APPARATUS AND METHOD FOR DETERMINING REFRIGERANT CHARGE LEVEL

• US 20070163276A1
• Filed: 01/18/2007
• Published: 07/19/2007
• Est. Priority Date: 01/18/2006
• Status: Active Grant

• Current Assignee: Purdue Research Foundation (The Trustees of Purdue University (d/b/a Purdue University))
• Original Assignee: Purdue Research Foundation (The Trustees of Purdue University (d/b/a Purdue University))
• Inventors: Braun, James E., Li, Haorong
• Granted Patent: US 7,631,508 B2
• Time in Patent Office: Days
• US Class Current: 62/149
• CPC Class Codes: F25B 2500/19 Calculation of parameters
• CPC Class Codes: F25B 2700/04 Refrigerant level
• CPC Class Codes: F25B 2700/21151 at the suction side of the compressor
• CPC Class Codes: F25B 2700/2116 of a condenser
• CPC Class Codes: F25B 2700/21163 of the refrigerant at the outlet of the condenser
• CPC Class Codes: F25B 2700/2117 of an evaporator
• CPC Class Codes: F25B 49/005 of safety devices F25B49/02 and F25B49/04 take precedence
• CPC Class Codes: F25D 2500/04 Calculation of parameters

Abstract

A method and apparatus for non-invasively determining a charge level of a refrigerant in a vapor-compression cycle system. The method and apparatus monitor the system while the system is operated to ascertain that the system is operating at approximately steady-state. The superheat and the subcooling of the system are then determined at the suction line and at the liquid line, respectively, and the refrigerant charge level is calculated based on the determined subcooling, the determined superheat, and rated operating conditions of the system, including rated refrigerant charge level, rated liquid line subcooling, and rated suction line superheat.

Claims

1. A method of non-invasively determining a charge level (m_total) of a refrigerant in a vapor-compression cycle system comprising a compressor, a condenser, an expansion device, an evaporator, a discharge line fluidically connecting the compressor to the condenser, a liquid line fluidically connecting the condenser to the expansion device, a distribution line fluidically connecting the expansion device to the evaporator, and a suction line fluidically connecting the evaporator to the compressor, the method comprising:

monitoring the system while operating the system to ascertain that the system is operating at approximately steady-state;

determining the superheat (T_sh) and the subcooling (T_sc) of the system at the suction line and at the liquid line, respectively; and

calculating the refrigerant charge level (m_total) based on the determined subcooling (T_sc) the determined superheat (T_sh), and rated operating conditions of the system including rated refrigerant charge level (m_total,rated), rated liquid line subcooling (T_sc,rated) and rated suction line superheat (T_sh,rated).

2. The method according to claim 1, wherein T_sc is determined by calculating the difference between the temperature of the refrigerant in the liquid line and the temperature of the refrigerant in the condenser, and T_sh is determined by calculating the difference between the temperature of the refrigerant in the suction line and the temperature of the refrigerant in the evaporator.

3. The method according to claim 1, wherein the refrigerant charge level (m_total) is calculated based solely on the determined subcooling (T_sc) the determined superheat (T_sh), the rated refrigerant charge level (m_total,rated), the rated liquid line subcooling (T_sc,rated) and the rated suction line superheat (T_sh,rated).

4. The method according to claim 1, wherein the refrigerant charge level (m_total) is calculated with the equation

(m_total−

m_total,rated)/m_total,rated=(1/k_ch){(T_sc−

T_sc,rated)−

k_sh/sc(T_sh−

T_sh,rated)}

wherein k_ch is an empirical constant and k_sh/sc is the slope of a straight line plot of (T_sc−

T_sc,rated) versus (T_sh−

T_sh,rated) for the rated refrigerant charge for the system.

5. The method according to claim 4, wherein T_sc is determined by calculating the difference between the temperature of the refrigerant in the liquid line and the temperature of the refrigerant in the condenser, and T_sh is determined by calculating the difference between the temperature of the refrigerant in the suction line and the temperature of the refrigerant in the evaporator.

6. The method according to claim 4, wherein k_ch is calculated with the equation

T_sc,rated/(1−

α

_hs,o,rated)X_high,rated)

wherein α

_hs,o,rated is the fraction of the rated refrigerant charge level (m_total,rated) under which the refrigerant is saturated liquid at an exit of the liquid line under the rated operating conditions, and X_high,rated is the ratio of rated refrigerant charge level at a high side of the system over the rated refrigerant charge level (m_total,rated) of the system.

7. The method according to claim 4, wherein k_ch is about 50°

C.

8. The method according to claim 4, wherein k_sh/sc is between about ¼

to about ½

.

9. The method according to claim 4, wherein k_sh/sc is about 1/2.5.

10. The method according to claim 1, wherein the determining and calculating steps are performed without training the system to develop a model correlating the subcooling and superheat of the system to refrigerant pressures in the system, and without empirical data regression.

11. An apparatus for non-invasively determining a charge level (m_total) of a refrigerant in a vapor-compression cycle system comprising a compressor, a condenser, an expansion device, an evaporator, a discharge line fluidically connecting the compressor to the condenser, a liquid line fluidically connecting the condenser to the expansion device, a distribution line fluidically connecting the expansion device to the evaporator, and a suction line fluidically connecting the evaporator to the compressor, the apparatus comprising:

means for monitoring the system while operating the system to ascertain that the system is operating at approximately steady-state;

means for determining the superheat (T_sh) and the subcooling (T_sc) of the system at the suction line and at the liquid line, respectively; and

means for calculating the refrigerant charge level (m_total) based on the determined subcooling (T_sc) the determined superheat (T_sh), and rated operating conditions of the system including rated refrigerant charge level (m_total,rated) rated liquid line subcooling (T_sc,rated) and rated suction line superheat (T_sh,rated).

12. The apparatus according to claim 11, wherein the determining means determines T_sc by calculating the difference between the temperature of the refrigerant in the liquid line and the temperature of the refrigerant in the condenser, and determines T_sh by calculating the difference between the temperature of the refrigerant in the suction line and the temperature of the refrigerant in the evaporator.

13. The apparatus according to claim 11, wherein the calculating means calculates the refrigerant charge level (m_total) based solely on the determined subcooling (T_sc) the determined superheat (T_sh) the rated refrigerant charge level (m_total rated), the rated liquid line subcooling (T_sc,rated) and the rated suction line superheat (T_sh,rated).

14. The apparatus according to claim 11, wherein the calculating means calculates the refrigerant charge level (m_total) with the equation

(m_total−

m_total,rated)/m_total,rated=(1/k_ch){(T_sc−

T_sc,rated)−

k_sh/sc(T_sh−

T_sh,rated)}

wherein k_ch is an empirical constant and k_sh/sc is the slope of a straight line plot of (T_sc−

T_sc,rated) versus (T_sh−

T_sh,rated) for the rated refrigerant charge for the system.

15. The apparatus according to claim 14, wherein the determining means determines T_sc by calculating the difference between the temperature of the refrigerant in the liquid line and the temperature of the refrigerant in the condenser, and determines T_sh by calculating the difference between the temperature of the refrigerant in the suction line and the temperature of the refrigerant in the evaporator.

16. The apparatus according to claim 14, wherein the calculating means calculates k_ch with the equation

T_sc,rated/(1−

α

_hs,o,rated)X_high,rated)

wherein α

_hs,o,rated is the fraction of the rated refrigerant charge level (m_total,rated) under which the refrigerant is saturated liquid at an exit of the liquid line under the rated operating conditions, and X_high,rated is the ratio of rated refrigerant charge level at a high side of the system over the rated refrigerant charge level (m_total,rated) of the system.

17. The apparatus according to claim 14, wherein k_ch is about 50°

C.

18. The apparatus according to claim 14, wherein k_sh/sc is between about ¼

to about ½

.

19. The apparatus according to claim 14, wherein k_sh/sc is about 1/2.5.

20. The apparatus according to claim 11, wherein the determining means and calculating means operate without training the system to develop a model correlating the subcooling and superheat of the system to refrigerant pressures in the system, and without empirical data regression.