Axis alignment method

Abstract

An apparatus and method for determining the rate of angular rotation of a moving body and, in particular, for alignment of the dither motion and the Coriolis acceleration sensing direction in a sensor adapted to be formed, i.e. micromachined, from a silicon substrate.

Description

FIELD OF THE INVENTION

The invention relates to an apparatus and method for determining the rate of angular rotation of a moving body and, in particular, to alignment of the dither motion and the Coriolis acceleration sensing direction in a sensor adapted to be formed, i.e. micromachined, from a silicon substrate.

REFERENCE TO RELATED APPLICATIONS

Reference is made to the following commonly assigned patents:

1) entitled “Monolithic Acclerometer,” U.S. Pat. No. 5,165,279 issued on Nov. 24, 1992, in the name of Brian L. Norling;

2) entitled “Accelerometer With Co-Planar Push-Pull Force Transducers,” U.S. Pat. No. 5,005,413 issued on Apr. 9, 1991, in the name of Mitch Novack;

3) entitled “Coriolis Inertial Rate and Acceleration Sensor,” U.S. Pat. No. 5,168,756 issued on Dec. 8, 1992, in the name of Rand H. Hulsing II;

4) entitled “Torque Coil Stress Isolator,” U.S. Pat. No. 5,111,694 issued on May 12, 1992, in the name of Steven Foote;

5) entitled “Micromachined Rate And Acceleration Sensor,” U.S. Pat. No. 5,627,314 issued on May 6, 1997, in the name of Rand H. Hulsing II;

6) entitled “Micromachined Rate And Acceleration Sensor,” U.S. Pat. No. 5,557,046 issued on Sep. 17, 1996, in the name of Rand H. Hulsing II;

7) entitled “Micromachined Rate And Acceleration Sensor Having Vibrating Beams,” U.S. Pat. No. 5,331,854 issued on Jul. 26, 1994, in the name of Rand H. Hulsing II;

8) entitled “Micromachined Rate And Acceleration Sensor,” U.S. Pat. No. 5,241,861 issued on Sep. 7, 1993, in the name of Rand H. Hulsing II;

9) entitled “Micromachined Rate And Acceleration Sensor,” U.S. application Ser. No. 08/893,721 filed Jul. 10, 1997, in the name of Rand H. Hulsing II; and

10) entitled “Micromachined Rate And Acceleration Sensor,” U.S. application Ser. No. 08/786,185 filed Jan. 20, 1997, in the name of Rand H. Hulsing II;

11) entitled “Low Vibration Link,” U.S. application Ser. No. 09/016,186 filed Jan. 30, 1998, in the name of Rand H. Hulsing II

all of which are incorporated herein by reference.

BACKGROUND OF THE INVENTION

The rate of rotation of a moving body about an axis may be determined by mounting an accelerometer on a frame and dithering it, with the accelerometer's sensitive axis and the direction of motion of the frame both normal to the rate axis about which rotation is to be measured. For example, consider a set of orthogonal axes X, Y and Z oriented with respect to the moving body. Periodic movement of the accelerometer along the Y axis of the moving body with its sensitive axis aligned with the Z axis results in the accelerometer experiencing a Coriolis acceleration directed along the Z axis as the moving body rotates about the X axis. A Coriolis acceleration is that perpendicular acceleration developed while the body is moving in a straight line, while the frame on which it is mounted rotates. This acceleration acting on the accelerometer is proportional to the velocity of the moving sensor body along the Y axis and its angular rate of rotation about the X axis. An output signal from the accelerometer thus includes a DC or slowly changing component or force signal F representing the linear acceleration of the body along the Z axis, and a periodic component or rotational signal Ω representing the Coriolis acceleration resulting from rotation of the body about the X axis.

The amplitude of that Coriolis component can be produced by vibrating the accelerometer, causing it to dither back and forth along a line perpendicular to the input axis of the accelerometer. Then, if the frame on which the accelerometer is mounted is rotating, the Coriolis acceleration component of the accelerometer's output signal will be increased proportional to the dither velocity. If the dither amplitude and frequency are held constant, then the Coriolis acceleration is proportional to the rotation rate of the frame.

The linear acceleration component and the rotational component representing the Coriolis acceleration may be readily separated by using two accelerometers mounted in back-to-back relationship to each other and processing their out put signals by sum and difference techniques. In U.S. Pat. No. 4,510,802, assigned to the assignee of this invention, two accelerometers are mounted upon a parallelogram with their input axes pointing in opposite directions. An electromagnetic D'Arsonval coil is mounted on one side of the parallelogram structure and is energized with a periodically varying current to vibrate the accelerometers back and forth in a direction substantially normal to their sensitive or input axis. The coil causes the parallelogram structure to vibrate, dithering the accelerometers back and forth. By taking the difference between the two accelerometer outputs, the linear components of acceleration are summed. By taking the sum of the two outputs, the linear components cancel and only the Coriolis or rotational components remain.

U.S. Pat. No. 4,509,801, commonly assigned to the assignee of this invention, describes the processing of the output signals of two accelerometers mounted for periodic, dithering motion to obtain the rotational rate signal Ω and the force or acceleration signal F representing the change in velocity, i.e. acceleration of the moving body, along the Z axis. U.S. Pat. No. 4,510,802, commonly assigned to the assignee of this invention, describes a control pulse generator, which generates and applies a sinusoidal signal of a frequency ω to the D'Arsonval coil to vibrate the parallelogram structure and thus the first and second accelerometer structures mounted thereon, with a dithering motion of the same frequency ω. The accelerometer output signals are applied to a processing circuit, which sums the accelerometer output signals to reinforce the linear components indicative of acceleration. The linear components are integrated over the time period T of the frequency ω corresponding to the dither frequency to provide the force signal F, which represents the change in velocity, i.e. acceleration, along the Z axis. The accelerometer output signals are also summed, whereby their linear components cancel and their Coriolis components are reinforced to provide a signal indicative of frame rotation. That difference signal is multiplied by a zero mean periodic function sgnc ωt. The resulting signal is integrated over a period T of the frequency ω by a sample and hold circuit to provide the signal Ω representing the rate of rotation of the frame.

The D'Arsonval coil is driven by a sinusoidal signal of the same frequency ω which corresponded to the period T in which the linear acceleration and Coriolis component signals were integrated. In particular, the pulse generator applies a series of pulses at the frequency ω to a sine wave generator, which produces the substantially sinusoidal voltage signal to be applied to the D'Arsonval coil. A pair of pick-off coils produce a feedback signal indicative of the motion imparted to the accelerometers. That feedback signal is summed with the input sinusoidal voltage by a summing junction, whose output is applied to a high gain amplifier. the output of that amplifier in turn is applied to the D'Arsonval type drive coil. The torque output of the D'Arsonval coil interacts with the dynamics of the parallelogram structure to produce the vibrating or dither motion. In accordance with well known servo theory, the gain of the amplifier is set high so that the voltage applied to the summing junction and the feedback voltage are forced to be substantially equal and the motion of the mechanism will substantially follow the drive voltage applied to the summing junction.

U.S. Pat. No. 4,881,408 describes the use of vibrating beam force transducers in accelerometers. In U.S. Pat. No. 4,372,173, the force transducer takes the form of a double-ended tuning fork fabricated from crystalline quartz. The transducer comprises a pair of side-by-side beams which are connected to common mounting structures at their ends. Electrodes are deposited on the beams and a drive circuit applies a periodic voltage signal to the electrodes causing the beams to vibrate toward and away from one another, 180 degrees out of phase. In effect, the drive circuit and beams form an oscillator with the beams playing the role of a frequency controlled crystal, i.e. the mechanical resonance of the beams controls the oscillation frequency. The vibrating beams are made of crystalline quartz, which has piezoelectric properties. Application of periodic drive voltages to such beams cause them to vibrate toward and away from one another, 180 degrees out of phase. When the beams are subjected to accelerating forces, the frequency of the mechanical resonance of the beams changes, which results in a corresponding change in the frequency of the drive signal. When subjected to acceleration forces that cause the beams to be placed in tension, the resonance frequency of the beams and thus the frequency of the drive signal increases. Conversely, if the beams are placed in a compression by the acceleration forces, the resonance frequency of the beams and the frequency of the drive signal is decreased.

Above referenced U.S. Pat. No. 5,005,413 describes accelerometers using vibrating force transducers require materials with low internal damping, to achieve high Q values that result in low drive power, low self-heating and insensitivity to electronic component variations. Transducer materials for high-accuracy instruments also require extreme mechanical stability over extended cycles at high stress levels. Crystalline silicon posses high Q values, and with the advent of low cost, micromachined mechanical structures fabricated from crystalline silicon, it is practical and desirable to create vibrating beams from a silicon substrate. Commonly assigned U.S. Pat. No. 4,912,990 describes a vibrating beam structure fabricated from crystalline silicon and including an electric circuit for applying a drive signal or current along a current path that extends in a first direction along a first beam and in a second, opposite direction along a second beam parallel to the first. A magnetic field is generated that intersects substantially perpendicular the conductive path, whereby the first and second beams are caused to vibrate towards and away from one another, 180 degrees out of phase.

Digital techniques employ stable, high frequency crystal clocks to measure a frequency change as an indication of acceleration forces applied to such vibrating beam accelerometers. To ensure precise integration or cosine demodulation, a crystal clock is used to set precisely the frequency of the dither drive signal. Outputs from two accelerometers are fed into counters to be compared to a reference clock signal produced by the crystal clock. A microprocessor reads the counters and processes the data to provide a force signal F and a rotational signal Ω. The main advantage of digital processing is the ability to demodulate with extreme precision. The short term stability of the reference crystal clock allows the half cycle time basis to be precisely equal. Thus a constant input to the cosine demodulator is chopped up into equal, positive half cycle and negative half cycle values, whose sum is exactly zero.

In an illustrative embodiment, the two accelerometers signals are counted in their respective counters over 100 Hz period (corresponding to a 100 Hz of the dither frequency ω) and are sampled at a 400 Hz data rate corresponding to each quarter cycle of the dither motion. The two accumulated counts are subtracted to form the force signal F. Since the counters act as an integrator, the acceleration signal is changed directly to a velocity signal. Taking the difference of the acceleration signals tends to reject all Coriolis signals as does the counter integration and locked period data sampling.

The Coriolis signals are detected by a cosine demodulation. The cosine demodulated signals from the first and second accelerometers are summed to produce the Δθ signal. Again, the counters integrate the rate data to produce an angle change. The sum also eliminates any linear acceleration and the demodulation cancels any bias source including bias operating frequency and accelerometer bias. The accelerometer temperature is used in a polynomial model to provide compensation for all the coefficients used to convert the frequency counts into output units. Thus, the scale factor, bias and misalignment of the sensor axes are corrected over the entire temperature range.

The demodulation of the frequency sample is straightforward once the data is gathered each quarter cycle. The cosine demodulation is simply the difference between the appropriate half cycles. The linear acceleration is the sum of all samples.

The state of the art in micromachined rate and acceleration sensors is represented by U.S. Pat. No. 5,341,682 which is commonly assigned to the assignee of the present invention and incorporated herein by reference. The rate of rotation of a moving body about an axis may be determined by mounting an accelerometer on a frame and dithering it, with the accelerometer's sensitive axis and the direction of motion of the frame both normal to the rate axis about which rotation is to be measured. A Coriolis acceleration is the measure of the acceleration developed while the body is moving in a straight line and the frame upon which it is mounted rotates about the rate axis. The amplitude of the Coriolis component can be produced by vibrating or dithering the accelerometer, causing it to dither back and forth along a line perpendicular to the input axis of the accelerometer. When the frame upon which the accelerometer is mounted is rotated, the Coriolis acceleration component of the accelerometer's output signal increases in proportion to the dither velocity.

The linear acceleration component and the rotational component representing the Coriolis acceleration may be readily separated by using two accelerometers mounted in back-to-back relationship to each other and processing their output signals by sum and difference techniques as described in U.S. Pat. No. 4,590,801, which is commonly assigned to the assignee of the present invention and incorporated herein by reference.

Rate and acceleration sensors, for example, U.S. Pat. No. 5,341,682, are comprised of two accelerometers aligned in a single plane such that the input or sensitive axes of the two accelerometers are parallel and the output or hinge axes of the two accelerometers are parallel. The two accelerometers are vibrated or dithered at a predetermined frequency along a dither axis parallel to the hinge axes. The two accelerometers tend to vibrate at slightly different frequencies due to slight mass mismatch. Even if driven by a drive signal of common frequency, the accelerometer motions tend to be out of phase with each other. A link is connected to each of the two accelerometers whereby motion imparted to one accelerometer results in like but opposite motion imparted to the other accelerometer. Thus, the dithering motion imparted to one accelerometer is ideally of the exact same frequency and precisely 180 degrees out of phase with that applied to the other accelerometer.

The link provides an interconnect between the two accelerometers which is stiff in the dither axis such that the motion imparted to one accelerometer is effectively transmitted to the other accelerometer and both accelerometers ideally dither at the same frequency and precisely 180 degrees out of phase. The link is pivotally fixed to the frame by a pivot flexure. The link is further connected to each of the two accelerometers by flexures. The link is typically formed in a complex asymmetric shape. The complexity of the link is driven by practical considerations involved in adapting the link to accommodate both the pivot flexure and the two link-to-accelerometer flexures. The link's complex asymmetric shape provides adequate clearance between the link and the frame for the pivot flexure. The link's shape also provides adequate clearance between the link and each accelerometer to provide the precise flexure length to ensure that the flexures exhibit a predetermined mix of simple arc bending and “S-bend” motion and to ensure that any motion imparted to one accelerometer by the flexures is imparted to the other accelerometer as a sinusoidal function without introducing a higher order harmonic into the translation motion.

Although the device described in above referenced U.S. Pat. No. 5,341,682 functions for the purposes intended, its exact behavior is difficult to predict and/or model analytically. For example, the complex shape of prior links results in spring rates which are asymmetrical and a shape which is difficult to solve analytically. Additionally, constructing the shape previously taught results in flexures whose thicknesses and hence vibration properties are difficult to control.

Above referenced U.S. application Ser. No. 09/016,186 provides a linkage between accelerometers in a micromachined rate and acceleration sensor which is relatively simple to solve analytically and results in flexures whose thicknesses are relatively insensitive to process variations. For example, according to one aspect of U.S. application Ser. No. 09/016,186, the link shape can be solved using classical mechanical equations. According to another aspect of the invention, the present invention provides a shape which is relatively insensitive to process variations by providing a relatively simple shape having a symmetrical configuration. U.S. application Ser. No. 09/016,186 provides a simple symmetrically shaped link having sufficient mechanical stiffness in the to effectively transmit motion imparted to one accelerometer to the other accelerometer such that both accelerometers dither at the same frequency and precisely 180 degrees out of phase.

U.S. application Ser. No. 09/016,186 provides a simple symmetrical link which provides adequate clearance between the link and each accelerometer for flexures having a length which ensures that the flexures exhibit a predetermined mix of simple arc bending and “S-bend” motion and which ensures that any motion imparted to one accelerometer by the flexures is imparted to the other accelerometer as a sinusoidal function without introducing a higher order harmonic into the translation motion. U.S. application Ser. No. 09/016,186 provides a simple symmetrical link having reduced sensitivity to vibration in the dither cross-axis by providing, for example, a simplified columnar shaped. U.S. application Ser. No. 09/016,186 provides a simple symmetrical link having reduced sensitivity to cross-axis vibration by providing, for example, a link having a columnar shape in the dither cross-axis.

As described in U.S. Pat. No. 5,341,682, the accelerometers are suspended from a dither or mounting frame by a pair of flexures or “dither legs” which vibrate upon application of a dithering force to translate the accelerometers in a predominantly linear relationship with each other. However, true orthogonality is not achieved between the dither motion and the Coriolis acceleration sensing direction in the normal manufacturing process. State of the art micromachined vibrating Coriolis rate and acceleration sensors, as represented by U.S. Pat. No. 5,341,682 and others of the above incorporated patents and patent applications, experience quadrature motion due to the manifold sources of mechanical imperfection resulting from the tolerances inherent in manufacturing processes. This axis misalignment in conjunction with a phase shift causes a rate bias error which limits performance.

One method and apparatus for overcoming the errors introduced by quadrature motion is described in co-pending U.S. Pat. No. 5,886,259, assigned to the assignee of the present invention, steers the accelerometer input axes to be orthogonal using capacitive attraction between the sensing mass and stationary members of the sensor frame. However, such capacitive steering requires very small gaps, on the order of microns, between the sensing mass and stationary members to generate sufficient applied force. Given the very small gaps necessary, actual implementation of this axis alignment feature is difficult in a normal manufacturing setting using conventional processing methods.

SUMMARY OF THE INVENTION

The present invention provides an apparatus and method for overcoming the limitations of the prior art by providing true orthogonality between the dither motion and the Coriolis acceleration sensing direction using normal manufacturing processes. The present invention provides axial alignment between the dither motion and the Coriolis acceleration sensing direction in a device which can be reduced to a planar silicon process within a substrate, uses a parallelogram operated off square to impart wide gaps. The axial alignment device of the present invention is realized in a compact apparatus easily manufactured using standard micromaching tolerances.

In accordance with the present invention, the dither axis is rotated orthogonal to the accelerometer input axis. By rotating the base of the dither leg, a different dither direction can be obtained with respect to the accelerometer axis. A component is added to the end of the dither leg to allow for easy rotation. A torque force is applied to the dither leg. A method for detecting, adjusting and maintaining this rotation is also provided.

According to one aspect of the present invention, the present invention provides a constant value of axis alignment in a one-time open loop correction, whereby axial alignment between the dither motion and the Coriolis acceleration sensing direction is achieved by applying fixed voltage and current levels in the ranges normally associated with such sensor devices. For example, in a typical application, the invention uses less than 5 volts and 5 milliamps to compensate for a milliradian of rotation about a dither leg which normally nulls quadrature errors to within acceptable limits to improve rate bias performance.

According to another aspect of the present invention, the present invention provides active axis alignment between the dither motion and the Coriolis acceleration sensing direction in a closed loop nulling scheme, whereby aging, package stresses, manufacturing errors, g-loading, temperature and other fixed and varying factors affecting performance are corrected.

According to another aspect of the present invention, the present invention rotates the dither axis into orthogonality with the accelerometer input axis by rotating the base of the dither leg. The present invention provides a unique use of leverage to increase the torsional rotation angle of the dither leg.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1A is a perspective view illustrating the rate and acceleration sensor of this invention;

FIG. 1B is a side, cross-sectional view illustrating the rate and acceleration sensor of this invention, rotated 90 degrees from view the in FIG. 1A ;

FIG. 1C is a cross-sectional, side view taken along line 1 C— 1 C of FIG. 1B ;

FIG. 1D is a bottom plan view of the sensor shown in FIGS. 1A and B ;

FIG. 1E is a top plan view of the flux path assembly included within the sensor as shown in FIGS. 1B , C and D;

FIG. 2A is a top plan view of the unitary substrate out of which are formed a pair of accelerometers disposed in a side-by-side relationship with their input axes pointing in opposite directions, as shown in FIGS. 1B , 1 C and 1 D;

FIG. 2B is a perspective view of one of the accelerometers formed in the substrate as shown in FIG. 2A ;

FIG. 2C is a cross-sectional view of the substrate and its accelerometer as taken along the line 2 C— 2 C of FIG. 2B ;

FIG. 3A is a circuit diagram of a first embodiment of an oscillator circuit for providing drive signals to the drive coils of the accelerometers shown in FIG. 2A ;

FIG. 3B is a circuit diagram responsive to the velocity out put signal of the circuit shown in FIG. 3A for gating the output signals from the accelerometer into counters;

FIG. 3C is a circuit diagram of a second embodiment of an oscillator circuit for sensing signals derived from the pick-off coils disposed on the accelerometers shown in FIG. 2A for providing drive signals to the coils of these accelerometers to effect the dither motion thereof;

FIG. 3D is a functional block diagram illustrating the processing of the output signals from the first and second accelerometers formed within the silicon substrate of FIG. 2A and , in particular, illustrates how a pair of counters are gated to effectively demodulate the accelerometer output signals to provide an indication of the specific force and angular rotation rate of the moving body;

FIG. 4 is a plan view of an ‘X’ shaped link for providing a linkage between accelerometers in a micromachined rate and acceleration sensor according to one embodiment of U.S. application Ser. No. 09/016,186;

FIG. 5 is a plan view of a modified ‘X’ shaped link for providing a linkage between accelerometers in a micromachined rate and acceleration sensor according to one embodiment of U.S. application Ser. No. 09/016,186;

FIG. 6 is a plan view of a link having a “dog leg” shape for providing a linkage between accelerometers in a micromachined rate and acceleration sensor according to one embodiment of U.S. application Ser. No. 09/016,186;

FIG. 7 is a plan view of a symmetric ‘U’ shaped link for providing a linkage between accelerometers in a micromachined rate and acceleration sensor according to one embodiment of U.S. application Ser. No. 09/016,186;

FIG. 8 is a plan view of a symmetric and mass, reduced ‘U’ shaped link for providing a linkage between accelerometers in a micromachined rate and acceleration sensor according to one embodiment of U.S. application Ser. No. 09/016,186;

FIG. 9 is a plan view of a mass reduced ‘U’ shaped link for providing a linkage between accelerometers in a micromachined rate and acceleration sensor according to one embodiment of U.S. application Ser. No. 09/016,186;

FIG. 10 illustrates one embodiment of the axis alignment feature of the rate and acceleration sensor according to the present invention in which axial misalignment between the dither motion and the Coriolis acceleration sensing direction is eliminated or “nulled,” FIG. 10 includes FIG. 10-1 which is a cross-sectional view of the X-flexure portion of the axis alignment feature according to the present invention taken across a plane perpendicular to the longitudinal axis of the feature;

FIG. 11 illustrates an isometric view of the X-flexure according to one embodiment of the axis alignment feature of the invention;

FIG. 12 is an end view of the X-flexure according to one embodiment of the axis alignment feature of the invention;

FIG. 13 is illustrative of the mask used in etching the X-flexure portion of the axis alignment feature of the present invention into the substrate using conventional etching processes, for example, a conventional potassium hydroxide (KOH) process that takes advantage of the orientation-dependent properties of silicon to etch specific shapes in silicon;

FIGS. 14A and 14B illustrate the break through and self-stopping features of the etching process in forming the X-flexures portion of the axis alignment feature in a silicon substrate;

FIG. 15 illustrates a preferred alternative embodiment of the X-flexure portion of the axis alignment feature of the invention wherein the X-flexure is formed as several independent struts which are free to rotate independently of the other members which greatly increases the torsional flexibility or compliance of the X-flexure; and

FIG. 16 details one embodiment of the heated beam portion of the axis alignment feature which are used to drive the rotation of the active X-flexure portion of the axis alignment feature.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT(S)

Referring now to the drawings, FIGS. 1A , B, C and D show the arrangement of a rate and acceleration sensor 10 according to the present invention. The sensor 10 includes a shell 12 housing a unitary substrate 16 , which is illustratively made of silicon and in which is formed, illustratively by micro-machining, a pair of accelerometers 32 a and 32 b disposed in side-by-side relation such that their input axes 38 a and 38 b are disposed in opposite directions (see FIG. 1 D), a unitary magnet 20 and a flux path assembly 18 , which provides a magnetic path for directing the flux emanating from the magnet 20 through the substrate 16 and its first and second accelerometers 32 a and b. As will be explained, the configuration and disposition of the accelerometers 32 a and b within the substrate 16 permits a simple, straightforward magnetic flux path to effect the operation of the dithering motion and the vibration of a sensor element of the accelerometers 32 a and b.

Referring now to FIG. 2A , the details of the substrate 16 are shown. The first and second accelerometers 32 a and b are micromachined from the unitary, silicon substrate 16 so that their input axes 38 a and 38 b are disposed in parallel but opposite directions. In FIG. 2A , the input axis 38 a of the accelerometer 32 a is disposed out of the page, whereas the input axes 38 b of the accelerometer 32 b is disposed into the page. Further, the input axes 38 a and b are disposed perpendicular to a dither or vibration axis 41 and to a rate axis 39 , As is well known in the art, the accelerometers 32 a and b will respond to linear acceleration along their input axes 38 a and b, respectively, and to rotation of the substrate 16 about its rate axis 39 .

The substrate 16 includes a dither or mounting frame 30 from which each of the accelerometers 32 a and b is suspended respectively by a pair of flexures 34 and 36 , which upon application of a dithering force vibrate with an “S bend” motion to translate the accelerometers 32 a and b in a predominantly linear relationship with each other. As will be further described, a periodic drive signal or current is applied via the external connectors 86 a and b to a conductor or conductive path 92 . The magnet 20 emanates a magnetic field substantially perpendicular to the surface of the substrate 16 , whereby the accelerometers 32 a and b are subjected to a periodic dithering motion along their dither axis 41 .

A link 72 is connected to the unsupported end of each accelerometer 32 to insure that the dithering motion imparted to one of the accelerometers 32 a will be of the exact same frequency and in phase with that applied to the other accelerometer 32 b. Without a link 72 therebetween, the accelerometers 32 a and b would tend to vibrate at slightly different frequencies due to slight mass mismatch. Even if driven by a drive signal of common frequency, the accelerometer motions would tend to be out of phase with each other. The link 72 is connected by a flexure 80 a to the free moving end of the first accelerometer 32 a opposite to the flexures 34 a and 36 a, which mount the accelerometer 32 a to the dither frame 30 . The link 72 resembles a lever pivotally mounted above a pivot point 73 provided by a pivot flexure 82 . The link 72 includes first and second lever arms 74 a and b extending in opposite directions from the pivot point 73 . The second lever arm 74 b is connected by a flexure 80 b to the free moving end of the accelerometer 32 b opposite to its end connected by the it flexures 34 b and 36 b to the dither frame 30 . The link 72 includes a pair of parallel members 76 a and 76 b interconnecting the pivot arms 74 a and 74 b to a brace 78 connected to the pivot flexure 82 . In turn, the pivot flexure 82 is mounted along a center axis of the substrate 16 by a support member 84 , which is in turn affixed to the dither frame 30 .

As more fully shown in FIG. 2B , each accelerometer 32 includes an element 48 sensing the acceleration imposed on the sensor 10 and including a pair of vibrating beams 54 and 56 , which are driven to vibrate in opposite directions as indicated by the arrows 57 ′ and 57 ″, respectively. It will be appreciated that the arrows 57 ′ and 57 ″ are aligned in a parallel relationship with the dither axis 41 and are disposed perpendicular to the input axes 38 a and b and to the rate axis 39 (see FIG. 2 A). One end of each of the vibrating beams 54 and 56 is affixed in a relatively stationary relationship to an accelerometer support frame 42 . The remote ends of the vibrating beams 54 and 56 are connected to a proof mass 40 , which is suspended by a pair of hinges 44 and 46 to the frame 42 . As shown in FIG. 2B , the hinges 44 and 46 define a hinge axis 47 about which the proof mass 40 rotates when accelerating forces are applied along the input axis 38 of each accelerometer 32 , its proof mass 40 tends to pivot about its hinge axis 47 . The opposite end of the proof mass 40 is pliantly or flexibly connected to the accelerometer support frame 42 by a strut 52 of reduced cross-section, whereby the proof mass 40 is free to move along its input axis 38 . As shown in FIG. 2C , the hinges 44 and 46 are formed by micromachining the silicon substrate 16 into a relatively thin flexure with respect to the width of the support frame 42 , whereby the proof mass 40 is permitted to pivot about the hinge axis 47 .

As shown in FIGS. 2A , B and C, each of the accelerometers 32 a and b has a corresponding strut 52 a or b, which tends to dampen or attenuate extraneous movements applied to the proof masses 40 a or b. A pendulous axis 53 is associated with each of accelerometers 32 and its proof mass 40 . As best shown in FIG. 2C , each proof mass 40 has a center of gravity 50 . The input axis 38 of each accelerometer 32 intersects the center of gravity 50 and is disposed perpendicular to the pendulous axis 53 . The pendulous axis 53 passes through the center of gravity 50 , the hinge axis 47 and the strut 52 . In an illustrative embodiment of this invention, the input axis 38 is tilted at an acute angle of approximately 80 with respect to the unitary substrate 16 and its support frame 42 . Also the dither axis 41 intersects the centers of gravity 56 a and b of both accelerometers 32 a and b and is perpendicular to their input axes 38 a and b. Undesired moments may be produced by acceleration forces acting along the hinge axis 47 to develop moments about the pendulous axis 53 equal to the product of such forces times a moment arm or equivalent radius of rotation 55 corresponding to the vertical distance between the rate axis 47 and the center of gravity 50 . In a preferred embodiment, each strut 52 is made of reduced cross sectional dimensions, e.g., 1 milli-inch square. A foot 58 is disposed at right angles to the strut 52 to interconnect the end of the strut 52 to the proof mass 40 . One end of the strut 52 is connected to an innerperipheral edge of the accelerometer support frame 42 , and its foot 58 is connected to an edge of the free end of the proof mass 40 remote from its hinges 44 and 46 and its hinge axis 47 . By maximizing the length of the strut 52 , its spring rate is reduced to provide maximum flexibility of the strut 52 . The foot 58 is so configured and dimensioned to render it relatively flexible, so that the foot 58 will “S-bend” to allow rotation of the proof mass 40 substantially only about its hinge axis 47 .

The vibrating beams 54 and 56 are also machined from the substrate 16 but on a surface of the substrate 16 opposite to that of the hinges 44 and 46 . Thus, as acceleration forces cause the proof mass 40 to rotate upwardly as shown in FIG. 2C , both of the vibrating beams 54 are put into compression, whereas when the proof mass 40 is pivoted downwardly as shown in FIG. 2C , both the vibrating beams 54 and 56 are placed in tension. When the vibrating beams 54 and 56 are placed in tension, the frequency of their natural vibration increases, and when put into compression, that frequency decreases.

As shown in FIGS. 2A and B , a drive signal or current is applied via connector pads 62 via a conductive path or conductor 60 that extends in a first direction along the vibrating beam 54 and in a second, opposite direction along the vibrating beam 56 , whereby in the presence of a magnetic field as generated by the magnet 20 , the vibrating beams 54 and 56 vibrate in opposite directions. A drive circuit 64 is incorporated in the accelerometer support Frame 42 to provide the current to the conductor 60 . The drive circuit 64 also provides an output to the external connector path 70 , indicative of the frequency at which the vibrating beams 54 and 56 are vibrating.

A significant advantage of this invention resides in the placement of the first and second accelerometers 32 a and b within the silicon substrate 16 , whereby a single magnet 20 may be employed to direct magnetic flux through each of the accelerometers 32 a and b for the dual purposes of imparting the dithering motion to the accelerometers 32 a and b, and imparting a vibrating motion to the sensor elements 48 in the form of the vibrating beams 54 and 56 . FIG. 1E shows the flux path assembly 18 in its flat state, before it is folded into the configuration shown in FIG. 1 D. The assembly 18 supports and retains the substrate 16 , a pole piece 22 and the magnet 20 in the positions as shown in FIGS. 1C and D , and includes a bottom member 100 , opposing side members 106 a and 106 b and top members 108 a and b. In turn, the assembly 18 is supported within the housing cover 12 by a pair of support legs 110 a and b, which extend downward to mate with a housing ring 14 and, in particular, a projection 15 , whereby the assembly 18 is securely held within the assembled housing cover 12 and base 14 .

As particularly shown in FIG. 1C , the assembly 18 provides a flux path therethrough for the flux emanating from the magnet 20 , and concentrated or focused by the pole piece 22 to pass primarily through the first and second accelerometers 32 a and b, before the flux returns into the restricted legs 102 a and b. Thereafter, the flux passes through the side members 106 a and b and their respective top members 108 a and b and into the magnet 20 to complete the flux path. The structure described, and in particular the pole piece 22 and the restricted legs 102 a and b, concentrate the flux to pass primarily through the accelerometers 32 a and b, such that when drive signals are applied to pass through the conductors 92 and 60 , a dither motion is imparted to the accelerometers 32 a and b, and a natural vibration motion is imparted to the vibrating beams 54 a and b, and 56 a and b. The pole piece 22 has a pair of projections 118 a and b of approximately the same dimensions as the corresponding cross-sectional areas of the accelerometers 32 a and b such that the flux passes primarily through the accelerometers 32 a and b. As shown particularly in FIGS. 1A and E , the restricted legs 102 form an opening 104 therethrough in which only a nominal flux appears, it being understood that most of the flux is concentrated to pass through the legs 102 a and b. It is estimated that this configuration of the flux path assembly 18 doubles the strength of the flux passing through the accelerometers 32 a and b, thus increasing proportionally the voltage appearing on the pickup coils and, thus, reducing the gain of that drive circuit 127 ′ to be explained with respect to FIG. 3 C. Thus, because of the placement of accelerometers 32 a and b in a side-by-side relationship within a single substantially planar substrate 16 , a single magnet 20 and a simple flux path assembly 18 may be employed to provide the magnetic flux to effect efficiently both the dithering and vibrating motion of accelerometers 32 a and b.

As shown in FIG. 2A , the conductive path 92 is deposited on the top surface of the substrate 16 and extends from the external connector 86 a down a leg of the dither frame 30 , horizontally across the flexure 36 a and the bottom peripheral edge of the accelerometer 32 a, down the vertical flexure 80 a, across the link arms 74 a and 74 b, down the vertical flexure 80 b, across the upper peripheral edge of accelerometer 32 b and its flexure 34 b, and down the opposing leg of the dither frame 30 to the external connector 86 b. The conductive path 92 has a center point, which is connected by a conductive path 92 c and a ground terminal 88 to ground. In order to maximize the efficiency of generating the dither motion, the conductive path 92 follows a path along the bottom portion of accelerometer 32 a and its flexure 36 a and the upper portion of the accelerometer 32 b and its flexure 34 b, which portions are closest to the center of the substrate 16 , whereby the magnetic flux emanating from the magnet 20 and focussed by the pole piece 22 and its projections 118 a and b, is concentrated to pass through these portions of the conductive path 92 . The conductive path 92 includes a first effective portion identified by the numeral 92 a mounted on the flexure 36 a and the bottom of the accelerometer frame 42 a of the accelerometer 32 a and a second effective portion 92 b similarly but oppositely mounted on the accelerometer 32 b, both effective portions 92 a and b disposed within the concentrated magnetic flux produced by the magnet 20 and its pole piece 22 . By so configuring the conductive path 92 and its effective portions 92 a and b, the driving force of the dither motion is maximized.

As shown in FIG. 1A , the substrate 16 is provided with a pair of dust covers 17 a and b disposed respectively upon the opposing surfaces of the substrate 16 . The dust covers 17 a and b may also be made of silicon and serve to protect the accelerometers 32 a and b from dust. Illustratively, the inner surfaces of the dust covers 17 a and b are recessed (not shown in the drawings) to permit movement of the proof masses 40 a and b and to provide stops for them.

As described above, the input axis 38 is oriented at an acute angle with respect to a line perpendicular to the surface of the substrate 16 . In an illustrative embodiment of this invention, the assembly 18 mounts the substrate 16 at a compensating angle with respect to the axis of the housing shell 12 , whereby the sensor 10 and thus, the input axes 38 of the accelerometers 32 a and b may be precisely oriented with respect to the vehicle or aircraft carrying the sensor 10 of this invention. The substrate 16 is mounted on a plurality of pads 114 . A pair of support arms 112 a and b extend from the leg 102 a to support the corners of the lower surface (as seen in FIG. 1E ) of the substrate 16 . In turn, a support arm 116 connects the pad 114 c to the leg 102 b of the assembly 18 , whereby the pad 114 e supports a center portion of the opposite edge of the substrate 16 . The numeral 113 designates the center of the opening 104 and is aligned with the pivot point 73 , when the substrate 16 is mounted within the flux path assembly 18 as shown in FIG. 1 A. The pivot point 73 forms the center of the silicon substrate 16 as shown in FIG. 2 A. Similarly, the axis of the permanent magnet 26 , shown in FIG. 1B as being of a cylindrical configuration, is also aligned with the center 113 and the pivot point 73 .

The assembly 18 solves a thermal stress problem resulting from the different coefficients of thermal expansion of the silicon substrate 16 and the flux path assembly 18 , i.e., the assembly 18 expands at a greater rate than the silicon substrate 16 . Illustratively, the silicon substrate 16 has a temperature coefficient of expansion in the order of 2.5 PPM/°C., whereas the assembly 18 is made of a silicon steel (having a silicon content of 3%), which in turn exhibits a temperature coefficient on the order of 11 PPM/°C., which is considerably greater than that of the substrate 16 . In the absence of thermal stress relief, the substrate 16 would tend to buckle, possibly break and/or separate from the assembly 18 . If the substrate 16 warps, the critical alignment of the accelerometers 32 a and b and its various parts will be thrown out of balance with the result that the desired compensation of extraneous motions applied to the sensor 10 will be defeated. As shown in FIG. 1E , each of the support arms 112 a and b, and 116 is disposed perpendicular respectively to each of a corresponding plurality of radial stress lines 111 a, b and c. Thus, as the assembly 18 expands and tends to place a radial stress on the arms 112 a, b, and 116 , their configuration as shown in FIG. 1E permits them to readily flex under the thermal stress rather than buckle or break the substrate 16 . In addition, each of the mounting pads 114 a, b, and c is connected to the substrate 16 by a resilient adhesive such as an epoxy.

As the temperature of the permanent magnet 20 , the assembly 18 and the substrate 16 vary, the mounting structure provided by the assembly 18 and the relative positions of the permanent magnet 20 and the substrate 16 therewith ensure that as the substrate 16 and its assembly 18 expand at different rates, the relative positions or these elements with respect to the magnet 20 remain the same. Therefore, the accelerometers 32 a and b remain in the same relative relationship with the permanent 20 and are exposed to a magnetic flux field of the same strength. If the magnet 20 , the assembly 18 and the substrate 16 were mounted such that the magnet 20 could shift even to a small degree with respect to the accelerometers 32 a and b, the flux emanating through the effective portions 92 a and b and the conductive paths 60 associated with vibrating beams 54 and 56 would also vary, whereby any extraneous motion imparted to the accelerometers 32 a and b, as well as the outputs derived from the conductors 60 of each of the accelerometers 32 a and b, would differ from each other.

The arrangement as shown in FIG. 2A of the accelerometers 32 a and b, their supporting flexures 34 and 36 and the interconnection therebetween by the link 72 provide equal and opposite dither motion to the accelerometers 32 a and b, and isolate the substrate 16 , its dither frame 30 and the accelerometers 32 a and b from extraneous stress, such that error signals are not introduced by data processing into the resultant force signals F and rotational signals and permits data processing using the output of the accelerometers 32 a and 32 b by relatively simple differentiating and scaling techniques. Further, the structure of FIG. 2A may be implemented by micromachining techniques upon a silicon substrate 16 , whereby the resultant structure is produced at a low cost and with a precision of which the prior art accelerometers were simply not capable. In turn, the extreme accuracy of construction afforded by micromachining techniques permits the relative placement of accelerometers 32 a and b and its link 72 to a precision in the order of 40 micro inches. As a result of such accuracy, the accelerometers 32 a and b are placed in precise balance with each other such that extraneous movements imposed upon the frame 30 do not upset this balance and introduce erroneous signals into the outputs of the accelerometers 32 a and b as may be otherwise caused by even slight misalignment of the accelerometers 32 a and 32 b.

First, the accelerometers 32 a and 32 b are mounted upon opposing sides of the dither frame 30 by their flexures 34 a and 36 a and 34 b and 36 b, respectively. Each of the flexures 34 and 36 is formed from the silicon substrate 16 to a height equal to the width of the substrate 16 , illustratively of 20 mils, and a thickness of 1.4 mil corresponding to the vertical dimension of the flexures 34 and 36 as shown in FIG. 2 A. The length of each of the flexures 34 a and b and 36 a and b is selected to provide a spring rate relative to the mass of accelerometers, e.g., of 0.1 gram, that will cause the flexures 34 and 36 to flex in an “S-bend” when subjected to the dither motion. The spring rate of the flexures is proportional to T 3 /L 3 , where T is the thickness of the flexures 34 and 36 and L is the length thereof. The length L and thickness T of the flexures 34 and 36 are set such that when dither motion is applied, the flexures 34 and 36 then flex in an S configuration, as shown in FIG. 2 A. Such “S-bend” flexures 34 and 36 permit the accelerometers 32 a and b to translate with predominantly linear motion, i.e., the vibrating beams 48 a and 48 b (as well as the other elements) of accelerometers 32 a and 32 b remain substantially parallel to each other as they are dithered along the dither axis 41 . In addition, the flexures 34 and 36 permit accelerometers 32 a and 32 b to move in a predominantly linear fashion with only an insignificant nonlinear frequency component imposed thereon.

The link 72 mechanically interconnects the first and second accelerometers 32 a and b so that any motion include dithering motion and extraneous motions applied to one of the accelerometers 32 , will also be applied in precisely equal and opposite fashion to the other accelerometer 32 . In this fashion, the outputs of the accelerometers 32 a and b may be processed simply by sum and difference techniques to provide a force signal F and the rotational signal, as well as to cancel out erroneous signals. Without the link 72 , the accelerometers 32 a and 32 b would operate at different frequencies due to slight mass mismatch of the proof masses 40 . If driven at a common frequency, the accelerometers 32 a and 32 b would without the link 72 operate out of phase with each other (other than 180°).

The configuration and the manner of mounting the link 72 are effected to permit the link 72 to effectively pivot about the pivot point 73 intersecting an axis passing through the lever arms 74 a and b. The pivot point 73 is disposed at a selected point along the length of the pivot flexure 82 . As shown in FIG. 2A , the bottom end of the pivot flexure 82 is affixed to the support member 84 and extends vertically along the dither axis 41 . The length of the pivot flexure 82 is selected, e.g., 100 mils, to impart a simple bending thereto, whereby that portion from the pivot point 73 to the point of interconnection to the link 72 is permitted to flex about the pivot point 73 , while the remaining portion of the flexure 82 between the pivot point 73 and the support member 84 flexes in a smooth arc. In this fashion, the end points of the link 72 are disposed a radial distance from the pivot point 73 equal to the effective radius of rotation provided by the “S-bend” flexures 34 and 36 for the accelerometers 32 a and 32 b.

As indicated above, the length of the pivot flexure 82 is determined so that it flexes with only a simple arc bending. To accommodate a pivot flexure 82 of the desired length, it is necessary to configure the link 72 with a U-shaped configuration comprised of the parallel members 76 a and b and the interconnecting member 78 . In addition, a portion of the support member 84 is removed to provide a cut out 85 , whereby the length of the pivot flexure 82 is set to provide the simple bend motion.

The vertically oriented flexures 80 a and b as shown in FIG. 2A are dimensioned and, in particular, their lengths are set such that they exhibit 50% simple arc bending and 50% “S-bend” motion. Opposite ends of the vertical struts 80 a and b are respectively interconnected between an edge of one of the accelerometers 32 a and b and an end of one of the link members 74 a and b. Portions of the link 72 and the accelerometers 32 are removed to provide cutouts 71 and 139 , respectively, so that the precise length of the flexures 80 a and b is determined to ensure that the flexures 80 have characteristics of 50 percent simple motion and 50 percent “S-bend” motion. Further with such characteristics, it is assured that any motion imparted by the flexures 80 to one of the accelerometers 32 is imparted as a sinusoidal function to the other without introducing a higher order harmonic into the translation motion. Without such flexures 80 and the link 72 , the dither motion as well as other extraneous motion applied to the substrate 16 , could impose high order harmonic motion to the accelerometers 32 a and b, whose outputs upon demodulation would bear an undesired bias signal.

As indicated above, the flexures 34 and 36 are made of such dimensions and, in particular, their length such that they flex with an “S-bend”. In particular, one end of each of the flexures 34 and 36 is respectively affixed to the inner periphery of the dither frame 30 and the other end to the accelerometer 32 . An external edge portion of the accelerometer support frame 42 is removed to provide a cut out 33 so that the length of the flexures 34 and 36 is critically set to provide the desired “S-bend” motion and so that the other end of the flexures 34 and 36 are connected to a midpoint of the horizontal edges of accelerometers 32 a and b. As shown in FIG. 2A , the flexures 34 and 36 support accelerometers 32 a and b so that their centers of gravity 50 and the pivot point 73 lie along the central axis of the substrate 16 so that the center axis coincides with the dither axis of 41 .

The “S-bend” flexures 34 and 36 have respectively pivot points 35 and 37 , which are disposed a distance ⅙th of the flexure length from the inner periphery of the dither frame 30 . The “S-bend” flexures 34 and 36 form respectively an effective radius from their pivot points 35 and 37 to their points of connection with their support frames 42 . That effective radius equals to ⅚ of the length of the flexures 34 and 36 , which in turn precisely equals the radius provided by the lever arms 74 from their pivot point 73 to the points of interconnection of the upright flexures 80 a and b to the extremities of the lever arms 74 a and b. By providing the link 72 and the accelerometers 32 a and b with equal radii of rotation about the respective pivot points 73 , and 37 and 35 , it is assured that the link 72 will provide equal and opposite motion to the accelerometers 32 a and b. As a result, if any extraneous noise is applied to one of the accelerometers 32 a and b, a like and opposite motion will be applied to the other, so that upon processing any noise in the outputs of the accelerometers 32 is effectively removed by sum and difference techniques.

Upon application of the dithering motion to the accelerometers 32 a and b, the “S-bend” flexures 34 and 36 move up and down in a substantially parallel relationship to each other due to the “S-bend” flexing of their flexures 34 and 36 . Each flexure 34 and 36 has a center point 239 and 240 , respectively. The bending motion resembles two smooth curves, the first terminating at the center point in one direction and the second curve with an opposite curve meeting the first at the center point. The “S-bend” flexures ensure that the horizontal and vertical edges of the support frames 42 a and b remain precisely parallel with the inner horizontal and vertical peripheral edges of the dither frame 30 .

As indicated above, the “S-bend” flexures 34 and 36 provide an effective rotation of the accelerometers 32 a and b about their pivot points 35 and 37 . In an illustrative embodiment, the commonly applied dithering forces move accelerometers 32 a and b through a positive and negative angular rotation with respect to their rest positions, whereby the centers of gravity 50 a and b move from the center axis of the substrate 16 a distance of only 37 microinches for a dithering motion having an amplitude of 1 mil along the dithering axis 41 .

The construction of accelerometers 32 a and b from the silicon substrate 16 results in extremely close alignment of the accelerometers 32 . This results from the high degree of flatness of the silicon substrate 16 and the relative proximity of the accelerometers 32 a and b micromachined from the substrate 16 . The flexures 34 , 36 , 80 and 82 are produced by etching near the surfaces of the substrate 16 . Such micromachining ensures that the input axes 38 a and b will be precisely perpendicular to the dither axis 41 , at least as good as the flatness and parallel relationship of the surfaces of the silicon substrate 16 , which can typically be achieved to a high degree. Thus, this invention achieves close alignment of the input and dither axes 38 and 41 , thus overcoming the problem of prior art Coriolis sensors with regard to such alignment. The suspension of the accelerometers 32 a and b by their flexures 34 a and 36 a, and 34 b and 36 b from opposing sides of the dither frame 30 so that their input axes 38 a and b point in opposite directions and the use of the link 72 provide excellent nonlinearity motion cancellation.

The well known Eular-Buckling curves represent the structural tensioning and compression characteristics of the accelerometers their vibrating beams 54 and 56 . The back-to-back orientation ensures that when the vibrating beams 54 and 56 of the accelerometer 32 a are in tension, the beams of the other accelerometer 32 b are in compression, and vice versa. As will be explained, the outputs of the accelerometers 32 a and 32 b are summed together to provide an indication of linear acceleration. This orientation insures that the beams 54 and 56 are operating in complementary portions of these curves and the summed outputs of the accelerometers 32 a and b provide an accurate indication of the linear acceleration by canceling the higher order nonlinearities of the vibrating beams 54 and 56 . In addition, extraneous movements acting on the accelerometers 32 a and b will at least to a first order of measure, tend cancel or dampen each other, whereby extraneous signals do not appear in the summed accelerometer outputs. In an analogous fashion when the difference of the accelerometer outputs is taken, the canceling characteristics of these curves ensure that second order nonlinearities in the resultant angular rotation signal will also average.

The construction of the two accelerometers 32 a and b from the silicon substrate 16 offers other advantages. First, the configuration and the dimensions of the accelerometers 32 , the various flexures and the link 72 may be determined with an extreme degree of accuracy, e.g., 40 microinches, so that the relative position of these elements is controlled to a like degree. Second, the construction of the flexures in the plane of the silicon substrate 16 ensures that the accelerometers 32 are dithered in that plane. As noted above, the link 72 ensures that the accelerometers 32 a and b move in equal and opposite directions under the influence of the applied dithering motion. Thus, the centers 50 a and b of gravity of the accelerometers 32 a and b are placed precisely upon the center axis of the substrate 16 , which is aligned with the dither axis 41 with a high degree of precision, whereby the dither motion caused by the current passing through the drive coils a and b causes the dithering motion to be applied precisely along the center axis of the substrate 16 . Such accuracy ensures that extraneous motions otherwise resulting from the dither motion are not imposed upon the accelerometers 32 a and b.

Secondly, the suspension of accelerometers 32 a and b by the “S-bend” flexures 34 and 36 , which are also formed in the plane of the silicon substrate 16 , produces a motion of the accelerometers 32 a and b of relatively small, opposing arcs as a result of this dithering motion. In one illustrative embodiment, dithering at maximum displacement (amplitude) of 1 milli-inch (corresponding to 1 degree of the total peak to peak angular travel), displaces the accelerometers 32 a and b from their center axis by a mere 37 microinches. During a single cycle of motion of each of the accelerometers 32 a and b up and down along the dither axis 41 , each accelerometer 32 is subjected to 2 translations as it rotates about its effective radius provided by its flexures 34 and 36 . However, since these double translations or “bobbings” occur within the plane of the silicon substrate 16 and not along the input axes 38 a and b, the problems that have occurred with the prior art sensors of parallelogram configuration are avoided. First, a corresponding double frequency error signal is not imposed upon the inputs of the accelerometers 32 , which required a phase servo adjustment in the processing as described in U.S. Pat. No. 4,799,385. Second, there is no need to offset the center of oscillation or to couple turn-around acceleration into the accelerometer input axis. As a result, for any position of the accelerometers 32 a and b during their dithering motion, there is very little double frequency motion imposed upon their input axis 50 , thus, there is no need to “steer” out the misalignment by adding a bias to the dither drive signal.

The various features of the silicon substrate 16 may be micromachined by various techniques well known in the prior art such as a wet chemical etch or a dry chemical etch such as plasma etching, sputter etching or reactive ion etching. For a detailed discussion of such techniques, reference is made to the following publications, which are incorporated herein by reference: VLSI FABRICATION PRINCIPLES by Sorab K. Ghandhi and SILICON PROCESSING FOR THE VLSI ERA. Vol. 1— PROCESS TECHNOLOGY by S. Wolf & R. J. Tauber.

In this illustrative embodiment of the silicon substrate 16 , the maximum misalignment of the accelerometers 32 from the substrate center axis would be less than 0.1 millirad. This has the benefit of not fully imposing second harmonic distortion resulting from the dither drive into the rotational component signal outputted by the accelerometers 32 a and b. Otherwise, as is disclosed by the prior art parallelogram drive arrangements, such second harmonic drive distortion could be multiplied by the squaring action of double dipping to generate primary and third harmonics, which can be coupled into the rate channels as error. These errors are avoided by the side-by-side placement and accurate micromachining of the accelerometers 32 a and b within the substrate 16 .

As noted above, each of the accelerometers 32 a and b is suspended by “S-bend” flexures 34 and 36 , which provide effective radii of rotation equal to that radius provided by the link arms 74 a and b; without such construction, the accelerometers 32 a and b would dither with a non-sinusoidal motion, which would introduce high order harmonic distortion in the rate signal. It is contemplated that there will be some coupling due to the offset of the input axis 38 resulting from the centers 50 of gravity being disposed above the flexures; however, such coupling is minor compared to that introduced by the parallelogram structures of the prior art.

Referring now to FIG. 3A , there is shown a dither drive circuit 127 for providing a sinusoidal voltage to be applied across the effective portions 92 a and b. The conductive path 92 forms the first effective portion 92 a for imparting a vibrating motion to the accelerometer 32 a and the second effective portion 92 b for imparting a vibrating motion to the accelerometer 32 b. The center point of the conductor 92 is connected to ground via the conductor 92 c and a ground terminal 88 . As shown in FIGS. 1A and 1D , a magnetic field is generated perpendicular to the surfaces of the substrate 16 and is focused by the pole piece 22 through the accelerometers 32 a and 32 b. Illustratively, the conductor 92 takes the form of a deposit of gold. In an illustrative embodiment of this invention wherein the length of the conductor 92 extending between terminals 86 a and 88 (or 86 b and 88 ) is approximately 1 inch and is deposited to a depth of 1μ meter and a width of 10μ meter, the resistance offered by such a length of the conductor 92 is in the order of 100 ohms. When the magnetic flux crosses the conductive path 92 , a voltage is induced thereacross of approximately 0.5 volt, which is approximately 2500 times the voltage amplitude of the velocity signal which is outputted by the dither drive circuit 127 of FIG. 3A on its output 86 and 91 . To effectively remove this resistance voltage, a bridge 125 shown in FIG. 3A is employed with one leg thereof being formed by the effective portions 92 a and b connected in parallel, and a second leg by a reference conductor 93 which is disposed on the dither frame 30 and has ends connected to terminals 91 and 95 , as shown in FIG. 2 A. The effective portions 92 a and b are connected in parallel by connecting the terminals 86 a and b together; in turn, the terminal 88 forms one node of the bridge 125 and the connected terminals 86 a and b another node. The conductive path 92 forms the two effective portions 92 a and b connected, with the interconnecting portion of conductor 92 being connected via the conductive path 92 c to the ground terminal 88 . The effective portions 92 a and 92 b are connected in parallel to form one leg of the bridge 125 . The other leg of the bridge 125 is formed of the reference conductor 93 having one-half the length of the conductor 92 between the terminals 86 a and 88 (or 86 b and 88 ), e.g., one-half inch. The reference conductor 93 is made of the same material as that of conductor 92 , e.g., gold, and is deposited to a like depth, whereby a like voltage, e.g., 0.5v, is developed across both of the parallel connected effective portions 92 a and b, and the reference conductor 93 . A single drive voltage is applied from a first bridge node 129 to ground, whereas an output of the bridge 125 as developed across bridge nodes 86 and 91 is taken and applied to a first operational amplifier 128 , which subtracts the voltage developed across the reference conductor 93 from that developed across the parallel connected effective portions 92 a and b. A second operational amplifier 130 provides the remaining gain to boost the output of the first operational amplifier 128 to approximately 2.5v peak at the output 132 . A feedback path is connected to the bridge circuit 125 providing position feedback plus an excess phase shift due to the high-order operational amplifier poles, whereby an oscillating circuit is established to provide the sinusoidal signal to drive the effective portions 92 a and b. The output 132 is clamped by a pair of Zener diodes D 1 and D 2 connected in opposition between the output 132 and ground, to clamp the output 132 and thereby stabilize the drive signal applied to the effective portions 92 a and b.

As shown in FIG. 3B , the velocity signal appearing on the output 132 of the dither drive circuit 127 is applied to a zero-crossing detector circuit 133 , whose outputs are used to gate the counters for counting the crystal clock signal, whereby the Coriolis rate signal and acceleration force signal can be demodulated. The velocity signal is coupled to an operation amplifier 134 by a capacitor C 1 and resistor R 10 to generate a zero-crossing signal. The open loop gain of the operational amplifier 134 “squares” the velocity signal and applies the “squared” signal to a pair of CMOS logic gates 136 and 138 connected in parallel with each other; these gates effect a voltage shift of the signal to levels compatible with the counters, e.g., 0 to + or −5v. Another inverting logic gate 140 inverts the signal. The signals illustrated in FIG. 3B are applied to the counters 152 and 154 , as shown in FIG. 3D , to count a signal indicative of the resonant, natural frequency for each half cycle of the dithering frequency f, whereby the Coriolis rate component is demodulated by inverting every other sample. As described in detail in U.S. Pat. No. 4,590,801, the acceleration is the sum of each such sample.

Referring now to FIG. 3C , there is shown an alternative of embodiment of the dither drive circuit 127 ′, which provides a dither drive signal across the external connectors 86 a and 86 b to the effective portions 92 a and b. As described above, a magnetic field is generated and directed by the magnet 20 and its flux path assembly 18 perpendicular to the surfaces of the substrate 16 and the effective portions 92 a and b disposed thereon, whereby a force is generated by the current flowing through the effective portions 92 a and b to move the accelerometers 32 a and b in a substantially rectilinear, vibrating movement up and down along the dither axes 41 as shown in FIG. 2 A. The accelerometers 32 a and b vibrate or dither at the frequency f determined by the mechanical characteristic including the spring rates of the flexures 34 , 36 , 80 and 82 the mass of the accelerometers 32 a and b. The dither drive signal outputted by the dither drive circuit 127 ′ is of a frequency corresponding to the frequency f of dither vibration and, as explained above, is used in the further processing of the accelerometer outputs to demodulate those signals to provide a force signal F and a rotational signal. Further, a wire (not shown) is disposed on the opposite side of the substrate 16 (from that shown in FIG. 2A ) and forms first and second pick-off portions 92 a′ and 92 b′. The interconnection of the pick-off portions 92 a′ and 92 b′ deposited on the opposite side to ground 35 is more clearly shown in FIG. 3 C. As accelerometers 32 a and b are vibrated, the pick-off portions 92 a′ and b′ move through the magnetic field created by the unitary magnet 20 and its assembly 18 , a current is induced therein and the resultant voltage is applied via resistors R 11 and R 12 to a pair of operational amplifiers 142 and 144 to be successively amplified with a relatively high gain, before being applied as the dither drive signal to the effective portions 92 a and b. Zener diodes D 4 and D 5 serve to clamp the dither drive voltage as derived from the output of the operational amplifier 144 to a known voltage level.

The configuration of the accelerometers 32 a and b within their silicon substrate 16 and the flux path assembly 18 and its unitary magnet 20 develop a considerable force in excess of that minimum turn-around acceleration required to effect the dither motions of accelerometers 32 a and b. It is understood in the art that a minimum turn-around acceleration is needed to cause each of the accelerometers 32 a and b to stop going in one direction and to accelerate in the opposite, whereby the dithering motion may occur. The acceleration force F tending to cause the dithering motion of accelerometers 32 a and b is set out by the following equation:

F= mg= L•i×B   (1)

where i is the current passing through the conductive path 92 making up the effective portions 92 a and b, L is the effective length of that portion of the conductive path 92 within the magnetic flux passing through the accelerometers 32 a and b, i.e., the length of the effective portions 92 a and b, and B is the magnitude of the flux. In an illustrative embodiment of this invention, a current of 5 milliamp may be applied to each of the effective portions 92 a and b, the effective portions 92 a and b may have an effective length L of 6 mm and 8 kilogauss may be readily provided bit the magnet 20 and its assembly 18 . Solving equation (1) for mass m, where g is the universal gravity constant, it is shown that a force of 2.4 milligrams may be readily developed by this illustrative embodiment. In such an embodiment, the resonant frequency of the dithering motion imposed upon the accelerometers 32 a and b is approximately 500 hz and a displacement D of accelerometers of 1 milli-inch. The drive acceleration a may be calculated by the following: $$ a = D ⁡ ( 2 ⁢   ⁢ π ⁢   ⁢ f ) 2 K ( 2 )

where D is the displacement, f is the dither frequency and K is a conversion factor. The calculated force for 1 milli-inch of displacement D at 500 Hz is 25 g's peak acceleration. Where the mechanical gain of the spring mass system formed by accelerometers Q is set at a modest value of 1,000, the force developed by the interaction of a current passing through the conductive path 92 and the magnetic flux directed through the accelerometers 32 , is 0.025 g's (25 g's/1,000). This force is sufficient to accelerate the calculated mass force of 0.024 grams. It is noted that the Q of pure crystals may be as high as 10,000, demonstrating that the dithering system described above is more than capable of developing sufficient force to effect the required dithering drive motion.

The following calculations demonstrate that the values of ε, the voltage induced in the pick-off portions 92 a′ and 92 b′, is relatively high compared to the noise found in those operational amplifiers as would be incorporated into the drive circuit 127 ′, as shown in FIG. 3 C. Values of ε are provided by the following equation:

ε= v×B•L   (3)

where v is the amplitude of the velocity output signal of the accelerometers 32 , B is the strength of the magnetic field crossing the effective portions 92 a and b, is the effective length of the conductor within the magnetic flux field. For a dither displacement D of 1 milli-inch, a natural frequency of accelerometer of 500 Hz, a velocity signal v of approximately 8 cm/sec., a length of the effective portions 92 a and b of 6 mm, and a flux strength of 8 kilogauss, the output of a single pick-off portion 92 a′ is 0.4 MV. If the outputs of accelerometers 32 a and b are connected in series, the output voltage is doubled to 0.8 MV. An operational amplifier, as may be incorporated into the drive circuits of FIGS. 3A and C , typically has a noise of 0.1 μv for a bandwidth of 10K Hz. If the operational amplifier has again of 3×10 3 , its output may typically be 2.4v peak, providing a noise to peak signal ratio of 0.01%, which is a good indicator that the sensor 10 of this invention is a good velocity sensor for the inherent of noise level found in the available operational amplifiers.

The accuracy with which the rate and acceleration sensor 10 may be made, the symmetry of the accelerometers 32 a and b and their suspension by the flexures 34 and 36 , and the interconnection of the link 72 to impose equal and opposite motions on the accelerometers 32 a and b, have an accumulative effect to greatly simplify the processing of the accelerometer output signals, essentially reducing it to a cosine demodulation step. This can be done every hale cycle, since neither sine nor double frequency sine demodulation is needed as was the case with the parallelogram structures of the prior art. Basically, the outputs of accelerometers 32 a and b are subtracted from each other to provide the linear acceleration signal and to average both signals while inverting every other sample to demodulate for the cosines to produce a rate of rotation signal ω. Neither an alignment servo nor a phase servo is needed for such processing thus increasing the band width of the rotational acceleration signal to be 1K Hz in one illustrative embodiment of this invention.

The rate and acceleration sensor 10 has a sensitivity to rotational acceleration imposed about its rate axis 39 , i.e., the moment of each of accelerometers 32 a and b about the rate axis 39 , which acceleration sensitivity will introduce an undesired noise component in the subsequent demodulation processing of the accelerometer output signals. That noise component can be effectively eliminated by differentiating the rotation rate signal e and scaling it. In effect, as indicated above, the demodulated outputs of accelerometers 32 are a measure of its rotation rate signal ω, which can be differentiated to obtain an indication of the angular acceleration of each accelerometer 32 . Since the dimensions and, in particular, the distance between the rate axis 39 and each of the centers 50 a and b of gravity is known to a high degree of precision, e.g., 40 microinches, that equivalent radius of rotation is multiplied by a measured angular acceleration force to obtain an accurate indication thereof of the linear acceleration caused by the angular acceleration. The calculated acceleration moment is subtracted from the accelerometer outputs to reduce or substantially eliminate such acceleration sensitivity.

Referring now to FIG. 3D , there is shown how the output signals f 1 and f 2 as derived from the respective drive circuits 127 a and c are processed and, in particular, are applied respectively to counters 152 and 154 . As explained above, as the vibrating beams 54 and 56 are placed in tension or in compression due to accelerations being applied along the force sensing axes 38 of the respective accelerometers 32 , the frequencies of the output signals f 1 and f 2 change. The dither drive circuit 127 b may preferably take the form of that circuit shown in FIG. 3C or alternatively FIG. 3 A. The drive circuits or signal generators 127 a and c may illustratively take the form of that circuit shown in FIG. 3 A.

The dither drive circuit 127 b provides an output signal, which is applied to the gating circuit 133 as discussed above with regard to FIG. 3 B. The output of the gating circuit 133 is a pair of squared gating signals which are applied to the counters 152 and 154 . This pair of gating signals occur at the velocity zero-crossings to gate the counters 152 and 154 . This is approximately a reading at 1k Hz or both edges of the velocity zero-crossings. The counters 152 and 154 count the frequencies of the accelerometer output signals f 1 and f 2 with respect to a reference clock signal generated and applied by a reference clock 150 to each of the counters 152 and 154 . In turn, a microprocessor reads the output of the counters 152 and 154 at an illustrative frequency of 1k Hz and process these counts to provide an indication of Δv and Δθ.

As explained in detail in commonly assigned U.S. Pat. No. 4,786,861, Δv is provided by the following equation:

Δ v i =A [ ( N 1 i −N 2 i )+ FT+B ( N 1 i +N 2 i )]  (4)

where vi is the “ith” sample of the velocity signal, A and F are scale factors, N1 i is the count derived from the counter 152 over a 1k Hz (1 m sec) period for the “ith” sample, N2 i is the count obtained from the counter 154 for the “ith” sample, T is the time period and B is the bias correction term. As well known in the art, Δθ i is provided by the following equation:

Δθ i =a (cos N 1 i +cos N 2 i )+ b (cos N 1 i −cos N 2 i )  (5)

where a is a scale factor and b is a bias/correction term, and

cos ( Nl i )= Nl i −N 1 (i-1) , over each 10 kHz period  (6)

or

cos ( N 1 i )=(−1) i N 1 i , at 10 kHz rate.  (7)

cos (Nl i )=Nl i −N1 (i-1) over each 500 Hz period or (6)

cos (N1 i )=(−1) i N1 i , at 1k Hz rate. (7) accelerometers 32 a or b, divided by the equivalent radius of rotation, r eq in accordance with the following equation:

α=A linear /r eq   (8)

In turn, angular acceleration α is a function of the measured rotation rate in accordance with the following equation:

α=dω/dt  (9)

In turn, the rotation rate may be expressed as follows:

ω=dθ/dt  (10)

Since the derivative of the rotation rate ω is equal to acceleration α, accelera $$ ω = Δ ⁢   ⁢ θ Δ ⁢   ⁢ t

be expressed by t following equation: $$ α = ω i - ω ( i - 1 ) Δ ⁢   ⁢ t = Δ ⁢   ⁢ θ i Δ ⁢   ⁢ t - Δ ⁢   ⁢ θ ( i - 1 ) Δ ⁢   ⁢ t Δ ⁢   ⁢ t ( 11 )

Thus, correction for linear acceleration A linear is provided by the following equation: $$ A linearcorrection ⁢   ⁢ α ⁢   ⁢ r eq . = r eq . ⁢ Δ ⁢   ⁢ θ i Δ ⁢   ⁢ t - Δ ⁢   ⁢ θ ( i - 1 ) Δ ⁢   ⁢ t Δ ⁢   ⁢ t ( 12 )

In turn, the microprocessor 156 is programmed in a conventional fashion to subtract values of A linear correction from the accelerometer outputs f 1 and f 2 to correct for angular acceleration.

FIG. 4 shows a plan view of one embodiment of a rate and acceleration sensor 200 including a link 210 according to one embodiment of the present invention. Link 210 comprises a simple rectangular beam 212 which is formed in the substrate material and in the two epitaxial layers 214 formed on opposing parallel surfaces of the substrate. Rectangular beam 212 is inherently balanced and axes-symmetric about its geometric center which is also the center of mass of rectangular beam 212 . Thus, the simple rectangular shape of rectangular beam 212 may be analyzed using classical methods commonly known to those of skill in the art. Link 210 , including rectangular beam 212 , minimizes mass while providing stiffness equal to or greater than that of the complex asymmetrical shape of the prior art.

In one preferred embodiment, a rectangular beam 212 is formed in an axis which is parallel to the rate axis 216 and normal to dither axis 218 . Link 210 is mechanically connected to accelerometers 220 by dither axis flexures 222 such that the geometric center of rectangular beam 212 is intermediate between dither axis flexures 222 . Link 210 further comprises eight epitaxial struts or legs 224 (four shown) which form an ‘X’ shape. The intersection of ‘X’ struts 224 is essentially centered at the geometric center of rectangular beam 212 . The ends of ‘X’ struts 224 opposite the intersection point connect to either of two solid cantilevered frame members 226 formed in the substrate material. A first four epitaxial struts 224 are formed in first epitaxial layer 214 and a second four epitaxial struts 224 (not shown) are formed in second epitaxial layer 214 .

The intersection point of ‘X’ struts 224 is both the geometric center and the center of mass of ‘X’ struts 224 by virtue of the symmetric ‘X’ shape of ‘X’ struts 224 . Thus, ‘X’ struts 224 are inherently balanced and axes-symmetric about the intersection point of ‘X’ struts 224 . In one preferred embodiment, both the geometric center and the center of mass of link 210 are located essentially at the geometric center and center of mass of rectangular beam 212 , which is also the geometric center and center of mass of ‘X’ struts 224 . Link 210 , including rectangular beam 212 and ‘X’ struts 224 , is thus inherently balanced and axes-symmetric about its own geometric center and center of mass by virtue of the location of ‘X’ struts 224 relative to rectangular beam 212 .

In one preferred embodiment, struts 224 are formed at 45 degree angles to rate and dither axes 216 , 218 . Solid dither axis flexures 222 connect the ends of link 210 to the free moving ends of accelerometer blocks 220 . Link 210 , including rectangular beam 212 and epitaxial struts 224 , provides reduced sensitivity to vibration in the dither cross-axis, having a cross-axis vibration sensitivity on the order of 4 or more times the dither frequency. Link 210 in combination with dither axis flexures 222 provides a linkage between accelerometer blocks 220 which pivots about the geometric center of rectangular beam 212 whereby the motion of one accelerometer block 220 , including dither motion, is transmitted to the other accelerometer block 220 as a sinusoidal function without introducing a higher order harmonic into the translation motion. Thus, the dithering motion imparted to one accelerometer is of the exact same frequency and precisely 180 degrees out of phase with that applied to the other accelerometer.

Link 210 , including epitaxial struts 224 , can be fabricated in double-sided epitaxial silicon wafers by conventional wet etching processing using a back-biased voltage as an etch stop. For example, wet etching may be accomplished using a potassium hydroxide (KOH) based etchant known to those of skill in the art that takes advantage of the orientation-dependent properties of silicon to etch specific shapes in silicon, also known as KOH processing. Link 210 , including rectangular beam 212 and epitaxial struts 224 , is insensitive to process variations in any of the widths of dither axis flexures 222 ; the etch times for forming link 210 , including rectangular beam 212 and struts 224 ; or the final width of struts 224 . For a detailed discussion of KOH etching, reactive ion etching and other etching techniques, reference is made to the following above incorporated publications: VLSI FABRICATION PRINCIPLES and Silicon Processing for the VLSI Era, Vol. 1: Process Technology.

Alternative Embodiments

One alternative embodiment of the present invention is shown in FIG. 5 . Link 310 comprises a rectangular beams 312 formed in the substrate and in the two epitaxial layers 314 formed on opposing surfaces of the substrate. Four ‘X’ struts or legs 316 of the configuration shown in FIG. 5 are formed in a first epitaxial layer 314 . Two perpendicular struts or legs 318 are formed in the opposing epitaxial layer 314 along an axis parallel to the dither axis 320 . Thus, link 310 comprises solid rectangular beam 312 formed in the substrate material and in two opposing epitaxial layers 314 ; four ‘X’ struts 316 formed in one epitaxial layer 314 ; and two struts 318 formed in the opposing epitaxial layer 314 essentially perpendicular to rectangular beam 312 at the approximate geometric center of rectangular beam 312 . The ends of perpendicular struts 318 connect to rectangular beam 312 and to either of two solid cantilevered frame members 322 formed in the substrate material. As in the configuration of FIG. 4 , the intersecting ends of ‘X’ struts 316 intersect rectangular beam 312 at the approximate geometric center of rectangular beam 312 and the ends of ‘X’ struts 316 opposite the intersection point connect to either of two solid cantilevered frame members 322 . As in the configuration of FIG. 4 , the geometric center and center of mass of rectangular beam 312 is also the geometric center and center of mass of link 310 about which link 310 is inherently balanced and axes-symmetric.

By providing ‘X’ struts 316 and perpendicular struts 318 which do not overlay one another in a plan view, link 310 may be fabricated using a combination of KOH etching and reactive ion etching. Perpendicular struts 318 are fabricated using KOH etching and back-biasing to ensure the integrity of epitaxial layer 314 . Opposing epitaxial layers 314 are cleared from one another using KOH etching. Perpendicular struts 318 are then defined using a reactive ion etching operation on the substrate side of epitaxial layer 314 which improves strut definition, allows for the fabrication of thinner struts, and provides a link which pivots about the approximate geometric center of rectangular beam 312 . Link 310 , including ‘X’ struts 316 and perpendicular struts 318 , increases stiffness over the configuration of FIG. 4 while providing the same relatively reduced sensitivity to vibration in the dither cross-axis. Link 310 , including rectangular beam 312 and epitaxial struts 316 , 318 , is insensitive to process variations in any of the widths of flexures 322 ; the etch times for forming link 310 , including rectangular beam 312 , ‘X’ struts 316 and perpendicular struts 318 ; or the final width of either ‘X’ struts 316 or perpendicular struts 318 .

FIG. 6 shows another alternative embodiment of the present invention. Link 410 comprises solid rectangular beam 412 formed in the substrate material and in the two epitaxial layers 414 formed on opposing surfaces of the substrate. Four struts or legs 416 are formed perpendicular to rectangular beam 412 at the approximate geometric center of rectangular beam 412 , two formed in each opposing epitaxial layer 414 . In one preferred embodiment, a first pair of perpendicular struts 416 formed in a first epitaxial layer 414 overlie the second pair of struts 416 formed in the second epitaxial layer 414 formed on the opposing surface of the substrate. In one preferred embodiment, each perpendicular strut 416 is formed having a jog or “dog leg.” The “dog leg” is formed such that the two longitudinal portions 418 , 420 are slightly offset from one another. In other words, the “dog leg” 422 formed between longitudinal portions 418 , 420 has a finite length longer than the combined widths of longitudinal portions 418 , 420 . The “dog leg” aids in clearing the bulk silicon from between overlying struts 416 . In one preferred embodiment, the “dog leg” is located at the approximate geometric center of perpendicular strut 416 . As in the configuration of FIG. 4 , the geometric center and center of mass of rectangular beam 412 is also the geometric center and center of mass of link 410 about which link 410 is inherently balanced and axes-symmetric. The configuration of FIG. 6 produces a link which pivots about the approximate geometric mid-point of rectangular beam 412 and provides the simplicity of analysis associated with the configurations of FIGS. 4 and 5 , above.

FIG. 7 shows another alternative link configuration. The link configuration of FIG. 7 is a symmetrical ‘U’ shape providing an analytically simplified configuration. Link 510 comprises a pair of parallel members 512 a, 512 b and interconnecting member 514 . The lengths of parallel members 512 a, 512 b extending along the sensor's dither axis 516 are substantially equal. Parallel members 512 a, 512 b interconnect pivot arms 518 a, 518 b to interconnecting member 514 which is connected to pivot flexure 520 . Link 510 resembles a lever pivotally mounted about a pivot point 522 provided by pivot flexure 520 . Thus, link 510 is inherently balanced and axes-symmetric about an axis 524 parallel to the longitudinal axes of parallel members 512 and passing through the geometric center of interconnecting member 514 . In one preferred embodiment, pivot flexure 520 , including pivot point 522 , is centered on axis 524 . Thus, link 510 is inherently balanced and axes-symmetric about pivot flexure 520 and about pivot point 522 .

Pivot flexure 520 , and thus pivot point 522 , is mounted along a center axis of frame 526 by a support member 528 which is, in turn, affixed to frame 526 . The ‘U’ shape of link 510 accommodates both pivot flexure 520 and interconnecting dither axis flexures 530 . First ends of flexures 530 are fixed to the ends of pivot arms 518 and second ends of flexures 530 are fixed to the moving ends of accelerometer blocks 532 . Thus, link 510 is interconnected to each of two accelerometer blocks 532 by flexures 530 . Link 510 in combination with interconnecting dither flexures 530 provides a linkage between accelerometer blocks 532 which pivots about pivot point 522 . In a preferred embodiment, link 510 pivots about pivot point 522 disposed intermediate between interconnecting dither flexures 530 .

Portions of link 510 are removed to provide cutouts 534 and 536 and portions are retained to form extensions 538 , 540 such that the precise length of interconnecting dither axis flexures 530 is determined to ensure that flexures 530 have characteristics of 50 percent simple motion and 50 percent “S-bend” motion. As noted above, such characteristics ensure that any motion imparted by dither axis flexures 530 to one accelerometer block 532 is imparted as a sinusoidal function to the other accelerometer block 532 without introducing a higher order harmonic into the translation motion. In a preferred embodiment, the dimensions of cutouts 534 , 536 and extensions 538 , 540 are chosen such that link 510 is inherently balanced and axes-symmetric about pivot flexure 520 and about pivot point 522 .

FIG. 8 shows another alternative link configuration comprising a mass reduced ‘U’ shaped link 610 . The link configuration of FIG. 8 is another symmetrical ‘U’ shape which provides an analytically simplified configuration. Link 610 comprises a pair of parallel members 612 a, 612 b and interconnecting member 614 . The lengths of parallel members 612 a, 612 b extending along the sensor's dither axis 616 are substantially equal. Portions of parallel members 612 a, 612 b are removed to form one or more cavities or through holes 618 which lighten or mass reduce link 610 . Parallel members 612 a, 612 b interconnect pivot arms 620 a, 620 b to brace 614 which is connected to pivot flexure 622 . In one preferred embodiment, four through holes 618 are formed in link 610 , two in each of parallel members 612 a, 612 b. In turn, pivot flexure 622 is mounted along a center axis of frame 624 by a support member 626 which is, in turn, affixed to frame 622 . The ‘U’ shape of link 610 accommodates both pivot flexure 622 and interconnecting dither axis flexures 628 .

First ends of interconnecting dither axis flexures 628 are fixed to the ends of pivot arms 620 and second ends of flexures 628 are fixed to the moving ends of accelerometer blocks 630 . Thus, link 610 is interconnected to each of two accelerometer blocks 630 by flexures 628 . Portions of link 610 are removed to provide cutouts 632 and 634 and portions are retained to form extensions 636 , 638 such that the precise length of dither axis flexures 628 is determined to ensure that dither axis flexures 628 have characteristics of 50 percent simple motion and 50 percent “S-bend” motion.

Thus, link 610 is inherently balanced and axes-symmetric about an axis 640 parallel to the longitudinal axes of parallel members 612 and passing through the geometric center of interconnecting member 614 . In one preferred embodiment, pivot flexure 622 , including a pivot point 642 , is centered on axis 640 . Thus, link 610 is inherently balanced and axes-symmetric about pivot flexure 622 and about pivot point 642 .

FIG. 9 shows yet another alternative link configuration comprising a mass reduced ‘U’ shaped link 710 . The link configuration of FIG. 9 is another ‘U’ shape which provides an analytically simplified configuration. Link 710 comprises a pair of parallel members 712 a, 712 b and interconnecting member 714 . The lengths of parallel members 712 a, 712 b extending along the sensor's dither axis 716 are substantially equal. In one preferred embodiment, portions of parallel members 712 a, 712 b are removed to form one or more cavities or through holes 717 which lighten or mass reduce link 710 . Parallel members 712 a, 712 b interconnect pivot arms 718 a, 718 b to interconnecting member 714 which is connected to pivot flexure 720 . Link 710 resembles a lever pivotally mounted about a pivot point 722 provided by pivot flexure 720 . Thus, link 710 is essentially balanced and axes-symmetric about an axis 724 parallel to the longitudinal axes of parallel members 712 and passing through the geometric center of interconnecting member 714 . In one preferred embodiment, pivot flexure 720 , including pivot point 722 , is centered on axis 724 . Thus, link 710 is essentially balanced and axes-symmetric about pivot flexure 720 and about pivot point 722 .

Pivot flexure 720 , and thus pivot point 722 , is mounted along a center axis of frame 726 by a support member 728 which is, in turn, affixed to frame 726 . The ‘U’ shape of link 710 accommodates both pivot flexure 720 and interconnecting dither axis flexures 730 . First ends of flexures 730 are fixed to the ends of pivot arms 718 and second ends of flexures 730 are fixed to the moving ends of accelerometer blocks 732 . Thus, link 710 is interconnected to each of two accelerometer blocks 732 by flexures 730 . Link 710 in combination with interconnecting dither flexures 730 provides a linkage between accelerometer blocks 732 which pivots about pivot point 722 . In a preferred embodiment, link 710 pivots about pivot point 722 disposed intermediate between interconnecting dither flexures 730 .

Portions of link 710 are removed to provide cutouts 734 and 736 and a portion is retained to form extension 738 such that the precise length of interconnecting dither axis flexures 730 is determined to ensure that flexures 730 have characteristics of 50 percent simple motion and 50 percent “S-bend” motion. As noted above, such characteristics ensure that any motion imparted by dither axis flexures 730 to one accelerometer block 732 is imparted as a sinusoidal function to the other accelerometer block 732 without introducing a higher order harmonic into the translation motion. In the embodiment of FIG. 9 , the configurations of cutouts 734 , 736 and extension 738 are dictated by practical considerations of space and minimum cross-section such that link 710 is prevented from being precisely balanced and axes-symmetric about pivot flexure 720 and about pivot point 722 . In a preferred embodiment, the configurations of cutouts 734 , 736 and extension 738 are chosen such that a minimum discrepancy in configuration exist between pivot arms 718 a, 718 b and link 710 is substantially balanced and axes-symmetric about pivot flexure 720 and about pivot point 722 .

Additional Alternative Embodiments

FIG. 10 illustrates one embodiment of the rate and acceleration sensor 10 according to the present invention in which axial misalignment between the dither motion and the Coriolis acceleration sensing direction is eliminated or “nulled.” In FIG. 10 , misalignment of the dither axis 41 relative to the accelerometer input axis 38 is corrected using an axis alignment feature located at the end of the dither leg which causes the dither leg to rotate in response to an applied torque force while a detector measures the misalignment. The preferred axis alignment feature includes a torsional flexure which is relatively stiff in the three orthogonal axes X, Y and Z oriented with respect to the silicon substrate 16 and is torsionally compliant to torque forces applied about a longitudinal axis aligned with the dither leg. This relative stiffness in the axis alignment feature's longitudinal and cross-axes allows the dither leg to operate in the nominal design mode while the torsional compliance allows the dither leg to rotate about its longitudinal axis.

Each of the following embodiments of the axis alignment feature of the present invention are achieved in relatively simple configurations such that the behavior of each is readily predicted and/or modeled analytically using classical methods commonly known to those of skill in the art.

In FIG. 10 , one embodiment of the present invention includes a axis alignment feature 800 formed with a torsional flexure. In the embodiment of FIG. 10 and the following alternative embodiments, the torsional flexure is described as having an “X” shaped cross-section or “X-flexure” 810 , extruded a nominal length in the longitudinal dimension of the S-bend flexures 34 and 36 which suspend accelerometers 32 a and b in the plane of the silicon substrate 16 . The X-flexure 810 , which is described in detail below, is relatively stiff in the three major orthogonal axes X, Y and Z oriented with respect to the silicon substrate 16 and is torsionally compliant to torque forces applied about the extruded axis. This relative stiffness in the longitudinal and cross-axes allows the S-bend flexures 34 and 36 to operate in the nominal design mode while the torsional compliance allows the S-bend flexures 34 and 36 to rotate about their respective longitudinal axes. By rotating the base of the S-bend flexures 34 and 36 , a different dither direction can be obtained with respect to the accelerometer axis 38 . Thus, a torque applied to the S-bend flexures 34 and 36 through the X-flexure 810 rotates the S-bend flexures 34 and 36 , whereby the dither axis 41 is rotated into an orthogonal relationship with the accelerometer input axis 38 . In a preferred embodiment, the torque force applied to each of the S-bend flexures 34 and 36 is independent of that torque force applied to each of the other S-bend flexures 34 and 36 such that varying amounts of axis misalignment correction is applied to each of the accelerometers 32 a and 32 b independently.

Those of ordinary skill in the relevant art will recognize that an effective torsional flexure is not limited to the X-flexure described below. Therefore, nothing in this description is intended to limit the scope of the invention to an X-shaped flexure nor is this description intended to limit the scope of the invention to a feature having four legs extending from a central longitudinal axis. For example, the torsional flexure of the invention is alternatively practiced using a “Y” shaped torsional flexure having three legs extending from and extruded alone a central longitudinal axis. Other shapes for the torsional flexure portion of the axis alignment feature lying within the contemplation of the present invention include, for example, a “+” shaped torsional flexure, an “*” shaped torsional flexure, and other suitably shaped torsional flexures which provide the relative stiffness in the three orthogonal X, Y and Z axes oriented with respect to the silicon substrate 16 and the torsional compliance to torque forces applied about the extruded axis.

The X-flexure 810 is formed in the silicon substrate 16 and the epitaxial layer 812 formed on the substrate surface, as described below. The X-flexure 810 projects form an innerperipheral edge of the dither or mounting frame 30 from which each of the accelerometers 32 a and 32 b is suspended. A distal end of each X-flexure 810 is fixed to each of the S-bend flexures 36 . According to the embodiment shown in FIG. 10 , one strut 814 projects laterally from the side of the distal end of X-flexure 810 . An inner beam 816 and an outer beams 818 extend between the distal end of the laterally projecting strut 814 and the innerperipheral edge of dither or mounting frame 30 near the base of X-flexure 810 . The inner and outer beams 816 , 818 are placed side-by-side with minimal spacing in between. The beams 816 , 818 are mechanically coupled at their first ends by connection with the laterally extending strut 814 via pivot flexure 819 . The beams 816 , 818 are also mechanically coupled at their second ends by connection with the mounting frame 30 via flexure 830 . Flexure 830 is preferably formed of two pliant portions 832 formed in the silicon substrate 16 by reactive ion etching between the ends of beams 816 , 818 and the innerperipheral edge of the mounting frame 30 . Optionally, the two pliant portions 832 of flexure 830 are interleaved between the innerperipheral edge of the mounting frame 30 and a finger portion 834 of mounting frame 30 extending between the pliant portions 832 , whereby the close proximity of the mounting frame 30 innerperipheral edge and the mounting frame finger 834 act to limit the lateral in-plane motion of the pliant portions 832 . Strut 814 and beams 816 and 818 are all formed in epitaxial layer 812 , illustratively about 20 μm thickness.

A conductive path 820 is deposited on the surface of epitaxial layer 812 and extends from an external ground connection 822 on mounting frame 30 across the two pliant portions 832 of flexure 830 . The conductive path 820 is electrically coupled to a highly resistive coating deposited in parallel paths across the inner and outer beams 816 and 818 . The resistive coating is, for example, a nickel-chromium material or another highly resistive metal suitable for deposition onto epitaxial layer 812 . The resistive coating deposited across the outer beam 818 is electrically interconnected by a continuation of the conductive path 820 a to an external connector 824 a on the dither frame 30 , thus forming a first heater portion 826 a. Similarly, the resistive coating deposited across the inner beam 816 is electrically interconnected by a parallel continuation of the conductive path 820 b to an external connector 824 b on the dither frame 30 to form a second heater portion 826 b. Each of the first and second heater portions 826 a and 826 b are interconnected to the rotational drive circuit via their common ground connection 822 and their respective external connectors 824 a and 824 b. A rotational force is applied to the S-bend flexures 36 by passing a rotational drive signal or current generated by the rotational drive circuit through the highly resistive coating via the external connectors 824 a or 824 b to respective conductive path 820 a or 820 b. The rotational drive current causes the highly resistive coating to heat and expand, thus causing the attached beam to lengthen. By applying a rotational drive current to one of the heater portions 826 a or 826 b, the inner beam 816 or the outer beam 818 is heated. The heated beam 816 or 818 expands toward or away from the lever 819 , whereby the S-bend flexure 36 is rotated either clockwise or counter clockwise and the axis misalignment of the dither axis 41 to the accelerometer input axis 38 is substantially corrected. The ability to impart either a clockwise or counter clockwise rotation provides the axis alignment feature 800 the flexibility to correct for either a positive or negative angular misalignment.

In the application illustrated herein, the invention compensates for ¼ milliradian of rotation about the S-bend flexures 36 with a reasonable delta temperature rise of less than 50° C. which is accomplished using less than 5 milliamps at 5 volts. Thus, the rotational drive signal normally used to null the quadrature errors to within acceptable limits is no greater than 5 milliamp. As with any lever, force is traded for motion. Since heating produces a length increase, the resulting force is very high. As shown in FIG. 10 , the epitaxial feature, inner beam 816 corresponding outer beam 818 , applies about a 6.5 to 1 leverage ratio. The embodiment of FIG. 10 operates at about 50% of the Euler buckling load of the beams, which ultimately limits the amount of leveraging.

A method for detecting, adjusting and maintaining this rotation about the S-bend flexure 36 is also provided. The misalignment between the dither motion and the Coriolis acceleration sensing direction is detected by measuring the quadrature component of the rate signal. For a system defined as a sine motion of the dither frame, the rate information is a cosine and the quadrature signal is a sine. Sine demodulation of the sensor output provides a measure of the sine component. For a given polarity of dither leg rotation, i.e. rotation about the S-bend flexure 36 , a component of the turn-around acceleration is summed into the accelerometer input axis 38 by subtracting from the quadrature component, whereby the misalignment error is ultimately nulled. The nulling is done as a one time open loop correction, by applying a fixed voltage to the beam heater. Optionally, the beam heater is driven with a temperature compensated voltage using a conventional circuit known to those of skill in the art. Alternatively, an integrated voltage of the sine demodulated output is applied as a closed loop nulling scheme. The latter closed loop nulling circuit nulls quadrature due to any source; aging, package stress, manufacturing errors, g-loading, temperature and other fixed and varying factors affecting performance are corrected.

As described above, the X-flexure 810 formed between an innerperipheral edge of the dither or mounting frame 30 and a first end of the of the dither leg, i.e. the S-bend flexures 34 and 36 , is an “active” misalignment correction feature. Optionally, a second “passive” axis alignment feature (not shown) is formed between a second end of the dither leg and the outerperipheral edge of a corresponding accelerometer 32 . Optionally, the second or passive X-flexure is formed similarly to active X-flexure 810 with an “X” shaped cross-section extruded a nominal length in the longitudinal dimension of the S-bend flexures 34 and 36 . The second or passive X-flexure is also relatively stiff in the three major orthogonal axes X, Y and Z oriented with respect to the silicon substrate 16 and is torsionally compliant to torque forces applied about the extruded axis, such that the S-bend flexures 34 and 36 are able to operate in the nominal design mode while rotating about their respective longitudinal axes.

In the preferred embodiments, active X-flexure 810 is disposed adjacent the mounting frame 30 rather than the accelerometer 32 because the electrical interconnection to the rotational drive circuit is more easily accomplished at this location. However, nothing in the illustrative placement of X-flexure 810 is intended to limit the scope of the invention. Those of skill in the art will readily recognize that the illustrative placement of X-flexure 810 is a matter of design convenience. The positions of the active X-flexure 810 and the passive X-flexure are reversed according to another alternative embodiment of the invention. Furthermore, as described above, the active X-flexure 810 are incorporated into the outer S-bend flexures 34 a and 36 b as a matter of design and manufacturing convenience because the layout of the dither drive and pick-off circuits limit the surface space available on epitaxial layer 812 on the inner S-bend flexures 34 b and 36 a. According to an alternative embodiment, active X-flexure 810 is incorporated into the inner S-bend flexures 34 b and 36 a. Optionally, an active X-flexure 810 is incorporated into both the inner S-bend flexures 34 b and 36 a and the outer S-bend flexures 34 a and 36 b. FIG. 10 includes FIG. 10-1 which is a cross-sectional view of the X-flexure 810 across a plane perpendicular to the longitudinal axis of the feature. FIG. 10-1 also illustrates the laterally projecting strut 814 formed in epitaxial layer 812 .

FIG. 11 illustrates one embodiment of the axis alignment feature of the invention. Accordingly, FIG. 11 illustrates an isometric view of the X-flexure 810 which includes four X-struts 840 projected from and extruded along a central longitudinal axis 842 in the substrate 16 . The ends of two of the X-struts each include a portion formed in epitaxial layer 812 . As shown, the laterally projecting struts 814 are also formed in epitaxial layer 812 as extensions of the epitaxial portion of the two X-struts at an extreme end of the extruded section. In one embodiment of the axis alignment feature used with the embodiment of the sensor 10 described herein, the X-strut section is formed through the entire thickness of a standard substrate 16 used in the integrated circuit industry, for example, according the present embodiment the substrate 16 is approximately 508 micrometers inclusive of the portion formed in epitaxial portion 812 . Each X-strut 840 is formed having a thickness and length and an angular orientation to the planar surfaces of the substrate 16 such that a predetermined cross-axes and longitudinal stiffness are achieved in combination with a predetermined rotational compliance about the longitudinal axis 842 of the X-flexure 810 . According to one the embodiment of the sensor 10 described herein, one configuration of the axis misalignment feature of the invention is formed with each X-strut 840 approximately 40 micrometers thick and joined at the feature's center line represented by the feature's longitudinal axis 842 . The feature is extruded approximately 0.015 inches along its longitudinal axis 842 .

FIG. 11 also illustrates one embodiment of the laterally projecting struts 814 . The laterally projecting struts 814 are preferably formed in epitaxial layer 812 as extensions of the epitaxial portion of X-struts 840 . Struts 814 are preferably formed having a length A, a width B, and a thickness C, whereby sufficient cross-section is achieved to provide the columnar strength necessary to transmit the rotational force from the heated beams 816 , 818 to the X-flexure 810 without buckling. According to the currently described embodiment, the struts 814 are preferably formed having a length A of approximately 0.0331 inches, a width B of approximately 30 micrometers, and a thickness C equal to the thickness of the deposited epitaxial layer 812 .

In FIG. 12 , each of the X-struts 840 are oriented at an angle relative to the substrate 16 in which they are formed and operated. The angle is calculated to co-act with the feature's thicknesses and extruded length to achieve the above mentioned predetermined cross-axes and longitudinal stiffness with a predetermined rotational compliance about the longitudinal axis 842 . As shown in FIG. 12 , the X-struts 840 of the current embodiment are oriented at an angle of approximately 54.74 degrees from the planar surface of substrate 16 .

FIG. 13 is illustrative of the mask used in etching the X-flexure 810 into the substrate 16 using conventional etching processes, for example, the above mentioned potassium hydroxide (KOH) process that takes advantage of the orientation-dependent properties of silicon to etch specific shapes in silicon. As shown, the mask protects two strips of a first planar surface of substrate 16 having a width W and a length L calculated to produce the desired X-flexure configuration using the etching process of choice, while exposing the expanse of substrate material between the strips to the etchant. Two similar opposing strips are protected on a second planar surface of substrate 16 , whereby the described X-flexures 810 are formed in the substrate 16 . For example, the above described axis alignment feature is formed using a mask designed to protect strips approximately 50 micrometers wide by 0.0286 inches long.

FIGS. 14A and 14B illustrate the break through and self-topping features of the etching process in forming X-flexures 810 in substrate 16 . The second or passive X-flexures are formed in a similar manner.

FIG. 15 illustrates a preferred alternative embodiment wherein X-flexures 810 are formed essentially the same as shown and described in FIGS. 11 through 14 , except that the material concentrated about the longitudinal axis 842 whereby the four the X-struts 840 are mechanically interconnected is also removed in an etching process. Thus, each of the four X-struts 840 are free to rotate independently of the other three members. The additional degree of freedom thus introduced greatly increases the torsional flexibility or compliance of the X-flexure 810 such that a lesser rotational force causes an similar degree of rotation of the X-flexure 810 about its longitudinal axis 842 . However, because the material is removed at the feature's neutral axis, the relative cross-axes and longitudinal stiffnesses are substantially undiminished such that the dither leg continues to operate satisfactorily in the nominal design mode.

FIG. 16 details one embodiment of the heated beams 816 , 818 . In FIG. 16 , the heated beams 816 , 818 used to drive the rotation of the above described active X-flexures 810 are preferably formed in epitaxial layer 812 . As described above, a highly resistive coating is deposited on each of the beams 816 , 818 . The coating is preferably deposited on the outer surface of the epitaxial layer 812 opposite the surface of substrate 16 . The heated beams 816 , 818 are preferably formed having a length A 2 , a width B 2 , and a thickness C 2 , whereby sufficient cross-section is achieved to provide the columnar strength necessary to impart the desired rotational force to the active X-flexures 810 without buckling or warping. According to the currently described embodiment, the heated beams 818 , 816 are preferably formed having a length A 2 of approximately 0.0331 inches, a width B 2 of approximately 30 micrometers, and a thickness C 2 equal to the thickness of the deposited epitaxial layer 812 .

The foregoing is illustrative of the present invention and is not to be construed as limiting thereof. For example, the heated beams are joined directly to the dither leg and impart the torsional force thereto. The invention is defined by the following claims, with equivalents of the claims to be included therein.

Claims

1. An apparatus for measuring the specific force and angular rotation rate of a moving body, comprising:a) a monolithic substrate having first and second substantially planar surfaces disposed substantially parallel to each other and an epitaxial layer adhered to at least one of said first and second planar surfaces; b) a first accelerometer formed of said substrate and having a first force sensing axis for producing a first output signal indicative of the acceleration of the moving body along said first force sensing axis, said first accelerometer having a proof mass, a support frame, and at least one flexure connecting said proof mass to said support frame; c) a second accelerometer formed of said substrate and having a second force sensing axis for producing a second output signal indicative of the acceleration of the moving body along said second force sensing axis, said second accelerometer having a proof mass, a support frame, and at least one flexure connecting said proof mass to said support frame; d) a dither frame formed of said substrate; e) a first pair of S-bend flexures connected between said support frame of said first accelerometer and said dither frame, and a second pair of S-bend flexures connected between said support frame of said second accelerometer and said dither frame, said S-bend flexures being formed of said substrate for mounting said first and second accelerometers such that said first and second force sensing axes are both oriented at substantially the same angle with respect to said first and second surfaces and such that said first and second accelerometers can be moved along a vibration axis substantially perpendicular to each of said first and second sensing axes; f) a drive circuit coupled to each of said first and second accelerometers for imparting a dithering motion thereto of a predetermined frequency along said vibration axis; g) said substrate having a rate axis substantially perpendicular to each of said first and second force sensing axes and said vibration axis; and h) first and second axis alignment features, said first axis alignment feature disposed between said first accelerometer and said dither frame and rotating one of said first pair of S-bend flexures in response to a first rotational drive signal and said second axis alignment feature disposed between said second accelerometer and said dither frame and rotating one of said second pair of S-bend flexures in response to a second rotational drive signal, whereby said dithering motion is orthogonally aligned with said rate axis and said first and second output signals have a Coriolis component indicative of the angular rotation of the moving body about said rate axis.

2. The specific force and angular rotation rate measuring apparatus recited in claim 1, wherein each of said first and second axis alignment features further comprise:a torsionally compliant flexure extending between said S-bend flexure and said dither frame; and a force member mechanically coupled to said dither frame and oriented to impart a torsional force to said torsionally compliant flexure.

3. The specific force and angular rotation rate measuring apparatus recited in claim 2, wherein each said force member includes a highly resistive conductor deposited thereon.

4. The specific force and angular rotation rate measuring apparatus recited in claim 3, further comprising an electrical circuit generating a current in said highly resistive conductor deposited on one or more of said force members, whereby the temperature of said one or more force members is elevated relative to another of said force members.

5. The specific force and angular rotation rate measuring apparatus recited in claim 2, wherein said torsionally compliant flexure is formed in said substrate and said force member is formed in said epitaxial layer.

6. The specific force and angular rotation rate measuring apparatus recited in claim 5, wherein said force member further comprises two or more spaced apart parallel beams.

7. The specific force and angular rotation rate measuring apparatus recited in claim 5, therein said torsionally compliant flexure comprises a plurality of struts projecting radially from a common longitudinal axis.

8. The specific force and angular rotation rate measuring apparatus recited in claim 7, wherein said radially projecting struts form an X-shape extruded along said common longitudinal axis.

9. The specific force and angular rotation rate measuring apparatus recited in claim 8, wherein said struts are joined at said common longitudinal axis into an integrated X-shaped torsionally compliant flexure.

10. The specific force and angular rotation rate measuring apparatus recited in claim 8, wherein said struts forming said X-shaped torsionally compliant flexure are mechanically coupled at their first and second ends.

11. The specific force and angular rotation rate measuring apparatus recited in claim 2, wherein said force member acts on said torsionally compliant flexure through one or more struts disposed between said force member and said torsionally compliant flexure.

12. The specific force and angular rotation rate measuring apparatus recited in claim 2, wherein said force member acts on said torsionally compliant flexure through one or more levers pivotally suspended between said force member and said torsionally compliant flexure.