Integrated adaptive capacity control for a steam turbine powered chiller unit

• US 7,328,587 B2
• Filed: 12/17/2004
• Issued: 02/12/2008
• Est. Priority Date: 01/23/2004
• Status: Expired due to Fees

• Current Assignee: Johnson Controls Tyco IP Holdings LLP (Johnson Controls International plc)
• Original Assignee: York International Corporation (Johnson Controls International plc)
• Inventors: Kachmar, Stephen Michael, Roberts, Brenda Jane, Shaffer, Dennis Lee, Eisensmith, Ryan Perry, Thompson, Russell Mark, Petroskie, Daniel J., Smyder, Eric John
• Primary Examiner(s): Jiang; Chen Wen
• Application Number:
  US11/015,388
• Publication Number:
  US 20050160748A1
• Time in Patent Office: 1,152 Days
• Field of Search: 622/281, 622/593, 621/26, 621/27, 606/00, 606/02, 417/228
• US Class Current: 62/228.1
• CPC Class Codes: F01D 15/08 Adaptations for driving, or combinations with, pumps
• 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: F05D 2270/44 active, predictive, or anticipative
• CPC Class Codes: F25B 11/00 Compression machines, plants or systems, using turbines, e.g. gas turbines
• CPC Class Codes: F25B 2600/0253 with variable speed
• CPC Class Codes: F25B 2600/2501 Bypass valves
• CPC Class Codes: F25B 27/00 Machines, plants or systems, using particular sources of energy F25B30/06 takes precedence
• CPC Class Codes: F25B 2700/195 of the condenser
• CPC Class Codes: F25B 2700/197 of the evaporator
• CPC Class Codes: F25B 49/02 for compression type machines, plants or systems
• CPC Class Codes: Y02B 30/70 Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Abstract

A control system for a steam turbine driven chiller unit is provided. The control system automatically utilizes the full range of the governor, compressor pre-rotation vanes, and hot gas bypass valve capabilities to control the capacity of the chiller and provide anti-surge and override control functions to prevent undesirable operational ranges while maintaining maximum efficiency of operation.

Claims

1. A method of controlling the capacity of a chiller system driven by a steam turbine, the method comprising the steps of:

providing a steam system having a steam supply, a steam turbine and a steam condenser connected in a steam loop;

providing a refrigerant system having a compressor, a refrigerant condenser, and an evaporator connected in a refrigerant loop, wherein the compressor is driven by the steam turbine;

sensing a value representative of a load of the refrigerant system;

determining a system pressure differential of the refrigerant system; and

controlling a speed of the steam turbine in response to the sensed load value and the determined system pressure differential to control capacity of the chiller system.

2. The method of claim 1 further comprising the steps of:

providing pre-rotation vanes to regulate flow of refrigerant to the compressor; and

controlling a position of the pre-rotation vanes in response to the sensed load value and the determined system pressure differential to control capacity of the chiller system.

3. The method of claim 2 further comprising the steps of:

providing a hot gas bypass valve to regulate flow of refrigerant between a high pressure side of the refrigerant system and a low pressure side of the refrigerant system; and

controlling the hot gas bypass valve in response to the sensed load value and the determined system pressure differential to control capacity of the chiller system.

4. The method of claim 3 wherein:

the step of controlling a speed of the steam turbine includes adjusting a speed of the steam turbine to maintain a desired system load condition;

the step of controlling a position of the pre-rotation vanes includes positioning the pre-rotation vanes in a predetermined minimum position, wherein the predetermined minimum position is based on the system pressure differential; and

the step of controlling the hot gas bypass valve includes positioning the hot gas bypass valve in a closed position.

5. The method of claim 4 wherein the predetermined minimum position for the pre-rotation vanes prevents the compressor from operating in a surge condition.

6. The method of claim 3 wherein:

the step of controlling a speed of the steam turbine includes operating the steam turbine at a predetermined minimum speed, wherein the predetermined minimum speed is based on the system pressure differential;

the step of controlling a position of the pre-rotation vanes includes adjusting a position of the pre-rotation vanes to maintain a desired system load condition; and

the step of controlling the hot gas bypass valve includes positioning the hot gas bypass valve in a closed position.

7. The method of claim 6 wherein the predetermined minimum speed for the steam turbine prevents the compressor from operating in a surge condition.

8. The method of claim 3 wherein:

the step of controlling a speed of the steam turbine includes operating the steam turbine at a predetermined minimum speed, wherein the predetermined minimum speed is based on the system pressure differential;

the step of controlling a position of the pre-rotation vanes includes positioning the pre-rotation vanes in a predetermined minimum position, wherein the predetermined minimum position is based on the system pressure differential; and

the step of controlling the hot gas bypass valve includes adjusting a position of the hot gas bypass valve to maintain a desired system load condition.

9. The method of claim 8 wherein:

the predetermined minimum position for the pre-rotation vanes prevents the compressor from operating in a surge condition; and

the predetermined minimum speed for the steam turbine prevents the compressor from operating in a surge condition.

10. The method of claim 2 wherein the step of controlling a position of the pre-rotation vanes includes:

determining a minimum position for the pre-rotation vanes in response to the determined system pressure differential, wherein the determined minimum position for the pre-rotation vanes prevents the compressor from operating in a surge condition; and

sending a control signal to the pre-rotation vanes to set a position of the pre-rotation vanes to the determined minimum position.

11. The method of claim 1 wherein the step of controlling a speed of the steam turbine includes:

determining a minimum speed for the steam turbine in response to the determined system pressure differential, wherein the determined minimum speed for the steam turbine prevents the compressor from operating in a surge condition; and

sending a control signal to the steam turbine to set a speed of the steam turbine to the determined minimum speed.

12. The method of claim 1 wherein the step of sensing a value representative of a load of the refrigerant system includes determining a leaving chilled liquid temperature from the evaporator.

13. The method of claim 1 wherein the step of determining a system pressure differential includes:

measuring a condenser pressure;

measuring an evaporator pressure; and

subtracting the measured evaporator pressure from the measured condenser pressure to determine the system pressure differential.

14. The method of claim 1 further comprising the step of engaging an override control to control the speed of the steam turbine in response to a detection of a fault condition in the chiller system.

15. The method of claim 14 wherein the fault condition in the chiller system comprises at least one of an out of range condenser pressure or evaporator pressure, a steam turbine first stage pressure measurement exceeding a predetermined pressure setpoint, or a governor valve position measurement exceeding a predetermined position setpoint.

16. A chiller system comprising:

a steam system comprising a steam supply, a steam turbine and a steam condenser connected in a steam loop;

a refrigerant system comprising a compressor, a refrigerant condenser, and an evaporator connected in a refrigerant loop, wherein the compressor is driven by the steam turbine; and

a central control panel to control operation of both the steam system and the refrigerant system, the central control panel comprising a capacity control system, the capacity control system being configured to adjust a speed of the steam turbine to control the capacity of the refrigerant system in response to a leaving chilled liquid temperature and a system pressure differential.

17. The chiller system of claim 16 wherein:

the refrigerant system further comprises pre-rotation vanes to regulate flow of refrigerant to the compressor; and

the capacity control system being configured to adjust a position of the pre-rotation vanes to control the capacity of the refrigerant system in response to a leaving chilled liquid temperature and a system pressure differential.

18. The chiller system of claim 17 wherein:

the refrigerant system further comprises a hot gas bypass valve to regulate flow of refrigerant between a high pressure side of the refrigerant system and a low pressure side of the refrigerant system; and

the capacity control system being configured to adjust a position of the hot gas bypass valve to control the capacity of the refrigerant system in response to a leaving chilled liquid temperature and a system pressure differential.

19. The chiller system of claim 18 wherein the capacity control system is configured to control the pre-rotation vanes, the hot gas bypass valve and the speed of the compressor to prevent the compressor from operating in a surge condition.

20. The chiller system of claim 18 wherein the capacity control system is configured to operate in one of a hot gas bypass control mode, a pre-rotation vane control mode, or a turbine speed control mode to control the capacity of the refrigerant system.

21. The chiller system of claim 20 wherein:

the hot gas bypass control mode includes operation at a predetermined minimum turbine speed and a predetermined minimum pre-rotation vane position;

the pre-rotation vane control mode includes operation with a closed hot gas bypass valve and at a predetermined minimum turbine speed; and

the turbine speed control mode includes operation with a closed hot gas bypass valve and at a predetermined minimum pre-rotation vane position.

22. The chiller system of claim 16 wherein the compressor, refrigerant condenser, evaporator and steam turbine are integrally mounted on a structural frame.

23. The chiller system of claim 16 wherein a cooling water output from the refrigerant condenser is operatively connected to a cooling water input to the steam condenser.

24. A chiller system comprising:

a steam system comprising a steam supply, a steam turbine and a steam condenser connected in a steam loop;

a refrigerant system comprising a compressor, a refrigerant condenser, and an evaporator connected in a refrigerant loop, wherein the compressor is driven by the steam turbine;

a turbine baseplate configured and disposed to mount the steam turbine in the chiller system, the turbine baseplate comprising a coupling device to rigidly connect the turbine baseplate and the compressor; and

a central control panel to control operation of both the steam system and the refrigerant system.

25. The chiller system of claim 24 wherein:

the turbine baseplate includes a base portion, the base portion being configured and disposed to support at least a portion of the steam turbine; and

the coupling device being disposed substantially perpendicularly to the base portion.

26. The chiller system of claim 25 wherein the compressor includes a housing with a machined face and the coupling device is connected to the machined face of the housing.

27. The chiller system of claim 24 wherein the turbine baseplate has a first end disposed adjacent the compressor and a second end opposite the first end, the first end of the turbine baseplate is mounted on a mounting arrangement for the compressor and the second end of the turbine baseplate is mounted on a tube sheet for the evaporator.