Method and apparatus for staged startup of air-cooled low charged packaged ammonia refrigeration system

Abstract

An apparatus for staged startup of air-cooled low charged packaged ammonia refrigeration system includes motorized valves on condenser coil inlets, a main compressor discharge motorized valve, a bypass pressure regulator valve in the main compressor piping, and check valves on the condenser outlets. The condenser inlet motorized valves provide precise control of gas feed to the condensers, so pressure can build without collapsing oil pressure. The condenser outlet contains check valves to prevent liquid backflow during coil isolation. The compressor discharge line contains a motorized valve for regulating discharge pressure at start-up. The motorized valve in the compressor discharge piping includes a bypass with a pressure regulator for precise regulation at minimum discharge pressure. Once discharge pressure rises above the setpoint, the condenser inlet solenoid coils open one at a time. The discharge pressure regulating motorized valve simultaneously regulates the discharge pressure until the condenser maintains discharge pressure.

Claims

1. A method for start-up of an air-cooled ammonia refrigeration system having an evaporator, liquid/vapor separator, a compressor, an air-cooled condenser having a plurality of condenser coils, and a collection vessel without the need for a stand-alone oil pump to maintain oil pressure during start-up, said method comprising: starting refrigerant flow through said condenser coils one at a time; waiting to start refrigerant flow through each subsequent condenser coil until each prior started condenser coil is running at constant discharge and oil pressure; using a motorized valve in a discharge line from said compressor for control of gas flow out of said compressor; using a bypass pressure regulator valve in said discharge line from said compressor for additional control of gas flow out of said compressor; using motorized valves at an inlet of at least one condenser coil in said air-cooled condenser to control gas feed to said condenser coil; using check valves at an outlet of at least one condenser coil to prevent liquid backflow during coil isolation; monitoring gas pressure in said discharge line from said compressor and controlling the opening of said motorized valves based on said monitored gas pressure using a microcontroller or programmable logic controller.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 is a schematic of a refrigeration system according to a single compressor embodiment of the invention.

(2) FIG. 2 is a blow-up of the upper right hand portion of FIG. 1.

(3) FIG. 3 is a schematic of a refrigeration system according to a dual compressor embodiment of the invention.

(4) FIG. 4 is a blow-up of the upper right hand portion of FIG. 3.

DETAILED DESCRIPTION

(5) FIG. 1 is a process and instrumentation diagram for a single compressor, air-cooled (non-evaporative) condenser, low charge packaged penthouse refrigeration system according to an embodiment of the invention. A blow-up of the upper right quadrant of FIG. 1 is presented in FIG. 2. FIG. 3 is a process and instrumentation diagram for a dual compressor, air-cooled condenser, low charge packaged penthouse refrigeration system according to an embodiment of the invention. A blow-up of the upper right quadrant of FIG. 3 is presented in FIG. 4.

(6) The system includes evaporators 2a and 2b, including evaporator coils 4a and 4b, respectively, condenser 8, compressor(s) 10, expansion devices 11a and 11b (which may be provided in the form of valves, metering orifices or other expansion devices), pump 16, liquid-vapor separation device 12, and economizer 14. According to one embodiment, liquid-vapor separation device 12 may be a recirculator vessel. According to other embodiments, liquid-vapor separation device 12 and economizer 14 may one or both provided in the form of single or dual phase cyclonic separators. The foregoing elements may be connected using standard refrigerant tubing in the manner shown in FIGS. 1-4. As used herein, the term “connected to” or “connected via” means connected directly or indirectly, unless otherwise stated.

(7) According to the embodiment shown in FIGS. 1-4, low pressure liquid refrigerant (“LPL”) is supplied to the evaporator by pump 16 via expansion devices 11. The refrigerant accepts heat from the refrigerated space, leaves the evaporator as low pressure vapor (“LPV”) and liquid and is delivered to the liquid-vapor separation device 12 (which may optionally be a cyclonic separator) which separates the liquid from the vapor. Liquid refrigerant (“LPL”) is returned to the pump 16, and the vapor (“LPV”) is delivered to the compressor 10 which condenses the vapor and sends high pressure vapor (“HPV”) to the condenser 8 which compresses it to high pressure liquid (“HPL”). The HPL is delivered to the economizer 14 which improves system efficiency by reducing the high pressure liquid (“HPL”) to intermediate pressure liquid (“IPL”) then delivers it to the liquid-vapor separation device 12, which supplies the pump 16 with low pressure liquid refrigerant (“LPL”), completing the refrigerant cycle.

(8) FIGS. 1-4 also include numerous control, isolation, and safety valves, as well as temperature and pressure sensors (a.k.a. indicators or gages) for monitoring and control of the system.

Single Compressor Penthouse Improved Startup Configuration and Method

(9) Referring to the single compressor embodiment (FIGS. 1 and 2, and particularly FIG. 2), motorized condenser inlet 101, 102 and 103 valves are installed on the inlet of the condenser coil bundles. The motorized valves can function as variable control valves or on/off valves.

(10) A single condenser bundle is open to ensure proper surface is available during start-up. As the system begins increasing load, valves 101, 102 and 103 will begin to open. Once all valves are open, variable fan control takes over pressure control. The sequencing of the use of valves and fan operation can vary, based on system operation and design.

(11) Motorized valve 104 and ammonia pressure regulator valve 105 provide precise ammonia gas control during start-up of the system in low ambient conditions. During start-up, all motorized valves are closed and the pressure regulator provides compressor differential pressure control to ensure proper oil flow. The ammonia pressure regulator 105 provides low volume flow control. As the compressor begins to load, more ammonia gas flow is generated. Motorized valve 104 begins to open and control the discharge pressure, compressor differential pressure and oil flow.

(12) The next step during system start-up is to begin opening the condenser motorized valves 101, 102 and 103 and concomitant staging the startup of the condenser fans.

(13) Check valves 106, 107, 108 and 109 installed at the outlet to the condenser bundles are utilized to ensure liquid ammonia does not backflow into the condenser or other coil bundles during periods of downtime or normal operating periods.

(14) Each of valves 101, 102, 103 and 105 are activated by attached microcontrollers or PLC (programmable logic control). A central microcontroller or PLC monitors the status of each valve, as well as discharge pressure, and directs the action of the valves accordingly for sequential startup of the condenser coils while maintaining gas and oil pressure.

(15) Not all valves are required for a every ambient condition. In fact, above a certain ambient temperature, low ambient control may not be required. Therefore, valves can be installed and arranged to optimize operation at startup based on the ambient temperature.

Dual Compressor Penthouse Improved Startup Configuration and Method

(16) (Isolated Compressor Operation)

(17) FIGS. 3 and 4 show a process and instrumentation diagram for a dual compressor, air-cooled condenser, low charge packaged penthouse refrigeration system. The dual compressor design utilizes and isolated compressor concept. The compressors use different oil separators, oil coolers, and condenser bundles.

(18) Motorized valves 110, 111, 112 and 113 are installed on the inlet of the condenser coil bundles. The motorized valves can function as variable control valves or on/off valves.

(19) During startup, motorized valves 111 and 112 will be opened to a minimum position to allow ammonia gas flow to the condenser coil. As the system begins increasing load, valves 111 and 112 will open to 100% and valves 113 and 110 will begin opening. Once all valves are open, variable fan control takes over pressure control. The sequencing of the use of valves and fan operation can vary, based on system operation and design.

(20) Fine ammonia gas control during start-up of the system is provided by:

Compressor #1

(21) a. Valve #114 Motorized valve

(22) b. Valve #115 Pressure regulator

(23) c. Start-up requires all motorized valves are closed and the pressure regulator provides compressor differential pressure to ensure proper oil flow. During start-up, all motorized valves are closed and the pressure regulator provides compressor differential pressure control to ensure proper oil flow. The ammonia pressure regulator provides low volume flow control. As the compressor begins to load, more ammonia gas flow is generated. Motorized valve #114 begins to open and control the discharge pressure, compressor differential pressure and oil flow.

Compressor #2

(24) a. Valve #116 Motorized valve

(25) b. Valve #117 Pressure regulator

(26) c. Start-up requires all motorized valves are closed and the pressure regulator provides compressor differential pressure to ensure proper oil flow. During start-up, all motorized valves are closed and the pressure regulator provides compressor differential pressure control to ensure proper oil flow. The ammonia pressure regulator provides low volume flow control. As the compressor begins to load, more ammonia gas flow is generated. Motorized valve #116 begins to open and control the discharge pressure, compressor differential pressure and oil flow.

(27) The next stage is to begin opening the condenser motorized valves (110, 111, 112 and 113) and staging the condenser fans accordingly.

(28) Check valves (118, 119, 120 and 121) are utilized to ensure liquid ammonia does not backflow into the condenser or other coil bundles during periods of downtime or normal operating periods.

(29) As with the single compressor embodiment, each of valves 110-117 is activated by attached microcontrollers or PLC. A central microcontroller or PLC monitors the status of each valve, as well as discharge pressure, and directs the action of the valves accordingly for sequential startup of the condenser coils while maintaining gas and oil pressure. Not all valves are required for every ambient condition. In fact, above a certain ambient temperature, low ambient control may not be required. Therefore, valves can be installed and arranged to optimize operation at startup based on the ambient temperature.

(30) According to various embodiments, the evaporator is housed in the evaporator (penthouse) module, and the remaining components of the system shown in FIGS. 1-4 (except for the condenser coils and fans and associated structures) are housed in an enclosure such as a machine room module. The condenser coils and fans may be mounted on top of the enclosure or machine room module for a complete self-contained rooftop system. The air-cooled condenser may optionally be fitted with an adiabatic air pre-cooling system. The entire system may be completely self-contained in two roof-top modules making it very easy for over-the-road transport to the install site, using e.g., flat bed permit load non-escort vehicles. The penthouse and machine room modules can be separated for shipping and/or for final placement, but according to most preferred embodiments, the penthouse and machine room modules are mounted adjacent to one-another to maximize the reduction in refrigerant charge. According to a most preferred embodiment, the penthouse module and the machine room module are integrated into a single module, although the evaporator space is separated and insulated from the machine room space to comply with industry codes. According to an alternative embodiment, the evaporator coil may be mounted in a refrigerated space adjacent to, below, or remote from, the machine room module.

(31) The combination of features as described herein provides a very low charge refrigeration system compared to the prior art. Specifically, the present invention is configured to require less than six pounds of ammonia per ton of refrigeration capacity. According to a preferred embodiment, the present invention can require less than four pounds of ammonia per ton of refrigeration. And according to most preferred embodiments, the present invention can operate efficiently with less than two pounds per ton of refrigeration capacity.

(32) While the present invention has been described primarily in the context of refrigeration systems in which ammonia is the refrigerant, it is contemplated that this invention will have equal application for refrigeration systems using other natural refrigerants, including carbon dioxide.

(33) The description of the invention is merely exemplary in nature and, thus, variations that do not depart from the concept of a packaged (one-or two-module integrated and compact system) low refrigerant charge (i.e., less than 10 lbs of refrigerant per ton of refrigeration capacity) refrigeration system are intended to be within the scope of the invention. Any variations from the specific embodiments described herein but which otherwise constitute a packaged, pumped liquid, recirculating refrigeration system with charges of 10 lbs or less of refrigerant per ton of refrigeration capacity should not be regarded as a departure from the spirit and scope of the invention set forth in the following claims.