JP2015206542A - Cooling medium circuit device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To curb electric power consumption by reducing driving of heating means such as a heater.SOLUTION: A cooling medium circuit device comprises a cooling medium circuit 10 which has: a compressor 21; a heat exchanger for heating 32 arranged inside a heating storage 5; an intra-storage heat exchanger 25 arranged inside a cooling storage 5; an ejector 23 that sucks a cooling medium passed through the intra-storage heat exchanger 25 with pressure thereof reduced through heat radiation in the heat exchanger for heating 32 and discharges the cooling medium after agitating the same; and a gas-liquid separator 24 that separates the cooling medium supplied through the ejector 23 into a gas phase cooling medium and a liquid phase cooling medium. The cooling medium circuit device also has a control section 50 which synchronizes timing when a temperature inside the heating storage 5 reaches a heating off temperature with the timing when inside the cooling storage 5 reaches a cooling off temperature by adjusting a decompression amount of the ejector 23.

Description

  The present invention relates to a refrigerant circuit device, and more particularly to a refrigerant circuit device that is applied to, for example, a vending machine and that cools and heats the internal air of a product container defined in a vending machine body. It is.

  2. Description of the Related Art Conventionally, as a refrigerant circuit device applied to, for example, a vending machine, one having a refrigerant circuit having a function as a heat pump is known. Such a refrigerant circuit is configured by sequentially connecting a compressor, a heat exchanger for heating, an expansion mechanism, and an internal heat exchanger through a refrigerant pipe.

  The compressor is disposed in a machine room inside the vending machine main body and outside the commodity storage, and compresses the sucked refrigerant to be discharged in a high temperature and high pressure state. The heat exchanger for heating is arrange | positioned inside the goods storage. More specifically, it is disposed inside a product storage (hereinafter also referred to as a heating store) that stores products to be heated. The expansion mechanism is configured by, for example, a capillary tube or an electronic expansion valve. This expansion mechanism is disposed in the machine room in the same manner as the compressor, and depressurizes the refrigerant that has passed through the heat exchanger for heating and adiabatically expands the refrigerant. The internal heat exchanger is disposed inside the commodity storage. More specifically, it is arranged inside a product storage (hereinafter also referred to as a cooling store) that stores products to be cooled.

  In such a refrigerant circuit, the refrigerant compressed by the compressor reaches the heating heat exchanger and dissipates heat by the heating heat exchanger. Thereby, the internal air of a heating chamber is heated. The refrigerant radiated by the heating heat exchanger is adiabatically expanded by the expansion mechanism, evaporated by the internal heat exchanger, sucked into the compressor, compressed again, and circulated. Thereby, the internal air of a refrigerator is cooled (for example, refer patent document 1).

JP 2006-011604 A

  However, in the refrigerant circuit device as described above, there is one refrigerant circulation path, and the heat exchanger for heating and the internal heat exchanger are connected in series. Therefore, if the opening degree of the expansion mechanism is increased to increase the evaporation temperature of the refrigerant in the internal heat exchanger, both the cooling capacity in the internal heat exchanger and the heating capacity in the heating heat exchanger are reduced. It has the characteristic.

  Because it has such characteristics, for example, even if the rotation speed of the compressor is reduced to extend the heat pump operation time, the heating capacity also decreases as the cooling capacity decreases, resulting in the operation of the compressor. It only takes a long time, and it is necessary to drive a heater or the like in order to heat the internal air of the heating cabinet, and it has been difficult to reduce the power consumption.

  Incidentally, a refrigerant circuit device that realizes a heat pump cycle is known in which an ejector is used instead of a capillary tube or an electronic expansion valve.

  The ejector draws and sucks the low-pressure refrigerant (low-pressure refrigerant) discharged from the internal heat exchanger using the energy generated by reducing the pressure of the high-pressure refrigerant (high-pressure refrigerant) that has passed through the heating heat exchanger. The low-pressure refrigerant mixed with the high-pressure refrigerant is discharged after the pressure of the low-pressure refrigerant is increased.

  In a refrigerant circuit device using such an ejector, after boosting the sucked low-pressure refrigerant, it is discharged and supplied to the gas-liquid separator, where it is separated into a gas-phase refrigerant and a liquid-phase refrigerant. Thus, the liquid-phase refrigerant is sent to the heating heat exchanger, while the gas-phase refrigerant is sucked into the compressor. That is, in the refrigerant circuit device using the ejector, the refrigerant flow is separated and circulated by the gas-liquid separator between the compressor side (heating side) and the internal heat exchanger side (cooling side).

  Therefore, if the pressure reduction amount of the ejector is increased to increase the flow rate of the high-pressure refrigerant at the nozzle portion of the ejector, the suction amount of the low-pressure refrigerant increases, while the pressure reduction amount of the ejector is reduced and the nozzle portion is reduced. If the flow rate of the high-pressure refrigerant is reduced, the amount of suction of the low-pressure refrigerant will decrease, while the cooling capacity will increase while the heating capacity will decrease, while the heating capacity will increase while the cooling capacity will decrease. It has the characteristic of

  In view of the above circumstances, an object of the present invention is to provide a refrigerant circuit device capable of reducing power consumption by reducing driving of a heating unit such as a heater.

  In order to achieve the above object, a refrigerant circuit device according to the present invention includes a compressor that compresses sucked refrigerant and a heating chamber that is a heating target, and dissipates the supplied refrigerant to dissipate the refrigerant. A heat exchanger for heating that heats the internal air of the heating cabinet, and an internal heat exchange that cools the internal air of the cooling cabinet by evaporating the supplied refrigerant that is disposed inside the cooling cabinet to be cooled. , An ejector that sucks the refrigerant that has passed through the internal heat exchanger by depressurizing the refrigerant radiated by the heating heat exchanger, and mixes and discharges the refrigerant, and the refrigerant supplied from the ejector A refrigerant circuit having gas-liquid separation means for separating the gas phase refrigerant into the gas phase refrigerant and the liquid phase refrigerant and sucking the gas phase refrigerant into the compressor while supplying the liquid phase refrigerant to the internal heat exchanger. In the refrigerant circuit device, the ejector By adjusting the pressure amount, a timing at which the inside temperature of the heating cabinet reaches a preset heating off temperature, and a timing at which the inside temperature of the cooling cabinet reaches a preset cooling off temperature. A control means for matching is provided.

  Further, in the refrigerant circuit device according to the present invention, the control unit calculates a degree of heating at the heating chamber at a time when a temperature inside the cooling chamber exceeds the cooling off temperature, and calculates the heating attainment. The difference between the degree value and the predetermined heating achievement target value is calculated, the opening adjustment amount corresponding to the difference calculated from the table of the preset difference and the opening adjustment amount is obtained, and the current ejector The amount of pressure reduction is adjusted by adding the opening adjustment amount obtained to the opening.

  Further, in the refrigerant circuit device according to the present invention, the control means calculates a degree of achievement of cooling in the refrigerator and a degree of achievement of heating in the heating compartment, and calculates the difference between the calculated difference and the difference target. A deviation from the value is obtained, PID calculation is performed based on the deviation, and the opening amount of the ejector is adjusted to a set opening amount to adjust the amount of pressure reduction.

  According to the present invention, the control means adjusts the amount of decompression of the ejector, so that the timing at which the inside temperature of the heating cabinet reaches the preset heating off temperature and the inside temperature of the cooling cabinet are preset. Since the timing to reach the cooling off temperature is matched, driving of heating means such as a heater to heat the internal air of the heating chamber can be reduced, and power consumption can be reduced. There is an effect.

FIG. 1 is an explanatory diagram showing a case where the internal structure of a vending machine to which the refrigerant circuit device according to the first embodiment of the present invention is applied is viewed from the front. FIG. 2 is a cross-sectional side view of a vending machine to which the refrigerant circuit device according to Embodiment 1 of the present invention is applied. FIG. 3 is a conceptual diagram conceptually showing the refrigerant circuit device applied to the vending machine shown in FIGS. 1 and 2. FIG. 4 is an explanatory diagram showing a characteristic control system of the refrigerant circuit device shown in FIG. FIG. 5 is a schematic diagram of the ejector shown in FIG. FIG. 6 is an explanatory diagram illustrating an example of a table stored in the memory. FIG. 7 is a schematic diagram schematically showing the flow of the refrigerant in the CCC operation. FIG. 8 is a schematic diagram schematically showing the flow of the refrigerant in the HCC operation. FIG. 9 is a flowchart showing the processing contents of the cooling operation control process performed by the control unit shown in FIG. FIG. 10 is a flowchart showing the processing content of the heating operation control process performed by the control unit shown in FIG. FIG. 11 is a flowchart showing the processing contents of the ejector opening degree control processing performed by the control unit shown in FIG. FIG. 12 is an explanatory diagram showing a characteristic control system of the refrigerant circuit device according to the second embodiment of the present invention. FIG. 13 is a flowchart showing the processing contents of the ejector opening degree control processing performed by the control unit shown in FIG.

  Exemplary embodiments of a refrigerant circuit device according to the present invention will be explained below in detail with reference to the accompanying drawings.

<Embodiment 1>
1 and 2 each show a vending machine to which the refrigerant circuit device according to Embodiment 1 of the present invention is applied, and FIG. 1 is an explanatory diagram showing a case where the internal structure is viewed from the front, FIG. 2 is a sectional side view. The vending machine illustrated here includes a main body cabinet 1.

  The main body cabinet 1 is formed as a rectangular heat insulator having an open front surface. The main body cabinet 1 is provided with an outer door 2 and inner doors 3a and 3b on the front surface thereof, and three independent commodity storage boxes 5 partitioned by, for example, two heat insulating partition plates 4 in the left and right. It is provided in a side-by-side manner.

  More specifically, the outer door 2 is for opening and closing the front opening of the main body cabinet 1, and the inner doors 3 a and 3 b are for opening and closing the front surface of the commodity storage 5. The inner doors 3a and 3b are divided into upper and lower parts, and the upper door 3a opens and closes when a product is replenished. The commodity storage 5 is for storing commodities such as canned drinks and plastic bottled drinks while maintaining a desired temperature.

  The product storage 5 is provided with a product storage rack 6, a payout mechanism 7 and a carry-out shooter 8. The commodity storage rack 6 is for storing commodities in a manner arranged in the vertical direction. The payout mechanism 7 is provided in the lower part of the product storage rack 6 and is used to carry out the products at the lowest level of the product group stored in the product storage rack 6 one by one. The carry-out shooter 8 guides the product delivered from the delivery mechanism 7 to a product outlet (not shown) provided in the outer door 2 through a product outlet 3c provided in the lower inner door 3b. belongs to.

  FIG. 3 is a conceptual diagram conceptually showing the refrigerant circuit device applied to the vending machine shown in FIGS. 1 and 2, and FIG. 4 is a characteristic control system of the refrigerant circuit device shown in FIG. It is explanatory drawing which shows. The refrigerant circuit device illustrated here includes a refrigerant circuit 10 in which a refrigerant is sealed. The refrigerant circuit 10 includes a main path 20, a high-pressure refrigerant introduction path 30, and a return path 40. Yes.

  The main path 20 is configured by sequentially connecting a compressor 21, an external heat exchanger 22, an ejector 23, a gas-liquid separator 24, and an internal heat exchanger 25 through a refrigerant pipe 26.

  The compressor 21 is disposed in the machine room 9 as shown in FIG. The machine room 9 is a room inside the main body cabinet 1 and partitioned from the product storage 5 and below the product storage 5. The compressor 21 sucks the refrigerant through the suction port, compresses the sucked refrigerant to be in a high-temperature and high-pressure state (high-pressure refrigerant), and discharges it from the discharge port.

  The external heat exchanger 22 is disposed in the machine room 9 like the compressor 21, and includes a first external heat exchanger 22a and a second external heat exchanger 22b. In addition, an outside air blower fan F1 is disposed in the vicinity of the outside heat exchanger 22.

  When the refrigerant compressed by the compressor 21 passes through its own flow path, the first external heat exchanger 22a exchanges heat with ambient air to dissipate heat. A three-way valve 271 is provided in the refrigerant pipe 26 that connects the external heat exchanger 22 and the compressor 21. The three-way valve 271 will be described later.

  The second external heat exchanger 22b is integrated with the first external heat exchanger 22a in a state where the fin member thermally connected to the flow path of the second external heat exchanger 22b is shared with the first external heat exchanger 22a. It is structured. The second external heat exchanger 22b is configured to dissipate heat by exchanging heat between the refrigerant passing through the flow path, that is, the heat dissipated by the first external heat exchanger 22a, with the ambient air.

  Although details will be described later, the ejector 23 reduces the pressure of the high-pressure refrigerant (high-pressure refrigerant) radiated by the external heat exchanger 22 (second external heat exchanger 22b) by the internal heat exchanger 25. The discharged low-pressure refrigerant (low-pressure refrigerant) is sucked, and the sucked low-pressure refrigerant is mixed with the high-pressure refrigerant from the external heat exchanger 22 and is discharged after being pressurized. As shown in FIG. 5, the ejector 23 according to the first embodiment is a two-phase flow ejection type ejector, and includes a nozzle portion 231, a mixing portion 232, and a diffuser portion 233.

  The nozzle part 231 is a part that depressurizes and accelerates the high-pressure refrigerant from the external heat exchanger 22 sucked through the high-pressure refrigerant introduction port 234. By accelerating the high-pressure refrigerant in this way, the low-pressure refrigerant discharged from the internal heat exchanger 25 through the refrigerant suction port 235 can be sucked. The nozzle portion 231 is provided with a nozzle valve 231a. The nozzle valve 231a is a valve body for adjusting the nozzle diameter for depressurizing the high-pressure refrigerant. That is, the opening degree of the ejector 23 can be adjusted by driving the nozzle valve 231a.

  The mixing unit 232 is a part that mixes the high-pressure refrigerant accelerated by the nozzle unit 231 and the low-pressure refrigerant sucked through the refrigerant suction port 235.

  The diffuser unit 233 is a part that pressurizes the refrigerant (mixed refrigerant) mixed in the mixing unit 232. The pressurized mixed refrigerant is discharged toward the gas-liquid separator 24.

  The gas-liquid separator 24 separates the mixed refrigerant discharged from the ejector 23 into a gas-phase refrigerant and a liquid-phase refrigerant. The gas-phase refrigerant separated by the gas-liquid separator 24 is sucked into the compressor 21, while the separated liquid-phase refrigerant is discharged to the internal heat exchanger 25.

  A plurality (three in the illustrated example) of the internal heat exchangers 25 are provided, and each of the internal heat exchangers 25 is disposed on the front side of the rear duct D in the low internal area of each commodity storage 5. In the vicinity of each internal heat exchanger 25, an internal air blower fan F2 is disposed.

  The refrigerant conduit 26 connecting the internal heat exchanger 25 and the gas-liquid separator 24 is branched into three by a distributor 28 disposed in the middle thereof, and the right commodity storage 5 (hereinafter, right side). The internal heat exchanger 25 (hereinafter also referred to as the right internal heat exchanger 25a) disposed in the storage 5a) and the central product storage 5 (hereinafter also referred to as the internal storage 5b). In-compartment heat exchanger 25 (hereinafter, also referred to as “inside-compartment heat exchanger 25b”) and in-compartment heat exchanger 25 (hereinafter, “left”) disposed in the left product storage 5 (hereinafter also referred to as “left-compartment 5c”) It is respectively connected to the inlet side of the internal heat exchanger 25c).

  In the refrigerant pipe 26, an electromagnetic valve 272 is provided on the way from the distributor 28 to the left-inside heat exchanger 25c. The electromagnetic valve 272 is a valve body that opens and closes in response to a command given from the control unit 50 described later.

  The refrigerant pipes 26 connected to the respective outlet sides of the internal heat exchanger 25 are connected to the ejector 23 in such a manner that they merge at the first junction P1 and communicate with the refrigerant inlet 235 of the ejector 23. Has been.

  The high-pressure refrigerant introduction path 30 is configured by a high-pressure refrigerant introduction pipe 31 having one end connected to the three-way valve 271 and the other end connected to the inlet side of the heating heat exchanger 32 disposed in the left warehouse 5c. ing. The high-pressure refrigerant introduction path 30 is for introducing the high-pressure refrigerant compressed by the compressor 21 into the heating heat exchanger 32.

  Here, the three-way valve 271 is between a first delivery state in which the high-pressure refrigerant compressed by the compressor 21 is delivered to the first external heat exchanger 22a and a second delivery state in which the high-pressure refrigerant is delivered to the heating heat exchanger 32. The valve body can be switched alternatively. The switching operation of the three-way valve 271 is performed according to a command given from the control unit 50.

  The return path 40 has one end connected to the outlet side of the heating heat exchanger 32 and the other end connected to the refrigerant pipe 26 constituting the main path 20, that is, the first external heat exchanger 22a and the second external heat. It is comprised by the return line 41 connected to the 2nd junction P2 of the refrigerant line 26 between the exchangers 22b. The return path 40 is for returning the refrigerant that has passed through the heating heat exchanger 32 to the main path 20. In addition, the code | symbol 42 in FIG. 3 is a check valve.

  The refrigerant circuit device as described above includes the input unit 100, the internal temperature sensor S1, and the control unit 50 in addition to the above configuration.

  The input unit 100 is for performing various setting inputs such as a remote controller, for example, and the information set and input here is given to the control unit 50.

  The in-compartment temperature sensor S1 is disposed inside each commodity storage 5 and detects the internal temperature (internal temperature) of the commodity storage 5 in which it is disposed. The internal temperature detected by the internal temperature sensor S1 is given to the control unit 50 as an internal temperature signal.

  The control unit 50 controls the compressor 21, the ejector 23, the three-way valve 271, and the electromagnetic valve 272 constituting the refrigerant circuit device in accordance with programs and data stored in the memory 60. The input processing unit 51, valve drive A processing unit 52, a compressor operation control unit 53, and an ejector control unit 54 are provided.

  The input processing unit 51 performs input processing of commands and signals given from the input means 100 and the internal temperature sensors S1. The valve drive processing unit 52 controls the drive of the electromagnetic valve 272 and the three-way valve 271.

  The compressor operation control unit 53 includes a temperature determination unit 531 and a compressor drive processing unit 532. The temperature determination unit 531 is the internal temperature given by the internal temperature sensor S1 provided inside the commodity storage (cooling storage) 5 to be cooled, that is, the internal temperature detected by the internal temperature sensor S1. It is determined whether or not the temperature is within the target cooling temperature range, and the internal temperature given from the internal temperature sensor S1 disposed inside the commodity storage (heating storage) 5 to be heated, that is, It is determined whether or not the internal temperature detected by the internal temperature sensor S1 is within the target heating temperature range.

  More specifically, as to whether or not the internal temperature of the refrigerator 5 is in the cooling temperature range, whether or not the detected internal temperature is lower than the cooling off temperature or the detected internal temperature is cooled. It is determined whether or not the ON temperature is exceeded. Further, as to whether or not the internal temperature of the heating chamber 5 is in the heating temperature range, whether or not the detected internal temperature is lower than the heating on temperature, or the detected internal temperature exceeds the heating off temperature. Whether or not. The cooling off temperature, the cooling on temperature, the heating on temperature, and the heating off temperature used in the temperature determination unit 531 are stored in the memory 60.

  The compressor drive processing unit 532 gives a drive command or a drive stop command to the compressor 21 to drive or stop the compressor 21 at a predetermined rotational speed.

  The ejector control unit 54 includes a calculation unit 541, a calculation unit 542, an opening adjustment amount determination unit 543, and an ejector drive processing unit 544.

  The calculation unit 541 calculates the degree of heating (ηh) in the heating chamber 5 at the time when the internal temperature of the cooling chamber 5 exceeds the cooling off temperature by the following equation (1).

Formula (1)
ηh = (Th−Thi) / (Ths−Thi)
(Here, Th is the internal temperature of the heating chamber 5, Thi is the heating on temperature, and Ths is the heating off temperature.)

  The calculation unit 542 calculates a difference (dη) between the value of the heating achievement calculated through the calculation unit 541 and the heating achievement target value (ηt = 1) stored in the memory 60.

  The opening adjustment amount determination unit 543 reads a table of the difference and the opening adjustment amount as shown in FIG. 6 from the memory 60, and determines the opening adjustment amount from the table and the difference calculated through the calculation unit 542. Is. FIG. 6 shows an example of a table, where a, b, α, and β are numbers greater than 0, and a relationship of a <b and α <β is established.

  The ejector drive processing unit 544 sets the opening degree of the ejector 23 by adding the opening degree adjustment amount determined through the opening degree adjustment amount determination unit 543 to the current opening degree of the ejector 23 to set a new opening degree of the ejector 23. Is given to the ejector 23.

  In the refrigerant circuit device as described above, the internal temperature of each commodity storage 5 can be adjusted to a desired temperature state by controlling the three-way valve 271 and the electromagnetic valve 272 through the control unit 50. Thus, the product stored in the product storage 5 can be cooled or heated. Here, in the case of performing the CCC operation (operation for cooling the internal air of all the product containers 5) and the HCC operation (heating the internal air of the left warehouse 5c and cooling the internal air of the right warehouse 5a and the middle warehouse 5b). The case where the operation is performed will be described as a representative example.

  First, the case where the CCC operation is performed will be described. In this case, the control unit 50 brings the three-way valve 271 to the first delivery state and opens the electromagnetic valve 272.

  As a result, the refrigerant compressed by the compressor 21 passes through the three-way valve 271 in the first delivery state and reaches the first external heat exchanger 22a, as shown in FIG. The refrigerant that has reached the first external heat exchanger 22a performs heat exchange with ambient air (outside air) while passing through the first external heat exchanger 22a, and dissipates heat. The refrigerant radiated by the first external heat exchanger 22a reaches the second external heat exchanger 22b, and further exchanges heat with ambient air while passing through the second external heat exchanger 22b. The refrigerant radiated by the second external heat exchanger 22b is sent to the ejector 23.

  The refrigerant (high-pressure refrigerant) sent to the ejector 23 enters the nozzle portion 231 through the high-pressure refrigerant introduction port 234 and is accelerated by being decompressed. As a result, the refrigerant (low-pressure refrigerant) that has passed through the internal heat exchanger 25 is sucked through the refrigerant suction port 235. Then, in the mixing unit 232 of the ejector 23, the accelerated high-pressure refrigerant and the sucked low-pressure refrigerant are mixed to become a mixed refrigerant and reach the diffuser unit 233, and the mixed refrigerant is pressurized by the diffuser unit 233. After being discharged.

  The mixed refrigerant discharged from the ejector 23 is sent to the gas-liquid separator 24, and is separated into a gas-phase refrigerant and a liquid-phase refrigerant by the gas-liquid separator 24. The separated gas phase refrigerant is sucked into the compressor 21. On the other hand, the separated liquid phase refrigerant is sent to each internal heat exchanger 25 via the distributor 28.

  The refrigerant (low-pressure refrigerant) sent to each internal heat exchanger 25 passes through a refrigerant flow path (not shown) and exchanges heat with ambient air (internal air) to cool the ambient air. The cooled air circulates in the interior by driving the internal blower fan F2 disposed in the vicinity of each internal heat exchanger 25, whereby the products stored in each product storage 5 are cooled by the circulating air. Is done.

  The refrigerant that has passed through each of the internal heat exchangers 25 joins at the first junction P1, and then is sucked into the refrigerant suction port 235 of the ejector 23 by the suction force generated when the high-pressure refrigerant is depressurized and accelerated in the ejector 23. It reaches. In this way, the refrigerant repeats the cycle of circulating through the refrigerant circuit 10.

  Next, a case where the HCC operation is performed will be described. In this case, the control unit 50 puts the three-way valve 271 in the second delivery state and closes the electromagnetic valve 272.

  As a result, as shown in FIG. 8, the refrigerant compressed by the compressor 21 passes through the three-way valve 271 in the second delivery state, and is sent to the heating heat exchanger 32 through the high-pressure refrigerant introduction pipe 31.

  The refrigerant (high-pressure refrigerant) sent to the heating heat exchanger 32 passes through a refrigerant channel (not shown), exchanges heat with ambient air (internal air), and condenses to heat the ambient air. The heated air circulates in the interior by driving the internal blower fan F2, and thereby the product stored in the left compartment 5c is heated by the circulating air.

  The refrigerant that has passed through the heat exchanger 32 for heating reaches the second junction P2 after passing through the return pipe 41, and enters the main path 20 at the second junction P2. The refrigerant that has entered the main path 20 passes through the second external heat exchanger 22b. While passing through the second external heat exchanger 22b, heat is exchanged with ambient air to dissipate heat. The refrigerant radiated by the second external heat exchanger 22b is sent to the ejector 23.

  The refrigerant (high-pressure refrigerant) sent to the ejector 23 enters the nozzle portion 231 through the high-pressure refrigerant introduction port 234 and is accelerated by being decompressed. As a result, the refrigerant (low-pressure refrigerant) that has passed through the internal heat exchanger 25 is sucked through the refrigerant suction port 235. Then, in the mixing unit 232 of the ejector 23, the accelerated high-pressure refrigerant and the sucked low-pressure refrigerant are mixed to become a mixed refrigerant and reach the diffuser unit 233, and the mixed refrigerant is pressurized by the diffuser unit 233. After being discharged.

  The mixed refrigerant discharged from the ejector 23 is sent to the gas-liquid separator 24, and is separated into a gas-phase refrigerant and a liquid-phase refrigerant by the gas-liquid separator 24. The separated gas phase refrigerant is sucked into the compressor 21. On the other hand, the separated liquid phase refrigerant is sent to the right internal heat exchanger 25a and the internal internal heat exchanger 25b via the distributor 28.

  The refrigerant (low-pressure refrigerant) sent to the right-side internal heat exchanger 25a passes through a refrigerant flow path (not shown) and exchanges heat with ambient air (internal air) to cool the ambient air. The cooled air circulates in the interior by driving the internal blower fan F2 disposed in the vicinity of the right internal heat exchanger 25a, whereby the product stored in the right internal 5a is cooled by the circulating air. .

  The refrigerant (low-pressure refrigerant) sent to the internal heat exchanger 25b passes through a refrigerant flow path (not shown) and exchanges heat with ambient air (internal air) to cool the ambient air. The cooled air circulates in the interior by driving the internal blower fan F2 disposed in the vicinity of the internal heat exchanger 25b, whereby the product stored in the internal store 5b is cooled by the circulating air. .

  After the refrigerant that has passed through the right internal heat exchanger 25a and the internal internal heat exchanger 25b joins at the first junction P1, the suction force generated by the high pressure refrigerant being depressurized and accelerated in the ejector 23, It reaches the refrigerant suction port 235 of the ejector 23. In this way, the refrigerant repeats the cycle of circulating through the refrigerant circuit 10.

  In the refrigerant circuit device that performs such an HCC operation, the control unit 50 individually performs the cooling operation control process and the heating operation control process. In addition, when performing CCC operation, only cooling operation control processing is performed.

  FIG. 9 is a flowchart showing the processing content of the cooling operation control process performed by the control unit shown in FIG. 4, and FIG. 10 shows the processing content of the heating operation control process performed by the control unit shown in FIG. It is a flowchart.

  In the cooling operation control process shown in FIG. 9, the internal temperature sensor S1 (in the case of HCC operation, the internal temperature sensor S1 of the right compartment 5a and the central compartment 5b) while the compressor 21 is being driven is input. When the internal temperature is respectively input from the compressor (step S101: Yes, step S102: Yes), the compressor operation control unit 53 of the control unit 50 reads out information related to the cooling off temperature from the memory 60 through the temperature determination unit 531 and starts. The cooling off temperature and each internal temperature are compared, and it is determined whether or not each internal temperature is lower than the cooling off temperature (step S103).

  When the internal temperature is lower than the cooling off temperature (step S103: Yes), the compressor operation control unit 53 of the control unit 50 gives a drive stop command to the compressor 21 through the compressor drive processing unit 532 to stop driving. (Step S104), then the procedure is returned to end the current process.

  According to this, the cooling with respect to the internal air of the right warehouse 5a and the middle warehouse 5b is stopped, and it changes in the direction where the internal temperature rises. In this case, since the refrigerant does not flow into the heating heat exchanger 32, the internal air of the left chamber 5c is not heated by the heating heat exchanger 32.

  When the internal temperature is not lower than the cooling off temperature (step S103: No), that is, when the internal temperature is equal to or higher than the cooling off temperature, the compressor operation control unit 53 of the control unit 50 instructs the compressor 21. The compressor 21 is kept driven (step S105), and then the procedure is returned to end the current process.

  According to this, as a result of the refrigerant evaporating in the right internal heat exchanger 25a and the internal internal heat exchanger 25b, the cooling of the internal air of the right internal 5a and the internal 5b is continued, and the internal temperature is It moves in the direction of decline. In this case, as a result of the refrigerant condensing also in the heating heat exchanger 32, the heating of the internal air of the left warehouse 5c is continued, and the internal temperature of the left warehouse 5c is increased.

  On the other hand, when the internal temperature is input from the internal temperature sensor S1 (the internal temperature sensor S1 of the right compartment 5a and the central compartment 5b) through the input processing unit 51 in a state where the compressor 21 is not driven (step S101: No, Step S106: Yes), the compressor operation control unit 53 of the control unit 50 reads out information related to the cooling on temperature from the memory 60 through the temperature determination unit 531, and compares the cooling on temperature with the internal temperature of each chamber. Then, it is determined whether or not the internal temperature exceeds the cooling on temperature (step S107).

  When the internal temperature exceeds the cooling on temperature (step S107: Yes), the compressor operation control unit 53 of the control unit 50 gives a drive command to the compressor 21 through the compressor drive processing unit 532 to drive it (step S108). ) And then return the procedure to end the current process.

  According to this, as a result of the refrigerant evaporating in each of the right compartment heat exchanger 25a and the middle compartment heat exchanger 25b, the internal air of each of the right compartment 5a and the middle compartment 5b is cooled, and the inside temperature decreases. Transition in the direction. In this case, as a result of the refrigerant condensing also in the heat exchanger 32 for heating, the internal air of the left warehouse 5c is heated, and the internal temperature of the left warehouse 5c is increased.

  When the internal temperature does not exceed the cooling on temperature (step S107: No), that is, when the internal temperature is equal to or lower than the cooling on temperature, the compressor operation control unit 53 of the control unit 50 controls the compressor 21. The drive stop of the compressor 21 is maintained without giving a command (step S109), and then the procedure is returned to end the current process.

  According to this, internal air is not cooled in each of the heat exchanger 25a in the right warehouse and the heat exchanger 25b in the middle warehouse, and the respective interior temperatures of the right warehouse 5a and the middle warehouse 5b are increased. Transition to. In this case, the internal air of the left warehouse 5c is not heated by the heating heat exchanger 32.

  In the heating operation control process shown in FIG. 10, the internal temperature from the internal temperature sensor S <b> 1 (in the case of HCC operation, the internal temperature sensor S <b> 1 of the left compartment 5 c) through the input processing unit 51 while the compressor 21 is driven. Is input (step S111: Yes, step S112: Yes), the compressor operation control unit 53 of the control unit 50 reads out information related to the heating off temperature from the memory 60 through the temperature determination unit 531, and the heating off temperature and the warehouse. The internal temperature is compared to determine whether or not the internal temperature exceeds the heating off temperature (step S113).

  When the internal temperature exceeds the heating off temperature (step S113: Yes), the compressor operation control unit 53 of the control unit 50 gives a drive stop command to the compressor 21 through the compressor drive processing unit 532 to stop driving. (Step S114), then the procedure is returned to end the current process.

  According to this, the heating with respect to the internal air of the left warehouse 5c is stopped, and it changes in the direction in which the internal temperature falls. In this case, since the refrigerant does not flow into the right warehouse 5a and the middle warehouse 5b, the internal air of the right warehouse 5a and the middle warehouse 5b is not cooled by the internal heat exchanger 25.

  When the internal temperature does not exceed the heating off temperature (step S113: No), that is, when the internal temperature is equal to or lower than the heating off temperature, the compressor operation control unit 53 of the control unit 50 instructs the compressor 21. Is maintained (step S115), and then the procedure is returned to end the current process.

  According to this, as a result of the refrigerant condensing in the left-side warehouse heat exchanger 25c, the heating of the internal air of the left-side warehouse 5c is continued, and the temperature inside the warehouse rises. In this case, as a result of the refrigerant evaporating also in the right compartment heat exchanger 25a and the middle compartment heat exchanger 25b, the cooling of the internal air of the right compartment 5a and the middle compartment 5b is continued, and the right compartment 5a and the middle compartment 5b are stored. The internal temperature changes in a decreasing direction.

  On the other hand, when the internal temperature is input from the internal temperature sensor S1 (internal temperature sensor S1 of the left storage 5c) through the input processing unit 51 in a state where the compressor 21 is not driven (Step S111: No, Step S116: Yes), the compressor operation control unit 53 of the control unit 50 reads the information about the heating on temperature from the memory 60 through the temperature determination unit 531, compares the heating on temperature with the inside temperature, and the inside temperature is heated on. It is determined whether the temperature falls below (step S117).

  When the internal temperature is lower than the heating on temperature (step S117: Yes), the compressor operation control unit 53 of the control unit 50 gives a drive command to the compressor 21 through the compressor drive processing unit 532 to drive it (step S118). ) And then return the procedure to end the current process.

  According to this, as a result of the refrigerant condensing in the heat exchanger 32 for heating, the internal air of the left warehouse 5c is heated, and the internal temperature is changed in a rising direction. In this case, as a result of the refrigerant evaporating in each of the right internal heat exchanger 25a and the internal internal heat exchanger 25b, the internal air of each of the right internal 5a and the internal 5b is cooled, and the internal temperature decreases. Transition.

  When the internal temperature does not fall below the heating-on temperature (step S117: No), that is, when the internal temperature is equal to or higher than the heating-on temperature, the compressor operation control unit 53 of the control unit 50 controls the compressor 21. The drive stop of the compressor 21 is maintained without giving a command (step S119), and then the procedure is returned to end the current process.

  According to this, the internal air is not heated in the heat exchanger 32 for heating, and the internal temperature of the left compartment 5c changes in the direction of decreasing. In this case, the internal air of the right compartment 5a and the middle compartment 5b is not cooled by the right compartment internal heat exchanger 25a and the middle compartment heat exchanger 25b.

  As described above, when the HCC operation is performed, the cooling operation control process and the heating operation control process are performed, but actually, the internal temperature of the left chamber 5c reaches the heating on temperature and the heating off temperature. Since the temperature inside the right warehouse 5a and the middle warehouse 5b reaches the cooling on temperature or the cooling off temperature earlier, the cooling operation control process is generally prioritized over the heating operation control process. It is.

  Then, when such a cooling operation control process is performed, the refrigerant circuit device performs the following ejector opening degree control process when the inside temperature of the refrigerator 5 exceeds the cooling off temperature.

  FIG. 11 is a flowchart showing the processing contents of the ejector opening degree control processing performed by the control unit shown in FIG.

  In this ejector opening degree control process, the ejector control unit 54 of the control unit 50 heats through the calculation unit 541 when the internal temperature (Th) of the left chamber (heating chamber) 5c is input through the input processing unit 51 (step S201). The degree of achievement is calculated by the above equation (1) (step S202).

  The ejector control unit 54 that has calculated the heating achievement degree reads the heating achievement target value from the memory 60 through the calculation unit 542, and the difference between the heating achievement value calculated through the calculation unit 541 and the heating achievement target value ( dη) is calculated (step S203).

  The ejector control unit 54 having calculated the difference (dη) reads the table from the memory 60 through the opening adjustment amount determination unit 543, and determines the opening adjustment amount from the table and the difference (dη) calculated through the calculation unit 542. (Step S204). In the example shown in FIG. 6, the opening adjustment amount determination unit 543 determines any opening adjustment amount of + β, + α, 0, −α, and −β.

  The ejector control unit 54 that has determined the opening adjustment amount in this way determines the opening adjustment amount determined through the opening adjustment amount determination unit 543 with respect to the current opening of the ejector 23 through the ejector drive processing unit 544. (+ Β, + α, 0, -α, -β) are added to set the opening of the new ejector 23, and the opening command is sent to the ejector 23 as a command signal (step S205). Return and end the current process.

  Here, the processing in step S205 will be described in detail. When the opening adjustment amount determined in step S204 is “0”, the current opening of the ejector 23 is maintained. When the opening adjustment amount determined in step S204 is “+ α” or “+ β”, the opening of the ejector 23 is increased by the opening adjustment amount from the current opening of the ejector 23. In this case, the pressure reduction amount of the ejector 23 is reduced, and the flow rate of the high-pressure refrigerant in the nozzle portion 231 is reduced. Therefore, the suction amount of the low-pressure refrigerant decreases, and the heating capacity increases while the cooling capacity decreases. If the opening adjustment amount determined in step S204 is “−α” or “−β”, the opening degree of the ejector 23 is decreased by the opening adjustment amount from the current opening degree of the ejector 23; Become. In this case, the pressure reduction amount of the ejector 23 is increased, and the flow rate of the high-pressure refrigerant at the nozzle portion 231 is increased. Therefore, the suction amount of the low-pressure refrigerant increases, and the cooling capacity increases while the heating capacity decreases.

  Such an ejector opening degree control process is repeatedly performed at the time when the inside temperature of the refrigerator 5 exceeds the cooling-off temperature in the cooling operation control process, so that the heating capacity according to the ratio between the heating load and the cooling load. And the cooling capacity can be adjusted.

  As described above, according to the refrigerant circuit device according to the first embodiment, the controller 50 opens the ejector each time the inside temperature of the right compartment (cooling compartment) 5a or the like exceeds the cooling off temperature. By performing the degree control process, the heating capacity and the cooling capacity can be adjusted according to the ratio between the heating load and the cooling load, and the internal temperature of the left chamber (heating chamber) 5c reaches the heating off temperature. The timing can coincide with the timing at which the inside temperature of the right compartment (cooling compartment) 5a or the like reaches the cooling off temperature. As a result, it is possible to reduce driving of heating means such as a heater to heat the internal air of the left chamber (heating chamber) 5c, and power consumption can be reduced.

  According to the refrigerant circuit device, since the ejector 23 is used as the expansion mechanism, the vortex energy that has been lost in the conventional electronic expansion valve or the like can be recovered, thereby reducing the power consumption. Can do.

<Embodiment 2>
FIG. 12 is an explanatory diagram showing a characteristic control system of the refrigerant circuit device according to the second embodiment of the present invention. In the following, only the components different from the refrigerant circuit device of the first embodiment described above will be described, and the same components as those of the refrigerant circuit device will be denoted by the same reference numerals and description thereof will be omitted. .

  In the refrigerant circuit device according to the second embodiment of the present invention, the control unit 50 ′ is different from the refrigerant circuit device according to the first embodiment.

  The control unit 50 ′ controls the compressor 21, the ejector 23, the three-way valve 271, and the electromagnetic valve 272 that constitute the refrigerant circuit device in accordance with programs and data stored in the memory 61, and includes an input processing unit 51, a valve A drive processing unit 52, a compressor operation control unit 53, and an ejector control unit 55 are provided.

  The ejector control unit 55 includes a calculation unit 551, a calculation unit 552, an opening setting unit 553, and an ejector drive processing unit 554.

  The calculation unit 551 uses the internal temperature of the refrigerator 5 and the internal temperature of the heating chamber 5 that are input through the input processing unit 51 to calculate the degree of cooling (ηc) by the following formula (2) and the following formula (3). And the degree of heating achievement (ηh) is calculated.

Formula (2)
ηc = (Tc−Tci) / (Tcs−TCi)
(Here, Tc is the internal temperature of the refrigerator 5, Tci is the cooling on temperature, and Tcs is the cooling off temperature.)

Formula (3)
ηh = (Th−Thi) / (Ths−Thi)
(Here, Th is the internal temperature of the heating chamber 5, Thi is the heating on temperature, and Ths is the heating off temperature.)

  The calculation unit 552 calculates the difference (dη) between the degree of cooling achievement and the degree of heating calculated through the calculation unit 551 by the following equation (4).

Formula (4)
dη = ηh−ηc

  The opening setting unit 553 calculates a deviation between the difference calculated through the calculation unit 552 and the difference target value read from the memory 61, and performs PID calculation based on the deviation.

  The ejector drive processing unit 554 gives an opening amount corresponding to the calculation result of the opening setting unit 553 to the ejector 23 as a command signal.

  In the refrigerant circuit device having the above-described configuration, the following ejector opening degree control process is performed at a predetermined timing when the compressor 21 is driven in the cooling operation control process.

  FIG. 13 is a flowchart showing the processing contents of the ejector opening degree control processing performed by the control unit shown in FIG.

  In this ejector opening degree control process, the ejector control unit 55 of the control unit 50 ′ inputs the internal temperatures (Th, Tc) of the left warehouse (heating cabinet) 5 c and the right warehouse (cooling cabinet) 5 a through the input processing unit 51. In the case (step S301), the cooling achievement and the heating achievement are calculated by the above formulas (2) and (3) through the calculation unit 551 (step S302).

  The ejector control unit 55 that has calculated the cooling achievement and the heating achievement calculates the difference (dη) between the cooling achievement and the heating achievement through the calculation unit 552 according to the above equation (4) (step S303).

  The ejector control unit 55 that has calculated the difference (dη) reads the difference target value (“0”) from the memory 61 through the opening setting unit 553 (step S304), and uses the opening setting unit 553 to calculate the difference and the difference target value. And a PID calculation is performed based on the deviation (step S305).

  The ejector control unit 55 that has performed the PID calculation sends the opening amount according to the calculation result to the ejector 23 as a command signal through the ejector drive processing unit 554 (step S306), and then returns the procedure to end the current process. To do.

  According to this, the opening amount of the ejector 23 is set so that the difference (dη) becomes the difference target value (“0”), and the pressure reduction amount is adjusted.

  As described above, according to the refrigerant circuit device of the second embodiment, the control unit 50 ′ performs the ejector opening degree control process at a predetermined timing, so that the degree of cooling achievement and the degree of heating achievement are reduced. The opening amount of the ejector 23 is set so that the difference (dη) becomes the difference target value (“0”), and the amount of pressure reduction is adjusted. As a result, the inside temperature of the left compartment (heating compartment) 5c becomes the heating off temperature. And the timing at which the inside temperature of the right compartment (cooling compartment) 5a or the like reaches the cooling off temperature can be matched. Therefore, it is possible to reduce driving of heating means such as a heater to heat the internal air of the left chamber (heating chamber) 5c, and power consumption can be reduced.

  According to the refrigerant circuit device, since the ejector 23 is used as the expansion mechanism, the vortex energy that has been lost in the conventional electronic expansion valve or the like can be recovered, thereby reducing the power consumption. Can do.

  The preferred embodiment 1 and embodiment 2 of the present invention have been described above, but the present invention is not limited to these, and various modifications can be made.

  In Embodiment 1 and Embodiment 2 described above, the liquid-phase refrigerant separated by the gas-liquid separator 24 is sent to the internal heat exchanger 25. However, in the present invention, the liquid-phase refrigerant is separated by the gas-liquid separator. The liquid-phase refrigerant thus made may be adiabatically expanded by an expansion mechanism such as an electronic expansion valve and then sent to the internal heat exchanger.

DESCRIPTION OF SYMBOLS 10 Refrigerant circuit 20 Main path | route 21 Compressor 22 External heat exchanger 23 Ejector 24 Gas-liquid separator 25 Internal heat exchanger 271 Three-way valve 272 Solenoid valve 30 High-pressure refrigerant introduction path 31 High-pressure refrigerant introduction pipe 32 Heat exchange for heating 40 Return path 41 Return line 50 Control unit 51 Input processing unit 52 Valve drive processing unit 53 Compressor operation control unit 531 Temperature determination unit 532 Compressor drive processing unit 54 Ejector control unit 541 Calculation unit 542 Calculation unit 543 Opening adjustment Quantity determination unit 544 Ejector drive processing unit 60 Memory S1 Internal temperature sensor

Claims (3)

A compressor for compressing the sucked refrigerant;
A heat exchanger for heating, which is disposed inside the heating chamber to be heated, and heats the internal air of the heating chamber by dissipating the supplied refrigerant,
An internal heat exchanger that is disposed inside a refrigerator to be cooled and evaporates the supplied refrigerant to cool the internal air of the refrigerator;
An ejector that sucks the refrigerant that has passed through the internal heat exchanger by depressurizing the refrigerant that has dissipated heat in the heating heat exchanger, and mixes and discharges the refrigerant;
Gas-liquid separation means for separating the refrigerant supplied from the ejector into a gas-phase refrigerant and a liquid-phase refrigerant, and sucking the gas-phase refrigerant into the compressor, while supplying the liquid-phase refrigerant to the internal heat exchanger; In a refrigerant circuit device comprising a refrigerant circuit having
By adjusting the amount of decompression of the ejector, the timing at which the inside temperature of the heating cabinet reaches a preset heating off temperature, and the inside temperature of the cooling cabinet reaches a preset cooling off temperature. A refrigerant circuit device comprising control means for matching timing.   The control means calculates the degree of heating achieved in the heating chamber at the time when the temperature inside the refrigerator exceeds the cooling off temperature, and calculates the value of the calculated degree of heating and a predetermined degree of heating achieved. Calculate the difference from the target value, obtain the opening adjustment amount according to the difference calculated from the table of preset difference and opening adjustment amount, and add the obtained opening adjustment amount to the current ejector opening The refrigerant circuit device according to claim 1, wherein the pressure reduction amount is adjusted.   The control means calculates a degree of cooling achievement in the refrigerator and a degree of heating achievement in the heating compartment, calculates a difference between them, obtains a deviation between the calculated difference and a difference target value, and based on the deviation The refrigerant circuit device according to claim 1, wherein the decompression amount is adjusted by adjusting the opening degree of the ejector to an opening amount set by performing PID calculation.

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