending to the transmission side. As is apparent from FIGS. 2 and 3, the radial intermediate portion of the drive plate 15 is an annular recess that is recessed toward the engine. The seal plate 16 is a disk-shaped member disposed on the transmission side of the drive plate 15. The outer peripheral portion of the drive plate 15 and the outer peripheral portion of the seal plate 16 are in contact with each other and are fixed to each other by a plurality of bolts 41. In this way, the drive plate 15 and the seal plate 16 function as a first rotating member. Further, the outer peripheral portions of the plates 15 and 16 are fixed to the protruding portion 4 a of the first flywheel 4 by a plurality of bolts 42. An O-ring 28 is disposed between the outer peripheral portions of the drive plate 15 and the seal plate 16. The inner diameter of the seal plate 16 is larger than the inner diameter of the drive plate 15, and an annular gap is formed between the inner periphery of the seal plate 16 and the inner periphery of the drive plate 15. An annular fluid chamber 17 is formed between the annular recess of the drive plate 15 and the seal plate 16. The annular fluid chamber 17 is filled with a fluid such as grease.
[0038]
The driven plate 18 functions as a second rotating member that can rotate relative to the plates 15 and 16, and includes an annular portion 18a and an engagement extending radially outward from the annular portion 18a at two locations facing each other in the radial direction. It consists of the joint part 18b (2nd engaging part). A part of the annular part 18 a is disposed between the drive plate 15 and the inner peripheral edge of the seal plate 16, and the engaging part 18 b is inserted into the annular fluid chamber 17. The engaging portion 18b is shorter in the radial direction than the annular fluid chamber 17, and a large gap is formed between the outer peripheral side inner wall surface (described later) of the chamber 17 and the engaging portion 18b. The engaging portion 18b is bent in the axial direction at both ends in the circumferential direction. Furthermore, as shown in FIG. 4, the engagement recessed part 18c is formed in the circumferential direction both sides of the engaging part 18b. The inner peripheral portion of the second flywheel 5 is fixed to the inner peripheral portion of the annular portion 18 a via a plurality of bolts 43. Both the annular portion 18 a and the inner peripheral portion of the second flywheel 5 are supported by the inner peripheral protruding portion 15 a of the drive plate 15 via bearings 44 so as to be relatively rotatable.
[0039]
The second flywheel 5 has a friction surface 5a against which the friction disk of the clutch disk assembly 14 is pressed on the transmission side.
Next, the sealing structure of the entire annular fluid chamber 17 will be described. Both side walls of the annular fluid chamber 17 are formed by plates 15 and 16, that is, a pair of disk-shaped portions. A cylindrical annular seal 27 is disposed on the outer peripheral side of the annular fluid chamber. The annular seal 27 covers the joint portion between the drive plate 15 and the seal plate 16 and serves as an outer peripheral side inner wall surface of the annular fluid chamber 17. An annular support ring 22 (annular seal member) is disposed between the annular portion 18 a of the drive plate 18 and the drive plate 15. A support ring 22 is disposed between the annular portion 18 a and the seal plate 16. Both support rings 22 engage with the drive plate 15, the seal plate 16, and the driven plate 18 so that they cannot move in the radial direction and can rotate. As shown in FIG. 10, these support rings 22 have a cylindrical portion 22a and a flange 22b extending from one end of the cylindrical portion 22a to the outer peripheral side. The cylindrical portion 22a seals between the plates 15 and 16 and the annular portion 18a. The flanges 22b are engaged with grooves formed in the drive plate 15 and the seal plate 16, respectively. Other structures and functions of the support ring 22 will be described later. The bearing 44 is of a lubricant sealing type, seals the lubricant therein, and seals between the inner peripheral portion of the driven plate 18 and the inner peripheral protruding portion 15a of the drive plate 15. Further, an annular seal member 29 is disposed between the seal plate 16 and the second flywheel 5.
[0040]
In the annular fluid chamber 17 described above, at the position corresponding to the engaging portion 18b of the driven plate 18, the engaging plate 25 (first engaging portion) is respectively connected to the drive plate 15 and the seal plate 16 with the rivet 26. It is fixed by. The engagement plate 25 is shorter in the circumferential direction than the engagement portion 18 b and is close to the inner peripheral side in the annular fluid chamber 17. By the engagement portion 18b and the engagement plate 25, the annular fluid chamber 17 is partitioned into two arc-shaped spaces. A curved leaf spring 19 and a pair of sheet members 20 extending in an arc shape are disposed in each arc space.
[0041]
As shown in detail in FIGS. 29 to 31, the bent leaf spring 19 is obtained by bending a plate member having a predetermined width into a wave shape, and extends long in an arc shape. The bent leaf spring 19 has substantially the same axial width as that of the annular fluid chamber 17, and its axial end is in contact with or close to both side wall surfaces (drive plate 15, seal plate 16). The bent leaf spring 11 forms a plurality of series spring elements including ring portions 51 and 52 and a lever portion 53. The outer ring part 51 and the inner ring part 52 are alternately arranged in the circumferential direction. Both ring parts 51 and 52 have a deviated section whose thickness gradually decreases from the fulcrums 55 and 56 toward the center part. The outer ring part 51 has a larger diameter than the inner ring part 52. The outer ring part 51 and the inner ring part 52 are connected by a lever part 53. The lever part 53 is opened so that the gap becomes wider as it goes outward when viewed from the ring parts 51 and 52. As shown in FIG. 31, the lever portion 53 has an outer peripheral lever fulcrum 55 with a clearance in the circumferential direction in the vicinity of the ring opening portion of the ring portion 51, and in the vicinity of the ring opening portion of the inner peripheral side ring portion 52. An inner peripheral lever fulcrum 56 having a gap in the circumferential direction is provided. As shown in FIG. 30, the lever portion 53 has a constricted shape in which the intermediate portion has a shorter axial width than the both fulcrum 55 and 56 sides, that is, both ends. Fluid can pass smoothly in the circumferential direction through the gap between the constricted portion of the lever portion 53 and the plates 15 and 16. By providing the concave portion 54 in each lever portion 53, the ability to store elastic energy in the lever portion 53 is increased.
[0042]
Sheet members 20 are disposed at both ends in the circumferential direction of the bent leaf spring 19. The sheet member 20 is also a member for supporting and sealing both ends of the bent leaf spring 19 in the circumferential direction to form a viscous resistance generating space 47 between the pair of sheet members 20. The sheet member 20 is in contact with an outer peripheral ring portion 51 and an inner peripheral ring portion 52 at both ends on the outer peripheral side in the circumferential direction. Further, a lever portion 53 extending from the outer circumferential ring portion 51 on the outermost circumferential direction is also in contact with the seat member 20.
[0043]
As shown in FIGS. 6 and 7, the sheet member 20 includes two members 20 </ b> A and 20 </ b> B that are engaged from the axial direction to form an integral member. In this embodiment, the first member 20A and the second member 20B are fixed to each other by pins inserted into the holes 36 formed respectively. As shown in detail in FIGS. 4 to 7, the sheet member 20 is a member that extends long in the annular fluid chamber 17 over substantially the entire radial direction. Further, the sheet member 20 has such a size that both side surfaces and inner peripheral surface thereof form only a slight gap (first choke gap) on the inner wall surface constituting the annular fluid chamber 17. Further, a slider 21 is disposed on the outer peripheral side of the sheet member 20. As apparent from FIG. 3, the slider 21 has an outer peripheral surface that is in contact with the annular seal 27 or a slight gap, and both axial ends are in contact with the drive plate 15 and the seal plate 16 or a slight gap. It is arranged with. In this way, the fluid on both sides in the circumferential direction is blocked by the sheet member 20 and the slider 21, and only the first choke gap can be communicated. That is, the sheet member 20 and the slider 21 function as a sheet member that blocks the space on both sides in the circumferential direction and allows the fluid to move only through the first choke gap. The sheet member 20 and the slider 21 may be an integral sheet member, or the slider 21 may be omitted and the sheet member 20 may extend to the outer peripheral side of the annular fluid chamber and be sealed. The first choke gap is not limited to the gap between the sheet member 20 and the slider 21 and the annular fluid chamber 17. The sheet member 20 may be provided with a hole, a surface groove, or the like communicating in the circumferential direction as the first choke gap.
[0044]
Thus, the viscous resistance generation space 47 is formed between the circumferential directions of the pair of sheet members 20 on both sides in the circumferential direction of each bent leaf spring 19. The viscous resistance generation space 47 is a space whose volume decreases when the pair of sheet members 30 move so as to approach each other. Further, at that time, the fluid flows out from the viscous resistance generating space 47 through the first choke gap to spaces (described later) on both sides in the circumferential direction.
[0045]
The sheet member 20 has a recessed portion 20a on the side facing the engaging portion 18b, and the engaging portion 18b can be inserted into the recessed portion 20a. An engaging convex portion 35 is formed in the concave portion 20 a of the sheet member 20. The engaging convex portion 35 corresponds to the engaging concave portion 18c formed in the engaging portion 18b. In addition, the engagement recessed part may be formed in the sheet | seat member 20, and the engagement convex part may be formed in the engaging part 18b.
[0046]
In the sheet member 20, a small viscous resistance generating mechanism 31 is provided on the radially outer side, that is, on the radially outer portion of the engaging portion 18 b and the engaging plate 25. More specifically, a slider accommodating chamber 32 (first passage) extending in the circumferential direction is formed in the sheet member 20. A passage 33 (second passage) is formed on both sides in the circumferential direction of the slider accommodating chamber 32. The passage 33 has a smaller area than the slider accommodating chamber 32 and is provided at the center thereof. As apparent from FIGS. 6 to 9, the slider accommodating chamber 32 and the passage 33 have a substantially square cross section. An open / close slider 34 (closing member) is disposed in the slider accommodating chamber 32. The open / close slider 34 is movable in the circumferential direction within the slider accommodating chamber 32. As shown in FIG. 9, the open / close slider 34 has a plurality of protrusions 34 a that abut against each side of the slider accommodating chamber 32. A gap 34b (passage portion) between the plurality of protrusions 34a is a passage through which fluid can move in the circumferential direction in the slider accommodating chamber 32. The passage 33 and the gap 34b serve as a second choke gap through which fluid can pass between the viscous resistance generating space 47 and the outer circumferential space. The open / close slider 34 moves in the circumferential direction in the slider accommodating chamber 32 when a pressure difference occurs between both sides of the second choke gap in the circumferential direction. The central portion of the open / close slider 34 is a closed portion that closes the passage 33 at a position where the open / close slider 34 moves most to either side in the circumferential direction in the slider accommodating chamber 32.
[0047]
In each viscous resistance generating space 47, a slider 21 disposed between the bent leaf spring 19 and the sheet member 20 and the annular seal 27 (outer peripheral inner wall surface) is provided. As shown in FIGS. 22 to 25, the slider 21 has a shape along the outer peripheral side inner wall surface of the viscous resistance generating space 47. The slider 21 is composed of a slider body 21a and a rotating pin 21b. The slider body 21a extends long in the circumferential direction. The slider body 21 a has substantially the same axial dimension as the annular fluid chamber 17, and both axial ends are close to or in contact with the plates 15 and 16. Two grooves 21c are formed on the outer peripheral surface of the slider body 21a. The groove 21c extends in the axial direction and has a predetermined width in the circumferential direction. The rotation pin 21b is inserted into each groove 21c, protrudes further outward in the radial direction from the slider body 21a, and contacts the annular seal 27. That is, a slight gap is ensured between the outer peripheral surface of the slider main body 21a and the annular seal 27 even when the slider 21 moves most outward in the radial direction. Furthermore, a recess 21f that is deeper than the groove 21c and wider in the circumferential direction is formed in the groove 21c. Thereby, the periphery of the rotating pin 21b is sufficiently lubricated by the fluid accumulated in the recess 21f. The rotating pin 21b is movable in the circumferential direction while rotating in the groove 21c while being in contact with the annular seal 27.
[0048]
Two engaging portions 21d projecting radially inward are formed on the inner peripheral portion of the slider body 21a. One outer ring portion 51 is disposed between the engaging portions 21d. Thereby, the slider 21 can move integrally with the outer peripheral side ring portion 51. A predetermined gap is secured in the circumferential direction between the engaging portion 21d and the outer peripheral ring portions 51 on both sides. Furthermore, the slider main body 21a has a support portion 21e disposed on the outer side in the radial direction of the two outer peripheral side ring portions 51 on both sides. The support portion 21e supports the outer peripheral ring portions 51 on both sides in the radial direction in a state where the bent leaf spring 19 is compressed in the circumferential direction.
[0049]
The slider 21 provided on the outer peripheral side of the sheet member 20 has substantially the same structure as the slider 21 described above. The slider 21 provided on the sheet member 20 engages with the sheet member 21 and engages with the outer peripheral side ring portions 51 arranged at the most circumferential ends. The slider 21 has an engaging portion 21f for engaging with the sheet member 20 so as not to be relatively rotatable. As described above, the slider 21 seals both ends of the viscous resistance generating space 47 in the circumferential direction together with the sheet member 20. Although a gap is secured between the slider body 21a and the annular seal 27, the rotary pin 21 has substantially the same axial length as the slider body and is in contact with the annular seal 27. On the outer side in the radial direction of 21, it is difficult to smoothly flow to both sides in the circumferential direction.
[0050]
A pair of plate-like seals 24 is arranged on the inner peripheral portion of each viscous resistance generating space 47. The plate seal 24 has an axial width substantially the same as the axial length of the annular fluid chamber 17, abuts against the plates 15, 16, and extends in an arc shape in the circumferential direction. One end of each plate-like seal 24 is a locking portion 24a bent outward in the radial direction, and the locking portion 24a is fitted into a slit 38 formed at the radially inner end of the sheet member 20. As shown in FIGS. 27 and 28, the other end of the plate-like seal 24 extends to the mating sheet member 20 side, and a part thereof overlaps in the radial direction. The plate-like seal 24 is in contact with the outer peripheral surface of the cylindrical portion 22a of the support ring 22 described above. As the pair of plate-like seals 24 approaches the circumferential direction of the pair of sheet members 20, the overlapping portions in the radial direction become longer. Further, the pair of plate-like seals 24 are pressed against the support ring 27 by the pressure generated in the viscous resistance generating space 47. Is done. Since the plate-like seal 24 has only one end supported by the sheet member 20, the other end is easily deformed. In this way, the sealing performance of the inner peripheral portion of the viscous resistance generating space 47 is enhanced.
[0051]
As shown in FIG. 10, a pair of holes 22d and a plurality of slits 22c (notches) extending in the circumferential direction are formed in the flange 22b of the support ring 22 described above. Both support rings 22 are fixed to each other by a pin (not shown) so as to rotate integrally. This pin extends in the axial direction, and both ends thereof are inserted into the holes 22d. In each viscous resistance generating space 47, three slits 22c are formed in the flange 22b. The slits 22c are formed so that the slits 22c on both sides in the circumferential direction are longer than the slit 22c in the middle. Corresponding to each slit 22c, a pin 23 (restricting member) is arranged. The pin 23 extends long in the axial direction, is inserted into the inner peripheral ring portion 52 of the bent leaf spring 19, and both ends thereof are disposed in slits 22c formed in flanges 22b on both axial sides. As a result, the bent leaf spring 19 is restricted from moving outward in the radial direction. In addition, as shown in FIG. 1, the pins 23 in the slits 22c on both sides in the circumferential direction are arranged on the outer side in the circumferential direction in a neutral state. Since the pin 23 can move in the circumferential direction in the slit 22c formed in the flange 22b, the bending angle of the bent leaf spring 19 is sufficiently wide. The reason why the slits 22c on both sides in the circumferential direction are long in the circumferential direction and the pins 23 are arranged on the outer side in the circumferential direction of the slit 22c is that the amount of movement of the leaf spring element on the outer peripheral side is on the inner peripheral side in the bent leaf spring 19. It is because it is large compared.
[0052]
The structure in the annular fluid chamber 17 described above will be further described. As shown in FIGS. 18 and 19, the annular fluid chamber 17 is partitioned into a pair of arcuate spaces by a pair of engaging plates 25 and engaging portions 18b, respectively. Furthermore, each arcuate space is a viscous resistance generating space 47 in which both ends in the circumferential direction are sealed by a pair of sheet members 20. The bent leaf springs 19 are arranged in the viscous resistance generating space 47, respectively. Further, spaces 48 are formed between the spaces near the engaging plate 25 and the engaging portion 18b, that is, between the adjacent sheet members 20. This space 48 is a space arranged on both sides in the circumferential direction of the viscous resistance generating space 47, and is reversely expanded when the viscous resistance generating space 47 is reduced. At that time, the viscous resistance space 47 is a space through which fluid flows.
[0053]
On the inner wall surfaces of the drive plate 15 and the seal plate 16, that is, both side wall surfaces of the annular fluid chamber 17, fluid passage recesses 45 are formed corresponding to the respective sheet members 20. As shown in FIGS. 12 and 15, the fluid passage recess 45 is longer in the circumferential direction than the sheet member 20 and shorter in the radial direction. As shown in FIG. 19, the fluid passage recess 45 partially overlaps the sheet member 20 in each viscous resistance generation space 47, but the inner side in the circumferential direction, that is, opposite to the engagement portion 18 b and the engagement plate 25 side. It is displaced to the side. In this state, fluid can flow back and forth between the viscous resistance generating space 47 and the space 48 separated by the sheet member 20 only by the first choke gap.
[0054]
Action
When the crankshaft 2 rotates, torque is transmitted to the first flywheel 4, and the torque is further transmitted to the second flywheel 5 via the viscous damper 6. Further, the torque is transmitted to the clutch disk assembly 14 in the clutch engaged state, and finally output to the main drive shaft of the transmission.
[0055]
In the viscous damper 6, torque transmission is performed as follows. When the drive plate 15 and the seal plate 16 are rotated, the engagement plate 25 pushes the sheet member 20, and the engagement portion 18 b of the driven plate 18 is pushed via the bent plate spring 19. In this way, torque is transmitted from the plates 15 and 16 to the driven plate 18.
[0056]
When torsional vibration (torque fluctuation) is input to the viscous damper mechanism 6, the plates 15 and 16 and the driven plate 18 periodically rotate relative to each other, and the bent leaf spring 19 is compressed in the circumferential direction. At this time, the fluid passes through the first choke gap, the small viscous resistance generating mechanism 31, the fluid passage recess 45, and the like.
The operation and characteristics of the viscous damper 6 with respect to torsional vibration will be described in more detail. For example, it is assumed that a minute torsional vibration generated in the practical engine speed range is input in the neutral state shown in FIG. At this time, the bent leaf spring 19 is provided with low torsional rigidity because each lever portion 53 bends with the central portion of the ring portions 51 and 52 as a fulcrum. Further, in the small viscous resistance generating mechanism 31, the open / close slider 34 moves in a piston on both sides in the circumferential direction in the slider accommodating chamber 32. At this time, the fluid mainly passes through the slider accommodating chamber 32 and the passage 33 (second choke gap) of the small viscous resistance generating mechanism 31. That is, no or little fluid flows through the first choke gap. In other words, as shown in FIG. 20, the fluid flows between the viscous resistance generation space 47 and the space 48 through the small viscous resistance generation mechanism 31. Furthermore, in the state of FIG. 20, the sheet member 20 on the rotation direction R <b> 2 side in each viscous resistance generation space 47 is at the center position of the fluid passage recess 45. In this state, as is apparent from FIGS. 13 and 16, the viscous resistance generation space 47 and the space 48 communicate with each other through a large gap between the sheet member 20 and the fluid passage recess 45. As described above, in the state of FIG. 20, the viscous resistance generating space 47 and the space 48 are communicated with each other by both the small viscous resistance generating mechanism 31 and the fluid passage recess 45, but this is sufficiently effective only with either one. There is. Moreover, the timing, angle, etc. which make both communication or complete | finish communication can be set arbitrarily.
[0057]
Further, for example, as shown in FIG. 21, when a minute torsional fluctuation in the practical engine speed range is input in a state where the relative angle between the plates 15 and 16 and the driven plate 18 is increased, the state shown in FIG. Thus, the open / close slider 34 that has sealed the space between the slider housing chamber 32 and the passage 33 in the small viscous resistance generating mechanism 31 moves the piston in the circumferential direction in the slider housing chamber 32. As a result, the fluid moves through the second choke gap of the small viscous resistance generating mechanism 31 between the viscous resistance generating space 47 and the space 48. As a result, no large viscous resistance is generated, and minute torsional vibration can be effectively absorbed.
[0058]
Further, in each viscous resistance generating space 47, the fluid flows in the circumferential direction through a gap between the lever portion 53 of the bent leaf spring 19 and both side walls of the annular fluid chamber 17. Accordingly, it is difficult for large viscous resistance to be generated in the viscous resistance generating space 47.
As described above, the viscous damper 6 has a structure in which a viscous resistance larger than necessary is not generated when, for example, a minute torsional vibration generated in a practical engine speed range is transmitted.
[0059]
Further, the viscous damper 6 is provided with various devices that do not generate a large sliding resistance against minute torsional vibrations. In the state shown in FIG. 20, the sheet member 20 on the rotation direction R <b> 2 side of each viscous resistance generation space 47 is pressed in the circumferential direction against the engaging portion 18 a of the driven plate 18. In this state, the engaging convex part 35 and the engaging concave part 18b are engaged with each other. Thereby, the sheet member 20 is difficult to move outward in the radial direction. As a result, the pressure contact force acting on the annular seal 27 from the slider 21 provided on the sheet member 20 is reduced. Further, in the bent leaf spring 19, the inner ring 52 is restricted from moving radially outward by the pins 23 at a plurality of locations. Accordingly, the bent leaf spring 19 is difficult to move outward in the radial direction, and the pressure contact force acting on the annular seal 27 from the slider 21 is reduced.
[0060]
As described above, since the movement of the members (the bent leaf spring 19 and the sheet member 20) that rotate relative to the annular fluid chamber 17 in the radially outward direction is limited, the members or the slider 21 and the inner side of the chamber 17 on the outer peripheral side are restricted. Sliding resistance with the wall surface (annular plate 27) is reduced.
Further, in each slider 21, the rotary pin 21 b is provided so as to be rotatable and movable in a circumferential direction within a groove 21 c provided in the slider main body 21 a, so that the slider 21 is relative to the annular plate 27. When rotating, the sliding resistance generated between the two is greatly reduced.
[0061]
As described above, when transmitting a minute torsional vibration, the vibration is effectively absorbed by the characteristics of low rigidity, small viscous resistance, and small sliding resistance. As a result, noise such as rattling noise on the transmission side is suppressed.
Next, the operation and characteristics of the viscous damper 6 during transmission of large torque fluctuations (large torsional vibration) that occur when the engine speed passes through the resonance point will be described. When the large torsional vibration is transmitted, for example, the torsion angle between the plates 15 and 16 and the driven plate 18 is increased from the state shown in FIG. 19, and the transition is made in the order of FIG. Further, returning to the state of FIG. 19 from the state of FIG. 20, the plates 15 and 16 are similarly twisted in the opposite direction with respect to the driven plate 18. In such a state, the operation in a region with a large twist angle and a region with a small twist angle will be described.
[0062]
As the torsional angle increases, the bent leaf spring 19 is brought into a state where the outer peripheral lever fulcrum 55 and the inner peripheral lever fulcrum 56 are in close contact with each other, and thereafter the lever portion with the fulcrums 55 and 56 as fulcrums. 53 is deformed. At this time, the rigidity is higher than that in a region where the twist angle is small.
Further, in the state shown in FIG. 21, the fluid in the viscous resistance generating space 47 flows into the space 48 through the first choke gap, and a large viscous resistance is generated. That is, in this state, the fluid passage recess 45 and the small viscous resistance generating mechanism 30 are sealed. Here, since the viscous resistance generating space 47 is formed by the pair of sheet members 20, a large pressure can be generated in the viscous resistance generating space 47, and as a result, a large viscous resistance can be generated. Further, since the inner peripheral portion of the viscous resistance generating space 47 is sealed by the plate seal 24 and the support ring 22, it is difficult for fluid to leak from the viscous resistance generating space 47. As a result, a large viscous resistance can be generated in the first choke gap.
[0063]
Further, on the outer peripheral side of the bent leaf spring 19, as shown in FIG. 26, the rotating pin 21 b that is close to one side in the circumferential direction slides on the annular seal 27. In this state, since the circumferential movement and rotation of the rotating pin 21 b are restricted, a large sliding resistance is generated between the rotating pin 21 b and the annular seal 27.
As described above, when a large torsional vibration is transmitted, in a large torsional angle state as shown in FIG. 21, the rigidity is high, the viscous resistance is large, and a large sliding resistance is obtained. Thereby, the large torsional vibration when passing through the resonance point can be effectively damped.
[0064]
When transmitting such a large torsional vibration, for example, the state shown in FIG. 20 is passed in a region where the torsion angle is small. That is, the viscous resistance generation space 47 and the space 48 communicate with each other through the fluid passage recess 45. At this time, the fluid in the space 48 returns to the viscous resistance generation space 47 through the fluid passage recess 45. In this way, since the fluid is returned to the viscous resistance generating space 47 in a region where the twist angle is small, a state where the fluid is insufficient in the viscous resistance generating space 47 hardly occurs. As a result, it is possible to generate a large viscous resistance against a large torsional vibration over a long period of time. Here, the sheet member 20 functions as a slider member that moves in the annular fluid chamber 17 in a state where the fluid is restricted from communicating between the viscous resistance generation space 47 and the space 48 on both sides in the circumferential direction. .
[0065]
The viscous damper 6 described above has a simple structure and is downsized by arranging the bent leaf spring 19 and the viscous resistance generating portion (first choke gap, small viscous resistance generating mechanism 31) in the circumferential direction. Further, the viscous damper 6 is easy to manufacture and manage because the first flywheel 4 and the second flywheel 5 are separate subassemblies.
Second embodiment
The flywheel assembly 1 shown in FIGS. 33 to 35 has substantially the same structure as that of the first embodiment. Here, only the structure different from the first embodiment will be described. As is apparent from the drawing, the slider 21, the pin 23, and the plate-like seal 24 in the embodiment are not provided. Therefore, the radially outer portion of the sheet member 22 comes into contact with and slides on the annular seal 27, and the gap between the sheet member 22 and the inner wall surface of the annular fluid chamber 17 is the first choke gap. . Further, the outer peripheral ring portion 51 of the bent leaf spring 19 is in direct contact with the annular seal 27 and slides. Furthermore, the support plate 22 has only a cylindrical portion. Also in such an embodiment, it is possible to obtain a large viscous resistance by forming the viscous resistance generating space 47 by the pair of sheet members 20.
Third embodiment
As shown in FIGS. 36 and 37, a plurality of fluid reservoir recesses 81 a may be formed on the outer peripheral surface of the slider 81. By collecting the fluid in the fluid reservoir recess 81a, the space between the slider 81 and the inner peripheral wall surface of the viscous resistance generating space is sufficiently lubricated, and a state in which no large sliding resistance is generated for a long period can be maintained. That is, the sliding resistance on the outer peripheral side of the bent leaf spring can be reduced.
[0066]
[Other variations]
The slider 21 disclosed in the first embodiment can also be used for a damper mechanism that is not filled with fluid. The rotating body is not limited to a cylindrical shape, and may be a sphere.
The viscous damper 6 can be used for devices other than the flywheel assembly. For example, it can be employed in a clutch disk assembly and a lock-up device for a torque converter.
[0067]
Further, in the flywheel assembly, the first flywheel 4 and the plates 15 and 16 may be formed as an integral member, or the driven plate 18 and the second flywheel 5 may be formed as an integral member. Also good. Further, the structure constituting the annular fluid chamber is not limited to the shapes of the plates 15 and 16 and the driven plate 18 of the embodiment.
[0068]
Adjacent fluid passage recesses 45 may be integrally formed and may extend over the entire space 48.
There may be three or more arcuate spaces and spring members.
The structure of the bent leaf spring is not limited to the above embodiment. Also, other types of springs may be used instead of the bent leaf springs.
[0069]
【The invention's effect】
In the viscous damper mechanism according to the present invention, since the viscous resistance generating space in which both ends in the circumferential direction are sealed by a pair of sheet members is provided, the viscous resistance generated when the fluid flows through the viscous resistance generating portion is reduced. growing.
[Brief description of the drawings]
FIG. 1 is a plan view with a part of a flywheel assembly in which a first embodiment of the present invention is adopted removed.
FIG. 2 is a longitudinal sectional view of a flywheel assembly.
FIG. 3 is a longitudinal sectional view of a flywheel assembly.
4 is a partially enlarged view of FIG. 1;
FIG. 5 is a plan view of a sheet member.
6 is a view taken in the direction of arrow VI in FIG.
7 is a sectional view taken along line VII-VII in FIG.
FIG. 8 is a view corresponding to FIG. 4 showing one operation state of the damper mechanism.
9 is a view taken along arrow IX in FIG.
FIG. 10 is a plan view of a support plate.
11 is a sectional view taken along line XI-XI in FIG.
FIG. 12 is a partially enlarged view of FIG. 1;
13 is a view corresponding to FIG. 12, showing one operation state of the viscous damper mechanism.
FIG. 14 is a view corresponding to FIG. 12, showing one operating state of the viscous damper.
FIG. 15 is a schematic cross-sectional view for illustrating a relationship between a sheet member 20 and a fluid passage recess.
FIG. 16 is a schematic cross-sectional view for illustrating a relationship between a sheet member 20 and a fluid passage recess.
FIG. 17 is a schematic cross-sectional view for illustrating a relationship between a sheet member 20 and a fluid passage recess.
FIG. 18 is a plan view of a viscous damper.
FIG. 19 is a schematic plan view for illustrating an outline of a viscous damper.
FIG. 20 is a view corresponding to FIG. 19 for explaining one operating state of the viscous damper.
FIG. 21 is a view corresponding to FIG. 19 for explaining one operating state of the viscous damper.
FIG. 22 is a front view of the slider.
FIG. 23 is a plan view of a slider.
FIG. 24 is a rear view of the slider.
25 is a partially enlarged view of FIG. 1;
FIG. 26 is a view corresponding to FIG. 25 for illustrating one operation state of the slider.
FIG. 27 is a partially enlarged view of FIG. 1;
FIG. 28 is a plan view showing a sheet member and a plate-like seal.
FIG. 29 is a plan view of a bent leaf spring.
FIG. 30 is a cross-sectional view of a bent leaf spring.
FIG. 31 is a partially enlarged view of FIG. 29;
FIG. 32 is a view corresponding to FIG. 31 for showing one operation state of the viscous damper.
FIG. 33 is a schematic longitudinal sectional view of a flywheel assembly according to a second embodiment.
FIG. 34 is a plan view showing a state where a part of the flywheel assembly is removed.
FIG. 35 is a partial longitudinal sectional view of the flywheel assembly.
FIG. 36 is a front view of a slider in the third embodiment.
FIG. 37 is a cross-sectional view of a slider.
[Explanation of symbols]
1 Flywheel assembly
2 Crankshaft
3 Clutch cover assembly
4 First flywheel
5 Second flywheel
6 Viscous damper
15 Drive plate
16 Seal plate
17 Annular fluid filling chamber
18 Driven plate
19 Bent leaf spring
21 Slider
22 Support ring
23 pins
24 Plate seal
25 engagement plate
27 Annular seal
31 Mechanism for generating small viscous resistance
32 Slider storage chamber
33 Passage
34 Opening and closing slider
45 Fluid passage recess
47 Viscous resistance generation space
48 spaces

Claims (19)

A first rotating member that forms a chamber extending in a circumferential direction and filled with fluid, and having a first engaging portion extending into the chamber;
A second rotating member that has a second engaging portion disposed in a position displaced in a circumferential direction with respect to the first engaging portion in the chamber, and is rotatable relative to the first rotating member;
An elastic member extending between the first engagement portion and the second engagement portion in the chamber;
The elastic member is disposed on both sides in the circumferential direction of the elastic member in the chamber to support the elastic member, and the viscous resistance generation space is formed by sealing both sides in the circumferential direction of the elastic member in the chamber 1 A pair of sheet members;
When the pair of sheet members approach each other to reduce the viscous resistance generating space, a viscous resistance generating portion including a first choke gap in which a fluid can move between the viscous resistance generating space and an outer space thereof is provided. Prepared,
The sheet member has a second choke gap that is wider than the first choke gap and allows fluid to pass between a space between the sheet members on both sides in the circumferential direction of the elastic members and a space outside the circumferential direction. Formed,
A viscous damper mechanism, further comprising a closing member capable of closing the second choke gap according to a change in pressure on both sides in the circumferential direction of the second choke gap. A first rotating member having a plurality of first engaging portions arranged to divide the chamber into a plurality of arcuate spaces, forming a chamber extending in the circumferential direction and filled with fluid;
A second rotating member rotatable relative to the first rotating member, and having a plurality of second engaging portions arranged in the chamber corresponding to each of the plurality of first engaging portions;
A plurality of elastic members disposed in each of the plurality of arcuate spaces;
A plurality of elastic members are arranged on both sides in the circumferential direction of the elastic members to support the elastic members, and form a viscous resistance generation space by sealing both sides of the elastic members in the circumferential direction in the chamber. A sheet member;
Viscous resistance including a first choke gap through which fluid flows out to the outside in the circumferential direction of the viscous resistance generating space when sheet members arranged on both sides in the circumferential direction of the elastic member approach each other to reduce the viscous resistance generating space. A generator and
The sheet member has a second choke gap that is wider than the first choke gap and allows fluid to pass between a space between the sheet members on both sides in the circumferential direction of the elastic members and a space outside the circumferential direction. Formed,
A viscous damper mechanism, further comprising a closing member capable of closing the second choke gap according to a change in pressure on both sides in the circumferential direction of the second choke gap. A first rotating member having a pair of first engaging portions forming an annular chamber filled with fluid and extending into the chamber and dividing the annular chamber into a pair of arcuate spaces;
A second rotating member having a pair of second engaging portions disposed in the chamber corresponding to the pair of first engaging portions, respectively.
A pair of arcuate elastic members disposed in each of the pair of arcuate spaces;
A sheet which is disposed on both sides in the circumferential direction of the elastic member in the chamber and supports the elastic member, and forms a viscous resistance generating space by sealing both sides in the circumferential direction of the elastic member in the chamber. Members,
When the sheet members disposed on both sides in the circumferential direction of each elastic member approach each other to reduce the viscous resistance generation space, the viscosity includes a first choke gap through which fluid flows out to the outer side in the circumferential direction of the viscous resistance generation space. A resistance generator,
The sheet member has a second choke gap that is wider than the first choke gap and allows fluid to pass between a space between the sheet members on both sides in the circumferential direction of the elastic members and a space outside the circumferential direction. Formed,
A viscous damper mechanism, further comprising a closing member capable of closing the second choke gap according to a change in pressure on both sides in the circumferential direction of the second choke gap.   The viscous damper mechanism according to any one of claims 1 to 3, wherein the second engagement portion and the sheet member each have an engagement portion that can be engaged with and detached from each other in a circumferential direction. One end is fixed to the radially inner end of the sheet member, extends in an arc shape toward the sheet member provided on the opposite side of the elastic member, and between the sheet members disposed on both sides in the circumferential direction of the elastic member The viscous damper mechanism according to any one of claims 1 to 4 , further comprising a pair of arcuate plate seals for sealing the inner periphery. The viscous damper mechanism according to claim 5 , wherein the other end of the pair of arcuate plate seals is overlapped in the radial direction. The first rotating member includes a pair of disk-shaped portions forming both side walls of the chamber,
The second rotating member has an annular portion disposed on the inner peripheral side of the first rotating member, and the second engaging portion extending from the annular portion into the chamber,
On the inner peripheral side of the pair of arcuate plate seal members, between the annular portion and one inner peripheral portion of the pair of disc-like portions, and between the annular portion and the pair of disc-like portions. The viscous damper mechanism according to claim 5 or 6 , further comprising a pair of annular seal members respectively disposed between the other inner peripheral portion. The first rotating member includes a pair of disk-shaped portions forming both side walls of the chamber,
The second rotating member has an annular portion disposed on the inner peripheral side of the first rotating member, and the second engaging portion extending from the annular portion into the chamber,
Arranged between the annular portion and one inner peripheral portion of the pair of disc-shaped portions, and between the annular portion and the other inner peripheral portion of the pair of disc-shaped portions, respectively. The viscous damper mechanism according to any one of claims 1 to 5 , further comprising a pair of annular seal members. The pair of annular seal members are immovable in the radial direction with respect to the first and second rotating members;
The locked to a pair of annular sealing member, said further comprising a limiting member for limiting the movement of the radially outward of said resilient member by engaging the elastic member, according to claim 7 or 8 The viscous damper mechanism described in 1. The viscous damper mechanism according to claim 9 , wherein a plurality of notches extending in a circumferential direction are formed in the pair of annular seal members, and both ends of the engaging member extend into the notches. Wherein the inner wall surface of the chamber, the circumferential width of long fluid passage recess than the sheet member is formed to correspond to the sheet member, the viscous damper mechanism according to any of claims 1-10. Wherein disposed between the outer peripheral side inner wall surface of the elastic member and the chamber further comprises a slidable slider in the circumferential direction with respect to the outer peripheral side inner wall surface, to any one of claims 1 to 11 The viscous damper mechanism described. Wherein disposed between the outer peripheral side inner wall surface of the sheet member and the chamber further comprises a slidable slider in the circumferential direction with respect to the outer peripheral side inner wall surface, to any one of claims 1 to 12 The viscous damper mechanism described. The slider, the slider body and the slider body outer peripheral surface rotatably locked in the containing can contact the rotating body on the outer peripheral side inner wall surface of the chamber, the viscous damper mechanism according to claim 12 or 13. The viscous damper mechanism according to claim 14 , wherein a groove having a length capable of moving the rotating body in a circumferential direction is formed on an outer peripheral surface of the slider body. The viscous damper mechanism according to claim 14 or 15 , wherein the rotating body is a cylindrical member extending in an axial direction. The viscous damper mechanism according to claim 14 or 15 , wherein an outer peripheral surface of the slider has a shape along an outer peripheral side inner wall surface of the chamber, and a fluid reservoir recess is formed on the outer peripheral surface of the slider body. The elastic member is a bent leaf spring having a plurality of leaf spring elements which are connected in series, the viscosity damper mechanism according to any of claims 1 to 17. The bent leaf spring has a plurality of ring portions and a plurality of lever portions connecting the plurality of ring portions, and the central portion of the plurality of lever portions has an axial width narrower than both ends. The viscous damper mechanism according to claim 18 .

Images