EP1227056B1 - Kettentrieb mit einem polygonalen Kettenrad - Google Patents

Kettentrieb mit einem polygonalen Kettenrad Download PDF

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Publication number
EP1227056B1
EP1227056B1 EP01101782A EP01101782A EP1227056B1 EP 1227056 B1 EP1227056 B1 EP 1227056B1 EP 01101782 A EP01101782 A EP 01101782A EP 01101782 A EP01101782 A EP 01101782A EP 1227056 B1 EP1227056 B1 EP 1227056B1
Authority
EP
European Patent Office
Prior art keywords
manner
chain drive
drive according
chain
wheel
Prior art date
Legal status (The legal status 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 status listed.)
Revoked
Application number
EP01101782A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1227056A1 (de
Inventor
Univ.-Prof. Dipl.-Ing. Dr. techn. Jörg Oser O.
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
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Individual
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Publication date
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=8176299&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1227056(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Individual filed Critical Individual
Priority to ES01101782T priority Critical patent/ES2208471T3/es
Priority to DE50100794T priority patent/DE50100794D1/de
Priority to AT01101782T priority patent/ATE252052T1/de
Priority to EP01101782A priority patent/EP1227056B1/de
Priority to US10/037,794 priority patent/US6905432B2/en
Priority to JP2002015778A priority patent/JP2002276766A/ja
Publication of EP1227056A1 publication Critical patent/EP1227056A1/de
Publication of EP1227056B1 publication Critical patent/EP1227056B1/de
Application granted granted Critical
Anticipated expiration legal-status Critical
Revoked legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D3/00—Portable or mobile lifting or hauling appliances
    • B66D3/18—Power-operated hoists
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/1987—Rotary bodies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/1987—Rotary bodies
    • Y10T74/19884—Irregular teeth and bodies

Definitions

  • the invention relates to a chain drive with a traction device made of steel link chains or from round steel chains for gear wheels with a polygonal sprocket and Means to transmit fluctuations in speed and transmitted to the sprocket Reduce acceleration from at least one connected to the sprocket axle
  • Gear-wheel gears consist of one on the sprocket axle non-rotatable output gear with a different sized pitch circle is.
  • Chain drives are generally used in both conveyor and drive technology used for hoists as well as for continuous conveyors.
  • the compensation of the polygon effect was often with different, mostly complicated differential gears tries. Because of the complex construction of differential gears for reduction Due to the polygon effect, hardly any applications are known in practice.
  • the chain drive described at the outset is known from DE 15 31 307 A1.
  • the pitch circle is of different sizes, with a smallest radius meets the center of each link plate, while the largest Radius of the pitch circle coincides with the pitch circle diameter of the chain wheel.
  • there is no optimal speed compensation and acceleration compensation can be achieved because z. B. in the replacement polygon for Round steel chains additionally reduce the radius of the pitch circle at the location of the Tooth center of the chain wheel is required.
  • the known proposal takes into account furthermore not that a spur gear toothing in the intersection points of the Rolling curves due to the discontinuous concave rolling curve shape with currently known ones Out-of-round gearing processes are hardly technically and economically impossible to produce. In addition, it remains completely open which geometric shape the pitch curve shape is between the intersection points of the individual sections.
  • the invention has for its object these tangential acceleration fluctuations largely compensate and unwanted vibrations from Keep chain drive away.
  • the object is achieved according to the invention in that the driven wheel and the drive wheel from non-circular gears that are coordinated with one another in terms of translation exist, the drive gear in such a position assignment to the output gear stands that the smallest angular velocity with the Corners of the sprocket polygon coincide and the greater the angular velocity in the middle of a polygon line.
  • This suggestion exists advantageously with one or more gear stages of a gear train variable angular velocity.
  • the pitch circle radii of the toothed or are Pair of wheels designed so that they consist of piece-wise continuous, toothed sections the roll curves of non-circular gears exist and such a relative position to the sprocket, so that the tangential speed fluctuation the chain is largely avoided.
  • the effect or the non-circular gear pairs a variable output angular velocity at constant input angular velocity such that with the increasing or decreasing radial stand during chain circulation the chain from the fulcrum an opposite or increasing angular velocity is generated and thus the speed fluctuation in the tangent direction is achieved.
  • one or more non-circular gear stages not just any, but only certain medium ratios can be realized.
  • a particular advantage is therefore that the design equally for link chains with the same pitch angle and for round steel chains with unequal pitch angles for the replacement polygon of the chain wheel can be used.
  • round steel chains small sprockets with fewer Number of teeth mostly referred to as chain sprocket or chain sprocket.
  • the training of the teeth of the sprocket is irrelevant and whether the sprocket is designed with an even or odd number of teeth.
  • the pitch circle radius of the driven gear for round steel chains is larger in the middle of the shorter replacement polygon line than in the middle the longer replacement polygon line.
  • gear wheel gearbox has one or has several non-circular gear stages, at least the last stage as Non-circular gearing is executed. About one or more such non-circular gear stages can affect the gear ratio or other parameters become.
  • the speeds and accelerations are influenced after others Characterized in that the output gear for articulated chains on the circumference of the pitch circle has a number of continuous roll curve sections that are the same size as is the number of teeth on the sprocket.
  • the advantage is an almost even movement the chain by making the chain speed the same in every angular position is.
  • the output gear for round steel chains has a number of continuous roll curve sections on the circumference of the circle, which is twice the number of teeth on the sprocket. This causes the desired effect also for such round steel chains.
  • the steady roll curve movement also occurs because the drive gear is also formed with continuous roll curve sections on the circumference of the pitch circle.
  • the drive gear for link chains has any number of continuous roll curve sections equal to or greater than two. This allows the gear ratio to be set accordingly.
  • the geometric shape of the continuous Roll curve sections is designed so that at constant drive angular velocity the output angular velocity largely as a product of the mean Translation with the cosine of the output angle is achievable. This allows suitable curve shapes are used.
  • continuous roll curve sections are geometrical are designed so that the translation by simple or compound Polynomials, trigonometric functions, Fourier series or periodic or approximate mathematical functions.
  • An improvement in the joints between individual roll curve sections can advantageously be achieved in that the roll curve sections of the driven gear in the intersection points concave, one-sided have curved transition arcs that are tangent to the roll curve sections issue.
  • the compensation curves are symmetrical and mathematical by at least a fourth order polynomial or a modified trigonometric Function are at least of the form x sin x.
  • the compensation curves and the Transition arcs at the angle of the intersection of the continuous roll curve sections have a radius of curvature equal to or greater than the radius a machining tool.
  • the driven gear is at the intersection points is carried out at least in two parts, that after joining a Primary part and a secondary part concave sharp curve curve intersections without Transition arcs or compensation curves are provided.
  • the arc gap at the same time as a tool outlet and can be used as centering for the respective complementary part.
  • an embodiment is provided in such a way that that in partial areas cannot be compensated by transition arches or compensation curves Polygon effect with or with the next higher non-circular toothed output gears and drive gears through extensive correct assignment of transitionally correct transitional arches to the centric ones Output gears and drive gears can be compensated.
  • a gear wheel gear 2 with a non-circular toothed output gear 3a can be seen on the sprocket axle 1, with a traction means from a Steel link chain 7 or from a round steel chain 8, which is by means of a non-circular toothed Drive gear 4a is driven.
  • the latter is off a gear stage upstream of a drive gear 4 and an output gear 3, which by a Electric motor is driven on the drive side 5.
  • At least the last stage 12 of the gear wheel transmission 2 has a polygonal chain wheel 10 and means, to fluctuations in speed and acceleration transmitted to the sprocket 10 to reduce that of at least one connected to the sprocket axle 1
  • Gear-wheel transmission 2 consist of one on the sprocket axis 1 rotationally non-circular toothed output gear 3a with a different large pitch circle is formed.
  • the desired transmission behavior between ⁇ 1 and ⁇ 2 is only solved by one or more non-circular gear pair (s) 3, 4 or 3a, 4a with piecewise continuous roll curve sections 9 in such a way that for the rolling condition the partial sheet lengths 27 and 13 are the same size Rolling radii of the toothing r 1 ( ⁇ 1 ) and r 2 ( ⁇ 2 ) but depending on the location of ⁇ 1 and ⁇ 2 should be selected so that the transmission behavior is established according to equation 4.
  • Non-circular gears can also be economical today for complicated roll curve shapes getting produced. In addition, they are for the frequent case of a round steel sprocket 10 with unequal pitch angles as easy to implement as with same pitch angles.
  • the gear wheel gear 2 can one or more Have non-circular gear stages 11, at least the last stage 12 must be designed as non-circular teeth 14.
  • the output gear 3 has for a joint chain 7 on the pitch circle circumference 13 a number of continuous Rullkurvenabitese 9, which is the same size as the number of teeth of the chain wheel 10. Furthermore, the output gear 3 for the round steel chain 8 on the pitch circle circumference 13 has a number of continuous roll curve sections 9 which is twice as large as the number of teeth c of the chain wheel 10.
  • the drive gear 4 is also provided with such continuous roll curve sections 9 on the pitch circle circumference 13.
  • the drive gear 4 for an articulated chain 7 has any number of continuous roll curve sections 9 equal to or less than two. Each of these roll curves 9a forms an arc "b". In the case of round steel chains 8, the drive gear 4 has an even number of continuous roll curve sections 9.
  • the continuous roll curve sections 9 are also geometrically designed such that the translation "i" by simple or compound polynomials, trigonometric Functions, Fourier series or periodic or mathematical approximation functions can be achieved.
  • the lever arm “h” is a function of the drive or rotation angle ⁇ 2 at the output angular velocity ⁇ 2 .
  • the roll curve sections 9 of the driven gear 3 show at the intersection point 17 concave, one-sided curved transition arches 16, the tangential abut the roll curve sections 9.
  • the tangential transition arches 16 to the roll curves 9a can be counter-curved compensation curves 18 within tangential points of contact 19 of the continuous roll curve sections 9 lie.
  • the compensation curves 18 are symmetrical and can be mathematical by at least a fourth order polynomial or a modified trigonometric Function at least of the form x. sin x can be represented.
  • the compensation curves 18 and the transition arches 16 point at the angle of the intersection point 17 of the continuous roll curve sections 9 have a radius of curvature that can be equal to or greater than the radius of a machining tool 20.
  • the driven gear 3 is at least at the intersection points 17 executed in two parts.
  • a primary part 21 can be joined together with a secondary part 22 so that concave, sharp roll curve intersections 23 (without Transition arcs 16 or compensation curves 18) arise.
  • 6B-6D show that every second roll curve section 9 is omitted and an arc gap 24 is radially reduced up to a centering radius 25.
  • the gap in the bow 24 can be used as a tool outlet and as a centering for the respective Complementary part can be used.
  • transition areas 16 or the compensating curves 18 do not completely compensate for the existing polygon effect there is the possibility with or with the next higher non-circular toothed Output gears 3a and drive gears 4a through a comparison a circumferentially correct assignment of translations that are correct Transition arches 16 to the centrally formed output gears 3a and drive gears 4a.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gears, Cams (AREA)
  • Structure Of Transmissions (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
EP01101782A 2001-01-26 2001-01-26 Kettentrieb mit einem polygonalen Kettenrad Revoked EP1227056B1 (de)

Priority Applications (6)

Application Number Priority Date Filing Date Title
ES01101782T ES2208471T3 (es) 2001-01-26 2001-01-26 Transmision de cadena provista de una rueda poligonal de cadena.
DE50100794T DE50100794D1 (de) 2001-01-26 2001-01-26 Kettentrieb mit einem polygonalen Kettenrad
AT01101782T ATE252052T1 (de) 2001-01-26 2001-01-26 Kettentrieb mit einem polygonalen kettenrad
EP01101782A EP1227056B1 (de) 2001-01-26 2001-01-26 Kettentrieb mit einem polygonalen Kettenrad
US10/037,794 US6905432B2 (en) 2001-01-26 2002-01-04 Chain drive arrangement
JP2002015778A JP2002276766A (ja) 2001-01-26 2002-01-24 多角形鎖車を駆動する歯車伝動装置のための牽引機構としてピボット鋼チェンまたは丸鋼チェンを有するチェン駆動装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP01101782A EP1227056B1 (de) 2001-01-26 2001-01-26 Kettentrieb mit einem polygonalen Kettenrad

Publications (2)

Publication Number Publication Date
EP1227056A1 EP1227056A1 (de) 2002-07-31
EP1227056B1 true EP1227056B1 (de) 2003-10-15

Family

ID=8176299

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01101782A Revoked EP1227056B1 (de) 2001-01-26 2001-01-26 Kettentrieb mit einem polygonalen Kettenrad

Country Status (6)

Country Link
US (1) US6905432B2 (ja)
EP (1) EP1227056B1 (ja)
JP (1) JP2002276766A (ja)
AT (1) ATE252052T1 (ja)
DE (1) DE50100794D1 (ja)
ES (1) ES2208471T3 (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009021266A1 (de) 2009-05-14 2010-12-09 Oser, Jörg, Em. Univ.-Prof. Dipl.-Ing. Dr. techn. Rundstahlkettentrieb

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7125356B2 (en) * 2001-11-06 2006-10-24 Borgwarner Inc. Tension-reducing random sprocket
CN1650199B (zh) 2002-04-26 2010-05-12 爱普生拓优科梦株式会社 叠层波长板及使用它的光学拾波器
NL1020535C2 (nl) * 2002-05-03 2003-11-04 Theodorus Henricus Johannes Carolina Korse Kettingoverbrenging.
CA2582737A1 (en) * 2004-10-06 2006-04-13 Schaeffler Kg Out-of-round rotation disc for a timing drive
KR101652225B1 (ko) 2007-09-28 2016-08-30 보르그워너 인코퍼레이티드 체인과 스프로킷 시스템의 다수의 장력 감소 스프로킷들
DK2131064T3 (da) 2008-06-04 2011-10-24 Vkr Holding As Tryk-træk kædeoperator med reduceret polygoneffekt
DE112011105280B4 (de) * 2011-05-23 2017-02-02 Otis Elevator Company Polygon-Kompensationskopplung für ketten- und zahnradgetriebene Systeme
CN102745618A (zh) * 2012-07-17 2012-10-24 费忠才 电动环链葫芦的链轮轴结构
US9163706B2 (en) * 2012-08-29 2015-10-20 Greg SEBLANTE, SR. Sprocket box for increasing the gas mileage of a vehicle with an automatic transmission
US8851455B2 (en) 2012-09-13 2014-10-07 Ventra Group, Inc. Reel assembly for chain hoist
US9850098B2 (en) * 2013-03-15 2017-12-26 Otis Elevator Company Polygon compensation coupling system for chain and sprocket driven systems
WO2015042936A1 (zh) * 2013-09-30 2015-04-02 高则行 手拉葫芦
WO2016203433A1 (en) * 2015-06-18 2016-12-22 Antonello Briosi Gearwheel for motion transmission systems onto cycles
US10907721B2 (en) * 2015-12-09 2021-02-02 Borgwarner Inc. Non-prevalent order random sprocket
JP6955157B2 (ja) * 2017-11-06 2021-10-27 株式会社椿本チエイン スプロケット及び伝動機構
CN109761011A (zh) * 2017-11-09 2019-05-17 中西金属工业株式会社 输送装置
CN108438754B (zh) * 2018-04-20 2019-12-10 苏州市相城区黄桥工业园经济发展有限公司 一种消除链式输送机中正多边形链条振动的方法
CN112377573B (zh) * 2020-12-03 2023-08-25 福建思普计量检测科技有限公司 一种简易齿轮传动结构
CN112377575A (zh) * 2020-12-03 2021-02-19 福建思普计量检测科技有限公司 一种多层齿轮传动机构
CN112555356A (zh) * 2020-12-03 2021-03-26 福建思普计量检测科技有限公司 一种齿轮加速传动单元
CN112377576A (zh) * 2020-12-03 2021-02-19 福建思普计量检测科技有限公司 一种齿轮加速传动结构
CN113550104A (zh) * 2021-07-20 2021-10-26 浙江邂美科技有限公司 模具式波浪状布料定型装置及其定型方法

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US836789A (en) * 1906-07-09 1906-11-27 Yale & Towne Mfg Co Portable electric hoist.
US3362685A (en) * 1965-05-18 1968-01-09 Paul R. Noye Chain hoist
GB1167907A (en) * 1966-11-01 1969-10-22 King Ltd Geo W Improvements in or relating to Electrically Operated Chain Hoists.
US3523463A (en) * 1969-02-19 1970-08-11 Us Army Sprocket wheel
DE2314462A1 (de) * 1973-03-23 1974-10-03 Multivac Hagenmueller Kg Vorschubgetriebe fuer verpackungsmaschinen
JPH0776078B2 (ja) * 1991-10-31 1995-08-16 象印チエンブロック株式会社 レバー形牽引機
FI106304B (fi) * 1999-03-26 2001-01-15 Kci Kone Cranes Int Oy Ketjunostin

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009021266A1 (de) 2009-05-14 2010-12-09 Oser, Jörg, Em. Univ.-Prof. Dipl.-Ing. Dr. techn. Rundstahlkettentrieb

Also Published As

Publication number Publication date
EP1227056A1 (de) 2002-07-31
US6905432B2 (en) 2005-06-14
DE50100794D1 (de) 2003-11-20
JP2002276766A (ja) 2002-09-25
US20020142873A1 (en) 2002-10-03
ES2208471T3 (es) 2004-06-16
ATE252052T1 (de) 2003-11-15

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