Patent Application
20170027409
This application relates generally to warewashers such as those used in commercial applications such as cafeterias and restaurants and, more particularly, to a heat recovery system that adapts to operating conditions of the warewasher.
Commercial warewashers commonly include a housing area which defines washing and rinsing zones for dishes, pots, pans and other wares. Heat recovery systems have been used to recover heat from the machine that would ordinarily be lost to the machine exhaust.
Waste heat recovery systems such as a heat pump or refrigeration system uses evaporator(s), compressor(s) and condenser(s) such that the operation involves thermal fluids (including refrigerant) for recovering waste energy and re-using captured energy at areas of interest. The systems require the thermal fluid to operate within a specified envelope to prevent system shut down from high or low pressure, hence, the need for effective controls.
It would be desirable to provide a heat recovery system that adapts to machine operating conditions in order to make more effective use of heat recovery. It would also be desirable to provide a heat recovery system that is able to more effectively maintain desired subcooled condition of refrigerant medium. It would also be desirable to support such heat recovery systems to enable operation continuously or semi-continuously at startup, at steady state or at the standby or idle mode while simultaneously recovering waste energy and tempering the waste hot stream to a predetermined temperature by the use of thermal fluid(s).
In one aspect, a warewash machine for washing wares includes a chamber for receiving wares, the chamber having at least one wash zone. A waste heat recovery unit is arranged to transfer heat from exhaust air of the machine to incoming water traveling along a water flow path through the waste heat recovery unit to a booster heater of the machine. A refrigerant medium circuit includes at least a first condenser arranged to deliver refrigerant medium heat to the incoming water. A control arrangement monitors subcooled refrigerant medium condition and responsively modifies operation of one or more of: (i) speed of a compressor of the refrigerant medium circuit, (ii) speed of an exhaust fan the causes air flow across the waste heat recovery unit or (iii) speed of a pump that controls incoming water flow along the water flow path.
In another aspect, a warewash machine for washing wares includes a chamber for receiving wares, the chamber having at least one wash zone. A waste heat recovery unit is arranged to transfer heat from exhaust air of the machine to incoming water traveling along a water flow path through the waste heat recovery unit into the machine. A refrigerant medium circuit includes a condenser arranged to deliver refrigerant medium heat to the incoming water. A control arrangement includes one or more sensors and a controller for determining a condition of subcooled refrigerant medium in the refrigeration medium circuit. The controller is configured to vary, based at least in part upon the condition of the subcooled refrigerant medium, one or more of: (i) a speed of a compressor of the refrigerant medium circuit, (ii) a speed of an exhaust fan the causes air flow across the waste heat recovery unit or (iii) a speed of a pump that controls incoming water flow along the water flow path.
In a further aspect, a method is provided for adaptively controlling a warewash machine that includes a chamber for receiving wares, the chamber having at least one wash zone, a refrigerant medium circuit including at least one condenser through which the incoming water to the machine flows, and a waste heat recovery unit through which incoming water to the machine flows. The method involves: identifying an under-condensed condition of subcooled refrigerant medium in the refrigerant medium circuit or an over-condensed condition of subcooled refrigerant medium in the refrigeration medium circuit; and in response to identification of the under-condensed or over-condensed condition, varying at least one of (i) a speed of a compressor of the refrigerant medium circuit, (ii) a speed of an exhaust fan that causes air flow across the waste heat recovery unit or (iii) a speed of a pump that controls incoming water flow through the waste heat recovery unit and the condenser.
The details of one or more embodiments are set forth in the accompanying drawings and the description below. Other features, objects, and advantages will be apparent from the description and drawings, and from the claims.
Referring to
The racks proceed to a next curtain 38 into a main wash chamber or zone 40, where the wares are subject to sprays of cleansing wash liquid (e.g., typically water with detergent) from upper and lower wash manifolds 42 and 44 with spray nozzles 47 and 49, respectively, these sprays being supplied through a supply conduit 46 by a pump 48, which draws from a main tank 50. A heater 58, such as an electrical immersion heater provided with suitable thermostatic controls (not shown), maintains the temperature of the cleansing liquid in the tank 50 at a suitable level. Not shown, but which may be included, is a device for adding a cleansing detergent to the liquid in tank 50. During normal operation, pumps 32 and 48 are continuously driven, usually by separate motors, once the warewash system 10 is started for a period of time.
The warewash system 10 may optionally include a power rinse (also known as post-wash) chamber or zone (not shown) that is substantially identical to main wash chamber 40. In such an instance, racks of wares proceed from the wash chamber 40 into the power rinse chamber, within which heated rinse water is sprayed onto the wares from upper and lower manifolds.
The racks 12 of wares 14 exit the main wash chamber 40 through a curtain 52 into a final rinse chamber or zone 54. The final rinse chamber 54 is provided with upper and lower spray heads 56, 57 that are supplied with a flow of fresh hot water via pipe 62 running from a hot water booster 70 under the control of a variable speed pump 114 (or alternatively any other suitable valve capable of automatic control). A rack detector 64 may be actuated when a rack 12 of wares 14 is positioned in the final rinse chamber 54 and through suitable electrical controls (e.g., the controller mentioned below), the detector causes actuation of pump 114 which delivers incoming water and causes hot rinse water to move from the booster 70 to the spray heads 56, 57. The water then drains from the wares and is directed into the tank 50 by gravity flow. The rinsed rack 12 of wares 14 then exits the final rinse chamber 54 through curtain 66, moving into dryer unit 18, before exiting the outlet end 17 of the machine.
An exhaust system 80 for pulling hot moist air from the machine (e.g., via operation of a blower 81) may be provided. As shown, a cold water input 72 line may run through a waste heat recovery unit 82 (e.g., a fin-and-tube heat exchanger through which the incoming water flows, though other variations are possible) to recover heat from the exhaust air flowing across and/or through the unit 82. The water line or flow path 72 then runs through one or more condensers 84 (e.g., in the form of a plate heat exchanger or shell-and-tube heat exchangers, though other variations are possible), before delivering the water to the booster 70 for final heating. A condenser 88 may be located in the wash tank and a condenser 90 may be located in the blower dryer unit 18. A second waste heat recovery unit 92 may also be provided.
Referring now to
Generally, condenser 88 may take the form of coil submerged in the wash tank 50 to deliver refrigerant heat to the wash water, condenser 90 may take the form of a coil over which the drying air blows to deliver some refrigerant heat to the drying air and condenser 84, which may be a plate-type heat exchanger, delivers residual refrigerant heat to the incoming fresh water. The incoming water to the booster heater passes through both the waste heat recovery unit 82 and condenser 84. In the event of undesired conditions within the machine, adjustments can be made to compensate.
In this regard, one or more sensors 110 are provided to monitor the conditions of the subcooled refrigerant. The monitoring may be continuous, periodic or triggered by some event (e.g., identification of a rack at a certain location in the machine). By way of example, both a temperature sensor and a pressure sensor may be used to monitor the subcooled refrigerant medium downstream of the last condenser 84 and upstream of the thermal expansion valve 101. If the monitoring indicates that the condition of the subcooled refrigerant medium has departed from a set specification, then corrective action can be take.
For example, any of the following conditions within the machine could lead to the condition of the subcooled refrigerant medium falling below a desired condition operating range, meaning the refrigerant medium has not been condensed sufficiently: an increase in the incoming cold water temperature, a decrease in the incoming cold water rate, an increase in the incoming cold water temperature and a decrease in the incoming cold water rate, an increase in waste moist hot air rate, an increase in waste moist hot air temperature, both increase in the waste moist hot air rate and waste moist hot air temperature, a decrease in the load on the warewash machine with an increase in the waste moist hot air rate and/or waste moist hot air temperature, or an inability of one of the condenser(s) to absorb or transfer the intended heat, as well as any combination of the above. All of these conditions will cause a decrease in the amount of condensation of the refrigerant medium that takes place in the refrigerant medium circuit 100 and could eventually cause the below range condition of the subcooled refrigerant medium.
When a low or below range subcooled condition is identified, any or all of the following corrective actions could be initiated: controlling the compressor 102 to slow down while the electronic thermal expansion valve 101 automatically adjusts to maintain the necessary superheat to the compressor (e.g., based upon indications from a temperature sensor 115), decreasing the speed of exhaust fan 81 while monitoring air flow via meter 106 to maintain the necessary heat load across the waste heat recovery units 82 and 92 and to maintain the necessary superheat to the compressor 102, or increasing the speed of variable speed pump 114 that delivers the incoming cool fresh water. Any of these actions will increase the level of condensation that takes place and can be used to bring the condition of the subcooled refrigerant medium back up into the desired operating range.
As another example, any of the following conditions within the machine could lead to the condition of the subcooled refrigerant medium falling above a desired condition operating range, meaning the refrigerant medium has been overly condensed or subcooled: a decrease in the incoming cold water temperature, an increase in the incoming cold water rate, both decrease in the incoming cold water temperature and increase of incoming cold water rate, a decrease in waste moist hot air rate, a decrease in waste moist hot air temperature, a decrease in both the waste moist hot air rate and waste moist hot air temperature, an increase in the load on the warewash machine with a decrease in the waste moist hot air rate and/or waste moist hot air temperature. All of these conditions will cause an increase in the amount of condensation of the refrigerant medium that takes place in the refrigerant medium circuit 100 and could eventually cause the above range condition of the subcooled refrigerant medium.
When a high or above range or overly subcooled condition is identified, any or all of the following corrective actions can be initiated: controlling the compressor 102 to speed up while the electronic thermal expansion valve 101 adjusts to maintain the necessary superheat to the compressor, or increasing the speed of the exhaust fan 81 to maintain the necessary heat load across the waste heat recovery units 82 and 92 in order to maintain the necessary superheat to the compressor 102, or decreasing the speed of the variable speed pump 114 that delivers the incoming cool fresh water. Any of these actions will decrease the level of condensation that takes place and can be used to bring the condition of the subcooled refrigerant medium back down into the desired operating range.
Moreover, in a situation where the heat load required by one or more of the condensers is satisfied, the speed of both the compressor 102 and exhaust fan 81 may be decreased, relying upon the excess heat load to maintain the minimum heat required in the machine and also to prevent unnecessary steam escape from the loading and unloading ends of the machine. In a standby mode of the machine (e.g., when wares are not being moved through the machine for cleaning) the speed of the exhaust fan 81 may be decreased to conserve heat in the machine. The exhaust fan 81 is typically on when the compressor 102 is on to prevent low pressure, unless conditions are close to high pressure, in which case the fan 81 may be shutdown. The moist hot air temperature (as indicated by temperature sensor 108) and flowrate (as indicated by sensor 106) may be used to determine the fan speed to maintain a desired set temperature drop across the waste heat recovery units 82 and 92, thereby maintaining the needed superheat and exhaust conditions.
By way of example, the subcooled condition of the refrigerant medium may be a difference between the actual temperature indicated by the temperature sensor 110 less a condenser saturation temperature corresponding to the pressure indicated by pressure sensor 110. An exemplary acceptable subcooled condition operating range may be between 10° F. and 15° F., though variations are possible. Above 15° F. indicates the refrigerant medium has been overly condensed or subcooled, and below 10° F. indicates that the refrigerant medium has not been condensed enough (e.g., gas may be present). The condenser saturation temperature may be determined by reading the pressure indicated by pressure sensor 110 and (i) using a refrigerant pressure/temperature chart or table (e.g., stored in controller memory) to convert the pressure reading to the condenser saturation temperature or (ii) using an equation fitted to a refrigerant medium pressure/temperature chart to convert the pressure reading to the condenser saturation temperature.
A controller 150 may be provided to effect initiation and control of any of the corrective actions mentioned above based upon indications from the temperature sensor and pressure sensor, as well as for controlling other functions and operations of the machine as discussed above. As used herein, the term controller is intended to broadly encompass any circuit (e.g., solid state, application specific integrated circuit (ASIC), an electronic circuit, a combinational logic circuit, a field programmable gate array (FPGA)), processor (e.g., shared, dedicated, or group—including hardware or software that executes code) or other component, or a combination of some or all of the above, that carries out the control functions of the machine or the control functions of any component thereof. The controller may include variable adjustment functionality that enables, for example, the acceptable subcooled condition operating range to be varied (e.g., via an operator interface associated with the controller 150 or via a restricted service/maintenance personnel interface).
Ensuring that the refrigerant medium remains in a desired operating range as indicated above can help system operation by (i) assuring that the refrigerant medium is fully condensed to assist efficient operation of the thermal expansion valve 101, and/or (ii) reducing or eliminating the presence of gas in the refrigerant medium at the upstream side of the thermal expansion valve as the presence of such gas will tend to restrict refrigerant medium flow hence starving the evaporator of refrigerant medium, and/or (ii) assuring that the refrigerant medium is not overcooled coming out of the condenser chain, as such overcooling will require more energy delivery to the refrigerant medium at the evaporator in order to raise the refrigerant medium to desired compressor suction conditions, and if the evaporator is unable to deliver sufficient energy the performance and/or life of the compressor may be adversely impacted.
The above machine provides an advantageous method of correcting undesired conditions of a refrigerant medium circuit in a warewash machine. In particular, the method involves: identifying an under-condensed condition of subcooled refrigerant medium in the refrigerant medium circuit or an over-condensed condition of subcooled refrigerant medium in the refrigeration medium circuit; and in response to identification of the under-condensed or over-condensed condition, varying at least one of (i) a speed of a compressor of the refrigerant medium circuit, (ii) a speed of an exhaust fan that causes air flow across the waste heat recovery unit or (iii) a speed of a pump that controls incoming water flow through the waste heat recovery unit and the condenser. In one implementation, the identifying step includes sensing a refrigerant medium temperature and a refrigerant medium pressure downstream of all condensers in the refrigerant medium circuit. In one example of such an implementation, the identifying step includes determining a difference between the sensed refrigerant medium temperature less a condenser saturation temperature corresponding to the sensed refrigerant medium pressure. If the under-condensed condition of subcooled refrigerant medium is identified, the varying step involves at least one of: (i) reducing the speed of the compressor, (ii) reducing the speed of the exhaust fan or (iii) increasing the speed of the pump. If the over-condensed condition of subcooled refrigerant medium is identified, the varying step involves at least one of: (i) increasing the speed of the compressor, (ii) increasing the speed of the exhaust fan or (iii) decreasing the speed of the pump. The method may also involve monitoring temperature and flow rate of exhaust air and responsively adjusting the speed of the exhaust fan to maintain a set temperature drop across the waste heat recovery unit.
It is to be clearly understood that the above description is intended by way of illustration and example only and is not intended to be taken by way of limitation, and that changes and modifications are possible. Accordingly, other embodiments are contemplated and modifications and changes could be made without departing from the scope of this application. For example, the term refrigerant commonly refers to known acceptable refrigerants, but other thermal fluids could be used in refrigerant type circuits. The term “refrigerant medium” is intended to encompass all such traditional refrigerants and other thermal fluids. Embodiments with varying numbers of waste heat recovery units and/or numbers of condensers are also contemplated.
| Number | Date | Country | |
|---|---|---|---|
| 62199367 | Jul 2015 | US |
