WO2001067060A2

WO2001067060A2 - Multi-axis load cell

Info

Publication number: WO2001067060A2
Application number: PCT/US2001/006767
Authority: WO
Inventors: Richard A. Meyer; Jodi L. Sommerfeld; Douglas J. Olson; Alan J. Kempainen; David M. Burruss
Original assignee: Mts Systems Corporation
Priority date: 2000-03-03
Filing date: 2001-03-02
Publication date: 2001-09-13
Also published as: WO2001067060A3; AU2001240009A1

Abstract

A load cell (150) for transmitting forces and moments in plural directions includes a central hub (154), an annular ring (156) concentric with the central hub (154), and sensing structures (160) connecting the central hub (154) with the annular ring (156). In one embodiment, the sensing structures (160) include radial tubes (160). Each radial tube (160) has an outer surface (190) having a plurality of concave portions (196A, 196B, 198A and 198B). In another embodiment, the annular ring (156) includes spaced apart flanges (218A and 218B) that are adapted to support a tire.

Description

MULTI-AXIS LOAD CELL

BACKGROUND OF THE INVENTION The present invention relates to a load cell that transmits and measures linear forces along and moments about three orthogonal axes. More particularly, a compact load cell body is disclosed having a rigid central hub, a rigid annular ring concentric with the hub and radial members extending between the central hub and the annular ring.

Transducers or load cells for determining forces along and moments about three orthogonal axes are known. Two such load cells are disclosed in U.S. Patent Nos . 4,640,138 and 4,821,582. U.S. Pat. No. 4,640,138 illustrates a multiple axis load-sensitive transducer having inner and outer members that are joined by a pair of axially spaced spiders. The spiders comprise arms that are integral with the inner member and are connected to the outer member by flexible straps that have longitudinal lengths with the ends of the straps fixed to the outer member. The arms of the spiders are fixed to the center of the associated strap. Loads are sensed as a function of bending on the spider arms.

U.S. Pat. No. 4,821,582 illustrates a load transducer that measures linear forces in three axes and moments about two of the axes. The transducer has inner and outer structures connected by load-sensitive spider arms or shear beams . The outer ends of the spider are connected to outer lengths which are stiff when the inner structure is loaded in a direction along an axis perpendicular to the plane of the spider.

Other, more compact, load cells are described in United Kingdom Patent Application GB 2096777 A. These load cells include a central hub portion and an annular ring portion with four radial spoke portions connecting the hub and ring portions and having suitable strain gauges adhered thereon. A prior art load cell having this construction is discussed in GB 2096777 A but does not measure moments applied about axes extending through the spokes. United Kingdom patent application GB 2096777 A discloses solid spokes having trunk sections and end sections. Each end section has a "width" dimension that is less than the corresponding trunk section. The reduced width of each end section is sufficiently small to make it flexible with respect to a twisting force about the extending direction of the spoke.

There is an ongoing need to provide an improved compact load cell, which is easy to manufacture and measures components of force and moment in plural directions .

SUMMARY OF THE INVENTION A load cell for transmitting forces and moments in plural directions includes a central hub, an annular ring concentric with the central hub, and sensing structures connecting the central hub with the annular ring. In one embodiment, the sensing structures include radial tubes. Each tube has an outer surface having a plurality of concave portions. In another embodiment, the annular ring include spaced apart flanges that are adapted to support a tire. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a load cell. FIG. 2 is a side elevational view of a load cell with a portion removed to show a radial tube in section .

FIG. 3 is a side elevational view of the load cell with a portion removed to show an alternative radial tube in section.

FIG. 4 is a side elevational view of the load cell mounted to a tire rim illustrated in section. FIG. 5 is a top plan view of a second embodiment of a load cell.

FIG. 6 is a sectional view of the load cell of FIG. 5.

FIG. 7 is a top plan view of the second embodiment with a slip ring mounting plate and connectors .

FIG. 8 is a general block diagram of a controller .

FIG. 9 is a block diagram of a scaling and geometric transformation circuit.

FIG. 10 is a circuit diagram of a portion of a cross-coupling matrix circuit.

FIG. 11 is a block diagram of a coordinate transformation circuit. FIG. 12 is a side elevational view of the load cell with a portion removed to show an alternative radial tube in section.

FIG. 13 is a schematic diagram of a Wheatstone bridge . FIG. 14 is a top plan view of a third embodiment of a load cell .

FIG. 15 is a perspective view of the third load cell of FIG. 14.

FIG. 16 is a sectional view of the third load cell taken along lines 16--16 in Fig. 14.

FIG. 17 is a sectional view of a radial tube.

FIG. 18 is a top plan view of a wheel force transducer . FIG. 19 is a sectional view of the wheel force transducer .

FIG. 20 is a sectional view of a portion of the wheel force transducer. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

FIG. 1 illustrates a first embodiment of a load cell 10 of the present invention. The load cell 10 preferably includes an integral body 12 of the present invention fabricated from a single block of material . The body 12 includes a rigid central hub 14 and a rigid annular ring 16 that is concentric with the central hub 14. A plurality of radial tubes 20 join the central hub 14 to the annular ring 16. In the embodiment illustrated, the plurality of radial tubes 20 comprises four tubes 21, 22, 23 and 24. Each of the tubes 21-24 extend radially from the central hub 14 toward the annular ring 16 along corresponding longitudinal axes 21A, 22A, 23A and 24A. Preferably, axis 21A is aligned with axis 23A, while axis 22A is aligned with axis 24A. In addition, axes 21A and 23A are perpendicular to axes 22A and 24A. Although illustrated wherein the plurality of radial tubes 20 equals four, it should be understood that any number of tubes three or more can be used to join the central hub 14 to the annular ring 16. Preferably, the plurality of radial tubes 20 are spaced at equal angular intervals about a central axis indicated at 26.

Flexure members 31, 32, 33 and 34 join an end of each radial tube 21-24, respectively, to the annular ring 16. The flexure members 31-34 are compliant for displacements of each corresponding radial tube 21-24 along the corresponding longitudinal axes 21A-24A. In the embodiment illustrated, the flexure members 31-34 are identical and include integrally formed flexure straps 36 and 38. The flexure straps 36 and 38 are located on opposite sides of each longitudinal axis 21A-24A and join the corresponding radial tube 21-24 to the annular ring 16.

A plurality of strain sensors 40 are mounted on the plurality of tubes 20 to sense strain therein. Although the plurality of sensors 40 can be located on the plurality of radial tubes 20 to provide an indication of bending stresses therein, preferably the strain sensors are mounted conventionally to provide an output signal indicative of shear stresses in the walls of the plurality of radial tubes 20. In the embodiment illustrated, four sets of strain sensors are provided on each tube 21-24, preferably, approximately at the center of the longitudinal length of each tube. A first pair of strain sensors 44 is provided on an upwardly facing portion of each radial tube 21-24. A second pair of strain sensors, not shown, is mounted on a downwardly facing surface approximately 180 degrees from the first pair of strain sensors 44. The first and second pairs of strain sensors on each tube 21-24 are connected in a conventional Wheatstone bridge to form a first sensing circuit on each radial tube 21-24. A third pair of strain sensors 46 is mounted approximately 90 degrees from the first pair of strain sensors 44 while a fourth pair of strain sensors 48 is mounted approximately 180 degrees from the third pair of strain sensors 46. The third and fourth pairs of strain sensors on each tube 21- 24 are also connected in a conventional Wheatstone bridge to form a second sensing circuit on each radial tube 21- 24. Commonly, the plurality of sensors 40 comprise resistive strain gages. However, other forms of sensing devices such as optically based sensors or capacitively based sensors can also be used.

In the embodiment illustrated having four radial tubes 21-24, eight individual shear-sensing Wheatstone bridges are used. The number of sensing circuits can be increased or decreased, depending on the number of radial tubes used. However, at least three radial tubes are preferred.

Output signals from the strain sensors 40 are indicative of force and moment components transmitted between the central hub 14 and the annular ring 16 in six degrees of freedom. For purposes of explanation, an orthogonal coordinate system 47 can be defined wherein an X-axis is aligned with the longitudinal axes 21A and 23A; a Z-axis is aligned with the longitudinal axes 22A and 24A; and a Y-axis is aligned with the central axis 26.

In the embodiment illustrated, the load cell 10 measures eight forces on the plurality of tubes 20. The eight forces are then transformed to provide forces along and moments about the axes of the coordinate system 47. Specifically, force along the X-axis is measured as principal strains due to shear stresses created in the radial tubes 22 and 24 since the flexure members 31 and 33 on the ends of the radial tubes 21 and 23 are compliant in this direction. This can be represented as:

F^r ₂₂X + F ^r 24X

where the first sensing circuits having strain sensors 44 on tubes 22 and 24 provide the output signals.

Similarly, force along the Z-axis is measured as principal strains due to shear stresses created in the radial tubes 21 and 23 since the flexure members 32 and 34 on the ends of the tubes 22 and 24 are compliant in this direction. This can be represented as:

FZ = ^r F21Z + ^r F23Z

where the first sensing circuits having strain sensors 44 on tubes 21 and 23 provide the output signals.

Force along the Y-axis or central axis 26 is measured as principal strains due to shear stresses created in all of the radial tubes 21-24. This can be represented as:

F ^r = ^r F21 Y + ^Γ F22 Y ^r F22 Y + ^Γ F 24 Y

where the second sensing circuits having strain sensors 46 and 48 on tubes 21-24 provide the output signals. An overturning moment about the X-axis is measured as principal strains due to shear stresses created in the radial tubes 22 and 24 from the opposed forces applied thereto. The radial tubes 21 and 23 are substantially stiff for an overturning moment about the X-axis. This can be represented as: ^l M^lX = F ^C 22 Y - F ^r 2<k Y

where the second sensing circuits including strain sensors 46 and 48 on tubes 22 and 24 provide the output signals . Likewise, an overturning moment about the Z- axis is measured as principal strains due to shear stresses created in the radial tubes 21 and 23 from the opposed forces applied thereto. The radial tubes 22 and 24 are substantially stiff for an overturning moment about the Z axis. This can be represented by:

M_z - F_{21 Y} 23 Y

where the second sensing circuits including strain sensors 46 and 48 on the tubes 21 and 23 provide the output signals.

An overturning moment about the Y-axis is measured as principal strains due to shear stresses created in all of the radial tubes 21-24. This can be represented as : Y ⁼ '^■'-22A^{* ~"} ^ 24X' ⁺ '-^21Z ~ ^23 Z'

where the first sensing circuits including strain sensors 44 on tubes 21-24 provide the output signals. It should be understood that the number of strain sensors 40 and the number of sensing circuits can be reduced if measured forces and moments of less than six degrees of freedom is desired.

In a preferred embodiment, each of the radial tubes 21-24 include a plurality of spaced-apart wall portions of reduced thickness to concentrate stress therein. Referring to FIG. 2 and radial tube 23 by way of example, the radial tube 23 has a non-rectangular outer surface 60 wherein the wall portions of reduced thickness are indicated at 62A, 62B, 62C and 62D. The wall portions of reduced thickness 62A-62D are formed by a cylindrical bore 64 in the radial tube 23 and a first pair of parallel planar surfaces 66A and 66B facing in opposite directions and a second set of planar surfaces 68A and 68B also facing in opposite directions. The second set of planar surfaces 68A and 68B are substantially orthogonal to the first set of planar surfaces 66A and 66B such that the planar surfaces of the first set and the second set are alternately disposed about the corresponding longitudinal axis 23A. Although illustrated wherein the thickness of the portions 62A-62D are approximately equal, if desired, the thickness can be made different to provide desired sensitivity in selected directions. Preferably, the thickness of portion 62A should be approximately equal to portion 62C, and the thickness of portion 62B should be approximately equal to portion 62D.

The strain sensors 44 of the first sensing circuit are mounted on the first pair of parallel planar surfaces 66A and 66B, while the strain sensors 46 and 48 of the second sensing circuit are mounted on the second set of planar surfaces 68A and 68B. Planar mounting surfaces are preferred because measured output signals lower hysteresis and lower creep gage bonding due to uniform gage clamp pressure on flat surfaces versus curved mounting surfaces, which locks residue stress in gage. Also, alignment scribing and affixing of the gages to the scribed lines is more difficult on a curved surface. The non-rectangular outer surface 60 is also beneficial because this form concentrates stress in portions of the radial tube 23, which are proximate the strain sensors 40. Although a tube having a rectangular cross-section (four flat surfaces that intersect at the corners) can be used, significant stress concentration occurs at the intersection of the flat surfaces where strain sensors cannot be easily mounted. Thus, performance is substantially reduced. In contrast, the non-rectangular radial tube 23 illustrated in FIG. 2 includes planar surfaces 70A, 70B, 70C and 70D that extend between each planar surface of the first set and the successive planar surface of the second set . In a preferred embodiment, the planar surfaces 66A, 66B, 68A, 68B and 70A-70D preferably form an octagon in cross- section. Forming each of the radial tubes 21-24 with an octagonal outer surface 60 simplifies construction and reduces manufacturing costs since the planar surfaces can be easily machined. Although illustrated wherein one planar surface extends between each planar surface of the first set and successive surface of the second set, for example, planar surface 70A, it should be understood that a plurality of intervening planar surfaces can be used. Similarly, the flat planar surfaces 70A-70D can be replaced with curved wall portions 76A, 76B, 76C and 76D to form a non-rectangular radial tube 23' as illustrated in FIG. 3. Unlike a tubular structure having an annular wall of uniform thickness, the radial tube 23' also has spaced-apart portions of reduced wall thickness 62A-62D created by the flat surfaces 66A, 66B, 68A and 68B that concentrate stress therein similar to the octagonal cross -section .

The octagonal cross-section of radial tube 23 or the cross-section of radial tube 23 ' provides approximately 14% higher output (signal to noise ratio) and sensitivity than a tube with uniform annular wall thickness of the same area. This can be shown by comparing the shear stress created in the octagonal tube 23 versus a tube of uniform annular wall thickness.

The shear stress T at any point q in a beam is given by the following equation: T = ^VA'^Z> lb where V is the vertical shear at any section containing q, A' is the area of that part of the section above (or below) q, z' is the distance from the neutral axis to the centroid of A' and b is the net breadth of the section measured through q (herein two times the wall thickness of the tube) , and I is the moment of inertia.

For a octagonal tube having an inner bore radius of 0.650 inches, a minimum wall thickness (portions 62A-62D) of 0.150 inches and using a point q on the neutral axis, A' is approximately equal to 0.398 square-inches, z' is approximately equal to 0.471 inches, I is approximately equal 0.219 inches⁴ and b is approximately equal to 0.300 inches. Assuming a vertical shear force of 1,000 pounds, the shear stress for the octagonal tube is approximately 2,853 psi .

Assuming an inner bore radius of 0.650 inches (inner diameter equal to 1.300 inches) for a tube of uniform annular wall thickness, an outer diameter would equal 1.643 inches to have approximately the same area as the octagonal tube given above. For a point q on the neutral axis, the centroid z' is approximately equal to 0.471 inches, I is approximately equal to 0.218 inches⁴ and b is approximately equal to 0.343 inches. Assuming the same vertical shear force of 1,000 pounds, the shear stress for the tube with uniform annular wall thickness, as given by the equation above, approximately equals 2,504 psi. Shear stress concentration for the octagonal tube is thus approximately 14% greater than that of the tube having uniform annular wall thickness. Increased stress concentration proximate the sensors 40 provides higher signal to noise ratio and higher sensitivity. In addition, this improved performance is obtained with a higher moment of inertia and bending strength ratio. In addition, fatigue life is increased. For example, if the body 12 is made from 2024 T3 aluminum, the fatigue life increases from 10⁶ cycles for a tube having uniform annular wall thickness to 4 X 10⁶ cycles for an octagonal tube. This provides more output for the same fatigue life. Other suitable materials include titanium, 4340 steel, 17-4PH stainless steel or other high strength materials. Many of the advantages described above also apply to the tube 23' illustrated in FIG. 3.

The load cell 10 is particularly well suited for measuring the force and moment components of a rolling wheel. A second embodiment 10' of the present invention is illustrated in FIGS. 4, 5, 6 and 7. The load cell 10' is substantially similar to the load cell 10 wherein like components have been identified with the same reference numerals.

Referring to FIG. 4, the load cell 10' replaces a center portion of a tire rim 70. The annular ring 16 includes threaded apertures 72 that receive a plurality of fasteners 74, which secure the load cell 10' to the tire rim 70. An inner mounting plate 75 is fastened to the central hub using a plurality of fasteners 76 secured in corresponding threaded apertures 78 provided in the central hub 14 (FIG. 4) . The inner mounting plate 75 is secured on a vehicle spindle, not shown, using suitable fasteners 80. Power is supplied to and output signals are obtained from the plurality of strain sensors 40 by a controller 82 through a slip ring assembly 84, if the tire rim 70 rotates or partially rotates. The controller 82 calculates, records and/or displays the force and moment components measured by the load cell 10 ' .

In a preferred embodiment, the load cell 10' includes amplifying circuits 71 and 73 mounted in recesses 75 and 77, respectively, as illustrated in FIG. 7. The amplifying circuits 71 and 73 are connected to the sensing circuits on the radial tubes 21-24 and amplify the output signals prior to transmission through the slip ring assembly 84. By amplifying the output signals, problems associated with noise introduced by the slip ring assembly 84 are reduced. Connectors 79 and 81 mounted in apertures 83 and 85 connect the amplifying circuits 71 and 73 to the slip ring assembly 84. A mounting plate 87 mounts the slip ring assembly 84 to the central hub 14. Passageways 87A and 87B are provided in the mounting plate 87 to carry conductors from the slip ring assembly 84 to the connectors 79 and 81. An encoder

89 provides an angular input signal to the controller 82 indicative of the angular position of the load cell 10' .

FIG. 8 illustrates generally operations performed by the controller 82 to transform the output signals 88 received from the eight individual sensing circuits on the tubes 21-24 to obtain output signals 108 indicative of force and moment components with respect to six degrees of freedom in a static orthogonal coordinate system. As illustrated, output signals 88 from the sensing circuits are received by a scaling and geometric transformation circuit 90. The scaling and geometric transformation circuit 90 adjusts the output signals 88 to compensate for any imbalance between the sensing circuits. Circuit 90 also combines the output signals 88 according to the equations given above to provide output signals 94 indicative of force and moment components for the orthogonal coordinate system 47 (FIG. 1 ) ■

A cross-coupling matrix circuit 96 receives the output signals 94 and adjusts the output signals so as to compensate for any cross-coupling effects. A coordinate transformation circuit 102 receives output signals 100 from the cross-coupling matrix circuit 96 and an angular input 104 from an encoder or the like. The coordinate transformation circuit 102 adjusts the output signals 100 and provides output signals 108 that are a function of a position of the load cell 10 ' so as to provide force and moment components with respect to a static orthogonal coordinate system.

FIG. 9 illustrates the scaling and geometric transformation circuit 90 in detail . High impedance buffer amplifiers 110A-110H receive the output signals 88 from the slip ring assembly 84. In turn, adders 112A- 112H provide a zero adjustmenc while, preferably, adjustable amplifiers 114A-114H individually adjust the output signals 88 so that any imbalance associated with physical differences such as variances in the wall thickness of the location of the strain sensors 40 on the tubes 21-24, or variances in the placement of the sensors 40 from tube to tube can be easily compensated. Adders 116A-116H combine the output signals from the amplifiers 114A-114H in accordance with the equations above. Adjustable amplifiers 118A-118D are provided to ensure that output signals from adders 116A-116D have the proper amplitude .

As stated above, cross-coupling compensation is provide by circuit 96. By way of example, FIG. 10 illustrates cross-coupling compensation for signal F_x . Each of the other output signals F_y, F_z, M_x, M_γ and M_z are similarly compensated for cross-coupling effects. FIG. 11 illustrates in detail the coordinate transformation circuit 102. The encoder 89 provides an index for sine and cosine digital values stored in suitable memory 120 and 122 such as RAM (random access memory) . Digital-to-analog converters 124 and 126 receive the appropriate digital values and generate corresponding analog signals indicative of the angular position of the load cell 10' . Multipliers 128A-128H and adders 130A-130D combine force and moment output signals along and about the X-axis and the Z-axis so as to provide force and moment output signals 108 with respect to a static orthogonal coordinate system.

The load cells 10 and 10' described above have arranged the plurality of sensors 40 to function as shear sensors to provide an indication of shear stresses created in the radial tubes 20. If desired, the plurality of sensors 40 can be mounted to the radial tubes 20 to function as bending sensors to provide an indication of bending stresses in the radial tubes 20. In a preferred embodiment, the bending sensors can be located at a root of the tube or start of the fillet joining each tube 21-24 to the central hub 14, for example, as indicated at 140 and 142 on tube 21 in FIG. 5. A method of the present invention for making the load cell body 12 of FIGS. 1 and 5 includes fabricating from a single block of material the integral rigid central hub 14, the rigid annular ring 16 concentric with the hub 14 and radial members extending from the central hub 14 to the annular ring 16 wherein the flexure members 31-34 extend between an end of each radial member to the annular ring 16. The flexure member 31-34 are compliant for displacements of each corresponding radial member 21-24 along the corresponding longitudinal axis 21A-24A. Due to symmetry of the load cell body 12, it can be easily manufactured using conventional controlled machining processes. From a single block having two major surfaces, the load cell body 12 is secured so as to machine the first major surface and form essentially half of each of the principal components such as the central hub 14, the annular ring 16 and radial members 21-24. The block of material is then turned over to orient the second major surface to the machining apparatus. Machining operations are then performed on the second surface to form the balance of the central hub 14, the annular ring 16 and the radial members 21-24. Preferably, as stated above, the radial members 21-24 are machined to have a non- rectangular outer surface 60 with flat, orthogonally arranged sides 66A, 66B, 68A and 68D.

The method further includes forming a bore 64 within each radial member 21-24 along the corresponding longitudinal axis 21A-24A to form a tubular structure, wherein the sensitivity of the load cell body 12 is a function of the diameters of the bores 64 formed in the radial members 21-24. Referring to FIGS. 2 and 12, bores 64 and 64' in tube 23 are of different size. By varying the diameter of the bores in the tubes 21-24, the thickness of the wall of the tubes can be adjusted. In a preferred embodiment , apertures 120 (FIG. 1) are formed in the annular ring 16 and are aligned with the bores 64 of the tubes 21-24. Preferably, the apertures 120 are of at least the same diameter of the bores 64 in the tubes 21-24 and are formed just prior to making the bores 64 by drilling through the annular ring 16 toward the central hub 14. Forming the apertures 120 also in the annular ring 16 allows the sensitivity of the load cell body 12 to be easily adjusted since the bores 64 can be easily formed by drilling through the annular ring 16 toward the central hub 14. The bores 64 can be cylindrical or take other forms, such as oblong, if desired.

In a further preferred embodiment as illustrated in FIG. 5, the bores 64 in the radial tubes 21-24 extend also through the central hub 14, tapering slightly to smaller openings 122.

FIGS. 14 and 15 illustrate a further embodiment of a load cell 150. The load cell 150 is similar to the embodiments described above and includes an integral body that comprises a central hub 154, an annular ring 156 and radial tubes 160 extending from the central hub 154 to the annular ring 156. The central hub 154 is arranged so as to be concentric with the annular ring 156. Mounting apertures 157 and 159 are provided in the central hub 154 and the annular ring 156, respectively. As known to those skilled in the art, the mounting apertures 157 and 159 can be counterbored, and reliefs 151, 153 and 155 can be provided on the mounting surfaces to increase and make more uniform contact stresses . The plurality of radial tubes 160 join the central hub 154 to the annular ring 156. In the embodiment illustrated, the plurality of radial tubes 160 comprises four tubes 161, 162, 163 and 164. Each of the tubes 161-164 extend radially from the central hub 154 toward the annular ring 156 along corresponding longitudinal axes 161A, 162A, 163A and 164A. Preferably, axis 161A is aligned with axis 163A, while axis 162A is aligned with axis 164A. In addition, axes 161A and 163A are perpendicular to axes 162A and 164A. Although illustrated wherein the plurality of radial tubes 160 equals four, it should be understood that any number of tubes three or more can be used to join the central hub 154 to the annular ring 156. Preferably, the plurality of radial tubes 160 are spaced at equal angular intervals about a central axis indicated at 166. Flexure members 171, 172, 173 and 174 join an end of each radial tube 161-164, respectively, to the annular ring 156. The flexure members 171-174 are compliant for displacements of each corresponding radial tube 161-164 along the corresponding longitudinal axes 161A-164A. In the embodiment illustrated, the flexure members 171-174 are identical and include integrally formed flexure straps 176 and 178. The flexure straps 176 and 178 are located on opposite sides of each longitudinal axis 161A-164A and join the corresponding radial tube 161-164 to the annular ring 156.

Each flexure member 171-174 is formed by an aperture 175A disposed on a first side of the corresponding longitudinal axis 161A-164A, and a second aperture 175B disposed on a second side of the corresponding longitudinal axis 161A-164A. A slot 177 extends between the apertures 175A and 175B. The apertures 175A and 175B are shaped to minimize stress proximate each corresponding radial tube 161A and 164A, while strengthening the portion of the load cell 150 proximate the connection of the flexure straps to the annular ring 156. Accordingly, each aperture 175A and 175B is shaped to have a larger concave fillet 179 proximate the corresponding radial tube 161A-164A, and a smaller concave fillet 181 proximate the connection of the flexure straps 176 and 178 to the annular ring 156. In effect, the larger concave fillet 179 spreads the stress that will occur between the flexure straps 176 and 178 and the radial tubes 161-164, while the smaller concave fillet 181 retains the mass of the annular ring 156, thereby strengthening it . As used herein, "concave" is not limited to a portion of an inner surface of a hollow sphere, but includes all outwardly opening curved surfaces, for example, cylindrical, parabolic, elliptical, etc. For ease of machining, the concave fillets 179 and 181 can be a portion of an inner surface of a cylinder defined by a fixed radius. Although illustrated wherein the flexure members 171-174 are used to join the radial tubes 161-164 to the annular ring 156, it should be understood that the flexure members 171-174 could be used to join the radial tubes 161-164 to the central hub 154, in addition, or in the alternative to using flexure members joined to the annular ring 156.

As in the embodiments discussed above, a plurality of strain sensors 40 can be mounted on the plurality of tubes 160 to sense strain therein. Although the plurality of sensors 40 can be located on the plurality of radial tubes 160 to provide an indication of bending stresses therein, preferably the strain sensors are mounted conventionally to provide an output signal indicative of shear stresses in the walls of the plurality of radial tubes 160. The plurality of sensors 40 can be connected as described above for measurement of forces and moments in up to six degrees of freedom. Commonly, the plurality of sensors 40 comprise resistive strain gages. However, other forms of sensing devices such as optically based sensors or capacitively based sensors can also be used.

Each of the radial tubes 161-164 include a plurality of spaced-apart wall portions of reduced thickness to concentrate stress therein. Referring to FIG. 16 and radial tube 163 by way of example, the radial tube 163 has an outer surface 190 that is octagonal, being defined by eight distinct wall sections. The wall portions of reduced thickness are indicated at 192A, 192B, 192C and 192D. The wall portions of reduced thickness 192A-192D are formed by a cylindrical bore 194 in the radial tube 163 and a first pair of concave surfaces 196A and 196B facing in opposite directions and a second set of concave surfaces 198A and 198B also facing in opposite directions. Each of the bores 194 are aligned with an aperture 185 provided in the annular ring 156, an aperture 187 provided in each of the flexure members 171-174, and an aperture 189 provided in the central hub 154. Use of the concave surfaces 196A-196B, 198A-198B and the straight bore 194 can have the advantage of providing gradual stress concentration to the wall portions of reduced thickness 192A-192D. In addition, since the thickness of the walls from the wall portions of reduced thickness 192A-192D increases greatly over a small distance from the portions of reduced thickness 192A-192D, the structure is stiffer for overturning moments. The second set of concave surfaces 198A and

198B are substantially orthogonal to the first set of concave surfaces 196A and 196B such that the concave surfaces of the first set and the second set are alternately disposed about the corresponding longitudinal axis 163A. Although illustrated wherein the thickness of the portions 192A-192C is the same thickness of the portions 192B and 192D, the thickness can be made the same or different to provide desired sensitivity in selected directions. Preferably, the thickness of portion 192A should be approximately equal to portion 192C, and the thickness of portion 192B should be approximately equal to portion 192D. Each of the strain sensors 40 are disposed in the center of each concave surface proximate to the area of reduced thickness .

The concave surfaces 196A-196B and 198A-198B can be defined by one or more centers or foci, wherein the definition of "concave" provided above applies. However, in the embodiment illustrated, each of the concave surfaces 196A-196B and 198A-198B is defined by a fixed radius, which provides easy machining of the load cell 150. FIG. 17 is a detail sectional view of the tube 163 illustrating wall portions 192A and 192C, and concave surfaces 196A and 196B. It should be noted that concave surfaces 196A-196B and 198A-198B can have the same fixed radius or different fixed radii. In the embodiment illustrated in FIGS. 14 and 16, each of the intervening wall sections 200 between the concave surfaces 196A-196B and 198A-198B are also concave, preferably defined by a fixed radius. This design simplifies machining, but if desired, intervening wall sections 200 can have other configurations .

FIGS . 18 and 19 illustrate an embodiment of a wheel force transducer 210. In one aspect of the present invention, the wheel force transducer 210 includes an integral body that comprises a central hub 214, an annular ring 216, and sensing structures 220, herein illustrated as radial tubes. However, in contrast to the load cells described above, the annular ring 216 includes spaced apart flanges 218A and 218B adapted to support a tire 222 directly thereon.

In the embodiment illustrated, the radial tubes 220 are of the form described above with respect to the load cell 150, but it should be noted that this is just one exemplary embodiment in that the radial tubes used in the other load cells can also be used. Furthermore, it should be noted that other integral sensing structures (both radially and non-radially oriented) including but not limited to solid and hollow straps, bars and flexures can be used.

In the embodiment illustrated, the central hub 214 also includes required mounting apertures 224 in a pattern to allow the wheel force transducer 210 to be mounted directly to a vehicle spindle (not shown) . The wheel force transducer 210 illustrated includes a central aperture 225 of size for use on a formula one racing car. However, it should be understood that the mounting apertures 224 and 225 are exemplary and the number and pattern can be varied depending on the vehicle that the wheel force transducer 210 will be used on. Inclusion of mounting apertures 224 and 225 in the central hub 214 minimizes unnecessary mass of the wheel force transducer 210, thereby allowing the wheel force transducer 210 to approximate a standard wheel used on the vehicle. However, if desired, the inner mounting plate 75 described above can be used in order to allow the wheel force transducer 210 to be used on vehicles with different mounting designs.

The annular ring 216 includes apertures 230 that are aligned with corresponding bores of the radial tubes 220 for the reasons discussed above. However, in view that the annular ring 216 supports the tire 222, which is pressurized, sealing plugs 232 are provided. The plugs 232 can include any number of sealing mechanisms such as face seals or gland seals 233, as illustrated. In the embodiment illustrated, each of the plugs 232 include threads that mate with corresponding threads provided in the apertures 230 in order to retain the plugs 232 in the apertures 230. As appreciated by those skilled in the art, other means for retaining the plugs 232 in the apertures 230 can be used such as welding, bonding, gluing, set screws, snap rings, etc. FIG. 20 illustrates a snap ring 236 engaging a groove 238 in the aperture 230 to retain the plug 232 in the aperture 230.

The wheel force transducer 210 can include the amplifying circuits 71, 73, the mounting plate 87 and the slip ring assembly 84, as discussed above. However, since one use of the wheel force transducer 210 is on race cars, and since race cars often experience heavy braking loads, the wheel force transducer 210 can be exposed to excessive heat from the car' s braking components. This environment may require at least relocation of the amplifying circuits 71 and 73 from the recesses 75 and 77. For instance, it may be necessary to mount the amplifying circuits 71 and 73 to the mounting plate 87. In yet other situations, it may be necessary to eliminate the amplifying circuits 71 and 73 and pass low level sensor signals through the slip ring assembly 84. The slip ring assembly 84 can also be eliminated and replaced with a telemetry circuit having a suitable transmitter mounted to the wheel force transducer 210 and a suitable receiver located in the vehicle . Sensing devices such as described above can be mounted to the wheel force transducer 210. If strain, or other heat sensitive, sensors are mounted to the sensing structures, such as the radial tubes 220, it may be necessary to shield or insulate the sensors from radiant heat from the braking components of the vehicle. FIG. 18 illustrates shields 240 that can be disposed over the sensors receiving excessive radiant energy. The shields 240 can comprise one or more rigid members 242 joined to the individual tube, flexure member, central hub 214 and/or annular ring 216. In other embodiments, the shields 240 can be a tape disposed over the sensors. In either case, the shields 240 can be reflective to reflect radiant energy away from the respective sensor. If desired, an insulator, such as silicone rubber or other elastomer, can be deposited or disposed over the sensors in addition, or in the alternative, to the shields 240. In some applications, the shields 240 also protect the sensors from physical damage.

Although the present invention has been described with reference to preferred embodiments, workers skilled in the art will recognize that changes may be made in form and detail without departing from the spirit and scope of the invention.

Claims

WHAT IS CLAIMED IS:

1. A load cell body for transmitting forces and moments in plural directions, the load cell body comprising : an integral assembly having: a rigid central hub; a rigid annular ring concentric with the central hub; at least three radial tubes extending radially along corresponding longitudinal axes from the central hub to the annular ring, wherein an outer surface of each tube comprises a plurality of concave portions; and a flexure member extending between an end of each radial tube to at least one of the annular ring and central hub, the flexure member being compliant for displacements of each corresponding radial tube along the corresponding longitudinal axis.

2. The load cell body of claim 1 wherein each of the concave portions is defined by a fixed radius.

3. The load cell body of claim 1 wherein the outer surface of each tube includes eight distinct portions about the circumference of each tube.

4. The load cell body of claim 3 wherein the concave portions of each tube comprise a first set of concave portions facing in opposite directions and a second set of concave portions facing in opposite directions, the second set of concave portions being substantially orthogonal to the first set of concave portions such that concave portions of the first set and the second set are alternately disposed about each corresponding longitudinal axis.

5. The load cell body of claim 4 wherein the concave portions of the first and second sets are defined by the same fixed radius.

6. The load cell body of claim 4 wherein each portion is concave.

7. The load cell body of claim 4 wherein each of the concave portions is defined by a fixed radius.

8. The load cell body of claim 4 wherein a concave portion extends between each concave portion of the first set and the successive concave portion of the second set .

9. The load cell body of claim 4 wherein a first set of shear sensors is mounted on the first set of concave portions comprising a first shear sensing circuit for each tube, and a second set of shear sensors is mounted on the second set of concave portions comprising a second shear sensing circuit for each tube.

10. The load cell body of claim 1 wherein four radial tubes extend from the central hub to the annular ring, wherein a first pair of radial tubes is substantially aligned on a first axis, and a second pair of tubes is substantially aligned on a second axis, the first axis being substantially orthogonal to the second axis .

11. The load cell body of claim 1 wherein the annular ring includes an aperture aligned with a bore of each of the radial tubes.

12. A load cell for measuring selected components of force or moment, the load cell comprising: a rigid central hub; a rigid annular ring concentric with the central hub; a plurality of radial tubes extending radially along corresponding longitudinal axes from the central hub to the annular ring; wherein each tube includes a plurality of spaced-apart outwardly facing concave wall portions of reduced thickness to concentrate stress therein; a flexure member extending between an end of each radial tube to at least one of the annular ring and central hub, the flexure member being compliant for displacements of each corresponding radial tube along the corresponding longitudinal axis; and a plurality of shear sensors mounted on the concave wall portions of each radial tube to provide output signals indicative of strain therein.

13. The load cell of claim 12 wherein the central hub, the annular ring and the plurality of radial tubes are integrally formed from a single block of material.

14. The load cell of claim 12 wherein the plurality of shear sensors comprises a quantity to provide outputs indicative of a plurality of forces or moments .

15. The load cell of claim 12 wherein each tube includes four spaced-apart concave wall portions of reduced thickness.

16. The load cell of claim 15 wherein the plurality of shear sensors comprises a quantity to provide outputs indicative of forces along a set of three orthogonal axes and moments about the set of three orthogonal axes .

17. The load cell of claim 16 wherein each tube comprises eight distinct portions in section perpendicular to each corresponding longitudinal axis.

18. The load cell of claim 17 wherein each distinct portion of each tube comprises an outwardly facing concave portion.

19. A load cell for transmitting forces and moments in plural directions, the load cell comprising: an integral assembly having: a rigid central hub; a rigid annular ring concentric with the central hub; at least three radial tubes extending radially along corresponding longitudinal axes from the central hub to the annular ring, wherein an outer surface of each radial tube includes a plurality of opposed concave portions; a flexure member extending between an end of each radial tube to the annular ring, the flexure member being compliant for displacements of each corresponding radial tube along the corresponding longitudinal axis; and a strain sensor mounted on selected radial tubes to measure strain therein, wherein each strain sensor comprises shear sensors mounted to each of the plurality of opposed planar surfaces.

20. The load cell of claim 19 wherein each of the outer surfaces comprises a first set of concave portions facing in opposite directions and a second set of concave portions facing in opposite directions, the second set of concave portions being substantially orthogonal to the first set of concave portions such that concave portions of the first set and the second set are alternately disposed about each corresponding longitudinal axis and wherein the shear sensors are mounted to the concave portions of the first and second sets.

21. The load cell of claim 19 wherein a concave portion extends between each concave portion of the first set and the successive concave portion of the second set.

22. The load cell of claim 19 wherein a first set of shear sensors is mounted on the first set of concave portions comprising a first shear sensing circuit for each tube, and a second set of shear sensors is mounted on the second set of concave portions comprising a second shear sensing circuit for each tube.

23. The load cell of claim 22 wherein four radial tubes extend from the central hub to the annular ring, wherein a first pair of radial tubes is substantially aligned on a first axis, and a second pair of tubes is substantially aligned on a second axis, the first axis being substantially orthogonal to the second axis.

24. A load cell body for transmitting forces and moments in plural directions, the load cell body comprising : an integral assembly having: a rigid central hub; a rigid annular ring concentric with the central hub; at least three radial tubes extending radially along corresponding longitudinal axes from the central hub to the annular ring; and a flexure member extending between an end of each radial tube to the annular ring, the flexure member being compliant for displacements of each corresponding radial tube along the corresponding longitudinal axis, each flexure member formed from two apertures and a slot therebetween, the apertures configured to minimize stress proximate the radial tube and strengthen the portion proximate the connection to the annular ring.

25. A load cell body for transmitting forces and moments in plural directions, the load cell body comprising: an integral assembly having: a rigid central hub; a rigid annular ring concentric with the central hub and having a plurality of apertures; at least three radial tubes extending radially along corresponding longitudinal axes from the central hub to the annular ring; and a flexure member extending between an end of each radial tube to at least one of the annular ring and central hub, the flexure member being compliant for displacements of each corresponding radial tube along the corresponding longitudinal axis, the flexure member being defined by two apertures and a slot extending therebetween, the apertures defined by a first concave fillet proximate the corresponding radial tube and having greater concavity than a second fillet proximate the connection to the annular ring or central hub .

26. The load cell of claim 25 wherein each fillet is defined by a fixed radius.

27. A wheel force transducer body comprising: an integral assembly having: a rigid central hub; a rigid annular ring concentric with the central hub and having spaced apart extending flanges adapted to support a tire; and a plurality of sensing structures joining the central hub to the annular ring.

28. The wheel force transducer of claim 27 wherein the plurality of sensing structures comprise radially oriented members from the central hub to the annular ring.

29. The wheel force transducer of claim 28 wherein the plurality of sensing structures comprise at least three radial tubes extending radially along corresponding longitudinal axes from the central hub to the annular ring .

30. The wheel force transducer of claim 29 and further comprising: a flexure member extending between an end of each radial tube to at least one of the annular ring and central hub, the flexure member being compliant for displacements of each corresponding radial tube along the corresponding longitudinal axis.

31. The wheel force transducer body of claim 30 wherein the annular ring includes an aperture aligned with a bore of each radial tube.

32. The wheel force transducer body of claim 31 and a plug adapted to seal each aperture in the annular ring .

33. The wheel force transducer body of claim 32 and means for retaining each plug in the corresponding aperture.

34. The wheel force transducer body of claim 33 wherein the means for retaining comprises mating threads provided on the plug and the aperture .

35. The wheel force transducer body of claim 33 wherein the means for retaining comprises a snap ring.

36. The wheel force transducer body of claim 29 wherein an outer surface of each radial tube includes a first pair of opposed surfaces and corresponding portions of reduced thickness, and a second pair of opposed surfaces and corresponding portions of reduced thickness, the second pair of opposed surfaces orthogonally oriented with respect to the first pair of opposed surfaces.

37. The wheel force transducer body of claim 36 wherein each of the opposed surfaces is planar.

38. The wheel force transducer body of claim 36 wherein each of the opposed surfaces is concave.

39. The wheel force transducer body of claim 30 and further comprising a shield protecting each of the tubes .

40. The wheel force transducer body of claim 27 wherein the central hub includes apertures for mounting the wheel force transducer body directly to a vehicle spindle .