Refrigeration system having a self adjusting control range

• US 5,392,612 A
• Filed: 06/04/1993
• Issued: 02/28/1995
• Est. Priority Date: 08/08/1984
• Status: Expired due to Term

• Current Assignee: Richard H. Alsenz
• Original Assignee: Richard H. Alsenz
• Inventors: Alsenz, Richard H.
• Primary Examiner(s): Tanner, Harry B.
• Application Number:
  US08/072,525
• Time in Patent Office: 634 Days
• Field of Search: 62/210, 62/211, 62/212, 62/222, 62/223, 62/224, 62/225, 62/204, 62/205, 62/206, 62/115, 62/119
• US Class Current: 62/115
• CPC Class Codes: F25B 2400/075 with parallel compressors
• CPC Class Codes: F25B 2500/15 Hunting, i.e. oscillation of controlled refrigeration variables reaching undesirable values
• CPC Class Codes: F25B 2600/21 Refrigerant outlet evaporator temperature
• CPC Class Codes: F25B 2600/2513 Expansion valves
• CPC Class Codes: F25B 2700/21173 at the outlet
• CPC Class Codes: F25B 2700/21174 of the refrigerant at the inlet of the evaporator
• CPC Class Codes: F25B 2700/21175 of the refrigerant at the outlet of the evaporator
• CPC Class Codes: F25B 41/347 with the valve member being opened and closed cyclically, e.g. with pulse width modulation
• 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 closed loop vapor compression refrigeration system wherein the control range of a control parameter for controlling the flow of the refrigerant through the evaporator coil is automatically adjusted as the operating conditions change is disclosed. A control parameter for controlling the refrigerant flow through the evaporator and a dynamic control range for the control parameter are defined. The control range is made a function of certain system parameters. A nonlinear flow control response function associated with the control parameter is selected. During operation, the control range is automatically adjusted as the values of the selected system parameters change. The flow through a flow control device, such as an expansion valve, coupled to the evaporator, is adjusted according to the flow control response function as the value of the control parameter changes.

Claims

1. A method of operating a refrigeration system having an evaporator for evaporating a liquid refrigerant into a gas refrigerant, said method comprising the steps of:

(a) selecting a control parameter;

(b) establishing a dynamic control region for the control parameter as a function of a system parameter of the refrigeration system;

(c) determining the value of the control parameter; and

(d) increasing the flow of the liquid refrigerant into the evaporator when the value of the control parameter is above the dynamic control region and decreasing the flow when the value of the control parameter is below the dynamic control region.

2. A method of operating a refrigeration system having an evaporator for evaporating a liquid refrigerant into a gas refrigerant, said method comprising the steps of:

(a) defining a control parameter

(b) establishing for the control parameter a control region that is functionally related to a system parameter;

(c) defining a flow control response function for the flow rate of the liquid refrigerant into the evaporator for the values of the control parameter above the control region and a response function for the values of the control parameter below the control region;

(d) determining the value of the control parameter; and

(e) adjusting the flow of the liquid refrigerant into the evaporator when the value of the control parameter is outside the control region according to the flow control response function which corresponds to the value of the control parameter.

3. The method of claim 2, wherein the control parameter is the superheat of the refrigerant leaving the evaporator.

4. The method of claim 2, wherein the evaporator has a return air associated therewith and wherein the control parameter is the superheat of the refrigerant leaving the evaporator and the system parameter is the temperature of the return air.

5. The method of claim 2, wherein the evaporator has a return air associated therewith and wherein the control parameter is the superheat of the refrigerant leaving the evaporator and the system parameter is a function of the temperature difference between the return air temperature and the boiling temperature of the refrigerant in the evaporator.

6. The method of claim 2, wherein the evaporator has a return air associated therewith and wherein the control parameter is the superheat of the refrigerant leaving the evaporator and the control region has an upper limit, U, defined as U=K (Tr-Ti) and a lower limit, L, defined as L=M(Tr-Ti), where Tr is the return air temperature, Ti is the boiling temperature of the refrigerant in the evaporator, K and M are predetermined parameters and K is greater than M.

7. The method of claim 6, wherein K=0.7 and M=0.4.

8. The method of claim 2, wherein the evaporator has a discharge air associated therewith and wherein the control parameter is the superheat of the refrigerant leaving the evaporator and the control region has an upper limit, U, defined as U=A (Td-Ti) and a lower limit, L, defied as L=B(Td-Ti), where Td is the discharge air temperature, Ti is the boiling temperature of the refrigerant in the evaporator, A and B are predetermined parameters and A is greater than B.

9. The method of claim 8, wherein A=0.6 and B=0.4.

10. The method of claim 2, wherein the flow control response function for the values of the control parameter above the control region is a nonlinear function.

11. The method of claim 2, wherein the flow control response function for the values of the control parameter below the control region is a nonlinear function.

12. The method of claim 2, wherein the flow control response functions are nonlinear functions.

13. A method of operating a refrigeration system having an evaporator for evaporating a liquid refrigerant into a gas refrigerant, said method comprising the steps of:

(a) establishing a control parameter;

(b) establishing a plurality of dynamic control regions for the control parameter as a function of a system parameter;

(b) defining a flow control response function for the flow rate of the liquid refrigerant into the evaporator corresponding to each of the control regions in said plurality of control regions;

(c) determining the value of the control parameter; and

(d) adjusting the flow rate of the liquid refrigerant entering the evaporator to the level defined by the control response function which corresponds to the value of the control parameter.