WO2010047193A1 - ダンパー機構 - Google Patents
ダンパー機構 Download PDFInfo
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- WO2010047193A1 WO2010047193A1 PCT/JP2009/065853 JP2009065853W WO2010047193A1 WO 2010047193 A1 WO2010047193 A1 WO 2010047193A1 JP 2009065853 W JP2009065853 W JP 2009065853W WO 2010047193 A1 WO2010047193 A1 WO 2010047193A1
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- WIPO (PCT)
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- disposed
- hole
- damper mechanism
- pair
- protrusion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
- F16F15/123—Wound springs
Definitions
- the present invention relates to a damper mechanism, and more particularly to a damper mechanism for damping torsional vibration in a power transmission system.
- a damper mechanism is used in the power transmission system of the vehicle to attenuate torsional vibration.
- a clutch device that transmits and cuts off torque from the engine will be described as an example.
- the clutch device has a clutch disc assembly disposed in proximity to the flywheel and a clutch cover assembly for pressing the clutch disc assembly against the flywheel.
- a clutch function and a damper function are realized by the clutch disk assembly.
- the clutch cover assembly includes an annular clutch cover that is fixed to the flywheel, a pressure plate that is axially movable and integrally rotatable with respect to the clutch cover, and biases the pressure plate toward the flywheel. And a diaphragm spring.
- the clutch disk assembly includes a clutch disk sandwiched between a pressure plate and a flywheel, a pair of input side plates on which the clutch disk is fixed and arranged opposite to each other, and a pair of input side plates.
- a hub flange disposed between the axial directions, a coil spring that elastically connects the pair of input side plates and the hub flange in the rotational direction, and an output side that is elastically connected to the hub flange in the rotational direction And a hub.
- a damper mechanism is constituted by the pair of input side plates, the hub flange, and the coil spring.
- a stop pin is used as a member for restricting relative rotation between the input side plate and the hub flange within a predetermined torsion angle range.
- the stop pin connects a pair of input side plates and passes through a hole formed in the hub flange.
- the stopper mechanism is realized by the contact between the stop pin and the hole in the rotational direction.
- the stop pin needs to have a certain diameter in order to ensure strength, and further needs to be arranged further radially inward from the outer peripheral edge of the pair of input side plates. For this reason, the relative torsion angle between the pair of input side plates and the hub flange cannot be sufficiently increased. In this case, even if a highly rigid coil spring is used, a sufficient relative twist angle cannot be obtained. Therefore, the conventional stop pin type stopper mechanism cannot make full use of the capacity of the coil spring.
- An object of the present invention is to provide a damper mechanism that can increase the efficiency of assembly work.
- the damper mechanism includes a first rotating body, a second rotating body, and a plurality of elastic members.
- the first rotating body includes a first member, a second member arranged in line with the first member in the axial direction, and a plurality of connecting portions that connect the first member and the second member. .
- the second rotating body is disposed between the first and second members in the axial direction, and is provided to be rotatable relative to the first rotating body.
- the plurality of elastic members elastically connect the first and second rotating bodies in the rotation direction, and are disposed between the rotation directions of the connecting portions.
- the second rotating body has a pair of protrusions that can be in contact with the connecting portion in the rotation direction between the connecting portions in the rotating direction.
- the first member has a pair of first holes arranged at positions facing each other across the rotation shaft. The pair of first holes can be inserted with positioning pins used at the time of assembly, and are arranged adjacent to the pair of protrusions in the rotation direction.
- the protrusion is used as the first member so that the positioning pin and the protrusion are in contact with each other in the rotation direction.
- the second rotating body can be easily set at the correct position with respect to the first member. Thereby, the efficiency of the assembly operation of the damper mechanism can be increased.
- FIG. 1 is a schematic longitudinal sectional view of the clutch disk assembly 1
- FIG. 2 is a schematic plan view of the clutch disk assembly 1.
- the OO line in FIG. 1 is the rotation axis of the clutch disk assembly 1.
- an engine and a flywheel are arranged on the left side of FIG. 1
- a transmission is arranged on the right side of FIG.
- the R1 side in FIG. 2 is the rotational direction drive side (positive side) of the clutch disk assembly 1
- the R2 side is the opposite side (negative side).
- the clutch disc assembly 1 is a mechanism used in a clutch device that constitutes a power transmission system of a vehicle, and has a clutch function and a damper function.
- the clutch function is a function of transmitting and interrupting torque when the clutch disk assembly 1 is pressed and released from a flywheel (not shown) by a pressure plate (not shown).
- the damper function is a function that absorbs and attenuates torsional vibration input from the flywheel side by a coil spring or the like.
- the clutch disk assembly 1 mainly includes a clutch disk 23 to which torque is input from a flywheel, and a damper mechanism 4 to absorb and attenuate torsional vibration input from the clutch disk 23. It is equipped with.
- the clutch disc 23 is a portion that is pressed against a flywheel (not shown), and mainly includes a pair of annular friction facings 25 and a cushioning plate 24 to which the friction facings 25 are fixed.
- the cushioning plate 24 is fixed to the outer periphery of the damper mechanism 4. Details of the cushioning plate 24 will be described later.
- FIG. 3 is a schematic plan view of the damper mechanism 4
- FIG. 4 is a plan view of the hub flange 6
- FIG. 5 is a plan view of the input rotating body 2
- FIGS. 6 and 7 are partial sectional views of the damper mechanism 4.
- the damper mechanism 4 mainly includes an input rotator 2 (an example of a first rotator) to which the clutch disk 23 is fixed, and a hub flange 6 (a second rotator of the second rotator) arranged so as to be rotatable relative to the input rotator 2.
- An example a spline hub 3 that is rotatably arranged with respect to the hub flange 6, a first coil spring 7 that elastically connects the hub flange 6 and the spline hub 3 in the rotational direction, and an input rotator 2.
- a second coil spring 8 (an example of an elastic member) that elastically couples the hub flange 6 in the rotational direction.
- the spline hub 3 is spline-engaged with the end of the input shaft of a transmission (not shown).
- the input rotator 2 has a clutch plate 21 and a retaining plate 22.
- the clutch plate 21 and the retaining plate 22 are disk-shaped or annular members made of sheet metal, and are arranged at predetermined intervals in the axial direction.
- the clutch plate 21 is disposed on the engine side, and the retaining plate 22 is disposed on the transmission side.
- the clutch plate 21 and the retaining plate 22 are fixed to each other by a connecting portion 31 described later. For this reason, the clutch plate 21 and the retaining plate 22 can be integrally rotated with a predetermined interval maintained in the axial direction.
- a first fixing portion 24 c and a second fixing portion 24 e of the clutch disk 23 are fixed to the outer peripheral portion of the clutch plate 21 by rivets 27.
- the clutch plate 21 and the retaining plate 22 have a function of holding the second coil spring 8.
- the retaining plate 22 includes an annular first main body portion 28 (an example of a first member), four cut-and-raised portions 35a, and four cut-and-raised portions 35b.
- the clutch plate 21 includes a second main body portion 29 (an example of a second member), two cut-and-raised portions 35a, two cut-and-raised portions 35b, and four connecting portions 31.
- the cut-and-raised portions 35a and 35b form a holding portion 35 that holds the second coil spring 8 so as to be elastically deformable.
- the connecting portion 31 is disposed between the rotation directions of the holding portion 35.
- the holding part 35 has cut-and-raised parts 35a and 35b on the inner peripheral side and the outer peripheral side.
- the cut and raised portions 35a and 35b restrict the movement of the second coil spring 8 in the axial direction and the radial direction.
- the dimension of the holding portion 35 in the rotation direction substantially coincides with the length of the second coil spring 8.
- contact surfaces 36 that are in contact with or close to the end of the second coil spring 8 are formed.
- the four holding portions 35 are arranged so that adjacent pitches are different (see FIG. 5). Specifically, the left and right holding portions 35 in FIG.
- the first main body portion 28 has four holes 34 and a pair of first holes 28a arranged at positions facing each other across the rotation axis O.
- the hole 34 is a hole for inserting the rivet 27, and the inner diameter of the hole 34 is set slightly larger than the outer shape of the head of the rivet 27.
- the first hole 28a is a hole into which the positioning pin P (see FIG. 4) is inserted during assembly, and is disposed on the R1 side of the hole 34.
- the inner diameter of the first hole 28a and the outer diameter of the positioning pin P are set to be substantially the same so that the retaining plate 22 does not move relative to the positioning pin P with the positioning pin P inserted into the first hole 28a.
- the first hole 28a is disposed adjacent to the first protrusion 45 in the rotation direction.
- the contour line of the first hole 28 a is the rotational end of the first protrusion 45 (described later) of the hub flange 6 (more specifically, The first hole 28a is disposed at a position in contact with the contour line on the R2 side end. For this reason, the hub flange 6 can be set at a neutral position with respect to the retaining plate 22 by assembling the hub flange 6 so that the positioning pin P and the first projecting portion 45 abut.
- the second main body portion 29 has four holes 29b and a pair of second holes 29a arranged at positions facing each other with the rotation axis O interposed therebetween.
- the second hole 29a is a hole into which the positioning pin P is inserted during assembly, and is disposed at a position facing the first hole 28a in the axial direction.
- the inner diameter of the second hole 29a and the outer diameter of the positioning pin P are set to be substantially the same so that the clutch plate 21 does not move relative to the positioning pin P with the positioning pin P inserted into the second hole 29a. ing.
- the second hole 29a is disposed between the connecting portion 31 and the first projecting portion 45 in the rotational direction.
- the second hole 29a is disposed adjacent to the first protrusion 45 in the rotation direction. More specifically, in the neutral state in which no power is input to the damper mechanism 4, the contour line of the second hole 29a is at the rotational end of the first protrusion 45 (more specifically, the end on the R2 side).
- the second hole 29a is disposed at a position in contact with the contour line.
- the connecting portion 31 is disposed on the outer peripheral portion of the first main body portion 28 and connects the first main body portion 28 and the second main body portion 29.
- the connecting portion 31 includes a contact portion 32 that extends in the axial direction from the outer peripheral edge of the first body portion 28 to the second body portion 29, and a fixed portion that extends radially inward from the end portion of the contact portion 32. 33 (see FIG. 7).
- the connecting portion 31 is integrally formed with the first main body portion 28.
- the fixing portion 33 has a hole 33a into which the rivet 27 is inserted.
- the fixing portion 33 is fixed to the second main body portion 29 of the clutch plate 21 by a rivet 27 together with the fixing portion 24 c of the clutch disk 23.
- the hub flange 6 is disposed between the clutch plate 21 and the retaining plate 22 so as to be relatively rotatable, and is elastically connected to the clutch plate 21 and the retaining plate 22 by the second coil spring 8.
- the hub flange 6 includes an annular portion 48, a pair of first protrusions 45, a pair of second protrusions 46, and a pair of first window holes 41. And a pair of second window holes 42.
- the first projecting portion 45 is a portion projecting radially outward from the annular portion 48, and is disposed at a position facing the rotation axis O.
- the pair of first protrusions 45 have a point-symmetric shape about the rotation axis O.
- the first protrusion 45 includes a first protrusion main body 45a in which the first window hole 41 is formed, a protrusion 45b protruding in the rotation direction from the first protrusion main body 45a, and a radially outer side from the first protrusion main body 45a.
- a first abutting portion 49 projecting from the first contact portion 49.
- the first contact portion 49 can contact the contact portion 32 of the connecting portion 31.
- a pair of stopper surfaces 50 are formed at the end of the first contact portion 49 in the rotational direction.
- the stopper surface 50 can contact the stopper surface 39 of the connecting portion 31.
- the protrusion 45 b is disposed radially inward of the first contact portion 49.
- the protrusion 45b is disposed at a position where it overlaps with a part of the second hole 29a when the hub flange 6 is assembled to the second main body 29 upside down, for example. Further, the protrusion 45b is disposed at a position where it overlaps with a part of the first hole 28a when the hub flange 6 is assembled to the second main body portion 29 upside down.
- the second projecting portion 46 is a portion projecting radially outward from the annular portion 48, and is disposed at a position facing the rotation axis O.
- the pair of second protrusions 46 have a point-symmetric shape about the rotation axis O.
- the second protrusion 46 includes a second protrusion main body 46a in which the second window hole 42 is formed, and a second contact portion 57 that protrudes radially outward from the second protrusion main body 46a. .
- the second contact portion 57 can contact the contact portion 32 of the connecting portion 31.
- a pair of stopper surfaces 51 are formed at the end of the second contact portion 57 in the rotational direction. The stopper surface 51 can come into contact with the stopper surface 39 of the connecting portion 31.
- a center line in the rotation direction of the first protrusion 45 is defined as a first center line L1.
- a center line in the rotation direction of the second protrusion 46 is defined as a second center line L2.
- the first center line L1 is orthogonal to the second center line L2.
- the pair of first window holes 41 and the pair of second window holes 42 are arranged at positions corresponding to the four holding portions 35.
- the pair of first window holes 41 are arranged to face each other in the radial direction, and the pair of second window holes 42 are arranged to face each other in the radial direction.
- the second coil spring 8 is accommodated in the first window hole 41 and the second window hole 42.
- the rotation direction dimension of the first window hole 41 is set longer than that of the holding part 35, and the rotation direction dimension of the second window hole 42 is set to be substantially the same as that of the holding part 35.
- a first contact surface 44 and a second contact surface 47 that are in contact with or close to the end of the second coil spring 8 are formed at both ends in the circumferential direction. Yes.
- the spline hub 3 is disposed in the center holes 37 and 38 of the clutch plate 21 and the retaining plate 22.
- the spline hub 3 has a cylindrical boss 52 extending in the axial direction and a flange 54 extending radially outward from the boss 52.
- a spline hole 53 that engages with an input shaft (not shown) of the transmission is formed in the inner peripheral portion of the boss 52.
- the plurality of outer peripheral teeth 55 formed on the outer peripheral portion of the flange 54 mesh with the plurality of inner peripheral teeth 59 formed on the inner peripheral portion of the hub flange 6.
- a first notch 56 and a second notch 58 in which the first coil spring 7 is accommodated are formed on the outer peripheral edge of the flange 54 and the inner peripheral edge of the hub flange 6.
- a pair of spring seats is attached to the end of the first coil spring 7.
- a gap is formed between the rotation directions of the outer peripheral teeth 55 and the inner peripheral teeth 59.
- the twist angles corresponding to the gap are the gap angles ⁇ 1p and ⁇ 1n.
- the gap formed on the R1 side of the outer peripheral tooth 55 corresponds to the gap angle ⁇ 1p
- the gap formed on the R2 side of the outer peripheral tooth 55 corresponds to the gap angle ⁇ 1n.
- the second coil spring 8 has a pair of coil springs arranged concentrically and having different diameters.
- the second coil spring 8 has a larger diameter and a longer length than the first coil spring 7.
- the spring constant of the second coil spring 8 is set to a much larger value than the spring constant of the first coil spring 7. That is, the second coil spring 8 is much more rigid than the first coil spring 7. Therefore, when torque is input to the input rotating body 2, the first coil spring 7 starts to compress between the hub flange 6 and the spline hub 3, and when the hub flange 6 and the spline hub 3 rotate together, the input The second coil spring 8 starts to compress between the rotating body 2 and the hub flange 6.
- the torque input to the input rotating body 2 is transmitted to the hub flange 6 through the second coil spring 8, and the hub flange 6 and the spline hub 3 rotate relative to each other.
- the first coil spring 7 is compressed between the hub flange 6 and the spline hub 3.
- the relative torsion angle between the hub flange 6 and the spline hub 3 reaches a predetermined angle
- the outer peripheral teeth 55 and the inner peripheral teeth 59 come into contact with each other, and both the members 6 and 3 rotate together.
- the second coil spring 8 is compressed between the input rotating body 2 and the hub flange 6.
- the first coil spring 7 acts in parallel and the second coil spring 8 acts in parallel.
- the damper mechanism 4 is provided with a first stopper 9 and a second stopper 10 that function as a stopper mechanism in order to directly transmit the torque input to the input rotating body 2.
- the first stopper 9 is a mechanism for restricting the relative rotation between the hub flange 6 and the spline hub 3 within a certain range, and includes an outer peripheral tooth 55 of the spline hub 3, an inner peripheral tooth 59 of the hub flange 6, have.
- the first stopper 9 allows relative rotation between the hub flange 6 and the spline hub 3 within the range of the gap angles ⁇ 1p and ⁇ 1n.
- the second stopper 10 is a mechanism for limiting the relative rotation between the input rotator 2 and the hub flange 6 within a certain range.
- the second stopper 10 is a first contact between the connecting portion 31 of the input rotator 2 and the hub flange 6. This is realized by the portion 49 and the second contact portion 57.
- a gap is secured between the rotation direction of the connecting portion 31 and the first contact portion 49 and the second contact portion 57.
- the twist angle corresponding to this gap is the gap angle ⁇ 3p or ⁇ 3n.
- the gap formed on the R1 side of the connecting portion 31 corresponds to the gap angle ⁇ 3p, and the gap formed on the R2 side of the connecting portion 31 corresponds to the gap angle ⁇ 3n.
- the damper mechanism 4 is provided with a friction generating mechanism 5 that generates a hysteresis torque using frictional resistance in order to more effectively absorb and attenuate torsional vibration.
- the friction generating mechanism 5 includes a first friction washer 79, a second friction washer 72, and a third friction washer 85.
- the first friction washer 79 is disposed between the flange 54 of the spline hub 3 and the inner peripheral portion of the retaining plate 22 in the axial direction, and is disposed on the outer peripheral side of the boss 52.
- the first friction washer 79 is made of resin.
- the first friction washer 79 mainly has an annular main body 81 and a plurality of protrusions 82 extending radially outward from the main body 81.
- the main body 81 is in contact with the transmission side surface of the flange 54, and a first cone spring 80 is disposed between the main body 81 and the retaining plate 22.
- the first cone spring 80 is compressed in the axial direction between the main body 81 and the retaining plate 22. Therefore, the friction surface of the first friction washer 79 is pressed against the flange 54 by the first cone spring 80.
- the plurality of protrusions 82 are engaged with recesses 77 (described later) of the second friction washer 72. Thereby, the 1st friction washer 79 and the 2nd friction washer 72 can rotate integrally.
- the second friction washer 72 is disposed between the inner peripheral portion of the hub flange 6 and the inner peripheral portion of the retaining plate 22, and is disposed on the outer peripheral side of the first friction washer 79.
- the second friction washer 72 mainly includes an annular main body 74, a plurality of engaging portions 76 extending from the inner peripheral portion of the main body 74 to the transmission side, and a recess 77 formed on the transmission side of the inner peripheral portion of the main body 74. ,have.
- the second friction washer 72 is made of resin, for example.
- the main body 74 is in contact with the transmission side surface of the hub flange 6, and a second cone spring 73 is disposed between the main body 74 and the retaining plate 22.
- the second cone spring 73 is compressed between the main body 74 and the retaining plate 22.
- the friction surface of the second friction washer 72 is pressed against the hub flange 6 by the second cone spring 73.
- the engaging portion 76 passes through the hole portion of the retaining plate 22.
- the 2nd friction washer 72 and the retaining plate 22 can rotate integrally.
- the protrusions 82 of the first friction washer 79 are engaged with the recess 77. For this reason, the first friction washer 79 can rotate integrally with the retaining plate 22 via the second friction washer 72.
- the urging force of the first corn spring 80 is designed to be smaller than the urging force of the second corn spring 73. Further, the first friction washer 79 has a lower coefficient of friction than the second friction washer 72. For this reason, the friction (hysteresis torque) generated by the first friction washer 79 is significantly smaller than the friction (hysteresis torque) generated by the second friction washer 72.
- the third friction washer 85 is disposed between the flange 54 and the inner peripheral portion of the clutch plate 21, and is disposed on the outer peripheral side of the boss 52.
- the third friction washer 85 is made of resin, for example.
- the third friction washer 85 mainly has an annular main body 87 and a plurality of engaging portions 88 extending from the main body 87 to the engine side.
- the main body 87 is in contact with the surface of the flange 54 and the hub flange 6 on the engine side, and is in contact with the surface of the clutch plate 21 on the transmission side.
- the engaging portion 88 passes through a hole formed in the clutch plate 21.
- the third friction washer 85 can rotate integrally with the clutch plate 21 by the engaging portion 88.
- the main body 87 engages with the central hole 37 of the clutch plate 21 so as not to be relatively rotatable, and an inner peripheral surface thereof is slidably contacted with an outer peripheral surface of the boss 52. That is, the clutch plate 21 is positioned in the radial direction by the boss 52 via the third friction washer 85.
- the first friction washer 79 and the third friction washer 85 constitute the large friction generating mechanism 14, and the second friction washer 72 and the third friction washer 85 constitute the small friction generating mechanism 15. .
- the hub flange 6 and the spline hub 3 rotate relative to each other, hysteresis torque is generated by the large friction generating mechanism 14 and the small friction generating mechanism 15, and the damper mechanism 4 can more effectively attenuate and absorb the torsional vibration. Can be done automatically.
- the cushioning plate 24 has an annular portion 24a, eight cushioning portions 24b, a pair of first fixing portions 24c, and a pair of second fixing portions 24e.
- the cushioning portion 24b is a portion to which the friction facing 25 is fixed, and is provided on the outer peripheral side of the annular portion 24a.
- the cushioning portions 24b are arranged at an equal pitch in the rotation direction.
- the pair of first fixing portions 24c are portions protruding radially inward from the annular portion 24a, and are sandwiched between the fixing portion 33 of the connecting portion 31 and the second main body portion 29 in the axial direction.
- a hole 24d corresponding to the hole 33a of the connecting portion 31 and the hole 29b of the second main body portion 29 is formed in the first fixing portion 24c.
- the pair of second fixing portions 24e are portions protruding radially inward from the annular portion 24a, and are sandwiched between the fixing portion 33 of the connecting portion 31 and the second main body portion 29 in the axial direction.
- the second fixing portion 24e is formed with a hole 24f corresponding to the hole 33a of the connecting portion 31 and the hole 29b of the second main body portion 29.
- the second fixing portion 24e is formed with a third hole 24g disposed adjacent to the hole 24f.
- the third hole 24g is a hole for inserting the positioning pin P, and is disposed at a position corresponding to the first hole 28a and the second hole 29a.
- the four plurality of connecting portions 31 are not arranged at the same pitch, but are arranged so that adjacent pitches are different.
- the rotation direction center of the fixing portion 33 of the connecting portion 31 is arranged so that the adjacent pitches are different.
- the angle A1 formed by the two connecting portions 31 disposed on both sides in the rotation direction of the first protrusion 45 is larger than the angle A2 formed by the two connecting portions 31 disposed on both sides in the rotation direction of the second protrusion 46. large.
- the reference (pitch reference) of the angles A1 and A2 is the rotational center of the rivet 27 that fixes the fixing part 33 of the connecting part 31 (or the rotational center of the hole 33a through which the rivet 27 passes).
- the two connecting portions 31 arranged on the R1 side of the two first projecting portions 45 are arranged at positions facing each other with the rotation axis O therebetween. Further, the two connecting portions 31 arranged on the R2 side of the two second projecting portions 46 are arranged at positions facing each other with the rotation axis O therebetween.
- the shape of the notch 43 is complementary to the shape of the corresponding fixing portion 33 and is slightly larger than the fixing portion 33. This is because the fixing portion 33 allows the notch 43 to pass in the axial direction during assembly. Therefore, when the connection part 31 is arrange
- the four second coil springs 8 have the same size, but the first window hole 41 can have a larger rotational dimension than the second window hole 42. For this reason, it is possible to ensure a gap between the first contact surface 44 of the first window hole 41 and the end portion of the second coil spring 8 in the rotational direction.
- the twist angles corresponding to the gap are the gap angles ⁇ 2p and ⁇ 2n.
- the gap formed on the R1 side of the end of the second coil spring 8 corresponds to the gap angle ⁇ 2p
- the gap formed on the R2 side of the end of the second coil spring 8 corresponds to the gap angle ⁇ 2n. is doing.
- the gap angle ⁇ 2p is set smaller than the gap angle ⁇ 2n.
- the damper mechanism 4 can realize the two-stage torsional characteristics by using the second coil spring 8 as described later.
- the rotational direction center of the contact portion 32 and the rotational direction center of the fixed portion 33 are different in the rotational direction position.
- the rotation of the fixing portion 33 corresponding to the abutting portion 32 is such that the rotation direction center of the abutting portion 32 has a smaller adjacent pitch with reference to the connecting portion 31 corresponding to the abutting portion 32.
- the position in the rotational direction is deviated from the center of the direction.
- the rotational direction center of the contact portion 32 is disposed on the R1 side with respect to the rotational direction center of the fixed portion 33.
- this connection part 31 is made into the reference
- the positional relationship between the stopper surface 50 and the first protrusion main body 45a is different from the conventional one by shifting the position of the contact portion 32 with respect to the fixed portion 33 in the rotation direction.
- the two stopper surfaces 50 formed in the first contact portion 49 are more outward in the rotational direction than the two first contact surfaces 44 formed in the first window hole 41.
- the stopper surface 50 on the R1 side is disposed on the R1 side with respect to the first contact surface 44 on the R1 side
- the stopper surface 50 on the R2 side is disposed on the R2 side with respect to the first contact surface 44 on the R2 side. Has been.
- the rotational length of the first contact portion 49 is longer than the rotational length of the first window hole 41.
- the two stopper surfaces 51 formed on the second contact portion 57 are rotated in the direction of rotation more than the two second contact surfaces 47 formed on the second window hole 42.
- the stopper surface 51 on the R1 side is disposed on the R2 side with respect to the second contact surface 47 on the R1 side, and the stopper surface 51 on the R2 side is more than the second contact surface 47 on the R2 side. Is also arranged on the R1 side. Therefore, the rotation direction length of the second contact portion 57 is shorter than the rotation direction length of the second window hole 42.
- the radial dimension of the first window hole 41 can be increased, and the diameter of the second coil spring 8 corresponding to the first window hole 41 can be further increased.
- the outer side in the rotational direction refers to the outer side in the rotational direction with reference to the rotational center of the first protrusion 45, the rotational center of the first contact portion 49, or the rotational direction center of the first window hole 41.
- the inside in the rotational direction means the center in the rotational direction of the second protrusion 46, the center in the rotational direction of the second contact portion 57 or the center of the second window hole 42 in the rotational direction. is doing.
- the rotation direction centers of the first projecting portion 45, the first contact portion 49, and the first window hole 41 coincide with each other and are disposed on the first center line L1.
- the rotation direction center of the 2nd protrusion part 46, the 2nd contact part 57, and the 2nd window hole 42 corresponds, and is arrange
- FIG. 9 is a mechanical circuit diagram of the damper mechanism 4 as described above. This mechanical circuit diagram schematically shows the relationship in the rotation direction of each member in the damper mechanism. Therefore, the integrally rotating member is handled as the same member.
- the hub flange 6 is disposed between the rotation direction of the input rotating body 2 and the spline hub 3.
- the hub flange 6 is elastically connected to the spline hub 3 via the first coil spring 7 in the rotational direction.
- a first stopper 9 is formed between the hub flange 6 and the spline hub 3.
- the first coil spring 7 can be compressed within the range of the first gap angles ⁇ 1p and ⁇ 1n in the first stopper 9.
- the hub flange 6 is elastically connected to the input rotating body 2 via the second coil spring 8 in the rotational direction.
- a second stopper 10 is formed between the hub flange 6 and the input rotating body 2.
- the second coil spring 8 can be compressed within the range of the gap angles ⁇ 3p and ⁇ 3n in the second stopper 10. As described above, the input rotating body 2 and the spline hub 3 are elastically connected in the rotational direction by the first coil spring 7 and the second coil spring 8 arranged in series via the hub flange 6. Yes.
- the hub flange 6 functions as an intermediate member disposed between two types of coil springs.
- the structure described above includes a first damper composed of a plurality of first coil springs 7 and a first stopper 9 arranged in parallel, and a plurality of second coil springs 8 and a second stopper arranged in parallel.
- the second damper composed of 10 is arranged in series.
- the overall rigidity of the first coil spring 7 is set to be much smaller than the overall rigidity of the second coil spring 8. Therefore, the second coil spring 8 is hardly compressed in the rotational direction within a range of torsional angles up to the first gap angles ⁇ 1 and ⁇ 1n.
- FIGS. 10 to 12 show mechanical circuit diagrams during operation
- FIG. 13 shows torsional characteristic diagrams.
- the positive side torsional characteristic of twisting the input rotating body 2 toward the R1 side with respect to the spline hub 3 from the neutral state shown in FIG. 9 is described, and the negative side torsional characteristic is the same. Since there is, explanation is omitted.
- the three-stage torsional characteristics are realized by the first coil spring 7, the second coil spring 8, and the gap angles ⁇ 1p, ⁇ 2p, and ⁇ 3p.
- the retaining plate 22 is set on the jig so that the rivet 27 is inserted into the hole 34 and the hole 33a of the retaining plate 22.
- the positioning pin P since the positioning pin P is set in the jig, it is necessary to set the retaining plate 22 in the direction in which the positioning pin P is inserted into the first hole 28a of the retaining plate 22. That is, the positioning pin P can prevent the retaining plate 22 from being set upside down.
- first cone spring 80, the second cone spring 73, the first friction washer 79, and the second friction washer 72 are assembled to the retaining plate 22.
- the hub flange 6 is assembled on the upper side of the retaining plate 22.
- the first hole 28a is disposed adjacent to the first protrusion 45 of the hub flange 6 in the rotational direction. More specifically, the position of the first hole 28a is such that the positioning pin P contacts the first protrusion 45 in the rotational direction in a state where the hub flange 6 is assembled to the retaining plate 22 at a correct mounting angle. Has been determined.
- the hub flange 6 can be positioned by the positioning pin P, and the hub flange 6 can be easily arranged at the correct position with respect to the retaining plate 22. As a result, it becomes easy to insert the second coil spring 8 into the first window hole 41 and the second window hole 42 in a later step.
- the protrusion 45b interferes with the positioning pin P when the hub flange 6 is assembled reversely with respect to the retaining plate 22. Even if the hub flange 6 is assembled upside down so that the projection 45b and the positioning pin P do not interfere with each other, the projection 45b and the positioning pin P interfere with each other in the rotation direction, so that the first window hole 41 and the holding portion 35 are provided. And the rotational position of the second window hole 42 and the holding portion 35 do not match. As a result, the second coil spring 8 cannot be inserted into the first window hole 41 and the second window hole 42 in the step of assembling the second coil spring 8. In other words, by providing the protrusion 45b, it is possible to reliably prevent the hub flange 6 from being assembled reversely with respect to the retaining plate 22.
- the hub flange 6 After the hub flange 6 is assembled, the first coil spring 7 and the spline hub 3 are assembled to the hub flange 6. Thereafter, the two second coil springs 8 are inserted into the second window holes 42. At this time, since the hub flange 6 is assembled at the correct angle by the positioning pin P, the second coil spring 8 can be easily assembled. Since the rotation direction dimension of the second window hole 42 and the free length of the second coil spring 8 are substantially the same, the hub flange 6 with respect to the retaining plate 22 is assembled by assembling the second coil spring 8 to the second window hole 42. The position of is determined.
- the clutch disk 23 is assembled to the retaining plate 22 so that the rivets 27 are inserted into the holes 24d and 24f. At this time, since it is necessary to assemble the clutch disk 23 to the retaining plate 22 in the direction in which the positioning pin P is inserted into the third hole 24g of the cushioning plate 24, it is possible to prevent the clutch disk 23 from being assembled upside down.
- the clutch plate 21 is assembled to the retaining plate 22 so that the rivet 27 is inserted into the hole 29b. At this time, since it is necessary to assemble the clutch plate 21 to the retaining plate 22 in the direction in which the positioning pin P is inserted into the second hole 29a, it is possible to prevent the clutch plate 21 from being installed upside down.
- a third friction washer 85 is attached to the clutch plate 21 in advance.
- the protrusion 45 b is disposed at a position that overlaps at least a part of the second hole 29 a when the hub flange 6 is assembled to the retaining plate 22 in the reverse direction. Therefore, when the hub flange 6 is assembled to the retaining plate 22 upside down, the protrusion 45b interferes with the positioning pin P inserted into the second hole 29a, and the hub flange 6 is brought to the correct position (mounting angle). It cannot be set. For this reason, an operator can easily recognize that the hub flange 6 is assembled upside down, and an error in the assembling work can be prevented.
- the dimension of the protrusion 45b is determined so that the protrusion 45b overlaps with more than half of the first hole 28a, and the rotational direction dimension of the second window hole 42 is substantially the same as the free length of the second coil spring 8. Therefore, when the hub flange 6 is assembled upside down, the second coil spring 8 cannot be assembled into the second window hole 42. Therefore, the worker can recognize an error in the assembly work at this point.
- the first hole 28 a is disposed radially inward of the first contact portion 49 of the hub flange 6, and therefore, the first projecting portion that is a portion other than the first contact portion 49.
- the main body 45 a is used for positioning the hub flange 6. For this reason, it can prevent that the 1st contact part 49 is damaged at the time of an assembly
- the clutch disk assembly 1 on which the damper mechanism 4 is mounted has been described as an example.
- the present invention is not limited to this.
- the damper mechanism 4 can be applied to other power transmission devices such as a two-mass flywheel and a lockup device for a fluid torque transmission device.
- the first hole 28a is provided in the retaining plate 22 and the second hole 29a is provided in the clutch plate 21 as holes for the positioning pins P.
- either one of the holes (for example, the first hole 28a) is provided. ) Only.
- the protrusion 45b only needs to overlap with at least a part of the first hole 28a and the second hole 29a, and the protrusion 45b may overlap with all of the first hole 28a and the second hole 29a.
- the damper mechanism according to the present invention can increase the efficiency of assembly work, the present invention is useful in a power transmission system.
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Abstract
Description
図1または図2を用いて、本発明に係るダンパー機構4が搭載されたクラッチディスク組立体1について説明する。図1にクラッチディスク組立体1の縦断面概略図、図2にクラッチディスク組立体1の平面概略図を示す。図1のO-O線は、クラッチディスク組立体1の回転軸線である。また、図1の左側にエンジンおよびフライホイール(図示せず)が配置されており、図1の右側にトランスミッション(図示せず)が配置されている。さらに、図2のR1側がクラッチディスク組立体1の回転方向駆動側(正側)であり、R2側がその反対側(負側)である。
ここで、図3~図7を用いてダンパー機構4を構成する各部材について詳細に説明する。図3にダンパー機構4の平面概略図、図4にハブフランジ6の平面図、図5に入力回転体2の平面図、図6および図7にダンパー機構4の部分断面図を示す。
また、ダンパー機構4には、入力回転体2に入力されたトルクを直接伝達するために、ストッパ機構として機能する第1ストッパ9および第2ストッパ10が設けられている。
さらに、ダンパー機構4には、捩り振動をより効果的に吸収・減衰させるために、摩擦抵抗を利用してヒステリシストルクを発生させる摩擦発生機構5が設けられている。具体的には、摩擦発生機構5は、第1摩擦ワッシャ79と、第2摩擦ワッシャ72と、第3摩擦ワッシャ85と、を有している。
図8を用いてクッショニングプレート24について説明する。
一方で、隙間角度θ3pを確保するために、第2当接部57に形成される2つのストッパ面51は、第2窓孔42に形成される2つの第2当接面47よりも回転方向内側に配置されている。具体的には、R1側のストッパ面51は、R1側の第2当接面47よりもR2側に配置されており、R2側のストッパ面51は、R2側の第2当接面47よりもR1側に配置されている。したがって、第2当接部57の回転方向長さは、第2窓孔42の回転方向長さよりも短い。
以上のようなダンパー機構4を機械回路図で示すと、図9のようになる。この機械回路図は、ダンパー機構における各部材の回転方向の関係を模式的に描いたものである。したがって一体回転する部材は同一の部材として取り扱っている。
次に、図9~図13を用いてクラッチディスク組立体1のダンパー機構の動作および捩り特性について説明する。図10~図12に動作中の機械回路図、図13に捩り特性線図を示す。なお、以下の説明は、図9に示す中立状態からスプラインハブ3に対して入力回転体2をR1側に捩っていく正側捩り特性を説明しており、負側捩り特性については同様であるため説明は省略する。
ここで、クラッチディスク組立体1の組み立て作業について説明する。クラッチディスク組立体1の組み立てには、組み立て用の治具(図示せず)が用いられる。この治具は、クラッチディスク組立体1の回転軸Oが鉛直方向と概ね平行になるように、設計されている。治具には、位置決めピンPがセットされている。
以上に説明したクラッチディスク組立体1の特徴を以下にまとめる。(1)
このクラッチディスク組立体1では、位置決めピンPが挿入可能な第1孔28aが第1突出部45と回転方向に隣接して配置されているため、位置決めピンPと第1突出部45とが回転方向に当接するようにハブフランジ6をリテーニングプレート22に対して組み付けると、リテーニングプレート22に対してハブフランジ6を正しい位置(取付角度)にセットしやすくなる。これにより、クラッチディスク組立体1の組み立て作業の効率を高めることができる。
このクラッチディスク組立体1では、リテーニングプレート22に対してハブフランジ6が裏表逆に組み付けられた際に第2孔29aの少なくとも一部と重なり合う位置に突起45bが配置されている。このため、リテーニングプレート22に対してハブフランジ6を裏表逆に組み付けられると、第2孔29aに挿入された位置決めピンPに突起45bが干渉し、ハブフランジ6を正しい位置(取付角度)にセットすることができない。このため、ハブフランジ6を裏表逆に組み付けたことを作業員が容易に認識することができ、組み付け作業のミスを防止することができる。
このクラッチディスク組立体1では、クラッチプレート21が第2孔29aを有しているため、リテーニングプレート22に対してクラッチプレート21が裏表逆に組み付けられるのを防止できる。
このクラッチディスク組立体1では、ハブフランジ6の第1当接部49よりも半径方向内側に第1孔28aが配置されているため、第1当接部49以外の部分である第1突出部本体45aがハブフランジ6の位置決めに用いられる。このため、組み付け時に第1当接部49が損傷するのを防止できる。
本発明の具体的な構成は、前述の実施形態に限られるものではなく、発明の要旨を逸脱しない範囲で種々の変更および修正が可能である。
前述の実施形態では、ダンパー機構4が搭載されたクラッチディスク組立体1を例に説明しているが、これに限定されない。例えば、このダンパー機構4は2マスフライホイールや流体式トルク伝達装置のロックアップ装置などの他の動力伝達装置にも適用可能である。
前述の実施形態では、位置決めピンP用の孔としてリテーニングプレート22に第1孔28a、クラッチプレート21に第2孔29aがそれぞれ設けられているが、いずれか一方の孔(例えば第1孔28a)のみであってもよい。
突起45bは第1孔28aおよび第2孔29aの少なくとも一部と重なり合っていればよく、さらに突起45bが第1孔28aおよび第2孔29aの全部と重なり合っていてもよい。
2 入力回転体(第1回転体の一例)
3 スプラインハブ
4 ダンパー機構
5 摩擦発生機構
6 ハブフランジ(第2回転体の一例)
7 第1コイルスプリング
8 第2コイルスプリング(弾性部材の一例)
9 第1ストッパ
10 第2ストッパ
28 第1本体部(第1部材の一例)
28a 第1孔
29 第2本体部(第2部材の一例)
29a 第2孔
35 保持部
31 連結部
32 当接部
33 固定部
43 切欠き
41 第1窓孔
42 第2窓孔
45 第1突出部
45a 第1突出部本体
45b 突起
46 第2突出部
46a 第2突出部本体
P 位置決めピン
Claims (7)
- 第1部材と、前記第1部材と軸方向に並んで配置された第2部材と、前記第1部材と前記第2部材とを連結する複数の連結部と、を有する第1回転体と、
前記第1および第2部材の軸方向間に配置され前記第1回転体と相対回転可能に設けられた第2回転体と、
前記第1および第2回転体を回転方向に弾性的に連結し前記連結部の回転方向間に配置された複数の弾性部材と、を備え、
前記第2回転体は、前記連結部の回転方向間であって前記連結部と回転方向に当接可能な1対の突出部を有しており、
前記第1部材は、組み立て時に用いられる位置決めピンが挿入可能であり回転軸を挟んで互いに対向する位置に配置された1対の第1孔を有しており、
前記1対の第1孔は、前記1対の突出部と回転方向に隣接して配置されている、
ダンパー機構。 - 前記突出部は、前記弾性部材が収容される開口を有する突出部本体と、前記突出部本体から回転方向に突出し前記第2回転体が前記第1部材に対して裏表逆に組み付けられた際に前記第1孔の少なくとも一部と重なり合う位置に配置された突起と、を有している、
請求項1に記載のダンパー機構。 - 前記第2部材は、前記位置決めピンを挿入可能であり前記1対の第1孔と軸方向に対向する位置に配置された1対の第2孔を有している、
請求項1または2に記載のダンパー機構。 - 前記突出部は、前記連結部と回転方向に当接可能な当接部を有しており、
前記第1孔は、前記当接部よりも半径方向内側に配置されている、
請求項1から3のいずれかに記載のダンパー機構。 - 前記複数の連結部は、隣り合うピッチが異なるように配置されており、
前記突出部は、前記ピッチが大きい前記連結部同士の回転方向間に配置されている、
請求項1から4のいずれかに記載のダンパー機構。 - 前記連結部は、前記第1部材から軸方向に延びる当接部と、前記当接部の端部から半径方向内側へ延び前記第2部材に固定される固定部と、を有しており、
前記第1孔は、前記固定部と前記突出部との回転方向間に配置されている、
請求項5に記載のダンパー機構。 - 前記当接部の回転方向中心は、前記固定部の中心に対して前記第1孔と反対側にずれている、
請求項6に記載のダンパー機構。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/121,104 US8454446B2 (en) | 2008-10-24 | 2009-09-10 | Damper mechanism |
DE112009002555T DE112009002555T5 (de) | 2008-10-24 | 2009-09-10 | Dämpfungsmechanismus |
CN200980142395.6A CN102187117B (zh) | 2008-10-24 | 2009-09-10 | 减振机构 |
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Application Number | Priority Date | Filing Date | Title |
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JP2008-274897 | 2008-10-24 | ||
JP2008274897A JP4451914B1 (ja) | 2008-10-24 | 2008-10-24 | ダンパー機構 |
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WO2010047193A1 true WO2010047193A1 (ja) | 2010-04-29 |
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PCT/JP2009/065853 WO2010047193A1 (ja) | 2008-10-24 | 2009-09-10 | ダンパー機構 |
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JP (1) | JP4451914B1 (ja) |
CN (1) | CN102187117B (ja) |
DE (1) | DE112009002555T5 (ja) |
WO (1) | WO2010047193A1 (ja) |
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JP5576245B2 (ja) * | 2010-11-02 | 2014-08-20 | アイシン・エィ・ダブリュ工業株式会社 | ダンパ装置 |
CN105074271B (zh) * | 2013-04-02 | 2018-10-23 | 舍弗勒技术股份两合公司 | 扭矩传递装置 |
WO2014194358A1 (en) * | 2013-06-04 | 2014-12-11 | Clutch Industries Pty Ltd | A clutch plate |
DE102015212366A1 (de) | 2014-07-30 | 2016-02-04 | Schaeffler Technologies AG & Co. KG | Dämpferbaugruppe mit einer axial befestigten Reibungsbaugruppe |
DE102018108142A1 (de) * | 2018-04-06 | 2019-10-10 | Schaeffler Technologies AG & Co. KG | Kupplungsscheibe mit Pendelwippendämpfer mit nur einer Bewegungsrichtung zwischen seinen Flanschbereichen; sowie Reibkupplung |
JP7236889B2 (ja) * | 2019-03-15 | 2023-03-10 | 株式会社エクセディ | ダンパ装置 |
CN113557370B (zh) * | 2019-07-01 | 2023-07-18 | 舍弗勒技术股份两合公司 | 离合器从动盘及离合器 |
DE102020108408A1 (de) | 2020-03-26 | 2021-09-30 | Schaeffler Technologies AG & Co. KG | Anschlagkonzept für einen Dämpfer mit langem Verdrehwinkel trotz radial eingeschränktem Bauraum |
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JPS59166723A (ja) * | 1983-03-10 | 1984-09-20 | Aisin Seiki Co Ltd | トルク変動吸収装置 |
JPH0972382A (ja) * | 1995-08-31 | 1997-03-18 | Yutaka Giken Co Ltd | 2マス型フライホイール |
JPH09196078A (ja) * | 1996-01-11 | 1997-07-29 | Exedy Corp | ダンパーディスク組立体 |
JPH10196729A (ja) * | 1986-07-05 | 1998-07-31 | Luk Lamellen & Kupplungsbau Gmbh | はずみ車 |
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DE3645258B4 (de) | 1985-09-07 | 2009-04-30 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Einrichtung zur Dämpfung von Drehschwingungen |
JP3434391B2 (ja) * | 1995-06-30 | 2003-08-04 | 株式会社エクセディ | ダンパーディスク組立体 |
US5778738A (en) | 1995-08-31 | 1998-07-14 | Kabushiki Kaisha Yutaka Giken | Two-mass type of flywheel device |
JP4385045B2 (ja) | 2006-10-02 | 2009-12-16 | 株式会社エクセディ | ダンパー機構 |
-
2008
- 2008-10-24 JP JP2008274897A patent/JP4451914B1/ja active Active
-
2009
- 2009-09-10 WO PCT/JP2009/065853 patent/WO2010047193A1/ja active Application Filing
- 2009-09-10 DE DE112009002555T patent/DE112009002555T5/de not_active Ceased
- 2009-09-10 US US13/121,104 patent/US8454446B2/en active Active
- 2009-09-10 CN CN200980142395.6A patent/CN102187117B/zh active Active
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
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JPS59166723A (ja) * | 1983-03-10 | 1984-09-20 | Aisin Seiki Co Ltd | トルク変動吸収装置 |
JPH10196729A (ja) * | 1986-07-05 | 1998-07-31 | Luk Lamellen & Kupplungsbau Gmbh | はずみ車 |
JPH0972382A (ja) * | 1995-08-31 | 1997-03-18 | Yutaka Giken Co Ltd | 2マス型フライホイール |
JPH09196078A (ja) * | 1996-01-11 | 1997-07-29 | Exedy Corp | ダンパーディスク組立体 |
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CN102187117A (zh) | 2011-09-14 |
JP4451914B1 (ja) | 2010-04-14 |
US8454446B2 (en) | 2013-06-04 |
DE112009002555T5 (de) | 2012-09-13 |
CN102187117B (zh) | 2013-07-17 |
JP2010101456A (ja) | 2010-05-06 |
US20110177869A1 (en) | 2011-07-21 |
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