AU762564B2 - An adaptive control for a refrigeration system - Google Patents

Description

1

AUSTRALIA

PATENTS ACT 1990 DIVISIONAL APPLICATION NAME OF APPLICANT(S): Copeland Corporation ADDRESS FOR SERVICE: S'DAVIES COLLISON CAVE Patent Attorneys 1 Little Collins Street Melbourne, 3000.

INVENTION TITLE: "AN ADAPTIVE CONTROL FOR A REFRIGERATION SYSTEM" The following statement is a full description of this invention, including the best method of performing it known to us: I I P.\OPER\SSB\2499480ldi\spccdoc-31/01/1)2 -1- AN ADAPTIVE CONTROL FOR A REFRIGERATION SYSTEM BACKGROUND OF THE INVENTION Conventionally, refrigeration systems for supermarket refrigeration cases have employed air-cooled or water-cooled condensers fed by a rack of compressors. The compressors are coupled in parallel so that they may be 0 switched on and off in stages to adjust the system cooling capacity to the 10 demands of the load. Commonly, the condensers are located outside, on the roof, or in a machine room adjacent the shopping area where the refrigeration cases are located.

Within each refrigeration case is an evaporator fed by lines from the condensers through which the expanded refrigerant circulates to cool the case.

15 Conventionally, a closed-loop control system regulates refrigerant flow through the evaporator to maintain the desired case temperature. Proportional-integral- -2derivative (PID) closed loop control systems are popular for this purpose, with temperature sensors and/or pressure sensors providing the sensed condition inputs.

It is common practice within supermarkets to use separate systems to supply different individual cooling temperature ranges: low temperature (for frozen foods, ice cream, nominally medium (for meat, dairy products, nominally 20 0 high (for floral, produce, nominally +35 to +40 0 The separate low, medium and high temperature systems are each optimized to their respective temperature ranges. Normally, each will employ its own rack of compressors and its own set of refrigerant conduits to and from the compressors and condensers.

The conventional arrangement, described above, is very costly to construct and maintain. Much of the cost is associated with the long refrigerant conduit runs.

Not only are long conduit runs expensive in terms of hardware and installation costs, but the quantity of refrigerant required to fill the conduits is also a significant factor. The longer the conduit run, the more refrigerant required. Adding to the cost are environmental factors. Eventually fittings leak, allowing the refrigerant to escape to atmosphere. Invariably, long conduit runs involve more pipefitting joints that may potentially leak. When a leak does occur, the longer the conduit run, the more refrigerant lost.

There is considerable interest today in environmentally friendly refrigeration systems. Shortening the conduit run is seen as one way to achieve a more "environmentally friendly system. To achieve this, new condenserlcompressor configurations and new control systems will need to be engineered.

Re-engineering condenser/compressor configurations for more environmentally friendly systems is not a simple task, because system efficiency should not be sacrificed. Generally, the conventional roof-mounted condenser system, supplied by condensers, benefits from economies of scale and is quite efficient. These systems serve as the benchmark against which more environmentally friendly systems of the future will need to be measured.

To appreciate why re-engineering an environmentally yet efficient system has proven so difficult, consider these thermodynamic issues. The typical refrigeration case operates in a very unpredictable environment. From a design -3standpoint, the thermal mass being cooled is rarely constant. Within the supermarket environment, the temperature and humidity may vary widely at different times of day and over different seasons throughout the year. The product load (items in the refrigeration case) can also change unpredictably. Customers removing product and store clerks replenishing product rarely synchronize.

Outside the supermarket environment, the outdoor air temperature and humidity may also vary quite widely between day and night and/or between summer and winter. The capacity of the system must be designed for the harshest conditions (when the condenser environment is the hottest). Thus systems may experience excess capacity in less harsh conditions, such as in the cool evenings or during the winter.

Periodic defrosting also introduces thermal fluctuations into the Unlike thermal fluctuations due to environmental conditions, the thermal fluctuations induced by the defrost cycle are cause by the control system itself and not by the surrounding environment.

In a similar fashion, the control system for handling multiple refrigeration cases can induce thermal fluctuations that are quite difficult to predict. If all cases ee within a multi-case system are suddenly turned on at once--to meet their respective cooling demands--the cooling capacity must rapidly be ramped up to maximum. Likewise, if all cases are suddenly switched off, the cooling capacity should be ramped down accordingly. However, given that individual refrigeration cases may operate independently of one another, the instantaneous demand for cooling capacity will tend to vary widely and unpredictably.

These are all problems that have made the engineering of environmentally friendly systems more difficult. Adding to these difficulties are user engineering/ergonomic problems. The present day PID controller can be difficult to adapt to distributed refrigeration systems. Experienced controls engineers know that a well-tuned PID controller can involve a degree of artistry in selecting the proper control constants used in the PID algorithm. In a large refrigeration system of the conventional architecture (non-distributed) the size of the system justifies having a controls engineer visit the site (perhaps repeatedly) to fine tune the control constant parameters.

P:\OPER\SSB.4994Y(Odisp.d3 I/01/0)2 -4- This may not be practical for distributed systems in which the components are individually of a much smaller scale and far more numerous. By way of comparison, a conventional system might employ one controller for an entire multicase store-wide system. A distributed system for the same store might involve a controller for each case or adjacent group of cases within the store. Distributed systems need to be designed to minimise end user involvement. It would therefore be desirable if the controller were able to auto configure. Currently control systems lack this capability.

The reference to any prior art in this specification is not, and should not be taken as, an acknowledgment or any form of suggestion that that prior art forms part of the common general knowledge in Australia.

SUMMARY OF THE INVENTION The present invention provides an adaptive self-tuning controller for a refrigerant pressure effecting component of refrigeration system, comprising: a control processor coupled to said pressure effecting component for providing a closed loop control over said component based on an error signal; S. said control processor including memory for storing first processing instructions for performing a control algorithm that includes at least one programmably adjustable gain factor; said control processor including memory for storing second processing instructions for adaptively changing said programmably adjustable gain factor by periodically generating a new gain factor; said second processing instructions causing said control processor to: monitor fluctuation in said error signal and generate a numeric value indicative of the percent fluctuation in said error signal over a predetermined time; fuzzify said numeric value by applying a membership function to generate a set of fuzzy input values indicative of degree of membership; apply a predetermined set of rules upon said fuzzy input values to generate a set of fuzzy output values, the predetermined set of rules reflecting the degree to which the gain factor associated with a given member of said P:\OPER\SSB\14743-02 rcp.do-14/04/03 membership function is to be changed; and defuzzifying said fuzzy output values by a combining operation yielding said new gain factor.

The present invention provides a method for controlling a refrigerant pressure effecting component of a cooling system, said steps comprising: providing a closed loop control over a pressure effecting component based on an error signal; storing first processing instructions for performing a control algorithm that includes at least one programmably adjustable gain factor; and storing second processing instructions for adaptably changing said programmably adjustable gain factor by periodically generating a new gain factor; wherein said step of storing said second processing instructions -includes monitoring fluctuation in said error signal; generating a numeric value indicative of the percent fluctuation,-in said: error;. signal over a predetermine time; fuzzifying said numeric value by applying a membership function; generating a set of fuzzy input values indicating degree of membership: of said numeric values; applying a predetermine set of rules upon said fuzzy input values, said 20 predetermined set of rules reflecting the degree to which -said gain factor associated with a given member of said membership function is to be changed; generating a set of fuzzy output values; and defuzzifying said fuzzy output values by a combining operation to yield said new gain factor.

25 The present invention relates generally to refrigeration systems, compressor control systems and refrigerant regulating valve control systems.

Certain embodiments of the invention relate to a refrigeration system employing a pulse width modulated compressor or evaporator stepper regulator controlled by a variable duty cycle signal derived from a load sensor. Preferably an adaptive controller generates the variable duty cycle signal. The compressor has two mechanical elements separated by a seal, and these mechanical elements are cyclically movable relative to one another to develop fluid pressure. The 1 P:'OPER\SSB\14743-02 rcp.doc-14/0 03 -6compressor includes a mechanism to selectively break the seal in response to the control signal, thereby modulating the capacity of the system.

The refrigeration system can be deployed as a distributed system in refrigeration cases and the like. The preferred arrangement allows the compressor and condenser subsystems to be disposed in or mounted on the refrigeration case, thereby greatly reducing the length of refrigerant conduit and refrigerant required.

An embodiment of the invention relates to a distributed refrigeration system in which the -condenser is disposed on the refrigeration case and serviced by a special pulse width modulated, compressor that may be also disposed within the case. If desired, the condenser and compressor can be coupled to. service a group of adjacent refrigeration cases, each case. having its own evaporator.: The pulse width modulated compressor preferably employs two mechanical.,.::, ,Ir elements, such as scroll members, that move rotationally relative to .oneanother.to:.:-.:', develop. fluid: pressure for-pumping the refrigerant. The compressor preferably.- includes.i mechanism that will selectively break. the seaLi-between..:the; :two mechanical- elements, thereby. altering the fluid: pressure developed. by ;the: compressor while allowing the mechanical elements to maintain substantially: constant relative movement with one another. The compressor can be pulse width.

20 modulated by making and breaking the fluid seal without the-teed to start and stop the electric motor driving the mechanical elements.

The pulse width modulated compressor may be driven by a control system that supplies a variable duty cycle control signal based on measured system load.

The controller may also regulate the frequency (or cycle,time) of the control signal 25 to minimize pressure fluctuations in the refrigerant system. The on time is thus equal to the duty cycle multiplied by the cycle time, where the cycle time is the inverse of the frequency.

The refrigeration system of certain embodiments of the invention has a number of advantages. Because the instantaneous capacity of the system is easily regulated by variable duty cycle control, an oversized compressor can be used to achieve faster temperature pull down at startup and after defrost, without causing short cycling as conventional compressor systems would. Another benefit of variable duty cycle control is that the system can respond quickly to sudden changes in condenser temperature or case temperature set point. The controller adjusts capacity in response to disturbances without producing unstable oscillations and without significant overshoot. Also, the ability to match instantaneous capacity to the demand allows the system to operate at higher evaporator temperatures. (Deep drops in temperature experjenced by conventional systems at overcapacity are avoided.) Operating at higher evaporator temperatures reduces the defrost energy required because the system develops frost more slowly at higher temperatures.

Also, the time between defrosts can be lengthened by a percentage proportional to the accumulated runtime as dictated by the actual variable duty cycle control :i signal. For example, a sixty percent duty cycle would increase a standard threehour time between defrosts to five hours The pulse width modulated operation of the system yields improved oil S. :return. The refrigerant flow pulsates between high capacity and low capacity (e.g.

100% and creating more turbulence which breaks down the oil boundary layer in the heat exchangers.

Another benefit of the variable duty cycle control system is its ability to operate with a variety of expansion devices, including the simple orifice, the thermal expansion valve (TXV) and the electronic expansion valve. A signal C• derived from the expansion device controller can be fed to the compressor controller of the invention. This signal allows the variable duty cycle control signal and/or its frequency to be adjusted to match the instantaneous operating conditions of the expansion device. A similar approach may be used to operate variable speed fans in air cooled condenser systems. In such case the controller of the invention may provide a signal to control fan speed based on the current operating duty cycle of the compressor.

Yet another benefit of certain embodiments of the invention is its ability to detect when the system is low on refrigerant charge, an important environmental concern. Low refrigerant charge can indicate the presence of leaks in the system.

Low charge may be detected by observing the change in error between actual temperature and set P:'opersb\9308-9es doc-301/)1/02 -8point temperature as the system duty cycle is modulated. The control system may be configured to detect when the modulation in duty cycles does not have the desired effect on temperature maintenance. This can be due to a loss of refrigerant charge, a stuck thermal expansion valve or other malfunctions.

For a more complete understanding of the features of the invention, and its advantages, reference should be made to the following detailed description, which is by way of example only, and to the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a system block diagram of a prior art refrigeration system configuration; :Figure 2 is a block diagram of a refrigeration system in accordance with an embodiment of the present invention; Figure 3 is a cross-sectional view of an embodiment of the pulse width modulated compressor, shown in the loaded state; Figure 4 is a cross-sectional view of the compressor of Figure 3, shown in the unloaded state; Figure 5 is a system block diagram of a refrigeration or cooling system in accordance with an embodiment of the present invention; 20 Figure 6 is a block diagram of the controller; Figure 7 is a block diagram showing how the controller may be used to modulate an evaporator stepper regulator; Figure 8 is a block diagram of the signal conditioning module of the controller of Figure 6; Figure 9 is a block diagram of the control module of the controller of Figure 6; is a state diagram depicting the operating states of the controller; Figure 11 is a flowchart diagram illustrating the presently preferred PI control algorithm; Figure 12 is a waveform diagram illustrating the variable duty cycle signal produced by the controller and illustrating the operation at a constant frequency; P:zpcr\sb\)3O)7.9gres.doc-30U/) I/i02 -9- Figure 13 is a waveform diagram of the variable duty cycle signal illustrating variable frequency operation; Figure 14 is a series of graphs comparing temperature and pressure dynamics of system employing the invention with a system of conventional design; Figure 15 is a block diagram illustrating the adaptive tuning module of an embodiment of the invention; Figure 16a is a flowchart diagram illustrating the presently preferred operation of the adaptive tuning module, specifically with respect to the decision Swhether to start tuning; Figure 16b is a flowchart diagram illustrating the presently preferred process performed by the adaptive tuning module in the integration mode; Figure 16c is a flowchart diagram illustrating the operation of the adaptive tuning module in the calculation mode; Figure 17 is a state diagram illustrating the operative states of the adaptive 15 tuning module; Figure 18 is a block diagram illustrating the fuzzy logic block of the adaptive tuning loop; Figure 19 is a membership function diagram for the fuzzy logic block of Figure 18; 20 Figure 20 is a truth table relating to the membership function of Figure 19 as used by the fuzzy logic block of Figure 18; Figure 21 is an output membership function diagram for the fuzzy logic block of Figure 18; and Figure 22 is a schematic illustrating exemplary sensor location for controlrelated and diagnostic-related functions of an embodiment of the present invention.

P:Aopcr\ssb\93087-98res doc-31/01/02 DESCRIPTION OF THE PREFERRED EMBODIMENTS Figure 1 illustrates how a conventional supermarket refrigeration system is configured. As previously discussed, it is conventional practice to place the compressors 30 and the condenser 32 in a location remote from the refrigeration cases 34. In this illustration, the compressors 30 are configured in a parallel bank located on the roof 36 of the building. The bank of compressors supply a large condenser 32, which may be air cooled or water cooled. The condenser supplies liquid refrigerant to a receiver 38. The receiver 38, in turn, supplies the individual -11refrigeration cases, which are connected in parallel, as illustrated. In most implementations a liquid line solenoid valve 40 is used to regulate flow to the associated evaporator 42. The refrigerant is supplied to the evaporator through a suitable expansion device such as expansion valve 44. The expansion valve 44 provides a restricted orifice that causes the liquid refrigerant to atomize into liquid droplets that are introduced into the inlet side of the evaporator 42. The evaporator 42, located within the refrigeration case 34, extracts heat from the case and its contents by vaporization of the liquid refrigerant droplets into a gas. The compressors 30 extract this gas by suction and compress it back into the liquid state. The liquid refrigerant is then cooled in the condenser 32 and returned to the receiver 38, whereupon the cycle continues.

To match cooling capacity to the load, the compressors 30 may be switched on and off individually or in groups, as required. In a typical supermarket ooo arrangement there may be several independent systems, each configured as shown in Figure 1, to handle different operating temperature ranges. Note that the liquid line 46 and the suction line 48 may each need to be quite lengthy up to 150 feet) to span the distance from refrigeration case to roof.

Figure 2 shows a refrigeration case 34 configured according to the principles S• of the present invention. The condenser 32 and compressor 30 are both disposed within case 34 or attached thereto. Evaporator 42 and the associated expansion valve 44 are likewise disposed within case 34. The condenser 32 is provided with a heat removal mechanism 50 by which heat is transferred to ambient. The heat removal mechanism can be a water jacket connected to suitable plumbing for carrying waste heat to a water cooling tower located on the building roof.

Alternatively, the heat removal mechanism can be a forced-air cooling system or a passive convection-air cooling system.

The refrigeration system of the invention employs a compressor controller 52 that supplies a pulse width modulated control signal on line 54 to a solenoid valve 56 on compressor 30. The compressor controller adjusts the pulse width of the control signal using an algorithm described below. A suitable load sensor such as temperature sensor 58 supplies the input signal used by the controller to determine pulse width.

-12- Figures 3 and 4 show the details of compressor 30. Figure 3 shows the compressor in its loaded state and Figure 4 shows the compressor in its unloaded state. The solenoid valve 56 switches the compressor between these two states while the compressor motor remains energized. One important advantage of this configuration is that the compressor can be pulse width modulated very rapidly between the loaded and unloaded states without interrupting power to the compressor motor. This pulse width modulated cycling exerts less wear on the compressor, because the motor is not subjected to sudden changes in angular momentum.

Referring to Figures 3 and 4, there is shown an exemplary compressor Compressor 30 may be used within a hermetic scroll compressor such as generally of the type described in assignee's U.S. Patent No. 5,102,316.

~The exemplary compressor 30 includes an outer shell 61 and an orbiting ~scroll member 64 supported on upper bearing housing 63 and drivingly connect to crankshaft 62 via crank pin 65 and drive bushing 60. A second non-orbiting scroll member 67 is positioned in meshing engagement with scroll member 64 and axially movably secured to upper bearing housing 63. A partition plate 69 is provided adjacent the upper end of shell 61 and serves to define a discharge chamber at the upper end thereof.

In operation, as orbiting scroll member 64 orbits with respect to scroll member 67, suction gas is drawn into shell 61 via suction inlet 71 and thence into .e~ ~compressor 30 through inlet 72 provided in non-orbiting scroll member 67. The "intermeshing wraps provided on scroll members 64 and 67 define moving fluid pockets which progressively decrease in size and move radially inwardly as a result of the orbiting motion of scroll member 64 thus compressing the suction gas entering via inlet 72. The compressed gas is then discharged into discharge chamber 70 via discharge port 73 provided in scroll member 67 and passage 74.

In order to unload compressor 30, solenoid valve 56 will be actuated in response to a signal from control module 87 to interrupt fluid communication to increase the pressure within chamber 77 to that of the discharge gas. The biasing force resulting from this discharge pressure will overcome the sealing biasing force thereby causing scroll member 67 to move axially upwardly away from orbiting -13scroll member 64. This axial movement will result in the creation of a leakage path between the respective wrap tips and end plates of scroll members 64 and 67 thereby substantially eliminating continued compression of the suction gas.

A flexible fluid line 91 extends from the outer end of passage 90 to a fitting 92 extending through shell 61 with a second line 93 connecting fitting 92 to solenoid valve 56. Solenoid valve 56 has fluid lines 82 and 84 connected to suction line 83 and discharge line 85 and is controlled by control module 87 in response to conditions sensed by sensor 88 to effect movement of non-orbiting scroll member 67 between the positions shown in Figures 3 and 4.

When compression of the suction gas is to be resumed, solenoid valve 56 will be actuated so as to move scroll member 67 into sealing engagement with scroll member 64.

The refrigeration case embodiment of Figure 2 may be packaged as a selfcontained.unit. While that may be a desirable configuration for many applications, the invention is not restricted to stand alone, self-contained refrigeration case configurations. Rather, the invention lends itself to a variety of different distributed refrigeration systems. Figure 5 shows an example of such a distributed system.

Referring to Figure 5, a single compressor 30 and condenser 32 can service i several distributed refrigeration cases or several distributed cooling units in a heating and cooling (HVAC) system. In Figure 5 the refrigeration cases or cooling system housings are shown as dashed boxes, designated 34a,,34b, and 34c.

Conveniently, the compressor 30 and condenser 32 may be disposed within or attached to one of the refrigeration cases or housings, such as refrigeration case or housing 34a.

Each refrigeration case or housing has its own evaporator and associated expansion valve as illustrated at 42 b, c) and 44 b, In addition, each refrigeration case or housing may have its own temperature sensor 58 b, c) supplying input information to the compressor controller 52. Finally, a pressure sensor 60 monitors the pressure .of the suction line 48 and supplies this information to compressor controller 52. The compressor controller supplies a variable duty cycle signal to the solenoid valve 56 as previously described.

-14- The multiple case or multiple cooling unit embodiment of Figure 5 shows how a single compressor can be pulse width modulated by compressor controller 52 to supply the instantaneous demand for cooling. The temperature sensors 58 b, c) collectively provide an indication of the load on the system, as does pressure sensor 60. The controller adjusts the pulse width of the control signal to modulate the compressor between its high capacity and low capacity states (100%, to meetthe instantaneous demand for refrigerant.

As an alternate control technique, one or more of the suction lines exiting the evaporator can be equipped with an electrically controlled valve, such as an evaporator pressure regulator valve 45c. Valve 45c is coupled to controller 52, as illustrated. It may be supplied with a suitable control signal, depending on the type of the valve. A stepper motor valve may be used for this purpose, in which case :controller 30 would supply a suitable signal to increment or decrement the setting of the stepper motor to thereby adjust the orifice size of the valve. Alternatively, a pulse width modulated valve could be used, in which case it may be controlled with the same variable duty cycle signal as supplied to the compressor Controller 52 is not limited to solely compressor control applications. The variable duty cycle control signal can also be used to control other types of refrigerant flow and pressure control devices, such as refrigerant regulating valves.

Figure 7 shows such an application, where the output of controller 52 supplies control signals to evaporator stepper regulator 43. This device is a fluid pressure regulator that is adjusted by stepper motor 45. The evaporator stepper regulator (ESR) valve 43 adjusts the suction pressure to thereby adjust the capacity of the system.

A block diagram of the presently preferred compressor controller is illustrated in Figure 6. A description of the various signals and data values shown in this and successive figures is summarized in Table I below.

TABLE I *0 3 3 1 Signal Conditioning: Sensor Alarm Sensor Mode -Sampling Time (Ts) Control Type Control Block: Sensor Alarm r System Alarm I 4aiov Min 0.5 sec T/P Type False False

-SSL

Defrost Status Pull_DownTime Gain (K) Integral Time (Ti) Control Time (Tc) Control Set Pt. (St) Operating State Defrost Control Defrost Status Defrost Type Description Indicates Sensor Reading is not within expected range User configuration to indicate if Min/Max/Avg is performed for all temperature Sensors Rate at which Signal conditionina block is executed if controlled by only Temp. or both Temp. Pressure Same as before Generated by Adaptive Block indicative some system problem Steady state loading Whether system is in defrost Time taken to pull down after defrost Gain used in PI algorithm used in PI used in PI used in PI What state the machine is operating at If defrost status of the case If the defrost is from external timer or Internal clock of controller Time between defrost Defrost Duration Termination temperature for defrost i' -0 False -0 -7 100 10 Sec

-OF

-1 False External Defrost Interval 8 hrs Defrost Duration 1 hr Defrost Termination 50F Temp.

defrost -16- At the heart of the controller is control block module 102. This module is responsible for supplying the variable duty cycle control signal on lead 104.

Module 102 also supplies the compressor ON/OFF signal on lead 106 and an operating state command signal on lead 108. The compressor ON/OFF signal drives the contactors that supply operating current to the compressor motor. The operating state signal indicates what state the state machine (Fig 10) is in currently.

The control block module receives inputs from several- sources, including temperature and pressure readings from the temperature and pressure sensors previously described. These temperature readings are passed through signal conditioning module 110, the details of which are shown in the pseudocode Appendix. The control block module also receives a defrost status signal from defrost control module 112. Defrost control module 112 contains logic to determine when defrost is performed. The present embodiment allows defrost to be controlled either by an external logic signal (supplied through lead 114) or by an S. internal logic signal generated by the defrost control module itself. The choice of *o°whether to use external or internal defrost control logic is user selectable through user input 116. The internal defrost control uses user-supplied parameters *supplied through user input 118.

The preferred compressor controller in one form is autoconfigurable. The Scontroller includes an optional adaptive tuning module 120 that automatically adjusts the control algorithm parameters (the proportional constant K) based on operating conditions of the system. The adaptive tuning module senses the percent loading (on lead 104) and the operating state (on lead 108) as well as the measured temperature after signal conditioning (on lead 122). Module 120 supplies the adaptive tuning parameters to control block 102, as illustrated. The current embodiment supplies proportional constant K on lead 124 and SSL parameter on lead 126, indicative of steady-state loading percent. A system alarm signal on lead 126 alerts the control block module when the system is not responding as expected to changes in the adaptively tuned parameters. The alarm thus signals when there may be a system malfunction or loss of refrigerant charge.

The alarm can trigger more sophisticated diagnostic routines, if desired. The -17compressor controller provides a number of user interface points through which user-supplied settings are input. The defrost type (internal/external) input 116 and the internal defrost parameters on input 118 have already been discussed. A user input 128 allows the user to specify the temperature set point to the adaptive tuning module 120. The same information is supplied on user input 130 to the control block module 102. The user can also interact directly with the control block module in a number of ways. User input 132 allows the user to switch the compressor on or off during defrost mode. User input 134 allows the user to specify the initial controller parameters, including the initial proportional constant K. The proportional constant K may thereafter be modified by the adaptive tuning module 120. User input 136 allows the user to specify the pressure differential (dP) that the system uses as a set point.

In addition to these user inputs, several user inputs are provided for interacting with the signal conditioning module 110. User input 138 selects the sensor mode of operation for the signal conditioning module. This will be described in more detail below. User input 140 allows the user to specify the sampling time used by the signal conditioning module. User input 142 allows the s. user to specify whether the controller shall be operated using temperature sensors Osso only or temperature and pressure sensors 20 Referring now to Figure 8, the signal conditioning module is shown in detail.

The inputs (temperature and/or pressure sensors) are shown diagrammatically at 144. These inputs are processed through analog to digital convertor 146 and then supplied to the control type selector 148. Temperature readings from the temperature and/or pressure sensors are taken sequentially and supplied serially through the analog to digital convertor. The control type selector codes or stores the data so that pressure and temperature values are properly interpreted.

Digital filtering is then applied to the signal at 150 to remove spurious fluctuations and noise. Next, the data are checked in module 152 to ensure that all readings are within expected sensor range limits. This may be done by converting the digital count data to the corresponding temperature or pressure values and checking these values against the pre-stored sensor range limits. If the -18readings are not within sensor range an alarm signal is generated for output on output 154.

Next a data manipulation operation is performed at 156 to supply the temperature and/or pressure data in the form selected by the sensor mode user input 138. The current embodiment will selectively average the data or determine the minimum or maximum of the data (Min/Max/Avg). The Min/Max/Avg mode can be used to calculate the swing in pressure differential, or a conditioned temperature value. The average mode can be used to supply a conditioned temperature value.

These are shown as outputs 158 and 160, respectively; 10 Figure 9 shows the control block module in greater detail. The conditioned ":""temperature or pressure signal is fed tocalculation module 162 that calculates the error between the actual temperature or pressure and the set point temperature or :pressure. Module 162 also calculates the rate of change in those values.

The control block module is designed to update the operating state of the system on a periodic basis (every T seconds, nominally once every second). The Find Operating State module 164 performs this update function. The state diagram of Figure 10 provides the details on how this is performed. Essentially, the operating state advances, from state to state, based on whether there is a sensor alarm (SA) present, whether there is a defrost status signal (DS) present and what the calculated error value is. The Find Operating State module 164 supplies the :i operating state parameter and the Pull Down Time parameter to the decision logic module 166.

Referring to Figure 10, the Find Operating State module 164 advances from state to state as follows. Beginning in the initial state 168 the module advances to the normal operating state 170 after initialization. It remains in that state until certain conditions are met. Figure 10 shows by label arrows what conditions are required to cycle from the normal operating state 170 to the defrost state 172; to the pull down state 174; to the sensor alarm pull down state 176; to the sensor alarm operating state 178 and to the sensor alarm defrost state 180.

The decision logic module 166 (Figure 9) determines the duty cycle of the variable duty cycle signal. This is output on lead 182, designated Loading. The decision logic module also generates the compressor ON/OFF signal on lead 184.

-19- The actual decision logic will be described below in connection with Figure 11.

The decision logic module is form of proportional integral (PI) control that is based on an adaptively calculated cycle time T

C

This cycle time is calculated by the calculation module 186 based on a calculated error value generated by module 188. Referring back to Figure 6, the conditioned pressure differential signal on lead 122 (Cond dP) is supplied to the Calculate Error module 188 (Figure 9) along with the pressure differential set point value as supplied through user input 136 (Figure The difference between actual and set point pressure differentials is calculated by module 188 and fed to the calculation module 186. The adaptive cycle time T, is a function of the pressure differential error and the operating state as determined by the find operating state module 164 according to the following calculation: Tcyc(new) Tcyc(old) K Error (1) where: KC: proportional constant; and Error: (actual set point) suction pressure swing.

The presently preferred PI control algorithm implemented by the decision logic module 166 is illustrated in Figure 11. The routine begins at step 200 by reading the user supplied parameters K, Ti, Tc and See Figure 6 for a description of these user supplied values. The constant Kp is calculated as being equal to the initially supplied value K; and the constant K i is calculated as the product of the initially supplied constant K and the ratio T/T,.

Next, at step 202 a decision is made whether the absolute value of the error between set point temperature and conditioned temperature (on lead 190, Figure 9) is greater than 5%F. If so, the constant Kp is set equal to zero in step 204. If not, the routine simply proceeds to step 206 where a new loading percent value is calculated as described by the equation in step 206 of Figure 11. If the load percent is greater than 100 (step 208), then the load percent is set equal to 100% at step 210. If the load percent is not greater than 100% but is less than 0% (step 212) the load percent is set equal to 0% at step 214. If the load percent is between the 0% and 100% limits, the load percent is set equal to the new load percent at step 216.

The variable duty cycle control signal generated by the controller can take several forms. Figures 12 and 13 give two examples. Figure 12 shows the variable duty cycle signal in which the duty cycle varies, but the frequency remains constant. In Figure 12, note that the cycle time, indicated by hash marks 220, are equally spaced. By comparison, Figure 13 illustrates the variable duty cycle signal wherein the frequency is also varied. In Figure 13, note that the hash marks 220 are not equally spaced. Rather, the waveform exhibits regions of constant frequency, regions of increasing frequency and regions of decreasing frequency.

The variable frequency illustrated in Figure 13 is the result of the adaptive modulation of the cycle time TC.

Figure 14 graphically shows the benefits that the control system of the i invention has in maintaining tighter temperature control and higher suction pressure with improved system efficiency. Note how the temperature curve 222 of the eoo* i invention exhibits considerably less fluctuation than the corresponding temperature curve 224 of a conventional controller. Similarly, note that the pressure curve 226 of the invention has a baseline well above that of pressure curve 228 of the conventional controller. Also, the peak-to-peak fluctuation in pressure exhibited by the invention (curve 226) is much smaller than that of the conventional controller S"(curve 228).

The controller of the invention operates at a rate that is at least four times i faster (typically on the order of at least eight times faster) than the thermal time constant of the load. In the presently preferred embodiment the cycle time of the variable duty cycle signal is about eight times shorter than the time constant of the load. By way of non-limiting example, the cycle time of the variable duty cycle signal might be on the order of 10 to 15 seconds, whereas the time constant of the system being cooled might be on the order of 1 to 3 minutes.

The thermal time constant of a system being cooled is generally dictated by physical or thermodynamic properties of the system. Although various models can be used to describe the physical or thermodynamic response of a heating or cooling system, the following analysis will demonstrates the principle.

-21- Modeling the thermal time constant of the system being cooled One can model the temperature change across the evaporator coil of a refrigeration system or heat pump as a first order system, wherein the temperature change may be modeled according to the following equation: AT AT,, AToexp(-T/y).

where: AT air temperature change across coil AT,, steady state air temperature change across coil ATo air temperature change across the coil at time zero 10 t time y time constant of coil.

SThe transient capacity of the unit can be obtained by multiplying the above equation by the air mass flow rate and specific heat at constant pressure and integrating with respect to time.

15 Generally, it is the removal of the refrigerant from the evaporator that controls the time required to reach steady state operating condition, and thus the steady state temperature change across the condenser coil. If desired, the system can be modeled using two time constants, one based on the mass of the coil and another based on the time required to get the excess refrigerant from the 20 evaporator into the rest of the system. In addition, it may also be desirable to take into account, as a further time delay, the time lag due to the large physical distance between evaporator and condenser coils in some systems.

The thermal response of the evaporator coil may be modeled by the following equation: 0 2 Vy,) (1-e 2 where: 0 temperature change across coil/steady state temperature change across coil t time -22- Y1 time constant based on mass of coil Y2 time constant based on time required to remove excess refrigerant from evaporator In practice, the controller of the invention cycles at a rate significantly faster than conventional controllers. This is because the conventional controller cycles on and off in direct response to the comparison of actual and set-point temperatures (or pressures). In other words, the conventional controller cycles on when there is demand for cooling, and cycles off when the error between actual and set-point temperature is below a predetermined limit. Thus the on-off cycle of the :i 10 conventional controller is very highly dependent on the time constant of the system being cooled.

In contrast, the controller of the invention cycles on and off at a rate dictated by calculated values that are not directly tied to the instantaneous relation between actual and set-point temperatures or pressures. Rather, the cycle time is dictated 15 by both the cycle rate and the duty cycle of the the variable duty cycle signal supplied by the controller. Notably, the point at which the controller cycles from on to off in each cycle is not necessarily the point at which the demand for cooling has ~been met, but rather the point dictated by the duty cycle needed to meet the demand.

20 Adaptive Tuningq The controller Geneva described above can be configured to perform a classic control algorithm, such as a conventional proportional-integral-derivative (PID) control algorithm. In the conventional configurationthe user would typically need to set the control parameters through suitable programming. The controller may also be of an adaptive type, described here, to eliminate the need for the user to determine and program the proper control parameters.

Thus, one important advantage of the adaptive controller is its ability to perform adaptive tuning. In general, tuning involves selecting the appropriate control parameters so that the closed loop system is stable over a wide range of operating conditions, responds quickly to reduce the effect of disturbance on the control loop and does not cause excessive wear of mechanical components 1 -23through continuous cycling. These are often mutually exclusive criteria, and a compromise must generally be made. In Figure 18 (and also Figure 6) there are two basic control loops: the refrigerationcontrol loop and the adaptive tuning loop.

The refrigeration control loop is administered by control block module 102; the adaptive loop is administered by adaptive tuning module 120. Details of the adaptive tuning module 120 are shown in Figures 15, 16a-16c and 17. The presently preferred adaptive tuning module uses a fuzzy logic control algorithm that will be described in connection with Figures 18-20.

Referring to Figure 15, the adaptive tuning module performs basically three functions. First, it decides whether to perform adaptive tuning. This is handled by module 240. Second, It gathers the needed parameters for performing adaptive i' tuning. This is handled by module 242. Third, it calculates the adaptive gain used :i by the control loop. This is handled by module 244.

Module 240 bases the decision on whether to start tuning upon two factors: the current operating state of the system and the control set point. The flowchart of Figure 16a shows the steps involved in this decision. Module 242 integrates key parameters needed for the calculations performed by module 244. Essentially, module 242 inputs the percent loading, the temperature and pressure values and the set point temperature. It outputs the following data: SER (the total number of conditioned temperature and pressure data points that are within 0.5 degrees or 1Psig of the set point value), S_Close (the total number of percent loading data points that goes to zero percent during a given sampling interval, e.g. 30 min.), S_Open (the total number of percent loading data points that goes to 100% in the sampling interval) and SSLP (a moving average or rolling average of the percent loading during the sampling interval). Module 242 is responsive to a tuning flag that is set by module 240. Module 242 performs the integration of these key parameters when signaled to do so by the tuning flag. Figure 16b shows the steps involved in performing integration of these key parameters.

Finally, the calculation block takes the data supplied by module 242 and calculates the adaptive gain using the process illustrated in Figure 16c.

The adaptive tuning module 120 will cycle through various operating states, depending on the state of a timer. Figure 17 is a state diagram showing how the -24presently preferred embodiment will function. Note that the sequence transitions from the initialization mode to either the integration mode or the no tuning mode, depending on whether the tuning flag has been set. Once in the integration mode, the system performs integration until the timer lapses (nominally 30 minutes), whereupon the calculation mode is entered. Once the calculations are completed the timer is reset and the system returns to the initialization mode.

The block diagram of the adaptive scheme is shown in Figure 18. There are two basic loops The first one is the PID control loop 260 that runs every "dt" second and the second is the adaptive loop 262 that runs every "ta" second.

When the control system starts, the PID control loop 260 uses a default value of gain to calculate the control output. The adaptive loop 262, checks the error e(t) 264 every "ta" seconds 266 (preferably less than 0.2 dt seconds). At module 268 if the absolute value of error, is less than desired offset a counter Ernew is incremented. The Offset (OS) is the acceptable steady-state error for temperature control it may be OF). This checking process continues for "tsum" seconds 270 (preferably 200 to 500 times dt seconds). After "tsum" seconds 270, the value Ernew is converted into percentage (Er_new% 272). The parameter Er_new% 272 indicates the percentage of sampled e(t) that was within accepted offset (OS) for "tsum" time. In other words, it is a measure of how well the control variable was controlled for past "tsum" seconds. A value of 100% means "tight" control and 0% means "poor" control. Whenever Er_new% is 100%, the gain remains substantially unchanged as it indicates tighter control.

However, if Ernew happens to be between 0 and 100%, adaptive fuzzy-logic algorithm module 274 calculates a new gain (K_new 276) that is used for next "tsum" seconds by the control algorithm module 278.

In the preferred embodiment, there is one output and two inputs to the fuzzy-logic algorithm module 274. The output is the new gain (K_new) calculated using the input, Er_new%, and a variable, Dir, defined as follows: Dir Sign[(ER-new% ER_old%) (K_new K-old)] (2) where: Sign stands for the sign -ve or zero) of the term inside the bracket; Er_new% is the percentage of e(t) that is within the offset for past "tsum" seconds; Er_old% is the value of Er_new% in "(tsum-1)" iteration; K_new is the gain used in "tsum" time; and K_old is the gain in (tsum-1) time.

For example, suppose the controller starts at 0 seconds with a default value of K=10 and, ta=1 seconds, tsum=1000. seconds and OS=1. Suppose 600 e(t) data out of a possible 1000 data was within the offset. Therefore, after 1000 sec, 600/1000*100), K_new=10. Erold% and K_old is set to zero 10 when the adaptive fuzzy-logic algorithm module 274 is used the first time.

Plugging these numbers in Eq.(2) gives the sign of the variable "Dir" as positive.

Accordingly, the inputs to the adaptive fuzzy-logic module 274 for the first iteration are respectively,. Er_new%=60 and Dir=+ve.

The next step is to perform fuzzification of these inputs into fuzzy inputs by using membership functions.

Fuzzification: A membership function is a mapping between the universe of discourse (x-axis) and the grade space (y-axis). The universe of discourse is the range of possible values for the inputs or outputs. For ER_new% it is preferably from 0 to 100. The value in the grade space typically ranges from 0 to 1 and is called a fuzzy input, truth value, or a degree of membership. Figure 19 shows graph 300 which contains the membership functions for the input, Er_new%. Ernew% is divided into three linguistic variables LARGE (304), MEDIUM (306) AND SMALL (308). For Ernew%=60, the fuzzy inputs (or degree of membership function) are 0.25 of LARGE and 0.75 of MEDIUM. The input variable "Dir" is well defined -ve or zero) and thus does not require a membership function in this application. The next step is to create the "Truth Table" or Rule Evaluation.

Rule Evaluation: -26- Rule evaluation takes the fuzzy inputs from the fuzzification step and the rules from the knowledge base and calculates fuzzy outputs. Figure 20 shows the rules as truth table. For the first column and first row, the rule is: "IF ER new% is LARGE AND Dir is NEGATIVE THEN New Gain is NO CHANGE if the percentage of e(t) data that is within the offset (OS) for last "tsum" seconds is LARGE and the direction (DIR) is NEGATIVE/ZERO then do not change the existing K value (NO CHANGE)).

In the example, because ERnew% has fuzzy inputs LARGE (0.25) AND MEDIUM (0.75) with POSITIVE Dir, the rules that will be used are: 10 IF ER new% is LARGE (0.25) AND Dir is POSITIVE THEN New Gain is NO :i CHANGE (NC=1) IF ER new% is MEDIUM (0.75) AND Dir is POSITIVE THEN New Gain is POSITIVE SMALL CHANGE (PSC=1.2) Defuzzification: 15 Finally, the defuzzification process converts the fuzzy outputs from the rule evaluation step into the final output by using Graph 310 of Figure 21. Graph 310, uses the following labels "NBC" for negative big change; "NSC" for negative small change; "NC" for no change; "PSC" for positive small change; and "PBC" for positive big change. The Center of Gravity or centroid method is used in the 20 preferred embodiment for defuzzification. The output membership function for change in gain is shown in Figure 21.

The centroid (the Fuzzy-Logic Output) is calculated as: Sal.x (-x Centroid K new allx (3) Sall.x where: p(x) is the fuzzy output value for universe of discourse value x.

In our example, the output (K_new) becomes -27- Output 0 .25(1) +0.75(1.2) (4) 0.25 +0.75 Once the three steps of fuzzification, rule evaluation, and defuzzification are finished and the output has been calculated, the process is repeated again for new set of Ernew%.

In the above example, after the first 1000 sec, the adaptive algorithm calculates a new gain of K_new=11.50. This new gain is used for the next 1000 sec from t=1000 to 2000 sec in real time) by the PID control loop. At t=1001 Ssec, counter Er new is set to zero to perform counting for the next 1000 seconds.

At the end of another 1000 seconds (ie. at t=2000 seconds), Ernew% is calculated again.

10 Suppose this time, Er_new% happens to be 25. This means, by changing K from 10 to 11.5, the control became worse. Therefore, it would be better to change gain in the other direction i.e. decrease the gain rather than increase.

'Thus, at t=2000 sec, Er_new%=25, Er_old%=60 (previous value of Ernew%), K _new=l 1.5 and K_old=10 (previous value of Applying a negative "Dir" 15 is obtained. With Er_new% of 25 and Dir=Negative, the fuzzy-logic calculation is performed again to calculate a new gain for the next 1000 seconds. The new value of gain is K_new=7.7 6 and is used from t=2000 to 3000 seconds by the PID Loop.

Suppose for the third iteration i.e. from t=2000 to 3000 seconds, Ernew% comes out to be 95% (which represents tighter control). Performing the same fuzzy-logic operation gives the same value of K_new, and the gain remains unchanged until Er_new% again degrades.

Exemplary Applications Both pulse width modulated (PWM) Compressors and electronic stepper regulator (ESR) Valves can be used to control evaporator temperature/pressure or evaporator cooling fluid (air or water) temperature. The former controls by modulating the refrigerant flow and the latter restricts the suction side to control the flow. Referring back to Figure 18, the block diagram of the control system for such I I, -28an actuator working in a refrigeration system 279 is shown. In Figure 18 one and preferably up to four temperatures of evaporator cooling fluid or one evaporator suction pressure (generally shown at 282) is sampled every dt seconds. A sampling time of dt=1O seconds was found to be optimum for both the applications.

After processing by the analog to digital module 284, the sampled signal is then reduced to one number by taking the average or the minimum or the maximum of the four temperatures depending on the system configuration or the user preference at module 286. Typically, in a single actuator (PWM/ESR) systems where the complete evaporator coil goes into defrost at one time, averaging of control signal is preferred. in a multiple evaporator-single actuator system where defrost of evaporator coils does not occur at the same time, minimum is the preferred mode. The value obtained after avg/min/max is called conditioned sic,- At comparison module 288 this is compared with the desired set point to calculate the error, e(t).

The control algorithm used in the loop is a Proportion-Integral (PI) control technique (PID). The PI algorithm calculates the valve position (0-100%) in case of ESR or calculates the percentage loading (O to 100%) in case of PWM compressor. A typical integral reset time, Ti, for both the actuators is 60 seconds.

.The gain is tuned adaptively by the adaptive loop, The adaptive algorithm is turned off in the preferred embodiment whenever: the system is in defrost; is going through pull-down; there a big set point change; sensor failure has been detected; ~or any other system failure is detected.

Consequently, the adaptive algorithm is typically used when the system is working under normal mode. The time "ta" preferably used is about 1 seconds and "tsum" is about 1800 seconds (30 minutes).

Diagnostics Related to PWM Compressor/ESR Valves Referring to Figure 22, a discharge cooling fluid temperature sensor 312 an evaporator coil inlet temperature sensor 314 (Ti) and an evaporator coil exit temperature sensor 316 (To) ban provide diagnostic features for the evaporator control using PWM/ESR. The Inlet temperature sensor 314 can be anyyvhere in -29evaporator coil 318. However, the preferred location is about one third of the total evaporator length from the evaporator coil distributor 320.

Using these three temperature sensors, system learning can be performed that can be used for diagnostics. For example, diagnostics can be performed for ESR/PWM when it is used in a single evaporator along with an expansion valve.

In this example, the following variables are tracked every "tsum" second in the adaptive loop. The variables can be integrated just after ER_new integration is done in the adaptive loop.

N-Close: Number of times Valve position /PWM loading was 0%.

10 N-Open: Number of times Valve position/PWM loading was 100%.

MAVP: The moving average of the Valve position /PWM loading for "tsum" seconds.

SSLP: The steady-state Valve position /PWM loading is set equal to MAVP if for the "tsum" duration ER_new% is greater than dT: Moving average of the difference between Ta and Ti (Ta-Ti).

SH: Moving average of the difference between To and Ti (To-Ti) in the said duration. This is approximately the evaporator superheat.

N FL: Number of times To was less than Ti during the said duration i.e. "tsum" seconds. This number will indicate how much the expansion valve is flooding the evaporator.

In addition, Pull-down time after defrost, tpd, is also learnt. Based on these variables, the following diagnostics are performed: temperature sensor failure; degraded expansion valve; degraded ESR valve/PWM Compressor; oversized ESR/PWM; undersized ESR/PWM; and no air flow.

Temperature Sensor Failure: Failures of temperature sensors are detected by checking whether the temperature reading falls within the expected range. If PWM/ESR is controlled using Ta as the control variable, then when it fails, the control is done as follows.

The above said actuator is controlled based on Ti, or the Ta values are estimated using the learned dT add dT to Ti value to estimate Ta). During pull down, the valve/PWM can be set to full-open/load for the learned pull-down time (tpd).

.If Ti also fails at the same time or is not available, the actuator is opened 100% during pull down time and then set to steady-state loading percent (SSLP) after pull-down-time. An alarm is sent to the supervisor upon such a condition.

Degraded Expansion Valve: If an expansion valve sticks or is off-tuned or is undersized/oversized, the following combinations of the tracked variable can be used to diagnose such problems. N_FL 50% and ER_new% >10% indicate the expansion valve is stuck open or is off-tuned or may be even oversized and thus is flooding the evaporator 10 coil. An alarm is sent upon such a condition. Moreover, SH>20 and N_FL=0% indicate an off-tuned expansion valve or an undersized valve or the valve is stuck closed.

Degraded ESR Valve/PWM Compressor .i A degraded ESR is one that misses steps or is stuck. A degraded PWM Compressor is one whose solenoid is stuck closed or stuck open. These problems are detected in a configuration where defrost is performed by setting the ESR/PWM to The problem is detected as follows.

If ER new% 50% before defrost and during defrost Ti 32 0 F and SH Ai 5° F, then the valve is determined to be missing steps. Accordingly, the valve is 20 closed by another 100% and if Ti and SH remain the same then this is highly indicative that the valve is stuck.

If ER new%=0 and N_Close is 100% and Ti 32 0 F and SH 5"F then PWM/ESR is determined to be stuck open. If ER_new%=0 and N_Open is 100% and Ti 320 F and SH 50 F then PWM/ESR is determined to be stuck closed.

Over-sized

ESR/PWM:

If N Close 90% and 30% ER_new% 100%, then an alarm is sent for oversized 'alve/PWM Compressor.

Under-sized

ESR/PWM:

-31- If N_Opeh 90% and ER_new% =0 and SH 5, then an alarm is sent for undersized valve/PWM Compressor.

No Air Flow: If N_Open =100%, ER_new%=0, SH 50 F and Ti <250 F and N_FL then either the air is blocked or the fans are not working properly.

Additionally, these diagnostic strategies can also be applied to an electronic expansion valve controller.

The embodiments which have been set forth above were for the purpose of illustration and were not intended to limit the invention. It will be appreciated by 10 those skilled in the art that various changes and modifications may be made to the embodiments discussed in this specification without departing from the spirit and scope of the invention as defined by the appended claims.

Throughout this specification and the claims which follow, unless the context requires otherwise, the word "comprise", and variations such as "comprises" and "comprising", will be understood to imply the inclusion of a stated integer or step or group of integers or steps but not the exclusion of any other integer or step or group of integers or steps.

S

-32- Appendix Pseudocode for performing signal conditioning Repeat the following every Ts Seconds: Read User Inputs: -Sampling Time (Ts) -Control Type (P or T) -Sensor Mode (Avg/Min/Max) Perform Analog to Digital Conversion (ADC) -on all (four) Temp. Sensor Channels output data as Counts Digitally Filter Counts -Ynew 0.75 Yold 0.25 Counts output data as Filtered Counts Convert Filtered Counts to Deg F.

15 Test if at least one Sensor is within normal operating limits within -40 and If none are within limit--Set Sensor Alarm to TRUE S. Else Perform Avg/Min/Max operation based on Sensor Mode If Control Type is NOT a T/P Control Type Then End Signal Conditioning Routine (until next Ts cycle) Else (Control Type is T/P) Do the Following: Perform ADC on Pressure Sensor Channel -output data as Counts Digitally Filter Counts -Ynew 0.75 Yold 0.25 Counts -output data as Filtered Counts Convert Filtered Counts to Psig Test if pressure Sensor is within normal operating limits within 0 and +200 If not within limit: Set dP dP Set Pt.

Else Calculate dP Pmax-Pmin Set Sensor Alarm to Conditioned T/dP End Signal Conditioning Routine (until next Ts cycle)

Claims (22)

1. An adaptive self-tuning controller for a refrigerant pressure effecting component of refrigeration system, comprising: a control processor coupled to said pressure effecting component for providing a closed loop control over said component based on an error signal; said control processor including memory for storing first processing instructions for performing a control algorithm that includes at least one programmably adjustable gain factor; 10 said control processor including memory for storing second processing instructions for adaptively changing said programmably adjustable gain factor by o:.ooi periodically generating a new gain factor; said second processing instructions causing said control processor to: monitor fluctuation in said error signal and generate a numeric value S 15 indicative of the percent fluctuation in said error signal over a predetermined time; fuzzify said numeric value by applying a membership function to generate a set of fuzzy input values indicative of degree of membership; apply a predetermined set of rules upon said fuzzy input values to generate a set of fuzzy output values, the predetermined set of rules reflecting the 20 degree to which the gain factor associated with a given member of said membership function is to be changed; and defuzzifying said fuzzy output values by a combining operation yielding said new gain factor.

2. The controller of claim 1 wherein said first processing instructions cause said control processor to effect proportional closed loop control and wherein said gain factor is a proportioning constant.

3. The controller of claim 2 wherein said first processing instructions further cause said control processor to effect integral closed loop control. P:\OPER\SSB\2499480dispe..doc.3 1/01/02 34

4. The controller of claim 1 wherein said first processing instructions cause said control processor to effect integral closed loop control and wherein said gain factor is an integrating constant.

5. The controller of claim 1 wherein said membership function defines a plurality of linguistic variables representing different ranges of error values.

6. The controller of claim 5 wherein said linguistic variables include at least 0 three variables representing predefined, LARGE, MEDIUM and SMALL error value 0 00e ranges. .e oeeoo

7. The controller of claim 1 wherein said membership function defines at least three overlapping ranges of membership function values such that at least some of said numeric values indicative of percent fluctuation map onto more than one membership function value.

8. The controller of claim 1 wherein said second processing instructions further cause said control processor to monitor direction of fluctuation in said error 0signal and wherein said predetermined set of rules includes a first subset of rules S 20 for positive error signal fluctuations and a second subset of rules for negative error signal fluctuations.

9. The controller of claim 1 wherein said second processing instructions cause said controller to defuzzify said fuzzy output values by calculating the centroid of said fuzzy output values to derive a multiplier that is applied to said programmably adjustable gain factor to yield said new gain factor. The controller of claim 1 wherein said pressure effecting component is a compressor.

P:OPER\SSB\I4743-02 rspdoc-14/0403

11. The controller of claim 1 wherein said pressure effecting component is a valve.

12. The controller of claim 1 wherein said pressure effecting component is a stepper regulator valve.

13. A method for controlling a refrigerant pressure effecting component of a cooling system, said steps comprising: providing a closed loop control over a pressure effecting component based on an error signal; storing first processing instructions for performing a control algorithm that...- includes at least one programmably adjustable gain factor, and. storing second processing instructions for adaptabily; hangingsaid programmably adjustable gain factor by periodically generatinganew gain factor,; 'i W ".herein said step of storing said second processing instructions includes monitoring fluctuation in said error signal; generating a numeric value indicative of the percent fluctuation in said error signal over a predetermine time; fuzzifying said numeric value by applying a membership function; generating a set of fuzzy input values indicating degree of membership of said numeric values; applying a predetermine set of rules upon said fuzzy input values, said predetermined set of rules reflecting the degree to which ;said gain factor Sassociated with a given member of said membership function is to be changed; generating a set of fuzzy output values; and defuzzifying said fuzzy output values by a combining operation to yield said new gain factor.

14. The method of claim 13 wherein said step of storing first processing instructions includes effecting proportional closed loop control when said gain factor is a proportioning constant.

P:MOPER\SSm14743-02 resp.doc-14/04/03 -36- The method of claim 14 wherein said step of storing first processing instructions effects integral closed loop control.

16. The method of claim 13 wherein said step of storing first processing instructions includes effecting integral closed loop control when said gain factor is an integrating constant.

17. The method of claim 13 wherein said step of fuzzifying said numeric value by applying a. membership function includes defining a plurality of linguistic variables representing different ranges of error values.

18. The method of claim 13 further comprising the step of monitoringa directio'n:: ioffludtuation in said error signal, wherein said predetermind-.setof rules includes S.i aifirst subset of rules for positive error signal fluctuations andsa: second subset of rules:for negative error signal fluctuations. o oo *oooo* *°oo *~o oooo* *ooo*o* ooo09

19. The method of claim 13 further comprising the step of calculating the centroid of said fuzzy output value and deriving a multiplier that is applied to said programmably adjustable gain factor to yield said newgain factor.

An adaptive self-tuning controller substantially as hereinbefore described with reference to Figures 2 to 22.

21. A method for controlling a refrigerant pressure effecting component of a cooling system substantially as hereinbefore described with reference to Figures 2 to

22. DATED this 14 th day of April, 2003 Copeland Corporation by DAVIES COLLISON CAVE Patent Attorneys for the Applicant