CN106482375A - Air conditioner - Google Patents
Air conditioner Download PDFInfo
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- CN106482375A CN106482375A CN201610597027.2A CN201610597027A CN106482375A CN 106482375 A CN106482375 A CN 106482375A CN 201610597027 A CN201610597027 A CN 201610597027A CN 106482375 A CN106482375 A CN 106482375A
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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
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
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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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- 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
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
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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
- F25B2500/00—Problems to be solved
- F25B2500/28—Means for preventing liquid refrigerant entering into the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2101—Temperatures in a bypass
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The present invention provides a kind of air conditioner, and which is provided with gas-liquid separator, and which is by preventing liquid backflow phenomenon, it is possible to increase the efficiency of air adjustment, is capable of the reliability of height-regulating device.The air conditioner possesses：Temperature sensor (51), which is in the temperature of the downstream measurement cold-producing medium of the flow control division (8) of bypass pipe arrangement (9)；Temperature sensor (52), its be connected to the connecting portion with bypass pipe arrangement of main pipe arrangement (10) of compressor (11) near two pipe arrangement of measurement interflow before cold-producing medium temperature；And control unit (50), the detection temperature of its detection temperature based on temperature sensor and temperature sensor, it is controlled in the way of adjusting the flow of the gas refrigerant adjusted by flow control division.Control unit by make the detection temperature of temperature sensor and the difference of the detection temperature of front temperature sensor in optimal ceiling temperature poor with poorer than the poor low optimal lower limit temperature of the optimal ceiling temperature between in the way of carry out above-mentioned control.
Description
Technical field
The present invention relates to air conditioner.
Background technology
As the background technology of the art, with Japanese Unexamined Patent Publication 2008-45837 publication (patent document 1).The public affairs
Report describe " a kind of conditioner for possessing the gas bypass circuit to compressor suction side bypass gases cold-producing medium, on
State gas refrigerant to be isolated by the gas-liquid separator being located between expansion valve and outdoor heat converter, the air is adjusted
Regulating device possesses：Flow control valve, its adjust the flow of gas bypass circuit；Detection means, which is to supplying to outdoor heat converter
Give by the fluid exit section of the gas-liquid separator in the liquid refrigerant loop of the separated liquid refrigerant of gas-liquid separator
Detected with the pressure differential of the fluid entry section of outdoor heat converter；And control device, which is adjusted according to above-mentioned pressure differential
The aperture of throttling adjustable valve " (with reference to summary).
Prior art literature
Patent document
Patent document 1：Japanese Unexamined Patent Publication 2008-45837 publication
Content of the invention
Above-mentioned patent document 1 describes following point, carries out the opening of flow control valve of gas bypass circuit according to pressure differential
The regulation of degree, above-mentioned pressure differential are to supply by the liquid system of the separated liquid refrigerant of gas-liquid separator to outdoor heat converter
The fluid exit section of the gas-liquid separator in refrigerant circuit and the pressure differential of the fluid entry section of outdoor heat converter.
However, the technology for patent document 1, it is impossible to prevent liquid refrigerant from also bypassing to pressure through gas bypass circuit
The liquid backflow phenomenon of contracting machine entrance side, it is impossible to prevent the efficiency of air adjustment from reducing and the reliability of air conditioner reduces.
Therefore, the problem of the present invention is to provide a kind of air conditioner, and which is provided with gas-liquid separator, it is possible to increase air adjustment
Efficiency, and the reliability of device can be improved.
In order to solve above-mentioned problem, a scheme of the present invention is a kind of air conditioner, possesses outdoor heat converter, Indoor Thermal and hands over
Parallel operation, compressor, expansion valve, cross valve and the main pipe arrangement that they are connected, above-mentioned to change by switching above-mentioned cross valve
So as to carry out air adjustment, above-mentioned air conditioner is characterised by possessing gas-liquid separator, and which is located at for the flowing of the cold-producing medium in each portion
Connect the side for being provided with above-mentioned expansion valve in the above-mentioned main pipe arrangement of above-mentioned outdoor heat converter and above-mentioned indoor heat converter, right
The cold-producing medium flowed into from above-mentioned main pipe arrangement carries out gas-liquid separation, as above-mentioned expansion valve, possesses：First expansion valve, its be located at than
Above-mentioned gas-liquid separator is by the upstream side of the flowing of the cold-producing medium of above-mentioned main pipe arrangement during refrigeration；And second expansion valve, which is located at
The upstream side of the flowing of the above-mentioned cold-producing medium of above-mentioned main pipe arrangement during than above-mentioned gas-liquid separator by heating, above-mentioned air conditioner possess：
The above-mentioned main pipe arrangement of bypass pipe arrangement, its above-mentioned gas-liquid separator of connection and the entrance side for being connected to above-mentioned compressor；Flow-rate adjustment
Portion, its are located in above-mentioned bypass pipe arrangement, and the flow of the gas refrigerant from above-mentioned gas-liquid separator is adjusted；First
Temperature sensor, its are located at the above-mentioned flow control division downstream than above-mentioned bypass pipe arrangement；Second temperature sensor, its are located at
Between the connecting portion with above-mentioned bypass pipe arrangement of above-mentioned main pipe arrangement and above-mentioned cross valve；And control unit, which is based on above-mentioned first
The detection temperature of temperature sensor and the detection temperature of above-mentioned second temperature sensor, to adjusted using above-mentioned flow control division
The flow of gas refrigerant is controlled.
In addition, the another way of the present invention is a kind of air conditioner, which possesses outdoor heat converter, indoor heat converter, pressure
Contracting machine, expansion valve, cross valve and the main pipe arrangement for connecting them, change above-mentioned each portion by switching above-mentioned cross valve
So as to carry out air adjustment, above-mentioned air conditioner is characterised by possessing gas-liquid separator for the flowing of cold-producing medium, and which is located in connection
The side for being provided with above-mentioned expansion valve in the above-mentioned main pipe arrangement of outdoor heat converter and above-mentioned indoor heat converter is stated, to from above-mentioned
The cold-producing medium that main pipe arrangement is flowed into carries out gas-liquid separation, and above-mentioned expansion valve is located at than above-mentioned gas-liquid separator by above-mentioned during cooling operation
The upstream side of the flowing of the cold-producing medium of main pipe arrangement, above-mentioned air conditioner possess：Bypass pipe arrangement, its above-mentioned gas-liquid separator of connection and company
Be connected to above-mentioned compressor above-mentioned refrigeration when entrance side above-mentioned main pipe arrangement；Flow control division, its are located at above-mentioned bypass pipe arrangement
In, and the flow of the gas refrigerant from above-mentioned gas-liquid separator is adjusted；First temperature sensor, which is located at than upper
State the above-mentioned flow control division downstream of bypass pipe arrangement；Second temperature sensor, above-mentioned master when which is located at cooling operation are joined
Between the connecting portion with above-mentioned bypass pipe arrangement of pipe and above-mentioned indoor heat converter；And control unit, its in cooling operation, base
In the detection temperature of above-mentioned first temperature sensor and the detection temperature of above-mentioned second temperature sensor, to being adjusted using above-mentioned flow
The flow of the gas refrigerant that section portion is adjusted is controlled.
The effect of invention
In accordance with the invention it is possible to provide a kind of air conditioner, which is provided with gas-liquid separator, it is possible to increase the effect of air adjustment
Rate, and the reliability of device can be improved.
For problem other than the above, structure and effect, will become more clear by the explanation of following embodiment.
Description of the drawings
Fig. 1 is the integrally-built explanatory diagram of the air conditioner that embodiments of the invention 1 are described.
Fig. 2 be represent one embodiment of the invention, based on control unit, the block figure of the control system of air conditioner.
Fig. 3 is the chart of the effect of the air conditioner that one embodiment of the invention is described by p-h line chart.
Fig. 4 is the effect of the air conditioner that one embodiment of the invention is described by temperature difference and cryogen gaseous ratio
Chart.
Fig. 5 is the flow chart of the action of the air conditioner that one embodiment of the invention is described.
Fig. 6 is the aperture by flow control division and temperature difference the effect of the air conditioner of one embodiment of the invention to be described
Chart.
Fig. 7 is, by the time change of the aperture of flow control division and temperature difference, the sky of one embodiment of the invention is described
The chart of the effect of tune machine.
Fig. 8 is the integrally-built explanatory diagram of the air conditioner that embodiments of the invention 2 are described.
Fig. 9 is the integrally-built explanatory diagram of the air conditioner that embodiments of the invention 3 are described.
The explanation of symbol
1 air conditioner, 2 cross valves, 3 outdoor heat converters, 4 expansion valves (the first expansion valve), 5 expansion valves
(the second expansion valve), 6 indoor heat converters, 7 gas-liquid separators, 8 flow control divisions, 9 bypass pipe arrangements, 10 masters are joined
Pipe, 11 compressors, 50 control units, 51 first temperature sensors, 52 second temperature sensors, the optimal upper limit of dTu
Temperature difference (first reference value), the optimal lower limit temperature of dTl poor (the second a reference value).
Specific embodiment
As the method that the efficiency for realizing freeze cycle is improved, it is known that realize the pressure loss of the low-pressure side in freeze cycle
Reduction method.For example, above-mentioned patent document 1 discloses that a kind of conditioner, which is handed over outdoor heat in expansion valve
Pipe arrangement between parallel operation possesses gas-liquid separator, bypasses by the gas of the gas-liquid separator separates to the refrigerant inlet side of compressor
The gas bypass circuit of cryogen and adjust the gas bypass circuit gas refrigerant flow flow control valve.
This be using gas-liquid separator to little to heat exchange contribution gas refrigerant in the cold-producing medium that flows into evaporimeter
Separated.So, by the liquid refrigerant for only having separated gas refrigerant is createed to evaporimeter, can reduce freezing
The refrigerant pressure loss of the low-pressure side in circulation (is born when cold-producing medium is by heat exchanger and is made from the frictional resistance of pipe arrangement
The phenomenon of the pressure drop of cryogen).In addition, the aridity of the cold-producing medium by making evaporator inlet reduces, evaporator inlet is made
Enthalpy reduce, obtain the enthalpy difference of larger evaporimeter such that it is able to the cooling that compensation causes because the internal circulating load of cold-producing medium reduces
The reduction of ability, therefore improves air-conditioner efficiency.
Here, in patent document 1, for the gas system in the two-phase system cryogen according to the entrance for flowing into gas-liquid separator
The amount of cryogen adjusting the aperture of flow control valve, according to the outlet of the liquid refrigerant of gas-liquid separator and outdoor heat converter
The variation detection of the pressure differential of liquid refrigerant entrance has been mixed into gas refrigerant in liquid refrigerant loop, and then to being located at
The aperture of the flow control valve of gas bypass circuit is adjusted.
But, as preventing the aperture for opening above-mentioned flow control valve excessive and liquid refrigerant inflow gas bypass pipe arrangement
Liquid backflow phenomenon control, only using make pressure differential fix minimum aperture carry out as the target aperture of flow control valve
Aperture regulation.That is, in so that flow control valve is operated with optimal aperture, even if there occurs due to the variation of air conditioner load
Liquid backflow phenomenon, also due to the pressure of saturated liquid cold-producing medium is not changed in itself and above-mentioned pressure differential is fixed, and can not
Judge the generation of liquid backflow phenomenon.
Accordingly, there exist due to liquid backflow phenomenon and the minimizing of the liquid refrigerant of Returning evaporimeter, the efficiency of air adjustment
The problem of reduction.In addition, from gas-liquid separator to compressor, cold-producing medium was returned originally in the way of gas refrigerant, and present
Liquid refrigerant has also returned to compressor, therefore there is also the relatively low problem of the reliability of compressor.
Hereinafter, for the embodiments of the invention that can solve the problem that these problems, have multiple examples and illustrate.
Embodiment 1
Fig. 1 is the integrally-built explanatory diagram of the air conditioner for representing embodiments of the invention 1.
Air conditioner 1 is generally made up of off-premises station 60 and indoor set 61.And, air conditioner 1 is for possessing outdoor heat converter
3rd, indoor heat converter 6, compressor 11, expansion valve 4 and 5, cross valve 2 and the main pipe arrangement 10 that is attached these etc. is cold
Freeze EGR, and can optionally be made by the flowing of the cold-producing medium in the above-mentioned each portion of the switching change of cross valve 2
Cold or heat.
That is, when being heated, by the switching state of cross valve 2 shown in solid in Fig. 1, cold-producing medium is made along solid line arrow
The direction circulation of head.It is, the liquid refrigerant of low pressure, low temperature is by the outdoor heat converter 3 as evaporimeter and outdoor
Air carries out heat exchange and gasifies, absorbs heat, and becomes gas refrigerant.The gas refrigerant is transported to compressor through cross valve 2
11, and be formed as high temperature, high pressure in compressor 11, then indoor heat converter 6 is delivered to through cross valve 2.In this case, indoor
Heat exchanger 6 as condenser, gas refrigerant carry out heat exchange with room air and liquefy, heat release, so as to become high temperature, height
The liquid refrigerant of pressure.Then, the liquid refrigerant is expanded by the expansion valve 5 as the second expansion valve and is formed as low
Temperature, the liquid refrigerant (gas-liquid two-phase cold-producing medium) of low pressure, and return outdoor heat converter 3.
On the other hand, when being freezed, by the switching state of cross valve shown in dotted lines in Figure 12, cold-producing medium edge is made
The direction circulation of dotted arrow.That is, low pressure, the liquid refrigerant of low temperature gasified by the indoor heat converter 6 as evaporimeter,
Absorb heat and become gas refrigerant.The gas refrigerant is transported to compressor 11 through cross valve 2, and is formed as in compressor 11
High temperature, high pressure, are then delivered to outdoor heat converter 3 through cross valve 2.In this case, outdoor heat converter 3 is used as condenser,
Gas refrigerant liquefaction, heat release, become the liquid refrigerant of high temperature, high pressure.Then, the liquid refrigerant is swollen by being used as first
The expansion valve 4 of swollen valve is expanded and is formed as the liquid refrigerant (gas-liquid two-phase cold-producing medium) of low temperature, low pressure, and is returned indoor
Heat exchanger 6.It is the action of basic freeze cycle above.
In connection outdoor heat converter 3 and the side main pipe arrangement 10, being provided with expansion valve 4,5 of indoor heat converter 6, if
Have carries out the gas-liquid separator 7 of gas-liquid separation to the cold-producing medium flowed into from main pipe arrangement 10.Gas-liquid separator 7 is following device, its
Two-phase system cryogen is separated into liquid refrigerant and gas refrigerant using gravity, centrifugation force, surface force etc., and obtain as
Good separative efficiency down：From bypass pipe arrangement 9 usually can only eluting gas cold-producing medium, (freeze with two-phase from main pipe arrangement 10
The pipe arrangement of the contrary side in the inflow side of agent) substantially being capable of only trickle cold-producing medium.
And, as described above, in cooling operation, the ratio gas-liquid separator 7 located at main pipe arrangement 10 leans on the flowing of cold-producing medium
Upstream side expansion valve 4 be the first expansion valve, in heating operation, located at main pipe arrangement 10 ratio gas-liquid separator 7 by freeze
The expansion valve 5 of the upstream side of the flowing of agent is the second expansion valve.
Bypass pipe arrangement 9 connects the entrance side of gas-liquid separator 7 and compressor 11.Additionally, symbol 12 is for preventing liquid
The Suction cop of the return of cold-producing medium.In addition, the temperature for being provided with the outlet refrigerant temperature of detection compressor 11 in compressor 11 is passed
Sensor 53.
Flow control division 8 is in bypass pipe arrangement 9, and the flow of the gas refrigerant from gas-liquid separator 7 is carried out
Adjust.Flow control division 8 can adjust aperture, and expect using the expansion valve that can be closed bypass pipe arrangement 9 in minimum aperture.
Or, it is also possible to be configured to only to be opened and closed the two-way valve of two actions, fixation as the capillary of flow path resistance and unidirectional
Valve is connected.
The conduct of the temperature of measurement cold-producing medium is provided with the position of the side farther downstream of specific discharge adjustment portion 8 of bypass pipe arrangement 9
The temperature sensor 51 of the first temperature sensor.
In addition, between the linking part with bypass pipe arrangement 9 and cross valve 2 of main pipe arrangement 10, in the example of Fig. 1, in connection
The position of the positive front side with the interflow of bypass pipe arrangement 9 of the main pipe arrangement 10 of the entrance side of cross valve 2 and compressor 11 is provided with measurement
The temperature sensor 52 as second temperature sensor of the temperature of cold-producing medium.
And, outdoor heat converter 3, indoor heat converter 6 be also respectively equipped with detection temperature temperature sensor 54,
55.Temperature sensor 51～55 is the thermometer of thermal resistor etc., and which is fixed on pipe arrangement 9,10 by using spring etc. to examine
Testing temperature.
Control unit 50 is the control device of control air conditioner 1.Fig. 2 is based on control unit 50, represents the control of air conditioner 1
The block figure of system processed.Control unit 50 is mainly made up of such as microcomputer, its through predetermined interface respectively with temperature sensor
51～55, cross valve 2 (driver), compressor 11 (driver), expansion valve 4 and 5 (driver), flow control division 8
(driver) connects.
Below, the distinctive action to air conditioner 1 as above is described in detail.
First, gas-liquid separation circulation pattern during heating operation is described.In FIG, when switching cross valve 2 so that
When the direction (solid arrow direction) that cold-producing medium represents along solid line is flowed, cold-producing medium is according to compressor 11 (outlet), cross valve
2nd, indoor heat converter 6, expansion valve 5, gas-liquid separator 7, expansion valve 4, outdoor heat converter 3, cross valve 2, compressor 11 (
Entrance) sequential flowing.Expansion valve 5 is adjusted to the aperture of the appropriateness for corresponding to air conditioner load by control unit 5, by indoor heat exchange
The cold-producing medium that device 6 is condensed and liquefied becomes gas-liquid two-phase flow by expansion valve 5, and flows into gas-liquid separator 7.
Then, the aperture of flow control division 8 is adjusted, and makes the cold-producing medium liquid system is completely separated into by gas-liquid separator 7
Cryogen and gas refrigerant, and liquid refrigerant flowed into outdoor heat converter 3, and gas refrigerant is to the entrance of compressor 11
Flow into.The liquid refrigerant is fully evaporated by outdoor heat converter 3, and the entrance side in compressor 11 with divide from gas-liquid
Collaborate through the gas refrigerant that bypass pipe arrangement 9 is flowed into from device 7, return to compressor 11.
For the effect of such freeze cycle, illustrated by the Mollier diagram shown in Fig. 3.Fig. 3 is to represent p-h line
The chart of figure.Symbol 101 represents saturated liquid line, and symbol 102 represents saturated vaporline.In figure 3, dotted line represents not possess gas
The state of liquid/gas separator 7 and bypass pipe arrangement 9, air conditioner 1 in the case of common freeze cycle cold-producing medium.That is, symbol A4
Represent change of the cold-producing medium in the state of compressor 11 between → A1.Represent cold-producing medium in condenser (Indoor Thermal between symbol A1 → A2
Exchanger 6) state change.Represent change of the cold-producing medium in the state of expansion valve 4 between symbol A2 → A3.Between symbol A3 → A4
Represent change of the cold-producing medium in the state of evaporimeter (outdoor heat converter 3).
In contrast, the heavy line of Fig. 3 represents that possessing gas-liquid separator 7 and bypass pipe arrangement 9, the present embodiment gas-liquid divides
The state of the cold-producing medium of the air conditioner 1 in the case of the circulation pattern.That is, represent cold-producing medium in compressor 11 between symbol B4 → B1
State change.Represent change of the cold-producing medium in the state of condenser (indoor heat converter 6 (when heating)) between symbol B1 → B2
Change.Represent change of the cold-producing medium in the state of expansion valve 4 between symbol B2 → B3.Represent cold-producing medium in evaporimeter between symbol B3 → B4
The change of the state of (outdoor heat converter 3).Additionally, illustrating with carrying out for trickle spaced and parallel of heavy line and dashed interval
Part, actually two line overlaps, but for convenience, be spaced trickle interval and illustrated.
In the gas-liquid separation circulation, between symbol B3 → B4, line is two intervals, and interval B 33 represents is joined by bypass
The cold-producing medium of pipe 9, interval B 34 represent the cold-producing medium for flowing to evaporimeter (outdoor heat converter 3) by main pipe arrangement 10.Will be by gas-liquid
The separated gas refrigerant of separator 7 is to entrance guiding (B32) of compressor 11, by remaining liquid refrigerant to evaporimeter
(outdoor heat converter 3 (when heating)) guides (B31), so as to as shown in figure 3, the ratio of evaporimeter (outdoor heat converter 3) entrance
Enthalpy reduces from ha to hb, and the ratio enthalpy difference of evaporimeter (outdoor heat converter 3) becomes big, and then cooling capacity increases.And, gas system
The refrigerant flow to evaporimeter (outdoor heat converter 3) of cryogen reduces, and refrigerant pressure loss reduces, so as to compressor 11
Suction pressure rise from pa to pb, and then cold-producing medium suction density increase, cooling capacity increase.The result is, and usual
Freeze cycle be compared, improve efficiency.
Next, Fig. 3, Fig. 4 is used, to the flow for having given play to the effect of gas-liquid separation circulation pattern to greatest extent
The action of adjustment portion 8 is illustrated.
The two-phase system cryogen for flowing into gas-liquid separator 7 is separated into gas refrigerant and liquid refrigerating by gas-liquid separator 7
Agent, and gas refrigerant, to the entrance inflow of compressor 11, liquid refrigerant is flowed into outdoor heat converter 3.Divide in gas-liquid
From device 7, using gravity, in lower section storing liquid, liquid surface is carried out by the pressure balance with the gas refrigerant of surrounding
Keep.Now, the gas refrigerant after being separated by gas-liquid separator 7 is gas-liquid separator 7 in the upstream side of flow control division 8
The saturation temperature (temperature T1) (B32) of internal two-phase system cryogen.By flow control division 8, after being separated by gas-liquid separator 7
Gas refrigerant be decompressed to B4 in specific enthalpy.
And, according to the aperture of flow control division 8, control the gas refrigerant after gas-liquid separation to 11 side of compressor
Quantity delivered.In the case that gas refrigerant quantity delivered is few, due to the 8 upstream side of specific discharge adjustment portion of bypass pipe arrangement 9
The environment temperature of pipe arrangement, gas refrigerant are heated, and increase when being reduced pressure than thermal insulation so as to temperature.
On the other hand, the liquid refrigerant (B31) of evaporimeter (outdoor heat converter 3 (when heating)) is flowed into from outside
Air heat absorption, evaporate and become gas refrigerant, and towards after entrance side and the above-mentioned gas-liquid separation of compressor 11
Gas refrigerant interflow (B4).Now, by outdoor heat converter 3, temperature reduces the liquid refrigerant of gasification, becomes temperature
Degree T2.The magnitude relationship of temperature is usually T2 ＜ T1.As shown in figure 4, carrying out the gas after gas-liquid separation by gas-liquid separator 7
Refrigerant amount is more, and the temperature difference " T1-T2 " is less.
When the aperture for arranging flow control division 8 is excessive, in gas-liquid separator 7, the reduced pressure of gas, liquid surface
Can not keep, foaming is produced, the gas refrigerant (liquid backflow phenomenon) of bypass pipe arrangement 9 is mixed into so as to liquid refrigerant.When
In gas refrigerant after gas-liquid separation during doping liquid refrigerant, to the liquid system that evaporimeter (outdoor heat converter 3) is flowed into
Cryogen is greatly decreased, and with respect to the heat-shift that air has, the heat that cold-producing medium can be exchanged is reduced, so as to liquid refrigerant
Excessively vaporization, refrigerant superheat, become " T2 ＞ T1 ", temperature T1 is overturned with the temperature difference of temperature T2.
Therefore, the temperature of cold-producing medium is detected by temperature sensor 51 and temperature sensor 52, according to the big of its temperature difference
Little relation, is adjusted the control of flow control division 8 by control unit 50, so that the liquid for being produced gas by gas-liquid separator 7 divides
Maximum from effect, wherein, temperature sensor 51 is in downstream detection connection gas-liquid separator 7 and the compressor of flow control division 8
Temperature T1 of the bypass pipe arrangement 9 of 11 sides, temperature sensor 52 detect connection compressor 11 and cross valve 2 main pipe arrangement 10 in
Temperature T2 of the part before the interflow of bypass pipe arrangement 9.
During the gas-liquid separation effect maximum produced by gas-liquid separator 7, during ideally for temperature difference " T1-T2 " for 0,
But the manufacture deviation of the thermal resistor used due to temperature sensor, the difference of refrigerant temperature and pipe arrangement surface temperature,
And pipe arrangement surface and the reasons such as the thermal contact resistance of thermal resistor, not temperature T1 is mutually synthermal (temperature difference with temperature T2
" T1-T2 " is not 0).
Accordingly, as target temperature poor " T1-T2 ", enter in the way of the absolute value of the temperature difference " T1-T2 " becomes minimum
Row control.
The effect that the evaporating pressure loss of this gas-liquid separation circulation pattern reduces is big.That is, as main pipe arrangement 10 is longer, system
The internal circulating load of cryogen is more, and the pressure loss of cold-producing medium is bigger, the effect is significant that therefore evaporating pressure loss reduces.Conversely,
In the case that the internal circulating load of cold-producing medium is few, effect diminishes.Therefore, the low-pressure side of cold-producing medium main pipe arrangement 10 short heat fortune
When turning, in air conditioner load, the rotating speed of little and compressor 11 is low and in the case that the internal circulating load of cold-producing medium is few, it is also possible to not to pass through
Flow control division 8 adjusts the gas-liquid separation circulation pattern of flow and the common cyclic module to completely close flow control division 8
Formula is operated, it is also possible to according to circumstances switched.
Next, illustrating to gas-liquid separation circulation pattern during cooling operation.In this case, in FIG, as dotted line
Shown cross valve 2 is switched over, so that cold-producing medium is flowed along dotted arrow direction, so as to cold-producing medium according to compressor 11 (
Outlet side), cross valve 2, outdoor heat converter 3, expansion valve 4, gas-liquid separator 7, expansion valve 5, indoor heat converter 6, four-way
Valve 2, the sequential flowing of compressor 11 (entrance side).
Expansion valve 4 is adjusted to the aperture of the appropriateness for corresponding to air conditioner load, is fully condensed by outdoor heat converter 3 and liquefies
Cold-producing medium gas-liquid two-phase flow become by expansion valve 4, and flow into gas-liquid separator 7.Adjust opening for flow control division 8
Degree, makes the cold-producing medium be completely separated into liquid refrigerant and gas refrigerant by gas-liquid separator 7, and liquid refrigerant is supplied
Give to indoor heat converter 6, gas refrigerant is supplied to the entrance side of compressor 11.Liquid refrigerant passes through indoor heat converter
6 are fully evaporated, and the entrance side in compressor 11 and the gas refrigerant flowed into through bypass pipe arrangement 9 from gas-liquid separator 7
Interflow, returns to compressor 11
For the effect of the common freeze cycle illustrated with reference to Fig. 3 in the above-mentioned explanation for heating, except outdoor heat
Beyond the effect of exchanger 3 and indoor heat converter 6 is contrary, other are also identical in the refrigeration case, therefore omit the description.
Below, the flow for playing the effect of the gas-liquid separation circulation pattern in the case of freezing to greatest extent is adjusted
The action in section portion 8 is illustrated.
The two-phase system cryogen for flowing into gas-liquid separator 7 is separated into gas refrigerant and liquid refrigerant, and gas refrigeration
Agent is flowed into the entrance side inflow of compressor 11, liquid refrigerant to indoor heat converter 6.In gas-liquid separator 7, using weight
Power, in lower section storing liquid cold-producing medium, liquid surface is kept by the pressure balance with the gas refrigerant of surrounding.This
When, the gas refrigerant after being separated by gas-liquid separator 7 is the inside of gas-liquid separator 7 in the upstream side of flow control division 8
The saturation temperature (temperature T1 (Fig. 3)) of two-phase system cryogen.
On the other hand, the liquid refrigerant of inflow indoor heat exchanger 6 is absorbed heat from air, while evaporation, becomes gas
Cryogen, and towards compressor 11 entrance side with above-mentioned by the detached gas refrigerant of gas-liquid separator 7 interflow.By stream
The aperture of amount adjustment portion 8, the gas refrigerant after being separated by gas-liquid separator 7 is depressurized, and flow is conditioned.In the gas
In the case that refrigerant amount is few, as the environment temperature of bypass pipe arrangement 9, gas are heated, increase when temperature is reduced pressure than thermal insulation
High.
On the other hand, the liquid refrigerant of inflow indoor heat exchanger 6 is absorbed heat from air, while evaporation, becomes gas
Cryogen, and entrance side and the above-mentioned detached gas refrigerant interflow towards compressor 11.Now, the liquid system of gasification
By outdoor heat converter 3, temperature reduces cryogen, becomes temperature T2 (Fig. 3).Now, the magnitude relationship of temperature is " T2 ＜ T1 "
(Fig. 3).As described in Figure 4, by gas-liquid separator 7 separate after gas refrigeration dosage more, the temperature difference " T1-T2 " (Fig. 4)
Less.
Here, when the aperture for arranging flow control division 8 is excessive, in gas-liquid separator 7, the pressure drop of gas refrigerant
Low, it is impossible to keep liquid interface and produce foaming, liquid refrigerant is mixed into bypass pipe arrangement 9 (liquid backflow phenomenon).
So as to, when by gas-liquid separator 7 carry out gas-liquid separation and in the gas refrigerant for flowing to bypass pipe arrangement 9 adulterate
During liquid refrigerant, the liquid refrigerant flowed into indoor heat converter 6 is greatly decreased, with respect to the exchange that room air has
Heat, the heat that cold-producing medium can be exchanged are reduced, and therefore, liquid refrigerant is exceedingly gasified and refrigerant superheat, temperature
T1 and temperature T2 become " T2 ＞ T1 ", and temperature difference is overturned.
Therefore, detection temperature is distinguished by temperature sensor 51 and temperature sensor 52, is closed according to the size of its temperature difference
System, by control unit 50 control flow control division 8 so that gas-liquid separation effect is maximum, i.e. temperature difference " T1-T2 " (Fig. 4) exhausted
Become minimum to value, wherein, temperature sensor 51 detects the temperature of the bypass pipe arrangement 9 of connection gas-liquid separator 7 and 11 side of compressor
Degree T1, temperature sensor 52 detect connection compressor 11 and 2 side of cross valve main pipe arrangement 10 in bypass pipe arrangement 9 collaborate before
Partial temperature T2.
And, identical with during heating operation, because gas-liquid separation circulation pattern in the case that the internal circulating load of cold-producing medium is few
Effect reduce, therefore, with vulgar carry out cooling operation when, it is also possible to not with gas-liquid separation circulation pattern, and according to circumstances
Switching, for example, flow control division 8 is completely closed, is operated etc. with common freeze cycle pattern.
Hereinafter, with reference to Fig. 5, the specific control method of the action to illustrating is illustrated.Fig. 5 is that explanation supplies control unit
The flow chart of the content of 50 controls for executing.
First, by the air conditioner 1 that starts running, present treatment starts.After operation start, even if to open flow control division 8
The mode of violent cyclical variations will not be also produced, judges whether to obtain the license of gas-liquid separation circulation pattern (S1).In control
In portion 50, in the case of the license of gas-liquid separation circulation pattern is not obtained (NO of S1), S1 is returned.Here, conduct is being opened
During flow control division 8, freeze cycle becomes the main cause of not temperature, it is believed that be, after operation of air conditioner starts, as described above
Air conditioner load little (inner air and outer air temperature difference is little), as described above circulating mass of refrigerant few (rotating speed of compressor 11 is little), due to
Product unqualified and flow control division 8 exist leakage etc..In order to avoid these main causes, forbid gas-liquid in a case where
Separate circulation pattern：The difference for starting inside and outside portion's air themperature of rear set time and room temperature in operation of air conditioner is under fixed value,
Compressor rotary speed is below the desired speed, the temperature of above-mentioned temperature T2 of above-mentioned temperature T1 of bypass pipe arrangement 9 and pipe arrangement 10
Degree difference is such as the following for fixed value.In this case, flow control division 8 is completely closed, gas-liquid separation circulation pattern is not carried out, and is entered
The common freeze cycle pattern of row.
In the case of the license of gas-liquid separation circulation pattern is obtained (YES of S1), gas-liquid separation cyclic module is switched to
Formula, executes following process as gas-liquid separation circulation pattern.That is, by connecting gas-liquid separator 7 and 11 side of compressor
Temperature sensor 51 that temperature T1 of bypass pipe arrangement 9 is detected and to the interflow of bypass pipe arrangement 9 before main pipe arrangement 10 temperature
The temperature sensor 52 detected by degree T2, difference detection temperature T1, temperature T2.Then, according to the size of temperature difference " T1-T2 "
Relation adjusts flow control division 8.
For example, in heating operation (for example, if 7 DEG C of outside air temperature, 20 DEG C of indoor air temperature), close in flow control division 8
In the case of, T1=7 DEG C, T2=0 DEG C, therefore T1-T2=7 DEG C.When flow control division 8 is opened, as shown in fig. 6, flow is adjusted
The aperture in section portion 8 is bigger, and temperature difference " T1-T2 " is less, and " T1=T2 " (T1-T2=0) for gas-liquid separation circulate optimal
State.
Here, as temperature sensor 51,52, although the product with the structure for making thermal resistor etc. contact with tube wall
Deng, but, because the error containing thermal contact resistance etc., exist somewhat with the optimum state (T1=T2) of gas-liquid separation circulation
Amplitude.That is, set under optimal ceiling temperature difference dTu (first reference value) and slightly lower optimal of dTu poorer than optimal ceiling temperature
Limit temperature difference dTl (the second a reference value).For example, if dTu=1 DEG C, dTl=0 DEG C.
Next, it is determined whether " T1-T2 ＜ dTu " and " T1-T2 ＞ dTl ", i.e. whether " T1-T2 " is in optimal upper limit temperature
Scope (S2) between degree difference dTu and optimal lower limit temperature difference dTl.If here, temperature difference " T1-T2 " is that optimal lower limit temperature is poor
Below dTl (excessively opens flow control division 8), then be easy to produce liquid backflow phenomenon.Fig. 6 is represented in the case of dTl=0 DEG C
, temperature difference " T1-T2 ", the aperture of flow control division 8, the figure of the relation of liquid backflow phenomenon, it illustrates, in temperature difference
When " T1-T2 " (excessively opens flow control division 8) below for 0 (optimal lower limit temperature difference dTl), it is easy to produce liquid backflow existing
As.Conversely, if temperature difference " T1-T2 " is optimal ceiling temperature difference more than dTu (excessively closing flow control division 8), gas-liquid is divided
The effect of script can not be played from device 7.
At " T1-T2 ＜ dTu " and when " T1-T2 ＞ dTl " (YES of S2), gas-liquid separation circulation pattern is with optimal state
Operated, therefore S1 is returned, the aperture of flow control division 8 is maintained the statusquo.
On the other hand, when not being " T1-T2 ＜ dTu " and " T1-T2 ＞ dTl " (NO of S2), S3 is entered.Then, exist
When " T1-T2 >=dTu " (YES of S3), flow control division 8 is opened scheduled volume (S4).As long as the process is repeated, flow is adjusted
The aperture in section portion 8 gradually will expand.When not being " T1-T2 >=dTu " (NO of S3), S5 is entered.Then, " T1-T2≤
During dTl " (YES of S5), flow control division 8 is closed scheduled volume (S4).As long as the process is repeated, flow control division 8
Aperture will be gradually reduced.When the process of S5 has been carried out, S1 is returned.When not being " T1-T2≤dTl " (NO of S5), also return
Return S1.
Fig. 7 is the time change for representing carry out, temperature difference " T1-T2 " and the aperture of flow control division 8 according to the control
Chart.Solid line represents temperature difference " T1-T2 ", and dotted line represents the aperture of flow control division 8.The rwo is in same time correlation
Connection.
As shown in fig. 7, control unit 50 increases the aperture of flow control division 8, until it reaches optimal lower limit temperature difference dTl, when
When temperature difference " T1-T2 " is less than optimal lower limit temperature difference dTl, the aperture of flow control division 8 is reduced, is finally controlled to temperature difference
" T1-T2 " is stable between optimal ceiling temperature difference dTu and optimal lower limit temperature difference dTl.
If temperature difference " T1-T2 " is set at less than value, i.e. T2 ＞ T1, temperature T1 and the temperature of optimal lower limit temperature difference dTl
The temperature difference of T2 is overturned, then adulterate in the gas refrigerant after being separated by gas-liquid separator 7 liquid refrigerant, produces liquid and returns
Flow phenomenon, has that the reliability of compressor 11 is impaired, therefore, it is desirable to the configuration bit corresponding to temperature sensor 51,52
Put, state, optimal ceiling temperature difference dTu and optimal lower limit temperature difference dTl be safety value.Of course it is desirable to optimal ceiling temperature is poor
The difference of dTu dTl poor with optimal lower limit temperature is reduced in the scope that this discomfort does not occur as best one can.
Same control is also carried out in the case of cooling operation, so as to producing after being separated by gas-liquid separator 7
Gas refrigerant in adulterate liquid refrigerant liquid backflow phenomenon, be able to carry out obtaining gas-liquid separation effect to greatest extent
Control.
Additionally, in the present embodiment, it is illustrated based on the control of gas-liquid separation circulation pattern, but as freezing
The overall control of circulation, based on the exhaust temperature of the cold-producing medium of the compressor 11 for for example being detected by temperature sensor 53, also same
The overall control of Shi Jinhang freeze cycle.Now, in order to the variation of freeze cycle is suppressed to Min., in flow control division
During 8 open, it is also possible to the rotating speed of fixing compressor 11.
In addition, in the present embodiment, it is desirable in stopping operation of air conditioner, and after compressor 11 also stops, by Flow-rate adjustment
Portion 8 fully opens.The fixation of the valve of the flow control division 8 when this is to prevent air conditioner 1 from stopping for a long time.
And, in the case that the air conditioner 1 by the present embodiment is moved etc., need refrigerant-recovery operating is carried out, and make
Cryogen reclaims the operating operated as under kind of refrigeration cycle, now expects not opening flow control division 8.
The air conditioner 1 of the present embodiment from the description above, is prevented from due to liquid backflow phenomenon and Returning evaporimeter
Liquid refrigerant reduce, it is possible to increase the efficiency of air adjustment.In addition, being also prevented from following discomfort：Originally, for will system
Cryogen returns compressor 11, the liquid refrigerant due to liquid backflow phenomenon from gas-liquid separator in the form of gas refrigerant
Compressor 11 is returned, therefore reduces the reliability of compressor 11.
In addition, the part being connected with the entrance of compressor 11 of main pipe arrangement 10 is connected with bypass pipe arrangement 9, therefore fortune is being heated
When turning, 11 side of compressor can be suppressed to form high pressure.Therefore, when flow control division 8 arranges check valve, strength need not be set
(therefore manufacturing cost is high) check valve, operates in the bypass pipe arrangement 9 in the case of stopping as long as arranging and taking into consideration only air conditioner 1
The check valve of the backflow of cold-producing medium.
Embodiment 2
Fig. 8 is the integrally-built explanatory diagram of the air conditioner for representing embodiments of the invention 2.
In fig. 8, same as Example 1 with the part of Fig. 1 same-sign etc., therefore omit detailed description.
Embodiment 2 is first, there is no the expansion valve 5 of embodiment 1 from the different of embodiment 1.That is, as expansion valve,
Only exist located at cooling operation when main pipe arrangement 10 cold-producing medium flowing gas-liquid separator 7 upstream side expansion valve 4.
In addition, second temperature sensor 52 is located at the connecting portion with bypass pipe arrangement 9 and the interior of the main pipe arrangement 10 when freezing
Between heat exchanger 6.More specifically, in the example of Fig. 2, second temperature sensor 52 is located at connection cross valve 2 and compressor
The position of the positive front side with the interflow of bypass pipe arrangement 9 of the main pipe arrangement 10 of 11 entrance side.
In addition, for the gas-liquid separation circulation pattern illustrated in embodiment 1, which is carried out in cooling operation, heating
Do not carry out during operating, this point is also different.So, because gas-liquid separation circulation pattern is carried out in cooling operation, in heating operation
When do not carry out, so do not need expansion valve 5.
For the present embodiment, in gas-liquid separation circulation pattern, for ease of obtaining its effect (as described above), generally increase
The long evaporimeter (indoor heat converter 6) from for cold-producing medium evaporation is to the path of the main pipe arrangement 10 of gas-liquid separator 7, concern and warp
The situation of normal cooling operation.
That is, in heating operation, the path of above-mentioned main pipe arrangement 10 is shorter, it is difficult to obtain gas-liquid separation circulation pattern
Above-mentioned effect, therefore, is configured to, and implements gas-liquid separation circulation pattern only in the case of cooling operation.
According to such structure, compared with the situation of embodiment 1, it is impossible to there is expansion valve 5, manufacturing cost can be reduced.
In addition, the control logic executed by control unit 50 also can be simplified than embodiment 1, therefore can also reduce manufacture in this regard
Cost.
Embodiment 3
Fig. 9 is the integrally-built explanatory diagram of the air conditioner for representing embodiments of the invention 3.
In fig .9, same as Example 2 with the part of Fig. 8 same-sign etc., therefore omit detailed description.
In the present embodiment, also common with embodiment 2, gas-liquid separation circulation pattern is carried out in cooling operation, heating
Gas-liquid separation circulation pattern is not carried out during operating.In addition, second temperature sensor 52 located at refrigeration when main pipe arrangement 10 with
Aspect between the connecting portion of bypass pipe arrangement 9 and indoor heat converter 6, also common with embodiment 2.
Difference of the embodiment 3 from embodiment 2 be, in the where connecting bypass of the main pipe arrangement 10 of 11 side of compressor
Pipe arrangement 9, and configure temperature sensor 52 where then.I.e., in the present embodiment, by compression during cooling operation
The ratio cross valve 2 of the main pipe arrangement 10 of the entrance side of machine 11 leans on the position of the upstream side of cold-producing medium and gas-liquid separator 7 to be attached.
Then, temperature sensor 52 located at cooling operation when compressor 11 entrance side main pipe arrangement 10 ratio and bypass pipe arrangement 9
Connecting portion is by the position of the upstream side of cold-producing medium.
According to the present embodiment 3, even if in gas-liquid separation circulation pattern, by the gas refrigerant of bypass pipe arrangement 9
Doping liquid refrigerant, does not flow directly into the entrance of compressor 11 yet, and through a cross valve 2, so liquid backflow phenomenon
Length than embodiment 1,2 example reduce, improve compressor 11 reliability.
Additionally, the present invention is not limited to above-mentioned embodiment, which includes various modifications example.For example, above-mentioned embodiment party
Formula for convenience of description the present invention and be illustrated in detail, and be not limited to possess the described all of structure for understanding.Separately
Outward, a part for the structure of certain embodiment can be replaced as the structure of other embodiment, in addition, it is also possible in certain enforcement
Add the structure of other embodiment in the structure of mode.In addition, for a part for the structure of each embodiment, can
Carry out adding, delete, replacing for other structures.
Claims (5)
1. a kind of air conditioner, possess outdoor heat converter, indoor heat converter, compressor, expansion valve, cross valve and by it
The main pipe arrangement that connects, change the flowing of the cold-producing medium in above-mentioned each portion so as to carry out air tune by switching above-mentioned cross valve
Save, above-mentioned air conditioner is characterised by,
Possesses gas-liquid separator, which is located in the above-mentioned main pipe arrangement for connecting above-mentioned outdoor heat converter and above-mentioned indoor heat converter
The side for being provided with above-mentioned expansion valve, the cold-producing medium to flowing into from above-mentioned main pipe arrangement carries out gas-liquid separation,
As above-mentioned expansion valve, possess：First expansion valve, its are located at than above-mentioned gas-liquid separator by above-mentioned main pipe arrangement during refrigeration
The upstream side of the flowing of cold-producing medium；And second expansion valve, above-mentioned main pipe arrangement when which is located at than above-mentioned gas-liquid separator by heating
Above-mentioned cold-producing medium flowing upstream side,
Above-mentioned air conditioner possesses：
The above-mentioned main pipe arrangement of bypass pipe arrangement, its above-mentioned gas-liquid separator of connection and the entrance side for being connected to above-mentioned compressor；
Flow control division, its are located in above-mentioned bypass pipe arrangement, and the flow to the gas refrigerant from above-mentioned gas-liquid separator
It is adjusted；
First temperature sensor, its are located at the above-mentioned flow control division downstream than above-mentioned bypass pipe arrangement；
Second temperature sensor, its are located between the connecting portion with above-mentioned bypass pipe arrangement of above-mentioned main pipe arrangement and above-mentioned cross valve；
And
Control unit, the detection temperature of its detection temperature based on above-mentioned first temperature sensor and above-mentioned second temperature sensor,
The flow of the gas refrigerant to being adjusted using above-mentioned flow control division is controlled.
2. a kind of air conditioner, it possess outdoor heat converter, indoor heat converter, compressor, expansion valve, cross valve and will
The main pipe arrangement that they connect, changes the flowing of the cold-producing medium in above-mentioned each portion so as to carry out air tune by switching above-mentioned cross valve
Save, above-mentioned air conditioner is characterised by,
Possesses gas-liquid separator, which is located in the above-mentioned main pipe arrangement for connecting above-mentioned outdoor heat converter and above-mentioned indoor heat converter
The side for being provided with above-mentioned expansion valve, the cold-producing medium to flowing into from above-mentioned main pipe arrangement carries out gas-liquid separation,
Above-mentioned expansion valve is located at the upstream than above-mentioned gas-liquid separator by the flowing of the cold-producing medium of above-mentioned main pipe arrangement during cooling operation
Side,
Above-mentioned air conditioner possesses：
Bypass pipe arrangement, it is above-mentioned with entrance side during the above-mentioned refrigeration for being connected to above-mentioned compressor which connects above-mentioned gas-liquid separator
Main pipe arrangement；
Flow control division, its are located in above-mentioned bypass pipe arrangement, and the flow to the gas refrigerant from above-mentioned gas-liquid separator
It is adjusted；
First temperature sensor, its are located at the above-mentioned flow control division downstream than above-mentioned bypass pipe arrangement；
Second temperature sensor, above-mentioned main pipe arrangement when which is located at cooling operation with the connecting portion of above-mentioned bypass pipe arrangement and above-mentioned
Between indoor heat converter；And
Control unit,, in cooling operation, the detection temperature based on above-mentioned first temperature sensor and above-mentioned second temperature are sensed for which
The detection temperature of device, the flow of the gas refrigerant to being adjusted using above-mentioned flow control division are controlled.
3. air conditioner according to claim 2, it is characterised in that
Above-mentioned bypass pipe arrangement connects to the above-mentioned main pipe arrangement of entrance side and above-mentioned gas-liquid separator that are connected to above-mentioned compressor
Connect,
Above-mentioned second temperature sensor is located at the above-mentioned bypass pipe arrangement of the ratio of above-mentioned main pipe arrangement that is connected with the entrance of above-mentioned compressor
Coupling part by cold-producing medium upstream side.
4. air conditioner according to claim 2, it is characterised in that
The above-mentioned cross valve of the ratio of the above-mentioned main pipe arrangement of the entrance side of above-mentioned compressor during above-mentioned bypass pipe arrangement connection cooling operation
Position and above-mentioned gas-liquid separator by the upstream side of cold-producing medium,
Above-mentioned second temperature sensor located at above-mentioned cooling operation when above-mentioned compressor entrance side main pipe arrangement ratio with upper
State the position of the connecting portion by upstream side of bypass pipe arrangement.
5. the air conditioner according to any one of Claims 1 to 4, it is characterised in that
Above-mentioned control unit is so that the detection temperature of the detection temperature of above-mentioned first temperature sensor and above-mentioned second temperature sensor
Difference be in mode between first reference value and the second a reference value lower than the first reference value and carry out above-mentioned control.
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107178925A (en) * | 2017-06-12 | 2017-09-19 | 广东美的暖通设备有限公司 | Air-conditioning system and air-conditioning |
| CN107763774A (en) * | 2017-11-09 | 2018-03-06 | 青岛海尔空调器有限总公司 | Air conditioner cooling cycle system and air conditioner |
| CN110207432A (en) * | 2019-05-13 | 2019-09-06 | 西安交通大学 | A kind of air conditioner and operation method using shut-off valve |
| CN110785611A (en) * | 2018-05-14 | 2020-02-11 | 日立江森自控空调有限公司 | Air conditioner |
| US11162705B2 (en) | 2019-08-29 | 2021-11-02 | Hitachi-Johnson Controls Air Conditioning, Inc | Refrigeration cycle control |
| CN113864989A (en) * | 2021-10-27 | 2021-12-31 | 珠海格力电器股份有限公司 | Control method and device of air conditioner, storage medium, processor and air conditioner |
| WO2022237909A1 (en) * | 2021-05-14 | 2022-11-17 | 浙江三花汽车零部件有限公司 | Refrigerating system, expansion valve assembly and method for controlling refrigerating system |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2024047894A (en) * | 2022-09-27 | 2024-04-08 | 三菱重工サーマルシステムズ株式会社 | Air conditioners |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4335893B2 (en) * | 2006-08-18 | 2009-09-30 | 三星電子株式会社 | Air conditioner |
| CN202747706U (en) * | 2012-09-17 | 2013-02-20 | 珠海格力电器股份有限公司 | Refrigeration system and air-conditioning system with same |
| CN203893511U (en) * | 2014-06-11 | 2014-10-22 | 珠海格力电器股份有限公司 | Heat pump system |
| CN104567135A (en) * | 2013-10-17 | 2015-04-29 | 三菱电机株式会社 | Air conditioning device |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0239179Y2 (en) * | 1985-02-28 | 1990-10-22 | ||
| JP3918421B2 (en) * | 2000-09-21 | 2007-05-23 | 三菱電機株式会社 | Air conditioner, operation method of air conditioner |
| JP3864980B2 (en) * | 2005-04-18 | 2007-01-10 | ダイキン工業株式会社 | Air conditioner |
| JP2010032106A (en) * | 2008-07-29 | 2010-02-12 | Hitachi Appliances Inc | Air conditioner |
-
2015
- 2015-08-28 JP JP2015168518A patent/JP6546813B2/en active Active
-
2016
- 2016-07-26 CN CN201610597027.2A patent/CN106482375B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4335893B2 (en) * | 2006-08-18 | 2009-09-30 | 三星電子株式会社 | Air conditioner |
| CN202747706U (en) * | 2012-09-17 | 2013-02-20 | 珠海格力电器股份有限公司 | Refrigeration system and air-conditioning system with same |
| CN104567135A (en) * | 2013-10-17 | 2015-04-29 | 三菱电机株式会社 | Air conditioning device |
| CN203893511U (en) * | 2014-06-11 | 2014-10-22 | 珠海格力电器股份有限公司 | Heat pump system |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107178925A (en) * | 2017-06-12 | 2017-09-19 | 广东美的暖通设备有限公司 | Air-conditioning system and air-conditioning |
| CN107763774A (en) * | 2017-11-09 | 2018-03-06 | 青岛海尔空调器有限总公司 | Air conditioner cooling cycle system and air conditioner |
| WO2019091241A1 (en) * | 2017-11-09 | 2019-05-16 | 青岛海尔空调器有限总公司 | Cooling circulation system for air conditioning, and air conditioner |
| CN110785611A (en) * | 2018-05-14 | 2020-02-11 | 日立江森自控空调有限公司 | Air conditioner |
| CN110785611B (en) * | 2018-05-14 | 2021-06-22 | 日立江森自控空调有限公司 | Air conditioner |
| CN110207432A (en) * | 2019-05-13 | 2019-09-06 | 西安交通大学 | A kind of air conditioner and operation method using shut-off valve |
| CN110207432B (en) * | 2019-05-13 | 2023-05-30 | 西安交通大学 | Air conditioner using stop valve and operation method |
| US11162705B2 (en) | 2019-08-29 | 2021-11-02 | Hitachi-Johnson Controls Air Conditioning, Inc | Refrigeration cycle control |
| WO2022237909A1 (en) * | 2021-05-14 | 2022-11-17 | 浙江三花汽车零部件有限公司 | Refrigerating system, expansion valve assembly and method for controlling refrigerating system |
| CN113864989A (en) * | 2021-10-27 | 2021-12-31 | 珠海格力电器股份有限公司 | Control method and device of air conditioner, storage medium, processor and air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2017044435A (en) | 2017-03-02 |
| CN106482375B (en) | 2019-03-26 |
| JP6546813B2 (en) | 2019-07-17 |
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Effective date of registration: 20180613 Address after: Tokyo, Japan, Japan Applicant after: Hitachi Johnson Controls Air Conditioning Co., Ltd. Address before: Hongkong, China Applicant before: Johnson Controls Hitachi air conditioning technology (Hongkong) Co., Ltd. |
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