Control method and apparatus for a centrifugal chiller using a variable speed impeller motor drive

• US 5,355,691 A
• Filed: 08/16/1993
• Issued: 10/18/1994
• Est. Priority Date: 08/16/1993
• Status: Expired due to Term

• Current Assignee: Trane International Inc. (Trane Technologies plc)
• Original Assignee: American Standard Inc. (Trane Technologies plc)
• Inventors: Sullivan, Brian T., Rentmeester, Paul C., Goshaw, Craig M.
• Primary Examiner(s): Tanner, Harry B.
• Application Number:
  US08/107,391
• Time in Patent Office: 428 Days
• Field of Search: 62/201, 62/203, 62/204, 62/209, 62/228.1, 62/228.3, 62/228.4, 62/228.5, 62/217, 62/185, 62/182, 417/15, 417/29, 417/20, 417/32, 417/43, 417/316, 415/1, 415/15, 415/17, 415/36
• US Class Current: 62/201
• CPC Class Codes: F04D 27/0246 by varying geometry within the pumps, e.g. by adjusting vanes
• CPC Class Codes: F04D 27/0261 by varying driving speed
• CPC Class Codes: F04D 27/0284 Conjoint control of two or more different functions
• CPC Class Codes: F25B 1/053 of turbine type
• CPC Class Codes: F25B 2600/021 Inverters therefor
• CPC Class Codes: F25B 49/022 Compressor control arrangements
• CPC Class Codes: Y02B 30/70 Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Abstract

A controller for controlling the capacity of a centrifugal chiller compressor. The compressor is driven by an electric motor and has variable inlet guide vanes that control the flow of refrigerant to the compressor. The controller establishes a dimensionless plot of possible points of compressor operation relating the pressure coefficient and the capacity coefficient of the compressor. The current operating point of the centrifugal compressor is located on the plot and a dynamic surge boundary control curve is positioned proximate a region of actual surge. Control is exercised responsive to the variations of the region of actual surge and the surge boundary control curve for controlling compressor capacity by varying the opening of the inlet guide vanes and varying the speed of the compressor to move the operating point of the compressor proximate the surge boundary control curve.

Claims

1. A controller for adjusting the capacity of a variable capacity centrifugal compressor driven by a motor, the controller adapted for adjusting the capacity of the compressor in response to demand while minimizing electric power consumption and avoiding surge conditions, comprising:

means for establishing a dimensionless plot of possible points of compressor operation relating the pressure coefficient and the capacity coefficient of the centrifugal compressor;

means for determining the current operating point of the centrifugal compressor on the plot;

means for determining a region of actual surge on the plot;

means for plotting a dynamic surge boundary control curve proximate the region of actual surge; and

means responsive to variations of the region of actual surge and the surge boundary control curve for controlling compressor capacity by varying the opening of the inlet guide vanes and varying the speed of the compressor to move the operating point of the compressor proximate the surge boundary control curve.

2. The controller for adjusting the capacity of the compressor of claim 1, wherein the surge boundary control curve is continually updated with the plot of each new surge event.

3. The controller for adjusting the capacity of the compressor of claim 1, wherein the surge boundary control curve is continually repositioned with respect to the region of actual surge to provide efficient compressor operation and avoid surge conditions.

4. The controller for adjusting the capacity of the compressor of claim 3, wherein the surge boundary control curve includes means for continually repositioning the surge boundary control curve as a function of:

a. determining when the compressor operating point is within a set deadband about the surge boundary control curve;

b. sensing that no surge event has occurred since the last calculating time period;

c. determining that the surge boundary control curve has not been updated since the last calculating time period.

5. The controller for adjusting the capacity of the compressor of claim 1, having a first control mode wherein the capacity of the compressor is controlled by varying the inlet guide vane position and by varying the compressor speed and having a second control mode wherein the inlet guide vanes are set to a predetermined full open condition and compressor capacity is controlled only by varying the speed of the compressor.

6. The controller for adjusting the capacity of the compressor of claim 5, wherein the first mode of controlling compressor capacity includes first means for approaching the most efficient operating point of the compressor by determining that the chilled water temperature is in control, iteratively reducing the speed of the compressor, and correspondingly opening the inlet guide vanes to compensate for the reduced compressor speed to maintain control of the chilled water temperature.

7. The controller for adjusting the capacity of the compressor of claim 5, wherein the second mode of controlling compressor capacity second means for approaching the most efficient operating point of the compressor by determining that the chilled water temperature is in control and iteratively reducing the speed of the compressor, while maintaining control of the chilled water temperature.

8. The controller for adjusting the capacity of the compressor of claim 5, wherein the mode of controlling the operation of the compressor includes first means for shifting from the second mode to the first mode as a function of determining at least one of the following:

a. sensing that a surge event has occurred;

b. determining that the compressor operating point is located above the surge boundary control;

c. sensing that an operating limit of the air conditioning system has been exceeded;

d. sensing that the inlet guide vanes are not in the full open position.

9. The controller for adjusting the capacity of the compressor of claim 5, wherein the mode of controlling the operation of the compressor includes second means for shifting from the first mode to the second mode as a function of determining the following:

a. the chilled water temperature is in control;

b. the inlet guide vanes are at a predetermined maximum position.

10. A control method for a centrifugal chiller having a centrifugal compressor integrated into a refrigeration loop, the refrigeration loop additionally comprising a condenser and an evaporator, the compressor being adapted for the most efficient operation proximate an undesirable surge operating condition, the centrifugal compressor having an impeller and variable inlet guide vanes, the method comprising:

generating a dimensionless plot of possible operating points of the centrifugal compressor;

periodically sampling actual surge events experienced by the compressor during operation, to determine a region of actual surge;

periodically positioning an operating limit curve proximate the region of actual surge on the plot to define a compressor operating area that provides for efficient operation and yet avoids the occurrence of surge events;

defining the actual operating point of the compressor on the plot; and

controlling the operating point of the compressor by selectively adjusting the impeller speed and variable inlet guide vanes to position the operating point of the compressor at the operating limit curve.

11. The control method of claim 10 wherein the dimensionless plot is a two dimensional plot having two axes;

the first axis representing values of the capacity coefficient of the centrifugal chiller, the capacity coefficient being a function of the refrigerant tonnage produced by the chiller, the rotational speed of the impeller and the diameter of the impeller; and

the second axis representing the pressure coefficient of the chiller, the pressure coefficient being a function of the rotational speed of the impeller, the diameter of the impeller, the number of impellers, where more than one impeller is employed, and the isentropic enthalpy rise across the condenser.

12. The control method of claim 10 wherein the control method includes a bias that seeks an operating point of the chiller in which the inlet guide vanes are in a predetermined fully open position and chiller capacity is being controlled solely by the rotational speed of the impeller, the rotational speed of the impeller being set at a speed that places the operating point of the chiller proximate the operating limit curve.

13. The control method of claim 10 wherein the control method is responsive to the occurrence of a surge event and reacts to redefine the region of actual surge, reposition the operating limit curve to avoid the region of actual surge and controls the chiller to reposition the operating point of the compressor to avoid the reoccurrence of a surge condition.

14. The control method of claim 13 wherein, at the occurrence of a surge event, the control method transitions from a mode of control of the compressor that solely utilizes impeller speed control to a mode of operation in which control of the compressor utilizing inlet guide vane positioning and impeller speed is enabled.

15. A control method for use with a control system in controlling a centrifugal compressor, the compressor having variable inlet guide vanes and at least one rotationally driven impeller and being adapted such that the most efficient operation of the compressor occurs when the variable inlet guide vanes are in a predetermined fully open position and compressor capacity is controlled solely by the speed of the impeller, the control system sensing a steady state operating condition of the compressor, defined limits compelling that the compressor be unloaded, the inlet guide vane position, the impeller speed, sensing the current operating condition of the compressor the control method comprising:

a first control mode in which the control of the compressor capacity is a function of inlet guide vane positioning and impeller speed variations;

a second control mode in which the control of the compressor capacity is a function of impeller speed variations with the inlet guide vanes fixed in the fully open position;

defining an operating condition control limit region that is proximate a operating condition where a surge condition is known to occur;

transitioning from the first control mode to the second control mode predicated upon sensing that the compressor is operating in a steady state condition and the inlet guide vanes are in the predetermined fully open position; and

transitioning from the second control mode to the first control mode upon the occurrence of at least one of the following;

a. detecting that the compressor is operating outside the operating condition control limit region;

b. detecting that the defined limits compelling that the compressor be unloaded have been exceeded;

c. detecting the occurrence of a surge condition.

16. A controller for adjusting the capacity of a variable capacity centrifugal compressor driven by a motor to maintain a setpoint, the controller adapted for adjusting said capacity in response to demand while minimizing electric power consumption and avoiding a surge conditions, comprising:

means for determining the operating capacity of the compressor and expressing said capacity as a first variable;

means for determining the energy input of the compressor to the refrigerant and expressing said energy input as a second variable;

means for relating the first variable that is indicative of the operating capacity of the compressor to the second variable that is indicative of the energy input of the compressor to the refrigerant;

means for sensing the current operating condition of the compressor;

means for sensing surge conditions and thereby determining a region of actual surge;

plot generation means, responsive to the operating capacity variable sensing means, the energy input constant sensing means and the surge sensing means for plotting a surge curve and an operating limits curve, the operating limits curve being proximate the region of actual surge and defining a region of operation of the compressor such that compressor operation therein avoids surge conditions yet maintains a setpoint in an energy efficient manner; and

control means, responsive to the current operating condition sensing means, for relating the operating condition to the first variable that is indicative of the operating capacity of the compressor and the second variable that is indicative of the energy input of the compressor to the refrigerant said control means being adapted for controlling the compressor such that the operating condition of the compressor is within the operating limits curve proximate the region of actual surge.

17. An anti-surge method for a centrifugal compressor comprising the steps of:

determining a machine coefficient;

determining a pressure coefficient;

plotting a compressor operating point as a function of the machine coefficient and pressure coefficient;

monitoring actual surge events;

determining a surge boundary control curve as a function of the monitored actual surge events;

operating the compressor so that the compressor operating point approaches the surge boundary control curve; and

modifying the boundary control curve each time a surge event is detected.

18. The method of claim 17 including determining the machine coefficient as a function of compressor vapor flow, the rotational speed of the impellers, and the diameter of the impellers.

19. The method of claim 18 including determining the pressure coefficient as a function of the isentropic enthalpy rise, the number of compressor stages, the impeller diameter, and the rotational speed of the impellers.

20. The method of claim 19 wherein the machine coefficient is determined by the formula:

##EQU4## and the pressure coefficient is determined by the formula;

##EQU5##

21. The method of claim 20 wherein the step of operating the compressor includes the steps of varying the speed of the compressor and varying the position of inlet guide vanes.

22. The method of claim 17 wherein surges are detected by monitoring motor current, noise, or compressor pressure differential.

23. The method of claim 17 including the further step of establishing a deadband having upper and lower limits about the pressure boundary curve.

24. The method of claim 23 further including the further steps of establishing an upper limit of the deadband proximate a region of actual surge as determined by the monitored surge events and operating the compressor to place the compressor operating point between the surge boundary control curve and a lower limit of the deadband.

25. An anti-surge system for a centrifugal compressor comprising:

a compressor;

means for determining a machine coefficient;

means for determining a pressure coefficient;

means for plotting a compressor operating point as a function of the machine coefficient and pressure coefficient;

means for monitoring actual surge events;

means, responsive to the monitoring means, for determining a surge boundary control curve;

means for operating the compressor so that the compressor operating point approaches the surge boundary control curve; and

means for modifying the surge boundary control curve each time a surge event is detected.

26. The system of claim 25 wherein the machine coefficient is determined as a function of compressor vapor flow, the rotational speed of the impellers, and the diameter of the impellers.

27. The system of claim 26 wherein the pressure coefficient is determined as a function of the isentropic enthalpy rise, the number of compressor stages, the impeller diameter, and the rotational speed of the impellers.

28. The anti-surge system of claim 27 wherein the machine coefficient is determined by the formula:

##EQU6## and the pressure coefficient is determined by the formula;

##EQU7##

29. The system of claim 28 wherein operating means includes means for varying the speed of the compressor and the means for varying position of inlet guide vanes.

30. The system of claim 29 wherein the monitoring means including means for detecting surges by monitoring motor current, noise, or compressor pressure differential.

31. The system of claim 28 including a deadband about the surge boundary control curve.

32. The system of claim 25 wherein an upper limit of the deadband is proximate a region of actual surge as determined by monitored surge events and wherein the compressor is operated to place the compressor operating point between the surge boundary control curve and a lower limit of the deadband.

33. The system of claim 25 wherein the machine coefficient determining means and the pressure coefficient determining means are determined based upon measurements made relative to an evaporator and a condenser.

34. A method of operating a centrifugal compressor having variable position inlet guide vanes and having impellers controlled by a variable speed motor, comprising the steps of:

operating the variable speed motor at a constant high speed;

modulating the variable position of the inlet guide vanes until the variable position reaches a predetermined maximum position; and

incrementally reducing the speed of the motor as long as the variable position of the inlet guide vanes remains at the predetermined maximum position.

35. The method of claim 34 wherein the variable position of the inlet guide vanes is not measured, but is determined on the basis of position commands issued by a controller.

36. A method of operating a centrifugal compressor having impellers motivated by a variable speed impeller motor and having variable position inlet guide vanes, comprising the steps of:

operating in a first mode of operation where the position of the inlet guide vanes is modulated and the speed of the impeller motor is held constant;

operating in a second mode of operation wherein the position of the inlet guide vanes is maintained in a constant position and the speed of the impeller motor is modulated;

transitioning from the first mode of operation to the second mode of operation when the position of the inlet guide vanes approaches a predetermined maximum; and

transitioning from the second mode of operation to the first mode of operation when the impeller speed approaches a predetermined maximum.