US20050229615A1 - Air-conditioning control unit - Google Patents

Air-conditioning control unit Download PDF

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Publication number
US20050229615A1
US20050229615A1 US11/088,181 US8818105A US2005229615A1 US 20050229615 A1 US20050229615 A1 US 20050229615A1 US 8818105 A US8818105 A US 8818105A US 2005229615 A1 US2005229615 A1 US 2005229615A1
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United States
Prior art keywords
air
air passage
control unit
heat exchanger
temperature
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Abandoned
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US11/088,181
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English (en)
Inventor
Kojiro Nakamura
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Marelli Corp
Original Assignee
Calsonic Kansei Corp
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Assigned to CALSONIC KANSEI CORPORATION reassignment CALSONIC KANSEI CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: NAKAMURA, KOJIRO
Publication of US20050229615A1 publication Critical patent/US20050229615A1/en
Abandoned legal-status Critical Current

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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
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H1/00899—Controlling the flow of liquid in a heat pump system
    • B60H1/00921—Controlling the flow of liquid in a heat pump system where the flow direction of the refrigerant does not change and there is an extra subcondenser, e.g. in an air duct
    • 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
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00735—Control systems or circuits characterised by their input, i.e. by the detection, measurement or calculation of particular conditions, e.g. signal treatment, dynamic models
    • B60H1/00792—Arrangement of detectors
    • 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
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00821—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being ventilating, air admitting or air distributing devices
    • B60H1/00835—Damper doors, e.g. position control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
    • 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
    • F25B2600/25—Control of valves
    • F25B2600/2507—Flow-diverting valves
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part

Definitions

  • the present invention relates to an air-conditioning control unit used for an air conditioning system that performs heating operation using a refrigerant of a fuel car, electric car or the like as a heat source.
  • a Well-known conventional air conditioning system adjusts temperature of air in a cabin by mixing hot air from a heat exchanger of a radiator for an engine as a heat source and cold air from a cooler using refrigerant as disclosed in a patent brochure, Japanese Patent Application Laid-Open No. 2002-274147.
  • an air-conditioning control unit ( 26 ) used in a air conditioning system ( 1 ) which comprises: a refrigerant circuit ( 2 ); a first indoor heat exchanger ( 10 ) having a low refrigerant temperature; a second indoor heat exchanger ( 4 ) having a high refrigerant temperature; controlled components ( 5 , 12 ); a first air passage ( 21 ); and a second air passage ( 22 ) and a third air passage ( 23 ) which are distributed by an airflow distributing door ( 16 ) from the first air passage ( 21 ), wherein the air-conditioning control unit ( 26 ) controls the controlled components ( 5 , 12 ) and the airflow distributing door ( 16 ); wherein the first indoor heat exchanger ( 10 ) is provided in the first air passage ( 21 ); wherein the second indoor heat exchanger ( 4 ) is provided in the second air passage ( 22 ); wherein adjusting air sent from the first air passage ( 21 ) is
  • the airflow distributing door ( 16 ) when cooling operation is switched to heating operation, the airflow distributing door ( 16 ) is controlled so as to increase the quantity of adjusting air flowing into the second air passage ( 22 ) prior to switching of the refrigerant circuit from the cooling control mode to the heating control mode.
  • the temperature of the adjusting air can be detected more accurately by the air temperature sensor ( 25 ) provided at the downstream of the second indoor heat exchanger ( 4 ).
  • an air-conditioning control unit ( 26 ) wherein the airflow distributing door ( 16 ) is controlled so as to flow smaller quantity of adjusting air into the second air passage ( 22 ) than the air flowing into the third air passage ( 23 ) in the air flowing state during cooling.
  • the airflow distributing door ( 16 ) is controlled so that smaller quantity of adjusting air flows into the second air passage ( 22 ) than the air flowing into the third air passage ( 23 ) during cooling operation, rapid change in temperature of the adjusting air can be suppressed.
  • an air-conditioning control unit ( 26 ) wherein the airflow distributing door ( 16 ) is controlled so as to flow smaller quantity of adjusting air into the third air passage ( 23 ) than the air flowing into the second air passage ( 22 ) in the air flowing state during heating.
  • the airflow distributing door ( 16 ) is controlled so that smaller quantity of adjusting air flows into the third air passage ( 23 ) than the air flowing into the second air passage ( 22 ) during heating operation, rapid change in temperature of the adjusting air can be suppressed.
  • an air-conditioning control unit ( 26 ) wherein the second air passage ( 22 ) is connected to an air outlet on the lower side in the room and the third air passage ( 23 ) is connected to an air outlet on the upper side in the room.
  • the upper side in the room can be maintained at relatively low temperatures, improving comfortability during heating operation.
  • an air-conditioning control unit ( 26 ) wherein position of the airflow distributing door ( 16 ) is changed so as to decrease a difference between blowing temperature of the adjusting air and control target temperature.
  • the position of the airflow distributing door ( 16 ) is changed so as to decrease a difference between the blowing temperature of adjusting air and the control target temperature, rapid change in temperature of the adjusting air can be suppressed.
  • FIGS, 1 A and 1 B are views showing position of an airflow distribution door of an air conditioning system during cooling operation ( FIG. 1A ) and heating operation ( FIG. 1B ) in accordance with the embodiment of the present invention
  • FIG. 2 is a view showing an improved air conditioning system comprising an air-conditioning control unit in accordance with an embodiment of the present invention (cooling operation state).
  • FIG. 3 is a view showing an improved air conditioning system comprising an air-conditioning control unit in accordance with the embodiment of the present invention (heating operation state).
  • FIG. 4 is a flowchart showing an example of a control procedure of the air-conditioning control unit in accordance with the embodiment of the present invention.
  • FIG. 5 is a flowchart showing an example of a control procedure of the air-conditioning control unit in accordance with the embodiment of the present invention (continued from FIG. 4 ).
  • FIG. 6 is a flowchart showing an example of a control procedure of the air-conditioning control unit in accordance with the embodiment of the present invention (continued from FIGS. 4 and 5 ).
  • FIG. 7 is a view showing a control example of the airflow distribution door in accordance with the embodiment of the present invention in the cooling operation state.
  • FIG. 8 is a view showing a control example of the airflow distribution door in accordance with the embodiment of the present invention in the heating operation state.
  • FIGS. 1A and 1B show a first embodiment of the present invention.
  • the drawings show an arrangement of a first air passage 21 which are divided by a wall into a second air passage 22 and a third air passage 23 in a duct 20 .
  • a first indoor heat exchanger 10 in the first air passage 21
  • a second indoor heat exchanger 4 in the second air passage 22 .
  • a airflow distribution door 16 which is swungly controlled by an air-conditioning unit 26 according to the present invention.
  • control is carried out by using an air temperature sensor 24 which is located at the downstream end of the first indoor heat exchanger 10 .
  • cooling level is adjusted by controlling the number of revolutions of a compressor and basically, no air is flown to the side of the second indoor heat exchanger 4 . For this reason, high-temperature air may stagnate in the vicinity of the second indoor heat exchanger 4 during cooling operation.
  • another air temperature sensor 25 is located at the downstream end of the second indoor heat exchanger 4 .
  • heating operation mode (as shown in FIG. 1A ) is carried out right after cooling operation mode (as shown in FIG. 1B )
  • cooling operation mode (as shown in FIG. 1B ) since control is carried out based on the temperature detected by an air temperature sensor 25 immediately since switching from the cooling operation mode to the heating operation mode, it is wrongly determined that air in the second air passage is sufficiently heated although not sufficiently heated in fact. This may lead to inadequate control.
  • FIG. 2 to FIG. 8 A second embodiment of the air conditioning system 1 including the air-conditioning control unit 26 will be described hereinbelow with referring to the accompanying drawings, FIG. 2 to FIG. 8 .
  • the second embodiment is improved in such point described in the former paragraph.
  • FIGS. 2 and 3 show the air conditioning system 1 having the air-conditioning unit 26 according to the present invention. Especially, FIG. 2 shows the cooling operation mode and FIG. 3 shows the heating operation mode.
  • a compressor 3 the second indoor heat exchanger 4 , the outdoor heat exchanger 6 , an internal heat exchanger 8 , an expansion valve 9 , the first indoor heat exchanger 10 , an accumulator 11 and an internal heat exchanger 8 are connected to each other by piping in this order and a refrigerant circulates in the direction of arrows (first refrigerant cycle 2 c ).
  • the compressor 3 is disposed, for example, at the outside of the vehicle, compresses a sucked low-pressure refrigerant and discharges the compressed high-temperature and high-pressure refrigerant.
  • the compressor 3 is, for example, an electric compressor driven by electric power.
  • the outdoor heat exchanger 6 is disposed at the outside of the car and exposed to outside air by driving a blowing means (not shown) such as an electric fan.
  • the outdoor heat exchanger 6 radiates heat of the refrigerant to the outside air by exchanging heat between the high-temperature and high-pressure refrigerant passing theretrough and the outside air.
  • the expansion valve 9 reduces the pressure of the refrigerant, the heat of which is radiated in the outdoor beat exchanger 6 .
  • the first indoor heat exchanger 10 is disposed in the car and air is sent into the car through the first indoor heat exchanger 10 by driving a blowing means (not shown) such as a blower fan.
  • the first indoor heat exchanger 10 extracts heat from air flowing in the car and cools the air by exchanging heat between the low-temperature and low-pressure refrigerant and the blown air.
  • the internal heat exchanger 8 allows heat to be exchanged between the high-pressure refrigerant, the heat of which is radiated in the outdoor heat exchanger 6 , and the low-pressure refrigerant, the heat of which is absorbed in the first indoor heat exchanger 10 .
  • the accumulator 11 separates the refrigerant from the first indoor heat exchanger 10 into the liquid one and the gaseous one, sends only the gaseous refrigerant and stores the liquid refrigerant temporarily.
  • the compressor 3 , the second indoor heat exchanger 4 , the internal heat exchanger 8 , the expansion valve 15 , the outdoor heat exchanger 6 , the accumulator 11 and the internal heat exchanger 8 are connected to each other by piping in this order and the refrigerant circulates in the direction of arrows (second refrigerant cycle 2 h ).
  • the second indoor heat exchanger 4 is disposed in the car and air is sent into the car through the second indoor heat exchanger 4 by driving a blowing means (not shown) such as a blower fan.
  • the second indoor heat exchanger 4 heats the air flowing in the car and radiates heat of the refrigerant by exchanging heat between the high-temperature and high-pressure refrigerant passing therethrough and the blown air.
  • the expansion valve 15 reduces the pressure of the refrigerant, the heat of which is radiated in the second indoor heat exchanger 4 .
  • the outdoor heat exchanger 6 is disposed at the outside of the car and exposed to outside air by driving a blowing means (not shown) such as an electric fan.
  • the outdoor heat exchanger 6 allows the refrigerant to absorb heat by exchanging heat between the low-temperature and low-pressure refrigerant passing therethrough and the outside air.
  • Reference numeral 5 designates a three-way valve
  • reference numeral 12 designates a solenoid valve.
  • the three-way valve 5 and the solenoid valve 12 are collectively constituted as controlled component 5 , 12 which are controlled by the air-conditioning control unit 26 .
  • Reference numerals 7 , 13 and 14 designate a check valve.
  • An air-conditioning control unit 26 consisting of a microcomputer controls the expansion valves 9 , 15 , the three-way valve 5 , the solenoid valve 12 , (a drive mechanism of) an airflow distribution door 16 and other equipment based on detected values of various sensors (an air temperature sensor 24 and the like) or input information of an operational panel (not shown) and the like.
  • the three-way valve 5 and the solenoid valve 12 are controlled components relating to the switching of the refrigerant cycles.
  • the air cooled in the first indoor heat exchanger 10 is distributed into a second air passage 22 passing through the second indoor heat exchanger 4 and another third air passage 23 bypassing the second indoor heat exchanger 4 at an appropriate ratio by the airflow distribution door 16 .
  • the airflow distribution door 16 is controlled so as to positioned to block the second air passage 22 in the cooling operation state (hereinafter referred to as F/COOL) ( FIG. 2 ) and to block the third air passage 23 in the heating operation state (hereinafter referred to as F/HOT) ( FIG. 3 ).
  • the air passing through the second air passage 22 and the air passing through the third air passage 23 are mixed in an air mix chamber (not shown) and blown out from an air outlet (not shown) toward the inside of the car.
  • FIGS. 4 to 6 are flowcharts of the control procedures
  • FIG. 7 is a view showing an air passage running certain quantity of regulating air at the side of the second air passage in the cooling operation state
  • FIG. 8 is a view showing an air passage running certain quantity of regulating air at the side of the third air passage in the heating operation state.
  • the airflow distribution door 16 is referred to as A/MIX.
  • the air-conditioning control unit 26 determines whether or not a time interval Ti has passed after previous control.
  • the procedure of determining a control target position of the airflow distribution door 16 is carried out and when Ti has not passed, the procedure of controlling the airflow distribution door 16 at the control target position is carried out ( FIG. 6 ).
  • this Ti is determined depending on rate of change of room air temperature. It is set to be six seconds, for example.
  • the air-conditioning control unit 26 carries out procedures of changing the control target position of the airflow distribution door 16 depending on an air outlet mode, position of the airflow distribution door 16 and a difference between a blowing temperature and a control target temperature (steps S 12 to S 19 ; FIG. 4 ).
  • the air-conditioning control unit 26 carries out procedures of changing the control target position of the airflow distribution door 16 depending on the number of revolutions of the compressor 3 , position of the airflow distribution door 16 and a difference between a blowing temperature and a control target temperature (steps S 21 to S 29 ; FIG. 5 ).
  • the air-conditioning control unit 26 carries out procedures of driving and controlling the airflow distribution door 16 at the control target position (steps S 30 to S 32 ; FIG. 6 ).
  • the air outlet mode is set at bi-level (described as B/L in the figure).
  • the bi-level is the state where the third air passage 23 is connected to the air outlet on the upper side in the room and the second air passage 22 is the air outlet on the lower side in the room.
  • the target position of the airflow distribution door 16 is set at F/HOT (see FIG. 3 ) (step S 13 ).
  • a step S 14 it is determined whether or not the airflow distribution door 16 is located closer to the F/COOL side than a second specified position (see FIG. 2 ).
  • the control target position is defined as the second specified position.
  • the second specified position is a position at which small quantity of adjusting air is distributed into the third air passage 23 .
  • the airflow distribution door 16 is located at the second specified position, smaller quantity of adjusting air flows into the third air passage 23 than the air-flowing into the second air passage 22 .
  • the airflow distribution door 16 is located at the second specified position in the state where the air outlet mode is set at bi-level. This leads to an advantage of improving comfortability since cool air is blown to the upper side in the room and heat air is blown to the lower side in the room.
  • step S 14 When the airflow distribution door 16 is not located closer to the F/COOL side than the second specified position at a step S 14 , an absolute value of temperature difference between the blowing temperature and the control target temperature is compared with a predetermined threshold value and it is determined whether or not the blowing temperature is much lower than the control target temperature at a step S 16 . Subsequently, when the blowing temperature is much lower than the control target temperature, the control target position of the airflow distribution door 16 is shifted toward the F/HOT side (step S 17 ).
  • step S 18 an absolute value of temperature difference between the blowing temperature and the control target temperature is compared with a predetermined threshold value and it is determined whether or not the blowing temperature is much higher than the control target temperature at a step S 18 . Subsequently, when the blowing temperature is much higher than the control target temperature, the control target position of the airflow distribution door 16 is shifted toward the F/COOL side (step S 19 ).
  • the shift of the control target position in the steps S 17 and S 19 is performed in increments of a predetermined relatively minute angle (for example, an angle obtained by dividing an angle between the F/COOL and F/HOT positions by 125).
  • Such control has an advantage of suppressing rapid change in temperature of the adjusting air. As described herein, in terms of heating efficiency, it is advantageous that control is carried out so as to reduce the temperature difference only when the temperature difference between the blowing temperature and the control target temperature is large.
  • the cooling control mode at a step S 21 , it is determined whether or not the number of revolutions of the compressor 3 equals a threshold number of revolutions Nth or more.
  • the threshold number of revolutions Nth is set to be close to the minimum number of revolutions of the compressor 3 in the state where heating operation is switched to cooling operation and vice versa. For example, when the number of revolutions of the compressor 3 ranges from 30 Hz to 120 Hz, Nth is set to be 40 Hz. By doing so, it is possible to know switching from the cooling control mode to the heating control mode in advance.
  • the target position of the airflow distribution door 16 is set at F/COOL (see FIG. 2 ) (step S 22 ).
  • step S 25 when the number of revolutions of the compressor 3 is lower than Nth, it is determined whether or not the airflow distribution door 16 is located closer to the F/COOL side than a first specified position. Then, when the airflow distribution door 16 is located closer to the F/COOL side than the first specified position, the control target position is defined as the first specified position (step S 25 ).
  • the first specified position is a position at which small quantity of adjusting air is distributed into the second air passage 22 .
  • the airflow distribution door 16 When the airflow distribution door 16 is located at the first specified position, smaller quantity of adjusting air flows into the second air passage 22 than the air flowing into the third air passage 23 . In this state, since both of warm air and cool air are blown into the room, such control is effective especially when rapid change in temperature of the adjusting air is undesirable, for example, at switching from heating to cooling.
  • step S 24 When the airflow distribution door 16 is not located closer to the F/COOL side than the first specified position at a step S 24 , an absolute value of temperature difference between the blowing temperature and the control target temperature is compared with a predetermined threshold value and it is determined whether or not the blowing temperature is much lower than the control target temperature at a step S 26 . Subsequently, when the blowing temperature is much lower than the control target temperature, the control target position of the airflow distribution door 16 is shifted toward the F/HOT side (step S 27 ).
  • a step S 28 for example, an absolute value of temperature difference between the blowing temperature and the control target temperature is compared with a predetermined threshold value and it is determined whether or not the blowing temperature is much higher than the control target temperature.
  • the control target position of the airflow distribution door 16 is shifted toward the F/COOL side (step S 29 ).
  • the shift of the control target position in the steps S 27 and S 29 is performed in increments of the above-mentioned angle.
  • Such control has an advantage of suppressing rapid change in temperature of the adjusting air.
  • it is especially advantageous that control is carried out so as to reduce the temperature difference only when the temperature difference between the blowing temperature and the control target temperature is large.
  • the air-conditioning control unit 26 caries out a procedure as shown in FIG. 6 to move the airflow distribution door 16 to the control target position thus determined.
  • the air-conditioning control unit 26 determines whether or not a time interval T 0 has passed since previous positional control. When T 0 has passed, the position of the airflow distribution door 16 is controlled and when T 0 has not passed, this control is finished. This prevents the airflow distribution door 16 from moving frequently, thereby suppressing uncomfortable feeling due to the frequent operation noise.
  • T 0 is set to be one second, for example.
  • a difference between the control target position and the current position of the airflow distribution door 16 is acquired.
  • the airflow distribution door 16 is shifted toward the determined control target position at a step S 32 (DRIVE A/MIX). At this time, it is preferred that the airflow distribution door 16 is driven in increments of the above-mentioned angle.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air-Conditioning For Vehicles (AREA)
US11/088,181 2004-03-31 2005-03-24 Air-conditioning control unit Abandoned US20050229615A1 (en)

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JP2004104820A JP2005289152A (ja) 2004-03-31 2004-03-31 空調制御装置
JP2004-104820 2004-03-31

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WO2022193109A1 (en) * 2021-03-16 2022-09-22 Honeywell International Inc. Automatic changeover control of a fan coil unit of a building
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JP2019060580A (ja) * 2017-09-28 2019-04-18 株式会社デンソー 冷凍サイクル装置
WO2020063678A1 (zh) * 2018-09-25 2020-04-02 杭州三花研究院有限公司 空调***及其控制方法

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