WO1998004897A1 - Procede servant a ameliorer la precision d'une machine a mesurer l'uniformite des pneus - Google Patents

Procede servant a ameliorer la precision d'une machine a mesurer l'uniformite des pneus Download PDF

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Publication number
WO1998004897A1
WO1998004897A1 PCT/US1996/012484 US9612484W WO9804897A1 WO 1998004897 A1 WO1998004897 A1 WO 1998004897A1 US 9612484 W US9612484 W US 9612484W WO 9804897 A1 WO9804897 A1 WO 9804897A1
Authority
WO
WIPO (PCT)
Prior art keywords
load cells
signals
differential
tire uniformity
uniformity machine
Prior art date
Application number
PCT/US1996/012484
Other languages
English (en)
Inventor
Audice Wendell Barnette, Jr.
Original Assignee
The Goodyear Tire & Rubber 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 Goodyear Tire & Rubber Company filed Critical The Goodyear Tire & Rubber Company
Priority to PCT/US1996/012484 priority Critical patent/WO1998004897A1/fr
Priority to AU66840/96A priority patent/AU6684096A/en
Priority to EP96926813A priority patent/EP0916081A1/fr
Priority to PL96333378A priority patent/PL333378A1/xx
Priority to JP50875298A priority patent/JP2002511137A/ja
Priority to US09/180,044 priority patent/US6035709A/en
Priority to CA002261801A priority patent/CA2261801A1/fr
Publication of WO1998004897A1 publication Critical patent/WO1998004897A1/fr

Links

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
    • G01M17/00—Testing of vehicles
    • G01M17/007—Wheeled or endless-tracked vehicles
    • G01M17/02—Tyres
    • G01M17/022—Tyres the tyre co-operating with rotatable rolls
    • G01M17/024—Tyres the tyre co-operating with rotatable rolls combined with tyre surface correcting or marking means
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M17/00—Testing of vehicles
    • G01M17/007—Wheeled or endless-tracked vehicles
    • G01M17/02—Tyres
    • G01M17/022—Tyres the tyre co-operating with rotatable rolls

Definitions

  • This invention relates to the field of enhancing the measurement accuracy of a machine, and more particularly to a method of enhancing the measurement accuracy of a tire uniformity machine by combining differential signals generated by supplementary load cells with signals generated by measuring load cells to cancel signals generated by the vibration of the tire uniformity machine.
  • a tire uniformity machine which includes an assembly for rotating a test tire against the surface of a freely rotating load wheel.
  • the load wheel is moved in a manner dependent on the forces exerted by the rotating tire and those forces are measured by appropriately placed measuring devices, e.g., load cells.
  • shoulder and center rib grinders are used to remove a small amount of the tire tread at precisely the location of non- uniformities detected by the measuring devices.
  • the tire is rotated, it is measured and ground simultaneously.
  • TUM tire uniformity machine
  • an apparatus for enhancing the measurement accuracy of a tire uniformity machine includes primary load cells supporting a load wheel spindle with a freely rotating load wheel mounted on the spindle.
  • Supplementary load cells are each mounted to the tire uniformity machine in close proximity to a corresponding primary load cells .
  • Each of the supplementary load cells has a fixed mass attached thereto.
  • An electric signal conditioner includes a plurality of signal conversion sections which convert force measurement voltage signals generated by the primary load cells into force measurement signals that can be inputted into a computer.
  • a plurality of differential input sections convert differential voltage signals from the supplementary load cells into differential signals that can be inputted into the computer.
  • a signal summing section is provided to sum the force measurement signals and the differential signals and to output the difference between the measurement signals and the differential signals to the computer.
  • a method of enhancing the measurement accuracy of a tire uniformity machine comprising the following steps.
  • the forces generated by the vibration of the tire uniformity machine are monitored with primary load cells supporting a wheel spindle of the tire uniformity machine with a . freely rotating load wheel mounted thereon and force measurement voltage signals are generated in response thereto.
  • the forces generated by the vibration of the tire uniformity machine are monitored with supplementary load cells mounted to the tire uniformity machine and differential voltage signals are generated in response thereto.
  • the force measurement voltage signals generated by the primary load cells are converted into analog voltage measurement signals .
  • the differential output voltage signals are reversed and converted into analog differential signals.
  • the analog voltage measurement signals and the analog differential voltage signals are summed and summed analog voltage signals equal to their difference are outputted to the computer to substantially cancel the effect of vibrational forces generated by the tire uniformity machine.
  • Fig. 1 is a schematic illustration of a plan view of a tire uniformity machine in accordance with the invention with a tire mounted thereon;
  • Fig. 2 is a schematic illustration of a side view through line 2-2 of Fig. 1, showing a load wheel mounted between two primary load cells which generate output signals in response to the force variations of a tire, two supplementary load cells mounted to the frame of the tire uniformity machine, and electrical circuitry for detecting and canceling extraneous vibrations picked up by the tire uniformity machine;
  • Fig. 3 is a schematic illustration of the electrical circuitry interconnecting one of the primary load cells to a corresponding supplementary load cell;
  • Figs. 4A and 4B, collectively Fig. 4 is flow diagram of the process of the present invention.
  • Tire 12 is typically a pneumatic tire having a circumferential tire tread with top and bottom shoulder regions and a central region between the top and bottom shoulder regions.
  • the tire 12 can be mounted on a rim 14 secured to a tire spindle 16 and inflated to a desired pressure.
  • the tire 12 can be placed under load by a load wheel 18, which is rotatably supported on a fixed spindle 20 extending through the load wheel and suspended from primary load cells 22,24 at either end.
  • the primary load cells 22,24 are mounted to the frame supports 26,28, respectively, of the tire uniformity machine.
  • Each of the primary load cells 22,24 includes a lateral load cell section conventionally used to measure the lateral force exerted by the tire 12 against load wheel 18 in a direction parallel to the axis of rotation extending about which the load wheel rotates.
  • the primary load cells 22,24 also include a radial load cell section conventionally used to measure the radial force at the point of intersection of the tire 12 and the load wheel 18 exerted by the tire 12 against the load wheel 18 and through spindle 20 about which the load wheel rotates.
  • An important aspect of the present invention relates to the provision of supplementary load cells 30,32 mounted in close proximity to the primary load cells 22,24, such as on the frame supports 26,28, respectively, as shown.
  • Each supplementary load cell 30,32 has a fixed mass, such as weight 34,36, respectively, attached thereto to simulate the fixed mass attached to each of the primary load cells
  • supplementary load cells 30,32 are shown mounted to frame supports 26,28 in one location, it is also within the terms of the invention to mount them at other locations on the TUM 10, as long as they are in close proximity to and oriented in the same direction as primary load cells 22,24.
  • the load wheel 18 is pressed against the tire to load the inflated tire with a specified force (for example, 600 to 1900 lb) to simulate road conditions.
  • the spindle 20 is mounted to bearing blocks (not shown) and is moved by conventional means, such as an electric motor (not shown) operating through a ball-and-screw connection, to move the load wheel 18 into and out of engagement with the tire 12.
  • a shoulder grinding assembly 38 is located substantially 180° with respect to tire 12 from load wheel 18.
  • the shoulder grinding assembly 38 includes substantially identical top and bottom shoulder grinders 40a and 40b (only top shoulder grinder 40a is illustrated and described) , which include grinding wheels that are powered by motors and are independently moved into and out of engagement with the shoulder regions of tire 12.
  • the top shoulder grinder 40a has a grinding wheel 42a powered by a motor 44a and can be moved into and out of engagement with the shoulder portions of tire 12 by any conventional means, such as an hydraulic servo device (not shown) .
  • a center grinder assembly 46 is located adjacent wheel 12 approximately 90° counterclockwise about tire 12 from load wheel 18.
  • the center grinder assembly 46 has a grinding wheel 48 that is powered by a motor 50 and is moved into and out of engagement with the central region of the tread of tire 12 by conventional means, such as with an hydraulic servo device (not shown) .
  • Voltage signals are generated by primary load cells 22,24 and inputted through lines 52 and 54, respectively, into an electric signal conditioner 56.
  • the electric signal conditioner 56 includes substantially identical signal conversion sections 58 and 60 which convert the force measurement voltage signals generated by primary load cells 22,24, respectively, into signals that are conditioned so that they can be inputted to and stored in a computer 62.
  • the signal conversion sections 58 and 60 as shown in Fig. 3, each includes at least one amplifier 64 connected by lines 52,54 to primary load cells 22, 24, respectively.
  • the amplified output signal from the amplifier 64 is directed through line 66 into an anti-aliasing filter 68 to cut off the high frequency outputs, i.e.
  • the electric signal conditioner 60 also includes a low pass filter 70 connected in series to anti- aliasing filter 68 through line 72.
  • the low pass filter 70 attenuates frequencies greater than 16 hertz, from the amplified output signal of amplifier 64 so that the signal bandwidth is limited to frequencies generated by the tire and load wheel .
  • the output signal from low pass filter 62 is directed through lines 74,76 into a signal summing sections 78,80, respectively, as discussed below.
  • the present invention is directed to the measurement and elimination of deviations from the prescribed specifications of the TUM 10, i.e., operating under conditions without extraneous vibrations, caused primarily by extraneous vibrations generated by or induced in machine 10.
  • the extraneous vibrations are caused by rotating components such as a motor-driven tire spindle 16, the tire grinding assemblies 38, and the center grinding assembly 46, the motor bearings wearing out, the grind wheels being defective or improperly installed, and/or noise and vibration from machines external to the tire uniformity machine 10.
  • the primary sensors for many of the required measurements used in operating the TUM 10 are primary load cells 22,24 which are normally in the electrical differential mode. This fact, combined with the inherent low impedance of primary load cells 22,24, usually provides an adequate quality signal output for the TUM 10.
  • the primary load cells 22,24 cannot discriminate between the signal components generated by the force measurement of the tire and a vibration or force component generated by an extraneous vibration generated or picked up by the TUM 10.
  • supplementary load cells 30,32 with substantially identical characteristics to the primary load cells 22,24 are mounted to the TUM 10 so as to be oriented in the same direction and in very close proximity to the primary measuring load cells 22,24, respectively.
  • the supplementary load cells 30,32 have a fixed mass, such as weight 34, 36, respectively, attached thereto.
  • the output voltage signals from the supplementary load cells 30, 32 are directed through pairs of electrical lines 80 and 81 into substantially identical differential input sections 84,86, respectfully. Since differential input sections 84,86 are substantially identical, only differential input sections 86 is shown and described. Referring to Fig.
  • the pair of electrical lines 82 are reversed in differential input section 86 and are inputted into a gain adjustment amplifier 88.
  • the differential voltage signal being output from gain adjustment amplifier 88 is then directed into a line 90 and into a phase adjustment amplifier 92.
  • the voltage output signal from phase adjustment amplifier 92 is then outputted through line 94 into signal summing section 78.
  • the voltage signals through electrical lines 76 and 94 are directed through resistors 96 and 98, respectively, and then combined into line 100 and inputted into a summing amplifier 102.
  • the summing amplifier 102 subtracts the voltage signals from lines 94 and 76 and the resulting amplified signal from summing amplifier 102 is then outputted from signal summing section 80 through line 106 into computer 62.
  • the resulting amplified signal outputted from signal summing section 78 through line 106 is directed into computer 62.
  • Each supplementary load cell 30,32 and corresponding primary measuring load cell 22,24 measure virtually the same noise and vibration components when the TUM 10 is running with no load on the load wheel 18. Since both the primary load cells 22,24 and their corresponding supplementary load cells 30,32 are operating in the differential mode, the pair of signal wires 81,82 from the supplementary load cells can be reversed, as shown in Fig. 3, without any adverse electrical effects. Using this configuration, a positive vibration in the TUM 10 will generate both a positive signal output from the primary measuring load cells 22,24 and a negative signal output from the supplementary load cells
  • the amplifier 92 provides a phase angle adjustment which can be adjusted to correct for the difference in location of the supplementary load cells 30,32 with respect to the corresponding primary load cells 22 and 24. That is, the machine 10 can be calibrated with the rotating portions, such as the motors and grinders turned off.
  • a conventional vibration generating device such as a Model No. 2706 power amplifier and Model No. 4809 shaker from Beuel & Kjaer of Denmark.
  • the gain and phase of the voltage output signals from the supplementary load cells are adjusted with amplifiers 88 and 92 in sections 84 and 86 so that there is a minimum difference between the output voltage signals being outputted by the summing sections 78 and 80 as calculated by computer 62.
  • This calibration effectively cancels the vibration signals induced in the TUM 10 that are picked up by both the primary and supplementary load cells.
  • FIG. 4 there is illustrated a flow diagram of the present invention.
  • a TUM 10 which incorporates the electric signal conditioner 56 of the present invention is running without force applied by the load wheel 18, the voltage signals inputted through lines 104 and 106 into the computer 62 will be close to zero.
  • the measuring load cells 22,24 will respond to the additional load plus the vibration components produced by the rotating components and any extraneous vibrations .
  • the supplementary load cells 30,32 will see only the vibration components produced by the rotating components and any extraneous vibrations.
  • the vibrational components measured by the primary load cells will be canceled out.
  • the remaining signal components, generated by the primary load cells 22,24 will, for the most part, result from the load forces of the tire against the load wheel 18. That is, the two analog signals being outputted from signal summing sections 78,80 correspond to the monitored radial and/or lateral forces with very low background noise generated by the tire 12 loaded against the load wheel 18 during a predetermined period of time.
  • the computer 62 independently samples the analog signals being inputted from the summing sections 78,80 for a predetermined time and converts the analog signals to digital signals.
  • computer 62 converts the digital signals to a frequency domain signal representation using a Conventional Fast Fourier Transform (FFT) program for each of the primary load cell signals less the supplementary load cells being monitored.
  • FFT Fast Fourier Transform
  • the phase shift for each primary load cell can be calculated and a correction table generated for each frequency present in the spectrum.
  • signals can be acquired periodically while running without a load on the tire and new FFT's can be calculated and compared with the original FFT's. Comparing the frequency spectrum and the amplitudes of each rotating component of TUM 10 would enable, an operator to discover the malfunction of some part of the rotating components. The malfunction could generate an alarm signal .
  • the computer 62 than operates on the frequency domain signal representation to calculate a power spectrum, as discussed in the previously discussed U.S. Patent Application entitled Method of Machine Vibration Analysis For The Tire Uniformity Machine, of discrete frequency components in hertz versus the amplitude or magnitude of the discrete frequency components in pounds. Selected frequency components are then compared with selected groupings of frequencies representing critical frequencies of different moving parts of the tire uniformity machine 10. An acceptable amplitude for the selected groups of frequencies, representing critical frequencies of the moving parts operating as designed, is inputted into the computer.
  • an alarm signal is output by the computer.
  • the alarm signal indicates that a rotating portion of the tire uniformity machine 10 is defective.
  • the alarm signal could be inputted into a display monitor and/or used to activate an alarm device such as a light or audible alarm, i.e., a bell or buzzer, to alert a machine operator that the tire uniformity machine 10 is vibrating at a level beyond an acceptable limit.
  • the moving component of the tire uniformity machine 10 or external vibration source which is causing the unwanted vibration can be isolated as generally described in the application entitled Method of Machine Vibration Analysis For The Tire Uniformity Machine.
  • Computer 62 is conventionally programmed to determine the conicity, lateral force values, radial run-out, and radial force values of the tire 12, and to control the corrective grinding action to take, as discussed in U.S. Patent Application Serial No.
  • 08/534,809 entitled METHOD OF CORRECTING CONICITY, RADIAL RUN OUT, AND FORCE VARIATIONS IN A PNEUMATIC TIRE, assigned to The Goodyear Tire & Rubber Co., the assignee of the present invention, is connected to the shoulder grinding assembly 24 and to the center grinder assembly 26 to position these grinding assemblies, as required.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Testing Of Balance (AREA)
  • Force Measurement Appropriate To Specific Purposes (AREA)

Abstract

Procédé servant à améliorer la précision d'une machine à mesurer l'uniformité des pneus en combinant des signaux générés par des cellules supplémentaires de charge à des signaux générés par des cellules correspondantes de mesure de charge par rapport à des signaux de vibration générés par la machine à mesurer l'uniformité du pneu.
PCT/US1996/012484 1996-07-30 1996-07-30 Procede servant a ameliorer la precision d'une machine a mesurer l'uniformite des pneus WO1998004897A1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
PCT/US1996/012484 WO1998004897A1 (fr) 1996-07-30 1996-07-30 Procede servant a ameliorer la precision d'une machine a mesurer l'uniformite des pneus
AU66840/96A AU6684096A (en) 1996-07-30 1996-07-30 Method of enhancing the measurement accuracy of a tire uniformity machine
EP96926813A EP0916081A1 (fr) 1996-07-30 1996-07-30 Procede servant a ameliorer la precision d'une machine a mesurer l'uniformite des pneus
PL96333378A PL333378A1 (en) 1996-07-30 1996-07-30 Method of increasing measuring accuracy of a tyre balancing machine
JP50875298A JP2002511137A (ja) 1996-07-30 1996-07-30 タイヤ均一性装置の測定確度を高める方法
US09/180,044 US6035709A (en) 1996-07-30 1996-07-30 Method of enhancing the measurement accuracy of a tire uniformity machine
CA002261801A CA2261801A1 (fr) 1996-07-30 1996-07-30 Procede servant a ameliorer la precision d'une machine a mesurer l'uniformite des pneus

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US1996/012484 WO1998004897A1 (fr) 1996-07-30 1996-07-30 Procede servant a ameliorer la precision d'une machine a mesurer l'uniformite des pneus

Publications (1)

Publication Number Publication Date
WO1998004897A1 true WO1998004897A1 (fr) 1998-02-05

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Application Number Title Priority Date Filing Date
PCT/US1996/012484 WO1998004897A1 (fr) 1996-07-30 1996-07-30 Procede servant a ameliorer la precision d'une machine a mesurer l'uniformite des pneus

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EP (1) EP0916081A1 (fr)
JP (1) JP2002511137A (fr)
AU (1) AU6684096A (fr)
CA (1) CA2261801A1 (fr)
WO (1) WO1998004897A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001002826A1 (fr) * 1999-07-07 2001-01-11 Illinois Tool Works, Inc. Systeme de compensation de vibrations pour systemes d'essai de pneus
JP2004516452A (ja) * 2000-06-08 2004-06-03 ブリヂストン／フアイヤーストーン・ノース・アメリカン・タイヤ・エルエルシー タイヤ試験ステーション用動的力測定システム
JP2004537711A (ja) * 1999-07-07 2004-12-16 イリノイ トゥール ワークス インコーポレイティド タイヤ試験システム用の振動補正システム
US6834559B1 (en) 1999-07-09 2004-12-28 Illinois Tool Works Inc. Vibration compensation system for tire testing systems

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5541689B2 (ja) * 2010-03-16 2014-07-09 株式会社神戸製鋼所 バランス試験における監視方法及び動バランス計測装置
WO2015118657A1 (fr) * 2014-02-07 2015-08-13 三菱重工マシナリーテクノロジー株式会社 Dispositif de mesure de force de réaction de pneu et dispositif d'essai de pneu

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61231432A (ja) * 1985-04-05 1986-10-15 Yokohama Rubber Co Ltd:The タイヤユニフオミテイマシンに於ける検査方法
EP0342773A2 (fr) * 1988-05-16 1989-11-23 General Tire Inc. Méthode et appareil pour l'équilibrage par meulage de pneumatiques

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61231432A (ja) * 1985-04-05 1986-10-15 Yokohama Rubber Co Ltd:The タイヤユニフオミテイマシンに於ける検査方法
EP0342773A2 (fr) * 1988-05-16 1989-11-23 General Tire Inc. Méthode et appareil pour l'équilibrage par meulage de pneumatiques

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 011, no. 068 (P - 553) 28 February 1987 (1987-02-28) *

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001002826A1 (fr) * 1999-07-07 2001-01-11 Illinois Tool Works, Inc. Systeme de compensation de vibrations pour systemes d'essai de pneus
JP2004537711A (ja) * 1999-07-07 2004-12-16 イリノイ トゥール ワークス インコーポレイティド タイヤ試験システム用の振動補正システム
JP2011107163A (ja) * 1999-07-07 2011-06-02 Micro-Poise Measurement Systems Llc タイヤ試験システム用の振動補正システム
JP4741126B2 (ja) * 1999-07-07 2011-08-03 マイクロ−ポイズ メジャーメント システムズ，リミティド ライアビリティ カンパニー タイヤ試験システム用の振動補正システム
EP1203213A1 (fr) * 1999-07-09 2002-05-08 Illinois Tool Works Inc. Systeme de compensation de vibrations pour systemes d'essai de pneus
EP1203213A4 (fr) * 1999-07-09 2002-11-13 Illinois Tool Works Systeme de compensation de vibrations pour systemes d'essai de pneus
US6834559B1 (en) 1999-07-09 2004-12-28 Illinois Tool Works Inc. Vibration compensation system for tire testing systems
JP2004516452A (ja) * 2000-06-08 2004-06-03 ブリヂストン／フアイヤーストーン・ノース・アメリカン・タイヤ・エルエルシー タイヤ試験ステーション用動的力測定システム
EP1287324B1 (fr) * 2000-06-08 2010-02-24 Bridgestone/Firestone North American Tire, LLC Systeme de mesure de force dynamique pour banc d'essai de pneus

Also Published As

Publication number Publication date
JP2002511137A (ja) 2002-04-09
AU6684096A (en) 1998-02-20
EP0916081A1 (fr) 1999-05-19
CA2261801A1 (fr) 1998-02-05

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