Patent Application
20250164168
The present disclosure relates to a heat source unit and a refrigeration apparatus.
The refrigeration apparatus described in Patent Document 1 is provided with a heat source unit including a compression unit, a heat-source-side heat exchanger, and a subcooling heat exchanger. The refrigerant compressed by the compression unit dissipates heat in the heat-source-side heat exchanger and then flows through the first flow path of the subcooling heat exchanger. The subcooling heat exchanger exchanges heat between the refrigerant flowing through the first flow path and the refrigerant decompressed by the subcooling-side decompression valve and then flowing through the second flow path. Accordingly, the refrigerant flowing though the first flow path is cooled, and the degree of subcooling of the refrigerant is increased.
A first aspect is directed to a heat source unit including: a refrigerant circuit including a compression unit, a heat-source-side heat exchanger, a subcooling-side decompression valve, and a subcooling heat exchanger having a first flow path and a second flow path, where the first flow path is a flow path through which a refrigerant having dissipated heat in the heat-source-side heat exchanger flows, and where the second flow path is a flow path through which a refrigerant passing through the first flow path and then decompressed by the subcooling-side decompression valve flows; and a controller configured to control the subcooling-side decompression valve according to a degree of subcooling of a refrigerant flowing out of the first flow path of the subcooling heat exchanger. Based on the fact that an opening degree of the subcooling-side decompression valve becomes larger, the controller determines whether there is a shortage of a refrigerant in the refrigerant circuit.
Embodiments of the present disclosure will be described in detail below with reference to the drawings. The present disclosure is not limited to the embodiments shown below, and various changes can be made within the scope without departing from the technical concept of the present disclosure. Since each of the drawings is intended to illustrate the present disclosure conceptually, dimensions, ratios, or numbers may be exaggerated or simplified as necessary for the sake of ease of understanding.
A refrigeration apparatus (1) according to an embodiment performs cooling of an object to be cooled and air-conditioning of an indoor space in parallel. The object to be cooled herein includes air in facilities such as a refrigerator, a freezer, and a show case. Hereinafter, such facilities are each referred to as a refrigeration facility.
As illustrated in
The refrigeration apparatus (1) includes four connection pipes (2, 3, 4, 5) for connecting the heat source unit (10), the air-conditioning unit (60), and the refrigeration-facility unit (70). In the refrigeration apparatus (1), the heat source unit (10), the air-conditioning unit (60), and the refrigeration-facility unit (70) are connected by the connection pipes (2, 3, 4, 5), thereby forming a refrigerant circuit (6).
The refrigerant circuit (6) is filled with a refrigerant. The refrigerant circuit (6) circulates the refrigerant to perform a refrigeration cycle. The refrigerant of this embodiment is carbon dioxide. The refrigerant circuit (6) performs the refrigeration cycle so that the refrigerant has a pressure equal to or greater than a critical pressure. The refrigerant may be a natural refrigerant other than carbon dioxide.
The four connection pipes (2, 3, 4, 5) include a first liquid connection pipe (2), a first gas connection pipe (3), a second liquid connection pipe (4), and a second gas connection pipe (5). The first liquid connection pipe (2) and the first gas connection pipe (3) correspond to the air-conditioning unit (60). The second liquid connection pipe (4) and the second gas connection pipe (5) correspond to the refrigeration-facility unit (70).
The heat source unit (10) includes a heat source circuit (11) and an outdoor fan (12). The heat source circuit (11) includes a compression unit (20), an outdoor heat exchanger (24), and a gas-liquid separator (25). The heat source circuit (11) includes a first outdoor expansion valve (26) and a second outdoor expansion valve (27). The heat source circuit (11) also includes a subcooling heat exchanger (28) and an intercooler (29).
The heat source circuit (11) includes four shut-off valves (13, 14, 15, 16). The four shut-off valves include a first gas shut-off valve (13), a first liquid shut-off valve (14), a second gas shut-off valve (15), and a second liquid shut-off valve (16).
The first gas shut-off valve (13) is connected with the first gas connection pipe (3). The first liquid shut-off valve (14) is connected with the first liquid connection pipe (2). The second gas shut-off valve (15) is connected with the second gas connection pipe (5). The second liquid shut-off valve (16) is connected with the second liquid connection pipe (4).
The heat source unit (10) includes a flow path switching mechanism (30). In the piping system diagram of the refrigerant circuit in e.g.,
The compression unit (20) compresses a refrigerant. The compression unit (20) includes a first compressor (21), a second compressor (22), and a third compressor (23). The compression unit (20) performs an operation for compressing a refrigerant in a single stage and an operation for compressing a refrigerant in two stages.
The first compressor (21) is a refrigeration-facility compressor corresponding to the refrigeration-facility unit (70). The first compressor (21) is an example of a first compression element. The second compressor (22) is an air-conditioning compressor corresponding to the air-conditioning unit (60). The second compressor (22) is an example of a second compression element. The first compressor (21) and the second compressor (22) are lower-stage compressors. The first compressor (21) and the second compressor (22) are connected in parallel.
The third compressor (23) is a higher-stage compressor. The third compressor (23) is connected in series to the first compressor (21). The third compressor (23) is connected in series to the second compressor (22).
The first compressor (21), the second compressor (22), and the third compressor (23) are rotary-type compressors, each of which includes a compression mechanism driven by a motor. The first compressor (21), the second compressor (22), and the third compressor (23) are variable-capacity-type compressors. The number of rotations of the motors of the first compressor (21), the second compressor (22), and the third compressor (23) is adjusted by an inverter device. In other words, the operating capacities of the first compressor (21), the second compressor (22), and the third compressor (23) are adjustable.
The first compressor (21) is connected with a first suction pipe (21a) and a first discharge pipe (21b). The second compressor (22) is connected with a second suction pipe (22a) and a second discharge pipe (22b). The third compressor (23) is connected with a third suction pipe (23a) and a third discharge pipe (23b).
The heat source circuit (11) includes an intermediate flow path (18). The intermediate flow path (18) connects the discharge portions of the first compressor (21) and the second compressor (22) with the suction portion of the third compressor (23). The intermediate flow path (18) includes a first discharge pipe (21b), a second discharge pipe (22b), and a third suction pipe (23a).
The outdoor heat exchanger (24) is an example of a heat-source-side heat exchanger.
The outdoor heat exchanger (24) is a fin-and-tube air heat exchanger. The outdoor fan (12) is disposed near the outdoor heat exchanger (24). The outdoor fan (12) transfers outdoor air. The outdoor heat exchanger exchanges heat between a refrigerant flowing therethrough and outdoor air transferred from the outdoor fan (12).
The heat source circuit (11) includes a liquid-side flow path (40). The liquid-side flow path (40) is provided between the liquid-side end of the outdoor heat exchanger (24) and the two liquid shut-off valves (14, 16). The liquid-side flow path (40) includes first to fifth pipes (40a, 40b, 40c, 40d, 40e).
One end of the first pipe (40a) is connected to the liquid-side end of the outdoor heat exchanger (24). The other end of the first pipe (40a) is connected to the top of the gas-liquid separator (25). One end of the second pipe (40b) is connected to the bottom of the gas-liquid separator (25). The other end of the second pipe (40b) is connected to the second liquid shut-off valve (16). One end of the third pipe (40c) is connected to an intermediate portion of the second pipe (40b). The other end of the third pipe (40c) is connected to the first liquid shut-off valve (14). One end of the fourth pipe (40d) is connected to the first pipe (40a) between the first outdoor expansion valve (26) and the gas-liquid separator (25). The other end of the fourth pipe (40d) is connected to an intermediate portion of the third pipe (40c). One end of the fifth pipe (40e) is connected to the first pipe (40a) between the outdoor heat exchanger (24) and the first outdoor expansion valve (26). The other end of the fifth pipe (40e) is connected to the second pipe (40b) between the gas-liquid separator (25) and the junction between the second pipe (40b) and the third pipe (40c).
The first outdoor expansion valve (26) is provided in the first pipe (40a). The first outdoor expansion valve (26) is provided in the first pipe (40a) between the liquid-side end of the outdoor heat exchanger (24) and the junction between the first pipe (40a) and the fourth pipe (40d). The second outdoor expansion valve (27) is provided in the fifth pipe (40e). The first outdoor expansion valve (26) and the second outdoor expansion valve (27) are expansion valves of which the opening degrees are adjustable. The first outdoor expansion valve (26) and the second outdoor expansion valve (27) are electronic expansion valves of which the opening degrees are adjusted based on pulse signals.
The gas-liquid separator (25) is a hermetically closed container that stores a refrigerant. The gas-liquid separator (25) separates the refrigerant into a gas refrigerant and a liquid refrigerant. A gas layer and a liquid layer are formed inside the gas-liquid separator (25). The gas layer is formed near the top of the gas-liquid separator (25). The liquid layer is formed near the bottom of the gas-liquid separator (25).
The heat source circuit (11) includes a venting pipe (41). One end of the venting pipe (41) is connected to the top of the gas-liquid separator (25). The other end of the venting pipe (41) is connected to the intermediate flow path (18). The venting pipe (41) sends the gas refrigerant in the gas-liquid separator (25) to the intermediate flow path (18).
The venting pipe (41) is provided with a venting valve (42). The venting valve (42) is an expansion valve of which the opening degree is adjustable. The venting valve (42) is an electronic expansion valve of which the opening degree is adjusted based on pulse signals.
The subcooling heat exchanger (28) includes a first flow path (28a) as a high-pressure flow path and a second flow path (28b) as a low-pressure flow path. The subcooling heat exchanger (28) exchanges heat between the refrigerant in the first flow path (28a) and the refrigerant in the second flow path (28b). In other words, the subcooling heat exchanger (28) cools the refrigerant flowing in the first flow path (28a) by the refrigerant flowing in the second flow path (28b).
The second flow path (28b) is a part of the injection flow path (43). The injection flow path (43) includes an upstream flow path (44) and a downstream flow path (45).
One end of the upstream flow path (44) is connected to a portion of the third pipe (40c) upstream of the junction with the fourth pipe (40d). The other end of the upstream flow path (44) is connected to the inflow end of the second flow path (28b). The upstream flow path (44) is provided with an injection valve (46) as a subcooling-side decompression valve. The injection valve (46) is an expansion valve of which the opening degree is adjustable. The injection valve (46) is an electronic expansion valve of which the opening degree is adjusted based on pulse signals.
One end of the downstream flow path (45) is connected to the outflow end of the second flow path (28b). The other end of the downstream flow path (45) is connected to the intermediate flow path (18).
The intercooler (29) is provided in the intermediate flow path (18). The intercooler (29) is a fin-and-tube air heat exchanger. A cooling fan (29a) is disposed near the intercooler (29). The intercooler (29) exchanges heat between the refrigerant flowing therethrough and the outdoor air transferred from the cooling fan (29a).
The heat source circuit (11) includes an oil separation circuit. The oil separation circuit includes an oil separator (50), a first oil return pipe (51), and a second oil return pipe (52).
The oil separator (50) is connected to the third discharge pipe (23b). The oil separator (50) separates oil from the refrigerant discharged from the compression unit (20). Inflow ends of the first oil return pipe (51) and the second oil return pipe (52) communicate with the oil separator (50). An outflow end of the first oil return pipe (51) is connected to the intermediate flow path (18). The first oil return pipe (51) is provided with a first oil level control valve (53).
An outflow portion of the second oil return pipe (52) branches into a first branch pipe (52a) and a second branch pipe (52b). The first branch pipe (52a) is connected to an oil reservoir of the first compressor (21). The second branch pipe (52b) is connected to an oil reservoir of the second compressor (22). The first branch pipe (52a) is provided with a second oil level control valve (54). The second branch pipe (52b) is provided with a third oil level control valve (55).
The heat source circuit (11) includes a first bypass pipe (56), a second bypass pipe (57), and a third bypass pipe (58). The first bypass pipe (56) is associated with the first compressor (21). The second bypass pipe (57) is associated with the second compressor (22). The third bypass pipe (58) is associated with the third compressor (23).
Specifically, the first bypass pipe (56) directly connects the first suction pipe (21a) and the first discharge pipe (21b) together. The second bypass pipe (57) directly connects the second suction pipe (22a) and the second discharge pipe (22b) together. The third bypass pipe (58) directly connects the third suction pipe (23a) and the third discharge pipe (23b) together.
The heat source circuit (11) includes a plurality of check valves. The plurality of check valves includes first to twelfth check valves (CV1 to CV12). The check valves (CV1 to CV12) allow the flow of a refrigerant in the direction of the arrow in
The first check valve (CV1) and the second check valve (CV2) are provided in a flow path switching mechanism (30) described in detail later.
The third check valve (CV3) is provided in the third discharge pipe (23b). The fourth check valve (CV4) is provided in the first pipe (40a). The fifth check valve (CV5) is provided in the third pipe (40c). The sixth check valve (CV6) is provided in the fourth pipe (40d). The seventh check valve (CV7) is provided in the fifth pipe (40e). The eighth check valve (CV8) is provided in the first bypass pipe (56). The ninth check valve (CV9) is provided in the second bypass pipe (57). The tenth check valve (CV10) is provided in the third bypass pipe (58). The eleventh check valve (CV11) is provided in the first discharge pipe (21b). The twelfth check valve (CV12) is provided in the second discharge pipe (22b).
The air-conditioning unit (60) is a first utilization unit installed indoors. The air-conditioning unit (60) includes an indoor circuit (61) and an indoor fan (62). The liquid-side end of the indoor circuit (61) is connected with the first liquid connection pipe (2). The gas-side end of the indoor circuit (61) is connected with the first gas connection pipe (3).
The indoor circuit (61) includes an indoor expansion valve (63) and an indoor heat exchanger (64) in the sequence from the liquid-side end to the gas-side end. The indoor expansion valve (63) is an expansion valve of which the opening degree is adjustable. The indoor expansion valve (63) is an electronic expansion valve of which the opening degree is adjusted based on pulse signals.
The indoor heat exchanger (64) is a fin-and-tube air heat exchanger. The indoor heat exchanger (64) is an example of a first utilization-side heat exchanger. The indoor fan (62) is disposed near the indoor heat exchanger (64). The indoor fan (62) transfers indoor air. The indoor heat exchanger (64) exchanges heat between the refrigerant flowing therethrough and the indoor air transferred by the indoor fan (62).
The refrigeration-facility unit (70) is a second utilization unit that cools its internal space. The refrigeration-facility unit (70) includes a refrigeration-facility circuit (71) and a refrigeration-facility fan (72). The liquid-side end of the refrigeration-facility circuit (71) is connected with the second liquid connection pipe (4). The gas-side end of the refrigeration-facility circuit (71) is connected with the second gas connection pipe (5).
The refrigeration-facility circuit (71) includes a refrigeration-facility expansion valve (73) and a refrigeration-facility heat exchanger (74) in the sequence from the liquid-side end to the liquid-side end. The refrigeration-facility expansion valve (73) is an expansion valve of which the opening degree is adjustable. The refrigeration-facility expansion valve (73) is an electronic expansion valve of which the opening degree is adjusted based on pulse signals.
The refrigeration-facility heat exchanger (74) is a fin-and-tube air heat exchanger. The refrigeration-facility heat exchanger (74) is an example of a second utilization-side heat exchanger. The refrigeration-facility fan (72) is disposed near the refrigeration-facility heat exchanger (74). The refrigeration-facility fan (72) transfers inside air. The refrigeration-facility heat exchanger (74) exchanges heat between the refrigerant flowing therethrough and the inside air transferred by the refrigeration-facility fan (72).
The evaporation temperature of the refrigeration-facility heat exchanger (74) is lower than the evaporation temperature of the indoor heat exchanger (64).
The flow path switching mechanism (30) is provided in the heat source circuit (11). As illustrated in
The first port (P1) is connected with the discharge portion of the first compressor (21) and the discharge portion of the second compressor (22). The discharge portion of the first compressor (21) is connected with the first port (P1) via a first discharge line (L1). The first discharge line (L1) is a flow path, one end of which is connected with the discharge portion of the first compressor (21) and the other end of which is connected with the first port (P1). In other words, the first discharge line (L1) is a flow path extending from the discharge portion of the first compressor (21) to the first port (P1).
The discharge portion of the second compressor (22) is connected with the first port (P1) via a second discharge line (L2). The second discharge line (L2) is a flow path, one end of which is connected with the discharge portion of the second compressor (22) and the other end of which is connected with the first port (P1). In other words, the second discharge line (L2) is a flow path extending from the discharge portion of the second compressor (22) to the first port (P1).
The second port (P2) is connected with the suction portion of the second compressor (22). The second port (P2) is not connected with the suction portion of the first compressor (21). The second port (P2) is connected with the suction portion of the second compressor (22) via a suction line (L3). The suction line (L3) is a flow path, one end of which is connected with the suction portion of the second compressor (22) and the other end of which is connected with the second port (P2). In other words, the suction line (L3) is a flow path extending from the suction portion of the second compressor (22) to the second port (P2).
The third port (P3) is connected with the gas end portion of the indoor heat exchanger (64). The third port (P3) is connected with the gas end portion of the indoor heat exchanger (64) via a first gas line (L4). The first gas line (L4) is a flow path, one end of which is connected with the indoor heat exchanger (64) and the other end of which is connected with the third port (P3). In other words, the first gas line (L4) is a flow path extending from the gas end portion of the indoor heat exchanger (64) to the third port (P3).
The fourth port (P4) is connected with the gas end portion of the outdoor heat exchanger (24). The fourth port (P4) is connected with the gas end portion of the outdoor heat exchanger (24) via a second gas line (L5). The second gas line (L5) is a flow path, one end of which is connected with the gas end portion of the outdoor heat exchanger (24) and the other end of which is connected with the fourth port (P4). The second gas line (L5) is a flow path extending from the gas end portion of the outdoor heat exchanger (24) to the fourth port (P4).
The first discharge line (L1), the second discharge line (L2), the suction line (L3), the first gas line (L4), and the second gas line (L5) refer to the flow paths including pipes and elements connected to the pipes.
As schematically shown in
As illustrated in
The first opening/closing mechanism (81) includes a plurality of first on-off valves (V1). The first switching flow path (31) is provided with two or more first on-off valves (V1) provided in parallel. The first switching flow path (31) of this example is provided with seven first on-off valves (V1). Each first branch flow path (31a) is provided with one first on-off valve (V1). The plurality of first on-off valves (V1) include a first expansion valve (91) and a first electromagnetic on-off valve (92). The number of the first expansion valves (91) is one, and the number of the first electromagnetic on-off valves (92) is six. The first expansion valve (91) is an electronic expansion valve of which the opening degree is variable.
The second opening/closing mechanism (82) includes a plurality of second on-off valves (V2). The second switching flow path (32) is provided with two or more second on-off valves (V2) provided in parallel. The second switching flow path (32) of this example is provided with seven second on-off valves (V2). Each second branch flow path (32a) is provided with one second on-off valve (V2). The plurality of second on-off valves (V2) include a second expansion valve (93) and a second electromagnetic on-off valve (94). The number of the second expansion valves (93) is one, and the number of the second electromagnetic on-off valves (94) is six. The second expansion valve (93) is an electronic expansion valve of which the opening degree is variable.
The third opening/closing mechanism (83) includes a plurality of third on-off valves (V3). The third switching flow path (33) is provided with two or more third on-off valves (V3) provided in parallel. The third switching flow path (33) of this example is provided with four third on-off valves (V3). Each third branch flow path (33a) is provided with one third on-off valve (V3). The third on-off valves (V3) are electromagnetic on-off valves.
The fourth opening/closing mechanism (84) includes one fourth on-off valve (V4). The fourth switching flow path (34) is provided with the fourth on-off valve (V4). The fourth on-off valve (V4) is an electromagnetic on-off valve.
The first on-off valve (V1), the second on-off valve (V2), the third on-off valve (V3), and the fourth on-off valve (V4) may be simply referred to as the on-off valve (V) as shown in
The flow path switching mechanism (30) includes check valves (CV1, CV2). Specifically, the fourth switching flow path (34) is provided with the first check valve (CV1). The first switching flow path (31) is provided with the second check valve (CV2).
The first check valve (CV1) in the fourth switching flow path (34) restricts the flow of a refrigerant from the second port (P2) to the fourth port (P4). More precisely, the first check valve (CV1) in the fourth switching flow path (34) allows the flow of a refrigerant from the fourth port (P4) to the second port (P2) and disallows the flow of a refrigerant from the second port (P2) to the fourth port (P4). The first check valve (CV1) in the fourth switching flow path (34) is provided closer to the second port (P2) than the on-off valve (V) is.
The second check valve (CV2) in the first switching flow path (31) restricts the flow of a refrigerant from the third port (P3) to the first port (P1). More precisely, the second check valve (CV2) in the first switching flow path (31) allows the flow of a refrigerant from the first port (P1) to the third port (P3) and disallows the flow of a refrigerant from the third port (P3) to the first port (P1). The second check valve (CV2) is provided in the main flow path (31b) of the first switching flow path (31). The main flow path (31b) is a flow path connected with the ends of the plurality of first branch flow paths (31a). The second check valve (CV2) in the first switching flow path (31) is provided closer to the third port (P3) than the on-off valve (V) is.
As illustrated in
The refrigerant pressure sensors include a high pressure sensor (101), an intermediate pressure sensor (102), a first suction pressure sensor (103), a second suction pressure sensor (104), and a liquid-side pressure sensor (105). The high pressure sensor (101) is provided in the third discharge pipe (23b). The high pressure sensor (101) detects the pressure of a refrigerant on the discharge side of the compression unit (20), in other words, detects the high pressure of the refrigerant circuit (6). The intermediate pressure sensor (102) is provided in the third suction pipe (23a). The intermediate pressure sensor (102) detects the pressure of a refrigerant between the lower-stage compressor and the higher-stage compressor, in other words, detects the intermediate pressure of the refrigerant circuit (6). The first suction pressure sensor (103) is provided in the first suction pipe (21a). The first suction pressure sensor (103) detects the pressure of a refrigerant on the suction side of the first compressor (21). The second suction pressure sensor (104) is provided in the second suction pipe (22a). The second suction pressure sensor (104) detects the pressure of a refrigerant on the suction side of the second compressor (22).
The liquid-side pressure sensor (105) is provided in the liquid-side flow path (40). Specifically, the liquid-side pressure sensor (105) is provided in the second pipe (40b). The liquid-side pressure sensor (105) detects the pressure corresponding to the internal pressure of the gas-liquid separator (25). The liquid-side pressure sensor (105) detects the pressure corresponding to the pressure of the refrigerant in the first flow path (28a).
The refrigerant temperature sensor includes a first discharge temperature sensor (111), a first suction temperature sensor (112), a second discharge temperature sensor (113), a second suction temperature sensor (114), a third discharge temperature sensor (115), a third suction temperature sensor (116), a liquid-side temperature sensor (117), an injection-side temperature sensor (118), and a heat-source-side temperature sensor (119). The first discharge temperature sensor (111) is provided in the first discharge pipe (21b) and detects the temperature of the refrigerant discharged from the first compressor (21). The first suction temperature sensor (112) is provided in the first suction pipe (21a) and detects the temperature of the refrigerant sucked into the first compressor (21). The second discharge temperature sensor (113) is provided in the second discharge pipe (22b) and detects the temperature of the refrigerant discharged from the second compressor (22). The second suction temperature sensor (114) is provided in the second suction pipe (22a) and detects the temperature of the refrigerant sucked into the second compressor (22). The third discharge temperature sensor (115) is provided in the third discharge pipe (23b) and detects the temperature of the refrigerant discharged from the third compressor (23). The third suction temperature sensor (116) is provided in the third suction pipe (23a) and detects the temperature of the refrigerant sucked into the third compressor (23).
The liquid-side temperature sensor (117) is provided in the liquid-side flow path (40). Specifically, the liquid-side temperature sensor (117) is provided on the outflow side of the first flow path (28a) of the subcooling heat exchanger (28) in the liquid-side flow path (40). More specifically, the liquid-side temperature sensor (117) is provided in the liquid-side flow path (40) between the outflow end of the first flow path (28a) and the inflow end of the injection flow path (43). The liquid-side temperature sensor (117) detects the temperature of the refrigerant flowing out of the first flow path (28a).
The injection-side temperature sensor (118) is provided in the downstream flow path (45) of the injection flow path (43). In other words, the injection-side temperature sensor (118) is provided on the outflow side of the second flow path (28b) of the subcooling heat exchanger (28). The injection-side temperature sensor (118) detects the temperature of the refrigerant flowing out of the second flow path (28b).
The heat-source-side temperature sensor (119) is provided in the heat transfer tube of the outdoor heat exchanger (24). The heat-source-side temperature sensor (119) is provided at the liquid-side end of the outdoor heat exchanger (24). The heat-source-side temperature sensor (119) detects the temperature of the refrigerant at the liquid-side end of the outdoor heat exchanger (24).
The air temperature sensor includes an outdoor air temperature sensor (121). The outdoor air temperature sensor (121) detects the temperature of outdoor air.
As illustrated in
As illustrated in
The controller (130) receives control commands and detection signals from the sensors. The controller (130) controls each device of the refrigeration apparatus (1). Specifically, the controller (130) controls ON/OFF of the first compressor (21), the second compressor (22), and the third compressor (23). The controller (130) regulates the capacities of the first compressor (21), the second compressor (22), and the third compressor (23) (more precisely, the number of revolutions of the motor). The controller (130) controls ON/OFF of each fan (12, 62, 72). The controller (130) adjusts the opening degree of each expansion valve (26, 27, 63). The controller (130) switches the on/off state of each valve (42, 43). The controller (130) switches the on/off state of each on-off valve (V) and adjusts the opening degree of each on-off valve (V).
The controller (130) determines the degree of subcooling (sc) of the refrigerant flowing out of the first flow path (28a) of the subcooling heat exchanger (28). The controller (130) determines the degree of subcooling (sc) based on the values detected by the liquid-side pressure sensor (105) and the liquid-side temperature sensor (117). Specifically, the controller (130) determines the difference between the saturated temperature corresponding to the pressure detected by the liquid-side pressure sensor (105) and the temperature detected by the liquid-side temperature sensor (117) as the degree of subcooling (sc). The liquid-side pressure sensor (105) and the liquid-side temperature sensor (117) constitute a degree-of-subcooling determination unit for determining the degree of subcooling (sc).
The controller (130) controls the opening degree of the injection valve (46) according to the degree of subcooling (sc). The controller (130) controls the opening degree of the injection valve (46) so that the current degree of subcooling (sc) becomes the target degree of subcooling (Tsc). The control of the degree of subcooling will be described in detail later.
When controlling the degree of subcooling, the controller (130) determines whether there is a shortage of a refrigerant in the refrigerant circuit (6). Here, the shortage of a refrigerant in the refrigerant circuit (6) means that the amount of a refrigerant in the refrigerant circuit (6) is smaller than a predetermined amount. If there is a shortage of a refrigerant in the refrigerant circuit (6), a desired refrigeration cycle fails to be executed, and the refrigeration apparatus (1) exhibits lower refrigerating capacity.
Based on the opening degree of the injection valve (46), the controller (130) determines whether there is a shortage of a refrigerant in the refrigerant circuit (6). Under the condition that the opening degree of the injection valve (46) is equal to or greater than a predetermined value, the controller (130) determines that there is a shortage of a refrigerant in the refrigerant circuit (6). The detail of this determination will be described later.
The controller (130) includes an alerting unit (134) that alerts that there is a shortage of a refrigerant in the refrigerant circuit (6). As illustrated in
The operation of the refrigeration apparatus (1) will be described. The operation of the refrigeration apparatus (1) includes a refrigeration-facility operation, a cooling operation, a cooling and refrigeration-facility operation, a heating operation, a heating and refrigeration-facility operation, and a defrosting operation. The heating and refrigeration-facility operation includes a first heating and refrigeration-facility operation, a second heating and refrigeration-facility operation, and a third heating and refrigeration-facility operation.
In the refrigeration-facility operation, the refrigeration-facility unit (70) cools inside air, and the air-conditioning unit (60) is stopped. In the cooling operation, the refrigeration-facility unit (70) is stopped, and the air-conditioning unit (60) performs cooling of the indoor space. In the cooling and refrigeration-facility operation, the refrigeration-facility unit (70) cools inside air, and the air-conditioning unit (60) performs cooling of the indoor space. In the heating operation, the refrigeration-facility unit (70) is stopped, and the air-conditioning unit (60) performs heating of the indoor space. In the heating and refrigeration-facility operation, the refrigeration-facility unit (70) cools inside air, and the air-conditioning unit (60) performs heating of the indoor space. In the defrosting operation, the frost on the outdoor heat exchanger (24) is melted.
The first heating and refrigeration-facility operation is an operation in which the heat taken by the refrigerant in the outdoor heat exchanger (24) and the refrigeration-facility heat exchanger (74) is used for heating. The second heating and refrigeration-facility operation is an operation in which the outdoor heat exchanger (24) is deactivated and the heat taken by the refrigerant in the refrigeration-facility heat exchanger (74) is used for heating. The third heating and refrigeration-facility operation is an operation in which the heat of the refrigerant is released from the outdoor heat exchanger (24).
The outline of each operation will be described with reference to
In the refrigeration-facility operation shown in
In the refrigeration-facility operation, the refrigeration cycle is performed in which the outdoor heat exchanger (24) functions as a radiator, the function of the indoor heat exchanger (64) is substantially deactivated, and the refrigeration-facility heat exchanger (74) functions as an evaporator.
Specifically, the refrigerant compressed by the first compressor (21) is cooled in the intercooler (29), and then is sucked into the third compressor (23). The refrigerant compressed to a pressure equal to or greater than the critical pressure by the third compressor (23) dissipates heat in the outdoor heat exchanger (24), and then passes through the first outdoor expansion valve (26). The first outdoor expansion valve (26) decompresses the refrigerant to a pressure lower than the critical pressure.
The refrigerant in a subcritical state flows into the gas-liquid separator (25). The gas-liquid separator (25) separates the refrigerant into a gas refrigerant and a liquid refrigerant.
The liquid refrigerant separated by the gas-liquid separator (25) is cooled in the subcooling heat exchanger (28) by the refrigerant flowing through the injection flow path (43). The refrigerant in the injection flow path (43) is sent to the intermediate flow path (18).
The refrigerant cooled by the subcooling heat exchanger (28) is sent to the refrigeration-facility unit (70). The refrigerant sent to the refrigeration-facility unit (70) is decompressed by the refrigeration-facility expansion valve (73), and then evaporates in the refrigeration-facility heat exchanger (74). As a result, the inside air is cooled. The refrigerant evaporated in the refrigeration-facility heat exchanger (74) is sucked into and compressed again by the first compressor (21).
In the cooling operation shown in
In the cooling operation, the refrigeration cycle is performed in which the outdoor heat exchanger (24) functions as a radiator, the indoor heat exchanger (64) functions as an evaporator, and the function of the refrigeration-facility heat exchanger (74) is substantially deactivated.
Specifically, the refrigerant compressed by the second compressor (22) is cooled in the intercooler (29), and then is sucked into the third compressor (23). The refrigerant compressed to a pressure equal to or greater than the critical pressure by the third compressor (23) dissipates heat in the outdoor heat exchanger (24), and then passes through the first outdoor expansion valve (26). The first outdoor expansion valve (26) decompresses the refrigerant to a pressure lower than the critical pressure.
The refrigerant in a subcritical state flows into the gas-liquid separator (25). The gas-liquid separator (25) separates the refrigerant into a gas refrigerant and a liquid refrigerant.
The liquid refrigerant separated by the gas-liquid separator (25) is cooled in the subcooling heat exchanger (28) by the refrigerant flowing through the injection flow path (43). The refrigerant in the injection flow path (43) is sent to the intermediate flow path (18).
The refrigerant cooled by the subcooling heat exchanger (28) is sent to the air-conditioning unit (60). The refrigerant sent to the air-conditioning unit (60) is decompressed by the indoor expansion valve (63), and then evaporates in the indoor heat exchanger (64). As a result, the indoor air is cooled. The refrigerant evaporated in the indoor heat exchanger (64) is sucked into and compressed again by the second compressor (22).
In the cooling and refrigeration-facility operation shown in
In the cooling and refrigeration-facility operation, the refrigeration cycle is performed in which the outdoor heat exchanger (24) functions as a radiator, and the indoor heat exchanger (64) and the refrigeration-facility heat exchanger (74) function as evaporators.
Specifically, the refrigerant compressed by the first compressor (21) and the second compressor (22) is cooled by the intercooler (29), and then is sucked into the third compressor (23). The refrigerant compressed to a pressure equal to or greater than the critical pressure by the third compressor (23) dissipates heat in the outdoor heat exchanger (24), and then passes through the first outdoor expansion valve (26). The first outdoor expansion valve (26) decompresses the refrigerant to a pressure lower than the critical pressure.
The refrigerant in a subcritical state flows into the gas-liquid separator (25). The gas-liquid separator (25) separates the refrigerant into a gas refrigerant and a liquid refrigerant.
The liquid refrigerant separated by the gas-liquid separator (25) is cooled in the subcooling heat exchanger (28) by the refrigerant flowing through the injection flow path (43). The refrigerant in the injection flow path (43) is sent to the intermediate flow path (18).
The refrigerant cooled by the subcooling heat exchanger (28) is sent to the air-conditioning unit (60) and the refrigeration-facility unit (70). The refrigerant sent to the air-conditioning unit (60) is decompressed by the indoor expansion valve (63), and then evaporates in the indoor heat exchanger (64). As a result, the indoor air is cooled. The refrigerant evaporated in the indoor heat exchanger (64) is sucked into and compressed again by the first compressor (21).
The refrigerant sent to the refrigeration-facility unit (70) is decompressed by the refrigeration-facility expansion valve (73), and then evaporates in the refrigeration-facility heat exchanger (74). As a result, the inside air is cooled. The refrigerant evaporated in the refrigeration-facility heat exchanger (74) is sucked into and compressed again by the second compressor (22).
In the heating operation shown in
In the heating operation, the refrigeration cycle is performed in which the indoor heat exchanger (64) functions as a radiator, the outdoor heat exchanger (24) functions as an evaporator, and the function of the refrigeration-facility heat exchanger (74) is substantially deactivated.
Specifically, the refrigerant compressed by the second compressor (22) is cooled in the intercooler (29), and then is sucked into the third compressor (23). The refrigerant compressed by the third compressor (23) is sent to the air-conditioning unit (60).
The refrigerant sent to the air-conditioning unit (60) dissipates heat in the indoor heat exchanger (64). As a result, the indoor air is heated. The refrigerant having dissipated heat in the indoor heat exchanger (64) flows into the gas-liquid separator (25). The gas-liquid separator (25) separates the refrigerant into a gas refrigerant and a liquid refrigerant.
The liquid refrigerant separated by the gas-liquid separator (25) is cooled in the subcooling heat exchanger (28) by the refrigerant flowing through the injection flow path (43). The refrigerant in the injection flow path (43) is sent to the intermediate flow path (18).
The refrigerant cooled by the subcooling heat exchanger (28) is decompressed by the second outdoor expansion valve (27), and then evaporates in the outdoor heat exchanger (24). The refrigerant evaporated in the outdoor heat exchanger (24) is sucked into and compressed again by the second compressor (22).
The first heating and refrigeration-facility operation shown in
In the first heating and refrigeration-facility operation, the refrigeration cycle is performed in which the indoor heat exchanger (64) functions as a radiator, and the outdoor heat exchanger (24) and the refrigeration-facility heat exchanger (74) function as evaporators.
Specifically, the refrigerant compressed by the first compressor (21) and the second compressor (22) is cooled by the intercooler (29), and then is sucked into the third compressor (23). The refrigerant compressed by the third compressor (23) is sent to the air-conditioning unit (60).
The refrigerant sent to the air-conditioning unit (60) dissipates heat in the indoor heat exchanger (64). As a result, the indoor air is heated. The refrigerant having dissipated heat in the indoor heat exchanger (64) flows into the gas-liquid separator (25). The gas-liquid separator (25) separates the refrigerant into a gas refrigerant and a liquid refrigerant.
The liquid refrigerant separated by the gas-liquid separator (25) is cooled in the subcooling heat exchanger (28) by the refrigerant flowing through the injection flow path (43). The refrigerant in the injection flow path (43) is sent to the intermediate flow path (18).
A part of the refrigerant cooled by the subcooling heat exchanger (28) is decompressed by the second outdoor expansion valve (27), and then evaporates in the outdoor heat exchanger (24). The refrigerant evaporated in the outdoor heat exchanger (24) is sucked into and compressed again by the first compressor (21).
The rest of the refrigerant cooled by the subcooling heat exchanger (28) is sent to the refrigeration-facility unit (70). The refrigerant sent to the refrigeration-facility unit (70) is decompressed by the refrigeration-facility expansion valve (73), and then evaporates in the refrigeration-facility heat exchanger (74). As a result, the inside air is cooled. The refrigerant evaporated in the refrigeration-facility heat exchanger (74) is sucked into and compressed again by the second compressor (22).
The second heating and refrigeration-facility operation shown in
In the second heating and refrigeration-facility operation, the refrigeration cycle is performed in which the indoor heat exchanger (64) functions as a radiator, the outdoor heat exchanger (24) is substantially stopped, and the refrigeration-facility heat exchanger (74) functions as an evaporator.
Specifically, the refrigerant compressed by the first compressor (21) is cooled in the intercooler (29), and then is sucked into the third compressor (23). The refrigerant compressed by the third compressor (23) is sent to the air-conditioning unit (60).
The refrigerant sent to the air-conditioning unit (60) dissipates heat in the indoor heat exchanger (64). As a result, the indoor air is heated. The refrigerant having dissipated heat in the indoor heat exchanger (64) flows into the gas-liquid separator (25). The gas-liquid separator (25) separates the refrigerant into a gas refrigerant and a liquid refrigerant.
The liquid refrigerant separated by the gas-liquid separator (25) is cooled in the subcooling heat exchanger (28) by the refrigerant flowing through the injection flow path (43). The refrigerant in the injection flow path (43) is sent to the intermediate flow path (18).
The refrigerant cooled by the subcooling heat exchanger (28) is decompressed by the refrigeration-facility expansion valve (73), and then evaporates in the refrigeration-facility heat exchanger (74). As a result, the inside air is cooled. The refrigerant evaporated in the refrigeration-facility heat exchanger (74) is sucked into and compressed again by the first compressor (21).
The third heating and refrigeration-facility operation shown in
In the third heating and refrigeration-facility operation, the refrigeration cycle is performed in which the indoor heat exchanger (64) and the outdoor heat exchanger (24) function as radiators, and the refrigeration-facility heat exchanger (74) functions as an evaporator.
Specifically, the refrigerant compressed by the first compressor (21) is cooled in the intercooler (29), and then is sucked into the third compressor (23). A part of the refrigerant compressed by the third compressor (23) is sent to the air-conditioning unit (60). The refrigerant sent to the air-conditioning unit (60) dissipates heat in the indoor heat exchanger (64). As a result, the indoor air is heated. The refrigerant having dissipated heat in the indoor heat exchanger (64) flows into the gas-liquid separator (25). The rest of the refrigerant compressed by the third compressor (23) dissipates heat in the outdoor heat exchanger (24), and then flows into the gas-liquid separator (25). The gas-liquid separator (25) separates the refrigerant into a gas refrigerant and a liquid refrigerant.
The liquid refrigerant separated by the gas-liquid separator (25) is cooled in the subcooling heat exchanger (28) by the refrigerant flowing through the injection flow path (43). The refrigerant in the injection flow path (43) is sent to the intermediate flow path (18).
The refrigerant cooled by the subcooling heat exchanger (28) is decompressed by the refrigeration-facility expansion valve (73), and then evaporates in the refrigeration-facility heat exchanger (74). As a result, the inside air is cooled. The refrigerant evaporated in the refrigeration-facility heat exchanger (74) is sucked into and compressed again by the first compressor (21).
The defrosting operation is executed to melt the frost on the outdoor heat exchanger (24) in winter or the like. For example, during the heating and refrigeration-facility operation, the controller (130) executes the defrosting operation if the condition for the outdoor heat exchanger (24) being frosted is satisfied. The basic operation of the defrosting operation is the same as the cooling operation shown in
In each of the above operations, the refrigeration apparatus (1) controls the degree of subcooling (sc) of the refrigerant flowing out of the first flow path (28a) of the subcooling heat exchanger (28). The control of the degree of subcooling will be described with reference to
In step S11, the controller (130) determines whether the degree of subcooling (sc) is smaller than the target degree of subcooling (Tsc). Here, the degree of subcooling (sc) may be an average value of the degree of subcooling at the present time and one or more degrees of subcooling at some time back from that present time by predetermined time. If the degree of subcooling (sc) is smaller than the target degree of subcooling (Tsc), the process proceeds to step S13. In step S13, the controller (130) adds a pulse corresponding to the difference (Tsc-sc) between the target degree of subcooling (Tsc) and the degree of subcooling (sc) to the current pulse of the injection valve (46). This pulse refers to the modulation width of a pulse signal for controlling the opening degree of the injection valve (46) (a command for the opening degree). As a result, the opening degree of the injection valve (46) increases according to the added pulse. As the difference between the target degree of subcooling (Tsc) and the degree of subcooling (sc) becomes larger, the pulse added in step S13 becomes larger. In other words, as the difference between the target degree of subcooling (Tsc) and the degree of subcooling (sc) becomes larger, the amount of an increase in the opening degree of the injection valve (46) becomes larger. As the difference becomes smaller, the amount of a decrease in the opening degree of the injection valve (46) becomes smaller.
In step S12, the controller (130) determines whether the degree of subcooling (sc) is larger than the target degree of subcooling (Tsc). If the degree of subcooling (sc) is larger than the target degree of subcooling (Tsc), the process proceeds to step S14. In step S14, the controller (130) subtracts a pulse corresponding to the difference (sc-Tsc) between the degree of subcooling (sc) and the target degree of subcooling (Tsc) from the current pulse of the injection valve (46). As a result, the opening degree of the injection valve (46) decreases according to the subtracted pulse. As the difference between the degree of subcooling (sc) and the target degree of subcooling (Tsc) becomes larger, the pulse subtracted in step S14 becomes larger. In other words, as the difference between the degree of subcooling (sc) and the target degree of subcooling (Tsc) becomes larger, the amount of a decrease in the opening degree of the injection valve (46) becomes larger. As the difference becomes smaller, the amount of a decrease in the opening degree of the injection valve (46) becomes smaller.
In the control of the degree of subcooling, the control of steps S11 to S14 is repeated every predetermined time (e.g., every 10 seconds). Accordingly, the degree of subcooling (sc) converges to the target degree of subcooling (Tsc).
When the refrigeration apparatus (1) is shipped out or installed, the amount of filling in the refrigerant circuit (6) is small in some cases. In particular, for the refrigeration apparatus (1) using carbon dioxide where the high pressure is equal to or greater than the critical pressure, the amount of filling in the refrigerant circuit (6) is set relatively small in some cases in consideration of the endurance pressure of the gas-liquid separator (25) and the like. Further, in the refrigeration apparatus (1) after installation, the refrigerant circuit (6) might leak a refrigerant. In this way, if there is a shortage of a refrigerant in the refrigerant circuit (6), the refrigeration apparatus (1) exhibits lower cooling capacity.
In this embodiment, in order to solve the above problems, the controller (130) determines whether there is a shortage of a refrigerant in the refrigerant circuit (6). When the degree of subcooling is being controlled as described above, the controller (130) determines whether there is a shortage of a refrigerant in the refrigerant circuit (6). This control of determination will be described in detail with reference to
In step S21, the controller (130) determines whether the opening degree of the injection valve (46) continues to remain equal to or greater than the first opening degree for a predetermined duration time (the first duration time) or more. In this embodiment, the first opening degree is the opening degree of the injection valve (46) that is fully opened. In other words, in step S22, the controller (130) determines whether the opening degree of the injection valve (46) continues to remain the opening degree of the injection valve (46) that is fully opened for the first duration time or more. If the condition of step S21 is satisfied, the process proceeds to step S23, and the controller (130) determines that there is a shortage of a refrigerant.
If there is a shortage of a refrigerant in the refrigerant circuit (6), a gas refrigerant might flow through the subcooling heat exchanger (28) or a gas-liquid two-phase refrigerant of which the dryness is relatively high might flow through the subcooling heat exchanger (28). In particular, if there is a shortage of a refrigerant in the refrigerant circuit (6) and there is almost no liquid refrigerant in the gas-liquid separator (25), a gas refrigerant flows through the first flow path (28a). In this case, the degree of subcooling of the refrigerant flowing out of the first flow path (28a) of the subcooling heat exchanger (28) continues to remain low or zero. If, under this situation, the degree of subcooling is controlled as described above, the opening degree of the injection valve (46) gradually increases, and in the end, the injection valve (46) continues to remain fully opened. Then, if the condition of step S21 is satisfied, the controller (130) determines that there is a shortage of a refrigerant in the refrigerant circuit (6). If it is determined that there is a shortage of a refrigerant, the alerting unit (134) alerts in step S24 that there is a shortage of a refrigerant. Accordingly, the target entity can be promptly informed that there is a shortage of a refrigerant in the refrigerant circuit (6).
In step S22, the controller (130) determines whether the opening degree of the injection valve (46) continues to remain equal to or greater than the second opening degree for a predetermined duration time (the second duration time) or more. In this embodiment, the second opening degree is a predetermined opening degree smaller than the first opening degree. The second duration time is a predetermined duration time longer than the first duration time. That is, the condition of step S22 is satisfied if the opening degree of the injection valve (46) continues to remain the second opening degree smaller than the first opening degree for the second duration time longer than the first duration time. If the condition of step S22 is satisfied, the process proceeds to step S23, and the controller (130) determines that there is a shortage of a refrigerant.
If, as described above, there is a shortage of a refrigerant in the refrigerant circuit (6), and a gas refrigerant or a gas-liquid two-phase refrigerant of which the dryness is relatively high flows through the first flow path (28a), the opening degree of the injection valve (46) continues to remain relatively large for a long duration time due to the control of the degree of subcooling. Then, if the condition of step S22 is satisfied, the controller (130) determines that there is a shortage of a refrigerant in the refrigerant circuit (6). If it is determined that there is a shortage of a refrigerant, the alerting unit (134) alerts in step S24 that there is a shortage of a refrigerant.
It is conceivable that, in the control of the degree of subcooling, whether there is a shortage of a refrigerant in the refrigerant circuit (6) is determined using the degree of subcooling itself. Specifically, in the control of the degree of subcooling, if the condition that the degree of subcooling is smaller than a predetermined value is satisfied, the controller (130) determines whether there is a shortage of a refrigerant in the refrigerant circuit (6). However, the degree of subcooling tends to change sharply according to the state of the refrigerant in comparison with the opening degree of the injection valve (46) in the control of the degree of subcooling. This is because, as described above, the opening degree of the injection valve (46) changes according to the value obtained by adding or subtracting the pulse based on the difference between the degree of subcooling (sc) and the target degree of subcooling (Tsc), whereas the degree of subcooling (sc) is an index that directly reflects a change in the state of the refrigerant.
If whether there is a shortage of a refrigerant in the refrigerant circuit (6) is determined according to the degree of subcooling, whether there is a shortage of a refrigerant in the refrigerant circuit (6) might be determined erroneously if the state of the refrigerant is temporarily changed due to some influence. Specifically, for example, if the separated gas refrigerant temporarily flows into the first flow path (28a) in a state in which the liquid surface in the gas-liquid separator (25) is unstable, the degree of subcooling might temporarily fall below a predetermined value. In this case, despite the fact that there is no shortage of a refrigerant in the refrigerant circuit (6), it might be determined erroneously that there is a shortage of a refrigerant in the refrigerant circuit (6).
In contrast, in this embodiment, whether there is a shortage of a refrigerant in the refrigerant circuit (6) is determined using the opening degree of the injection valve (46) which changes more gradually than the degree of subcooling. Thus, for the above reasons, it is possible to determine less erroneously whether there is a shortage of a refrigerant in the refrigerant circuit (6) when the gas refrigerant temporarily flows through the first flow path (28a).
In order to reduce erroneous determination about the refrigerant circuit (6), the controller (130) under the conditions described below refuses to determine whether there is a shortage of a refrigerant in the refrigerant circuit (6). The following conditions can be interpreted as the conditions that the degree of subcooling (sc) of the refrigerant flowing out of the first flow path (28a) is unstable. In other words, under the condition that the degree of subcooling (sc) is stable, the controller (130) determines that there is a shortage of a refrigerant in the refrigerant circuit (6).
Condition (a): During the period between when the compression unit (20) starts to operate and when a predetermined time (15 minutes) elapses, the controller (130) refuses to determine whether there is a shortage of a refrigerant in the refrigerant circuit (6). This is because during the period between when the compression unit (20) starts to operate and when a predetermined time (e.g., 15 minutes) elapses, the degree of subcooling (sc) is unstable. In other words, after the period between when the compression unit (20) starts to operate and when a predetermined time elapses, the controller (130) determines whether there is a shortage of a refrigerant in the refrigerant circuit (6).
Condition (b): If the outdoor heat exchanger (24) operates as a radiator and the outside air temperature is higher than a predetermined temperature Ta (e.g., 32° C.), the controller (130) controls the opening degree of the injection valve (46) so that the intermediate pressure of the refrigerant circuit (6) approaches a predetermined target value in order to increase the high pressure of the refrigerant circuit (6). Here, the intermediate pressure is detected by the intermediate pressure sensor (102). Under this condition, the injection valve (46) is not subjected to the control of the degree of subcooling, and thus the controller (130) refuses to determine whether there is a shortage of a refrigerant in the refrigerant circuit (6).
Condition (c): If the indoor heat exchanger (64) operates as a radiator and the outside air temperature is lower than a predetermined temperature Tb (e.g., 10° C.), the controller (130) controls the opening degree of the injection valve (46) so that the intermediate pressure of the refrigerant circuit (6) approaches a predetermined target value in order to increase the high pressure of the refrigerant circuit (6). Under this condition, the injection valve (46) is not subjected to the control of the degree of subcooling, and thus the controller (130) refuses to determine whether there is a shortage of a refrigerant in the refrigerant circuit (6).
Condition (d): Under the condition that the outside air temperature is higher than a predetermined temperature (e.g., 32° C.), the high pressure of the refrigerant circuit (6) or the internal pressure of the gas-liquid separator (25) increases. Thus, the controller (130) increases the opening degree of the venting valve (42) or decreases the opening degree of the first outdoor expansion valve (26). Under this condition, the degree of subcooling (sc) of the refrigerant flowing out of the first flow path (28a) is unstable, and thus the controller (130) refuses to determine whether there is a shortage of a refrigerant in the refrigerant circuit (6). That is, under the condition that the outside air temperature is higher than a predetermined temperature; the condition that the high pressure is higher than a predetermined value; or the condition that the internal pressure of the gas-liquid separator (25) is higher than a predetermined value, the controller (130) refuses to determine whether there is a shortage of a refrigerant in the refrigerant circuit (6).
Condition (e): During the period between when the various operations described above switch from one operation to another and when a predetermined time elapses, the controller (130) refuses to determine whether there is a shortage of a refrigerant in the refrigerant circuit (6). This is because during the period between when the various operations described above switch from one operation to another and when a predetermined time elapses, the degree of subcooling (sc) is unstable. In other words, after the period between when the various operations described above switch from one operation to another and when a predetermined time elapses, the controller (130) determines whether there is a shortage of a refrigerant in the refrigerant circuit (6).
Under the condition that the opening degree of a subcooling-side decompression valve (46) is equal to or greater than a predetermined opening degree, the controller (130) determines that there is a shortage of a refrigerant in the refrigerant circuit (6).
If there is a shortage of a refrigerant in the refrigerant circuit (6), the degree of subcooling of the refrigerant flowing out of the first flow path (28a) is small or zero, and the opening degree of the subcooling-side decompression valve (46) is equal to or greater than a predetermined opening degree. By using this, it is possible to determine that there is a shortage of a refrigerant in the refrigerant circuit (6).
The opening degree of the subcooling-side decompression valve (46) fluctuates more gradually than the degree of subcooling itself, and thus it is possible to determine less erroneously whether there is a shortage of a refrigerant in the refrigerant circuit (6).
In particular, under the condition that the opening degree of the subcooling-side decompression valve (46) continues to remain equal to or greater than a predetermined opening degree for a predetermined duration time or more, the controller (130) determines that there is a shortage of a refrigerant.
Thus, it is possible to further determine less erroneously whether there is a shortage of a refrigerant in the refrigerant circuit (6).
Under the condition that the opening degree of the subcooling-side decompression valve (46) continues to remain equal to or greater than the first opening degree for the first duration time or more, or under the condition that the opening degree of the subcooling-side decompression valve (46) continues to remain equal to or greater than the second opening degree for the second duration time or more, the controller (130) determines that there is a shortage of a refrigerant. The second duration time is longer than the first duration time, and the second opening degree is smaller than the first opening degree.
According to these conditions, if the opening degree of the subcooling-side decompression valve (46) is relatively large, it is possible to relatively promptly determine that there is a shortage of a refrigerant in the refrigerant circuit (6). Also if the opening degree of the subcooling-side decompression valve (46) is relatively small and this situation continues for a relatively long duration time, it is possible to determine that there is a shortage of a refrigerant in the refrigerant circuit (6).
Under the condition that the opening degree of the subcooling-side decompression valve (46) is the opening degree of the subcooling-side decompression valve (46) that is fully opened, the controller (130) determines that there is a shortage of a refrigerant in the refrigerant circuit (6).
If there is a shortage of a refrigerant in the refrigerant circuit (6), the degree of subcooling of the refrigerant flowing out of the first flow path (28a) should be zero, and thus in the end, the subcooling-side decompression valve (46) reaches the maximum opening degree in the possible control range. Thus, by employing the condition that the opening degree of the subcooling-side decompression valve (46) is the opening degree of the subcooling-side decompression valve (46) that is fully opened, it is possible to precisely determine that there is a shortage of a refrigerant in the refrigerant circuit (6).
The refrigerant circuit (6) is configured to be able to perform a refrigeration cycle in which the high pressure is equal to or greater than the critical pressure. Thus, the degree of subcooling (sc) of the refrigerant flowing out of the first flow path (28a) is easily unstable. In contrast, the opening degree of the subcooling-side decompression valve (46) changes more gradually than the degree of subcooling itself, and thus it is possible to reduce erroneous determination as to whether there is a shortage of a refrigerant in the refrigerant circuit (6) due to the degree of subcooling (sc) being unstable.
The refrigerant circuit (6) is provided with the gas-liquid separator (25) between the outdoor heat exchanger (24) and the first flow path (28a) of the subcooling heat exchanger (28). Thus, when the liquid surface of the gas-liquid separator (25) is unstable, a gas refrigerant might temporarily flow through the first flow path (28a). In contrast, the opening degree of the subcooling-side decompression valve (46) changes more gradually than the degree of subcooling itself, and thus it is possible to reduce erroneous determination as to whether there is a shortage of a refrigerant in the refrigerant circuit (6) due to the degree of subcooling (sc) being unstable.
If the opening degree of the subcooling-side decompression valve (46) instantaneously becomes equal to or greater than a predetermined opening degree, the controller (130) may determine that there is a shortage of a refrigerant in the refrigerant circuit (6).
If determining that there is a shortage of a refrigerant, the controller (130) may execute a predetermined control such as stopping the operation of the refrigeration apparatus (1).
The compression unit (20) may be a single compressor.
The injection flow path (43) may send the refrigerant to the suction side of the compression unit (20).
The first utilization-side heat exchanger (64) may be a heat exchanger for heating or cooling water, brine, and the like. The first utilization-side heat exchanger (64) may be used as a heat source for a water heater.
While the embodiments and variations thereof have been described above, it will be understood that various changes in form and details may be made without departing from the spirit and scope of the claims. The elements according to the embodiment, the variations thereof, and the other embodiments may be combined and replaced with each other.
The ordinal numbers such as “first,” “second,” “third,” . . . , described above are used to distinguish the terms to which these expressions are given, and do not limit the number and order of the terms.
As described above, the present disclosure is useful for a heat source unit, and a refrigeration apparatus.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2022-148706 | Sep 2022 | JP | national |
This application is a continuation application of International Application No. PCT/JP2023/032832, filed Sep. 8, 2023, which claims priority to Japanese Patent Application No. 2022-148706, filed Sep. 20, 2022, the contents of these applications are incorporated herein by reference in their entirety.
| Number | Date | Country | |
|---|---|---|---|
| Parent | PCT/JP2023/032832 | Sep 2023 | WO |
| Child | 19033766 | US |
