WO2009066823A1 - Amortisseur de vibrations de torsion de type à ressort hydraulique - Google Patents

Amortisseur de vibrations de torsion de type à ressort hydraulique Download PDF

Info

Publication number
WO2009066823A1
WO2009066823A1 PCT/KR2007/005967 KR2007005967W WO2009066823A1 WO 2009066823 A1 WO2009066823 A1 WO 2009066823A1 KR 2007005967 W KR2007005967 W KR 2007005967W WO 2009066823 A1 WO2009066823 A1 WO 2009066823A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
hub ring
torsional vibration
ring
vibration damper
Prior art date
Application number
PCT/KR2007/005967
Other languages
English (en)
Inventor
Jeong Gyu Kim
Original Assignee
Jeong Gyu Kim
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 Jeong Gyu Kim filed Critical Jeong Gyu Kim
Priority to PCT/KR2007/005967 priority Critical patent/WO2009066823A1/fr
Publication of WO2009066823A1 publication Critical patent/WO2009066823A1/fr

Links

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
    • F16F15/14—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
    • F16F15/1407—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 the rotation being limited with respect to the driving means
    • F16F15/1414—Masses driven by elastic elements
    • F16F15/1421—Metallic springs, e.g. coil or spiral 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
    • F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
    • F16F15/161—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material characterised by the fluid damping devices, e.g. passages, orifices
    • 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
    • F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
    • F16F15/167—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material having an inertia member, e.g. ring
    • F16F15/173—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material having an inertia member, e.g. ring provided within a closed housing

Definitions

  • the present invention relates to a vibration damper coupled to an output shaft of an engine so as to damp vibrations generated from the output shaft of the engine, and more particularly, to a hydraulic spring type torsional vibration damper that has a combined structure consisting of a viscosity damper and a spring damper.
  • vibrations are generated by periodically varying physical quantities such as the position or installed state of an object or the strength of an electric current with respect to a given value, and all of objects have their natural frequencies.
  • an engine which converts a linear movement where a cylinder performs an upwardly and downwardly reciprocating motion into a rotating movement thereof by its own explosive force, generates a vibration by the external force applied upon the explosion, and in this case, the vibration is called a forced vibration.
  • the resonance is generated when a vacuum gauge receives an external force having the frequency being equal to the natural frequency of an object, thereby allowing the amplitude of the vibration to be remarkably increased, and if the resonance phenomenon occurs in the engine being actuated at a high speed, the amplitude is gradually increased with a result of the breakdown of the engine.
  • a damper for damping the vibration is mounted at a position like an engine where the vibration is periodically generated, and in this case, the damper is simply called a vibration damper.
  • a rotary type torsional vibration damper is mounted on a rotary operating member like a crankshaft of an engine, for damping the vibration caused by the rotational motion.
  • the rotary type torsional vibration damper basically has various kinds such as a viscosity damper, a spring damper, a rubber damper, and so on, and among them, generally, the viscosity damper having no elastic coupling or the spring damper using a spring and oil viscosity is most popular in this field.
  • the viscosity damper does not have any elastic coupling, unlike the spring damper or the rubber damper, it has a stress damping effect on critical revolution of a rotating shaft with respect to a resonance frequency.
  • the viscosity damper does not have any vibration stress distributing effect on the critical revolution, has a relatively large size, and has a difficulty in exchanging high viscosity of si1icon oil.
  • the spring damper has a vibration stress distributing effect on the critical revolution through the elastic coupling thereof, but it has a relatively high production cost and an additional problem that the spring may be broken.
  • the present invention has been made to solve the above problems occurring in the prior art, and it is an object of the present invention to provide a hydraulic spring type torsional vibration damper that has an advantage of a viscosity damper having a stress damping effect on critical revolutions with respect to a resonance frequency, while having an advantage of a spring damper having an excellent vibration stress distributing effect on the critical revolutions.
  • a hydraulic spring type torsional vibration damper including: a hub ring coupled to a crankshaft of an engine; a circular ring disposed spaced apart from the hub ring by a given distance toward the outside of the hub ring; a plurality of pressure plates arranged along a circumferential direction between the hub ring and the circular ring, while connecting the hub ring and the circular ring, in such a manner as to define a plurality of space portions along the circumferential direction; a plurality of inert ial masses disposed in the plurality of space portions between the hub ring and the circular ring defined by the plurality of pressure plates, each of the inertial masses having an oil chamber formed at both sides of each pressure plate, the oil chamber having oil filled thereinto; a plurality of steel springs fixedly mounted onto the hub ring so as to elastically support the plurality of inertial masses; an inside cover plate and an outside cover plate mounted on the both outsides of the inertial masses,
  • a hydraulic spring type torsional vibration damper according to the present invention has a combined structure wherein the function of a viscosity damper is performed by means of pressure plates and pressurizing oil and the function of a spring damper is performed by inertial masses and steel springs, so that structural costs can be greatly reduced, and relatively low structural stress can be obtained, thereby enhancing a structural stability.
  • the hydraulic spring type torsional vibration damper according to the present invention just uses system oil in a prime mover, without using separate oil, so that an oil exchanging process is not needed, which reduces the costs consumed for repair, and since the system oil is kept circulated, further, the heat generated in the damper is naturally emitted to the outside.
  • FIG.l is a perspective view showing a completely assembled state of a hydraulic spring type torsional vibration damper according to the present invention.
  • FIG.2 is a perspective view showing a state where inside and outside cover plates are uncovered in the hydraulic spring type torsional vibration damper according to the present invention.
  • FIG.3 is a front view showing the hydraulic spring type torsional vibration damper according to the present invention.
  • FIG.4 is a partly detailed view of FIG.3.
  • FIG.5 is a sectional view taken along the line A-A of FIG.3.
  • FIG.6 is an exploded perspective view showing a state where a pressure plate is mounted on a hub ring in the hydraulic spring type torsional vibration damper according to the present invention.
  • FIG.6 is an exploded perspective view showing a state where a pressure plate is mounted on a hub ring in the hydraulic spring type torsional vibration damper according to the present invention.
  • FIG.l is a perspective view showing a completely assembled state of a hydraulic spring type torsional vibration damper according to the present invention
  • FIG.2 is a perspective view showing a state where inside and outside cover plates are uncovered in the hydraulic spring type torsional vibration damper according to the present invention
  • FIG.3 is a front view showing the hydraulic spring type torsional vibration damper according to the present invention
  • FIG.4 is a partly detailed view of FIG.3
  • FIG.5 is a sectional view taken along the line A-A of FIG.3.
  • the torsional vibration damper according to the present invention is coupled to a crankshaft 1 of an engine and includes a viscosity damper unit 3 and a spring damper unit 5 each serving to absorb the vibration transmitted to the crankshaft 1.
  • the viscosity damper unit 3 includes a hub ring 7 coupled to the crankshaft 1 of the engine, a circular ring 9 disposed spaced apart from the hub ring 7 by a given distance toward the outside of the hub ring 7, and a plurality of pressure plates 11 arranged along a circumferential direction between the hub ring 7 and the circular ring 9, while connecting the hub ring 7 and the circular ring 9, in such a manner as to define a plurality of space portions 13 along the circumferential direction.
  • the spring damper unit 5 includes a plurality of inert ial masses 17 disposed in the plurality of space portions 13 between the hub ring 7 and the circular ring 9 defined by the plurality of pressure plates 11, each of the inert ial masses 17 having an oil chamber 15 formed at both sides of each pressure plate 11, the oil chamber 15 having oil filled thereinto, and a plurality of steel springs 19 fixedly mounted onto the hub ring 7 so as to elastically support the plurality of inert ial masses 17.
  • each of the inertial masses 17 does not have such a size as to be fully filled in each space portion 13 formed between the adjacent two pressure plates 11, but has a somewhat smaller size than a distance between the adjacent two pressure plates 11, such that a space portion having a predetermined size into which oil is filled, that is, the oil chamber 15, is formed between each pressure plate 11 and each inertial mass 17.
  • the hub ring 7 and the circular ring 9 are provided an inside cover plate 21 and an outside cover plate 23 that are coupled integrally with the inertial masses 17 by means of bolts 25 and are adapted to allow the hub ring 7 and the circular ring 9 to be watertight and freely rotated.
  • the inside cover plate 21 and the outside cover plate 23 serve to keep the both sides of the hub ring 7 and the circular ring 9 at a watertight state, the space portions 13 are formed between the hub ring 7 and the circular ring 9 and the inertial masses 17 are inserted into the space portions 13, thereby filling the oil between each inertial mass 17 and each pressure plate 11.
  • the inside cover plate 21 and the outside cover plate 23 are coupled to the inertial masses 17 by means of the bolts 25, thereby advantageously permitting the mass of the inertial masses 17 to be increased.
  • the hub ring 7 has an oil cover plate 27 mounted at the central portion thereof coupled to the crankshaft 1 of the engine, and an oil circulation chamber 31 is formed between the hub ring 7 and the oil cover plate 27 in such a manner as to communicate with an oil supply passageway 29 of the crankshaft 1.
  • the hub ring 7 has a plurality of oil passageways 33 formed radially therealong in such a manner as to communicate with the oil circulation chamber 31, and as shown in FIG.4, the plurality of pressure plates 11 coupled to the hub ring 7 have a plurality of oil passageways 35 formed radially therealong.
  • each of the plurality of pressure plates 11 has a plurality of orifices 37 formed to pass through the left and right sides thereof, and one of the plurality of orifices 37 communicates with the oil passageway 35 in a crossing relation therewith.
  • oil is supplied from the oil circulation system of the engine and flows along an oil supply passageway 29 in the crankshaft 1, thereby serving to help the lubrication of the crankshaft 1 and the cooling action thereof, and if the oil flows into the oil circulation chamber 31, it is passed sequentially through the oil passageways 33 formed along the hub ring 7 and the oil passageways 35 and the orifices 37 formed along the plurality of pressure plates 11 and is then supplied to the oil chamber 15 between each pressure plate 11 and each inertial mass 17.
  • the oil is filled into the oil chamber 15 formed at both sides of each pressure plate 11 such that the pressure plates 11 are kept supported by the oil.
  • the pressure plates 11 connecting the hub ring 7 and the circular ring 9 are rotated, and at this time, as the pressure plates 11 are rotated, the oil is moved to the left or right sides by means of the orifices 37 in each pressure plate 11, such that the variations of the pressure generated in the oil chambers 15 formed at both sides of each pressure plate 11 are adjusted.
  • each of the plurality of pressure plates 11 are forcedly press-fitted to insertion grooves 7a and 9a formed on the hub ring 7 and the circular ring 9, and therefore, no separate fixing and coupling way like welding is needed.
  • the forcedly press-fitting of each pressure plate 11 permits the resistance to the torsional moment to be improved.
  • Each of the plurality of steel springs 19 serving to elastically connect the hub ring 7 with each inertial mass 17 is attached to each of a plurality of trapezoidal base springs 39 insertedly formed along the circumferential surface of the hub ring 7, and during the rotation of the hub ring 7, the base springs 39 support the steel springs 19, thereby preventing the bar-like steel springs 19 from escaping from its position toward the outside.
  • each of the plurality of inertial masses 17 has an insertion groove 41 adapted to have the bar-like steel spring 19 inserted thereinto, and at the state where the steel spring 19 is just inserted into the insertion groove 41, each steel spring 19 and each inertial mass 17 are coupled with each other.
  • crankshaft 1 and the hub ring 7 are coupled to each other by coupling a flange part Ia formed along the front end portion of the crankshaft 1 with a flange part 7a of the hub ring 7 by means of bolts 43.
  • the viscosity damper unit 3 and the spring damper unit 5 are at an equilibrium state to each other, and at this time, the oil that is supplied along the oil supply passageway 29 in the crankshaft 1 in the oil circulation system of the engine is passed sequentially through the oil circulation chamber 31, the oil passageways 33 of the hub ring 7 and the oil passageways 35 and the orifices 37 of the plurality of pressure plates 11 and is then supplied to the oil chamber 15.
  • the inertial masses 17 formed between the adjacent pressure plates 11 are encompassed by the oil filled into the oil chambers 15 and supported by means of the steel springs 19, such that the inertial masses 17 are not rotated and have relative motions with respect to the steel springs 19.
  • the pressure plates 11 and the inertial masses 17 are desirably 6 to 24 in number, and if necessary, they can have more than 24.
  • the steel spring 19 connected to the inertial mass 17 causes the deformity of the displacement generated by the exciting torque and has a function of damping vibration and a function of applying a spring constant, and in addition thereto, the steel spring 19 allows the inertial mass 17 to be located at the initial equilibrium state upon a stop state or a zero exciting torque state.
  • the pressure plates 11 connecting the plurality of damper sections formed between the hub ring 7 and the circular ring 9 by coupling the hub ring 7 and the circular ring 9 to each other have inertial moment, and if necessary, the number of orifices 35 formed in each pressure plate 11 can be varied.
  • the torsional vibration damper according to the present invention has a combined structure wherein the function of the viscosity damper is performed by means of the plurality of pressure plates 11 and the pressurizing oil and the function of the spring damper is performed by the plurality of inertial masses 17 and the plurality of steel springs 19, so that structural costs can be greatly reduced, and relatively low structural stress can be obtained, thereby enhancing a structural stability.
  • the torsional vibration damper according to the present invention just uses the system oil in the prime mover, without using separate oil, so that an oil exchanging process is not needed, which reduces the costs consumed for repair, and since the system oil is kept circulated, further, the heat generated in the damper is naturally emitted to the outside.
  • the torsional vibration damper is constructed wherein the pressure plates having the orifices formed therein are moved between the hub ring and the circular ring, thereby damping the vibration received from the crankshaft through the hub ring and wherein the inert ial masses are connected to the hub ring by means of the steel springs, thereby offsetting the exciting torque.
  • the torsional vibration damper according to the present invention obtains all of effects the viscosity damper and the spring damper have, enhances the vibration damping effect, while having a simplified configuration, and has relatively low structural stress, thereby enhancing a structural stability.

Landscapes

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

Abstract

La présente invention se rapporte à un amortisseur de vibrations de torsion de à type ressort hydraulique comprenant une pluralité de plaques de pression qui ont des orifices formés à l'intérieur et sont déplacées entre un anneau de moyeu et un anneau circulaire, amortissant de cette façon les vibrations reçues d'un vilebrequin par l'intermédiaire de l'anneau de moyeu et comprenant une pluralité de masses d'inertie qui sont reliées à l'anneau de moyeu au moyen d'une pluralité de ressorts en acier, compensant de cette façon le couple d'excitation. Par conséquent, l'amortisseur de vibrations de torsion selon la présente invention acquiert tous les effets que l'amortisseur visqueux et l'amortisseur à ressort peuvent avoir, améliore l'effet d'amortissement de vibrations, tout en ayant une configuration simplifiée et une contrainte structurelle relativement faible pour obtenir une stabilité structurelle élevée.
PCT/KR2007/005967 2007-11-23 2007-11-23 Amortisseur de vibrations de torsion de type à ressort hydraulique WO2009066823A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/KR2007/005967 WO2009066823A1 (fr) 2007-11-23 2007-11-23 Amortisseur de vibrations de torsion de type à ressort hydraulique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/KR2007/005967 WO2009066823A1 (fr) 2007-11-23 2007-11-23 Amortisseur de vibrations de torsion de type à ressort hydraulique

Publications (1)

Publication Number Publication Date
WO2009066823A1 true WO2009066823A1 (fr) 2009-05-28

Family

ID=40667636

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR2007/005967 WO2009066823A1 (fr) 2007-11-23 2007-11-23 Amortisseur de vibrations de torsion de type à ressort hydraulique

Country Status (1)

Country Link
WO (1) WO2009066823A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011026872A3 (fr) * 2009-09-01 2011-05-05 B.E.C. Breitbach Engineering Consulting Gmbh Amortisseur d'oscillations destiné aux oscillations qui se superposent à un mouvement de rotation autour d'un axe de rotation
CN103159009A (zh) * 2013-03-29 2013-06-19 无锡市诚信洗选设备有限公司 一种停车导轮
CN105899310A (zh) * 2014-01-25 2016-08-24 博格华纳公司 旋转减振器
DE102017211204A1 (de) * 2017-06-30 2019-01-03 Zf Friedrichshafen Ag Tilgersystem
DE102020205602A1 (de) 2020-05-04 2021-11-04 Volkswagen Aktiengesellschaft Torsionsschwingungsdämpfer sowie Brennkraftmaschine mit Torsionsschwingungsdämpfer und Ölabscheider

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5188002A (en) * 1988-07-25 1993-02-23 Woco Franz-Josef Wolf & Co. Torsional vibration damper
JP2004132491A (ja) * 2002-10-11 2004-04-30 Toyota Motor Corp 衝突型ロータリダンパ
KR100534824B1 (ko) * 2003-09-04 2005-12-08 현대자동차주식회사 비틀림 진동 댐퍼

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5188002A (en) * 1988-07-25 1993-02-23 Woco Franz-Josef Wolf & Co. Torsional vibration damper
JP2004132491A (ja) * 2002-10-11 2004-04-30 Toyota Motor Corp 衝突型ロータリダンパ
KR100534824B1 (ko) * 2003-09-04 2005-12-08 현대자동차주식회사 비틀림 진동 댐퍼

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011026872A3 (fr) * 2009-09-01 2011-05-05 B.E.C. Breitbach Engineering Consulting Gmbh Amortisseur d'oscillations destiné aux oscillations qui se superposent à un mouvement de rotation autour d'un axe de rotation
CN103159009A (zh) * 2013-03-29 2013-06-19 无锡市诚信洗选设备有限公司 一种停车导轮
CN105899310A (zh) * 2014-01-25 2016-08-24 博格华纳公司 旋转减振器
CN105899310B (zh) * 2014-01-25 2019-01-01 博格华纳公司 旋转减振器
DE102017211204A1 (de) * 2017-06-30 2019-01-03 Zf Friedrichshafen Ag Tilgersystem
US10844929B2 (en) 2017-06-30 2020-11-24 Zf Friedrichshafen Ag Lubricated absorber system
DE102020205602A1 (de) 2020-05-04 2021-11-04 Volkswagen Aktiengesellschaft Torsionsschwingungsdämpfer sowie Brennkraftmaschine mit Torsionsschwingungsdämpfer und Ölabscheider
DE102020205602B4 (de) 2020-05-04 2023-06-01 Volkswagen Aktiengesellschaft Torsionsschwingungsdämpfer sowie Brennkraftmaschine mit Torsionsschwingungsdämpfer und Ölabscheider

Similar Documents

Publication Publication Date Title
KR101358998B1 (ko) 차량용 토크 컨버터
US9958027B2 (en) Vibration damping device
US9416860B2 (en) Vibration damping device
CN106468340B (zh) 扭转振动吸收系统
EP2685127B1 (fr) Dispositif d'amortissement des vibrations
US8146457B2 (en) Disk pendulum vibration damper
CN100441903C (zh) 发动机的平衡器从动齿轮
WO2009066823A1 (fr) Amortisseur de vibrations de torsion de type à ressort hydraulique
KR101366107B1 (ko) 축진동 유압식 진동 댐퍼 겸용 유연 커플링
KR20080080993A (ko) 엔진용 트랙션 메커니즘 구동부
US11867251B2 (en) Pulley decoupler having a centrifugal pendulum device with a first friction device
CN102434623B (zh) 用于消除旋转振动的装置
CN203627744U (zh) 扭矩波动减小装置
US10113611B2 (en) Torsional vibration damper and engine assembly including the same
KR100845983B1 (ko) 유압식 스프링형 비틀림 진동댐퍼
US20030000783A1 (en) Rotary machine
US20020168126A1 (en) Rotation shaft support structure of a motor/generator
RU2405991C1 (ru) Демпфер
JP2019507295A (ja) 車両のドライブトレイン用ねじり振動減衰装置
US20130217511A1 (en) Torsional vibration damper
EP2414701B1 (fr) Dispositif et procede pour attenuer la vibration d'un moteur a piston et moteur a piston
CN110486417B (zh) 机动车发动机和扭振减振器的应用
CN103032325A (zh) 螺杆压缩机
KR101836635B1 (ko) 차량용 진동 저감 장치
KR101449530B1 (ko) 폐쇄형 코일 스프링 비틀림 진동 댐퍼

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 07834264

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 07834264

Country of ref document: EP

Kind code of ref document: A1