Patent Application
20050155368
This application claims the benefit of the Korean Application No. P2004-3881 filed on Jan. 19, 2004, which is hereby incorporated by reference.
1. Field of the Invention
The present invention relates to multi-type air conditioner, and more particularly, to a method for controlling a multi-type air conditioner which enables to minimize stagnation of refrigerant at turned off indoor units during some of the indoor units are in operation for heating rooms, and reduce noise occurred when the stagnant refrigerant is removed.
2. Background of the Related Art
In general, the air conditioner is an apparatus for cooling or heating rooms, such as residential space, restaurant, office, and the like. Nowadays, for effective cooling/heating of a room space divided into a plurality of rooms, there has been ceaseless development of the multi-type air conditioner that can perform cooling or heating, or cooling and heating at the same time depending on an operation condition.
The multi-type air conditioner has a plurality of indoor units connected to one outdoor unit, so that only some of the indoor units perform cooling or heating according to user's requirement.
In this instance, in a case some of the indoor units of the multi-type air conditioner perform heating, even though the indoor units which perform heating is turned on, rest of the indoor units are turned off.
However, since the refrigerant is supplied from the outdoor unit to all of the indoor units of the multi-type air conditioner, the refrigerant is introduced into the turned off indoor units unnecessarily and stagnant therein as the heating is progressed.
The stagnant refrigerant at the turned off indoor units results in shortage of refrigerant circulating through the multi-type air conditioner, not only to reduce operation efficiency, but also elevate a discharge temperature of the refrigerant and reduce a discharge pressure, owing to a low flow rate of refrigerant in/out of the compressor.
Therefore, a control part of the multi-type air conditioner opens an expansion valve on the turned off indoor unit, to prevent stagnation of the refrigerant.
However, the uniform opening of the expansion valves at regular intervals by the control part of the related art multi-type air conditioner makes performance of proper operation control difficult.
Particularly, because a loud noise is occurred when the expansion valve is opened to discharge the refrigerant, if the expansion valve is opened periodically regardless of operation condition, to occur the noise periodically, product reliability drops, and complaints from users will result in.
Accordingly, the present invention is directed to a method for controlling a multi-type air conditioner that substantially obviates one or more of the problems due to limitations and disadvantages of the related art.
An object of the present invention is to provide a method for controlling a multi-type air conditioner, which can minimize stagnant refrigerant at turned off indoor units during heating operation of some of the indoor units.
Other object of the present invention is to provide a method for controlling a multi-type air conditioner, which can reduce noise occurred when the stagnant refrigerant is removed from the turned off indoor units.
Additional features and advantages of the invention will be set forth in the description which follows, and in part will be apparent to those having ordinary skill in the art upon examination of the following or may be learned from practice of the invention. The objectives and other advantages of the invention will be realized and attained by the structure particularly pointed out in the written description and claims hereof as well as the appended drawings.
To achieve these objects and other advantages and in accordance with the purpose of the present invention, as embodied and broadly described herein, the method for controlling a multi-type air conditioner having a plurality of indoor units each with an expansion valve, an indoor heat exchanger, and an indoor fan, some of which heat rooms, and rest of which are turned off, includes the steps of (S11) defining a saturation temperature of refrigerant by using a heating cycle of the refrigerant, and Mollier chart, (S12) measuring a temperature of the refrigerant stagnant at the turned off indoor units, (S13) determining if a temperature difference of the refrigerant temperature and the saturation temperature is within a temperature range preset at a control part, (S14) opening the expansion valves of the turned off indoor units, if the temperature difference is within the temperature range preset at the control part, and (S15) closing the expansion valve of the turned off indoor units, if the temperature difference is not within the temperature range preset at the control part.
Preferably, the S14 step includes the step of opening the expansion valve at an extent of opening of 1%<A<20%. Preferably, the method further includes the step of performing all the steps starting from the Sli step again after the S14 or S15 step is performed.
The refrigerant is pure refrigerant, and the saturation temperature is defined as a temperature T1 or T2 of a point where a condensing section of the heating cycle and Mollier chart meet.
The refrigerant is mixed refrigerant, and the saturation temperature is defined as an average temperature of the temperatures T1 and T2 of points where a condensing section of the heating cycle and Mollier chart meet.
The refrigerant is mixed refrigerant, and the saturation temperature is defined as a weighted average temperature of the temperatures T1 and T2 of points where a condensing section of the heating cycle and Mollier chart meet.
In the meantime, the refrigerant temperature is a temperature of the refrigerant introduced into/discharged from the indoor heat exchanger.
The refrigerant temperature is an average of a temperature of the refrigerant introduced into the indoor heat exchanger, and a temperature of the refrigerant discharged from the indoor heat exchanger.
In the meantime, preferably the temperature range preset at the control part varies with a room temperature, or an outdoor temperature. Preferably, the temperature range preset at the control part varies with a room temperature and an outdoor temperature.
In other aspect of the present invention, there is provided a method for controlling a multi-type air conditioner having a plurality of indoor units each with an expansion valve, an indoor heat exchanger, and an indoor fan, some of which heat rooms, and rest of which are turned off, including the steps of (S21) defining a room temperature, (S22) measuring a temperature of the refrigerant stagnant at the turned off indoor units, (S23) determining if a temperature difference of the refrigerant temperature and the saturation temperature is within a temperature range preset at a control part, (S24) opening the expansion valves of the turned off indoor units, if the temperature difference is within the temperature range preset at the control part, and (S25) closing the expansion valve of the turned off indoor units, if the temperature difference is not within the temperature range preset at the control part.
In another aspect of the present invention, there is provided a method for controlling a multi-type air conditioner having a plurality of indoor units each with an expansion valve, an indoor heat exchanger, and an indoor fan, some of which heat rooms, and rest of which are turned off, including the steps of (S31) opening the expansion valves of the turned off indoor units at a first extent ‘B’ of opening, (S32) defining a saturation temperature of refrigerant by using a heating cycle of the refrigerant, and Mollier chart, (S33) measuring a temperature of the refrigerant stagnant at the turned off indoor units, (S34) determining if a temperature difference of the refrigerant temperature and the saturation temperature is within a temperature range preset at a control part, (S35) opening the expansion valves of the turned off indoor units at a second extent ‘C’ of opening greater than the first extent of opening, if the temperature difference is within the temperature range preset at the control part, and (S36) opening the expansion valves of the turned off indoor units at the first extent of opening ‘B’, if the temperature difference is not within the temperature range preset at the control part.
Preferably, the first extent ‘B’ of opening of the expansion valve is 1%<B<10%, and the second extent ‘C’ of opening of the expansion valve is 4%<C<20%.
The method further includes the step of performing all the steps in succession again starting from the S32 step after the S35 or S36 step is performed.
In the meantime, the refrigerant is pure refrigerant, and the saturation temperature is defined as a temperature T1 or T2 of a point where a condensing section of the heating cycle and Mollier chart meet.
The refrigerant is mixed refrigerant, and the saturation temperature is defined as an average temperature of the temperatures T1 and T2 of points where a condensing section of the heating cycle and Mollier chart meet.
The refrigerant is mixed refrigerant, and the saturation temperature is defined as a weighted average temperature of the temperatures T1 and T2 of points where a condensing section of the heating cycle and Mollier chart meet.
The refrigerant temperature is a temperature of the refrigerant introduced into or discharged from the indoor heat exchanger.
The refrigerant temperature is an average of a temperature of the refrigerant introduced into the indoor heat exchanger, and a temperature of the refrigerant discharged from the indoor heat exchanger.
Preferably, the temperature range preset at the control part varies with a room temperature, or an outdoor temperature. The temperature range preset at the control part varies with a room temperature and an outdoor temperature.
In further aspect of the present invention, there is provided a method for controlling a multi-type air conditioner having a plurality of indoor units each with an expansion valve, an indoor heat exchanger, and an indoor fan, some of which heat rooms, and rest of which are turned off, including the steps of (S41) opening the expansion valves of the turned off indoor units at a first extent ‘B’ of opening, (S42) measuring a room temperature, (S43) measuring a temperature of the refrigerant stagnant at the turned off indoor units, (S44) determining if a temperature difference of the refrigerant temperature and the room temperature is within a temperature range preset at a control part, (S45) opening the expansion valves of the turned off indoor units at a second extent ‘C’ of opening greater than the first extent of opening, if the temperature difference is within the temperature range preset at the control part, and (S46) opening the expansion valves of the turned off indoor units at the first extent of opening ‘B’, if the temperature difference is not within the temperature range preset at the control part.
It is to be understood that both the foregoing description and the following detailed description of the present invention are exemplary and explanatory and are intended to provide further explanation of the invention claimed.
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the invention and together with the description serve to explain the principle of the invention.
In the drawings;
Reference will now be made in detail to the preferred embodiments of the present invention, examples of which are illustrated in the accompanying drawings. In describing the embodiments, same parts will be given the same names and reference symbols, and repetitive description of which will be omitted.
Referring to
The outdoor unit 10 includes a compressor 11, an outdoor heat exchanger 12, an outdoor fan 13, and accumulator 14, and the each of the indoor units 30a, 30b, and 30c includes an indoor heat exchanger 31a, 31b, or 31c, an indoor fan 32a, 32b, or 32c, and an expansion valve 33a, 33b, and 33c.
The distributor 20 guides the refrigerant from the outdoor unit 10 to the indoor units 30, and vice versa. For this, the distributor 20 is connected to the outdoor heat exchanger 12 with a first refrigerant pipe 21, and to the compressor 11 with a second refrigerant pipe. The distributor 20 is also connected to the indoor heat exchangers. 30a, 30b, and 30c with first branch pipes 21a, 21b, and 21c branched from the first refrigerant pipe 21, and second branch pipes 22a, 22b, and 22c branched from the second refrigerant pipe 22.
The first branch pipes 21a, 21b, and 21c has expansion valves 33a, 33b, 33c mounted thereon. The expansion valves 33a, 33b, and 33c are ordinary LEVs (Linear Expansion Valve).
The operation of the multi-type air conditioner will be described with reference to the attached drawings.
Referring to
The refrigerant is then introduced into the distributor 20 following the first refrigerant pipe 21, and guided to the expansion valves 33a, 33b, and 33c of respective indoor units 30a, 30b, and 30c following the first branch pipes 21a, 21b, and 21c. In this instance, the refrigerant expands at respective expansion valves 33a, 33b, and 33c, and becomes into low temperature refrigerant.
Then, the refrigerant is introduced into the indoor heat exchangers 31a, 31b, and 31c, and heat exchanges with room air by the indoor fans 32a, 32b, and 32c, when the room air becomes low temperature air by heat exchange with the refrigerant, and discharged to the room.
Then, the refrigerant is introduced into the distributor 20 following the second branch pipes 22a, 22b, and 22c, and therefrom to the outdoor unit 10 following the second refrigerant pipe 22.
As above process is repeated, the low temperature air is supplied to the room, to cool down the room.
In the meantime, as described, if all the indoor units 30a, 30b, and 30c perform cooling, all the expansion valves 33a, 33b, and 33c open, to supply refrigerant to all the indoor heat exchangers 31a, 31b, and 31c. However, in a case only some of the indoor units 30 perform cooling, the expansion valves on turned off indoor units are closed. Therefore, in the case only some of the indoor units perform cooling, no refrigerant is supplied to the indoor heat exchangers of the turned off indoor units.
Referring to
In the following description, it is assumed that, of the three indoor units 30, two indoor units 30a, and 30c heat rooms, and rest one indoor unit 30b is in a turned off state.
At first, the refrigerant introduced into the indoor unit 30a, and 30c heating the rooms is introduced into the indoor heat exchangers 31a, and 31c, and heat exchanges with room air. The room air heat exchanged with the refrigerant to be high temperature is discharged to the rooms by the indoor fans 32a, and 32c.
Thereafter, the refrigerant passes through, and expands at the expansion valves 33a, and 33c, and introduced into the distributor 20 following the first branch pipes 21a, and 21c. Then, the refrigerant is introduced into the outdoor heat exchanger 12 through the first refrigerant pipe 21, and heat exchanges with outdoor air, and returns to the, compressor 11 through the accumulator 14.
In the meantime, the refrigerant introduced into the turned off indoor unit 30b becomes stagnant at the indoor unit 30b as the expansion valve 33b is closed. In more detail, the refrigerant is stagnant at the indoor heat exchanger 31b and the second pipe 22b, and a part of the first pipe 21b between the expansion valve 33b and the indoor heat exchanger 31b.
According to this, the user controls the multi-type air conditioner, for removing the stagnant refrigerant from the turned off indoor unit 30b.
Unexplained reference symbol Tin denotes a temperature of the refrigerant introduced into the indoor heat exchanger 31b of the turned off indoor unit 30b, and Tout denotes a temperature of the refrigerant discharged from the indoor heat exchanger 31b of the turned off indoor unit 30b.
Referring to
At first, when some indoor units 30a, and 30c start heating, a saturation temperature is define by using a heating cycle of the refrigerant, and the Mollier chart (S11).
Referring to
The heating cycle ‘C’ on the Mollier chart represents state changes of the refrigerant circulating the multi-type air conditioner. The state changes of the refrigerant moving according to the heating cycle ‘C’ will be described.
At first, in an a-b section (a compression section) of the heating cycle ‘C’, the refrigerant is compressed to a high temperature Td and high pressure Pd by the compressor 11. The Td and Pd denote a temperature and a pressure of the refrigerant discharged from the compressor 11.
That is, as the refrigerant passes the compressor 11, a temperature, and a pressure of the refrigerant rise from Ts to Td, and from Ps to Pd, respectively. In this instance, the enthalpy ‘h’ of the refrigerant also increases according to the increase of the temperature.
Then, the refrigerant is introduced into the indoor heat exchangers 31a, and 31c in a b-c section (a condensing section), and heat exchanged with room air, when the refrigerant loses heat, and has enthalpy reduced.
Then, the refrigerant passes through, and expands at the expansion valves 33a, and 33c in a c-d section (expansion section), to become low pressure Ps refrigerant, and is guided to the compressor 11 again through the outdoor heat exchanger 12 in a d-a section (evaporating section).
The saturation temperature is defined as a temperature T1 or T2 where the heat cycle ‘C’ of the refrigerant and the Mollier chart meet.
In more detail, the saturation temperature T1 or T2 is a refrigerant temperature the b-c section (condensing section) of the heating cycle ‘C’ and Mollier chart meet. That is, the saturation temperature T1 is a refrigerant temperature at a point where the condensing section of the heating cycle ‘C’ and the saturated vapor line L1 meet, and the saturation temperature T2 is a refrigerant temperature at a point where the condensing section of the heating cycle ‘C’ and the saturated liquid line L2 meet.
In the meantime, the b-c section of the heating cycle is horizontal P=Pd when the refrigerant is pure, like R22. The horizontal line connecting the saturated vapor line L1 and the saturated liquid line L2 is an isothermal line. That is, the saturation temperatures T1, and T2 are the same when the refrigerant is pure.
Therefore, the saturation temperature T1 and T2 can be obtained by using the Mollier chart and the heating cycle once the pressure Pd of the refrigerant discharged from the compressor 11 is measured.
However, though not shown, in a case of mixed refrigerant, such as R407C, the b-c section of the heating cycle is not horizontal, which means that T1 and T2 are not equal. Therefore, when mixed refrigerant is used, it is preferable that the saturation temperature is defined as an average or weighted average of the T1 and T2.
In this instance, the average is an arithmetic average [(T1+T2)/2] of the T1 and T2, and the weighted average is a value having a weighted value ‘a’ added to the average temperature [{(T1+T2)/2}+a]. Of course, it is apparent that the saturation temperature is defined As either T1 or T2 even in a case the mixed refrigerant is used.
After the saturation temperature is defined, a temperature of the refrigerant stagnant at the turned off indoor unit 30b is measured (S12). The refrigerant temperature is a temperature of the refrigerant in Tin/out Tout of the indoor heat exchanger 31b (see
Of course, the refrigerant temperature Tin or Tout can be obtained by measuring a surface temperature of the second branch pipe 22b and a surface temperature of the first branch pipe 21b that connects the expansion valve 33b and the indoor heat exchanger 31b, approximately.
Then, it is determined if a temperature difference between the saturation temperature and the temperature of the refrigerant stagnant at the turned off indoor unit is in a temperature range preset at the control part (S13).
If the temperature difference is in the temperature range preset at the control part, the expansion valve 33b of the turned off indoor unit 30b is opened, to remove the stagnant refrigerant from the turned off indoor unit 30b (S14).
In this instance, it is preferable that the extent ‘A’ of opening of the expansion valve is 1%<A<20%. The extent of opening is determined taking a number of the turned off indoor units, or the temperature difference into account, particularly, to minimize noise caused by opening of the expansion valve 33b.
That is, even though a noise level of a general residential area is required to be below 65 dB in the morning, 70 dB during the day, and 55 dB during the night, it is verified from experiment that a noise level caused by opened expansion valve can be lower than above noise level, if the extent of opening is 1%<A<20%.
In the meantime, a temperature range set at the control part may be fixed, or varied with the following parameters.
At first, the temperature range may be varied with a room temperature. Or, the temperature range may be varied with an outdoor temperature. The room temperature and the outdoor temperature fix a flow rate of the refrigerant to the indoor unit for heating.
Thus, because an amount, and a time period of the refrigerant stagnant at the turned off indoor unit 30b can vary with the room temperature and the outdoor temperature, it is preferable that the room temperature and the outdoor temperature are taken into account in fixing the temperature range.
Of course, the temperature range may vary both with the room temperature and the outdoor temperature.
If the temperature difference is not within the temperature range preset at the control part, the expansion valve of the turned off indoor unit is closed (S15). That is, since the temperature difference being out of the preset temperature range implies that no refrigerant is stagnant at the turned off indoor unit 30b, the expansion valve 33b is closed, to prevent occurrence of the noise in advance.
In the meantime, it is preferable that above steps are repeated during some of the indoor units perform heating. Particularly, it is preferable that after the step 14 or 15 is performed, all the steps from S11 are performed in succession.
Such a feedback control enables realtime monitoring of a state of the turned off indoor unit 30b, and opening/closing of the expansion valve at a proper time, to minimize noise from the multi-type air conditioner caused by unnecessary opening of the expansion valve.
Referring to
In this instance, if the stagnant refrigerant is removed from the turned off indoor unit 30b by opening the expansion valve 33b to the extent of opening in accordance with the first preferred embodiment of the present invention, the temperatures Tin/Tout of the refrigerant in/out of the indoor heat exchanger 31b rise. This implies that, as the expansion valve 33b is opened, low temperature refrigerant is discharged, and new high temperature refrigerant is supplied to the indoor heat exchanger 30b.
Referring to
At first, when some of the indoor units 30a, and 30c start heating operation, a room temperature is measured (S21). After measuring a temperature of the refrigerant stagnant at the turned off indoor unit 30b (S22), it is determined if a temperature difference of the refrigerant temperature and the room temperature is within a temperature range preset at the control part (S23).
If the temperature difference is within the temperature range preset at the control part, the expansion valve of the turned off indoor unit is opened (S24), and if the temperature difference is not within the temperature range preset at the control part, the expansion valve of the turned off indoor unit is closed (S25).
Thus, the second embodiment of the present invention is different from the first embodiment of the present invention, in that the second embodiment of the present invention determines opening of the expansion valve, not depending on the saturation temperature, but the room temperature. Particularly, the second embodiment is mostly applicable to a case the indoor units 30a, and 30c that heat the rooms are operated at a low temperature.
Referring to
At first, when some 30a, and 30c of the indoor units start heating operation, the expansion valve of the turned off indoor unit is opened at a first extent ‘B’ of opening (S31). It is preferable that the expansion valve 33b is opened after the multi-type air conditioner performs the heating operation for a certain time period.
It is preferable that the first extent ‘B’ of opening of the expansion valve is 1%<B<10%. The range of the first extent ‘B’ of opening is determined taking a time period required for removing the refrigerant, and a level of noise occurred into account. That is, if the first extent of opening ‘B’ is below 1%, to much time is required for removing the refrigerant, and if the first extent of opening ‘B’ is over 10%, too loud noise occurs in the heating operation.
Then, a saturation temperature of the refrigerant is defined by using the heating cycle of the refrigerant, and Mollier chart (S32). Since the saturation temperature is defined in a fashion the same with the first embodiment, no further description will be given.
In the meantime, after the saturation temperature is determined, a refrigerant temperature stagnant at the turned off indoor unit 30b is measured (S33). Then, it is determined if a temperature difference of the saturation temperature and the refrigerant temperature stagnant at the turned off indoor unit is within a temperature range preset at the control part (S34).
The refrigerant temperature is a temperature Tin or Tout of the refrigerant in/out of the indoor unit 31b (see
Of course, the refrigerant temperatures Tin and Tout can be obtained by measuring a surface temperature of the second branch pipe 22b and a surface temperature of the first branch pipe 21b connecting the expansion valve 33b and the indoor heat exchanger 31b, approximately.
If the temperature difference is within a temperature range preset at the control part, the expansion valve 33b of the turned off indoor unit is opened at a second extent of opening ‘C‘greater than the first extent of opening ‘B’ , and to remove the stagnant refrigerant from the turned off indoor unit (S35).
In this instance, it is preferable that the second extent of opening ‘C’ of the expansion valve 33b is 4%<C<20%. The second extent ‘C’ of opening is determined taking a number of the turned off indoor units, and/or the temperature difference into account, particularly, to minimize noise caused by opening of the expansion valve 33b.
In the meantime, the temperature range preset at the control part may be fixed, or varied with the following parameters.
At first, the temperature range may be varied with a room temperature. Or, the temperature range may be varied with an outdoor temperature. The room temperature and the outdoor temperature fix a flow rate of the refrigerant to the indoor unit for heating.
Thus, because an amount, and a time period of the refrigerant stagnant at the turned off indoor unit 30b can vary with the room temperature and the outdoor temperature, it is preferable that the room temperature and the outdoor temperature are taken into account in fixing the temperature range.
Of course, it is apparent that the temperature range may vary both with the room temperature and the outdoor temperature.
If the temperature difference is not within the temperature range preset at the control part, the expansion valve of the turned off indoor unit is opened at the first extent “B” of opening (S36).
In the meantime, it is preferable that a feedback control is performed during some of the indoor units perform heating, in which, after the S35 step or the S36 step is performed, steps starting from the S32 step are performed in succession again.
Referring to
In this instance, if the stagnant refrigerant is removed from the turned off indoor unit 30b by opening the expansion valve 33b to the second extent ‘C’ of opening, the temperatures Tin/Tout of the refrigerant in/out of the indoor heat exchanger 31b rise. This implies that, as the expansion valve 33b is opened to the second extent ‘C’ of opening, low temperature refrigerant is discharged, and new high temperature refrigerant is supplied to the indoor heat exchanger 30b.
However, since the expansion valve 33b is in an opened state from the starting at the first extent ‘B’ of opening in the third embodiment of the present invention, the refrigerant is not liable to be stagnant at the turned off indoor unit 30b, and the refrigerant temperature also drops moderately compared to the first, or second embodiment.
Accordingly, the third embodiment of the present invention can reduce noise as frequency of opening of the expansion valve 33b is reduced for the same time period.
Referring to
When some indoor units 30a, and 03c start heating operation, the expansion valve of the turned off indoor unit is opened at a first extent ‘B’ of opening (S41). It is preferable that the first extent ‘B’ of opening of the expansion valve is 1%<B<10%.
Then, a room temperature is measured (S42). Then, a temperature of the refrigerant stagnant at the turned off indoor unit 30b is measured (S43), and it is determined if a temperature difference of the refrigerant temperature and the room temperature is within a temperature range preset at the control part (S44).
If the temperature difference is within the temperature range preset at the control part, the expansion valve 33b of the turned off indoor unit is opened to a second extent ‘C’ of opening greater than the first extent of opening ‘B’, to remove the stagnant refrigerant from the turned off indoor unit (S45).
If the temperature difference is not within the preset temperature range, the expansion valve 33b of the turned off indoor unit is opened at the first extent ‘B’ of opening (S46).
Thus, the fourth embodiment of the present invention is different from the third embodiment in that the fourth embodiment of the present invention determines opening of the expansion valve 33b, not depending on the saturation temperature, but depending on the room temperature. Particularly, the fourth embodiment is mostly used when the indoor units 30a, and 30c that heat the rooms are operated at a low temperature.
As has been described, the method for controlling a multi-type air conditioner of the present invention has the following advantages.
First, by opening the expansion valve within an appropriate range, an amount of refrigerant stagnant at the turned off indoor unit is minimized, and noise caused by opening of the expansion valve is reduced.
Second, the realtime measurement of the saturation temperature of the refrigerant and the temperature of the refrigerant stagnant at the turned off indoor unit, and opening of the expansion valve according to the measurement permits an operation for removing the stagnant refrigerant from the indoor unit at an appropriate time.
Third, the minimizing of an amount of refrigerant stagnant at the turned off indoor unit by opening the expansion valve at the first extent of opening permits to increase an opening period of the expansion valve, to reduce noise caused by the opening of the expansion valve.
Fourth, the minimizing of refrigerant stagnant at the turned off indoor unit permits to increase an amount of refrigerant circulating through the heating cycle. According to this, the unnecessary temperature rise, and drop of a discharge pressure of the refrigerant discharged from the compressor caused by reduction of circulating refrigerant amount can be reduced.
It will be apparent to those skilled in the art that various modifications and variations can be made in the present invention without departing from the spirit or scope of the invention. Thus, it is intended that the present invention cover the modifications and variations of this invention provided they come within the scope of the appended claims and their equivalents.
| Number | Date | Country | Kind |
|---|---|---|---|
| P2004-003881 | Jan 2004 | KR | national |
