Abstract:
A temperature-controlled beverage dispenser is disclosed, which provides a cold plate having disposed therein beverage lines and refrigerant lines. The refrigerant lines may be connected to a cooling system, such as a heat exchanger, which is configured to remove heat from the cold plate. The beverage lines may be connected to a beverage supply for dispensing a desired beverage. Valves and a pressure sensor in the refrigerant line are connected to a microprocessor. At regular intervals, the microprocessor closes the valves, waits a short time, and then takes a pressure reading, which corresponds to a temperature. If the temperature falls below a desired value, then the cooling system is shut off. This permits the microprocessor to closely control the temperature of the beverage being dispensed.

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
       [0001]    This application claims priority to U.S. provisional application 61/312,089 entitled “Microprocessor-Controlled Multi-Mode Beverage Dispenser,” filed Mar. 9, 2010, which is incorporated herein by reference. 
     
    
     BACKGROUND 
       [0002]    The device disclosed is related generally to beverage dispensing systems employing a cooling subsystem, more particularly, a self-contained tabletop beverage dispenser incorporating a refrigerant chilled cold plate for cooling a beverage. 
         [0003]    When beer (or other beverage) is charged with a gas, such as a carbon dioxide, to move the beer through the various lines, the gas is entrained to dissolve in the fluid and resides in a stable state for temperatures at or below about 30° F. The gas typically does not bubble out of the fluid, but is carried in the fluid and gives a beverage a distinctive effervescence when consumed. However, as the temperature of the beer rises above 30° F., absent increase in pressure on the system, the gas becomes increasingly unstable and begins to bubble or foam out of the flowing beer. Further warming of the beer increases the foaming effect, as the gas bubbles form and propagate downstream. Foaming is further exacerbated by disturbances in the beer, such as the turbulence generated when the beer is dispensed from the dispensing valve. When beer is warmed to 45° F. or more, such as when exposed to normal ambient room temperature, the gas becomes sufficiently unstable and so much foam is generated when it is dispensed that it often cannot be served to patrons. As a result, as waste increases, and profits decrease. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0004]      FIG. 1  is a perspective view of the tabletop unit showing the housing, the beverage outlets, and the spill tray. 
           [0005]      FIG. 2  is an equipment layout, not to scale, showing the relative positions of the elements of Applicants&#39; novel beer cooling system. 
           [0006]      FIG. 2A  is a block diagram illustrating the microprocessor inputs and outputs. 
           [0007]      FIGS. 3 and 4  are perspective views of the equipment layout showing the elements of the cooling system in place with the housing cover removed therefrom. 
           [0008]      FIG. 5  is an elevational view of the beverage or beer lines and refrigeration lines within the cold plate. 
           [0009]      FIG. 6  is a perspective view of a layout for use with Applicants&#39; novel beverage cooling system which shows a tabletop supporting the unit, which tabletop in turn is supported by legs or a cart or the like; the product here, two different beverages, are provided in feed lines to the rear of the housing of the unit. 
           [0010]      FIG. 7  is a perspective view of the cold plate showing refrigeration lines and beer lines laying adjacent one another and embedded within an aluminum casting. 
           [0011]      FIG. 8  is a flow chart illustrating the standby mode. 
           [0012]      FIG. 9  is a flow chart illustrating the compressor mode. 
           [0013]      FIG. 10  is a flow chart illustrating the pump down mode. 
       
    
    
     SUMMARY OF THE INVENTION 
       [0014]    The present invention is directed to a beverage dispensing system for dispensing chilled beverages, the system comprising a housing with one or more beverage inlet connections extending from said housing and one or more beverage dispenser valves extending from said housing. A beverage cooling system is positioned within said housing, said cooling system comprising a reservoir capable of receiving a supply of refrigerant, a cold plate in fluid communication with said refrigerant reservoir, wherein the refrigerant lines extend through said cold plate, wherein beverage lines also extend through said cold plate adjacent to said refrigerant lines. 
         [0015]    The cooling system further includes an accumulator, a compressor, a refrigerant condenser, and a thermal expansion valve positioned between said refrigerant reservoir and said cold plate to adjust the flow of refrigerant depending upon the temperature of the cold plate. 
         [0016]    If freeze-up of the beverage in the beverage lines occurs, refrigerant may be controlled by means of a hot gas valve to divert the flow of refrigerant from the cold plate, adding hot gas from the high side of the compressor to the cold plate refrigerant inlet line. 
         [0017]    A beer or beverage evaporator valve, typically a solenoid, is provided upstream of the accumulator and downstream of the cold plate. A liquid line valve is provided typically downstream of the condenser and upstream of the reservoir, also solenoid controlled. A thermal expansion valve is provided downstream of the reservoir upstream of and close to the refrigerant inlet of the cold plate, for metering refrigerant into the cold plate in response to a thermal bulb at the outlet of the refrigerant lines on the cold plate. 
         [0018]    Electronic sensors, such as transducers (including thermal or pressure sensors), may be provided in conjunction with a microprocessor to control the operation of the system. In one embodiment, a temperature sensor (such as a thermistor) or pressure transducer is located upstream of the evaporator valve and a pressure transducer is located near the suction or low side of the compressor. When the system is energized, that is, in a “run” or “on” mode, the microprocessor will control the compressor. The microprocessor, responsive to the evaporator (cold plate) condition, will initiate a system shutoff when a predetermined psi, for example approximately 55 psi, is reached. The first step of the system shutoff will be to de-energize the normally closed beer evaporator and liquid line valves (thus closing them), thus “trapping” the refrigerant between the valves and in the evaporator and begin monitoring of the sensor at the low end of the compressor or suction side, continuing the compressor running until a predetermined pressure, for example about 10-35 psi, is sensed (thereby assuring the accumulator is void of liquid). At a compressor low end of 10-35 psi, the compressor de-energizes and the system will wait again for a signal from the transducer just downstream from the evaporator. When this transducer hits 70 psi or the associated temperature, the microprocessor will initiate an “on” command to the compressor will be turned on and the solenoids will be energized and opened. 
         [0019]    Restated, the microprocessor, in response to a high set point (cold plate too warm) from the first transducer (just upstream of the beer evaporator valve and downstream of the cold plate), will energize the compressor and open the liquid line valve and the evaporator valve, and responsive to an intermediate set point (cold plate low temperature) from the first transducer will close the liquid line valve and evaporator valve, but keep the compressor going, and in response to a low set point from the second transducer (accumulator dry), de-energizes the compressor and goes back to begin the cycle, monitoring the first transducer for the high set point. 
         [0020]    There are three modes of operation of the microprocessor/controller (“microprocessor”). The microprocessor has inputs from the first transducer TS 1  and the second transducer PT 1 . The function of the microprocessor is to keep the cold plate temperature between acceptable highs and acceptable lows, or in what may be referred to as a preferred temperature range. This may be found in Table 1, wherein nine such ranges (and a test mode) are providing for setting the microprocessor. For example, certain of these ranges may be more appropriate for beer and others may be more appropriate for soda and still other ranges of the nine set forth in Table 1 may be appropriate for water. Note that the TS 1  range, which correlates to temperature range of the cold plate (evaporator), is a spread of about 2.5 psi between ON and OFF for the compressor setting. 
         [0021]    A second function of the microprocessor program and control is to, upon compressor shutdown, draw down the low side to avoid liquid accumulation in the accumulator and slugging of the compressor when the compressor restarts, as set forth above. 
         [0022]    A third function of the microprocessor controller program is to avoid excessive cycling of the compressor between the on-off mode. This is achieved by an adjusted reading (vaves closed) of the cold plate and maintaining the system in either standby, a compressor mode or pump down mode. 
       DETAILED DESCRIPTION OF THE EMBODIMENTS 
       [0023]    self-contained beverage dispenser  10  of the present invention is shown in  FIG. 1 . Although the subject invention will be described in the context of the beverage to be dispensing being beer, it is to be understood the invention is not limited to the dispensing of beer. Beverage dispensing valves  10   a  and  10   b  stand out the front end of housing  14 . The beverage dispensing outlets may be beer taps or other such dispensers as those known in the art. A beverage spill tray  16  is positioned beneath the outlets  10   a  and  10   b.  Beverage dispenser  1  may be mounted on a countertop, rolling cart or other support surface. The beverage dispenser  1  may be easily installed at a desired location. One need simply to run the product lines from the beverage supply, for example, a beer keg, to the location for connection to the beverage dispensing unit. 
         [0024]    The refrigerant cooling system  20  of the subject invention is shown in  FIG. 2 . The cooling system  20  includes reservoir  22  which acts as the reservoir for the refrigerant, which is in fluid communication with cold plate  24  via refrigerant line  25 . Refrigerant cooling lines acting as an evaporator, extend through cold plate  24  to cool corresponding beverage lines which also extend through cold plate  24 . The cold plate utilized, including, for example, 40 pounds of cast aluminum, is a standard cold plate known to those skilled in the art wherein the beverage and refrigerant lines may be wound or located within the cold plate to increase the length of the lines positioned within said cold plate. The cooling system  20  also includes accumulator  26 , compressor  28  and refrigerant condenser  30 . As shown, refrigerant exits the cold plate  24  and flows to accumulator  26  via refrigerant line  27 . From the accumulator  26 , the refrigerant travels to the compressor  28  via refrigerant line  29 . The refrigerant flows from the compressor  28  to the condenser  30  via refrigerant line  31 . 
         [0025]    The operation of the refrigerant system is described below, in connection with  FIGS. 2 and 3 . 
         [0026]    The refrigerant, which in a preferred embodiment is type 404a, enters the compressor  28  at point A as a low pressure gas and is discharged from the compressor as a high pressure gas at point B. It then enters the top of the condenser  30  at point C. 
         [0027]    The refrigerant is cooled in the condenser, exiting it as a high pressure liquid, and passes through a drier  32  (which retains unwanted scale, dirt and moisture) to the liquid line valve  34 , which is open whenever the cold plate  24  is warm enough to require cooling, as determined by a pressure switch Transducer TS  1  (pressure transducer or thermistor, for example). 
         [0028]    The refrigerant, still in a high pressure liquid state, flows through the liquid line valve  34  and enters the reservoir tank  22 , which serves as a storage or surge tank for the refrigerant at point D. 
         [0029]    At point E, the refrigerant exits the reservoir tank, passes through a sight glass  36  (where bubbles will be observed if the system is low on refrigerant) and encounters the thermal expansion valve TXV  38 . 
         [0030]    A pressure differential is provided across the thermal expansion valve. This valve includes a sensor bulb that measures the degree (or lack) of superheat of the suction gas exiting the cold plate and expands or contracts to allow the flow of refrigerant to be varied according to need. The refrigerant leaving the thermal expansion valve will be in a low pressure liquid or liquid/vapor state when it enters the cold plate. 
         [0031]    At the thermal expansion valve  38  there may also be a small equalizer tube  39  connected to the outlet cold plate  24 . The equalizer tube  38  helps to equalize the pressure between the inlet and outlet side of the cold plate  24 . 
         [0032]    After passing through the thermal expansion valve  38 , the refrigerant enters the cold plate  24  at point G. As the liquid or liquid/vapor refrigerant enters the cold plate it is subjected to a much lower pressure due to the suction created by the compressor and the pressure drop across the expansion valve. It will also be adjacent warmer beer lines. Thus, the refrigerant tends to expand and evaporate. In doing so, the liquid refrigerant absorbs energy (heat) from beverage lines within the cold plate  24 . 
         [0033]    The low pressure gas leaving the cold plate  24  encounters the evaporator valve  40 , whose function is to trap refrigerant in the cold plate during system shutdown cycle. From the evaporator valve  40 , the gas passes into accumulator  26 , which help prevent any slugs of liquid refrigerant from passing directly into the compressor, and continues back to the compressor  28 . The thermal expansion valve  38  mentioned above is used instead of a capillary tube in order to provide improved response to the cooling needs of the cold plate  24 . 
         [0034]    The microprocessor controlled electrical control system  50  is illustrated in  FIGS. 2 and 2A . Refrigeration on/off switch SW 1  provides power to the entire system by manually depressing the switch. Pressure transducer PT 1  monitors the refrigerant pressure in the compressor low side and cycles off the compressor and condenser fan (not shown) when the pressure drops to a predetermined level, 15 psi in a preferred embodiment, and cycles the compressor and fan back on when the temperature sensor or pressure transducer TS  1  reaches a second predetermined level, 75 psi in a preferred embodiment. TS  1  monitors refrigerant temperature (or pressure) just downstream of the beverage cold plate. When the pressure drops to a predetermined level, approximately 55 psi in a preferred embodiment, TS  1  through control system  50  cycles off the beverage evaporator coil or cold plate by shutting liquid line solenoid coil  34  and evaporator valve  40 . The microprocessor then reads the transducer PT 1  until drawdown to a lower pressure than 55 psi is reached, here for example, 10-35 psi, where the compressor is cycled off by the microprocessor/controller. The monitor then looks to TS  1 . With the compressor off, the cold plate starts to warm. When the refrigerant pressure at TS  1  rises to a second predetermined level, approximately 72-75 psi in a preferred embodiment, the TS  1  through microprocessor/control system  50  turns on the compressor and opens evaporator solenoid coil  40  and liquid line solenoid  34  A push-button defrost switch  42  is provided to cycle on the hot gas solenoid and cycle off the condenser fan to deliver hot gas to the cold plate should the product in the cold plate become frozen. 
         [0035]    Sensor/transducer TS  1  responds to the cold plate  24  temperature by reading the pressure or temperature of the refrigerant as it is discharged from the cold plate. When the cold plate becomes warm enough, the liquid line valve  34  and the evaporator valve  40  open, thereby allowing refrigerant to flow throughout the system. When the cold plate becomes cool enough these valves  34 / 40  will close, trapping most refrigerant in the system but with the electronic control a] lowing refrigerant to pump from the accumulator into the compressor down until PT 1  reads about 15 psi (typically between 10-35 psi). 
         [0036]    As shown in  FIG. 2 , defrost valve  42  is installed between the compressor discharge tube and the cold plate inlet. A manually operated momentary switch  44  may be deployed to trigger the defrost cycle. This signals the microprocessor to open the defrost valve  42  for a preset defrost cycle time, normally 30 seconds, and allows high pressure gas from the compressor to be pumped into the cold plate to thaw it, should it freeze up or get too cold. To prevent damaging the system, the switch should not be held longer than necessary. 
         [0037]    The TXV  38  controls and meters the amount of refrigerant that flows into the evaporator based on the temperature with a sensing bulb  41  that is typically located on the suction line where it leaves the evaporator coil. The temperature differential of the evaporator inlet and outlet typically determines the opening and closing of the TXV  38  valve seat to either add refrigerant or constrict refrigerant flow to the evaporator. Other devices known in the art may control pressure of refrigerant into the evaporator. 
         [0038]    An electronic microprocessor/controller  50  operates the compressor, condenser fan, and solenoids  34 / 40 . The microprocessor controller engages a power off switch, a defrost switch  42 , temperature sensor (from evaporator thermal sensor, a temperature sensor or pressure transducer) TS  1 , and an overheat temperature sensor  51  (from high side of condenser), as well as a pressure/transducer PT 1  just upstream of the low end of the compressor. 
         [0039]    Outputs (110 volt AC) include normally closed solenoids (2)  34 / 40 , the compressor (typically about one-third horsepower) and the condenser fan (typically about 14 watt). Defrost solenoid  42  and a power on and defrost cycle LED include controller outputs. 
         [0040]    In the on/run mode (when the power switch is activated), the compressor, condenser fan, and solenoid pair  34 / 40  are activated. Compressor pumps refrigerant and the temperature of the cold plate will drop as the refrigerant goes through the cold plate. The “power on” LED is on. The monitor is looking at TS  1  looking for the solenoid valves shutoff condition, the intermediate set point here, for example, about 55 psi. 
         [0041]    “Stop” mode occurs when the intermediate set point evaporator temperature  sensor TS  1  is reached, for example, approximately 29° F. (68.0 psi with Suva® 404A). The solenoids  34 / 40  are closed trapping liquid refrigerant in the cold plate and reservoir. The condenser fan and compressor continue to run until the pressure/vacuum transducer PT 1  set point is reached. This is about 15 psi. This action assures that there is little or no liquid refrigerant left in the accumulator. At this point, the fan and the compressor turn off and wait for a microprocessor signal from the evaporator temperature sensor TS  1 . “Power on” LED remains energized. 
         [0042]    When temperature of the evaporator at TS  1  increases to an upper limit, typically about 33° F. (74.0 psi with 404A or other suitable refrigerant), the “on” mode is automatically activated by the controller and cycles the compressor on and the solenoids open. 
         [0043]    This illustrates the controller in its normal operating mode. However, if the temperature of the high side thermal sensor  51  exceeds a set point (overheat), the system shuts down the compressor, fan, and solenoids and alternately flashes the LED indicators. This is a warning that the system has overheated. 
         [0044]    If the system freezes up or gets too cold, the momentary “defrost” switch is activated. The defrost solenoid is activated and the defrost LED flashes for a defrost cycle. The cycle is timed to last about 15-20 seconds, after which the LED turns off and the dispenser returns to the normal on/run cycle. 
         [0045]    One of the purposes of the electronic controller  50  is to maintain the compressor in an off position until the temperature of the evaporator reaches an upper limit, typically about 33° F., and the on mode is activated again. Thus, if there is any liquid refrigerant in the accumulator and it evaporates, as the system warms up or pressure increases, the pressure switch at the low end of the compressor will not cycle the compressor on. That is to say, the microprocessor controller  50  will provide for compressor run/on when solenoids  34 / 40  are de-energized and closed, but only until PT 1  reads about 15 psi or between about 10-35 psi, (thereby ensuring evaporation of any liquid refrigerant in accumulator  26 ). 
         [0046]      FIGS. 3 and 4  illustrate an equipment layout for the embodiment of Applicants&#39; device as set forth in  FIGS. 1 and 2 . It is seen with respect to  FIGS. 3 and 4 , that the cold plate  24  is set vertically with respect to a base  25  of the cooling system  20 . Furthermore, it can be seen 
         [0047]    that the condenser  30  is also set vertically and spaced apart from the cold plate  24 . A substantial number of the elements are set between the vertically oriented cold plate and condenser, including the compressor, drier, solenoids, sight glass, liquid line valve, thermal control valve, evaporator valve, reservoir tank, and accumulator. Moreover, the fan for the condenser is mounted inside the unit exhausting air through vents in the rear view of the unit (see  FIG. 4 ). 
         [0048]      FIGS. 5 and 7  illustrate an embodiment of an arrangement of refrigeration lines and beer lines that may be used in the cold plate. It is seen with respect to  FIG. 5  that refrigeration lines lay in a plane, as do the beverage lines. Adjacent to each beer line plane lays a refrigeration time plane for uniform heat transfer. 
         [0049]      FIG. 6  illustrates a manner in which Applicants&#39; novel cooling system  20  may be set up on a support surface or a table top TT, wherein the product (beverage) being supplied to the system, here from two kegs or other containers of liquid product, may enter the system from the rear. In an alternate preferred embodiment, the lines from the product to the cooling system may enter the system from beneath the table top TT and beneath the base  25 . Another suitable arrangement would be provided on a table top TT with a support member that is in the nature of a cart  31  having wheels (not shown), so that the unit may be wheeled around. 
         [0050]    Part of the advantages of the system described is the microprocessor controlled solenoid valves trapping refrigerant responsive to the microprocessor signals as set forth above. Normally on most systems when the system shuts down, the pressure differential will bleed back down to equilibrium, and in a normal situation when the system starts up, there is a time lag to drive up pressure in the condenser as the system starts back up. In the system set forth herein, however, by the action of the solenoid shutdown, pressure is maintained and bleed down is avoided. That is to say, there is a “stop action” freeze of the refrigeration cycle which allows an almost instantaneous return to the refrigeration cycle without the necessity of loading up the condenser. 
         [0051]    Operation is driven by readings from two pressure transducers TS 1  (cold plate), PT 1  (suction side of compressor). One TS  1  measures pressure of gas in the evaporator which reflects the temperature of the cold plate. The other, PT 2 , measures pressure of the pump down cycle. The firmware controls the compressor  28 , fan  29 , run solenoids  34 / 40 , defrost solenoid  42 , and status LED&#39;s  41 / 43 / 45  (se Table 1). There is a ten position switch that determines the setpoints for the cold plate temperature. There is a defrost switch for starting a defrost cycle. 
         [0052]    The unit operates in one of the following modes depending on the pressure transducer readings. 
         [0053]      FIG. 8 , Standby mode (green LED  41  blinking): 
         [0054]    Evaporator pressure indicates cold plate temperature below “on” setpoint. 
         [0055]    Run valves  34 / 40  and defrost solenoid  42  are off (valves closed.) Compressor  20  and fan  28  are off. 
         [0056]    When evaporator pressure TS  1  indicates cold plate temperature above “on” setpoint, example 71.0 psi, unit enters compressor mode. 
         [0057]      FIG. 9 , Compressor mode (green LED  41  blinking, red LED  43  on steady): 
         [0058]    Run solenoids  34 / 40  are on (valves open) and defrost solenoid  42  is off (valve closed). Compressor  28  and fan  29  are on. Evaporator pressure indicates cold plate temperature above “off” setpoint, example 68.5 psi. 
         [0059]    Runs compressor with run valves open, monitors TS 1  for a time period T 1 , every, for example 10 seconds, until evaporator pressure is below 60 or the “off&#39; setpoint, example 68.5 psi, minus 8 (whichever is greater). This pressure reading is done with the run valves open which typically gives a pressure reading of 15 to 20 pounds lower than a reading with the valves closed. Closing the valves, waiting a short period, and then measuring the cold plate gives a more accurate cold plate temperature. The valves closed reading would be one that more accurately reflects the temperature of the cold plate. 
         [0060]    After the evaporator pressure TS  1  (with the valves open) gets below 60 (or off set point minus 8), the unit starts checking the evaporator pressure with the run valves closed for a period of T 2 , for example, every 10 seconds. It does this by closing the run valves (with the compressor still running), waiting 1.5 seconds for the pressure to stabilize, and then taking a TS 1  pressure reading. If the pressure is not below the “off&#39; setpoint, the valves are reopened and the unit stays in compressor mode. Otherwise the unit enters pump down mode with the valve  34 / 40  closed. 
         [0061]      FIG. 10 , Pump down mode (green LED blinking, red and yellow LED&#39;s on): 
         [0062]    Pump down pressure above  10  as measured at PT 1 . Run solenoids  34 / 40  are off (valves closed) and defrost solenoid is off (valve closed). Compressor  28  and fan  29  are on. 
         [0063]    Remains in pump down mode until pump down pressure PT 1  is below 10 or evaporator pressure TS  1  is above “on” setpoint. If the pump down pressure reaches 10, the unit enters standby mode. If the evaporator pressure goes above the “on” setpoint, the unit enters compressor mode. 
         [0064]    Defrost mode (green LED blinking, yellow LED on): 
         [0065]    Defrost mode is entered when the defrost switch is manually pressed. 
         [0066]    Run solenoids  34 / 40  are on (valves opened) and defrost solenoid  42  is on (valve open). Compressor  28  is on and fan  29  is off. Defrost mode runs for a period of T 3 , for example, for 40 seconds then standby mode is entered. Defrost mode cannot be reentered until a compressor mode cycle has completed. 
         [0000]    
       
         
               
             
               
               
               
               
               
             
               
               
               
               
               
             
           
               
                 TABLE 1 
               
             
             
               
                   
               
               
                 Setpoints 
               
             
          
           
               
                   
                 On 
                 Off 
                 Temp On 
                 Temp Off 
               
               
                   
                   
               
             
          
           
               
                 1 
                 65 
                 62.5 
                 27.1 
                 25.5 
               
               
                 2 
                 67 
                 64.5 
                 28.4 
                 26.8 
               
               
                 3 
                 69 
                 66.5 
                 29.7 
                 28.1 
               
               
                 4 
                 71 
                 68.5 
                 31.0 
                 29.4 
               
               
                 5 
                 73 
                 70.5 
                 32.3 
                 30.7 
               
               
                 6 
                 75 
                 72.5 
                 33.6 
                 32.0 
               
               
                 7 
                 77 
                 74.5 
                 34.9 
                 33.3 
               
               
                 8 
                 79 
                 76.5 
                 36.2 
                 34.6 
               
               
                 9 
                 81 
                 78.5 
                 37.5 
                 35.9 
               
               
                   
               
             
          
         
       
     
         [0000]    
       
         
               
               
               
             
               
               
               
               
             
           
               
                   
                 TABLE 2 
               
               
                   
                   
               
               
                   
                 Temperature 
                 Pressure 
               
               
                   
                   
               
             
             
               
                   
               
             
          
           
               
                   
                 LOW 
                 28 
                 68 
               
               
                   
                 HIGH 
                 36 
                 78 
               
               
                   
                 Diff 
                 8 
                 12 
               
               
                   
                   
                 Pressure Diff per degree 
                 1.53 
               
               
                   
                   
               
             
          
         
       
     
         [0067]    T 1  (see  FIG. 8 ) is a period of time in which the system is in a standby mode which was entered after the cold plate was sufficiently cold and the low end PT 1  pressure was below a preset minimum, for example, 10 psi. The system, left in the standby mode, would typically warm up, for example, towards room temperature or when a beer is drawn from adding heat to the cold plate. Thus in standby mode, the cold plate is being monitored for a period of time T 1 . This period should be short enough to be responsive to temperature change at the cold plate, for example, drawing a beer. It should not be too short generating unnecessary monitoring. 
         [0068]    Time period T 2  is a time period between leaving standby mode, when the on set point is exceeded and entering compressor mode. That is, time period T 2  should not be too long, as the system needs heat removed therefrom. 
         [0069]    In compressor mode, the microprocessor (monitor) is looking at the cold plate temperature and comparing it to a pre-selected temperature of either 60 psi or the compressor off temperature −8 psi or an appropriate value below the off set point. It has been determined, through experimentation, that a more accurate reading of the cold plate occurs if run valves  34 / 40  are closed for a period of time, for example, T 3 , here 1.5 seconds, after which period of time the cold plate is monitored. If, in the compressor mode, the closed valve reading is below the off set point, here, for example, 68.5, then the system will enter the pump down mode. If the closed valve reading is greater than the off set point, the valves will open and the time period, for example, T 4  will be applied and then the cold plate pressure will again be checked. For a time period, T 3  experimentation can determine as short a time as possible for pressure in the cold plate to stabilize. For a period of time T 4  is not too long or the off set point here, for example, 68.5, may be overshot. If T 4  is too short, you are hurting your cooling capacity by having the valves closed again for T 3 . 
         [0070]    While the subject of this specification has been described in connection with one or more exemplary embodiments, it is not intended to limit the claims to the particular forms set forth. On the contrary, the appended claims are intended to cover such alternatives, modifications and equivalents as may be included within their spirit and scope.