Lecture 10 Sinusoidal Steady-State and Frequency Response

Total Page:16

File Type:pdf, Size:1020Kb

Lecture 10 Sinusoidal Steady-State and Frequency Response S. Boyd EE102 Lecture 10 Sinusoidal steady-state and frequency response sinusoidal steady-state ² frequency response ² Bode plots ² 10{1 Response to sinusoidal input convolution system with impulse response h, transfer function H PSfrag replacements u y H sinusoidal input u(t) = cos(!t) = ej!t + e¡j!t =2 t ¡ ¢ output is y(t) = h(¿) cos(!(t ¿)) d¿ Z0 ¡ let's write this as 1 1 y(t) = h(¿) cos(!(t ¿)) d¿ h(¿) cos(!(t ¿)) d¿ Z0 ¡ ¡ Zt ¡ ¯rst term is called sinusoidal steady-state response ² second term decays with t if system is stable; if it decays it is called the ² transient Sinusoidal steady-state and frequency response 10{2 if system is stable, sinusoidal steady-state response can be expressed as 1 ysss(t) = h(¿) cos(!(t ¿)) d¿ Z0 ¡ 1 = (1=2) h(¿) ej!(t¡¿) + e¡j!(t¡¿) d¿ Z0 ³ ´ 1 1 = (1=2)ej!t h(¿)e¡j!¿ d¿ + (1=2)e¡j!t h(¿)ej!¿ d¿ Z0 Z0 = (1=2)ej!tH(j!) + (1=2)e¡j!tH( j!) ¡ = ( H(j!)) cos(!t) ( H(j!)) sin(!t) < ¡ = = a cos(!t + Á) where a = H(j!) , Á = 6 H(j!) j j Sinusoidal steady-state and frequency response 10{3 conclusion if the convolution system is stable, the response to a sinusoidal input is asymptotically sinusoidal, with the same frequency as the input, and with magnitude & phase determined by H(j!) H(j!) gives ampli¯cation factor, i.e., RMS(y )=RMS(u) ² j j ss 6 H(j!) gives phase shift between u and y ² ss special case: u(t) = 1 (i.e., ! = 0); output converges to H(0) (DC gain) frequency response transfer function evaluated at s = j!, i.e., 1 H(j!) = h(t)e¡j!tdt Z0 is called frequency response of the system since H( j!) = H(j!), we usually only consider ! 0 ¡ ¸ Sinusoidal steady-state and frequency response 10{4 Example transfer function H(s) = 1=(s + 1) ² input u(t) = cos t ² SSS output has magnitude H(j) = 1=p2, phase 6 H(j) = 45± ² j j ¡ u(t) (dashed) & y(t) (solid) 1 0.5 0 −0.5 PSfrag replacements −1 0 5 10 15 20 t Sinusoidal steady-state and frequency response 10{5 more generally, if system is stable and the input is asymptotically sinusoidal, i.e., u(t) Uej!t ! < as t , then ¡ ¢ ! 1 y(t) y (t) = Y ej!t ! ss < ss as t , where ¡ ¢ ! 1 Yss = H(j!)U Y H(j!) = ss U for a stable system, H(j!) gives ratio of phasors of asymptotic sinusoidal output & input Sinusoidal steady-state and frequency response 10{6 thus, for example (assuming a stable system), H(j!) large means asymptotic response of system to sinusoid with ² frequnecy ! is large H(0) = 2 means asymptotic response to a constant signal is twice the ² input value H(j!) small for large ! means the asymptotic output for high ² frequency sinusoids is small Sinusoidal steady-state and frequency response 10{7 Measuring frequency response for ! = !1; : : : ; !N , apply sinusoid at frequency !, with phasor U ² wait for output to converge to SSS ² measure Y ² ss (i.e., magnitude and phase shift of yss) N can be a few tens (for hand measurements) to several thousand Sinusoidal steady-state and frequency response 10{8 Frequency response plots frequency response can be plotted in several ways, e.g., H(j!) & H(j!) versus ! ² < = H(j!) = H(j!) + j H(j!) as a curve in the complex plane (called ² Nyquist plot< ) = H(j!) & 6 H(j!) versus ! (called Bode plot) ² j j the most common format is a Bode plot Sinusoidal steady-state and frequency response 10{9 example: RC circuit 1­ 1 PSfrag replacements Y (s) = U(s) 1 + s u(t) 1F y(t) 1 H(j!) = 1 + j! 0 0 −5 j ) ! −10 j −30 ) ( −15 ! H j j −20 ( 10 −25 H 6 −60 log −30 20 PSfrag replacements −35 PSfrag replacements −40 −2 −1 0 1 2 −90 −2 −1 0 1 2 10 10 10 10 10 10 10 10 10 10 ! ! Sinusoidal steady-state and frequency response 10{10 example: suspension system of page 8-6 with m = 1, b = 0:5, k = 1, 0:5s + 1 ( 0:75!2 + 1) j0:5!3 H(s) = ; H(j!) = ¡ ¡ s2 + 0:5s + 1 !4 1:75!2 + 1 ¡ 10 0 j 0 −20 ) ! j −10 −40 ( H j −20 (degrees) −60 ) 10 ! −30 j ( −80 log H 20 PSfrag replacements −40 PSfrag replacements6 −100 −50 −120 −2 −1 0 1 2 −2 −1 0 1 2 10 10 10 10 10 10 10 10 10 10 ! ! Sinusoidal steady-state and frequency response 10{11 Bode plots frequency axis logarithmic scale for ! ² horizontal distance represents a ¯xed frequency ratio or factor: ² ratio 2 : 1 is called an octave; ratio 10 : 1 is called a decade magnitude H(j!) j j expressed in dB, i.e., 20 log H(j!) ² 10 j j vertical distance represents dB, i.e., a ¯xed ratio of magnitudes ² ratio 2 : 1 is +6dB, ratio 10 : 1 is +20dB slopes are given in units such as dB/octave or dB/decade ² phase 6 H(j!) multiples of 360± don't matter ² phase plot is called wrapped when phases are between 180± (or ² 0; 360±); it is called unwrapped if multiple of 360± is chosen§ to make phase plot continuous Sinusoidal steady-state and frequency response 10{12 Bode plots of products consider product of transfer functions H = F G: PSfrag replacements u G F y frequency response magnitude and phase are 20 log H(j!) = 20 log F (j!) + 20 log G(j!) 10 j j 10 j j 10 j j 6 H(j!) = 6 F (j!) + 6 G(j!) here we use the fact that for a; b C, 6 (ab) = 6 a + 6 b 2 so, Bode plot of a product is the sum of the Bode plots of each term (extends to many terms) Sinusoidal steady-state and frequency response 10{13 example. F (s) = 1=(s + 10), G(s) = 1 + 1=s 0 −20 j ) ! −25 j ) ( ! F −30 j j −45 ( 10 −35 F 6 log PSfrag replacements −40 PSfrag replacements 20 −90 −45 −2 −1 0 1 2 −2 −1 0 1 2 10 10 10 10 10 10 10 10 10 10 ! ! 40 0 j 35 ) ! 30 j ( 25 ) ! G j 20 j −45 ( 10 15 G 6 log 10 PSfrag replacements 20 5 PSfrag replacements 0 −90 −2 −1 0 1 2 −2 −1 0 1 2 10 10 10 10 10 10 10 10 10 10 ! ! Sinusoidal steady-state and frequency response 10{14 Bode plot of 1 + 1=s s + 1 H(s) = F (s)G(s) = = s + 10 s(s + 10) −30 20 j 10 −40 ) ! j −50 0 ) ( ! H j j −10 ( −60 10 H −20 6 −70 log PSfrag replacements 20 −30 PSfrag replacements −80 −40 −2 −1 0 1 2 −90 −2 −1 0 1 2 10 10 10 10 10 10 10 10 10 10 ! ! Sinusoidal steady-state and frequency response 10{15 Bode plots from factored form rational transfer function H in factored form: (s z ) (s z ) H(s) = k ¡ 1 ¢ ¢ ¢ ¡ m (s p ) (s p ) ¡ 1 ¢ ¢ ¢ ¡ n m 20 log H(j!) = 20 log k + 20 log j! z 10 j j 10 j j 10 j ¡ ij Xi=1 n 20 log j! p ¡ 10 j ¡ ij Xi=1 m n 6 H(j!) = 6 k + 6 (j! z ) 6 (j! p ) ¡ i ¡ ¡ i Xi=1 Xi=1 (of course 6 k = 0± if k > 0, and 6 k = 180± if k < 0) Sinusoidal steady-state and frequency response 10{16 Graphical interpretation: H(j!) j j s = j! m i=1 dist(j!; zi) H(j!) = k n j j j jQi=1 dist(j!; pi) Q since for u; v C, dist(u; v) = u v 2 j ¡ j PSfrag replacements therefore, e.g.: H(j!) gets big when j! is near a pole ² j j H(j!) gets small when j! is near a zero ² j j Sinusoidal steady-state and frequency response 10{17 Graphical interpretation: 6 H(j!) s = j! m n 6 H(j!) = 6 k+ 6 (j! z ) 6 (j! p ) ¡ i ¡ ¡ i Xi=1 Xi=1 PSfrag replacements therefore, 6 H(j!) changes rapidly when a pole or zero is near j! Sinusoidal steady-state and frequency response 10{18 Example with lightly damped poles poles at s = 0:01 j0:2, s = 0:01 j0:7, s = 0:01 ¡j1:3, § ¡ § ¡ § 50 0 j ) 0 ! j ) −180 ( ! H j j −50 ( 10 H 6 −360 log −100 PSfrag replacements 20 PSfrag replacements −540 −150 −1 0 1 −1 0 1 10 10 10 10 10 10 ! ! Sinusoidal steady-state and frequency response 10{19 All-pass ¯lter (s 1)(s 3) H(s) = ¡ ¡ (s + 1)(s + 3) 1 0 j ) 0.5 ! −90 j ) ( ! H j j 0 ( −180 10 H 6 log −0.5 −270 PSfrag replacements 20 PSfrag replacements −1 −360 −3 −2 −1 0 1 2 3 −3 −2 −1 0 1 2 3 10 10 10 10 10 10 10 10 10 10 10 10 10 10 ! ! called all-pass ¯lter since gain magnitude is one for all frequencies Sinusoidal steady-state and frequency response 10{20 Analog lowpass ¯lters analog lowpass ¯lters: approximate ideal lowpass frequency response H(j!) = 1 for 0 ! 1; H(j!) = 0 for ! > 1 j j · · j j by a rational transfer function (which can be synthesized using R, L, C) example nth-order Butterworth ¯lter PSfrag replacements ¼=(2n) ¼=n p1 p2 1 ¼=n H(s) = (s p )(s p ) (s p ) ¡ 1 ¡ 2 ¢ ¢ ¢ ¡ n n stable poles, equally spaced ¼=n pn¡1 on the unit circle pn ¼=n ¼=(2n) Sinusoidal steady-state and frequency response 10{21 magnitude plot for n = 2, n = 5, n = 10 0 −20 j ) ! j ( −40 H j n = 2 log −60 n = 5 PSfrag replacements 20 −80 n = 10 −100 −2 −1 0 1 2 10 10 10 10 10 ! Sinusoidal steady-state and frequency response 10{22 Sketching approximate Bode plots sum property allows us to ¯nd Bode plots of terms in TF, then add simple terms: constant ² factor of sk (pole or zero at s = 0) ² real pole, real zero ² complex pole or zero pair ² from these we can construct Bode plot of any rational transfer function Sinusoidal steady-state and frequency response 10{23 Poles and zeros at s = 0 the term sk has simple Bode plot: phase is constant, 6 = 90k± ² magnitude has constant slope 20kdB=decade ² magnitude plot intersects 0dB axis at ! = 1 ² examples: integrator (k = 1): 6 = 90±, slope is 20dB=decade ² ¡ ¡ ¡ di®erentiator (k = +1): 6 = 90±, slope is +20dB=decade ² Sinusoidal steady-state and frequency response 10{24 Real poles and zeros H(s) = 1=(s p) (p < 0 is stable pole; p > 0 is unstable pole) ¡ magnitude: H(j!) = 1= !2 + p2 j j p for p < 0, 6 H(j!) = arctan(!= p ) ¡ j j for p > 0, 6 H(j!) = 180± + arctan(!=p) § Sinusoidal steady-state and frequency response 10{25 Bode plot for H(s) = 1=(s + 1) (stable pole): Bode Diagrams 0 −10 −20 −30 −40 −50 −60 0 −20 Phase (deg); Magnitude (dB) −40 −60 −80 0.001 0.01 0.1 1 10 100 1000 Frequency (rad/sec) Sinusoidal steady-state and frequency response 10{26 Bode plot for H(s) = 1=(s 1) (unstable pole): ¡ Bode Diagrams 0 −10 −20 −30 −40 −50 −60 −100 Phase (deg); Magnitude (dB) −120 −140 −160 −180 0.001 0.01 0.1 1 10 100 1000 Frequency (rad/sec) magnitude same as stable pole; phase starts at 180±, increases ¡ Sinusoidal
Recommended publications
  • RANDOM VIBRATION—AN OVERVIEW by Barry Controls, Hopkinton, MA
    RANDOM VIBRATION—AN OVERVIEW by Barry Controls, Hopkinton, MA ABSTRACT Random vibration is becoming increasingly recognized as the most realistic method of simulating the dynamic environment of military applications. Whereas the use of random vibration specifications was previously limited to particular missile applications, its use has been extended to areas in which sinusoidal vibration has historically predominated, including propeller driven aircraft and even moderate shipboard environments. These changes have evolved from the growing awareness that random motion is the rule, rather than the exception, and from advances in electronics which improve our ability to measure and duplicate complex dynamic environments. The purpose of this article is to present some fundamental concepts of random vibration which should be understood when designing a structure or an isolation system. INTRODUCTION Random vibration is somewhat of a misnomer. If the generally accepted meaning of the term "random" were applicable, it would not be possible to analyze a system subjected to "random" vibration. Furthermore, if this term were considered in the context of having no specific pattern (i.e., haphazard), it would not be possible to define a vibration environment, for the environment would vary in a totally unpredictable manner. Fortunately, this is not the case. The majority of random processes fall in a special category termed stationary. This means that the parameters by which random vibration is characterized do not change significantly when analyzed statistically over a given period of time - the RMS amplitude is constant with time. For instance, the vibration generated by a particular event, say, a missile launch, will be statistically similar whether the event is measured today or six months from today.
    [Show full text]
  • Lecture 3: Transfer Function and Dynamic Response Analysis
    Transfer function approach Dynamic response Summary Basics of Automation and Control I Lecture 3: Transfer function and dynamic response analysis Paweł Malczyk Division of Theory of Machines and Robots Institute of Aeronautics and Applied Mechanics Faculty of Power and Aeronautical Engineering Warsaw University of Technology October 17, 2019 © Paweł Malczyk. Basics of Automation and Control I Lecture 3: Transfer function and dynamic response analysis 1 / 31 Transfer function approach Dynamic response Summary Outline 1 Transfer function approach 2 Dynamic response 3 Summary © Paweł Malczyk. Basics of Automation and Control I Lecture 3: Transfer function and dynamic response analysis 2 / 31 Transfer function approach Dynamic response Summary Transfer function approach 1 Transfer function approach SISO system Definition Poles and zeros Transfer function for multivariable system Properties 2 Dynamic response 3 Summary © Paweł Malczyk. Basics of Automation and Control I Lecture 3: Transfer function and dynamic response analysis 3 / 31 Transfer function approach Dynamic response Summary SISO system Fig. 1: Block diagram of a single input single output (SISO) system Consider the continuous, linear time-invariant (LTI) system defined by linear constant coefficient ordinary differential equation (LCCODE): dny dn−1y + − + ··· + _ + = an n an 1 n−1 a1y a0y dt dt (1) dmu dm−1u = b + b − + ··· + b u_ + b u m dtm m 1 dtm−1 1 0 initial conditions y(0), y_(0),..., y(n−1)(0), and u(0),..., u(m−1)(0) given, u(t) – input signal, y(t) – output signal, ai – real constants for i = 1, ··· , n, and bj – real constants for j = 1, ··· , m. How do I find the LCCODE (1)? .
    [Show full text]
  • Amplifier Frequency Response
    EE105 – Fall 2015 Microelectronic Devices and Circuits Prof. Ming C. Wu [email protected] 511 Sutardja Dai Hall (SDH) 2-1 Amplifier Gain vO Voltage Gain: Av = vI iO Current Gain: Ai = iI load power vOiO Power Gain: Ap = = input power vIiI Note: Ap = Av Ai Note: Av and Ai can be positive, negative, or even complex numbers. Nagative gain means the output is 180° out of phase with input. However, power gain should always be a positive number. Gain is usually expressed in Decibel (dB): 2 Av (dB) =10log Av = 20log Av 2 Ai (dB) =10log Ai = 20log Ai Ap (dB) =10log Ap 2-2 1 Amplifier Power Supply and Dissipation • Circuit needs dc power supplies (e.g., battery) to function. • Typical power supplies are designated VCC (more positive voltage supply) and -VEE (more negative supply). • Total dc power dissipation of the amplifier Pdc = VCC ICC +VEE IEE • Power balance equation Pdc + PI = PL + Pdissipated PI : power drawn from signal source PL : power delivered to the load (useful power) Pdissipated : power dissipated in the amplifier circuit (not counting load) P • Amplifier power efficiency η = L Pdc Power efficiency is important for "power amplifiers" such as output amplifiers for speakers or wireless transmitters. 2-3 Amplifier Saturation • Amplifier transfer characteristics is linear only over a limited range of input and output voltages • Beyond linear range, the output voltage (or current) waveforms saturates, resulting in distortions – Lose fidelity in stereo – Cause interference in wireless system 2-4 2 Symbol Convention iC (t) = IC +ic (t) iC (t) : total instantaneous current IC : dc current ic (t) : small signal current Usually ic (t) = Ic sinωt Please note case of the symbol: lowercase-uppercase: total current lowercase-lowercase: small signal ac component uppercase-uppercase: dc component uppercase-lowercase: amplitude of ac component Similarly for voltage expressions.
    [Show full text]
  • Control Theory
    Control theory S. Simrock DESY, Hamburg, Germany Abstract In engineering and mathematics, control theory deals with the behaviour of dynamical systems. The desired output of a system is called the reference. When one or more output variables of a system need to follow a certain ref- erence over time, a controller manipulates the inputs to a system to obtain the desired effect on the output of the system. Rapid advances in digital system technology have radically altered the control design options. It has become routinely practicable to design very complicated digital controllers and to carry out the extensive calculations required for their design. These advances in im- plementation and design capability can be obtained at low cost because of the widespread availability of inexpensive and powerful digital processing plat- forms and high-speed analog IO devices. 1 Introduction The emphasis of this tutorial on control theory is on the design of digital controls to achieve good dy- namic response and small errors while using signals that are sampled in time and quantized in amplitude. Both transform (classical control) and state-space (modern control) methods are described and applied to illustrative examples. The transform methods emphasized are the root-locus method of Evans and fre- quency response. The state-space methods developed are the technique of pole assignment augmented by an estimator (observer) and optimal quadratic-loss control. The optimal control problems use the steady-state constant gain solution. Other topics covered are system identification and non-linear control. System identification is a general term to describe mathematical tools and algorithms that build dynamical models from measured data.
    [Show full text]
  • Step Response of Series RLC Circuit ‐ Output Taken Across Capacitor
    ESE 271 / Spring 2013 / Lecture 23 Step response of series RLC circuit ‐ output taken across capacitor. What happens during transient period from initial steady state to final steady state? 1 ESE 271 / Spring 2013 / Lecture 23 Transfer function of series RLC ‐ output taken across capacitor. Poles: Case 1: ‐‐two differen t real poles Case 2: ‐ two identical real poles ‐ complex conjugate poles Case 3: 2 ESE 271 / Spring 2013 / Lecture 23 Case 1: two different real poles. Step response of series RLC ‐ output taken across capacitor. Overdamped case –the circuit demonstrates relatively slow transient response. 3 ESE 271 / Spring 2013 / Lecture 23 Case 1: two different real poles. Freqqyuency response of series RLC ‐ output taken across capacitor. Uncorrected Bode Gain Plot Overdamped case –the circuit demonstrates relatively limited bandwidth 4 ESE 271 / Spring 2013 / Lecture 23 Case 2: two identical real poles. Step response of series RLC ‐ output taken across capacitor. Critically damped case –the circuit demonstrates the shortest possible rise time without overshoot. 5 ESE 271 / Spring 2013 / Lecture 23 Case 2: two identical real poles. Freqqyuency response of series RLC ‐ output taken across capacitor. Critically damped case –the circuit demonstrates the widest bandwidth without apparent resonance. Uncorrected Bode Gain Plot 6 ESE 271 / Spring 2013 / Lecture 23 Case 3: two complex poles. Step response of series RLC ‐ output taken across capacitor. Underdamped case – the circuit oscillates. 7 ESE 271 / Spring 2013 / Lecture 23 Case 3: two complex poles. Freqqyuency response of series RLC ‐ output taken across capacitor. Corrected Bode GiGain Plot Underdamped case –the circuit can demonstrate apparent resonant behavior.
    [Show full text]
  • Frequency Response and Bode Plots
    1 Frequency Response and Bode Plots 1.1 Preliminaries The steady-state sinusoidal frequency-response of a circuit is described by the phasor transfer function Hj( ) . A Bode plot is a graph of the magnitude (in dB) or phase of the transfer function versus frequency. Of course we can easily program the transfer function into a computer to make such plots, and for very complicated transfer functions this may be our only recourse. But in many cases the key features of the plot can be quickly sketched by hand using some simple rules that identify the impact of the poles and zeroes in shaping the frequency response. The advantage of this approach is the insight it provides on how the circuit elements influence the frequency response. This is especially important in the design of frequency-selective circuits. We will first consider how to generate Bode plots for simple poles, and then discuss how to handle the general second-order response. Before doing this, however, it may be helpful to review some properties of transfer functions, the decibel scale, and properties of the log function. Poles, Zeroes, and Stability The s-domain transfer function is always a rational polynomial function of the form Ns() smm as12 a s m asa Hs() K K mm12 10 (1.1) nn12 n Ds() s bsnn12 b s bsb 10 As we have seen already, the polynomials in the numerator and denominator are factored to find the poles and zeroes; these are the values of s that make the numerator or denominator zero. If we write the zeroes as zz123,, zetc., and similarly write the poles as pp123,, p , then Hs( ) can be written in factored form as ()()()s zsz sz Hs() K 12 m (1.2) ()()()s psp12 sp n 1 © Bob York 2009 2 Frequency Response and Bode Plots The pole and zero locations can be real or complex.
    [Show full text]
  • Evaluation of Audio Test Methods and Measurements for End-Of-Line Loudspeaker Quality Control
    Evaluation of audio test methods and measurements for end-of-line loudspeaker quality control Steve Temme1 and Viktor Dobos2 (1. Listen, Inc., Boston, MA, 02118, USA. [email protected]; 2. Harman/Becker Automotive Systems Kft., H-8000 Székesfehérvár, Hungary) ABSTRACT In order to minimize costly warranty repairs, loudspeaker OEMS impose tight specifications and a “total quality” requirement on their part suppliers. At the same time, they also require low prices. This makes it important for driver manufacturers and contract manufacturers to work with their OEM customers to define reasonable specifications and tolerances. They must understand both how the loudspeaker OEMS are testing as part of their incoming QC and also how to implement their own end-of-line measurements to ensure correlation between the two. Specifying and testing loudspeakers can be tricky since loudspeakers are inherently nonlinear, time-variant and effected by their working conditions & environment. This paper examines the loudspeaker characteristics that can be measured, and discusses common pitfalls and how to avoid them on a loudspeaker production line. Several different audio test methods and measurements for end-of- the-line speaker quality control are evaluated, and the most relevant ones identified. Speed, statistics, and full traceability are also discussed. Keywords: end of line loudspeaker testing, frequency response, distortion, Rub & Buzz, limits INTRODUCTION In order to guarantee quality while keeping testing fast and accurate, it is important for audio manufacturers to perform only those tests which will easily identify out-of-specification products, and omit those which do not provide additional information that directly pertains to the quality of the product or its likelihood of failure.
    [Show full text]
  • Calibration of Radio Receivers to Measure Broadband Interference
    NBSIR 73-335 CALIBRATION OF RADIO RECEIVERS TO MEASORE BROADBAND INTERFERENCE Ezra B. Larsen Electromagnetics Division Institute for Basic Standards National Bureau of Standards Boulder, Colorado 80302 September 1973 Final Report, Phase I Prepared for Calibration Coordination Group Army /Navy /Air Force NBSIR 73-335 CALIBRATION OF RADIO RECEIVERS TO MEASORE BROADBAND INTERFERENCE Ezra B. Larsen Electromagnetics Division Institute for Basic Standards National Bureau of Standards Boulder, Colorado 80302 September 1973 Final Report, Phase I Prepared for Calibration Coordination Group Army/Navy /Air Force u s. DEPARTMENT OF COMMERCE, Frederick B. Dent. Secretary NATIONAL BUREAU OF STANDARDS. Richard W Roberts Director V CONTENTS Page 1. BACKGROUND 2 2. INTRODUCTION 3 3. DEFINITIONS OF RECEIVER BANDWIDTH AND IMPULSE STRENGTH (Or Spectral Intensity) 5 3.1 Random noise bandwidth 5 3.2 Impulse bandwidth in terms of receiver response transient 7 3.3 Voltage-response bandwidth of receiver 8 3.4 Receiver bandwidths related to voltage- response bandwidth 9 3.5 Impulse strength in terms of random-noise bandwidth 10 3.6 Sum-and-dif ference correlation radiometer technique 10 3.7 Impulse strength in terms of Fourier trans- forms 11 3.8 Impulse strength in terms of rectangular DC pulses 12 3.9 Impulse strength and impulse bandwidth in terms of RF pulses 13 4. EXPERIMENTAL PROCEDURE AND DATA 16 4.1 Measurement of receiver input impedance and phase linearity 16 4.2 Calibration of receiver as a tuned RF volt- meter 20 4.3 Stepped- frequency measurements of receiver bandwidth 23 4.4 Calibration of receiver impulse bandwidth with a baseband pulse generator 37 iii CONTENTS [Continued) Page 4.5 Calibration o£ receiver impulse bandwidth with a pulsed-RF source 38 5.
    [Show full text]
  • Linear Time Invariant Systems
    UNIT III LINEAR TIME INVARIANT CONTINUOUS TIME SYSTEMS CT systems – Linear Time invariant Systems – Basic properties of continuous time systems – Linearity, Causality, Time invariance, Stability – Frequency response of LTI systems – Analysis and characterization of LTI systems using Laplace transform – Computation of impulse response and transfer function using Laplace transform – Differential equation – Impulse response – Convolution integral and Frequency response. System A system may be defined as a set of elements or functional blocks which are connected together and produces an output in response to an input signal. The response or output of the system depends upon transfer function of the system. Mathematically, the functional relationship between input and output may be written as y(t)=f[x(t)] Types of system Like signals, systems may also be of two types as under: 1. Continuous-time system 2. Discrete time system Continuous time System Continuous time system may be defined as those systems in which the associated signals are also continuous. This means that input and output of continuous – time system are both continuous time signals. For example: Audio, video amplifiers, power supplies etc., are continuous time systems. Discrete time systems Discrete time system may be defined as a system in which the associated signals are also discrete time signals. This means that in a discrete time system, the input and output are both discrete time signals. For example, microprocessors, semiconductor memories, shift registers etc., are discrete time signals. LTI system:- Systems are broadly classified as continuous time systems and discrete time systems. Continuous time systems deal with continuous time signals and discrete time systems deal with discrete time system.
    [Show full text]
  • Simplified, Physically-Informed Models of Distortion and Overdrive Guitar Effects Pedals
    Proc. of the 10th Int. Conference on Digital Audio Effects (DAFx-07), Bordeaux, France, September 10-15, 2007 SIMPLIFIED, PHYSICALLY-INFORMED MODELS OF DISTORTION AND OVERDRIVE GUITAR EFFECTS PEDALS David T. Yeh, Jonathan S. Abel and Julius O. Smith Center for Computer Research in Music and Acoustics (CCRMA) Stanford University, Stanford, CA [dtyeh|abel|jos]@ccrma.stanford.edu ABSTRACT retained, however, because intermodulation due to mixing of sub- sonic components with audio frequency components is noticeable This paper explores a computationally efficient, physically in- in the audio band. formed approach to design algorithms for emulating guitar distor- tion circuits. Two iconic effects pedals are studied: the “Distor- Stages are partitioned at points in the circuit where an active tion” pedal and the “Tube Screamer” or “Overdrive” pedal. The element with low source impedance drives a high impedance load. primary distortion mechanism in both pedals is a diode clipper This approximation is also made with less accuracy where passive with an embedded low-pass filter, and is shown to follow a non- components feed into loads with higher impedance. Neglecting linear ordinary differential equation whose solution is computa- the interaction between the stages introduces magnitude error by a tionally expensive for real-time use. In the proposed method, a scalar factor and neglects higher order terms in the transfer func- simplified model, comprising the cascade of a conditioning filter, tion that are usually small in the audio band. memoryless nonlinearity and equalization filter, is chosen for its The nonlinearity may be evaluated as a nonlinear ordinary dif- computationally efficient, numerically robust properties.
    [Show full text]
  • Control System Design Methods
    Christiansen-Sec.19.qxd 06:08:2004 6:43 PM Page 19.1 The Electronics Engineers' Handbook, 5th Edition McGraw-Hill, Section 19, pp. 19.1-19.30, 2005. SECTION 19 CONTROL SYSTEMS Control is used to modify the behavior of a system so it behaves in a specific desirable way over time. For example, we may want the speed of a car on the highway to remain as close as possible to 60 miles per hour in spite of possible hills or adverse wind; or we may want an aircraft to follow a desired altitude, heading, and velocity profile independent of wind gusts; or we may want the temperature and pressure in a reactor vessel in a chemical process plant to be maintained at desired levels. All these are being accomplished today by control methods and the above are examples of what automatic control systems are designed to do, without human intervention. Control is used whenever quantities such as speed, altitude, temperature, or voltage must be made to behave in some desirable way over time. This section provides an introduction to control system design methods. P.A., Z.G. In This Section: CHAPTER 19.1 CONTROL SYSTEM DESIGN 19.3 INTRODUCTION 19.3 Proportional-Integral-Derivative Control 19.3 The Role of Control Theory 19.4 MATHEMATICAL DESCRIPTIONS 19.4 Linear Differential Equations 19.4 State Variable Descriptions 19.5 Transfer Functions 19.7 Frequency Response 19.9 ANALYSIS OF DYNAMICAL BEHAVIOR 19.10 System Response, Modes and Stability 19.10 Response of First and Second Order Systems 19.11 Transient Response Performance Specifications for a Second Order
    [Show full text]
  • Mathematical Modeling of Control Systems
    OGATA-CH02-013-062hr 7/14/09 1:51 PM Page 13 2 Mathematical Modeling of Control Systems 2–1 INTRODUCTION In studying control systems the reader must be able to model dynamic systems in math- ematical terms and analyze their dynamic characteristics.A mathematical model of a dy- namic system is defined as a set of equations that represents the dynamics of the system accurately, or at least fairly well. Note that a mathematical model is not unique to a given system.A system may be represented in many different ways and, therefore, may have many mathematical models, depending on one’s perspective. The dynamics of many systems, whether they are mechanical, electrical, thermal, economic, biological, and so on, may be described in terms of differential equations. Such differential equations may be obtained by using physical laws governing a partic- ular system—for example, Newton’s laws for mechanical systems and Kirchhoff’s laws for electrical systems. We must always keep in mind that deriving reasonable mathe- matical models is the most important part of the entire analysis of control systems. Throughout this book we assume that the principle of causality applies to the systems considered.This means that the current output of the system (the output at time t=0) depends on the past input (the input for t<0) but does not depend on the future input (the input for t>0). Mathematical Models. Mathematical models may assume many different forms. Depending on the particular system and the particular circumstances, one mathemati- cal model may be better suited than other models.
    [Show full text]