JP2010054194A - Refrigerating device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To perform appropriate refrigerant injection to each compressor using an injection circuit in a refrigerating device having the plurality of compressors. <P>SOLUTION: The refrigerating device is provided with the injection circuit (40) comprising first injection piping (37) branched from the first refrigerant piping (32) of a refrigerant circuit (10) and branched injection piping (37a, 37b, 37c) each further branched from the first injection piping (37). A supercooling pressure reducing valve (29) is installed in the first injection piping (37), and flow rate regulating valves (30a, 30b, 30c) are installed in the branched injection piping (37a, 37b, 37c), respectively. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a refrigeration apparatus that has a plurality of compressors and performs a vapor compression refrigeration cycle, and particularly relates to a refrigeration apparatus that includes an injection circuit that injects refrigerant into each compressor.

  Conventionally, a refrigeration apparatus having a refrigerant circuit that has a plurality of compressors and performs a vapor compression refrigeration cycle is known. Among this type of refrigeration apparatus, as shown in Patent Document 1, there is an apparatus provided with an injection circuit that injects a refrigerant branched from the main pipe of the refrigerant circuit into each compressor.

  One end side of the injection circuit is connected to a branch pipe branched from the high-pressure line of the refrigerant circuit, and the other end side is connected to an intermediate port that branches into a plurality and opens into a compression chamber at an intermediate pressure position in each compressor. ing. The branch pipe is provided with a pressure reducing valve for reducing the pressure of the refrigerant.

  According to this configuration, the refrigerant discharged from each compressor joins and then flows into the outdoor heat exchanger. The discharged refrigerant is condensed in the outdoor heat exchanger, and then a part of the discharged refrigerant flows into a branch pipe branched from the refrigerant circuit. And it is pressure-reduced to predetermined pressure with the pressure-reduction valve of this branch piping. The refrigerant decompressed by the pressure reducing valve is diverted toward the intermediate ports of the compressors, and then injected into the compression chambers of the compressors through the intermediate ports.

  Here, the refrigeration apparatus includes a temperature sensor that detects the discharge pipe temperature of each compressor. Based on the amount of change per unit time in the discharge pipe temperature detected by the temperature sensor, the decompression valve is opened. By adjusting the degree, the temperature of the refrigerant discharged from each compressor can be set within a predetermined temperature range.

JP 2008-076017 A

  However, depending on the configuration of the refrigerant circuit, the temperature of the refrigerant discharged from each compressor may not easily fall within a predetermined temperature range even when a conventional injection circuit is used.

  For example, there is a case where at least one of the plurality of compressors in the refrigerant circuit is configured by a variable capacity compressor and the other is configured by a fixed capacity compressor. In such a refrigerant circuit, the variable capacity compressor is operated with a predetermined operating capacity, and the refrigerant of the injection circuit is injected into each compressor while operating the fixed capacity compressor with a fixed operating capacity. Suppose that it is in a state. At this time, the temperature of the refrigerant discharged from each compressor is assumed to be within a predetermined temperature range by injection.

  From this state, in order to reduce the operating capacity of the variable capacity compressor, the operating frequency is set lower than the current frequency. Then, the period of the volume change of the compression chamber in this compressor becomes longer, and the time during which the compression chamber is at the intermediate pressure position also becomes longer. This also increases the opening time of the intermediate port that opens to the intermediate pressure position of the compression chamber. As the opening time of the intermediate port becomes longer, the refrigerant in the injection circuit is more easily sucked into the variable capacity compressor.

  As a result, in the injection circuit, the refrigerant decompressed by the pressure reducing valve flows more toward the variable capacity compressor than the fixed capacity compressor, and the temperature of the refrigerant discharged from the variable capacity compressor is It may be lower than a fixed capacity compressor. If it becomes like this, the temperature of the refrigerant | coolant discharged from each compressor will become difficult to become in a predetermined temperature range.

  Another example is a case where a plurality of compressors in the refrigerant circuit are composed of a first compressor and a second compressor having different suction pressures. In this case, the refrigerant circuit is provided with a first evaporator corresponding to the first compressor and a second evaporator corresponding to the second compressor, and the first evaporator and the second evaporator, The refrigerants flowing through are configured to evaporate at different evaporation temperatures.

  Thus, if the suction pressure is different between the first compressor and the second compressor, the pressure in the compression chamber at the intermediate pressure position is also different. Thereby, the refrigerant decompressed by the pressure reducing valve is easily sucked into the lower compressor than the compressor having the higher pressure in the compression chamber at the intermediate pressure position. As a result, the temperature of the discharged refrigerant in the compressor having the lower pressure becomes lower than that of the compressor having the higher pressure. If it becomes like this, the temperature of the refrigerant | coolant discharged from each compressor will become difficult to become in a predetermined temperature range.

  As described above, in the injection circuit, depending on the configuration and operating state of the refrigerant circuit, the refrigerant decompressed by the decompression valve may be biased to one of the compressors.

  This invention is made | formed in view of this point, The objective is to perform appropriate refrigerant | coolant injection with respect to each compressor in the refrigeration apparatus provided with the several compressor.

  The first invention includes a refrigerant circuit (10) having a plurality of compressors (21a, 21b, 21c) for performing a vapor compression refrigeration cycle, and a branch from the high-pressure line (33) of the refrigerant circuit (10) Main pipe (37) and branch pipes (37a, 37b, 37c) further branched from the main pipe (37), and each branch pipe (37a, 37b, 37c) is connected to each compressor (21a, 21b, 21c) refrigeration apparatus comprising an injection circuit (40) connected to the intermediate port (5, 6, 7) and a decompression means (29) provided in the main pipe (37) of the injection circuit (40) Is assumed.

  In the refrigerant circuit (10), at least one of the plurality of compressors (21a, 21b, 21c) includes a variable displacement compressor (21a), and the plurality of compressors (21a, 21b, 21c) Of these, at least the branch pipes (37a, 37b, 37c) on the variable capacity compressor (21a) side are provided with flow rate adjusting means (30a, 30b, 30c). Here, the intermediate port (5, 6, 7) is provided in the compressor (21a, 21b, 21c) so as to open to the compression chamber at the intermediate pressure position.

  In the first invention, a part of the high-pressure refrigerant flowing through the high-pressure line (high-pressure pipe) (33) of the refrigerant circuit (10) is branched and flows into the main pipe (37). The high-pressure refrigerant that has flowed into the main pipe (37) is depressurized by the pressure-reducing means (29), and then branches and flows into the branch pipe (37a, 37b, 37c). Each refrigerant flowing into the branch pipes (37a, 37b, 37c) passes through the intermediate ports (5, 6, 7) after the flow rate is adjusted by the flow rate adjusting means (30a, 30b, 30c). And it is comprised so that it may inject into the said compression chamber.

  Therefore, as described above, at least one of the plurality of compressors (21a, 21b, 21c) is composed of a variable capacity compressor (21a), and the other is a fixed capacity compressor (21b, 21c). In such a case, when the operating capacity of the variable capacity compressor (21a) is reduced, the opening degree of the flow rate adjusting means (30a) corresponding to the variable capacity compressor (21a) is reduced. Thus, it is possible to suppress a large amount of refrigerant from being injected toward the variable capacity compressor (21a).

  When the suction pressure of one of the plurality of compressors (21a, 21b, 21c) becomes smaller than the suction pressure of the other compressor (21b, 21c), By reducing the opening of the flow rate adjusting means (30a) corresponding to the variable capacity compressor (21a), it is possible to prevent a large amount of refrigerant from being injected toward the variable capacity compressor (21a). Is possible.

  According to a second invention, in the first invention, a flow rate adjusting means (30a, 30b, 30c) is provided for each branch pipe (37a, 37b, 37c) of the injection circuit (40). Yes.

  In the second invention, by providing the flow rate adjusting means (30a, 30b, 30c) to all the branch pipes (37a, 37b, 37c), for example, among the plurality of compressors (21a, 21b, 21c) When the suction pressure of one compressor (21a) becomes smaller than the suction pressure of the other compressor (21b, 21c), the flow rate adjusting means (30a) corresponding to the compressor (21a) having the smaller suction pressure ) Is reduced, it is possible to prevent a large amount of refrigerant from being injected into the compressor (21a) having a lower suction pressure.

  According to a third aspect, in the first or second aspect, a decompression side passage (28b) through which the refrigerant decompressed by the decompression means (29) flows and a high pressure side passage through which the high pressure refrigerant of the refrigerant circuit (10) flows. (28a) having a supercooling heat exchanger (28), wherein the pressure reducing side channel (28b) is connected to the main pipe (37) of the injection circuit (40), and the high pressure side channel (28a) Is connected to the high-pressure line (33) of the refrigerant circuit (10).

  In the third invention, by providing the supercooling heat exchanger (28), the refrigerant decompressed by the decompression means (29) is subjected to heat exchange with the high-pressure refrigerant flowing through the refrigerant circuit (10). The compression chambers (21a, 21b, 21c) can be injected.

  According to a fourth aspect of the present invention, in any one of the first to third aspects, the compressor (21a, 21b) is provided in the discharge pipe (22a, 22b, 22c) of each compressor (21a, 21b, 21c). , 21c) an oil separator (38a, 38b, 38c) that separates the refrigeration oil from the discharged refrigerant, and an oil outflow pipe (39a, 39b, 39c) connected to the oil separator (38a, 38b, 38c) , One end side is connected to the oil outflow pipe (39a, 39b, 39c), and the other end side is connected to a branch pipe branched from the injection circuit (40) to each compressor from the oil outflow pipe (39a, 39b, 39c) And an oil return circuit (39) for returning the refrigeration oil to (21a, 21b, 21c).

  In the fourth invention, the refrigerating machine oil separated from the refrigerant discharged by the oil separator (38a, 38b, 38c) is supplied to the intermediate pressure position in each compressor (21a, 21b, 21c) via the injection circuit (40). It can be returned to the compression chamber.

  According to a fifth invention, in any one of the first to fourth inventions, the flow rate adjusting means (30a, 30b, 30c) is a flow rate adjusting valve having a variable opening.

  In the fifth invention, the flow rate adjusting means (30a, 30b, 30c) is constituted by a flow rate adjusting valve, whereby the opening degree of the valve can be freely changed between fully open and fully closed.

  According to a sixth invention, in any one of the first to fifth inventions, the flow rate adjusting means (30a, 30b, 30c) is an on-off valve. Here, reducing the opening degree of the flow rate adjusting means (30a, 30b, 30c) means closing the on-off valve, and increasing the opening degree means opening the on-off valve. is there.

  In the sixth aspect of the invention, the flow rate adjusting means (30a, 30b, 30c) is constituted by an on-off valve, for example, as compared with the case where the flow rate adjusting means (30a, 30b, 30c) is constituted by a flow rate adjusting valve. The structure of the valve can be simplified and the cost can be reduced.

  According to a seventh invention, in any one of the first to sixth inventions, the plurality of compressors (21a, 21b, 21c) includes a variable capacity compressor (21a) and a fixed capacity compressor ( 21b, 21c) and the flow rate adjusting means (30a) provided in the branch pipe (37a) connected to the intermediate port (5) of the variable capacity compressor (21a) is variable in opening degree. The flow rate adjusting valve (30b, 37c) is provided in the branch pipe (37b, 37c) connected to the intermediate port (6, 7) of the fixed capacity compressor (21b, 21c). 30c) is characterized by being an on-off valve.

  In the seventh invention, the injection amount of the variable displacement compressor (21a) is adjusted by the flow rate adjusting valve, and the injection amount of the fixed displacement compressor (21b, 21c) is adjusted by the on-off valve. be able to.

  According to an eighth invention, in any one of the first to seventh inventions, there is provided a discharge refrigerant temperature detection means (61) for detecting the temperature of the discharge refrigerant discharged from the compressors (21a, 21b, 21c). And a control means (9) for adjusting the opening degree of each flow rate adjusting means (30a, 30b, 30c) so that the value detected by the discharged refrigerant temperature detecting means (61) is within a predetermined temperature range. It is characterized by having.

  In the eighth invention, if there is a compressor (21a, 21b, 21c) having a higher temperature than the predetermined temperature range among the plurality of compressors (21a, 21b, 21c), the compressor (21a , 21b, 21c), the opening of the flow rate adjusting means (30a, 30b, 30c) can be increased to increase the injection amount of the compressor (21a, 21b, 21c). As a result, the temperature of the discharged refrigerant can be lowered to a predetermined temperature range.

  In addition, if there is a compressor (21a, 21b, 21c) whose discharge refrigerant temperature is lower than a predetermined temperature range, flow rate adjusting means (30a, 30b, 30c) corresponding to the compressor (21a, 21b, 21c) The amount of injection of the compressor (21a, 21b, 21c) can be reduced by reducing the opening degree of the compressor. Thereby, the temperature of a discharge refrigerant | coolant can be raised and can be in a predetermined temperature range.

  According to a ninth invention, in any one of the third to seventh inventions, the discharge state detecting means (61, 61) for detecting at least one of the discharge temperature and the discharge superheat degree in the compressors (21a, 21b, 21c). 66), discharge state setting means (76) for setting a discharge target value Tm for at least one of the discharge temperature and the discharge superheat degree in each of the compressors (21a, 21b, 21c), and the supercooling heat exchanger Intermediate superheat degree detecting means (75) for detecting the degree of superheat of the intermediate pressure refrigerant after passing through the pressure reduction side flow path (28b) of (28), and the pressure reduction side flow path of the supercooling heat exchanger (28) ( 28b) intermediate superheat degree setting means (77) for setting the intermediate superheat degree target value Tgsm with respect to the superheat degree of the intermediate pressure refrigerant after passing through each of the discharge state detecting means (61, 66). Maximum detection value Ttd which is the maximum value among detection values Td for each compressor (21a, 21b, 21c) The first discharge target control section (56a) that changes the opening of the pressure reducing means (29) so that the discharge target value Tm becomes equal to the discharge target value Tm, and the detected value Tgsh of the intermediate superheat degree detecting means (75) is the intermediate superheat degree. When the refrigerant state value of the refrigerant in the intermediate superheat degree control unit (60) that changes the opening degree of the pressure reducing means (29) so as to be the target value Tgsm and the refrigerant circuit (10) is within a predetermined range, And a first control unit (16) that performs control by selecting the first discharge target control unit (56a) or the intermediate superheat degree control unit (60) based on the refrigerant state value. It is said.

  Here, the discharge state setting means (76) sets, as the discharge target value Tm, an appropriate value at which each of the compressors (21a, 21b, 21c) does not undergo a relatively excessive overheating operation or a wet operation. Further, the intermediate superheat degree setting means (77) is configured so that the intermediate pressure refrigerant after passing through the pressure reducing side channel (28b) of the supercooling heat exchanger (28) is in a relatively excessive superheated state or wet state. An appropriate value that is not obtained is set as the intermediate superheat degree target value Tgshm. The predetermined range of the refrigerant state value is set in a range where the compressors (21a, 21b, 21c) do not operate abnormally.

  In the ninth invention, when the refrigerant state value of the refrigerant circuit (10) is within a predetermined range, that is, when the compressor (21a, 21b, 21c) is not operating abnormally, the first control unit (16 ) Selects the first discharge target control section (56a) or the intermediate superheat degree control section (60). When the first discharge target control unit (56a) is selected, the decompression means (56a) is configured so that the discharge temperature or the discharge superheat degree of each compressor (21a, 21b, 21c) becomes constant at the target value. 29) When the opening degree is changed and the intermediate superheat degree control unit (60) is selected, the intermediate pressure refrigerant superheat degree on the decompression side flow path (28b) side in the supercooling heat exchanger (28) is selected. The opening degree of the pressure reducing means (29) is changed so that becomes constant at the target value.

  In a tenth aspect based on the ninth aspect, the first control section (16) is configured such that the maximum detection value Ttd of the discharge state detection means (61, 66) is greater than the discharge target value Tm. The first discharge target control unit (56a) is selected to execute control.

  In the tenth invention, when the maximum detection value Ttd of the discharge state detection means (61, 66) is larger than the discharge target value Tm, that is, one of the compressors (21a, 21b, 21c) is In the case of a comparatively excessive overheating operation, the opening degree of the pressure reducing means (29) is changed by the first discharge target control section (56a). Thereby, the discharge temperature or discharge superheat degree of the compressor (21a, 21b, 21c) can be maintained at an appropriate value.

  In an eleventh aspect based on the ninth or tenth aspect, the first control unit (16) is configured such that the maximum detection value Ttd of the discharge state detection means (61, 66) is equal to or less than the discharge target value Tm. The intermediate superheat control unit (60) is selected to execute control.

  In the eleventh aspect of the invention, when the maximum detection value Ttd of the discharge state detection means (61, 66) is equal to or less than the discharge target value Tm, that is, all the compressors (21a, 21b, 21c) are relatively excessively overheated. When not in operation, the opening degree of the decompression means (29) is changed by the intermediate superheat control unit (60). As a result, the intermediate pressure refrigerant superheat degree on the decompression side flow path (28b) side in the supercooling heat exchanger (28) can be maintained at an appropriate value.

  In a twelfth aspect based on any one of the ninth to eleventh aspects, the first control unit (16) is configured such that the maximum detection value Ttd of the discharge state detecting means (61, 66) is within a predetermined time t1. When continuously decreasing, the intermediate superheat degree control unit (60) is selected to execute control.

  In the twelfth aspect, when the maximum detection value Ttd of the discharge state detection means (61, 66) continuously decreases within the predetermined time t1, for example, the plurality of compressors (21a, 21b, 21c) One of them is a relatively excessive overheating operation. If the excessive overheating operation is approaching a wet operation, the intermediate operation is performed regardless of the operation state of the compressor (21a, 21b, 21c). The degree of opening of the pressure reducing means (29) is changed by the superheat degree control section (60). By doing so, the operation start of the intermediate superheat control unit can be accelerated.

  In a thirteenth invention according to any one of the ninth to twelfth inventions, the first overheating avoidance control unit (78a) for making the opening of the decompression means (29) larger than the present one and the decompression means (29 ) When the refrigerant state value of the refrigerant in the refrigerant circuit (10) exceeds the predetermined range, the refrigerant state value is within the predetermined range. And an avoidance control unit (58) that selects and executes the first overheat avoidance control unit (78a) or the first wetness avoidance control unit (79a) until the inside is included.

  In the twelfth invention, when the refrigerant state value exceeds a predetermined range, that is, when the compressor (21a, 21b, 21c) is operating abnormally, until the refrigerant state value falls within the predetermined range, The decompression means (29) is controlled by the avoidance control unit (58). By doing so, the refrigeration apparatus can be prevented from continuing abnormal operation. Therefore, when the refrigerant state value of the refrigerant circuit (10) is within a predetermined range, the pressure reducing means (29) is controlled by the first control unit (16), and the refrigerant state value falls within the predetermined range. When it exceeds, the depressurization means (29) is controlled by the avoidance control section (58).

  In a fourteenth aspect based on the thirteenth aspect, the avoidance control unit (58) is arranged on the upper limit side where the detection value Td of the discharge state detection means (61, 66) is set larger than the discharge target value Tm. At least one of a case where it is larger than the threshold value Tdmax and a case where the detected value Tgsh of the intermediate superheat degree detection means (75) is larger than the upper limit side threshold value Tgshmax set larger than the intermediate superheat degree target value Tgshm. Sometimes, the first overheat avoiding control unit (78a) is selected to execute control.

  Here, as the refrigerant state value of the refrigerant circuit (10), at least one of the detection value Td of the discharge state detection means (61, 66) and the detection value Tgsh of the intermediate superheat degree detection means (75) is used. Further, upper limit threshold values Tdmax and Tgshmax set larger than the target value Tm corresponding to the detected values Td and Tgsh are used as the maximum values within the predetermined range in the refrigerant state value.

  In the fourteenth invention, the discharge temperature or the discharge superheat degree as the refrigerant state value becomes too high, and the detection values Td and Tgsh exceed the upper thresholds Tdmax and Tgshmax, and the compressors (21a, 21b , 21c) is in an abnormal overheating operation state, the opening degree of the pressure reducing means (29) is adjusted by the first overheating avoidance control unit (78a), and the opening degree is forcibly increased.

  In a fifteenth aspect based on the thirteenth or fourteenth aspect, the avoidance control unit (58) sets the detection value Td of the discharge state detection means (61, 66) to be smaller than the discharge target value Tm. When it is smaller than the lower limit side threshold value Tdmin, and when the detected value Tgsh of the intermediate superheat degree detection means (75) is further smaller than the lower limit side threshold value Tgshmin set smaller than the intermediate superheat degree target value Tgshm. In at least one of the cases, the first wetting avoidance control unit (79a) is selected to perform control.

  Here, as in the fourteenth aspect of the invention, as the refrigerant state value of the refrigerant circuit (10), the detection value Td of the discharge state detection means (61, 66) and the detection value Tgsh of the intermediate superheat degree detection means (75) At least one of the above is used. Further, lower threshold values Tdmin and Tgshmin set smaller than the target values Tdm and Tgshm corresponding to the detected values Td and Tgsh are used as the minimum values within the predetermined range in the refrigerant state value.

  In the fifteenth invention, the discharge temperature or the discharge superheat degree as the refrigerant state value becomes too low, and the detection values Td and Tgsh exceed the lower limit side thresholds Tdmin and Tgshmin, and the compressors (21a, 21b , 21c) is in an abnormal wet operation state, the opening degree of the decompression means (29) is adjusted by the first wetting avoidance control unit (79a), and the opening degree is forcibly reduced.

  In a sixteenth aspect based on any one of the ninth to fifteenth aspects, the detection values Td for the compressors (21a, 21b, 21c) in the discharge state detecting means (61, 66) are close to each other. The second control unit (17) for changing the opening degree of the flow rate adjusting means (30a, 30b, 30c) is provided.

  In the sixteenth aspect, the discharge temperatures or discharge superheat degrees of the compressors (21a, 21b, 21c) can be made closer to each other.

  In a seventeenth aspect based on any one of the third to seventh aspects, the plurality of compressors (21a, 21b, 21c) includes a first compressor (21a, 21b) and a second compressor (21c). The low-pressure line of the refrigerant circuit (10) is provided in the suction side of the first compressor (21a, 21b) and the refrigerant circuit (10) for cooling heat exchange for cooling the inside of the cabinet Heat exchange for air conditioning, which is provided on the suction side of the second compressor (21c) and the refrigerant circuit (10) for air conditioning in the room, connecting the compressor (53b, 81) to the compressor (53b, 81) A low-pressure detecting means (120, 121) configured to detect a pressure of a low-pressure refrigerant flowing through the first and second low-pressure lines (102, 101), and a second low-pressure line (101) connecting the vessel (53a); Intermediate pressure detecting means (71) for detecting the pressure of the intermediate pressure refrigerant after being depressurized by the pressure reducing means (29), and the pressure reducing side flow path of the supercooling heat exchanger (28) 28b) intermediate superheat degree detecting means (75) for detecting the superheat degree of the intermediate pressure refrigerant after passing through, and the intermediate pressure after passing through the pressure reducing side flow path (28b) of the supercooling heat exchanger (28). Intermediate superheat degree setting means (77) for setting an intermediate superheat degree target value Tgsm with respect to the superheat degree of the refrigerant, and the detected value MP of the intermediate pressure detection means (71) is the low pressure detection means (120, 121). The intermediate pressure control unit (59) for changing the opening degree of the pressure reducing means (29) so as to be larger than the detected value LP of each low pressure line (102, 101), and the detected value of the intermediate superheat degree detecting means (75) The intermediate superheat degree control unit (60) for changing the opening degree of the pressure reducing means (29) so that Tgsh becomes the intermediate superheat degree target value Tgshm, and the plurality of compressors (21a, 21b, 21c) are activated. Based on the intermediate pressure control unit (59) or the intermediate superheat control unit (60) And a third control unit (18) for executing control by selecting the item.

  Here, when the evaporation temperatures of the cooling heat exchanger (53b, 81) and the air conditioning heat exchanger (53a) are compared, the evaporation temperature of the cooling heat exchanger (53b, 81) is generally low. Therefore, when the pressures of the low-pressure refrigerant flowing through the first low-pressure line (102) and the second low-pressure line (101) are compared, the pressure of the low-pressure refrigerant in the first low-pressure line (102) is reduced.

  Further, the intermediate superheat degree setting means (77) is configured so that the intermediate pressure refrigerant after passing through the pressure reducing side flow path (28b) of the supercooling heat exchanger (28) is relatively similar to the eighth invention. An appropriate value that does not cause an excessive overheating state or a wet state is set as the intermediate superheating degree target value Tgsm.

  In the seventeenth aspect, the intermediate pressure control unit (59) or the intermediate superheat degree control unit (60) is selected based on the startup state of the compressors (21a, 21b, 21c). When the intermediate pressure control unit (59) is selected, the pressure in the injection circuit (40) is controlled to be always higher than the pressure in the first and second low pressure lines (102, 101), When the intermediate superheat degree control unit (60) is selected, control is performed so that the intermediate pressure refrigerant superheat degree on the decompression side flow path (28b) side in the supercooling heat exchanger (28) is constant at the target value. Is done.

  In an eighteenth aspect based on the seventeenth aspect, the third control unit (18) is configured such that the first compressor (21a, 21b) and the second compressor (21c) are both activated. The intermediate pressure control unit (59) is selected to execute control.

  Here, when both the first compressor (21a, 21b) and the second compressor (21c) are activated, the pressure of the low-pressure refrigerant flowing through the first low-pressure line (102) is increased. 2 The pressure of the low-pressure refrigerant flowing through the low-pressure line (101) is lower, and the suction pressure of the first compressor (21a, 21b) is also lower than the suction pressure of the second compressor (21c). Accordingly, the pressure at the intermediate port of the first compressor (21a, 21b) is also lower than the pressure at the intermediate port of the second compressor (21c).

  Therefore, the low-pressure refrigerant sucked into the second compressor (21c) from the second low-pressure line (101) is compressed by the second compressor (21c) while being compressed by the second compressor (21c). ) Flow out of the intermediate port (7) and backflow to the intermediate port (5, 6) of the first compressor (21a, 21b) through the injection circuit (40).

  In the eighteenth invention, when the first compressor (21a, 21b) and the second compressor (21c) are both activated, the intermediate pressure control unit (59) causes the pressure reducing means (29). By changing the opening degree, the pressure of the injection circuit (40) is controlled so as to be always higher than the pressures of the first and second low-pressure lines. Therefore, it is possible to prevent the refrigerant from flowing back from the second compressor (21c) to the first compressor (21a, 21b) as described above.

  In a nineteenth aspect based on the seventeenth or eighteenth aspect, the third control unit (18) is configured such that one of the first compressor (21a, 21b) and the second compressor (21c) is activated. The intermediate superheat control unit (60) is selected and the control is executed.

  Here, when one of the first compressor (21a, 21b) and the second compressor (21c) is activated, the first compression is performed from the second compressor (21c) as described above. The refrigerant does not flow back to the machine (21a, 21b).

  In the nineteenth invention, when one of the first compressor (21a, 21b) and the second compressor (21c) is activated, the second compressor (21c) to the first compressor Since it is not necessary to consider the reverse flow of the refrigerant to (21a, 21b), the intermediate superheat degree control unit (60) adjusts the opening of the decompression means (29). Thereby, the intermediate-pressure refrigerant superheat degree on the decompression side flow path (28b) side in the supercooling heat exchanger (28) is maintained at an appropriate value.

  According to a twentieth aspect, in any one of the seventeenth to nineteenth aspects, the discharge state detecting means (61, 61) detects at least one of the discharge temperature and the discharge superheat degree in the compressors (21a, 21b, 21c). 66) and discharge state setting means (76) for setting a discharge target value Tm for at least one of the discharge temperature and the discharge superheat degree in each of the compressors (21a, 21b, 21c), and the discharge state A second discharge target control section (56b) for changing the opening of the flow rate adjusting means (30a, 30b, 30c) so that the detection value Td of the detection means (61, 66) becomes the discharge target value Tm; The second overheating avoidance control unit (78b) for increasing the opening degree of the adjusting means (30a, 30b, 30c) than the present time, and the second overheating avoidance control unit (30a, 30b, 30c) for decreasing the opening degree of the flow rate adjusting means (30a, 30b, 30c). 2 Wetting avoidance control unit (79b) and the refrigerant state value of the refrigerant in the refrigerant circuit (10) are within a predetermined range When the second discharge target control unit (56b) is selected and the refrigerant state value exceeds a predetermined range, the second overheat avoidance control unit (78b) or the second wetness avoidance control unit (79b) And a fourth control unit (19) that executes control by selecting the item.

  Here, the discharge state setting means (76) sets, as the discharge target value Tm, an appropriate value at which each of the compressors (21a, 21b, 21c) does not undergo a relatively excessive overheating operation or a wet operation.

  In the twentieth invention, based on the refrigerant state value of the refrigerant circuit (10), three control units (second discharge target control unit (56b), second overheat avoidance control unit (78b), and second wetness avoidance control). Part (79b)) is selected.

  And when the said 2nd discharge target control part (56b) is selected, it controls so that the discharge temperature or discharge superheat degree of each compressor (21a, 21b, 21c) becomes fixed with a target value, When the second overheat avoidance control unit (78b) is selected, the flow rate adjusting means (30a, 30b, 30c) is controlled so that the opening degree is larger than the present, and the second wetness avoidance control unit (79b) ) Is selected, the flow rate adjusting means (30a, 30b, 30c) is controlled to be smaller than the current opening.

  In a twenty-first aspect based on the twentieth aspect, the fourth control unit (19) is configured such that the detection value Td of the discharge state detection means (61, 66) is set to be higher than the discharge target value Tm. At least one of a case where the detected value Tgsh of the intermediate superheat degree detecting means (75) is larger than an upper limit side threshold value Tgshmax set larger than the intermediate superheat degree target value Tgshm. In this case, the second overheat avoiding control unit (78b) is selected and executed to perform control.

  Here, as the refrigerant state value of the refrigerant circuit (10), at least one of the detection value Td of the discharge state detection means (61, 66) and the detection value Tgsh of the intermediate superheat degree detection means (75) is used. Further, upper limit threshold values Tdmax and Tgshmax set larger than the target value Tm corresponding to the detected values Td and Tgsh are used as the maximum values within the predetermined range in the refrigerant state value.

  In the twenty-first aspect, the discharge temperature or the discharge superheat degree as the refrigerant state value becomes too high, and the detected value Td or the detected value Tgsh exceeds the upper limit side threshold value Tdmax or Tgshmax. 21a, 21b, 21c) is in an abnormal overheat operation state, the second overheat avoidance control unit (78b) causes the compressor (21a, 21b, 21c) in the abnormal overheat operation state to The opening degree of the corresponding flow regulating valve (30a, 30b, 30c) is adjusted, and the opening degree is forcibly increased.

  In a twenty-second aspect based on the twentieth or twenty-first aspect, the fourth control unit (19) sets the detection value Td of the discharge state detection means (61, 66) to be smaller than the discharge target value Tm. When the detection value Tgsh of the intermediate superheat degree detection means (75) is further smaller than the lower limit side threshold value Tgshmin set to be smaller than the intermediate superheat degree target value Tgshm. At least one of the above, the second wetting avoidance control unit (79b) is selected to execute control.

  Here, lower threshold values Tdmin and Tgshmin set smaller than the target value Tm corresponding to the detected values Td and Tgsh are used as the minimum values within the predetermined range in the refrigerant state value.

  In the twenty-second aspect, the discharge temperature or the discharge superheat degree as the refrigerant state value becomes too low, and the detection value Td or the detection value Tgsh exceeds the lower limit side threshold value Tdmin or Tgshmin. 21a, 21b, 21c) is in an abnormal wet operation state, the second wetness avoidance control unit (79b) causes the compressor (21a, 21b, 21c) in the abnormal wet operation state to The opening degree of the corresponding flow regulating valve (30a, 30b, 30c) is adjusted, and the opening degree is forcibly reduced.

  In a twenty-third aspect, in any one of the twentieth to twenty-second aspects, the fourth control unit (19) is configured such that the detection value Td of the discharge state detection means (61, 66) is greater than the discharge target value Tm. Is less than or equal to the lower limit threshold Tdmin set smaller than the upper limit threshold Tdmax set larger than the target discharge value Tm, the second discharge target control unit (56b) is selected. And is configured to execute control.

  In the twenty-third aspect, the second discharge target control unit (56b) adjusts the flow rate corresponding to the compressor (21a, 21b, 21c) having a discharge temperature or discharge superheat degree as the refrigerant state value within a predetermined range. The opening of the valve (30a, 30b, 30c) is changed

  According to the present invention, by providing the flow rate adjusting means (30a, 30b, 30c), the flow rate of the refrigerant flowing through the branch pipes (37a, 37b, 37c) after being depressurized by the pressure reducing means (29) is changed. It can be adjusted for each compressor (21a, 21b, 21c). Therefore, appropriate injection can be performed for each compressor (21a, 21b, 21c).

  Further, according to the second invention, since the flow rate adjusting means (30a, 30b, 30c) is provided in all the branch pipes (37a, 37b, 37c), the flow rate adjusting means selected according to the operating state of the refrigeration apparatus. The opening degree of (30a, 30b, 30c) can be adjusted. Therefore, proper injection can be performed on the compressors (21a, 21b, 21c) corresponding to the selected flow rate adjusting means (30a, 30b, 30c).

  Further, according to the third aspect of the invention, the degree of supercooling of the high-pressure refrigerant can be increased while injecting into each compressor (21a, 21b, 21c). Thereby, compared with the case where the said supercooling heat exchanger (28) is not provided, it can inject into a some compressor (21a, 21b, 21c), improving the COP of the said freezing apparatus.

  Further, according to the fourth aspect of the invention, the refrigerant is injected into each compressor (21a, 21b, 21c) via the injection circuit (40), and the compressor (21a, 21b, 21c) is refrigerated. Machine oil can be returned.

  According to the fifth aspect of the present invention, the flow rate adjusting means (30a, 30b, 30c) is constituted by a flow rate adjusting valve so that the opening degree of the valve can be freely changed between fully open and fully closed. Can do. Thereby, the quantity of the refrigerant | coolant which passes a valve can be adjusted accurately, and a more appropriate injection can be performed with respect to each compressor (21a, 21b, 21c).

  According to the sixth aspect of the present invention, the flow rate adjusting means (30a, 30b, 30c) is constituted by an on-off valve so that the flow rate adjusting means (30a, 30b, 30c) can be changed in opening degree. The configuration of the valve can be simplified as compared with the case of the configuration. Thereby, the injection amount of each compressor (21a, 21b, 21c) can be adjusted at low cost.

  According to the seventh aspect of the invention, as described above, the variable capacity compressor (21a) changes the amount of refrigerant sucked from the intermediate port (5) due to a change in its operating capacity. . Therefore, with respect to the variable capacity compressor (21a), the injection amount can be accurately adjusted by the flow rate adjusting valve. On the other hand, since the operating capacity of the fixed capacity type compressor (21b, 21c) does not change, the amount of refrigerant sucked from the intermediate port (6, 7) is greater than that of the variable capacity type compressor (21a). Also difficult to change. Therefore, for this fixed capacity type compressor (21b, 21c), it is not always necessary to accurately adjust the injection amount with the flow rate adjusting valve. Therefore, the cost of the refrigeration apparatus can be reduced by using an on-off valve having a simpler structure than the flow rate adjusting valve.

  According to the eighth invention, the control means (9) causes the injection of each compressor (21a, 21b, 21c) according to the temperature of the refrigerant discharged from the plurality of compressors (21a, 21b, 21c). The amount of refrigerant discharged in each compressor (21a, 21b, 21c) can be adjusted within a predetermined temperature range by adjusting the amount. Thereby, more appropriate injection can be performed to each compressor (21a, 21b, 21c).

  Further, according to the ninth invention, the first control section (16) causes the pressure reducing means (16a) to reduce the discharge temperature or discharge superheat degree of each compressor (21a, 21b, 21c) to be constant at a target value. 29) or the pressure reducing means (29) is controlled so that the intermediate pressure refrigerant superheat degree on the pressure reducing side flow path (28b) side in the supercooling heat exchanger (28) is constant at a target value. be able to. By properly using these two controls, more appropriate injection can be performed for each compressor (21a, 21b, 21c).

  According to the tenth invention, when one of the plurality of compressors (21a, 21b, 21c) is in a relatively excessive overheating operation, the first discharge target control unit ( The opening degree of the pressure reducing means (29) is changed by 56a). As a result, the discharge temperature or discharge superheat degree of the compressor (21a, 21b, 21c) can be maintained at an appropriate value, and all the compressors (21a, 21b, 21c) can be operated in a relatively excessive overheat. Thus, proper injection can be performed on the compressors (21a, 21b, 21c).

  According to the eleventh aspect of the invention, when all the compressors (21a, 21b, 21c) are not in a relatively excessive superheat operation, the intermediate superheat degree control unit (60) controls the pressure reducing means. The opening degree of (29) is changed. Thereby, the intermediate-pressure refrigerant superheat degree on the decompression side flow path (28b) side in the supercooling heat exchanger (28) can be maintained at an appropriate value.

  For example, when one of the compressors (21a, 21b, 21c) is in a relatively excessive overheating operation, the first discharge target control unit (56a) of the ninth invention is all After the compressor (21a, 21b, 21c) of the engine is relatively overheated, the decompression means (29) is opened by the intermediate superheat degree control unit (60) of the tenth invention. The degree is changed. Thereby, the intermediate-pressure refrigerant superheat degree can be maintained at an appropriate value.

  According to the twelfth aspect, for example, one of the plurality of compressors (21a, 21b, 21c) is in a relatively excessive overheat operation, but approaches the wet operation from the excessive overheat operation. If so, the intermediate superheat control unit (60) changes the opening of the decompression means (29) regardless of the operating state of the compressor (21a, 21b, 21c). Thus, the operation start of the intermediate superheat degree control unit can be accelerated. Thereby, the intermediate-pressure refrigerant superheat degree on the decompression side flow path (28b) side in the supercooling heat exchanger (28) can be quickly maintained at an appropriate value.

  Further, according to the thirteenth aspect, when the refrigerant state value exceeds a predetermined range and the compressor (21a, 21b, 21c) is operating abnormally, the refrigerant state value falls within the predetermined range. The pressure reducing means (29) is controlled by the avoidance control unit (58). Thereby, more appropriate injection can be performed to each compressor (21a, 21b, 21c) while avoiding the refrigeration apparatus from continuing abnormal operation.

  According to the fourteenth aspect of the invention, the discharge temperature or discharge superheat degree of the compressor (21a, 21b, 21c) becomes too high, and the compressor (21a, 21b, 21c) enters an abnormal overheat operation state. When falling, the opening degree of the decompression means (29) is adjusted by the first overheating avoidance control unit (78a), and the opening degree is forcibly increased. As a result, the intermediate pressure refrigerant flowing from the intermediate ports (5, 6, 7) of the compressor (21a, 21b, 21c) increases, and the abnormal overheating operation state of the compressor (21a, 21b, 21c) is increased. It can be avoided to continue.

  According to the fifteenth aspect of the invention, the discharge temperature or discharge superheat degree of the compressors (21a, 21b, 21c) becomes too low, and the compressor (21a, 21b, 21c) is in an abnormal wet operation state. In this case, the opening degree of the decompression means (29) is adjusted by the first wetting avoidance control unit (79a), and the opening degree is forcibly reduced. Thereby, the intermediate pressure refrigerant flowing from the intermediate ports (5, 6, 7) of the compressors (21a, 21b, 21c) can be reduced, and the abnormal wet operation state can be avoided from continuing.

  According to the sixteenth aspect of the invention, the discharge temperature or discharge superheat degree of the compressors (21a, 21b, 21c) can be brought close to each other by the second control unit (17). As a result, the discharge temperature or discharge superheat degree of the plurality of compressors (21a, 21b, 21c) becomes substantially the same temperature, compared to the case where the discharge temperature or discharge superheat degree differs for each compressor (21a, 21b, 21c). Thus, it becomes easy to perform operation control on the refrigeration apparatus.

  According to the seventeenth aspect of the invention, the pressure of the injection circuit (40) is always controlled to be higher than the pressure of the first and second low pressure lines (102, 101) by the third control unit (18). Alternatively, the intermediate pressure refrigerant superheat degree on the decompression side flow path (28b) side in the supercooling heat exchanger (28) is controlled to be constant at the target value. By properly using these two controls, more appropriate injection can be performed for each compressor (21a, 21b, 21c).

  According to an eighteenth aspect of the invention, when both the first compressor (21a, 21b) and the second compressor (21c) are activated, the intermediate pressure control unit (59) By changing the opening degree of the decompression means (29), the pressure (intermediate pressure) of the injection circuit (40) can always be higher than the pressures (low pressure) of the first and second low pressure lines. Thereby, injection is performed to each compressor (21a, 21b, 21c) while preventing the reverse flow of the refrigerant from the second compressor (21c) to the first compressor (21a, 21b) as described above. be able to.

  According to the nineteenth invention, when one of the first compressor (21a, 21b) and the second compressor (21c) is activated, the second compressor (as described above) There is no reverse flow of refrigerant from 21c) to the first compressor (21a, 21b). Therefore, by changing the opening of the pressure reducing means (29) not by the intermediate pressure control unit (59) but by the intermediate superheat degree control unit (60), the pressure reducing side in the supercooling heat exchanger (28) Injection can be performed to each compressor (21a, 21b, 21c) while maintaining the intermediate pressure refrigerant superheat degree on the flow path (28b) side at an appropriate value.

  Further, according to the twentieth invention, whether the discharge temperature or the discharge superheat degree of each compressor (21a, 21b, 21c) is controlled to be constant at the target value by the fourth control unit (19), Control the opening degree of the flow rate adjusting means (30a, 30b, 30c) to be larger than the current level, or control the opening degree of the flow rate adjusting means (30a, 30b, 30c) to be smaller than the current level. can do. By properly using these three controls, more appropriate injection can be performed for each compressor (21a, 21b, 21c).

  Further, according to the twenty-first aspect, the discharge temperature or discharge superheat degree of each compressor (21a, 21b, 21c) becomes too high, and each compressor (21a, 21b, 21c) operates abnormally. The flow rate adjusting valve (30a, 30b, 30c) corresponding to the compressor (21a, 21b, 21c) that has entered the abnormal overheat operation state by the second overheat avoidance control unit (78b) The opening of is forcibly increased. Thereby, the intermediate pressure refrigerant flowing in from the intermediate ports (5, 6, 7) of the compressors (21a, 21b, 21c) increases, and the abnormal overheating operation state can be avoided.

  Further, according to the twenty-second aspect, the discharge temperature or discharge superheat degree of the compressors (21a, 21b, 21c) becomes too low, and the compressors (21a, 21b, 21c) operate abnormally. The flow rate adjusting valve (30a, 30b, 30c) corresponding to the compressor (21a, 21b, 21c) in the abnormal wet operation state by the second wetness avoidance control unit (79b) The opening of is forcibly reduced. Thereby, the intermediate pressure refrigerant flowing from the intermediate ports (5, 6, 7) of the compressors (21a, 21b, 21c) is reduced, and the abnormal wet operation state can be avoided.

  According to the twenty-third aspect, when the discharge temperature or the discharge superheat degree of each compressor (21a, 21b, 21c) is within a predetermined range, the second discharge target control unit (56b) The opening degree of the flow rate adjusting valve (30a, 30b, 30c) corresponding to the compressor (21a, 21b, 21c) within the predetermined range is changed. As a result, an appropriate amount of intermediate pressure refrigerant flows from the intermediate ports (5, 6, 7) of the compressors (21a, 21b, 21c), and the discharge temperature or discharge superheat of the compressors (21a, 21b, 21c). The degree can be kept at an appropriate value.

2 is a refrigerant circuit diagram of the refrigeration apparatus according to Embodiment 1. FIG. FIG. 6 is a refrigerant circuit diagram of a refrigeration apparatus according to Embodiment 2. It is a refrigerant circuit figure of the refrigerating device concerning other embodiments. It is a refrigerant circuit figure of the refrigerating device concerning the modification of this Embodiment 1. It is a control flowchart of the said 1st control part. It is a control flow figure of the 1st wetness avoidance control part in the above-mentioned avoidance control part. It is a control flow figure of the 1st overheating avoidance control part in the above-mentioned avoidance control part. It is a control flowchart of the said 2nd control part. It is a refrigerant circuit figure of the refrigerating device concerning the modification of this Embodiment 2. It is a control flowchart of the said 3rd control part. It is a control flowchart of the said 4th control part.

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

  The refrigeration apparatus (1) of the present embodiment cools a plurality of refrigerated warehouses. As shown in FIG. 1, the refrigeration apparatus (1) includes an external unit (2), a plurality of internal units (3), and a controller (9). The outside unit (2) is installed outdoors, and each inside unit (3) is installed in each refrigerated warehouse. The outside unit (2) is provided with an outside circuit (20), and each inside unit (3) is provided with an inside circuit (50). The refrigerant circuit (10) of the refrigeration apparatus (1) is configured by connecting a plurality of internal circuits (50) in parallel to the external circuit (20) so as to perform a vapor compression refrigeration cycle. Has been.

  Specifically, the external circuit (20) and the internal circuit (50) are connected to each other by a first connection pipe (14) and a second connection pipe (15). One end of the first connection pipe (14) is connected to a first closing valve (11) provided at one end of the external circuit (20), and the other end of the first connection pipe (14) is branched. And it is connected to one end of each internal circuit (50), respectively. One end of the second connection pipe (15) is connected to a second closing valve (12) provided at the other end of the external circuit (20), and the other of the second connection pipe (15). The end branches and is connected to the other end of each internal circuit (50).

<Outside unit>
The external circuit (20) of the external unit (2) includes three compressors (21a, 21b, 21c) from first to third, a four-way switching valve (24), and external heat. An exchanger (25), a receiver (27), a supercooling heat exchanger (28), a supercooling pressure reducing valve (pressure reducing means) (29), and an outdoor expansion valve (31) are provided.

  All compressors (21a, 21b, 21c) are all hermetic high-pressure dome type scroll compressors, and each compressor (21a, 21b, 21c) has an intermediate port that opens to an intermediate pressure position. A compression mechanism including a compression chamber having (5, 6, 7) and an electric motor for driving the compression mechanism are provided.

  The electric motor of the first compressor (21a) is connected to an inverter that can freely change the rotation speed of the electric motor within a predetermined range. The inverter can adjust the rotational speed of the electric motor to increase or decrease the operating capacity of the first compressor (21a). The motors of the second and third compressors (21b, 21c) are not provided with an inverter, and the rotation speed of the motors is fixed. Therefore, the operating capacity of the above-mentioned 2, 3 compressors (21b, 21c) is constant.

  Discharge pipes (discharge pipes) (22a, 22b, 22c) are connected to the discharge sides of the compressors (21a, 21b, 21c), respectively. Each discharge pipe (22a, 22b, 22c) is provided with a check valve (CV). These discharge pipes (22a, 22b, 22c) are connected to the first port of the four-way switching valve (24) via the discharge junction pipe (22). The check valve (CV) is provided in such a direction as to allow only the refrigerant flow from each compressor (21a, 21b, 21c) toward the discharge junction pipe (22).

  Each of the discharge pipes (22a, 22b, 22c) is provided with an oil separator (38a, 38b, 38c) on the upstream side of the check valve (CV). Each said oil separator (38a, 38b, 38c) is for isolate | separating refrigeration oil from the high pressure refrigerant | coolant of a compressor (21a, 21b, 21c). Each oil separator (38a, 38b, 38c) is connected to an oil outflow pipe (39a, 39b, 39c) for flowing out the refrigerating machine oil. These three oil spill pipes (39a, 39b, 39c) join at one end of the oil spill join pipe (39d). The other end of the oil outflow merging pipe (39d) is connected to a connection part of a gas vent pipe (48) in a second injection pipe (38) described later. Each oil outflow pipe (39a, 39b, 39c) is provided with a check valve (CV) and a capillary tube (CP) in order from the oil separator (38b, 38c) side.

  The three oil outflow pipes (39a, 39b, 39c) and the oil outflow confluence pipe (39d) constitute an oil return circuit (39). The check valves (CV) provided in the oil outflow pipes (39a, 39b, 39c) are provided in a direction that allows only the flow of the refrigerating machine oil toward the oil outflow merge pipe (39d).

  Suction pipes (23a, 23b, 23c) are connected to the suction sides of the compressors (21a, 21b, 21c), respectively. These suction pipes (23a, 23b, 23c) are connected to the second port of the four-way switching valve (24) via the suction junction pipe (23).

  One end of the external heat exchanger (25) is connected to the third port of the four-way switching valve (24), and the second closing valve (12) is connected to the fourth port of the four-way switching valve (24). Has been. The four-way switching valve (24) includes a first state (state indicated by a solid line in FIG. 1) in which the first port and the third port communicate with each other, and the second port and the fourth port communicate with each other; And the fourth port communicate with each other and the second port and the third port communicate with each other.

  The other end of the external heat exchanger (25) is connected to the top of the receiver (27) via the first refrigerant pipe (32). The external heat exchanger (25) is a cross-fin type fin-and-tube heat exchanger. An outdoor fan (26) is provided in the vicinity of the outdoor heat exchanger (25). The outdoor heat exchanger (25) is configured to exchange heat between the outdoor air sent by the outdoor fan (26) and the refrigerant flowing in the outdoor heat exchanger (25). The first refrigerant pipe (32) is provided with a check valve (CV), and the check valve (CV) only sends the refrigerant flow from the external heat exchanger (25) to the receiver (27). It is provided in an allowable direction.

  The supercooling heat exchanger (28) has a high pressure side flow path (28a) and a pressure reduction side flow path (28b), and flows through the high pressure side flow path (28a) and the pressure reduction side flow path (28b). The refrigerant is configured to exchange heat.

  The inflow end of the high-pressure channel (28a) is connected to the bottom of the receiver (27). The outflow end of the high-pressure channel (28a) is connected to the first closing valve (11) via the second refrigerant pipe (high-pressure line) (33). The second refrigerant pipe (33) is provided with a check valve (CV), and the check valve (CV) is a refrigerant directed from the supercooling heat exchanger (28) to the first closing valve (11). It is provided in a direction that allows only the flow of air. On the other hand, the inflow end and the outflow end of the decompression side flow path (28b) are each connected to the injection circuit (40) according to the present invention.

  The injection circuit (40) is for injecting refrigerant into the compressors (21a, 21b, 21c). The first injection pipe (main pipe) (37), the second injection pipe (38), and the second 1, second and third branch injection pipes (branch pipes) (37a, 37b, 37c).

  The first injection pipe (37) branches from the upstream side of the check valve (CV) in the second refrigerant pipe (33), and is connected to the inflow end of the pressure reducing side flow path (28b). The first injection pipe (37) is provided with a supercooling pressure reducing valve (pressure reducing means) (29). The supercooling pressure reducing valve (29) is an electronic expansion valve having a variable opening.

  One end of the second injection pipe (38) is connected to the outflow end of the pressure reducing side channel (28b), and the other end of the second injection pipe (38) is connected to the first, second, and third branch injections. Branches to piping (37a, 37b, 37c). The first, second, and third branch injection pipes (37a, 37b, 37c) are connected to the intermediate ports (5, 6, 7) of the compressors (21a, 21b, 21c), respectively.

  The first, second, and third branch injection pipes (37a) are respectively provided with first, second, and third flow rate adjusting valves (flow rate adjusting means) (30a, 30b, 30c). The first, second, and third flow rate adjustment valves (30a, 30b, 30c) are configured by electronic expansion valves with variable opening.

  As described above, the receiver (27) is disposed between the external heat exchanger (25) and the supercooling heat exchanger (28), and when the four-way switching valve (24) is in the first state. The high-pressure refrigerant condensed in the external heat exchanger (25) can be temporarily stored. One end of a gas vent pipe (48) having a solenoid valve (SV) is connected to the top of the receiver (27). The other end of the gas vent pipe (48) is connected in the middle of the second injection pipe (38). The gas vent pipe (48) is configured such that the gas refrigerant flows from the receiver (27) to the second injection pipe (38) by opening the solenoid valve (SV).

  One end of the third refrigerant pipe (35) is connected between the check valve (CV) and the first closing valve (11) in the second refrigerant pipe (33). The other end of the third refrigerant pipe (35) is connected to the downstream side of the check valve (CV) in the first refrigerant pipe (32). The third refrigerant pipe (35) is provided with a check valve (CV), and the check valve (CV) is only for the flow of refrigerant from the first closing valve (11) to the first refrigerant pipe (32). It is provided in a direction that allows

  A fourth refrigerant pipe (36) that bypasses the receiver (27) and the supercooling heat exchanger (28) is connected between the first refrigerant pipe (32) and the second refrigerant pipe (33). Yes. One end of the fourth refrigerant pipe (36) is connected to the upstream side of the check valve (CV) in the first refrigerant pipe (32). The other end of the fourth refrigerant pipe (36) is connected to the upstream side of the connection portion of the first injection pipe (37) in the second refrigerant pipe (33). The fourth refrigerant pipe (36) is provided with an outdoor expansion valve (31). The outdoor expansion valve (31) is an electronic expansion valve whose opening degree can be adjusted.

  The external circuit (20) is provided with various sensors and pressure switches. Specifically, each discharge pipe (22a, 22b, 22c) is provided with a discharge pipe temperature sensor (discharge refrigerant temperature detection means) (61) and a high-pressure switch (62). The discharge pipe temperature sensor (61) detects the temperature of the discharge pipe (22a, 22b, 22c), and the high pressure switch (62) detects the discharge pressure, and when the abnormally high pressure is detected, the refrigeration system (1) is urgently stopped It is something to be made. The suction junction pipe (23) is provided with a suction pipe temperature sensor (63) for detecting the temperature of the suction junction pipe (23).

  A discharge pressure sensor (21a, 21b, 21c) for detecting the discharge pressure of the compressor (21a, 21b, 21c) is provided at the junction of each discharge pipe (22a, 22b, 22c) (that is, the inflow end of the discharge junction pipe (22)). 64). A suction pressure sensor (65) for detecting the suction pressure of the compressors (21a, 21b, 21c) is provided at the junction of each suction pipe (23a, 23b, 23c). In the vicinity of the outdoor fan (26), an outside air temperature sensor (67) for detecting the outside air temperature is provided.

  The second refrigerant pipe (33) is provided with a first liquid temperature sensor (68). A second liquid temperature sensor (69) is provided downstream of the supercooling pressure reducing valve (29) in the first injection pipe (37). Each liquid temperature sensor (68, 69) detects the temperature of the liquid refrigerant.

<Inside unit>
The two internal units (3) are configured similarly. Each in-compartment unit (3) is provided with an in-compartment circuit (50). The internal circuit (50) is provided with a heating pipe (51), an internal expansion valve (52), and an internal heat exchanger (53) in order from one end side to the other end side.

  The heating pipe (51) is attached to a drain pan (55) provided below the internal heat exchanger (53). The drain pan (55) collects the condensed water dripping from the internal heat exchanger (53). Here, the heating pipe (51) is attached to the drain pan (55) because the heat of the high-pressure refrigerant flowing through the heating pipe (51) flows through the ice blocks generated by freezing of the condensed water. It is for melting by using.

  The internal expansion valve (52) is an electronic expansion valve whose opening degree can be adjusted.

  The internal heat exchanger (53) is a cross-fin type fin-and-tube heat exchanger, and an internal fan (54) is provided in the vicinity of the internal heat exchanger (53). It has been. The internal heat exchanger (53) is configured to exchange heat between the internal air sent by the internal fan (54) and the refrigerant flowing through the internal heat exchanger (53). Has been.

  The internal circuit (50) is provided with three temperature sensors. Specifically, the heat transfer tube of the internal heat exchanger (53) is provided with an evaporation temperature sensor (72) for detecting the evaporation temperature of the refrigerant. A refrigerant temperature sensor (73) for detecting the temperature of the gas refrigerant is provided in the vicinity of the gas side end of the internal circuit (50). In the vicinity of the internal fan (54), an internal temperature sensor (74) for detecting the internal temperature is provided.

<controller>
The controller (control means) (9) receives detection values of the sensors (61 to 69, 71 to 74) and the high pressure switch (62) described above. Based on these detected values, the controller (9) controls the drive of the compressors (21a, 21b, 21c) and the fans (26, 54) and various valves (24, 29, 31, 52, SV). ), The opening degree adjustment, and the operation frequency of the inverter are controlled, and the operation of the refrigeration apparatus (1) is controlled.

  For example, in the controller (9), the opening adjustment of the first, second, and third flow rate adjusting valves (30a, 30b, 30c) is performed based on each discharge pipe temperature sensor (61). Specifically, the valve opening degree of each flow rate adjustment valve (30a, 30b, 30c) is adjusted so that the temperature detected by the discharge pipe temperature sensor (61) falls within a predetermined temperature range. If there is a compressor (21a, 21b, 21c) whose discharge refrigerant temperature is higher than the specified temperature range, the flow control valve (30a, 30b, 30c) corresponding to the compressor (21a, 21b, 21c) is opened. Increase the degree to increase the injection amount of the compressor (21a, 21b, 21c). As a result, the temperature of the discharged refrigerant can be lowered to a predetermined temperature range.

  If there is a compressor (21a, 21b, 21c) whose discharge refrigerant temperature is lower than a predetermined temperature range, the flow rate adjusting valve (30a, 30b, 30c) corresponding to the compressor (21a, 21b, 21c) To reduce the injection amount of the compressor (21a, 21b, 21c). Thereby, the temperature of a discharge refrigerant | coolant can be raised and can be in a predetermined temperature range.

  Here, since the operating frequency of the first compressor is configured to be variable by an inverter, the temperature of the discharged refrigerant is likely to be lower than a predetermined temperature range. As described above, when the operating frequency of the first compressor (21a) is lowered, the intermediate pressure refrigerant of the injection circuit (40) is increased by the amount that the opening time of the intermediate port (5) is increased. This is because it is easy to suck into the first compressor (21a).

  Therefore, when the operating capacity of the first compressor (21a) is reduced, the temperature of the discharged refrigerant decreases, so that the opening degree of the first flow rate adjustment valve (30a) is reduced according to this temperature change. As a result, a large amount of refrigerant is prevented from being injected toward the first compressor (21a).

-Driving action-
The operation of the refrigeration apparatus (1) will be described below. The refrigeration apparatus (1) is configured to execute control by selecting a cooling operation for maintaining the inside of the refrigerated warehouse at a predetermined temperature (for example, 5 ° C.).

  In this cooling operation, at least one of the three compressors (21a, 21b, 21c) is driven, and the interior is cooled by each interior unit (3). Here, a case where all three compressors (21a, 21b, 21c) are driven will be described. In this cooling operation, the four-way selector valve (24) is set to the first state. Moreover, while the opening degree of the supercooling pressure reducing valve (29) and the internal expansion valve (52) is appropriately adjusted, the outdoor expansion valve (31) is set to a fully closed state. Each solenoid valve (SV) is opened and closed according to the operating state.

  In this cooling operation, when the first, second, and third compressors (21a, 21b, 21c) are driven, the refrigerant flows in the direction of the solid arrow shown in FIG. 1 in the refrigerant circuit (10). At this time, the external heat exchanger (25) functions as a condenser, and the internal heat exchanger (53) functions as an evaporator, so that the vapor compression refrigeration is performed in the refrigerant circuit (10). A cycle is performed.

  Specifically, the high-pressure gas refrigerant compressed by the first, second, and third compressors (21a, 21b, 21c) is discharged from the discharge pipes (22a, 22b, 22c). The high-pressure gas refrigerant discharged from each discharge pipe (22a, 22b, 22c) flows into each oil separator (38a, 38b, 38c). In each oil separator (38a, 38b, 38c), the refrigeration oil is separated from the high-pressure refrigerant. The separated refrigeration oil is temporarily stored in each oil separator (38a, 38b, 38c), and then passed through each oil outflow pipe (39a, 39b, 39c) and the oil outflow junction pipe (39d). It flows into the injection pipe (38). The refrigerating machine oil that has flowed into the second injection pipe (38) is divided and passes through the branch injection pipes (37a, 37b, 37c), and then passes through the intermediate ports (5, 6, 7). It is sucked into the compressors (21a, 21b, 21c).

  On the other hand, the high-pressure refrigerant from which the refrigeration oil has been separated flows out from the oil separators (38a, 38b, 38c) and joins in the discharge junction pipe (22). The high-pressure refrigerant joined in the discharge junction pipe (22) flows into the external heat exchanger (25) through the four-way switching valve (24). In the outdoor heat exchanger (25), the high-pressure refrigerant is condensed by exchanging heat with outdoor air. The condensed refrigerant passes through the first refrigerant pipe (32), the receiver (27), and the high-pressure channel (28a) of the supercooling heat exchanger (28) in this order, and then flows into the second refrigerant pipe (33). . A part of the refrigerant flowing into the second refrigerant pipe (33) flows to the first injection pipe (37), and the other flows to the first connection pipe (14) via the first shut-off valve (11).

  The high-pressure refrigerant that has flowed toward the first injection pipe (37) is depressurized to a predetermined pressure by the supercooling pressure reducing valve (29) to become an intermediate pressure refrigerant, and then the supercooling heat exchanger (28). Into the decompression side flow path (28b). In the supercooling heat exchanger (28), the intermediate-pressure refrigerant and the high-pressure refrigerant flowing through the high-pressure side flow path (28a) exchange heat. As a result, the high-pressure refrigerant is cooled to increase the degree of supercooling, while the intermediate-pressure refrigerant is heated to become a gas refrigerant. This gas refrigerant flows out of the supercooling heat exchanger (28) and then splits into the first, second, and third branch injection pipes (37a, 37b, 37c) via the second injection pipe (38). .

  The intermediate pressure refrigerant flowing into the branch injection pipes (37a, 37b, 37c) is adjusted in flow rate by the flow rate adjusting valves (30a, 30b, 30c), and then the compressors (21a, 21b, 21c) is injected into the compression chamber at the intermediate pressure position. Here, the controller (9) adjusts the valve opening degree of each flow rate adjusting valve (30a, 30b, 30c) so that the temperature detected by the discharge pipe temperature sensor (61) falls within a predetermined temperature range. The

  On the other hand, the high-pressure refrigerant that has flowed toward the first communication pipe (14) is divided into each internal circuit (50). The high-pressure refrigerant that has flowed into the internal circuit (50) flows through the heating pipe (51). At that time, in the drain pan (55), ice blocks in which condensed water has been frozen by the refrigerant flowing through the heating pipe (51) are melted by the refrigerant in the heating pipe (51). As a result, the high-pressure refrigerant flowing through the heating pipe (51) is further subcooled. The high-pressure refrigerant that has flowed out of the heating pipe (51) is depressurized by the internal expansion valve (52) to become low-pressure refrigerant, and then flows into the internal heat exchanger (53).

  In the internal heat exchanger (53), the low-pressure refrigerant evaporates by exchanging heat with the internal air. Thereby, the air in a warehouse is cooled. The refrigerant evaporated in each internal heat exchanger (53) flows again into the external circuit (20) through the second connection pipe (15). The low-pressure refrigerant that has flowed into the external circuit (20) flows to the suction junction pipe (23) via the four-way switching valve (24), and from the suction pipe (23a, 23b, 23c) to each compressor (21a, 21b, Inhaled to 21c). The low-pressure refrigerant sucked into the compressors (21a, 21b, 21c) is compressed to a predetermined pressure together with the intermediate-pressure refrigerant flowing from the intermediate ports (5, 6, 7), and becomes high-pressure refrigerant. The high-pressure refrigerant is discharged again from the compressors (21a, 21b, 21c). As the refrigerant circulates in this manner, a cooling operation for maintaining the inside of each refrigerated warehouse at a predetermined temperature is performed.

  When the four-way switching valve (24) is set from the first state to the second state, the refrigerant circulation direction is reversed. Thereby, the said external heat exchanger (25) becomes an evaporator and the said internal heat exchanger (53) becomes a condenser, and a reverse cycle defrost operation is also possible.

-Effect of Embodiment 1-
According to the first embodiment, by providing the flow rate adjusting valves (30a, 30b, 30c), the branch injection pipes (37a, 37b, 37c) are decompressed by the supercooling pressure reducing valve (29). The flow rate of the refrigerant flowing through can be adjusted for each compressor (21a, 21b, 21c). Therefore, it is possible to perform appropriate injection with respect to the compressors (21a, 21b, 21c).

  Further, according to the first embodiment, the control means (9) causes the injection of each compressor (21a, 21b, 21c) according to the temperature of the refrigerant discharged from the plurality of compressors (21a, 21b, 21c). The amount of refrigerant discharged in each compressor (21a, 21b, 21c) can be adjusted within a predetermined temperature range by adjusting the amount. Thereby, appropriate injection can be reliably performed with respect to each compressor (21a, 21b, 21c).

  Further, according to the first embodiment, by providing the supercooling heat exchanger (28), the refrigerant decompressed by the supercooling pressure reducing valve (29) is converted into a high-pressure refrigerant flowing through the refrigerant circuit (10). After the heat exchange, the above-mentioned compression chambers (4a, 4b, 4c) can be injected. Thereby, compared with the case where the said supercooling heat exchanger (28) is not provided, it can inject into a some compressor (21a, 21b, 21c), improving the COP of a freezing apparatus (1).

-Modification of Embodiment 1-
FIG. 4 is a refrigerant circuit according to a modification of the first embodiment. The configuration of the controller that controls the operation of the refrigeration apparatus (1) is different between the first embodiment and the modification. An intermediate refrigerant temperature sensor for measuring the temperature of the intermediate pressure refrigerant after passing through the pressure reducing side passage (28b) of the supercooling heat exchanger (28) is provided in the second injection pipe (38) of Modification 1. (70) and an intermediate pressure sensor (71) for measuring the pressure of the intermediate pressure refrigerant are provided.

  The controller (4) of the modified example of the first embodiment includes a first control unit (16), an avoidance control unit (58), and a second control unit (17). The opening degree of the supercooling pressure reducing valve (29) is adjusted by the first control unit (16) and the avoidance control unit (58), and the flow rate adjusting means (30a, 30b, 30c is adjusted by the second control unit (17). ) Is adjusted.

  The controller (4) includes a discharge pipe temperature sensor (61) and a discharge pressure sensor (64) as the discharge state detection means, an intermediate refrigerant temperature sensor (70) as the intermediate superheat degree detection means, and an intermediate The pressure sensor (71) is electrically connected. The controller (4) is provided with a discharge state setting section (discharge state setting means) (76) and an intermediate superheat degree setting section (intermediate superheat degree setting means) (77). The discharge state setting unit (76) sets a target value Tm of the discharge temperature of the compressor (21a, 21b, 21c), and the intermediate superheat setting unit (77) includes the injection circuit (40 ) Is set as a target value Tgshm for the superheat degree of the intermediate pressure refrigerant flowing through the refrigerant.

  Next, control operations of the first control unit (16), the avoidance control unit (58), and the second control unit (17) will be described with reference to the control flow diagrams of FIGS.

<First control unit>
The first control unit (16) includes a first discharge target control unit (56a) and an intermediate superheat degree control unit (60). The discharge temperature of the compressor (21a, 21b, 21c) and the injection circuit Based on the degree of superheat of the intermediate pressure refrigerant in (40), the first discharge target control section (56a) or the intermediate superheat degree control section (60) is selected to execute control.

  Specifically, as shown in FIG. 5, first, in step ST1, the largest value among the detection values Td1 to Td3 of the discharge pipe temperature sensor (61) is calculated, and the calculated value is the discharge pipe temperature. It is set as the maximum value Ttd of the sensor (61).

  Next, in step ST2, it is determined whether any one of the first, second, and third conditions is satisfied. Here, the first condition is a condition that the maximum value Ttd set in step ST1 is equal to or less than the target value Tm set by the discharge state setting unit (76) of the controller (4). The second condition is a condition that the maximum value Ttd in step ST1 is larger than the target value Tm, and the maximum value Ttd continuously decreases within the time t1.

  The third condition is that the maximum value Ttd in step ST1 is larger than a value obtained by adding a predetermined value Tdx to the target value Tm of the discharge state setting section (76), and the maximum value Ttd is larger than the target value Tm. It is a case where the detection value Tgsh of the intermediate superheat degree detection unit (75) is smaller than the predetermined intermediate superheat degree value Tgshs when it is smaller than the upper limit side threshold value Tdmax that is set to be large. It is a condition. The upper threshold Tdmax is set to a value that causes the compressor (21a, 21b, 21c) to perform an abnormal overheating operation when the maximum value Ttd in step ST1 exceeds the threshold Tdmax. .

  In step ST2, if any one of the first, second, and third conditions is satisfied, the process proceeds to step ST3. In step ST3, the detection value Tgsh of the intermediate refrigerant superheat degree detected based on the intermediate refrigerant temperature sensor (70) and the intermediate pressure sensor (71) and the target value Tgshm of the intermediate superheat degree setting unit (77). Based on the difference, a change amount dpls of the opening value in the supercooling pressure reducing valve (29) is calculated. Note that the amount of change dpls decreases as the difference decreases. Next, in step ST5, a value obtained by adding the amount of change dpls calculated in step ST3 to the current opening value EV2 · pls of the supercooling pressure reducing valve (29) is set as a new opening value EV2 · pls. Is done. Then, the opening degree of the supercooling pressure reducing valve (29) is changed to the new opening degree value EV2 · pls.

  The processing in step ST3 and step ST5 corresponds to the control operation of the intermediate superheat degree control unit (60). By this operation, the superheat degree of the intermediate pressure refrigerant that has flowed out of the supercooling heat exchanger (28) can be made constant at the target value of the intermediate superheat degree setting section (77).

  On the other hand, in step ST2, if all of the first, second, and third conditions are not satisfied, the process proceeds to step ST4. In step ST4, based on the difference between the maximum value Ttd of step ST1 and the target value Tm of the discharge state setting unit (76), the amount of change dpls of the opening value in the supercooling pressure reducing valve (29) is calculated. The Note that the amount of change dpls decreases as the difference decreases. Next, in step ST5, a value obtained by adding the amount of change dpls calculated in step ST4 to the current opening value EV2 · pls of the supercooling pressure reducing valve (29) is set as a new opening value EV2 · pls. Is done. Then, the opening degree of the supercooling pressure reducing valve (29) is changed to the new opening degree value EV2 · pls.

  The processing of step ST4 and step ST5 corresponds to the control operation of the first discharge target control unit (56a). By this operation, the discharge temperature of the compressor (21a, 21b, 21c) can be made constant at the target value of the discharge state setting unit (76).

  As described above, when the compressor (21a, 21b, 21c) seems to be overheated, the first discharge target control unit (56a) controls the discharge temperature, and the compressor (21a, 21b, 21c). ) Is not overheating operation, intermediate superheat control is performed by the intermediate superheat control unit (60).

  When step ST5 is completed, the process returns to step ST1, and the maximum value Ttd of each discharge pipe temperature sensor (61) is calculated again. Then, the processes from step ST1 to step ST5 are repeated. In this way, by properly using the two controls, it is possible to perform more appropriate injection for each compressor (21a, 21b, 21c) as compared with the case where the discharge temperature control is always performed as in the first embodiment. it can.

<Avoidance control unit>
The avoidance control unit (58) includes a first overheating avoidance control unit (78a) and a first wetness avoidance control unit (79a), and the compressor (21a) , 21b, 21c) prevents the compressor (21a, 21b, 21c) from continuing the abnormal operation when the operation becomes abnormal overheating or abnormal wet operation. The first overheating avoidance control unit (78a) performs a control operation for avoiding the compressor (21a, 21b, 21c) from abnormal overheating operation, and the first wetting avoidance control unit (79a) A control operation for avoiding (21a, 21b, 21c) from an abnormal wet operation is performed.

  First, after describing the control operation of the first wetting avoidance control unit (79a), the control operation of the first overheat avoidance control unit (78a) will be described.

  As shown in FIG. 6, the first wetting avoidance control unit (79a) first determines in step ST6 whether or not both the fourth and fifth conditions are satisfied. Here, the fourth condition is that the detected value Tgsh as the intermediate refrigerant superheat degree detected based on the intermediate refrigerant temperature sensor (70) and the intermediate pressure sensor (71) is the value of the intermediate superheat degree setting unit (77). This is a condition that a state smaller than the lower limit side threshold value Tgshmin set smaller than the intermediate superheat degree target value Tgshm continues for t3 hours or more. The lower threshold Tgshmin is set to a value that causes the compressor (21a, 21b, 21c) to perform an abnormal wet operation when the detected value Tgsh as the intermediate refrigerant superheat degree exceeds the threshold Tgshmin. Has been.

  The fifth condition is that at least one of detected values Tdsh1 to Tdsh3 as the discharge superheat degree detected based on the discharge pipe temperature sensor (61) and the discharge pressure sensor (64) is the discharge state setting unit. This is a condition that the discharge superheat degree target value Tdshm (76) is smaller than the lower limit side threshold value Tdshmin. Based on the fourth and fifth conditions, it is determined whether or not the compressor (21a, 21b, 21c) is in an abnormal wet operation.

  In step ST6, the determination in step ST6 is repeated until both the fourth and fifth conditions are satisfied. And if both the 4th and 5th conditions are satisfied, it will move to step ST7 noting that it has fallen into the abnormal wet operation.

  In step ST7, the change amount dpls of the opening value in the supercooling pressure reducing valve (29) is calculated based on the current opening value EV2 · pls of the supercooling pressure reducing valve (29). Here, if the current opening value EV2 · pls is large, the change amount dpls is also increased, and if the current opening value EV2 · pls is small, the change amount dpls is also reduced.

  Next, in step ST8, a value obtained by subtracting the amount of change dpls calculated in step ST7 from the current opening value EV2 · pls of the supercooling pressure reducing valve (29) is a new opening value EV2 · pls. Is set. As a result, the opening degree of the supercooling pressure reducing valve (29) is reduced.

  When step ST8 ends, the process returns to step ST6, and it is determined again in step ST6 whether the fourth and fifth conditions are both satisfied. The processing from step ST6 to step ST8 is repeated.

  Thus, the discharge temperature or the discharge superheat degree of each compressor (21a, 21b, 21c) becomes too low due to the load fluctuation of the refrigeration apparatus (1), etc., and the compressor (21a, 21b, 21c) Is in an abnormal wet operation state, the opening degree of the supercooling pressure reducing valve (29) becomes small. Thereby, the intermediate pressure refrigerant flowing from the intermediate ports (5, 6, 7) of the compressors (21a, 21b, 21c) can be reduced, and the abnormal wet operation state can be avoided from continuing.

  In the first overheating avoidance control unit (78a), as shown in FIG. 7, first, in step ST9, the largest value among the detected values Td1 to Td3 of the discharge pipe temperature sensors (61) is calculated. The calculated value is set as the maximum value Ttd of the discharge pipe temperature sensor (61).

  Next, in step ST10, it is determined whether or not at least one of the sixth and seventh conditions is satisfied. Here, the sixth condition is a condition that at least one of the predicted discharge temperatures of all the compressors (21a, 21b, 21c) is larger than the upper threshold Tpmax with respect to the predicted discharge temperature. The upper threshold Tpmax is set to a value that causes the compressor (21a, 21b, 21c) to perform an abnormal overheating operation when the predicted discharge temperature Tp exceeds the threshold Tpmax.

  Here, the predicted discharge temperature of the compressor (21a, 21b, 21c) is calculated by a predicted discharge temperature calculation unit (70) provided in the controller (4). The predicted discharge temperature calculation unit (70) assumes that the compression operation of the compressor (21a, 21b, 21c) is a polytropic compression operation, and the discharge pressure and suction pressure in the compressor (21a, 21b, 21c). The predicted discharge temperature of the compressor (21a, 21b, 21c) is calculated based on the suction temperature.

  The seventh condition is a condition that the maximum value Ttd set in step ST7 is further larger than the upper limit side threshold value Tdmax set larger than the target value Tm of the discharge state setting section (76). The upper threshold value Tdmax is set to a value that causes the compressor (21a, 21b, 21c) to perform an abnormal overheating operation when the maximum value Ttd in step ST7 exceeds the threshold value Tdmax. . Based on the sixth and seventh conditions, it is determined whether or not the compressor (21a, 21b, 21c) is in an abnormal overheating operation.

  In step ST10, steps ST9 and ST10 are repeated until at least one of the sixth and seventh conditions is satisfied. If at least one of the sixth and seventh conditions is established, the compressor (21a, 21b, 21c) is assumed to be in an abnormal overheating operation, and the process proceeds to step ST11.

  In step ST11, based on the difference between the maximum value Ttd set in step ST9 and the upper threshold value Tdmax, the first change amount dpls1 of the opening value in the supercooling pressure reducing valve (29) is calculated. . Note that the amount of change dpls1 decreases as this difference decreases. Next, in step ST12, based on the difference between the calculated value Tp of the predicted discharge temperature calculating unit (70) and the upper threshold value Tpmax, the second opening value of the supercooling pressure reducing valve (29) is set. A change amount dpls2 is calculated. Note that the amount of change dpls2 decreases as this difference decreases. Here, when all the compressors (21a, 21b, 21c) are activated, of the calculated values Tp for each compressor (21a, 21b, 21c) in the predicted discharge temperature calculation unit (70). Based on the difference between the maximum value and the upper limit side threshold value Tpmax, the second change amount dpls2 of the supercooling pressure reducing valve (29) is calculated. Note that the amount of change dpls2 decreases as this difference decreases.

  Next, in step ST13, the maximum value of the first change amount dpls1 calculated in step ST11 and the second change amount dpls2 calculated in step ST12 is the opening degree in the supercooling pressure reducing valve (29). It is set as a value change amount dpls. Here, when the amount of change dpls is larger than 15, it is limited to 15. The opening value of the supercooling pressure reducing valve (29) has a minimum value of zero (fully closed state) and a maximum value of 480 (fully open state).

  Next, in step ST14, a value obtained by adding the change amount dpls set in step ST13 to the current opening value EV2 · pls of the supercooling pressure reducing valve (29) is set as a new opening value EV2 · pls. Is set. Then, the opening degree of the supercooling pressure reducing valve (29) is changed to the new opening degree value EV2 · pls.

  When step ST14 ends, the process returns to step ST9, and the maximum value Ttd of each discharge pipe temperature sensor (61) is calculated again in step ST9. The processing from step ST9 to step ST14 is repeated.

  Thus, the discharge temperature or the discharge superheat degree of each compressor (21a, 21b, 21c) becomes too high due to the load fluctuation of the refrigeration apparatus (1), and the compressor (21a, 21b, 21c) Is in an abnormal overheating operation state, the opening degree of the supercooling pressure reducing valve (29) is increased. Thereby, it is possible to avoid the intermediate pressure refrigerant flowing from the intermediate ports (5, 6, 7) of the compressors (21a, 21b, 21c) from increasing and continuing the abnormal overheating operation state.

<Second control unit>
The second control unit (17) makes the discharge temperatures of the compressors (21a, 21b, 21c) close to each other. In this modification, the first compressor (21a) is composed of a variable capacity compressor, and the second and third compressors (21b, 21c) are composed of a fixed capacity compressor. , 3 The discharge temperatures of the compressors (21b, 21c) are considered to be substantially equal. Therefore, the second control unit (17) adjusts the opening temperature of the first flow rate adjustment valve (30a) corresponding to the first compressor (21a), thereby adjusting the discharge temperature of the first compressor (21a). Control is performed so as to approach the discharge temperature of the second and third compressors (21b, 21c).

  Specifically, as shown in FIG. 8, first, in step ST15, the detected value Td1 of the discharge pipe temperature sensor (61) of the first compressor (21a) and the second and third compressors (21b, 21c). The determination in step ST15 is repeated until the absolute value of the difference between the detected values Td2 and Td3 of the discharge pipe temperature sensor (61) is equal to or greater than a predetermined value T1. If the absolute value is equal to or greater than the predetermined value T1, the process proceeds to step ST16 because the difference in discharge temperature between the first compressor (21a) and the second and third compressors (21b, 21c) is large.

  In step ST16, the detection value Td1 of the discharge pipe temperature sensor (61) of the first compressor (21a) and the detection value Td2 of the discharge pipe temperature sensor (61) of the second and third compressors (21b, 21c). Based on the difference from the maximum value of Td3, the amount of change dpls of the opening value in the first flow rate adjusting valve (30a) is calculated. Note that the amount of change dpls decreases as the difference decreases.

  Next, in step ST17, it is determined whether or not the current opening value of the first flow rate adjustment valve (30a) is larger than a predetermined opening value b. If the opening value of the first flow rate adjusting valve (30a) is larger than the predetermined opening value b, the process proceeds to step ST18, and if not, the process proceeds to step ST19.

  In step ST18, if the change amount dpls calculated in step ST16 is smaller than -0.08 times the predetermined opening value b, the change amount dpls is corrected to -0.08 times the predetermined opening value b. If the change amount dpls calculated in ST16 is larger than 0.08 times the predetermined opening value b, the change amount dpls is corrected to 0.08 times the predetermined opening value b. That is, when the opening degree of the first flow rate adjustment valve (30a) is large, the opening degree is changed relatively large. This 0.08 is an example, and may be set within a range that limits the opening value of the first flow rate adjustment valve (30a).

  In step ST19, if the change amount dpls calculated in step ST16 is smaller than -0.04 times the predetermined opening value b, the change amount dpls is corrected to -0.04 times the predetermined opening value b. If the change amount dpls calculated in ST16 is larger than 0.04 times the predetermined opening value b, the change amount dpls is corrected to 0.04 times the predetermined opening value b. That is, when the opening degree of the first flow rate adjustment valve (30a) is small, the opening degree is changed relatively small. Note that 0.04 is an example, and the first flow rate adjustment valve (30a) is opened. You may set in the range which limits a degree value.

  Next, in step ST20, a value obtained by adding the amount of change dpls corrected as necessary in step ST18 or step ST19 to the current opening value EV3 · pls in the first flow rate adjusting valve (30a) is newly set. The opening value EV3 · pls is set. Then, the opening degree of the first flow rate adjusting valve (30a) is changed to become the new opening degree value EV3 · pls.

  When step ST20 is completed, the process returns to step ST15. In step ST15, the detection value Td1 of the discharge pipe temperature sensor (61) of the first compressor (21a) and the second and third compressors (21b, 21c) are again detected. It is determined whether or not the absolute value of the difference between the detected values Td2 and Td3 of the discharge pipe temperature sensor (61) is greater than or equal to a predetermined value T1. By repeating the processing from step ST15 to step ST20, the first flow rate adjusting valve (30a) is adjusted, and the discharge temperature of the first compressor (21a) is adjusted to the second and third compressors (21b, 21c). ) Approaches the discharge temperature.

  As described above, the controller (4) can perform appropriate injection to the compressors (21a, 21b, 21c) and uniform discharge temperature of the compressors (21a, 21b, 21c). It can be made.

<< Embodiment 2 >>
The refrigeration apparatus (91) of Embodiment 2 is installed in a convenience store or the like, and performs cooling of a refrigerator and a freezer and air conditioning in a room at the same time.

  As shown in FIG. 2, the refrigeration apparatus (91) includes an external unit (92), an air conditioning unit (93), a refrigeration unit (94), a refrigeration unit (95), and a controller (9). ing.

  The external unit (92) is provided with an external circuit (96). The air conditioning unit (93) is provided with an air conditioning circuit (97). The refrigeration unit (94) is provided with a refrigeration circuit (98). The refrigeration unit (95) is provided with a refrigeration circuit (99). In this embodiment, the air conditioning circuit (97) constitutes the first usage system, and the refrigeration circuit (98) and the refrigeration circuit (99) constitute the second usage system.

  In this refrigeration apparatus (91), a plurality of use side circuits (97, 98, 99) are connected in parallel to the external circuit (96), thereby forming a refrigerant circuit for performing a vapor compression refrigeration cycle. ing. The outside circuit (96) and each use side circuit (97, 98, 99) are connected to each other by the liquid side connecting pipe (100), the first gas side connecting pipe (101) and the second gas side connecting pipe (102). It is connected. One end of the liquid side connecting pipe (100) is connected to the liquid side closing valve (103) of the external circuit (96). The other end of the liquid side connection pipe (100) branches into three and is connected to the air conditioning circuit (97), the refrigeration circuit (98), and the refrigeration circuit (99), respectively. One end of the first gas side communication pipe (101) is connected to the first gas side closing valve (105) of the external circuit (96), and the other end is connected to the air conditioning circuit (97). One end of the second gas side communication pipe (102) is connected to the second gas side closing valve (104) of the external circuit (96). The other end of the second gas side communication pipe (102) branches into two and is connected to the refrigeration circuit (98) and the refrigeration circuit (99), respectively.

  Hereinafter, although it demonstrates in detail for every unit, the same code | symbol is attached | subjected to the same part as Embodiment 1, and the description of the part is simplified. Since the air conditioning unit (93) and the refrigeration unit (94) have the same configuration as the internal unit (3) of the first embodiment, the description thereof is omitted.

<Outside unit>
The external circuit (96) of the external unit (2) includes three compressors (21a, 21b, 21c) from first to third, a first four-way switching valve (24), and a warehouse. An external heat exchanger (25), a receiver (27), a supercooling heat exchanger (28), a supercooling pressure reducing valve (pressure reducing means) (29), and an outdoor expansion valve (31) are provided. Yes. Furthermore, in the second embodiment, second and third four-way switching valves (42, 43) are provided.

  The three compressors (21a, 21b, 21c) from the first to the third are composed of a compressor of a first usage system and a compressor of a second usage system. Specifically, in principle, the first compressor (21a) is fixedly used in the second usage system for refrigeration and freezing, and the third compressor (21c) is in principle used for the first use for air conditioning. Used fixedly in the system. On the other hand, the second compressor (21b) is used by switching to the first usage system and the second usage system, and constitutes one compressor of the first usage system and the second usage system.

  One end sides of the first, second and third suction pipes (23a, 23b, 23c) are connected to the suction sides of the first, second and third compressors (21a, 21b, 21c), respectively. The other end of the first suction pipe (23a) branches into two, one connected to the second gas side shut-off valve (104) and the other connected to the third four-way selector valve (43). ing. The other end of the second suction pipe (23b) is connected to the third four-way switching valve (43). The other end of the third suction pipe (23c) branches into two, one is connected to the third four-way switching valve (43) and the other is connected to the second four-way switching valve (42). It is connected.

  The first suction pipe (23a) is provided with a first suction pressure sensor (120), and the third suction pipe (23c) is provided with a second suction pressure sensor (121). The first suction pressure sensor (120) can detect the low pressure on the freezing side, and the second suction pressure sensor (121) can detect the low pressure on the air conditioning side.

  The three four-way switching valves (24, 42, 43) from the first to the third are respectively provided with four ports from the first to the fourth. The first four-way switching valve (24) has a first port for the discharge junction pipe (22), a second port for the fourth port of the second four-way switching valve (42), and a third port for external heat exchange. A fourth port is connected to the first gas side shut-off valve (105) on one end side of the vessel (25). The second four-way selector valve (42) has a first port connected to the discharge junction pipe (22) and a second port connected to the third suction pipe (23c), while the third port is closed.

  The first four-way switching valve (24) and the second four-way switching valve (42) are in a first state in which the first port and the third port communicate with each other and the second port and the fourth port communicate with each other. (The state indicated by the solid line in FIG. 1) and the second state (the state indicated by the broken line in FIG. 1) in which the first port and the fourth port communicate with each other and the second port and the third port communicate with each other It is possible.

  The third four-way selector valve (43) has a first port connected to the third refrigerant pipe (35), a second port connected to the second suction pipe (23b), and a third port connected to the third suction pipe. (23c) and the fourth port is connected to the first suction pipe (23a). Further, there is a check valve between the first suction pipe (23a) and the third four-way switching valve (43) and between the third suction pipe (23c) and the third four-way switching valve (43). Is provided. Here, in the third four-way selector valve (43), the discharge pressures of the compressors (31, 32, 33) always act on the first port, while the second port, the third port, and the fourth port. The suction pressures of the second compressor (21b), the third compressor (21c), and the first compressor (21a) act on the compressor, respectively.

  The third four-way selector valve (43) has a first state (state indicated by a solid line in FIG. 1) in which the first port and the third port communicate with each other and the second port and the fourth port communicate with each other. The first port and the fourth port can communicate with each other, and the second port and the third port can communicate with each other.

<Refrigeration unit>
The refrigeration circuit (99) of the refrigeration unit (95) has one end (liquid side end) connected to the branch end of the liquid side connecting pipe (100) and the other end (gas side end) connected to the second gas side connecting pipe ( 102). The refrigeration circuit (99) is provided with a refrigeration expansion valve (82), a refrigeration heat exchanger (81), and a booster compressor (84) in order from the liquid side end. The refrigeration heat exchanger (81) is a cross-fin type fin-and-tube heat exchanger. A refrigeration fan (83) is provided in the vicinity of the refrigeration heat exchanger (81). In the refrigeration heat exchanger (81), heat exchange is performed between the refrigerant and the internal air blown by the refrigeration fan (83).

  In the refrigeration circuit (99), an outlet refrigerant temperature sensor (111) is provided on the outflow side of the refrigeration heat exchanger (81). The refrigeration expansion valve (82) is a temperature-sensitive expansion valve whose opening degree is adjusted according to the temperature detected by the outlet refrigerant temperature sensor (111). An openable / closable electromagnetic valve (SV) is provided in the vicinity of the upstream side of the refrigeration expansion valve (82). Further, in the vicinity of the refrigeration heat exchanger (81), an in-compartment temperature sensor (112) for detecting the temperature of air in the freezer is provided.

  The booster compressor (84) is a high-pressure dome type scroll compressor, and constitutes a variable capacity compressor. The discharge pipe (85) of the booster compressor (84) is connected to the second gas side communication pipe (102), and the suction pipe (86) of the booster compressor (84) is connected to the refrigeration heat exchanger (81). Yes. The discharge pipe (85) is provided with a high pressure switch (113), an oil separator (87), and a check valve (CV) in order from the booster compressor (84) side. The suction pipe (86) is provided with a suction pressure sensor (114) for detecting the suction pressure of the booster compressor (84). An oil return pipe (88) for returning the refrigeration oil separated from the refrigerant to the suction side (suction pipe (86)) of the booster compressor (84) is connected to the oil separator (87). The oil return pipe (88) is provided with a capillary tube (CP).

  The refrigeration circuit (99) is also provided with a bypass pipe (89) that connects the suction pipe (86) and the discharge pipe (85). The bypass pipe (89) is provided with a check valve (CV). The bypass pipe (89) is configured such that the refrigerant flowing through the suction pipe (86) bypasses the booster compressor (84) and flows to the discharge pipe (85) when the booster compressor (84) fails. Yes.

  In the refrigeration apparatus (91) of the present embodiment, the refrigerant evaporating temperatures in the air conditioning circuit (97), the refrigeration circuit (98), and the refrigeration circuit (99) are different from each other. That is, the air-conditioning circuit (97), the refrigeration circuit (98), and the refrigeration circuit (99) have mutually different refrigerant evaporating pressures.

  Thereby, the suction pressures of the compressors (21a, 21b, 21c) connected to the first usage system and the second usage system are also different from each other. In such a case, the intermediate pressure refrigerant in the injection circuit (40) is likely to be sucked into the compressor having the lower pressure in the compression chamber at the intermediate pressure position. As a result, the temperature of the refrigerant discharged from the compressor decreases. The opening degree of each flow rate adjustment valve (30a, 30b, 30c) becomes small according to this temperature change. This suppresses a large amount of refrigerant from being injected into the compressor (21a, 21b, 21c).

-Driving action-
Next, the operation of the refrigeration apparatus (91) will be described. In this refrigeration apparatus (91), the refrigerator is cooled by the refrigeration unit (94), the cooling unit is cooled by the air conditioning unit (93) while the refrigerator is cooled by the refrigeration unit (95), and the refrigeration unit (94) The air conditioner unit (93) can be switched between a heating operation and a heating operation while the refrigerator is cooled and the freezer is cooled by the refrigeration unit (95). Here, the part of the cooling operation will be described.

  In this cooling operation, the second compressor (21b) is used in the second usage system for refrigeration / freezing, and the second mode is used in which the second compressor (21b) is used in the first usage system for air conditioning. The mode can be switched to.

  As shown in FIG. 2, in the cooling operation in the first mode, all the four-way switching valves (24, 42, 43) are set to the first state. Further, the outdoor expansion valve (36) is set to a fully closed state. Furthermore, the opening degrees of the indoor expansion valve (52), the refrigeration expansion valve (52), and the refrigeration expansion valve (82) are adjusted as appropriate. In addition, the fans (26, 54, 83), the three compressors (21a, 21b, 21c), and the booster compressor (84) are in operation.

  The high-pressure gas refrigerant compressed by the first, second, and third compressors (21a, 21b, 21c) is discharged from the discharge pipes (22a, 22b, 22c). The high-pressure gas refrigerant discharged from each discharge pipe (22a, 22b, 22c) flows into each oil separator (38a, 38b, 38c). In each oil separator (38a, 38b, 38c), the refrigeration oil is separated from the high-pressure refrigerant. The separated refrigeration oil is temporarily stored in each oil separator (38a, 38b, 38c), and then passed through each oil outflow pipe (39a, 39b, 39c) and the oil outflow junction pipe (39d). It flows into the injection pipe (38). The refrigerating machine oil that has flowed into the second injection pipe (38) is divided and passes through the branch injection pipes (37a, 37b, 37c), and then passes through the intermediate ports (5, 6, 7). It is sucked into the compressors (21a, 21b, 21c).

  On the other hand, the high-pressure refrigerant from which the refrigerating machine oil has been separated flows out of the oil separators (38a, 38b, 38c), and then joins in the discharge junction pipe (22). The high-pressure refrigerant joined in the discharge junction pipe (22) flows into the external heat exchanger (25) through the first and second four-way switching valves (24, 42). In the outdoor heat exchanger (25), the high-pressure refrigerant is condensed by exchanging heat with outdoor air. The condensed refrigerant passes through the first refrigerant pipe (32), the receiver (27), and the high-pressure channel (28a) of the supercooling heat exchanger (28) in this order, and then flows into the second refrigerant pipe (33). . A part of the refrigerant flowing into the second refrigerant pipe (33) flows to the first injection pipe (37), and the other flows to the liquid side connection pipe (100) via the first closing valve (11).

  The high-pressure refrigerant that has flowed toward the first injection pipe (37) is depressurized to a predetermined pressure by the supercooling pressure reducing valve (29) to become an intermediate pressure refrigerant, and then the supercooling heat exchanger (28). Into the decompression side flow path (28b). In the supercooling heat exchanger (28), the intermediate-pressure refrigerant and the high-pressure refrigerant flowing through the high-pressure side flow path (28a) exchange heat. As a result, the high-pressure refrigerant is cooled to increase the degree of supercooling, while the intermediate-pressure refrigerant is heated to become a gas refrigerant. This gas refrigerant flows out of the supercooling heat exchanger (28) and then splits into the first, second, and third branch injection pipes (37a, 37b, 37c) via the second injection pipe (38). .

  The intermediate pressure refrigerant flowing into the branch injection pipes (37a, 37b, 37c) is adjusted in flow rate by the flow rate adjusting valves (30a, 30b, 30c), and then the compressors (21a, 21b, 21c) is injected into the compression chamber at the intermediate pressure position. Here, the controller (9) adjusts the valve opening degree of each flow rate adjusting valve (30a, 30b, 30c) so that the temperature detected by the discharge pipe temperature sensor (61) falls within a predetermined temperature range. The

  On the other hand, the liquid refrigerant flowing into the liquid side communication pipe (100) is divided into the air conditioning circuit (97), the refrigeration circuit (98), and the refrigeration circuit (99).

  The high-pressure refrigerant flowing into the air conditioning circuit (97) is depressurized by the indoor expansion valve (52) and then flows to the indoor heat exchanger (53). In the indoor heat exchanger (53), the refrigerant absorbs heat from the indoor air and evaporates. As a result, the indoor air is cooled and the store is cooled. The refrigerant evaporated in the indoor heat exchanger (53) passes through the first gas side communication pipe (101), the first four-way switching valve (24), and the second four-way switching valve (42) in this order, The air is sucked into the third compressor (21c) from the suction pipe (23c).

  The refrigerant flowing into the refrigeration circuit (98) flows through the heating pipe (51). At that time, in the drain pan (55), ice blocks in which condensed water has been frozen by the refrigerant flowing through the heating pipe (51) are melted by the refrigerant in the heating pipe (51). As a result, the high-pressure refrigerant flowing through the heating pipe (51) is further subcooled. The high-pressure refrigerant flowing out of the heating pipe (51) is depressurized by the refrigeration expansion valve (52) and then flows to the refrigeration heat exchanger (81). In the refrigeration heat exchanger (81), the refrigerant absorbs heat from the internal air and evaporates. As a result, the refrigerator is cooled. In the refrigeration unit (94), for example, the internal temperature is maintained at 5 ° C. The refrigerant evaporated in the refrigeration heat exchanger (81) flows to the second gas side communication pipe (102).

  The refrigerant flowing into the refrigeration circuit (99) is depressurized by the refrigeration expansion valve (82) and then flows to the refrigeration heat exchanger (81). In the refrigeration heat exchanger (81), the refrigerant absorbs heat from the internal air and evaporates. As a result, the inside of the freezer is cooled. In this refrigeration unit (95), for example, the internal temperature is maintained at −10 ° C. The refrigerant evaporated in the refrigeration heat exchanger (81) is compressed by the booster compressor (84), then flows into the second gas side communication pipe (102), and merges with the refrigerant from the refrigeration circuit (98). The merged refrigerant flows to the first suction pipe (106), a part of the refrigerant is sucked into the first compressor (21a), and the rest passes through the third connection pipe (49c) and the third four-way switching valve (43). Through the second suction pipe (107) to the second compressor (21b).

  The cooling operation in the second mode is the same except that the third four-way switching valve (43) is switched to the second state in the state of the first mode.

  In the cooling operation in this mode, the refrigerant evaporated in the indoor heat exchanger (53) passes through the first four-way switching valve (24) and the second four-way switching valve (42) in order from the first gas side communication pipe (101). Through the third suction pipe (23c). Part of the refrigerant flowing into the third suction pipe (23c) is sucked into the third compressor (21c), and the rest passes through the third four-way switching valve (43), and then the second suction pipe (23b). To the second compressor (21b).

  Further, when only the first four-way switching valve (24) is switched to the second state from the cooling operation state, the heating operation can be performed. In this case, if the outdoor expansion valve (31) is fully closed, the first heating operation is performed. If the opening degree is adjusted as necessary without fully closing the outdoor expansion valve (31), the second heating operation is performed. Become.

  Further, the first four-way switching valve (24) and the second four-way switching valve (42) are switched to the second state, and the opening degree is adjusted as necessary without fully closing the outdoor expansion valve (31). And it becomes the 3rd heating operation.

  Here, in the first heating operation, the air conditioning heat exchanger (53a) provided in the air conditioning circuit (97) serves as a condenser, and is provided in the refrigeration heat exchanger (81) and the refrigeration circuit (98). The refrigerated heat exchanger (53b) serves as an evaporator. In the second heating operation, the heat exchanger for air conditioning (53a) serves as a condenser, and the external heat exchanger (25), the refrigeration heat exchanger (53b), and the refrigeration heat exchanger (81) serve as evaporators. In the third heating operation, the air conditioner heat exchanger (53a) and the external heat exchanger (25) serve as a condenser, and the refrigeration heat exchanger (81) and the refrigerated heat exchanger (53b) serve as an evaporator. Become.

-Effect of Embodiment 2-
According to the second embodiment, the plurality of compressors (21a, 21b, 21c) are composed of compressors having different suction pressures. Even in such a case, by providing the flow rate adjusting valves (30a, 30b, 30c), the pressure is reduced by the supercooling pressure reducing valve (29) and then the branch injection pipes (37a, 37b, 37c). ) Can be adjusted for each compressor (21a, 21b, 21c). Therefore, it is possible to perform appropriate injection with respect to the compressors (21a, 21b, 21c).

  Further, according to the second embodiment, the refrigerant oil is injected into each compressor (21a, 21b, 21c) via the injection circuit (40), while the refrigerating machine oil is supplied to each compressor (21a, 21b, 21c). Can be returned. Thus, since the injection circuit (40) can be used as a circuit for returning the refrigeration machine oil, it is not necessary to separately provide a dedicated oil return circuit, and the cost of the refrigeration apparatus can be reduced.

-Modification of Embodiment 2-
FIG. 9 is a refrigerant circuit according to a modification of the second embodiment. The configuration of the controller that controls the operation of the refrigeration apparatus (1) is different between the second embodiment and its modification. An intermediate refrigerant temperature sensor for measuring the temperature of the intermediate pressure refrigerant after passing through the pressure reducing side passage (28b) of the supercooling heat exchanger (28) is provided in the second injection pipe (38) of Modification 2. (70) and an intermediate pressure sensor (71) for measuring the pressure of the intermediate pressure refrigerant are provided.

  The controller (8) according to the modification of the second embodiment includes a third control unit (18) and a fourth control unit (19). The opening degree of the supercooling pressure reducing valve (29) is adjusted by the third control part (18), and the opening degree of the flow rate adjusting means (30a, 30b, 30c) is adjusted by the fourth control part (19). The

  The controller (8) includes first and second suction pressure sensors (120, 121) as the low pressure detection means, an intermediate pressure sensor (71) as the intermediate pressure detection means, and the intermediate superheat degree. An intermediate refrigerant temperature sensor (70) and an intermediate pressure sensor (71) as detection means and a discharge pipe temperature sensor (61) and a discharge pressure sensor (64) as discharge state detection means are electrically connected. Yes. The controller (8) is provided with a discharge state setting section (discharge state setting means) (76) and an intermediate superheat degree setting section (intermediate superheat degree setting means) (77).

  The discharge state setting unit (76) sets a target value Tm of the discharge temperature of the compressor (21a, 21b, 21c), and the intermediate superheat setting unit (77) includes the injection circuit (40 ) Is set as a target value Tgshm for the superheat degree of the intermediate pressure refrigerant flowing through the refrigerant.

  Next, control operations of the third control unit (18) and the fourth control unit (19) will be described with reference to the control flowcharts of FIGS.

<Third control unit>
The third control unit (18) includes the intermediate pressure control unit (59), the intermediate superheat degree control unit (60), and based on the start-up states of the compressors (21a, 21b, 21c). The intermediate pressure control unit (59) or the intermediate superheat degree control unit (60) is selected to execute control.

  Specifically, as shown in FIG. 10, first, in step ST21, the compressor (21a, 21b) connected to the first low pressure line (102) and the second low pressure line (101) were connected. It is determined whether or not the compressor (21c) is activated together.

  If the compressor (21a, 21b) of the first low pressure line (102) and the compressor (21c) of the second low pressure line (101) are both activated in step ST21, the process proceeds to step ST22. In step ST22, the supercooling is performed based on the difference between the minimum value of the detected values LP1 and LP2 of the first and second suction pressure sensors (120, 121) and the detected value MP of the intermediate pressure sensor (71). A change amount dpls of the opening value in the pressure reducing valve (29) is calculated. Note that the amount of change dpls decreases as the difference decreases. If the change amount dpls becomes a negative value, the change amount dpls is set to zero.

  Next, in step ST24, a value obtained by adding the amount of change dpls calculated in step ST21 to the current opening value EV2 · pls of the supercooling pressure reducing valve (29) is set as a new opening value EV2 · pls. Is done. Then, the opening degree of the supercooling pressure reducing valve (29) is changed to the new opening degree value EV2 · pls.

  The processing of step ST22 and step ST24 corresponds to the control operation of the intermediate pressure control unit (59). By this operation, the pressure (intermediate pressure) of the injection circuit (40) can always be higher than the pressures (low pressure) of the first and second low pressure lines.

  On the other hand, in step ST21, if one of the compressor (21a, 21b) of the first low pressure line (102) and the compressor (21c) of the second low pressure line (101) is activated, the process proceeds to step ST23. Move. In step ST23, the detected value Tgsh of the intermediate refrigerant superheat degree detected based on the intermediate refrigerant temperature sensor (70) and the intermediate pressure sensor (71) and the target value Tgshm of the intermediate superheat degree setting unit (77) Based on the difference, the amount of change dpls of the opening value in the supercooling pressure reducing valve (29) is calculated. Note that the amount of change dpls decreases as the difference decreases.

  Next, in step ST24, a value obtained by adding the amount of change dpls calculated in step ST23 to the current opening value EV2 · pls of the supercooling pressure reducing valve (29) is set as a new opening value EV2 · pls. Is done. Then, the opening degree of the supercooling pressure reducing valve (29) is changed to the new opening degree value EV2 · pls.

  The processing of step ST23 and step ST24 corresponds to the control operation of the intermediate superheat control unit (60). By this operation, the superheat degree of the intermediate pressure refrigerant that has flowed out of the supercooling heat exchanger (28) can be made constant at the target value of the intermediate superheat degree setting section (77).

  Thus, when both the compressor (21a, 21b) of the first low pressure line (102) and the compressor (21c) of the second low pressure line (101) are activated, the intermediate pressure control is performed. The intermediate pressure control is performed by the section (59), and one of the compressor (21a, 21b) of the first low pressure line (102) and the compressor (21c) of the second low pressure line (101) is activated. In this case, intermediate superheat control is performed by the intermediate superheat control unit (60). As a result, as described above, the refrigerant flows backward from the intermediate port of the compressor (21c) of the second low pressure line (101) to the intermediate port of the compressor (21a, 21b) of the first low pressure line (102). There is nothing.

  In addition, when one of the compressor (21a, 21b) of the first low pressure line (102) and the compressor (21c) of the second low pressure line (101) is activated, the above-described reverse flow of the refrigerant occurs. Since this does not occur, the compressor (21a, 21b, 21c) is injected while maintaining the intermediate pressure refrigerant superheat degree on the decompression side flow path (28b) side in the supercooling heat exchanger (28) at an appropriate value. be able to.

  When step ST24 is completed, the process returns to step ST21, and whether the compressor (21a, 21b) of the first low-pressure line (102) and the compressor (21c) of the second low-pressure line (101) are both activated again. It is determined whether or not. Then, the processes from step ST21 to step ST24 are repeated. In this way, by properly using the two controls, it is possible to perform more appropriate injection for each compressor (21a, 21b, 21c) as compared with the case where the discharge temperature control is always performed as in the second embodiment. it can.

<4th control part>
The fourth control unit (19) includes a second discharge target control unit (56b), a second overheat avoidance control unit (78b), and a second wetness avoidance control unit (79b), and the compressor (21a, 21b, 21c) based on the discharge temperature and discharge superheat degree and the superheat degree of the intermediate pressure refrigerant in the injection circuit (40), the second discharge target control section (56b), the second overheat avoidance control section (78b) and One of the second wetting avoidance control units (79b) is selected and executed. The control operation of the fourth control unit (19) is performed for each of the first, second, and third flow rate adjusting valves (30a, 30b, 30c). Here, the first flow rate adjusting valve (30a) is used. ) Will be described only.

  Specifically, as shown in FIG. 11, first, in step ST25, it is determined whether or not at least one of the eighth condition and the ninth condition is satisfied. Here, the eighth condition is that the detected value Tdsh1 as the discharge superheat degree detected based on the discharge pipe temperature sensor (61) and the discharge pressure sensor (64) is smaller than a predetermined discharge superheat degree Tdshs, and The detection value Td1 of the tube temperature sensor (61) is further smaller than the lower limit side threshold Tdmin set smaller than the discharge temperature target value Td of the discharge state setting section (76), and the intermediate refrigerant temperature sensor (70). And the detected value Tgsh as the intermediate refrigerant superheat degree detected based on the intermediate pressure sensor (71) is smaller than the intermediate superheat degree target value Tgshm of the intermediate superheat degree setting unit (77).

  The eighth condition is a condition for determining whether or not the first compressor (21a) is in an abnormal wet operation. Here, the predetermined discharge superheat degree Tdshs is set within a range in which the first compressor (21a) does not perform an abnormal wet operation. The lower limit side threshold value Tdmin is set to a value that causes the first compressor (21a) to perform an abnormal wet operation when the detection value Td1 of the discharge pipe temperature sensor (61) exceeds the threshold value Tdmin. Has been.

  The ninth condition is that the detection value Td1 of the discharge pipe temperature sensor (61) is larger than the upper threshold value Tdmax set larger than the discharge temperature target value Tm of the discharge state setting section (76). It is.

  The ninth condition is a condition for determining whether or not the first compressor (21a) is in an abnormal overheating operation. Here, the upper limit side threshold value Tdmax is set to a value that causes the first compressor (21a) to perform an abnormal overheating operation when the detection value Td1 of the discharge pipe temperature sensor (61) exceeds the threshold value Tdmax. Is set.

  If at least one of the eighth and ninth conditions is satisfied in step ST25, it is determined that the first compressor (21a) is performing an abnormal wet operation or an abnormal wet operation, and step ST26. Move on.

  In step ST26, it is determined whether or not the ninth condition is satisfied. If the ninth condition is satisfied, the process proceeds to step ST28. In step ST28, based on the current opening degree value EV3 · pls of the first flow rate adjustment valve (30a), the change amount dpls of the opening degree value in the first flow rate adjustment valve (30a) is calculated. Here, if the current opening degree value EV3 · pls is large, the change amount dpls also becomes large, and if the current opening degree value EV2 · pls is small, the change amount dpls becomes small. Next, in step ST30, a value obtained by adding the amount of change dpls calculated in step ST28 to the current opening value EV3 · pls of the first flow rate adjusting valve (30a) is set as a new opening value EV3 · pls. Is set. As a result, the opening degree of the supercooling pressure reducing valve (29) increases.

  The processing of step ST28 and step ST30 corresponds to the control operation of the second overheat avoidance control unit (78b). By this operation, the intermediate pressure refrigerant flowing from the intermediate port (5) of the first compressor (21a) is increased, and the continuation of the abnormal overheating operation state is avoided.

  On the other hand, if the ninth condition is not satisfied in step ST26, the process proceeds to step ST29. In step ST29, based on the current opening degree value EV3 · pls of the first flow rate adjusting valve (30a), a change amount dpls of the opening degree value in the first flow rate adjusting valve (30a) is calculated. Here, if the current opening degree value EV3 · pls is large, the change amount dpls also becomes large, and if the current opening degree value EV2 · pls is small, the change amount dpls becomes small. Next, in step ST30, a value obtained by subtracting the change amount dpls calculated in step ST29 from the current opening value EV3 · pls of the first flow rate adjusting valve (30a) is set as a new opening value EV3 · pls. Is set. As a result, the opening degree of the supercooling pressure reducing valve (29) is reduced.

  The processing of step ST29 and step ST30 corresponds to the control operation of the second wetness avoidance control unit (79b). By this operation, the intermediate pressure refrigerant flowing from the intermediate port (5) of the first compressor (21a) is reduced, and the continuation of the abnormal wet operation state is avoided.

  On the other hand, if both the eighth and ninth conditions are not satisfied in step ST25, it is determined that the first compressor (21a) has not caused an abnormal wet operation or an abnormal wet operation. Move on to ST27.

  In step ST27, based on the difference between the detection value Td1 of the discharge pipe temperature sensor (61) and the discharge temperature target value Tm of the discharge state setting unit (76), the opening degree in the first flow rate adjustment valve (30a). A value change amount dpls is calculated. Note that the amount of change dpls decreases as the difference decreases. Next, in step ST30, in step ST30, a value obtained by adding the amount of change dpls calculated in step ST29 to the current opening value EV3 · pls of the first flow rate adjustment valve (30a) is a new opening value. It is set as EV3 · pls. Then, the opening degree of the first flow rate adjusting valve (30a) is changed to become the new opening degree value EV2 · pls.

    The processing of step ST27 and step ST30 corresponds to the control operation of the second discharge target control unit (56b). By this operation, the discharge temperature of the first compressor (21a) can be made constant at the target value of the discharge state setting unit (76).

  When step ST30 ends, the process returns to step ST25, and the determination in step ST25 is performed again. Then, the processing from step ST25 to step ST30 is repeated. In this way, by properly using the three controls, it is possible to perform more appropriate injection for each compressor (21a, 21b, 21c) compared to the case where the discharge temperature control is always performed as in the first embodiment. it can.

<< Other Embodiments >>
About the said embodiment, it is good also as the following structures.

  In the above embodiment, the flow rate adjusting means (30a, 30b, 30c) for adjusting the injection amount of each compressor (21a, 21b, 21c) are all configured by motor-operated valves. You may comprise by this solenoid valve. In this case, the injection amount may be adjusted by the holding time of the electromagnetic valve open setting. That is, when the injection amount is increased, the holding time of the electromagnetic valve open setting is lengthened. Conversely, when the injection amount is reduced, the holding time of the electromagnetic valve open setting is shortened.

  In addition, as shown in FIG. 3, the injection amount of the first compressor (21a) with variable capacity is adjusted with a motor-operated valve, and the injection amounts of the second and third compressors (21b, 21c) with fixed capacity are adjusted with solenoid valves. You may adjust with. If it carries out like this, in the case of a 1st compressor (21a), the injection amount of this 1st compressor (21a) can be accurately adjusted with the said motor operated valve according to the operating capacity change.

  On the other hand, in the case of the second and third compressors (21b, 21c), since the operation capacity is fixed, it is not always necessary to accurately adjust the injection amount with the motor-operated valve. Therefore, the cost of the refrigeration apparatus can be reduced by using an electromagnetic valve having a simpler structure than that of the electric valve.

  As described above, when an electric valve and an on-off valve are used as the flow rate adjusting means of the injection circuit, the CV values (flow rate coefficients) of these valves may be varied. For example, if the CV value of the motor-operated valve when fully opened is greater than the CV value of the on-off valve, the second and third compressors (21b, 21c) when the motor-operated valve is fully open and the solenoid valve is open. ), The amount of injection of the first compressor (21a) can be increased.

  In the above embodiment, all the branch pipes (37a, 37b, 37c) in the injection circuit (40) are provided with the flow rate adjusting means (30a, 30b, 30c). The flow rate adjusting means (30a, 30b, 30c) may be provided only in the branch pipe (37a).

  In addition, the above embodiment is an essentially preferable illustration, Comprising: It does not intend restrict | limiting the range of this invention, its application thing, or its use.

  As described above, the present invention is useful for a refrigeration apparatus that has a plurality of compressors and performs a vapor compression refrigeration cycle.

1 Refrigeration equipment
5,6,7 Intermediate port
9 Controller (control means)
10 Refrigerant circuit
21a First compressor (compressor)
21b Second compressor (compressor)
21c 3rd compressor (compressor)
28 Supercooling heat exchanger
29 Pressure reducing valve for supercooling (pressure reducing means)
30a 1st flow rate adjustment valve (flow rate adjustment means)
30b Second flow control valve (flow control means)
30c Third flow control valve (flow control means)
32 First refrigerant piping (high pressure line)
37 1st injection piping (main piping)
38 Second injection piping
37a First branch injection pipe (branch pipe)
37b Second branch injection pipe (branch pipe)
37c Third branch injection pipe (branch pipe)
40 Injection circuit

Claims (23)

A refrigerant circuit (10) having a plurality of compressors (21a, 21b, 21c) and performing a vapor compression refrigeration cycle, and a main pipe (37) branched from the high-pressure line (33) of the refrigerant circuit (10) And branch pipes (37a, 37b, 37c) further branched from the main pipe (37), and each branch pipe (37a, 37b, 37c) is connected to an intermediate port of each compressor (21a, 21b, 21c) ( 5, 6 and 7) a refrigeration apparatus comprising an injection circuit (40) and a decompression means (29) provided in the main pipe (37) of the injection circuit (40),
At least one of the plurality of compressors (21a, 21b, 21c) includes a variable capacity compressor (21a), and at least one of the plurality of compressors (21a, 21b, 21c) is a variable capacity compressor. (21a) A refrigeration apparatus comprising a branch pipe (37a, 37b, 37c) on the side provided with flow rate adjusting means (30a, 30b, 30c). In claim 1,
A refrigeration apparatus comprising a flow rate adjusting means (30a, 30b, 30c) for each branch pipe (37a, 37b, 37c) of the injection circuit (40). In claim 1 or 2,
A supercooling heat exchanger (28) having a decompression side passage (28b) through which the refrigerant decompressed by the decompression means (29) flows and a high pressure side passage (28a) through which the high-pressure refrigerant in the refrigerant circuit (10) flows. With
The decompression side flow path (28b) is connected to the main pipe (37) of the injection circuit (40), and the high pressure side flow path (28a) is connected to the high pressure line (33) of the refrigerant circuit (10). A refrigeration apparatus characterized by comprising: In any one of Claims 1-3,
Oil separators (38a, 38b) that are provided in the discharge pipes (22a, 22b, 22c) of the compressors (21a, 21b, 21c) and separate the refrigeration oil from the refrigerant discharged from the compressors (21a, 21b, 21c) , 38c), the oil spill pipe (39a, 39b, 39c) connected to the oil separator (38a, 38b, 38c), one end is connected to the oil spill pipe (39a, 39b, 39c), and others An oil return circuit (39) whose end is connected to a branch pipe branched from the injection circuit (40) and returns the refrigeration oil from the oil outflow pipe (39a, 39b, 39c) to each compressor (21a, 21b, 21c); A refrigeration apparatus comprising: In any one of Claims 1-4,
The flow rate adjusting means (30a, 30b, 30c) is a flow rate adjusting valve having a variable opening degree. In any one of claims 1 to 5,
The refrigeration apparatus characterized in that the flow rate adjusting means (30a, 30b, 30c) is an on-off valve. In any one of Claims 1-6,
The plurality of compressors (21a, 21b, 21c) includes a variable capacity compressor (21a) and a fixed capacity compressor (21b, 21c).
The flow rate adjusting means (30a) provided in the branch pipe (37a) connected to the intermediate port (5) of the variable capacity compressor (21a) is a variable flow rate adjusting valve, and the fixed The flow rate adjusting means (30b, 30c) provided in the branch pipe (37b, 37c) connected to the intermediate port (6, 7) of the capacity type compressor (21b, 21c) is an on-off valve. Refrigeration equipment characterized. In any one of Claims 1-7,
A discharge refrigerant temperature detection means (61) for detecting the temperature of the discharge refrigerant discharged from the compressor (21a, 21b, 21c),
Control means (9) for adjusting the opening of each flow rate adjusting means (30a, 30b, 30c) so that the value detected by the discharged refrigerant temperature detecting means (61) is within a predetermined temperature range. A refrigeration apparatus characterized by that. In any one of claims 3 to 7,
A discharge state detecting means (61, 66) for detecting at least one of a discharge temperature and a discharge superheat degree in each of the compressors (21a, 21b, 21c);
A discharge state setting means (76) for setting discharge target values Tm, Tdshm for at least one of discharge temperature and discharge superheat degree in each of the compressors (21a, 21b, 21c);
Intermediate superheat degree detection means (75) for detecting the superheat degree of the intermediate pressure refrigerant after passing through the pressure reducing side channel (28b) of the supercooling heat exchanger (28);
Intermediate superheat degree setting means (77) for setting an intermediate superheat degree target value Tgshm for the superheat degree of the intermediate pressure refrigerant after passing through the pressure reducing side flow path (28b) of the supercooling heat exchanger (28). And having
The maximum detection value Ttd, which is the maximum value of the detection values Td for the compressors (21a, 21b, 21c) in the discharge state detection means (61, 66), is set to the discharge target values Tm, Tdshm. A first discharge target control section (56a) for changing the opening of the decompression means (29);
An intermediate superheat degree control section (60) for changing the opening of the pressure reducing means (29) so that the detected value Tgsh of the intermediate superheat degree detection means (75) becomes the intermediate superheat degree target value Tgshm;
When the refrigerant state value of the refrigerant in the refrigerant circuit (10) is within a predetermined range, the first discharge target control unit (56a) or the intermediate superheat degree control unit (60) is selected based on the refrigerant state value And a first control unit (16) for executing control. In claim 9,
The first control unit (16) selects the first discharge target control unit (56a) when the maximum detection value Ttd of the discharge state detection means (61, 66) is larger than the discharge target value Tm. The refrigeration apparatus is configured to execute control. In claim 9 or 10,
The first control unit (16) selects and controls the intermediate superheat degree control unit (60) when the maximum detection value Ttd of the discharge state detection means (61, 66) is equal to or less than the discharge target value Tm. The refrigeration apparatus is configured to execute In any one of claims 9 to 11,
When the maximum detection value Ttd of the discharge state detection means (61, 66) continuously decreases within the predetermined time t1, the first control unit (16) is configured to perform the intermediate superheat degree control unit (60). A refrigeration apparatus configured to execute control by selecting In any one of claims 9 to 12,
A first overheating avoidance control unit (78a) for making the opening of the decompression means (29) larger than the present time;
A first wetting avoidance control unit (79a) for making the opening of the decompression means (29) smaller than the present time;
When the refrigerant state value of the refrigerant in the refrigerant circuit (10) exceeds the predetermined range, the first overheat avoidance control unit (78a) or the first wetness avoidance control until the refrigerant state value falls within the predetermined range. The avoidance control part (58) which selects a part (79a) and performs control is provided, The freezing apparatus characterized by the above-mentioned. In claim 13,
The avoidance control unit (58) determines that the detection value Td of the discharge state detection means (61, 66) is larger than the upper limit side threshold Tdmax set larger than the discharge target value Tm, and the intermediate overheating. When the detected value Tgsh of the degree detection means (75) is larger than the upper limit side threshold value Tgshmax set larger than the intermediate superheat degree target value Tgshm, the first overheat avoidance control unit (78a) ) To select and execute control. In claim 13 or 14,
The avoidance control unit (58) is configured to detect when the detection value Td of the discharge state detection means (61, 66) is further smaller than a lower limit side threshold Tdmin set smaller than the discharge target value Tm, and the intermediate overheating. When the detected value Tgsh of the degree detection means (75) is at least one of the cases where the detected value Tgsh is smaller than the lower limit side threshold value Tgshmin set smaller than the intermediate superheat degree target value Tgshm, the first wetting avoidance control unit (79a ) To select and execute control. In any one of claims 9 to 15,
The opening degree of the flow rate adjusting means (30a, 30b, 30c) is changed so that the detection values Td for the respective compressors (21a, 21b, 21c) in the discharge state detecting means (61, 66) approach each other. 2. A refrigeration apparatus comprising a control unit (17). In any one of claims 3 to 7,
The plurality of compressors (21a, 21b, 21c) includes a first compressor (21a, 21b) and a second compressor (21c),
The low-pressure line of the refrigerant circuit (10) is provided on the suction side of the first compressor (21a, 21b) and the refrigerant circuit (10) to cool the interior of the refrigerator (53b, 81). ), A heat exchanger for air conditioning (53a) provided on the suction side of the second compressor (21c) and the refrigerant circuit (10) for air conditioning the room. The second low-pressure line (101) connecting the
Low pressure detection means (120, 121) for detecting the pressure of the low pressure refrigerant flowing through the first and second low pressure lines (102, 101), and the pressure of the intermediate pressure refrigerant after being reduced in pressure by the pressure reduction means (29) Intermediate pressure detection means (71), intermediate superheat degree detection means (75) for detecting the superheat degree of the intermediate pressure refrigerant after passing through the pressure reducing side flow path (28b) of the supercooling heat exchanger (28), Intermediate superheat degree setting means (77) for setting an intermediate superheat degree target value Tgshm for the superheat degree of the intermediate pressure refrigerant after passing through the pressure reducing side flow path (28b) of the supercooling heat exchanger (28). And having
The opening degree of the pressure reducing means (29) is changed so that the detected value MP of the intermediate pressure detecting means (71) is larger than the detected value LP of the low pressure lines (102, 101) in the low pressure pressure detecting means (120, 121). Intermediate pressure control section (59);
An intermediate superheat degree control unit (60) for changing the opening of the pressure reducing means (29) so that the detected value Tgsh of the intermediate superheat degree detection means (75) becomes the intermediate superheat degree target value Tgshm;
A third control unit (selecting the intermediate pressure control unit (59) or the intermediate superheat degree control unit (60) and executing control based on the starting states of the plurality of compressors (21a, 21b, 21c) ( And 18) a refrigeration apparatus. In claim 17,
The third control unit (18) selects the intermediate pressure control unit (59) when both the first compressor (21a, 21b) and the second compressor (21c) are activated. The refrigeration apparatus is configured to execute control. In claim 17 or 18,
The third control unit (18) selects the intermediate superheat degree control unit (60) when one of the first compressor (21a, 21b) and the second compressor (21c) is activated. The refrigeration apparatus is configured to execute control. In any one of claims 17 to 19,
A discharge state detecting means (61, 66) for detecting at least one of a discharge temperature and a discharge superheat degree in each of the compressors (21a, 21b, 21c); a discharge temperature in each of the compressors (21a, 21b, 21c); A discharge state setting means (76) for setting a discharge target value Tm for at least one of the discharge superheat degrees,
A second discharge target control section (56b) for changing the opening of the flow rate adjusting means (30a, 30b, 30c) so that the detection value Td of the discharge state detection means (61, 66) becomes the discharge target value Tm; ,
A second overheating avoidance control unit (78b) for making the opening degree of the flow rate adjusting means (30a, 30b, 30c) larger than the present one;
A second wetting avoidance control unit (79b) that makes the opening of the flow rate adjusting means (30a, 30b, 30c) smaller than the present one;
When the refrigerant state value of the refrigerant in the refrigerant circuit (10) is within a predetermined range, the second discharge target control unit (56b) is selected, and when the refrigerant state value exceeds the predetermined range, the second overheating is performed. A refrigeration apparatus comprising: an avoidance control unit (78b) or a second wetness avoidance control unit (79b) and a fourth control unit (19) that executes control. In claim 20,
When the detection value Td of the discharge state detection means (61, 66) is larger than the upper limit side threshold value Tdmax set larger than the discharge target value Tm, the fourth control unit (19), or the intermediate When the detection value Tgsh of the superheat degree detection means (75) is larger than the upper limit side threshold value Tgshmax set larger than the intermediate superheat degree target value Tgshm, the second overheat avoidance control unit ( 78b) is selected and control is performed, The freezing apparatus characterized by the above-mentioned. In claim 20 or 21,
When the detection value Td of the discharge state detection means (61, 66) is further smaller than the lower limit side threshold value Tdmin set smaller than the discharge target value Tm, the fourth control unit (19), or the intermediate When the detected value Tgsh of the superheat degree detection means (75) is smaller than the lower limit side threshold value Tgshmin set smaller than the intermediate superheat degree target value Tgshm, the second wetness avoiding control unit ( 79b) is selected to execute the control. In any one of claims 20 to 22,
The fourth control unit (19) has a detection value Td of the discharge state detection means (61, 66) equal to or greater than a lower limit threshold Tdmin set smaller than the discharge target value Tm, and the discharge target value. A refrigeration apparatus configured to execute control by selecting the second discharge target control unit (56b) when the threshold value is equal to or less than an upper threshold Tdmax set larger than Tm.

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