WO2016167026A1 - Amortisseur de vibrations dynamique - Google Patents

Amortisseur de vibrations dynamique Download PDF

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Publication number
WO2016167026A1
WO2016167026A1 PCT/JP2016/055302 JP2016055302W WO2016167026A1 WO 2016167026 A1 WO2016167026 A1 WO 2016167026A1 JP 2016055302 W JP2016055302 W JP 2016055302W WO 2016167026 A1 WO2016167026 A1 WO 2016167026A1
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WO
WIPO (PCT)
Prior art keywords
torque
input
dynamic vibration
drive plate
plate
Prior art date
Application number
PCT/JP2016/055302
Other languages
English (en)
Japanese (ja)
Inventor
富山　直樹
Original Assignee
株式会社エクセディ
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 株式会社エクセディ filed Critical 株式会社エクセディ
Priority to DE112016000892.9T priority Critical patent/DE112016000892T5/de
Publication of WO2016167026A1 publication Critical patent/WO2016167026A1/fr

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Classifications

    • 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
    • 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
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • 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
    • F16H2045/0205—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type two chamber system, i.e. without a separated, closed chamber specially adapted for actuating a lock-up clutch
    • 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
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0263—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means the damper comprising a pendulum
    • 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

  • a conventional torque converter has been proposed that has a lockup device and an inertia member attached to an output member of the lockup device (see Patent Document 1).
  • an inertia member (84 in Fig. 1) is used to attenuate the torque fluctuation output from the output member of the lockup device.
  • variation of the torque output from the output member of a lockup apparatus is attenuate
  • the torque fluctuation from the lockup device is attenuated by the relative movement of the inertia member with respect to the output member.
  • the vibration response in the rotation speed range to be attenuated can be reduced.
  • the vibration response may increase in a rotational speed range different from the rotational speed range to be attenuated, for example, in a rotational speed range larger than the rotational speed range to be attenuated.
  • the present invention has been made in view of the above problems, and an object of the present invention is to provide a dynamic vibration absorber capable of appropriately attenuating torque fluctuations in a wide range of rotation speeds.
  • a dynamic vibration damping device is for attenuating fluctuations in torque transmitted from an engine to a transmission.
  • the present dynamic vibration absorber includes an input unit, an inertial mass unit, a connecting unit, an elastic unit, and an output unit.
  • the input unit can be rotated by inputting torque.
  • the inertial mass unit can attenuate the torque fluctuation input to the input unit by moving relative to the input unit.
  • a connection part connects an input part and an inertial mass part so that relative movement is possible.
  • the connecting part can swing between the input part and the inertial mass part. Torque is transmitted to the connecting portion from the input portion and the inertial mass portion.
  • the elastic part elastically connects the input part and the inertial mass part.
  • the output unit supports the coupling unit in a swingable manner. The output unit outputs torque transmitted from the input unit and the inertial mass unit to the coupling unit.
  • the connecting part swings between the input part and the inertial mass part with respect to the output part, while the inertial mass part receives the input. Move relative to the part.
  • the torque fluctuation is attenuated by the relative movement of the inertial mass portion with respect to the input portion.
  • the torque transmitted from the input unit and the inertia mass unit to the connecting unit is output from the output unit.
  • the inertial mass unit moves relative to the input unit by swinging between the input unit and the inertial mass unit in a state where the coupling unit is engaged with the input unit and the inertial mass unit.
  • the connecting portion can reliably connect the input portion and the inertia mass portion, and can stably swing between the input portion and the inertia mass portion. That is, the dynamic vibration absorber can be operated smoothly with an easy configuration.
  • the dynamic vibration damping device is preferably configured as follows.
  • the input part has a first engagement part with which the connecting part engages in a direction away from the rotation center of the input part.
  • the inertial mass portion has a second engagement portion with which the connecting portion engages in a direction away from the rotation center of the input portion.
  • the connecting portion can swing with reference to the swing center between the first engaging portion and the second engaging portion.
  • the connecting portion engages with the first engaging portion of the input portion and engages with the second engaging portion of the inertia mass portion in a direction away from the rotation center of the input portion.
  • the inertial mass portion moves relative to the input portion by the connecting portion swinging with respect to the swing center between the first engaging portion and the second engaging portion.
  • the dynamic vibration damping device is preferably configured as follows. When the elastic part is actuated, the connecting part swings with respect to the output part between the input part and the inertial mass part.
  • the dynamic vibration absorber according to another aspect of the present invention is preferably configured as follows.
  • the connecting portion swings with respect to the output portion in a state where the swing center of the connecting portion does not substantially move due to torque fluctuation.
  • the dynamic vibration damping device is preferably configured as follows. When the elastic part is not activated, the connecting part moves together with the input part and the inertial mass part without substantially swinging.
  • the torque input to the input unit can be efficiently output from the output unit.
  • the torque input to the input unit can be efficiently output from the output unit by operating the dynamic vibration absorber with the above-described configuration at a rotational speed at which attenuation of torque fluctuation is not required.
  • the dynamic vibration damping device is preferably configured as follows. Torque output from the lockup device of the torque converter is input to an input unit connected to the lockup device. Then, the torque output from the output unit is transmitted to the transmission.
  • torque fluctuations included in the torque output from the lockup device can be further attenuated. That is, the torque fluctuation can be attenuated step by step by the lockup device and the dynamic vibration absorber.
  • FIG. 1 is a partial sectional view of a torque converter 1 according to an embodiment of the present invention.
  • An engine (not shown) is arranged on the left side of FIG. 1, and a transmission (not shown) is arranged on the right side of the figure.
  • the rotating shaft of the torque converter 1 is indicated by a symbol O.
  • the axial direction is a direction in which the rotation axis O of the torque converter 1 extends or a direction along the rotation axis O of the torque converter 1.
  • the circumferential direction is a direction around the rotation axis O of the torque converter 1.
  • the radial direction is a direction away from the rotation axis O of the torque converter 1.
  • the torque converter 1 is a device for transmitting torque from an engine-side crankshaft (not shown) to a transmission input shaft, and includes a front cover 2 fixed to an engine-side member and three types of impellers ( A torque converter main body 6 including an impeller 3, a turbine 4, and a stator 5), a lockup device 7, and a dynamic vibration absorber 8 are configured.
  • the front cover 2 is a disk-shaped member, and an outer peripheral cylindrical portion 10 that protrudes toward the transmission side is formed on the outer peripheral portion thereof.
  • the impeller 3 includes an impeller shell 12 fixed to the outer peripheral cylindrical portion 10 of the front cover 2 by welding, a plurality of impeller blades 13 fixed to the inside thereof, and a cylindrical shape provided on the inner peripheral side of the impeller shell 12.
  • the impeller shell 12 has a shell body 12a and an outer shell 12b fixed to the outer periphery of the shell body 12a.
  • the outer shell 12b is fixed to the outer cylindrical portion 10 of the front cover 2 by welding.
  • the inner peripheral portion of the shell body 12a is fixed to the impeller hub 14 by welding.
  • the turbine 4 is disposed to face the impeller 3 in the fluid chamber.
  • the turbine 4 includes a turbine shell 15, a plurality of turbine blades 16 fixed to the turbine shell 15, and a turbine hub 17 fixed to the inner peripheral side of the turbine shell 15.
  • the turbine hub 17 has a flange 17a extending to the outer peripheral side.
  • the inner peripheral portion of the turbine shell 15 is fixed to the flange 17 a by a plurality of rivets 18.
  • An input shaft of a transmission (not shown) is splined to the inner peripheral portion of the turbine hub 17.
  • the stator 5 is disposed between the inner periphery of the impeller 3 and the inner periphery of the turbine 4.
  • the stator 5 is a mechanism for rectifying hydraulic fluid that returns from the turbine 4 to the impeller 3.
  • the stator 5 is mainly composed of a stator carrier 5a and a plurality of stator blades 21 provided on the outer peripheral surface thereof.
  • the stator carrier 5a is supported on the fixed shaft via a one-way clutch.
  • the lockup device 7 is disposed in a space between the front cover 2 and the turbine 4.
  • the lockup device 7 includes a piston 24, a first drive plate 25, a first torsion spring 26, and a first driven plate 28.
  • the piston 24 is a disk-shaped plate and is disposed on the transmission side of the front cover 2.
  • a cylindrical portion 24 a extending to the transmission side is formed at the inner peripheral end of the piston 24.
  • the cylindrical portion 24a is supported on the outer peripheral surface of the turbine hub 17 so as to be axially movable and relatively rotatable.
  • a flat portion 24 b is formed on the outer peripheral portion of the piston 24.
  • An annular friction material 33 is fixed to the surface of the flat portion 24b on the front cover 2 side. When the friction material 33 is pressed against the front cover 2, torque is transmitted from the front cover 2 to the piston 24. That is, the piston 24 and the friction material 33 constitute a clutch portion.
  • a stepped portion including a small-diameter portion 17b on the engine side and a large-diameter portion 17c on the transmission side is formed on the outer peripheral side of the turbine hub 17.
  • the piston 24 is supported by the small diameter portion 17b.
  • a seal member 35 is attached to the small diameter portion 17b. Thereby, the space between the inner peripheral surface of the piston 24 and the turbine hub 17 is sealed. Further, the axial movement of the piston 24 toward the transmission side is restricted by the tip of the cylindrical portion 24a coming into contact with the side surface of the large diameter portion 17c.
  • the first drive plate 25 is fixed to the side surface on the transmission side in the outer peripheral portion of the piston 24. Specifically, the first drive plate 25 is formed in a substantially annular shape. An inner peripheral portion 25 a of the first drive plate 25 is fixed to a transmission side surface of the piston 24 by a rivet 37. A plurality of first engaging portions 25 b are formed on the outer peripheral portion of the first drive plate 25. The first engaging portion 25b is formed by bending the outer peripheral portion of the first drive plate 25 toward the transmission side and the rotating shaft O side. The first engaging portion 25 b is engaged with both ends of the first torsion spring 26 in the circumferential direction.
  • first spring holding portions 25c protruding toward the transmission side are formed in the radial direction intermediate portion of the first drive plate 25.
  • the plurality of first spring holding portions 25c are formed at predetermined intervals in the circumferential direction.
  • Each first spring holding portion 25 c supports the inner peripheral side of the first torsion spring 26.
  • the first driven plate 28 has a driven main body portion 28a, a second engagement portion 28b, and a second spring holding portion 28b.
  • the driven main body 28a is connected to a dynamic vibration absorber 8 to be described later. By this connection, torque is transmitted from the lockup device 7 to the dynamic vibration absorber 8.
  • the driven main body portion 28a is formed in an annular shape.
  • the second engaging portion 28b is a portion extending from the driven main body portion 28a to the engine side.
  • the second engagement portion 28b is formed integrally with the driven main body portion 28a.
  • the second engaging portions 28b are provided at a predetermined interval in the circumferential direction.
  • a first torsion spring 26 is disposed between the second engaging portions 28b adjacent to each other in the circumferential direction.
  • the second engaging portion 28 a is engaged with both ends of the first torsion spring 26 in the circumferential direction.
  • the second spring holding portion 28b is a recess provided between the second engaging portions 28a adjacent to each other in the circumferential direction.
  • the second spring holding portion 28b restricts the movement of the first torsion spring 26 toward the transmission side.
  • the dynamic vibration absorber 8 is for attenuating fluctuations in torque transmitted from the engine to the transmission. Specifically, the dynamic vibration damping device 8 is for attenuating fluctuations in torque output from the lockup device 7.
  • the rotation center of the second drive plate 51 (described later) is used in the same meaning as the rotation axis of the second drive plate 51.
  • the rotation axis of the second drive plate 51 is coaxial with the rotation axis O of the torque converter 1.
  • the axial direction is a direction in which the rotation axis O of the second drive plate 51 extends or a direction along the rotation axis O of the second drive plate 51.
  • the circumferential direction is a direction around the rotation axis O of the second drive plate 51.
  • the radial direction is a direction away from the rotation axis O of the second drive plate 51.
  • the dynamic vibration absorber 8 includes a second drive plate 51 (an example of an input unit), an inertia ring 53 (an example of an inertia mass unit), a link unit 55 (an example of a connecting unit), 2 torsion springs 57 (an example of an elastic part) and a second driven plate 59 (an example of an output part).
  • the second drive plate 51 is configured to be rotatable by inputting torque.
  • the second drive plate 51 is connected to the first driven plate 28.
  • the second drive plate 51 is fixed to the first driven plate 28.
  • the second dry plate may be formed integrally with the first driven plate 28.
  • the second drive plate 51 has a main plate 61, a side plate 63, and an inner pin 65 (an example of a first engagement portion).
  • the main plate 61 is fixed to the first driven plate 28. Specifically, the main plate 61 is fixed to the driven main body portion 28a of the first driven plate 28 by fixing means such as welding.
  • the main plate 61 has a first spring storage part 71 and a link storage part 72.
  • the first spring storage portion 71 is formed in a substantially annular shape.
  • the first spring accommodating portion 71 has a plurality of (for example, four) first window portions 71a.
  • a second torsion spring 57 is disposed in the first window portion 71a.
  • a pair of wall portions opposed to each other in the circumferential direction in the first window portion 71 a abuts against both end portions of the second torsion spring 57.
  • the link storage unit 72 stores the link unit 55.
  • the link storage portion 72 stores the inner pin 65. Specifically, the inner pins 65 are attached to the link storage portion 72.
  • the link storage portion 72 is a portion pushed out to the piston 24 side (engine side).
  • the link storage part 72 has an outer peripheral side cylinder part 72a and an annular part 72b.
  • the outer peripheral side cylinder part 72 a is formed integrally with the first spring storage part 71 so as to protrude from the inner peripheral part of the first spring storage part 71 to the piston 24 side (engine side).
  • the annular portion 72b is formed in an annular shape.
  • the outer peripheral part of the annular part 72b is formed integrally with the outer peripheral side cylinder part 72a.
  • a link portion 55, an inner pin 65, and an outer pin 75 are disposed on the transmission side of the annular portion 72b.
  • the outer pin 75 is disposed on the outer peripheral side of the annular portion 72b
  • the inner pin 65 is disposed on the inner peripheral side of the annular portion 72b.
  • the link portion 55 connects the outer pin 75 and the inner pin.
  • the link storage portion 72 having this configuration is disposed between the piston 24 and the torque converter body 6 (for example, the turbine 4) in the axial direction.
  • the link storage portion 72 is disposed on the inner peripheral side of the first torsion spring 26. Thereby, a torque converter can be reduced in size in an axial direction.
  • the side plate 63 is provided facing the main plate 61 in the axial direction.
  • the side plate 63 is disposed to face the main plate 61 with a predetermined interval.
  • the side plate 63 is fixed to the main plate 61 by fixing means such as bolts. As a result, the side plate 63 rotates integrally with the main plate 61.
  • a stopper 62 is fixed between the side plate 63 and the main plate 61 by the fixing means such as the bolt described above.
  • the side plate 63 is substantially annular. More specifically, the outer peripheral portion of the side plate 63 is formed in an annular shape, and the inner peripheral portion of the side plate 63 is bent toward the piston 24 (engine side). With this configuration, the side plate 63 can be disposed along the outer peripheral surface of the torque converter body 6 (for example, the turbine 4). That is, the torque converter can be reduced in size in the axial direction.
  • the inner pin 65 is attached to the main plate 61.
  • the inner pin 65 is fixed to the inner peripheral portion of the main plate 61 by fixing means such as caulking, welding, and bolts. More specifically, the inner pin 65 is fixed to the hole of the link storage portion 72 of the main plate 61 by the fixing means described above.
  • the inner pin 65 is provided to face the outer pin 75 in the radial direction.
  • the inner pins 65 are provided on the main plate 61 with a predetermined interval in the circumferential direction.
  • each of a plurality of (for example, eight) inner pins 65 is fixed to the inner peripheral portion of the main plate 61 at a predetermined interval in the circumferential direction.
  • a link portion 55 is engaged with each inner pin 65. Specifically, the link portion 55 is rotatably attached to the inner pin 65.
  • the inner pin 65 has a mounting portion 65a, a shaft portion 65b, and a positioning portion 65c.
  • the mounting portion 65a is fixed to the inner peripheral portion (link storage portion 72) of the main plate 61 by the fixing means described above.
  • a link portion 55 is rotatably attached to the shaft portion 65b.
  • the shaft portion 65 b is disposed inside a first long hole portion 55 b (described later) of the link portion 55.
  • the positioning part 65c positions the link part 55 in the axial direction.
  • the positioning portion 65c is formed with a larger diameter than the shaft portion 65b.
  • the positioning portion 65c is disposed between the main plate 61 (the annular portion 72b of the link storage portion 72) and the link portion 55 in the axial direction.
  • the positioning portion 65c is formed integrally with the mounting portion 65a and the shaft portion 65b.
  • the positioning portion 65c may be a bush disposed around the shaft portion 65b.
  • the inertia ring 53 is configured to be capable of attenuating torque fluctuations input to the second drive plate 51 by moving relative to the second drive plate 51. Specifically, when the inertia ring 53 moves relative to the second drive plate 51, the inertia force of the inertia ring 53 acts in a direction opposite to the direction in which the second drive plate 51 rotates. Thereby, the torque fluctuation
  • the inertia ring 53 is disposed between the main plate 61 and the side plate 63 in the axial direction.
  • the inertia ring 53 is formed in a substantially annular shape.
  • the inertia ring 53 includes a ring main body portion 74 and an outer pin 75 (an example of a second engagement portion).
  • the ring main body portion 74 is disposed between the first spring storage portion 71 and the second spring storage portion 73.
  • the ring main body 74 includes a second annular portion 74a, a plurality (for example, four) of concave portions 74b, and a plurality (for example, four) of third window portions 74c.
  • the second annular portion 74a is formed in an annular shape.
  • the second annular portion 74a is formed in a substantially annular shape. Specifically, the outer peripheral portion of the second annular portion 74a is formed in an annular shape, and the inner peripheral portion of the second annular portion 74a is bent toward the piston 24 (engine side).
  • the plurality of concave portions 74b are provided on the outer peripheral portion of the second annular portion 74a.
  • each of the plurality of concave portions 74b is provided on the outer peripheral portion of the second annular portion 74a with a predetermined interval in the circumferential direction.
  • fixing means for connecting the main plate 61 and the side plate 63 for example, a shaft portion of a bolt, is arranged.
  • the third window portion 74c is provided on the outer peripheral portion of the second annular portion 74a.
  • the third window portion 74c is provided on the outer peripheral portion of the second annular portion 74a between the concave portions 74b adjacent in the circumferential direction.
  • the third window portion 74c is disposed to face the first window portion 71a and the second window portion 73a in the axial direction.
  • a second torsion spring 57 is disposed in the third window portion 74c.
  • a pair of wall portions facing each other in the circumferential direction in the third window portion 74 c abuts against both end portions of the second torsion spring 57.
  • the frame portion of the third window portion 74c can contact the stopper 62 in the circumferential direction.
  • the outer pin 75 is attached to the inertia ring 53.
  • the outer pin 75 is fixed to the inner peripheral portion of the inertia ring 53 by fixing means such as press fitting and welding.
  • the outer pin 75 is provided to face the inner pin 65 in the radial direction.
  • the outer pins 75 are provided on the ring body 74 with a predetermined interval in the circumferential direction.
  • each of the plurality of (for example, eight) outer pins 75 is fixed to the inner peripheral portion of the second annular portion 74a with a predetermined interval in the circumferential direction.
  • a link portion 55 engages with each outer pin 75. Specifically, the link portion 55 is rotatably attached to a shaft portion 75a (described later) of the outer pin 75 and a shaft portion 65b of the inner pin 65.
  • the outer pin 75 has a shaft portion 75a and a flange portion 75b.
  • a link portion 55 is rotatably attached to the shaft portion 75a.
  • the shaft portion 75 a is disposed inside a second long hole portion 55 c (described later) of the link portion 55.
  • the base end portion of the shaft portion 75a is fixed to the inertia ring 53 by a fixing means such as press fitting.
  • the flange portion 75b abuts on the main plate 61 (the annular portion 72b of the link storage portion 72). In this state, the flange portion 75 b is disposed between the main plate 61 (the annular portion 72 b of the link storage portion 72) and the link portion 55 in the axial direction.
  • the inner pin 65 has a mounting portion 65a, a shaft portion 65b, and a positioning portion 65c.
  • the mounting portion 65a is fixed to the inner peripheral portion (link storage portion 72) of the main plate 61 by the fixing means described above.
  • a link portion 55 is rotatably attached to the shaft portion 65b.
  • the positioning part 65c positions the link part 55 in the axial direction.
  • the positioning portion 65c is formed with a larger diameter than the shaft portion 65b.
  • the positioning portion 65c is disposed between the main plate 61 (the annular portion 72b of the link storage portion 72) and the link portion 55 in the axial direction.
  • the positioning portion 65c is formed integrally with the mounting portion 65a and the shaft portion 65b.
  • the positioning portion 65c may be a bush disposed around the shaft portion 65b.
  • the link portion 55 connects the second drive plate 51 and the inertia ring 53. Specifically, the link portion 55 connects the second drive plate 51 and the inertia ring 53 so that the inertia ring 53 can move relative to the second drive plate 51. More specifically, the link part 55 connects the second drive plate 51 and the inertia ring 53 so that the inertia ring 53 can rotate relative to the second drive plate 51.
  • a plurality of (for example, five) link portions 55 are arranged between the second drive plate 51 and the inertia ring 53.
  • Each link portion 55 engages with the second drive plate 51 and the inertia ring 53 so as to be swingable between the second drive plate 51 and the inertia ring 53. Specifically, each link portion 55 is disposed between the outer pin 75 and the inner pin 65 in the radial direction. In this state, each link portion 55 is rotatably engaged with the shaft portion 75 a of the outer pin 75 and the shaft portion 65 b of the inner pin 65.
  • Each link portion 55 is rotatably supported by the second driven plate 59.
  • Each link portion 55 includes a link main body portion 55a, a first long hole portion 55b, a second long hole portion 55c, and a hole portion 55d.
  • the link body 55a is formed in a plate shape that is long in one direction.
  • the first long hole 55b is formed at one end of the link main body 55a.
  • the inner pin 65 engages with the first long hole portion 55b.
  • the shaft portion 65b of the inner pin 65 is disposed in the first long hole portion 55b.
  • the shaft portion 65b of the inner pin 65 is movable inside the first long hole portion 55b.
  • the second slot 55c is formed at the other end of the link body 55a.
  • the outer pin 75 engages with the second long hole portion 55c.
  • the shaft portion 75a of the outer pin 75 is disposed in the second long hole portion 55c.
  • the shaft portion 75a of the outer pin 75 is movable inside the second long hole portion 55c.
  • the hole 55d is formed in the inner periphery of the link main body 55a.
  • a support portion 77 (described later) of the second driven plate 59 is disposed in the hole portion 55d.
  • the link main body portion 55 a is supported by the second driven plate 59 in a state where the inner pin 65 is engaged with the first long hole portion 55 b and the outer pin 75 is engaged with the second long hole portion 55 c. It can swing around 77.
  • the second torsion spring 57 elastically connects the second drive plate 51 and the inertia ring 53.
  • the second torsion spring 57 is disposed in the first window 71 a and the second window 73 a of the second drive plate 51 and the third window 74 c of the inertia ring 53.
  • both end portions of the second torsion spring 57 are connected to the wall portion of the first window portion 71a and the wall portion of the second window portion 73a of the second drive plate 51 (the main plate 61 and the side plate 63), and the inertia. It abuts against the wall of the third window 74c of the ring 53 (ring body 74) in the circumferential direction.
  • the second torsion spring 57 When it is considered that the second torsion spring 57 is pressed in the circumferential direction by the inertia ring 53, one end portion of the second torsion spring 57 is circled by the inertia ring 53 (wall portion of the third window portion 74c). When pressed in the circumferential direction, the second end of the second torsion spring 57 is supported by the second drive plate 51 (the wall portion of the first window portion 71a and the wall portion of the second window portion 73a). The torsion spring 57 is compressed.
  • the second driven plate 59 is configured to output torque transmitted from the second drive plate 51 and the inertia ring 53 to the link portion 55.
  • the second driven plate 59 is attached to the turbine hub 17.
  • the second driven plate 59 is fixed to the turbine hub 17.
  • the second driven plate 59 is fixed to the flange 17 a of the turbine hub 17 by fixing means such as the rivet 18.
  • the second driven plate 59 can rotate integrally with the turbine 4 and the turbine hub 17.
  • the second driven plate 59 supports the link portion 55 so as to be swingable.
  • the second driven plate 59 has a plate body 76 and a support portion 77.
  • the support portion 77 includes a shaft portion 77a and a sliding member 77b.
  • the shaft portion 77a is formed integrally with the plate body 76.
  • the shaft portion 77 a protrudes from the plate body 76 toward the engine side and is formed integrally with the plate body 76.
  • the shaft portion 77 a is disposed in the hole portion 55 d of the link portion 55.
  • the shaft center of the shaft portion 77 a is the rotation center P of the link portion 55.
  • the shaft portion 77a may be separated from the plate body 76.
  • the shaft portion 77a may be configured by attaching the pin member to the plate body 76 as a separate body.
  • the sliding member 77b is for smoothly rotating the link portion 55 with respect to the shaft portion 77a.
  • the sliding member 77b is, for example, a bush disposed on the outer peripheral portion of the shaft portion 77a.
  • the bush 77b is disposed between the hole portion 55d of the link portion 55 and the shaft portion 77a.
  • a shaft portion 77a is disposed on the inner peripheral portion of the cylindrical portion of the bush 77b.
  • a hole portion 55d of the link portion 55 is disposed on the outer peripheral portion of the cylindrical portion of the bush 77b.
  • a flange portion provided at one end portion of the cylindrical portion of the bush 77b is disposed between the link portion 55 and the plate body 76 of the second driven plate 59 in the axial direction.
  • the torque output from the lockup device 7 is input to the dynamic vibration absorber 8.
  • the torque output from the first driven plate 28 (driven main body portion 28a) of the lockup device 7 is input to the second drive plate 51 (main plate 61 and side plate 63) of the dynamic vibration absorber 8. .
  • first torque transmission path T1 For example, torque transmitted from the main plate 61 of the second drive plate 51 to the inner pin 65 is transmitted to the link portion 55.
  • torque input to the second drive plate 51 (the main plate 61, the side plate 63, and the inner pin 65) is directly transmitted to the link portion 55.
  • this torque transmission path is referred to as a first torque transmission path T1.
  • the torque transmitted from the main plate 61 and the side plate 63 of the second drive plate 51 to the second torsion spring 57 is transmitted to the inertia ring 53 and the outer pin 75.
  • This torque is transmitted from the outer pin 75 to the link portion 55.
  • the torque input to the second drive plate 51 (the main plate 61 and the side plate 63) is indirectly transmitted to the link portion 55 via the second torsion spring 57, the inertia ring 53, and the outer pin 95. Is done.
  • this torque transmission path is referred to as a second torque transmission path T2.
  • the second torsion spring 57 when the torque transmitted from the main plate 61 and the side plate 63 to the second torsion spring 57 (the torque of the second torque transmission path T2) is less than the operating torque of the second torsion spring 57, the second The torsion spring 57 is not compressed. For this reason, the link portion 55 does not substantially swing between the second drive plate 51 (including the inner pin 65) and the inertia ring 53 (including the outer pin 75).
  • the link portion 55 (the swing center of the link portion 55) rotates together with the second drive plate 51 and the inertia ring 53 while the link portion 55 is not substantially swung. Move in the direction.
  • the amount of movement in this case is indicated by a symbol Y0.
  • the link part 55 moves in the rotation direction without swinging, the average component of the torque of the first torque transmission path T1 and the average component of the torque of the second torque transmission path T2 are the link part 55.
  • the second driven plate 59 To the second driven plate 59.
  • the torque fluctuation component of the first torque transmission path T1 and the torque fluctuation component of the second torque transmission path T2 are It is not substantially attenuated.
  • the second drive plate 51 rotates around the rotation axis by the average component of torque.
  • the rotation angle at this time is the rotation angle Y11.
  • the inertia ring 53 rotates with respect to the second drive plate 51 by a torque fluctuation component (torque fluctuation).
  • the rotation direction of the inertia ring 53 is opposite to the rotation direction of the second drive plate 51.
  • the rotation angle at this time is the rotation angle Y12.
  • the absolute value of the rotation angle Y12 of the inertia ring 53 is smaller than the absolute value of the rotation angle Y11 of the second drive plate 51. For this reason, the rotation center P of the link portion 55 moves in the circumferential direction between the rotation center P0 determined by the average component of torque and the rotation center P1 determined by the torque fluctuation component. In this state, the link portion 55 swings between the second drive plate 51 (including the inner pin 65) and the inertia ring 53 (including the outer pin 75).
  • the rotation center P of the link portion 55 is the rotation center P0 and the rotation center P1 in the circumferential direction with respect to the rotation center P0. Moves in the circumferential direction between the opposite positions (not shown).
  • the average component of the torque of the first torque transmission path T1 and the average component of the torque of the second torque transmission path T2 are output from the link portion 55 to the second driven plate 59. Further, the torque fluctuation component of the first torque transmission path T1 and the torque fluctuation component of the second torque transmission path T2 are attenuated by the relative rotation of the inertia ring 53 with respect to the second drive plate 51. In this case, since the rotation center P moves due to a torque fluctuation component, the second drive plate 51 is transmitted with a rotation speed fluctuation corresponding to this movement.
  • the second drive plate 51 rotates around the rotation axis O by the average component of torque.
  • the rotation angle at this time is the rotation angle Y21.
  • the inertia ring 53 rotates with respect to the second drive plate 51 by a torque fluctuation component.
  • the rotation direction of the inertia ring 53 is opposite to the rotation direction of the second drive plate 51.
  • the rotation angle at this time is the rotation angle Y22.
  • the absolute value of the rotation angle Y22 of the inertia ring 53 is substantially the same as the absolute value of the rotation angle Y21 of the second drive plate 51.
  • the rotation center P0 determined by the average component of torque and the rotation center P1 determined by the torque fluctuation component substantially coincide. That is, in this case, the rotation center P of the link portion 55 does not substantially move in the circumferential direction due to a torque fluctuation component. In this state, the link portion 55 swings between the second drive plate 51 (including the inner pin 65) and the inertia ring 53 (including the outer pin 755).
  • the average component of the torque of the first torque transmission path T1 and the average component of the torque of the second torque transmission path T2 are output from the link portion 55 to the second driven plate 59. Further, the torque fluctuation component of the first torque transmission path T1 and the torque fluctuation component of the second torque transmission path T2 are attenuated by the relative rotation of the inertia ring 53 with respect to the second drive plate 51. In this case, since the rotation center P does not substantially move due to the torque fluctuation component, the rotation speed fluctuation is not transmitted to the second drive plate 51.
  • the state shown in FIG. 4D that is, the state in which the rotation center P of the link portion 55 does not substantially move in the circumferential direction due to the torque fluctuation component attenuates the torque fluctuation component most effectively. It is ready. That is, in the present embodiment, as shown by the solid line in FIG. 5, the dynamic vibration absorber 8 can most effectively attenuate the torque fluctuation component at the rotational speed TG to be attenuated.
  • the dynamic vibration absorber 8 is for attenuating fluctuations in torque transmitted from the engine to the transmission.
  • the dynamic vibration absorber 8 includes a second drive plate 51, an inertia ring 53, a link portion 55, a second torsion spring 57, and a second driven plate 59.
  • the second drive plate 51 can be rotated by inputting torque.
  • the inertia ring 53 can attenuate the torque fluctuation input to the second drive plate 51 by moving relative to the second drive plate 51.
  • the link part 55 connects the second drive plate 51 and the inertia ring 53 so as to be relatively movable.
  • the link portion 55 can swing between the second drive plate 51 and the inertia ring 53.
  • Torque is transmitted to the link portion 55 from the second drive plate 51 and the inertia ring 53.
  • the second torsion spring 57 elastically connects the second drive plate 51 and the inertia ring 53.
  • the second driven plate 59 supports the link portion 55 so as to be swingable.
  • the second driven plate 59 outputs the torque transmitted from the second drive plate 51 and the inertia ring 53 to the link portion 55.
  • the link portion 55 is connected between the second drive plate 51 and the inertia ring 53 by the second driven plate 59.
  • the inertia ring 53 moves relative to the second drive plate 51 while swinging relative to the second drive plate 51.
  • the inertia ring 53 moves relative to the second drive plate 51 to attenuate the torque fluctuation.
  • torque transmitted from the second drive plate 51 and the inertia ring 53 to the link portion 55 is output from the second driven plate 59.
  • the dynamic vibration absorber 8 As described above, in the dynamic vibration absorber 8, the torque fluctuation attenuation due to the operation of the inertia ring 53 and the torque transmission from the second drive plate 51 and the inertia ring 53 to the second driven plate 59 are transmitted via the link portion 55. Has been done. Thereby, in this dynamic vibration absorber 8, the vibration response which generate
  • the dynamic vibration absorber 8 is preferably configured as follows.
  • the link portion 55 is engaged with the second drive plate 51 and the inertia ring 53 so as to be swingable between the second drive plate 51 and the inertia ring 53.
  • the inertia ring 53 is moved by swinging between the second drive plate 51 and the inertia ring 53 while the link portion 55 is engaged with the second drive plate 51 and the inertia ring 53. It moves relative to the second drive plate 51.
  • the link portion 55 can reliably connect the second drive plate 51 and the inertia ring 53 and can swing stably between the second drive plate 51 and the inertia ring 53. That is, the dynamic vibration absorber 8 can be smoothly operated with an easy configuration.
  • the dynamic vibration absorber 8 is preferably configured as follows.
  • the second drive plate 51 has an inner pin 65 with which the link portion 55 engages in a direction away from the rotation center of the second drive plate 51.
  • the inertia ring 53 has an outer pin 75 with which the link portion 55 engages in a direction away from the rotation center of the second drive plate 51.
  • the link portion 55 can swing with reference to the swing center between the inner pin 65 and the outer pin 75.
  • the link portion 55 engages with the inner pin 65 of the second drive plate 51 and engages with the outer pin 75 of the inertia ring 53 in a direction away from the rotation center of the second drive plate 51. . In this state, the link portion 55 swings with respect to the swing center between the inner pin 65 and the outer pin 75, so that the inertia ring 53 moves relative to the second drive plate 51.
  • the link portion 55 can reliably connect the second drive plate 51 and the inertia ring 53 and can swing stably between the second drive plate 51 and the inertia ring 53. Further, by providing the swing center of the link portion 55 between the inner pin 65 and the outer pin 75 in a direction away from the rotation center of the second drive plate 51, the dynamic vibration absorber 8 can be connected to the second drive plate 51. The size can be reduced in the direction in which the rotation center extends, that is, in the direction of the rotation axis.
  • the dynamic vibration absorber 8 is preferably configured as follows. When the second torsion spring 57 operates, the link portion 55 swings with respect to the second driven plate 59 between the second drive plate 51 and the inertia ring 53.
  • the link portion 55 is located between the second drive plate 51 and the inertia ring 53.
  • the inertia ring 53 moves relative to the second drive plate 51 while swinging.
  • the inertia ring 53 can be stably moved relative to the second drive plate 51, and the torque fluctuation can be reliably attenuated in the rotation speed range to be attenuated. That is, the dynamic vibration absorber 8 can be stably operated.
  • the dynamic vibration damping device 8 is preferably configured as follows. When the second torsion spring 57 is actuated, the link portion 55 swings with respect to the second driven plate 59 in a state where the swing center of the link portion 55 does not substantially move.
  • the link portion 55 is in a state in which the swing center does not substantially move. Thus, it swings between the second drive plate 51 and the inertia ring 53, and the inertia ring 53 moves relative to the second drive plate 51.
  • the torque fluctuation is not substantially output from the output unit.
  • the dynamic vibration damping device 8 by operating the dynamic vibration damping device 8 with the above-described configuration at the rotational speed at which attenuation of torque fluctuation is required, the torque fluctuation can be effectively attenuated in the rotational speed range to be attenuated. That is, the dynamic vibration absorber 8 can be operated effectively.
  • the dynamic vibration damping device 8 is preferably configured as follows. When the second torsion spring 57 is not actuated, the link portion 55 moves together with the second drive plate 51 and the inertia ring 53 in a state in which the second torsion spring 57 is not substantially swung.
  • the link portion 55 is connected to the second drive plate 51 and the inertia ring 53. It moves with the ring 53. That is, when the second torsion spring 57 is not operated, the torque input to the second drive plate 51 is transferred to the second driven plate 59 via the link portion 55 that moves together with the second drive plate 51 and the inertia ring 53. Is output from.
  • the torque input to the second drive plate 51 can be efficiently output from the second driven plate 59.
  • the torque input to the second drive plate 51 is efficiently output from the second driven plate 59 by operating the dynamic vibration absorber 8 with the above-described configuration at a rotational speed at which no torque fluctuation attenuation is required. be able to.
  • the dynamic vibration absorber 8 is preferably configured as follows. Torque output from the lockup device 7 of the torque converter is input to the second drive plate 51 connected to the lockup device 7. The torque output from the second driven plate 59 is transmitted to the transmission.
  • the dynamic vibration absorber 8 can further attenuate the torque fluctuation included in the torque output from the lockup device 7. That is, the torque fluctuation can be attenuated stepwise by the lockup device 7 and the dynamic vibration absorber 8.
  • the present invention is applied to the lock-up device 7 of the torque converter, but can be applied to other power transmission devices in the same manner.

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

Abstract

L'invention concerne un absorbeur de vibrations dynamique, lequel amortisseur peut amortir de manière adéquate des fluctuations dans le couple sur une large plage de vitesses de rotation. Un amortisseur de vibrations dynamique (8) a : une seconde plaque d'entraînement (51), une bague d'inertie (53), une unité de liaison (55), un second ressort de torsion (57), et une seconde plaque entraînée (59). La seconde plaque d'entraînement (51) peut être mise en rotation par une entrée de couple. La bague d'inertie (53) est mobile par rapport à la seconde plaque d'entraînement (51). L'unité de liaison (55) couple la seconde plaque d'entraînement (51) et la bague d'inertie (53) de manière à être mobiles l'une par rapport à l'autre. L'unité de liaison (55) est apte à osciller entre la seconde plaque d'entraînement (51) et la bague d'inertie (53). Le second ressort de torsion (57) relie élastiquement la seconde plaque d'entraînement (51) et la bague d'inertie (53). La seconde plaque entraînée (59) porte l'unité de liaison (55) de manière à pouvoir basculer.
PCT/JP2016/055302 2015-04-13 2016-02-23 Amortisseur de vibrations dynamique WO2016167026A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112016000892.9T DE112016000892T5 (de) 2015-04-13 2016-02-23 Dynamische Vibrationsdämpfungsvorrichtung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015081670A JP2016200238A (ja) 2015-04-13 2015-04-13 動吸振装置
JP2015-081670 2015-04-13

Publications (1)

Publication Number Publication Date
WO2016167026A1 true WO2016167026A1 (fr) 2016-10-20

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PCT/JP2016/055302 WO2016167026A1 (fr) 2015-04-13 2016-02-23 Amortisseur de vibrations dynamique

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Country Link
JP (1) JP2016200238A (fr)
DE (1) DE112016000892T5 (fr)
WO (1) WO2016167026A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10503578A (ja) * 1995-06-01 1998-03-31 オートモーティヴ・プロダクツ・パブリック・リミテッド・カンパニー 二質量フライホイール
JP2001520735A (ja) * 1998-02-13 2001-10-30 オートモーティヴ・プロダクツ・パブリック・リミテッド・カンパニー 減衰装置
US20140302937A1 (en) * 2011-11-23 2014-10-09 Daniel Lorenz Torsional vibration damper assembly, in particular for the drive train of a motor vehicle

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10503578A (ja) * 1995-06-01 1998-03-31 オートモーティヴ・プロダクツ・パブリック・リミテッド・カンパニー 二質量フライホイール
JP2001520735A (ja) * 1998-02-13 2001-10-30 オートモーティヴ・プロダクツ・パブリック・リミテッド・カンパニー 減衰装置
US20140302937A1 (en) * 2011-11-23 2014-10-09 Daniel Lorenz Torsional vibration damper assembly, in particular for the drive train of a motor vehicle

Also Published As

Publication number Publication date
DE112016000892T5 (de) 2017-11-09
JP2016200238A (ja) 2016-12-01

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