WO2014114281A1 - Ressort de compression hélicoïdal et amortisseur de vibrations de torsion - Google Patents

Ressort de compression hélicoïdal et amortisseur de vibrations de torsion Download PDF

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Publication number
WO2014114281A1
WO2014114281A1 PCT/DE2013/200371 DE2013200371W WO2014114281A1 WO 2014114281 A1 WO2014114281 A1 WO 2014114281A1 DE 2013200371 W DE2013200371 W DE 2013200371W WO 2014114281 A1 WO2014114281 A1 WO 2014114281A1
Authority
WO
WIPO (PCT)
Prior art keywords
helical compression
compression spring
spring
torsional vibration
vibration damper
Prior art date
Application number
PCT/DE2013/200371
Other languages
German (de)
English (en)
Inventor
Hartmut Mende
Ad Kooy
Christian Bahrmann
Original Assignee
Schaeffler Technologies AG & Co. KG
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 Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to DE112013006492.8T priority Critical patent/DE112013006492A5/de
Priority to CN201380071111.5A priority patent/CN104937305B/zh
Publication of WO2014114281A1 publication Critical patent/WO2014114281A1/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
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • 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
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/04—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
    • F16F15/12—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

Definitions

  • the invention relates to a helical compression spring, in particular for a torsional vibration damper, with a plurality of spring coils spaced apart, which are compressible on block with a corresponding load, and a torsional vibration damper, in particular two-mass flywheel, with such helical compression springs.
  • a helical compression spring is known from steel spring wire having a plurality of extending along its length windings, wherein the coil spring can be pressed on block, wherein the coil spring between its two end turns at least two winding types with different outer diameter, namely a first , larger outer diameter and a second, smaller outer diameter, these types of turns - viewed in the longitudinal direction of the spring - both arranged sequentially according to a certain pattern as well as wound so are that the spring has diametrically opposed Windungs Schemee, based on the longitudinal direction of the Coil spring considered in the radial direction, at least approximately at the same height are on one side, whereas the diametrically opposite Windungs Schemee the two types of winding at least approximately ver to their outer diameter difference ver are set to create a torsional vibration damper, which has a large damping potential and a long life.
  • DE 10 2008 005 140 A1 discloses a torsional vibration damper with a drive-side and an output-side transmission element, which are rotatable against one another between these intended damping device with circumferentially effective energy storage, wherein the transmission elements have Beaufschlagungs Schemee for the energy storage and radially inside or radially outside the energy storage at least one energy-absorbing, between the support elements provided on the support elements einspannbares delimiting element is provided which is limited rotatable relative to two transmission elements and to limit the allowed by the damping device relative rotation between the transmission elements to the effective between the two transmission elements damping device, in particular the energy storage, to protect against overloading.
  • a torsional vibration damper is known from DE 10 2008 009 656 A1 with a drive-side and an output-side transmission element, which are rotatable relative to each other at least one provided between these damping device with at least one effective in the circumferential direction long coil spring to each other, wherein the transmission elements have loading areas for the coil spring and radially within the coil spring at least one limiting the rotation between the transmission elements effecting stop element is provided, wherein the stop element two to ten degrees before the maximum allowable Kompressionsweg the coil spring is effective, in particular effective between the two transmission elements damping device, in particular by coil springs formed energy storage to protect against overloading.
  • the invention has for its object to improve an initially mentioned helical compression spring structurally and / or functionally.
  • a burden should be reduced at peak momentary moments.
  • a functional impairment should be prevented due to jerky peak moments.
  • a reliability should be increased.
  • a maximum mileage should be increased.
  • a ride comfort should be increased.
  • a requirement of a peak torque limiter in a release system should be eliminated.
  • a requirement for a high overall spring stiffness should be eliminated.
  • a requirement of a torque limiter should be omitted.
  • a requirement of a clutch torque reduction should be omitted.
  • a stop moment should be reduced.
  • an effort should be reduced.
  • a high insulation effect should be ensured.
  • an internal centrifugal pendulum should be used.
  • a structurally and / or functionally improved torsional vibration damper is to be provided.
  • a solution of the problem is carried out with a helical compression spring, in particular for a torsional vibration damper, with a plurality of spaced spring coils which are compressible under appropriate load on block, wherein the helical compression spring is claimed in a block load in a time-stable area.
  • the helical compression spring may have a longitudinal axis.
  • the helical compression spring may have a circular cross-section.
  • the helical compression spring can be wound from a spring wire.
  • the spring wire may have a circular cross section.
  • the helical compression spring may be cold formed.
  • the helical compression spring can be thermoformed.
  • the helical compression spring can be made of a spring steel.
  • the helical compression spring may have a cylindrical shape.
  • the helical compression spring may have an arcuate shape.
  • the helical compression spring may have an arcuate longitudinal axis.
  • the screws B compression spring may have two ends. The ends can serve to transfer forces to and / or from the helical compression spring.
  • the helical compression spring can be used for arrangement in a channel or torus-like receiving space.
  • the helical compression spring may be compressible in the extension direction of its longitudinal axis.
  • a block load may be a radially inner block load in a helical compression spring having an arcuate longitudinal axis.
  • the helical compression spring need not be compressed circumferentially on block.
  • the term "time-stable" can refer to a fatigue strength The fatigue strength can be determined in methodical tests The fatigue strength can be determined in fatigue tests or Wöhlerver- search The term "time-stable" can serve to delineate a permanent area.
  • a permanent region may have a nominal voltage amplitude S a of at most approximately 1200 N / mm 2 .
  • the time-stable range may be an area below about 1 x 10 6 to about 5 x 10 6 swing games.
  • the time-stable range can be a range between about 10 4 and about 2 x 10 6 swinging games.
  • the time-stable range can be an area below about 10 4 to about 10 5 swinging games.
  • the time-stable range can be a short-term range.
  • the helical compression spring can be at a block load in the range of a nominal voltage amplitude S a > 1,000 N / mm 2 , in particular in the range of a nominal voltage amplitude S a > 1,200 N / mm 2 , in particular in the range of a nominal voltage amplitude S a > 1,400 N / mm 2 , in particular in the range a nominal voltage amplitude S a > 1,600 N / mm 2 , to be claimed.
  • the helical compression spring may have a spring characteristic which is at least approximately unchanged in the region of a non-blocking load.
  • the helical compression spring can have an extended characteristic.
  • the helical compression spring may have a characteristic section with an increased pitch.
  • the extended characteristic can be used at least in sections to improve insulation and starting behavior.
  • the helical compression spring can have at least sections between the spring coils enlarged Windungsabmaladies.
  • the helical compression spring may have increased Windungsabexcellent between the spring ends. gleenfederend rock the Windungsabnote can not be increased. For example, the first one to five turns can be made without increased distances.
  • the helical compression spring may have an at least approximately constant coil diameter. This helical compression spring can be referred to as a high-capacity spring.
  • the helical compression spring may have a varying coil diameter. The winding diameter may vary in sections such that, when the helical compression spring is compressed, windings are at least partially pushed into one another, whereby with friction increased damping occurs. This helical compression spring can be referred to as a high-capacity damping spring.
  • a solution of the problem underlying the invention with a torsional vibration damper, in particular two-mass flywheel, comprising an input part and an output part with a common axis of rotation about which the input part and the output part rotatable together and rotatable relative to each other are limited, and one between the input part and the Output member effective spring-damper device arranged in the circumferential direction of the torsional vibration damper such helical compression springs.
  • the torsional vibration damper can have an increased impact torque.
  • Stop torque can be a moment in which the helical compression springs are compressed to block.
  • the abutment torque may be greater than an engine torque.
  • the abutment torque may be about 1.5 to about 2.1 times the engine torque.
  • the torsional vibration damper can be arranged in a drive train of a
  • the drive train may include an internal combustion engine.
  • the powertrain may include a friction clutch device.
  • the drive train may have a transmission.
  • the drive train may have at least one drivable wheel.
  • the torsional vibration damper may be arrangeable in the drive train between the internal combustion engine and the friction clutch device.
  • the torsional vibration damper can serve to reduce torsional vibrations, which are excited by periodic processes, in particular in the internal combustion engine.
  • the torsional vibration damper may comprise a centrifugal pendulum device.
  • the centrifugal pendulum device may have at least one pendulum mass displaceable under centrifugal force.
  • the centrifugal pendulum device can be arranged on the input part.
  • the centrifugal pendulum device may be arranged on the output part.
  • the centrifugal pendulum device can be inboard.
  • the centrifugal pendulum device may be protected like a box.
  • the input part can serve for driving connection with the internal combustion engine.
  • the input part may have a flange portion.
  • the input part may have a lid portion.
  • the flange portion and the lid portion may define a receiving space for the helical compression springs.
  • the input part may have abutment sections for the helical compression springs.
  • the contact sections of the input part can protrude into the receiving space.
  • the output part may have a flange part.
  • the end- gang part may have abutment sections for the helical compression springs.
  • the contact sections of the output part can protrude into the receiving space.
  • the helical compression springs can with their longitudinal axes in the circumferential direction of the
  • the helical compression springs can be arranged distributed in the circumferential direction of the torsional vibration damper.
  • the helical compression springs can each be supported on the one hand on the input part and on the other hand on the output part.
  • the torsional vibration damper may comprise at least a first helical compression spring and at least one second helical compression spring.
  • the at least one first helical compression spring can be associated with a force flow in the pulling direction.
  • the at least one second helical compression spring can be associated with a force flow in the thrust direction.
  • the torsional vibration damper may have a plurality of first helical compression springs.
  • the plurality of first coil springs may be arranged in series.
  • the plurality of first coil springs may be arranged in parallel.
  • the plurality of first coil springs may be arranged nested one inside the other.
  • the torsional vibration damper may have a plurality of second helical compression springs.
  • the plurality of second coil springs may be arranged in series.
  • the plurality of second coil springs may be arranged in parallel.
  • the plurality of second coil springs may be nested one inside the other.
  • the spring-damper device may comprise a friction device.
  • a spring design can be modified in such a way that a block stress is applied far beyond a fatigue strength range (> 1200 to 1600 N / mm 2 ). In this case, a stress at z. B. engine torque be unchanged. This design can lead to a very high impact torque, which can be 20% to 60% above a conventional impact safety of about 1, 3 x engine torque. The energy that can be absorbed over a normal impact moment can be above 50 J.
  • Impacts can be cushioned to a large extent "softly.”
  • these can be conventionally designed Firstly, a spring rate and thus an insulating effect can be better, secondly, the high-capacity spring can be better protected against excessive impacts, since a blocking of windings a further increase of the stresses prevents a constructional execution by a block load in the time-stability range with a stop moment> 1.6 x motor torque.
  • a high-capacity damping spring This is characterized by a varying winding diameter.
  • the high-capacity damper spring can be extended apart in the circumferential direction until similar stresses are applied to a voltage-determining winding as on the high-capacity spring. These can then be significantly increased compared to a current design guideline.
  • a characteristic of the high-capacity damping spring can be significantly extended and Impacts can - as in the high-capacity standard spring - are already largely reduced before the contact of the damping spring.
  • a part of the characteristic curve extension can also be used for improving the insulation and starting behavior of the damping spring.
  • the high-capacity damper spring can have the advantage over a high-capacity standard spring that more energy can be dissipated via an emerging friction between the windings than with the high-capacity standard spring.
  • the principal disadvantage of the damping spring can still arise in the case of the high-capacity damping spring, as is the loss of spring capacity compared with a standard spring (standard design voltages) or the high-capacity standard spring (increased permissible stresses) , Due to the fact that impacts are already largely reduced before the stop of the high-capacity damping spring, the variation of the winding diameter and thus a loss of capacity can be minimized.
  • the high-capacity damper spring can be designed as a counterpart to the high-capacity standard spring with comparable design features with regard to spring tension and setting specifications.
  • Fig. 1 is a arranged between an input part and an output part of a dual mass flywheel high-capacitive helical compression spring and
  • Fig. 2 is a diagram with a characteristic of a dual-mass flywheel with high-capacitive helical compression springs.
  • Fig. 1 shows a between an input part 100 and an output part 102 of a
  • FIG. 2 shows a diagram 200 with a characteristic curve 202 of a dual-mass flywheel with high-capacitance helical compression springs, such as helical compression springs 104 according to FIG. 1.
  • the dual-mass flywheel which is otherwise not shown, is used for arrangement in a drive train of an internal combustion engine-driven motor vehicle between an internal combustion engine and a friction clutch in order to damp torsional vibrations.
  • abrupt peak moments also occur during operation.
  • the helical compression springs, such as 104 which serve as an energy store in the dual-mass flywheel, can be compressed to block.
  • a corresponding loading direction is shown in FIG. 1 with an arrow a.
  • Such peak moments can amount to a multiple of the maximum engine torque.
  • Such peak moments are also referred to as impacts. Impacts occur in particular in a fast closing of the friction clutch when a clutch input part and a clutch output part have large speed differences.
  • Such closing operations occur, for example, in sporty driving style, but also in case of incorrect operation, such as slipping off a clutch pedal on.
  • occurrence of such closing operations is facilitated by a subsequent change factory-set control parameters of electrical control devices, such as an engine control unit, a transmission control unit and / or a clutch control unit, with the aim of increasing performance.
  • electrical control devices such as an engine control unit, a transmission control unit and / or a clutch control unit
  • chip tuning Such changes are also referred to as chip tuning.
  • the high-capacity helical compression spring 104 With the help of the high-capacity helical compression spring 104, a high impact torque is achieved.
  • the helical compression spring 104 has a constant winding diameter D over its length.
  • the winding diameter D is determined in particular by an available space.
  • the helical compression spring 104 has a constant wire thickness d.
  • a tension of the helical compression spring 104 is defined. Between the turns, the helical compression spring 104 extended distances, as s, on. The winding distances s are decisive for the stop moment. The abutment torque is increased due to the extended winding spacing s, so that the helical compression spring 104 has an increased capacity.
  • the characteristic curve 202 shown in FIG. 2 has a branch 204, which has a tensile load of
  • characteristic curve 202 is extended on the tension side as well as the thrust side with respect to a conventional characteristic curve 208 and ends at significantly higher torque values. In the present case, characteristic 202 ends at approx. 675 numbers.

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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 concerne un ressort de compression hélicoïdal (104) destiné en particulier à un amortisseur de vibrations de torsion, comportant plusieurs spires de ressort espacées les unes des autres qui peuvent être comprimées à bloc sous l'effet d'une contrainte appropriée, le ressort de compression hélicoïdal étant sollicité lors de l'application d'une charge à bloc dans une plage définie dans le temps. L'invention concerne également un amortisseur de vibrations de torsion, en particulier un volant bimasse, comprenant un élément d'entrée (100) et un élément de sortie (102) présentant un axe de rotation commun autour duquel l'élément d'entrée et l'élément de sortie peuvent tourner ensemble et peuvent se déplacer de façon limitée l'un par rapport à l'autre, et un dispositif d'amortissement à ressorts agissant entre l'élément d'entrée et l'élément de sortie et comportant des ressorts de compression hélicoïdaux de ce type agencés dans la direction circonférentielle de l'amortisseur de vibrations de torsion.
PCT/DE2013/200371 2013-01-23 2013-12-17 Ressort de compression hélicoïdal et amortisseur de vibrations de torsion WO2014114281A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112013006492.8T DE112013006492A5 (de) 2013-01-23 2013-12-17 Schraubendruckfeder und Drehschwingungsdämpfer
CN201380071111.5A CN104937305B (zh) 2013-01-23 2013-12-17 螺旋压力弹簧和扭转振动减振器

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE102013201047 2013-01-23
DE102013201045 2013-01-23
DE102013201047.8 2013-01-23
DE102013201045.1 2013-01-23
DE102013212706.5 2013-06-28
DE102013212706 2013-06-28

Publications (1)

Publication Number Publication Date
WO2014114281A1 true WO2014114281A1 (fr) 2014-07-31

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ID=50071373

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2013/200371 WO2014114281A1 (fr) 2013-01-23 2013-12-17 Ressort de compression hélicoïdal et amortisseur de vibrations de torsion

Country Status (3)

Country Link
CN (1) CN104937305B (fr)
DE (2) DE112013006492A5 (fr)
WO (1) WO2014114281A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022027827A1 (fr) * 2020-08-05 2022-02-10 中国华能集团清洁能源技术研究院有限公司 Appareil et procédé d'amortissement de vibrations de torsion de pale pour ensemble générateur d'énergie éolienne à axe horizontal

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104763765B (zh) * 2015-04-10 2016-10-05 山东大学 一种高静低动刚度的分段线性隔振器及其工作方法
DE112016002586A5 (de) * 2015-06-11 2018-05-24 Schaeffler Technologies AG & Co. KG Antriebsstrang für ein kraftfahrzeug

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19912970A1 (de) 1998-03-25 1999-09-30 Luk Lamellen & Kupplungsbau Drehschwingungsdämpfer sowie Schraubendruckfeder für einen Drehschwingungsdämpfer
DE102008005140A1 (de) 2007-02-08 2008-08-14 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Torsionsschwingungsdämpfer
DE102008009656A1 (de) 2007-03-08 2008-09-11 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Torsionsschwingungsdämpfer

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10209409A1 (de) * 2001-03-08 2002-09-12 Luk Lamellen & Kupplungsbau Drehschwingungsdämpfer
WO2006042495A1 (fr) * 2004-10-23 2006-04-27 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Roue volante a deux masses
KR20080074091A (ko) * 2005-12-09 2008-08-12 루크 라멜렌 운트 쿠플룽스바우베타일리궁스 카게 회전 진동 댐퍼

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19912970A1 (de) 1998-03-25 1999-09-30 Luk Lamellen & Kupplungsbau Drehschwingungsdämpfer sowie Schraubendruckfeder für einen Drehschwingungsdämpfer
DE102008005140A1 (de) 2007-02-08 2008-08-14 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Torsionsschwingungsdämpfer
DE102008009656A1 (de) 2007-03-08 2008-09-11 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Torsionsschwingungsdämpfer

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022027827A1 (fr) * 2020-08-05 2022-02-10 中国华能集团清洁能源技术研究院有限公司 Appareil et procédé d'amortissement de vibrations de torsion de pale pour ensemble générateur d'énergie éolienne à axe horizontal

Also Published As

Publication number Publication date
DE102013226235A1 (de) 2014-07-24
DE112013006492A5 (de) 2015-10-29
CN104937305B (zh) 2018-07-17
CN104937305A (zh) 2015-09-23

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