Patent Application
20100043467
The present invention relates to a refrigeration system including a refrigerant circuit having a plurality of heat exchangers, particularly to measures to cope with an imbalance in refrigerant flow between the heat exchangers.
There are known individually controllable refrigeration systems capable of meeting both a heating demand and a cooling demand in rooms at the same time. Such a refrigeration system includes a plurality of heat-using units placed in different rooms, respectively, so that some units perform cooling, and the other units perform heating.
Patent Document 1 discloses a refrigeration system of this kind. As shown in
This refrigeration system (100) can perform a refrigeration cycle in which, for example, the heat-source heat exchanger (103) and the first heat-using heat exchanger (104) function as condensers, and the second heat-using heat exchanger (105) functions as an evaporator. In operation shown in
In this manner, the refrigeration system (100) performs the refrigeration cycle by using the heat-using heat exchangers (104, 105) individually as the evaporator or the condenser, so as to allow independently switchable heating/cooling operation that satisfies both of the cooling and heating demands in the rooms at the same time.
In the above-described refrigeration system (100), however, during operation (concurrent operation) of performing a refrigeration cycle in which the heat-source heat exchanger (103) functions as a condenser, and at least one heat-using heat exchanger (104) functions as a condenser, heating capability of the heat-using heat exchanger (104) may deteriorate due to an imbalance in refrigerant flow. This phenomenon will be described below with reference to
In operation shown in
For the above-described reason, this refrigeration system may experience imbalance in refrigerant flow between the heat-source heat exchanger (103) and the heat-using heat exchangers (104, 105). As a result, in the refrigeration system of this kind, the amount of the refrigerant flowing into the heat exchanger may become insufficient due to the imbalance in refrigerant flow, and operation cannot be performed with reliability.
In view of the foregoing, the present invention was developed. The present invention is directed to a refrigeration system capable of performing a refrigeration cycle in which a heat-source heat exchanger functions as a condenser, and at least one of the other heat exchangers functions as a condenser, and the invention aims to prevent the imbalance in refrigerant flow between the heat exchangers.
A first aspect of the invention is directed to a refrigeration system including: a refrigerant circuit (10) including a compressor (21), a heat-source heat exchanger (22) connected to a discharge side of the compressor (21) at one end thereof, a liquid pipe (15) connected to the other end of the heat-source heat exchanger (22) through a heat-source expansion valve (23), a plurality of heat exchangers (31, 41, 51, 92) connected in parallel to the liquid pipe (15) at one ends thereof, a plurality of expansion valves (32, 42, 52, 93), each of which is provided on one end of the corresponding heat exchanger (31, 41, 51, 92) to adjust an amount of a refrigerant flowing to the corresponding heat exchanger (31, 41, 51, 92), and a switching mechanism (24, 25, SV) which switches a flow path of the refrigerant so that the other ends of the heat exchangers (31, 41, 51, 92) are connected to one of a suction side and a discharge side of the compressor (21). The refrigeration system includes a high-pressure-side pressure difference detection means (Ps1, Ps3, Ts7) which detects an index of pressure difference between a high pressure refrigerant on the discharge side of the compressor (21) and a refrigerant in the liquid pipe (15) in concurrent operation of performing a refrigeration cycle in which the heat-source heat exchanger (22) functions as a condenser, and simultaneously, at least one of the plurality of heat exchangers (31, 41, 51, 92) functions as a condenser, and at least one of the plurality of heat exchangers (31, 41, 51, 92) functions as an evaporator, and an expansion valve control means (17) which adjusts the degree of opening of the heat-source expansion valve (23) in the concurrent operation so that a value detected by the high-pressure-side pressure difference detection means (Ps1, Ps3, Ts7) becomes larger than a predetermined value.
The refrigeration system according to the first aspect of the invention allows concurrent operation of performing a refrigeration cycle in which the heat-source heat exchanger (22) functions as a condenser, at least one of the other heat exchangers (31, 41, 51, 92) functions as a condenser, and at least one of the other heat exchangers (31, 41, 51, 92) functions as an evaporator. In this concurrent operation, the other end of the first heat exchanger serving as a condenser is connected to the discharge side of the compressor (21), and the other end of the second heat exchanger serving as an evaporator is connected to the suction side of the compressor (21) by switching the setting of the switching mechanism (24, 25, SV). In this state, the refrigerant discharged from the compressor (21) is divided to flow into the heat-source heat exchanger (22) and the first heat exchanger. The refrigerant condensed in the heat-source heat exchanger (22) passes through the heat-source expansion valve (23), and flows into the liquid pipe (15). On the other hand, the refrigerant condensed in the first heat exchanger passes through the corresponding first expansion valve, and flows into the liquid pipe (15). The refrigerants are joined into one in the liquid pipe (15) and reduced in pressure by the second expansion valve corresponding to the second heat exchanger, and evaporates in the second heat exchanger. The refrigerant evaporated in the second heat exchanger is then sucked into the compressor (21) for recompression.
In this concurrent operation, the degree of opening of the first expansion valve is adjusted to control the amount of heat dissipation by the refrigerant in the first heat exchanger. When the degree of opening of the first expansion valve is increased too much for increasing the amount of heat dissipation, pressure difference between the high pressure refrigerant on the discharge side of the compressor (21) and the refrigerant in the liquid pipe (15) is reduced. Therefore, the refrigerant primarily flows into the heat-source heat exchanger (22), and the amount of the refrigerant sent to the first heat exchanger may become insufficient.
In view of the foregoing, according to the first aspect of the invention, the high-pressure-side pressure difference detection means (Ps1, Ps3, Ts7) obtains an index of pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe (15) in the concurrent operation. Then, the expansion valve control means (17) adjusts the degree of opening of the heat-source expansion valve (23) so that the index of pressure difference becomes larger than a predetermined value, thereby maintaining the pressure difference at a certain value or higher. Specifically, when the pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe (15) is reduced in the above-described manner, and for example, the amount of the refrigerant in the first heat exchanger becomes insufficient, the expansion valve control means (17) reduces the degree of opening of the heat-source expansion valve (23). This reduces the pressure of the refrigerant downstream of the heat-source expansion valve (23), i.e., the refrigerant in the liquid pipe (15), and therefore increases the pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe (15). The increase in pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe ensures the pressure difference which allows the refrigerant to flow sufficiently into the first heat exchanger. As a result, a larger amount of the refrigerant flows into the first heat exchanger. Thus, the present invention can prevent the lack of the refrigerant flowing into the heat exchanger serving as a condenser due to the imbalance in refrigerant flow.
In a second aspect of the invention, the refrigerant circuit (10) in the refrigeration system according to the first aspect of the invention includes three or more heat exchangers (31, 41, 51, 92) connected in parallel to the liquid pipe (15), and a low-pressure-side pressure difference detection means (Ps2, Ps3, Ts1, Ts3, Ts5) which detects an index of pressure difference between the refrigerant in the liquid pipe (15) and a low pressure refrigerant on the suction side of the compressor (21), and the expansion valve control means (17) adjusts the degree of opening of the heat-source expansion valve (23) so that a value detected by the high-pressure-side pressure difference detection means (Ps1, Ps3, Ts7) becomes larger than a predetermined value, and a value detected by the low-pressure-side pressure difference detection means (Ps2, Ps3, Ts1, Ts3, Ts5) becomes larger than a predetermined value, in the concurrent operation of performing a refrigeration cycle in which the heat-source heat exchanger (22) functions as a condenser, and simultaneously, at least two of the plurality of heat exchangers (31, 41, 51, 92) function as evaporators, and at least one of the plurality of heat exchangers (31, 41, 51, 92) functions as a condenser.
The refrigerant circuit (10) according to the second aspect of the invention includes three or more heat exchangers (31, 41, 51, 92), in addition to the heat-source heat exchanger (22). Therefore, the refrigeration system allows concurrent operation of performing a refrigeration cycle in which the heat-source heat exchanger (22) functions as a condenser, at least two heat exchangers function as evaporators, and at least one heat exchanger functions as a condenser. In this concurrent operation, the other end of the first heat exchanger serving as a condenser is connected to the discharge side of the compressor (21), and the other ends of the second and third heat exchangers serving as evaporators are connected to the suction side of the compressor (21) by switching the setting of the switching mechanism (24, 25, SV). In this state, the refrigerant discharged from the compressor (21) is divided to flow into the heat-source heat exchanger (22) and the first heat exchanger. The refrigerant condensed in the heat-source heat exchanger (22) passes through the heat-source expansion valve (23), and flows into the liquid pipe (15). On the other hand, the refrigerant condensed in the first heat exchanger passes through the corresponding first expansion valve, and flows into the liquid pipe (15). The refrigerants are joined into one in the liquid pipe (15) and divided to flow into the second and third heat exchangers. That is, one divided refrigerant flow is reduced in pressure by the second expansion valve corresponding to the second heat exchanger, and evaporates in the second heat exchanger. The other divided refrigerant flow is reduced in pressure by the third expansion valve corresponding to the third heat exchanger, and evaporates in the third heat exchanger. The refrigerants evaporated in the second and third heat exchangers, respectively, are joined into one, and sucked into the compressor (21) for recompression.
In this concurrent operation, like in the first aspect of the invention, the high-pressure-side pressure difference detection means (Ps1, Ps3, Ts7) obtains pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe (15), and the degree of opening of the heat-source expansion valve (23) is adjusted so that the pressure difference becomes larger than a predetermined value. Specifically, the degree of opening of the heat-source expansion valve (23) is reduced to maintain a sufficient amount of the refrigerant in the heat exchanger serving as a condenser. When the degree of opening of the heat-source expansion valve (23) is reduced, and the pressure of the refrigerant in the liquid pipe (15) becomes too low, the imbalance in refrigerant flow may occur between the plurality of heat exchangers serving as evaporators.
Specifically, in the above-described concurrent operation, the second and third heat exchangers function as evaporators. Suppose that a pipe connecting the compressor (21) and the third heat exchanger is longer than a pipe connecting the compressor (21) and the second heat exchanger in the refrigeration system, and that the pipe connected to the third heat exchanger experiences higher pressure loss. Under these conditions, when the degree of opening of the heat-source expansion valve (23) is reduced, and the pressure of the refrigerant in the liquid pipe (15) is reduced too much, the refrigerant in the liquid pipe (15) may primarily flow into the second heat exchanger, and therefore the amount of the refrigerant sent to the third heat exchanger may be decreased. As a result, even in the operation condition in which the amount of heat absorption in the third heat exchanger should be maintained to a sufficient degree, the amount of the refrigerant in the third heat exchanger becomes insufficient. Thus, a problem of decrease in reliability of the refrigeration system arises.
To cope with this problem, in the second aspect of the invention, the low-pressure-side pressure difference detection means (Ps2, Ps3, Ts1, Ts3, Ts5) obtains the index of pressure difference between the refrigerant in the liquid pipe (15) and the low pressure refrigerant. Then, the expansion valve control means (17) adjusts the degree of opening of the heat-source expansion valve (23) so that the pressure difference (the index of pressure difference) becomes larger than a predetermined value, and that the above-described pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe also becomes larger than the predetermined value. Specifically, the expansion valve control means (17) adjusts the degree of opening of the heat-source expansion valve (23) so that the pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe is maintained at a certain level, and simultaneously, the pressure difference between the refrigerant in the liquid pipe and the low pressure refrigerant is maintained at a sufficient level. This prevents the imbalance in refrigerant flow between the heat-source heat exchanger (22) and the heat exchanger serving as a condenser, like in the first aspect of the invention. In parallel with this, according to the second aspect of the invention, the pressure difference between the refrigerant in the liquid pipe and the low pressure refrigerant is also maintained at a sufficient level. Therefore, a sufficient amount of the refrigerant can be sent to, for example, the third heat exchanger which experiences high pressure loss. Thus, the present invention can prevent the imbalance in refrigerant flow between the plurality of heat exchangers serving as evaporators.
In a third aspect of the invention, the high-pressure-side pressure difference detection means in the refrigeration system according to the first or second aspect of the invention includes a high-pressure-side pressure sensor (Ps1) provided on the discharge side of the compressor (21), and an on-liquid-pipe pressure sensor (Ps3) provided on the liquid pipe (15), and the high-pressure-side pressure difference detection means is configured to detect difference between pressure detected by the high-pressure-side pressure sensor (Ps1) and pressure detected by the on-liquid-pipe pressure sensor (Ps3) as the index of pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe (15).
In the third aspect of the invention, the high-pressure-side pressure sensor (Ps1) and the on-liquid-pipe pressure sensor (Ps3) are used to obtain the pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe (15) in the concurrent operation according to the first or second aspect of the invention. Specifically, the high-pressure-side pressure difference detection means (Ps1, Ps3) directly detects the pressure of the high pressure refrigerant and the pressure of the refrigerant in the liquid pipe (15) to obtain the pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe.
In a fourth aspect of the invention, the high-pressure-side pressure difference detection means in the refrigeration system according to the first or second aspect of the invention includes a condensation temperature detection means (Ps1) which detects condensation temperature of the refrigerant in the heat-source heat exchanger (22) in the concurrent operation, and an on-liquid-pipe temperature sensor (Ts7) provided on the liquid pipe (15), and the high-pressure-side pressure difference detection means is configured to detect difference between temperature detected by the condensation temperature detection means (Ps1) and temperature detected by the on-liquid-pipe temperature sensor (Ts7) as the index of pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe (15).
In the fourth aspect of the invention, the condensation temperature of the refrigerant in the heat-source heat exchanger (22) and the temperature of the refrigerant in the liquid pipe (15) are used to obtain the pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe (15) in the concurrent operation according to the first or second aspect of the invention. Specifically, the condensation temperature detection means (Ps1) detects the condensation temperature of the refrigerant in the heat-source heat exchanger (22), and the on-liquid-pipe temperature sensor (Ts7) detects the temperature of the refrigerant that passed through the heat-source expansion valve (23). Since the condensation temperature varies depending on change in pressure of the high pressure refrigerant, it will be an index of the pressure of the high pressure refrigerant. Further, since the temperature of the refrigerant in the liquid pipe (15) also varies depending on change in pressure of the refrigerant in the liquid pipe (15), it will be an index of the pressure of the refrigerant in the liquid pipe (15). Thus, the high-pressure-side pressure difference detection means (Ps1, Ts7) indirectly grasp the pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe from the difference between the detected temperatures.
In a fifth aspect of the invention, the low-pressure-side pressure difference detection means in the refrigeration system according to the second aspect of the invention includes an on-liquid-pipe pressure sensor (Ps3) provided on the liquid pipe (15), and a low-pressure-side pressure sensor (Ps2) provided on the suction side of the compressor (21), and the low-pressure-side pressure difference detection means is configured to detect difference between pressure detected by the on-liquid-pipe pressure sensor (Ps3) and pressure detected by the low-pressure-side pressure sensor (Ps2) as the index of pressure difference between the refrigerant in the liquid pipe (15) and the low pressure refrigerant.
In the fifth aspect of the invention, the on-liquid-pipe pressure sensor (Ps3) and the low-pressure-side pressure sensor (Ps2) are used to obtain the pressure difference between the refrigerant in the liquid pipe (15) and the low pressure refrigerant in the concurrent operation according to the second aspect of the invention. Specifically, the low-pressure-side pressure difference detection means (Ps3, Ps2) directly detect the pressure of the refrigerant in the liquid pipe (15) and the pressure of the low pressure refrigerant, respectively, to obtain the pressure difference between the refrigerant in the liquid pipe and the low pressure refrigerant.
In a sixth aspect of the invention, the low-pressure-side pressure difference detection means in the refrigeration system according to the second aspect of the invention includes an on-liquid-pipe temperature sensor (Ts7) provided on the liquid pipe (15), and an evaporation temperature detection means (Ts1, Ts3, Ts5) which detects evaporation temperature of the refrigerant in the heat exchanger (31, 41, 51) serving as an evaporator in the concurrent operation, and the low-pressure-side pressure difference detection means is configured to detect difference between temperature detected by the on-liquid-pipe temperature sensor (Ts7) and temperature detected by the evaporation temperature detection means (Ts1, Ts3, Ts5) as the index of pressure difference between the low pressure refrigerant and the refrigerant in the liquid pipe (15).
In the sixth aspect of the invention, the temperature of the refrigerant in the liquid pipe (15) and the evaporation temperature of the refrigerant are used to obtain the pressure difference between the refrigerant in the liquid pipe (15) and the low pressure refrigerant in the concurrent operation according to the second aspect of the invention. Specifically, the on-liquid-pipe temperature sensor (Ts7) detects the temperature of the refrigerant that passed through the heat-source expansion valve (23), and the evaporation temperature detection means (Ts1, Ts3, Ts5) detects the evaporation temperature in the refrigerant in the heat exchanger (31, 41, 51) serving as an evaporator. Since the temperature of the refrigerant in the liquid pipe (15) varies depending on change in pressure of the refrigerant in the liquid pipe (15), it will be an index of the pressure of the refrigerant in the liquid pipe (15). Further, since the evaporation temperature varies depending on change in pressure of the low pressure refrigerant, it will be an index of the pressure of the low pressure refrigerant. Thus, the low-pressure-side pressure difference detection means (Ts7, Ts1, Ts3, Ts5) indirectly grasp the pressure difference between the refrigerant in the liquid pipe and the low pressure refrigerant from the difference between their detected temperatures.
In a seventh aspect of the invention, the liquid pipe (15) in the refrigeration system according to any one of the first to sixth aspects of the invention is provided with a cooling means (28) which cools the refrigerant that passed through the heat-source expansion valve (23) in the concurrent operation.
In the seventh aspect of the invention, the refrigerant reduced in pressure by the heat-source expansion valve (23) is cooled by the cooling means (28) in the concurrent operation. Specifically, in the concurrent operation, when the refrigerant is reduced in pressure by the heat-source expansion valve (23), the refrigerant becomes a vapor-liquid two phase refrigerant. Then, the cooling means (28) subcools the vapor-liquid two phase refrigerant to convert it into a liquid refrigerant. Thus, the liquid refrigerant can be sent to the heat exchanger (31, 41, 51) serving as an evaporator, and noise generated upon passage of the refrigerant through the expansion valve (32, 42, 52) corresponding to the heat exchanger (31, 41, 51) can be reduced.
In an eighth aspect of the invention, the refrigerant circuit (10) in the refrigeration system according to the seventh aspect of the invention includes an injection pipe (19), having a pressure reducing valve (19a), which is branched from the liquid pipe (15) and connected to the suction side of the compressor (21), and temperature difference detection means (Ts7, Ts8) which detect temperature difference between the refrigerant flowing into the cooling means (28) and the refrigerant flowing out of the cooling means (28), the cooling means is constituted of a subcooling heat exchanger (28) which allows heat exchange between the refrigerant in the liquid pipe (15) and the refrigerant in the injection pipe (19) that passed through the pressure reducing valve (19a), and the refrigeration system includes an injection amount control means (18) which adjusts the degree of opening of the pressure reducing valve (19a) in the concurrent operation so that the refrigerant temperature difference detected by the temperature difference detection means (Ts7, Ts8) becomes larger than a predetermined value.
In the eighth aspect of the invention, the subcooling heat exchanger (28) is provided as the cooling means. In the subcooling heat exchanger (28) in the concurrent operation, heat exchange occurs between the refrigerant reduced in pressure by the heat-source expansion valve (23) to become a vapor-liquid two phase refrigerant and passed through the liquid pipe (15), and the refrigerant reduced in pressure by the pressure reducing valve (19a) and flows into the injection pipe (19). As a result, the refrigerant in the injection pipe (19) absorbs heat from the refrigerant in the liquid pipe (15) and evaporates, and the refrigerant in the liquid pipe (15) is subcooled. Further, in the present invention, the temperature difference detection means (Ts7, Ts8) detect the temperature difference between the refrigerant flowing into the subcooling heat exchanger (28) and the refrigerant flowing out of the subcooling heat exchanger (28) in the concurrent operation. Then, the injection amount control means (18) adjusts the degree of opening of the pressure reducing valve (19a) so that the temperature difference becomes larger than the predetermined value. As a result, the subcooling heat exchanger (28) reliably subcools the refrigerant in the liquid pipe (15) and converts it into a liquid refrigerant. Thus, the liquid refrigerant can reliably be sent to the heat exchanger (31, 41, 51) serving as an evaporator, and noise generated upon passage of the refrigerant through the expansion valve (32, 42, 52) corresponding to the heat exchanger (31, 41, 51) is reduced with reliability.
According to the present invention, the expansion valve control means (17) adjusts the degree of opening of the heat-source expansion valve (23) in the concurrent operation so that the pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe can be maintained at a sufficient level. Therefore, the present invention allows the prevention of the imbalance in refrigerant flow between the heat-source heat exchanger (22) and the other heat exchangers (31, 41, 51) serving as condensers. This makes it possible to supply a sufficient amount of the refrigerant to the heat exchangers (31, 41, 51). As a result, the amount of heat dissipation by the refrigerant in the heat exchangers (31, 41, 51) can be maintained at a sufficient level. Thus, the heat exchangers (31, 41, 51) can provide sufficient heating capability in heating the rooms.
In the second aspect of the invention, the expansion valve control means (17) adjusts the degree of opening of the heat-source expansion valve (23) in the concurrent operation so as to maintain the pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe, and maintain the pressure difference between the refrigerant in the liquid pipe and the low pressure refrigerant. Therefore, according the second aspect of the invention, the imbalance in refrigerant flow between the heat-source heat exchanger (22) and the other heat exchangers (31, 41, 51) serving as condensers can be prevented, and simultaneously, the imbalance in refrigerant flow between the other heat exchangers (31, 41, 51, 92) serving as evaporators can also be prevented. Thus, the amount of heat absorption by the refrigerant in the heat exchangers (31, 41, 51, 92) can be maintained at a sufficient level. Thus, the heat exchangers (31, 41, 51) can exhibit sufficient cooling capability in heating the rooms.
In the third aspect of the invention, the pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe is directly obtained from the difference between the pressures detected by the high-pressure-side pressure sensor (Ps1) and the on-liquid-pipe pressure sensor (Ps3). This allows reliable detection of the pressure difference and adequate control of the heat-source expansion valve (23).
In the fifth aspect of the invention, the pressure difference between the refrigerant in the liquid pipe and the low pressure refrigerant is directly obtained from the difference between the pressures detected by the on-liquid-pipe pressure sensor (Ps3) and the low-pressure-side pressure sensor (Ps2). This allows reliable detection of the pressure difference and adequate control of the heat-source expansion valve (23).
In the fourth and sixth aspects of the invention, the on-liquid-pipe temperature sensor (Ts7) is used in place of the on-liquid-pipe pressure sensor (Ps3). This relatively low-cost sensor allows estimation of the pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe, and the pressure difference between the refrigerant in the liquid pipe and the low pressure refrigerant.
In the seventh aspect of the invention, the cooling means (28) cools the refrigerant reduced in pressure by the heat-source expansion valve (23) in the concurrent operation. Therefore, the liquid refrigerant can be sent to the heat exchangers (31, 41, 51). This allows the reduction of noise generated upon passage of the refrigerant through the expansion valve (32, 42, 52) corresponding to the heat exchanger (31, 41, 51) in the concurrent operation.
Particularly in the eighth aspect of the invention, the degree of opening of the pressure reducing valve (19a) of the injection pipe (19) is adjusted so that the difference in temperature between the refrigerant flowing into the subcooling heat exchanger (28) and the refrigerant flowing out of the subcooling heat exchanger (28) will be a predetermined value. Thus, the refrigerant in the liquid pipe (15) can reliably be subcooled to become the liquid refrigerant. Thus, the noise generated upon passage of the refrigerant through the expansion valve (32, 42, 52) corresponding to the heat exchanger (31, 41, 51) in the concurrent operation can be reduced with more reliability.
Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.
A refrigeration system according to Embodiment 1 of the present invention constitutes an air conditioner (1) capable of individually heating or cooling a plurality of rooms. The air conditioner (1) is an independently switchable air conditioner capable of heating one room and cooling the other rooms simultaneously.
As shown in
The outdoor unit (20) constitutes a heat-source unit, and includes a compressor (21), an outdoor heat exchanger (22), an outdoor expansion valve (23), a first three-way valve (24), and a second three-way valve (25). The compressor (21) constitutes a variable-volume inverter compressor. The outdoor heat exchanger (22) is a cross-fin heat exchanger and constitutes a heat-source heat exchanger of the present invention. The outdoor expansion valve (23) is an electronic expansion valve and constitutes a heat-source expansion valve of the present invention.
The first three-way valve (24) and the second three-way valve (25) are constituted of four-way valves, respectively, in each of which one of four ports has been sealed. That is, each of the three-way valves (24, 25) has first to third ports. In the first three-way valve (24), the first port is connected to a discharge side of the compressor (21), the second port is connected to the outdoor heat exchanger (22), and the third port is connected to a suction side of the compressor (21). In the second three-way valve (25), the first port is connected to the discharge side of the compressor (21), the second port is connected to the BS units (60, 70, 80), and the third port is connected to the suction side of the compressor (21). Each f the three-way valves (24, 25) is switchable between a state in which the first port and the second port communicate with each other, and simultaneously, the third port is closed (a state indicated by a solid line in
The outdoor unit (20) is provided with a plurality of pressure sensors (Ps1, Ps2, Ps3) for detecting pressure of the refrigerant. Specifically, a high-pressure-side pressure sensor (Ps1) for detecting pressure of a high pressure refrigerant is provided on the discharge side of the compressor (21), and a low-pressure-side pressure sensor (Ps2) for detecting pressure of a low pressure refrigerant is provided on the suction side of the compressor (21). An on-liquid-pipe pressure sensor (Ps3) for detecting pressure of the refrigerant flowing in the liquid pipe (15) is provided on a liquid pipe (15) between the outdoor expansion valve (23) and the indoor units (30, 40, 50). The high-pressure-side pressure sensor (Ps1) and the on-liquid-pipe pressure sensor (Ps3) constitute a high-pressure-side pressure difference detection means of the present invention for detecting an index of pressure difference between the high pressure refrigerant on the discharge side of the compressor (21) and the refrigerant in the liquid pipe (15). Further, the on-liquid-pipe pressure sensor (Ps3) and the low-pressure-side pressure sensor (Ps2) constitute a low-pressure-side pressure difference detection means of the present invention for detecting an index of pressure difference between the refrigerant in the liquid pipe (15) and the low pressure refrigerant on the suction side of the compressor (21).
The air conditioner (1) includes first to third indoor units (30, 40, 50). The indoor units (30, 40, 50) include first to third indoor heat exchangers (31, 41, 51) and first to third indoor expansion valves (32, 42, 52), respectively. The indoor heat exchangers (31, 41, 51) are cross-fin heat exchangers and constitute heat-using heat exchangers. The indoor heat exchangers (31, 41, 51) constitute “a plurality of heat exchangers” as claimed, which are connected in parallel to an end of the liquid pipe (15) at one ends thereof. The indoor expansion valves (32, 42, 52) are, for example, electronic expansion valves. The indoor expansion valves (32, 42, 52) constitute “a plurality of expansion valves” as claimed, each of which is provided on one end of the corresponding indoor heat exchanger (31, 41, 51).
Each of the indoor units (30, 40, 50) includes a plurality of temperature sensors (Ts1, Ts2, Ts3, . . . ) for detecting the refrigerant's temperature. Specifically, in the first indoor unit (30), a first temperature sensor (Ts1) is arranged between an end of the first indoor heat exchanger (31) and the first indoor expansion valve (32), and a second temperature sensor (Ts2) is arranged at the other end of the first indoor heat exchanger (31). In the second indoor unit (40), a third temperature sensor (Ts3) is arranged between an end of the second indoor heat exchanger (41) and the second indoor expansion valve (42), and a fourth temperature sensor (Ts4) is arranged at the other end of the second indoor heat exchanger (41). Further, in the third indoor unit (50), a fifth temperature sensor (Ts5) is arranged between an end of the third indoor heat exchanger (51) and the third indoor expansion valve (52), and a sixth temperature sensor (Ts6) is arranged at the other end of the third indoor heat exchanger (51).
The air conditioner (1) includes first to third BS units (60, 70, 80) corresponding to the indoor units (30, 40, 50), respectively. Each of the BS units (60, 70, 80) includes a first branch pipe (61, 71, 81) and a second branch pipe (62, 72, 82) branched from the corresponding indoor unit (30, 40, 50). Each of the first branch pipes (61, 71, 81) and the second branch pipes (62, 72, 82) is provided with an open/close solenoid valve (SV-1, SV-2, SV-3, . . . ). The BS unit (60, 70, 80) constitutes a switching mechanism of the present invention which switches the flow path of the refrigerant by opening or closing the solenoid valve (SV1, SV-2, SV-3, . . . ) so that the other end of the corresponding indoor heat exchanger (31, 41, 51) is connected to the suction side or the discharge side of the compressor (21).
The air conditioner (1) has a controller (16) which controls the three-way valves (24, 25), the solenoid valves (SV-1, SV-2, SV-3, . . . ), the compressor (21), and the like. The controller (16) receives signals detected by the above-described sensors. Further, the controller (16) is provided with an expansion valve control means (17), which constitutes a feature of the present invention. The expansion valve control means (17) is configured to perform, in concurrent operation of the present invention described later, liquid pressure control operation by adjusting the degree of opening of the outdoor expansion valve (23) in response to pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe (15), and pressure difference between the refrigerant in the liquid pipe (15) and the low pressure refrigerant.
An operation mechanism of the air conditioner (1) of Embodiment 1 will be described. In the air conditioner (1), the operation can be performed in various modes depending on the setting of the three-way valves (24, 25) and the open/close state of the solenoid valves (SV-1, SV-2, SV-3, . . . ) of the BS units (60, 70, 80). Among them, representative operation modes will be described below.
In all heating operation, all the indoor units (30, 40, 50) perform heating of the corresponding rooms. As shown in
In this operation, a refrigeration cycle is performed in which the outdoor heat exchanger (22) functions as an evaporator, and the indoor heat exchangers (31, 41, 51) function as condensers. In this figure and the other figures illustrating the other operation mechanisms, heat exchangers serving as condensers are shown as dot-patterned heat exchangers, and heat exchangers serving as evaporators are shown as white heat exchangers. In this refrigeration cycle, the refrigerant discharged from the compressor (21) passes through the second three-way valve (25), and is divided to flow into the first branch pipes (61, 71, 81) of the BS units (60, 70, 80), respectively. After passing through the BS units (60, 70, 80), the refrigerant is sent to the corresponding indoor units (30, 40, 50).
For example, in the first indoor unit (30), when the refrigerant flows into the first indoor heat exchanger (31), it dissipates heat into indoor air in the first indoor heat exchanger (31) and condenses. As a result, the room corresponding to the first indoor unit (30) is heated. The refrigerant condensed in the first indoor heat exchanger (31) passes through the first indoor expansion valve (32). The degree of opening of the first indoor expansion valve (32) is adjusted in response to the degree of subcooling of the refrigerant obtained by the first temperature sensor (Ts1), the second temperature sensor (Ts2), and the like. Specifically, the degree of opening of the first indoor expansion valve (32) is increased so as to increase the flow rate of the refrigerant when a heating demand in the room is high, and the degree of subcooling of the refrigerant is high. On the other hand, the degree of opening of the first indoor expansion valve (32) is reduced so as to reduce the flow rate of the refrigerant when the heating demand in the room is low, and the degree of subcooling of the refrigerant is low. In the second indoor unit (40) and the third indoor unit (50), the refrigerant flows in the same manner as in the first indoor unit (30), and the corresponding rooms are heated.
The refrigerants discharged from the indoor units (30, 40, 50) are joined into one in the liquid pipe (15). The refrigerant is reduced in pressure as it passes through the outdoor expansion valve (23) to become a low pressure refrigerant, and flows into the outdoor heat exchanger (22). In the outdoor heat exchanger (22), the refrigerant absorbs heat from outdoor air and evaporates. The refrigerant evaporated in the outdoor heat exchanger (22) passes through the first three-way valve (24), and is sucked into the compressor (21) for recompression.
In all cooling operation, all the indoor units (30, 40, 50) perform cooling of the corresponding rooms. As shown in
In this operation, a refrigeration cycle is performed in which the outdoor heat exchanger (22) functions as a condenser, and the indoor heat exchangers (31, 41, 51) function as evaporators. Specifically, the refrigerant discharged from the compressor (21) passes through the first three-way valve (24), and flows into the outdoor heat exchanger (22). In the outdoor heat exchanger (22), the refrigerant dissipates heat into the outdoor air and condenses. The refrigerant condensed in the outdoor heat exchanger (22) passes through the fully opened outdoor expansion valve (23), flows through the liquid pipe (15), and is divided to flow into the indoor units (30, 40, 50).
For example, in the first indoor unit (30), the refrigerant is reduced in pressure as it passes through the first indoor expansion valve (32) to become a low pressure refrigerant, and flows into the first indoor heat exchanger (31). In the first indoor heat exchanger (31), the refrigerant absorbs heat from the indoor air and evaporates. As a result, the room corresponding to the first indoor unit (30) is cooled. The degree of opening of the first indoor expansion valve (32) is adjusted in response to the degree of superheating of the refrigerant obtained by the first temperature sensor (Ts1), the second temperature sensor (Ts2), and the like. Specifically, the degree of opening of the first indoor expansion valve (32) is increased so as to increase the flow rate of the refrigerant when a cooling demand in the room is high, and the degree of superheating of the refrigerant is high. On the other hand, the degree of opening of the first indoor expansion valve (32) is reduced so as to reduce the flow rate of the refrigerant when the cooling demand in the room is low, and the degree of superheating of the refrigerant is low. In the second indoor unit (40) and the third indoor unit (50), the refrigerant flows in the same maimer as in the first indoor unit (30), and the corresponding rooms are cooled. The refrigerants discharged from the indoor units (30, 40, 50) pass through the second branch pipes (62, 72, 82) of the BS units (60, 70, 80), respectively, and they are joined into one and sucked into the compressor (21) for recompression.
In simultaneous heating/cooling operation, some indoor units perform heating of the rooms, and the other indoor units perform cooling of the rooms. In the simultaneous heating/cooling operation, the outdoor heat exchanger (22) functions as an evaporator or a condenser depending on the operating condition. In the indoor units (30, 40, 50), the indoor heat exchanger in the room which demands the heating functions as a condenser, while the indoor heat exchanger in the room which demands the cooling functions as an evaporator. Hereinafter, examples of concurrent operation according to the present invention will be described, in which the outdoor heat exchanger (22) is used as a condenser, at least one of the indoor heat exchangers (31, 41, 51) is used as a condenser, and the remaining indoor heat exchangers are used as evaporators.
In first concurrent operation, the first indoor unit (30) and the second indoor unit (40) perform heating of the corresponding rooms, and the third indoor unit (50) performs cooling of the corresponding room. As shown in
In this operation, a refrigeration cycle is performed in which the outdoor heat exchanger (22), the first indoor heat exchanger (31), and the second indoor heat exchanger (41) function as condensers, and the third indoor heat exchanger (51) functions as an evaporator. Specifically, the refrigerant discharged from the compressor (21) is divided to flow into the first three-way valve (24) and the second three-way valve (25). The refrigerant passed through the first three-way valve (24) condenses in the outdoor heat exchanger (22), passes through the outdoor expansion valve (23) opened to a predetermined degree, and then flows into the liquid pipe (15).
On the other hand, the refrigerant passed through the second three-way valve (25) is divided to flow into the first BS unit (60) and the second BS unit (70). The refrigerant flowed out of the first BS unit (60) flows into the first indoor heat exchanger (31). In the first indoor heat exchanger (31), the refrigerant dissipates heat into the indoor air and condenses. As a result, the room corresponding to the first indoor unit (30) is heated. The degree of opening of the first indoor expansion valve (32) is adjusted in response to the heating demand in the room, in the same manner as in the all heating operation described above. The refrigerant used in the first indoor unit (30) to heat the room flows into the liquid pipe (15). Likewise, the refrigerant flowed out of the second BS unit (70) is used in the second indoor unit (40) to heat the room, and then flows into the liquid pipe (15).
The refrigerants are joined into one in the liquid pipe (15), and guided to the third indoor unit (50). The refrigerant is reduced in pressure as it passes through the third indoor expansion valve (52) to become a low pressure refrigerant, and then flows into the third indoor heat exchanger (51). In the third indoor heat exchanger (51), the refrigerant absorbs heat from the indoor air and evaporates. As a result, the room corresponding to the third indoor unit (50) is cooled. The refrigerant used in the third indoor unit (50) to cool the room passes through the third BS unit (80), and is sucked into the compressor (21) for recompression.
In second concurrent operation, the first indoor unit (30) performs heating of the corresponding room, and the second indoor unit (40) and the third indoor unit (50) perform cooling of the corresponding rooms. As shown in
In this operation, a refrigeration cycle is performed in which the outdoor heat exchanger (22) and the first indoor heat exchanger (31) function as condensers, and the second indoor heat exchanger (41) and the third indoor heat exchanger (51) function as evaporators. Specifically, the refrigerant discharged from the compressor (21) is divided to flow into the first three-way valve (24) and the second three-way valve (25). The refrigerant passed through the first three-way valve (24) condenses in the outdoor heat exchanger (22), passed through the outdoor expansion valve (23) opened to a predetermined degree, and then flows into the liquid pipe (15).
On the other hand, the refrigerant passed through the second three-way valve (25) is sent to the first indoor unit (30) through the first BS unit (60). In the first indoor unit (30), the refrigerant condenses in the first indoor heat exchanger (31) to heat the room. The refrigerant used in the first indoor unit (30) to heat the room flows into the liquid pipe (15).
The refrigerants are joined into one in the liquid pipe (15), and then divided to flow into the second indoor unit (40) and the third indoor unit (50). In the second indoor unit (40), the refrigerant reduced in pressure by the second indoor expansion valve (42) evaporates in the second indoor heat exchanger (41) to cool the room. Likewise, in the third indoor unit (50), the refrigerant reduced in pressure by the third indoor expansion valve (52) evaporates in the third indoor heat exchanger (51) to cool the room. The refrigerants used in the indoor units (40, 50) to cool the rooms pass through the second BS unit (70) and the third BS unit (80), respectively, and they are joined into one and sucked into the compressor (21) for recompression.
In the above-described concurrent operation using the outdoor heat exchanger (22) as a condenser, heating or cooling capability of the indoor units (30, 40, 50) may deteriorate due to an imbalance in refrigerant flow. This phenomenon will be described with reference to the first and second concurrent operations described above.
As shown in
In the concurrent operation shown in
The expansion valve control means (17) adjusts the degree of opening of the outdoor expansion valve (23) so that the pressure difference ΔP1 thus obtained becomes larger than a predetermined target value. The target value is variable depending on indoor temperature, outdoor temperature, operation states of the indoor units (30, 40, 50), operation frequency of the compressor (21), and the like. Further, the expansion valve control means (17) adjusts the degree of opening of the outdoor expansion valve (23) so that the pressure difference ΔP1 does not exceed a predetermined upper limit value. That is, the expansion valve control means (17) adjusts the degree of opening of the outdoor expansion valve (23) to keep the pressure difference ΔP1 within a predetermined target range.
When the pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe (15) is reduced for the above-described reason, and therefore pressure difference ΔP1 becomes equal to or smaller than a predetermined value, the expansion valve control means (17) reduces the degree of opening of the outdoor expansion valve (23). This reduces the pressure of the refrigerant in the liquid pipe (15), and the pressure difference ΔP1 becomes larger than the predetermined value. As a result, the pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe can be maintained at a certain level or higher. Thus, the refrigerant discharged from the compressor (21) sufficiently flows into the first indoor unit (30) and the second indoor unit (40), and the heating capability of the indoor units (30, 40) can reliably be maintained at a sufficient level.
The outdoor expansion valve (23) is adjusted so that the pressure difference ΔP1 does not exceed the upper limit value. Specifically, the degree of opening of the outdoor expansion valve (23) is adjusted so as to prevent excessive reduction of the pressure of the refrigerant. This avoids excessive decrease in pressure of the refrigerant flowing in the liquid pipe (15).
As shown in
In the concurrent operation shown in
The expansion valve control means (17) adjusts the degree of opening of the outdoor expansion valve (23) so that the pressure difference ΔP1 between the high pressure refrigerant and the refrigerant in the liquid pipe becomes larger than a predetermined target value, and that the pressure difference ΔP2 between the refrigerant in the liquid pipe and the low pressure refrigerant becomes larger than a predetermined target value. The target values are variable depending on indoor temperature, outdoor temperature, preset room temperature, operation states of the indoor units (30, 40, 50), operation frequency of the compressor (21), and the like.
When the pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe (15) is reduced, and the pressure difference ΔP1 between the high pressure refrigerant and the refrigerant in the liquid pipe becomes equal to or smaller than the predetermined value for the above-described reason, the expansion valve control means (17) reduces the degree of opening of the outdoor expansion valve (23). As a result, the pressure difference ΔP1 is maintained, and the imbalance in refrigerant flow between the outdoor heat exchanger (22) and the first indoor heat exchanger (31) is suppressed. This makes it possible to supply a sufficient amount of the refrigerant to the first indoor heat exchanger (31), and to solve the lack of heating capability of the first indoor unit (30).
When the pressure difference between the refrigerant in the liquid pipe (15) and the low pressure refrigerant is reduced, and the pressure difference ΔP2 between the refrigerant in the liquid pipe and the low pressure refrigerant becomes equal to or smaller than the predetermined value, the expansion valve control means (17) increases the degree of opening of the outdoor expansion valve (23). As a result, the pressure of the refrigerant in the liquid pipe (15) is increased, and the pressure difference ΔP2 is maintained. This suppresses the imbalance in refrigerant flow between the second indoor heat exchanger (41) and the third indoor heat exchanger (51), and maintains the cooling capability of the indoor units (40, 50) at a sufficient level.
In Embodiment 1, the expansion valve control means (17) adjusts, in the above-described first concurrent operation, the degree of opening of the outdoor expansion valve (23) to maintain the pressure difference ΔP1 between the high pressure refrigerant and the refrigerant in the liquid pipe. Therefore, according to Embodiment 1, the imbalance in refrigerant flow between the outdoor heat exchanger (22) and the indoor heat exchangers (31, 41) serving as condensers can be prevented, and a sufficient amount of the refrigerant can reliably be supplied to the indoor heat exchangers (31, 41). This allows prevention of the deterioration in heating capability of the indoor units (30, 40), and improvement in reliability of the air conditioner (1).
In the above-described second concurrent operation, in particular, the expansion valve control means (17) adjusts the degree of opening of the outdoor expansion valve (23) to maintain the pressure difference ΔP1 between the high pressure refrigerant and the refrigerant in the liquid pipe, and to maintain the pressure difference ΔP2 between the refrigerant in the liquid pipe and the low pressure refrigerant. Therefore, according to Embodiment 1, the imbalance in refrigerant flow between the outdoor heat exchanger (22) and the indoor heat exchanger (31) serving as a condenser can be prevented, and simultaneously, the imbalance in refrigerant flow between the indoor heat exchangers (41, 51) serving as evaporators can also be prevented. This allows prevention of the deterioration in heating and cooling capability of the indoor units (30, 40, 50), and improvement in reliability of the air conditioner (1).
A refrigeration system according to Embodiment 2 of the present invention is configured by adding a plurality of outdoor units (20, 90) to the air conditioner of Embodiment 1. Hereinafter, difference from Embodiment 1 will be described.
As shown in
The air conditioner (1) of Embodiment 2 is also provided with an expansion valve control means (17) which performs liquid pressure control operation in the above-described concurrent operation by adjusting the degree of opening of the outdoor expansion valves (23, 93). In the concurrent operation described in Embodiment 1, the degree of opening of the outdoor expansion valves (23, 93) corresponding to the outdoor heat exchangers (20, 90) serving as condensers is adjusted in response to pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe, and pressure difference between the refrigerant in the liquid pipe and the low pressure refrigerant.
Further, in the air conditioner of Embodiment 2, the liquid pressure control operation of the present invention can also be applied to the following concurrent operation.
In an example shown in
In the example shown in
In an example shown in
In the example shown in
Embodiments 1 and 2 described above may be modified in the following manner.
As a high-pressure-side pressure detection means which detects an index of pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe, for example, the high-pressure-side pressure sensor (Ps1) and an on-liquid-pipe temperature sensor (Ts8) may be used as shown in
In the concurrent operation, the refrigerant passed through the outdoor expansion valve (23) is guided to the liquid pipe (15). Since this refrigerant is reduced to a predetermined pressure by the outdoor expansion valve (23), it is in a vapor-liquid two phase. The on-liquid-pipe temperature sensor (Ts8) detects the temperature of the vapor-liquid two phase refrigerant in the liquid pipe (15).
The condensation temperature in the outdoor heat exchanger (22) varies depending on change in pressure of the high pressure refrigerant. Therefore, it will be an index of the pressure of the high pressure refrigerant. On the other hand, the temperature of the refrigerant in the liquid pipe (15) varies depending on change in pressure of the refrigerant in the liquid pipe (15). Therefore, it will be an index of the pressure of the refrigerant in the liquid pipe (15). Accordingly, pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe can be grasped by obtaining difference ΔT1 between the condensation temperature and the temperature of the refrigerant in the liquid pipe (15). In the concurrent operation, the expansion valve control means (17) adjusts the degree of opening of the outdoor expansion valve (23) so that the temperature difference ΔT1 becomes larger than a predetermined target value. This maintains the pressure difference between the high pressure refrigerant and the refrigerant in the liquid pipe, and prevents the above-described imbalance in refrigerant flow.
As a low-pressure-side pressure detection means which detects an index of pressure difference between the refrigerant in the liquid pipe and the low pressure refrigerant, the on-liquid-pipe temperature sensor (Ts8), and the first temperature sensor (Ts1), the third temperature sensor (Ts3), and the fifth temperature sensors (Ts5) provided on the indoor units (30, 40, 50) may be used. Specifically, in the above-described concurrent operation shown in
The evaporation temperature of the refrigerant in the indoor heat exchangers (41, 51) may vary depending on change in pressure of the low pressure refrigerant. Therefore, it will be an index of the pressure of the low pressure refrigerant. Accordingly, pressure difference between the refrigerant in the liquid pipe and the low pressure refrigerant can be grasped by obtaining difference ΔT2 between the temperature of the refrigerant in the liquid pipe (15) and the evaporation temperature. In the concurrent operation, the expansion valve control means (17) adjusts the degree of opening of the outdoor expansion valve (23) so that the temperature difference ΔT2 becomes larger than a predetermined target value. This maintains the pressure difference between the refrigerant in the liquid pipe and the low pressure refrigerant, and prevents the above-described imbalance in refrigerant flow.
(Modified Example Added with Subcooling Heat Exchanger)
As shown in
The liquid pipe (15) is further provided with a first on-liquid-pipe temperature sensor (Ts7) provided on the inlet side of the subcooling heat exchanger (28) in the concurrent operation, and a second on-liquid-pipe temperature sensor (Ts8) provided on the outlet side of the subcooling heat exchanger (28). The on-liquid-pipe temperature sensors (Ts7, Ts8) constitute a temperature difference detection means which detects temperature difference between the refrigerant flowing into the subcooling heat exchanger (28) and the refrigerant flowing out of the subcooling heat exchanger (28). In this example, a controller (16) includes an injection amount control means (18) which adjusts the degree of opening of the pressure reducing valve (19a) so that the difference between the temperatures detected by the on-liquid-pipe temperature sensors (Ts7, Ts8) becomes larger than a predetermined value in the concurrent operation.
In the modified example of the air conditioner (1), the degree of opening of the pressure reducing valve (19a) is adjusted in the above-described concurrent operation so that the refrigerant flowing from the liquid pipe (15) to the low pressure side does not become a vapor-liquid two phase refrigerant. Specifically, in the concurrent operation shown in
Specifically, referring to
The liquid refrigerant thus obtained is sent to the low pressure third indoor unit (50). In the third indoor unit (50), the liquid refrigerant passes through the third indoor expansion valve (52). Therefore, noise generation by the refrigerant passing through the expansion valve is reduced as compared with the noise generation by the vapor-liquid two phase refrigerant.
The above-described embodiments and modified examples may be configured in the following manner.
The number of indoor units and outdoor units described in the above embodiments is indicated merely as an example. Therefore, the air conditioner may include a larger number of indoor and outdoor units.
As described above, the present invention relates to a refrigeration system including a refrigerant circuit having a plurality of heat exchangers, and is particularly useful as measures to cope with an imbalance in refrigerant flow between the heat exchangers.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2006-326474 | Dec 2006 | JP | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2007/072918 | 11/28/2007 | WO | 00 | 5/22/2009 |
