CN106482375B - Air conditioner - Google Patents
Air conditioner Download PDFInfo
- Publication number
- CN106482375B CN106482375B CN201610597027.2A CN201610597027A CN106482375B CN 106482375 B CN106482375 B CN 106482375B CN 201610597027 A CN201610597027 A CN 201610597027A CN 106482375 B CN106482375 B CN 106482375B
- Authority
- CN
- China
- Prior art keywords
- mentioned
- gas
- refrigerant
- temperature
- temperature sensor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
-
- 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
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
-
- 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
-
- 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
Landscapes
- 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 be equipped with gas-liquid separator can be improved the efficiency of air conditioning, be capable of the reliability of height-regulating device by preventing liquid reflux phenomenon.The air conditioner has: temperature sensor (51), in the temperature of the downstream side measurement refrigerant of the flow control division (8) of bypass pipe arrangement (9)；Temperature sensor (52), the temperature of the refrigerant before the interflow of two pipings is measured near the interconnecting piece with bypass pipe arrangement for the main piping (10) for being connected to compressor (11)；And control unit (50), the detection temperature of detection temperature and temperature sensor based on temperature sensor are controlled in a manner of adjusting the flow of the gas refrigerant adjusted by flow control division.Control unit with make the difference of the detection temperature of temperature sensor and the detection temperature of preceding temperature sensor be in best ceiling temperature difference and low best lower limit temperature poorer than the best ceiling temperature it is poor between mode carry out above-mentioned control.
Description
Technical field
The present invention relates to air conditioners.
Background technique
As the background technique of the art, there is Japanese Unexamined Patent Publication 2008-45837 bulletin (patent document 1).The public affairs
Report describe " a kind of conditioner for having the gas bypass circuit to compressor suction side bypass gases refrigerant, on
It states gas refrigerant to be isolated by the gas-liquid separator being set between expansion valve and outdoor heat exchanger, the air tune
Regulating device has: flow control valve, the flow of regulating gas bypass circulation；Detection device, opposite outdoor heat exchanger supply
To the fluid exit section of the gas-liquid separator in the liquid refrigerant circuit by the separated liquid refrigerant of gas-liquid separator
It is detected with the pressure difference of the fluid entry section of outdoor heat exchanger；And control device, according to above-mentioned pressure difference tune
The aperture of throttling adjustable valve " (referring to abstract).
Existing technical literature
Patent document
Patent document 1: Japanese Unexamined Patent Publication 2008-45837 bulletin
Summary of the invention
Above patent document 1 describes following point, carries out opening for the flow control valve of gas bypass circuit according to pressure difference
The adjusting of degree, above-mentioned pressure difference are the liquid system to outdoor heat exchanger supply by the separated liquid refrigerant of gas-liquid separator
The pressure difference of the fluid entry section of the fluid exit section and outdoor heat exchanger of gas-liquid separator in refrigerant circuit.
However, cannot prevent liquid refrigerant from also bypassing through gas bypass circuit to pressure the technology of patent document 1
The reliability of the liquid reflux phenomenon of contracting machine entrance side, the efficiency reduction and air conditioner that cannot prevent air conditioning reduces.
Therefore, the issue of the present invention is to provide a kind of air conditioners, are equipped with gas-liquid separator, can be improved air conditioning
Efficiency, and can be improved the reliability of device.
In order to solve the above problems, a scheme of the invention is a kind of air conditioner, has outdoor heat exchanger, Indoor Thermal is handed over
Parallel operation, compressor, expansion valve, four-way valve and the main piping for connecting them, it is above-mentioned to change by switching above-mentioned four-way valve
To carry out air conditioning, above-mentioned air conditioner is characterized in that having gas-liquid separator, is set to for the flowing of the refrigerant in each portion
The side equipped with above-mentioned expansion valve in the above-mentioned main piping of above-mentioned outdoor heat exchanger and above-mentioned indoor heat exchanger is connected, it is right
The refrigerant flowed into from above-mentioned main piping, which carries out gas-liquid separation, to be had as above-mentioned expansion valve: the first expansion valve, be set to than
The upstream side of the flowing of the refrigerant of above-mentioned main piping when above-mentioned gas-liquid separator is by refrigeration；And second expansion valve, it is set to
The upstream side of the flowing of the above-mentioned refrigerant of above-mentioned main piping, above-mentioned air conditioner have when than above-mentioned gas-liquid separator by heating:
Bypass pipe arrangement connects above-mentioned gas-liquid separator and is connected to the above-mentioned main piping of the entrance side of above-mentioned compressor；Flow is adjusted
Portion is set in above-mentioned bypass pipe arrangement, and the flow of the gas refrigerant from above-mentioned gas-liquid separator is adjusted；First
Temperature sensor is set to the above-mentioned flow control division downstream than above-mentioned bypass pipe arrangement；Second temperature sensor is set to
Above-mentioned main piping between the interconnecting piece and above-mentioned four-way valve of above-mentioned bypass pipe arrangement；And control unit, it is based on above-mentioned first
The detection temperature of temperature sensor and the detection temperature of above-mentioned second temperature sensor, to what is adjusted using above-mentioned flow control division
The flow of gas refrigerant is controlled.
In addition, another way of the invention is a kind of air conditioner, have outdoor heat exchanger, indoor heat exchanger, pressure
Contracting machine, expansion valve, four-way valve and the main piping for connecting them, change above-mentioned each portion by switching above-mentioned four-way valve
To carry out air conditioning, above-mentioned air conditioner is characterized in that having gas-liquid separator for the flowing of refrigerant, is set in connection
The side equipped with above-mentioned expansion valve in the above-mentioned main piping of outdoor heat exchanger and above-mentioned indoor heat exchanger is stated, to from above-mentioned
The refrigerant that main piping flows into carries out gas-liquid separation, and above-mentioned expansion valve is above-mentioned when being set to than above-mentioned gas-liquid separator by refrigeration operation
The upstream side of the flowing of the refrigerant of main piping, above-mentioned air conditioner have: bypass pipe arrangement, connect above-mentioned gas-liquid separator and company
The above-mentioned main piping of entrance side when being connected to the above-mentioned refrigeration of above-mentioned compressor；Flow control division is set to above-mentioned bypass pipe arrangement
In, and the flow of the gas refrigerant from above-mentioned gas-liquid separator is adjusted；First temperature sensor is set to than upper
State the above-mentioned flow control division downstream of bypass pipe arrangement；Second temperature sensor, above-mentioned master when being set to refrigeration operation match
Pipe between the interconnecting piece and above-mentioned indoor heat exchanger of above-mentioned bypass pipe arrangement；And control unit, in refrigeration operation, base
In the detection temperature of above-mentioned first temperature sensor and the detection temperature of above-mentioned second temperature sensor, to the above-mentioned flow tune of utilization
The flow for 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, it is equipped with gas-liquid separator, can be improved the effect of air conditioning
Rate, and can be improved the reliability of device.
For project other than the above, structure and effect, will become more clear by the explanation of the following embodiments and the accompanying drawings.
Detailed description of the invention
Fig. 1 is the integrally-built explanatory diagram for illustrating the air conditioner of the embodiment of the present invention 1.
Fig. 2 be indicate one embodiment of the invention, based on control unit, the block figure of the control system of air conditioner.
Fig. 3 is the chart for illustrating the effect of air conditioner of one embodiment of the invention by p-h line chart.
Fig. 4 is the effect for illustrating the air conditioner of one embodiment of the invention by temperature difference and cryogen gaseous ratio
Chart.
Fig. 5 is the flow chart for illustrating the movement of air conditioner of one embodiment of the invention.
Fig. 6 is the effect for illustrating the air conditioner of one embodiment of the invention by the aperture and temperature difference of flow control division
Chart.
Fig. 7 is the sky for illustrating one embodiment of the invention by the time change of the aperture of flow control division and temperature difference
The chart of the effect of tune machine.
Fig. 8 is the integrally-built explanatory diagram for illustrating the air conditioner of the embodiment of the present invention 2.
Fig. 9 is the integrally-built explanatory diagram for illustrating the air conditioner of the embodiment of the present invention 3.
The explanation of symbol
1-air conditioner, 2-four-way valves, 3-outdoor heat exchangers, 4-expansion valves (the first expansion valve), 5-expansion valves
(the second expansion valve), 6-indoor heat exchangers, 7-gas-liquid separators, 8-flow control divisions, 9-bypass pipe arrangements, 10-masters match
Pipe, 11-compressors, 50-control units, the 51-the first temperature sensor, 52-second temperature sensors, the best upper limit of dTu-
Temperature difference (first reference value), the best lower limit temperature of dTl-are poor (the second a reference value).
Specific embodiment
As the method for realizing that the efficiency of refrigerating cycle improves, it is known that realize the pressure loss of the low-pressure side in refrigerating cycle
Reduced method.For example, above-mentioned patent document 1 discloses a kind of conditioner, handed in expansion valve and outdoor heat
Piping between parallel operation has gas-liquid separator, the gas to the refrigerant inlet side of compressor bypass by the gas-liquid separator separates
The gas bypass circuit of cryogen and adjust the gas bypass circuit gas refrigerant flow flow control valve.
This is to contribute heat exchange small gas refrigerant in the refrigerant flowed into using gas-liquid separator opposite direction evaporator
It is separated.In this way, only having separated the liquid refrigerant of gas refrigerant by createing to evaporator, freezing can reduce
(refrigerant is by bearing the frictional resistance system from piping when heat exchanger for the refrigerant pressure loss of low-pressure side in circulation
The phenomenon that pressure decline of cryogen).In addition, the aridity of the refrigerant by making evaporator inlet reduces, make evaporator inlet
Enthalpy reduce, obtain the enthalpy difference of biggish evaporator, it is cooling because caused by being reduced the internal circulating load of refrigerant so as to compensate
The reduction of ability, therefore improve air-conditioner efficiency.
Here, in patent document 1, in order to according to the gas system in the two-phase system cryogen for the entrance for flowing into gas-liquid separator
The amount of cryogen adjusts the aperture of flow control valve, according to the outlet of the liquid refrigerant of gas-liquid separator and outdoor heat exchanger
The variation detection of the pressure difference of liquid refrigerant entrance has been mixed into gas refrigerant in liquid refrigerant circuit, and then to being set to
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 is excessive and liquid refrigerant inflow gas bypass pipe arrangement
Liquid reflux phenomenon control, the minimum aperture that only pressure difference will be made fixed is as the progress of the target aperture of flow control valve
Aperture regulation.That is, making during flow control valve operated with best aperture, though due to air conditioner load variation and have occurred
Liquid reflux phenomenon, also due to pressure of saturated liquid refrigerant itself is without variation and above-mentioned pressure difference is fixed, and cannot
Judge the generation of liquid reflux phenomenon.
Accordingly, there exist the liquid refrigerant of the Returning evaporimeter reduction due to liquid reflux phenomenon, the efficiency of air conditioning
Reduced project.In addition, refrigerant is returned in a manner of gas refrigerant originally from gas-liquid separator to compressor, and it is present
Liquid refrigerant has also returned to compressor, therefore there is also the lower projects of the reliability of compressor.
Hereinafter, having multiple examples for the embodiment of the present invention for being able to solve these projects and being illustrated.
Embodiment 1
Fig. 1 is the integrally-built explanatory diagram for indicating the air conditioner of the embodiment of the present invention 1.
Air conditioner 1 is generally made of outdoor unit 60 and indoor unit 61.Moreover, air conditioner 1 is to have outdoor heat exchanger
3, indoor heat exchanger 6, compressor 11, expansion valve 4 and 5, four-way valve 2 and by the cold of these main pipings 10 being attached etc.
Freeze circulator, and the flowing for the refrigerant that can change above-mentioned each portion by the switching of four-way valve 2 is selectively made
Cold or heating.
That is, by the switching state of four-way valve 2 shown in solid in Fig. 1, making refrigerant along solid line arrow when being heated
The direction circulation of head.It is, the liquid refrigerant of low pressure, low temperature passes through outdoor heat exchanger 3 as evaporator and outdoor
Air carries out heat exchange and gasifies, absorbs heat, and becomes gas refrigerant.The gas refrigerant is transported to compressor through four-way valve 2
11, and be formed as high temperature, high pressure in compressor 11, then indoor heat exchanger 6 is delivered to through four-way valve 2.In this case, indoor
Heat exchanger 6 is used as condenser, and gas refrigerant and room air carry out heat exchange and liquefy, heat release, to become high temperature, height
The liquid refrigerant of pressure.Then, which is formed as low and the expansion valve 5 as the second expansion valve is expanded
The liquid refrigerant (gas-liquid two-phase refrigerant) of temperature, low pressure, and return to outdoor heat exchanger 3.
On the other hand, when being freezed, by the switching state of four-way valve 2 shown in dotted lines in Figure 1, make refrigerant edge
It circulates in the direction of dotted arrow.That is, the liquid refrigerant of low pressure, low temperature by as evaporator indoor heat exchanger 6 gasification,
It absorbs heat and becomes gas refrigerant.The gas refrigerant is transported to compressor 11 through four-way valve 2, and is formed as in compressor 11
Then high temperature, high pressure are delivered to outdoor heat exchanger 3 through four-way valve 2.In this case, outdoor heat exchanger 3 is used as condenser,
Gas refrigerant liquefaction, heat release, become the liquid refrigerant of high temperature, high pressure.Then, which passes through swollen as first
The expansion valve 4 of swollen valve is expanded and is formed as the liquid refrigerant (gas-liquid two-phase refrigerant) of low temperature, low pressure, and is returned indoor
Heat exchanger 6.The above are the movements of basic refrigerating cycle.
Connection outdoor heat exchanger 3 and indoor heat exchanger 6 main piping 10, side equipped with expansion valve 4,5, if
There is the gas-liquid separator 7 that gas-liquid separation is carried out to the refrigerant flowed into from main piping 10.Gas-liquid separator 7 is following device,
Two-phase system cryogen is separated into liquid refrigerant and gas refrigerant using gravity, centrifugation force, surface tension etc., and obtain as
Under good separative efficiency: from bypass pipe arrangement 9 usually can only eluting gas refrigerant, from it is main piping 10 (with two-phase freeze
The piping of the opposite side in the inflow side of agent) it substantially being capable of only trickle refrigerant.
Moreover, as described above, leaning on the flowing of refrigerant set on the ratio gas-liquid separator 7 of main piping 10 in refrigeration operation
Upstream side expansion valve 4 be the first expansion valve, in heating operation, set on it is main piping 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.
The entrance side of bypass pipe arrangement 9 connection gas-liquid separator 7 and compressor 11.In addition, symbol 12 is for preventing liquid
The Suction cop of the return of refrigerant.In addition, being passed in the temperature that compressor 11 is equipped with the outlet refrigerant temperature of detection compressor 11
Sensor 53.
Flow control division 8 is set in bypass pipe arrangement 9, and is carried out to the flow of the gas refrigerant from gas-liquid separator 7
It adjusts.Flow control division 8 can adjust aperture, and it is expected using the expansion valve that can be closed bypass pipe arrangement 9 in minimum aperture.
Alternatively, be also configured to by be only opened and closed the two-way valves of two movements, fixation as the capillary of flow path resistance and unidirectional
Valve series connection.
Bypass pipe arrangement 9 specific discharge adjustment portion 8 farther downstream side position be equipped with measurement refrigerant temperature conduct
The temperature sensor 51 of first temperature sensor.
In addition, in the example of Fig. 1, being connected between the linking part and four-way valve 2 of bypass pipe arrangement 9 in main piping 10
The main piping 10 of the entrance side of four-way valve 2 and compressor 11 is equipped with measurement with the position of the positive front side at the interflow of bypass pipe arrangement 9
The temperature sensor 52 as second temperature sensor of the temperature of refrigerant.
Moreover, outdoor heat exchanger 3, indoor heat exchanger 6 also be respectively equipped with detection temperature temperature sensor 54,
55.Temperature sensor 51~55 is the thermometer of thermal resistor etc., is fixed on piping 9,10 by using spring etc. to examine
Testing temperature.
Control unit 50 is the control device for controlling air conditioner 1.Fig. 2 is control based on control unit 50, indicating air conditioner 1
The block figure of system processed.Control unit 50 is mainly made of such as microcomputer, through scheduled interface respectively with temperature sensor
51~55, four-way valve 2 (driver), compressor 11 (driver), expansion valve 4 and 5 (drivers), flow control division 8
(driver) connection.
In the following, being described in detail to the characteristic movement of air conditioner 1 as above.
Firstly, gas-liquid separation circulation pattern when to heating operation describes.In Fig. 1, when switching four-way valve 2 so that
When refrigerant is flowed along the direction that solid line indicates (solid arrow direction), refrigerant is according to compressor 11 (outlet), four-way valve
2, indoor heat exchanger 6, expansion valve 5, gas-liquid separator 7, expansion valve 4, outdoor heat exchanger 3, four-way valve 2, compressor 11 (
Entrance) sequential flowing.Expansion valve 5 is adjusted to the aperture of the appropriateness of corresponding air conditioner load by control unit 5, passes through indoor heat exchange
The refrigerant 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 for adjusting flow control division 8 makes the refrigerant be completely separated into liquid system by gas-liquid separator 7
Cryogen and gas refrigerant, and liquid refrigerant is flowed into outdoor heat exchanger 3, entrance of the gas refrigerant to compressor 11
It flows into.The liquid refrigerant is sufficiently evaporated by outdoor heat exchanger 3, and is divided in the entrance side of compressor 11 with from gas-liquid
From the gas refrigerant interflow that device 7 is flowed into through bypass pipe arrangement 9, returned to compressor 11.
For the effect of such refrigerating cycle, it is illustrated by Mollier diagram shown in Fig. 3.Fig. 3 is to indicate p-h line
The chart of figure.Symbol 101 indicates that saturated liquid line, symbol 102 indicate saturated vaporline.In Fig. 3, dotted line expression does not have gas
The state of the refrigerant of air conditioner 1 in the case of liquid/gas separator 7 and bypass pipe arrangement 9, common refrigerating cycle.That is, symbol A4
Indicate refrigerant in the variation of the state of compressor 11 between → A1.Indicate refrigerant in condenser (Indoor Thermal between symbol A1 → A2
Exchanger 6) state variation.Indicate refrigerant in the variation of the state of expansion valve 4 between symbol A2 → A3.Between symbol A3 → A4
Indicate refrigerant in the variation of the state of evaporator (outdoor heat exchanger 3).
In contrast, the heavy line expression of Fig. 3 has gas-liquid separator 7 and bypass pipe arrangement 9, the present embodiment gas-liquid point
The state of the refrigerant of air conditioner 1 in the case where from circulation pattern.That is, indicating refrigerant in compressor 11 between symbol B4 → B1
State variation.Indicate refrigerant in the change of the state of condenser (indoor heat exchanger 6 (when heating)) between symbol B1 → B2
Change.Indicate refrigerant in the variation of the state of expansion valve 4 between symbol B2 → B3.Indicate refrigerant in evaporator between symbol B3 → B4
The variation of the state of (outdoor heat exchanger 3).In addition, the spaced and parallel progress subtle for heavy line and dashed interval illustrate
Part, actually two line overlaps, but for convenience are spaced subtle interval and are illustrated.
In gas-liquid separation circulation, between symbol B3 → B4, line is two sections, and interval B 33 indicates to match by bypass
The refrigerant of pipe 9, interval B 34 indicate the refrigerant that evaporator (outdoor heat exchanger 3) is flowed to by main piping 10.It will be by gas-liquid
The separated gas refrigerant of separator 7 is to the entrance of compressor 11 guidance (B32), by remaining liquid refrigerant to evaporator
(outdoor heat exchanger 3 (when heating)) guides (B31), thus as shown in figure 3, the ratio of evaporator (outdoor heat exchanger 3) entrance
Enthalpy reduces from ha to hb, and the ratio enthalpy difference of evaporator (outdoor heat exchanger 3) becomes larger, and then cooling capacity increases.Moreover, gas system
Cryogen reduces to the refrigerant flow of evaporator (outdoor heat exchanger 3), and refrigerant pressure loss reduces, thus compressor 11
Suction pressure from pa to pb rise, and then refrigerant sucking density increase, cooling capacity increase.The result is, and usual
Refrigerating cycle be compared, improve efficiency.
Next, using Fig. 3, Fig. 4, to the flow of the effect for playing gas-liquid separation circulation pattern to the maximum extent
The movement 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 is flowed into the entrance of compressor 11, and liquid refrigerant is flowed into outdoor heat exchanger 3.In gas-liquid point
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
It keeps.At this point, 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 B4 is decompressed in specific enthalpy.
Moreover, according to the aperture of flow control division 8, gas refrigerant after controlling gas-liquid separation to 11 side of compressor
Supply amount.In the case where gas refrigerant supply amount is few, due to the 8 upstream side of specific discharge adjustment portion of bypass pipe arrangement 9
The ambient temperature of piping, gas refrigerant are heated, so that temperature increases when being depressurized than insulation.
On the other hand, the liquid refrigerant (B31) of evaporator (outdoor heat exchanger 3 (when heating)) is flowed on one side from outside
Air heat absorption, evaporate on one side and become gas refrigerant, and towards after the entrance side of compressor 11 and above-mentioned gas-liquid separation
Gas refrigerant collaborate (B4).At this point, the liquid refrigerant of gasification is reduced by 3 temperature of outdoor heat exchanger, become temperature
Spend T2.The size relation of temperature is usually T2 < T1.As shown in figure 4, carrying out the gas after gas-liquid separation by gas-liquid separator 7
Refrigeration dose is more, and the temperature difference " T1-T2 " is smaller.
When the aperture that flow control division 8 is arranged is excessive, in gas-liquid separator 7, the pressure reduction of gas, liquid surface
It is not able to maintain, blistering is generated, so that liquid refrigerant is mixed into the gas refrigerant (liquid reflux phenomenon) of bypass pipe arrangement 9.When
When adulterating liquid refrigerant in the gas refrigerant after gas-liquid separation, to the liquid system of evaporator (outdoor heat exchanger 3) inflow
Cryogen is greatly decreased, and relative to the exchange heat that air has, the heat that refrigerant can exchange is reduced, thus liquid refrigerant
Excessive vaporization, refrigerant superheat, becomes " T2 > T1 ", and the temperature difference of temperature T1 and temperature T2 are reverse.
Therefore, the temperature that refrigerant is detected by temperature sensor 51 and temperature sensor 52, according to the big of its temperature difference
The control of flow control division 8 is adjusted by control unit 50 for small relationship, so as to generate the liquid point of gas by gas-liquid separator 7
From effect maximum, wherein temperature sensor 51 is in the downstream side of flow control division 8 detection connection gas-liquid separator 7 and compressor
The temperature T1 of the bypass pipe arrangement 9 of 11 sides, temperature sensor 52 detect in the main piping 10 of connect compressor 11 and four-way valve 2 with
The temperature T2 of part before the interflow of bypass pipe arrangement 9.
When the gas-liquid separation effect maximum generated by gas-liquid separator 7, when being ideally 0 for temperature difference " T1-T2 ",
But the difference of the manufacture deviation of the thermal resistor as used in temperature sensor, refrigerant temperature and piping surface temperature,
And the reasons such as thermal contact resistance with pipe surface and thermal resistor, not temperature T1 is mutually synthermal (temperature difference with temperature T2
0) " T1-T2 " is not.
Therefore, poor " T1-T2 " as target temperature, with the absolute value of the temperature difference " T1-T2 " become least way into
Row control.
It is big that the evaporating pressure of this gas-liquid separation circulation pattern loses reduced effect.That is, since main piping 10 is longer, system
The internal circulating load of cryogen is more, and the pressure loss of refrigerant is bigger, therefore evaporating pressure loses reduced significant effect.On the contrary,
In the case where the internal circulating load of refrigerant is few, effect becomes smaller.Therefore, the heating fortune short in the main piping 10 of the low-pressure side of refrigerant
When turning, revolving speed small in air conditioner load and compressor 11 is low and in the case that the internal circulating load of refrigerant is few, can not also be to pass through
Flow control division 8 adjust flow gas-liquid separation circulation pattern and the common cyclic module to completely close flow control division 8
Formula is operated, and can also according to circumstances be switched.
Next, gas-liquid separation circulation pattern when to refrigeration operation is illustrated.In this case, in Fig. 1, such as dotted line
It is shown that four-way valve 2 is switched over, make refrigerant along dotted arrow direction flow, thus refrigerant according to compressor 11 (
Outlet side), four-way valve 2, outdoor heat exchanger 3, expansion valve 4, gas-liquid separator 7, expansion valve 5, indoor heat exchanger 6, four-way
The sequential flowing of valve 2, compressor 11 (entrance side).
Expansion valve 4 is adjusted to the aperture of the appropriateness of corresponding air conditioner load, sufficiently condenses and liquefies by outdoor heat exchanger 3
Refrigerant gas-liquid two-phase flow is become by expansion valve 4, and flowed into gas-liquid separator 7.Adjust opening for flow control division 8
Degree makes the refrigerant be completely separated into liquid refrigerant and gas refrigerant by gas-liquid separator 7, and liquid refrigerant supplies
To indoor heat exchanger 6, gas refrigerant is supplied to the entrance side of compressor 11.Liquid refrigerant passes through indoor heat exchanger
6 are sufficiently evaporated, and in the entrance side of compressor 11 and the gas refrigerant flowed into from gas-liquid separator 7 through bypass pipe arrangement 9
Interflow is returned to compressor 11
For in the explanation of above-mentioned heating referring to the effect of Fig. 3 common refrigerating cycle illustrated, in addition to outdoor heat
Other than exchanger 3 is opposite with the effect of indoor heat exchanger 6, other also identical in the refrigeration case, and the description is omitted.
In the following, to the flow tune of the effect for playing the gas-liquid separation circulation pattern in the case where freezing to the maximum extent
The movement 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 of compressor 11, and liquid refrigerant is flowed into indoor heat exchanger 6.In gas-liquid separator 7, weight is utilized
Power, in lower section storing liquid refrigerant, liquid surface is kept by the pressure balance with the gas refrigerant of surrounding.This
When, 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 absorbs heat from air on one side, evaporates on one side, becomes gas
Cryogen, and collaborate towards the entrance side of compressor 11 with the above-mentioned gas refrigerant isolated by gas-liquid separator 7.Pass through stream
The aperture for measuring 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 refrigeration dose is few, due to the ambient temperature of bypass pipe arrangement 9, gas is heated, increasing when temperature is depressurized than insulation
It is high.
On the other hand, the liquid refrigerant of inflow indoor heat exchanger 6 absorbs heat from air on one side, evaporates on one side, becomes gas
Cryogen, and collaborate towards the entrance side of compressor 11 and above-mentioned isolated gas refrigerant.At this point, the liquid system of gasification
Cryogen is reduced by 3 temperature of outdoor heat exchanger, becomes temperature T2 (Fig. 3).At this point, the size relation of temperature is " T2 < T1 "
(Fig. 3).As described in Figure 4, the gas refrigeration dosage after being separated by gas-liquid separator 7 is more, the temperature difference " T1-T2 " (Fig. 4)
It is smaller.
Here, when the aperture that flow control division 8 is arranged is excessive, in gas-liquid separator 7, the pressure drop of gas refrigerant
It is low, it is not able to maintain liquid interface and generates blistering, liquid refrigerant is mixed into bypass pipe arrangement 9 (liquid reflux phenomenon).
Thus when carrying out gas-liquid separation by gas-liquid separator 7 and being adulterated in the gas refrigerant for flowing to bypass pipe arrangement 9
When liquid refrigerant, the liquid refrigerant flowed into indoor heat exchanger 6 is greatly decreased, the exchange having relative to room air
Heat, the heat that refrigerant can exchange are reduced, and therefore, liquid refrigerant is exceedingly gasified and refrigerant superheat, temperature
T1 and temperature T2 becomes " T2 > T1 ", and temperature difference is reverse.
Therefore, temperature is detected by temperature sensor 51 and temperature sensor 52 respectively, 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, that is, temperature difference " T1-T2 " (Fig. 4) it is exhausted
Minimum is become to value, wherein the temperature of the bypass pipe arrangement 9 of the detection of temperature sensor 51 connection gas-liquid separator 7 and 11 side of compressor
T1 is spent, before temperature sensor 52 detects collaborating in the main piping 10 of connect compressor 11 and 2 side of four-way valve with bypass pipe arrangement 9
Partial temperature T2.
Moreover, it is identical when with heating operation, because of the gas-liquid separation circulation pattern in the case where the internal circulating load of refrigerant is few
Effect reduce, therefore, can not also be with gas-liquid separation circulation pattern, and according to circumstances when with vulgar progress refrigeration operation
Switching, for example, flow control division 8 is completely closed, is operated etc. with common refrigerating cycle mode.
Hereinafter, being illustrated referring to Fig. 5 to the specific control method of the movement illustrated.Fig. 5 is illustrated for control unit
The flow chart of the content of 50 controls executed.
Firstly, present treatment starts by the air conditioner 1 that starts running.After operation start, even if to open flow control division 8
The mode that violent cyclical variations will not be generated judges whether the license for obtaining gas-liquid separation circulation pattern (S1).It is controlling
In portion 50, in the case where the license of gas-liquid separation circulation pattern has not been obtained (NO of S1), S1 is returned to.Here, as opening
Refrigerating cycle becomes the main reason for not temperature when flow control division 8, it is believed that is, after operation of air conditioner starts, as described above
Air conditioner load small (inner air and outer air temperature difference is small), as described above circulating mass of refrigerant few (revolving speed of compressor 11 is small), due to
Product is unqualified and there is leakage etc. in flow control division 8.In order to avoid these main causes, forbid gas-liquid in a case where
Separation 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 in the temperature of the above-mentioned temperature T2 of desired speed or less, the above-mentioned temperature T1 of bypass pipe arrangement 9 and piping 10
Degree difference is that fixed value is such as the following.In this case, flow control division 8 is completely closed, without gas-liquid separation circulation pattern, and into
The common refrigerating cycle mode of row.
In the case where obtaining the license of gas-liquid separation circulation pattern (YES of S1), gas-liquid separation cyclic module is switched to
Formula executes processing below as gas-liquid separation circulation pattern.That is, by connection gas-liquid separator 7 and compressor 11 side
Temperature sensor 51 that the temperature T1 of bypass pipe arrangement 9 is detected and to the temperature with the main piping 10 before the interflow of bypass pipe arrangement 9
The temperature sensor 52 that degree T2 is detected, detects temperature T1, temperature T2 respectively.Then, according to the size of temperature difference " T1-T2 "
Relationship adjusts flow control division 8.
For example, being closed in heating operation (for example, setting 7 DEG C of outside air temperature, 20 DEG C of indoor air temperature) in flow control division 8
In the case where, T1=7 DEG C, T2=0 DEG C, therefore T1-T2=7 DEG C.When opening flow control division 8, as shown in fig. 6, flow tune
The aperture in section portion 8 is bigger, and temperature difference " T1-T2 " is smaller, and " T1=T2 " (T1-T2=0) is the best of gas-liquid separation circulation
State.
Here, as temperature sensor 51,52, although having the product for the structure for contacting thermal resistor etc. with tube wall
Deng, still, because of the error containing thermal contact resistance etc., with gas-liquid separation circulation optimum state (T1=T2) exist slightly
Amplitude.That is, set best ceiling temperature difference dTu (first reference value) and it is dTu poorer than best ceiling temperature it is slightly lower it is best under
It limits temperature difference dTl (the second a reference value).For example, setting dTu=1 DEG C, dTl=0 DEG C.
Next, it is determined whether " T1-T2 < dTu " and " T1-T2 > dTl ", that is, whether " T1-T2 " is in best upper limit temperature
Spend the range (S2) between difference dTu and best lower limit temperature difference dTl.Here, if temperature difference " T1-T2 " is that best lower limit temperature is poor
DTl or less (excessively opens flow control division 8), then is easy to generate liquid reflux phenomenon.Fig. 6 is indicated in the case where dTl=0 DEG C
, the figure of the relationship of temperature difference " T1-T2 ", the aperture of flow control division 8, liquid reflux phenomenon, it illustrates in temperature difference
When " T1-T2 " is that 0 (best lower limit temperature difference dTl) (excessively opens flow control division 8) below, it is existing to be easy to generate liquid reflux
As.On the contrary, if temperature difference " T1-T2 " is best ceiling temperature difference dTu or more (excessively closing flow control division 8), gas-liquid point
From the effect that device 7 cannot play script.
In " T1-T2 < dTu " and " T1-T2 > dTl " (YES of S2), gas-liquid separation circulation pattern is with optimal state
It is operated, therefore returns to S1, 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), into S3.Then, exist
When " T1-T2 >=dTu " (YES of S3), flow control division 8 is opened into predetermined amount (S4).As long as the processing is repeated, flow tune
The aperture in section portion 8 will be gradually expanded.When not being " T1-T2 >=dTu " (NO of S3), into S5.Then, " T1-T2≤
When dTl " (YES of S5), flow control division 8 is closed into predetermined amount (S4).As long as the processing is repeated, flow control division 8
Aperture will be gradually reduced.When having carried out the processing of S5, S1 is returned.When not being " T1-T2≤dTl " (NO of S5), also return
Return S1.
Fig. 7 be indicate to be carried out according to the control, the time change of the aperture of temperature difference " T1-T2 " and flow control division 8
Chart.Solid line indicates temperature difference " T1-T2 ", and dotted line indicates 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 reach best lower limit temperature difference dTl, when
When temperature difference " T1-T2 " is lower than best lower limit temperature difference dTl, the aperture of flow control division 8 is reduced, final control is temperature difference
" T1-T2 " stablizes between best ceiling temperature difference dTu and best lower limit temperature difference dTl.
If temperature difference " T1-T2 " is set to be lower than the value of best lower limit temperature difference dTl, i.e. T2 > T1, temperature T1 and temperature
The temperature difference of T2 is reverse, then liquid refrigerant is adulterated in the gas refrigerant after being separated by gas-liquid separator 7, generates liquid and returns
Flow phenomenon has what the reliability of compressor 11 was damaged, therefore, it is desirable to correspond to the configuration bit of temperature sensor 51,52
It sets, state, best ceiling temperature difference dTu and best lower limit temperature difference dTl are safety value.Of course it is desirable to which best ceiling temperature is poor
The difference of dTu and best lower limit temperature difference dTl reduces as best one can in the range that this discomfort does not occur.
It is also similarly controlled in the case of cooling operation, to will not generate after being separated by gas-liquid separator 7
Gas refrigerant in adulterate liquid refrigerant liquid reflux phenomenon, be able to carry out and obtain gas-liquid separation effect to the maximum extent
Control.
In addition, in the present embodiment, be illustrated based on the control of gas-liquid separation circulation pattern, but as freezing
The whole control of circulation, the exhaust temperature of the refrigerant based on the compressor 11 for example detected by temperature sensor 53, also together
The control of Shi Jinhang refrigerating cycle entirety.At this point, in order to which the variation of refrigerating cycle is suppressed to minimum limit, in flow control division
It, can also be with the revolving speed of fixing compressor 11 during 8 open.
In addition, in the present embodiment, it is expected that stopping operation of air conditioner, and after compressor 11 also stops, flow is adjusted
Portion 8 fully opens.This is the fixation of the valve of the flow control division 8 when air conditioner 1 stops for a long time in order to prevent.
Moreover, needing to carry out refrigerant-recovery operating in the case thats the air conditioner 1 of the present embodiment is mobile etc., and make
Cryogen recycling operates as the operating under refrigeration cycle, it is expected not opening flow control division 8 at this time.
The air conditioner 1 of the present embodiment from the description above, can prevent due to liquid reflux phenomenon and Returning evaporimeter
Liquid refrigerant reduce, can be improved the efficiency of air conditioning.In addition, can also prevent following discomfort: it is original, for that will make
Cryogen returns to compressor 11 from gas-liquid separator in the form of gas refrigerant, the liquid refrigerant due to liquid reflux phenomenon
Compressor 11 is returned, therefore reduces the reliability of compressor 11.
In addition, the part of main piping 10 connecting with the entrance of compressor 11 is connected with bypass pipe arrangement 9, therefore transported in heating
When turning, it is able to suppress 11 side of compressor and forms high pressure.Therefore, when check valve is arranged in flow control division 8, strength that no setting is required
(therefore manufacturing cost is high) check valve, as long as setting takes into consideration only in the bypass pipe arrangement 9 in the case that the operating of air conditioner 1 stops
The check valve of the reflux of refrigerant.
Embodiment 2
Fig. 8 is the integrally-built explanatory diagram for indicating the air conditioner of the embodiment of the present invention 2.
In fig. 8, same as Example 1 with the component of Fig. 1 the same symbol etc., therefore omit detailed description.
Embodiment 2 and the difference of embodiment 1 are, firstly, the expansion valve 5 of embodiment 1 is not present.That is, as expansion valve,
The expansion valve 4 of the upstream side of the gas-liquid separator 7 of the flowing of the refrigerant of main piping 10 when there is only set on refrigeration operation.
In addition, main piping 10 when second temperature sensor 52 is set to refrigeration with the interconnecting piece of bypass pipe arrangement 9 and indoor
Between heat exchanger 6.More specifically, in the example of Fig. 2, second temperature sensor 52 is set to connection four-way valve 2 and compressor
The position with the positive front side at the interflow of bypass pipe arrangement 9 of the main piping 10 of 11 entrance side.
In addition, being carried out for the gas-liquid separation circulation pattern illustrated in embodiment 1 in refrigeration operation, heating
Without this point is also different when operating.In this way, because gas-liquid separation circulation pattern is carried out in refrigeration operation, in heating operation
When without so not needing expansion valve 5.
For the present embodiment, in gas-liquid separation circulation pattern, for ease of obtaining its effect (as described above), usually increase
The path of the long main piping 10 from the evaporator (indoor heat exchanger 6) evaporated for refrigerant to gas-liquid separator 7, concern and warp
The case where normal refrigeration operation.
That is, the path of above-mentioned main piping 10 is shorter, it is difficult to obtain gas-liquid separation circulation pattern in heating operation
Therefore above-mentioned effect is configured to, only implement gas-liquid separation circulation pattern in the case of cooling operation.
According to this structure, compared with embodiment 1 the case where, there cannot be expansion valve 5, can reduce manufacturing cost.
In addition, the control logic executed by control unit 50 can also be simplified than embodiment 1, therefore it also can reduce manufacture in this regard
Cost.
Embodiment 3
Fig. 9 is the integrally-built explanatory diagram for indicating the air conditioner of the embodiment of the present invention 3.
It is same as Example 2 with the component of Fig. 8 the same symbol etc. in Fig. 9, therefore omit detailed description.
In the present embodiment, also common with embodiment 2, gas-liquid separation circulation pattern is carried out in refrigeration operation, is being heated
Without gas-liquid separation circulation pattern when operating.In addition, second temperature sensor 52 be set to refrigeration when main piping 10 with
Aspect between the interconnecting piece and indoor heat exchanger 6 of bypass pipe arrangement 9, it is also common with embodiment 2.
Embodiment 3 and embodiment 2 the difference lies in that 11 side of compressor main piping 10 where connecting bypass
Piping 9, and then by temperature sensor 52 configure where.That is, in the present embodiment, compression when by refrigeration operation
The ratio four-way valve 2 of the main piping 10 of the entrance side of machine 11 is attached by the position of the upstream side of refrigerant and gas-liquid separator 7.
Then, the ratio of the main piping 10 of the entrance side of the compressor 11 when temperature sensor 52 is set on refrigeration operation and bypass pipe arrangement 9
Position of the interconnecting piece by the upstream side of refrigerant.
According to the present embodiment 3, even if in gas-liquid separation circulation pattern, in the gas refrigerant by bypass pipe arrangement 9
Liquid refrigerant is adulterated, does not also flow directly into the entrance of compressor 11, and passes through a four-way valve 2, so liquid reflux phenomenon
Length than embodiment 1,2 example reduce, improve compressor 11 reliability.
In addition, it includes various modifications examples the present invention is not limited to above-mentioned embodiment.For example, above-mentioned embodiment party
Formula is of the invention for ease of description and is illustrated in detail, and is not limited to have described clear all structures.Separately
Outside, a part of the structure of certain embodiment can be replaced as to the structure of other embodiment, in addition, also can be in certain implementation
The structure of other embodiment is added in the structure of mode.In addition, for a part of the structure of each embodiment, it can
Carry out addition, deletion, the displacement of other structures.
Claims (6)
1. a kind of air conditioner, have outdoor heat exchanger, indoor heat exchanger, compressor, expansion valve, four-way valve and by they
The main piping of connection, changes the flowing of the refrigerant in above each portion by switching above-mentioned four-way valve to carry out air conditioning,
Above-mentioned air conditioner is characterized in that,
Have gas-liquid separator, is set in the above-mentioned main piping for connecting above-mentioned outdoor heat exchanger and above-mentioned indoor heat exchanger
The side equipped with above-mentioned expansion valve, to from it is above-mentioned it is main piping flow into refrigerant carry out gas-liquid separation,
As above-mentioned expansion valve, have: the first expansion valve, above-mentioned main piping when being set to than above-mentioned gas-liquid separator by refrigeration
The upstream side of the flowing of refrigerant；And second expansion valve, above-mentioned main piping when being set to than above-mentioned gas-liquid separator by heating
Above-mentioned refrigerant flowing upstream side,
Above-mentioned air conditioner has:
Bypass pipe arrangement connects above-mentioned gas-liquid separator and is connected to the above-mentioned main piping of the entrance side of above-mentioned compressor；
Flow control division is set in above-mentioned bypass pipe arrangement, and to the flow of the gas refrigerant from above-mentioned gas-liquid separator
It is adjusted；
First temperature sensor is set to the above-mentioned flow control division downstream of ratio of above-mentioned bypass pipe arrangement；
Second temperature sensor, set on above-mentioned main piping between the interconnecting piece and above-mentioned four-way valve of above-mentioned bypass pipe arrangement；
And
Control unit, the detection temperature of detection temperature and above-mentioned second temperature sensor based on above-mentioned first temperature sensor,
The flow of the gas refrigerant adjusted using above-mentioned flow control division is controlled.
2. air conditioner according to claim 1, which is characterized in that
Above-mentioned control unit is so that the detection temperature of above-mentioned first temperature sensor and the detection temperature of above-mentioned second temperature sensor
The mode that is between first reference value and the second a reference value lower than the first reference value of difference carry out above-mentioned control.
3. a kind of air conditioner, have outdoor heat exchanger, indoor heat exchanger, compressor, expansion valve, four-way valve and by it
The main piping that connects, change the flowing of the refrigerant in above each portion by switching above-mentioned four-way valve to carry out air tune
It saving, above-mentioned air conditioner is characterized in that,
Have gas-liquid separator, is set in the above-mentioned main piping for connecting above-mentioned outdoor heat exchanger and above-mentioned indoor heat exchanger
The side equipped with above-mentioned expansion valve, to from it is above-mentioned it is main piping flow into refrigerant carry out gas-liquid separation,
The upstream of above-mentioned expansion valve flowing of the refrigerant of above-mentioned main piping when being set to than above-mentioned gas-liquid separator by refrigeration operation
Side,
Above-mentioned air conditioner has:
Bypass pipe arrangement, connect above-mentioned gas-liquid separator and be connected to above-mentioned compressor above-mentioned refrigeration when entrance side it is above-mentioned
Main piping；
Flow control division is set in above-mentioned bypass pipe arrangement, and to the flow of the gas refrigerant from above-mentioned gas-liquid separator
It is adjusted；
First temperature sensor is set to the above-mentioned flow control division downstream of ratio of above-mentioned bypass pipe arrangement；
Second temperature sensor, above-mentioned main piping when being set to refrigeration operation with the interconnecting piece of above-mentioned bypass pipe arrangement and above-mentioned
Between indoor heat exchanger；And
Control unit, in refrigeration operation, detection temperature and above-mentioned second temperature sensing based on above-mentioned first temperature sensor
The detection temperature of device controls the flow of the gas refrigerant adjusted using above-mentioned flow control division.
4. air conditioner according to claim 3, which is characterized in that
Above-mentioned bypass pipe arrangement connects the above-mentioned main piping for the entrance side for being connected to above-mentioned compressor and above-mentioned gas-liquid separator
It connects,
Above-mentioned second temperature sensor is set to the above-mentioned bypass pipe arrangement of ratio for the above-mentioned main piping connecting with the entrance of above-mentioned compressor
Coupling part lean on refrigerant upstream side.
5. air conditioner according to claim 3, which is characterized in that
The above-mentioned four-way valve of ratio of the above-mentioned main piping of the entrance side of above-mentioned compressor when above-mentioned bypass pipe arrangement connection refrigeration operation
Position and above-mentioned gas-liquid separator by the upstream side of refrigerant,
Above-mentioned second temperature sensor be set to above-mentioned refrigeration operation when above-mentioned compressor entrance side main piping ratio with it is upper
State the position of the interconnecting piece of bypass pipe arrangement on the upstream side.
6. the air conditioner according to any one of claim 2-5, which is characterized in that
Above-mentioned control unit is so that the detection temperature of above-mentioned first temperature sensor and the detection temperature of above-mentioned second temperature sensor
The mode that is between first reference value and the second a reference value lower than the first reference value of difference carry out above-mentioned control.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015168518A JP6546813B2 (en) | 2015-08-28 | 2015-08-28 | Air conditioner |
| JP2015-168518 | 2015-08-28 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106482375A CN106482375A (en) | 2017-03-08 |
| CN106482375B true CN106482375B (en) | 2019-03-26 |
Family
ID=58209597
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610597027.2A Active CN106482375B (en) | 2015-08-28 | 2016-07-26 | Air conditioner |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6546813B2 (en) |
| CN (1) | CN106482375B (en) |
Families Citing this family (8)
| 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 |
| JP6685473B1 (en) * | 2018-05-14 | 2020-04-22 | 日立ジョンソンコントロールズ空調株式会社 | Air conditioner |
| 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 |
| CN115342539A (en) * | 2021-05-14 | 2022-11-15 | 浙江三花汽车零部件有限公司 | Refrigeration system, expansion valve assembly and refrigeration system control method |
| 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 |
| 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 conditioner |
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 | Refrigerating 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 | Refrigerating 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 |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6546813B2 (en) | 2019-07-17 |
| JP2017044435A (en) | 2017-03-02 |
| CN106482375A (en) | 2017-03-08 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106482375B (en) | Air conditioner | |
| US8459051B2 (en) | Air conditioner and method of controlling the same | |
| US8353173B2 (en) | Refrigerating cycle apparatus and operation control method therefor | |
| US20140290292A1 (en) | Refrigerating and air-conditioning apparatus | |
| AU2004267299B2 (en) | Refrigeration system | |
| WO2019091241A1 (en) | Cooling circulation system for air conditioning, and air conditioner | |
| CN104364591B (en) | Conditioner | |
| JP6895901B2 (en) | Air conditioner | |
| WO2013145006A1 (en) | Air conditioning device | |
| CN105874282B (en) | Air-conditioning device | |
| CN107178833B (en) | Heat recovery external machine system and air conditioning system | |
| US20100206000A1 (en) | Air conditioner and method of controlling the same | |
| JP2002081767A (en) | Air conditioner | |
| CN114322106B (en) | Air conditioning system | |
| WO2019091240A1 (en) | Heating circulation system for air conditioning, and air conditioner | |
| CN114151934A (en) | Air conditioner | |
| WO2011074028A1 (en) | Air conditioner | |
| CN106949657B (en) | Air conditioning system with supercooling device and control method thereof | |
| US11841179B2 (en) | Heating, ventilation, and air-conditioning systems and methods | |
| CN109084392A (en) | Air conditioner | |
| JP4462436B2 (en) | Refrigeration equipment | |
| CN213089945U (en) | Air conditioner | |
| US11662125B2 (en) | Combined heat exchanger, heat exchanging system and the optimization method thereof | |
| KR101416939B1 (en) | Outdoor heat exchanger | |
| JPH04214153A (en) | Refrigerating cycle device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| TA01 | Transfer of patent application right |
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. |
|
| TA01 | Transfer of patent application right | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |