CN1991276A - Air adjustor - Google Patents
Air adjustor Download PDFInfo
- Publication number
- CN1991276A CN1991276A CNA2006101725028A CN200610172502A CN1991276A CN 1991276 A CN1991276 A CN 1991276A CN A2006101725028 A CNA2006101725028 A CN A2006101725028A CN 200610172502 A CN200610172502 A CN 200610172502A CN 1991276 A CN1991276 A CN 1991276A
- Authority
- CN
- China
- Prior art keywords
- indoor
- heat converter
- valve
- mentioned
- expansion valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- 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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- 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
- F24F11/50—Control or safety arrangements characterised by user interfaces or communication
- F24F11/52—Indication arrangements, e.g. displays
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F3/153—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification with subsequent heating, i.e. with the air, given the required humidity in the central station, passing a heating element to achieve the required temperature
-
- 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
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F2003/144—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by dehumidification only
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2110/00—Control inputs relating to air properties
- F24F2110/20—Humidity
-
- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
- F25B2313/0232—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with bypasses
- F25B2313/02321—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with bypasses during cooling
-
- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
- F25B2313/0234—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements
- F25B2313/02343—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements during dehumidification
-
- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
-
- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0314—Temperature sensors near the indoor heat exchanger
-
- 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
- F25B2600/2513—Expansion 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/02—Humidity
-
- 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
-
- 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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Human Computer Interaction (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Air Conditioning Control Device (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention provides an air conditioner 1 which has an outdoor unit 2 and an indoor unit 3 for forming refrigeration circulation. The outdoor unit 2 has a liquid storage means 7, a compressor 8, a four-way valve 6, an outdoor heat exchanger 9 and an outdoor expansion valve 10 which are arranged on the tubing for the refrigerant circulation; the outdoor unit 3 has a first outdoor heat exchanger 15, a check valve 16, an indoor expansion valve 17, a second indoor heat exchanger 18 and an indoor electromagnetic valve 20 which is arranged on the tubing 19 which rounds the first indoor heat exchanger 15 and the check valve 16, wherein, a controlling device can lower the temperature of the refrigerant of exhaust side of the compressor 8 to the predetermined value according to the signal of the electromagnetic valve 20 turnoff during the reheating- dehumidifying operation. In addition, another control device can regulate the jaw opening of the indoor expansion valve 17 during the reheating- dehumidifying operation, and can regulate the jaw opening of the outdoor expansion valve 10 during the refrigerant operation.
Description
Technical field
The present invention relates to air regulator, particularly relate to the air regulator that has again hot dehumidification function.
Background technology
Air regulator connects off-premises station and indoor set by pipe arrangement, and forms freeze cycle by refrigerant is circulated, and described off-premises station has compressor, outdoor heat converter etc., and described indoor set has indoor expansion valve, indoor heat converter etc.As such air regulator, known have a so-called air regulator that has again hot dehumidification function, this air regulator will be heated near indoor temperature once more, send to indoor then by the air of cooling and dehumidifying in indoor heat converter in the refrigeration plant operation mode.Hot again dehumidification function is to realize by in the indoor set of the upstream side of indoor expansion valve reheater being set.That is owing to make outdoor heat converter and reheater carry out work as condenser respectively, therefore utilize reheater by heat exchange will be in indoor heat converter the air of cooling and dehumidifying be heated to again near the indoor temperature.And, walk around the pipe arrangement of reheater and the indoor electric magnet valve of switching pipe arrangement by setting, switch heat dehumidifying running again and do not follow the cooling operation of hot dehumidifying again.That is, during magnetic valve, reheater is as the part effect of condenser in close chamber, and institute thinks heat dehumidifying running again; And when opening the indoor electric magnet valve, owing to walk around reheater, so be in the cooling operation of not following again hot dehumidification function.
By carrying out the such dehumidifying of heat again running, can prevent cold dehumidifying, but be in highly when removing humidity load that the cooling capacity of indoor heat converter will rise sometimes, the heating efficiency again of reheater is insufficient indoor.
In patent documentation 1, put down in writing and be provided with the pipe arrangement (bypass pipe arrangement) of walking around outdoor heat converter and the adjustment valve of adjusting the coolant quantity that flows through the bypass pipe arrangement.In view of the above,, the flow that can adjust and walk around outdoor heat converter, keeps the refrigerant of high specific enthalpy, refrigerant is circulated to reheater, therefore, can adjust the power of heat energy again of reheater, carry out the adjustment of superfine humidity and temperature in when running heat dehumidifying again.
But, patent documentation 1 described technology, need walk around outdoor heat converter pipe arrangement, adjust the adjustment valve of the coolant quantity flow through the bypass pipe arrangement etc., it is complicated that refrigerant circulation road becomes.And, in the structure of the air regulator in the past that has again hot dehumidification function, when not following again the cooling operation of hot dehumidification function, owing to liquid coolant accumulates in the reheater, so the required coolant quantity of freeze cycle increases.Corresponding, if increase the coolant quantity of supplying with to freeze cycle, then when the less heating running of required coolant quantity etc., will produce the residue refrigerant, the compressor injury that hydraulic pressure contracts etc. in the time of will causing starting sometimes, reduction reliability.
Summary of the invention
The objective of the invention is the power of heat energy again by simple structure control reheater.
Other purposes of the present invention are necessary coolant quantity, the raising reliabilities when suppressing cooling operation.
In order to achieve the above object, air regulator of the present invention, off-premises station and indoor set are set on the pipe arrangement that makes the refrigerant circulation and form freeze cycle, described off-premises station has reservoir (ア キ ユ system レ one ), compressor, cross valve and outdoor heat converter; Described indoor set has first indoor heat converter, check-valves, indoor expansion valve, second indoor heat converter and is arranged on indoor electric magnet valve on the pipe arrangement of walking around first indoor heat converter and check-valves, it is characterized in that, be provided with control device, this control device is in when running heat dehumidifying again, makes the refrigerant temperature of the discharge side of compressor be reduced to design temperature according to the signal of indoor closed electromagnetic valve.
That is, if reduce the refrigerant temperature of the discharge side of compressor, then according to mollier diagram as can be known, the refrigerant of the wet condition that the ratio of liquid coolant is big will circulate to reservoir.Thus, accumulate liquid coolant in reservoir, the coolant quantity that circulates in outdoor heat converter reduces, so outdoor heat converter is in the state of cold medium shortage.Thus, the refrigerant of the outlet of outdoor heat converter is in the state of gas-liquid two-phase, increases as the enthalpy difference in first indoor heat converter of reheater, so can improve the power of heat energy again of reheater.That is, can be by the simple structure of the pipe arrangement (bypass pipe arrangement) of walking around outdoor heat converter and the adjustment valve of adjusting the coolant quantity that flows through the bypass pipe arrangement etc., the power of heat energy again of control reheater are not set.
In addition, the control device that the aperture that strengthens indoor expansion valve also can be set replaces being provided with the control device that the discharge side refrigerant temperature that makes compressor is reduced to design temperature, solves above-mentioned problem with this.
That is, by strengthening the aperture of indoor expansion valve, can reduce the decompression amount of the refrigerant in the indoor expansion valve, so become high pressure as the evaporating pressure in second indoor heat converter of evaporimeter, evaporating temperature uprises.Thus, the heat that exchanges in second heat exchanger reduces, and becomes the refrigerant of the ratio wet condition how of liquid coolant to the refrigerant of reservoir circulation.Its result, accumulates liquid coolant at ground same as described above in reservoir, outdoor heat converter is in the state of cold medium shortage.Thus, the refrigerant of the outlet of outdoor heat converter is in the state of gas-liquid two-phase, increases as the enthalpy difference in first indoor heat converter of reheater, so can improve the power of heat energy again of reheater.That is, can be by the simple structure of the pipe arrangement (bypass pipe arrangement) of walking around outdoor heat converter and the adjustment valve of adjusting the coolant quantity that flows through the bypass pipe arrangement etc., the power of heat energy again of control reheater are not set.
In addition, air regulator also can be following structure, that is, off-premises station and indoor set are set on the pipe arrangement of refrigerant circulation and form freeze cycle making, and described off-premises station has reservoir, compressor, cross valve, outdoor heat converter and outdoor expansion valve; Described indoor set has first indoor heat converter, check-valves, indoor expansion valve, second indoor heat converter and is arranged on indoor electric magnet valve on the pipe arrangement of walking around first indoor heat converter and check-valves, wherein, be provided with control device, this control device is in when running heat dehumidifying again, according to the aperture of the indoor expansion valve of signal controlling of indoor closed electromagnetic valve; When cooling operation, the aperture of the outdoor expansion valve of opening according to the indoor electric magnet valve of signal controlling.
In view of the above, when the indoor electric magnet valve was opened, first indoor heat converter was bypassed, and be in not follow the cooling operation of heat dehumidifying again, but the part of refrigerant also circulated to the first indoor heat converter side.So, be arranged on by control first indoor heat converter upstream side outdoor expansion valve aperture, refrigerant is reduced pressure, the part of refrigerant that is in the gas-liquid two-phase state of low pressure will circulate to first indoor heat converter.That is, by forming such structure, first indoor heat converter is not as reheater, but as the evaporimeter effect, therefore, the delay of liquid coolant can not take place.Therefore, the necessary coolant quantity in the time of can controlling cooling operation, raising reliability.
According to the present invention, can be by the power of heat energy again of simple structure control reheater, and the necessary coolant quantity can suppress cooling operation the time, improve reliability.
Description of drawings
Fig. 1 is the figure of structure of the air regulator of expression present embodiment.
Fig. 2 is the figure of structure of the reservoir of expression present embodiment.
Fig. 3 be the expression present embodiment reservoir service performance figure.
Fig. 4 is the figure that the freeze cycle of the dehumidifying of the heat again running under the situation of compressor effluent air temp is similarly set in expression when the cooling operation.
Fig. 5 is the figure that the compressor effluent air temp is set at the freeze cycle of the dehumidifying of the heat again running under the situation when being lower than cooling operation
Fig. 6 is the figure of notion of the setting value of expression compressor effluent air temp.
The specific embodiment
Use Fig. 1～Fig. 6 that the embodiment that is suitable for air regulator of the present invention is described below.
Fig. 1 is the figure of structure of the air regulator of expression present embodiment.As shown in Figure 1, air regulator 1 has the gas side connecting pipings 4 and the hydraulic fluid side connecting pipings 5 of off-premises station 2, indoor set 3, ring-type connection off-premises station 2 and indoor set 3.
Off-premises station 2 is by forming with the pipe arrangement connection cross valve 6, reservoir 7, compressor 8, outdoor heat converter 9, the outdoor expansion valve 10 that make the refrigerant circulation.In addition,, be provided with compressor effluent air temp sensor 11 and high-pressure sensor 12, in outdoor heat converter 9, be provided with the outdoor draft fan 13 that outdoor air is blowed to outdoor heat converter 9 in the discharge side of compressor 8.
Below, use Fig. 2, Fig. 3 that the structure of reservoir 7 is elaborated.Fig. 2 is the figure of the structure of expression reservoir 7.Reservoir 7 has container 30, is arranged on ingress pipe 31 and U type pipe 32 in the container 30.On U type pipe 32, be provided with spill port 33 in the bottom, be provided with balancing orifice 34 on top.
If make the freeze cycle circulation, refrigerant and lubricating oil are returned in the container 30 by ingress pipe 31 from cross valve 6, the lubricating oil that then is dissolved in the refrigerant will temporarily accumulate in the bottom of container 30.U type pipe 32 flows out the gas coolant on top, simultaneously, from spill port 33 suck bottoms lubricating oil, make it turn back to the suction side of compressor 8.Fig. 3 is the figure of an example of the service performance of expression reservoir 7.As shown in Figure 3, according to the height H L of refrigerant circulation and liquid level, the aridity of returning the refrigerant of compressor suction side changes.That is, under the low situation of the aridity of the refrigerant of the inlet of reservoir 7, the liquid coolants that accumulate in the reservoir 7 become many, and on the contrary, under the high situation of aridity, the liquid coolant that accumulates in the reservoir 7 tails off.Like this, accumulate in coolant quantity in the reservoir 7 according to the refrigerant state decision of the inlet of reservoir 7.
Below, the running action when cooling operation is described.When cooling operation, shown in the solid line of Fig. 1, switch cross valve 6 like that, connect discharge side and outdoor heat converter 9, reservoir 7 and the gas side connecting pipings 4 of compressor 8.Thus, the pressurized gas refrigerant from compressor 8 is discharged carries out heat exchange and condensation with outdoor air by cross valve 6 in outdoor heat converter 9.In outdoor expansion valve 10, reduce pressure, be in the refrigerant of low-pressure gas-liquid two-phase, be transported to indoor set 3 by hydraulic fluid side connecting pipings 5.In indoor set 3, by indoor expansion valve 17 inflows second indoor heat converter 18 of open indoor electric magnet valve 20 and standard-sized sheet.The refrigerant that in second indoor heat converter 18 room air is carried out cooling and dehumidifying and evaporate turns back to off-premises station 2 once more by gas side connecting pipings 4, and is inhaled into compressor 8 via cross valve 6 from reservoir 7, finishes a circulation.
At this, though the part of refrigerant flows into first indoor heat converter 15,, owing to decompression in outdoor expansion valve 10 is in low-pressure state, so first indoor heat converter is as the evaporimeter effect.Thus, owing to refrigerant gasifies, the delay of liquid coolant do not take place, so can cut down the refrigerant enclosed volume.Its result, because the liquid refluence when compressor start does not take place etc., so can improve reliability.
Below, the action when heat dehumidifying running again is described.In when running heat dehumidifying again, that cross valve 6 is identical towards switching to cooling operation the time.The pressurized gas refrigerant of discharging from compressor 8 in the same manner during thus, with refrigeration carries out heat exchange and condensation with outdoor air by cross valve 6 outdoor heat converter 9.Because outdoor expansion valve 10 is in full-gear, so refrigerant is carried to indoor set 3 with reducing pressure hardly.In indoor set 3, owing to indoor electric magnet valve 20 is closed, so refrigerant flows into first indoor heat converter 15.The refrigerant of circulation in first indoor heat converter 15 carries out heat exchange and cools off with the room air of cooling in second indoor heat converter 18.That is, first indoor heat converter 15 is as the reheater effect of heating room air.Condensation or overcooled refrigerant in first indoor heat converter 15, decompression flows into second indoor heat converter 18 then in indoor expansion valve 17.The refrigerant of circulation is carrying out being heated after the heat exchange with room air in second indoor heat converter 18.That is, second indoor heat converter 18 is as the cooler effect that room air is cooled off, dehumidifies.By room air and heated refrigerant, evaporation is also returned off-premises station 2 via gas side connecting pipings 4 in second indoor heat converter 18.In off-premises station 2, refrigerant returns the suction side pipe arrangement of compressor 8 from cross valve 6 via reservoir 7, finish a circulation.
At this, the operating condition of the mollier diagram that uses Fig. 4 and Fig. 5 during to heat dehumidifying running again is elaborated.Fig. 4 is the figure that the freeze cycle of the dehumidifying of the heat again running under the situation of compressor effluent air temp is similarly set in expression when the cooling operation.At this, the aperture of expansion valve 17 in the control room is about 0.95 so that make the aridity of reservoir.The compressor effluent air temp of this moment is controlled as shown in Figure 6.Promptly, aperture by indoor expansion valve 17 is controlled, so that make the temperature that detects by compressor effluent air temp sensor 11, condensation temperature with respect to the discharge gas pressure that detects by high-pressure sensor 12 only exceeds uniform temperature, and the target effluent air temp is represented by following formula.
Several 1 formulas
Tdo＝Tc(Pd)+SHa
Target effluent air temp when Tdo is common, Tc is a condensation temperature, and Pd discharges gas pressure, and SHa discharges the gas superheat degree usually.
At this, discharge gas superheat degree Sha usually and be set in usually about 25～40 ℃.In addition, target effluent air temp Tdo is in order to ensure the reliability of compressor, as shown in the formula such capping Tdomax and lower limit Tdomin in the time of usually.
Several 2 formulas
Tdomin＜Tdo＜Tdomax
The aperture of expansion valve 17 in the control room, so that the aridity of reservoir 7 is reached about 0.95, so, as shown in Figure 3, can not turn round, therefore, can supply with necessary coolant quantity to outdoor heat converter 9 as condenser on reservoir 7 inner product liquid storage body refrigerant ground.Therefore, be in the liquid coolant state of total condensation in the outlet of outdoor heat converter 9.Thus, shown in the mollier diagram of Fig. 4, diminish as the enthalpy difference in first indoor heat converter 15 of reheater, heat energy power diminishes again.
Relative therewith, the freeze cycle of the dehumidifying of the heat again running shown in the mollier diagram of Fig. 5 is that effluent air temp is set at the operating condition that is lower than under the common situation.As shown in Figure 6, target discharge gas setting temperature is represented by following formula.
Several 3 formulas
Tdor＝Tc(Pd)+SHb
Target effluent air temp when Tdor is heat dehumidifying running again, Tc is a condensation temperature, Pd discharges gas pressure, the discharge gas superheat degree when SHb is heat dehumidifying running again.
In addition, with above-mentioned same, target effluent air temp Tdo was in order to ensure the reliability of compressor, as shown in the formula such capping Tdomax and lower limit Tdomin when the heat dehumidifying was turned round again.
Several 4 formulas
Tdomin＜Tdor＜Tdomax
At this, the discharge gas superheat degree SHb when the heat dehumidifying is turned round again is set at lower than common discharge gas superheat degree Sha, for example is set at about 15～25 ℃.In addition, the pressure loss in the Δ PL analog representation hydraulic fluid side connecting pipings 5 of Fig. 4, Fig. 5.
By such lowland control effluent air temp, the refrigerant of wet condition returns reservoir 7, so according to the characteristic of reservoir shown in Figure 37, liquid coolant accumulates in the reservoir 7.Thus, because outdoor heat converter 9 is in the state of cold medium shortage, so the refrigerant of the outlet side of outdoor heat converter 9 is in the gas-liquid two-phase state, as shown in Figure 5, the enthalpy difference in the reheater increases, heat increases again.Thus, when suppressing cooling capacity, can bring into play high dehumidifying effect, even reduce the low humidity of room temperature in the high lowland only of also can realizing when removing humidity load.
In addition, the control desired value of effluent air temp is changed.According to this control method, for example, the difference in air temperature that sucks and blow out can be controlled to be necessarily, can control necessary amount of cooling water, can carry out more high-precision room temperature, humidity control.
In addition, the control desired value of effluent air temp is changed.For example, significantly be higher than when setting humidity or comfortable humidity near design temperature, indoor humidity in room temperature, than lowland control effluent air temp, so that the difference in air temperature that sucks and blow out is diminished.According to this control method, indoor temperature and humidity can be controlled at comfortable humidity range.
In Fig. 1 of structure of the air regulator of expression present embodiment, be arranged on the check-valves 16 in the indoor set 3, be used to prevent that refrigerant is low to 15 inflows of first indoor heat converter and inhibition ability when heating is turned round, but it also can replace the fluid obstacle device of magnetic valve, capillary etc.In addition, when heating is turned round, make indoor expansion valve 17 be in full-gear, implement depressurization, can reduce the circulating resistance of indoor electric magnet valve 20, in this case, also can omit the circulation hinder device of check-valves 16 grades with this by outdoor expansion valve 10.
Claims (3)
1. air regulator is provided with off-premises station and indoor set and forms freeze cycle on the pipe arrangement that makes the refrigerant circulation, described off-premises station has reservoir, compressor, cross valve and outdoor heat converter; Described indoor set has first indoor heat converter, check-valves, indoor expansion valve, second indoor heat converter and is arranged on indoor electric magnet valve on the pipe arrangement of walking around above-mentioned first indoor heat converter and above-mentioned check-valves, it is characterized in that,
Be provided with control device, this control device is in when running heat dehumidifying again, makes the above-mentioned refrigerant temperature of the discharge side of above-mentioned compressor be reduced to design temperature according to the signal of above-mentioned indoor closed electromagnetic valve.
2. air regulator is provided with off-premises station and indoor set and forms freeze cycle on the pipe arrangement that makes the refrigerant circulation, described off-premises station has reservoir, compressor, cross valve and outdoor heat converter; Described indoor set has first indoor heat converter, check-valves, indoor expansion valve, second indoor heat converter and is arranged on indoor electric magnet valve on the pipe arrangement of walking around above-mentioned first indoor heat converter and above-mentioned check-valves, it is characterized in that,
Be provided with control device, this control device is in when running heat dehumidifying again, makes the aperture of above-mentioned indoor expansion valve greater than setting aperture according to the signal of above-mentioned indoor closed electromagnetic valve.
3. air regulator is provided with off-premises station and indoor set and forms freeze cycle on the pipe arrangement that makes the refrigerant circulation, described off-premises station has reservoir, compressor, cross valve, outdoor heat converter and outdoor expansion valve; Described indoor set has first indoor heat converter, check-valves, indoor expansion valve, second indoor heat converter and is arranged on indoor electric magnet valve on the pipe arrangement of walking around above-mentioned first indoor heat converter and above-mentioned check-valves, it is characterized in that,
Be provided with control device, this control device is in when running heat dehumidifying again, according to the aperture of the above-mentioned indoor expansion valve of signal controlling of above-mentioned indoor closed electromagnetic valve; When cooling operation, the aperture of the above-mentioned outdoor expansion valve of opening according to above-mentioned indoor electric magnet valve of signal controlling.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005371785 | 2005-12-26 | ||
| JP2005371785A JP4730738B2 (en) | 2005-12-26 | 2005-12-26 | Air conditioner |
| JP2005-371785 | 2005-12-26 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1991276A true CN1991276A (en) | 2007-07-04 |
| CN1991276B CN1991276B (en) | 2010-09-08 |
Family
ID=37846368
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2006101725028A Expired - Fee Related CN1991276B (en) | 2005-12-26 | 2006-12-26 | Air adjustor |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP1801520B1 (en) |
| JP (1) | JP4730738B2 (en) |
| CN (1) | CN1991276B (en) |
| DE (1) | DE602006010312D1 (en) |
| ES (1) | ES2335302T3 (en) |
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102927715A (en) * | 2012-10-31 | 2013-02-13 | 青岛海信日立空调系统有限公司 | Multiple-on-line heat pump air-conditioning system and method for controlling multiple-on-line heat pump air-conditioning system |
| CN103017410A (en) * | 2013-01-22 | 2013-04-03 | 北京德能恒信科技有限公司 | Heating-cooling type heat pipe and heat pump combined circulating system |
| CN104583684A (en) * | 2012-10-15 | 2015-04-29 | 日立空调·家用电器株式会社 | Air conditioner |
| CN105115181A (en) * | 2015-07-21 | 2015-12-02 | 上海日立电器有限公司 | Air conditioning system |
| CN106885387A (en) * | 2015-12-16 | 2017-06-23 | 上海日立电器有限公司 | A kind of air-conditioning system |
| CN106885402A (en) * | 2015-12-16 | 2017-06-23 | 上海日立电器有限公司 | Sensible heat latent heat separates the air-conditioning system of control |
| CN106885388A (en) * | 2015-12-16 | 2017-06-23 | 上海日立电器有限公司 | A kind of air-conditioning system |
| CN106885403A (en) * | 2015-12-16 | 2017-06-23 | 上海日立电器有限公司 | Sensible heat latent heat separates the air-conditioning system of control |
| CN107076434A (en) * | 2014-08-11 | 2017-08-18 | 黄利华 | Water cooling SPLIT AIR-CONDITIONING SYSTEM |
| CN109855184A (en) * | 2019-01-23 | 2019-06-07 | 青岛海尔空调器有限总公司 | Air conditioner and its dehumidification control method |
| CN110207330A (en) * | 2019-06-04 | 2019-09-06 | 广东美的暖通设备有限公司 | Air conditioner and its control method and device |
| CN112771320A (en) * | 2018-09-25 | 2021-05-07 | 东芝开利株式会社 | Air conditioner |
| CN112797657A (en) * | 2019-10-28 | 2021-05-14 | 广东美的制冷设备有限公司 | Air conditioner and control method thereof |
| CN114046612A (en) * | 2021-11-02 | 2022-02-15 | 南京天加环境科技有限公司 | Air conditioner/floor heating/ground cooling multi-connected system with double evaporation temperatures |
| CN114263991A (en) * | 2021-12-03 | 2022-04-01 | 雅凯热能技术(江苏)有限公司 | Fresh air dehumidification system |
| CN114761107A (en) * | 2019-12-12 | 2022-07-15 | 三菱电机株式会社 | Dehumidifying device |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011048724A1 (en) * | 2009-10-22 | 2011-04-28 | ダイキン工業株式会社 | Flow path switching valve, and air conditioner provided therewith |
| CN102645056A (en) * | 2011-02-16 | 2012-08-22 | 广东美芝制冷设备有限公司 | Refrigerating device for flammable refrigerant |
| JP5370551B1 (en) * | 2012-07-31 | 2013-12-18 | ダイキン工業株式会社 | Container refrigeration equipment |
| CN105987430A (en) * | 2015-02-05 | 2016-10-05 | 佛山市禾才科技服务有限公司 | Household air conditioner and anti-condensation method thereof |
| GB2537105A (en) * | 2015-03-30 | 2016-10-12 | Mcgowan Gregory | Air conditioning system |
| US10345003B2 (en) * | 2016-05-02 | 2019-07-09 | Lee Wa Wong | Split-type air conditioning and heat pump system with energy efficient arrangement |
| NL2025130B1 (en) | 2020-03-13 | 2021-10-19 | Air Supplies Holland B V | Climate control unit and system comprising the same |
| JP7112787B1 (en) * | 2021-12-02 | 2022-08-04 | 株式会社Ｆｈアライアンス | air conditioning ventilation system |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB8721986D0 (en) * | 1987-09-18 | 1987-10-28 | Ici Plc | Pyridine derivative |
| JPH01106865U (en) * | 1988-01-12 | 1989-07-19 | ||
| JPH0618074A (en) * | 1992-07-01 | 1994-01-25 | Fujitsu General Ltd | Controlling method for air conditioner |
| JPH07294060A (en) * | 1994-04-28 | 1995-11-10 | Sanyo Electric Co Ltd | Air conditioner |
| JP3884591B2 (en) * | 1999-03-25 | 2007-02-21 | 三菱電機株式会社 | Air conditioner |
| JP2002107000A (en) * | 2000-09-29 | 2002-04-10 | Fujitsu General Ltd | Air conditioner |
| JP4258117B2 (en) * | 2000-09-29 | 2009-04-30 | 三菱電機株式会社 | Air conditioner |
| JP3900976B2 (en) * | 2002-03-06 | 2007-04-04 | 三菱電機株式会社 | Air conditioner and method of operating air conditioner |
| JP4288979B2 (en) * | 2003-03-27 | 2009-07-01 | 三菱電機株式会社 | Air conditioner, and operation control method of air conditioner |
| JP2005133976A (en) * | 2003-10-28 | 2005-05-26 | Hitachi Ltd | Air-conditioner |
| JP4270555B2 (en) * | 2004-03-31 | 2009-06-03 | 日立アプライアンス株式会社 | Reheat dehumidification type air conditioner |
| JP2006194525A (en) * | 2005-01-14 | 2006-07-27 | Hitachi Ltd | Multi-chamber type air conditioner |
| JP4544461B2 (en) * | 2005-01-24 | 2010-09-15 | 日立アプライアンス株式会社 | Air conditioner |
-
2005
- 2005-12-26 JP JP2005371785A patent/JP4730738B2/en not_active Expired - Fee Related
-
2006
- 2006-12-21 EP EP06256498A patent/EP1801520B1/en not_active Expired - Fee Related
- 2006-12-21 DE DE602006010312T patent/DE602006010312D1/en active Active
- 2006-12-21 ES ES06256498T patent/ES2335302T3/en active Active
- 2006-12-26 CN CN2006101725028A patent/CN1991276B/en not_active Expired - Fee Related
Cited By (26)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104583684A (en) * | 2012-10-15 | 2015-04-29 | 日立空调·家用电器株式会社 | Air conditioner |
| CN104583684B (en) * | 2012-10-15 | 2017-05-24 | 江森自控日立空调技术（香港）有限公司 | Air conditioner |
| CN102927715B (en) * | 2012-10-31 | 2015-07-01 | 青岛海信日立空调系统有限公司 | Multiple-on-line heat pump air-conditioning system and method for controlling multiple-on-line heat pump air-conditioning system |
| CN102927715A (en) * | 2012-10-31 | 2013-02-13 | 青岛海信日立空调系统有限公司 | Multiple-on-line heat pump air-conditioning system and method for controlling multiple-on-line heat pump air-conditioning system |
| CN103017410A (en) * | 2013-01-22 | 2013-04-03 | 北京德能恒信科技有限公司 | Heating-cooling type heat pipe and heat pump combined circulating system |
| CN103017410B (en) * | 2013-01-22 | 2016-09-21 | 北京丰联奥睿科技有限公司 | A kind of heating-refrigerating heat-pipe heat-pump type combined cycle system |
| CN107076434A (en) * | 2014-08-11 | 2017-08-18 | 黄利华 | Water cooling SPLIT AIR-CONDITIONING SYSTEM |
| CN105115181B (en) * | 2015-07-21 | 2018-06-26 | 上海海立电器有限公司 | A kind of air-conditioning system |
| CN105115181A (en) * | 2015-07-21 | 2015-12-02 | 上海日立电器有限公司 | Air conditioning system |
| CN106885388A (en) * | 2015-12-16 | 2017-06-23 | 上海日立电器有限公司 | A kind of air-conditioning system |
| CN106885403A (en) * | 2015-12-16 | 2017-06-23 | 上海日立电器有限公司 | Sensible heat latent heat separates the air-conditioning system of control |
| CN106885387A (en) * | 2015-12-16 | 2017-06-23 | 上海日立电器有限公司 | A kind of air-conditioning system |
| CN106885388B (en) * | 2015-12-16 | 2018-07-27 | 上海海立电器有限公司 | A kind of air-conditioning system |
| CN106885403B (en) * | 2015-12-16 | 2018-11-02 | 上海海立电器有限公司 | The air-conditioning system of sensible heat latent heat separation control |
| CN106885402B (en) * | 2015-12-16 | 2019-01-29 | 上海海立电器有限公司 | The air-conditioning system of sensible heat latent heat separation control |
| CN106885402A (en) * | 2015-12-16 | 2017-06-23 | 上海日立电器有限公司 | Sensible heat latent heat separates the air-conditioning system of control |
| CN112771320A (en) * | 2018-09-25 | 2021-05-07 | 东芝开利株式会社 | Air conditioner |
| CN112771320B (en) * | 2018-09-25 | 2022-08-02 | 东芝开利株式会社 | Air conditioner |
| CN109855184A (en) * | 2019-01-23 | 2019-06-07 | 青岛海尔空调器有限总公司 | Air conditioner and its dehumidification control method |
| CN110207330A (en) * | 2019-06-04 | 2019-09-06 | 广东美的暖通设备有限公司 | Air conditioner and its control method and device |
| CN112797657A (en) * | 2019-10-28 | 2021-05-14 | 广东美的制冷设备有限公司 | Air conditioner and control method thereof |
| CN114761107A (en) * | 2019-12-12 | 2022-07-15 | 三菱电机株式会社 | Dehumidifying device |
| CN114046612A (en) * | 2021-11-02 | 2022-02-15 | 南京天加环境科技有限公司 | Air conditioner/floor heating/ground cooling multi-connected system with double evaporation temperatures |
| CN114046612B (en) * | 2021-11-02 | 2023-05-26 | 南京天加环境科技有限公司 | Air conditioner/floor heating/floor cooling multi-system with double evaporating temperatures |
| CN114263991A (en) * | 2021-12-03 | 2022-04-01 | 雅凯热能技术(江苏)有限公司 | Fresh air dehumidification system |
| CN114263991B (en) * | 2021-12-03 | 2024-01-30 | 雅凯热能技术(江苏)有限公司 | Fresh air dehumidification system |
Also Published As
| Publication number | Publication date |
|---|---|
| ES2335302T3 (en) | 2010-03-24 |
| DE602006010312D1 (en) | 2009-12-24 |
| EP1801520B1 (en) | 2009-11-11 |
| EP1801520A1 (en) | 2007-06-27 |
| JP2007170769A (en) | 2007-07-05 |
| CN1991276B (en) | 2010-09-08 |
| JP4730738B2 (en) | 2011-07-20 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1991276A (en) | Air adjustor | |
| CN100501270C (en) | Refrigerating apparatus | |
| US7377119B2 (en) | Air conditioning system and control method thereof | |
| KR101343711B1 (en) | Air conditioning／hotwater supply system and heat pump unit | |
| CA2745109C (en) | Heat pump/air conditioning apparatus with sequential operation | |
| CN107110570A (en) | Heat storage type air conditioner | |
| WO2006013834A1 (en) | Freezing apparatus | |
| US7353664B2 (en) | Heat pump and compressor discharge pressure controlling apparatus for the same | |
| JP4848480B2 (en) | Process air temperature control method and apparatus for desiccant air conditioner | |
| JP5145026B2 (en) | Air conditioner | |
| KR100563899B1 (en) | Waste heat recoverable air conditioner | |
| EP3104102B1 (en) | Air conditioner and operation method of the same | |
| CN1672002A (en) | Refrigeration equipment | |
| US5799497A (en) | Refrigerating apparatus | |
| JP4084915B2 (en) | Refrigeration system | |
| CN1690595A (en) | Heat pump and compressor discharge pressure controlling apparatus for the same | |
| CN210154138U (en) | Expansion valve assembly, bidirectional throttling system and air conditioner | |
| CN2625805Y (en) | Wide temperate zone air source heat pump refrigerating unit | |
| CN110057144A (en) | A kind of expansion valve component, bidirectional throttle system and air conditioner | |
| CN115200250B (en) | Fluorine pump pressure refrigeration system and control method thereof | |
| CN217236259U (en) | Drying apparatus | |
| CN216203942U (en) | Heat pump system | |
| KR101270816B1 (en) | An air conditioner and a control method the same | |
| KR20050074133A (en) | A multiple air-conditioner and the control method for the same | |
| JP6569081B2 (en) | Air conditioner |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C41 | Transfer of patent application or patent right or utility model | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20160810 Address after: Hongkong, China Patentee after: Johnson Controls Hitachi air conditioning technology (Hong Kong) Co.,Ltd. Address before: Tokyo, Japan Patentee before: Hitachi Appliances, Inc. |
|
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20180710 Address after: Tokyo, Japan Patentee after: HITACHI-JOHNSON CONTROLS AIR CONDITIONING, Inc. Address before: Hongkong, China Patentee before: Johnson Controls Hitachi air conditioning technology (Hong Kong) Co.,Ltd. |
|
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20100908 Termination date: 20211226 |