WO2017010085A1 - Dispositif d'amortisseur - Google Patents

Dispositif d'amortisseur Download PDF

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Publication number
WO2017010085A1
WO2017010085A1 PCT/JP2016/003292 JP2016003292W WO2017010085A1 WO 2017010085 A1 WO2017010085 A1 WO 2017010085A1 JP 2016003292 W JP2016003292 W JP 2016003292W WO 2017010085 A1 WO2017010085 A1 WO 2017010085A1
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WO
WIPO (PCT)
Prior art keywords
coil spring
curvature
rotating member
guide
side rotating
Prior art date
Application number
PCT/JP2016/003292
Other languages
English (en)
Japanese (ja)
Inventor
光輝 三村
Original Assignee
日本発條株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日本発條株式会社 filed Critical 日本発條株式会社
Priority to JP2017528289A priority Critical patent/JP6796583B2/ja
Publication of WO2017010085A1 publication Critical patent/WO2017010085A1/fr

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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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/46—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs in which two axially-movable members, of which one is attached to the driving side and the other to the driven side, are pressed from one side towards an axially-located member
    • 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
    • F16F15/131—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 the rotating system comprising two or more gyratory masses
    • F16F15/133—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 the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type

Definitions

  • the present invention relates to a damper device for a torque transmission device such as a lock-up clutch used in a vehicle or the like.
  • An automatic vehicle (hereinafter referred to as an “AT vehicle”) that transmits engine output to an automatic transmission via a fluid transmission such as a torque converter or a fluid coupling is widely known.
  • Some of these fluid transmissions have a lockup clutch provided in parallel so that the engine and the automatic transmission can be directly connected.
  • This lock-up clutch is provided for the purpose of improving fuel efficiency and is generally provided with a damper device to absorb torque vibration accompanying engine rotation.
  • Such a damper device is assembled, for example, in the torque transmission device of Patent Document 1, and has a structure including a driving side rotating member and a driven side rotating member, a coil spring guide, and a coil spring.
  • the driving side rotating member and the driven side rotating member are assembled so as to have the same axis, and the driving side rotating member is configured to receive engine output.
  • the coil spring guide is formed in an arc whose center of curvature is the axis, and is disposed on either the driving side rotating member or the driven side rotating member.
  • the coil spring is housed in an arcuate curved state on the inner peripheral side of the coil spring guide, and both end portions are separately engaged with the driving side rotating member and the driven side rotating member.
  • the coil spring expands and contracts with the relative rotation of the driving side rotating member and the driven side rotating member, and the torque vibration accompanying the engine rotation can be damped.
  • a long coil spring has a problem that hysteresis torque is generated in the transmission torque due to the fact that the middle part of the coil is easily bent so as to bend, and the frictional force increases when the coil spring expands and contracts with respect to the coil spring guide.
  • FIG. 13 is a graph showing the relationship between the torsion angle and the transmission torque during torque transmission between the driving side rotating member and the driven side rotating member.
  • the horizontal axis represents the twist angle
  • the vertical axis represents the transmission torque.
  • the forward torque on the compression side of the coil spring between the driving side rotating member and the driven side rotating member is indicated by a solid line
  • the return path torque on the extension side is indicated by a broken line.
  • FIG. 14 shows the spring restoring force by such assembly.
  • FIG. 14 is an explanatory view showing the spring restoring force, and shows a state in which the coil spring 101 whose coil center line is linear before assembly is assembled to the curved coil spring guide 103.
  • the coil spring 101 is pressed against the coil spring guide 103 by such a spring restoring force P1, and a hysteresis torque is generated by the frictional force.
  • centrifugal force is applied to the spring, so that the spring is pressed against the guide surface, the frictional force is increased, and a larger hysteresis torque is generated.
  • the coil spring 101 bends due to an external force input to the end of the coil spring 101 during the rotation, and the friction between the coil spring 101 and the coil spring guide 103 can be sufficiently reduced. Also, hysteresis torque was generated, and the substantial spring constant could not be reduced sufficiently.
  • FIG. 15 is a diagram for explaining such a situation, and is an explanatory diagram showing a situation of a resultant force when an external force is applied along the coil spring guide.
  • FIG. 16 is an explanatory view showing the damper device with a part cut away
  • FIG. 17 is an explanatory view showing the curvature of the coil spring with respect to the coil spring guide.
  • an arc-shaped (arc-shaped) coil spring 101 is disposed between the claw portion 105a of the driving side rotation member 105 and the claw portion 107a of the driven side rotation member 107, and the coil spring It is accommodated in the guide 103.
  • the coil spring guide 103 is fitted inside a cylindrical portion 109 that is a driving side rotating member.
  • the arc curvature of the coil spring 101 is made larger than the curvature of the coil spring guide 103 to reduce the contact area of the coil spring 101 with the coil spring guide 103.
  • Patent Document 2 It is disclosed in Patent Document 2 that the reduction of the contact area can suppress the generation of hysteresis torque and reduce the substantial spring constant.
  • this damper device has a problem that local wear occurs due to a decrease in the contact area, resulting in failure in stable torque transmission over a long period of time.
  • the central portion of the curve of the coil spring 101 is located on the outer diameter side with respect to the set position of the seating surface 101 a of the coil spring 101, which tends to cause an increase in centrifugal force. Conducive to general wear and tear.
  • the problem to be solved is that the generation of hysteresis torque and the occurrence of local wear could not be suppressed at the same time.
  • a driving side rotating member and a driven side rotating member that are relatively rotatable around a common axis, and the shaft
  • a coil spring guide that is curved with a center of curvature on the center side and is disposed on either the driving side rotating member or the driven side rotating member, and is housed in an arc shape in the coil spring guide, and one end portion is driven
  • a coil spring that engages with the side rotation member and the other end engages with the driven side rotation member, and the coil spring expands and contracts with relative rotation between the drive side rotation member and the driven side rotation member.
  • a damper device for a torque transmission device that dampens input rotation from the driving side rotating member and outputs it from the driven side rotating member, wherein the coil spring has an arc shape in a free state, and the arc-shaped curvature. Center is in front Characterized in that on the opposite side of the coil spring across the axis.
  • the present invention has the above-described configuration, the arc-shaped central portion side of the coil spring can be easily arranged on the axial center side with respect to the end portion, the generation of hysteresis torque is suppressed, and the substantial spring constant is lowered. Generation of local wear can be suppressed and stable torque transmission can be performed.
  • Example 1 It is a front view of a damper device of a lockup clutch.
  • Example 1 It is the perspective view seen from the back side of the damper device of a lockup clutch.
  • Example 1 It is a side view of the damper apparatus of a lockup clutch.
  • Example 1 It is a perspective view which removes the disk of a back surface side and sees a damper apparatus from the back surface side.
  • Example 1 It is a front view which shows the relationship of the curvature radius of a damper apparatus.
  • Example 1 It is a front view which shows the contact angle of the coil spring and claw part of a damper apparatus.
  • Example 1 It is explanatory drawing which shows the reduction
  • Example 1 It is a graph which shows the relationship between the angle of the nail
  • the attachment with the clearance of the coil spring with respect to a coil spring guide is shown, (A) is before rotation, (B) is explanatory drawing at the time of rotation. (Comparative example) It is a graph of the relationship between R3 / R1 of FIG.
  • Example 5 It is a graph which concerns on the comparison of the relationship between transmission torque and hysteresis torque.
  • Example 1 It is a graph which shows the relationship between the twist angle at the time of the torque transmission between a drive side rotation member and a driven side rotation member, and transmission torque.
  • Conventional example It is explanatory drawing which shows the condition of the resultant force when external force is applied along a coil spring guide.
  • Conventional example It is explanatory drawing which shows the curvature of a coil spring with respect to a coil spring guide.
  • a coil spring in which the coil center line forms an arc shape in a free state is used, and the arc-shaped center of curvature is centered on the axis. This is realized by being located on the opposite side of the coil spring.
  • the coil center line of the coil spring only needs to form an arc near the center, and may be a straight line near the seat surface.
  • the drive-side rotating member includes a claw portion that engages with a circumferential edge of the seating surface of the coil spring, and the seating surface and the contact edge pass through the center of curvature of the coil spring. It may be along the radial line.
  • the drive-side rotating member includes a claw portion that engages with a contact edge portion in the circumferential direction on a seating surface of the coil spring, and the contact edge portion is an outer diameter side of the coil spring in the radius direction of curvature. You may contact
  • the coil spring guide may include a guide surface having a curvature that guides the entire outer diameter side of the coil spring in the radius direction of curvature.
  • FIG. 1 is a front view of a damper device of a lockup clutch
  • FIG. 2 is a perspective view as seen from the back side of the damper device of the lockup clutch
  • 3 is a side view of the damper device of the lock-up clutch
  • FIG. 4 is a perspective view showing the damper device viewed from the back side with the disk on the back side removed
  • FIG. 5 is a front view showing the relationship of the radius of curvature of the damper device.
  • FIGS. 6 and 6 are front views showing contact angles between the coil spring and the claw portion of the damper device
  • FIG. 7 is an explanatory diagram showing a decrease in the radial component of the resultant force between the claw portion and the coil spring guide.
  • the rotation direction means the rotation direction of the damper device
  • the radial direction means the radial direction of the damper device.
  • the damper device 1 of the lock-up clutch is rotationally elastic, and during the damping between the claw plate 3 as the driving side rotating member and the disks 5 and 7 as the driven side rotating member.
  • Coil springs 9 for accumulating power are provided at three locations in a 120 ° arrangement. Note that the number of coil springs 9 can be set freely, and for example, it can be configured such that the coil springs 9 are disposed at four locations in an arrangement of 90 ° or the like.
  • the damper device 1 of the lock-up clutch damps and outputs the torque fluctuation of the input rotation from the claw plate 3 by the expansion and contraction of the coil spring 9 as the claw plate 3 and the disks 5 and 7 rotate relative to each other.
  • the claw plate 3 can be a driven side rotating member
  • the disks 5 and 7 can be a driving side rotating member.
  • the lock-up clutch is an example of a torque transmission device.
  • the damper device of the present invention can also be applied to torque transmission devices other than the lockup clutch.
  • the damper device of the present invention can also be applied to a torque transmission device such as a clutch disk used in a manual vehicle or the like, a dual mass flywheel, or a belt that drives automobile auxiliary equipment.
  • the driving side rotating member is a member that receives driving input
  • the driven side rotating member may be a member that performs driving output.
  • the damper device absorbs torque vibration between the driving side rotating member and the driven side rotating member, and the driving side rotating member and the driven side rotating member are members corresponding to the target torque transmission device.
  • the claw plate 3 and the disks 5 and 7 are arranged so as to be relatively rotatable around a common axis.
  • the drive-side claw plate 3 is configured such that a hole 3a is coupled to, for example, the crankshaft side of the engine and receives input from the engine.
  • the discs 5 and 7 on the driven side have holes 5a and 7a coupled to the output side of the torque converter via a friction plate (not shown).
  • the claw plate 3 and the disks 5 and 7 are connected to each other by, for example, three rivets 11 in the circumferential direction.
  • the claw plate 3 and the disks 5 and 7 can be rotated relative to each other and cannot be moved relative to each other in the axial direction.
  • the lockup clutch is locked up.
  • the connection between the engine and the transmission is changed from the torque transmission state by the torque converter to the direct connection state via the damper device 1.
  • the damper device 1 can attenuate the impact of torque transmission between the engine and the transmission during the direct connection and the engine torque vibration after the direct connection.
  • the claw plate 3 is formed with arc-shaped restriction recesses 13 at three positions at 120 ° with respect to the rivet 11.
  • the restricting recess 13 is formed in a concave shape in the radial direction and having a length in the circumferential direction, and has an arcuate length equal to both sides in the rotational direction with respect to the rivet 11 in a stationary state.
  • the relative rotation between the claw plate 3 and the disks 5 and 7 is allowed in the circumferential length range of the regulating recess 13 by the relative guide between the rivet 11 and the regulating recess 13.
  • driving claw plate 3 and the driven disks 5 and 7 can each be formed of a single plate.
  • the claw plate 3 is formed of a plate that is relatively thicker than the disks 5 and 7, and integrally includes a claw portion 15 that protrudes in the radial direction between the circumferential directions of the respective restriction recesses 13.
  • claw part 15 is provided in the circumferential direction 3 places by 120 degree arrangement
  • the claw portion 15 corresponds to the coil spring 9, and if the coil spring 9 is disposed at 90 °, for example, the claw portion 15 is also disposed at 90 ° or the like.
  • the outer peripheral edge 15 a of the claw portion 15 is formed in an arc shape, and the outer peripheral edge 15 a is formed along the outer peripheral edges of the disks 5 and 7.
  • the outer peripheral edge 15a of the claw portion 15 can be arranged on the inner diameter side or the outer diameter side of the outer peripheral edge of the discs 5 and 7, and when arranged on the inner diameter side, the claw portion 15 is disposed on the outer peripheral portion of the discs 5 and 7.
  • a cylindrical portion covering the outer peripheral edge 15a can also be formed.
  • Each claw portion 15 is formed in a concave shape on both sides in the circumferential direction between the outer peripheral edge 15a and the restricting concave portion 13, and the contact edge portions 15b and 15c are linearly formed.
  • the contact edge portions 15b and 15c are set on the seating surface 9a of the coil spring 9 in the circumferential direction. The set angles of the contact edge portions 15b and 15c will be further described later.
  • Coil spring guides 18 and 19 are formed on the disks 5 and 7.
  • the coil spring guides 18 and 19 are curved with a center of curvature on the common axis side of the claw plate 3 and the disks 5 and 7, and are either the driving side rotating member or the driven side rotating member. Then, it is arranged on the disks 5 and 7 of the driven side rotating member.
  • the coil spring guides 18 and 19 of the present embodiment are formed in an arc shape with a constant curvature on the outer peripheral side of the rivet 11.
  • the arc-shaped lengths of the coil spring guides 18 and 19 are formed substantially the same as the length on the coil center line between the seating surfaces 9a and 9b of the coil spring 9 in the free state.
  • the coil spring 9 is housed in an arc shape in the coil spring guides 18 and 19, and one end of the coil spring 9 engages with the claw plate 3 and the other end engages with the disks 5 and 7.
  • the coil spring guides 18 and 19 are composed of guide holes 20 and 21 and guide tongue portions 23a, 23b, 25a and 25b.
  • the radial widths of the guide holes 20 and 21 are formed substantially constant over the circumferential direction.
  • Locking edge portions 20a and 20b and locking edge portions 21a and 21b are linearly formed at both ends in the circumferential direction of the guide holes 20 and 21, respectively.
  • the locking edge portions 20a and 20b and the locking edge portions 21a and 21b are formed so as to face both the seating surfaces 9a and 9b of the coil spring 9, and lock both the seating surfaces 9a and 9b in the circumferential direction. . Therefore, the locking edge portions 21a and 21b are in the circumferential direction ends of the guide holes 20 and 21 in the direction in which both the seating surfaces 9a and 9b are orthogonal to the coil center line, or in the direction orthogonal to the inclined shape, and in the inclined direction. Formed in the part.
  • the guide tongues 23a and 23b and the guide tongues 25a and 25b have a center of curvature on the axial center side of the damper device 1 and are curved in the circumferential direction, either the driving side rotating member or the driven side rotating member. In the example, it is disposed on the disks 5 and 7 of the driven side rotating member.
  • the guide tongues 23 a and 25 a are formed along the outer peripheral side edges of the guide holes 20 and 21, and are integrally cut and raised from the disks 5 and 7.
  • the guide tongues 23 b and 25 b are formed along the radial side edges of the guide holes 20 and 21, and are formed by being cut and raised integrally from the disks 5 and 7.
  • the guide tongues 23 b and 25 b are cut and raised in the cross-sectional direction of the disks 5 and 7.
  • the guide tongues 23 b and 25 b are curved in the cross-sectional direction of the disks 5 and 7.
  • the curvature of curvature in the cross-sectional direction of the guide tongues 23b and 25b substantially matches the coil diameter of the coil spring 9.
  • the guide tongues 23b and 25b can be formed so as to be inclined without being curved in the cross-sectional direction of the disks 5 and 7, or as a locking wall oriented in the axial direction without being inclined.
  • the curvature of the guide tongues 23b and 25b in the cross-sectional direction of the disks 5 and 7 may be a part of the guide tongues 23b and 25b in the circumferential direction, and the remainder may be an inclined surface or the like.
  • the guide tongues 23b and 25b are curved and formed with substantially the same curvature along the outer circumference of the coil spring 9 in the coil circumferential direction, and face the guide holes 20 and 21 side.
  • the guide tongues 23b and 25b are formed over the entire circumferential direction of the guide holes 20 and 21.
  • the guide tongues 23b and 25b can be formed by selecting a part of the guide holes 20 and 21 in the circumferential direction. This selection in the circumferential direction is performed so that the operation of the coil spring 9 is not hindered during the damping operation.
  • the guide tongues 23b and 25b may be set on both ends in the circumferential direction of the guide holes 20 and 21 or on one end.
  • the outer peripheral side edges of the guide holes 20 and 21 and the guide tongue portions 23a and 25a are guided by the guide surfaces 20c and 21c having a curvature that guides the entire outer diameter side of the coil spring 9 in the arc-shaped curvature radius direction. Is provided over the entire length facing the coil spring 9.
  • the guide surfaces 20c and 21c have a curvature corresponding to the curvature of the guide tongues 23b and 25b in the cross-sectional direction of the disks 5 and 7. However, it can also be formed with an inclined surface, a locking surface, or the like having no curvature according to the setting of the guide tongue portions 23b and 25b.
  • the guide tongues 23a and 23b of both the disks 5 and 7 and the guide tongues 25a and 25b are paired to surround the coil spring 9 from the coil radial direction.
  • the coil spring guides 18 and 19 guide the expansion and contraction of the coil spring 9 along the guide holes 20 and 21 while preventing the coil spring 9 from falling off.
  • the guide tongues 23a and 23b and the guide tongues 25a and 25b can be formed separately from the disks 5 and 7 and can be assembled to the disks 5 and 7 by welding, bonding, screwing or the like.
  • the guide tongue portions 23a and 23b and the guide tongue portions 25a and 25b can be partly cut and raised, and the others can be assembled to the disks 5 and 7 by welding, bonding, screwing or the like.
  • the guide tongue can be replaced with a guide provided on the claw plate 3 which is a driving side rotating member.
  • the guide portion is set in a range in which the operation of compressing the coil spring 9 can be secured, and the guide portion is configured to rotate together with the claw plate 3. At this time, the guide portion can perform the functions described later in the relative relationship with the coil spring 9.
  • the guide tongue portions 23a and 23b are not limited to the form cut and raised from the disk 5, but can be formed as an integral guide portion in which the portions are continuous in a circular arc shape.
  • the integrated guide portion having an arcuate cross section may be formed of a plate member separate from the disk 5 and fixed to the edge portion of the guide hole 20 by welding, bonding, screwing or the like.
  • the guide tongues 25a and 25b can be formed as an integral guide part that is continuous in an arc shape in cross section. And can be fixed to the edge of the guide hole 21 later by welding, bonding, screwing or the like.
  • the coil spring guides 18 and 19 are not limited to the guide holes 20 and 21, the guide tongue portions 23 a and 23 b, and the guide tongue portions 25 a and 25 b, but a two-member configuration including a concave guide portion and a cover serving as a lid thereof. Etc. can also be formed.
  • the claw plate 3 is disposed side by side between the disks 5 and 7, for example, a guide portion curved in the circumferential direction is hooked to the disk 7.
  • a cover that is attached by hooking or the like and has a circular cross-sectional shape facing the guide portion and having a circumferentially curved portion is attached to the disk 5, and a spring holding space for guiding the coil spring 9 is formed between the guide portion and the cover.
  • the claw portion of the claw plate 3 is bent, for example, in the thickness direction of the disks 5 and 7 and is disposed opposite to the end portion of the coil spring 9 in the circumferential direction.
  • the end portion of the coil spring 9 is exposed to an opening portion for the circumferential operation range of the claw portion formed by cutting the cover, and the claw portion is exposed to the end portion of the coil spring 9 from this opening portion.
  • the discs 5 and 7 are provided as one piece, and the claw plate 3 is disposed side by side with the single disc.
  • a guide portion that is substantially cylindrical and covers the coil spring is attached to a single disk, and the claw portion of the claw plate 3 is bent in the disc thickness direction, for example, and is disposed opposite to the end portion of the coil spring 9 in the circumferential direction. Is done.
  • the end portion of the coil spring 9 is exposed to an opening portion for the circumferential operation range of the claw portion formed by cutting out the guide portion, and the claw portion faces the end portion of the coil spring 9 from this opening portion.
  • a coil spring 9 is disposed in the guide holes 20 and 21 on the inner periphery of the guide tongue portions 23a and 23b and the guide tongue portions 25a and 25b.
  • the coil spring 9 is housed in an arc shape in the coil spring guides 18 and 19, and the seating surfaces 9 a and 9 b at both ends engage with the claw plate 3 which is a driving side rotating member and the disks 5 and 7 which are driven side rotating members. To do.
  • the coil spring 9 is formed in an arc shape (arc shape) having a constant curvature in the direction along the coil center line in the free state.
  • the curvature radius of the arc-shaped outer periphery side of the coil spring 9 is formed so as to substantially coincide with the curvature radius of the guide tongue portions 23a and 25a in the circumferential direction.
  • the arc shape of the coil spring 9 prevents the surface pressure from concentrating locally when it is accommodated in the coil spring guides 18 and 19. For this reason, at least a part of the coil of the coil spring 9 is in an arc shape in a free state, and the arc-shaped curvature only needs to substantially match the arc-shaped curvature of the coil spring guides 18 and 19.
  • the seating surfaces 9a and 9b of the coil spring 9 are directed to the radial direction side of the damper device 1 orthogonal to the coil center line in this embodiment.
  • the directivity of the seating surfaces 9a and 9b toward the radial direction can be appropriately inclined.
  • the coil springs are inserted into the guide holes 20 and 21 so that the seating surfaces 9a and 9b are engaged with the locking edges 20a and 20b and the locking edges 21a and 21b of the guide holes 20 and 21 in a free state. 9 is housed. In this state, the contact edge portions 15 b and 15 c of the claw portion 15 are also opposed to the seating surfaces 9 a and 9 b of the coil spring 9.
  • FIG. 5 is a front view showing the relationship of the radius of curvature of the damper device.
  • R1 A circle (rotation on the claw portion 15) passing through the point where the coil center line of the coil spring 9 intersects at the position of both seating surfaces 9a, 9b of the coil spring 9 with the rotation center (axial center) O1 as the origin. Radius of curvature). However, depending on the arrangement of the coil spring 9 and the coil spring guides 18 and 19, when one of the seat surfaces 9a and 9b of the coil spring 9 is relatively shifted to the inner diameter side, both seat surfaces of the coil spring 9 are used.
  • R2 The shortest distance from the rotation center O1 to the coil center line of the coil spring 9.
  • R3 The radius of curvature of the arc-shaped coil center line of the coil spring 9 is used.
  • each R is set so that R3> R1> R2. Therefore, the center of curvature O3 of the coil center line of the coil spring 9 is located on the opposite side of the coil spring 9 and the coil spring guides 18 and 19 with the axis O1 of the damper device 1 interposed therebetween.
  • a circle having the axis O1 as the origin and a radius R1 and a circle having the center of curvature O3 as the origin and a radius R3 intersect each other.
  • the arc-shaped curvatures of the coil spring guides 18 and 19 and the arc-shaped curvature of the coil spring 9 are set to substantially coincide with each other. Therefore, the arc-shaped curvature centers of the coil spring guides 18 and 19 are set.
  • the position of the center of curvature O3 of the coil center line of the coil spring 9 is set such that the shortest distance R2 from the rotation center O1 to the coil center line of the coil spring 9 is shorter than the radius of curvature R1 and the working radius of the centrifugal force is increased. Try to decrease. Therefore, the position of the curvature center O3 is not particularly limited as long as it is located on the opposite side of the coil spring 9 and the coil spring guides 18 and 19 with the axis O1 of the damper device 1 interposed therebetween.
  • the coil center line comes on the rotation locus of the claw portion 15. Accordingly, the coil spring is arranged on a circle having a radius R1 with the rotation center (axial center) O1 as the origin.
  • both seating surfaces 9a and 9b of the coil spring 9 are located on the same circumference with respect to the rotation center (axial center) O1, and are located symmetrically with respect to the coil center.
  • the both seating surfaces 9a and 9b of the coil spring 9 are not limited to being located on the same circumference, and one of the seating surfaces 9a and 9b may be positioned somewhat on the inner diameter side with respect to the other.
  • R1 has the rotation center (axial center) O1 as the origin, and the seat surface 9a, 9b located relatively on the inner diameter side between the coil center line of the coil spring 9 and the both seat surfaces 9a, 9b of the coil spring 9.
  • the radius of curvature of the circles that coincide at one of the positions is set, and the relationship of each R is similarly set.
  • the coil spring guides 18 and 19 and the coil spring 9 may be formed in an arc shape with the same curvature, and the arc-shaped curvature may be changed slightly by making the curvature on the central side relatively small along the coil center. Good.
  • the center of curvature O3 of the present embodiment is a coil in which the coil spring 9 is accommodated on the plane passing through the center of the coil spring guides 18 and 19 and the coil spring 9 in the arcuate circumferential direction with the rotation center (axial center) O1 interposed therebetween.
  • the spring guides 18 and 19 are positioned so as to be shifted to the opposite side.
  • FIG. 6 is a front view showing the contact angle between the coil spring and the claw portion of the damper device.
  • the contact edge portions 15b and 15c of the claw portion 15 are in a so-called surface pressing state in which the entire contact edge portions 15b and 15c press the entire seating surfaces 9a and 9b, respectively, at the time of damping. Yes.
  • L1 a radial line passing through the position of the seating surface on the rotation center (axial center) O1 and the coil center line (a line oriented in the radial direction and a line directed to the radial direction and not necessarily coincident with the radial direction, but on the radial direction side) Including both directing lines).
  • L2 Radial direction line passing through the position of the seating surface on the center of curvature O3 of the coil center line of the coil spring 9 and the coil center line (a line oriented in the radial direction and a line directed to the radial direction and not necessarily in the radial direction, but on the radial direction side) Including both directing lines).
  • L3 The contact edge 15b (15c) (see FIG.
  • ⁇ 1 The angles of the contact edge 15b (15c), the locking edge 20a (20b), and the locking edge 21a (21b) of the claw portion 15.
  • ⁇ 2 is the angle of the seating surface 9a (9b).
  • the seating surfaces 9a and 9b of the coil spring 9, the contact edges 15b and 15c of the claw 15 and the locking edges 20a and 20b and the locking edges 21a and 21b of the guide holes 20 and 21 are in the radial line L2. It becomes the form along. This form is a so-called surface pressing state.
  • ⁇ 1> 0 and ⁇ 2> 0 can also be set.
  • the contact edge portions 15b and 15c are in contact with the seating surfaces 9a and 9b at a position biased toward the outer radius side of the radius of curvature of the coil spring 9, which is a so-called outer peripheral pushing state.
  • the biased positions where the contact edge portions 15b and 15c contact the seating surfaces 9a and 9b are set by the relative relationship between the contact edge portions 15b and 15c and the seating surfaces 9a and 9b, and Can be changed.
  • the selection of the surface pressing and the outer periphery pressing can be performed by setting the seating surfaces 9a and 9b for the coil spring 9.
  • the contact edge portions 15b and 15c of the claw portion 15 and the locking edge portions 20a and 20b and the locking edge portions 21a and 21b of the guide holes 20 and 21 are formed along the radial line L2, and the seat surface 9a and 9b can be inclined with respect to the radial line L2 by being inclined and polished with respect to the coil center line of the coil spring 9, and the outer periphery can be pushed.
  • the contact state with the friction member can be controlled, and the input / output side of the torque converter can be engaged in a slip state in which the torque converter relatively rotates at a predetermined relative rotational speed.
  • the coil spring 9 is in contact with the contact edge portions 15b and 15c involved in torque transmission, for example, the contact edge portion 15c, the locking edge portions 20a and 21a, and the locking edge. Torque fluctuations are absorbed by expansion and contraction between one of the edges 20b and 21b, for example, the locking edges 20a and 21a, and the torque transmitted to the output side of the torque converter is stabilized.
  • the radial outward force acting on the coil spring 9 during torque transmission is reduced as compared with a conventional general arc-shaped coil spring.
  • FIG. 7 is an explanatory diagram showing a decrease in the resultant force acting in the radial direction between the claw portion and the coil spring guide.
  • the coil center line is on a circle C2 having a radius R3 with O3 as the origin.
  • the general arc-shaped coil spring will be described together.
  • the coil center line is on a circle C1 having a radius R1 with O1 as the origin.
  • the pressing force acting on the claw portion and the engaging edge of the guide hole on the seat surface 9 b of the coil spring 9 acts in the tangential direction of the coil center line of the coil spring 9. .
  • a pressing force acts on one of the seat surfaces 9a and 9b of the coil spring, for example, the seat surface 9b from the claw portion 15 and the guide holes 20 and 21 in the direction of arrow A2 in FIG.
  • the resultant force acting in the radial direction decreases to the size of the arrow B2.
  • the shortest distance R2 (see FIG. 5) from the rotation center O1 to the coil spring 9 can be made smaller than the radius R1 of the arc-shaped coil spring having a general arrangement.
  • the centrifugal force acting on the coil spring 9 at the time of high rotation is reduced as compared with an arc-shaped coil spring having a general arrangement.
  • the outer diameter side of the arc-shaped radius of curvature of the coil spring 9 is pressed against the outer edge side of the guide holes 20 and 21 and the guide surfaces inside the guide tongues 23a and 25a by centrifugal force. Hysteresis torque is reduced compared to a typical arrangement of arcuate coil springs.
  • the coil spring 9 when the coil spring 9 receives a force outward or radially outward in the direction of arrow A2 in FIG. 7 by a pressing force or centrifugal force, the arc-shaped radius of curvature of the coil spring 9 is outside the guide holes 20 and 21. It is guided by being entirely pressed against the guide surfaces on the edge side and inside the guide tongues 23a, 25a in the circumferential direction. This overall guide suppresses local wear and stress generation of the coil spring 9.
  • FIG. 8 is a graph showing the relationship between the angle of the claw portion with respect to the seat surface and the hysteresis torque
  • FIG. 9 is an explanatory diagram showing the contact of the claw portion with the outer diameter side of the seat surface.
  • the hysteresis torque changed with respect to the angle of the claw portion with respect to the seating surface.
  • the measurement was performed by applying a general torque measuring device and mounting a coil spring and a claw portion corresponding to this embodiment.
  • the inner peripheral pushing in FIG. 8 is a form in which the contact edges 15b and 15c of the claw 15 are brought into contact with the seating surfaces 9a and 9b at a position biased toward the inner radius side of the coil spring 9 in the radius direction of curvature. This contact form is a state opposite to the outer peripheral pushing state.
  • the hysteresis torque increased with an increase in the angle in the minus direction in the inner peripheral pushing state, and the hysteresis torque was almost unchanged in the outer peripheral pushing state.
  • the state in which the hysteresis torque does not change regardless of the increase in the claw angle in the outer peripheral pushing state is the contact state on the left side of FIG.
  • the claw portion 15 abuts against the seating surface 9 b of the coil spring 9, but the angle of the seating surface 9 b does not follow the angle of the claw portion 15, and the force direction does not change, so the hysteresis torque changes. There is no.
  • the hysteresis torque can be suppressed by selecting the outer peripheral pressing state or the surface pressing state in the contact of the contact edge portions 15b, 15c of the claw portion 15 with the seating surfaces 9a, 9b of the coil spring 9.
  • FIG. 10 shows the attachment of the coil spring guide with a gap of the coil spring, (A) is an explanatory view before rotation, and (B) is an explanatory view during rotation.
  • the coil spring 9 is deformed like a bow so as to be bent in the coil radial direction (spring lateral folding), and high stress is generated in the portion 9c having a high curvature.
  • the durability is low and the long-term stable operation cannot be performed.
  • the side edges and the guide tongues 23a and 25a are configured to guide and contact the outer diameter side of the arc-shaped curvature radius direction of the coil spring 9 as a whole, and bend the spring, suppress the spring restoring force, local wear Was able to be suppressed.
  • the claw plate 3 and the discs 5 and 7 which can be relatively rotated around a common axis, and the disc 5 and 7 which are curved with a center of curvature on the axis side are arranged.
  • Coil spring guides 18 and 19 and coil springs 9 which are housed in an arcuate curved state on the inner peripheral side of the coil spring guides 18 and 19 and whose both ends engage with the claw plate 3 and the disks 5 and 7.
  • the coil spring 9 In the free state, the coil spring 9 has an arc-shaped coil center line, and the arc-shaped curvature center O3 is located on the opposite side of the coil spring guides 18 and 19 across the axis O1.
  • the radially outward force acting on the coil spring 9 can be reduced as compared with a conventional arc coil spring having a general arrangement, and generation of hysteresis torque can be suppressed.
  • the substantial spring constant can be lowered.
  • FIG. 11 is a graph showing the relationship between R3 / R1 in FIG. 5 and the reduction rate of hysteresis torque.
  • the rate of decrease in hysteresis torque increases significantly until R3 / R1 is 1.3, and gradually increases beyond that. That is, in FIG. 5, the hysteresis torque was measured with the coil spring guide and the coil spring as arcs of a general arrangement, and this case was compared as R1.
  • R3 / R1 is desirably higher than 1.3.
  • R3 / R1 is not as good as it is large, but is preferably about 1.3.
  • FIG. 12 shows the relationship between the torsion angle and the transmission torque at the time of torque transmission with the same transmission torque for the general arc coil spring and the coil spring 9 of the embodiment of the present invention.
  • the torque change due to the coil spring of a general arc is T2
  • the torque change due to the coil spring 9 of the embodiment of the present invention is T2
  • the generation of hysteresis torque is suppressed.
  • the coil spring 9 can bring the arc-shaped intermediate portion closer to the center of rotation with respect to the support position in the radial direction of the seating surfaces 9a, 9b, and the mounting state of the arc-shaped coil spring of the conventional general arrangement
  • the centrifugal force can be reduced compared to
  • the claw plate 3 includes claw portions 15 that engage the contact edges 15b and 15c facing in the circumferential direction with the seat surfaces 9a and 9b of the coil spring 9, and the seat surfaces 9a and 9b and the contact edges 15b and 15c. Is along a radial line passing through the center of curvature O3 of the coil spring 9.
  • the claw portion 15 can be brought into the face-pressed state on the coil spring 9 as described above, and the hysteresis torque can be reliably suppressed as shown in FIG.
  • the claw plate 3 includes a claw portion 15 that engages the contact edges 15 b and 15 c facing in the circumferential direction with the seating surfaces 9 a and 9 b of the coil spring 9, and the contact edges 15 b and 15 c It abuts on the seating surfaces 9a and 9b at a position biased toward the outer diameter side in the radius direction of curvature.
  • the claw portion 15 can be pushed to the outer periphery of the coil spring 9, and the hysteresis torque can be reliably suppressed as shown in FIG.
  • the coil spring guides 18 and 19 are provided with a guide surface having a curvature that guides the entire outer diameter side of the coil spring 9 in the radius direction of curvature in the outer peripheral side edges of the guide holes 20 and 21 and the guide tongues 23a and 25a.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Springs (AREA)

Abstract

L'invention concerne un dispositif d'amortisseur pour un dispositif de transmission de couple tel qu'un embrayage de verrouillage pour permettre une suppression simultanée de génération de couple d'hystérésis et d'apparition d'usure locale. Le dispositif d'amortisseur (1) pour un dispositif de transmission de couple comprend : des disques (5, 7) et une plaque de cliquet (3) qui peuvent tourner les uns par rapport aux autres autour d'un axe commun ; des guides de ressort hélicoïdaux (18, 19) qui sont incurvés avec le centre de courbure qui est situé du côté de l'axe, et qui sont disposés au niveau de l'un ou l'autre des disques (5 ou 7) ; et un ressort hélicoïdal (9) qui est renfermé sous une forme d'arc du côté de périphérie interne des guides de ressort hélicoïdaux (18, 19), qui a une extrémité venant en prise avec la plaque de cliquet (3), et dont l'autre extrémité vient en prise avec les disques (5, 7). Le ressort hélicoïdal (9) est comprimé et dilaté en association avec une rotation relative entre la plaque de cliquet (3) et les disques (5, 7) pour amortir une rotation d'entrée à partir de la plaque de cliquet (3), et la rotation amortie est délivrée par les disques (5, 7). L'enroulement du ressort hélicoïdal (9) se présente sous une forme d'arc dans un état libre, et le centre de courbure (O3) de la forme d'arc est situé du côté opposé aux guides de ressort hélicoïdaux (18, 19) par rapport à un axe (O1).
PCT/JP2016/003292 2015-07-13 2016-07-12 Dispositif d'amortisseur WO2017010085A1 (fr)

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JP2015139603 2015-07-13

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08105508A (ja) * 1994-10-05 1996-04-23 Toyota Motor Corp 車両用ロックアップクラッチのダンパ装置
US20050239557A1 (en) * 2004-04-21 2005-10-27 Zf Friedrichshafen Ag Torsional vibration damper
US20070017767A1 (en) * 2005-07-22 2007-01-25 Zf Friedrichshafen Ag Torsional vibration damper
WO2013146659A1 (fr) * 2012-03-27 2013-10-03 アイシン・エィ・ダブリュ工業株式会社 Ressort en arc et dispositif amortisseur

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08105508A (ja) * 1994-10-05 1996-04-23 Toyota Motor Corp 車両用ロックアップクラッチのダンパ装置
US20050239557A1 (en) * 2004-04-21 2005-10-27 Zf Friedrichshafen Ag Torsional vibration damper
US20070017767A1 (en) * 2005-07-22 2007-01-25 Zf Friedrichshafen Ag Torsional vibration damper
WO2013146659A1 (fr) * 2012-03-27 2013-10-03 アイシン・エィ・ダブリュ工業株式会社 Ressort en arc et dispositif amortisseur

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