WO2018001236A1 - Amortisseur de vibrations de torsion - Google Patents

Amortisseur de vibrations de torsion Download PDF

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Publication number
WO2018001236A1
WO2018001236A1 PCT/CN2017/090282 CN2017090282W WO2018001236A1 WO 2018001236 A1 WO2018001236 A1 WO 2018001236A1 CN 2017090282 W CN2017090282 W CN 2017090282W WO 2018001236 A1 WO2018001236 A1 WO 2018001236A1
Authority
WO
WIPO (PCT)
Prior art keywords
flexible
side plate
power output
output side
damping block
Prior art date
Application number
PCT/CN2017/090282
Other languages
English (en)
Chinese (zh)
Inventor
袁辉
Original Assignee
苏州辉美汽车科技有限公司
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 苏州辉美汽车科技有限公司 filed Critical 苏州辉美汽车科技有限公司
Publication of WO2018001236A1 publication Critical patent/WO2018001236A1/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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
    • F16F7/104—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted
    • F16F7/108—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted on plastics 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
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/124—Elastomeric springs
    • F16F15/126—Elastomeric springs consisting of at least one annular element surrounding the axis of rotation

Definitions

  • the present disclosure relates to the field of mechanical technology, for example to a torsional vibration damper.
  • the torsional vibration damper device is adopted in the automobile power transmission system.
  • the vibration damping effect of the torsional vibration damper also greatly affects the quality of the transmission system of the automobile power. .
  • the related art torsional vibration damper includes the following two application forms.
  • the torsional vibration damper is incorporated on the clutch friction plate. This form is limited by the arrangement space, the torsion angle of the damper is limited, the vibration damping effect is not ideal, and the natural frequency cannot avoid the resonance frequency.
  • the torsional vibration damper is combined on the dual mass flywheel. Compared with the form of the torsional vibration damper combined with the clutch friction plate, the torsional vibration damper combined with the double mass flywheel has a larger vibration damping space, can achieve a larger torsion angle, and has better vibration damping effect.
  • the spring force is complicated, and the cost of the torsional vibration damper is high, the wear is large, and the life is short.
  • the elastic damping element of the torsional vibration damper adopts a cylindrical helical compression spring
  • the cylindrical helical compression spring is arranged along the circumferential tangential direction of the power transmission shaft
  • the curved spring introduced on the double mass flywheel is substantially A variant of a cylindrical helical compression spring.
  • application documents of the application number CN201510997935.6 and the application number CN2016100844146 respectively provide a flat scroll spring and a multi-layer hollow.
  • the torsion damper scheme of the torsion bar spring is simpler in structure, which can obtain more ideal nonlinear elastic stiffness and optimize the natural resonance frequency.
  • the forming process of the planar scroll spring and the multilayer hollow torsion bar spring is complicated. Production consistency is difficult to guarantee.
  • the present disclosure provides a torsional vibration damper.
  • a torsional vibration damper includes a power input side plate, a first power output side plate and a first flexible vibration damping block, wherein the first flexible vibration damping block is located on the power input side plate and the first power output side Between the plates; two sides of the flexible vibration damping block are respectively fixedly fixed to the power input side plate and the first power output side plate, the power input side plate, the first power output side plate and the first flexible reduction
  • the vibration block can rotate around the same center of rotation.
  • the material of the flexible vibration damping block comprises a polymer material or a polymer matrix composite material
  • the polymer material comprises rubber or plastic
  • the polymer matrix composite material comprises a composite material of rubber and plastic.
  • the flexible vibration damping block material comprises a high strength low modulus silicone rubber.
  • the thickness of the first flexible vibration damping block gradually increases from the center outward.
  • the thickness of the first flexible vibration damping block gradually decreases from the center outward.
  • the torsional vibration damper further includes a second power output side plate, and a second flexible vibration damping block is disposed between the second power output side plate and the power input side plate, and the second flexible vibration damping block
  • the two sides of the power input side plate and the second power output side plate are respectively fixed and fixed, and the power input side plate, the second power output side plate and the second flexible vibration damping block can rotate around the same rotation center;
  • the first flexible damping block and the second flexible damping block are in a side-by-side relationship in the power transmission path.
  • first flexible damping block and the second flexible damping block are respectively disposed on two sides of the power input side plate.
  • first flexible damping block and the second flexible damping block are both disposed on the same side of the power input side plate.
  • the first flexible vibration damping block and the second flexible vibration damping block are provided with an elastic stiffness difference, and the second power output side plate enters the power transmission path later than the first power output side plate.
  • the torsional vibration damper is applied to a clutch driven disc or a dual mass flywheel, the clutch driven disc comprising a friction plate and a spline a bushing, wherein the torsional vibration damper is applied to a clutch driven plate, the power input side plate is connected to the friction plate, and the first power output side plate is connected to the spline bushing;
  • the dual mass flywheel includes a first mass flywheel and a second mass flywheel, wherein the torsional vibration damper is applied to the dual mass flywheel, the power input side panel is connected to the first mass flywheel, the first power output side panel and the second mass flywheel Connected.
  • an idle flexible block is coaxially disposed between the first power output side plate and the spline bushing, and one side of the idle flexible block is fixedly adhered to the first power output side plate, and the other is Side and said a spline bushing fixedly blocking; the elastic stiffness of the idle flexible block is less than an elastic stiffness of the first flexible buckling block; or
  • the first power output side plate is coaxially disposed with the second mass flywheel with an idle flexible block, and one side of the idle flexible block is fixedly adhered to the first power output side plate, and the other side is The second mass flywheel is fixedly stuck; the elastic stiffness of the idle flexible block is smaller than the elastic stiffness of the first flexible vibration damping block.
  • the torsional vibration damper with flexible damping block provided by the present disclosure has better elastic characteristics, good vibration damping effect, simple structure, light weight, low rotational inertia, easy molding, and easy to ensure batch production consistency, and Avoid spring wear problems.
  • FIG. 1 is a schematic view showing the working position connection of the torsional vibration damper in the power train of the present disclosure
  • FIG. 2 is a schematic structural view of a torsional vibration damper of the present disclosure applied to a clutch driven disc;
  • FIG. 3 is a schematic structural view of a torsional vibration damper of the present disclosure applied to a dual mass flywheel;
  • FIG. 4 is a schematic structural view of another torsional vibration damper of the present disclosure.
  • FIG. 5 is a schematic structural view of a torsional vibration damper with an idle flexible damping block according to the present disclosure
  • Figure 6 is a cross-sectional structural view of Figure 5 along section line AA in the present disclosure
  • FIG. 7 is a schematic structural view of a torsional vibration damper with a double-layer flexible vibration damping block according to the present disclosure
  • FIG. 8 is a schematic structural view of another torsional vibration damper with a double-layer flexible vibration damping block according to the present disclosure.
  • FIG. 1 is a schematic diagram of the working position connection of the torsional vibration damper in the powertrain of the present disclosure. As shown in FIG. 1 , the torsional vibration damper 3 is interposed between the engine 1 and the transmission 2 . between.
  • the torsional vibration damper 3 includes a power input side plate 6, a first power output side plate 8, and a first flexibility between the power input side plate 6 and the first power output side plate 8. Damping block 7. Two sides of the first flexible vibration damping block 7 are respectively fixedly fixed to the power input side plate 6 and the first power output side plate 8, and the power input side plate 6, the first power output side plate 8 and the first A flexible damping block 7 can be surrounded Rotate with the same center of rotation.
  • the first flexible damper block 7 and the power input side plate 6 and the first power output side plate 8 are bonded in the above manner, and may also be connected in the form shown in FIG. 4, two of the first flexible damper blocks 7 The sides are fixedly adhered to the power input side plate 6 and the first power output side plate 8, respectively.
  • the material of the first flexible vibration damping block 7 is a polymer material or a polymer matrix composite material, wherein the polymer material comprises rubber or plastic; the polymer matrix composite material comprises a composite material of rubber and plastic. Alternatively, a high strength low modulus silicone rubber can be used.
  • the first flexible vibration-damping block 7 may be disposed in a uniform thickness form, or may be set to a thickness correspondingly according to an equal shear stress or an approximately equal shear stress principle. For example, when both end faces of the first flexible vibration damping block are fixedly adhered to the power input side plate and the first power output side plate, respectively, the thickness of the first flexible vibration damping block is from the center outward. Gradually increase.
  • the thickness of the first flexible vibration damping block gradually decreases from the center outward.
  • the torsional vibration damper 3 can be applied to a clutch driven disc or a dual mass flywheel.
  • the clutch driven plate includes a spline bushing 9 and a friction plate 11, and when the torsional vibration damper 3 is applied to the clutch driven plate, the power input side plate 6 is connected to the friction plate 11, The first power output side panel 8 is coupled to the spline bushing 9.
  • the power transmission path is: engine 1 - friction plate 11 - torsion damper power input side plate 6 - torsion damper first flexible vibration damping block 7 - torsion damper first power output side plate 8 - flower Key bushing 9 - transmission 2.
  • the dual mass flywheel includes a first mass flywheel 4a and a second mass flywheel 4b.
  • the power input side plate 6 is connected to the first mass flywheel 4a.
  • the first power output side panel 8 is connected to the second mass flywheel 4b.
  • the power transmission path is: engine 1 - first mass flywheel 4a - torsional vibration damper power input side plate 6 - torsional vibration damper first flexible vibration damping block 7 - torsional vibration damper first power output side plate 8 - second mass flywheel 4b - transmission 2.
  • the torsional vibration damper further includes a second power output side plate 13 , and the second power output side 13 plate is disposed on the other side of the power input side plate 6 .
  • a second flexible vibration damping block 12 is disposed between the second power output side plate 13 and the power input side plate 6; the first power output side plate 8 and the second power output side plate 13 are The power transmission path is in a side-by-side relationship, that is, the torsional load of the power input side plate is shared by the first flexible vibration damping block 7 and the second flexible vibration damping block 12 in a certain proportion.
  • the second flexible vibration damping block 12 side is connected to the power input side plate 6, the other side is connected to the second power output side plate 13, and the second power output side is
  • the plate 13 and the first power output side plate 8 are both disposed on the same side of the power input side plate, and the power input side plate 6, the second power output side plate 13, and the second flexible vibration damping block 12 may surround Rotate with the same center of rotation.
  • the first flexible vibration damping block 7 and the second flexible vibration damping block 12 are provided with an elastic rigidity difference, and the second power output side plate 13 enters the power transmission path later than the first power output side plate 8 .
  • the first power output side plate and the spline bushing can also be coaxially arranged to meet the lower elastic vibration damping rigidity requirement under the engine idle speed condition.
  • the engine idle condition refers to the engine no-load operation state, that is, the clutch is in the combined position, and the transmission is in the neutral position.
  • the elastic stiffness of the idle flexible block 14 is much smaller than that.
  • An idle rotation stroke is disposed between the first power output side plate 8 and the spline bushing 9; when the power transmission torque is small, the first power output side plate 8 and the spline bushing 9 are in an empty rotation stroke. in.
  • an idle running stroke is set between the first power output side plate and the spline bushing, that is, an idle speed damping angle ⁇ ; when the power torque is small under the idle speed condition, the first power output side plate 8 is damped by the idle speed Block 14 delivers torque.
  • the power transmission path is: engine-friction plate-torsing damper power input side plate-torsing damper first flexible vibration damping block-torsing damper first power output side plate-idle flexible block-spline shaft Set - transmission.
  • the idle rotation stroke between the first power output side plate 8 and the spline bushing 9 is eliminated, and the idle speed flexible block is no longer further twisted.
  • the first power output side plate overcomes the elasticity of the idle flexible damping block, and the first power output side plate limit tooth abuts the spline bushing limit groove, and the idle speed is reduced.
  • the vibration angle ⁇ idle stroke is eliminated, and the first power output side plate 8 directly transmits torque through the spline bushing 9.
  • the power transmission path is: engine-friction plate-torsing damper power input side plate-torsing damper first flexible vibration damping block-torsion damper first power output side plate-spline bushing-transmission.
  • the first power output side plate and the second mass flywheel may also be the same in order to meet the lower elastic vibration damping stiffness requirement under the engine idle speed condition.
  • the shaft is provided with an idle flexible block. One side of the idle flexible block is fixedly adhered to the first power output side plate, and the other side is fixedly adhered to the second mass flywheel; the elastic stiffness of the idle flexible block is much smaller than the first The elastic stiffness of the flexible damping block.
  • the torsional vibration damper with flexible damping block provided by the present disclosure has better elastic characteristics, good vibration damping effect, simple structure, light weight, low rotational inertia, easy molding, and easy to ensure batch production consistency, and Avoid spring wear problems.
  • the present disclosure provides a torsional vibration damper with a flexible vibration damping block, which has better elastic characteristics, good vibration damping effect, simple structure, light weight, low rotational inertia, easy molding, easy to ensure mass production consistency, and avoid Spring wear problem.

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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)

Abstract

L'invention porte sur un amortisseur de vibrations de torsion comprenant un panneau latéral (6) d'entrée de puissance, un premier panneau latéral (8) de sortie de puissance, et un premier bloc (7) d'amortissement de vibrations flexible. Le premier bloc (7) d'amortissement de vibrations flexible est situé entre le panneau latéral (6) d'entrée de puissance et le premier panneau latéral (8) de sortie de puissance. Deux côtés du premier bloc (7) d'amortissement de vibrations flexible sont collés et fixés respectivement au panneau latéral (6) d'entrée de puissance et au premier panneau latéral (8) de sortie de puissance. Le panneau latéral (6) d'entrée de puissance, le premier panneau latéral (8) de sortie de puissance et le premier bloc (7) d'amortissement de vibrations flexible peuvent tourner autour d'un même centre de rotation.
PCT/CN2017/090282 2016-06-27 2017-06-27 Amortisseur de vibrations de torsion WO2018001236A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201610475750.3A CN105937578B (zh) 2016-06-27 2016-06-27 扭转减振器
CN201610475750.3 2016-06-27

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Publication Number Publication Date
WO2018001236A1 true WO2018001236A1 (fr) 2018-01-04

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Application Number Title Priority Date Filing Date
PCT/CN2017/090282 WO2018001236A1 (fr) 2016-06-27 2017-06-27 Amortisseur de vibrations de torsion

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CN (1) CN105937578B (fr)
WO (1) WO2018001236A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105937578B (zh) * 2016-06-27 2019-05-10 苏州辉元变速器科技有限公司 扭转减振器
CN108825719B (zh) * 2018-08-08 2024-01-26 华域动力总成部件系统(上海)有限公司 减振阻尼补偿装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2477081A (en) * 1945-06-27 1949-07-26 Harold A King Means for damping torsional vibrations in internal-combustion engines
JPS5624242A (en) * 1979-05-18 1981-03-07 Hartz Helmut Tortional vibration damper
CN105937578A (zh) * 2016-06-27 2016-09-14 苏州辉元变速器科技有限公司 扭转减振器
CN205824034U (zh) * 2016-06-27 2016-12-21 苏州辉元变速器科技有限公司 扭转减振器

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Publication number Priority date Publication date Assignee Title
US1913984A (en) * 1930-04-02 1933-06-13 Chrysler Corp Torsional vibration damper
US1948247A (en) * 1931-03-25 1934-02-20 Gen Motors Corp Vibration damper
GB486917A (en) * 1935-12-04 1938-06-07 Max Goldschmidt Improvements in and relating to elastic couplings of rubber and metal, more particularly for motor vehicles
GB520437A (en) * 1938-10-20 1940-04-24 Colin Macbeth Improvements in, and connected with, clutches
US2234443A (en) * 1938-10-21 1941-03-11 Macbeth Colin Clutch
US2585382A (en) * 1948-06-25 1952-02-12 Gen Motors Corp Torsional vibration damper
DE7707472U1 (de) * 1977-03-11 1979-02-15 Goetze Ag, 5093 Burscheid Befestigungsflansch
DE3007238A1 (de) * 1980-02-27 1981-09-03 Goetze Ag, 5093 Burscheid Schwingungstilger fuer rotierende wellen
JPS61139317U (fr) * 1985-02-19 1986-08-29
US5382194A (en) * 1987-01-30 1995-01-17 Ktr Kupplungstechnik Gmbh Plug-in axially and angularly yieldable toothed coupling for transmitting torque
DE3816324A1 (de) * 1987-07-07 1989-01-19 Metzeler Gmbh Drehschwingungsdaempfer
JP5772098B2 (ja) * 2011-03-15 2015-09-02 アイシン精機株式会社 トルク変動吸収装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2477081A (en) * 1945-06-27 1949-07-26 Harold A King Means for damping torsional vibrations in internal-combustion engines
JPS5624242A (en) * 1979-05-18 1981-03-07 Hartz Helmut Tortional vibration damper
CN105937578A (zh) * 2016-06-27 2016-09-14 苏州辉元变速器科技有限公司 扭转减振器
CN205824034U (zh) * 2016-06-27 2016-12-21 苏州辉元变速器科技有限公司 扭转减振器

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Publication number Publication date
CN105937578B (zh) 2019-05-10
CN105937578A (zh) 2016-09-14

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