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EP1922495A1 - Palier capteur de charge - Google Patents

Palier capteur de charge

Info

Publication number
EP1922495A1
EP1922495A1 EP06814176A EP06814176A EP1922495A1 EP 1922495 A1 EP1922495 A1 EP 1922495A1 EP 06814176 A EP06814176 A EP 06814176A EP 06814176 A EP06814176 A EP 06814176A EP 1922495 A1 EP1922495 A1 EP 1922495A1
Authority
EP
European Patent Office
Prior art keywords
sensor
outer race
load sensing
bearing assembly
bearing outer
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.)
Withdrawn
Application number
EP06814176A
Other languages
German (de)
English (en)
Inventor
Graham Mcdearmon
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.)
Timken Co
Original Assignee
Timken Co
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 US11/219,933 external-priority patent/US7240570B2/en
Application filed by Timken Co filed Critical Timken Co
Publication of EP1922495A1 publication Critical patent/EP1922495A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L5/00—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes
    • G01L5/0009—Force sensors associated with a bearing
    • 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
    • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/02—Bearings
    • 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

Definitions

  • the present invention relates generally to bearings and, in particular to a bearing assembly configured with sensors to monitor applied forces and torques to provide responsive signals for use by devices, which monitor the bearing loads.
  • the bearing assembly of the present invention may be used to measure radial forces, thrust force, tilting moments, rotation speeds, and temperature at the bearing for use in many applications such as Vehicle Dynamics Control Systems (Vehicle Stability Control Systems), vehicle rollover prevention systems, tire-integrity monitoring systems, road- condition monitoring systems, and vehicle suspension-control systems.
  • Vehicle Dynamics Control Systems Vehicle Stability Control Systems
  • vehicle rollover prevention systems tire-integrity monitoring systems
  • road- condition monitoring systems road- condition monitoring systems
  • vehicle suspension-control systems Vehicle Dynamics Control Systems
  • bearing loading information in electrical signal form, is utilized by a Vehicle Dynamics Control (“VDC") Systems to monitor the driving conditions of the vehicle, enabling the system to control the torque supplied to the vehicle wheels.
  • VDC Vehicle Dynamics Control
  • An antifriction rolling bearing disclosed in U.S. Patent No. 5,140,849 to Fujita et al. uses two strain gages to monitor the general loads applied to a bearing.
  • the '849 Fujita et al. bearing assembly is unable to provide the multi-faceted data needed by high-level VDC electronic systems or by the processor-controlled systems in the rolling-mills industry or the machine-tool industry.
  • United States Patent No. 4,748,844 to Yoshikawa et a/ discloses a load-detection device related to the automotive industry, consisting of a multi-component load cell structure fixed to a hub on which a road wheel is mounted. The load cell structure is attached so as to rotate with the tire of the wheel.
  • the device disclosed in the '844 Yoshikawa et a/., patent cannot provide signals indicating all loads and all torques required to enable a high level VDC electronic device or other such monitoring devices to function properly.
  • the device employs strain gages in only one plane, perpendicular to the axis about which the wheel rotates. As a result, the signals from the strain gages on the device are unable to detect the forces tending to cause a vehicle to skid sideways or to roll the vehicle over.
  • steel rolling mills utilize electronic processing and control to manipulate the speed and loads associated with rollers during a steel rolling process. Specifically, rolling mills need bearing feedback regarding indications of a belt slipping on rollers or indications that a particular set of rollers is experiencing higher loads and torques.
  • programmable controllers and processors monitor and control the speed and loads associated with spindles in a variety of milling, cutting, and drilling machines.
  • Computer controlled machine tools monitor the amount of force and torque being experienced by bearings supporting a spindle in order to assess whether cutting and drilling tools have become dull or whether the cutting or drilling force, torque, and speeds exceed the limits established for proper machining operations.
  • Figure 1A illustrates a front view of a load sensing bearing assembly of the present invention
  • Figure 1 B illustrates a sectional view of the load sensing bearing assembly of Fig. 1A, taken along segment A-A;
  • Figure 2A illustrates a front view of an alternate load sensing bearing assembly configuration of the present invention
  • Figure 2B illustrates a sectional view of the load sensing bearing assembly of Fig. 2A, taken along segment A-A.
  • Figure 3A illustrates a front view of an alternate load sensing bearing assembly configuration of the present invention
  • Figure 3B illustrates a sectional view of the load sensing bearing assembly of Fig. 3A, taken along segment A-A.
  • Figure 4A illustrates a front view of an alternate load sensing bearing assembly configuration of the present invention
  • Figure 4B illustrates a sectional view of the load sensing bearing assembly of Fig. 4A, taken along segment A-A.
  • Figure 5A illustrates a front view of an alternate load sensing bearing assembly configuration of the present invention
  • Figure 5B illustrates a sectional view of the load sensing bearing assembly of Fig. 5A, taken along segment A-A.
  • Figure 6A illustrates a front view of an alternate load sensing bearing assembly configuration of the present invention
  • Figure 6B illustrates a sectional view of the load sensing bearing assembly of Fig. 6A, taken along segment A-A.
  • Figure 7A illustrates a front view of an alternate load sensing bearing assembly configuration of the present invention
  • Figure 7B illustrates a sectional view of the load sensing bearing assembly of Fig. 7A, taken along segment A-A.
  • Figure 8A illustrates a front view of an alternate load sensing bearing assembly configuration of the present invention
  • Figure 8B illustrates a sectional view of the load sensing bearing assembly of Fig. 8A 1 taken along segment A-A.
  • Figure 9A illustrates a front view of an alternate load sensing bearing assembly configuration of the present invention
  • Figure 9B illustrates a sectional view of the load sensing bearing assembly of Fig. 9A, taken along segment A-A.
  • Figure 10A illustrates a front view of an alternate load sensing bearing assembly configuration of the present invention
  • Figure 10B illustrates a sectional view of the load sensing bearing assembly of Fig. 10A, taken along segment A-A.
  • Figure 11A illustrates a front view of an alternate load sensing bearing assembly configuration of the present invention
  • Figure 11 B illustrates a sectional view of the load sensing bearing assembly of Fig. 11 A, taken along segment A-A.
  • Figure 12A illustrates a front view of an alternate load sensing bearing assembly configuration of the present invention
  • Figure 12B illustrates a sectional view of the load sensing bearing assembly of Fig. 12A, taken along segment A-A.
  • Figure 13A illustrates a front view of an alternate load sensing bearing assembly configuration of the present invention
  • Figure 13B illustrates a sectional view of the load sensing bearing assembly of Fig. 13A, taken along segment A-A.
  • Figure 14A illustrates a front view of an alternate load sensing bearing assembly configuration of the present invention
  • Figure 14B illustrates a sectional view of the load sensing bearing assembly of Fig. 14A, taken along segment A-A.
  • Figure 15A illustrates a front view of an alternate load sensing bearing assembly configuration of the present invention
  • Figure 15B illustrates a sectional view of the load sensing bearing assembly of Fig. 15A, taken along segment A-A.
  • Figure 15C illustrates a sectional view of the load sensing bearing assembly of Fig. 15A, taken along segment B-B.
  • FIGS. 1A and 1 B illustrate a general load sensing bearing assembly 100 of the present invention.
  • the load-sensing bearing assembly 100 is generally constructed to support an inner race or cone (not shown) and rolling elements (not shown, but which can be any type of rolling elements such as, but not limited to, tapered, cylindrical, ball, needle, or spherical).
  • the load-sensing bearing assembly 100 includes a bearing outer race or cup 102 which can assume any orientation about the Y-axis, and a flange assembly 104 for attachment of the bearing outer race or cup 102 to an application structure 106 by a suitable number of attachment bolts 108 secured with associated bolt holes 110 in the flange assembly 104.
  • Exemplary bearing structures are the UNIPAC- and TS-style of bearing assemblies manufactures and sold by The Timken Company of Canton, Ohio. Those of ordinary skill will recognize that the present invention may be utilized with a wide range of bearing types and configurations which have an outer structure such as a bearing outer race or cup secured to an application structure.
  • the flange assembly 104 consists of an inner annular flange 104A, and an outer annular flange 104B, coupled together by a set of annularly spaced anisotropic spring regions 112 which are disposed between the annular flanges 104a and 104b, linking them together.
  • the inner annular flange 104a may be integrally formed with the bearing outer race or cup 102, and correspondingly, that the outer annular flange 104b may be integrally formed with the application structure 106.
  • anisotropic spring regions 112 are illustrated as disposed between the inner annular flange 104a and outer annular flange 104b, but more or fewer may be utilized within the scope of the invention. Gaps 114 disposed between the anisotropic spring regions 112 facilitate deformation of the anisotropic spring regions 112, and allow for a limited range of displacement and/or rotation of the bearing outer race or cup 102 and inner annular flange 104a relative to the outer annular flange 104b and application structure 106.
  • anisotropic spring regions may be constructed of a variety of shapes and materials, and in a variety of configurations such as shown below in the various alternate embodiments, and which may include webs and elastomeric materials.
  • the function of each anisotropic spring region is to permit a limited range of displacement and/or rotation of the bearing outer race or cup 102 and inner annular flange 104a relative to the outer annular flange 104b and supporting application structure 106 as described above.
  • a set of sensor modules 116 are disposed across the gaps 114, linking the inner annular flange 104a to the outer annular flange 104b.
  • Each sensor module 116 includes at least one sensor unit which is capable of measuring displacement, rotation, or strain, such that the set of sensor modules 116 as a whole provides measurements which are representative of the applied forces (Fx, Fy, Fz) and applied moments (Mx and Mz).
  • the amount of deformation provided by the anisotropic spring regions 112 must be sufficient to allow the sensors modules 116 to detect and measure the particular applied forces and/or moments intended to be measured.
  • the sensor modules 116 may also contain a temperature sensor or other type of sensor (e.g. speed sensors or accelerometers) that may be important for the end application in which the bearing assembly 100 is to be used, such as condition monitoring.
  • a temperature sensor is utilized in a sensor module 116 for thermal compensation, it is preferably placed in close proximity to an associated strain sensor.
  • the sensor units utilized within the sensor modules 116 may employ any suitable strain, displacement, rotation, or temperature sensor technology, such as, but not limited to, metal foil, piezoresistive, MEMS, vibrating wire, capacitive, inductive, optical, ultrasonic, etc.
  • quarter-, half-, or full-bridge strain sensors may be utilizes as are known in the art.
  • the signals accumulated from the set of sensor modules 116 are analyzed to produce measurements of the applied radial force components (Fx and Fz), thrust force component (Fy), tilting moment components (Mx and Mz), and bearing temperature (if at least one temperature sensor is included in the set of sensors 116) for the load- sensing bearing 100.
  • the set of sensor modules 116 preferably provides measurement for at least one of five degrees of freedom Fx, Fy, Fz, Mx, and Mz.
  • the measurement of temperature may be used to compensate for known thermal effects on the sensor units within the sensor modules 116, as well as directly for use as a measurement parameter in an end application.
  • the anisotropic spring regions 112 can assume a wide variety of orientations about the Y-axis of the bearing assembly 100.
  • the anisotropic spring regions 116 may be of any of a wide variety of conventional designs to enhance movement between the bearing outer race or cup 102 and the outer annular flange 104b, so as to increase or reduce the values obtained by the set of sensor modules 116.
  • anisotropic spring regions 112 may be designed to enhance only specific movements between the bearing outer race or cup 102 and the outer annular flange 104b to increase or reduce specific forces required to obtain data to determine the values for the forces Fx, Fy, Fz, or moments Mx, Mz, that may be experienced by the load- sensing bearing assembly 100.
  • the general premise for the load sensing bearing assembly 100 of the present invention, and the various alternate embodiments, is that the structures supporting the bearing outer race or cup 102 relative to the application structure 106 include at least one anisotropic spring region 112 between the bearing outer race or cup 102 and the bolts 108 or other attachment points to the application structure 106. With the anisotropic spring region(s) 112 suspending the bearing outer race or cup from the application structure 106, forces and/or moments applied to the bearing assembly 100 will cause the bearing outer race or cup 102 to displace and/or rotate with respect to the application structure 106.
  • a set of displacement, rotation and/or strain sensors 116 strategically placed about the bearing outer race or cup 102, anisotropic spring region(s) 112, or supporting structure measure the relative bearing outer race or cup displacements, strains, and/or rotations.
  • the signals from the set of sensor modules 116 are used to produce measures of the applied radial forces, thrust forces, and tilting moments.
  • FIGS 2A and 2B illustrate an alternate embodiment for the load- sensing bearing assembly 100, indicated generally as 100a.
  • Four equally spaced anisotropic spring regions 112 are disposed around the outer circumference of an inner annular flange 104a supporting the bearing outer race or cup 102.
  • the center of each anisotropic spring region 112 is generally located about 45 degrees from the X-axis.
  • Each of the anisotropic spring regions 112 includes an axial beam 118 generally aligned parallel to the Y-axis, integral at one end by with an inner cross beam 120 coupled to the inner annular flange 104a supporting the bearing outer race or cup 102, and integral at an opposite end with an outer cross beam 122 coupled to the outer annular flange 104b which is secured to the application structure 106.
  • the inner annular flange 104a, inner cross beam 120, and axial beam 118 define an inner channel 124
  • the outer annular flange 104b, outer cross beam 122, and axial beam 118 define an outer channel 126.
  • a resilient material (not shown) may be utilized to fill the channels 124 and 126.
  • the resilient material is selected to permit a desired range of movement between the inner annular flange 104a and the outer annular flange 104b and to prevent unwanted materials (e.g. road debris) from entering the channels 124 and 126.
  • a polyurethane material may be used if it meets the operating parameters of the application.
  • a set of five sensor modules 116a - 116e form an array with each sensor module 116 bridging the gap 114 between the inner annular flange 104a and the outer annular flange 104b.
  • Each sensor module 116 includes at least one sensor unit which is capable of measuring displacement, rotation, or strain, such that the set of sensor modules 116 as a whole provides measurements which are representative of the applied forces (Fx, Fy, Fz) and applied moments (Mx and Mz), as previously described.
  • sensor module 116a may include a displacement sensor aligned with the Z-axis to measure displacements in the Z direction, and to provide information about the force Fz acting on the bearing assembly 100a.
  • Sensor module 116c may include a displacement sensor aligned with the X-axis to measure displacements in the X direction, and to provide information about the force Fx acting on the bearing assembly 100a.
  • Sensor modules 116b, 116d, and 116e, each configured with displacement sensors to measure displacements in the Y-axis are shown disposed at about 120 degree intervals about the Y axis, with the sensor module 116d aligned with the Z-axis. Together, displacement sensor modules 116b, 116d, and 116e provide signals that enable a determination of the value for the force Fy and the moments Mx and Mz.
  • sensor modules 116b, 116d, and 116e may be eliminated in favor of integrating a rotation sensor and at least one Y-axis displacement sensor into sensor modules 116a and 116c. If the sensor module 116a contains the Y-axis displacement sensor, sensor module 116a would provide measurements of displacements in the Y- direction and Z-direction, as well as rotation about the Z-axis. The measured displacement in the Z-direction provides information about the force Fz, and the measured rotation about the Z-axis provides information about the moment Mz. Sensor module 116c would, in-turn, provide measurements of displacement in the X-direction and rotation about the X- axis.
  • the measured displacement in the X-direction provides information about the force Fx
  • the measured rotation about the X-axis provides information about the moment Mx.
  • the displacements measured in the Y- direction by the Y-axis displacement sensor in sensor module 116a can be combined with the measured rotations about the X-axis to provide measurements of the force Fy.
  • FIGS 3A and 3B illustrate a similar alternate embodiment for the load-sensing bearing assembly 100, indicated generally as 100b.
  • a total of three equally spaced anisotropic spring regions 112 are disposed around the outer circumference of an inner annular flange 104a supporting the bearing outer race or cup 102.
  • Each of the anisotropic spring regions 112 includes an axial beam 118 generally aligned parallel to the Y-axis, integral at one end with an inner cross beam 120 coupled to the inner annular flange 104a supporting the bearing outer race or cup 102, and integral at an opposite end with an outer cross beam 122 coupled to the outer annular flange 104b which is secured to the application structure 106.
  • the inner annular flange 104a, inner cross beam 120, and axial beam 118 define an inner channel 124, while the outer annular flange 104b, outer cross beam 122, and axial beam 118 define an outer channel 126.
  • a resilient material (not shown) may be utilized to fill the channels 124 and 126.
  • the resilient material is selected to permit a desired range of movement between the inner annular flange 104a and the outer annular flange 104b and to prevent unwanted materials (e.g. road debris) from entering the channels 124 and 126.
  • a polyurethane material may be used if it meets the operating parameters of the application.
  • a set of five sensor modules 116a - 116e form an array with each sensor module 116 bridging the gap 114 between the inner annular flange 104a and the outer annular flange 104b.
  • Each sensor module 116 includes at least one sensor unit which is capable of measuring displacement, rotation, or strain, such that the set of sensor modules 116 as a whole provides measurements which are representative of the applied forces (Fx, Fy, Fz) and applied moments (Mx and Mz), as previously described.
  • sensor module 116c may include a displacement sensor aligned with the Z-axis to measure displacements in the Z-direction, and provide information about the force Fz acting on the bearing assembly 100b.
  • Sensor module 116b may include a displacement sensor aligned with the X-axis to measure displacements in the X direction, and provide information about the force Fx acting on the bearing assembly 100b.
  • Sensor modules 116a, 116d, and 116e, each configured with displacement sensors to measure displacements in the Y-axis are shown disposed at about 120 degree intervals about the Y-axis. Together, displacement sensor modules 116a, 116d, and 116e provide signals that enable a determination of the value for the force Fy and the moments Mx and Mz.
  • sensor modules 116a, 116d, and 116e may be eliminated in favor of integrating a rotation sensor and at least one Y-axis displacement sensor into sensor modules 116b and 116c. If the sensor module 116c contains the Y-axis displacement sensor, sensor module 116c would provide measurements of displacements in the Y- direction and Z-direction, as well as rotation about the Z-axis. The measured displacement in the Z-direction provides information about the force Fz, and the measured rotation about the Z-axis provides information about the moment Mz. Sensor module 116b would, in-turn, provide measurements of displacement in the X-direction and rotation about the X- axis.
  • the measured displacement in the X-direction provides information about the force Fx
  • the measured rotation about the X-axis provides information about the moment Mx.
  • the displacements measured in the Y- direction by the Y-axis displacement sensor in sensor module 1 16c can be combined with the measured rotations about the X-axis to provide measurements of the force Fy.
  • FIGs 4A and 4B illustrate an alternate embodiment of the load sensing bearing assembly 100 of the present invention, indicated generally at 100c, in which the outer annular flange 104b is secured to an application structure 106 by bolts 108 secured within bolt holes 1 10.
  • the anisotropic spring regions 112 are identical to those shown in Figures 2A and 2B, however the placement, type and quantity of the sensor modules 1 16 are different.
  • the array of sensor modules 116 includes two displacement and rotation sensor modules 116a, 1 16b aligned to the Z-axis and two displacement and rotation sensor modules 1 16c, 116d aligned to the X-axis of a bearing outer race or cup 102 and annular flanges 104a, 104b, with each of the sensor modules 116 bridging the gap 1 14 between the inner annular flange 104a and outer annular flange 104b.
  • the four displacement and rotation sensor modules 1 16 may instead be disposed on the radial centerlines of each of the four anisotropic regions 1 12 to bridge the outer channel 126 between the axial beam 1 18 and the outer annular flange 104b. Signals from the sensor modules 116a' - 116d' are utilized to calculate the values of three forces, Fx 1 Fy, and Fz, and two moments, Mx and Mz acting on the load sensing bearing assembly 100c.
  • the four sensor modules 116 including at least one strain sensor each, may instead be disposed on the radial centerlines of each of the four anisotropic spring regions 112, on the inner cross beams 120 over the inner channel 124 defined by the inner annular flange 104a and the axial beam 118.
  • Signals from the sensor modules 116a" - 116d” are utilized to calculate the values of three forces, Fx, Fy, and Fz, and two moments, Mx and Mz acting on the load sensing bearing assembly 100c.
  • Those of ordinary skill in the art will readily recognize that other combinations of sensor modules 116 can be used to provide measurements of three forces, Fx, Fy, and Fz, as well as the two moments, Mx and Mz acting on the load sensing bearing assembly 100c.
  • the outer annular flange 104b of the various embodiments of the load sensing bearing assembly 100 described herein may be integrally formed with the application structure 106 associated with the load sensing bearing assembly 100, eliminating bolts 108 and bolt holes 110.
  • a load sensing bearing assembly 100d is shown which is substantially identical to load sensing bearing assembly 100c shown in Figures 4A and 4B, with the exception that the application structure 106 is integral with, and defines, the outer annular flange 104b.
  • the specific shape and configuration of the application structure 106 will vary, depending upon the particular application in which the load sensing bearing assembly 100d is to be utilized.
  • FIGS 6A and 6B illustrate an alternate embodiment of the load sensing bearing assembly 100 of the present invention, indicated generally at 10Oe, utilizing an alternative style of anisotropic spring regions 112 and an alternative array of sensor modules 116.
  • the anisotropic spring regions 112 comprise four equidistantly spaced connecting members 128 coupling the bearing outer race or cup 102 and inner annular flange 104a to the outer annular flange 104b of the load- sensor bearing 100e.
  • Each of the connecting members 128 includes an outer radial spoke 130 coupled to the outer annular flange 104b, two inner radial spokes 132 coupled to the inner annular flange 104a, and a connecting element 134 linking the outer and inner radial spokes 130, 132.
  • An enclosed channel 136 is defined by the inner annular flange 104a, the two inner radial spokes 132, and the connecting element 134 of each connecting member 128.
  • the array of sensor modules 116 utilized with the load sensing bearing 100e preferably includes two displacement sensor modules 138a and 138c arranged on the Z-axis over the gap 114 between the inner and outer annular flanges 104a, 104b, and two displacement sensor modules 138b and 138d arranged on the X-axis over the gap 114 between the inner and outer annular flanges 104a, 104b.
  • the set of sensor modules 116 as a whole provides measurements which are representative of the applied forces (Fx, Fy, Fz) and applied moments (Mx and Mz), as previously described.
  • FIGs 7A and 7B illustrate a variation of the embodiment of the load sensing bearing assembly 100e shown in Figures 6A and 6B, in which a tab 142 extends radially inward from the outer annular flange 104a between each anisotropic spring region 112.
  • Each tab 142 provides an attachment point for a displacement sensor 138 in an array of sensor modules 116, reducing the width of the gap 114 over which each displacement sensor 138 is disposed.
  • the array of sensor modules 116 includes four displacement sensor modules 138a', 138b', 138c', and 138d' disposed on the radial centerlines of the connecting members 128, between the inner annular flange 104a and the connecting elements 134 over the enclosed channels 136.
  • the set of sensor modules 116 as a whole provides measurements which are representative of the applied forces (Fx, Fy, Fz) and applied moments (Mx and Mz), as previously described.
  • the array of sensor modules 116 includes eight strain sensor modules 140a through 14Oh disposed on the connecting elements 134 of the connecting members 128, on opposite sides of the outer radial spokes 130.
  • the set of sensor modules 116 as a whole provides measurements which are representative of the applied forces (Fx, Fy, Fz) and applied moments (Mx and Mz), as previously described.
  • Figures 8A and 8B illustrates at 100g a variation of the embodiment of the load sensing bearing assembly 100f shown in Figures 7A and 7B, in which one of the tabs 142 is eliminated, and the array of sensor modules 116 is altered.
  • a single sensor module 116a is radially aligned with the Z- axis between the inner annular flange 104a and a tab 142 over the gap 114
  • a second sensor module 116b is radially aligned with the X-axis between the inner annular flange 104a and a second tab 142 over the gap 114.
  • a speed sensor module 144 is coupled to the inner annular flange 104a and bearing outer race or cup 102 on the X-axis of the load sensing bearing assembly 100g, opposite from the second sensor module 116b.
  • This alternate arrangement and type of anisotropic spring regions 112 coupled with the arrangement of sensor modules 116a, 116b, and 144 provides a set of sensor signals that can be used to calculate the values of the three forces, Fx, Fy, and Fz, and two moments, Mx and Mz, acting on the bearing outer race or cup 102, together with the bearing outer race or cup rotation speed.
  • FIGs 9A and 9B illustrate an alternate embodiment of the load sensing bearing assembly 100 of the present invention, indicated generally at 100h, in which each anisotropic spring region 112 comprises a single radial spoke 146 coupling the inner annular flange 104a and the bearing outer race or cup 102 to the outer annular flange 104b and application structure 106.
  • Each spoke 146 is equidistantly disposed about the Y-axis of the load sensing bearing assembly 100h, such as shown in Figure 9A, in which four spokes 146 are illustrated.
  • the spokes permit limited displacement and rotation of the inner annular flange 104a and bearing outer race or cup 102 relative to the outer annular flange 104b and application structure 106, in much the same manner as similar anisotropic spring region structures previously described.
  • the set of sensor modules 116 includes a first sensor module 116a radially aligned with the Z-axis between the inner annular flange 104a and a tab 142 over the gap 114, a second sensor module 116b radially aligned with the X-axis between the inner annular flange 104a and a second tab 142 over the gap 114, and a third sensor module 116c radially aligned with the Z-axis between the inner annular flange 104a and a tab 142 over the gap 114, opposite from the first sensor module 116a.
  • a speed sensor module 144 is coupled to the inner annular flange 104a and bearing outer race or cup 102 on the X-axis of the load sensing bearing assembly 100h, opposite from the second sensor module 116b.
  • This alternate arrangement and type of anisotropic spring regions 112 coupled with the arrangement of sensor modules 116a, 116b, 116c, and 144 provides a set of sensor signals that can be used to calculate the values of the three forces, Fx, Fy, and Fz, and two moments, Mx and Mz, acting on the bearing outer race or cup 102, together with the bearing outer race or cup rotation speed.
  • Figures 10A and 10B illustrate a variation on the embodiment shown in Figures 9A and 9B, in which the speed sensor module 144 is replaced with a fourth sensor module 116d radially aligned with the X-axis between the inner annular flange 104a and a tab 142 over the gap 114, opposite from the second sensor module 116b.
  • a first channel 148 is formed across the width of one face of the spoke 146
  • a second channel 150 is formed across the width of the opposite face of the spoke 146, radially displaced outward from the first channel 148.
  • the first and second channels 148, 150 define an "S" shaped region within the structure of the spoke 146.
  • This structure permits limited displacement and rotation of the inner annular flange 104a and bearing outer race or cup 102 relative to the outer annular flange 104b and application structure 106, in much the same manner as similar anisotropic spring region structures previously described.
  • This alternate structure and arrangement of sensor modules 116a, 116b, 116c, and 116d provides a set of sensor signals that can be used to calculate the values of the three forces, Fx, Fy, and Fz, and two moments, Mx and Mz, acting on the bearing outer race or cup 102.
  • FIGs 11A and 11B illustrate an alternate embodiment of the load sensing bearing assembly 100 of the present invention, indicated generally as 100j, in which an annular anisotropic spring region 152 is disposed between the bearing outer race or cup 102 with inner annular flange 104a, and the outer annular flange 104b attached to the application structure 106.
  • the annular anisotropic spring region 152 includes a set of four axially aligned, equidistantly disposed, slots 154a-154d passing through the flange assembly 104 parallel to the Y-axis.
  • Slots 154a and 154c are perpendicular & ' to the Z- axis, while slots 154b and 154d are perpendicular to the X-axis of the load-sensing bearing 100j.
  • Each slot 154a-154d is filled with a soft or elastomeric fill 156.
  • a set of sensor modules 116 is disposed about the annular anisotropic spring region 152, with at least one sensor module 116 centrally disposed within each slot 154a-154d.
  • the sensor modules 116 may each comprise at least one displacement and/or rotation sensor, or may include strain sensors sufficient to provide signals used to calculate the values of the three forces, Fx, Fy, and Fz, and two moments, Mx and Mz, acting on the bearing outer race or cup 102.
  • FIGS 12A and 12B illustrate an alternate embodiment of the load sensing bearing assembly 100 of the present invention, indicated generally as 100k, in which the flange assembly 104 is not annular, but instead comprises a series of four equidistantly spaced flange protrusions 158 that extend radially outward from the bearing outer race or cup 102 and define the anisotropic spring regions 112.
  • the load sensing bearing assembly 100k is secured to an application structure 106 by seating each of the flange protrusions 158 within a receiving notch 160 in the application structure.
  • a bolt 108 is passed through a bolt hole 110 in an overlapping retaining clip 162, and coupled the application structure 106.
  • each of the flange protrusions 158 is provided with a slot 164 within which is disposed a sensor module 116.
  • the sensor modules 116 may each comprise at least one displacement and/or rotation sensor, or may include strain sensors sufficient to provide signals used to calculate the values of the three forces, Fx, Fy, and Fz, and two moments, Mx and Mz, acting on the bearing outer race or cup 102.
  • FIGS 13A and 13B illustrate an alternate embodiment of the load sensing bearing assembly 100 of the present invention, indicated generally at 1001, in which the bearing outer race or cup 102 is generally integrated with the flange assembly 104.
  • the flange assembly 104 is substantially rectangular in shape, with truncated corners 166 and inwardly offset sides 168.
  • Bolt holes 110 adjacent the truncated corners 166 of the flange assembly 104 receive bolts 108 for attachment of the load sensing bearing assembly 1001 to the application structure 106.
  • the load sensing bearing assembly 1001 is received within an oversize opening 170 within the application structure 106.
  • the void between the load sensing bearing assembly 1001 and application structure 106 can be filled with a soft elastomeric material 172 for sealing purposes.
  • the regions between the bolt holes 110 and the bearing outer race or cup 102 of the load sensing bearing assembly 1001 define the anisotropic spring regions 112.
  • a set of sensor modules 116 are disposed between each of the offset sides 168 of the flange assembly 104 and the application structure 106.
  • the sensor modules 116 may each comprise at least one displacement and/or rotation sensor, or may include strain sensors sufficient to provide signals used to calculate the values of the three forces, Fx, Fy, and Fz, and two moments, Mx and Mz, acting on the bearing outer race or cup 102.
  • FIGS 14A and 14B illustrate an alternate embodiment of the load sensing bearing assembly 100 of the present invention, indicated generally as 100m, in which the anisotropic spring regions 112 are substantially formed by four equidistantly spaced radial mounting posts 174 that protrude from the bearing outer race or cup 102.
  • the four mounting posts 174 have a generally rectangular cross-section, defining four side surfaces 176, and include bolt holes 110 through an axially raised surface 178 for receiving bolts 108 to secure the bearing assembly 100m to the application structure 106.
  • a set of sensor modules 116 are disposed on the side surfaces 176 of at least one of the mounting posts 174 between the bearing outer race or cup 102 and the application structure 106.
  • the set of sensor modules 116 comprises a sufficient number of displacement and/or strain sensors positioned to provide signals used to calculate the values of the three forces, Fx, Fy, and Fz, and two moments, Mx and Mz, acting on the bearing outer race or cup 102.
  • FIGS 15A through 15C illustrate an alternate embodiment of the load sensing bearing assembly 100 of the present invention, indicated generally at 100n, in which the flange assembly 104 is in the form of an annular member 180 integral with the bearing outer race or cup 102 and coupled to the application structure 106 via bolts 108 passed through bolt holes 110.
  • the load sensing bearing assembly 100n can include a ring of elastomeric material 172 fitted into an annular space between the bearing outer race or cup 102 and the application structure 106 for sealing purposes.
  • the anisotropic spring regions 112 permit limited displacement and rotation of the bearing outer race or cup 102 relative to the application structure 106.
  • the anisotropic spring regions 112 within the load sensing bearing assembly 100n are each defined by a set of slots 182 equidistantly spaced through the annular member 180, at a common diameter from the Y-axis of the load sensing bearing assembly 100n, radially disposed between the bearing outer race or cup 102 and the bolt holes 110.
  • a set of sensor modules 116 comprising a plurality of displacement sensor modules 138 and/or a plurality of strain sensor modules 140 is disposed within the anisotropic spring regions 112.
  • Each displacement sensor module 138 is positioned across the radial centerline of each slot 182 on a front face 184 of the annular member 180.
  • a strain sensor module 140 is disposed on each side of the bolt holes 110, approximately aligned with each end of the adjacent slots 182, and on a common circumference with the bolt holes 110, as best seen in Figure 15C with reference to Figure 15A.
  • This alternate arrangement and type of anisotropic spring regions 112, coupled with the set of sensor modules 116 provides a set of sensor signals that can be used to calculate the values of the three forces, Fx, Fy, and Fz, and two moments, Mx and Mz, acting on the bearing outer race or cup 102.
  • Figure 1A through Figure 15C illustrate various embodiments of the load sensing bearing assembly 100 with cyclic symmetry every 90 degrees in the circumferential direction about the Y-axis (i.e., four cycles around the circumference)
  • other cyclic symmetries are possible, such as, but not limited to, 120 degrees (i.e., three cycles around the circumference), 60 degrees (i.e., six cycles around the circumference), and 45 degrees (i.e., eight cycles around the circumference).
  • bearing outer race or cup 102 and flange assembly 104 in the various exemplary embodiments shown herein are parts generally separate from the application structure 106 upon which the load sensing bearing assembly 100 is mounted, the bearing outer race or cup 102, anisotropic spring regions 112, 152 and the flange assembly 104 may be integrally formed with the application structure 106 within the scope of the present invention.
  • each individual sensor module 116 within a set of sensors modules for the various illustrated embodiments may contain either a single sensor unit or a multitude of sensors units to detect various types of information, including without limitation: strain, displacement, rotation, or temperature, as necessary to provide sufficient information to determineat least one of the forces Fx, Fy, Fz and moment forces Mx and Mz acting on the load sensing bearing assembly 100.
  • the sensor units included within the set of sensors modules may optionally be used to monitor vibration and temperature for condition monitoring.
  • one or more temperature sensor units may be included within the set of sensor modules 116, preferably in close proximity to a strain, displacement, or other sensor units, to provide temperature information to compensate for thermal effects on the strain, displacement, or other sensors units.
  • strain sensors such as, but not limited to, resistive, optical sensors, capacitive sensors, inductive sensors, piezoresistive, magnetostrictive, MEMS, vibrating wire, piezoelectric, and acoustic sensors are suitable and may be used within the scope of the invention.
  • quarter-bridge, half-bridge, or full bridge sensors units which are well known in the art, may be used.
  • the specific locations of the sensor modules illustrated in the various embodiments of the present invention may be adjusted to some extent. Due to the adjustable nature of the signal processing software used to translate the sensor signals into the three forces, two moments, optional temperature signals and/or optional speed signals, minor adjustments or misalignments in the placement of sensor modules can be compensated for by adjusting parameters within the analyzing software.
  • an X-axis, a Y-axis, and a Z-axis have been identified in relation to the longitudinal axis of the load-sensing bearing assembly 100. These axes are for the description of the load-sensing bearing assembly embodiments and do not dictate or require any specific orientation of the present invention.
  • the axial centerline of the load-sensing bearing 100 may be in any direction as long as the general relationship between the anisotropic spring regions, sensor modules, flange assembly, and bearing outer race or cup are maintained as described within each of the above embodiments.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Force Measurement Appropriate To Specific Purposes (AREA)

Abstract

L'invention porte sur un ensemble palier capteur de charge (100) comprenant une bague externe ou coupelle (102) fixée à une structure d'application (106) par un ensemble bride (104) comprenant une pluralité de régions de ressort anisotropes (112) qui autorisent une plage limitée de déplacement et/ou de rotation de la bague externe de roulement ou coupelle (102) par rapport à la structure d'application (106) en réaction aux forces ou moments appliqués. Un ensemble de modules de capteur (116) introduit dans la bague externe de roulement ou coupelle (102) et l'ensemble bride (104) peut obtenir des mesures à partir desquelles on peut déterminer les forces radiales, les forces de poussée et les moments d'inclinaison exercés sur la bague externe de roulement ou coupelle (102).
EP06814176A 2005-09-06 2006-09-06 Palier capteur de charge Withdrawn EP1922495A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US11/219,933 US7240570B2 (en) 2005-09-06 2005-09-06 Load-sensing bearing
US72915405P 2005-10-21 2005-10-21
PCT/US2006/034579 WO2007030461A1 (fr) 2005-09-06 2006-09-06 Palier capteur de charge

Publications (1)

Publication Number Publication Date
EP1922495A1 true EP1922495A1 (fr) 2008-05-21

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP06814176A Withdrawn EP1922495A1 (fr) 2005-09-06 2006-09-06 Palier capteur de charge

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EP (1) EP1922495A1 (fr)
JP (1) JP2009507244A (fr)
WO (1) WO2007030461A1 (fr)

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Publication number Priority date Publication date Assignee Title
EP2414704B8 (fr) 2009-03-30 2013-10-16 TQ-Systems GmbH Engrenage, unite moteur-engrenage, et element de transmission de force
FR2947643B1 (fr) * 2009-07-06 2011-08-19 Renault Sa Systeme de commande pour machine tournante a roulement instrumente
WO2012123010A1 (fr) * 2011-03-11 2012-09-20 Aktiebolaget Skf Dispositif pour renfermer un palier comportant un système pour détecter la charge appliquée au palier
WO2014147583A1 (fr) 2013-03-20 2014-09-25 Tq-Systems Gmbh Démultiplicateur harmonique à couronne de broches
WO2015060836A1 (fr) 2013-10-23 2015-04-30 Halliburton Energy Services, Inc. Détection d'usure d'élément d'étanchéité pour dispositifs de puits de forage
JP6724751B2 (ja) * 2016-09-13 2020-07-15 日本精工株式会社 センシング装置付ホイール
DE102016122845A1 (de) 2016-11-28 2018-05-30 Tq-Systems Gmbh Harmonisches Pinring-Getriebe, Drehmomentmessvorrichtung und Freilaufanordnung
JP6987676B2 (ja) * 2018-03-08 2022-01-05 日本電産コパル電子株式会社 トルクセンサ
JP7091545B2 (ja) * 2018-03-08 2022-06-27 日本電産コパル電子株式会社 トルクセンサ
EP3803153B1 (fr) 2018-05-31 2023-07-19 TQ-Systems GmbH Engrenage avec moyen de traction
DE102019216992A1 (de) * 2019-11-05 2021-05-06 Aktiebolaget Skf Lagereinheit mit zumindest zwei Arten von Messfühlern, die an einem Gehäuse befestigt sind

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GB1012210A (en) * 1961-11-08 1965-12-08 Davy & United Eng Co Ltd Improvements in or relating to rolling mills
JPS62263434A (ja) * 1986-05-09 1987-11-16 Yamato Scale Co Ltd 実車測定装置
JPH01269722A (ja) * 1988-04-22 1989-10-27 Toshiro Higuchi 磁気制御軸受ユニット
US5140849A (en) 1990-07-30 1992-08-25 Agency Of Industrial Science And Technology Rolling bearing with a sensor unit
US7669941B2 (en) * 2005-05-12 2010-03-02 The Timken Company Wheel end with load sensing capabilities

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Also Published As

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WO2007030461A1 (fr) 2007-03-15
JP2009507244A (ja) 2009-02-19

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