Dry suction industrial ammonia refrigeration system

• US 6,018,958 A
• Filed: 01/20/1998
• Issued: 02/01/2000
• Est. Priority Date: 01/20/1998
• Status: Expired due to Term

• Current Assignee: Fredric J. Lingelbach, John F. Lingelbach
• Original Assignee: Fredric J. Lingelbach, John F. Lingelbach
• Inventors: Lingelbach, John F., Lingelbach, Fredric J.
• Primary Examiner(s): Bennett, Henry
• Assistant Examiner(s): NORMAN, MARC E
• Application Number:
  US09/009,428
• Time in Patent Office: 742 Days
• Field of Search: 62/503, 62/119, 62/222
• US Class Current: 62/222
• CPC Class Codes: F25B 1/00 Compression machines, plants or systems with non-reversible cycle F25B3/00, F25B5/00, F25B6/00, F25B7/00, F25B9/00 take precedence
• CPC Class Codes: F25B 1/10 with multi-stage compression with cascade operation F25B7/00
• CPC Class Codes: F25B 2400/16 Receivers
• CPC Class Codes: F25B 2500/01 Geometry problems, e.g. for reducing size
• CPC Class Codes: F25B 9/002 characterised by the refrigerant

Abstract

A dry suction refrigeration system includes an evaporator fed with liquid refrigerant which discharges a vapor refrigerant to an accumulator. A compressor receives vapor refrigerant from the accumulator and compressies the vapor refrigerant. A condenser receives the compressed vapor refrigerant from the compressor and transforms the refrigerant into liquid refrigerant. A receiver receives the liquid refrigerant from the condenser and supplies it to the evaporator. The evaporator includes an electronic expansion valve operable to continuously monitor the evaporation of liquid refrigerant in the evaporator and to continuously meter the flow of liquid refrigerant, so as to cause a complete vaporization of the liquid refrigerant. Because the liquid refrigerant is completely evaporated, the vapor refrigerant is moved through the system by pressure differential alone.

Claims

1. A dry suction refrigeration system, comprising:

an evaporator fed with liquid refrigerant and discharging a vapor refrigerant;

an accumulator for accumulating vapor refrigerant discharged from the evaporator;

a compressor receiving vapor refrigerant from the accumulator, for compressing the vapor refrigerant;

a condenser receiving compressed vapor refrigerant from the compressor, for condensing it into liquid refrigerant;

a receiver receiving the liquid refrigerant from the condenser and supplying it to the evaporator;

said evaporator including an electronic expansion valve operable to continuously monitor the evaporation of liquid refrigerant in the evaporator and to continuously adjust the flow of liquid refrigerant to the evaporator, to cause complete vaporization of the liquid refrigerant; and

an electronic expansion valve located to monitor vapor refrigerant temperature entering the accumulator and operable to inject liquid refrigerant from the receiver into the vapor refrigerant to selectively lower the temperature thereof.

2. The system of claim 1, wherein vapor refrigerant is moved from the evaporator to the accumulator, compressor and condenser by pressure differential alone.

3. The system of claim 1, further comprising a trap interposed between the condenser and receiver, the trap of a type which allows only liquid to pass therethrough while maintaining a pressure differential across the trap.

4. The system of claim 3, wherein pressure on the upstream side of the trap is regulated by the capacity of the condenser, and wherein pressure on the downstream side of the trap is regulated by the compressor.

5. The system of claim 1, further comprising a second dedicated compressor connected between the receiver and the downstream side of the first compressor, for controlling the pressure within the receiver.

6. The system of claim 5, wherein said second compressor is connected to the receiver for receiving vapor refrigerant within the receiver, and for compressing the vapor refrigerant to control pressure in the receiver.

7. The system of claim 1, wherein liquid refrigerant is moved from the receiver to the evaporators solely by pressure differential between the evaporator and the receiver.

8. The system of claim 1, wherein said refrigerant is ammonia.

9. The system of claim 8, wherein the vapor refrigerant has a pressure of about 25-30 psi from the accumulator to the compressor, wherein the compressed vapor refrigerant has a pressure of about 110-185 psi;

from the compressor to the condenser and wherein the liquid refrigerant has a pressure of about 55-60 psi from the condenser to the receiver and thence to the evaporator.

10. The system of claim 1, wherein said accumulator includes:

a vapor refrigerant tank supported on a liquid refrigerant leg, such that any liquid removed from the fluid flow into the accumulator is stored in the liquid leg below the tank;

said tank having an intake conduit in an upper end thereof extending downwardly into the tank at least half way to the lower end of the tank;

said tank having at least one exhaust port in the upper end thereof, for exhausting accumulated vapor refrigerant.

11. The system of claim 10, wherein said tank intake conduit extends approximately three-fourths of the distance from the upper end of the tank to the lower end of the tank.

12. The system of claim 10, further comprising a liquid transfer tank connected to the accumulator leg and operable to transfer liquid from the leg to the receiver upon the liquid level in the leg reaching a predetermined level.

13. The system of claim 1, further comprising a second, low temperature, low pressure stage for a low temperature evaporation, said evaporator, accumulator, compressor, and receiver being hereinafter identified as the high stage evaporator, accumulator, compressor and receiver, said high stage accumulator including a tank having liquid refrigerant collected in a lower end thereof, and vapor refrigerant accumulated in an upper end thereof, and wherein said second low stage includes:

a low stage receiver for receiving low temperature liquid refrigerant from the lower end of the high stage accumulator tank, said low temperature liquid refrigerant having a lower temperature and pressure than the liquid refrigerant in the high stage, and supplying the low temperature liquid refrigerant to a low temperature evaporator;

said low temperature evaporator evaporating the low temperature liquid refrigerant and discharging a low temperature vapor refrigerant;

a low stage accumulator for accumulating low temperature vapor refrigerant discharged from the low stage evaporator;

a low stage compressor receiving low temperature vapor refrigerant from the low stage accumulator, for compressing the low temperature vapor refrigerant;

said condenser including a second section for receiving compressed low temperature vapor refrigerant and cooling the vapor refrigerant and supplying it to the high stage accumulator;

said low temperature evaporator including an electronic expansion valve operable to continuously monitor the evaporation of low temperature vapor refrigerant and to continuously adjust the flow of the low temperature liquid refrigerant to the low temperature evaporator, to cause complete evaporation of the low temperature liquid refrigerant.

14. The system of claim 10, wherein said tank includes two diametrically opposed exhaust ports in the upper end thereof, for splitting the flow of exhausting accumulated vapor refrigerant.