JP2011181001A - Refrigerant circulation device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigerant circulation device allowing suppression of reduction of cooling performance of an evaporator by dehumidifying a chamber disposed with the evaporator. <P>SOLUTION: This refrigerant circulation device includes a refrigerant circulation circuit 10 configured by sequentially connecting: a compressor 21 compressing a refrigerant; a box outside heat exchanger 22 condensing the refrigerant compressed in the compressor 21; a first capillary tube 23 adiabatically expanding the refrigerant condensed in the box outside heat exchanger 22; and an in-box heat exchanger 24 evaporating the refrigerant adiabatically expanded in the first capillary tube 23. The refrigerant circulation device includes a controller 70 performing dehumidification operation to reduce a drive amount of an in-box fan F1 disposed inside a commodity storage 3 for a prescribed time while driving the compressor 21 when reaching a predetermined time point, and to stop the driving of the compressor 21 while driving the in-box fan F1 after the prescribed time lapses. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a refrigerant circulation device, and more particularly to a refrigerant circulation device that is applied to, for example, a vending machine and cools an internal atmosphere of a product storage box defined in a vending machine body. .

  2. Description of the Related Art Conventionally, as a refrigerant circulation device applied to, for example, a vending machine, a refrigerant circulation device having a function as a heat pump and a controller are known. Such a refrigerant circuit generally has a cooling path and a heating path.

  The cooling path is configured by sequentially connecting an evaporator, a compressor, a condenser, and an expansion mechanism through a refrigerant pipe. The evaporator is disposed inside the commodity storage of the vending machine. This evaporator cools the internal air (internal atmosphere) of the product storage box by the supplied refrigerant passing through a predetermined flow path and evaporating.

  The compressor is disposed in the machine room inside the vending machine main body and outside the product container. The compressor sucks the refrigerant evaporated by the evaporator and compresses the sucked refrigerant into a high temperature and high pressure state. Are discharged. The condenser is disposed in the machine room in the same manner as the compressor, introduces the refrigerant compressed by the compressor through the refrigerant pipe, and heats the ambient air by condensing the introduced refrigerant, that is, into the ambient air. It dissipates heat. The expansion mechanism is disposed in the machine room in the same manner as the compressor and the condenser, and decompresses the refrigerant condensed in the condenser and adiabatically expands the refrigerant.

  The heating path is a path having an internal heat exchanger. The internal heat exchanger is disposed inside the commodity storage. In more detail, it is arrange | positioned inside the goods storage container which accommodates the goods used as the heating object. This internal heat exchanger has an inlet side connected to a branch pipe branched from a refrigerant pipe connecting a compressor and a condenser constituting a cooling path, and a refrigerant pipe connecting a condenser and an expansion mechanism. An outlet side is connected to a return pipe provided in a mode of joining. Such an in-compartment heat exchanger heats the internal air of the product storage container in which the refrigerant is compressed by introducing the refrigerant compressed by the compressor through the branch pipe and condensing the introduced refrigerant.

  In such a refrigerant circulation circuit, when the refrigerant compressed by the compressor flows in each of the cooling path and the heating path, the refrigerant flowing in the cooling path among the refrigerant compressed by the compressor reaches the condenser, and the condensation The condensed refrigerant is adiabatically expanded by the expansion mechanism and evaporated by the evaporator. The refrigerant evaporated in the evaporator is sucked by the compressor, compressed again, and circulated. As a result, the internal air of the product storage (cooler) in which the evaporator is disposed is cooled.

  On the other hand, the refrigerant flowing through the heating path among the refrigerant compressed by the compressor reaches the internal heat exchanger through the branch pipe, and condenses in the internal heat exchanger. Thereby, the internal air of the product storage (heating chamber) in which the internal heat exchanger is disposed is heated. The refrigerant condensed in the internal heat exchanger returns to the cooling path through the return pipe, is adiabatically expanded by the expansion mechanism, is evaporated by the evaporator, is sucked into the compressor, is compressed again, and is circulated.

  The controller is for controlling the drive of the compressor. When the temperature inside the product storage box in which the evaporator is disposed exceeds a predetermined cooling on temperature, or the heat exchanger in the box is arranged. The compressor is driven when the inside temperature of the installed product storage is below a predetermined heating-on temperature. On the other hand, when the internal temperature of the product storage with the evaporator is lower than the predetermined cooling-off temperature, or the internal temperature of the product storage with the internal heat exchanger is turned off. When the temperature is exceeded, the driving of the compressor is stopped (for example, see Patent Document 1).

JP 2003-173647 A

  By the way, also in the vending machine to which the above-described refrigerant circulation device is applied, the product storage is opened at the time of product replenishment as in the case of a normal vending machine, and the outside air enters the product storage. . For this reason, for example, in the summer season or a rainy season such as the rainy season, the internal humidity of the product storage case may increase due to the entry of the outside air. When the internal humidity of the product storage chamber increases as described above, there is a possibility that the moisture contained in the internal air is iced on the surface of the evaporator, leading to a decrease in the cooling performance of the evaporator.

  In view of the above circumstances, an object of the present invention is to provide a refrigerant circulation device that can suppress a decrease in cooling performance of an evaporator by dehumidifying a chamber in which the evaporator is disposed.

  In order to achieve the above object, a refrigerant circulation device according to claim 1 of the present invention includes a compressor that compresses a refrigerant, a condenser that condenses the refrigerant compressed by the compressor, and a condenser that condenses the refrigerant. In a refrigerant circulation device including a refrigerant circulation circuit configured by sequentially connecting an expansion mechanism for adiabatically expanding a refrigerant and an evaporator disposed inside the chamber and evaporating the refrigerant adiabatically expanded by the expansion mechanism, When the predetermined time is reached, the driving amount of the air blowing means disposed in the chamber is reduced for a predetermined time while driving the compressor, and the air blowing means is driven after the predetermined time has elapsed. Control means for performing a dehumidifying operation for stopping the operation of the compressor is provided.

  Moreover, the refrigerant circulation apparatus according to claim 2 of the present invention is characterized in that, in the above-described claim 1, the control means increases the drive amount of the blower means during the dehumidifying operation after the predetermined time has elapsed. .

  According to a third aspect of the present invention, there is provided the refrigerant circulation device according to the first or second aspect, wherein the control means is configured such that the temperature in the vicinity of the evaporator is equal to or higher than a preset release temperature, or The dehumidifying operation is terminated when a predetermined dehumidifying time has elapsed from the time point.

  According to the refrigerant circulation device of the present invention, when the control means reaches a predetermined time point, the driving amount of the air blowing means disposed inside the chamber is reduced for a predetermined time while driving the compressor. The moisture contained in the internal atmosphere of the chamber can be attached to the surface of the evaporator to cause frosting. Then, since the compressor is stopped while the air blowing means is driven after a predetermined time has elapsed, the frost attached to the evaporator can be evaporated. Therefore, by dehumidifying the chamber in which the evaporator is disposed, there is an effect that it is possible to suppress a decrease in the cooling performance of the evaporator.

FIG. 1 is a cross-sectional view showing a case where an internal structure of a vending machine to which a refrigerant circulation apparatus according to an embodiment of the present invention is applied is viewed from the front. FIG. 2 shows the internal structure of the vending machine shown in FIG. 1, and is a cross-sectional side view of the right commodity storage. FIG. 3 is a conceptual diagram conceptually showing the refrigerant circulation device according to the embodiment of the present invention. FIG. 4 is a block diagram schematically showing a control system of the refrigerant circulation device according to the embodiment of the present invention. FIG. 5 is a conceptual diagram conceptually showing the refrigerant flow in the refrigerant circuit when the CCC operation is performed. FIG. 6 is a conceptual diagram conceptually showing the refrigerant flow in the refrigerant circuit when the HHC operation is performed. FIG. 7 is a flowchart showing the processing contents of the cooling operation control performed by the controller. FIG. 8 is a flowchart showing the processing contents of the dehumidifying operation control performed by the controller.

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

  FIG. 1 is a cross-sectional view showing a case where an internal structure of a vending machine to which a refrigerant circulation apparatus according to an embodiment of the present invention is applied is viewed from the front. The vending machine illustrated here includes a main body cabinet 1.

  The main body cabinet 1 has a rectangular shape with an open front surface. The main body cabinet 1 is provided with three independent commodity containers 3 partitioned by, for example, two heat insulating partition plates 2 in a side-by-side manner. This product storage 3 is for storing products such as canned beverages and beverages containing plastic bottles while maintaining them at a desired temperature, and has a heat insulating structure.

  FIG. 2 shows the internal structure of the vending machine shown in FIG. 1 and is a cross-sectional side view of the right product storage case 3. Here, the internal structure of the right product storage (hereinafter also referred to as right storage) 3a is shown, but the central product storage (hereinafter also referred to as intermediate storage) 3b and the left product storage (hereinafter referred to as right storage) 3a. The internal structure of 3c is also substantially the same as that of the right warehouse 3a. In the present specification, the right side indicates the right side when the vending machine is viewed from the front, and the left side indicates the left side when the vending machine is viewed from the front.

  As shown in FIG. 2, an outer door 4 and an inner door 5 are provided on the front surface of the main body cabinet 1. The outer door 4 is for opening and closing the front opening of the main body cabinet 1, and the inner door 5 is for opening and closing the front surface of the commodity storage 3. The inner door 5 is divided into upper and lower parts, and the upper door 5a opens and closes when a product is replenished.

  The product storage 3 is provided with a product storage rack 6, a carry-out 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 carry-out mechanism 7 is provided at the lower part of the product storage rack 6 and is used to carry out the products at the bottom of the product group stored in the product storage rack 6 one by one. The carry-out shooter 8 is for guiding the product carried out from the carry-out mechanism 7 to the product take-out port 4 a provided in the outer door 4.

  FIG. 3 is a conceptual diagram conceptually showing the refrigerant circulation device according to the embodiment of the present invention. The refrigerant circulation device exemplified here includes a main path 20, a branch path 30, a heat radiation path 40, and a return path 50, and includes a refrigerant circulation circuit 10 in which a refrigerant is sealed.

  The main path 20 is configured by sequentially connecting a compressor 21, an external heat exchanger 22, a first capillary tube 23, and an internal heat exchanger 24 through a refrigerant pipe 25.

  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, partitioned from the product storage 3 and below the product storage 3. 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-temperature and high-pressure refrigerant), and discharges it from the discharge port.

  As shown in FIG. 2, the external heat exchanger 22 is disposed in the machine room 9 similarly to the compressor 21. This external heat exchanger 22 condenses the refrigerant that passes therethrough. More specifically, the refrigerant compressed by the compressor 21 and discharged from the discharge port and sent out through the refrigerant pipe 25 is condensed by exchanging heat with ambient air.

  The refrigerant pipe 25 connecting the external heat exchanger 22 and the compressor 21 is provided with a high-pressure side electromagnetic valve 261. The high-pressure side electromagnetic valve 261 is a valve body that can be opened and closed. When the opening command is given from the controller 70 to be described later, the high-pressure side electromagnetic valve 261 opens and allows the passage of the refrigerant, while when the closing command is given. It closes and regulates the passage of refrigerant.

  As shown in FIG. 2, the first capillary tube 23 is disposed in the machine room 9 similarly to the compressor 21 and the external heat exchanger 22. The first capillary tube 23 is an expansion mechanism that adiabatically expands by depressurizing the refrigerant passing therethrough.

  A plurality of (three in the illustrated example) heat exchangers 24 in the cabinet are provided, which are disposed in the lower interior of each commodity storage 3 and on the front side of the rear duct D (see FIG. 2). is there. The refrigerant pipe 25 connecting the internal heat exchanger 24 and the first capillary tube 23 is branched into three by a distributor 27 disposed in the middle thereof, and the internal heat disposed in the right warehouse 3a. On the inlet side of the exchanger 24 (hereinafter also referred to as the right internal heat exchanger 24a), the inlet of the internal heat exchanger 24 (hereinafter also referred to as the internal heat exchanger 24b) disposed in the intermediate warehouse 3b. The inlet side of the internal heat exchanger 24 (hereinafter also referred to as the left internal heat exchanger 24c) disposed inside the left warehouse 3c is connected to each side.

  Moreover, in this refrigerant | coolant piping 25, low pressure side solenoid valve 262,263, on the way from the divider | distributor 27 to each of the right side heat exchanger 24a, the center internal heat exchanger 24b, and the left side heat exchanger 24c. H.264 is provided. The low pressure side solenoid valves 262, 263, and 264 are openable and closable valve elements, which are opened when the opening command is given from the controller 70 and allow passage of the refrigerant, while when the closing command is given. Is closed to restrict the passage of refrigerant.

  Refrigerant piping 25 connected to the outlet side of the internal heat exchanger 24b and the left internal heat exchanger 24c merges at the first junction P1 on the way, and further to the outlet side of the right internal heat exchanger 24a. The connected refrigerant pipe 25 joins at the second joining point P <b> 2 and is connected to the compressor 21 via the accumulator 28. Here, the accumulator 28 is for storing the liquid-phase refrigerant and allowing the gas-phase refrigerant to pass through when the refrigerant passing therethrough is a gas-liquid mixed refrigerant.

  In the refrigerant pipe 25 connected to the outlet side of the internal heat exchanger 24b and the left internal heat exchanger 24c, return solenoid valves 265 and 266 are arranged upstream of the first junction P1, respectively. is there. These return solenoid valves 265 and 266 are valve bodies that can be opened and closed. When the opening command is given from the controller 70, the feedback solenoid valves 265 and 266 are opened to allow passage of the refrigerant, whereas when the closing command is given. It closes and regulates the passage of refrigerant.

  The branch path 30 branches from a high-pressure side branch point in the middle of the path between the compressor 21 and the high-pressure side solenoid valve 261, and further branches in the middle, one of which is a refrigerant on the inlet side of the internal heat exchanger 24b. The other of the pipes 25 is constituted by a branch pipe 31 that joins the refrigerant pipe 25 on the inlet side of the left-side internal heat exchanger 24c. This branch path 30 is a path for introducing the refrigerant (high-pressure refrigerant) compressed by the compressor 21. Here, in the refrigerant pipes 25 on the inlet side of the internal heat exchanger 24b and the left internal heat exchanger 24c, a path upstream from the junction with each branch pipe 31 (each branch path 30), that is, Check valves 267 and 268 are provided in a path between each junction and the low-pressure side solenoid valves 263 and 264 located upstream thereof.

  In the branch path 30, branch solenoid valves 321 and 322 are provided on the downstream side of the branch point, respectively. The branch solenoid valves 321 and 322 are valve bodies that can be opened and closed. When the opening command is given from the controller 70, the branch solenoid valves 321 and 322 are opened to allow the passage of the refrigerant. Thus, the passage of the refrigerant is restricted.

  That is, when the refrigerant compressed by the compressor 21 is supplied through the branch path 30, the inner heat exchanger 24 b and the left inner heat exchanger 24 c condense the refrigerant passing therethrough and become a target product. The internal air of the storage 3 (the central storage 3b and the left storage 3c) is heated.

  The heat radiation path 40 is branched in the middle of each of the refrigerant pipes 25 connected to the outlet side of the inner heat exchanger 24b and the left heat exchanger 24c, and merges at the third junction P4. The heat dissipating pipe 42 is connected to the inlet side of the gas cooler 41 disposed in a manner adjacent to the exchanger 22. The heat dissipation path 40 is for supplying the gas cooler 41 with the refrigerant condensed in at least one of the internal heat exchanger 24b and the left internal heat exchanger 24c. In the gas cooler 41 to which the refrigerant is supplied through the heat radiation path 40, heat exchange is performed between the refrigerant and the ambient air, and the refrigerant radiates heat. That is, the heat radiation path 40 introduces the refrigerant condensed in the internal heat exchanger 24 and supplies the refrigerant to the gas cooler 41, and the gas cooler 41 exchanges heat with ambient air to dissipate heat.

  The third junction from the branch point of the refrigerant pipe 25 connected to the outlet side of the heat exchanger 24b and the left heat exchanger 24c in the middle of the heat radiation pipe 42 constituting the heat radiation path 40. On the way to P4, check valves 431 and 432 are provided, respectively.

  The return path 50 is connected to the outlet side of the gas cooler 41 and is connected to the refrigerant pipe 25 constituting the main path 20, that is, the fourth junction P <b> 5 of the refrigerant pipe 25 between the first capillary tube 23 and the distributor 27. It is the path | route comprised by the return piping 51 to do.

  A second capillary tube 52 is provided in the middle of the return pipe 51 constituting the return path 50. The second capillary tube 52 is for adiabatic expansion by reducing the pressure of the refrigerant passing therethrough.

  In the refrigerant circulation circuit 10, three strainers, that is, a first strainer S1, a second strainer S2, and a third strainer S3 are provided. The first strainer S <b> 1 is disposed in the refrigerant pipe 25 between the external heat exchanger 22 and the first capillary tube 23 in the main path 20. The first strainer S1 has a desiccant for removing moisture and a filter for removing foreign matter, and removes moisture from the refrigerant passing through the refrigerant pipe 25 and removes foreign matter. It is the removal member to perform.

  The second strainer S <b> 2 is disposed in the return pipe 51 in the return path 50, that is, the return pipe 51 between the gas cooler 41 and the second capillary tube 52. The second strainer S2 has a filter for removing foreign matter, and is a foreign matter removing member that only removes foreign matter from the refrigerant passing through the refrigerant pipe 25.

  The third strainer S3 is disposed in the refrigerant pipe 25 on the discharge port side of the compressor 21 in the main path 20. The third strainer S3 has a filter for removing foreign matter, and is a foreign matter removing member that removes foreign matter from the refrigerant passing through the refrigerant pipe 25. In the present embodiment, the third strainer S3 is also disposed in the refrigerant pipe 25 connected to the discharge port side of the compressor 21, but such a strainer is not essential, and the application conditions of the refrigerant circulation device, etc. Depending on the situation, it may be installed appropriately.

  FIG. 4 is a block diagram schematically showing a control system of the refrigerant circulation device according to the embodiment of the present invention. As shown in FIG. 4, the refrigerant circulation device includes an input means 60, a right compartment temperature sensor 61, a middle compartment temperature sensor 62, a left compartment temperature sensor 63, a right compartment heat exchanger temperature sensor 64, and a middle compartment. An internal heat exchanger temperature sensor 65, a left internal heat exchanger temperature sensor 66, a right internal fan F1, a central internal fan F2, a left internal fan F3, and a controller 70 are provided.

  The input means 60 is for performing various setting inputs such as a remote controller, for example, and the information set and input here is given to the controller 70.

  The right-chamber interior temperature sensor 61 is a detection means that is disposed inside the right-hand warehouse 3a and detects the internal temperature (room temperature) of the right warehouse 3a. The inside temperature sensor 62 is a detection means that is disposed inside the inside 3b and detects the inside temperature (indoor temperature) of the inside 3b. The left warehouse temperature sensor 63 is disposed in the left warehouse 3c, and is a detection means for detecting the temperature (indoor temperature) of the left warehouse 3c. Information regarding the temperatures detected by the right chamber temperature sensor 61, the inner chamber temperature sensor 62, and the left chamber temperature sensor 63 is provided to the controller 70 as a temperature signal.

  The right internal heat exchanger temperature sensor 64 is disposed in the vicinity of the right internal heat exchanger 24a, and is a detecting means for detecting the temperature of the right internal heat exchanger 24a. The in-compartment heat exchanger temperature sensor 65 is disposed in the vicinity of the in-compartment heat exchanger 24b, and is a detecting means for detecting the temperature of the in-compartment heat exchanger 24b. The left-inside heat exchanger temperature sensor 66 is disposed in the vicinity of the left-inside heat exchanger 24c, and is a detection unit that detects the temperature of the left-inside heat exchanger 24c. Information regarding the temperatures detected by the right-inside heat exchanger temperature sensor 64, the inner-inside heat exchanger temperature sensor 65, and the left-inside heat exchanger temperature sensor 66 is given to the controller 70 as a temperature signal.

  As shown in FIG. 2, the right internal fan F1 is disposed at the bottom of the right internal 3a and on the front side of the right internal heat exchanger 24a. This right internal heat exchanger 24a is a blowing means for circulating the internal air of the right internal 3a. Although not shown in the drawing, the inside fan F2 is disposed at the bottom of the inside 3b and on the front side of the inside heat exchanger 24b. This internal heat exchanger 24b is a blowing means for circulating the internal air of the internal storage 3b. Although not shown in the drawing, the left internal fan F3 is disposed at the bottom of the left internal 3c and on the front side of the left internal heat exchanger 24c. This left internal heat exchanger 24c is a blowing means for circulating the internal air of the left internal 3c.

  The controller 70 comprehensively controls the operation of each part of the refrigerant circulation circuit 10 according to programs and data stored in the memory 80. The controller 70 is an input processing unit 71, an electromagnetic valve drive processing unit 72, and a temperature determination unit 73. The compressor drive processing unit 74 and the dehumidifying operation control unit 75 are provided.

  Here, various information is stored in the memory 80, and as characteristic features of the present invention, cooling temperature information and dehumidifying operation information are stored. The cooling temperature information is for determining a target cooling temperature range of the commodity storage (cooling) 3 to be cooled, and includes a cooling on temperature as an upper limit value and a cooling off temperature as a lower limit value. It is.

  The dehumidifying operation information is for dehumidifying the inside of the commodity storage 3 to be cooled, and a specific time (for example, 3:30 am) when the dehumidifying operation is started, and a frosting time (for example, 30 minutes) in the dehumidifying operation. ) And a dehumidifying time (for example, 3 hours), and a release temperature (for example, 7 ° C.) in the dehumidifying operation.

  The input processing unit 71 is for inputting information such as commands and data given from the input means 60 and the internal temperature sensors 61 to 66. The solenoid valve drive processing unit 72 issues an open command to each solenoid valve, that is, the high pressure side solenoid valve 261, the low pressure side solenoid valves 262, 263, and 264, the feedback solenoid valves 265 and 266, and the branch solenoid valves 321 and 322, respectively. Alternatively, a close command is given to open or close them individually.

  The temperature determination unit 73 is detected by the temperature given from the internal temperature sensors 61, 62, 63 disposed inside the refrigerator (commodity storage) 3, that is, the internal temperature sensors 61, 62, 63 detect the temperature determination unit 73. It is determined whether or not the internal temperature is within the target cooling temperature range. More specifically, it is determined whether or not the detected internal temperature is lower than the cooling off temperature, or whether or not the detected internal temperature exceeds the cooling on temperature.

  The compressor drive processing unit 74 performs a process of driving the compressor 21 at a predetermined rotational speed by giving a drive command or a drive stop command to the compressor 21.

  The dehumidifying operation control unit 75 includes a time measurement unit 751, a compressor drive monitoring unit 752, a temperature comparison unit 753, and an internal fan drive processing unit 754.

  The time measuring unit 751 measures time. The compressor drive monitoring unit 752 monitors the drive of the compressor 21. The temperature comparison unit 753 stores in the memory 80 the temperature (detected temperature) given from the internal heat exchanger temperature sensors 64, 65, and 66 disposed in the inside of the refrigerator that is the target of the dehumidifying operation. The release temperature is compared to determine whether the detected temperature is equal to or higher than the release temperature. The internal fan drive processing unit 754 gives drive commands to the internal fans F1, F2, and F3, and drives the internal fans F1, F2, and F3 while adjusting the drive amounts (rotations).

  The refrigerant circulation device having the above-described configuration cools or heats the products stored in the product storage 3 as follows.

  First, the case where the CCC operation (operation for cooling the internal air of all the commodity containers 3) is performed will be described. In this case, the controller 70 given a command to perform the CCC operation through the input means 60 closes the branch solenoid valves 321 and 322 through the solenoid valve drive processing unit 72, and the high pressure side solenoid valve 261, the low pressure side solenoid valve. 262, 263, 264 and feedback solenoid valves 265, 266 are opened. As a result, the refrigerant compressed by the compressor 21 circulates as shown in FIG.

  That is, the refrigerant compressed by the compressor 21 passes through the high-pressure side electromagnetic valve 261 to be opened and reaches the external heat exchanger 22. The refrigerant that has reached the external heat exchanger 22 dissipates heat to the surrounding air (outside air) and condenses while passing through the external heat exchanger 22. The refrigerant condensed in the external heat exchanger 22 passes through the first strainer S <b> 1 to remove moisture and foreign matter, and then adiabatically expands in the first capillary tube 23.

  The refrigerant adiabatically expanded and vaporized by the first capillary tube 23 is branched into three by the distributor 27, and reaches the right internal heat exchanger 24a, the central internal heat exchanger 24b, and the left internal heat exchanger 24c. Then, each of the internal heat exchangers 24 evaporates and takes heat from the internal air of the product storage 3 to cool the internal air. The cooled internal air circulates in the interior by driving the internal fans F1, F2, and F3, whereby the products stored in the product storage 3 are cooled to the circulating internal air. The refrigerant evaporated in each internal heat exchanger 24 is gas-liquid separated by the accumulator 28, and then the gas phase portion is sucked into the compressor 21 and compressed by the compressor 21 to repeat the above-described circulation.

  Next, the case of performing the HHC operation (operation for heating the internal air of the middle warehouse 3b and the left warehouse 3c and cooling the internal air of the right warehouse 3a) will be described. In this case, the controller 70 to which an instruction to perform the HHC operation through the input means 60 is sent to the high pressure side solenoid valve 261, the low pressure side solenoid valves 263, 264, and the feedback solenoid valves 265, 266 through the solenoid valve drive processing unit 72. Is closed, and the low-pressure side solenoid valve 262 and the branch solenoid valves 321 and 322 are opened. As a result, the refrigerant compressed by the compressor 21 circulates as shown in FIG.

  That is, the refrigerant compressed by the compressor 21 passes through the branch path 30 and reaches the internal heat exchanger 24b and the left internal heat exchanger 24c. The refrigerant reaching the internal heat exchanger 24b exchanges heat with the internal air of the internal storage 3b while passing through the heat exchanger, and dissipates heat to the internal air to condense. Thereby, the internal air of the internal storage 3b is heated. The heated internal air circulates inside each of the internal storages 3b by driving the internal storage fan F2, whereby the products accommodated in the internal storage 3b are heated to the circulating internal air.

  On the other hand, the refrigerant that has reached the left internal heat exchanger 24c exchanges heat with the internal air of the left internal 3c while passing through the heat exchanger, and dissipates heat to the internal air to condense. Thereby, the internal air of the left warehouse 3c is heated. The heated internal air circulates in each of the left warehouses 3c by driving the left warehouse fan F3, whereby the products stored in the left warehouse 3c are heated to the circulating internal air.

  The refrigerant condensed in the internal heat exchanger 24b and the left internal heat exchanger 24c merges at the third junction P4, and then passes through the heat radiation pipe 42 constituting the heat radiation path 40 to reach the gas cooler 41. The gas cooler 41 radiates heat to the surrounding air. The refrigerant radiated by the gas cooler 41 passes through the second strainer S <b> 2 to remove foreign matter, and then adiabatically expands in the second capillary tube 52.

  The refrigerant vaporized by adiabatic expansion in the second capillary tube 52 passes through the low pressure side electromagnetic valve 262 opened via the distributor 27 and reaches the right internal heat exchanger 24a, and this right internal heat exchanger. It evaporates at 24a and takes heat from the internal air of the right case 3a to cool the internal air. The cooled internal air circulates through the inside of the right warehouse 3a by driving the right warehouse fan F1, thereby cooling the product accommodated in the right warehouse 3a. After the refrigerant evaporated in the right-side heat exchanger 24a is gas-liquid separated by the accumulator 28, the gas phase portion is sucked into the compressor 21 and compressed by the compressor 21, and the above-described circulation is repeated. Thus, the refrigerant circuit 10 has a function as a heat pump.

  In such a refrigerant circulation circuit 10, the external heat exchanger 22 constitutes a condenser that condenses the refrigerant compressed by the compressor 21, and the internal heat exchanger 24 evaporates the refrigerant adiabatically expanded. Is configured.

  When the inside temperature of each commodity storage 3 reaches a desired temperature range by performing the CCC operation and the HHC operation, the controller 70 performs the following refrigerant operation control and dehumidification operation control.

  FIG. 7 is a flowchart showing the processing contents of the cooling operation control performed by the controller 70. The operation of the refrigerant circulation device will be described while explaining the processing contents. Here, for convenience of explanation, a case where the HHC operation is performed will be described.

  In the cooling operation control shown in FIG. 7, when the compressor 21 is driven and the internal temperature is input from the internal temperature sensor (right internal temperature sensor 61) of the refrigerator through the input processing unit 71. (Step S101: Yes, Step S102: Yes), the controller 70 reads out information related to the cooling-off temperature from the memory 80 through the temperature determination unit 73, compares the cooling-off temperature and the internal temperature, and the internal temperature is It is determined whether or not the 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 controller 70 stops driving the compressor 21 through the compressor drive processing unit 74 (step S104), and then returns the procedure to this time. Terminate the process. According to this, the internal temperature of the right warehouse 3a changes in the increasing direction.

  When the internal temperature does not fall below the cooling off temperature (step S103: No), that is, when the internal temperature is equal to or higher than the cooling off temperature, the controller 70 maintains the drive of the compressor 21 thereafter. Return the procedure to end the current process. According to this, the internal temperature of the right warehouse 3a changes in the downward direction.

  On the other hand, when the compressor 21 is stopped driving and the internal temperature is input from the internal temperature sensor (right internal temperature sensor 61) of the refrigerator through the input processing unit 71 (step S101: No, In step S105: Yes), the controller 70 reads out the information about the cooling on temperature from the memory 80 through the temperature determination unit 73, compares the cooling on temperature with the inside temperature, and determines whether the inside temperature exceeds the cooling on temperature. It is determined whether or not (step S106).

  When the internal temperature exceeds the cooling on temperature (step S106: Yes), the controller 70 drives the compressor 21 through the compressor drive processing unit 74 (step S107), and then returns the procedure to this time. The process ends. According to this, the internal temperature of the right warehouse 3a changes in the downward direction.

  When the internal temperature does not exceed the cooling on temperature (step S106: No), that is, when the internal temperature is equal to or lower than the cooling on temperature, the controller 70 maintains the drive stop of the compressor 21 and thereafter To return the procedure to end the current process. According to this, the internal temperature of the right warehouse 3a changes in the increasing direction.

  FIG. 8 is a flowchart showing the processing contents of the dehumidifying operation control performed by the controller 70. The operation of the refrigerant circulation device will be described while explaining the processing contents. Here, for convenience of explanation, a case where the HHC operation is performed will be described.

  In the dehumidifying operation control shown in FIG. 8, when a specific time (3:30 am) for starting the dehumidifying operation stored in the memory 80 has elapsed (step S201: Yes), the controller 70 The drive of the compressor 21 is monitored through the compressor drive monitoring unit 752 (step S102). When the compressor 21 is not driven (step S202: No), the controller 70 drives the compressor 21 through the compressor drive processing unit 74 (step S203) and proceeds to the next step. Is driven (step S202: Yes), the process proceeds to the next step as it is.

  In a state where the compressor 21 is driven, the controller 70 reduces the drive amount (rotation speed) of the right internal fan F1 through the internal fan drive processing unit 754 of the dehumidifying operation control unit 75 (step S204). At this time, the controller 70 starts measuring the frosting time and measures the time through the time measuring unit 751.

  If the frosting time has elapsed as a result of the time measurement through the time measuring unit 751 (step S205: Yes), the controller 70 increases the drive amount of the right internal fan F1 through the internal fan drive processing unit 754. At the same time, the drive of the compressor 21 is stopped through the compressor drive processing unit 74 (steps S206 and S207). At this time, the controller 70 starts measuring the dehumidifying time and measures the time through the time measuring unit 751.

  Thereafter, when a temperature (detected temperature) in the vicinity of the right-side heat exchanger 24a is input from the right-side heat exchanger temperature sensor 64 in a predetermined time cycle within the dehumidifying time (step S208: Yes), the controller 70 The release temperature is read from the memory 80 through the temperature comparison unit 753, and the release temperature and the detected temperature are compared. When the detected temperature is equal to or higher than the release temperature (Yes in step S209), the compressor is processed through the compressor drive processing unit 74. 21 is driven (step S210), and then the procedure is returned to end the current process.

  If the dehumidifying time has elapsed even if the detected temperature does not exceed the release temperature (step S209: No, step S211: Yes), the controller 70 drives the compressor 21 through the compressor drive processing unit 74. (Step S210), and then the procedure is returned to end the current process.

  Thus, the controller 70 reduces the drive amount of the right internal fan F1 during a predetermined frosting time, so that it is included in the internal air of the right internal 3a on the surface of the right internal heat exchanger (evaporator) 24a. Moisture can be attached to form frost. Then, after the frosting time has elapsed, the internal temperature of the right compartment 3a can be increased by stopping the drive of the compressor 21 while driving the right internal fan F1, and the right internal heat exchanger. The frost (moisture) adhering to 24a can be evaporated. Thereby, the inside of the right warehouse 3a can be dehumidified.

  According to the refrigerant circulation device according to the present embodiment as described above, when the controller 70 reaches a predetermined specific time, the drive amount of the right internal fan F1 is predetermined while driving the compressor 21. Since the compressor 21 is stopped while the right internal fan F1 is driven after the frost formation time has elapsed, the right storage 3a in which the right internal heat exchanger 24a is disposed is dehumidified. Thereby, the fall of the cooling performance of this right-side heat exchanger 24a can be suppressed.

  Further, according to the refrigerant circulation device of the present embodiment, the amount of drive of the right internal fan F1 is increased during the dehumidifying operation after the frosting time has elapsed, so that frost adhering to the right internal heat exchanger 24a can be surely removed. Can be evaporated.

  The preferred 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 embodiment, the implementation contents of the cooling operation control and the dehumidifying operation control are described when performing the HHC operation. However, in the present invention, the cooling operation control and the dehumidifying operation are also performed when performing the CCC operation and the HCC operation. Operation control may be performed.

  Further, in the above-described embodiment, the dehumidifying operation is performed by stopping the driving of the compressor and increasing the driving amount of the internal fan. However, in the present invention, the interior of the commodity storage is as necessary. It is also possible to energize the heater disposed on the, and evaporate frost attached to the evaporator by the heater.

  As described above, the cooling device according to the present invention is useful for cooling or heating the internal atmosphere of the commodity storage box defined in the vending machine main body of the vending machine to be applied.

DESCRIPTION OF SYMBOLS 10 Refrigerant circuit 20 Main path 21 Compressor 22 External heat exchanger 23 1st capillary tube 24 Internal heat exchanger 25 Refrigerant piping 27 Distributor 30 Branch path 31 Branch pipe 40 Heat radiation path 41 Gas cooler 42 Heat radiation pipe 50 Return path 51 Return Pipe 52 Second Capillary Tube 61 Right Chamber Temperature Sensor 62 Inside Chamber Temperature Sensor 63 Left Chamber Temperature Sensor 64 Right Chamber Heat Exchanger Temperature Sensor 65 Inside Chamber Heat Exchanger Temperature Sensor 66 Left Chamber Temperature Exchange Temperature sensor 70 Controller 71 Input processing unit 72 Solenoid valve drive processing unit 73 Temperature determination unit 74 Compressor drive processing unit 75 Dehumidification operation control unit 751 Time measurement unit 752 Compressor drive monitoring unit 753 Temperature comparison unit 754 Internal fan drive processing Part 80 Memory D Rear duct F1 Right compartment fan F2 Middle compartment fan F3 Left compartment Fan S1 1st strainer S2 2nd strainer S3 3rd strainer

Claims (3)

A compressor that compresses the refrigerant; a condenser that condenses the refrigerant compressed by the compressor; an expansion mechanism that adiabatically expands the refrigerant condensed by the condenser; and an expansion mechanism that is disposed inside a chamber and that expands In the refrigerant circulation device including the refrigerant circulation circuit configured by sequentially connecting an evaporator for evaporating the refrigerant adiabatically expanded in
When the predetermined time is reached, the driving amount of the air blowing means disposed in the chamber is reduced for a predetermined time while driving the compressor, and the air blowing means is driven after the predetermined time has elapsed. A refrigerant circulating apparatus comprising control means for performing a dehumidifying operation for stopping driving of the compressor.   2. The refrigerant circulation device according to claim 1, wherein the control unit increases a driving amount of the blower unit during a dehumidifying operation after the predetermined time has elapsed.   The control means terminates the dehumidifying operation when the temperature in the vicinity of the evaporator is equal to or higher than a preset release temperature, or when a predetermined dehumidifying time has elapsed from the time point. The refrigerant circulation device according to claim 1 or 2.

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