WO2007024176A1 - A method and an arrangement for avoiding low load problems in rolling bearings - Google Patents

A method and an arrangement for avoiding low load problems in rolling bearings Download PDF

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Publication number
WO2007024176A1
WO2007024176A1 PCT/SE2006/000962 SE2006000962W WO2007024176A1 WO 2007024176 A1 WO2007024176 A1 WO 2007024176A1 SE 2006000962 W SE2006000962 W SE 2006000962W WO 2007024176 A1 WO2007024176 A1 WO 2007024176A1
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WO
WIPO (PCT)
Prior art keywords
bearing
load
additional
bearings
rolling
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.)
Ceased
Application number
PCT/SE2006/000962
Other languages
French (fr)
Inventor
Hans Wendeberg
Håkan Leander
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SKF AB
Original Assignee
SKF AB
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Filing date
Publication date
Application filed by SKF AB filed Critical SKF AB
Publication of WO2007024176A1 publication Critical patent/WO2007024176A1/en
Anticipated expiration legal-status Critical
Ceased 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F03D80/70—Bearing or lubricating arrangements
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F16C19/522—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to load on the bearing, e.g. bearings with load sensors or means to protect the bearing against overload
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C39/00—Relieving load on bearings
    • F16C39/02—Relieving load on bearings using mechanical means
    • 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
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/50—Bearings
    • F05B2240/54—Radial bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/40—Transmission of power
    • F05B2260/403—Transmission of power through the shape of the drive components
    • F05B2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
    • F16C19/26—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with a single row of rollers
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • Rolling bearings require a minimum load for operating satisfactorily. This minimum load is dependent of bearing size, bearing type, lubricant viscosity, retainer design, rotational speed, etcetera. However it is possible to establish this minimum load with a sufficient accuracy with use of simple calculations. When bearings are used at a load below this minimum load, there is risk that they are affected by low load problems, which result in more or less serious sliding or smearing damages, between rolling bodies and race tracks.
  • An alternative manner of reducing the risk for low load problems for bearings without angular contact is to coat the surfaces of rolling bodies and/or race tracks with material having a lower tendency of smearing than steel.
  • the drawback with coatings is that the costs increase with improved functionality and extended service life for the coating, and today the service life over long periods is not known for the best coatings.
  • the purpose of the present application is to propose a method and an arrangement for avoiding the risk for low load problems for bearings operating without angular contact, and this has been achieved with the method defined in the accompanying claim 1, and with an arrangement defined in the accompanying claim 4.
  • the single drawing figure shows schematically and as an example of an appropriate application a section of a gear box equipped with an arrangement according to the invention.
  • Fig. 1 shows in a view from above a casing 1 for a gear box with a driven input shaft 2, which is supported in a double-row spherical roller bearing 3 arranged in a seat in one wall of the gear box casing and in a toroidal roller bearing 4 arranged in a seat in the opposed wall of the casing, and having gear wheel 5 mounted to rotate with the shaft 2.
  • a second shaft 6 Aligned with the input shaft 2 is a second shaft 6.
  • this second shaft 6 is supported in a double-row spherical roller bearing 7 and a toroidal roller bearing 8, and this second, or intermediate shaft 6 has two gear wheels 9, 10 fixedly connected thereto.
  • a first one 9 of these two gear wheels 9, 10, is positioned to be in engagement with the gear wheel 5 on the input shaft 2, and this gear wheel 9 on the intermediate shaft has a much smaller diameter than the gear wheel on the input shaft, whereby the intermediate shaft 6 will rotate at a rotational speed higher than that of the input shaft.
  • the second gear wheel 10, which is also fixedly connected to the intermediate shaft 6, is positioned axially displaced from the first gear wheel 9, and it has a much larger diameter than the first gear wheel 9 on the intermediate shaft 6.
  • This second gear wheel 10 on the intermediate shaft 6 is in engagement with a single gear wheel 11 fixedly arranged on an output shaft 12, which is aligned with the input shaft 2 and the intermediate shaft 6 and supported in a double-row spherical roller bearing 13 and a toroidal roller bearing 14.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Rolling Contact Bearings (AREA)
  • Support Of The Bearing (AREA)
  • General Details Of Gearings (AREA)

Abstract

The present invention refers to a method and an arrangement for avoiding low load problems in rolling bearing installations, incorporating the steps of: determining by calculations the positions of rolling bearings (13, 14) having the biggest risk for being subjected to loads below recommended minimum load in an installation (1), which has a number of bearing positions (3, 4, 7, 8, 13, 14); determining by calculations the positions and direction of an additional load (F) required for giving such rolling bearings (13, 14) the minimum load required in accordance with recommendations; providing a component (12) associated with such rolling bearings (13, 14) with an additional rolling bearing (15), and applying the minimum additional load (F) required to the additional bearing (15).

Description

A METHOD AND AN ARRANGEMENT FOR AVOIDING LOW LOAD PROBLEMS IN ROLLING BEARINGS
Rolling bearings require a minimum load for operating satisfactorily. This minimum load is dependent of bearing size, bearing type, lubricant viscosity, retainer design, rotational speed, etcetera. However it is possible to establish this minimum load with a sufficient accuracy with use of simple calculations. When bearings are used at a load below this minimum load, there is risk that they are affected by low load problems, which result in more or less serious sliding or smearing damages, between rolling bodies and race tracks.
In machine applications where the bearing load is dependent of the gravitation only to a small part and the load instead is mainly generated by the machine itself, such as for instance in gear boxes, and where the machine is used within a varying load range, there is a big risk that some bearing in some service situation, will work at a load which is lower than the recommended minimum load. This is particularly pronounced at shafts operating at high rotational speeds in machines where the load not only varies but also can change direction, for instance as speed increasing gear boxes in wind power turbines where driving as well as retarding moments vary.
Low load problems in rolling bearings with angular contact, such as axially loaded deep groove ball bearings, angular contact ball bearings, taper roller bearings, etcetera, can be eliminated via axial preload, which then affects all or almost all rolling bodies, but bearings having no angular contact, i.e. typical radial bearings such as cylindrical roller bearings or toroidal roller bearings, have not this possibility. A radial preload achieved by eliminating the internal clearance would solve the problem, but it requires a very high precision in the adjoining components and a controlled lubrication for avoiding that the preload will become self-generating as a result of the fact that the expansion of the shaft and the inner bearing ring is faster than that of the outer bearing ring and the housing. An alternative manner of reducing the risk for low load problems for bearings without angular contact is to coat the surfaces of rolling bodies and/or race tracks with material having a lower tendency of smearing than steel. The drawback with coatings is that the costs increase with improved functionality and extended service life for the coating, and today the service life over long periods is not known for the best coatings.
The purpose of the present application is to propose a method and an arrangement for avoiding the risk for low load problems for bearings operating without angular contact, and this has been achieved with the method defined in the accompanying claim 1, and with an arrangement defined in the accompanying claim 4.
Hereinafter the invention will be described with reference to an explanatory embodiment shown as a non-limiting example in the accompanying drawing.
The single drawing figure shows schematically and as an example of an appropriate application a section of a gear box equipped with an arrangement according to the invention.
Fig. 1 shows in a view from above a casing 1 for a gear box with a driven input shaft 2, which is supported in a double-row spherical roller bearing 3 arranged in a seat in one wall of the gear box casing and in a toroidal roller bearing 4 arranged in a seat in the opposed wall of the casing, and having gear wheel 5 mounted to rotate with the shaft 2. Aligned with the input shaft 2 is a second shaft 6. Also this second shaft 6 is supported in a double-row spherical roller bearing 7 and a toroidal roller bearing 8, and this second, or intermediate shaft 6 has two gear wheels 9, 10 fixedly connected thereto. A first one 9 of these two gear wheels 9, 10, is positioned to be in engagement with the gear wheel 5 on the input shaft 2, and this gear wheel 9 on the intermediate shaft has a much smaller diameter than the gear wheel on the input shaft, whereby the intermediate shaft 6 will rotate at a rotational speed higher than that of the input shaft. The second gear wheel 10, which is also fixedly connected to the intermediate shaft 6, is positioned axially displaced from the first gear wheel 9, and it has a much larger diameter than the first gear wheel 9 on the intermediate shaft 6. This second gear wheel 10 on the intermediate shaft 6 is in engagement with a single gear wheel 11 fixedly arranged on an output shaft 12, which is aligned with the input shaft 2 and the intermediate shaft 6 and supported in a double-row spherical roller bearing 13 and a toroidal roller bearing 14.
This arrangement results in that the rotational speed of the input shaft 2 is changed up twice. In such a gear box the bearings supporting the output shaft 12 are generally the bearings having the largest risk for low load problems at normal operating conditions, as they have the highest rotational speed at the same time as the load from the gear wheels is the lowest. Every change of the input speed of the input shaft 2 will also give the output shaft 12 an acceleration (or retardation) which is multiplied in dependency of the gear ratio of the gear box, and this will further increase the risk for slipping between rolling bodies and the race tracks. For solving this problem, it is now proposed to give the output shaft 12 the minimum extra load needed for avoiding the low load problems, by providing an extra bearing 15, which is subjected to a load F. In the typical case described such a bearing could preferably be a deep groove ball bearing, as shown. Such a bearing should probably result in the least expensive installation when compared with the carrying capacity.
For any specific given machine, it is possible to determine via calculations at which positions there are biggest risks that the bearings shall be affected by too low loads, and also which those loads are. Those calculations can be used as basis for determining the position where extra bearings shall be positioned and the direction and size of the loads they shall be subjected to, for eliminating or at least reducing the risk for low load problems.
The invention is not limited to the embodiment illustrated in the drawing and described in connection thereto, but the method and arrangement defined in the accompanying claims can be applied wherever bearings are at risk for being subjected to low load problems such as described.

Claims

1. A method for avoiding low load problems in rolling bearing installations, incorporating the steps of: determining by calculations the positions of rolling bearings (13, 14) having the biggest risk for being subjected to loads below recommended minimum load in an installation (1), which has a number of bearing positions (3, 4, 7, 8, 13, 14); determining by calculations the positions and direction of an additional load (F) required for giving such rolling bearings (13, 14) the minimum load required in accordance with recommendations; providing a component (12) associated with such rolling bearings (13, 14) with an additional rolling bearing (15), and applying the minimum additional load (F) required to the additional bearing (15).
2. A method as claimed in claim 1, characterized therein, that the component associated with the bearings (13, 14) is a shaft (12) supported in the said bearings (13, 14) and that the additional bearing (15) is fitted to said shaft
(12).
3. A method as claimed in claim 1 or 2, characterized therein, that a deep groove ball bearing is used as the additional bearing (15).
4. An arrangement for performing the method according to claim 1 for avoiding low load problems in rolling bearing installations, characterized therein, that in the installation, a machine member (12) supported in bearings (13, 14), which are considered during operation to be at risk of being subjected to loads lower than the recommended load, is equipped with an additional bearing (15), arranged to be subjected to a load (F), ascertaining that the bearings (13, 14) risking to have low load, and also the additional bearing (15) are subjected to a load at least corresponding to the lowest recommended load.
5. An arrangement as claimed in claim 4, characterized therein, that the additional bearing is a deep groove ball bearing (15).
6. An arrangement as claimed in anyone of claims 4 or 5, characterized therein, that at least one bearing (14) which is at risk of being subjected to loads lower than the recommended load, is a rolling bearing without angular contact, such as a cylindrical roller bearing or a toroidal roller bearing.
7. An arrangement as claimed in anyone of claims 4 to 6, characterized therein, that the machine member (12) is an output shaft in a gear box, particularly for a wind power plant.
PCT/SE2006/000962 2005-08-26 2006-08-23 A method and an arrangement for avoiding low load problems in rolling bearings Ceased WO2007024176A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE0501884-1 2005-08-26
SE0501884A SE528915C2 (en) 2005-08-26 2005-08-26 A method and arrangement for avoiding low load problems in rolling bearings

Publications (1)

Publication Number Publication Date
WO2007024176A1 true WO2007024176A1 (en) 2007-03-01

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PCT/SE2006/000962 Ceased WO2007024176A1 (en) 2005-08-26 2006-08-23 A method and an arrangement for avoiding low load problems in rolling bearings

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WO (1) WO2007024176A1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008024049C5 (en) * 2008-05-16 2016-06-16 Eickhoff Antriebstechnik Gmbh Bearing arrangement with a biasing device
DE102015207693A1 (en) * 2015-04-27 2016-10-27 Zf Friedrichshafen Ag Exchange and fixation of a warehouse
EP3327313A1 (en) * 2016-11-29 2018-05-30 Toyota Jidosha Kabushiki Kaisha Power transmission mechanism

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10325946B3 (en) * 2003-06-07 2004-09-16 Voith Paper Patent Gmbh Self-aligning roller bearing, for a calender roller, is tested under a minimum load for a given time span to check for damage before mounting at the roller

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10325946B3 (en) * 2003-06-07 2004-09-16 Voith Paper Patent Gmbh Self-aligning roller bearing, for a calender roller, is tested under a minimum load for a given time span to check for damage before mounting at the roller

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008024049C5 (en) * 2008-05-16 2016-06-16 Eickhoff Antriebstechnik Gmbh Bearing arrangement with a biasing device
DE102015207693A1 (en) * 2015-04-27 2016-10-27 Zf Friedrichshafen Ag Exchange and fixation of a warehouse
EP3327313A1 (en) * 2016-11-29 2018-05-30 Toyota Jidosha Kabushiki Kaisha Power transmission mechanism
CN108119610A (en) * 2016-11-29 2018-06-05 丰田自动车株式会社 Transmission mechanism
TWI666139B (en) * 2016-11-29 2019-07-21 Toyota Jidosha Kabushiki Kaisha Power transmission mechanism
US10683910B2 (en) 2016-11-29 2020-06-16 Toyota Jidosha Kabushiki Kaisha Power transmission mechanism
CN108119610B (en) * 2016-11-29 2021-04-02 丰田自动车株式会社 Transmission mechanism

Also Published As

Publication number Publication date
SE0501884L (en) 2007-02-27
SE528915C2 (en) 2007-03-13

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