Method for operating a refrigeration system in steady state operation

<u>BACKGROUND OF THE INVENTION</u>

This invention relates to a method of optimizing a control scheme of a refrigeration system during steady state operation. In particular, the method is directed to a container refrigeration system.

A refrigeration system attached to the container cools the goods within the container to a target temperature. In the steady state regime system cooling capacity must be matched to the required refrigeration load in order to maintain tight temperature control. At any given point in time, the refrigeration system cooling capacity is determined by the system operating conditions, which in turn depend on the ambient temperature, the temperature inside the refrigerated container and the characteristics, and mode of operation, of the compressor and other refrigeration system components, such as suction modulation valve, heat exchangers, etc. On the other hand, the required refrigeration load is mostly a function of ambient temperature, temperature in refrigerated space, product respiration load and container size and insulation characteristics.

Once the system has reached, or at least approached, the target temperature, it is necessary to continuously adjust the capacity of the refrigeration system, while maintaining operation within a predetermined range of the target temperature. In the past, the controls associated with the refrigeration systems have not been sophisticated enough to achieve the reduced capacity while maintaining reliable and energy efficient system operation with accurate temperature control. Instead, generally, the refrigeration systems have simply on/off-cycled the compressor. Despite the simplicity and ease of on and off control, many refrigeration systems cannot effectively use this method due to the inability to maintain a tight temperature control in the refrigerated space. Further, this method has sometimes had reliability problems with electric motors and compressors caused by mechanical and/or electrical overloading due to the on/off cycling. Finally, in applications wherein there are widely varying load conditions, this method results in poor energy efficiency.

The prior art tried to achieve tight temperature control using throttle valves in the suction lines, and additional components such as compressor unloaders, bypass schemes, split coils, variable speed drives, multiple compressors, and various operations of the several systems to achieve the reduced capacity. However, these techniques often proved to be costly or unreliable thus there has still been a desire to achieve a more sophisticated method of controlling the capacity to optimize steady state control with respect to temperature control accuracy, energy efficiency and reliability.

<u>SUMMARY OF THE INVENTION</u>

In a disclosed embodiment of this invention, a microprocessor-based control algorithm attempts to tailor refrigeration cycle configuration in a way that results in the best match between required cooling load and available system capacity. The system available capacity is adjusted through several steps of capacity control and fine-tuned via continuous modulation of suction throttling valve. High temperature, low suction pressure, and high discharge pressure limits are monitored to ensure reliable operation. Control logic is altered in order to maintain the limits in a way that establishes desired tradeoff between energy efficiency, reliability and control accuracy across operating envelope.

The present invention will be explained in some detail below, however, it should be understood that many modifications of the detailed method to be described would come within the scope of this invention.

<u>BRIEF DESCRIPTION OF THE DRAWINGS</u>

Figure 1 schematically shows a refrigeration system.

Figure 2 is a flow chart of one method of steady state operation included in the present invention.

<u>DETAILED DESCRITION OF A PREFERRED EMBODIMENT</u>

A refrigeration system 20 is illustrated in Figure 1 having a compressor 22 delivering a refrigerant to a condenser 24. The condenser 24 delivers refrigerant to an economizer heat exchanger 26. From the economizer heat exchanger, a portion of the refrigerant passes into an evaporator expansion device 30, and then to the evaporator itself 32. From evaporator 32, the refrigerant passes to a suction throttling device 34, and then back to compressor 22. This is a basic refrigeration system, as is known.

As known, a portion of the fluid from condenser 24 expands through economizer expansion device 44 and passes through the economizer heat exchanger and is returned to the compressor via economizer shutoff valve 28, into an economizer port 42, if the economizer shutoff valve 28 is open. An unloader valve 36, positioned in by-pass line 46, communicates the economizer line 40 to the suction line 38, and is selectively opened to reduce the capacity in an unloaded state of operation. This economizer and unloader valve positioning is disclosed in co-pending United States Patent Application Serial No. 09/114,395, entitled "Scroll Compressor with Unloader Valve Between Economizer and Suction" and filed on July 13, 1998.

Preferably, the refrigeration system 20 is used for cooling a container box for holding a cargo. That is, the box air, such as shown, is being delivered against the evaporator 32.

A method for steady state operation of the refrigeration system 20 is illustrated in the flow chart form in Figure 2.

As shown, when the system is initially started, the container is typically at a temperature above a target temperature. Thus, a pull down method is initiated. The pull down method is best described in co-pending United States Patent Application Serial No. 08/108,787, filed July 2, 1998, and entitled "Method of Optimizing Cooling Capacity, Energy Efficiency and Reliability of a Refrigeration System During Temperature Pull Down."

As the pull down is ongoing, a control continues to compare the temperature in the refrigerated container, or the boxT temperature to the target_T temperature. If the two temperatures are not within a predetermined range of each other, then the pull down mode continues. However, at some point, the temperature difference between the temperature in the container boxT is within a predetermined range of the target_T temperature. At that point, the control enters steady state operation.

The flow chart shown in Figure 2 is a simplified representation of one rather detailed control method. Selected portions of this method may be utilized rather than the entire method, and the basic concept of driving the refrigeration system to optimum capacity regime may also be utilized in a more simplified form. As shown in the Figure 2 flow chart, once steady state operation is entered, the microprocessor checks if the refrigeration system is operating in its lowest capacity state.

For the refrigeration system shown in Figure 2, there are several basic states which are available. Generally, the highest capacity state would include the economizer being operated, with the unloader valve closed and the suction throttling device 34 fully opened. By opening and closing the suction throttling device, various gradations between the broader modes of operation can be achieved.

Generally speaking, the next lowest capacity would include the economizer circuit being closed by the shutoff valve 28 and the by-pass line 46 being closed by unloader valve 36. This is known as standard operation.

The next lowest capacity operation would include the economizer circuit being closed, and the unloader valve 36 being opened.

As shown in the flowchart of Figure 2, once pull down is complete, which is defined as the box temperature T_box being within a particular range of the desired box temperature T_boxset, then steady state mode is entered. As shown in Figure 2, steady state mode begins with a box 100 wherein a suction modulation valve is modulated to close or open depending on the difference between T_box and T_boxset. Preferably, the suction modulation valve is closed in a series of steps. Controls for controlling and closing the suction modulation valve in a series of steps are known, however, they have not been utilized to perform the method such as in this application. If the T_box is above the T_boxset, then the suction modulation valve opening is increased, whereas if the T_box is below or equal to the T_boxset, the suction modulation valve opening is decreased. At box 102, if the suction modulation valve is closed below a predetermined minimum percentage, then a timer is initiated, and if predetermined time is exceeded, then the system moves to a lower capacity mode, as set forth at box 108. On the other hand, if the suction modulation valve is not closed below the predetermined minimum, then the system moves to box 104 which checks if the suction modulation valve is above a maximum number. Again, if the answer to box 104 is yes for a period of time which exceeds a timer, then the system moves to box 106, wherein the capacity of the compressor is increased. Box 106, and box 104, in response to a no, return to box 100.

After box 108, the control checks if the suction pressure is less than a minimum at box 110. If the answer is no, the system returns to box 100. If the answer is yes, then the system moves to pressure control mode, rather than temperature control mode. As shown in box 112, in pressure control mode the suction modulation valve modulation is based upon an error defined as the suction pressure set point P_sucset, minus the actual suction pressure P_suc. The suction modulation valve is modulated then to ensure that the suction pressure does not drop to an undesirably low value. From box 112, the control moves to box 114, which checks whether the temperature in the container T_box is greater than T_boxset plus a range for error. If the answer is yes, then the system moves out of pressure control and back to box 100. If the answer is no, then the control checks whether the T_box number is less than T_boxset minus a range. If the answer to box 116 is no then, the system returns to box 112. Essentially, the loop of boxes 112, 114, and 116 ensure that the suction pressure does not drop below acceptable value when the system is operating at very low capacity.

If the answer to box 116 is yes, then the system cycles the compressor off at box 118. The control continues to monitor T_box and T_boxset, and as long as the T_box does not exceed the T_boxset plus a range, the compressor is maintained at cycled off at box 118. Once the T_box exceeds the range at box 120, the system returns to box 100. The flowchart as shown in Figure 2 will result in the refrigeration system being maintained at the lowest capacity mode, while allowing for proper operation of other system components.

In addition, the discharge temperature at the compressor outlet is monitored. If there is very low flow of refrigerant to the compressor, it may sometimes occur that the compressor temperature can increase to undesirable levels. If it is determined that the compressor is at an undesirably high temperature, then the suction modulation valve may be opened to increase refrigerant flow and to decrease the compressor temperature. Notably, this function is related to compressor temperature and not the temperature of the container, or T_box. Once the mass flow to the compressor is increased, at some time later it is likely that the container, T_box, will fall below the desired temperature T_boxset. The compressor then cycles off. The control would take this as the equivalent to box 118, and continue operation as shown in flowchart Figure 2 under these conditions.