CN1170095C - Air conditioner - Google Patents

Air conditioner Download PDF

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Publication number
CN1170095C
CN1170095C CNB018021328A CN01802132A CN1170095C CN 1170095 C CN1170095 C CN 1170095C CN B018021328 A CNB018021328 A CN B018021328A CN 01802132 A CN01802132 A CN 01802132A CN 1170095 C CN1170095 C CN 1170095C
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China
Prior art keywords
temperature
high pressure
desired value
air conditioner
liquid pipe
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Expired - Fee Related
Application number
CNB018021328A
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Chinese (zh)
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CN1386185A (en
Inventor
Ƭͩ����
片冈秀彦
西浦良广
����һ
坂本真一
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Daikin Industries Ltd
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Daikin Industries Ltd
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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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • 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
    • 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
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0315—Temperature sensors near the outdoor 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
    • 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
    • F25B2400/16—Receivers
    • 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
    • F25B2600/024—Compressor control by controlling the electric parameters, e.g. current or voltage
    • 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
    • F25B2600/05—Refrigerant levels
    • 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
    • F25B2700/15—Power, e.g. by voltage or current
    • F25B2700/151—Power, e.g. by voltage or current of the compressor motor
    • 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction 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
    • F25B2700/19—Pressures
    • F25B2700/195—Pressures of the condenser
    • 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
    • F25B2700/2106—Temperatures of fresh outdoor air
    • 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
    • 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
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • 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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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)

Abstract

A refrigerant circuit, comprising a bypass circuit bypassing a fluid pipe side pipe (131) and a gas pipe side pipe (132) having, thereon, a receiver (121) for recovering fluid refrigerant, a fluid pipe motor-operated valve (128) installed in a fluid pipe side connection pipe (122) for connecting the receiver (121) to a fluid pipe side pipe (131), and a gas pipe motor-operated valve (129) installed in a gas pipe side connection pipe (123) for connecting the receiver (121) to the gas pipe side pipe (132), wherein the current heat exchanging capacity of an outdoor heat exchanger (103) is checked to judge on whether an excess refrigerant is present or absent so as to control the fluid pipe motor-operated valve (128) and the gas pipe motor-operated valve (129), whereby the amount of refrigerant in the receiver (121) can be controlled.

Description

Air conditioner
Technical field
The present invention relates to air conditioner, be specifically related to a kind of air conditioner that is provided with the fluid reservoir that reclaims unnecessary cold-producing medium.
Background technology
The refrigerant loop of air conditioner is will be arranged on accumulator, compressor, cross valve and the outdoor heat converter in the off-premises station respectively and the indoor heat converter that is arranged in the indoor set is formed by connecting by refrigerant piping, thereby constitutes the peripheral passage of cold-producing medium.
In the refrigerant loop of this air conditioner, by the loop direction of cross valve control cold-producing medium, make outdoor heat converter during refrigeration as condenser working, indoor heat converter is as evaporator operation.And when heating, the loop direction by cross valve control cold-producing medium makes outdoor heat converter as evaporator operation, and indoor heat converter is as cooler work.
This air conditioner is considered the convenience when installing, the refrigerant amount of required additional injection when preferably the injection connecting pipings is the longest in outdoor pusher side refrigerant loop in advance.But refrigerant amount suitable during operation significantly changes with the indoor set capacity of operational mode, connection and the connecting pipings length of actual installation etc.Therefore, the unnecessary cold-producing medium that produces in the refrigerant loop will make the fluid refrigeration agent be trapped in the condenser, might cause the unusual rising of high pressure, and operational efficiency descends.
In order to handle this unnecessary cold-producing medium, the someone was proposed in the fluid reservoir that reclaims unnecessary cold-producing medium was set between outdoor heat converter and the liquid shut off valve in the past.
Traditional fluid reservoir loop is that fluid reservoir series connection is inserted in the liquid pipe side line portion from outdoor heat converter to the fluid shut off valve.Therefore, the amount of the liquid refrigerant in the fluid reservoir only (is equivalent to each chamber motor-driven valve with the motor-driven valve in fluid reservoir downstream during refrigerating operaton, when operation heating is equivalent to main pressure-reducing valve) cross the aperture control that thermal control carries out and increase and decrease, randomness is very big, be difficult to correctly to adjust the amount of fluid reservoir inner refrigerant, especially when low outer fate row or overburden can't adjust refrigerant amount in the fluid reservoir when moving etc. under the special running status.
For example, carry out under the situation of refrigerating operaton when the temperature degree is extremely low outside, the ability surplus of outdoor heat converter, then the high-pressure side descends.The height pressure reduction of compressor reduces like this, causes the reliability decrease of compressor.The unnecessary cold-producing medium that is recycled in the fluid reservoir if can be moved on to outdoor heat converter, just can be full of the part of outdoor heat converter, reduce the ability of outdoor heat converter, on high-tension side pressure is risen, can guarantee height pressure reduction with supercooling liquid.
Summary of the invention
Move when the object of the present invention is to provide the low outer gas of a kind of basis or operation conditions such as overburden is controlled unnecessary cold-producing medium, thereby move the air conditioner of control expeditiously.
Air conditioner of the present invention, it is characterized in that, have refrigerant loop, this refrigerant loop will comprise the compressor, cross valve and the outdoor heat converter that are arranged in the off-premises station at least and couple together at interior outdoor pusher side refrigerant loop and the indoor heat converter that is configured in the indoor set by liquid line side line and flue side line; Be provided with the fluid reservoir that on the bypass circulation that liquid line side line and flue side line is carried out bypass, reclaims liquid refrigerant, be located at the cold-producing medium switching device on liquid pipe side tube connector that is connected to the liquid line side line from fluid reservoir and the flue side tube connector that is connected to the flue side line; The present heat-exchange capacity of outdoor heat converter is judged to judge whether unnecessary cold-producing medium, and by the cold-producing medium switching device is controlled, amount with control fluid reservoir inner refrigerant, the cold-producing medium switching device constitutes by being arranged on the amount of liquid side tube connector and can regulating the liquid pipe motor-driven valve of the refrigerant flow that passes through and be arranged on the flue motor-driven valve that also can regulate the refrigerant flow that passes through on the flue side tube connector, during refrigerating operaton, compare by desired value and can judge whether unnecessary cold-producing medium the outlet temperature of outdoor heat converter outlet temperature and outdoor heat converter.
In addition, the outlet temperature of outdoor heat converter can be the detected value that is located near the outdoor liquid pipe compensation by thermistor of outdoor heat converter outlet.
And when refrigerating operaton, the desired value of outdoor heat converter outlet temperature depends on circulating mass of refrigerant and outer temperature degree, also can be depending on the frequency and the outer temperature degree of compressor.
The desired value of outdoor heat converter outlet temperature can be revised with crossing thermal control or the temperature controlled deviation of target discharge pipe.
The desired value of outdoor heat converter outlet temperature can be arranged in the high side of temperature in the middle of the heat exchange as higher limit with high pressure saturation temperature or outdoor heat converter, and the value of temperature gained that adds regulation with present outer temperature degree is as lower limit.
When refrigerating operaton, liquid pipe motor-driven valve is opened when the outdoor heat converter outlet temperature is lower than desired value, and liquid pipe motor-driven valve cuts out when the outlet temperature of outdoor heat converter is higher than desired value.
Compare to have judged whether unnecessary cold-producing medium when the desired value of saturation temperature by high pressure phase being worked as saturation temperature and high pressure phase during refrigerating operaton.
Under this occasion, be provided with the high pressure sensor that high voltage protective is used at the exhaust end of compressor, high pressure phase is calculated by the high-voltage value that high pressure sensor detects when saturation temperature.
In addition, the running frequency of the consumed power factor of available compressor suction side pressure, compressor and compressor is calculated high pressure phase and is worked as saturation temperature.
In the refrigerating operaton, high pressure phase also can decide according to the running frequency and the outer temperature degree of compressor when the desired value of saturation temperature can decide according to circulating mass of refrigerant and outer temperature degree.
And high pressure phase is worked as the desired value of saturation temperature by thermal control or the temperature controlled deviation of target discharge pipe are revised excessively.
High pressure phase adds that with present outer temperature degree setting is as lower limit when the desired value of saturation temperature can the high pressure saturation temperature add setting as higher limit.
Liquid pipe motor-driven valve cut out when the suitable saturation temperature of refrigerating operaton mesohigh was lower than desired value, and high pressure phase liquid pipe motor-driven valve when saturation temperature is higher than desired value is opened.
Warm oneself when moving by the typical value of liquid pipe temperature and the desired value of liquid pipe temperature are compared to have judged whether unnecessary cold-producing medium.
This moment, the typical value of liquid pipe temperature was got the operating liquid pipe of indoor set temperature minimum.
Liquid pipe temperature objectives value during the heating operation can be depending on circulating mass of refrigerant and room temperature, also can be depending on the running frequency and the room temperature of compressor.
Also available thermal control excessively of the desired value of liquid pipe temperature or the temperature controlled deviation of target discharge pipe are revised.
The high side of maximum that the desired value of liquid pipe temperature can be arranged in the temperature in the middle of the heat exchange with high pressure saturation temperature or indoor heat converter is as higher limit, adds that with the maximum of room temperature setting is as lower limit.
During the heating operation, the flue motor-driven valve is opened when the typical value of liquid pipe temperature is lower than desired value, and the flue motor-driven valve cuts out when the typical value of liquid pipe temperature is higher than desired value.
Compare to have judged whether unnecessary cold-producing medium when the desired value of saturation temperature by high pressure phase being worked as saturation temperature and high pressure phase when in addition, heating moves.
High pressure phase during the heating operation can be depending on circulating mass of refrigerant and room temperature when the desired value of saturation temperature, also can be depending on the running frequency and the room temperature of compressor.
High pressure phase is worked as the desired value of saturation temperature and can be revised by crossing thermal control or the temperature controlled deviation of target discharge pipe.
High pressure phase can be worked as saturation temperature with high pressure phase when the desired value of saturation temperature and add setting as higher limit, add that with room temperature setting is as lower limit.
The high pressure phase in service of warming oneself flue motor-driven valve when saturation temperature is lower than desired value cuts out, and high pressure phase flue motor-driven valve when saturation temperature is higher than desired value is opened.
Description of drawings
Fig. 1 is the general configuration figure in an example of the present invention air conditioner refrigeration agent loop of being adopted.
Fig. 2 is the control flow chart of the 1st example.
Fig. 3 is the control flow chart of the 1st example.
Fig. 4 is the control flow chart of the 1st example.
Fig. 5 is the control flow chart of the 1st example.
Fig. 6 is the control flow chart of the 2nd example.
Fig. 7 is the control flow chart of the 2nd example.
Fig. 8 is the control flow chart of the 2nd example.
Fig. 9 is the control flow chart of the 2nd example.
Figure 10 is the control flow chart of the 3rd example.
Figure 11 is the control flow chart of the 3rd example.
Figure 12 is the control flow chart of the 3rd example.
Figure 13 is the control flow chart of the 3rd example.
Figure 14 is the control flow chart of the 4th example.
Figure 15 is the control flow chart of the 4th example.
Figure 16 is the control flow chart of the 4th example.
Figure 17 is the control flow chart of the 4th example.
Figure 18 is the controlling party block diagram of an example.
Figure 19 is the controlling party block diagram in driven compressor loop.
Figure 20 is the flow chart of expression high pressure phase when the saturation temperature presuming method.
Figure 21 is the key diagram of saturation temperature calculating table.
The specific embodiment
(the 1st example)
The air conditioner refrigeration agent loop that the 1st example of the present invention is adopted as shown in Figure 1.
Off-premises station 100 has outdoor pusher side refrigerant loop, and this loop is made of compressor 101, cross valve 102, outdoor heat converter 103, accumulator 105 etc.The exhaust end of compressor 101 is provided with and is used to detect the unusual exhaust end pressure-head switch 108 that rises of pressure that spues, and is provided with the suction side pressure sensor 110 that is used to detect suction pressure in the suction side of compressor 101.
Exhaust end at compressor 101 is provided with oil eliminator 107, sends accumulator 105 sides after the lubricating oil separation that is used for cold-producing medium is contained back to.In this oil eliminator 107, be provided with and detect the spue discharge pipe compensation by thermistor 109 of temperature of compressor 101.
Be provided with the bypass circulation 194 that spues in the oily recurrent canal 197 of oil eliminator 107, this loop is connected from oily recurrent canal 197 branches and with the inlet side of energy storage canister 105.Be provided with the hot copulation canal portion 196 that imports accumulator 105 inside and volume controlled in this bypass circulation 194 that spues with spuing-suck motor-driven valve (EVP) 142.Be provided with capillary 141 in addition in the oily recurrent canal 197 of oil eliminator 107, the other end of this capillary 141 is connected with the suction side of energy storage canister 105.
The outdoor heat that is provided with the outlet temperature of the outer gas compensation by thermistor 111 that detects outer temperature degree, sensing chamber's outer heat-exchanger 103 in the off-premises station 100 hands over compensation by thermistor 112, detect the heat that is positioned at the temperature in the middle of the heat exchange hands over middle compensation by thermistor 113.In addition, also be provided with the fan electromotor 104 of fan 106 and this fan 106 of driving in the off-premises station 100, this fan is in order to suck outer gas and carry out heat exchange between the cold-producing medium of outer gas that sucks and outdoor heat converter 103 internal flows.
The refrigerant piping of deriving to indoor pusher side from off-premises station 100 has liquid pipe connector 114 of drawing from outdoor heat converter 103 and the flue connector 115 of drawing by cross valve 102, and each connector inboard is provided with liquid pipe shut off valve 116 and flue shut off valve 117.
Be provided with fluid reservoir 121 in the off-premises station 100, the unnecessary refrigerant liquid as the outdoor heat converter 103 of condenser working when being used for refrigerating operaton stores temporarily.Fluid reservoir 121 has liquid pipe side tube connector 122 and flue side tube connector 123, liquid pipe side tube connector 122 is connected with liquid pipe side line portion 131 between outdoor heat converter 103 and the liquid pipe shut off valve 116, and flue side tube connector 123 is connected with this side line portion 132 of gas between cross valve 102 and the flue shut off valve 117.
The liquid pipe side tube connector 122 of fluid reservoir 121 is provided with the liquid pipe motor-driven valve (EVL) 128 with decompression and cold-producing medium cut-out function, is provided with flue motor-driven valve (EVG) 129 in the flue side tube connector 123.
At flue motor-driven valve 129 and between the connecting portion of flue side line portion 132 secondary unit 133 is set.Liquid pipe side outlet configuration cryogenic heat exchanger 134 at outdoor heat converter 103.
Be provided with the exhaust capillary 130 that is used to retrieve from the gas shape cold-producing medium of fluid reservoir 121 towards the flue side line portion 132 between cross valve 102 and the gas shut-off valve 117.
Be connected with a plurality of branch unit 300A, 300B in the liquid pipe connector 114 of off-premises station 100 and the flue connector 115 ...Each branch unit 300A, 300B ... be respectively identical structure, so only branch unit 300A is explained other omissions.
Branch unit 300A has outside liquid pipe connector 301 that is connected with the liquid pipe connector 114 of off-premises station 100 and the outside flue connector 303 that is connected with the flue connector 115 of off-premises station 100.Branch unit 300A has the liquid pipe side branched bottom in the inside branch of outside liquid pipe connector 301, and its end constitutes the indoor flue connector 302 of the indoor set number that is connected.In addition, also have the flue side branched bottom in the inside branch of outside flue connector 303, its end constitutes the indoor flue connector 304 of the indoor set number that is connected.At this, the indoor set that is connected is 3, is provided with indoor liquid pipe connector 302A, 302B, 302C and indoor flue connector 304A, 304B, 304C.In addition, between outside liquid pipe connector 301 and outside flue connector 303, be provided with the motor-driven valve 308 that bypass is used.
Be provided for to the tributary circuit of each indoor liquid pipe connector 302A-302C the motor-driven valve 305A-305C of the refrigerant pressure decompression by inside respectively and be used to detect liquid pipe compensation by thermistor 306A-306C at the outside liquid pipe connector 301 in branch unit 300A by the refrigerant temperature of inside.In addition, be provided for detecting liquid pipe compensation by thermistor 307A-307C to the tributary circuit of each indoor liquid pipe connector 304A-304C respectively at the outside flue connector 303 in branch unit 300A by the refrigerant temperature of inside.
Each branch unit 300A, 300B ... in be connected with each indoor set 200 respectively.Illustrated can with each branch unit 300A, 300B ... the indoor set number that connects is 3, and branch unit 300A goes up and connects indoor set 200A-200C, and branch unit 300B goes up and connects indoor set 200D-200F.Each indoor set 200A-200F can use respectively and drag machine with indoor set or to the machine indoor set more, to using machine is explained with the occasion of indoor set as indoor set 200A here.
Indoor set 200A has indoor heat converter 201, and the refrigerant piping that is connected with this indoor heat converter 201 causes outdoor pusher side by liquid pipe connector 204 and flue connector 205.Be provided with the indoor heat friendship thermal resistance thermometer 203 that is used to detect the room temperature compensation by thermistor 202 of indoor temperature and is used to detect the temperature of indoor heat converter 201 among this indoor set 200A.
With drag more machine with indoor set as with indoor set that branch unit 300A, 300B are connected the time, sometimes be provided for examining the liquid pipe compensation by thermistor of the refrigerant temperature of liquid-measuring tube side line portion internal flow, under this occasion, can omit the liquid pipe compensation by thermistor in branch unit 300A, the 300B.
(the unnecessary cold-producing medium control during refrigerating operaton)
Now the situation of carrying out unnecessary cold-producing medium control by liquid pipe temperature during to refrigerating operaton according to flow chart shown in Figure 2 explains.
In step S11, judge whether to surpass the sampling time TSCSET of unnecessary cold-producing medium control.When reaching unnecessary cold-producing medium control sampling time TSCSET, the counting in elapsed time of timer enters step S12.
In step S12, target liquid pipe temperature is carried out computing.
In computing according to flowchart text target liquid pipe temperature shown in Figure 3.
In step S21, use the calculating variables D OATDs such as target frequency FMK, discharge pipe temperature deviation EDO of target liquid pipe temperature computation with COEFFICIENT K SCC1, KSCC2, KSCC3, EDOSC, compressor 101.
DOATD＝KSCC1×FMK+KSCC2-(EDO-EDOSC)×KSCC3
In step S22, whether judgment variable DOATD surpasses the lower limit DOATDMIN of target liquid pipe temperature.When surpassing the lower limit DOATDMIN of target liquid pipe temperature, judgement DOATD enters step S23.In step S23, the value of variables D OATD is arranged to target liquid pipe lowest temperature value DOATDMIN.
In step S24, whether judgment variable DOATD is below (temperature degree DOA outside the higher limit DOATDMAX-of target liquid pipe temperature).When surpassing (temperature degree DOA outside the upper limit DOATDMAX-of target liquid pipe temperature), judgment variable DOATD enters step S25.In step S25, the value of variables D OATD is arranged to (the outer temperature degree DOA of the higher limit DOATDMAX-of target liquid pipe temperature).
In step S26, calculate target liquid pipe temperature DELSET.Here, the outer temperature degree DOA+ variables D OATD of target liquid pipe temperature DELSET=.
In step S13, calculate liquid pipe temperature deviation Δ DEL.The outdoor heat of liquid pipe temperature deviation Δ DEL=target liquid pipe temperature DELSET-is surrendered a mouthful temperature DEL.
In step S14, carry out the computing of motor-driven valve operational ton.
The computing of this motor-driven valve operational ton is shown in the flow chart of Fig. 4.
In step S31, utilize the motor-driven valve operational ton to calculate and calculate motor-driven valve operational ton POSC with COEFFICIENT K OSCA1, KOSCA, liquid pipe temperature deviation Δ DEL, last not good liquor pipe temperature deviation Δ DELZ etc.
POSC＝KOSACA1×((ΔDEL-ΔDELZ)+ΔDEL/KOSCA)
The motor-driven valve operational ton of obtaining according to step S14 in step S15 carries out the motor-driven valve operation.
Here use the flowcharting motor-driven valve operational processes of Fig. 5.
The aperture EVL of liquid pipe motor-driven valve 128 is taken as (present aperture EVL+ motor-driven valve operational ton POSC).Aperture EVG with flue motor-driven valve 129 is controlled to be (present aperture EVG+ motor-driven valve operational ton POSC * KPOSC1) simultaneously.
Liquid pipe temperature during refrigerating operaton can hand over the detected value of thermal resistance thermometer 112 to try to achieve by being located near the outdoor heat of outdoor heat converter 103 outlets.Can utilize the unnecessary refrigerant amount in this liquid pipe temperature control fluid reservoir 121.
Therefore, even outside low, also can control unnecessary refrigerant amount under the occasions such as refrigerating operaton under the temperature degree, guarantee the height pressure reduction of compressor 101.
(the 2nd example)
(the unnecessary cold-producing medium control during refrigerating operaton)
Utilizing high pressure phase to work as unnecessary cold-producing medium that saturation temperature carries out in the refrigerating operaton controls available flow chart shown in Figure 6 and explains.Unnecessary cold-producing medium control when using the refrigerant loop identical to carry out refrigerating operaton here with the 1st example.
In step S51, judge whether to surpass the sampling time TSCSET of unnecessary cold-producing medium control.When reaching unnecessary cold-producing medium control sampling time TSCSET, the counting in elapsed time of timer enters step S52.
In step S52, carry out of the computing of target high pressure phase when saturation temperature.
Now according to flowchart text target high pressure phase shown in Figure 7 computing when saturation temperature.
In step S61, target frequency FMK, the discharge pipe temperature deviation EDO etc. that use the target high pressure phase to calculate with COEFFICIENT K SCC1, KSCC2, KSCC3, EDOSC, compressor 101 when saturation temperature calculate variables D OATD.
DOATD＝KSCC1×FMK+KSCC2-(EDO-EDOSC)×KSCC3
In step S62, whether judgment variable DOATD surpasses the lower limit DOATDMIN of target high pressure phase when saturation temperature.When judging that DOATD enters step S63 when surpassing the target high pressure phase as the lower limit DOATDMIN of saturation temperature.In step S63, the value of variables D OATD is arranged to the target high pressure phase as saturation temperature lower limit DOATDMIN.
In step S64, whether judgment variable DOATD is below (the target high pressure phase is as the higher limit DOATDMAX of saturation temperature).When surpassing (the target high pressure phase is as the higher limit DOATDMAX of saturation temperature), judgment variable DOATD enters step S65.In step S65, the value of variables D OATD is arranged to (the target high pressure phase is as the higher limit DOATDMAX of saturation temperature).
In step S66, calculate the target high pressure phase as saturation temperature TDSSET.Here, the target high pressure phase is as the outer temperature degree DOA+ variables D OATD of saturated TDSSET=.
In step S53, calculate high pressure phase as saturation temperature deviation delta TDS.High pressure phase is worked as saturation temperature TDSSET-high pressure phase when saturation temperature deviation delta TDS=target high pressure phase and is worked as saturation temperature TDS.
In step S54, carry out the computing of motor-driven valve operational ton.
The computing of this motor-driven valve operational ton is shown in the flow chart of Fig. 8.
In step S71, utilize the calculating of motor-driven valve operational ton to work as saturated deviation delta TDS, the suitable saturation temperature deviation delta of last sub-high pressure TDSZ etc. and calculate motor-driven valve operational ton POSC with COEFFICIENT K OSCA1, KOSCA, high pressure phase.
POSC＝KOSCA1×((ΔTDS-ΔTDSZ)+ΔTDS/KOSCA)
The motor-driven valve operational ton of obtaining according to step S54 in step S55 carries out the motor-driven valve operation.
Here use the flowcharting motor-driven valve operational processes of Fig. 9.
The aperture EVL of liquid pipe motor-driven valve 128 is taken as (present aperture EVL+ motor-driven valve operational ton POSC).Aperture EVG with flue motor-driven valve 129 is controlled to be (present aperture EVG+ motor-driven valve operational ton POSC * KPOSC1) simultaneously.
(the 3rd example)
Utilizing liquid pipe temperature to carry out unnecessary cold-producing medium control when utilizing flow chart shown in Figure 10 to the heating operation explains.
In step S91, judge whether to surpass the sampling time TSCSET of unnecessary cold-producing medium control.When reaching unnecessary cold-producing medium control sampling time TSCSET, the counting in elapsed time of timer enters step S92.
In step S92, calculate processing target liquid pipe temperature.
Now according to the computing of flowchart text target liquid pipe temperature shown in Figure 11.
In step S101, use the calculating variables D OATDs such as target frequency FMK of target liquid pipe temperature computation with COEFFICIENT K SCC1, KSCC2, compressor 101.
DOATD＝KSCC1×FMK+KSCC2
In step S102, whether judgment variable DOATD surpasses the lower limit DOATDMIN of target liquid pipe temperature.When surpassing the lower limit DOATDMIN of target liquid pipe temperature, judgement DOATD enters step S103.In step S103, the value of variables D OATD is arranged to target liquid pipe lowest temperature value DOATDMIN.
In step S104, whether judgment variable DOATD is below (the higher limit DOATDMAX-room temperature DA of target liquid pipe temperature).When surpassing (upper limit DOATDMAX-room temperature DA of target liquid pipe temperature), judgment variable DOATD enters step S105.In step S105, the value of variables D OATD is arranged to (the higher limit DOATDMAX-room temperature DA of target liquid pipe temperature).
In step S106, calculate target liquid pipe temperature DELSET.Here, target liquid pipe temperature DLSET=room temperature DA+ variables D OATD.
In step S93, calculate liquid pipe temperature deviation Δ DL.At the indoor heat converter 201 of minimum liquid pipe temperature in the present operating indoor set 200, with it as liquid pipe temperature typical value DL, this liquid pipe temperature deviation Δ DL=target liquid pipe temperature DLSET-liquid pipe temperature typical value DL.
In step S94, carry out the computing of motor-driven valve operational ton.
The computing of this motor-driven valve operational ton is shown in the flow chart of Figure 12.
In step S111, utilize the motor-driven valve operational ton to calculate and calculate motor-driven valve operational ton POSC with COEFFICIENT K OSCA1, KOSCA, liquid pipe temperature deviation Δ DL, last not good liquor pipe temperature deviation Δ DLZ etc.
POSC＝KOSACA1×((ΔDL-ΔDLZ)+ΔDL/KOSCA)
The motor-driven valve operational ton of obtaining according to step S94 in step S95 carries out the motor-driven valve operation.
Here use the flowcharting motor-driven valve operational processes of Figure 13.
The aperture EVG of flue motor-driven valve 129 is taken as (present aperture EVG+ motor-driven valve operational ton POSC).Aperture EVL with liquid pipe motor-driven valve 128 is controlled to be (present aperture EVL+ motor-driven valve operational ton POSC * KPOSC1) simultaneously.
The liquid pipe temperature in when operation heating as liquid pipe temperature typical value, can be utilized the unnecessary refrigerant amount in this liquid pipe temperature typical value control fluid reservoir 121 with liquid pipe temperature is minimum in the operating indoor set 200 value.
(the 4th example)
The situation of carrying out unnecessary cold-producing medium control by high pressure phase when saturation temperature when now utilizing flow chart shown in Figure 14 to the heating operation explains.
In step S131, judge whether to surpass the sampling time TSCSET of unnecessary cold-producing medium control.When reaching unnecessary cold-producing medium control sampling time TSCSET, the counting in elapsed time of timer enters step S132.
In step S132, calculate the processing target high pressure phase and work as saturation temperature.
Now according to flowchart text target high pressure phase shown in Figure 15 computing when saturation temperature.
In step S141, use the target high pressure phase to calculate the calculating variables D OATD such as target frequency FMK that use COEFFICIENT K SCC1, KSCC2, compressor 101 when saturation temperature.
DOATD＝KSCC1×FMK+KSCC2
In step S142, whether judgment variable DOATD surpasses the lower limit DOATDMIN of target high pressure phase when saturation temperature.When judging that DOATD enters step S143 when surpassing the target high pressure phase as the lower limit DOATDMIN of saturation temperature.In step S143, the value of variables D OATD is arranged to the target high pressure phase as saturation temperature lower limit DOATDMIN.
In step S144, whether judgment variable DOATD is below (the target high pressure phase is as the higher limit DOATDMAX of saturation temperature).When surpassing (the target high pressure phase is as the upper limit DOATDMAX of saturation temperature), judgment variable DOATD enters step S145.Among the step S145, the value of variables D OATD is arranged to (the target high pressure phase is as the higher limit DOATDMAX of saturation temperature).
In step S146, calculate the target high pressure phase as saturation temperature TDSSET.Here, the target high pressure phase is as saturation temperature TDSSET=room temperature DA+ variables D OATD.
In step S133, calculate high pressure phase as saturation temperature deviation delta TDS.High pressure phase is worked as saturation temperature TDSSET-high pressure phase when saturation temperature deviation delta TDS=target high pressure phase and is worked as saturation temperature TDS.
In step S134, carry out the computing of motor-driven valve operational ton.
The computing of this motor-driven valve operational ton is shown in the flow chart of Figure 16.
In step S151, motor-driven valve operational ton POSC utilizes the calculating of motor-driven valve operational ton to work as saturation temperature deviation delta TDS, the suitable saturation temperature deviation delta of last sub-high pressure TDSZ etc. with COEFFICIENT K OSCA1, KOSCA, high pressure phase and calculates.
POSC＝KOSACA1×((ΔTDS-ΔTDSZ)+ΔTDS/KOSCA)
The motor-driven valve operational ton of obtaining according to step S134 in step S135 carries out the motor-driven valve operation.
Here use the flowcharting motor-driven valve operational processes of Figure 17.
The aperture EVG of flue motor-driven valve 129 is taken as (present aperture EVG+ motor-driven valve operational ton POSC).Aperture EVL with liquid line motor-driven valve 128 is controlled to be (present aperture EVL+ motor-driven valve operational ton POSC * KPOSC1) simultaneously.
(high pressure phase is inferred when saturation temperature)
Below the presuming method of the suitable saturation temperature of aforementioned the 2nd example mesohigh is described.The controlling party block diagram of this occasion as shown in figure 18.
Control part 501 is made of the microprocessor that comprises CPU, ROM, RAM etc., and the ROM502 that deposits operation control program and various parameters and the RAM503 that will temporarily deposit operating variable etc. etc. are connected.
Being configured in off-premises station 100 interior various sensors is that suction side pressure sensor 110, discharge pipe compensation by thermistor 109, outer gas compensation by thermistor 111, outdoor heat friendship compensation by thermistor 112, the middle compensation by thermistor 113 of heat friendship etc. link to each other detected value input control part 501 separately with control part 501.And exhaust end pressure switch 108 is connected with control part 501.
The indoor communication interface 504 that is used for the output input of various data between indoor set 200 or the branch unit 300 is connected with control part 501.
And, be used to carry out the driven compressor loop 505 of the running frequency control of compressor 101, the fan electromotor that is used to carry out the FREQUENCY CONTROL of fan electromotor 104 and drive loop 506 etc. and be connected with control part 501.
The motor-driven valve 142 that spues-suck that is located at liquid pipe motor-driven valve 128, the gas motor-driven valve 129 of fluid reservoir 121 front and back and is located on the bypass circulation 194 that spues of compressor 101 is connected with control part 501.
Driven compressor loop 505 has active power filtering described later loop, and 2 side voltage sensors 507 and 2 side current sensors 508 of this active filter are connected with control part 501.
Figure 19 represents the controlling party block diagram in the driven compressor loop 505 of Figure 18.
Driven compressor loop 505 has the commutating circuit 512 that is connected with source power supply 511, active power filtering loop 513, inverting loop 514.
Commutating circuit 512 is made of the diode bridge that is connected with 4 diodes, and the AC power that source power supply 511 provides is carried out full-wave rectification.
Active power filtering loop 513 has reactor 521, diode 522, capacitor 523, switch element 524 and switch element 524 is carried out the active filtration drive device 525 etc. of switch control.
Active filtration circuit 513 has the 1st voltage sensor 526, the 1st current sensor 527 that detects 1 side electric current, the 2nd voltage sensor 507 that detects 2 side voltages that detects 1 side voltage, the 2nd current sensor 508 that detects 2 side electric currents.Active power filtering drive unit 525 carries out the switch control of switch element 524 so that the 2nd voltage sensor 507 detected 2 side voltages are consistent with predefined magnitude of voltage.Control the 1st current sensor 527 detected current values simultaneously with consistent with the phase place of the 1st voltage sensor 526 detected 1 side voltage.Significantly improve the power factor factor thus, and improve the precision of the consumption electric power of calculating according to the 2nd voltage sensor 507 detected 2 side voltages and the 2nd current sensor 508 detected 2 side galvanometer.
The pulse signal of certain voltage is sent in inverting loop 514 according to the output signal of the assigned voltage in active power filtering loop 513.The output frequency in the loop of inverting at this moment 514 is the running frequency of the compressor of determining according to present operation conditions.Therefore, drive motor for compressor 531 is driven by the output frequency in inverting loop 514.
Utilize 2 side magnitudes of voltage of the active filter 513 in driven compressor loop 505,2 side current values to calculate the consumption electric power of compressor 101 according to the flowchart text of Figure 20, calculate the method for high pressure phase when the presumed value of saturation temperature with this.
In step S171, detect input voltage VIN and the input current IIN that enters inverting loop 514.Entering the input voltage VIN in this inverting loop 514 and input current IIN can obtain according to the 2nd voltage sensor 507 of 2 side voltages of detection of active filter 513 and the value that detects the 2nd current sensor 508 of 2 side electric currents.
In step S172, can calculate the consumption electric power INPUT of compressor 101 according to 2 side voltage VIN of active filter 513 and 2 side electric current I IN.Here, the active filter drive unit 525 of active filter 513 carries out the control of switch element 524 to become optimum power factor, so can be with power factor as 1.Therefore can calculate compressor with INPUT=VIN * IIN * 1 (power factor) and consume electric power.
In step S173, obtain the output frequency FOUT and the suction pressure value LP of drive compression machine 101.Here, can determine output frequency FOUT according to the output frequency of the frequency converter 514 of drive compression machine drive motors 531.Can determine suction pressure value LP according to the detected value of suction side pressure sensor 110 in addition.
In step S174, obtain high-voltage value according to consumption electric power INPUT, output frequency FOUT, suction pressure value LP.Here can adopt high pressure to infer with COEFFICIENT K HPLL, KHPFF, KHPII, KHPLF, KHPFI, KHPLI, KHPL, KHPF, KHPI, KHPC and high pressure correction value HPHOSEI and by following formula tries to achieve.
HP＝KHPLL×LP 2+KHPFF×FOUT 2+KHPII×INPUT 2+KHPLF
×LP×FOUT+KHPFI×FOUT×INPUT+KHPLI×LP×INPUT+KHPL×
LP+KHPF×FOUT+KHPI×INPUT+KHPC+HPHOSEI
The high-voltage value HP that calculates according to step S174 in step S175 calculates high pressure phase as saturation temperature TDS.Here can adopt TDS=A * HP+B to try to achieve.Be used to calculate high pressure phase when the value of coefficient A, the B of saturation temperature, high-voltage value HP fixed by voting shown in Figure 21.
The possibility of utilizing on the industry
The present invention can adjust the unnecessary refrigerant amount that reclaims in the fluid reservoir according to operation conditions, can hand in outdoor heat Carry out the control of supercooling degree or the degree of superheat in the parallel operation. Thereby can make refrigerant amount the best of refrigerant circuit systems Change and carry out high-efficiency operation.

Claims (32)

1. air conditioner, it is characterized in that, has refrigerant loop, described refrigerant loop will comprise the compressor (101) that is arranged in the off-premises station (100) at least by liquid pipe side line and flue side line, and the outdoor pusher side refrigerant loop of cross valve (102) and outdoor heat converter (103) and the indoor heat converter (201) that is arranged in the indoor set (200) couple together;
Be provided with the fluid reservoir (121) that reclaims cold-producing medium on the bypass circulation of described liquid pipe side line (131) and flue side line (132) bypass, be located at the cold-producing medium switching device (128,129) on the flue side tube connector (123) that is connected to the liquid pipe side tube connector (122) of described liquid pipe side line (131) by described fluid reservoir (121) and is connected to flue side line (132);
The present heat-exchange capacity of described outdoor heat converter (103) is judged having judged whether unnecessary cold-producing medium, and is regulated refrigerant amount in the described fluid reservoir (121) by the described cold-producing medium switching device of control (128,129),
Described cold-producing medium switching device comprises: be arranged on described liquid pipe side tube connector (122) and go up and can regulate the liquid pipe motor-driven valve (128) of the refrigerant flow that passes through, be arranged on the flue motor-driven valve (129) that the refrigerant flow that passes through was gone up and can be regulated to described flue side tube connector (123)
Compare to have judged whether unnecessary cold-producing medium by desired value during refrigerating operaton the outlet temperature of the outlet temperature of described outdoor heat converter (103) and described outdoor heat converter (103).
2. air conditioner according to claim 1 is characterized in that, the outlet temperature of described outdoor heat converter (103) is for being located near the detected value of the outdoor liquid pipe compensation by thermistor (112) of described outdoor heat converter (103) outlet.
3. air conditioner according to claim 1 is characterized in that, the desired value of the outlet temperature of described outdoor heat converter (103) depends on circulating mass of refrigerant and outer temperature degree during refrigerating operaton.
4. air conditioner according to claim 1 is characterized in that, the desired value of the outlet temperature of described outdoor heat converter (103) depends on the running frequency and the outer temperature degree of described compressor (101) during refrigerating operaton.
5. according to claim 3 or 4 described air conditioners, it is characterized in that the desired value of the outlet temperature of described outdoor heat converter (103) is revised by crossing thermal control or the temperature controlled deviation of target discharge pipe.
6. air conditioner according to claim 5 is characterized in that, the desired value of the outlet temperature of described outdoor heat converter (103) is arranged in the high side of the middle temperature of heat exchange as higher limit with high pressure saturation temperature or outdoor heat converter (103).
7. air conditioner according to claim 5 is characterized in that, the desired value of the outlet temperature of described outdoor heat converter (103) adds that with present outer temperature degree set point of temperature is as lower limit.
8. air conditioner according to claim 5, it is characterized in that, when the outlet temperature of described outdoor heat converter (103) is lower than desired value, open described liquid pipe motor-driven valve (128) during refrigerating operaton, when the outlet temperature of described outdoor heat converter (103) is higher than desired value, close described liquid pipe motor-driven valve (128).
9. air conditioner according to claim 1 is characterized in that, in the refrigerating operaton high pressure phase is worked as saturation temperature and high pressure phase and compares to have judged whether unnecessary cold-producing medium when the desired value of saturation temperature.
10. air conditioner according to claim 9 is characterized in that, is provided with the high pressure sensor of high voltage protective at the exhaust end of described compressor (101), and described high pressure phase is calculated by the detected high-voltage value of described high pressure sensor when saturation temperature.
11. air conditioner according to claim 9 is characterized in that, utilizes the running frequency of the consumption electric power of the suction side pressure of described compressor (101), described compressor (101) and described compressor (101) to calculate described high pressure phase and works as saturation temperature.
12. air conditioner according to claim 9 is characterized in that, described high pressure phase depends on circulating mass of refrigerant and outer temperature degree when the desired value of saturation temperature during refrigerating operaton.
13. air conditioner according to claim 9 is characterized in that, described high pressure phase depends on the running frequency and the outer temperature degree of described compressor (101) during refrigerating operaton when the desired value of saturation temperature.
14., it is characterized in that described high pressure phase is revised when the desired value of saturation temperature, and described correction is caused by crossing thermal control or the temperature controlled deviation of target discharge pipe according to claim 12 or 13 described air conditioners.
15. air conditioner according to claim 14 is characterized in that, described high pressure phase is worked as saturation temperature when the desired value of saturation temperature with high pressure phase and is added that setting is as higher limit.
16. air conditioner according to claim 14 is characterized in that, the desired value that described high pressure phase is worked as saturation temperature adds that with present outer room temperature setting is as lower limit.
17. air conditioner according to claim 14, it is characterized in that, cold-producing medium is in service closes described liquid pipe motor-driven valve (128) when described high pressure phase when saturation temperature is lower than desired value, when described high pressure phase is opened described liquid pipe motor-driven valve (128) when saturation temperature is higher than desired value.
18. air conditioner according to claim 1 is characterized in that, warms oneself in service the typical value of liquid pipe temperature and the desired value of liquid pipe temperature to be compared to have judged whether unnecessary cold-producing medium.
19. air conditioner according to claim 18 is characterized in that, the typical value of described liquid pipe temperature adopts the minimum in the operating liquid pipe of indoor set (200) temperature.
20. air conditioner according to claim 18 is characterized in that, the desired value of the liquid pipe temperature in service of warming oneself depends on circulating mass of refrigerant and room temperature.
21. air conditioner according to claim 18 is characterized in that, the desired value of the liquid pipe temperature in service of warming oneself depends on the running frequency and the room temperature of compressor (101).
22. air conditioner according to claim 20 is characterized in that, the desired value of described liquid pipe temperature is revised, described correction is caused by crossing thermal control or the temperature controlled deviation of target discharge pipe.
23. air conditioner according to claim 22 is characterized in that, the desired value of described liquid pipe temperature is arranged in the high side of maximum of the temperature in the middle of the heat exchange as higher limit with high pressure saturation temperature or indoor heat converter (201).
24. air conditioner according to claim 22 is characterized in that, the desired value of described liquid pipe temperature adds that with the maximum of room temperature setting is as lower limit.
25. air conditioner according to claim 22 is characterized in that, opens flue motor-driven valve (129) when the typical value when liquid pipe temperature in service of warming oneself is lower than desired value, closes flue motor-driven valve (129) when the typical value of liquid pipe temperature is higher than desired value.
26. air conditioner according to claim 1 is characterized in that, the desired value that high pressure phase is worked as saturation temperature when saturation temperature and high pressure phase in service of warming oneself compares to have judged whether unnecessary cold-producing medium.
27. air conditioner according to claim 26 is characterized in that, the desired value that the high pressure phase in service of warming oneself is worked as saturation temperature depends on circulating mass of refrigerant and room temperature.
28. air conditioner according to claim 26 is characterized in that, the high pressure phase in service of warming oneself depends on the running frequency and the room temperature of described compressor (101) when the desired value of saturation temperature.
29., it is characterized in that described high pressure phase is revised when the desired value of saturation temperature, and described correction is caused by crossing thermal control or the temperature controlled deviation of target discharge pipe according to claim 27 or 28 described air conditioners.
30. air conditioner according to claim 29 is characterized in that, described high pressure phase is worked as saturation temperature when the desired value of saturation temperature with high pressure phase and is added that setting is as higher limit.
31. air conditioner according to claim 29 is characterized in that, the desired value that described high pressure phase is worked as saturation temperature adds that with room temperature setting is as lower limit.
32. air conditioner according to claim 26, it is characterized in that, warm oneself and in servicely when saturation temperature is lower than desired value, close described flue motor-driven valve (129) when described high pressure phase, when described high pressure phase is opened described flue motor-driven valve (129) when saturation temperature is higher than desired value.
CNB018021328A 2000-07-26 2001-07-24 Air conditioner Expired - Fee Related CN1170095C (en)

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WO2002008674A1 (en) 2002-01-31
KR20020035138A (en) 2002-05-09

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