US20060112702A1 - Energy efficient capacity control for an air conditioning system - Google Patents
Energy efficient capacity control for an air conditioning system Download PDFInfo
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- US20060112702A1 US20060112702A1 US11/305,969 US30596905A US2006112702A1 US 20060112702 A1 US20060112702 A1 US 20060112702A1 US 30596905 A US30596905 A US 30596905A US 2006112702 A1 US2006112702 A1 US 2006112702A1
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- refrigerant
- speed
- evaporator
- temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/025—Motor control arrangements
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00357—Air-conditioning arrangements specially adapted for particular vehicles
- B60H1/00378—Air-conditioning arrangements specially adapted for particular vehicles for tractor or load vehicle cabins
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H1/3204—Cooling devices using compression
- B60H1/3205—Control means therefor
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H1/3204—Cooling devices using compression
- B60H1/3205—Control means therefor
- B60H1/322—Control means therefor for improving the stop or idling operation of the engine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D29/00—Arrangement or mounting of control or safety devices
- F25D29/003—Arrangement or mounting of control or safety devices for movable devices
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H2001/3236—Cooling devices information from a variable is obtained
- B60H2001/3248—Cooling devices information from a variable is obtained related to pressure
- B60H2001/325—Cooling devices information from a variable is obtained related to pressure of the refrigerant at a compressing unit
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H2001/3236—Cooling devices information from a variable is obtained
- B60H2001/3255—Cooling devices information from a variable is obtained related to temperature
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H2001/3236—Cooling devices information from a variable is obtained
- B60H2001/3255—Cooling devices information from a variable is obtained related to temperature
- B60H2001/3261—Cooling devices information from a variable is obtained related to temperature of the air at an evaporating unit
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H2001/3236—Cooling devices information from a variable is obtained
- B60H2001/3255—Cooling devices information from a variable is obtained related to temperature
- B60H2001/3263—Cooling devices information from a variable is obtained related to temperature of the refrigerant at an evaporating unit
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H2001/3236—Cooling devices information from a variable is obtained
- B60H2001/3266—Cooling devices information from a variable is obtained related to the operation of the vehicle
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H2001/3269—Cooling devices output of a control signal
- B60H2001/327—Cooling devices output of a control signal related to a compressing unit
- B60H2001/3272—Cooling devices output of a control signal related to a compressing unit to control the revolving speed of a compressor
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H2001/3269—Cooling devices output of a control signal
- B60H2001/328—Cooling devices output of a control signal related to an evaporating unit
- B60H2001/3282—Cooling devices output of a control signal related to an evaporating unit to control the air flow
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H2001/3286—Constructional features
- B60H2001/3292—Compressor drive is electric only
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/025—Compressor control by controlling speed
- F25B2600/0253—Compressor control by controlling speed with variable speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/11—Fan speed control
- F25B2600/111—Fan speed control of condenser fans
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/11—Fan speed control
- F25B2600/112—Fan speed control of evaporator fans
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/21—Refrigerant outlet evaporator temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1931—Discharge pressures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction pressures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2104—Temperatures of an indoor room or compartment
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2116—Temperatures of a condenser
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
- F25B2700/21173—Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2700/00—Means for sensing or measuring; Sensors therefor
- F25D2700/12—Sensors measuring the inside temperature
Definitions
- the invention relates to vehicle air conditioning systems, and in more particular applications to air conditioning systems for the sleeper cabs or compartments of large trucks.
- auxiliary power units wherein a diesel engine rotates an automotive style AC compressor and an alternator DC/AC, and that interfaces with existing cab air handling and existing vehicle heating, venting and air conditioning (HVAC) cooling system; a generator set (GENSET) wherein a diesel engine powers a generator providing AC electric for use in a vehicle; 120 AC electricity, shore power wherein the truck stop provides electrical outlets; and auxiliary batteries wherein additional batteries are added for the vehicle for use by a sleeper HVAC system.
- HVAC heating, venting and air conditioning
- a method if provided for operating a vapor compression air conditioning system for a sleeper compartment of a truck including a variable speed compressor for pressurizing a refrigerant, a condenser, an evaporator, and a variable speed blower for directing an air flow through the evaporator.
- the method includes the steps of:
- step d adjusting the speed of the blower based on the monitoring of step d).
- step e) includes adjusting a voltage to the variable speed compressor.
- step f) includes adjusting a voltage to the variable speed blower.
- step e) includes comparing the air temperature out of the evaporator to a dew point.
- step e) includes comparing the sleeper compartment temperature to a set temperature. In a further feature, step e) further includes comparing the air temperature out of the evaporator to the set temperature. In yet a further feature, step e) further includes comparing the air temperature out of the evaporator to a dew point.
- step f) includes comparing the super heat of the refrigerant to a check value.
- the step e) includes comparing the discharge pressure to a check value.
- the method further includes:
- step g adjusting the speed of a condenser fan based on the monitoring of step g).
- an air conditioning system for use in cooling a sleeper compartment of a truck.
- the system includes a refrigerant flow path; a variable speed compressor to pressurize a refrigerant in the refrigerant flow path; a condenser in the refrigerant flow path downstream from the compressor; an evaporator in the refrigerant flow path downstream from the condenser; a variable speed blower configured to direct an air flow through the evaporator to cool the sleeper compartment; a plurality of sensors to monitor the air temperature of the sleeper compartment, the temperature of the air flow out of the evaporator, the refrigerant discharge pressure of the compressor; and the super heat of the refrigerant in the refrigerant flow path; and a controller connected to the sensors and the compressor and blower, the controller configured to selectively adjust the speed of the compressor and the blower based on signals received from the plurality of sensors.
- the controller is configured to adjust the speed of the compressor based on a signal indicating the air temperature of the sleeper compartment.
- the controller is configured to adjust the speed of the compressor based on a signal indicating the temperature of the air flow exiting the evaporator.
- the controller is configured to adjust the speed of the compressor based on a signal indicating the discharge pressure of the compressor.
- the controller is configured to adjust the speed of the compressor based on a signals indicating the air temperature of the sleeper compartment, the temperature of the air flow exiting the evaporator, and the discharge pressure of the compressor.
- the controller is configured to adjust the speed of the blower based on a signal that indicates the super heat of the refrigerant.
- the system further includes a variable speed condenser fan configured to direct an air flow through the condenser, and the controller is configured to adjust the speed of the fan based on a signal indicating the sub-cooling of the refrigerant.
- a method if provided for operating a vapor compression air conditioning system for a sleeper compartment of a truck including a variable speed compressor for pressurizing a refrigerant, a condenser, an evaporator, and a variable speed blower for directing an air flow through the evaporator.
- the method includes the steps of:
- step a) further includes adjusting the speed of the compressor based on the air temperature in the sleeper compartment.
- the method further includes the step of adjusting the speed of a variable speed condenser fan based on the sub-cooling of the refrigerant.
- an air conditioning system for use in cooling a sleeper compartment of a truck.
- the system includes a refrigerant flow path; a variable speed compressor to pressurize a refrigerant in the refrigerant flow path; a condenser in the refrigerant flow path downstream from the compressor; an evaporator in the refrigerant flow path downstream from the condenser; a variable speed blower configured to direct an air flow through the evaporator to cool the sleeper compartment; and a controller configured to selectively adjust the speed of the compressor and the blower based on signals indicating the temperature of the air flow out of the evaporator, the refrigerant discharge pressure out of the compressor, and the super heat of the refrigerant.
- system of further includes a variable speed fan configured to direct an air flow through the condenser, and wherein the controller is configured to adjust the speed of the fan based on a signal indicating the sub-cooling of the refrigerant.
- FIG. 1 is a diagrammatic representation of an air conditioning system embodying the present invention for use in cooling a sleeper cab or compartment of a truck;
- FIG. 2 is an electrical control schematic for the system of FIG. 1 ;
- FIG. 3 is a graph illustrating the non-idling cooling requirements of a sleeper compartment of a truck in which the system of FIG. 1 can be used;
- FIG. 4 is a control algorithm for the system of FIG. 1 ;
- FIG. 5 is a side elevation view of a truck in which the system of FIG. 1 can be used;
- FIG. 6 is a graph showing certain temperatures associated with the truck of FIG. 5 during certain non-idle conditions
- FIG. 7 is a table showing the weights of a test system built according to the invention.
- FIG. 8 is a graph showing the test results of a test system embodying the present invention.
- FIGS. 9 and 10 are graphs of input watts and cooling watts versus condenser ambient for a system embodying the present invention.
- FIG. 11 is a graph showing cooling capacity versus compression ratio for a system embodying the present invention.
- FIG. 12 is a table comparing certain system parameters of a system embodying the present invention.
- the invention provides an electrically driven, hermetic, vapor compression A/C system 10 that will maintain comfortable temperatures in a vehicle, shown schematically at 12 , without operating the main engine by utilizing an electronic control scheme or controller 14 that efficiently matches the cooling output to the cooling requirements.
- Wind tunnel tests were run on a typical class H sleeper cab 16 and some additional computer calculations were done to determine the cooling requirements for the cab 16 . The results are shown in FIG. 3 of this application.
- the system 10 according to the invention matches or attempts to match the cooling requirements exactly in order to operate the A/C system 10 in the most efficient manner.
- This system 10 consists of selected air conditioning components and sensors that can be controlled to deliver cooling capacity as required while minimizing the power consumed.
- the system 10 includes a compressor 20 , a compressor controller 21 , a condenser fan 22 , and an evaporator blower 24 , all of which are continuously variable speed.
- the system 10 further preferably includes a condenser 26 , a pressure reduction device 28 , such as an expansion valve, thermostatic expansion valve, orifice tube, and preferably an electronically controlled expansion valve 28 , and an evaporator 30 , all connected in series in a refrigerant flow path 32 with the compressor 20 .
- the sensors used to determine the control operation are shown in FIG.
- FIG. 1 which shows sensors 34 and 36 for monitoring the compressor discharge temperature T 1 and compressor discharge pressure P 1 , respectively, sensors 38 and 40 for monitoring the compressor suction temperature T 2 and compressor suction pressure P 2 , respectively, sensor 42 for monitoring the expansion valve inlet temperature T 3 , sensor 44 for monitoring the expansion valve outlet temperature T 4 , sensor 46 for monitoring the evaporator air outlet temperature T 5 , and sensor 47 for monitoring the vehicle interior temperature T 6 , which is preferably the interior temperature of the sleeper compartment 16 of the vehicle 12 .
- Sensors 48 and 49 are also included to monitor the ambient dry bulb and the ambient relative humidify, respectively.
- An operator control 50 is also provided and is connected to the controller 14 , as are the previously described sensors.
- the controller 14 will preferably include a printed circuit board having a control algorithm which will be described later.
- the system 10 is powered by a battery pack 52 when in non-idle mode, and by a vehicle alternator 54 , battery 56 , and charger/converter 58 when in idle mode.
- the charger/converter 58 converts 120 volt AC to 24 volt DC for unit and auxiliary battery charging.
- the system controller 14 preferably operates off of 12 volt DC, while the variable speed compressor 20 , condenser fan 22 , and evaporator blower 24 operate off of 24 volt DC. Further, while it has not been shown, an electronically controlled expansion valve 28 could be connected in the Electronic Control Schematic in the same fashion as the compressor 20 , condenser fan 22 , and evaporator blower 24 .
- FIG. 4 shows a System Algorithm Diagram that is used by the electronic controller. It should be noted that the values of various checking parameters shown represent a current best guess for a particular system, but can easily be changed in order to optimize the system and control scheme for each particular application. Accordingly, it should be understood that the values for the adjustments to the Set temperatures for the Sleeper Temperature and for the Evaporator Out Temperature, the adjustment to the Dew Point for the Evaporator Out Temperature versus Dew Point comparison, the check pressure value for the compressor discharge pressure (P 1 ), the check values for the subcooling (SC), and the check values for the superheat (SH) may all be adjusted to optimize each particular system dependent upon the particular components and parameters associated with each system.
- P 1 the check pressure value for the compressor discharge pressure
- SC subcooling
- SH superheat
- controller 14 is configured to adjust the speed of the compressor 20 , the fan 22 , and the blower 24 based on the air temperature in the sleeper compartment 16 , the temperature of the air flow out of the evaporator 30 , the discharge pressure P 1 of the compressor 20 , the subcooling of the refrigerant, and the superheat of the refrigerant.
- the controller preferably adjusts the speed of the compressor 20 , via an increase or decrease in the voltage to the compressor 20 , based upon the sleeper temperature in comparison to a set temperature, the temperature of the air flow out of the evaporator 30 in comparison to the set temperature, the temperature of air flow out of the evaporator 30 in comparison to the dew point, and the discharge pressure P 1 out of the compressor 20 in comparison to a check pressure.
- the controller 14 adjusts the speed of the blower 24 , via an increase or decrease in the voltage to the blower 24 , based upon the super heat of the refrigerant in comparison to a check value, and adjusts the speed of the fan 22 , via an increase or decrease in the voltage to the fan, based on the sub-cooling of the refrigerant in comparison to a check value.
- control of certain system components appears to be more critical to the goal of minimizing power consumption.
- the control of the compressor voltage appears to have the highest order effect on power consumption, followed by the control of the blower voltage, and then last by the control of the fan voltage.
- the algorithm would be changed by simply eliminating the checks of the sub-cooling (SC) and the associated commands to either increase or decrease the fan voltage.
- SC sub-cooling
- a system built and controlled according to the invention was installed in a test bed vehicle and performance tested in a wind tunnel.
- the test bed vehicle was a Class 8 heavy truck, as shown in FIG. 5 , which included a cab width of 6.5 feet, a sleeper width of 7.9 feet, a front windshield area of 6.8 square feet, a sleeper window of 3.3 square feet, a sleeper body of 5.9 feet length by 6.5 foot width by 9.8 foot height with almost no insulation in the walls.
- the test unit included a compressor 20 , a condenser fan 22 , and an evaporator blower 24 that were continuously variable.
- a manually controlled expansion valve 28 was used rather than an electronically controlled expansion valve.
- the test system 10 was built as a module that was 24 inches wide by 24 inches high by 16 inches deep and was installed beneath the sleeper bed. The weights of the system components are shown in FIG. 7 .
- the vehicle cooling load requirements shown in FIG. 3 were generated, at least in part, from the wind tunnel testing of the test vehicle, the results of which are shown in FIG. 6 for overnight cool down after the end of engine idle.
- the peak in the cooling requirements is a result of the engine heat (represented by the engine oil temperature and radiator top tank temperature), which heats the interior of the cab and sleeper during the initial non-idle time period.
- the results of this testing were then built into a simulation computer model, which generated an accurate comparison between the simulation results and the test results.
- FIGS. 9 and 10 show the results from initial tests that were done to help determine the most efficient operating points for the system. Further in this regard, FIG. 11 shows the effect of compressor compression ratio on capacity, and FIG. 12 is a table that relates the pressure ratio to amps, superheat, the suction pressure of the compressor 20 , and the discharge pressure of the compressor 20 and provides an indication of how to control the system 10 to get better battery life.
- the advantages of this invention include the proper selection of controllable components, and the controls that efficiently match the system output to the requirements thereby minimizing power consumption.
Abstract
An air conditioning system (10) is provided for cooling a compartment (16) of a truck when the main engine is not running. The system (10) includes a variable speed compressor (20), a variable speed condenser fan (22), a variable speed evaporator blower (24), and a controller (14) configured to optimize the cooling capacity of the system (10) to the cooling requirements of the compartment (16) by selectively adjusting the speeds of the variable speed components (20,22,24).
Description
- This application is a continuation-in-part application of Ser. No. 11/130,576, filed May 17, 2005, which claims priority to provisional application Ser. No. 60/572,654, filed May 18, 2004, entitled “Energy Efficient Capacity Control for an Air Conditioning System”.
- The invention relates to vehicle air conditioning systems, and in more particular applications to air conditioning systems for the sleeper cabs or compartments of large trucks.
- Currently, air conditioning systems for vehicles, and particularly for the sleeper cabs of large trucks, is provided via an engine driven air conditioning system. However, concern over pollution, both air and noise, is creating the potential that trucks will no longer be allowed in some instances to idle their engines in order to operate the air conditioning for the sleeper cab. In addition to concerns over pollution, it has been estimated that the costs for overnight idling include $2,400 per year in fuel consumption and $250 per year in added maintenance. With respect to air pollution, it has been estimated that a single truck idling for one year produces 250 lbs. of CO, 615 lbs. of NOx, and 17 tons of CO2.
- Possible alternatives to having the main engine idle include: auxiliary power units wherein a diesel engine rotates an automotive style AC compressor and an alternator DC/AC, and that interfaces with existing cab air handling and existing vehicle heating, venting and air conditioning (HVAC) cooling system; a generator set (GENSET) wherein a diesel engine powers a generator providing AC electric for use in a vehicle; 120 AC electricity, shore power wherein the truck stop provides electrical outlets; and auxiliary batteries wherein additional batteries are added for the vehicle for use by a sleeper HVAC system.
- Electrically driven, hermetic vapor compression air conditioning (A/C) systems are common but there are few used in vehicles. The main reason for not using this reliable means of providing air conditioning is the lack of available electric power. U.S. Pat. No. 6,622,500 describes a vapor compression A/C system that attempts to improve efficiency by controlling a variable displacement compressor.
- In accordance with one feature of the invention, a method if provided for operating a vapor compression air conditioning system for a sleeper compartment of a truck, the air conditioning system including a variable speed compressor for pressurizing a refrigerant, a condenser, an evaporator, and a variable speed blower for directing an air flow through the evaporator. The method includes the steps of:
- a) monitoring the air temperature of the sleeper compartment;
- b) monitoring the air flow temperature out of the evaporator;
- c) monitoring the refrigerant discharge pressure of the compressor;
- d) monitoring the super heat of the refrigerant;
- e) adjusting the speed of the compressor based on the monitoring of steps a), b) and c); and
- f) adjusting the speed of the blower based on the monitoring of step d).
- As one feature, step e) includes adjusting a voltage to the variable speed compressor.
- In one feature, step f) includes adjusting a voltage to the variable speed blower.
- According to one feature, step e) includes comparing the air temperature out of the evaporator to a dew point.
- In one feature, step e) includes comparing the sleeper compartment temperature to a set temperature. In a further feature, step e) further includes comparing the air temperature out of the evaporator to the set temperature. In yet a further feature, step e) further includes comparing the air temperature out of the evaporator to a dew point.
- As one feature, step f) includes comparing the super heat of the refrigerant to a check value.
- According to one feature, the step e) includes comparing the discharge pressure to a check value.
- In one feature, the method further includes:
- g) monitoring the sub-cooling of the refrigerant;
- h) adjusting the speed of a condenser fan based on the monitoring of step g).
- In accordance with one feature of the invention, an air conditioning system is provided for use in cooling a sleeper compartment of a truck. The system includes a refrigerant flow path; a variable speed compressor to pressurize a refrigerant in the refrigerant flow path; a condenser in the refrigerant flow path downstream from the compressor; an evaporator in the refrigerant flow path downstream from the condenser; a variable speed blower configured to direct an air flow through the evaporator to cool the sleeper compartment; a plurality of sensors to monitor the air temperature of the sleeper compartment, the temperature of the air flow out of the evaporator, the refrigerant discharge pressure of the compressor; and the super heat of the refrigerant in the refrigerant flow path; and a controller connected to the sensors and the compressor and blower, the controller configured to selectively adjust the speed of the compressor and the blower based on signals received from the plurality of sensors.
- As one feature, the controller is configured to adjust the speed of the compressor based on a signal indicating the air temperature of the sleeper compartment.
- In one feature, the controller is configured to adjust the speed of the compressor based on a signal indicating the temperature of the air flow exiting the evaporator.
- According to one feature, the controller is configured to adjust the speed of the compressor based on a signal indicating the discharge pressure of the compressor.
- In accordance with one feature, the controller is configured to adjust the speed of the compressor based on a signals indicating the air temperature of the sleeper compartment, the temperature of the air flow exiting the evaporator, and the discharge pressure of the compressor.
- In one feature, the controller is configured to adjust the speed of the blower based on a signal that indicates the super heat of the refrigerant.
- In one feature, the system further includes a variable speed condenser fan configured to direct an air flow through the condenser, and the controller is configured to adjust the speed of the fan based on a signal indicating the sub-cooling of the refrigerant.
- In accordance with one feature of the invention, a method if provided for operating a vapor compression air conditioning system for a sleeper compartment of a truck, the air conditioning system including a variable speed compressor for pressurizing a refrigerant, a condenser, an evaporator, and a variable speed blower for directing an air flow through the evaporator. The method includes the steps of:
- a) adjusting the speed of the compressor based on the temperature of the air flow out of the evaporator and the refrigerant discharge pressure out of the compressor; and
- b) adjusting the speed of the blower based on the super heat of the refrigerant.
- As one feature, step a) further includes adjusting the speed of the compressor based on the air temperature in the sleeper compartment.
- In one feature, the method further includes the step of adjusting the speed of a variable speed condenser fan based on the sub-cooling of the refrigerant.
- In accordance with one feature of the invention, an air conditioning system is provided for use in cooling a sleeper compartment of a truck. The system includes a refrigerant flow path; a variable speed compressor to pressurize a refrigerant in the refrigerant flow path; a condenser in the refrigerant flow path downstream from the compressor; an evaporator in the refrigerant flow path downstream from the condenser; a variable speed blower configured to direct an air flow through the evaporator to cool the sleeper compartment; and a controller configured to selectively adjust the speed of the compressor and the blower based on signals indicating the temperature of the air flow out of the evaporator, the refrigerant discharge pressure out of the compressor, and the super heat of the refrigerant.
- In one feature, the system of further includes a variable speed fan configured to direct an air flow through the condenser, and wherein the controller is configured to adjust the speed of the fan based on a signal indicating the sub-cooling of the refrigerant.
- Other objects, features, and advantages of the invention will become apparent from a review of the entire specification, including the appended claims and drawings.
-
FIG. 1 is a diagrammatic representation of an air conditioning system embodying the present invention for use in cooling a sleeper cab or compartment of a truck; -
FIG. 2 is an electrical control schematic for the system ofFIG. 1 ; -
FIG. 3 is a graph illustrating the non-idling cooling requirements of a sleeper compartment of a truck in which the system ofFIG. 1 can be used; -
FIG. 4 is a control algorithm for the system ofFIG. 1 ; -
FIG. 5 is a side elevation view of a truck in which the system ofFIG. 1 can be used; -
FIG. 6 is a graph showing certain temperatures associated with the truck ofFIG. 5 during certain non-idle conditions; -
FIG. 7 is a table showing the weights of a test system built according to the invention; -
FIG. 8 is a graph showing the test results of a test system embodying the present invention; -
FIGS. 9 and 10 are graphs of input watts and cooling watts versus condenser ambient for a system embodying the present invention; -
FIG. 11 is a graph showing cooling capacity versus compression ratio for a system embodying the present invention; and -
FIG. 12 is a table comparing certain system parameters of a system embodying the present invention. - With reference to
FIGS. 1 and 2 , the invention provides an electrically driven, hermetic, vapor compression A/C system 10 that will maintain comfortable temperatures in a vehicle, shown schematically at 12, without operating the main engine by utilizing an electronic control scheme orcontroller 14 that efficiently matches the cooling output to the cooling requirements. - Wind tunnel tests were run on a typical class
H sleeper cab 16 and some additional computer calculations were done to determine the cooling requirements for thecab 16. The results are shown inFIG. 3 of this application. Preferably, thesystem 10 according to the invention matches or attempts to match the cooling requirements exactly in order to operate the A/C system 10 in the most efficient manner. - This
system 10 consists of selected air conditioning components and sensors that can be controlled to deliver cooling capacity as required while minimizing the power consumed. Preferably, thesystem 10 includes acompressor 20, acompressor controller 21, acondenser fan 22, and anevaporator blower 24, all of which are continuously variable speed. Thesystem 10 further preferably includes acondenser 26, apressure reduction device 28, such as an expansion valve, thermostatic expansion valve, orifice tube, and preferably an electronically controlledexpansion valve 28, and anevaporator 30, all connected in series in arefrigerant flow path 32 with thecompressor 20. The sensors used to determine the control operation are shown inFIG. 1 , which shows sensors 34 and 36 for monitoring the compressor discharge temperature T1 and compressor discharge pressure P1, respectively,sensors 38 and 40 for monitoring the compressor suction temperature T2 and compressor suction pressure P2, respectively,sensor 42 for monitoring the expansion valve inlet temperature T3,sensor 44 for monitoring the expansion valve outlet temperature T4,sensor 46 for monitoring the evaporator air outlet temperature T5, andsensor 47 for monitoring the vehicle interior temperature T6, which is preferably the interior temperature of thesleeper compartment 16 of thevehicle 12.Sensors operator control 50 is also provided and is connected to thecontroller 14, as are the previously described sensors. Thecontroller 14 will preferably include a printed circuit board having a control algorithm which will be described later. Preferably, as seen inFIG. 2 , thesystem 10 is powered by abattery pack 52 when in non-idle mode, and by avehicle alternator 54,battery 56, and charger/converter 58 when in idle mode. Preferably, the charger/converter 58converts 120 volt AC to 24 volt DC for unit and auxiliary battery charging. - With reference to
FIG. 2 , it can be seen that thesystem controller 14 preferably operates off of 12 volt DC, while thevariable speed compressor 20,condenser fan 22, andevaporator blower 24 operate off of 24 volt DC. Further, while it has not been shown, an electronically controlledexpansion valve 28 could be connected in the Electronic Control Schematic in the same fashion as thecompressor 20,condenser fan 22, andevaporator blower 24. -
FIG. 4 shows a System Algorithm Diagram that is used by the electronic controller. It should be noted that the values of various checking parameters shown represent a current best guess for a particular system, but can easily be changed in order to optimize the system and control scheme for each particular application. Accordingly, it should be understood that the values for the adjustments to the Set temperatures for the Sleeper Temperature and for the Evaporator Out Temperature, the adjustment to the Dew Point for the Evaporator Out Temperature versus Dew Point comparison, the check pressure value for the compressor discharge pressure (P1), the check values for the subcooling (SC), and the check values for the superheat (SH) may all be adjusted to optimize each particular system dependent upon the particular components and parameters associated with each system. - As seen in
FIG. 4 ,controller 14 is configured to adjust the speed of thecompressor 20, thefan 22, and theblower 24 based on the air temperature in thesleeper compartment 16, the temperature of the air flow out of theevaporator 30, the discharge pressure P1 of thecompressor 20, the subcooling of the refrigerant, and the superheat of the refrigerant. More specifically, it can be seen that the controller preferably adjusts the speed of thecompressor 20, via an increase or decrease in the voltage to thecompressor 20, based upon the sleeper temperature in comparison to a set temperature, the temperature of the air flow out of theevaporator 30 in comparison to the set temperature, the temperature of air flow out of theevaporator 30 in comparison to the dew point, and the discharge pressure P1 out of thecompressor 20 in comparison to a check pressure. Thecontroller 14 adjusts the speed of theblower 24, via an increase or decrease in the voltage to theblower 24, based upon the super heat of the refrigerant in comparison to a check value, and adjusts the speed of thefan 22, via an increase or decrease in the voltage to the fan, based on the sub-cooling of the refrigerant in comparison to a check value. - It should be understood that the control of certain system components appears to be more critical to the goal of minimizing power consumption. For example, the control of the compressor voltage appears to have the highest order effect on power consumption, followed by the control of the blower voltage, and then last by the control of the fan voltage. In this regard, it should be noted that in some systems it may be desirable to not control the lower order components, such as, for example, not to control the fan voltage. In such a case, the algorithm would be changed by simply eliminating the checks of the sub-cooling (SC) and the associated commands to either increase or decrease the fan voltage.
- A system built and controlled according to the invention was installed in a test bed vehicle and performance tested in a wind tunnel. The test bed vehicle was a
Class 8 heavy truck, as shown inFIG. 5 , which included a cab width of 6.5 feet, a sleeper width of 7.9 feet, a front windshield area of 6.8 square feet, a sleeper window of 3.3 square feet, a sleeper body of 5.9 feet length by 6.5 foot width by 9.8 foot height with almost no insulation in the walls. The test unit included acompressor 20, acondenser fan 22, and anevaporator blower 24 that were continuously variable. A manually controlledexpansion valve 28 was used rather than an electronically controlled expansion valve. Thetest system 10 was built as a module that was 24 inches wide by 24 inches high by 16 inches deep and was installed beneath the sleeper bed. The weights of the system components are shown inFIG. 7 . - The vehicle cooling load requirements shown in
FIG. 3 were generated, at least in part, from the wind tunnel testing of the test vehicle, the results of which are shown inFIG. 6 for overnight cool down after the end of engine idle. The peak in the cooling requirements is a result of the engine heat (represented by the engine oil temperature and radiator top tank temperature), which heats the interior of the cab and sleeper during the initial non-idle time period. The results of this testing were then built into a simulation computer model, which generated an accurate comparison between the simulation results and the test results. - Preliminary testing indicated that the required cooling capacity could be generated with the minimum electrical input. The testing showed the ability to provide almost eight hours of maintaining the sleeper compartment at 21° C./70° F. with a 32° C.-90° F. outside air ambient and required 2500 watts (electrical) over an eight hour period. A first generation unit at medium settings used two 12-
volt DC 100 amp hour batteries—producing six hours (2000 watts electrical). A second generation unit at medium settings used two 12-volt DC 125 amp hour batteries producing almost eight hours of performance. Extended life can be achieved with additional batteries and potentially with refined control strategies and refrigerant components.FIG. 8 is a graph showing the test results of a non-idle HVAC module overnight at 90° F. ambient and 40% relative humidity. -
FIGS. 9 and 10 show the results from initial tests that were done to help determine the most efficient operating points for the system. Further in this regard,FIG. 11 shows the effect of compressor compression ratio on capacity, andFIG. 12 is a table that relates the pressure ratio to amps, superheat, the suction pressure of thecompressor 20, and the discharge pressure of thecompressor 20 and provides an indication of how to control thesystem 10 to get better battery life. - The results of the above and other tests indicate that with the infinitely
variable compressor 20 and infinitelyvariable fan 22 andblower motors 24, asystem 10 can be operated more efficiently than with current production components. - The advantages of this invention include the proper selection of controllable components, and the controls that efficiently match the system output to the requirements thereby minimizing power consumption.
Claims (22)
1. A method of operating a vapor compression air conditioning system for a sleeper compartment of a truck, the air conditioning system including a variable speed compressor for pressurizing a refrigerant, a condenser, an evaporator, and a variable speed blower for directing an air flow through the evaporator, the method comprising the steps of:
a) monitoring the air temperature of the sleeper compartment;
b) monitoring the air flow temperature out of the evaporator;
c) monitoring the refrigerant discharge pressure of the compressor;
d) monitoring the super heat of the refrigerant;
e) adjusting the speed of the compressor based on the monitoring of steps a), b) and c); and
f) adjusting the speed of the blower based on the monitoring of step d).
2. The method of claim 1 wherein step e) comprises adjusting a voltage to the variable speed compressor.
3. The method of claim 1 wherein step f) comprises adjusting a voltage to the variable speed blower.
4. The method of claim 1 wherein step e) comprises comparing the air temperature out of the evaporator to a dew point.
5. The method of claim 1 wherein step e) comprises comparing the sleeper compartment temperature to a set temperature.
6. The method of claim 5 wherein step e) comprises comparing the air temperature out of the evaporator to the set temperature.
7. The method of claim 6 wherein step e) further comprises comparing the air temperature out of the evaporator to a dew point.
8. The method of claim 1 wherein step f) comprises comparing the sub-cooling of the refrigerant to a check value.
9. The method of claim 1 wherein the step e) comprises comparing the discharge pressure to a check value.
10. The method of claim 1 further comprising:
g) monitoring the sub-cooling of the refrigerant;
h) adjusting the speed of a condenser fan based on the monitoring of step g).
11. An air conditioning system for use in cooling a sleeper compartment of a truck, the system comprising:
a refrigerant flow path;
a variable speed compressor to pressurize a refrigerant in the refrigerant flow path;
a condenser in the refrigerant flow path downstream from the compressor;
an evaporator in the refrigerant flow path downstream from the condenser;
a variable speed blower configured to direct an air flow through the evaporator to cool the sleeper compartment;
a plurality of sensors to monitor the air temperature of the sleeper compartment, the temperature of the air flow out of the evaporator, the refrigerant discharge pressure of the compressor; and the super heat of the refrigerant in the refrigerant flow path; and
a controller connected to the sensors and the compressor and blower, the controller configured to selectively adjust the speed of the compressor and the blower based on signals received from the plurality of sensors.
12. The system of claim 11 wherein the controller is configured to adjust the speed of the compressor based on a signal indicating the air temperature of the sleeper compartment.
13. The system of claim 11 wherein the controller is configured to adjust the speed of the compressor based on a signal indicating the temperature of the air flow exiting the evaporator.
14. The system of claim 11 wherein the controller is configured to adjust the speed of the compressor based on a signal indicating the discharge pressure of the compressor.
15. The system of claim 11 wherein the controller is configured to adjust the speed of the compressor based on a signals indicating the air temperature of the sleeper compartment, the temperature of the air flow exiting the evaporator, and the discharge pressure of the compressor.
16. The system of claim 11 wherein the controller is configured to adjust the speed of the blower based on a signal that indicates the super heat of the refrigerant.
17. The system of claim 11 further comprising a variable speed condenser fan configured to direct an air flow through the condenser and wherein said controller is configured to adjust the speed of the fan based on a signal indicating the sub-cooling of the refrigerant.
18. A method of operating a vapor compression air conditioning system for a sleeper compartment of a truck, the air conditioning system including a variable speed compressor for pressurizing a refrigerant, a condenser, an evaporator, and a variable speed blower for directing an air flow through the evaporator, the method comprising the steps of:
a) adjusting the speed of the compressor based on the temperature of the air flow out of the evaporator and on the refrigerant discharge pressure out of the compressor; and
b) adjusting the speed of the blower based on the super heat the refrigerant.
19. The method of claim 18 wherein step a) further comprises adjusting the speed of the compressor based on the air temperature in the sleeper compartment.
20. The method of claim 18 further comprising the step of adjusting the speed of a variable speed condenser fan based on the sub-cooling of the refrigerant.
21. An air conditioning system for use in cooling a sleeper compartment of a truck, the system comprising:
a refrigerant flow path;
a variable speed compressor to pressurize a refrigerant in the refrigerant flow path;
a condenser in the refrigerant flow path downstream from the compressor;
an evaporator in the refrigerant flow path downstream from the condenser;
a variable speed blower configured to direct an air flow through the evaporator to cool the sleeper compartment; and
a controller configured to selectively adjust the speed of the compressor and the blower based on signals indicating the temperature of the air flow out of the evaporator, the refrigerant discharge pressure out of the compressor, and the super heat of the refrigerant.
22. The system of claim 21 further comprising a variable speed fan configured to direct an air flow through the condenser, and wherein the controller is configured to adjust the speed of the fan based on a signal indicating the sub-cooling of the refrigerant.
Priority Applications (5)
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US11/305,969 US20060112702A1 (en) | 2004-05-18 | 2005-12-19 | Energy efficient capacity control for an air conditioning system |
DE102006058165A DE102006058165A1 (en) | 2005-12-19 | 2006-12-09 | Method of operating air conditioning and air conditioning |
CNA2006101684530A CN1995847A (en) | 2005-12-19 | 2006-12-13 | Energy efficient capacity control for an air conditioning system |
JP2006340053A JP2007168775A (en) | 2005-12-19 | 2006-12-18 | Energy efficient capacity control for air conditioning system |
FR0655580A FR2894882A1 (en) | 2005-12-19 | 2006-12-18 | Operating method of air conditioning system involves adjusting compressor speed based on monitored air temperature, air flow temperature and refrigerant discharge pressure, and blower speed based on monitored refrigerant sub-cooling |
Applications Claiming Priority (3)
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US11/305,969 US20060112702A1 (en) | 2004-05-18 | 2005-12-19 | Energy efficient capacity control for an air conditioning system |
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US10076944B2 (en) * | 2016-01-29 | 2018-09-18 | Ford Global Technologies, Llc | Vehicle cabin air conditioning and battery cooling system |
US10486498B2 (en) * | 2016-02-23 | 2019-11-26 | Ford Global Technologies, Llc | Method and system for operating a heat pump of a vehicle |
CN111237988B (en) * | 2020-01-15 | 2021-05-28 | 北京天泽智云科技有限公司 | Control method and system for subway vehicle-mounted air conditioning unit |
CN111873751B (en) * | 2020-07-09 | 2021-10-08 | 徐州徐工矿业机械有限公司 | Mining dump truck and air volume adjustable ventilation cooling system and method thereof |
CN114393976B (en) * | 2022-02-24 | 2023-08-15 | 湖南行必达网联科技有限公司 | Intelligent air conditioning device for sleeper area, control method and automobile |
CN116213364B (en) * | 2023-05-11 | 2023-07-21 | 中国空气动力研究与发展中心设备设计与测试技术研究所 | Automatic wet gas cleaning method and system for large low-temperature wind tunnel |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6622500B1 (en) * | 2002-05-08 | 2003-09-23 | Delphi Technologies, Inc. | Energy-efficient capacity control method for an air conditioning compressor |
US6889762B2 (en) * | 2002-04-29 | 2005-05-10 | Bergstrom, Inc. | Vehicle air conditioning and heating system providing engine on and engine off operation |
-
2005
- 2005-12-19 US US11/305,969 patent/US20060112702A1/en not_active Abandoned
-
2006
- 2006-12-09 DE DE102006058165A patent/DE102006058165A1/en not_active Withdrawn
- 2006-12-13 CN CNA2006101684530A patent/CN1995847A/en active Pending
- 2006-12-18 FR FR0655580A patent/FR2894882A1/en not_active Withdrawn
- 2006-12-18 JP JP2006340053A patent/JP2007168775A/en active Pending
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6889762B2 (en) * | 2002-04-29 | 2005-05-10 | Bergstrom, Inc. | Vehicle air conditioning and heating system providing engine on and engine off operation |
US20050161211A1 (en) * | 2002-04-29 | 2005-07-28 | Bergstrom, Inc. | Vehicle air conditioning and heating system providing engine on and engine off operation |
US6622500B1 (en) * | 2002-05-08 | 2003-09-23 | Delphi Technologies, Inc. | Energy-efficient capacity control method for an air conditioning compressor |
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US8191377B2 (en) * | 2005-09-21 | 2012-06-05 | Hitachi Appliances, Inc. | Heat source apparatus and method of starting the apparatus |
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US20070227168A1 (en) * | 2006-04-04 | 2007-10-04 | Simmons Bryan D | Variable capacity air conditioning system |
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US9341398B2 (en) * | 2007-02-28 | 2016-05-17 | Valeo Systemes Thermiques | Air conditioning system provided with an electronic expansion valve |
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US20110209485A1 (en) * | 2007-10-10 | 2011-09-01 | Alexander Lifson | Suction superheat conrol based on refrigerant condition at discharge |
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US8739564B2 (en) * | 2008-03-18 | 2014-06-03 | GM Global Technology Operations LLC | Controlling temperature of vehicle devices using a variable speed fan |
US20090243527A1 (en) * | 2008-03-26 | 2009-10-01 | Atsushi Kakiuchi | Integral type air conditioner |
US8159170B2 (en) * | 2008-03-26 | 2012-04-17 | Sharp Kabushiki Kaisha | Integral type air conditioner |
US20100107668A1 (en) * | 2008-11-06 | 2010-05-06 | Trane International Inc. | Control scheme for coordinating variable capacity components of a refrigerant system |
US7975495B2 (en) * | 2008-11-06 | 2011-07-12 | Trane International Inc. | Control scheme for coordinating variable capacity components of a refrigerant system |
US8838277B2 (en) | 2009-04-03 | 2014-09-16 | Carrier Corporation | Systems and methods involving heating and cooling system control |
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US20110030414A1 (en) * | 2009-08-07 | 2011-02-10 | Hobart Brothers Company | Air conditioning systems with oversped induction motors |
US10202023B2 (en) | 2009-10-27 | 2019-02-12 | Carrier Corporation | Hybrid refrigeration system for a mobile unit and method of operation |
US20120210735A1 (en) * | 2009-10-27 | 2012-08-23 | Carrier Corporation | Hybrid refrigeration system for a mobile unit and method of operation |
US9557100B2 (en) * | 2009-10-27 | 2017-01-31 | Carrier Corporation | Hybrid refrigeration system for a mobile unit and method of operation |
US20120198865A1 (en) * | 2011-02-07 | 2012-08-09 | GM Global Technology Operations LLC | Vehicle air conditioning control |
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US20140116642A1 (en) * | 2012-10-26 | 2014-05-01 | Grant Courtney | Battery-Operated Auxiliary Power Unit |
US10934895B2 (en) | 2013-03-04 | 2021-03-02 | Echogen Power Systems, Llc | Heat engine systems with high net power supercritical carbon dioxide circuits |
US9568209B2 (en) | 2013-04-30 | 2017-02-14 | Eaton Corporation | System and method for controlling output flow of parallel connected blowers |
US11293309B2 (en) | 2014-11-03 | 2022-04-05 | Echogen Power Systems, Llc | Active thrust management of a turbopump within a supercritical working fluid circuit in a heat engine system |
US10507707B2 (en) * | 2015-06-12 | 2019-12-17 | Ford Global Technologies, Llc | Controlling HVAC compressor speed in a vehicle |
US20160361975A1 (en) * | 2015-06-12 | 2016-12-15 | Ford Global Technologies, Llc | Controlling hvac compressor speed in a vehicle |
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Also Published As
Publication number | Publication date |
---|---|
JP2007168775A (en) | 2007-07-05 |
DE102006058165A1 (en) | 2007-07-05 |
FR2894882A1 (en) | 2007-06-22 |
CN1995847A (en) | 2007-07-11 |
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