Abstract:
A device includes at least one magnetic field generator placed on a first plane of a right section of a shaft and at least one magnetic field detector placed in a second plane of a right section of the shaft. The detector produces a signal proportional to the torque following the relative angular shift of the field generator in relation to the detector, the magnetic field generator having a magnetic structure supported by support mechanisms connected to the turning shaft. The magnetic field detector is located roughly opposite the magnetic field generator and is supported by support mechanisms connected to the turning shaft.

Description:
This invention relates generally to the technical field of torque sensors and, more particularly, to a device for measuring the torque applied to a shaft. 
     In order to measure the torque imparted between two turning parts, elastically deforming torque meters are generally used. The deforming element frequently consists of a torsion bar. In order to prevent warp torsion and a concentration of stresses that may affect resistance to fatigue, torsion bars on torque meters are usually circular in cross section. For any given material, in isotropic linear elasticity, the angle of torsion θ equals, in pure torsion:        θ   =       32                 ML       π                   D   4        G                              
     where 
     D is the outer diameter of the bar, whether hollow or solid; 
     M is the torque applied to the torsion bar; 
     G is the crosswise modulus of elasticity; and 
     L is the working length of the bar. 
     Thus, given the material and geometry of a specific bar, it is possible to link the torsion angle to the torque applied to the bar. 
     Torsion bar torque meters are described in the following documents: FR-2 705 455, GB-2 306 641, WO-87/02319, WO-92/20560, WO-95/19557. WO-96/06330, WO-97/08527, WO-97/09221, EP-325 517, EP-369 311, EP-286,053, EP-437 437, EP-418 763, EP-453 344, EP-515 052, EP-555 987, EP-562 426, EP-566 168, EP-566 619, EP-638 791, EP-673 828, EP-681 955, EP-728 653, EP-738 647, EP-738 648, EP-765 795, EP-770 539, EP-802 107. 
     The primary methods for measuring the torque of a turning shaft, whether including the use of a torsion bar or not, are as follows: 
     methods based on electromagnetic phenomena 
     optical methods 
     electrical methods. 
     Magnetic methods are based essentially on the use of magnetostriction and the Hall effect. 
     Magnetostriction is understood to be a reversible mechanical deformation that accompanies a magnetic variation of a ferromagnetic solid. This phenomenon is reversible; that is, a deformation of a ferromagnetic material placed in a magnetic field causes a variation in magnetism (inverse magnetostriction). Examples of magnetostrictive detectors that measure torque by measuring variations in permeability of a magnetically anisotropic field are described in the following documents: EP-229 688, EP-261 980, EP-270 122, EP-288 049, EP-309 979, EP-321 662, EP-330 311, EP-338 227, EP-384 042, EP-420 136, EP-422 702, EP-444 575, EP-502 722, EP-523 025, EP-562 012, and EP-651 239. 
     The Hall effect is conventionally understood to be the generation of a normal magnetic field at the current density vector in a conductor or semiconductor located in a normal magnetic induction field at the current density vector. Torque sensors that operate using the Hall effect, are described in the following documents: FR-2,689,633, and FR-2,737,010. 
     Optical methods for measuring torque are essentially associated with interference phenomena or a measurement of optical density. Reference to these methods may be found, for example, in the following documents: EP-194 930, EP-555 987, U.S. Pat. Nos. 5,490,450, 4,676,925, 4,433,585, 5,001,937, 4,525,068, 4,939,368, 4,432,239, FR-2 735 232, FR-2 735 233, and WO-95/19557. 
     Electric torque measuring methods are associated essentially with capacitative measurement or measurement of a phase difference between two magnetic encoders mounted circumferentially on the torsion axis. Documents EP-263 219, EP-352 595, EP-573 808 describe devices to measure torque by extensiometric or stress gauges. Document EP-442 091 describes a mechanism to measure the angle of rotation or torque of a rotating or fixed element on a machine, which includes a torsion element in the shape of a wheel with spokes connected to various measuring devices, at least one spoke of the spoked wheel being cut so that the parts of the spoke or spokes are applied against one another after shifting caused by a predetermined bending of the other spokes. The measurement device employs Foucault currents. 
     The foregoing illustrates limitations known to exist in present devices and methods. Thus, it is apparent that it would be advantageous to provide an alternative directed to overcoming one or more of the limitations set forth above. Accordingly, a suitable alternative is provided including features more fully disclosed hereinafter. 
     SUMMARY OF THE INVENTION 
     In one aspect of the invention, this is accomplished by providing a device to measure torque on a turning shaft, the measuring device comprising at least one magnetic field generator placed in a first plane of a right section of the shaft, and at least one magnetic field detector placed in a second plane of a right section of the shaft. The detector produces a signal proportional to the torque producing a relative angular shift of the field generator in relation to the detector. The magnetic field generator is supported by support means connected to the turning shaft, the magnetic field detector is located roughly opposite the magnetic field generator and is supported by support means connected to the turning shaft. 
     The foregoing and other aspects will become apparent from the following detailed description of the invention when considered in conjunction with the accompanying drawing figures. 
    
    
     BRIEF DESCRIPTION OF THE DRAWING FIGURES 
     FIG. 1 is a perspective view of a hub with a bending test body illustrating one embodiment of the present invention; 
     FIG. 2 is a front view of the hub with a bending test body of FIG. 1; 
     FIG. 3 is a front view of a hub with a bending test body illustrating another embodiment of the present invention; 
     FIG. 4 is a front view of a hub with a bending test body provided with stop beams illustrating another embodiment of the present invention; 
     FIG. 5 is a cross sectional view along line V—V of FIG. 4; 
     FIG. 6 is a front view of a hub with a bending test body illustrating another embodiment of the present invention; 
     FIG. 7 is a cross sectional view along line VII—VII of FIG. 6; 
     FIG. 8 is a cross sectional view along line VIII—VIII of FIG. 6; 
     FIG. 9 is a perspective view of a hub with a bending test body illustrating another embodiment of the present invention; 
     FIG. 10 is a front view of the hub with a bending test body of FIG. 9; 
     FIG. 11 is a cross sectional view along line XI—XI of FIG. 10; 
     FIGS. 12,  13 , and  14  are front views of hubs with bending test bodies illustrating other embodiments of the present invention; and 
     FIG. 15 is a schematic drawing in perspective of a Hall effect sensor designed to be integrated in a hub as illustrated in FIGS. 1 through 14, according to one embodiment of the present invention. 
    
    
     DETAILED DESCRIPTION 
     Referring now to the drawings, FIG. 1 illustrates a hub with a bending test body, in perspective, designed to be integrated between a drive mechanism on a drive shaft and the drive shaft, or between a driving shaft and a drive shaft. Hub  1  includes cylindrical inner ring  2  and two outer rings  3   a ,  3   b  connected to inner ring  2  by elastically bending beams  4   a  and nondeforming beams  5 . 
     More precisely, the outer ring  3   a , to be fixed on a drive mechanism of a drive shaft by screws or the like passing through holes  6 , is connected to the inner ring by means of elastically bending beams  4   a . Outer rings  3   a ,  3   b  are, in this embodiment, roughly coaxial and of the same average diameter. In this embodiment, there are four deformable beams  4   a  evenly distributed circumferentially and directed perpendicularly to axis D of the drive shaft. In other embodiments, not illustrated, there may be two, three, or more than four of these deformable beams. 
     Outer ring  3   b  is connected to inner ring  2  by means of nondeforming radial beams  5 . In the illustrated embodiment, there are as many nondeforming beams  5  as there are elastically bending beams  4   a , beams  4   a  and  5  being generally located along two radial planes that are perpendicular to the axis of drive shaft D. In other embodiments, not shown, there may be two, three, or more than four beams  5 , while there are four beams  4   a . In certain embodiments, not shown, the number of beams  4   a  is not equal to four and not equal to the number of beams  5 . In other embodiments, not shown, the number of beams  4   a  is equal to the number of beams  5 , and that number is not equal to four. In yet other embodiments, not shown, outer ring  3   b  is connected to inner ring  2  by means of a ring-shaped web. 
     Beams  4   a ,  5  may be positioned directly above one another, as shown, on common radial planes. In other embodiments, not shown, beams  5  may be positioned on radial planes that are shifted in relation to the radial planes of beams  4   a . Outer deformable ring  3   a  of hub  1  is rigidly connected to the drive shaft drive mechanism, using screws or any equivalent fastener through holes  6  on attachment feet  7 . In a variant, the hub with the bending test body may form a single unit with the drive mechanism on the drive shaft, made of the same material as the latter, for example, or welded to it using any appropriate method. 
     When the drive shaft drive mechanism exerts force on outer ring  3   a , it causes beams  4   a  to bend in deformation, which deformation is stronger the more torque stress is imparted to the drive shaft. Outer ring  3   b  remains generally stress-free. Its position may, therefore, serve as a reference point for purposes of measuring the shift of outer ring  3   a . Outer ring  3   b  carries sensors  8  capable of measuring small shifts on the order a few microns or hundreds of microns. In the illustrated embodiment, there are two of these sensors  8  located in axially aligned housings  9  provided in outer ring  3   b  adjacent to outer ring  3   a.    
     Sensors  8  are Hall effect or magnetoresistant sensors. While a single Hall effect sensor would suffice to measure small angular shifts, it is possible for reasons of reliability to place more sensors in measurement air gap  10  in order to achieve redundancy. Each sensor may have its own electronic circuit. By comparing or combining the signals emitted by two, three, or four different sensors, it is possible to detect the possible failure of one sensor and thereby ensure reliability of the torque meter. 
     A second embodiment of hub  1  with a bending test body is illustrated in FIG.  3 . Like the hub that was just described, hub  1  represented in FIG. 3 includes deformable outer ring  3   a , stress-free outer ring  3   b , inner ring  2 , deformable beams  4   a  connecting ring  3   a  to inner ring  2 , and nondeformable beams  5  connecting ring  3   b  to inner ring  2 . In the embodiment of FIG. 3, the hub has four beams  4   a  whose cross section varies from base  11  to head  12  of the beams. In other embodiments, the hub includes one, two, three, or more than four beams whose cross section varies from the base to the head. 
     This variation of the cross section of the beams may be regular or otherwise. This variation may be connected to a variation in the width of the beam and/or to a variation in the thickness of the beam. Thickness h of the beam is measured tangentially to a circle whose center is axis D of the drive shaft. In the embodiment of FIG. 3, this thickness h varies at a generally linear rate. In other embodiments, not shown, thickness h varies at a polynomial rate, or logarithmically, whether constantly or not, the farther one moves from axis D of the drive shaft. Width b of beams  4   a , measured along direction D, is generally constant in the mode of embodiment shown in FIG.  3 . In other modes of embodiment, not shown, width b may vary at linear or polynomial rates, the height h also being capable of variation. 
     FIG. 4 is a front view illustrating a hub with a bending test body equipped with stop beams  13 . In the illustrated embodiment, two stop beams  13  run radially in a crosswise direction T from inner ring  2  to outer deformable ring  3   a . The length L of stop beams  13  is less than that of deformable beams  4   a , the end of each stop beam  13  being inserted, with predetermined play, into deformation stop  14 . Deformation stops  14  project inward from outer ring  3   a  and include groove  15 , whose width  1  is greater than the width  1 ′ of stop beams  13 . The play between the stops and beams  13 , which relates to the difference in widths  1 - 1 ′, may be determined as a function of the maximum allowable deformation of beams  4   a , for example, to prevent their plastic deformation. 
     FIGS. 6,  7  and  8  illustrate another embodiment of hub  1  with bending test body. In this embodiment, width b of deformable beams  4   a  decreases from base  11  to head  12  of the beams. This decrease may be linear or polynomial. The number of deformable beams  4   a , the angular distribution, thickness, and height of the beams and the material used to make them, as will be clear to an expert in the art, will affect the inertia module and the maximum stress on the beams for a given maximum torque, at breaking point for example. 
     The test body may be made of a material chosen from among the group that includes steel, cast iron, aluminum alloys, and magnesium alloys. The test body may be cast or tooled depending upon the materials used, the geometry of the beams, and acceptable costs, as may be determined by an expert in the art. When the test body is made of aluminum or a magnesium alloy, the latter may be cast with a metal insert that has grooves for mounting hub  1  on the drive shaft. 
     FIGS. 9 through 11 illustrate another embodiment of a hub with a torsion test body. Hub  1  consists of stress-free outer ring  3   b  whose outer edge is generally cylindrical in shape. This ring  3   b  is equipped with two housings  9  located in two diametrically opposed projections  16 . Between these projections  16  the inner surface of ring  3   b  is generally cylindrical. Ring  3   b  is attached to inner ring  2  by means of a beam  5 , a web, or any other generally rigid attachment. 
     In this embodiment, two radial beams  5  made of the same material as inner ring  2  and outer stress-free ring  3   b  connect the two rings  2 ,  3   b . The cross section of beams  5  is, in this embodiment, square and generally constant from base  11  to head  12 , and the beams  5  are roughly aligned. Inner ring  2  has a bore running through it that defines splined adapter  17  for attachment to the drive shaft and, at the opposite end, support surface  18  for the grooved drive shaft. Torsion-deforming tube  4   b  connects the inner ring to outer deformable ring  3   a . In one embodiment, the torsion-deforming tube is open lengthwise, the openings running in the direction of D and separating the bending, torsion-deforming beams. 
     Deformable ring  3   a  is rigidly attached to the mechanism that imparts torque to the drive shaft. Screws or comparable fasteners through holes  6  attach hub  1  to the mechanism that imparts torque to the drive shaft. When hub  1  is rigidly attached to the mechanism that imparts torque to the drive shaft, outer deformable ring  3   a  attached to the torque-imparting mechanism shifts in rotation in relation to outer stress-free ring  3   b . The measurement of this small shift by means of Hall effect or magnetoresistant sensors placed in housings  9  and magnets  8 ′ attached to support plate  19  connected to the drive shaft, permits measurement of the torque applied to the drive shaft. 
     FIG. 12 illustrates another embodiment of a hub with a bending test body. In this embodiment, the elastically deformable mechanisms connecting inner ring  2  and outer deformable ring  3   a  are in a serpentine shape. The serpentines form several elbows  20  separated by sections that are in the general shape of concentric circular arcs  21 . The serpentines run generally along the same plane perpendicular to the axis D of the drive shaft. The thickness of each serpentine is, in this embodiment, generally constant from base  22  to head  23  of the serpentine. In other embodiments, not shown, there are two, three, or more than four serpentines. The thickness of at least one serpentine may vary from its base to its head, as required. 
     FIGS. 13 and 14 are front views of a hub with a bending test body that comprises more than four deformable beams, in this case twelve beams distributed evenly and radially around axis D. From the starting point of the test body represented in FIG. 13, it is possible to obtain the test body shown in FIGS. 14, whether by tooling or using another comparable method, which has only ten deformable beams of which four act as stops upon application of torque exceeding a given threshold level. The stop is achieved, regardless of the rotation direction required of the transmission shaft, upon reaching a torque threshold value, whereupon end  24  of stop beams  25  comes into contact with the inner projection of nondeforming outer ring  3   b.    
     Depending upon the radial angular positioning of stop beams  25 , the maximum admissible torque in a clockwise direction H may be greater than, equal to, or less than the maximum admissible torque in a counterclockwise direction AH. In certain embodiments, the bending-deforming beams described above are cut. When torque is applied, only the beams that are not cut into two sections impart stress, while the sections of cut beams only impart bending stress when an applied torque exceeds a given threshold. The two sections of a cut beam, in one embodiment, are located a given lengthwise distance from one another as a function of the torque threshold value. 
     In one embodiment, the beam is cut at an angle of approximately 45 degrees in relation to the radial direction of the beam in question. Depending upon the number and positioning of the set of beams, by cutting at least one deformable beam  4   a  it may be possible, in particular, either to obtain protection against any overloads in both possible rotation directions, or to obtain a torque meter with several ranges of torque measurement, the rigidity of the torque meter increasing as more beams are subject to stress. 
     FIG. 15 is a perspective view of sensor  8  according to one embodiment. Sensor  8  comprises cylindrical body  26  made of a ferromagnetic material, and magnetic detector  27  designed to be positioned opposite a magnetic field generator such as magnet  8 ′. Sensor  8  includes, facing magnetic detector  27 , stop piece  28  that limits the axial movement of sensor  8  in housings  9 . Magnetic detector  27  has sensitive element  29  that is eccentric to the circular cross section of sensor  9  so that the rotation of sensor  8  on axis O z  produces a shift on axis O x  of sensitive element  29 . 
     During factory installation of sensors  8 , the operator completes assembly by using appropriate equipment to measure the signal produced by the two sensors  8 . This signal is a function of the position of sensitive element  29  vis-a-vis magnetic transition, so that by turning sensor  8  the operator may bring sensitive element  29  opposite the magnetic transition of the magnetic field generator and thereby neutralize the signal. Once this adjustment is made, the sensors are immobilized, with an adhesive for example. This adjustment is referred to as adjustment by eccentricity. 
     The strength of the signal produced by each magnetic detector  27  may also be modulated by modifying the axial penetration of sensors  8  in housings  9  in such a way as to alter the air gap between detector  27  and opposing magnet  8 ′. In one mode of embodiment of sensor  8  represented in FIG. 15, the minimum air gap is determined by the space formed by stop  28  which is flattened against the front face of the projections on nondeformable ring  3   b . The torque meter is calibrated, for example, by applying a calibrated load and adjusting the signal amplification level. 
     In another embodiment, an electronic circuit connected to the test body consists of: 
     a current input to supply power to the Hall effect sensors; 
     a circuit to filter the signal produced by the sensors in order to eliminate any background noise; 
     a module to convert the signal from analog to digital; 
     a module to control and compensate for any drift in the signal transmitted by the sensors caused by temperature, for example in the range of −40 to −80 degrees C; and 
     a safety module that regularly tests the proper functioning of each sensor. 
     If necessary, the electronic circuit may include a module that makes it possible to set a power steering triggering threshold, a given value threshold, or even a module for wireless or no-contact signal transmission. The electronic circuit may be attached by gluing it, for example, to the front face of nondeforming ring  3   b.