WO2015084636A1 - Réglage de paliers par analyse modale - Google Patents

Réglage de paliers par analyse modale Download PDF

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Publication number
WO2015084636A1
WO2015084636A1 PCT/US2014/067308 US2014067308W WO2015084636A1 WO 2015084636 A1 WO2015084636 A1 WO 2015084636A1 US 2014067308 W US2014067308 W US 2014067308W WO 2015084636 A1 WO2015084636 A1 WO 2015084636A1
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WO
WIPO (PCT)
Prior art keywords
bearing
natural frequency
actual
transmission assembly
modeled
Prior art date
Application number
PCT/US2014/067308
Other languages
English (en)
Inventor
Desheng Li
Original Assignee
The Timken Company
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 The Timken Company filed Critical The Timken Company
Publication of WO2015084636A1 publication Critical patent/WO2015084636A1/fr

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Classifications

    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M13/00—Testing of machine parts
    • G01M13/04—Bearings
    • G01M13/045—Acoustic or vibration analysis

Definitions

  • the present invention relates to setting bearing preload or clearance in a transmission assembly.
  • a correct setting (e.g., bearing preload or clearance) of bearings is important for bearing fife performance and proper functioning of power transmissions, including gearboxes.
  • setting methods based on rolling torque or deflection are widely used.
  • the consistency of these methods relies heavily on the experience and skill of the workers who perform the setting.
  • a new setting method that can improve the setting consistency and accuracy is needed in the art.
  • the invention provides a method for setting bearing preioad or clearance for a bearing mounted in a transmission assembly.
  • the method includes determining a modeled natural frequency of a vibration model of the bearing and
  • transmission assembly developed using a pre-calculated stiffness of the bearing, performing a modal analysis on an assembled bearing and transmission assembly to determine an actual natural frequency of the assembled bearing and transmission assembly, comparing the actual natural frequency of the assembled bearing and transmission assembly to the modeled natural frequency; and adjusting an actual preload or clearance of the bearing based on the comparison of the actuai natural frequency and the modeled natural frequency.
  • the invention provides a method for setting bearing preload or clearance for a bearing mounted in a transmission assembly.
  • the method includes calculating a stiffness of the bearing based on a design preload or clearance, developing a vibration model of the bearing and transmission assembly using the caiculated stiffness of the bearing, determining a modeled natural frequency of the vibration model, assembling the bearing into the transmission assembly, performing a modal analysis on the assembled bearing and transmission assembly to determine an actual natural frequency of the assembled bearing and transmission assembly, and comparing the actual natural frequency of the assembled bearing and transmission assembly to the modeled natural frequency.
  • the invention provides a method for setting bearing preload or clearance for a bearing mounted in a transmission assembly.
  • the method includes determining a modeled natural frequency of a vibration model of the bearing and
  • the transmission assembly developed using a computer modeling software with finite element analysis capabilities and using a pre-calcuiated stiffness of the bearing.
  • the pre-caieulated stiffness of the bearing is determined using computational software, and the modeled natural frequency of the vibration model is determined by the computer modeling software.
  • the method aiso includes performing a modal analysis with a modal analysis system on an assembled bearing and transmission assembly to determine an actual natural frequency of the assembled bearing and transmission assembly.
  • the modal analysis system includes a vibration sensor, a vibration excitation instrument, and a signal analyzer.
  • the method includes comparing the actual natural frequency of the assembled bearing and transmission assembly to the modeled natural frequency, and adjusting an actual preload or clearance of the bearing based on the comparison of the actual natural frequency and the modeled natural frequency, if the actual natural frequency is les than the modeled natural frequency, the actual preload of the bearing is increased by reducing an internal clearance of bearing components, if the actual natural frequency is greater than the modeled natural frequency, the actual preload of the bearing is decreased by increasing an internal clearance of bearing components.
  • Fig. 1 is a schematic drawing illustrating a gearbox and modal analysis kit in accordance with an embodiment of the invention.
  • Fig. 2 is a flowchart illustrating the steps for setting bearing preioad or clearance using modal analysis.
  • the invention presents a new setting method for bearings in gearboxes or other transmission assemblies.
  • the method uses modeling and modal analysis techniques.
  • the stiffness of bearings varies depending on a set preload or clearance of the bearing. Searings can be set with varying levels of clearance between bearing elements to vary the internal stress or preload of the bearing before the bearings receive an external load. A higher preioad on the bearing results i increased bearing stiffness, while a lower preioad will result in decreased bearing stiffness.
  • Bearing stiffness influences the natural frequency of the gearbox. It is possible to more accurately and consistently set and adjust the bearing preload or clearance through the comparison of modeled and experimentally determined natural frequencies of the gearbox assembly.
  • Fig. I illustrates a transmission assembly or gearbox 10 including a bearing 1 .
  • the bearing 14 is iliustraied as a tapered rolling bearing, but may also be one of various other types of bearings.
  • the bearing 14 receives a first shaft, or input shaft 16 in the bearing bore, which may be driven by various means.
  • the bearing 14 includes an inner ring or race 18a and an outer ring or race ⁇ 8b.
  • the outer ring i 8b is coupled to the gearbox 10 so that it does not rotate with the inner ring i 8a and the input shaft 16.
  • the rotational movement between the inner ring 1 8a and the outer ring 1 8b is facilitated by a low friction interface using various techniques such as, but not limited to, rolling elements.
  • the gearbox 10 further includes a second shaft or output shaft 20 and a plurality of gears (not shown) located within a housing 22.
  • the plurality of gears engages with each other to effectively transmit the rotational movement and torque from the input shaft 16 to the output shaft 20.
  • the plurality of gears may be of various sizes and types to provide a desired gear ratio for a specific application.
  • a modal analysis system 24 including a vibration sensor 26.
  • the vibration sensor 26 is attached to a computer or signal analyzer 30, for example, through an electrical cord 32.
  • the modal analysis system 24 also includes a vibration excitation instrument 38, which may be an impulse or Impact hammer or any other device (e.g., a shaker, modal exciter, etc.) capable of exciting the gearbox 1 0 to vibrate ai its natural frequency.
  • the vibration excitation instrument 38 may be attached to the signal analyzer 30, for example, by an electrical cord 34,
  • Fig. 2 illustrates the process a user would follow to use modeling and modal analysis to adjust the setting of the bearing 1 when it is assembled in the gearbox 10.
  • the user first calculates a bearing stiffness matrix of the bearing 14 using a designed bearing setting (e.g., preload or clearance). This calculation may be done using traditional analysis using known equations or with available computational software.
  • the user develops a vibration model of the gearbox 10 and the installed bearing 14 using the stiffness matrix previously calculated.
  • the vibration model may be created using computer modeling software (e.g.. finite element analysis software) which includes vibrational analysis capabilities, in step S3, the user determines a modeled natural frequency of the gearbox 10 and the installed bearing 14 using the created vibration model of the gearbox 10.
  • the actual bearing 14 is installed in the actual gearbox 10 with an approximate preload or clearance provided to the bearing 1 during installation, in step S4, the user then measures the actual natural frequency of the gearbox 10 and installed bearing 14 using the modal analysis system 24.
  • the user first couples the vibration sensor 26 to the assembled gearbox 1 .
  • the vibration excitation instrument or impact hammer 38 is used to induce vibration of the gearbox 10,
  • the vibration sensor 26, such as an accelerometer, detects the vibration of the gearbo 10 and the vibrational signal is received and recorded by the signal analyzer 30.
  • the actual natural frequency of the gearbox 10 and installed bearing 14 is determined.
  • step S5 the actual natural frequenc of the gearbox 10 and installed bearing 14 is compared to the modeled natural frequency previously determined. If the actual natural frequency of the gearbox 1 and installed bearing 14 is lower than the modeled natural frequency, the preload on the bearing 14 is too low, and is therefore increased as shown in step S6, As is understood in the art, bearing preload is increased by reducing the interna! clearance of the bearing elements relative to each other. For example, in a tapered roller bearing, when axial endplay (i,e, 5 a maximum relative displacement, in a direction parallel to the bearing axis, between the two rings of an unmounted bearing) is reduced, preload is increased.
  • axial endplay i,e, 5 a maximum relative displacement, in a direction parallel to the bearing axis, between the two rings of an unmounted bearing
  • the stiffness of the bearing 1 and natural frequency of the gearbox 10 and installed bearing 1 also increase, if the actual natural frequency of the gearbox 10 and installed bearing 14 is greater than the modeled natural frequency, the preload on the bearing is decreased as shown in step S7.
  • bearing preload is decreased by increasing the internal clearance of the bearing elements relative to each other. For example, in a tapered roller bearing, when the axial endplay is increased, the preload is decreased.
  • the stiffness of the bearing 14 and the natural frequency of the gearbox 10 and installed bearing 14 also decrease. If the actual natural frequency of the gearbox 10 approximately equals the modeied natural frequency, tlie preload of the bearing does not need t be changed.
  • the bearing preload may be set to zero (i.e., the bearing elements are not touching) and the bearing elements may be set with a desired clearance or separation. If changes to the bearing preload or clearance have been made, steps S4 and S5 are repeated until the actual natural frequency of the gearbox 10 and installed bearing 14 approximately equals the modeled natural frequency.

Landscapes

  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • General Physics & Mathematics (AREA)
  • Rolling Contact Bearings (AREA)
  • General Details Of Gearings (AREA)

Abstract

Un nouveau procédé de réglage pour des paliers dans des boîtes d'engrenages ou des ensembles de transmission utilise des techniques d'analyse par modélisation et d'analyse modale. La rigidité des paliers varie en fonction d'une précontrainte ou d'un jeu établi du palier. Les paliers peuvent être dotés de différents niveaux de jeu interne entre les éléments de palier pour faire varier la contrainte ou précontrainte interne du palier avant que celui-ci ne soit sollicité par une charge externe. La rigidité des paliers influence la fréquence naturelle de la boîte d'engrenages. Il est possible de définir et d'ajuster de façon plus précise et constante la précontrainte ou le jeu de palier en comparant la fréquence naturelle modélisée de l'ensemble de boîte d'engrenages et sa fréquence naturelle déterminée expérimentalement.
PCT/US2014/067308 2013-12-05 2014-11-25 Réglage de paliers par analyse modale WO2015084636A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201361912082P 2013-12-05 2013-12-05
US61/912,082 2013-12-05

Publications (1)

Publication Number Publication Date
WO2015084636A1 true WO2015084636A1 (fr) 2015-06-11

Family

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Family Applications (1)

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PCT/US2014/067308 WO2015084636A1 (fr) 2013-12-05 2014-11-25 Réglage de paliers par analyse modale

Country Status (1)

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WO (1) WO2015084636A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110095283A (zh) * 2019-05-16 2019-08-06 西安交通大学 一种考虑轴承时变激励的齿轮动力学测试装置
IT201900024030A1 (it) * 2019-12-16 2021-06-16 Skf Ab A system and method for determining bearing preload by vibration measurement
CN114186333A (zh) * 2021-11-19 2022-03-15 中国直升机设计研究所 一种振动传感器的安装支架的生成方法

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59188535A (ja) * 1983-04-12 1984-10-25 Nippon Seiko Kk ころがり軸受の予圧量検出方法および装置
US5341569A (en) * 1992-02-24 1994-08-30 Nsk Ltd. Preloading method for preload-adjustable rolling bearing and manufacturing method of the same
DE102005012914A1 (de) * 2005-03-21 2006-10-05 Koenig & Bauer Ag Verfahren zur Erkennung einer Einstellung eines Lagers eines rotierenden Bauteils und Verfahren zu dessen Einstellung

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59188535A (ja) * 1983-04-12 1984-10-25 Nippon Seiko Kk ころがり軸受の予圧量検出方法および装置
US5341569A (en) * 1992-02-24 1994-08-30 Nsk Ltd. Preloading method for preload-adjustable rolling bearing and manufacturing method of the same
DE102005012914A1 (de) * 2005-03-21 2006-10-05 Koenig & Bauer Ag Verfahren zur Erkennung einer Einstellung eines Lagers eines rotierenden Bauteils und Verfahren zu dessen Einstellung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
JUI P HUNG ET AL: "Prediction of the Dynamic Characteristics of a Milling Machine Using the Integrated Model of Machine Frame and Spindle Unit", WORLD ACADEMY OF SCIENCE, ENGINEERING AND TECHNOLOGY. INTERNATIONAL SCIENCE INDEX, vol. 6, no. 67, 21 July 2012 (2012-07-21), pages 626 - 632, XP055171144, ISSN: 1307-6892 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110095283A (zh) * 2019-05-16 2019-08-06 西安交通大学 一种考虑轴承时变激励的齿轮动力学测试装置
IT201900024030A1 (it) * 2019-12-16 2021-06-16 Skf Ab A system and method for determining bearing preload by vibration measurement
US11385111B2 (en) 2019-12-16 2022-07-12 Aktiebolaget Skf System and method for determining bearing preload by vibration measurement
CN114186333A (zh) * 2021-11-19 2022-03-15 中国直升机设计研究所 一种振动传感器的安装支架的生成方法

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