US20040166986A1 - Drive, particularly a planetary drive - Google Patents

Drive, particularly a planetary drive Download PDF

Info

Publication number
US20040166986A1
US20040166986A1 US10/475,408 US47540804A US2004166986A1 US 20040166986 A1 US20040166986 A1 US 20040166986A1 US 47540804 A US47540804 A US 47540804A US 2004166986 A1 US2004166986 A1 US 2004166986A1
Authority
US
United States
Prior art keywords
transmission
housing part
output shaft
face
drive
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.)
Abandoned
Application number
US10/475,408
Other languages
English (en)
Inventor
Thomas Bayer
Christof Old
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.)
Wittenstein SE
Original Assignee
Individual
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
Priority claimed from DE10125148A external-priority patent/DE10125148A1/de
Application filed by Individual filed Critical Individual
Assigned to WITTENSTEIN AG reassignment WITTENSTEIN AG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: OLD, CHRISTOF, BAYER, THOMAS
Publication of US20040166986A1 publication Critical patent/US20040166986A1/en
Priority to US11/302,851 priority Critical patent/US7121974B2/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/029—Gearboxes; Mounting gearing therein characterised by means for sealing the gearboxes, e.g. to improve airtightness
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0482—Gearings with gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0402—Cleaning of lubricants, e.g. filters or magnets
    • F16H57/0404—Lubricant filters

Definitions

  • the present invention relates to a transmission, in particular an epicyclic transmission, with a drive shaft and with at least one output shaft and with at least one output shaft which are connected via at least one element, the drive shaft and output shaft being mounted with respect to at least one housing part via bearings.
  • the elements may be positive gearwheels, nonpositive belts, ropes, chains or crank-type or slider-type mechanism elements.
  • the present invention will not be restricted to these.
  • one disadvantage of conventional epicyclic transmissions is that these are subject, in particular, to high wear, and, as a result, abrasion is distributed in the transmission and damages the surfaces of the elements.
  • the object on which the present invention is based is to provide a transmission, in particular an epicyclic transmission of the type initially mentioned, which eliminates the disadvantages mentioned and by means of which the useful life is to be increased in a highly cost-effective and efficient way. Furthermore, the manufacturing times and assembly costs of a transmission of this type are to be reduced. Moreover, a maintenance interval of the components, also, in particular, of the seals, is to be capable of being influenced.
  • At least one annular space for the reception of at least two sealing elements capable of being inserted one behind the other is formed between the at least one housing part and the drive and/or output shaft.
  • a transmission in particular an epicyclic transmission, is provided, in which an annular space between an inner surface area of housing parts and the shaft itself or a tension ring, said annular space preferably being of elongate design, is formed, in particular, near the bearings of the drive and/or output shaft.
  • the annular space has a depth which corresponds approximately to a width of at least two sealing elements, in particular of a shaft sealing ring.
  • the annular space may preferably receive two sealing elements, in particular two shaft sealing rings, arranged axially next to one another.
  • one of the two shaft sealing rings is inactive, that is to say its sealing lip does not bear against either the drive and/or output shaft or its tension ring. Only when the active tension ring undergoes a certain amount of wear, so that oil or lubricant emerges via leakages, is this detected by a corresponding sensor, so that the inactive shaft sealing ring is then activated and its sealing lip is brought to bear against the shafts or tension rings to be sealed off. This may take place automatically and be detected by a system. Under normal circumstances, during operation, the entire system in which a transmission of this type is integrated would have to be stopped immediately after detection of the leakage and the shaft sealing ring would have to be exchanged. This would incur high costs, which is undesirable.
  • a second inactive ring with an annular space specially provided in front of it, as a second securing ring.
  • a corresponding control not illustrated, knows when a sealing ring is spent due to wear, so that a second securing ring can be activated.
  • the damaged first sealing ring can then be exchanged, without complete production or the operation of the epicyclic transmissions having to be stopped temporarily for this purpose merely in order to change the one damaged sealing ring.
  • a plurality of permanent magnets preferably peripherally arranged radially are either arranged on the end face in the last housing part or may also be arranged, near the toothing, on an inner surface area of the middle housing part.
  • These permanent magnets serve permanently, and irrespective of the position of the epicyclic transmission, for immediately picking up abrasion or ferritic material caused by abrasion during operation, without this running through the individual elements during operation. Owing to the permanent magnets peripherally arranged radially, the epicyclic transmission is independent of its installation position.
  • the drive shaft in particular its rotary disk-type carrier, at least one permanent magnet which is inserted into the latter in its end face centrically to the mid-axis, so that a trough as a chip collecting space for chip abrasion, ferritic material, etc. is formed between an end face of the rotary disk-type carrier and the permanent magnet.
  • a further advantage in the present invention is that, owing to the housing designed in three parts, a toothing for the planet wheels can be produced within the middle housing part directly from the latter, for example by broaching.
  • the middle housing part can be produced from a material especially suitable for the toothing. This can then subsequently be connected to the first housing part.
  • the second housing part is welded to the first housing part on the end face firmly and with an exact fit.
  • FIG. 1 shows a perspective top view of a transmission, in particular epicyclic transmission, according to the invention
  • FIG. 2 shows a partially cut away perspective view of the epicyclic transmission according to FIG. 1;
  • FIG. 3 shows a diagrammatically illustrated longitudinal section through the epicyclic transmission according to FIG. 1;
  • FIG. 4 shows a longitudinal section through a further exemplary embodiment of a further epicyclic transmission according to FIG. 1;
  • FIG. 5 shows a part longitudinal section, illustrated enlarged, through the transmission according to FIG. 1 in the region of a first housing part
  • FIG. 6 shows a part, illustrated enlarged, of a part longitudinal section through the first housing part as a further exemplary embodiment
  • FIG. 7 shows a top view of a third housing part with a plurality of end-face blind holes for the reception of magnets.
  • a transmission R 1 according to the invention has a housing 1 which is preferably subdivided into three housing parts 2 . 1 , 2 . 2 , 2 . 3 .
  • the first housing part 2 . 1 is provided with a flange 3 for fixing the transmission R 1 to any desired drive element or the like.
  • a drive shaft 5 projects into the housing part 2 . 3 (see also FIG. 2) and is mounted rotatably with respect to the housing part 2 . 3 via at least one bearing 6 .
  • the drive shaft 5 is provided with a step 7 , an annular space 9 being formed between the step 7 and an inner surface area 8 .
  • the drive shaft 5 has seated on it a spur wheel 10 which preferably meshes with three planet wheels 11 mounted on bolt elements 12 via needle bearings 13 .
  • the bolt elements 12 are pressed into a rotary disk-type carrier 14 of an output shaft 15 .
  • a toothing 16 is peripherally arranged radially in the housing part 2 . 2 on the inside.
  • the housing part 2 . 2 is preferably designed as a sleeve and has the toothing 16 on the inside.
  • the planet wheels 11 mesh with the toothing 16 of the housing part 2 . 2 .
  • the output shaft 15 is mounted rotatably within the housing part 2 . 1 via two bearings 6 arranged next to one another and is fixed with respect to the housing part 2 . 2 via a tension ring 17 .
  • the housing part 2 . 3 is seated releasably on the housing part 2 . 2 on the end face via steps and flanges which are not numbered specifically here.
  • the housing part 2 . 3 can be connected directly to any desired adapter plate 4 .
  • the adapter plate 4 overlaps at least the outer ring of the bearing 6 , so that the bearing 6 is held in the housing part 2 . 3 .
  • the complete epicyclic transmission in particular the housing part 2 . 3 , can be fixed releasably and accurately to the adapter plate 4 .
  • a further step 19 is formed, adjacently to the bearings 6 of the housing part 2 . 1 , in the end-face region, a further annular space 9 being formed between the output shaft 15 and the step 19 or the inner surface area 8 of the housing part 2 . 1 .
  • the annular space 9 has a depth T which, in a preferred exemplary embodiment, corresponds to double the width B of a sealing element 20 . 1 .
  • An essential advantage in the present invention is that, as is not illustrated here, two sealing elements 20 . 1 can be inserted one into the other, in particular one behind the other, into the annular space 9 over its depth T.
  • the sealing element 20 . 1 is the sealing element closing off on the end face, while a second sealing element 20 . 2 (see FIG. 5) can be inserted into the annular space 9 .
  • the sealing element 20 . 1 or 20 . 2 may be used as an additional safety sealing element, which is inactive, in the annular space 9 . If one of the two sealing elements 20 . 1 or 20 . 2 fails or if one of the two sealing elements 20 . 1 or 20 .
  • the sealing elements 20 . 1 , 20 . 2 can be held or anchored firmly in the annular space 9 , there are provided on the inner surface area 8 of the housing parts 2 . 1 and 2 . 3 (see also FIGS. 3 and 6) preferably peripheral recesses 21 or elevations 22 , into which the material of the sealing element 20 . 1 , 20 . 2 engages, or the elevation 22 is pressed into the material of the sealing element 20 . 1 , 20 . 2 .
  • an edge 23 is formed, which prevents the sealing element 20 . 1 , 20 . 2 from slipping out of the annular space 9 .
  • the bearing 6 is arranged, directed outward, on the end face between the drive shaft 5 and the housing part 2 . 3 , since said bearing often has to be exchanged.
  • the annular space 9 for receiving the sealing elements 20 . 1 , 20 . 2 is formed between the step 7 of the drive shaft 5 and the inner surface area 8 of the housing part 2 . 3 .
  • a depth T of the surface area 8 preferably corresponds to double the width B of a sealing element 20 . 1 .
  • the end face 24 having the permanent magnet 26 provided is oriented near to the planet wheels 11 or toward the toothing 16 .
  • the end face 24 having the permanent magnet 26 provided is oriented near to the planet wheels 11 or toward the toothing 16 .
  • the end face 24 having the permanent magnet 26 is oriented near to the planet wheels 11 or toward the toothing 16 .
  • worn ferritic material can thereby be separated off and picked up in a highly effective way. If, for example, the bearing 6 is exchanged by the housing part 2 . 3 being unflanged from the housing part 2 . 2 , the troughs 27 can be cleaned in a highly accessible way.
  • a permanent magnet 26 is likewise inserted, set back, into one end face 30 of the output shaft 15 , in particular the rotary disk-type carrier 14 of the latter, so that a trough 27 for picking up chips and abrasion is formed between the end face 30 and the permanent magnet 26 .
  • the permanent magnet 26 is inserted into the rotary disk-type carrier 14 on the end face so as to be oriented centrically to the mid-axis M.
  • the bolt element 12 may be produced from solid round material.
  • a vent orifice 29 is then provided at the end of a reception orifice 28 in the rotary disk-type carrier 14 and serves for making it easier to press the bolt elements 12 into the reception orifice 28 .
  • the vent orifice 29 may be dispensed with. Then, as is likewise illustrated by dashes, a plurality of radial bores 30 are preferably provided in the bolt element 12 and serve for additional lubrication of the needle bearing 13 for the planet wheels 11 .
  • the exemplary embodiment according to FIG. 4 shows a transmission R 2 which corresponds essentially to that according to FIG. 3.
  • two possibilities for arranging the sealing elements 20 . 1 , 20 . 1 are indicated.
  • Either the sealing elements 20 . 1 , 20 . 2 are inserted into the annular space 9 in the end-face region of the housing part 2 . 3 , as is illustrated in longitudinal section above a mid-axis M, or they are arranged as illustrated below the mid-axis M, this corresponding to the arrangement in the exemplary embodiment according to FIG. 3.
  • the annular space 9 for receiving the two sealing elements 20 . 1 , 20 . 2 is formed within the bearing 6 . It is thereby likewise possible to influence the use of different bearings 6 so that they run in lubricant or are self-lubricating.
  • the output shaft 15 is mounted via two bearings 6 spaced apart from one another.
  • a ring X 1 is seated between the bearings 6 of the output shaft 15 and spaces the bearings 6 axially apart from one another.
  • a play of the output shaft 15 can be set via a shaft nut designed as a tension ring 17 .
  • one of the bearings 6 may come to bear on the end face against the rotary disk-type carrier 14 , if appropriate so as to be spaced apart via an additional spacer ring. This is likewise to come within the scope of the present invention.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)
  • Retarders (AREA)
  • Sealing Devices (AREA)
US10/475,408 2001-04-23 2002-02-08 Drive, particularly a planetary drive Abandoned US20040166986A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US11/302,851 US7121974B2 (en) 2001-04-23 2005-12-13 Transmission, in particular epicyclic transmission

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10119998.8 2001-04-23
DE10119998 2001-04-23
DE10125148.3 2001-05-22
DE10125148A DE10125148A1 (de) 2001-04-23 2001-05-22 Getriebe, insbesondere Planetengetriebe
PCT/EP2002/001318 WO2002086351A2 (de) 2001-04-23 2002-02-08 Getriebe, insbesondere planetengetriebe

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US11/302,851 Division US7121974B2 (en) 2001-04-23 2005-12-13 Transmission, in particular epicyclic transmission

Publications (1)

Publication Number Publication Date
US20040166986A1 true US20040166986A1 (en) 2004-08-26

Family

ID=26009155

Family Applications (2)

Application Number Title Priority Date Filing Date
US10/475,408 Abandoned US20040166986A1 (en) 2001-04-23 2002-02-08 Drive, particularly a planetary drive
US11/302,851 Expired - Lifetime US7121974B2 (en) 2001-04-23 2005-12-13 Transmission, in particular epicyclic transmission

Family Applications After (1)

Application Number Title Priority Date Filing Date
US11/302,851 Expired - Lifetime US7121974B2 (en) 2001-04-23 2005-12-13 Transmission, in particular epicyclic transmission

Country Status (6)

Country Link
US (2) US20040166986A1 (ja)
EP (1) EP1381793B1 (ja)
JP (1) JP2004526918A (ja)
DE (1) DE50207234D1 (ja)
ES (2) ES2266964T3 (ja)
WO (1) WO2002086351A2 (ja)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050085324A1 (en) * 2001-12-11 2005-04-21 Michael Christ Planetary gear, gear motor and series of gear motors
USD777815S1 (en) * 2014-06-30 2017-01-31 Wittenstein Se Gearbox
USD797173S1 (en) * 2015-08-24 2017-09-12 Wittenstein Se Gearing for electric motors
USD800196S1 (en) * 2015-06-10 2017-10-17 Sew-Eurodrive Gmbh & Co. Kg Transmission
USD808451S1 (en) * 2016-09-27 2018-01-23 Wittenstein Se Gearing
USD817373S1 (en) * 2016-10-14 2018-05-08 Sew-Eurodrive Gmbh & Co Kg Gearbox
USD855669S1 (en) * 2017-10-02 2019-08-06 Wittenstein Se Gearbox
USD873318S1 (en) * 2018-02-27 2020-01-21 Flender Gmbh Gear
USD931350S1 (en) * 2018-10-12 2021-09-21 Flender Gmbh Gear with casing
USD1029900S1 (en) * 2021-06-01 2024-06-04 Nabtesco Corporation Speed reducer

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DE10306728B4 (de) * 2003-02-17 2013-05-16 Sew-Eurodrive Gmbh & Co. Kg Welle mit Wellendichtring, Getriebe mit Welle mit Wellendichtring und Verfahren zur Temperatursteuerung und/oder -regelung einer Komponente eines Wellendichtrings mit Welle
DE10340802B4 (de) 2003-09-02 2020-08-06 Sew-Eurodrive Gmbh & Co Kg Vorrichtung mit Abtriebswelle und Wellendichtring
JP4482388B2 (ja) * 2004-07-21 2010-06-16 アロカ株式会社 超音波探触子
DE102007036554B4 (de) * 2007-07-25 2009-06-25 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Deckel-Lager-Anordnung und Verfahren zum Montieren einer Aktuatorwelle
US7717820B2 (en) * 2007-09-12 2010-05-18 Sheng Bor Wang Planet gear speed reducer
TWI395894B (zh) * 2009-12-22 2013-05-11 Apex Dynamics Inc 行星減速機
US20110172053A1 (en) * 2010-01-13 2011-07-14 Apex Dynamics, Inc. Planet-gear speed reducer
CN102068279B (zh) * 2011-01-14 2012-11-07 深圳市开立科技有限公司 一种超声扫描探头
DE102015105609A1 (de) * 2015-04-13 2016-10-13 Wittenstein Ag Sensor, Antriebsbauteil mit Sensor, Antrieb mit Antriebsbauteil sowie Auswertungsverfahren
US10408328B1 (en) * 2016-08-17 2019-09-10 Premium Oilfield Technologies, LLC Epicyclic washpipe swivel cartridge and method
DE102016012501C5 (de) * 2016-10-19 2022-08-04 Sew-Eurodrive Gmbh & Co Kg Getriebe, aufweisend eine Welle, ein Gehäuseteil und ein Adaptergehäuse
DE102020126114A1 (de) * 2020-10-06 2022-04-07 Wittenstein Se Koaxialgetriebe
CN112096843B (zh) * 2020-10-20 2024-09-10 贵州群建精密机械有限公司 一种立式传动机构用同轴式自润滑装置
CN113605234B (zh) * 2021-08-31 2022-12-06 江苏中矿大正表面工程技术有限公司 一种用于桥梁斜拉索的防火外层隔离体系

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US3686967A (en) * 1970-10-06 1972-08-29 Verson Mfg Co Plural speed transmission system
US4491037A (en) * 1983-02-10 1985-01-01 General Motors Corporation Seal arrangement for disengageable reduction drive unit
US5879259A (en) * 1996-10-02 1999-03-09 Tochigi Fuji Sangyo Kabushiki Kaisha Transmission for an auxiliary device
US6152454A (en) * 1995-12-21 2000-11-28 Eurocopter Sealing device for rotating shaft
US6705964B2 (en) * 2001-12-11 2004-03-16 Jatco Ltd Power transmission system
US6824495B1 (en) * 1999-11-25 2004-11-30 Zf Friedrichshafen Ag Planetary gear for mounting on an electromotor

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US3631741A (en) * 1970-08-07 1972-01-04 Borg Warner Transmission
US3686967A (en) * 1970-10-06 1972-08-29 Verson Mfg Co Plural speed transmission system
US4491037A (en) * 1983-02-10 1985-01-01 General Motors Corporation Seal arrangement for disengageable reduction drive unit
US6152454A (en) * 1995-12-21 2000-11-28 Eurocopter Sealing device for rotating shaft
US5879259A (en) * 1996-10-02 1999-03-09 Tochigi Fuji Sangyo Kabushiki Kaisha Transmission for an auxiliary device
US6824495B1 (en) * 1999-11-25 2004-11-30 Zf Friedrichshafen Ag Planetary gear for mounting on an electromotor
US6705964B2 (en) * 2001-12-11 2004-03-16 Jatco Ltd Power transmission system

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7182709B2 (en) * 2001-12-11 2007-02-27 Sew-Eurodrive Gmbh & Co. Kg Planetary gear, gear motor and series of gear motors
US20050085324A1 (en) * 2001-12-11 2005-04-21 Michael Christ Planetary gear, gear motor and series of gear motors
USD798928S1 (en) * 2014-06-30 2017-10-03 Wittenstein Se Gearbox
USD777815S1 (en) * 2014-06-30 2017-01-31 Wittenstein Se Gearbox
USD795934S1 (en) * 2014-06-30 2017-08-29 Wittenstein Se Gearbox
USD800196S1 (en) * 2015-06-10 2017-10-17 Sew-Eurodrive Gmbh & Co. Kg Transmission
USD797173S1 (en) * 2015-08-24 2017-09-12 Wittenstein Se Gearing for electric motors
USD809039S1 (en) * 2015-08-24 2018-01-30 Wittenstein Se Gearings for electric motors
USD821470S1 (en) * 2015-08-24 2018-06-26 Wittenstein Se Gearing for electric motor
USD808451S1 (en) * 2016-09-27 2018-01-23 Wittenstein Se Gearing
USD817373S1 (en) * 2016-10-14 2018-05-08 Sew-Eurodrive Gmbh & Co Kg Gearbox
USD855669S1 (en) * 2017-10-02 2019-08-06 Wittenstein Se Gearbox
USD873318S1 (en) * 2018-02-27 2020-01-21 Flender Gmbh Gear
USD931350S1 (en) * 2018-10-12 2021-09-21 Flender Gmbh Gear with casing
USD1029900S1 (en) * 2021-06-01 2024-06-04 Nabtesco Corporation Speed reducer

Also Published As

Publication number Publication date
DE50207234D1 (de) 2006-07-27
EP1381793A2 (de) 2004-01-21
US20060094563A1 (en) 2006-05-04
ES2266964T3 (es) 2007-03-01
EP1381793B1 (de) 2005-04-27
WO2002086351A3 (de) 2002-12-27
US7121974B2 (en) 2006-10-17
ES2240724T3 (es) 2005-10-16
JP2004526918A (ja) 2004-09-02
WO2002086351A2 (de) 2002-10-31

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