Dual mode control of a variable displacement refrigerant compressor

• US 6,038,871 A
• Filed: 11/23/1998
• Issued: 03/21/2000
• Est. Priority Date: 11/23/1998
• Status: Expired due to Term

• Current Assignee: Mahle International GmbH (MAHLE-STIFTUNG GmbH)
• Original Assignee: General Motors Corporation (General Motors Company)
• Inventors: Gutierrez, Ernesto Jose, Archibald, Charles Andrew, Brandon, Giles M., Kachur, Christopher M.
• Primary Examiner(s): WAYNER, WILLIAM E
• Application Number:
  US09/197,963
• Time in Patent Office: 484 Days
• Field of Search: 62/228.3, 62/133, 62/228.5, 236/78 D
• US Class Current: 62/133
• CPC Class Codes: B60H 1/3216 for improving a change in operation duty of a compressor in a vehicle
• CPC Class Codes: F04B 27/0895 driving means
• CPC Class Codes: F04B 27/1804 Controlled by crankcase pressure
• CPC Class Codes: F04B 49/065 and making use of computers
• CPC Class Codes: F25B 49/022 Compressor control arrangements

Abstract

An improved control method for an electronically controlled variable displacement refrigerant compressor, where the control has normal and high speed displacement control modes, with smooth transitions between such control modes. The displacement control mechanism is in the form of a solenoid valve, and the valve is pulse-width-modulated (PWM) at a variable duty cycle to regulate displacement of the compressor. When the compressor is operating in a normal speed range, a first control mode determines a normal PWM duty cycle to satisfy cooling demand; when the compressor is operating in a high speed range, a second control mode determines an alternate PWM duty cycle based on compressor speed. The solenoid valve is operated in accordance with the duty cycle corresponding to the lower displacement. A smooth transition from the normal control mode to the high speed control mode is achieved by scheduling the alternate duty cycle as a function of compressor speed. Once in the high speed control mode, the parameters of the first control mode are adjusted so that the normal duty cycle matches the alternate duty cycle. This ensures a smooth transition from the high speed control mode to the normal control mode when the compressor speed falls back into the normal speed range.

Claims

1. A method of operation for an engine driven refrigerant compressor of an automotive air conditioning system, the compressor having a displacement that is controlled in accordance with an electrical displacement control signal developed in response to a cooling demand signal, the method comprising the steps of:

detecting a driven speed of the compressor;

generating a feedback signal indicative of a cooling effect actually produced by said air conditioning system;

developing the displacement control signal in accordance with a first control mode when the detected compressor speed is within a normal speed range, the first control mode being effective to set the displacement control signal at a normal control value selected to bring the feedback signal into correspondence with the cooling demand signal; and

developing the displacement control signal in accordance with a second control mode when the detected compressor speed is in a high speed range above said normal speed range, the second control mode being effective to (1) set the displacement control signal at an alternate value based on the detected compressor speed without regard to said cooling demand signal, and (2) modify a control parameter of said first control mode so that said normal control value matches said alternate value.

2. The method of operation of claim 1, wherein the compressor includes a solenoid controlled valve, and said electrical displacement control signal represents a duty cycle of pulse width modulation of said valve.

3. The method of operation of claim 1, wherein the second control mode compares said alternate value to said normal control value, and sets the displacement control signal at the value corresponding to a lower displacement of said compressor.

4. The method of operation of claim 3, wherein the step of modifying a control parameter of said first control mode is suspended when the feedback signal indicates that the cooling effect actually produced is less than the cooling demand.

5. The method of operation of claim 4, wherein the second control mode is effective to modify a control parameter of said first control mode when the compressor speed re-enters said normal speed range.

6. The method of operation of claim 1, wherein:

the step of developing the displacement control signal in accordance with the first control mode includes developing an integral term based on a cumulative error between said feedback signal and said demand signal; and

the step of developing the displacement control signal in accordance with the second control mode includes the step of modifying said cumulative error so that said normal control value matches said alternate value.

7. The method of operation of claim 1, wherein:

the step of developing the displacement control signal in accordance with the first control mode includes the steps of determining a refrigerant pressure for bringing the feedback signal into correspondence with the demand signal, and developing a normal control value of said displacement control signal for producing the determined refrigerant pressure; and

the step of developing the displacement control signal in accordance with the second control mode includes the step of modifying a first control parameter of said first control mode for bringing the determined refrigerant pressure into correspondence with an actual refrigerant pressure, and modifying a second control parameter of said first control mode for bringing the normal control value into correspondence with said alternate value.

8. The method of operation of claim 7, wherein:

the step of determining the refrigerant pressure in accordance with the first control mode includes developing an integral term based on a first cumulative error between said feedback signal and said demand signal;

the step of developing a normal control value of said displacement control signal in accordance with the first control mode includes developing an integral term based on a second cumulative error between said determined refrigerant pressure and an actual refrigerant pressure; and

the step of developing the displacement control signal in accordance with the second control mode includes the step of modifying the first and second cumulative errors for bringing the determined refrigerant pressure into correspondence with the actual refrigerant pressure, and for bringing the normal control value into correspondence with said alternate value.

9. The method of operation of claim 8, wherein the step of modifying the first and second cumulative errors includes the steps of:

determining a first cumulative error that would cause the determined refrigerant pressure to be equal to the actual refrigerant pressure; and

determining a second cumulative error that would cause the normal control value to equal the alternate control value.

10. The method of operation of claim 1, wherein the second control mode is effective when the detected compressor speed enters said high speed range to set the displacement control signal to a predetermined initial value, and thereafter to set the displacement control signal at the alternate value based on the detected compressor speed.