KR102551112B1 - Receiver united type accumulator - Google Patents

Abstract

A receiver-integrated accumulator according to an embodiment of the present invention includes a casing in which an internal space having a constant cross-sectional area is formed; a barrier in contact with the inner surface of the casing and movable inside the casing; a receiver unit located on one side of the inside of the casing and having a receiver inlet passage and a receiver outlet passage connected thereto; and an accumulator part located on the other side of the casing partitioned from the receiver part by the barrier and communicating with the receiver part through the receiver outlet passage. As the barrier moves, volumes of the receiver unit and the accumulator unit may change.
According to this, the receiver-integrated accumulator can serve both the functions of the receiver and the accumulator. In addition, since each capacity of the receiver unit and the accumulator unit can be varied, the amount of refrigerant accommodated in each unit can be organically adjusted.

Description

Receiver Integrated Accumulator {RECEIVER UNITED TYPE ACCUMULATOR}

The present invention relates to an accumulator, and more particularly, to an accumulator integrated with a receiver.

In general, an air conditioner is a device that can cool or heat a room by using a refrigerant cycle of a refrigerant. When the refrigerant is sequentially compressed, condensed, expanded, and evaporated, and when the refrigerant is vaporized, it absorbs heat from the surroundings and becomes liquefied. It performs cooling or heating action by the characteristic of emitting heat.

In the air conditioner, the refrigerant discharged from the compressor can be condensed in the outdoor heat exchanger during cooling operation, the phase is changed to a low-temperature and low-pressure two-phase refrigerant while passing through the indoor expansion device, and then the heat can be transferred to the indoor air side through the indoor heat exchanger.

In the air conditioner, the flow of refrigerant during the heating operation is opposite to that during the cooling operation, so that the indoor heat exchanger functions as a condenser and the outdoor heat exchanger functions as an evaporator.

The air conditioner may have a plurality of indoor units having an indoor heat exchanger installed, and only some of the plurality of indoor units may be operated at partial load. When the refrigerant exists and the refrigerant is sealed in consideration of the number of connected indoor units, the amount of refrigerant in the non-operating indoor unit is moved to the outdoor heat exchanger, and the refrigerant circulation state is changed, so that the optimal refrigerant distribution may not be possible.

On the other hand, during heating operation, the functions of the outdoor heat exchanger and the indoor heat exchanger change. The volume ratio of the outdoor heat exchanger and the indoor heat exchanger changes according to the number of connected indoor units, and the amount of refrigerant needs to be controlled according to the change in the cooling and heating operation mode.

KR Special 2002-0008638 A (2002.01.31. Public)

One problem to be solved by the present invention is to provide a receiver-integrated accumulator, which is a single device capable of combining the functions of a receiver and an accumulator.

Another problem to be solved by the present invention is to provide a receiver-integrated accumulator in which capacities of a receiver unit and an accumulator unit can be varied.

A receiver-integrated accumulator according to an embodiment of the present invention includes a casing in which an internal space having a constant cross-sectional area is formed; a barrier in contact with the inner surface of the casing and movable inside the casing; a receiver unit located on one side of the inside of the casing and having a receiver inlet passage and a receiver outlet passage connected thereto; and an accumulator part located on the other side of the casing partitioned from the receiver part by the barrier and communicating with the receiver part through the receiver outlet passage. As the barrier moves, volumes of the receiver unit and the accumulator unit may change.

According to this, the receiver-integrated accumulator can serve both the functions of the receiver and the accumulator. In addition, since each capacity of the receiver unit and the accumulator unit can be varied, the amount of refrigerant accommodated in each unit can be organically adjusted.

A receiver-integrated accumulator according to an embodiment of the present invention includes a first limiter formed in the receiver and protruding inward of the casing; and a second limiter formed in the accumulator unit, protruding toward the inside of the casing, and spaced apart from the first limiter by a predetermined distance. The barrier may be movable between the first limiter and the second limiter.

According to this, it is possible to guarantee a minimum capacity for each of the receiver unit and the accumulator unit by limiting the movable range of the barrier.

The barrier may include a partition plate partitioning the receiver unit and the accumulator unit; and a piston ring provided on a circumference of the partition plate, in contact with an inner surface of the casing, and maintaining airtightness between the receiver and the accumulator.

According to this, it is possible to prevent leakage of the refrigerant accommodated in the receiver unit and the accumulator unit.

A volume of the receiver unit may be equal to or smaller than a volume of the accumulator unit.

When the barrier is in contact with the second limiter, the volume of the receiver unit and the volume of the accumulator may be the same.

The receiver unit may be located above the accumulator, and the barrier may be moved up and down.

One end of the receiver outlet passage may be connected to the receiver unit at a higher side than the first limiter, and the other end of the receiver outlet channel may be connected to the accumulator unit at a lower side than the second limiter.

A discharge passage through which gaseous refrigerant is discharged is connected to the accumulator unit, one end of the discharge passage is located below the second limiter inside the casing, and the other end of the discharge passage is located opposite to the one end of the discharge passage. may be located outside the casing.

A suction passage and a steam inflow bypass passage may be connected to the accumulator unit, and the suction passage and the steam inflow bypass passage may be connected to the accumulator unit below the second limiter.

According to this, even when the capacities of the receiver unit and the accumulator unit are respectively minimal, the functions of each unit can be normally performed.

A refrigerant control valve may be installed in at least one of the receiver inlet passage and the receiver outlet passage.

A refrigerant inlet control valve is installed in the receiver inlet passage, a refrigerant outlet control valve is installed in the receiver outlet passage, and the refrigerant inlet control valve and the refrigerant outlet control valve may operate opposite to each other.

An oil passage may be connected to the bottom of the accumulator unit.

According to a preferred embodiment of the present invention, the receiver-integrated accumulator has the advantage of being able to combine the functions of the receiver and the accumulator.

In addition, since each capacity of the receiver unit and the accumulator unit can be varied, there is an advantage in that the amount of refrigerant accommodated in each unit can be organically adjusted.

In addition, the minimum capacity of the receiver unit and the accumulator unit may be guaranteed by limiting the movable range of the barrier by the first limiter and the second limiter.

1 is a configuration diagram showing an example of an air conditioning system having a receiver-integrated accumulator according to an embodiment of the present invention.
FIG. 2 is a block diagram illustrating a flow direction of refrigerant when the refrigerant flows into the receiver during a cooling operation of the air conditioning system shown in FIG. 1 .
FIG. 3 is a block diagram illustrating a flow direction of the refrigerant when the refrigerant flows out of the receiver unit during a cooling operation of the air conditioning system shown in FIG. 1 .
FIG. 4 is a block diagram illustrating a flow direction of a refrigerant when the refrigerant flows into the receiver unit during a heating operation of the air conditioning system shown in FIG. 1 .
FIG. 5 is a block diagram illustrating a flow direction of the refrigerant when the refrigerant flows out of the receiver unit during a heating operation of the air conditioning system shown in FIG. 1 .
6 is a perspective view showing an exterior of a receiver-integrated accumulator according to an embodiment of the present invention.
7 is a diagram for explaining the structure of a receiver-integrated accumulator according to an embodiment of the present invention.
8 is a control block diagram of an air conditioning system having a receiver-integrated accumulator according to an embodiment of the present invention.
9 is a flowchart illustrating an example of a control method for adjusting the amount of circulating refrigerant during a cooling operation.
10 is a flowchart illustrating an example of a control method for adjusting the amount of circulating refrigerant during a heating operation.

Hereinafter, specific embodiments of the present invention will be described in detail with drawings.

1 is a configuration diagram showing an example of an air conditioning system having a receiver-integrated accumulator according to an embodiment of the present invention.

Referring to FIG. 1 , the air conditioning system 1 according to the present embodiment may be a multi air conditioning system for simultaneous cooling and heating. In the simultaneous cooling and heating multi-air conditioning system, a plurality of indoor units (B1, B2, B3, B4) are connected to one outdoor unit (A), and each indoor unit (B1, B2, B3, B4) is either heating or cooling. It is operated in the driving mode to air-condition the room.

Alternatively, the air conditioning system may be a cooling/heating switching type multi-air conditioning system. The cooling/heating switching type multi-air conditioning system may be configured such that a plurality of indoor units (B1, B2, B3, B4) and an outdoor unit (A) are connected through refrigerant pipes. In this case, the cooling/heating switching-type multi-air conditioning system may be switched to one of heating or cooling operation modes to air-condition the room. Such an air conditioning system may be referred to as a heat pump type air conditioning system.

Hereinafter, a case in which the air conditioning system is a simultaneous heating and cooling multi-air conditioning system will be described as an example.

The air conditioning system 1 according to the present embodiment may include an outdoor unit A, at least one indoor unit B1, B2, B3, and B4, and a distributor C.

The outdoor unit (A) includes compressors 51 and 52, receiver-integrated accumulators 100, outdoor heat exchangers 63 and 65, outdoor expansion devices 68 and 69, outdoor fans 64 and 66, and valve devices 60 and 61 ) may be included. In addition, the outdoor unit A may further include a supercooling device 67 and oil separators 53 and 54.

The compressors 51 and 52 may suck, compress, and then discharge the refrigerant. A plurality of compressors 51 and 52 may be connected in parallel or in series. Hereinafter, a case where the first compressor 51 and the second compressor 52 are connected in parallel will be described as an example.

The compressors 51 and 52 may include a first compressor 51 and a second compressor 52 . Each of the first compressor 51 and the second compressor 52 may be an inverter compressor capable of varying the compression capacity of the refrigerant or a constant speed compressor having a constant compression capacity of the refrigerant. Preferably, the first compressor 51 is an inverter compressor, and the second compressor 52 may be a constant speed compressor.

Compressors 51 and 52 may be connected to the receiver-integrated accumulator 100 . In more detail, suction units of the compressors 51 and 52 may be connected to the accumulator unit 120 of the receiver-integrated accumulator 100 .

The discharge passage 77 connected to the accumulator unit 120 may be connected to the refrigerant suction passages 78 and 79 connected to the compressors 51 and 52 . In more detail, the first refrigerant suction passage 78 may connect the discharge passage 77 and the first compressor 51, and the second refrigerant suction passage 79 may connect the discharge passage 77 and the second compressor 52. ) can be connected.

The gaseous refrigerant discharged from the accumulator unit 120 to the discharge passage 77 may be sucked into the compressors 51 and 52 through the refrigerant suction passages 78 and 79 . In more detail, the gaseous refrigerant discharged from the accumulator unit 120 to the discharge passage 77 may be sucked into the first compressor 51 through the first refrigerant suction passage 78, and the second refrigerant suction passage It can be sucked into the second compressor (52) through (79). That is, the refrigerant discharged through the discharge passage 77 may flow through the first refrigerant suction passage 78 and the second refrigerant suction passage 79 .

The compressors 51 and 52 may be connected to the refrigerant discharge passages 55 and 56 . In more detail, the first compressor 51 may be connected to the first refrigerant discharge passage 55, and the second compressor 52 may be connected to the second refrigerant discharge passage 56. The high-temperature and high-pressure gaseous refrigerant compressed in the compressors 51 and 52 may be discharged through the refrigerant discharge passages 55 and 56 .

The oil separators 53 and 54 may be connected to the refrigerant discharge passages 55 and 56 . In more detail, the first oil separator 53 may be connected to the first refrigerant discharge path 55, and the second oil separator 54 may be connected to the second refrigerant discharge path 56.

The oil separators 53 and 54 may serve to separate oil included in the refrigerant discharged from the compressors 51 and 52 .

The oil separators 53 and 54 and the compressors 51 and 52 may be connected to oil return passages 57 and 58 . In more detail, the first oil return passage 57 may connect the first oil separator 53 and the first compressor 51, and the second oil return passage 58 may connect the second oil separator 54 and the second oil return passage 58. 2 Compressor 52 can be connected.

The oil separated by the oil separators 53 and 54 may be returned to the compressors 51 and 52 through the oil return passages 57 and 58 .

The valve devices 60 and 61 may include a main valve device 60 and a sub valve device 61 . Each of the main valve device 60 and the sub valve device 61 may include a four-way valve.

The compressors 51 and 52 or the oil separators 53 and 54 may be connected to the first connection passage 59 . The first connection passage 59 may be connected to the second connection passage 62 . The second connection passage 62 may connect the main valve device 60 and the sub valve device 61 .

The refrigerant discharged from the compressors 51 and 52 may flow to the valve devices 60 and 61 through the first connection passage 59 and the second connection passage 62 . In more detail, the refrigerant compressed in the first compressor 51 and the second compressor 52 may be combined in the first connection passage 59 and may be guided to the second connection passage 62 .

The main valve device 60 may be connected to the third connection passage 91 and the low pressure gas passage 72 . The sub valve device 61 may be connected to the high pressure gas passage 71 and the low pressure gas passage 72 .

During the operation of the entire cooling chamber or the simultaneous operation of the main body of cooling, the high-temperature and high-pressure gaseous refrigerant flowing through the second connection passage 59 may be divided into the main valve device 60 and the sub-valve device 610 to flow. Main valve device 60 ) may be adjusted so that the refrigerant flowing into the second connection passage 62 is guided to the third connection passage 91. In addition, the sub-valve device 61 is configured to allow the refrigerant flowing into the second connection passage 62 to pass through. It can be adjusted to be guided to the high-pressure gas passage 71.

When the entire heating room is operated or the heating main body is operated simultaneously, all of the high-temperature and high-pressure gaseous refrigerant flowing through the second connection passage 59 may flow to the sub-valve device 61 . The sub-valve device 61 may be adjusted so that the refrigerant flowing through the second connection passage 62 is guided to the high-pressure gas passage 71 . In addition, the main valve device 60 may be adjusted so that the refrigerant flowing through the third connection passage 91 is guided to the low pressure gas passage 72 .

Meanwhile, in the outdoor heat exchangers 63 and 65, the refrigerant may be condensed or evaporated by heat exchange with outside air.

During the operation of the entire cooling room or the simultaneous operation of the main body of cooling, the outdoor heat exchangers 63 and 65 may serve as condensers. That is, the refrigerant may be condensed while discharging heat to the outside in the outdoor heat exchangers 63 and 65 .

When the entire heating room is operated or the heating main body is operated simultaneously, the outdoor heat exchangers 63 and 65 may serve as evaporators. That is, the refrigerant may be evaporated while absorbing heat from the outside in the outdoor heat exchanger (63, 65).

To facilitate heat exchange in the outdoor heat exchangers 63 and 65, the outdoor fans 64 and 66 may be installed facing the outdoor heat exchangers 63 and 65. The outdoor fans 64 and 66 may serve to blow outside air to the outdoor heat exchangers 63 and 65.

At least one outdoor heat exchanger (63, 65) may be provided in the outdoor unit (A). Hereinafter, a case in which the outdoor heat exchangers 63 and 65 include the first outdoor heat exchanger 63 and the second outdoor heat exchanger 65 will be described as an example.

The first outdoor heat exchanger 63 may be connected to the main valve device 60 through the third connection passage 91 . The first outdoor heat exchanger (63) may be connected to the second outdoor heat exchanger (65) through a relay passage (89). Also, the first outdoor heat exchanger 63 may be connected to the fourth connection passage 87 .

In more detail, one side of the first outdoor heat exchanger 63 may be connected to the third connection passage 91, and the other side of the first outdoor heat exchanger 63 may be connected to the fourth connection passage 87 and the relay passage 89. ) can be associated with

The first outdoor fan 64 is installed to face the first outdoor heat exchanger 63 and can blow air to the first outdoor heat exchanger 63 .

The second outdoor heat exchanger 65 may be connected to the first outdoor heat exchanger 65 through a relay passage 89 . Also, the second outdoor heat exchanger 65 may be connected to the fourth connection passage 87 through the heat exchanger connection passage 88 .

In more detail, one side of the second outdoor heat exchanger 65 may be connected to the relay passage 89, and the other side of the second outdoor heat exchanger 65 may be connected to the heat exchanger connection passage 88.

The second outdoor fan 66 is installed to face the second outdoor heat exchanger 65 and can blow air to the second outdoor heat exchanger 65 .

A first outdoor expansion device 68 may be installed in the fourth connection passage 87 . The first outdoor expansion device 68 may be installed between the first outdoor heat exchanger 63 and a connection portion of the fourth connection passage 87 to the heat exchanger connection passage 88 .

A second outdoor expansion device 69 may be installed in the heat exchanger connection passage 88 .

Each of the first outdoor expansion device 68 and the second outdoor expansion device 69 may be an electric expansion valve (EEV).

During operation of the entire cooling room or simultaneous operation of the main body of cooling, the first outdoor expansion device 68 and the second outdoor expansion device 69 may be fully open. In this case, the refrigerant may not expand while passing through the first outdoor expansion device 68 and the second outdoor expansion device 69 .

When the entire heating room is operated or the heating main body is operated simultaneously, the first outdoor expansion device 68 and the second outdoor expansion device 69 may be adjusted to a set opening degree. In this case, the refrigerant may be expanded while passing through the first outdoor expansion device 68 and the second outdoor expansion device 69 .

Meanwhile, the outdoor heat exchangers 63 and 65 may be connected to the supercooling device 67 through the fourth connection passage 87 . The supercooling mechanism 67 may serve to supercool the refrigerant that has passed through the outdoor heat exchangers 63 and 65 during operation of the cooling front room or simultaneous operation of the main body of cooling.

The supercooling mechanism 67 may include a supercooling heat exchanger 67a, a bypass inlet passage 67b, a supercooling expansion mechanism 67c, and a bypass outlet passage 67d.

The supercooled heat exchanger 67a may be installed while surrounding a part of the liquid passage 73 connected to the fourth connection passage 87 .

The bypass inlet passage 67b may connect the liquid passage 73 and the subcooling heat exchanger 67a. During the cooling front chamber operation or the simultaneous cooling operation, the bypass inlet passage 67b may guide a portion of the refrigerant flowing to the distributor C along the liquid passage 73 into the subcooling heat exchanger 67a.

The supercooled expansion mechanism 67c may be installed in the bypass inlet passage 67b. The supercooled expansion mechanism 67c may be an electronic expansion valve (EEV).

During the cooling front chamber operation or the simultaneous operation of the cooling main body, the refrigerant flowing through the bypass inlet passage 67b is expanded while passing through the supercooled expansion mechanism 67c, and may be guided into the supercooled heat exchanger 67a.

The bypass outlet passage 67d may connect the supercooled heat exchanger 67a, the low pressure gas passage 72, and the compressors 51 and 52. In more detail, one end of the bypass outlet passage 67c may be connected to the supercooling heat exchanger 67a and the other end may be connected to the vapor injection bypass passage 76 .

During the operation of the entire cooling chamber or simultaneous operation of the main body of cooling, the bypass outlet passage 67d may guide the refrigerant that has passed through the supercooled heat exchanger 67a between the low pressure gas passage 72 and the compressors 51 and 52 .

Meanwhile, the receiver-integrated accumulator 100 may include a receiver unit 110 and an accumulator unit 120 . The receiver unit 110 and the accumulator unit 120 may be partitioned from each other.

The receiver unit 110 may store some of the refrigerant when the amount of circulating refrigerant in the air conditioning system 1 is excessive, and supply refrigerant when the amount of circulating refrigerant is insufficient.

The receiver unit 110 can be operated while the air conditioning system is operating, and the optimal amount of circulating refrigerant can be adjusted while the air conditioning system 1 is air conditioning the room.

In the air conditioning system 1 , the optimal amount of circulating refrigerant circulating in the air conditioning system 1 may vary depending on the number of indoor units in operation among the plurality of indoor units B1 , B2 , B3 , and B4 . In addition, the optimum amount of circulating refrigerant circulating in the air conditioning system 1 may be different when the cooling of all rooms is operated or the main body of cooling is operated simultaneously, and the operation of all rooms of heating or the main body of heating is operated simultaneously.

A receiver inlet passage 74 and a receiver outlet passage 75 may be connected to the receiver unit 110 .

Refrigerant control valves 80 and 81 may be installed in at least one of the receiver inlet passage 74 and the receiver outlet passage 75 . The refrigerant control valves 80 and 81 may be electronic expansion valves (EEVs).

In more detail, a refrigerant inlet control valve 80 may be installed in the receiver inlet passage 74, and a refrigerant outlet control valve 81 may be installed in the receiver outlet passage 75.

The refrigerant inlet control valve 80 can control the amount of refrigerant flowing into the receiver unit 110 through the receiver inlet passage 74, and the refrigerant outlet control valve 81 passes through the receiver outlet passage 75 to the receiver unit. The amount of refrigerant flowing out of (110) can be adjusted.

The refrigerant inlet control valve 80 and the refrigerant outlet control valve 81 may operate opposite to each other. In more detail, when the amount of circulating refrigerant in the air conditioning system 1 is insufficient, the refrigerant inflow control valve 80 may be closed and the refrigerant outflow control valve 81 may be opened. Conversely, when the amount of circulating refrigerant in the air conditioning system 1 is excessive, the refrigerant inflow control valve 80 may be opened and the refrigerant outflow control valve 81 may be closed.

The receiver unit 110 may be connected to the fourth connection passage 87 through the receiver inlet passage 74 . That is, the receiver unit 110 may be connected between the outdoor heat exchangers 63 and 65 and the supercooling device 67 by the receiver inlet passage 74 . In this case, when the refrigerant inflow control valve 80 is open, a portion of the refrigerant flowing into the fourth connection passage 87 may flow into the receiver unit 110 through the receiver inlet passage 74 .

Alternatively, the receiver unit 110 may be connected to the liquid passage 73 through the receiver inlet passage 74 . That is, the receiver unit 110 may be connected between the supercooling device 67 and the distributor C by the receiver inlet passage 74 . In this case, when the refrigerant inlet control valve 80 is open, a part of the refrigerant flowing into the liquid passage 73 may flow into the receiver unit 110 through the receiver inlet passage 74 .

The receiver unit 110 may communicate with the accumulator unit 120 through the receiver outlet passage 75 . In this case, when the refrigerant outlet control valve 81 is open, the refrigerant in the receiver unit 110 may flow into the accumulator unit 120 through the receiver outlet passage 75.

The accumulator unit 120 may prevent liquid refrigerant from flowing into the compressors 51 and 52 . That is, liquid refrigerant among the refrigerants introduced into the accumulator unit 120 may accumulate in the accumulator unit 120, and gaseous refrigerant among the refrigerants introduced into the accumulator unit 120 may be sucked into the compressors 51 and 52.

A receiver outlet passage 75, a low pressure gas passage 72, and a discharge passage 77 may be connected to the accumulator unit 120. In addition, a steam inflow bypass passage 76 and an oil passage 84 may be connected to the accumulator unit 120 .

As described above, the receiver outlet passage 75 may guide the refrigerant of the receiver unit 110 to the accumulator unit 120 .

A part of the low-pressure gas passage 72 adjacent to the accumulator part 120 may be a suction passage through which low-pressure gaseous refrigerant flows into the accumulator part 120 .

The discharge passage 77 may guide gaseous refrigerant from the accumulator to the compressor. The discharge passage 77 may connect the refrigerant suction passages 78 and 79 and the accumulator unit 120 . The gaseous refrigerant may be discharged from the accumulator unit 120 to the discharge passage 77, and is divided into the first refrigerant suction passage 78 and the second refrigerant suction passage 79 to flow, respectively, to the first compressor 51, It can be sucked into the second compressor (52).

The steam inlet bypass passage 76 may connect the bypass outlet passage 67d and the accumulator unit 120 . A bypass valve 85 may be installed in the steam inlet bypass passage 76 . The bypass valve 85 may control the amount of refrigerant flowing into the accumulator unit 120 through the steam inlet bypass passage 76 .

When the bypass valve 85 is opened during the cooling operation of all rooms or the simultaneous operation of the main body of cooling, a part of the refrigerant flowing through the bypass outlet passage 67d flows into the steam inlet bypass passage 76 and the remaining part flows into the steam inflow passage It can flow to (82, 83). The refrigerant may be sucked into the first and second compressors 51 and 52 through the first and second steam introduction channels 81 and 82 . In addition, expansion valves are installed in the vapor inlet passages 81 and 82 to prevent liquid refrigerant from flowing into the compressors 51 and 52.

The oil passage 84 may be connected to the bottom of the accumulator unit 120 . This is to flow the oil accumulated below the inside of the accumulator part.

The oil passage 84 may connect the accumulator unit 120 and the discharge passage 77 . Accordingly, the oil flowing into the oil passage 84 may be sucked into the compressors 51 and 53 through the discharge passage 77 .

An oil return valve 86 may be installed in the oil passage 84 . The oil recovery valve 86 may control the amount of oil flowing out of the accumulator unit 120 through the oil passage 84 .

Meanwhile, the air conditioning system 1 may include at least one indoor unit B1, B2, B3, or B4. For example, the air conditioning system 1 may include a first indoor unit B1, a second indoor unit B2, a third indoor unit B3, and a fourth indoor unit B4. The plurality of indoor units B1 , B2 , B3 , and B4 may be connected to the distributor C in parallel.

Some of the plurality of indoor units B1 , B2 , B3 , and B4 may be operated, while others may be stopped. In addition, in the multi-air conditioning system 1 for simultaneous cooling and heating, some of the indoor units in operation may be operated for cooling, and others may be operated for heating.

The indoor units (B1, B2, B3, B4) include indoor heat exchangers (11, 21, 31, 41), indoor fans (15, 25, 35, 45), and indoor expansion devices (12, 22, 32, 42). can do.

In the indoor heat exchanger (11, 21, 31, 41), the refrigerant may be condensed or evaporated by heat exchange with indoor air.

The indoor heat exchangers 11, 21, 31, and 41 of the cooling-operated indoor units B1, B2, B3, and B4 may serve as evaporators. That is, the refrigerant may be evaporated while absorbing heat from the outside in the indoor heat exchanger (11, 21, 31, 41).

The indoor heat exchangers 11 , 21 , 31 , and 41 of the indoor units B1 , B2 , B3 , and B4 operated by heating may serve as condensers. That is, the refrigerant may be condensed while discharging heat to the outside in the indoor heat exchangers 11, 21, 31, and 41.

To facilitate heat exchange in the indoor heat exchangers 11, 21, 31, and 41, the indoor fans 15, 25, 35, and 45 may be installed facing the indoor heat exchangers 11, 21, 31, and 41. can The indoor fans 15, 25, 35, and 45 may serve to blow air heat-exchanged in the indoor heat exchanger 11, 21, 31, and 41 into the room.

The indoor heat exchangers 11, 21, 31, and 41 may be connected to the first indoor heat exchanger connection passages 13, 23, 33, and 43 and the second indoor heat exchanger connection passages 14, 24, 34, and 44. . In more detail, one side of each indoor heat exchanger (11, 21, 31, 41) may be connected to the distributor (C) through the first indoor heat exchanger connection passage (13, 23, 33, 43), and the other side may be connected to the first indoor heat exchanger connection passage (C). It can be connected to the distributor (C) by the two-room heat exchanger (14, 24, 34, 44).

The first indoor heat exchanger connection passages 13, 23, 33, and 43 connected to the cooling-operated indoor units B1, B2, B3, and B4 allow liquid refrigerant to expand indoors in the liquid header 83 of the distributor C. Instruments 12, 22, 32, 42 may be guided.

The second indoor heat exchanger connection passages (14, 24, 34, 44) connected to the indoor units (B1, B2, B3, B4) operated in cooling mode are low pressure vaporized in the indoor heat exchangers (11, 21, 31, 41). The gaseous refrigerant of may be guided to the low-pressure gas header 82 of the distributor (C).

The condensed liquid in the indoor heat exchanger (11, 21, 31, 41) is connected to the first indoor heat exchanger connection passage (13, 23, 33, 43) connected to the heating-operated indoor units (B1, B2, B3, B4). The refrigerant may be guided to the liquid header 83 of the distributor (C).

The second indoor heat exchanger connection passages 14, 24, 34, and 44 connected to the heating-operated indoor units B1, B2, B3, and B4 transfer the high-pressure gaseous refrigerant to the high-pressure gas header 81 of the distributor C. may be guided to the indoor heat exchanger (11, 21, 31, 41).

Between the indoor units (B1, B2, B3, B4) and the distributor (C) among the first indoor heat exchanger connection passages (13, 23, 33, 43) and the second indoor heat exchanger connection passages (14, 24, 34, 44) An on-off valve capable of opening and closing the flow path may be installed in a portion located at . The opening/closing valve may be selectively opened or closed depending on whether the indoor units B1, B2, B3, and B4 are operated/stopped.

Indoor expansion devices 12 , 22 , 32 , and 42 may be installed in the first indoor heat exchanger connection passages 13 , 23 , 33 , and 43 .

Each of the indoor expansion devices 12, 22, 32, and 42 may be an electric expansion valve (EEV).

The indoor expansion mechanisms 12, 22, 32, and 42 of the cooling-operated indoor units B1, B2, B3, and B4 may be adjusted to a set opening degree. In this case, the refrigerant can be expanded while passing through the first indoor expansion mechanism (12, 22, 32, 42).

The indoor expansion mechanisms 12, 22, 32, and 42 of the indoor units B1, B2, B3, and B4 operated by heating may be fully opened. In this case, the refrigerant passes through the indoor expansion mechanism 12, 22, 32, 42 and may not expand.

Meanwhile, the distributor (C) may be disposed between the outdoor unit (A) and the indoor unit (B1, B2, B3, B4) with respect to the flow of the refrigerant. The distributor C may distribute refrigerant to the indoor units B1 , B2 , B3 , and B4 according to the conditions of all cooling rooms, all heating rooms, simultaneous operation of the cooling subject, and simultaneous operation of the heating subject.

The distributor C may include a high-pressure gas header 81, a low-pressure gas header 82, a liquid header 83 and control valves (not shown).

A high-pressure gas passage 71 may be connected to the high-pressure gas header 81 . That is, the high-pressure gas passage 71 may connect the sub-valve device 61 of the outdoor unit A and the high-pressure gas header 81 of the distributor C.

Among the high-pressure gaseous refrigerants compressed by the compressors 51 and 52 , the refrigerant guided from the sub-valve device 61 to the high-pressure gas passage 71 may flow to the high-pressure gas header 81 . The high-pressure gas header 81 may flow the high-pressure gaseous refrigerant to the second indoor heat exchanger connection passages 14, 24, 34, and 44 connected to the indoor units B1, B2, B3, and B4 operated by heating.

A low-pressure gas passage 72 may be connected to the low-pressure gas header 82 . That is, the low-pressure gas passage 72 may connect the sub-valve device 61 of the outdoor unit A and the receiver-integrated accumulator 100 to the low-pressure gas header 82 of the distributor C.

The low-pressure gaseous refrigerant may flow to the low-pressure gas header 82 through the passages 14, 24, 34, and 44 connected to the second indoor heat exchanger connected to the indoor units B1, B2, B3, and B4 operated in cooling operation. . The low-pressure gas header 82 may flow low-pressure gaseous refrigerant into the low-pressure gas passage 72 . The refrigerant flowing through the low-pressure gas passage 72 may flow into the accumulator unit 120 of the receiver-integrated accumulator 100 .

A liquid passage 73 may be connected to the liquid header 83 . That is, the liquid passage 73 may connect the supercooling device 67 of the outdoor unit A and the liquid header 83 of the distributor C.

FIG. 2 is a block diagram showing the flow direction of the refrigerant when the refrigerant flows into the receiver during the cooling operation of the air conditioning system shown in FIG. 1 , and FIG. 3 is the refrigerant during the cooling operation of the air conditioning system shown in FIG. 1 . It is a configuration diagram showing the flow direction of the refrigerant when is leaked from the receiver unit.

Hereinafter, the operation of the air conditioning system 1 during operation of the entire cooling room or simultaneous operation of the main body of cooling will be described.

Referring to FIGS. 2 and 3 , the high-pressure gaseous refrigerant compressed by the compressors 51 and 52 of the outdoor unit A may be discharged to the refrigerant discharge passages 55 and 56 . Among the refrigerants discharged through the refrigerant discharge passages 55 and 56, oil may be separated from the oil separators 53 and 54 and returned to the oil return passages 57 and 58.

The refrigerant discharged through the refrigerant discharge passages 55 and 56 may flow to the second connection passage 62 through the first connection passage 59 . The refrigerant flowing through the second connection passage 62 may be divided into the main valve device 60 and the sub valve device 61 to flow.

At this time, the sub-valve device 61 may be adjusted so that the refrigerant does not flow into the high-pressure gas flow path 71 during the cooling front chamber operation. When the cooling main body is operated simultaneously, the sub-valve device 61 can be adjusted so that some refrigerant flows into the high-pressure gas flow path 71 since there are indoor units B1, B2, B3, and B4 operated in heating operation.

The main valve device 60 may guide the refrigerant flowing through the second connection passage 62 to the third connection passage 91 . The refrigerant may flow into the first outdoor heat exchanger 63 through the third connection passage 91 . The refrigerant may be condensed while exchanging heat with outdoor air in the first outdoor heat exchanger (63).

A part of the refrigerant condensed in the first outdoor heat exchanger 63 may flow to the fourth connection passage 87, and the remaining part may flow to the second outdoor heat exchanger 65 through the relay passage 89. there is. Alternatively, all of the refrigerant condensed in the first outdoor heat exchanger 63 may flow to the fourth connection passage 87, or conversely, all of the refrigerant condensed in the first outdoor heat exchanger 63 may flow to the second outdoor heat exchanger 65 through the relay passage 89. may be

The refrigerant flowing into the second outdoor heat exchanger 65 may be condensed while exchanging heat with outdoor air in the second outdoor heat exchanger 65 and may flow into the heat exchanger connection passage 88 .

Each of the outdoor inflation devices 68 and 69 can be fully opened. Accordingly, the refrigerant condensed in the first outdoor heat exchanger 63 and flowing into the fourth connection passage 87 may not expand in the first outdoor expansion device 68 . The refrigerant condensed in the second outdoor heat exchanger 65 and flowing into the heat exchanger connection passage 88 may not expand in the second outdoor expansion mechanism 69 .

The refrigerant condensed in the outdoor heat exchangers 63 and 65 may flow to the supercooling device 67 along the fourth connection passage 87 .

The refrigerant condensed in the outdoor heat exchangers (63, 65) passes through the liquid flow path (73) surrounded by the subcooled heat exchanger (67a), and then partially flows into the bypass inlet flow path (67b) and is cooled by the supercooled expansion mechanism (97c). can be inflated. The refrigerant expanded by the supercooled expansion mechanism 67c passes through the supercooled heat exchanger 67a and cools the refrigerant in the liquid passage 73 surrounded by the supercooled heat exchanger 67a.

The refrigerant inside the supercooled heat exchanger 67a may be sucked into the accumulator unit 120 of the receiver-integrated accumulator 100 and/or the compressors 51 and 52 through the bypass outlet passage 67d. In more detail, the refrigerant flowing from the bypass outlet passage 67d to the steam inlet bypass passage 76 flows into the accumulator unit 120, and from the bypass outlet passage 67d to the steam inlet passages 82 and 83. The refrigerant flowing into may be sucked into the compressors 51 and 52.

Meanwhile, some of the refrigerant cooled in the supercooled heat exchanger 67a may flow to the liquid header 83 of the distributor C through the liquid passage 73 .

The liquid header 83 may flow liquid refrigerant to the first indoor heat exchanger connection passages 13, 23, 33, and 43 connected to the indoor units B1, B2, B3, and B4 operated in a cooling operation. The refrigerant flowing through the first indoor heat exchanger connection passage (13, 23, 33, 43) can be expanded in the indoor expansion device (12, 22, 32, 42), and the indoor heat exchanger (11, 21, 31, 41) ) can flow.

The refrigerant flowing into the indoor heat exchangers 11, 21, 31, and 41 may be evaporated while exchanging heat with indoor air in the indoor heat exchangers 11, 21, 31, and 41. As a result, indoor air can be cooled to perform a cooling function.

The refrigerant evaporated in the indoor heat exchanger (11, 21, 31, 41) may flow to the low-pressure gas header (82) of the distributor (C) through the second indoor heat exchanger connection passage (14, 24, 34, 44). there is.

The low-pressure gas header 82 may flow refrigerant to the outdoor unit A through the low-pressure gas passage 72 .

The refrigerant flowing from the low-pressure gas header 82 to the low-pressure gas passage 72 may flow into the accumulator unit 120 of the receiver-integrated accumulator 100 .

Among the refrigerants in the accumulator unit 120 , gaseous refrigerant may be discharged through the discharge passage 77 and may be sucked into the compressors 51 and 52 through the refrigerant suction passages 78 and 79 . The compressors 51 and 52 may compress the refrigerant again, and the refrigerant may circulate through the air conditioning system 1 while repeating the above-described process.

On the other hand, as shown in FIG. 2, when the amount of refrigerant circulating in the air conditioning system 1 is excessive, a portion of the refrigerant flowing into the fourth connection passage 87 or the liquid passage 73 passes through the receiver inlet passage 74 to the receiver integrated accumulator. It can flow into the receiver unit 110 of (100). At this time, the refrigerant inlet control valve 80 may be opened, and the refrigerant outlet control valve 81 may be closed.

As a result, since some of the refrigerant is accommodated in the receiver unit 110, the amount of circulating refrigerant in the air conditioning system 1 can be reduced and the amount of circulating refrigerant can be adjusted to an optimal amount.

Conversely, as shown in FIG. 3 , when the amount of circulating refrigerant in the air conditioning system 1 is insufficient, the refrigerant in the receiver unit 110 may flow into the accumulator unit 120 through the receiver outlet passage 75 . At this time, the refrigerant inlet control valve 80 may be closed, and the refrigerant outlet control valve 81 may be opened.

As a result, since some refrigerant is supplied in a circulation cycle in the receiver unit 110, the amount of refrigerant circulating in the air conditioning system 1 can be increased and the amount of refrigerant circulating can be adjusted to an optimal amount.

FIG. 4 is a configuration diagram illustrating a flow direction of the refrigerant when the refrigerant flows into the receiver during the heating operation of the air conditioning system shown in FIG. 1, and FIG. 5 is the refrigerant during the heating operation of the air conditioning system shown in FIG. It is a configuration diagram showing the flow direction of the refrigerant when is leaked from the receiver unit.

Hereinafter, the operation of the air conditioning system 1 during operation of all heating rooms or simultaneous operation of heating subjects will be described.

Referring to FIGS. 4 and 5 , the high-pressure gaseous refrigerant compressed by the compressors 51 and 52 of the outdoor unit A may be discharged to the refrigerant discharge passages 55 and 56 . Among the refrigerants discharged through the refrigerant discharge passages 55 and 56, oil may be separated from the oil separators 53 and 54 and returned to the oil return passages 57 and 58.

The refrigerant discharged through the refrigerant discharge passages 55 and 56 may flow to the second connection passage 62 through the first connection passage 59 . The refrigerant flowing through the second connection passage 62 may be divided into the main valve device 60 and the sub valve device 61 to flow.

At this time, the main valve device 60 and the sub valve device 61 may be adjusted so that the refrigerant flowing through the second connection passage is guided to the high-pressure gas passage 71 .

The refrigerant flowing through the high-pressure gas passage 71 may flow into the high-pressure gas header 81 of the distributor (C).

The high-pressure gas header 81 may flow the refrigerant to the second indoor heat exchanger connection passages 14, 24, 34, and 44 connected to the heating-operated indoor units B1, B2, B3, and B4. The refrigerant flowing through the passages 14 , 24 , 34 , and 44 connecting the second indoor heat exchanger may flow into the indoor heat exchangers 11 , 21 , 31 , and 41 .

The refrigerant flowing into the indoor heat exchangers 11, 21, 31, and 41 may be condensed while exchanging heat with indoor air in the indoor heat exchangers 11, 21, 31, and 41. As a result, indoor air is heated to perform a heating function.

The indoor expansion mechanisms 12, 22, 32, and 42 of the indoor units B1, B2, B3, and B4 operated by heating may be fully opened. Therefore, the refrigerant condensed in the indoor heat exchanger (11, 21, 31, 41) may not be expanded in the indoor expansion mechanism (12, 22, 32, 42).

The refrigerant condensed in the indoor heat exchangers 11, 21, 31, and 41 may flow to the liquid header 83 of the distributor C through the first indoor heat exchanger connection passages 13, 23, 33, and 43. .

The liquid header 83 may flow the refrigerant to the outdoor unit A through the liquid passage 73 .

The refrigerant flowing from the liquid header 83 to the liquid passage 73 may flow to the fourth connection passage 87 . In the supercooling mechanism 67, supercooling of the refrigerant may not occur.

When subcooling of the refrigerant is performed in the supercooling mechanism 67, a portion of the refrigerant flowing into the liquid passage 73 flows into the bypass inlet passage 67b and can be expanded by the supercooling expansion mechanism 97c. The refrigerant expanded by the supercooled expansion mechanism 67c passes through the supercooled heat exchanger 67a and cools the refrigerant in the liquid passage 73 surrounded by the supercooled heat exchanger 67a.

The refrigerant inside the supercooled heat exchanger 67a may be sucked into the accumulator unit 120 of the receiver-integrated accumulator 100 and/or the compressors 51 and 52 through the bypass outlet passage 67d. In more detail, the refrigerant flowing from the bypass outlet passage 67d to the steam inlet bypass passage 76 flows into the accumulator unit 120, and from the bypass outlet passage 67d to the steam inlet passages 82 and 83. The refrigerant flowing into may be sucked into the compressors 51 and 52.

The refrigerant flowing from the liquid passage 73 to the fourth connection passage 87 may be expanded in the outdoor expansion devices 68 and 69 . In more detail, the refrigerant flowing from the fourth connection passage 87 to the first outdoor expansion device 68 can be expanded in the first outdoor expansion device 68, and the heat exchanger is connected to the fourth connection passage 87. The refrigerant flowing through the passage 88 may be expanded in the second outdoor expansion device 69 .

The refrigerant expanded in the first outdoor expansion device 68 may flow to the first outdoor heat exchanger 63 . In the first outdoor heat exchanger 63, the refrigerant may be evaporated while exchanging heat with outdoor air.

The refrigerant expanded in the second outdoor expansion device 69 may flow to the second outdoor heat exchanger 65 . In the second outdoor heat exchanger 65, the refrigerant may be evaporated while exchanging heat with outdoor air. The refrigerant evaporated in the second outdoor heat exchanger 65 may flow to the first heat exchanger 63 through the relay passage 89 and may further evaporate in the first outdoor heat exchanger 63 .

The refrigerant evaporated in the first outdoor heat exchanger 63 may flow to the main valve device 60 through the third connection passage 91 .

The main valve device 60 may be controlled such that the refrigerant flowing through the third connection passage 91 flows into the low pressure gas passage 72 . The refrigerant flowing through the low-pressure gas passage 72 may flow into the accumulator unit 120 of the receiver-integrated accumulator 100 .

Among the refrigerants in the accumulator unit 120 , gaseous refrigerant may be discharged through the discharge passage 77 and may be sucked into the compressors 51 and 52 through the refrigerant suction passages 78 and 79 . The compressors 51 and 52 may compress the refrigerant again, and the refrigerant may circulate through the air conditioning system 1 while repeating the above-described process.

On the other hand, as shown in FIG. 4, when the amount of refrigerant circulating in the air conditioning system 1 is excessive, a portion of the refrigerant flowing into the fourth connection passage 87 or the liquid passage 73 passes through the receiver inlet passage 74 to the receiver integrated accumulator. It can flow into the receiver unit 110 of (100). At this time, the refrigerant inlet control valve 80 may be opened, and the refrigerant outlet control valve 81 may be closed.

As a result, since some of the refrigerant is accommodated in the receiver unit 110, the amount of circulating refrigerant in the air conditioning system 1 can be reduced and the amount of circulating refrigerant can be adjusted to an optimal amount.

Conversely, as shown in FIG. 5 , when the amount of circulating refrigerant in the air conditioning system 1 is insufficient, the refrigerant in the receiver unit 110 may flow into the accumulator unit 120 through the receiver outlet passage 75 . At this time, the refrigerant inlet control valve 80 may be closed, and the refrigerant outlet control valve 81 may be opened.

As a result, since some refrigerant is supplied in a circulation cycle in the receiver unit 110, the amount of refrigerant circulating in the air conditioning system 1 can be increased and the amount of refrigerant circulating can be adjusted to an optimal amount.

6 is a perspective view showing an appearance of a receiver-integrated accumulator according to an embodiment of the present invention, and FIG. 7 is a view for explaining the structure of the receiver-integrated accumulator according to an embodiment of the present invention.

6 and 7 , the receiver-integrated accumulator 100 according to the present embodiment may include a casing 101, a barrier 130, a receiver unit 110, and an accumulator unit 120. The receiver-integrated accumulator 100 may further include a first limiter 111 and a second limiter 121 .

The casing 101 may form the exterior of the receiver-integrated accumulator 100 . The casing 101 may have a substantially cylindrical shape. The casing 101 may be formed vertically long.

The casing 101 may form an inner space of the receiver-integrated accumulator 100 . A cross-sectional area of the inner space may be constant. For example, the casing 101 has a cylindrical shape elongated in the vertical direction, and the cross-sectional area of the casing 101 may have a constant circle diameter.

The barrier 130 may be disposed inside the casing 101 . The barrier 130 may come into contact with an inner surface of the casing 101 .

The barrier 130 may have the same cross-sectional area as or a similar shape to that of the casing. For example, the casing 101 may have a cylindrical shape elongated in the vertical direction, and the barrier 130 may have a disk shape. Alternatively, the barrier 130 may have a low cylindrical shape.

The barrier 130 may partition the receiver unit 110 and the accumulator unit 120 .

The receiver unit 110 may be located on one side inside the casing 101, and the accumulator unit 120 may be located on the other side opposite to the one side with respect to the barrier 130 inside the casing 101.

For example, the upper space of the barrier 130 may be the receiver unit 110 and the lower space may be the accumulator unit 120 . That is, the receiver unit 110 may be located above the accumulator unit 120 .

The receiver unit 110 may refer to a space between an inner upper surface of the casing 101 and an upper surface of the barrier 130 . Also, the accumulator unit 120 may refer to a space between an inner bottom surface of the casing 101 and a bottom surface of the barrier 130 .

An upper surface of the barrier 130 may be the same as a bottom surface of the receiver unit 110 . Also, a bottom surface of the barrier 130 may be the same as a ceiling surface of the accumulator unit 120 .

The barrier 130 may maintain airtightness of the receiver unit 110 and the accumulator unit 120 . That is, it is possible to prevent the refrigerant of the receiver unit 110 from leaking from the inside of the casing 101 to the accumulator unit 120 .

The barrier 130 may include a partition plate 131 and a piston ring 132 .

The partition plate 131 may partition the receiver unit 110 and the accumulator unit 120 . The partition plate 131 may have a disk shape.

The piston ring 132 may mean a pressure ring and/or an oil ring. The piston ring 132 may include an O-ring.

The piston ring 132 may be provided on the circumference of the partition plate 131 . The piston ring 132 may come into contact with the inner surface of the casing 101 . Airtightness of the receiver unit 110 and the accumulator unit 120 may be maintained by the piston ring 132 . That is, the piston ring 132 may have pressure resistance characteristics capable of maintaining airtightness inside the casing 101 .

The barrier 130 may be movable inside the casing 101 . For example, the casing 101 has a cylindrical shape elongated in the vertical direction, and the barrier 130 can be moved up and down.

Since the pressure inside the receiver unit 110 is higher than the pressure inside the accumulator unit 120 and the receiver unit 110 is located above the accumulator unit 120, the barrier 130 moves downward due to the pressure difference and gravity. can receive strength. At the same time, the liquid refrigerant inside the accumulator unit 120 may push up the barrier 130 .

As the barrier 130 moves, the volumes of the receiver unit 110 and the accumulator unit 120 may change respectively.

The sum of the volume of the receiver unit 110 and the volume of the accumulator unit 120 may be constant. The sum of the volume of the receiver unit 110 and the volume of the accumulator unit 120 may be equal to the volume of the internal space of the casing 101 . That is, the total height of the casing 101 may be equal to (h1+h2) the sum of the height h1 of the receiver unit 110 and the height h2 of the accumulator unit 120.

For example, when the barrier 130 rises upward, the height h1 of the receiver unit 110 may decrease and the height h2 of the accumulator may increase. That is, the volume of the receiver unit 110 may decrease and the volume of the accumulator unit 120 may increase.

Conversely, when the barrier 130 moves downward, the height h1 of the receiver unit 110 may increase and the height h2 of the accumulator may decrease. That is, the volume of the receiver unit 110 may increase and the volume of the accumulator unit 120 may decrease.

The volume of the receiver unit 110 and the accumulator unit 120 can be varied by the movement of the barrier 130, so that the amount of circulating refrigerant in the air conditioning system 1 can be more organically adjusted.

In order to set a limit to the volume change of the receiver unit 110 and the accumulator unit 120, the barrier 130 may be movable only between the first limiter 111 and the second limiter 121.

In more detail, when the barrier 130 rises and the upper surface of the barrier 130 contacts the lower surface of the first limiter 111, the barrier 130 cannot rise any more. In addition, when the barrier 130 descends and the lower surface of the barrier 130 contacts the upper surface of the second limiter 121, the barrier 130 cannot descend any further.

The first limiter 111 may be formed in the receiver unit 110 and the second limiter 121 may be formed in the accumulator unit 120 . The first limiter 111 and the second limiter 121 may protrude toward the inside of the casing 101 .

In addition, the first limiter 111 and the second limiter 121 may be spaced apart from each other by a first set distance D1. The second limiter 121 may be spaced apart from the inner upper surface of the casing 101 by a second set distance D2. The first limiter 111 may be spaced apart from the inner bottom surface of the casing by a third set distance D3. Each of the set distances D1, D2, and D3 may be calculated ignoring the vertical thickness of the first and second limiters 111 and 121 themselves.

At this time, the total height of the casing 101 may be equal to (D2+D3-D1) obtained by subtracting the first set distance D1 from the sum of the second set distance D2 and the third set distance D3.

The first, second, and third set distances D1, D2, and D3 may be constant distances.

The movable area of the barrier 130 may correspond to the first set distance D1. The volume variable region of the receiver unit 110 may correspond to the second set distance D2. The volume variable region of the accumulator unit 120 may correspond to the third set distance D3.

In more detail, when the barrier 130 contacts the first limiter 111, the receiver unit 110 has a minimum volume and the accumulator unit 120 has a maximum volume. At this time, the height h1 of the receiver unit 110 is the same as (D2-D1) obtained by subtracting the first set distance D1 from the second set distance D2, and the height h2 of the accumulator unit 120 ) may be equal to the third set distance D3.

When the barrier 130 contacts the second limiter 121, the volume of the receiver unit 110 may be maximum and the volume of the accumulator unit 120 may be minimum. At this time, the height h1 of the receiver unit 110 is equal to the second set distance D2, and the height h2 of the accumulator unit 120 is from the third set distance D3 to the first set distance D1. ) may be the same as subtracting (D3-D1).

The volume of the receiver unit 110 may be equal to or smaller than the volume of the accumulator unit 120 . When the barrier 130 contacts the second limiter 121, the volume of the receiver unit and the accumulator unit may be the same.

For example, if the internal capacity of the casing 101 is 20L, the sum of the capacity of the receiver unit 110 and the capacity of the accumulator unit 120 may be constant at 20L. At this time, the capacity of the receiver unit 110 may vary from a minimum of 5L to a maximum of 10L, and the capacity of the accumulator unit 120 may vary from a minimum of 10L to a maximum of 15L.

Hereinafter, flow paths connected to the receiver unit 110 and the accumulator unit 120 will be described.

A receiver inlet passage 74 and a receiver outlet passage 75 may be connected to the receiver unit 110 .

As described above, the refrigerant inlet control valve 80 may be installed in the receiver inlet passage 74, and the refrigerant outlet control valve 81 may be installed in the receiver outlet passage 75.

When the amount of circulating refrigerant in the air conditioning system 1 is excessive, the refrigerant inflow control valve 80 is opened, and some of the circulating refrigerant may flow into the receiver unit 110 through the receiver inlet passage 74. At this time, the refrigerant outflow control valve 81 is closed to prevent the refrigerant from flowing out of the receiver unit 110 through the receiver outlet passage 75.

When the amount of circulating refrigerant in the air conditioning system 1 is insufficient, the refrigerant inflow control valve 80 is closed to prevent the circulating refrigerant from flowing into the receiver unit 110 through the receiver inlet passage 74. The refrigerant outlet control valve 81 is opened so that the refrigerant stored in the receiver unit 110 can be supplied to the accumulator unit 120 through the receiver outlet passage 75 .

Since the refrigerant introduced into the receiver inlet passage 74 accumulates from the bottom surface of the receiver part 110, the connection between the receiver part 110 and the receiver inlet passage 74 is the receiver part 110 and the receiver outlet passage 75 It may be located on the upper side than the connection part of.

One end of the receiver outlet passage 75 may be connected to the receiver unit 110 and the other end may be connected to the accumulator unit 120 . As a result, the receiver unit 110 and the accumulator unit 120 may communicate.

One end of the receiver outlet passage 75 is connected to the receiver unit 110 at an upper side than the first limiter 111, and the other end of the receiver outlet passage 75 is connected to the accumulator unit at a lower side than the second limiter 121 ( 120) can be connected.

In more detail, even when the barrier 130 is in contact with the first limiter 111 and the volume of the receiver unit 110 is minimal, in order for the function of the receiver unit 110 to operate normally, the receiver outlet passage 75 and the receiver The connection part of the part 110 may be located above the first limiter 111 .

Similarly, in order for the function of the accumulator unit 120 to operate normally even when the volume of the accumulator unit 120 is minimal because the barrier 130 is in contact with the second limiter 121, the receiver outlet passage 75 and the accumulator unit ( 120) may be located lower than the second limiter 121.

At least one of a low pressure gas passage 72 , a discharge passage 79 , a steam inlet bypass passage 76 , and an oil passage 84 may be connected to the accumulator unit 120 . In this case, the low-pressure gas passage 72 connected to the accumulator unit 120 may mean a suction passage.

In order to discharge gaseous refrigerant without discharging liquid refrigerant through the discharge passage 79 , one end of the discharge passage 79 may be located at an upper side within the accumulator unit 120 . The other end opposite to the one end of the discharge passage 79 may be located outside the casing 101 .

In order for the accumulator unit 120 to function normally even when the volume of the accumulator unit 120 is minimal due to the barrier 130 being in contact with the second limiter 121, one end of the discharge passage 79 is disposed in the casing 101. ) may be located below the second limiter 121 in the interior. In addition, the low pressure gas flow path 72 and the steam inlet bypass flow path 76 may be connected to the accumulator unit 120 at the lower side of the second limiter 121 .

The oil passage 84 may be connected to the bottom of the accumulator unit 120 . This is to flow the oil accumulated below the inside of the accumulator part.

According to a preferred embodiment of the present invention, the receiver-integrated accumulator 100 has the advantage of being able to combine the functions of a receiver and an accumulator.

In addition, since each capacity of the receiver unit 110 and the accumulator unit 120 can be varied, there is an advantage in that the amount of refrigerant accommodated in each unit can be organically adjusted.

In addition, the movable range of the barrier 130 is limited by the first limiter 111 and the second limiter 121 so that the minimum capacity of the receiver unit 110 and the accumulator unit 120 can be guaranteed. .

8 is a control block diagram of an air conditioning system having a receiver-integrated accumulator according to an embodiment of the present invention.

Referring to FIG. 8 , the air conditioning system 1 may include a controller 50. In addition, the air conditioning system 1 may include a temperature sensor 90 and a pressure sensor 47 . The controller 50 may receive values measured by the temperature sensor 90 and the pressure sensor 47 .

The temperature sensor 90 includes the outdoor heat exchanger temperature sensors 94 and 95, the outdoor heat exchanger outlet temperature sensor 96, the supercooling device inlet temperature sensor 97, the supercooling device outlet temperature sensor 98, and the intake temperature sensor 99. ), and at least one of the discharge temperature sensors 92 and 93.

The outdoor heat exchanger temperature sensors 94 and 95 may measure the temperature of the outdoor heat exchangers 63 and 65 .

The outdoor heat exchanger outlet temperature sensor 96 may measure the temperature of the refrigerant condensed in the outdoor heat exchangers 63 and 65 .

The supercooling device inlet temperature sensor 97 can measure the temperature of the refrigerant flowing into the supercooling device 67, and the supercooling device outlet temperature sensor 98 can measure the temperature of the refrigerant flowing out of the supercooling device 67. there is.

The suction temperature sensor 99 may measure the temperature of the refrigerant sucked into the compressors 51 and 52 or the accumulator unit 120 .

The discharge temperature sensors 92 and 93 may measure the temperature of the refrigerant discharged from the compressors 51 and 52 .

The pressure sensor 47 may include a high pressure sensor 48 and a low pressure sensor 49 .

The high-pressure sensor 48 may measure the pressure of the refrigerant compressed and discharged from the compressors 51 and 52 . The low pressure sensor 49 may measure the pressure of the refrigerant sucked into the compressors 51 and 52 .

On the other hand, the control unit 50 includes the compressors 51 and 52, the main valve device 60, the sub valve device 61, the refrigerant inlet control valve 80, the refrigerant outlet control valve 81, the bypass valve 85 , the oil return valve 96 can be controlled. The controller 50 may control additional components of the air conditioning system 1 in addition to this.

The controller 50 can turn on/off the compressors 51 and 52 and adjust the operating frequencies of the compressors 51 and 52 .

The control unit 50 may control the main valve device 60 to adjust the connection relationship between the flow passages 62 , 72 , and 91 connected to the main valve device 60 . Also, the control unit 50 may control the sub-valve device 61 to adjust the connection relationship between the passages 62 , 71 , and 72 connected to the sub-valve device 61 . Since the detailed connection relationship of each flow path has been described above, it will be omitted.

The controller 50 may open or close the refrigerant inlet control valve 80, the refrigerant outlet control valve 81, the bypass valve 85, and the oil return valve 96. The control unit 50 may also be able to adjust the opening degree of each valve.

For example, the controller 50 may open the refrigerant inflow control valve 80 and close the refrigerant outflow control valve 81 when the operation of the air conditioning system 1 is stopped.

9 is a flowchart illustrating an example of a control method for adjusting the amount of circulating refrigerant during a cooling operation.

Referring to FIG. 9 , the control method of the air conditioning system 1 during the operation of the entire cooling chamber or the simultaneous operation of the main body of cooling includes the detection steps S1 and S3 of detecting an excessive or insufficient amount of circulating refrigerant and supplying the refrigerant to the receiver unit 110. A refrigerant control step (S2, S4) of introducing or discharging the refrigerant of the receiver unit 110 may be included.

The controller 50 may calculate the amount of circulating refrigerant by measuring the degree of supercooling of the air conditioning system 1 . The controller 50 may be able to calculate the optimal amount of circulating refrigerant for each range of degree of undercooling.

The degree of subcooling of the air conditioning system 1 may be calculated according to the detected temperature of the outdoor heat exchanger outlet temperature sensor 96 and the detected temperature of the supercooling device outlet temperature sensor 98, and the control unit 50 calculates the calculated degree of subcooling The optimal refrigerant circulation amount can be calculated according to

The controller may determine whether the calculated degree of undercooling is higher than the first set temperature T1 (S1).

If the degree of undercooling is higher than the first set temperature T1, this may mean that the amount of circulating refrigerant in the air conditioning system 1 is excessive. The controller 50 may open the refrigerant inlet control valve 80 and close the refrigerant outlet control valve 81 (S2).

The control unit may determine whether the calculated degree of undercooling is lower than the second set temperature T2 lower than the first set temperature T1 (S3)

If the degree of undercooling is lower than the second set temperature T2, this may mean that the amount of refrigerant circulating in the air conditioning system 1 is insufficient. The controller 50 may close the refrigerant inlet control valve 80 and open the refrigerant outlet control valve 81 (S4).

10 is a flowchart illustrating an example of a control method for adjusting the amount of circulating refrigerant during a heating operation.

Referring to FIG. 10 , the control method of the air conditioning system 1 during operation of the entire heating room or simultaneous operation of the main heating unit includes the detection steps S5 and S7 of detecting an excessive or insufficient amount of circulating refrigerant and supplying the refrigerant to the receiver unit 110. A refrigerant control step (S6, S8) of introducing or discharging the refrigerant from the receiver unit 110 may be included.

The controller 50 may calculate the amount of circulating refrigerant by measuring the high pressure of the air conditioning system 1 . The control unit 50 may be able to calculate an optimal amount of circulating refrigerant for each high pressure range.

The control unit 50 may calculate an optimal refrigerant circulation amount according to the pressure detected by the high pressure sensor 48 .

The controller may determine whether the measured pressure of the high pressure sensor 48 is higher than the first set pressure P1 (S5).

If the measured pressure of the high pressure sensor 48 is higher than the first set pressure P1, it may mean that the amount of refrigerant circulating in the air conditioning system 1 is excessive. The controller 50 may open the refrigerant inlet control valve 80 and close the refrigerant outlet control valve 81 (S6).

The control unit may determine whether the measured pressure of the high pressure sensor 48 is lower than the second set pressure P2 lower than the first set pressure P1 (S7)

If the measured pressure of the high pressure sensor 48 is lower than the second set pressure P2, this may mean that the amount of refrigerant circulating in the air conditioning system 1 is insufficient. The controller 50 may close the refrigerant inlet control valve 80 and open the refrigerant outlet control valve 81 (S6).

The above description is merely an example of the technical idea of the present invention, and various modifications and variations can be made to those skilled in the art without departing from the essential characteristics of the present invention.

Therefore, the embodiments disclosed in the present invention are not intended to limit the technical idea of the present invention, but to explain, and the scope of the technical idea of the present invention is not limited by these embodiments.

The protection scope of the present invention should be construed according to the claims below, and all technical ideas within the equivalent range should be construed as being included in the scope of the present invention.

74: receiver inlet passage 75: receiver outlet passage
100: receiver integrated accumulator 101: casing
110: receiver unit 120: accumulator unit
130: barrier 131: partition plate
132: piston ring 111: first limiter
121: second limiter

Claims (12)

A casing in which an internal space having a constant cross-sectional area is formed;
a barrier in contact with the inner surface of the casing and movable inside the casing;
a receiver unit located on one side of the inside of the casing and having a receiver inlet passage and a receiver outlet passage connected thereto; and
An accumulator part located on the other side of the casing partitioned from the receiver part by the barrier and communicating with the receiver part and the receiver outlet passage,
The barrier is
a partition plate partitioning the receiver unit and the accumulator unit; and
A piston ring provided on the circumference of the partition plate, in contact with the inner surface of the casing, and maintaining airtightness of the receiver part and the accumulator part,
A receiver-integrated accumulator in which volumes of the receiver unit and the accumulator unit change as the barrier moves. According to claim 1,
a first limiter formed in the receiver and protruding inward of the casing; and
A second limiter formed in the accumulator unit, protruding toward the inside of the casing, and spaced apart from the first limiter by a predetermined distance;
The barrier is a receiver-integrated accumulator that is movable between the first limiter and the second limiter. delete According to claim 1,
The receiver-integrated accumulator, wherein the volume of the receiver part is equal to or smaller than the volume of the accumulator part. According to claim 2,
When the barrier is in contact with the second limiter, the receiver integrated accumulator has the same volume as the accumulator. According to claim 2,
The receiver unit is located on the upper side of the accumulator,
The barrier is a receiver-integrated accumulator capable of moving up and down. According to claim 6,
One end of the receiver outlet passage is connected to the receiver part above the first limiter,
The other end of the receiver outlet passage is connected to the accumulator unit at a lower side than the second limiter. According to claim 6,
A discharge passage through which gaseous refrigerant is discharged is connected to the accumulator unit,
One end of the discharge passage is located below the second limiter inside the casing,
The receiver-integrated accumulator of claim 1 , wherein the other end opposite to the one end of the discharge passage is located outside the casing. According to claim 6,
A suction flow path and a steam inlet bypass flow path are connected to the accumulator unit,
The suction flow path and the steam inlet bypass flow path are connected to the accumulator unit at the lower side of the second limiter. According to claim 1,
A receiver-integrated accumulator in which a refrigerant control valve is installed in at least one of the receiver inlet passage and the receiver outlet passage. According to claim 10,
A refrigerant inlet control valve is installed in the receiver inlet passage,
A refrigerant outflow control valve is installed in the receiver outlet passage,
The refrigerant inlet control valve and the refrigerant outlet control valve operate opposite to each other. According to claim 1,
A receiver-integrated accumulator having an oil flow path connected to the bottom of the accumulator unit.

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