AU2016224364A1 - Refrigeration cycle apparatus - Google Patents
Refrigeration cycle apparatus Download PDFInfo
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- AU2016224364A1 AU2016224364A1 AU2016224364A AU2016224364A AU2016224364A1 AU 2016224364 A1 AU2016224364 A1 AU 2016224364A1 AU 2016224364 A AU2016224364 A AU 2016224364A AU 2016224364 A AU2016224364 A AU 2016224364A AU 2016224364 A1 AU2016224364 A1 AU 2016224364A1
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- Australia
- Prior art keywords
- refrigeration cycle
- compressor
- pressure
- control unit
- limit value
- 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.)
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Classifications
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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
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/89—Arrangement or mounting of control or safety devices
-
- 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
- F25B1/00—Compression machines, plants or systems with non-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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Air Conditioning Control Device (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Through the present invention, a compressor is stopped in response to operation of a high-pressure switch, and subsequently, the compressor is restarted in response to returning of the high-pressure switch, and the lower-limit value of opening degree control for an expansion valve is also shifted to an increased value during the restarting.
Description
1 DESCRIPTION REFRIGERATION CYCLE APPARATUS Technical Field
Embodiments described herein relate generally to a refrigeration cycle apparatus coping with a rise in the pressure on the high-pressure side.
Background Art A refrigeration cycle apparatus incorporated in an air-conditioning apparatus or the like is provided with a high-pressure switch responding to the pressure on the high-pressure side of a refrigeration cycle, when the pressure on the high-pressure side rises and the high-pressure switch operates, the compressor is stopped, and when thereafter the pressure on the high-pressure side lowers and the high-pressure switch is restored, the compressor is restarted. When the high-pressure switch operates, the compressor is stopped, whereby the pressure on the high-pressure side is prevented from abnormally rising, and the safety of the refrigeration cycle equipment including the compressor is secured.
Citation List Patent Literature
Patent Literature 1: JP H04-251158 A
Patent Literature 2: JP 2008-224156 A Summary of Invention
Technical Problem
Even when the compressor is restarted in response to the restoration of the high-pressure switch, the pressure on the high-pressure side soon rises again, and the high-pressure switch operates in some cases.
In this case, the compressor frequently repeats a stop and restart to thereby cause a variation in the indoor temperature and deteriorate the comfort of air conditioning.
Further, as a refrigerant for the refrigeration cycle, in place of the R410A refrigerant, a changeover to the refrigerant R32 excellent in ability and energy efficiency is advancing. However, as for the refrigerant R32, the pressure thereof at the time when it is discharged from the compressor becomes higher than the case of the refrigerant R410A, and hence a state where the high-pressure switch is liable to operate is brought about.
An object of the present invention is to provide a refrigeration cycle apparatus capable of preventing the pressure on the high-pressure side after a restart of the compressor from rising, and thereby preventing frequent repetitions of a stop and restart of the compressor from occurring.
Solution to Problem
According to Claim 1, a refrigeration cycle apparatus includes a refrigeration cycle including a compressor, a condenser, an expansion valve, and an evaporator; a high-pressure switch responding to the pressure on the high-pressure side of the refrigeration cycle; and a control unit configured to stop the compressor in response to an operation of the high-pressure switch, thereafter restart the compressor in response to restoration of the high-pressure switch, and at the time of the restart, shift a lower-limit value of opening degree control for the expansion valve toward the increase side.
Brief Description of Drawings FIG. 1 is a block diagram showing the configuration of an embodiment. FIG. 2 is a flowchart showing the control of the embodiment. FIG. 3 is a view showing a relationship between the capacity of a refrigeration cycle at the time of cooling and the pressure on the high-pressure side in the embodiment. FIG. 4 is a view showing a relationship between the capacity of a refrigeration cycle at the time of heating and the pressure on the high-pressure side in the embodiment. FIG. 5 is a view showing examples of changes in the pressure on the high-pressure side, expansion valve opening, discharged refrigerant temperature, and compressor rotational speed.
Mode for Carrying Out the Invention
Hereinafter, an embodiment will be described with reference to the drawings.
As shown in FIG. 1, one end of an outdoor heat exchanger 3 is piping-connected to an discharge port of a compressor 1 through a four-way valve 2. One end of each of a plurality of indoor heat exchangers 5a, 5b, ... 5n is piping-connected to the other end of the outdoor heat exchanger 3 through each of a plurality of expansion valves 4a, 4b, ... 4n, and the other end of each of the plurality of indoor heat exchangers 5a, 5b, ... 5n is piping-connected to an inlet port of the compressor 1 through the four-way valve 2. These piping connections constitute a heat pump refrigeration cycle. This heat pump refrigeration cycle system is filled with a refrigerant including the refrigerant R32 in an amount of, for example, 50% or more.
At the time of cooling, as indicated by solid line arrows, the refrigerant discharged from the compressor 1 flows into the indoor heat exchangers (evaporators) 5a, 5b, ... 5n through the four-way valve 2, outdoor heat exchanger (condenser) 3, and expansion valves 4a, 4b, ... 4n, and the refrigerant flowing out of the indoor heat exchangers 5a, 5b, ... 5n is sucked into the compressor 1 through the four-way valve 2. At the time of heating, as indicated by broken line arrows, the flow paths in the four-way valve 2 are changed, whereby the refrigerant discharged from the compressor 1 flows into the indoor heat exchangers (condenser) 5a, 5b, ... 5n, and the refrigerant flowing out of the indoor heat exchangers 5a, 5b, ... 5n is sucked into the compressor 1 through expansion valves 4a, 4b, ... 4n, outdoor heat exchanger (evaporator) 3, and four-way valve 2. ,
An outdoor fan 6 is arranged in the vicinity of the outdoor heat exchanger 3, and indoor fans 7a, 7b, ... 7n are arranged in the vicinities of the indoor heat exchangers 5a, 5b, ... 5n. An inverter 8 is connected to a motor of the compressor 1. The inverter 8 converts a voltage of an AC source 9 into a DC voltage, and further converts the DC voltage into an AC voltage of a predetermined frequency F to output the AC voltage. The motor of the compressor 1 operates at a rotational speed corresponding to this output frequency F. A high-pressure switch 11 and refrigerant temperature sensor 12 are attached to the high-pressure side piping between the discharge port of the compressor 1 and the four-way valve 2. The high-pressure switch 11 operates when the pressure (called the pressure on the high-pressure side) Pd of the refrigerant discharged from the compressor 1 rises to a value greater than a set value Pd2, and is restored when the pressure Pd on the high-pressure side lowers to a value smaller than a set value Pdl (<Pd2). The refrigerant temperature sensor 12 detects the temperature Td of the refrigerant discharged from the compressor 1.
Each of the expansion valves 4a, 4b, ... 4n is a so-called pulse-motor valve in which the degree of opening continuously changes according to the number of pulses of a drive pulse signal input thereto.
In an outdoor unit A, the compressor 1, four-way valve 2, outdoor heat exchanger 3, expansion valves 4a, 4b, ... 4n, outdoor fan 6, and inverter 8 are incorporated. In a plurality of indoor units Ba,
Bb, ... Bn, the indoor heat exchangers 5a, 5b, ... 5n, and indoor fans 7a, 7b, ... 7n are respectively incorporated. A control unit 20 is connected to the outdoor unit A and indoor units Ba, Bb, ... Bn.
The control unit 20 is constituted of a microcomputer and peripheral circuit thereof, and includes, as main functions, a first control section 20a, second control section 20b, and third control section 20c.
The first control section 20a stops the compressor 1 in response to an operation of the high-pressure switch 11, and thereafter restarts the compressor 1 in response to the restoration of the high-pressure switch 11.
The second control section 20b controls, at the time of the operation of the heat pump refrigeration cycle, the degree of opening Q of each of the expansion valves 4a, 4b, ... 4n to be within a range of a predetermined upper-limit value Qmax to a predetermined lower-limit value Qmin in order that the degree of superheat (at the time of cooling) or the degree of supercooling (at the time of heating) of the indoor heat exchangers 5a, 5b, ... 5n may become a constant value.
The third control section 20c shifts (openingnarrowing control), at the time of a restart of the compressor 1 based on the restoration of the high-pressure switch 11, the lower-limit value Qmin of the opening degree control for each of the expansion valves 4a, 4b, ... 4n toward the increase side by a predetermined value AQ.
It should be noticed that the second control section 20b sets the predetermined value AQ which is the shift amount to different values (AQl, AQ2, ... AQn) according to the capacity (the number of indoor units Ba, Bb, ... Bn in operation) of the heat pump refrigeration cycle. More specifically, the second control section 20b sets the predetermined value AQ to a value proportional to the capacity of the heat pump refrigeration cycle at the time of cooling, and to a value inversely proportional to the capacity of the heat pump refrigeration cycle at the time of heating. Further, the second control section 20b selectively executes the opening-narrowing control of shifting the lower-limit value Qmin on the basis of a comparison between the discharged refrigerant temperature Td to be detected by the refrigerant temperature sensor 12 and a set value Tds. Furthermore, the second control section 20b cancels the selective execution of the openingnarrowing control concomitantly with shutdown of the heat pump refrigeration cycle.
Next, the control to be executed by the control unit 20 will be described below with reference to the flowchart of FIG. 2.
At the time of a start of an operation of at least one of the indoor units Ba, Bb, ... Bn (YES in step 51) , the control unit 20 starts the compressor 1 (step 52) . Concomitantly with the start, the control unit 20 confirms whether or not an opening degree limiting flag f is "0" (step S3).
When the opening degree limiting flag f is "0" (YES in step S3), the control unit 20 controls the degree of opening Q of each of the expansion valves 4a, 4b, ... 4n to be within the range of the predetermined upper-limit value Qmax to the predetermined lower-limit value Qmin in order that the degree of superheat (at the time of cooling) or the degree of supercooling (at the time of heating) of the indoor heat exchangers 5a, 5b, ... 5n may become a constant value (step S4).
The control unit 20 monitors the operation of the high-pressure switch 11 concomitantly with the opening degree control (step S7) . When the high-pressure switch 11 does not operate (NO in step S7), the control unit 20 monitors a shutdown of the indoor units Ba,
Bb, ... Bn (step S14).
When a shutdown of the indoor units Ba, Bb, ... Bn is not needed (NO in step S14), the control unit 20 returns to the flag determination of step S3. When a shutdown of the indoor units Ba, Bb, ... Bn is needed (YES in step S14), the control unit 20 stops the compressor 1 (step S15). Further, the control unit 20 resets the opening degree limiting flag f to ”0" (step S16), and returns to the operation start determination of first step SI. ·
On the other hand, when the high-pressure switch 11 operates (YES in step S7), the control unit 20 stops the compressor 1 (step S8). By this stop, the pressure on the high-pressure side is prevented from abnormally rising. Further, the control unit 20 starts time measurement t (step S9), and monitors the restoration of the high-pressure switch 11 (step S10). When the restoration of the high-pressure switch 11 is not obtained (NO in step S10), the time measurement t is continued (step S9).
When the pressure on the high-pressure side lowers, and the high-pressure switch 11 is restored (YES in step S10), the control unit 20 determines whether or not the time measurement t has reached a fixed time ts (step Sll). The fixed time ts is a restart limiting time for preventing the damage or the like of the compressor 1.
When the time measurement t has not reached the fixed time ts (NO in step Sll), the control unit 20 continues the time measurement t (step S9). When the time measurement t has reached the fixed time ts (YES in step Sll), the control unit 20 restarts the compressor 1 (step S12), and sets the opening degree limiting flag f to "1" (step S13). Further, the controller 20 monitors a shutdown of the indoor units Ba, Bb, ... Bn (step S14).
When a shutdown of the indoor units Ba, Bb, ... Bn is not needed (NO in step S14), the control unit 20 returns to the flag determination of step S3. At this time, the opening degree limiting flag f is "1" (NO in step S3), and hence the control unit 20 compares the discharged refrigerant temperature (detected temperature) Td detected by the refrigerant temperature sensor 12 and the set value Tds with each other (step S5) .
When the discharged refrigerant temperature Td is lower than the set value Tds (NO in step S5), the control unit 20 controls the degree of opening Q of each of the expansion valves 4a, 4b, ... 4n to be within the range of the upper-limit value Qmax to the normal lower-limit value Qmin (step S4).
When the discharged refrigerant temperature Td is higher than or equal to the set value Tds (YES in step S5), the control unit 20 shifts the lower-limit value Qmin of the opening degree control toward the increase side by a predetermined value AQ, and controls the degree of opening Q of each of the expansion valves 4a, 4b, ... 4n to be within the range of the upper-limit value Qmax to the lower-limit value "Qmin+AQ" (step S6) . A relationship between the outdoor air temperature and the pressure Pd on the high-pressure side, and a relationship between the outdoor air temperature and the discharged refrigerant temperature Td are respectively proportional relations. When the outdoor air temperature rises, the pressure Pd on the high-pressure side and the discharged refrigerant temperature Td also rise. In this state, when the degree of opening Q of each of the expansion valves 4a, 4b, ... 4n is narrowed to the lower-limit value Qmin, there is a possibility of the high-pressure switch 11 operating after an elapse of not so long a time from the restart of the compressor 1, and thereby stopping the compressor 1.
Thus, when the discharged refrigerant temperature Td is higher than or equal to the set value Tds, the opening-narrowing control of shifting the lower-limit value Qmin of the opening degree control toward the increase side is executed, whereby it is possible to prevent the pressure Pd on the high-pressure side after the restart of the compressor 1 from rising. Particularly, even when the refrigerant with which the heat pump refrigeration cycle system is filled is the refrigerant R32, by carrying out the opening-narrowing control as in the case of the refrigerant R410A, it is possible to prevent the pressure Pd on the high-pressure side after the restart of the compressor 1 from rising.
Accordingly, it is possible to prevent the operation of the high-pressure switch 11 at the time of the restart of the compressor 1 from being carried out, and by extension, to prevent frequent repetitions of a stop and restart of the compressor 1 from occurring.
Thereby, the indoor temperature which is the load can be stabilized, and the comfort of air conditioning is improved.
It should be noted that when the outdoor air temperature lowers, the pressure Pd on the high-pressure side and the discharged refrigerant temperature Td also lower, and hence there is a possibility of the opening-narrowing control becoming unnecessary. When the opening-narrowing control is furthermore carried out under such circumstances, there is a possibility of the operational state of the heat pump refrigeration cycle becoming unable to be held appropriate, and thereby causing a shortage of airconditioning capability. In consideration of these circumstances, when the discharged refrigerant temperature Td is lower than the set value Tds (NO in step S5), the control unit 20 controls the degree of opening Q to be within the range of the upper-limit value Qmax to the normal lower-limit value Qmin without executing the opening-narrowing control (step S4).
Thereafter, when a state where a shutdown of the indoor units Ba, Bb, ... Bn is needed is brought about (YES in step S14), the control unit 20 stops the compressor 1 (step S15). Then, the control unit 20 resets the opening degree limiting flag f (=1) to "0" (step S16), and returns to the operation start determination of first step SI. By resetting the opening degree limiting flag f to "0", the selective execution of the opening-narrowing control corresponding to the discharged refrigerant temperature Td is canceled.
Incidentally, the pressure Pd on the high-pressure side changes according to the capacity (the number of indoor units Ba, Bb, ... Bn in operation) of the heat pump refrigeration cycle. That is, at the time of cooling, as shown in FIG. 3, the larger the capacity, the higher the pressure Pd on the high-pressure side rises. Conversely, at the time of heating, as shown in FIG. 4, the smaller the capacity, the higher the pressure Pd on the high-pressure side rises.
In consideration of these circumstances, the control unit 20 sets the predetermined value AQ which is the shift amount of the opening-narrowing control to different values (AQl, AQ2, ... AQn) according to the number of indoor units Ba, Bb, ... Bn in operation.
That is, at the time of cooling, in consideration of the fact that the larger the number of indoor units in operation, the higher the pressure Pd on the high-pressure side rises, the control unit 20 sets the predetermined value AQl when the number of indoor units in operation is 1, sets the predetermined value Δ02 (>Q1) when the number is 2, sets the predetermined value AQ3 (>Q2) when the number is 3, and sets the predetermined value AQn (... >Q3) when the number is the largest number n. At the time of heating, in consideration of the fact that the smaller the number of indoor units in operation, the higher the pressure Pd on the high-pressure side rises, the control unit 20 sets the predetermined value AQn when the number of indoor units in operation is 1, and sets the predetermined values AQ3, AQ2, and AQl in sequence with the increase in the number of indoor units in operation. In short, on the side on which the rise in the pressure Pd on the high-pressure side is remarkable, the predetermined value AQ is made large.
Further, concomitantly with the switching of the predetermined values AQl, AQ2, ... AQn, the control unit 20 switches the set value Tds which is the criterion of the selective execution of the openingnarrowing control. That is, the control unit 20 selects a set value Tdsl when the predetermined value AQl is set, selects a set value Tds2 (>Tdsl) when the predetermined value AQ2 is set, selects a set value Tds3 (>Tds2) when the predetermined value AQ3 is set, 5 and selects a set value Tdsn (... >Tds3) when the predetermined value AQn is set.
As described above, the predetermined value AQ which is the shift amount of the opening-narrowing control is set to different values according to the 10 number of indoor units Ba, Bb, ... Bn in operation, and the set value Tds which is the criterion of the selective execution of the opening-narrowing control is switched according to the predetermined value AQ, whereby it is possible to prevent frequent repetitions 15 of a stop and restart of the compressor 1 from occurring irrespective of a change in the number of indoor units Ba, Bb, ... Bn in operation, i.e., irrespective of a change in the capacity of the heat pump refrigeration cycle. 20 Examples of changes in the pressure Pd on the high-pressure side, degree of opening Q of the expansion valve, discharged refrigerant temperature Td, and compressor rotational speed are shown in FIG. 5.
As the degree of opening Q is narrowed, the pressure Pd 25 on the high-pressure side rises, and when the pressure
Pd on the high-pressure side rises to a set value Pd2*4.1 MPa, the high-pressure switch 11 operates to thereby stop the compressor 1. Thereafter, when the pressure Pd on the high-pressure side lowers to a set 30 value Pdl*3.2 MPa, the high-pressure switch 11 is restored, and the compressor 1 is restored, however the discharged refrigerant temperature Td exceeds a set value Tds»65 °C, and hence narrowing of the degree of opening Q is limited to the minimum value Qmin«200 pis which is the value after the shift, and concomitantly with this, the rise in the pressure Pd on the high-pressure side is held to about 3.7 MPa.
It should be noticed that although in the above embodiment, a description has been given by taking the refrigeration cycle apparatus to be incorporated in the air-conditioning apparatus as an example, the embodiment is also similarly applicable to a refrigeration cycle apparatus to be incorporated in other apparatuses.
The above embodiment and modification examples have been presented by way of example only, and are not intended to limit the scope of the inventions. Indeed, the novel embodiment and modification examples described herein may be embodied in a variety of other forms; furthermore, various omissions, substitutions and changes in the form of the embodiment and modification examples described herein may be made without departing from the spirit of the inventions.
The accompanying claims and their equivalents are intended to cover such forms or modifications as would fall within the scope and spirit of the inventions. Reference Signs List 1 ... compressor, 2 ... four-way valve, 3 ... outdoor heat exchanger, 4a, 4b, ... 4n .... expansion valve, 5a, 5b, ... 5n .... indoor heat exchanger, 8 ... inverter, 9 ... AC source, and 20 ... control unit
Claims (6)
1. A refrigeration cycle apparatus characterized by comprising: a refrigeration cycle including a compressor, a condenser, an expansion valve, and an evaporator; a high-pressure switch responding to the pressure on the high-pressure side of the refrigeration cycle; and a control unit configured to stop the compressor in response to an operation of the high-pressure switch, thereafter restart the compressor in response to restoration of the high-pressure switch, and at the time of the restart, shift a lower-limit value of opening degree control for the expansion valve toward the increase side.
2. The refrigeration cycle apparatus of Claim 1, characterized in that the control unit sets a shift amount of the lower-limit value to different values according to the capacity of the refrigeration cycle.
3. The refrigeration cycle apparatus of Claim 2, characterized in that the refrigeration cycle is a heat pump refrigeration cycle capable of carrying out cooling and heating, and the control unit sets the shift amount of the lower-limit value to a value proportional to the capacity of the refrigeration cycle at the time of cooling, and to a value inversely proportional to the capacity of the refrigeration cycle at the time of heating.
4. The refrigeration cycle apparatus of any one of Claim 1 through Claim 3, characterized by further comprising temperature detecting section for detecting a temperature of a refrigerant discharged from the compressor, wherein the control unit selectively executes shifting of the lower-limit value according to whether or not a detected temperature of the temperature detecting section is higher than or equal to a set value.
5. The refrigeration cycle apparatus of any one of Claim 1 through Claim 3, characterized in that the control unit cancels the selective execution of the shifting of the lower-limit value concomitantly with a shutdown of the refrigeration cycle.
6. The refrigeration cycle apparatus of any one of Claim 1 through Claim 3, characterized in that the refrigerant of the refrigeration cycle contains the refrigerant R32 in an amount of 50% or more .
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015-038470 | 2015-02-27 | ||
| JP2015038470A JP2018063056A (en) | 2015-02-27 | 2015-02-27 | Refrigeration cycle device |
| PCT/JP2016/055914 WO2016136979A1 (en) | 2015-02-27 | 2016-02-26 | Refrigeration cycle device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| AU2016224364A1 true AU2016224364A1 (en) | 2017-09-21 |
| AU2016224364B2 AU2016224364B2 (en) | 2018-09-20 |
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| Application Number | Title | Priority Date | Filing Date |
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| AU2016224364A Active AU2016224364B2 (en) | 2015-02-27 | 2016-02-26 | Refrigeration cycle apparatus |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP2018063056A (en) |
| AU (1) | AU2016224364B2 (en) |
| WO (1) | WO2016136979A1 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106338168B (en) * | 2016-10-09 | 2019-02-19 | 深圳市共济科技股份有限公司 | A kind of refrigeration unit control method and system |
| WO2020103666A1 (en) * | 2018-11-19 | 2020-05-28 | 艾默生环境优化技术(苏州)有限公司 | Control system having both electronic control mode and mechanical control mode, and condensing unit |
| CN109798635A (en) * | 2019-01-15 | 2019-05-24 | 广东美的暖通设备有限公司 | The control method and air-conditioning system of air-conditioning system |
| JP2020197328A (en) * | 2019-05-31 | 2020-12-10 | シャープ株式会社 | Air conditioner |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61202052A (en) * | 1985-03-06 | 1986-09-06 | ダイキン工業株式会社 | Refrigerator with electric type expansion valve |
| JPH042371Y2 (en) * | 1986-06-11 | 1992-01-27 | ||
| JPH07158981A (en) * | 1993-12-09 | 1995-06-20 | Mitsubishi Electric Corp | Air conditioning device |
| JP3458293B2 (en) * | 1995-02-20 | 2003-10-20 | 松下電器産業株式会社 | Operation control device for multi-room air conditioner |
| JP4063041B2 (en) * | 2002-10-23 | 2008-03-19 | 株式会社富士通ゼネラル | Control method of multi-room air conditioner |
| JP2007218532A (en) * | 2006-02-17 | 2007-08-30 | Daikin Ind Ltd | Air conditioner |
| JP2007212135A (en) * | 2007-04-12 | 2007-08-23 | Mitsubishi Electric Corp | Air conditioner |
-
2015
- 2015-02-27 JP JP2015038470A patent/JP2018063056A/en active Pending
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2016
- 2016-02-26 AU AU2016224364A patent/AU2016224364B2/en active Active
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Also Published As
| Publication number | Publication date |
|---|---|
| WO2016136979A1 (en) | 2016-09-01 |
| JP2018063056A (en) | 2018-04-19 |
| AU2016224364B2 (en) | 2018-09-20 |
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