JP2009228996A - Cooling system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cooling system capable of setting the temperature of storages to a desired appropriate temperature while obtaining sufficiently high operating efficiency. <P>SOLUTION: The cooling system is equipped with a plurality of evaporators 211, 221 disposed in parallel with expansion valves 213, 223 for adiabatically expanding a refrigerant compressed by a compressor 11 and condensed by a condenser 12 for evaporating the adiabatically expanded refrigerant, and sets the temperature of each of the storages 1a-6a of show cases 1-6 to the desired temperature by having the evaporated refrigerant to be sucked by the compressor 11 and circulating the refrigerant. The cooling system further includes a plurality of booster compressors 231 disposed in parallel on the downstream side of a plurality of refrigerating evaporators 221 that are targets for lowering the evaporation temperature of the refrigerant in the refrigerating evaporators 221 by sucking and compressing the refrigerant, and a booster control part 42 for increasing or decreasing at least one of an operating number and operating speed of the plurality of booster compressors 231 according to load of the plurality of refrigerating evaporators 221. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a cooling system, and more particularly to an improvement of a cooling system that brings a storage case of a showcase to a desired temperature state, for example.

  For example, in a plurality of showcases that display and sell products in a cooled state, an evaporator is provided in each of them, and these evaporators are arranged in parallel with an expansion valve, and are provided with a compressor and a condenser provided outside. The cooling system is configured by sequentially connecting the vessel and piping. In such a cooling system, the refrigerant compressed by the compressor is condensed by the condenser, adiabatically expanded by each expansion valve, evaporated by each evaporator, and sucked by the compressor and circulated. When the refrigerant evaporates in each evaporator, the container is brought to a desired temperature state by taking heat of the air in the showcase using heat of vaporization.

  On the other hand, when there is something that cools the storage case more than other showcases, such as a refrigeration showcase, it is downstream of an evaporator (hereinafter also referred to as a refrigeration evaporator) provided in the showcase. An auxiliary compressor is provided on the upstream side of the compressor. The auxiliary compressor sucks and compresses the refrigerant evaporated in the refrigeration evaporator. Thereby, the refrigerant | coolant evaporation temperature can be lowered | hung by the pressure of the refrigerant | coolant in a freezing evaporator falling. That is, in a cooling system provided with an auxiliary compressor, it is possible to connect a plurality of evaporators having different refrigerant evaporation temperatures to a common compressor and condenser (see, for example, Patent Document 1 and Patent Document 2). .

Japanese Patent No. 3855683 Japanese Utility Model Publication No. 62-27817

  By the way, in the cooling system proposed in Patent Documents 1 and 2 as described above, since one auxiliary compressor is provided downstream of one refrigeration evaporator, that is, the refrigeration evaporator and the auxiliary compression. Since the compressor is provided in a one-to-one relationship, the evaporation temperature of the refrigerant in the refrigeration evaporator is adjusted by adjusting the operating rotational speed of the auxiliary compressor. In other words, the operating rotational speed of the auxiliary compressor is adjusted according to the load of the refrigeration evaporator.

  For this reason, the auxiliary compressor must be operated at all times, and it cannot be said that the operation efficiency is excellent. Further, even if the operation speed of the auxiliary compressor is reduced and sufficiently reduced, the refrigerant evaporating temperature in the refrigeration evaporator may still be low, and the cooling in the refrigeration evaporator may be excessive. On the other hand, even if the operation speed of the auxiliary compressor is increased and increased sufficiently, the refrigerant evaporation temperature in the refrigeration evaporator may still be high, and cooling in the refrigeration evaporator is insufficient. There was a problem that there was a risk of end.

  In view of the above circumstances, an object of the present invention is to provide a cooling system that can satisfactorily bring a container into a desired temperature state while obtaining sufficiently high operation efficiency.

  In order to achieve the above object, a cooling system according to claim 1 of the present invention is arranged in parallel with an expansion valve for adiabatically expanding a refrigerant compressed by a compressor and condensed by a condenser, and the expansion valve A plurality of evaporators for evaporating the refrigerant adiabatically expanded in the housing, and sucking the refrigerant evaporated in the evaporator into the compressor and circulating the refrigerant, thereby accommodating each showcase provided with the plurality of evaporators In the cooling system for bringing the storage into a desired temperature state, the cooling system is arranged in a manner in parallel with the downstream side of the plurality of refrigeration evaporators of the plurality of evaporators and the upstream side of the compressor, A plurality of auxiliary compressors that lower the evaporation temperature of the refrigerant in the refrigeration evaporator by sucking and compressing the refrigerant evaporated in the refrigeration evaporator, and depending on the load of the plurality of refrigeration evaporators Multiple auxiliary pressures Characterized by comprising a number of operating and auxiliary compression control means for increasing or decreasing at least one of the working rotational speed of the machine.

  A cooling system according to a second aspect of the present invention is the electromagnetic system according to the first aspect, wherein the upstream side of each of the refrigeration evaporators permits or regulates the supply of the refrigerant to the refrigeration evaporator. The auxiliary compression control means increases or decreases at least one of the number of operating and the number of operating revolutions of the plurality of auxiliary compressors according to the operating rate of each electromagnetic valve. .

  Further, in the cooling system according to claim 3 of the present invention, in the above-described claim 2, the auxiliary compression control means exceeds a preset reference operating rate upper limit value among operating rates of the electromagnetic valves. When there are one or more, at least one of the number of operating and the number of operating rotations of the plurality of auxiliary compressors is increased, while the operating rate of each solenoid valve is below a preset reference operating rate lower limit value When there are one or more things, at least one of the number of operating and the number of operating revolutions of the plurality of auxiliary compressors is reduced.

  The cooling system according to claim 4 of the present invention is the cooling system according to claim 1, wherein the degree of superheat in the refrigeration evaporator is calculated, and the calculated degree of superheat is below a preset reference superheat degree lower limit value. Is determined that the refrigerant discharged from the refrigeration evaporator is in a gas-liquid two-phase state, and if the calculated superheat degree exceeds a preset reference superheat degree upper limit value, the refrigeration evaporation is performed. The auxiliary compression control means is configured so that the refrigerant discharged from the refrigeration evaporator by the determination means is in a gas-liquid two-phase state. If there is one or more determined to be present, at least one of the number of operating and the number of operating revolutions of the plurality of auxiliary compressors is increased, while the determination means completes the evaporation of the refrigerant in the refrigeration evaporator The middle point When those determined to be in the near there are one or more, and wherein the reducing at least one of the number of operating units and operating rotational speed of the plurality of auxiliary compressor.

  A cooling system according to a fifth aspect of the present invention is the cooling system according to any one of the first to fourth aspects, wherein the compressor rotates according to loads of a plurality of evaporators including the refrigeration evaporator. A compression control means for increasing or decreasing the number is provided.

  The cooling system according to claim 6 of the present invention is the cooling system according to claim 5, wherein the compression control means is for refrigerating based on information on the load of the refrigerating evaporator given from the auxiliary compression control means. It is characterized by determining the load of the evaporator.

  A cooling system according to a seventh aspect of the present invention is the cooling system according to any one of the first to sixth aspects, wherein each of the plurality of evaporators including the refrigeration evaporator is standardized. It has a size, and the number provided in each showcase is determined in such a manner that the number of arrangement increases according to the size of the cooling load of the storage.

  A cooling system according to an eighth aspect of the present invention is the cooling system according to any one of the first to seventh aspects, wherein the indoor air of the room in which the showcase is installed is transferred between the inside and the outside of the room. The indoor air circulation means for circulation and an expansion mechanism for adiabatically expanding the refrigerant compressed by the compressor and condensed by the condenser are disposed outside the chamber and evaporate the refrigerant adiabatically expanded by the expansion mechanism. And an air conditioning evaporator for cooling indoor air circulated by the indoor air circulation means.

  The cooling system according to claim 9 of the present invention is the cooling system according to claim 8, characterized in that the compression control means increases or decreases the operating rotational speed of the compressor according to the load of the air conditioning evaporator. To do.

  In the cooling system according to claim 10 of the present invention, the temperature of indoor air passing from the chamber toward the air-conditioning evaporator is detected by the indoor air circulation means in claim 8 or claim 9 described above. A suction temperature detection means, and the compression control means increases the operating speed of the compressor when the temperature detected by the suction temperature detection means exceeds a predetermined reference suction temperature upper limit value. When the temperature detected by the suction temperature detecting means falls below a predetermined reference suction temperature lower limit value, the operating rotational speed of the compressor is reduced.

  A cooling system according to an eleventh aspect of the present invention is the refrigeration evaporation according to any one of the first to tenth aspects, wherein the refrigeration evaporator is excluded from the evaporator provided in the showcase. An auxiliary introduction path for branching in the middle of the path from the cooler to the compressor and merging with the upstream side of the auxiliary compressor, for guiding the refrigerant evaporated in the refrigeration evaporator to the auxiliary compressor, It is arranged in the auxiliary introduction path and allows passage of the refrigerant evaporated by the refrigeration evaporator when it is in an open state, while allowing passage of refrigerant evaporated by the refrigeration evaporator when it is in a closed state. The auxiliary introduction valve to be regulated and the path from the refrigeration evaporator to the compressor, disposed downstream of the branch point with the auxiliary introduction path, and when the auxiliary introduction valve is in a closed state For refrigeration in the open state A feedback valve that allows passage of the refrigerant evaporated by the generator while closing the auxiliary introduction valve when the auxiliary introduction valve is opened, and restricts passage of the refrigerant evaporated by the refrigeration evaporator. It is characterized by that.

  A cooling system according to a twelfth aspect of the present invention is the cold storage tank according to any one of the first to eleventh aspects, wherein the showcase stores cold heat generated by evaporation of the refrigerant in the evaporator. Is provided.

  The cooling system according to claim 13 of the present invention is the cooling system according to any one of claims 8 to 12, wherein the indoor air circulation means blows out the air cooled by the air conditioning evaporator into the chamber. It is provided with a blowing direction adjusting means for adjusting the temperature, and the inside air of the storage box sucked through the suction port is passed around the disposed evaporator, and is cooled through the evaporator through the blower outlet. An air circulation means that circulates the air inside the storage between the inside and outside of the storage, and a suction port that detects the temperature of the air that is sucked through the suction port Temperature detecting means; outlet temperature detecting means for detecting the temperature of the air in the compartment blown out through the outlet; interior temperature detecting means for detecting the air temperature in the interior of the storage; and the suction port Temperature detection If there is a storage container in which at least two detected temperatures exceed the preset reference temperatures among the temperatures detected by the stage, the outlet temperature detection means and the internal temperature detection means, the storage container The air is blown out through the air outlet and is turbulent in the air that reaches the air inlet, and a command is given to the air outlet direction adjusting means that blows out air around the installation location of the showcase including the storage. A blow direction control means for changing the blow direction is provided.

  According to a fourteenth aspect of the present invention, in the thirteenth aspect described above, the blowing direction control means is configured such that when there is a showcase during the defrosting operation, the air around the place where the showcase is installed. A command is given to the blowing direction adjusting means for blowing out the air, and the cooled air is blown out toward the showcase.

  The cooling system according to claim 15 of the present invention is the cooling system according to any one of claims 8 to 12, wherein the indoor air circulation means blows out the air cooled by the air conditioning evaporator into the chamber. And a blow-out amount adjusting means for adjusting the blow-out amount of the air into the chamber, and is disposed outside the showcase and detects the ambient temperature of the showcase. When the detected temperature by the ambient temperature detecting means and the ambient temperature detecting means is equal to or higher than a preset reference ambient temperature, the blowing direction adjusting means and the blowing amount adjusting means based on predetermined load reduction information And a blown air control means for giving a command to each of the compression control means and performing blown air control of the blown direction, blown amount and blown temperature of the air cooled by the air conditioning evaporator. That.

  The cooling system according to claim 16 of the present invention is the cooling system according to any one of claims 8 to 12, wherein the indoor air circulation means blows out the air cooled by the air conditioning evaporator to the chamber. A suction port for detecting the temperature of the air in the chamber that is sucked in through the suction port of the storage box, and comprising a blowing direction adjusting unit that adjusts the blowing direction adjusting means for adjusting the blowing amount of the air to the chamber When the temperature detected by the temperature detecting means and the inlet temperature detecting means is equal to or higher than a preset reference inlet temperature, the outlet direction adjusting means and the outlet amount adjustment based on predetermined load reduction information And a blown air control means for giving a command to each of the means and the compression control means, and performing blown air control of the blown direction, blown amount and blown temperature of the air cooled by the air-conditioning evaporator. That.

  The cooling system according to claim 17 of the present invention is the cooling system according to any one of claims 8 to 12, wherein the indoor air circulation means blows out the air cooled by the air conditioning evaporator into the chamber. And a blowing amount adjusting means for adjusting the blowing amount of the air into the chamber, and the absolute humidity around the showcase is equal to or higher than a preset reference absolute temperature. In this case, a command is given to each of the blowing direction adjusting means, the blowing amount adjusting means and the compression control means based on predetermined load reduction information, and the blowing direction of the air cooled by the air conditioning evaporator, A blown air control means for performing blown air control of the blowout amount and the blowout temperature is provided.

  The cooling system according to claim 18 of the present invention is the cooling system according to claim 17 described above, wherein the ambient temperature detecting means for detecting the ambient temperature of the showcase and the ambient relative temperature for detecting the relative humidity of the ambient air of the showcase. Humidity detection means, and the blown air control means is configured to detect the surroundings of the showcase from the ambient temperature detected by the ambient temperature detection means and the relative humidity of the ambient air detected by the ambient relative humidity detection means. It is characterized by deriving absolute humidity.

  A cooling system according to a nineteenth aspect of the present invention is the cooling system according to the fifth or sixth aspect, wherein a plurality of the compressors are provided, and the compression control means performs the compression according to loads of a plurality of evaporators. The number of operation of the machine and the number of rotations of the machine are increased or decreased, and the number of increase / decrease of the number of operation of the compressor by the compression control means in a preset setting time is predetermined and exceeds the reference number, and exceeds the reference number When there are a plurality of compressors operating at that time and the internal temperature of the storage is within a predetermined target temperature range, when the degree of superheat in the evaporator exceeds a predetermined threshold, The number of operating compressors is decreased by the compression control means, while the number of operating compressors is maintained by the compression control means when the degree of superheat is equal to or less than the threshold. Characterized by comprising a.

  The cooling system according to a twentieth aspect of the present invention is the cooling system according to the nineteenth aspect described above, wherein the operation number control means is configured such that the number of increase / decrease in the number of compressors operated by the compression control means in the set time is the reference number. When the number of compressors operating at the time of exceeding the reference number exceeds one and the internal temperature of the container is within a predetermined target temperature range, when the degree of superheat exceeds the threshold The operation speed of the compressor being operated is decreased by the compression control means, while the operation number of the compressors is maintained by the compression control means when the degree of superheat is equal to or less than the threshold value.

  A cooling system according to a twenty-first aspect of the present invention is the cooling system according to the fifth or sixth aspect described above, wherein a plurality of the compressors are provided, and the compression control means performs the compression according to loads of a plurality of evaporators. The number of operation of the machine and the number of rotations of the machine are increased or decreased, and the number of increase / decrease of the number of operation of the compressor by the compression control means in a preset setting time is predetermined and exceeds the reference number, and exceeds the reference number When there are a plurality of compressors operating at that time and the internal temperature of the container is within a predetermined target temperature range, when the operating rate of the solenoid valve is equal to or less than a predetermined threshold, The compression control means is provided with an operation number control means for reducing the operation number of the compressors, and when the operation rate exceeds the threshold value, the compression control means maintains the operation number of the compressors. Characterized in that was.

  The cooling system according to claim 22 of the present invention is the cooling system according to claim 21, wherein the operation number control means is configured such that the number of increase / decrease in the number of operation of the compressor by the compression control means during the set time is equal to the reference number. When the operating number is less than the threshold when the number of operating compressors at the time of exceeding the reference number is single and the internal temperature of the storage is within a predetermined target temperature range The compression control means decreases the operating rotational speed of the operating compressor, while the compression control means maintains the number of operating compressors when the operating rate exceeds the threshold value.

  The cooling system according to a twenty-third aspect of the present invention is the cooling system according to any one of the nineteenth to twenty-second aspects described above, wherein the operation number control means is a number of compressors operated by the compression control means in the set time. When the increase / decrease count exceeds the reference count, the number of compressors operating at the time when the reference count is exceeded, and the internal temperature of the container is less than the lower limit value of the target temperature range, While the compression control means reduces the number of operating compressors, when the internal temperature of the container exceeds the upper limit value of the target temperature range, the compression control means maintains the number of operating compressors. And

  The cooling system according to a twenty-fourth aspect of the present invention is the cooling system according to any one of the nineteenth to twenty-third aspects described above, wherein the operation number control means is a number of compressors operated by the compression control means in the set time. When the number of increase / decrease exceeds the reference number, the number of operating compressors at the time when the reference number is exceeded, and the internal temperature of the container is less than the lower limit value of the target temperature range, While the compression control means maintains the number of operating compressors, when the internal temperature of the container exceeds the upper limit value of the target temperature range, the compression control means increases the number of compressors operated. And

  The cooling system according to claim 25 of the present invention is the cooling system according to any one of claims 19 to 24 described above, wherein the operating number control means is a number of operating compressors by the compression control means in the set time. When the increase / decrease count exceeds the reference count, the control for increasing / decreasing the number of operating compressors and the operating rotational speed of the compressor by the compression control means is stopped during a preset standby time.

  According to the cooling system of the present invention, a plurality of auxiliary compressors arranged in parallel with a downstream side of a plurality of target refrigeration evaporators and an upstream side of the compressor among the plurality of evaporators. However, by sucking and compressing the refrigerant evaporated in the refrigeration evaporator, the refrigerant evaporation temperature in the refrigeration evaporator is lowered, and a plurality of auxiliary compression control means are provided according to the loads of the plurality of refrigeration evaporators. Since at least one of the number of operating and the number of operating revolutions of the auxiliary compressors is increased or decreased, it is not necessary to always operate all the auxiliary compressors. Moreover, since the refrigeration evaporator and the auxiliary compressor have a plural-to-multiple relationship, the refrigerant of each refrigeration evaporator can be increased or decreased by increasing or decreasing the number of operating units as well as the operating speed of the auxiliary compressor. The evaporating temperature can be controlled, and the cooling in each refrigeration evaporator can be finely adjusted. Therefore, there is an effect that the storage can be satisfactorily brought into a desired temperature state while sufficiently high operation efficiency is obtained.

  Exemplary embodiments of a cooling system according to the present invention will be described below in detail with reference to the accompanying drawings.

<Embodiment 1>
FIG. 1 is a schematic diagram schematically showing a cooling system according to the first embodiment of the present invention. The cooling system illustrated here includes a refrigerator 10, a showcase cooling unit 20, an air conditioning unit 30, and a control unit 40.

  The refrigerator 10 is installed outdoors, for example, and includes a compressor 11 and a condenser 12 as shown in FIG. The compressor 11 compresses the refrigerant into a high-temperature and high-pressure state (high-temperature and high-pressure gas refrigerant). Although the details will be described later, the compressor 11 is driven in accordance with a command given from the control unit 40.

  The condenser 12 condenses the refrigerant supplied from the compressor 11 through the refrigerant pipe, that is, the high-temperature and high-pressure gas refrigerant compressed by the compressor 11 into a liquid refrigerant.

  The showcase cooling unit 20 is, for example, for bringing the storage cases 1a to 6a of a plurality of (six in the illustrated example) showcases 1 to 6 installed at predetermined locations in a room into a desired temperature state. Evaporator group 21, refrigeration evaporator group 22, booster unit 23, booster introduction path (auxiliary introduction path) 24, booster introduction valve (auxiliary introduction valve) 25, and feedback valve 26. It is.

  The refrigeration evaporator group 21 is connected to the outlet side of the refrigerator 10 through the refrigerant line in a manner in parallel with the refrigeration evaporator group 22, while the refrigerant lines are connected to each other at the downstream junction point P. It joins and is connected to the inlet side of the refrigerator 10. The refrigeration evaporator group 21 is for bringing the storages 1 a to 3 a of the three refrigeration showcases 1 to 3 in FIG. 2 into a desired temperature state, and includes a plurality of refrigeration evaporators 211. ing.

  The refrigeration evaporator 211 is separately disposed in the refrigeration showcases 1 to 3 together with the cold storage tank 212, and evaporates the supplied refrigerant. The cold storage tank 212 is provided on the refrigerant pipe on the outlet side of the refrigeration evaporator 211, and cools heat from the refrigeration evaporator 211, that is, cold heat generated in the ambient air as the refrigerant evaporates in the refrigeration evaporator 211. Accumulate.

  In addition, the refrigeration evaporator 211 is connected to the refrigeration temperature expansion valve 213 through a refrigerant line, and is connected to the condenser 12 through the refrigerant line in a manner in parallel with the refrigeration temperature expansion valve 213. is there.

  The refrigeration temperature expansion valve 213 is for adiabatically expanding the liquid refrigerant discharged from the condenser 12 and supplying the liquid refrigerant to the downstream refrigeration evaporator 211. Thereby, the refrigeration evaporator 211 evaporates the refrigerant adiabatically expanded by the refrigeration temperature expansion valve 213.

  In the first embodiment, the refrigeration temperature expansion valve 213 is based on the degree of superheat defined as the difference between the refrigerant temperature on the outlet side of the refrigeration evaporator 211 and the refrigerant temperature on the inlet side of the refrigeration evaporator 211. A temperature expansion valve capable of changing the opening degree and adjusting the flow rate of the refrigerant passing therethrough is applied. More specifically, the refrigeration temperature expansion valve 213 has a large opening when the degree of superheat is large, and a small opening when the degree of superheat is small.

  In addition, a refrigeration solenoid valve 214 is disposed in the refrigerant pipe on the upstream side of each of the refrigeration temperature expansion valves 213. The refrigeration solenoid valve 214 is controlled to be turned on / off in response to a command from the control unit 40, that is, is opened or closed to cut off or allow the supply of refrigerant from the condenser 12 to the corresponding refrigeration temperature expansion valve 213. To do.

  A refrigerator temperature sensor 215 is provided inside the storage boxes 1 a to 3 a of the refrigerated showcases 1 to 3. The refrigerator internal temperature sensor 215 detects the internal temperature of the containers 1a to 3a.

  The refrigeration evaporator group 22 is for bringing the storages 4 a to 6 a of the three refrigeration showcases 4 to 6 in FIG. 2 into a desired temperature state, and includes a plurality of refrigeration evaporators 221. Yes. The refrigeration evaporators 221 are separately disposed inside the refrigeration showcases 4 to 6 together with the cold storage tank 222, and evaporate the supplied refrigerant.

  The cold storage tank 222 is provided on the refrigerant pipe on the outlet side of the refrigeration evaporator 221, and cools heat from the refrigeration evaporator 221, that is, cold heat generated in the ambient air as the refrigerant evaporates in the refrigeration evaporator 221. Accumulate.

  The refrigeration evaporator 221 is connected to the refrigeration temperature expansion valve 223 through the refrigerant line, and connected to the condenser 12 through the refrigerant line in a manner in parallel with the refrigeration temperature expansion valve 223. is there.

  The refrigeration temperature expansion valve 223 is for adiabatically expanding the liquid refrigerant discharged from the condenser 12 and supplying the refrigerant to the downstream refrigeration evaporator 221. Thereby, the freezing evaporator 221 evaporates the refrigerant adiabatically expanded by the freezing temperature expansion valve 223.

  In the first embodiment, the refrigeration temperature expansion valve 223 is based on the degree of superheat defined as the difference between the refrigerant temperature on the outlet side of the refrigeration evaporator 221 and the refrigerant temperature on the inlet side of the refrigeration evaporator 221. A temperature expansion valve capable of changing the opening degree and adjusting the flow rate of the refrigerant passing therethrough is applied. More specifically, the refrigeration temperature expansion valve 223 has a large opening when the degree of superheat is large, and a small opening when the degree of superheat is small.

  In addition, a freezing solenoid valve 224 is disposed in each of the refrigerant pipes upstream of the freezing temperature expansion valve 223. The refrigeration solenoid valve 224 is controlled to be turned on / off in response to a command from the control unit 40, that is, is opened or closed to cut off or allow the supply of refrigerant from the condenser 12 to the corresponding refrigeration temperature expansion valve 223. To do.

  A freezer temperature sensor 225 is provided inside the storage boxes 4a to 6a of the freezing showcases 4 to 6. The freezer temperature sensor 225 detects the internal temperature (freezer temperature) of the storage boxes 4a to 6a.

  The booster unit 23 is disposed downstream of the refrigeration evaporator group 22 and upstream of the junction P. More specifically, the booster unit 23 includes a plurality (four in the illustrated example) of booster compressors (auxiliary compressors) 231 and a booster electromagnetic valve 232, and these booster compressors 231 are configured as follows: Along with the booster solenoid valve 232, it is connected to the refrigeration evaporator group 22 through the refrigerant pipe in a parallel manner.

  The booster compressor 231 sucks and compresses the refrigerant evaporated in the refrigeration evaporator 221. As a result, the refrigerant pressure in the refrigeration evaporator 221 decreases, and as a result, the refrigerant evaporation temperature in the refrigeration evaporator 221 decreases.

  Each booster solenoid valve 232 is disposed upstream of the booster compressor 231. These booster solenoid valves 232 are turned on / off by receiving a command from the control unit 40, that is, are opened / closed to cut off or allow the supply of refrigerant from the refrigeration evaporator 221 to the corresponding booster compressor 231. To do.

  The booster introduction path 24 branches from the refrigerant line downstream of the refrigeration evaporator group 21 and joins the refrigerant line downstream of the refrigeration evaporator group 22 and upstream of the booster unit 23. It is a path constituted by piping. That is, the booster introduction path 24 is a path for introducing the refrigerant that has passed through the refrigeration evaporator group 21 into the booster unit 23.

  The booster introduction valve 25 is disposed in the booster introduction path 24. When the booster introduction valve 25 opens and closes in response to a command given from the control unit 40 and enters an open state, the booster introduction valve 25 is evaporated by the refrigerant that has passed through the refrigeration evaporator group 21, that is, the refrigeration evaporator 211. While the refrigerant is allowed to pass through the booster introduction path 24, the refrigerant that has passed through the refrigeration evaporator group 21, that is, the refrigerant that has evaporated in the refrigeration evaporator 211 is allowed to pass through the booster introduction path 24. Is restricted.

  The return valve 26 is disposed at a predetermined position of the refrigerant pipe line from the branch point with the booster introduction path 24 to the junction P. When the feedback valve 26 opens and closes in response to a command given from the control unit 40 and enters an open state, the refrigerant that has passed through the refrigeration evaporator group 21, that is, the refrigerant that has evaporated in the refrigeration evaporator 211. In the closed state, the passage of the refrigerant that has passed through the refrigeration evaporator group 21, that is, the refrigerant that has evaporated in the refrigeration evaporator 211, is restricted.

  The air conditioning unit 30 is for bringing the inside of the chamber 4 in which the showcases 1 to 6 to be cooled by the showcase cooling unit 20 are installed into a desired temperature state. As shown in FIG. The air conditioner expansion valve (expansion mechanism) 31 and the air conditioner evaporator 32 are provided.

  The air conditioning expansion valve 31 adiabatically expands the supplied refrigerant. The air conditioning evaporator 32 is disposed on the downstream side of the air conditioning expansion valve 31 and evaporates the refrigerant adiabatically expanded by the air conditioning expansion valve 31.

  The air conditioning expansion valve 31 and the air conditioning evaporator 32 constitute a refrigerant circulation circuit by sequentially connecting to the refrigerator 10 (the compressor 11 and the condenser 12) through a refrigerant pipe. In this refrigerant circuit, the high-temperature and high-pressure gas refrigerant discharged from the compressor 11 is cooled in the condenser 12 to become a high-temperature and high-pressure liquid refrigerant. This high-temperature and high-pressure liquid refrigerant is adiabatically expanded by the air conditioning expansion valve 31 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant and supplied to the air-conditioning evaporator 32. The low-temperature and low-pressure gas-liquid two-phase refrigerant supplied to the air conditioning evaporator 32 exchanges heat with the internal air of the chamber 4 (hereinafter also referred to as indoor air) sucked from the suction port 34 by the air conditioning fan 33 and absorbs heat. The room air is cooled by becoming a low-temperature and low-pressure gas refrigerant. The low-temperature and low-pressure gas refrigerant discharged from the air-conditioning evaporator 32 is sucked into the compressor 11 and again becomes a high-temperature and high-pressure gas refrigerant and supplied to the condenser 12. By the way, the room air cooled by the air conditioning evaporator 32 is blown out from the blowout port 35 by the air conditioning fan 33, whereby the inside of the chamber 4 can be cooled to a desired temperature state.

  In this way, the air conditioning fan 33 constitutes an indoor air circulation means for circulating the room air in the room 4 in which the showcases 1 to 6 are installed between the inside and the outside of the room 4 through the suction port 34 and the air outlet 35. is doing.

  A suction temperature sensor 36 is disposed in the vicinity of the suction port 34 of the upper duct 5. The suction temperature sensor 36 is a suction temperature detection unit that detects the temperature of the indoor air that is sucked through the suction port 34 by the air conditioning fan 33 and passes toward the air conditioning evaporator 32.

  The control unit 40 comprehensively controls the operation of the cooling system. As shown in FIG. 4, the control unit 40 includes a compression control unit (compression control unit) 41 and a booster control unit (auxiliary compression control unit) 42. It is configured.

  The compression control unit 41 includes a setting storage unit 411, a communication processing unit 412, a refrigeration electromagnetic valve drive processing unit 413, an operating rate calculation unit 414, a compressor drive processing unit 415, a valve drive processing unit 416, A temperature comparison unit 417 is provided.

  The setting storage unit 411 is for setting and storing a program and data necessary for the compression control unit 41 to perform control, and particularly in the first embodiment, the upper limit value of the target refrigerator internal temperature and The lower limit value, the upper limit value and the lower limit value of the reference suction room temperature are set and stored. The communication processing unit 412 is for performing various information communication processing with the booster control unit 42.

  The refrigeration solenoid valve drive processing unit 413 performs on / off control, that is, opens or closes, by giving a command to each refrigeration solenoid valve 214.

  The operation rate calculation unit 414 calculates a refrigerating solenoid valve operation rate, which is a ratio of an on-time (opening time) of each refrigerating solenoid valve 214 with respect to a predetermined time before every predetermined time.

  The compressor drive processing unit 415 gives a command to the compressor 11 to drive or stop it, and increases or decreases the operating rotational speed of the compressor 11.

  The valve drive processing unit 416 gives a command to each of the booster introduction valve 25 and the feedback valve 26, and when opening the booster introduction valve 25, closes the feedback valve 26 and closes the booster introduction valve 25. In this case, the feedback valve 26 is opened. In a normal state, the valve drive processing unit 416 closes the booster introduction valve 25 and opens the feedback valve 26.

  The temperature comparison unit 417 compares the temperature detected by each sensor with the upper limit value or lower limit value of the temperature stored in the setting storage unit 411.

  The booster control unit 42 includes a setting storage unit 421, a communication processing unit 422, a refrigeration electromagnetic valve drive processing unit 423, an operating rate calculation unit 424, a booster electromagnetic valve drive processing unit 425, and a booster compressor drive processing unit. 426.

  The setting storage unit 421 is for setting and storing programs and data necessary for the booster control unit 42 to perform control. In particular, in the first embodiment, the upper limit value of the target freezer temperature and The lower limit is set and stored. The communication processing unit 422 is for performing communication processing of various information with the compression control unit 41.

  The refrigeration solenoid valve drive processing unit 423 performs on / off control, that is, opens or closes, by giving a command to each refrigeration solenoid valve 224.

  The operation rate calculation unit 424 calculates a refrigeration solenoid valve operation rate, which is a ratio of the on-time (opening time) of each refrigeration solenoid valve 224 with respect to the previous fixed time every fixed time.

  The booster solenoid valve drive processing unit 425 is for performing on / off control, that is, opening or closing, by giving a command to each booster solenoid valve 232.

  The booster compressor drive processing unit 426 gives commands to the booster compressors 231 to drive them, or increases or decreases the operating rotational speeds of the booster compressors 231.

  In the cooling system as described above, the high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 11 constituting the refrigerator 10 is condensed in the condenser 12 to become a high-temperature and high-pressure liquid refrigerant. This high-temperature and high-pressure liquid refrigerant branches in the middle, and one is discharged to the showcase cooling unit 20 and the other is discharged to the air conditioning unit 30. The liquid refrigerant discharged to the showcase cooling unit 20 branches halfway and one is discharged to the refrigeration evaporator group 21 and the other is discharged to the refrigeration evaporator group 22.

  The liquid refrigerant discharged to the refrigeration evaporator group 21 is branched and supplied to the refrigeration temperature expansion valve 213 via the refrigeration solenoid valve 214, and is adiabatically expanded to become a low-temperature and low-pressure gas-liquid two-phase refrigerant. It is supplied to the evaporator 211.

  The low-temperature and low-pressure gas-liquid two-phase refrigerant supplied to the refrigeration evaporator 211 is stored in the storage cabinets 1a to 3a of the refrigeration showcases 1 to 3 supplied through the suction port 217 by the blower fan (internal air circulation means) 216. The inside air cooled by heat exchange with the inside air and evaporating to become a low-temperature and low-pressure gas refrigerant is blown out from the outlet 218 to the housings 1a to 3a, whereby the housings 1a to 3a Cooling takes place.

  The low-temperature and low-pressure gas refrigerant that has passed through the refrigeration evaporator 211 is sucked into the compressor 11 and then merges and passes through the feedback valve 26 that is discharged from the refrigeration evaporator group 21 and is in an open state. To the confluence P.

  The liquid refrigerant discharged to the refrigeration evaporator group 22 is branched and supplied to the refrigeration temperature expansion valve 223 via the refrigeration solenoid valve 224, and is adiabatically expanded to form a low-temperature and low-pressure gas-liquid two-phase refrigerant. Supplied to the evaporator 221.

  The low-temperature and low-pressure gas-liquid two-phase refrigerant supplied to the refrigeration evaporator 221 is stored in the storage cases 4a to 6a of the refrigeration showcases 4 to 6 supplied through a suction port 227 by a blower fan (internal air circulation means) 226. The inside air is cooled by exchanging heat with the inside air and evaporating into a low-temperature and low-pressure gas refrigerant. The cooled internal air is blown out from the outlet 228 to the storage boxes 4a to 6a, whereby the storage boxes 4a to 6a are cooled.

  Here, the refrigerant in the refrigeration evaporator 221 acts not only with the suction force by the compressor 11 but also with the suction force by the booster compressor 231 constituting the booster unit 23, so that the pressure in the refrigeration evaporator 211 is increased. It is lower than the refrigerant pressure. Therefore, the evaporating temperature of the refrigerant in the freezing evaporator 221 is lower than the evaporating temperature of the refrigerant in the refrigeration evaporator 211, so that the storage boxes 4 a to 6 a of the freezing showcases 4 to 6 are stored in the refrigeration show. It becomes lower than the storage 1a-3a of cases 1-3.

  The low-temperature and low-pressure gas refrigerant that has passed through the refrigeration evaporator 221 is sucked into the booster compressor 231 and the compressor 11, and then merges, discharged from the refrigeration evaporator group 22, and discharged to the booster unit 23. The

  The refrigerant discharged to the booster unit 23 is branched and supplied to the booster compressor 231 via the booster solenoid valve 232, and is compressed by the booster compressor 231, and the suction force of the compressor 11 acts and joins the booster unit. 23 is discharged to reach the confluence P.

  The refrigerant discharged from the refrigeration evaporator group 21 and the refrigerant discharged from the booster unit 23 after passing through the refrigeration evaporator group 22 merge at the junction P and are sucked into the compressor 11.

  The liquid refrigerant discharged to the air conditioning unit 30 is supplied to the air conditioning expansion valve 31, is adiabatically expanded, becomes a low-temperature low-pressure gas-liquid two-phase refrigerant, and is supplied to the air-conditioning evaporator 32. The low-temperature and low-pressure gas-liquid two-phase refrigerant supplied to the air-conditioning evaporator 32 exchanges heat with the room air supplied by the air-conditioning fan 33 and evaporates to become a low-temperature and low-pressure gas refrigerant, thereby cooling the chamber 4. . The low-temperature and low-pressure gas refrigerant that has passed through the air conditioning evaporator 32 is sucked into the compressor 11.

  And the control unit 40 which comprises such a cooling system performs each control processing as shown below.

  5, 6, and 8 to 11 are flowcharts showing the contents of the processing that the control unit 40 individually performs, FIG. 5 is a refrigeration electromagnetic valve control process, FIG. 6 is a booster unit control process (1), 8 is a refrigeration solenoid valve control process, FIG. 9 is a compressor drive control process (1), FIG. 10 is a compressor drive control process (2), and FIG. 11 is a valve switching control process. Hereinafter, the operation of the cooling system will be described with reference to these drawings.

  In the refrigeration solenoid valve control process shown in FIG. 5, the booster control unit 42 (control unit 40) detects the freezer temperature of the storage boxes 4 a to 6 a in the respective freezer showcases 4 to 6 through the freezer temperature sensor 225 ( Step S101), it is determined whether or not the detected freezer temperature exceeds the upper limit value of the target freezer temperature stored in the setting storage unit 421 (step S102).

  When the freezer temperature detected in any of the freezer showcases 4 to 6 exceeds the target freezer temperature upper limit (step S102: Yes), the booster control unit 42 passes through the freezing solenoid valve drive processing unit 423. The refrigeration solenoid valve 224 of the corresponding refrigeration showcases 4 to 6 is on-controlled (opened) to allow the refrigerant to be supplied to the refrigeration temperature expansion valve 223 (refrigeration evaporator 221) ( Step S103), and then the procedure is returned to end the current process.

  As a result, the storage cases 4a to 6a of the corresponding freezing showcases 4 to 6 are cooled, and the temperature in the freezer of the storage cases 4a to 6a is changed to be equal to or lower than the target freezer temperature.

  In step S102, when the freezer temperature of the storages 4a to 6a is equal to or lower than the target freezer temperature in any of the freezer showcases 4 to 6 (step S102: No), the booster control unit 42 then selects either It is determined whether or not the freezer temperature detected in the freezer showcases 4 to 6 is below the lower limit value of the target freezer temperature stored in the setting storage unit 421 (step S104).

  When the freezer temperature detected in any of the freezer showcases 4 to 6 is lower than the target freezer temperature lower limit (step S104: Yes), the booster control unit 42 passes through the freezing electromagnetic valve drive processing unit 423. The refrigeration solenoid valve 224 of the corresponding refrigeration showcases 4 to 6 is turned off (closed) to stop the supply of the refrigerant to the refrigeration temperature expansion valve 223 (refrigeration evaporator 221) (step S105). ), And then return to the procedure to end the current process.

  As a result, in the corresponding refrigeration showcases 4 to 6, heat exchange between the air in the storage 4 a to 6 a and the refrigeration evaporator 221 is suppressed, and the freezer temperature becomes equal to or higher than the target freezer temperature. It will change as follows.

  When the freezer temperature detected in any of the freezer showcases 4 to 6 in step S104 is equal to or higher than the target freezer temperature lower limit value (step S104: No), that is, all freezer temperatures (all containers 4a to 4). 6a) is equal to or lower than the target freezer temperature upper limit value and equal to or higher than the target freezer temperature lower limit value (hereinafter referred to as “target freezer temperature range”), the booster control unit 42 includes the freezing solenoid valve 224. In this state, the procedure is returned to end the current process.

  Hereinafter, by repeatedly performing the refrigeration solenoid valve control process at a predetermined cycle time, the freezer temperature of the storage boxes 4a to 6a is maintained in the target freezer temperature range in all the freezer showcases 4 to 6. Become.

  In the booster unit control process (1) shown in FIG. 6, the booster control unit 42 calculates the operation rate of each refrigeration solenoid valve 224 through the operation rate calculation unit 424 (step S111). As a result of the calculation, when the refrigeration capacity determination condition (a) as shown in FIG. 7 is satisfied (step S112: Yes), that is, the operation rate of at least one solenoid valve is 90% (reference operation rate upper limit value). If exceeded, the booster control unit 42 determines that the number of operating booster compressors 231 can be increased through the booster compressor drive processing unit 426, assuming that the refrigerating capacity is insufficient (step S113). .

  As a result, when the number of operating units can be increased (step S113: Yes), the booster control unit 42 controls the booster solenoid valve 232 to be turned on (opens operation) through the booster solenoid valve drive processing unit 425, and booster compression is performed. The corresponding booster compressor 231 is driven through the machine drive processing unit 426 (step S114, step S115), and then the procedure is returned to end the current process. As a result, the suction force of the refrigerant by the booster unit 23 increases, thereby reducing the refrigerant pressure of the refrigeration evaporator 221 constituting the refrigeration evaporator group 22, and the refrigerant evaporation temperature in the refrigeration evaporator 221. Can be reduced.

  When the evaporation temperature of the refrigerant is thus lowered, the storage cases 4a to 6a of the freezer showcases 4 to 6 are cooled. As described in the above-described freezing electromagnetic valve control process, the freezer temperature is set to the target freezer. It becomes possible to shift to the internal temperature range.

  In step S113, when the number of operating booster compressors 231 cannot be increased (step S113: No), the booster control unit 42 determines the operating rotational speed of the corresponding booster compressor 231 through the booster compressor drive processing unit 426. The number is increased (step S116), and then the procedure is returned to end the current process.

  As a result, the low pressure setting value of the booster compressor 231 with the increased operating rotational speed is lowered, the refrigerant pressure of the refrigeration evaporator 221 constituting the refrigeration evaporator group 22 is lowered, and It becomes possible to reduce the evaporation temperature of the refrigerant in the evaporator 221.

  When the evaporation temperature of the refrigerant is thus lowered, the storage cases 4a to 6a of the freezer showcases 4 to 6 are cooled. As described in the above-described freezing electromagnetic valve control process, the freezer temperature is set to the target freezer. It becomes possible to shift to the internal temperature range.

  When the operating rate of the refrigeration solenoid valve 224 calculated in step S111 meets the refrigeration capacity determination condition (b) (step S112: No, step S117: Yes), that is, the operating rates of all the solenoid valves are 40 to 90%. The booster control unit 42 maintains the state of the booster solenoid valve 232 and the booster compressor 231 (step S118), and then returns the procedure to end the current process, assuming that the refrigerating capacity is appropriate. To do.

  On the other hand, when the operating rate of the refrigeration solenoid valve 224 calculated in step S111 does not meet the refrigeration capacity determination condition (b) (step S112: No, step S117: No), that is, the calculated operating rate of the solenoid valve is refrigeration capacity. When the condition (c) is met, that is, when the operating rate of all solenoid valves is 90% or less and the operating rate of at least one solenoid valve is below 40% (reference operating rate lower limit value), the booster The control unit 42 determines whether the number of operating booster compressors 231 can be reduced through the booster compressor drive processing unit 426, assuming that the refrigerating capacity is excessive (step S119).

  As a result, when the number of operating units can be reduced (step S119: Yes), the booster control unit 42 controls to turn off the corresponding booster solenoid valve 232 through the booster solenoid valve drive processing unit 425 (step S120), and then performs the procedure. To end the current process.

  As a result, the refrigerant does not flow to the booster compressor 231 on the downstream side of the booster solenoid valve 232 that is off-controlled, and the booster compressor 231 is automatically stopped.

  By reducing the number of booster compressors 231 operated in this way, the refrigerant suction force by the booster unit 23 is reduced, thereby increasing the refrigerant pressure of the refrigeration evaporator 221 constituting the refrigeration evaporator group 22. It becomes possible to raise the evaporation temperature of the refrigerant in the freezing evaporator 221.

  As described above, when the evaporation temperature of the refrigerant is increased, the cooling of the storage cases 4a to 6a of the freezer showcases 4 to 6 is alleviated. As described in the above-described freezing electromagnetic valve control process, the freezer temperature is thus increased. It becomes possible to shift to the target freezer temperature range.

  In step S119, when the number of operating booster compressors 231 cannot be reduced (step S119: No), the booster control unit 42 determines the operating rotational speed of the corresponding booster compressor 231 through the booster compressor drive processing unit 426. (Step S121), and then the procedure is returned to end the current process.

  As a result, the low pressure setting value of the booster compressor 231 with the reduced operating rotational speed is increased, and the refrigerant pressure of the refrigeration evaporator 221 constituting the refrigeration evaporator group 22 is increased. It becomes possible to raise the evaporation temperature of the refrigerant in the evaporator 221.

  As described above, when the evaporation temperature of the refrigerant is increased, the cooling of the storage cases 4a to 6a of the freezer showcases 4 to 6 is alleviated. As described in the above-described freezing electromagnetic valve control process, the freezer temperature is thus increased. It becomes possible to shift to the target freezer temperature range.

  In the refrigeration solenoid valve control process shown in FIG. 8, the compression control unit 41 (control unit 40) detects the temperatures in the refrigerators of the storage boxes 1 a to 3 a in the respective refrigeration showcases 1 to 3 through the refrigerator temperature sensor 215 ( Step S131), it is determined whether or not the detected refrigerator temperature exceeds the upper limit value of the target refrigerator temperature stored in the setting storage unit 411 (Step S132).

  When the refrigerator internal temperature detected in any of the refrigeration showcases 1 to 3 exceeds the target refrigerator internal temperature upper limit (step S132: Yes), the compression control unit 41 performs the refrigeration electromagnetic valve drive processing unit 413. The refrigeration solenoid valve 214 of the corresponding refrigeration showcase 1 to 3 is controlled to be turned on (opened) through the refrigeration temperature expansion valve 213 (refrigeration evaporator 211) to allow the supply of refrigerant. (Step S133) After that, the procedure is returned to end the current process.

  As a result, the storage cases 1a to 3a of the corresponding refrigerated showcases 1 to 3 are cooled, and the temperature in the refrigerator changes so as to be equal to or lower than the target refrigerator temperature.

  In step S132, when the refrigerator temperature detected in any of the refrigerated showcases 1 to 3 is equal to or lower than the target refrigerator temperature (step S132: No), the compression control unit 41 then selects one of the refrigerators. It is determined whether or not the refrigerator temperature detected in showcases 1 to 3 is lower than the lower limit value of the target refrigerator temperature stored in setting storage unit 411 (step S134).

  When the refrigerator internal temperature detected in any of the refrigerated showcases 1 to 3 is lower than the target refrigerator internal temperature lower limit (step S134: Yes), the compression control unit 41 includes the refrigeration electromagnetic valve drive processing unit 413. The refrigeration solenoid valve 214 of the corresponding refrigeration showcases 1 to 3 is controlled to be turned off (closed), and the supply of the refrigerant to the refrigeration temperature expansion valve 213 (refrigeration evaporator 211) is stopped (step) After that, the procedure is returned to end the current process.

  As a result, in the corresponding refrigeration showcases 1 to 3, heat exchange between the air in the storages 1a to 3a and the refrigeration evaporator 211 is suppressed, and the refrigerator internal temperature is equal to or higher than the target refrigerator internal temperature. It will change as follows.

  If the refrigerator temperature detected in any of the refrigerated showcases 1 to 3 in step S134 is equal to or higher than the target refrigerator temperature lower limit (step S134: No), that is, the internal temperature of the storage 1a to 3a (refrigerator When the internal temperature is equal to or lower than the target refrigerator internal temperature upper limit value and equal to or higher than the target refrigerator internal temperature lower limit value (hereinafter referred to as “target refrigerator internal temperature range”), the compression control unit 41 changes the state of the refrigeration solenoid valve 214. The procedure is returned and the current process is terminated.

  Hereinafter, by repeatedly performing the refrigeration electromagnetic valve control process at a predetermined cycle time, the refrigerator internal temperatures of the storage cabinets 1a to 3a are maintained in the target refrigerator internal temperature range in all the refrigeration showcases 1 to 3. Become.

  In the compressor drive control process (1) shown in FIG. 9, when the compression control unit 41 (control unit 40) inputs the refrigeration solenoid valve operating rate from the booster control unit 42 through the communication processing unit 412 (step S141: Yes). Then, the operation rate of each refrigeration solenoid valve 214 is calculated through the operation rate calculation unit 414 (step S142).

  As a result of the calculation, when the refrigeration capacity determination condition (a) as shown in FIG. 7 is satisfied (step S143: Yes), that is, when the operation rate of at least one solenoid valve exceeds 90%, the compression control unit 41 Since the refrigerating capacity is insufficient, the operating speed of the compressor 11 is increased through the compressor drive processing unit 415 (step S144), and then the procedure is returned to end the current process.

  As a result, the low pressure setting value of the compressor 11 is lowered, the refrigerant pressure of each evaporator is lowered, and the evaporation temperature of the refrigerant in these evaporators can be lowered.

  When the evaporating temperature of the refrigerant is thus lowered, as a result of cooling the storages 1a to 3a of the showcases 1 to 6, the internal temperature of the storages 1a to 3a can be changed to a desired temperature range. It becomes possible.

  When the operating rate of the refrigerating electromagnetic valve 224 input in step S141 and the operating rate of the refrigerating electromagnetic valve 214 calculated in step S142 meet the refrigerating capacity judgment condition (b) (step S143: No, step S145: Yes) ), That is, when the operating rates of all the solenoid valves are 40 to 90%, the compression control unit 41 maintains the state of the compressor 11 assuming that the refrigerating capacity is appropriate (step S146), and then performs the procedure. To end the current process.

  On the other hand, when the operation rate of the refrigeration solenoid valve 224 input in step S141 and the operation rate of the refrigeration solenoid valve 214 calculated in step S142 do not meet the refrigeration capacity determination condition (b) (step S143: No, step S145). : No), that is, when the operating rate of the refrigeration solenoid valve 224 and the operating rate of the refrigeration solenoid valve 214 meet the refrigeration capacity judgment condition (c) shown in FIG. 7, that is, the operating rates of all solenoid valves are 90 % And the operation rate of at least one solenoid valve is less than 40%, the compression control unit 41 determines that the refrigerating capacity is excessive, and the operation rotation speed of the compressor 11 through the compressor drive processing unit 415. (Step S147), and then the procedure is returned to end the current process.

  As a result, the low pressure setting value of the compressor 11 is increased, the refrigerant pressure of each evaporator is increased, and the evaporation temperature of the refrigerant in each evaporator can be increased.

  When the evaporating temperature of the refrigerant is thus increased, the cooling of the storage containers 1a to 3a of the showcases 1 to 6 is alleviated, and as a result, the internal temperature of the storage containers 1a to 3a is changed to a desired temperature range. Is possible.

  In the compressor drive control process (2) shown in FIG. 10, the compression control unit 41 (control unit 40) detects the temperature of the indoor air that passes through the suction port 34 through the suction temperature sensor 36 (hereinafter also referred to as “suction room temperature”). Then, it is determined whether or not the detected suction room temperature exceeds the upper limit value of the reference suction room temperature stored in the setting storage unit 411 (step S152).

  When the suction room temperature exceeds the reference suction room temperature upper limit (step S152: Yes), the compression control unit 41 increases the operation rotational speed of the compressor 11 through the compressor drive processing unit 415 (step S153). Thereafter, the procedure is returned to end the current process.

  As a result, the low pressure setting value of the compressor 11 is lowered, the refrigerant pressure of each evaporator is lowered, and the evaporation temperature of the refrigerant in these evaporators can be lowered.

  If the evaporation temperature of the refrigerant is thus reduced, the chamber 4 is cooled, and as a result, the internal temperature of the chamber 4 (indoor temperature) can be shifted to a desired temperature range.

  In step S152, when the detected suction chamber temperature is equal to or lower than the reference suction chamber temperature (step S152: No), the compression control unit 41 then sets the reference suction chamber temperature stored in the setting storage unit 411. It is determined whether it is below the lower limit value (step S154).

  When the detected suction room temperature is lower than the reference suction room temperature lower limit (step S154: Yes), the compression control unit 41 reduces the operation rotational speed of the compressor 11 through the compressor drive processing unit 415 (step S155). ), And then return to the procedure to end the current process.

  As a result, the low pressure setting value of the compressor 11 is increased, the refrigerant pressure of each evaporator is increased, and the evaporation temperature of the refrigerant in each evaporator can be increased.

  When the evaporation temperature of the refrigerant is increased in this way, the cooling of the chamber 4 is relaxed, and as a result, the room temperature can be shifted to a desired temperature range.

  When the suction room temperature detected in step S154 is equal to or higher than the reference suction room temperature lower limit value (step S154: No), that is, the suction room temperature is equal to or lower than the reference suction room temperature upper limit value and equal to or higher than the reference suction room temperature lower limit value (less than). , “Reference suction room temperature range”), the compression control unit 41 maintains the operation state of the compressor 11, returns the procedure, and ends the current process.

  Hereinafter, by repeatedly performing the compressor drive control process (2) at a predetermined cycle time, the room temperature is maintained within the reference suction room temperature range.

  Such a compressor drive control process (2) is performed in parallel with the compressor drive control process (1) described above, but each storage of the refrigerated showcases 1 to 3 and the freezer showcases 4 to 6 Since products are displayed in 1a to 6a, the cooling system according to the first embodiment is such that the compressor drive control process (1) is given priority over the compressor drive control process (2). It is.

  When the operation speed of the compressor 11 reaches the maximum value in any one of the compressor drive control process (1) and the compressor drive control process (2), the control unit 40 has the following valve Perform switching control processing. As a premise of such valve switching control processing, it is assumed that the booster introduction valve 25 is closed and the feedback valve 26 is opened.

  In the valve switching control process shown in FIG. 11, the compression control unit 41 (control unit 40) determines whether or not the operating rotational speed of the compressor 11 is the maximum value through the compressor drive processing unit 415 (step S161). When the operation rotational speed is the maximum value (step S161: Yes), the compression control unit 41 detects the temperatures in the refrigerators of the storage boxes 1a to 3a in the refrigeration showcases 1 to 3 through the refrigerator temperature sensor 215. (Step S162), it is determined whether or not the refrigerator temperature detected through the temperature comparison unit 417 exceeds the upper limit value of the target refrigerator temperature stored in the setting storage unit 411 (Step S163).

  In any of the refrigerated showcases 1 to 3, when the refrigerator internal temperature (the internal temperature of the storage 1a to 3a) exceeds the target refrigerator internal temperature upper limit (step S163: Yes), the compression control unit 41 The booster introduction valve 25 is turned on (opened) through the drive processing unit 416 (step S164), and the feedback valve 26 is turned off (closed) (step S165).

  As a result, the refrigerant that has passed through the refrigeration evaporator group 21, that is, the refrigerant that has evaporated in the refrigeration evaporator 211, passes through the booster introduction path 24 and is discharged to the booster unit 23. That is, the refrigerant pressure of the refrigeration evaporator 211 is reduced by being sucked by the booster compressor 231, and the evaporation temperature of the refrigerant in the refrigeration evaporator 211 can be lowered.

  When the evaporation temperature of the refrigerant is thus lowered, the storages 1a to 3a of the refrigerated showcases 1 to 3 are further cooled. As a result, the refrigerator temperature can be changed to a desired temperature range.

  In any of the refrigerated showcases 1 to 3, when the refrigerator temperature is equal to or lower than the target refrigerator temperature upper limit (step S163: No), the compression control unit 41 maintains the state of the booster introduction valve 25 and the feedback valve 26. Then, the procedure is returned to end the current process.

  According to the cooling system of the first embodiment of the present invention as described above, the booster control unit 42 (control unit 40) sets a preset reference operation rate upper limit value among the operation rates of the refrigeration solenoid valves 224. If there is one or more exceeding (90%), at least one of the operating number and operating speed of the booster compressor 231 is increased, while the operating rate of each refrigeration solenoid valve 224 is set in advance. If there is one or more lower than the reference operating rate lower limit (40%), at least one of the operating number and operating speed of the booster compressors 231 is reduced, so that all the booster compressors 231 are always turned on. There is no need to drive. Moreover, since the refrigeration evaporator 221 and the booster compressor 231 are in a plural-to-multiple relationship, each refrigeration evaporation can be performed by increasing / decreasing not only the operation speed of the booster compressor 231 but also the operation number. The evaporation temperature of the refrigerant in the vessel 221 can be controlled, and the cooling in each refrigeration evaporator 221 can be finely adjusted. Therefore, it is possible to satisfactorily bring the containers 1a to 3a to a desired temperature state while obtaining sufficiently high operation efficiency.

  According to the cooling system, the compression control unit 41 determines the load of each evaporator from the operating rate of each electromagnetic valve in parallel with the booster unit control process (1) by the booster control unit 42 and the compressor 11 Since the number of operations is increased / decreased (compressor drive control process (1)), the operation efficiency can be improved, and energy saving of the operation of the entire system can be achieved.

  Further, according to the cooling system of the first embodiment, the compression control unit 41 performs the suction temperature sensor 36 in parallel with the compressor drive control process (1) and the booster unit control process (1) by the booster control unit 42. Since the load of the air conditioner evaporator 32 is judged from the deviation between the suction room temperature detected by the above and the reference suction room temperature, and the operation speed of the compressor 11 is increased or decreased, the operation efficiency can be improved. Energy saving of the entire operation can be achieved.

  Furthermore, according to the cooling system of the first embodiment, the compression control unit 41 determines that the refrigerator internal temperature detected by the refrigerator internal temperature sensor 215 is the target refrigerator internal temperature when the operation rotational speed of the compressor 11 is the maximum value. When the upper limit is exceeded, the booster introduction valve 25 is turned on and the feedback valve 26 is turned off, so that the booster compressor 231 is shared between the refrigerated evaporator group and the refrigerated evaporator group. In addition, the storage temperatures 1a to 3a of the refrigerated showcases 1 to 3 can be satisfactorily cooled by lowering the evaporation temperature of the refrigerant in the refrigeration evaporator 211.

  Furthermore, according to the cooling system of the first embodiment, since the cold storage tanks 212 and 222 store cold heat, the blower fan 216 uses the cold heat stored in the cold storage tanks 212 and 222 as necessary. , 226 can be cooled, so that the operating loads of the compressor 11 and the booster compressor 231 can be leveled to save energy.

  The first embodiment of the present invention has been described above, but the present invention is not limited to this, and various modifications can be made. For example, in the above-described first embodiment, the suction room temperature detected by the suction temperature sensor 36 when determining the load of the air conditioning evaporator 32 is used. However, in the present invention, the load of the air conditioning evaporator 32 is determined. As long as it can be used, it is not necessary to limit to the suction room temperature, the temperature of the room air blown out from the outlet (the temperature of the blowout room air) may be used, and the value obtained by subtracting the temperature of the blowout room from the suction room temperature May be used.

  Moreover, in Embodiment 1 mentioned above, in booster unit control processing (1), it implements centering on control of the number of operation | movement of the booster compressor 231, and when increase / decrease in the number of operation is impossible, the booster compressor 231 of Although control for increasing / decreasing the operating rotational speed has been performed, in the present invention, it is not always necessary to focus on controlling the number of operating booster compressors 231. I do not care.

<Embodiment 2>
FIG. 12 is a schematic diagram schematically showing a cooling system according to the second embodiment of the present invention. In addition, the same code | symbol is attached | subjected to what has the same structure as the cooling system of Embodiment 1 mentioned above, and the description is abbreviate | omitted suitably. The cooling system illustrated here includes the refrigerator 10, the showcase cooling unit 200, the air conditioning unit 30, and the control unit 400.

  The showcase cooling unit 200 is, for example, for bringing the storages 1a to 6a of a plurality of (six in the illustrated example) showcases 1 to 6 installed at predetermined locations in a room to a desired temperature state. Evaporator group 210, refrigeration evaporator group 220, booster unit 23, booster introduction path 24, booster introduction valve 25, and feedback valve 26.

  The refrigeration evaporator group 210 is connected to the outlet side of the refrigerator 10 through the refrigerant line in a manner in parallel with the refrigeration evaporator group 220, while the refrigerant lines are connected to each other at the downstream junction point P. It joins and is connected to the inlet side of the refrigerator 10. This refrigeration evaporator group 210 is for bringing the storages 1 a to 3 a of the three refrigeration showcases 1 to 3 in FIG. 13 into a desired temperature state, and includes a plurality of refrigeration evaporators 211. ing.

  The refrigeration evaporator 211 is separately disposed in the refrigeration showcases 1 to 3 together with the cold storage tank 212, and evaporates the supplied refrigerant. The cold storage tank 212 is provided on the refrigerant pipe on the outlet side of the refrigeration evaporator 211, and cools heat from the refrigeration evaporator 211, that is, cold heat generated in the ambient air as the refrigerant evaporates in the refrigeration evaporator 211. Accumulate.

  The refrigeration evaporator 211 is connected to the refrigeration electronic expansion valve 213a through a refrigerant line, and is connected to the condenser 12 through the refrigerant line in parallel with the refrigeration electronic expansion valve 213a. is there.

  The refrigeration electronic expansion valve 213 a is for adiabatically expanding the liquid refrigerant discharged from the condenser 12 and supplying it to the downstream refrigeration evaporator 211. Thereby, the refrigeration evaporator 211 evaporates the refrigerant adiabatically expanded by the refrigeration electronic expansion valve 213a.

  In the second embodiment, the refrigeration electronic expansion valve 213a changes the opening degree according to the opening degree command when an opening degree command is given from an electronic expansion valve controller (not shown), and changes the flow rate of the passing refrigerant. An electronic expansion valve that can be adjusted is applied. In addition, a refrigeration solenoid valve 214 is disposed in the refrigerant pipe on the upstream side of each of the refrigeration electronic expansion valves 213a.

  In these refrigeration evaporator groups 210, refrigerator internal temperature sensors 215 are provided inside the storages 1 a to 3 a of the respective refrigeration showcases 1 to 3, while refrigerant lines connected to the refrigeration evaporator 211 are provided. Refrigerant temperature sensors 219a, 219b, and 219c are respectively provided at the inlet, outlet, and intermediate portion. The inlet part refrigerant temperature sensor 219a and the outlet part refrigerant temperature sensor 219b detect the temperature of the refrigerant passing through the respective refrigerant pipes. The intermediate part refrigerant temperature sensor 219c detects the temperature of the refrigerant passing through a part close to the outlet part inside the refrigeration evaporator 211.

  The refrigeration evaporator group 220 is for bringing the storages 4 a to 6 a of the three refrigeration showcases 4 to 6 in FIG. 13 into a desired temperature state, and includes a plurality of refrigeration evaporators 221. Yes. The refrigeration evaporators 221 are separately disposed inside the refrigeration showcases 4 to 6 together with the cold storage tank 222, and evaporate the supplied refrigerant.

  The cold storage tank 222 is provided on the refrigerant pipe on the outlet side of the refrigeration evaporator 221, and cools heat from the refrigeration evaporator 221, that is, cold heat generated in the ambient air as the refrigerant evaporates in the refrigeration evaporator 221. Accumulate.

  The refrigerating evaporator 221 is connected to the refrigerating electronic expansion valve 223a through the refrigerant line, and connected to the condenser 12 through the refrigerating line in parallel with the refrigerating electronic expansion valve 223a. is there.

  The refrigeration electronic expansion valve 223 a is for adiabatically expanding the liquid refrigerant discharged from the condenser 12 and supplying it to the downstream refrigeration evaporator 221. Thereby, the freezing evaporator 221 evaporates the refrigerant adiabatically expanded by the freezing electronic expansion valve 223a.

  In the second embodiment, the freezing electronic expansion valve 223a changes the opening degree according to the opening degree command when the opening degree command is given from an electronic expansion valve controller (not shown), and changes the flow rate of the refrigerant passing therethrough. An electronic expansion valve that can be adjusted is applied. In addition, a refrigeration solenoid valve 224 is disposed in the refrigerant pipe on the upstream side of each of the refrigeration electronic expansion valves 223a.

  In these refrigeration evaporator groups 220, a freezer temperature sensor 225 is provided inside the storages 4 a to 6 a of the respective refrigeration showcases 4 to 6, while a refrigerant pipe connected to the refrigeration evaporator 221. Refrigerant temperature sensors 229a, 229b, and 229c are provided at the inlet portion, the outlet portion, and the intermediate portion, respectively. The inlet part refrigerant temperature sensor 229a and the outlet part refrigerant temperature sensor 229b detect the temperature of the refrigerant passing through the respective refrigerant pipes. The intermediate part refrigerant temperature sensor 229c detects the temperature of the refrigerant passing through a part close to the outlet part inside the refrigeration evaporator 221.

  The booster unit 23 is disposed downstream of the refrigeration evaporator group 220 and upstream of the junction P. More specifically, the booster unit 23 includes a plurality (four in the illustrated refrigerant) of booster compressors 231 and booster solenoid valves 232, and these booster compressors 231 together with the booster solenoid valves 232. These are arranged in parallel and connected to the refrigeration evaporator group 220 through the refrigerant pipe.

  The booster compressor 231 sucks and compresses the refrigerant evaporated in the refrigeration evaporator 221. As a result, the refrigerant pressure in the refrigeration evaporator 221 decreases, and as a result, the refrigerant evaporation temperature in the refrigeration evaporator 221 decreases.

  Each booster solenoid valve 232 is disposed upstream of the booster compressor 231. These booster solenoid valves 232 are turned on / off by receiving a command from the control unit 400, that is, are opened or closed to cut off or allow the supply of refrigerant from the refrigeration evaporator 221 to the corresponding booster compressor 231. To do.

  The booster introduction path 24 branches from the refrigerant line downstream of the refrigeration evaporator group 210 and joins the refrigerant line downstream of the refrigeration evaporator group 220 and upstream of the booster unit 23. It is a path constituted by piping. That is, the booster introduction path 24 is a path for introducing the refrigerant that has passed through the refrigeration evaporator group 210 into the booster unit 23.

  The booster introduction valve 25 is disposed in the booster introduction path 24 and opens and closes in response to a command given from the control unit 400. When the booster introduction valve 25 is in the open state, the refrigerant that has passed through the refrigeration evaporator group 210. That is, while the refrigerant evaporated in the refrigeration evaporator 211 is allowed to pass through the booster introduction path 24, the refrigerant that has passed through the refrigeration evaporator group 210, that is, the refrigeration evaporator, is in a closed state. The refrigerant evaporated in 211 is restricted from passing through the booster introduction path 24.

  The return valve 26 is disposed at a predetermined location in the refrigerant pipeline from the branching point to the booster introduction path 24 to the junction P, and opens and closes in response to a command given from the control unit 400 so that the open state is established. In this case, the refrigerant that has passed through the refrigeration evaporator group 210, that is, the refrigerant that has evaporated in the refrigeration evaporator 211 is allowed to pass, while in the closed state, the refrigerant passes through the refrigeration evaporator group 210. The passage of the refrigerated refrigerant, that is, the refrigerant evaporated by the refrigeration evaporator 211 is regulated.

  The control unit 400 comprehensively controls the operation of the cooling system, and includes a compression control unit 410 and a booster control unit 420 as shown in FIG.

  The compression control unit 410 includes a setting storage unit 4101, a communication processing unit 4102, a first temperature difference measurement unit 4103, a second temperature difference measurement unit 4104, a state determination unit 4105, a compressor drive processing unit 4106, A valve drive processing unit 4107 and a temperature comparison unit 4108 are provided.

  The setting storage unit 4101 is for setting and storing a program and data necessary for the compression control unit 410 to perform control, and particularly in the second embodiment, the upper limit value of the target refrigerator internal temperature and The lower limit value, the upper limit value and lower limit value of the reference superheat degree, and the upper limit value and lower limit value of the reference suction room temperature are set and stored. The communication processing unit 4102 is for performing various information communication processing with the booster control unit 420.

  The first temperature difference measuring unit 4103 calculates a first refrigerant temperature difference obtained by subtracting the refrigerant temperature detected by the inlet refrigerant temperature sensor 219a from the refrigerant temperature detected by the intermediate refrigerant temperature sensor 219c. The second temperature difference measuring unit 4104 calculates a second refrigerant temperature difference obtained by subtracting the refrigerant temperature detected by the intermediate refrigerant temperature sensor 219c from the refrigerant temperature detected by the outlet refrigerant temperature sensor 219b. Here, the first refrigerant temperature difference may be a value obtained by subtracting the refrigerant temperature detected by the inlet refrigerant temperature sensor 219a from the refrigerant temperature detected by the outlet refrigerant temperature sensor 219b.

  The state determination unit 4105 includes a first refrigerant temperature difference calculated by the first temperature difference measurement unit 4103, a second refrigerant temperature difference calculated by the second temperature difference measurement unit 4104, and a reference stored in the setting storage unit 4101. By comparing the upper limit value and the lower limit value of the superheat degree, it is determined whether or not the evaporation completion point of the refrigerant in the refrigeration evaporator 211 is in the vicinity of the intermediate portion, and the refrigerant discharged from the refrigeration evaporator 211 is the gas-liquid 2. It is determined whether or not a phase state exists, that is, whether or not a so-called liquid back phenomenon has occurred.

  If the state determination unit 4105 determines that the refrigerant evaporation completion point in the refrigeration evaporator 211 is in the vicinity of the intermediate portion, the state determination unit 4105 determines that the refrigeration capability in the refrigeration evaporator 211 is excessive. On the other hand, when it is determined that the refrigerant discharged from the refrigeration evaporator 211 is in a gas-liquid two-phase state, it is determined that the refrigeration capability of the refrigeration evaporator 211 is insufficient.

  The compressor drive processing unit 4106 gives a command to the compressor 11 to drive and stop the compressor 11 or increase / decrease the operating rotational speed of the compressor 11.

  The valve drive processing unit 4107 gives a command to each of the booster introduction valve 25 and the feedback valve 26, and when opening the booster introduction valve 25, closes the feedback valve 26 and closes the booster introduction valve 25. In this case, the feedback valve 26 is opened. In the normal state, the valve drive processing unit 4107 closes the booster introduction valve 25 and opens the feedback valve 26.

  The temperature comparison unit 4108 compares the temperature detected by each sensor with the upper limit value or lower limit value of the temperature stored in the setting storage unit 4101.

  The booster control unit 420 includes a setting storage unit 4201, a communication processing unit 4202, a first temperature difference measurement unit 4203, a second temperature difference measurement unit 4204, a state determination unit (determination means) 4205, and a booster solenoid valve drive. A processing unit 4206 and a booster compressor drive processing unit 4207 are provided.

  The setting storage unit 4201 is for setting and storing programs and data necessary for the booster control unit 420 to perform control, and particularly in the second embodiment, the upper limit value of the target freezer temperature and The lower limit value, the upper limit value and the lower limit value of the reference superheat degree are stored. The communication processing unit 4202 is for performing various information communication processing with the compression control unit 410.

  The first temperature difference measuring unit 4203 calculates a first refrigerant temperature difference obtained by subtracting the refrigerant temperature detected by the inlet refrigerant temperature sensor 229a from the refrigerant temperature detected by the intermediate refrigerant temperature sensor 229c. The second temperature difference measuring unit 4204 calculates a second refrigerant temperature difference obtained by subtracting the refrigerant temperature detected by the intermediate refrigerant temperature sensor 229c from the refrigerant temperature detected by the outlet refrigerant temperature sensor 229b. Here, the first refrigerant temperature difference may be a value obtained by subtracting the refrigerant temperature detected by the inlet refrigerant temperature sensor 229a from the refrigerant temperature detected by the outlet refrigerant temperature sensor 229b.

  The state determination unit 4205 includes the first refrigerant temperature difference calculated by the first temperature difference measurement unit 4203, the second refrigerant temperature difference calculated by the second temperature difference measurement unit 4204, and a reference stored in the setting storage unit 4201. By comparing the upper limit value and the lower limit value of the superheat degree, it is determined whether or not the evaporation completion point of the refrigerant in the refrigeration evaporator 221 is in the vicinity of the intermediate portion, and the refrigerant discharged from the refrigeration evaporator 221 is gas-liquid 2. It is determined whether or not a phase state exists, that is, whether or not a so-called liquid back phenomenon has occurred.

  Here, when the state determination unit 4205 determines that the refrigerant evaporation completion point in the refrigerating evaporator 221 is near the intermediate portion, it determines that the refrigerating capacity in the refrigerating evaporator 221 is excessive. On the other hand, when it is determined that the refrigerant discharged from the refrigerating evaporator 221 is in a gas-liquid two-phase state, it is determined that the refrigerating capacity of the refrigerating evaporator 221 is insufficient.

  The booster solenoid valve drive processing unit 4206 gives an on / off control, that is, opens or closes, by giving a command to each booster solenoid valve 232.

  The booster compressor drive processing unit 4207 gives a command to each booster compressor 231 to drive the booster compressor 231 or increase / decrease the operating rotational speed of each booster compressor 231.

  In the cooling system as described above, the high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 11 constituting the refrigerator 10 is condensed in the condenser 12 to become a high-temperature and high-pressure liquid refrigerant. This high-temperature and high-pressure liquid refrigerant branches in the middle, and one is discharged to the showcase cooling unit 200 and the other is discharged to the air conditioning unit 30. The liquid refrigerant discharged to the showcase cooling unit 200 branches in the middle, and one is discharged to the refrigeration evaporator group 210 and the other is discharged to the refrigeration evaporator group 220.

  The liquid refrigerant discharged to the refrigeration evaporator group 210 is branched and supplied to the refrigeration electronic expansion valve 213a, is adiabatically expanded, and is supplied to the refrigeration evaporator 211 as a low-temperature low-pressure gas-liquid two-phase refrigerant. The low-temperature and low-pressure gas-liquid two-phase refrigerant supplied to the refrigeration evaporator 211 exchanges heat with the air in the storage compartments 1a to 3a of the refrigeration showcases 1 to 3 supplied by the blower fan 216 through the suction port 217. Then, the internal air cooled by evaporating to become a low-temperature and low-pressure gas refrigerant is blown out from the outlet 218 to the storages 1a to 3a, whereby the storages 1a to 3a are cooled. The low-temperature and low-pressure gas refrigerant that has passed through the refrigeration evaporator 211 is sucked into the compressor 11 and then merges and passes through the feedback valve 26 that is discharged from the refrigeration evaporator group 210 and is in an open state. To the confluence P.

  The liquid refrigerant discharged to the refrigeration evaporator group 220 is branched and supplied to the refrigeration electronic expansion valve 223a, adiabatically expanded to become a low-temperature low-pressure gas-liquid two-phase refrigerant, and supplied to the refrigeration evaporator 221. . The low-temperature and low-pressure gas-liquid two-phase refrigerant supplied to the refrigeration evaporator 221 exchanges heat with the air in the storages 4a to 6a of the refrigeration showcases 4 to 6 supplied by the blower fan 226 through the suction port 227. Then, it evaporates and becomes a low-temperature and low-pressure gas refrigerant, thereby cooling the internal air. The cooled internal air is blown out from the outlet 228 to the storage boxes 4a to 6a, whereby the storage boxes 4a to 6a are cooled.

  Here, the refrigerant in the refrigeration evaporator 221 acts not only with the suction force by the compressor 11 but also with the suction force by the booster compressor 231 constituting the booster unit 23, so that the pressure in the refrigeration evaporator 211 is increased. It is lower than the refrigerant pressure.

  Therefore, the evaporating temperature of the refrigerant in the freezing evaporator 221 is lower than the evaporating temperature of the refrigerant in the refrigeration evaporator 211, so that the storage boxes 4 a to 6 a of the freezing showcases 4 to 6 are stored in the refrigeration show. It becomes lower than the storage 1a-3a of cases 1-3.

  The low-temperature and low-pressure gas refrigerant that has passed through the refrigeration evaporator 221 is sucked into the booster compressor 231 and the compressor 11, and then merges, discharged from the refrigeration evaporator group 220, and discharged to the booster unit 23. The

  The refrigerant discharged to the booster unit 23 is branched and supplied to the booster compressor 231 via the booster solenoid valve 232, and is compressed by the booster compressor 231, and the suction force of the compressor 11 acts and joins the booster unit. 23 is discharged to reach the confluence P.

  The refrigerant discharged from the refrigeration evaporator group 210 and the refrigerant discharged from the booster unit 23 through the refrigeration evaporator group 220 merge at the junction P and are sucked into the compressor 11.

  The liquid refrigerant discharged to the air conditioning unit 30 is supplied to the air conditioning expansion valve 31, is adiabatically expanded, becomes a low-temperature low-pressure gas-liquid two-phase refrigerant, and is supplied to the air-conditioning evaporator 32. The low-temperature and low-pressure gas-liquid two-phase refrigerant supplied to the air-conditioning evaporator 32 exchanges heat with the room air supplied by the air-conditioning fan 33 and evaporates to become a low-temperature and low-pressure gas refrigerant, thereby cooling the chamber 4. . The low-temperature and low-pressure gas refrigerant that has passed through the air conditioning evaporator 32 is sucked into the compressor 11.

  And the control unit 400 which comprises such a cooling system performs each control process as shown below.

  FIGS. 15 to 19 are flowcharts showing the contents of processing performed individually by the control unit. FIG. 15 shows load determination processing for the refrigeration evaporator, FIG. 16 shows load determination processing for the refrigeration evaporator, and FIG. Is a booster unit control process (2), FIG. 18 is a compressor drive control process (3), and FIG. 19 is a valve switching control process. Hereinafter, the operation of the cooling system will be described with reference to these drawings. The control unit 400 performs the compressor drive control process (2) described in the first embodiment, but since this process is the same as that in the first embodiment, the description of the process is omitted. .

  In the load determination process of the refrigeration evaporator 211 in FIG. 15, the compression control unit 410 detects the respective refrigerant temperatures through the inlet refrigerant temperature sensor 219a, the outlet refrigerant temperature sensor 219b, and the intermediate refrigerant temperature sensor 219c (step S201). ), The first refrigerant temperature difference and the second refrigerant temperature difference are respectively calculated through the first temperature difference measuring unit 4103 and the second temperature difference measuring unit 4104 (step S202).

  The compression control unit 410, which has calculated the first refrigerant temperature difference and the second refrigerant temperature difference through the first temperature difference measurement unit 4103 and the second temperature difference measurement unit 4104, respectively, has both the first refrigerant temperature difference and the second refrigerant temperature difference. It is determined whether or not the value is less than the reference superheat degree lower limit value stored in the setting storage unit 4101 (step S203).

  When both the first refrigerant temperature difference and the second refrigerant temperature difference are less than the reference superheat degree lower limit value (step S203: Yes), the compression control unit 410 discharges refrigerant from the refrigeration evaporator 211 through the state determination unit 4105. Is in a gas-liquid two-phase state, that is, a liquid back phenomenon has occurred, it is determined that the refrigeration evaporator 211 has insufficient refrigeration capacity (step S204), and the procedure returns to the current process. Exit.

  When both the first refrigerant temperature difference and the second refrigerant temperature difference are equal to or greater than the reference superheat degree lower limit value and both exceed the reference superheat degree upper limit value (step S203: No, step S205: Yes), the compression control unit 410 Determines that the refrigerant evaporation completion point in the refrigeration evaporator 211 is in the vicinity of the intermediate portion through the state determination unit 4105, and determines that the refrigeration capacity in the refrigeration evaporator 211 is excessive (step S206). Return the procedure and end the current process.

  On the other hand, when the first refrigerant temperature difference and the second refrigerant temperature difference are both greater than or equal to the reference superheat degree lower limit value and less than the reference superheat degree upper limit value, or at least one of the first refrigerant temperature difference and the second refrigerant temperature difference. Is between the lower limit value and the upper limit value of the reference superheat degree (step S203: No, step S205: No), the compression control unit 410 has an appropriate refrigeration capacity of the refrigeration evaporator 211 through the state determination unit 4105. Is determined (step S207), the procedure is returned, and the current process is terminated.

  In the load determination process of the refrigeration evaporator 221 in FIG. 16, the booster control unit 420 detects the respective refrigerant temperatures through the inlet refrigerant temperature sensor 229a, the outlet refrigerant temperature sensor 229b, and the intermediate refrigerant temperature sensor 229c (step S211). ), The first refrigerant temperature difference and the second refrigerant temperature difference are respectively calculated through the first temperature difference measuring unit 4203 and the second temperature difference measuring unit 4204 (step S212).

  When the first refrigerant temperature difference and the second refrigerant temperature difference are respectively calculated through the first temperature difference measurement unit 4203 and the second temperature difference measurement unit 4204, the booster control unit 420 determines the first refrigerant temperature difference and the second refrigerant temperature difference. Are both less than the reference lower limit value stored in the setting storage unit 4201 (step S213).

  When both the first refrigerant temperature difference and the second refrigerant temperature difference are less than the reference superheat degree lower limit (step S213: Yes), the booster control unit 420 discharges refrigerant from the refrigeration evaporator 221 through the state determination unit 4205. Is in a gas-liquid two-phase state, that is, a liquid back phenomenon has occurred, it is determined that the refrigerating capacity of the refrigerating evaporator 221 is insufficient (step S214), the procedure is returned, and the current process is performed. Exit.

  When both the first refrigerant temperature difference and the second refrigerant temperature difference are greater than or equal to the reference superheat degree lower limit value and both exceed the reference superheat degree upper limit value (step S213: No, step S215: Yes), the booster control unit 420 Determines that the refrigerant evaporation completion point in the refrigeration evaporator 221 is in the vicinity of the intermediate portion through the state determination unit 4205, and determines that the refrigeration capacity in the refrigeration evaporator 221 is excessive (step S216). Return the procedure and end the current process.

  On the other hand, when the first refrigerant temperature difference and the second refrigerant temperature difference are both greater than or equal to the reference superheat degree lower limit value and less than the reference superheat degree upper limit value, or at least one of the first refrigerant temperature difference and the second refrigerant temperature difference. Is between the lower limit value and the upper limit value of the reference superheat degree (step S213: No, step S215: No), the booster control unit 420 has an appropriate refrigeration capacity of the refrigeration evaporator 221 through the state determination unit 4205. (Step S217), the procedure is returned, and the current process is terminated.

  In the booster unit control process (2) shown in FIG. 17, the booster control unit 420 has one or more refrigeration evaporators 221 that are determined to have insufficient refrigeration capacity as a result of the load determination process of the refrigeration evaporator 221 described above ( Step S221: Yes), it is determined whether or not the number of booster compressors 231 can be increased through the booster compressor drive processing unit 4207 (Step S222).

  As a result, when the number of operating units can be increased (step S222: Yes), the booster control unit 420 performs on-control (open operation) of the corresponding booster solenoid valve 232 through the booster solenoid valve drive processing unit 4206, and booster compression. The corresponding booster compressor 231 is driven through the machine drive processing unit 4207 (step S223, step S224), and then the procedure is returned to end the current process.

  According to this, the suction force of the refrigerant by the booster unit 23 is increased, the refrigerant pressure of the refrigeration evaporator 221 constituting the refrigeration evaporator group 220 is decreased, and the refrigerant evaporation temperature in the refrigeration evaporator 221 is reduced. Can be reduced.

  When the evaporating temperature of the refrigerant is thus lowered, the storage cases 4a to 6a of the freezing showcases 4 to 6 are cooled. As a result, the freezer temperature can be shifted to a desired temperature range.

  In step S222, when the number of operating booster compressors 231 cannot be increased (step S222: No), the booster control unit 420 sets the operating rotational speed of the corresponding booster compressor 231 through the booster compressor drive processing unit 4207. The number is increased (step S225), and then the procedure is returned to end the current process.

  As a result, the low pressure setting value of the booster compressor 231 that has increased the operating rotational speed is decreased, and the refrigerant pressure of the refrigeration evaporator 221 that constitutes the refrigeration evaporator group 220 is decreased, thereby It becomes possible to reduce the evaporation temperature of the refrigerant in the evaporator 221.

  When the evaporating temperature of the refrigerant is thus lowered, the storage cases 4a to 6a of the freezing showcases 4 to 6 are cooled. As a result, the freezer temperature can be shifted to a desired temperature range.

  As a result of the load determination processing of the refrigeration evaporator 221 described above, there is no refrigeration evaporator 221 that is determined to be insufficient in refrigeration capacity, but there are one or more refrigeration evaporators 221 that are determined to be excessive in refrigeration capacity (step) S221: No, step S226: Yes), the booster control unit 420 determines whether or not the number of operating booster compressors 231 can be reduced through the booster compressor drive processing unit 4207 (step S227).

  As a result, when the number of operating units can be reduced (step S227: Yes), the booster control unit 420 controls to turn off the corresponding booster solenoid valve 232 through the booster solenoid valve drive processing unit 4206 (step S228), and then performs the procedure. To end the current process.

  As a result, the refrigerant does not flow to the booster compressor 231 on the downstream side of the booster solenoid valve 232 that is off-controlled, and the booster compressor 231 is automatically stopped. By reducing the number of booster compressors 231 operated, the suction power of the refrigerant by the booster unit 23 is reduced, whereby the refrigerant pressure of the refrigeration evaporator 221 constituting the refrigeration evaporator group 220 is increased, and It becomes possible to raise the evaporation temperature of the refrigerant in the evaporator 221.

  When the evaporating temperature of the refrigerant is thus increased, the cooling of the storage cases 4a to 6a of the refrigeration showcases 4 to 6 is eased, so that the freezer temperature can be shifted to a desired temperature range.

  When it is not possible to reduce the number of booster compressors 231 operated in step S227 (step S227: No), the booster control unit 420 reduces the operating rotational speed of the corresponding booster compressor 231 through the booster compressor drive processing unit 4207. (Step S229), and then the procedure is returned to end the current process.

  As a result, the low pressure setting value of the booster compressor 231 whose operating rotational speed has been reduced is increased, and the refrigerant pressure of the refrigeration evaporator 221 constituting the refrigeration evaporator group 220 is increased. It becomes possible to raise the evaporation temperature of the refrigerant in the evaporator 221.

  When the evaporating temperature of the refrigerant is thus increased, the cooling of the storage cases 4a to 6a of the refrigeration showcases 4 to 6 is eased, so that the freezer temperature can be shifted to a desired temperature range.

  As a result of the load determination process of the refrigeration evaporator 221 described above, when there is no refrigeration evaporator 221 that is determined to be insufficient in refrigeration capacity and no refrigeration evaporator 221 that is determined to be excessive in refrigeration capacity (step S221: No, step S226: No), the booster control unit 420 maintains the states of the booster solenoid valve 232 and the booster compressor 231, and then returns the procedure to end the current process.

  In the compressor drive control process (3) shown in FIG. 18, the compression control unit 410 (control unit 400) inputs the determination result of the state determination unit 4205 from the booster control unit 420 through the communication processing unit 4102, and the above-described refrigeration evaporation As a result of the load determination process of the refrigerator 221, there is one or more refrigeration evaporators 221 determined to be insufficient in refrigeration capacity, and as a result of the load determination process of the refrigeration evaporator 211 described above, it is determined that the refrigeration capacity is insufficient When there is one or more evaporators 211 (step S231: Yes), the operation speed of the compressor 11 is increased through the compressor drive processing unit 4106 (step S232), and then the procedure is returned to end the current process. To do.

  As a result, the low pressure setting value of the compressor 11 is lowered, the refrigerant pressure of each evaporator is lowered, and the evaporation temperature of the refrigerant in these evaporators can be lowered.

  When the evaporation temperature of the refrigerant is thus reduced, the storage cases 1a to 6a of the respective showcases 1 to 6 are cooled, so that the internal temperature of the storage cases 1a to 6a can be changed to a desired temperature range. It becomes possible.

  As a result of the load determination process of the refrigeration evaporator 221, there is no refrigeration evaporator 221 that has been determined to be insufficient in refrigeration capacity, but there are one or more refrigeration evaporators 221 that have been determined to have excessive refrigeration capacity, and As a result of the load determination process of the refrigeration evaporator 211, there is no refrigeration evaporator 211 that is determined to be insufficient in refrigeration capacity, but there are one or more refrigeration evaporators 211 that are determined to have excessive refrigeration capacity (step S231: No, step S233: Yes), the compression control unit 410 reduces the operating rotational speed of the compressor 11 through the compressor drive processing unit 4106 (step S234), and then returns the procedure to end the current process.

  As a result, the low pressure setting value of the compressor 11 is increased, the refrigerant pressure of each evaporator is increased, and the evaporation temperature of the refrigerant in each evaporator can be increased.

  When the evaporating temperature of the refrigerant is thus increased, the cooling of the storage containers 1a to 6a of the showcases 1 to 6 is alleviated, and as a result, the internal temperature of the storage containers 1a to 6a is changed to a desired temperature range. Is possible.

  As a result of the load determination process of the refrigeration evaporator 221, there is no refrigeration evaporator 221 that is determined to be insufficient in refrigeration capacity and excessive in refrigeration capacity, and as a result of the load determination process of the refrigeration evaporator 211, the refrigeration capacity is insufficient. And when there is no refrigeration evaporator 211 judged that the refrigeration capacity is excessive (step S231: No, step S233: No), the compression control unit 410 maintains the operation state of the compressor 11 and returns the procedure. This process is terminated.

  Such a compressor drive control process (3) is performed in parallel with the compressor drive control process (2) described in the first embodiment, but the refrigerated showcases 1 to 3 and the freezer showcase 4 to Since the goods are displayed in each of the storage bins 1a to 6a, the cooling system according to the second embodiment is such that the compressor drive control process (3) is more than the compressor drive control process (2). It has been given priority.

  When the operation speed of the compressor 11 reaches the maximum value in the compressor drive control process (3) and the compressor drive control process (2), the control unit 400 performs the following valve switching. Perform control processing. As a premise of such valve switching control processing, it is assumed that the booster introduction valve 25 is closed and the feedback valve 26 is opened.

  In the valve switching control process shown in FIG. 19, the compression control unit 410 (control unit 400) determines whether or not the operating rotational speed of the compressor 11 is the maximum value through the compressor drive processing unit 4106 (step S241). When the operation rotational speed is the maximum value (step S241: Yes), the compression control unit 410 detects the temperature in the refrigerator of the storage boxes 1a to 3a in the refrigeration showcases 1 to 3 through the refrigerator temperature sensor 215. (Step S242), it is determined whether or not the refrigerator temperature detected through the temperature comparison unit 4108 exceeds the upper limit value of the target refrigerator temperature stored in the setting storage unit 4201 (Step S243).

  In any of the refrigerated showcases 1 to 3, when the refrigerator internal temperature (the internal temperature of the storage 1a to 3a) exceeds the target refrigerator internal temperature upper limit (step S243: Yes), the compression control unit 410 includes a valve The booster introduction valve 25 is turned on (opened) through the drive processing unit 4107 (step S244), and the feedback valve 26 is turned off (closed) (step S245).

  As a result, the refrigerant that has passed through the refrigeration evaporator group 210, that is, the refrigerant that has evaporated in the refrigeration evaporator 211, passes through the booster introduction path 24 and is discharged to the booster unit 23. That is, the refrigerant pressure of the refrigeration evaporator 211 is reduced by being sucked by the booster compressor 231, and the evaporation temperature of the refrigerant in the refrigeration evaporator 211 can be lowered.

  When the evaporation temperature of the refrigerant is thus lowered, the storages 1a to 3a of the refrigerated showcases 1 to 3 are further cooled. As a result, the refrigerator temperature can be changed to a desired temperature range.

  In any of the refrigerated showcases 1 to 3, if the refrigerator temperature is equal to or lower than the target refrigerator temperature upper limit (step S243: No), the compression control unit 410 maintains the state of the booster introduction valve 25 and the feedback valve 26. Then, the procedure is returned to end the current process.

  According to the cooling system of the second embodiment of the present invention as described above, the booster control unit 420 (control unit 400) uses the gas-liquid two-phase refrigerant discharged from the freezing evaporator 221 by the state determination unit 4205. When there is one or more determined to be in a state, at least one of the number of operating boosters 231 and the number of operating revolutions is reduced, so it is not necessary to operate all the booster compressors 231 at all times. . Moreover, since the refrigeration evaporator 221 and the booster compressor 231 are in a plural-to-multiple relationship, each refrigeration evaporator can be adjusted by increasing / decreasing not only the operating speed of the booster compressor 231 but also the operating number. The evaporation temperature of the refrigerant 221 can be controlled, and the cooling in each refrigeration evaporator 221 can be finely adjusted. Therefore, it is possible to satisfactorily bring the containers 1a to 6a to a desired temperature state while obtaining sufficiently high operation efficiency.

  According to the cooling system, the compression control unit 410 judges the load on each evaporator and increases or decreases the number of operations of the compressor 11 in parallel with the booster unit control process (2) by the booster control unit 420 ( Compressor drive control process (3)) and operational efficiency can be improved, and thereby energy saving of the operation of the entire system can be achieved.

  Further, according to the cooling system of the second embodiment, the compression control unit 410 performs the suction temperature sensor 36 in parallel with the compressor drive control process (3) and the booster unit control process (2) by the booster control unit 420. Since the load of the air conditioner evaporator 32 is judged from the deviation between the suction room temperature detected by the above and the reference suction room temperature, and the operation speed of the compressor 11 is increased or decreased, the operation efficiency can be improved. Energy saving of the entire operation can be achieved.

  Furthermore, according to the cooling system of the second embodiment, the compression controller 410 determines that the refrigerator internal temperature detected by the refrigerator internal temperature sensor 215 is the target refrigerator internal temperature when the operation rotational speed of the compressor 11 is the maximum value. When the upper limit is exceeded, the booster introduction valve 25 is turned on and the feedback valve 26 is turned off, so that the booster compressor 231 is shared between the refrigerated evaporator group and the refrigerated evaporator group. In addition, the storage temperatures 1a to 3a of the refrigerated showcases 1 to 3 can be satisfactorily cooled by lowering the evaporation temperature of the refrigerant in the refrigeration evaporator 211.

  Furthermore, according to the cooling system of the second embodiment, since the cold storage tanks 212 and 222 store cold heat, the blower fan 216 uses the cold heat stored in the cold storage tanks 212 and 222 as necessary. , 226 can be cooled, so that the operating loads of the compressor 11 and the booster compressor 231 can be leveled to save energy.

  As mentioned above, although Embodiment 2 of this invention was demonstrated, this invention is not limited to this, A various change can be performed. For example, in Embodiment 2 described above, the suction room temperature detected by the suction temperature sensor 36 when the load of the air conditioning evaporator 32 is determined is used. However, in the present invention, the load of the air conditioning evaporator 32 is determined. As long as it can be used, it is not necessary to limit to the suction room temperature, the temperature of the room air blown out from the blowout port (blowout room air temperature) may be used, and the value obtained by subtracting the blowout room temperature from the suction room temperature May be used.

  Moreover, in Embodiment 2 mentioned above, in booster unit control process (2), it implements centering on control of the number of operation | movement of the booster compressor 231, and when increase / decrease in the number of operation is impossible, the booster compressor 231 of Although control for increasing / decreasing the operating rotational speed has been performed, in the present invention, it is not always necessary to focus on controlling the number of operating booster compressors 231. I do not care.

<Embodiment 3>
FIG. 20 is a schematic diagram schematically showing a cooling system according to the third embodiment of the present invention. In addition, the same code | symbol is attached | subjected to what has the same structure as the cooling system of Embodiment 1 mentioned above, and the description is abbreviate | omitted suitably. The cooling system illustrated here includes a refrigerator 10, a showcase cooling unit 201, an air conditioning unit 30, and a control unit 40.

  FIG. 21 is a schematic diagram schematically showing the main part of the showcase cooling unit 201 shown in FIG. 20, showing the characteristic parts of the third embodiment, and omitting the other parts explicitly. is doing.

  As shown in FIG. 21, the showcase cooling unit 201 is similar to the showcase cooling unit 20 that constitutes the cooling system of the first embodiment described above, for example, a plurality of showcases 1 installed at predetermined locations in the room. -6 of storage containers 1a-6a in a desired temperature state, evaporator group 210a for refrigeration, evaporator group 220a for freezing, booster unit 23, booster introduction path 24, booster introduction valve 25 and a feedback valve 26.

  And in the showcase cooling unit 201 in this Embodiment 3, the structure of the refrigerating evaporator 211 which comprises the refrigerating evaporator group 210a and the refrigerating evaporator 221 which comprises the refrigerating evaporator group 220a is implemented. Different from the showcase cooling unit 201 in the first embodiment.

  That is, each of the evaporators 211 and 221 has a common standardized size, and each showcase is configured in such a manner that the number of arrangements increases in accordance with the size of the cooling load of the containers 1a to 6a. The number provided in 1-6 is decided. If it demonstrates in detail, each evaporator 211,221 will be the magnitude | size which can cool the storage 1a with the smallest cooling load enough and necessary.

  And as shown in FIG. 21, one refrigerator 211 for refrigeration is arrange | positioned in the showcases 1-3 for refrigeration with the comparatively small cooling load of storage 1a-3a, and storage 4a-6a of storages 4a-6a. In the refrigeration showcases 4 to 6 having a relatively large cooling load, two refrigeration evaporators 221 are arranged in parallel or in series.

  Further, in the refrigeration showcases 4 to 6, an inflow side electromagnetic valve 221 a and a discharge side electromagnetic valve 221 b are provided in the refrigerant pipes connected to one inlet and outlet constituting the refrigeration evaporator 221, respectively. is there.

  When the inflow side solenoid valve 221a and the discharge side solenoid valve 221b are controlled to be turned on / off by, for example, a command from the control unit 40 and opened together, the refrigerant is allowed to pass through the corresponding evaporator. On the other hand, when both are closed, the passage of the refrigerant to the corresponding evaporator is restricted.

  Although not shown in the figure, when a plurality of refrigeration evaporators (221) are arranged in series, the inflow side solenoid valve (221a) and the discharge side solenoid valve (221b) It is not necessary to provide in the evaporator (221), and it may be provided on the inflow side and the discharge side of the refrigeration evaporator group 220a.

  The cooling system according to the third embodiment provided with such a showcase cooling unit 201 has the following effects in addition to the effects exhibited by the cooling system according to the first embodiment described above.

  In other words, the plurality of evaporators 211 and 221 each have a standardized common size, and the respective showcases are arranged in such a manner that the number of arrangements increases according to the size of the cooling load of the containers 1a to 6a. Since the number provided in 1-6 is decided, it is not necessary to design the magnitude | size of an evaporator according to the magnitude | size of the cooling load of storage 1a-6a. Therefore, the manufacturing cost can be reduced by mass production of the evaporator.

  According to the above cooling system, the size of each evaporator is sized so that the container 1a with the smallest cooling load can be sufficiently cooled, so that the heat exchange area of each evaporator can be increased well. As a result, efficient operation is possible, resulting in energy saving.

<Embodiment 4>
FIG. 22 is a schematic diagram schematically showing a cooling system according to the fourth embodiment of the present invention. In addition, the same code | symbol is attached | subjected to what has the same structure as the cooling system in Embodiment 1 mentioned above, and the description is abbreviate | omitted suitably.

  The cooling system illustrated here includes the refrigerator 10, the showcase cooling unit 20, the air conditioning unit 300, and the control unit 401.

  The air conditioning unit 300 is for bringing the inside of the chamber 4 in which the showcases 1 to 6 to be cooled by the showcase cooling unit 20 are installed into a desired temperature state. As shown in FIG. The air-conditioning expansion valve 31, the air-conditioning evaporator 32, the air-conditioning fan 33, the suction temperature sensor 36 and the louver 37 are arranged.

  The louver 37 is disposed in the vicinity of the air outlet 35 so that it can be opened and closed. The louver 37 is cooled by the air-conditioning evaporator 32 and adjusts the direction of the air that is blown out into the chamber 4 through the air outlet 35. Means.

  Although only one air conditioning unit 300 is explicitly shown in FIG. 23, a plurality of air conditioning units 300 may be provided in the present invention. Further, the illustrated air conditioning unit 300 will be described assuming that the refrigeration showcase 2 in the middle of the three refrigeration showcases 1 to 3 clearly shown in the figure is applied.

  In the refrigerated showcases 1 to 3, an outlet temperature sensor 219 a and an inlet temperature sensor 219 b are provided in addition to the refrigerator temperature sensor 215.

  The blower outlet temperature sensor 219a detects the temperature of the air in the cabinet blown out through the blower outlet 218 by the action of the blower fan 216, and the suction inlet temperature sensor 219b is sucked in through the suction inlet 217 by the action of the blower fan 216. This is to detect the temperature of the inside air.

  The control unit 401 comprehensively controls the operation of the cooling system, and includes a compression control unit 41, a booster control unit 42, and a blowing direction control unit 43, as shown in FIG. is there. The blowing direction control unit 43 includes a setting storage unit 431, a communication processing unit 432, a determination unit 433, and a louver drive processing unit 434.

  The setting storage unit 431 is for setting and storing programs and data necessary for the blow-out direction control unit 43 to perform control. In particular, in the fourth embodiment, each reference temperature (inside the reference chamber) Temperature, reference outlet temperature, reference inlet temperature) values are set and stored.

  Here, each reference temperature is obtained experimentally, and is obtained by adding a predetermined temperature (for example, 2 ° C. or 3 ° C.) to each temperature in a stable state when a predetermined time has elapsed after completion of the defrosting operation. It is. As is well known, the refrigerated showcase 2 repeatedly performs a defrosting operation, a pull-down operation, and a normal operation every set time.

  The communication processing unit 432 is for performing various information communication processes separately between the compression control unit 41 and the booster control unit 42.

  The determination unit 433 is blown out through the outlet 218 to the target refrigeration showcase 2 based on the temperatures detected by the refrigerator temperature sensor 215, the outlet temperature sensor 219a, and the inlet temperature sensor 219b. It is determined whether or not there is a turbulence in the air in the cabinet, that is, the air curtain.

  The louver drive processing unit 434 opens or closes the louver 37 by giving a command to the louver 37.

  FIG. 25 is a flowchart showing the contents of the blowing direction control process performed by the control unit 401. Hereinafter, the operation of the cooling system will be described with reference to FIG.

  In the blowing direction control process, the blowing direction control unit 43 (control unit 401) inputs the outlet temperature and the inlet temperature detected from the outlet temperature sensor 219a and the inlet temperature sensor 219b, and through the communication processing unit 432. When the refrigerator internal temperature is input from the compression control unit 41 (step S401: Yes), through the determination unit 433, each temperature is compared with each reference temperature stored in the setting storage unit 431 (step S402), and correspondingly. It is determined whether there are two or more temperatures exceeding the reference temperature (step S403).

  When there are no two or more temperatures exceeding the reference temperature (step S403: No), the blowing direction control unit 43 returns the procedure and ends the current process without performing the process described later.

  In step S403, when there are two or more temperatures exceeding the reference temperature (step S403: Yes), the blowing direction control unit 43 determines whether or not it is temporary (step S404).

  Here, whether or not it is temporary can be determined based on the data related to the moving average of the temperature for the past several years, or by inputting each temperature from each sensor after a predetermined time (for example, after 5 minutes). This is done by judging whether each reference temperature is exceeded.

  As a result, if it is temporary (step S404: Yes), the blowing direction control unit 43 returns the procedure and ends the current process without performing the process described later.

  On the other hand, when it is not temporary (step S404: No), the blowing direction control unit 43 determines that the air curtain is disturbed in the refrigeration showcase 2, and the louver 37 is moved through the louver drive processing unit 434. It is confirmed whether or not it is already directed downward (step S405), and when it is directed downward (step S405: Yes), the louver 37 is closed through the louver drive processing unit 434 (step S406), and thereafter Return to the procedure to end the current process. By thus closing the louver 37, the air outlet 218 is closed.

  When the louver 37 is not facing downward (step S405: No), the blowing direction control unit 43 opens the louver 37 by a predetermined amount through the louver drive processing unit 434 (step S407), and then returns the procedure. Then, the current process ends. As a result, the indoor air cooled by the air conditioning evaporator 32 can be blown out to the target refrigerated showcase 2.

  As described above, the cooling system according to Embodiment 4 of the present invention has the following effects in addition to the effects exhibited by the cooling system according to Embodiment 1 described above. That is, since it is determined that the air curtain is disturbed when two or more of the three temperatures (internal temperature, outlet temperature, and inlet temperature) exceed the corresponding reference temperature, Air curtain disturbance can be detected with sufficiently high accuracy. Then, when it is determined that the air curtain is disturbed, the louver 37 is opened to blow the indoor air cooled by the air-conditioning evaporator 32 to the corresponding refrigeration showcase 2, thereby refrigeration showcase 2. The container 2a can be kept within a certain temperature range, and energy can be saved without using wasted power.

  In addition, when the corresponding refrigerated showcase 2 is in the defrosting operation, the blowing direction control unit 43 opens the louver 37 through the louver drive processing unit 434 regardless of the blowing direction control process described above. The room air cooled by the air conditioning evaporator 32 may be blown out toward the refrigerated showcase 2. According to this, it is possible to avoid a situation where the temperature of the storage case 2a of the refrigerated showcase 2 during the defrosting operation rises more than necessary, and it is possible to maintain the cooling ability of the product.

<Embodiment 5>
FIG. 26 is a schematic diagram schematically showing a cooling system according to the fifth embodiment of the present invention. In addition, the same code | symbol is attached | subjected to what has the same structure as the cooling system in Embodiment 1 mentioned above, and the description is abbreviate | omitted suitably. The cooling system illustrated here includes a refrigerator 10, a showcase cooling unit 20, an air conditioning unit 300, and a control unit 402.

  The air conditioning unit 300 is for bringing the inside of the chamber 4 in which the showcases 1 to 6 to be cooled by the showcase cooling unit 20 are installed into a desired temperature state. As shown in FIG. The air-conditioning expansion valve 31, the air-conditioning evaporator 32, the air-conditioning fan 33, the suction temperature sensor 36 and the louver 37 are arranged.

  The louver 37 is disposed in the vicinity of the air outlet 35 so that it can be opened and closed. The louver 37 is cooled by the air-conditioning evaporator 32 and adjusts the direction of the air that is blown out into the chamber 4 through the air outlet 35. Means.

  Although only one air conditioning unit 300 is explicitly shown in FIG. 27, a plurality of air conditioning units 300 may be provided in the present invention. Further, the illustrated air conditioning unit 300 will be described assuming that the refrigeration showcase 2 in the middle of the three refrigeration showcases 1 to 3 clearly shown in the figure is applied.

  In the refrigerated showcase 2, an inlet temperature sensor 219b is provided. The suction port temperature sensor 219b detects the temperature of the internal air sucked through the suction port 217 by the action of the blower fan 216.

  The control unit 402 comprehensively controls the operation of the cooling system, and includes a compression control unit 41, a booster control unit 42, and a blown air control unit 44, as shown in FIG. is there. The blown air control unit 44 includes a setting storage unit 441, a communication processing unit 442, a timer unit 443, a determination unit 444, a louver drive processing unit 445, and a fan drive processing unit 446.

  The setting storage unit 441 is for setting and storing programs and data necessary for the blown air control unit 44 to perform control, and particularly in the fifth embodiment, the value of the load reduction information is set. And remember.

  Here, the load reduction information has a table as shown in FIGS. FIG. 29 is obtained experimentally in advance, and defines a standard value of the suction port temperature (hereinafter also referred to as a standard suction port temperature) for each elapsed time from the end of the defrosting operation. FIG. 30 is also obtained experimentally, in which the blowout air temperature, blowout direction, and blowout air amount for each temperature difference between the suction port temperature detected through the suction port temperature sensor 219b and the standard suction port temperature are determined. It is.

  In addition, when the difference between the inlet temperature detected in FIG. 30 and the standard inlet temperature is 1 ° C., the blown air temperature, the blow direction, and the blown air amount are maintained as being within the allowable range. .

  From these two tables, the reference inlet temperature is defined in the load reduction information. That is, the standard suction port temperature is determined by adding the temperature difference of 2 ° C. or more shown in FIG. 30 to the standard suction port temperature. Thereby, the value of the reference inlet temperature varies depending on the elapsed time from the end of the defrosting operation.

  The communication processing unit 442 is for performing communication processing of various information separately between the compression control unit 41 and the booster control unit 42.

  The timer unit 443 measures time, and in the fifth embodiment, measures time from the end of the defrosting operation.

  The determination unit 444 compares the suction port temperature detected through the suction port temperature sensor 219b with the reference suction port temperature included in the load reduction information stored in the setting storage unit 441. The load is determined, and the blown air temperature, blown direction, and blown air amount are determined.

  The louver drive processing unit 445 opens or closes the louver 37 by giving a command to the louver 37.

  The fan drive processor 446 drives the air conditioning fan 33 by giving a command to the air conditioning fan 33.

  FIG. 31 is a flowchart showing the contents of the blown air control process performed by the control unit 402. Hereinafter, the operation of the cooling system will be described with reference to FIG.

  In the following, time measurement by the timer unit 443 will not be described, but it is assumed that time measurement is performed from the end of the defrosting operation of the showcase 2.

  In the blown air control process, the blown air control unit 44 (control unit 402) inputs a suction port temperature detected from the suction port temperature sensor 219b at a certain time measured by the timer unit 443 (step S501: Yes). Through part 444, it is determined whether or not the detected inlet temperature is equal to or higher than a reference inlet temperature included in the load reduction information stored in setting storage unit 441 (step S502).

  When the detected suction port temperature is not equal to or higher than the reference suction port temperature (step S502: No), that is, when the detected suction port temperature is lower than the reference suction port temperature, that is, the standard suction for the time corresponding to the detected suction port temperature. If there is no difference of ± 1 ° C. or less compared to the mouth temperature, the blown air control unit 44 returns the procedure and ends the current process without performing the process described later.

  In step S502, when the detected suction port temperature is equal to or higher than the reference suction port temperature (step S502: Yes), the blown air control unit 44 assumes that the thermal load of the corresponding refrigeration showcase 2 has increased. Based on the table included in the load reduction information stored in the setting storage unit 441, the louver 37 is opened by a predetermined angle through the louver drive processing unit 445, and the rotation speed of the air conditioning fan 33 through the fan drive processing unit 446. Is increased to the determined size, and further, a command is given to the compression control unit 41 through the communication processing unit 442 to increase the compressor 11 to the determined operating rotational speed through the compressor drive processing unit 415 (step S503, step S503). S504, Step S505), the procedure is returned to end the current process.

  By opening the louver 37 in this way, the direction of the indoor air blown from the blower outlet 35 can be adjusted, and by increasing the number of rotations of the air conditioning fan 33, the blowout blown from the blower outlet 35. The amount of indoor air blown out can be increased, and the cooling capacity in the air conditioning evaporator 32 is improved by further increasing the operating rotational speed of the compressor 11. As a result, the indoor air blown out from the air outlet 35 is increased. The blowing temperature can be lowered.

  As described above, the cooling system according to the fifth embodiment of the present invention has the following effects in addition to the effects exhibited by the cooling system according to the first embodiment described above.

  That is, it is determined that the thermal load of the corresponding showcase 2 is increased when the inlet temperature detected through the inlet temperature sensor 219b is equal to or higher than the reference inlet temperature, and the table included in the load reduction information is used. Based on the control of the direction, the amount of blown air and the blown air temperature of the room air blown from the blower outlet 35, the heat load of the showcase 2 can be reduced, and as a result, energy saving can be achieved. it can.

  In Embodiment 5 of the present invention described above, the air load control process is performed by determining the thermal load of the showcase 2 based on the inlet temperature, but the present invention is limited to this. Instead, the air temperature control process may be performed by determining the thermal load of the showcase 2 on the basis of the ambient temperature of the corresponding showcase 2 and the ambient absolute humidity of the corresponding showcase 2 as follows. .

  For example, as shown in FIG. 32, ambient temperature sensors 219c are provided outside the refrigerated showcases 1 to 3, respectively. The ambient temperature sensor 219c detects the temperature around the refrigerated showcases 1 to 3.

  As shown in FIG. 33, the blown air control unit 44 includes a setting storage unit 441a, a communication processing unit 442, a timer unit 443, a determination unit 444a, a louver drive processing unit 445, and a fan drive processing unit 446. It is.

  The setting storage unit 441a is for setting and storing programs and data necessary for the blown air control unit 44 to perform control. In particular, in the present modification, the reference peripheral area is used instead of the reference inlet temperature. The temperature is set and memorized.

  The determination unit 444a determines the thermal load of the corresponding showcase 2 as a result of comparing the ambient temperature detected through the ambient temperature sensor 219c with the reference ambient temperature stored in the setting storage unit 441a, and determines the blown air temperature. The blowing direction and the blowing air amount are determined.

  FIG. 34 is a flowchart showing the contents of a modification of the blown air control process shown in FIG. Hereinafter, the operation of the cooling system will be described with reference to FIG. In the following, time measurement by the timer unit 443 will not be described, but it is assumed that time measurement is performed from the end of the defrosting operation of the showcase 2.

  In the blown air control process, the blown air control unit 44 (control unit 402) inputs the ambient temperature detected from the ambient temperature sensor 219c at a certain time measured by the timer unit 443 (step S511: Yes), and the determination unit 444a. Then, it is determined whether or not the detected ambient temperature is equal to or higher than the reference ambient temperature stored in the setting storage unit 441a (step S512).

  When the detected ambient temperature is not equal to or higher than the reference ambient temperature (step S512: No), that is, when the detected ambient temperature is less than the reference ambient temperature, the blown air control unit 44 performs the processing described later, Return the procedure and end the current process.

  In step S512, when the detected ambient temperature is equal to or higher than the reference ambient temperature (step S512: Yes), the blown air control unit 44 sets and stores the heat load of the corresponding refrigerated showcase 2 as increasing. Based on the table included in the load reduction information stored in the unit 441a, the louver 37 is opened by a predetermined angle through the louver drive processing unit 445, and the rotation speed of the air conditioning fan 33 is determined through the fan drive processing unit 446. Then, a command is given to the compression control unit 41 through the communication processing unit 442, and the compressor 11 is increased to the determined operating rotational speed through the compressor drive processing unit 415 (steps S513, S514). Step S515), the procedure is returned to end the current process.

  By opening the louver 37, the blowing direction of the room air blown from the blower outlet 35 can be adjusted, and by increasing the rotation speed of the air conditioning fan 33, the indoor air blown from the blower outlet 35 can be adjusted. The amount of blown air can be increased, and the operating speed of the compressor 11 is further increased to improve the cooling capacity of the air conditioning evaporator 32. As a result, the blowout temperature of the indoor air blown from the blowout port 35 is increased. Can be reduced.

  As described above, when the ambient temperature detected through the ambient temperature sensor 219c is equal to or higher than the reference ambient temperature, it is determined that the thermal load of the corresponding showcase 2 is increasing, and the air flow is determined based on the table included in the load reduction information. By controlling the blowing direction, the blowing air amount, and the blowing air temperature of the room air blown from the outlet 35, the heat load of the showcase 2 can be reduced, and as a result, energy saving can be achieved.

  Next, as another modified example, as shown in FIG. 35, enthalpy sensors are provided outside the refrigerated showcases 1 to 3, respectively. The enthalpy sensor detects the temperature and humidity around the refrigerated showcases 1 to 3.

  As shown in FIG. 36, the blown air control unit 44 includes a setting storage unit 441b, a communication processing unit 442, a timer unit 443, an absolute humidity deriving unit 447, a determination unit 444b, a louver drive processing unit 445, and a fan drive processing unit. 446 is provided.

  The setting storage unit 441b is for setting and storing programs and data necessary for the blown air control unit 44 to perform control. In particular, in this modification, the reference absolute temperature is used instead of the reference inlet temperature. Humidity is set and stored as load reduction information.

  The absolute humidity deriving unit 447 derives the ambient absolute humidity based on the ambient temperature and ambient humidity (relative humidity) detected through the enthalpy sensor.

  The determination unit 444b determines the thermal load of the corresponding showcase 2 as a result of comparing the ambient absolute temperature derived through the absolute humidity deriving unit 447 and the reference absolute humidity stored in the setting storage unit 441b. The air temperature, the blowing direction, and the blowing air amount are determined.

  FIG. 37 is a flowchart showing the contents of another variation of the blown air control process shown in FIG. Hereinafter, the operation of the cooling system will be described with reference to FIG.

  In the following, time measurement by the timer unit 443 will not be described, but it is assumed that time measurement is performed from the end of the defrosting operation of the showcase 2.

  In the blown air control process, the blown air control unit 44 (control unit 402) inputs the ambient temperature and ambient humidity (relative humidity) detected from the enthalpy sensor at a certain time measured by the timer unit 443 (step S521: Yes). ), And the surrounding absolute humidity is derived through the absolute humidity deriving unit 447 (step S522).

  The blowing air control unit 44 that has derived the ambient absolute humidity determines whether or not the derived ambient absolute humidity is equal to or higher than the reference absolute humidity stored in the setting storage unit 441b through the determination unit 444b (step S523).

  When the derived ambient absolute humidity is not equal to or higher than the reference absolute humidity (step S523: No), that is, when the derived ambient absolute humidity is less than the reference absolute humidity, the blown air control unit 44 performs processing to be described later. Instead, return to the procedure and end the current process.

  In step S523, when the derived ambient absolute humidity is equal to or higher than the reference absolute humidity (step S523: Yes), the blown air control unit 44 is set assuming that the heat load of the corresponding refrigeration showcase 2 is increased. Based on the table included in the load reduction information stored in the storage unit 441b, the louver 37 is opened by a predetermined angle through the louver drive processing unit 445, and the rotation speed of the air conditioning fan 33 is set through the fan drive processing unit 446. Then, the compressor 11 is given a command through the communication processing unit 442, and the compressor 11 is increased to the determined operating rotational speed through the compressor drive processing unit 415 (steps S524 and S525). , Step S526), the procedure is returned to end the current process.

  By opening the louver 37, the blowing direction of the room air blown from the blower outlet 35 can be adjusted, and by increasing the rotation speed of the air conditioning fan 33, the indoor air blown from the blower outlet 35 can be adjusted. The amount of blown air can be increased, and the operating speed of the compressor 11 is further increased to improve the cooling capacity of the air conditioning evaporator 32. As a result, the blowout temperature of the indoor air blown from the blowout port 35 is increased. Can be reduced.

  It is determined that the thermal load of the showcase 2 corresponding to the case where the ambient absolute humidity derived in this way is equal to or higher than the reference absolute humidity, and the air is blown out from the air outlet 35 based on the table included in the load reduction information. By controlling the direction of blowing indoor air, the amount of blown air and the blown air temperature, the heat load of the showcase 2 can be reduced, and as a result, energy saving can be achieved.

<Embodiment 6>
FIG. 38 is a schematic diagram schematically showing a cooling system according to the sixth embodiment of the present invention. In addition, the same code | symbol is attached | subjected to what has the same structure as the cooling system in Embodiment 1 mentioned above, and the description is abbreviate | omitted suitably.

  The cooling system illustrated here includes a refrigerator 100, a showcase cooling unit 20, an air conditioning unit 30, and a control unit 403.

  The refrigerator 100 is installed, for example, outdoors, and includes an inverter compressor 111, a constant speed compressor 112, and a condenser 12 as shown in FIG.

  Both the inverter compressor 111 and the constant speed compressor 112 compress the refrigerant into a high-temperature and high-pressure state (high-temperature and high-pressure gas refrigerant).

  The inverter compressor 111 and the constant speed compressor 112 are driven in accordance with a command given from the compression control unit 41 (compressor drive processing unit 415) constituting the control unit 403.

  Here, driving of the compressor 11 will be described. When the cooling load of the refrigerated showcases 1 to 3 or the freezing showcases 4 to 6 is low, only the inverter compressor 111 is operated. When the cooling load of the refrigerated showcases 1 to 3 or the refrigeration showcases 4 to 6 increases and the number of operations of the inverter compressor 111 reaches the maximum value, the constant speed compressor 112 starts driving and the inverter The operating rotational speed of the compressor 111 is a minimum value.

  Thereafter, when the cooling load of the showcases 1 to 3 for refrigeration or the showcases 4 to 6 for freezing increases, the operating rotational speed of the inverter compressor 111 increases and is adjusted to a predetermined low pressure setting value.

  On the other hand, when the cooling load of the showcases 1 to 3 for refrigeration or the showcases 4 to 6 for refrigeration is reduced, the constant speed compressor 112 is stopped and the operation speed of the inverter compressor 111 is set to the maximum value. Further, when the cooling load of the showcases 1 to 3 for refrigeration or the showcases 4 to 6 for refrigeration is reduced, the operating speed of the inverter compressor 111 is reduced and adjusted to a predetermined low pressure setting value.

  The control unit 403 comprehensively controls the operation of the cooling system. As shown in FIG. 39, the control unit 403 includes a compression control unit 41, a booster control unit 42, and an operating number control unit 45. is there.

  The operating number control unit 45 includes a setting storage unit 451, a communication processing unit 452, an internal temperature monitoring unit 453, a frequency measurement unit 454, a determination unit 455, and a compressor drive command unit 456.

  The setting storage unit 451 is for setting and storing programs and data necessary for the operation number control unit 45 to perform control, and particularly in the sixth embodiment, the upper limit value of the target refrigerator temperature. In addition, the lower limit value, the upper limit value and lower limit value of the target freezer temperature, the standby time, the reference number of increase / decrease times, and the solenoid valve operating rate threshold value are set and stored. The communication processing unit 452 is for performing communication processing of various information with each of the compression control unit 41 and the booster control unit 42.

  The internal temperature monitoring unit 453 inputs the refrigerator internal temperature detected from the compression control unit 41 through the refrigerator internal temperature sensor 215 and the freezer internal temperature detected from the booster control unit 42 through the freezer internal temperature sensor 225 through the communication processing unit 452. Then, it is monitored whether each internal temperature (refrigerator internal temperature and freezer internal temperature) is within the target temperature range.

  Here, within the target temperature range, in the case of the refrigerator temperature, it means a range that is equal to or lower than the upper limit value of the target refrigerator temperature and equal to or higher than the lower limit value of the target refrigerator temperature, and in the case of the freezer temperature, the target freezer The range which becomes below the upper limit of internal temperature and becomes more than the lower limit of target freezer internal temperature.

  The number measuring unit 454 measures the number of increase / decrease of the compressor 11, that is, the number of switching between the case where only the inverter compressor 111 is operated and the case where the inverter compressor 111 and the constant speed compressor 112 are operated. The number measuring unit 454 measures the number of increase / decrease times of the compressor 11 in a preset time.

  The determination unit 455 makes various determinations. More specifically, the increase / decrease number of the compressor 11 within a predetermined time measured by the number measurement unit 454 exceeds the reference number stored in the setting storage unit 451. Although the details will be described later, the solenoid valve operating rates (the refrigeration solenoid valve operating rate and the freezing solenoid valve operating rate) input from the compression control unit 41 and the booster control unit 42 are stored in the setting storage unit 451. It is determined whether or not the rate threshold has been exceeded, and whether or not the standby time stored in the setting storage unit 451 has elapsed.

  The compressor drive command unit 456 gives various drive commands to the compressor drive processing unit 415 constituting the compression control unit 41 via the communication processing unit 452. More specifically, a command to stop increasing / decreasing (switching) the compressor 11 is given to the compressor drive processing unit 415, or a command to reduce or maintain the number of operating units is given.

  FIG. 40 is a flowchart showing the contents of the operation number control process executed by the control unit 403.

  Hereinafter, the operation of the cooling system according to the sixth embodiment will be described with reference to FIG. In the following, for convenience of explanation, only the refrigerated showcases 1 to 3 will be described as application targets.

  In the operation number control process, the operation number control unit 45 measures the increase / decrease number of the compressor 11 in the set time through the number measurement unit 454 (step S601).

  As a result of measuring the increase / decrease number of the compressor 11, when it is determined through the determination unit 455 that the increase / decrease number exceeds the reference number stored in the setting storage unit 451 (step S <b> 602: Yes), the operation number control unit 45. Gives an increase / decrease stop command to the compressor drive processing unit 415 of the compression control unit 41 through the compressor drive command unit 456 (step S603).

  Thereby, the switching of the compressor 11 is stopped. When it is determined through the determination unit 455 that the predetermined standby time has elapsed after giving such an increase / decrease stop command (step S604: Yes), the operating unit number control unit 45 transmits from the compression control unit 41 through the internal temperature monitoring unit 453. The refrigerator internal temperature is input, and it is determined whether or not the refrigerator internal temperature is within the target temperature range (steps S605 and S606).

  When the refrigerator temperature is within the target temperature range (step S606: Yes), the operating number control unit 45 determines whether or not the operating number of the compressors 11 is plural when the increase / decrease stop command is given in step S603. (Step S607), that is, it is determined whether or not there are a plurality of operating units of the compressor 11 when the increase / decrease count exceeds the reference count. If there are a plurality of compressors 11 (step S607: Yes), A stand operation control process is performed (step S608), and in the case of a single unit (step S607: No), a single unit operation control process is executed (step S609).

  On the other hand, when the refrigerator internal temperature is not within the target temperature range (step S606: No), the operating number control unit 45 determines whether the refrigerator internal temperature is less than the lower limit value of the target refrigerator internal temperature (step S610). ). When the refrigerator internal temperature is lower than the target refrigerator internal temperature (step S610: Yes), the operating number control unit 45 determines whether or not the operating number of the compressors 11 is plural (step S611).

  When there are a plurality of operating units of the compressor 11 (step S611: Yes), the operating unit control unit 45 gives an operating unit number reduction command to the compressor drive processing unit 415 of the compression control unit 41 through the compressor drive command unit 456. (Step S612), and then the procedure is returned to end the current process.

  When the number of operating compressors 11 is singular (step S611: No), the operating number control unit 45 gives an operating number maintenance command to the compressor drive processing unit 415 of the compression control unit 41 through the compressor drive command unit 456. (Step S613), the procedure is then returned to end the current process.

  When the refrigerator internal temperature is not less than the lower limit value of the target refrigerator internal temperature (step S610: No), that is, when the refrigerator internal temperature exceeds the upper limit value of the target refrigerator internal temperature, the operating number control unit 45 It is determined whether or not there are a plurality of operating units (step S614).

  When there are a plurality of operating units of the compressor 11 (step S614: Yes), the operating unit control unit 45 gives an operating unit maintenance command to the compressor drive processing unit 415 of the compression control unit 41 through the compressor drive command unit 456. (Step S615), the procedure is then returned to end the current process.

  When the number of operating units of the compressor 11 is single (step S614: No), the operating unit control unit 45 gives an operating unit increase command to the compressor drive processing unit 415 of the compression control unit 41 through the compressor drive command unit 456. (Step S616), and then the procedure is returned to end the current process.

  FIG. 41 is a flowchart showing the process contents of the multiple-unit operation control process shown in FIG. In the multi-unit operation control process, the operation number control unit 45 receives the operation rate of the refrigeration solenoid valve 214 from the operation rate calculation unit 414 of the compression control unit 41 through the communication processing unit 452 (step S6081: Yes), and the determination unit Through 455, it is determined whether or not the input operation rate of the refrigeration solenoid valve 214 is equal to or less than the operation rate threshold value stored in the setting storage unit 451 (step S6082).

  When the operating rate of the refrigeration solenoid valve 214 is equal to or lower than the operating rate threshold value (step S6082: Yes), the operating number control unit 45 passes the compressor drive command unit 456 to the compressor drive processing unit 415 of the compression control unit 41. An operation number reduction command is given (step S6083), the procedure is returned, and the current process is terminated. Thereby, the compressor drive processing unit 415 operates only the inverter compressor 111.

  On the other hand, when the operation rate of the refrigeration solenoid valve 214 is not equal to or less than the operation rate threshold (step S6082: No), that is, when the operation rate of the refrigeration solenoid valve 214 exceeds the operation rate threshold, An operation number maintenance command is given to the compressor drive processing unit 415 of the compression control unit 41 through the compressor drive command unit 456 (step S6084), the procedure is returned, and the current process is terminated.

  Thereby, the operation number of the compressor 11 is maintained with two or more. The operating unit control unit 45 that has performed the multiple unit operation control process then returns the procedure and ends the operating unit control process.

  FIG. 42 is a flowchart showing the processing contents of the single-unit operation control process shown in FIG. In the single unit operation control process, the operation number control unit 45 inputs the operation rate of the refrigeration solenoid valve 214 from the operation rate calculation unit 414 of the compression control unit 41 through the communication processing unit 452 (step S6091: Yes). Through 455, it is determined whether or not the input operation rate of the refrigeration solenoid valve 214 is equal to or less than the operation rate threshold value stored in the setting storage unit 451 (step S6092).

  When the operating rate of the refrigeration solenoid valve 214 is equal to or lower than the operating rate threshold value (step S6092: Yes), the operating number control unit 45 performs the compressor drive processing unit 415 of the compression control unit 41 through the compressor drive command unit 456. An operation rotational speed reduction command is given (step S6093), the procedure is returned, and the current process is terminated. Thereby, the compressor drive processing unit 415 reduces the operating rotational speed of the inverter compressor 111.

  On the other hand, when the operation rate of the refrigeration solenoid valve 214 is not less than or equal to the operation rate threshold (step S6092: No), that is, when the operation rate of the refrigeration solenoid valve 214 exceeds the operation rate threshold, An operation number maintenance command is given to the compressor drive processing unit 415 of the compression control unit 41 through the compressor drive command unit 456 (step S6094), the procedure is returned, and the current process is terminated.

  Thereby, the operation number of the compressor 11 is maintained with the single number. The number-of-operations control unit 45 that has performed the single-unit operation control process thereafter returns the procedure and ends the operation number control process.

  As described above, according to the cooling system of the sixth embodiment, in addition to the functions and effects exhibited by the cooling system of the first embodiment described above, the following functions and effects are achieved.

  That is, the number of increase / decrease of the number of operation of the compressors 11 in the set time exceeds the reference number, and when the reference number is exceeded, there are a plurality of operation units of the compressor 11 and the refrigeration showcases 1 to 3 are accommodated. When the refrigerator internal temperature of the refrigerators 1a to 3a is within the target temperature range, when the operation rate of the refrigeration solenoid valve 214 is equal to or less than the operation rate threshold, the number of operating compressors 11 is decreased, while the refrigeration solenoid valve 214 When the operating rate exceeds the operating rate threshold value, the number of operating compressors 11 is maintained, so that the containers 1a to 3a can be cooled satisfactorily without frequently switching the operating number of the compressors 11 and necessary. Since the storages 1a to 3a are cooled by the number of compressors 11, energy saving in operation can be achieved.

  According to the cooling system, the number of increase / decrease of the number of operating compressors 11 in the set time exceeds the reference number, and when the reference number is exceeded, the number of operating compressors 11 is single, and the showcase for refrigeration When the operating temperature of the refrigeration solenoid valve 214 is equal to or lower than the operating rate threshold when the refrigerator internal temperatures of the storage containers 1a to 3a of 1 to 3 are within the target temperature range, the operating rotational speed of the compressor 11 is decreased. When the refrigeration solenoid valve operating rate exceeds the operating rate threshold value, the number of operating compressors 11 is maintained, so that the containers 1a to 3a can be cooled well without frequently switching the operating number of compressors 11. In addition, since the containers 1a to 3a are cooled by reducing the number of necessary operation revolutions, it is possible to save energy during operation.

  Further, according to the cooling system, since the increase / decrease in the number of operating compressors 11 is stopped during the preset standby time, it becomes possible to check the transition of the internal state of the target storages 1a to 3a. This also suppresses frequent switching of the number of operating compressors 11.

  In Embodiment 6 of the present invention described above, the number of operating compressors 11 is controlled based on the operating rate of the solenoid valve, but the present invention is not limited to this, and the following As described above, the number of operating compressors 11 may be controlled on the basis of the degree of superheat in the refrigeration evaporator 211 and the refrigeration evaporator 221.

  For example, in addition to the above configuration, the cooling system includes an inlet temperature sensor 211a of the refrigeration evaporator 211, an outlet temperature sensor 211b of the refrigeration evaporator 211, and an inlet temperature sensor of the refrigeration evaporator 221 as shown in FIG. 221a and an outlet temperature sensor 221b of the refrigeration evaporator 221 are provided.

  The inlet temperature sensor 211 a of the refrigeration evaporator 211 detects the temperature of the refrigerant passing near the inlet of the refrigeration evaporator 211. The outlet temperature sensor 211b of the refrigeration evaporator 211 detects the temperature of the refrigerant passing near the outlet of the refrigeration evaporator 211. The inlet temperature sensor 221 a of the refrigeration evaporator 221 detects the temperature of the refrigerant passing near the inlet of the refrigeration evaporator 221. The outlet temperature sensor 221b of the refrigeration evaporator 221 detects the temperature of the refrigerant passing through the vicinity of the outlet of the refrigeration evaporator 221.

  The compression control unit 41 configuring the control unit 403 includes a superheat degree calculation unit 418 in addition to the above configuration. The superheat degree calculation unit 418 calculates the degree of superheat defined as the difference between the temperature detected by the outlet temperature sensor 211b of the refrigeration evaporator 211 and the temperature detected by the inlet temperature sensor 211a of the refrigeration evaporator 211. It is to calculate.

  Moreover, the booster control part 42 which comprises the control unit 403 is provided with the superheat degree calculating part 427 other than the said structure. The superheat degree calculation unit 427 calculates the superheat degree from the temperature detected by the outlet temperature sensor 221b of the refrigeration evaporator 221 and the temperature detected by the inlet temperature sensor 221a of the refrigeration evaporator 221. .

  The number-of-operations control unit 45 includes a setting storage unit 451a, a communication processing unit 452, an internal temperature monitoring unit 453, a frequency measurement unit 454, a determination unit 455a, and a compressor drive command unit 456.

  The setting storage unit 451a is for setting and storing programs and data necessary for the operation number control unit 45 to perform control. In particular, in this modification, overheating is used instead of the solenoid valve operating rate threshold value. A degree threshold is set and stored.

  The determination unit 455a makes various determinations. In particular, in this modification, instead of determining whether the electromagnetic valve operation rate exceeds the operation rate threshold value stored in the setting storage unit 451, the degree of superheat is determined. It is determined whether or not the superheat degree threshold stored in the setting storage unit 451a has been exceeded.

  FIG. 44 is a flowchart showing the content of the operation number control process executed by the control unit 403 which is a modification of the sixth embodiment.

  Hereinafter, the operation of the cooling system according to this modification will be described with reference to FIG. In the following, for convenience of explanation, only the refrigerated showcases 1 to 3 will be described as application targets.

  In the operation number control process, the operation number control unit 45 measures the increase / decrease number of the compressor 11 in the set time through the number measurement unit 454 (step S621).

  As a result of measuring the number of times of increase / decrease of the compressor 11, if it is determined through the determination unit 455a that the number of increase / decrease exceeds the reference number stored in the setting storage unit 451a (step S622: Yes), the number-of-operations control unit 45 Gives an increase / decrease stop command to the compressor drive processing unit 415 of the compression control unit 41 through the compressor drive command unit 456 (step S623).

  Thereby, the switching of the compressor 11 is stopped. When it is determined through the determination unit 455a that the increase / decrease stop command has been given and the predetermined waiting time has elapsed (step S624: Yes), the operating number control unit 45 is controlled from the compression control unit 41 through the internal temperature monitoring unit 453. The refrigerator internal temperature is input, and it is determined whether or not the refrigerator internal temperature is within the target temperature range (steps S625 and S626).

  When the refrigerator temperature is within the target temperature range (step S626: Yes), the operating number control unit 45 determines whether or not there are a plurality of operating units of the compressor 11 when the increase / decrease stop command is given in step S623. (Step S627), that is, it is determined whether or not there are a plurality of operating units of the compressor 11 when the increase / decrease count exceeds the reference count. A stand operation control process is implemented (step S628), and in the case of a single unit (step S627: No), a stand operation control process is implemented (step S629).

  On the other hand, when the refrigerator internal temperature is not within the target temperature range (step S626: No), the operating number control unit 45 determines whether the refrigerator internal temperature is less than the lower limit value of the target refrigerator internal temperature (step S630). ). When the refrigerator internal temperature is lower than the target refrigerator internal temperature (step S630: Yes), the operating number control unit 45 determines whether or not the operating number of the compressors 11 is plural (step S631).

  When there are a plurality of operating units of the compressor 11 (step S631: Yes), the operating unit control unit 45 gives an operating unit number reduction command to the compressor drive processing unit 415 of the compression control unit 41 through the compressor drive command unit 456. (Step S632), and then the procedure is returned to end the current process.

  When the number of operating compressors 11 is single (step S631: No), the operating number control unit 45 gives an operating number maintenance command to the compressor drive processing unit 415 of the compression control unit 41 through the compressor drive command unit 456. (Step S633), the procedure is then returned to end the current process.

  When the refrigerator internal temperature is not less than the lower limit value of the target refrigerator internal temperature (step S630: No), that is, when the refrigerator internal temperature exceeds the upper limit value of the target refrigerator internal temperature, the operating number control unit 45 It is determined whether there are a plurality of operating units (step S634).

  When there are a plurality of operating units of the compressor 11 (step S634: Yes), the operating unit control unit 45 gives an operating unit maintenance command to the compressor drive processing unit 415 of the compression control unit 41 through the compressor drive command unit 456. (Step S635), the procedure is then returned to end the current process.

  When the number of operating units of the compressor 11 is single (step S634: No), the operating unit control unit 45 gives an operating unit increase command to the compressor drive processing unit 415 of the compression control unit 41 through the compressor drive command unit 456. (Step S636), the procedure is then returned to end the current process.

  FIG. 45 is a flowchart showing the contents of the multiple-unit operation control process shown in FIG. In the multi-unit operation control process, the operating unit control unit 45 receives the superheat degree in the refrigeration evaporator 211 from the superheat degree calculation unit 427 of the compression control unit 41 through the communication processing unit 452 (step S6281: Yes), and the determination unit It is determined through 455a whether or not the input superheat degree in the refrigeration evaporator 211 exceeds the superheat degree threshold stored in the setting storage unit 451a (step S6282).

  When the superheat degree in the refrigeration evaporator 211 exceeds the superheat degree threshold value (step S6282: Yes), the operating number control unit 45 passes the compressor drive command unit 456 to the compressor drive processing unit 415 of the compression control unit 41. A command for reducing the number of operating units is given (step S6283), the procedure is returned, and the current process is terminated. Thereby, the compressor drive processing unit 415 operates only the inverter compressor 111.

  On the other hand, when the superheat degree in the refrigeration evaporator 211 does not exceed the superheat degree threshold value (step S6282: No), the operating number control unit 45 performs the compressor drive processing unit of the compression control unit 41 through the compressor drive command unit 456. An operation number maintenance command is given to 415 (step S6284), the procedure is returned, and the current process is terminated.

  Thereby, the operation number of the compressor 11 is maintained with two or more. The operating unit control unit 45 that has performed the multiple unit operation control process then returns the procedure and ends the operating unit control process.

  FIG. 46 is a flowchart showing the processing contents of the single-unit operation control process shown in FIG. In the single unit operation control process, when the operation number control unit 45 inputs the superheat degree in the refrigeration evaporator 211 from the superheat degree calculation unit 427 of the compression control unit 41 through the communication processing unit 452 (step S6291: Yes), the determination unit Through 455a, it is determined whether or not the input superheat degree in the refrigeration evaporator 211 exceeds the superheat degree threshold stored in the setting storage unit 451a (step S6292).

  When the superheat degree in the refrigeration evaporator 211 exceeds the superheat degree threshold (step S6292: Yes), the operating number control unit 45 passes the compressor drive command unit 456 to the compressor drive processing unit 415 of the compression control unit 41. On the other hand, an operation rotational speed reduction command is given (step S6293), the procedure is returned, and the current process is terminated. Thereby, the compressor drive processing unit 415 reduces the operating rotational speed of the inverter compressor 111.

  On the other hand, when the superheat degree in the refrigeration evaporator 211 does not exceed the superheat degree threshold value (step S6292: No), the operating number control unit 45 passes through the compressor drive command unit 456 and the compressor drive processing unit of the compression control unit 41. An operation number maintenance command is given to 415 (step S6294), the procedure is returned, and the current process is terminated.

  Thereby, the operation number of the compressor 11 is maintained with the single number. The number-of-operations control unit 45 that has performed the single-unit operation control process thereafter returns the procedure and ends the operation number control process.

  Even with such a cooling system, the number of increase / decrease of the number of operating compressors 11 in the set time exceeds the reference number, and when the reference number is exceeded, the number of operating compressors 11 is plural, and the refrigeration show When the refrigerator internal temperature of the storages 1a to 3a of the cases 1 to 3 is within the target temperature range, when the superheat degree in the refrigeration evaporator 211 exceeds the superheat degree threshold, the number of operating compressors 11 is decreased, When the superheat degree in the refrigeration evaporator 211 is equal to or lower than the superheat degree threshold value, the number of operating compressors 11 is maintained. Therefore, the containers 1a to 3a can be cooled well without frequently switching the number of operating compressors 11. In addition, since the containers 1a to 3a are cooled by the required number of compressors 11, energy saving in operation can be achieved.

  According to the cooling system, the number of increase / decrease of the number of operating compressors 11 in the set time exceeds the reference number, and when the reference number is exceeded, the number of operating compressors 11 is single, and the showcase for refrigeration In the case where the refrigerator internal temperatures of the storage containers 1a to 3a of 1 to 3 are within the target temperature range, when the superheat degree in the refrigeration evaporator 211 exceeds the superheat degree threshold, the operating rotational speed of the compressor 11 is decreased, When the superheat degree in the refrigeration evaporator 211 is equal to or lower than the superheat degree threshold, the number of operating compressors 11 is maintained, so that the containers 1a to 3a can be cooled well without frequently switching the number of operating compressors 11. In addition, since the containers 1a to 3a are cooled by reducing the required number of operation revolutions, it is possible to save energy during operation.

  Further, according to the cooling system, since the increase / decrease in the number of operating compressors 11 is stopped during the preset standby time, it becomes possible to check the transition of the internal state of the target storages 1a to 3a. This also suppresses frequent switching of the number of operating compressors 11.

  As described above, the cooling system according to the present invention is useful for cooling the showcase storage.

It is a schematic diagram which shows typically the cooling system which is Embodiment 1 of this invention. It is a schematic diagram which shows typically the principal part of the cooling system shown in FIG. It is a schematic diagram which shows typically the principal part of the cooling system shown in FIG. It is a block diagram which shows the control system of the cooling system shown in FIG. It is a flowchart which shows the content of the refrigerating solenoid valve control processing which a control unit implements. It is a flowchart which shows the content of the booster unit control process (1) which a control unit implements. It is a chart which shows freezing capacity judgment conditions. It is a flowchart which shows the content of the refrigerating solenoid valve control processing which a control unit implements. It is a flowchart which shows the content of the compressor drive control process (1) which a control unit implements. It is a flowchart which shows the content of the compressor drive control process (2) which a control unit implements. It is a flowchart which shows the content of the valve switching control process which a control unit implements. It is a schematic diagram which shows typically the cooling system which is Embodiment 2 of this invention. It is a schematic diagram which shows typically the principal part of the cooling system shown in FIG. It is a block diagram which shows the control system of the cooling system shown in FIG. It is a flowchart which shows the processing content of the load judgment process of the refrigerator for refrigeration which the control unit shown in FIG. 12 implements. It is a flowchart which shows the processing content of the load determination process of the evaporator for freezing which the control unit shown in FIG. 12 implements. It is a flowchart which shows the processing content of the booster unit control process (2) which the control unit shown in FIG. 12 implements. It is a flowchart which shows the processing content of the compressor drive control process (3) which the control unit shown in FIG. 12 implements. It is a flowchart which shows the content of the valve switching control process which the control unit shown in FIG. 12 implements. It is a schematic diagram which shows typically the cooling system which is Embodiment 3 of this invention. It is a schematic diagram which shows typically the principal part of the cooling system shown in FIG. It is a schematic diagram which shows typically the cooling system which is Embodiment 4 of this invention. It is a schematic diagram which shows typically the principal part of the cooling system shown in FIG. It is a block diagram which shows the control system of the cooling system shown in FIG. It is a flowchart which shows the content of the blowing direction control process which a control unit implements. It is a schematic diagram which shows typically the cooling system which is Embodiment 5 of this invention. It is a schematic diagram which shows typically the principal part of the cooling system shown in FIG. It is a block diagram which shows the control system of the cooling system shown in FIG. FIG. 29 is a chart showing a table stored in a setting storage unit shown in FIG. 28. FIG. FIG. 29 is a chart showing a table stored in a setting storage unit shown in FIG. 28. FIG. It is a flowchart which shows the content of the blowing air control process which a control unit implements. It is a schematic diagram which shows typically the principal part of the cooling system which is a modification of Embodiment 5 of this invention. It is a block diagram which shows the control system of the cooling system which is a modification of Embodiment 5 of this invention. It is a flowchart which shows the content of the blowing air control process which a control unit implements. It is a schematic diagram which shows typically the principal part of the cooling system which is the other modification of Embodiment 5 of this invention. It is a block diagram which shows the control system of the cooling system which is the other modification of Embodiment 5 of this invention. It is a flowchart which shows the content of the blowing air control process which a control unit implements. It is a schematic diagram which shows typically the cooling system which is Embodiment 6 of this invention. It is a block diagram which shows the control system of the cooling system shown in FIG. It is a flowchart which shows the content of the operation number control process which a control unit implements. It is a flowchart which shows the content of the multi-unit operation control processing which a control unit implements. It is a flowchart which shows the content of the single unit operation control process which a control unit implements. It is a block diagram which shows the control system of the cooling system which is a modification of Embodiment 6 of this invention. It is a flowchart which shows the content of the operation number control process which a control unit implements. It is a flowchart which shows the content of the multi-unit operation control processing which a control unit implements. It is a flowchart which shows the content of the single unit operation control process which a control unit implements.

Explanation of symbols

1-6 Showcase 1a-6a Storage 10 Refrigerator 11 Compressor 12 Condenser 20 Showcase cooling unit 211 Refrigerator evaporator 212 Cold storage tank 213 Refrigeration temperature expansion valve 214 Refrigeration solenoid valve 215 Refrigerator temperature sensor 216 Blower Fan 221 Refrigeration evaporator 222 Cold storage tank 223 Refrigeration temperature expansion valve 224 Refrigeration solenoid valve 225 Freezer internal temperature sensor 226 Blower fan 23 Booster unit 231 Booster compressor 232 Booster solenoid valve 24 Booster introduction path 25 Booster introduction valve 26 Feedback valve 30 Air-conditioning unit 31 Air-conditioning expansion valve 32 Air-conditioning evaporator 33 Air-conditioning fan 34 Suction port 35 Suction port 36 Suction temperature sensor 40 Control unit 41 Compression control unit 411 Setting storage unit 412 Communication processing unit 413 Refrigerating solenoid valve drive Processing unit 414 Operation rate calculation unit 415 Compressor drive processing unit 416 Valve drive processing unit 417 Temperature comparison unit 42 Booster control unit 421 Setting storage unit 422 Communication processing unit 423 Refrigeration solenoid valve drive processing unit 424 Operation rate calculation unit 425 Booster electromagnetic Valve drive processing unit 426 Booster compressor drive processing unit

Claims (25)

It is arranged in parallel with an expansion valve that adiabatically expands the refrigerant compressed by the compressor and condensed by the condenser, and includes a plurality of evaporators that evaporate the refrigerant adiabatically expanded by the expansion valve. In the cooling system for bringing the storage of each showcase provided with the plurality of evaporators into a desired temperature state by causing the compressor to suck the refrigerant and circulating the refrigerant,
Among the plurality of evaporators, the refrigerant is disposed in a manner in parallel to the downstream side of the plurality of target refrigeration evaporators and upstream of the compressor, and sucks the refrigerant evaporated by the refrigeration evaporator. A plurality of auxiliary compressors that reduce the evaporation temperature of the refrigerant in the refrigeration evaporator by compressing
A cooling system comprising: auxiliary compression control means for increasing / decreasing at least one of the number of operating and the number of operating revolutions of the plurality of auxiliary compressors according to the loads of the plurality of refrigeration evaporators. An upstream side of each of the refrigeration evaporators is provided with an electromagnetic valve that allows or regulates the supply of the refrigerant to the refrigeration evaporator,
2. The cooling system according to claim 1, wherein the auxiliary compression control unit increases or decreases at least one of the number of operating and the number of operating revolutions of the plurality of auxiliary compressors according to an operating rate of each of the solenoid valves. .   When the auxiliary compression control means has one or more of the operating rates of the solenoid valves that exceed a preset reference operating rate upper limit value, the number of operating and operating speeds of the plurality of auxiliary compressors When at least one of the operating rates of the solenoid valves is lower than a preset reference operating rate lower limit value, the operating number and the operating number of the plurality of auxiliary compressors are increased. The cooling system according to claim 2, wherein at least one of the rotational speeds is reduced. When the degree of superheat in the refrigeration evaporator is calculated, and the calculated degree of superheat is below a preset reference superheat degree lower limit, the refrigerant discharged from the refrigeration evaporator is in a gas-liquid two-phase state. On the other hand, when the calculated degree of superheat exceeds a preset reference superheat degree upper limit value, a determination means is provided for determining that the refrigerant evaporation completion point in the refrigeration evaporator is in the vicinity of the intermediate portion. Consisting of
The auxiliary compression control means operates the plurality of auxiliary compressors when there is one or more refrigerants that are judged to be in a gas-liquid two-phase state by the judgment means. When at least one of the number of units and the number of operation revolutions is increased, and there is one or more of which the determination means determines that the refrigerant evaporation completion point in the refrigeration evaporator is in the vicinity of the intermediate portion, the plurality The cooling system according to claim 1, wherein at least one of the number of operating auxiliary compressors and the number of operating revolutions is reduced.   5. The compressor according to claim 1, further comprising a compression control unit configured to increase or decrease an operation rotational speed of the compressor according to loads of a plurality of evaporators including the refrigeration evaporator. Cooling system.   The cooling system according to claim 5, wherein the compression control unit determines a load of the refrigeration evaporator based on information on the load of the refrigeration evaporator given from the auxiliary compression control unit.   Each of the plurality of evaporators including the refrigeration evaporator has a standardized common size, and the number of arrangements increases in accordance with the cooling load of the storage. The cooling system according to claim 1, wherein the number provided in the showcase is determined. Indoor air circulation means for circulating indoor air of a room in which the showcase is installed between the inside and the outside of the room;
The refrigerant compressed by the compressor and condensed by the condenser is disposed outside the chamber together with an expansion mechanism for adiabatically expanding the refrigerant, and is circulated by the indoor air circulation means by evaporating the refrigerant adiabatically expanded by the expansion mechanism. The cooling system according to claim 1, further comprising: an air conditioning evaporator that cools the indoor air to be cooled.   The cooling system according to claim 8, wherein the compression control unit increases or decreases an operation rotational speed of the compressor according to a load of the air conditioning evaporator. A suction temperature detecting means for detecting a temperature of indoor air passing from the chamber toward the air conditioning evaporator by the indoor air circulation means;
When the temperature detected by the suction temperature detecting means exceeds a predetermined reference suction temperature upper limit value, the compression control means increases the operating speed of the compressor, while the suction temperature detecting means 10. The cooling system according to claim 8, wherein when the detected temperature falls below a predetermined reference suction temperature lower limit value, the operating rotational speed of the compressor is reduced. Among the evaporators provided in the showcase, it is provided in such a manner that it branches off in the path from the refrigeration evaporator excluding the refrigeration evaporator to the compressor and joins the upstream side of the auxiliary compressor. An auxiliary introduction path for guiding the refrigerant evaporated in the refrigeration evaporator to the auxiliary compressor;
It is arranged in the auxiliary introduction path and allows passage of the refrigerant evaporated by the refrigeration evaporator when it is in an open state, while allowing passage of refrigerant evaporated by the refrigeration evaporator when it is in a closed state. Auxiliary introduction valve to regulate,
A path from the refrigeration evaporator to the compressor, disposed downstream of a branch point with the auxiliary introduction path, and when the auxiliary introduction valve is in a closed state, the open state is established and the refrigeration is performed. A feedback valve that allows passage of the refrigerant evaporated by the evaporator for use while closing the auxiliary introduction valve when the auxiliary introduction valve is opened and restricts passage of the refrigerant evaporated by the evaporator for refrigeration. The cooling system according to any one of claims 1 to 10, wherein:   The cooling system according to any one of claims 1 to 11, wherein the showcase is provided with a cold storage tank that accumulates cold heat generated by evaporation of the refrigerant in the evaporator. The indoor air circulation means includes a blowing direction adjusting means for adjusting a blowing direction of the air cooled by the air conditioning evaporator to the chamber,
The inside of the storage of the storage is blown out through the evaporator through the blowout port through the air in the storage of the storage that has been sucked through the suction port around the disposed evaporator. In-compartment air circulation means for circulating air between the inside and outside of the storage;
Suction port temperature detection means for detecting the temperature of the air in the warehouse sucked through the suction port;
Outlet temperature detecting means for detecting the temperature of the air in the cabinet blown out through the outlet;
An internal temperature detection means for detecting an internal air temperature inside the storage;
In the case where there is a storage container in which at least two detection temperatures exceed the preset reference temperatures among the temperatures detected by the suction port temperature detection means, the outlet temperature detection means, and the internal temperature detection means. The blow direction adjusting means for blowing air around the installation location of a showcase provided with the storage, assuming that the storage is disturbed in the air that is blown out through the outlet and reaches the suction port. The cooling system according to any one of claims 8 to 12, further comprising: a blowing direction control means for changing the blowing direction by giving a command to the fan.   When there is a showcase during the defrosting operation, the blowing direction control means gives a command to the blowing direction adjusting means for blowing air around the place where the showcase is installed, and the cooled air is supplied to the showcase. The cooling system according to claim 13, wherein the cooling system is blown out. The indoor air circulation means includes a blow direction adjusting means for adjusting a blow direction of the air cooled by the air conditioning evaporator to the chamber, and a blow amount adjusting means for adjusting the blow amount of the air to the chamber. And
Ambient temperature detection means disposed outside the showcase and detecting the ambient temperature of the showcase;
When the detected temperature by the ambient temperature detecting means is equal to or higher than a preset reference ambient temperature, the blowing direction adjusting means, the blowing amount adjusting means, and the compression control means are based on predetermined load reduction information. A blown air control means for giving a command to each and performing blown air control of the blown air direction, blown amount and blown temperature of the air cooled by the air-conditioning evaporator. Or the cooling system according to any one of the above. The indoor air circulation means includes a blow direction adjusting means for adjusting a blow direction of the air cooled by the air conditioning evaporator to the chamber, and a blow amount adjusting means for adjusting the blow amount of the air to the chamber. And
Suction port temperature detecting means for detecting the temperature of the air in the cabinet sucked through the suction port of the storage;
When the temperature detected by the inlet temperature detecting means is equal to or higher than a preset reference inlet temperature, the outlet direction adjusting means, the outlet amount adjusting means, and the compression control based on predetermined load reduction information A blown air control means for giving a command to each of the means and performing blown air control of the blown air direction, blown amount and blown temperature of the air cooled by the air conditioning evaporator. The cooling system according to any one of the above. The indoor air circulation means includes a blow direction adjusting means for adjusting a blow direction of the air cooled by the air conditioning evaporator to the chamber, and a blow amount adjusting means for adjusting the blow amount of the air to the chamber. And
When the absolute humidity around the showcase is equal to or higher than a preset reference absolute temperature, the blowing direction adjusting means, the blowing amount adjusting means, and the compression control means are set based on predetermined load reduction information. 13. A blown air control means for giving a command to each and performing blown air control of a blown direction, a blown amount and a blown temperature of the air cooled by the air conditioning evaporator is provided. The cooling system according to one. Ambient temperature detection means for detecting the ambient temperature of the showcase;
Ambient relative humidity detection means for detecting the relative humidity of the ambient air of the showcase, and
The blown air control means derives the absolute humidity around the showcase from the ambient temperature detected by the ambient temperature detection means and the relative humidity of the ambient air detected by the ambient relative humidity detection means. The cooling system of claim 17, wherein A plurality of the compressors are provided, and the compression control means increases or decreases the number of operating compressors and the number of operating revolutions of the compressors according to the loads of a plurality of evaporators.
The number of increase / decrease of the number of operation of the compressor by the compression control means in the preset time is predetermined and exceeds the reference number, the number of operation of the compressor at the time of exceeding the reference number is plural, When the internal temperature of the storage is within a predetermined target temperature range, when the superheat degree in the evaporator exceeds a predetermined threshold, the compression control means reduces the number of operating compressors. The cooling system according to claim 5 or 6, further comprising an operation number control means for causing the compression control means to maintain the number of operating compressors when the degree of superheat is equal to or less than the threshold value.   The operation number control means is such that the number of increase / decrease in the number of operation of the compressor by the compression control means in the set time exceeds the reference number, and the number of operation of the compressor at the time when the reference number is exceeded is singular. When the internal temperature of the storage is within a predetermined target temperature range, when the superheat exceeds the threshold value, the compression control means reduces the operating rotational speed of the operating compressor, The cooling system according to claim 19, wherein when the degree of superheat is equal to or less than the threshold value, the compression control means maintains the number of operating compressors. A plurality of the compressors are provided, and the compression control means increases or decreases the number of operating compressors and the number of operating revolutions of the compressors according to the loads of a plurality of evaporators.
The number of increase / decrease of the number of operation of the compressor by the compression control means in the preset time is predetermined and exceeds the reference number, the number of operation of the compressor at the time of exceeding the reference number is plural, When the internal temperature of the storage is within a predetermined target temperature range, when the operating rate of the solenoid valve is equal to or less than a predetermined threshold, the compression control means reduces the number of operating compressors. The cooling system according to claim 5 or 6, further comprising an operation number control means for causing the compression control means to maintain the operation number of the compressors when the operation rate exceeds the threshold value.   The operation number control means is such that the number of increase / decrease in the number of operation of the compressor by the compression control means in the set time exceeds the reference number, and the number of operation of the compressor at the time when the reference number is exceeded is singular. In the case where the internal temperature of the storage is within a predetermined target temperature range, when the operation rate is equal to or less than the threshold value, the compression control means reduces the operating rotational speed of the operating compressor, The cooling system according to claim 21, wherein when the operating rate exceeds the threshold value, the compression control means causes the number of operating compressors to be maintained.   The operation number control means is configured such that the number of increase / decrease in the number of operation of the compressor by the compression control means in the set time exceeds the reference number, and the number of operation of the compressor when the reference number is exceeded is plural. When the internal temperature of the storage is less than the lower limit value of the target temperature range, the compression control means reduces the number of operating compressors, while the internal temperature of the storage is the upper limit of the target temperature range. The cooling system according to any one of claims 19 to 22, wherein when the value exceeds the value, the compression control means causes the number of operating compressors to be maintained.   The operation number control means is such that the number of increase / decrease in the number of operation of the compressor by the compression control means in the set time exceeds the reference number, and the number of operation of the compressor at the time when the reference number is exceeded is singular. When the internal temperature of the storage is less than the lower limit value of the target temperature range, the compression control means maintains the number of operating compressors, while the internal temperature of the storage is the upper limit of the target temperature range. The cooling system according to any one of claims 19 to 23, wherein when the value is exceeded, the number of operating compressors is increased in the compression control means.   The operation number control means, when the number of increase / decrease of the number of compressors operated by the compression control means in the set time exceeds the reference number, during the preset standby time, the compression control means The cooling system according to any one of claims 19 to 24, wherein control for increasing or decreasing the number of operating compressors and the operating rotational speed is stopped.

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