JP6478500B2 - vending machine - Google Patents

Description

  The present invention relates to a so-called heat pump type vending machine that includes a compressor that compresses a refrigerant, radiates the refrigerant with an indoor heat exchanger to heat the product storage room, absorbs a refrigerant and cools the product storage room. It is a thing.

  In the heat pump-type vending machine of the rabbit type, a plurality of product storage rooms are configured in the main body, one of them is a dedicated cooling room, and the rest can be switched between cooling and heating. It is considered as a cold switching room. Then, the cooling dedicated chamber is cooled by the indoor heat exchanger (first heat exchanger) for the cooling dedicated chamber that absorbs the refrigerant. Further, in the use condition for cooling the cold switching chamber, the refrigerant is absorbed by the indoor heat exchanger for the cold switching chamber, and in the use condition for heating, the refrigerant is dissipated by the indoor heat exchanger for the cold switching chamber. .

  In addition, an outdoor heat exchanger (second heat exchanger) is provided outside the product storage room, and when the cooling dedicated room is sufficiently cooled, the outdoor heat exchanger absorbs heat from the refrigerant and heats it up. When the cold switching chamber of the above is sufficiently heated, the outdoor heat exchanger dissipates the refrigerant (see, for example, Patent Document 1).

  In addition, although it is an air conditioner, as heat pump control, the degree of subcooling of the refrigerant is controlled by the expansion valve when heating with the indoor heat exchanger, and the degree of superheat is controlled when cooling with the room heat exchanger It is known to make the amount of refrigerant suitable for (see, for example, Patent Document 2).

JP 2005-216111 A Japanese Patent Application Laid-Open No. 60-243460

  However, if the vending machine throttles the expansion valve to increase the degree of subcooling of the indoor heat exchanger that radiates the refrigerant, and gives priority to the heat radiation, the amount of refrigerant in the indoor heat exchanger that absorbs the refrigerant decreases and the degree of superheat Becomes large and the evaporation pressure decreases. Conversely, if the refrigerant flow rate of the indoor heat exchanger that absorbs the refrigerant is increased by enlarging the valve opening degree of the expansion valve and the heat absorption is prioritized by decreasing the degree of superheat, the indoor heat exchanger that dissipates the refrigerant The degree of subcooling of the refrigerant is lowered, and the condensation pressure is lowered. Therefore, it has been difficult to maintain each product storage room at an appropriate temperature with high efficiency.

  In addition, when two or more indoor heat exchangers that release the refrigerant are connected in series, or when two or more indoor heat exchangers that absorb the refrigerant are connected in series, they are upstream with respect to the refrigerant flow Since the refrigerant starts to radiate or absorb heat in the indoor heat exchanger, the amount of heat radiation or heat absorption in the indoor heat exchanger located downstream with respect to the refrigerant flow is insufficient, and the commodity is heated or cooled in the indoor heat exchanger There has been a problem that it is difficult to maintain the storage room at an appropriate temperature.

  The present invention has been made to solve such conventional technical problems, and it is an object of the present invention to provide a vending machine capable of smoothly keeping each product storage room at an appropriate temperature.

The vending machine according to the invention of claim 1 comprises a plurality of product storage chambers configured in a main body, a compressor for compressing a refrigerant, and a heat radiation indoor heat exchanger for radiating a refrigerant and heating a product storage chamber; An indoor heat exchanger for heat absorption that cools a product storage room by absorbing heat from a refrigerant, and an outdoor heat exchanger that is provided outside the product storage room and releases or absorbs heat from the refrigerant A throttling means located on the refrigerant downstream side of the heat exchanger and located on the refrigerant upstream side of the heat absorption indoor heat exchanger, and a control means for controlling the throttling means, the control means being an outdoor heat exchanger When absorbing the heat of the refrigerant, the throttling means is controlled based on the degree of refrigerant supercooling at the outlet of the indoor heat exchanger for heat release, and when the heat is absorbed by the indoor heat exchanger for heat absorption, the refrigerant at the outlet of the indoor heat exchanger for heat absorption It controls the throttle means on the basis of the degree of superheat, endothermic If the refrigerant superheating degree of the indoor heat exchanger outlet is within a predetermined target range, and controlling the throttle means on the basis of the refrigerant supercooling degree of the heat-radiating inner heat exchanger outlet.

A vending machine according to a second aspect of the present invention is the room thermal system for a plurality of cold switching rooms provided respectively in the plurality of cold switching rooms as the product storage room and the plurality of cold switching rooms capable of switching between cooling and heating in the above invention. An indoor heat exchanger for a cold switching room is provided with an exchanger, a cooling dedicated room as a product storage room for cooling only, and an indoor heat exchanger for a cooling dedicated room provided in the cooling dedicated room. It functions as an exchanger or a heat absorption indoor heat exchanger, and is characterized in that the cooling-dedicated room indoor heat exchanger functions as a heat absorption indoor heat exchanger.

  According to the invention of claim 1, a plurality of product storage chambers configured in the main body, a compressor for compressing the refrigerant, a heat release indoor heat exchanger for radiating the refrigerant and heating the product storage chamber, the refrigerant An indoor heat exchange system for heat dissipation in a vending machine comprising: an indoor heat exchanger for absorbing heat to cool a product storage room; and an outdoor heat exchanger provided outside the product storage room to release or absorb heat from a refrigerant. Of the compressor, and throttling means positioned on the refrigerant upstream side of the heat-absorption indoor heat exchanger, and control means for controlling the throttling means, the control means including the refrigerant by the outdoor heat exchanger When heat is absorbed, the throttling means is controlled based on the degree of refrigerant supercooling at the outlet of the indoor heat exchanger for heat release, and when the refrigerant is absorbed by the indoor heat exchanger for heat absorption, the degree of refrigerant superheat at the outlet of the indoor heat exchanger for heat absorption Control of the throttling means based on When heat absorption is performed by the outdoor heat exchanger without absorbing the refrigerant by the heat absorption indoor heat exchanger, priority is given to the heating of the product storage room by the heat release indoor heat exchanger, and the refrigerant in the heat release indoor heat exchanger outlet is excessive The throttling means can be controlled based on the degree of cooling.

  On the other hand, when absorbing heat in the heat absorption indoor heat exchanger, priority is given to cooling of the product storage room by the heat absorption indoor heat exchanger, and the throttling means is selected based on the degree of refrigerant superheat at the heat absorption indoor heat exchanger outlet. Can be controlled. As a result, each product storage room can be maintained at an appropriate temperature.

  Here, if priority is given to heating of the product storage room by the heat release indoor heat exchanger at all times, when cooling of the product storage room by the heat absorption indoor heat exchanger is insufficient, the outdoor heat exchanger releases the refrigerant to the outside. I will have to let it go. Since the temperature outside the product storage room is much lower than the temperature of the product storage room heated by the heat release indoor heat exchanger, the high pressure side pressure of the refrigerant circuit is lowered, and the heat release in the heat release indoor heat exchanger is switched It takes time until the high pressure side pressure rises, and energy efficiency deteriorates. In addition, it is necessary to switch the flow path of the refrigerant to switch to the heat release in the outdoor heat exchanger, but when absorbing the refrigerant in the indoor heat exchanger for heat absorption as in the present invention, the refrigerant overheats at the outlet of the indoor heat exchanger for heat absorption By controlling the throttling means on the basis of the degree to give priority to cooling of the product storage room, it becomes possible to maintain each product storage room at an appropriate temperature with high efficiency without causing such problems. It is.

In this case, when the control means causes the heat absorption indoor heat exchanger to absorb the refrigerant, if the degree of refrigerant superheat at the outlet of the heat absorption indoor heat exchanger is within a predetermined target range, the heat release indoor heat exchanger outlet the so so as to control the means aperture based on the refrigerant subcooling degree, in the state where the product storage chamber is cooled by the heat-absorbing indoor heat exchanger is stably cooling, radiating inner heat exchanger outlet By switching to control of the throttling means according to the degree of refrigerant supercooling, it is possible to improve the heating of the product storage chamber heated by the heat release indoor heat exchanger. As a result, it is possible to smoothly achieve both cooling and heating in each product storage room.

As in the second aspect of the present invention , many of the actual vending machines are a plurality of cold temperature switching chambers as a product storage room capable of switching between cooling and heating and a plurality of cold temperature switching provided respectively in each cold temperature switching chamber. A room heat exchanger for room, a dedicated cooling room as a product storage room for cooling only, and a room heat exchanger for cooling room provided in the dedicated cooling room, and the room heat exchanger for a cold / warm switching room is Although it functions as an indoor heat exchanger for heat release or an indoor heat exchanger for heat absorption, and the indoor heat exchanger for exclusive use in cooling functions as an indoor heat exchanger for heat absorption, according to each of the above-mentioned inventions, the cold temperature switching chamber It is possible to maintain the temperature in each product storage room at an appropriate temperature in any of the use state of heating and the use state of cooling.

It is a front view of the vending machine of one example to which the present invention is applied. It is a perspective view of the state which opened the outer door of the vending machine of FIG. It is a refrigerant circuit figure of one Example of the vending machine of FIG. 1 (Example 1). It is a refrigerant circuit figure of the vending machine explaining the HCC indoor endothermic mode by the control apparatus of FIG. It is a refrigerant circuit figure of the vending machine explaining HCC outdoor thermal absorption mode by the control apparatus of FIG. It is a refrigerant circuit figure of the vending machine explaining the HCC outdoor thermal radiation mode by the control apparatus of FIG. It is a refrigerant circuit figure of the vending machine explaining HHC indoor heat-absorption mode by the control apparatus of FIG. It is a refrigerant circuit figure of the vending machine explaining the HHC outside heat absorption mode by the control apparatus of FIG. It is a refrigerant circuit figure of the vending machine explaining the H-H-C outdoor thermal radiation mode by the control apparatus of FIG. It is a refrigerant circuit figure of the vending machine explaining CCC mode by the control apparatus of FIG. It is a flowchart of expansion valve control by the control apparatus of FIG. It is a ph diagram explaining the refrigerant supercooling degree and the heating effect in an indoor heat exchanger. It is a schematic diagram explaining the refrigerant superheat degree and cooling effect in an indoor heat exchanger. It is a refrigerant circuit figure of the reference example of the vending machine of FIG. 1 ( reference example 1 ). It is a refrigerant circuit figure of the vending machine explaining the HCC mode by the control apparatus of FIG. It is a refrigerant circuit figure of the vending machine explaining the HHC mode by the control device of FIG. It is a refrigerant circuit figure of the vending machine explaining CCC mode by the control apparatus of FIG. It is a figure which shows the temperature of each part when not performing fan control of the indoor heat exchanger of a refrigerant | coolant upstream in FIG. It is a figure which shows the temperature of each part at the time of performing fan control of the indoor heat exchanger of a refrigerant | coolant upstream in FIG. It is a refrigerant circuit figure of the other reference example of the vending machine of FIG. 1 ( reference example 2 ). It is a figure which shows the change of the temperature of the goods storage chamber by fan control of the control apparatus of FIG.

  Hereinafter, embodiments of the present invention will be described in detail based on the drawings.

  In FIG. 1 and FIG. 2, the vending machine 1 of the embodiment is a main body which is a heat insulating box open at the front face composed of a steel sheet outer surface material 2A and a heat insulating material (not shown) provided inside thereof. 2 and an outer door 3 pivotally supported by the main body 2 on one side (left side in the embodiment) so as to close the front of the main body 2 openably and closably.

  A commodity sample chamber 4 is formed on the front upper portion of the outer door 3 and a plurality of commodity selection switches 6 are arranged corresponding to a plurality of commodity samples displayed in the commodity sample chamber 4. Further, an advertisement panel 5 is formed on the front of the outer door 3 on the lower side of the product sample room 4, and a product outlet 7 is formed on the lower front of the outer door 3 on the lower side of the advertisement panel 5. .

  Furthermore, a decorative panel 8 is attached to the right (non-pivoting side) central portion toward the front of the outer door 3, and a coin insertion slot 9 and a return lever 11 are provided in the decorative panel 8 There is. In addition, a money amount indicator 12 is attached to the front of the outer door 3 on the left side facing the decorative panel 8. Furthermore, a bill discriminating device (building burr) 14 is attached to the front of the outer door 3 below the money amount display 12, and a coin return port 13 is on the front of the outer door 3 on the right side of the product outlet 7. It is configured.

  On the other hand, at the upper part in the main body 2, the upper surface, the left and right surfaces, and the rear surface are surrounded by the heat insulating material, and the product storage portion 16 having the front opened is configured. The product storage section 16 is divided into three product storage chambers in the left-right direction by the heat insulating storage section partition plate 17. In this example, two are the cold switching chambers 15 (product storage rooms) from the right side. The left side is the cooling room 20 (product storage room).

  The dedicated cooling chamber 20 has a larger volume than the respective cold switching chambers 15. This is because the products sold by cooling are generally larger than the products sold by heating. The serpentine type product storage column 18 in which products to be sold are stored in a serpentine product passage is stored in the cooling / heating switching chambers 15 and 15 separated by the partition plate 17 and the cooling dedicated chamber 20 in the front-rear direction and the left-right direction. Are provided respectively.

  The front side of the product storage unit 16 has heat insulation, and the upper side inner door 21 for opening and closing the upper side of the front opening of the product storage unit 16 and the lower side of the front opening of the product storage unit 16 are opened and closed. A lower side inner door 22 is provided. The lower side inner door 22 is pivotally supported by the main body 2.

  Further, at the lower part of the lower side inner door 22, product outlet ports 23 communicating the respective cold switching chambers 15 of the product storage unit 16 and the cooling dedicated chamber 20 side and the outer door 3 side are arranged in parallel in the left-right direction. An openable door 24 is rotatably attached to each commodity outlet 23 around the upper edge, and is pushed by the commodity guided forward and rotated to open the commodity outlet 23 Are taken out to the product outlet 7.

  On the other hand, the upper side inner door 21 is attached to the outer door 3 corresponding to the rear side of the product sample chamber 4 of the outer door 3, and opening and closing the outer door 3 stores the product by the upper side inner door 21. The upper side of the front opening of the portion 16 is configured to be opened and closed. Furthermore, the upper side inner door 21 can be opened and closed rearward independently of the outer door 3 in a state in which the outer door 3 is opened, and in a state in which the upper side inner door 21 is opened rearward from the outer door 3 It is comprised so that the goods sample displayed in the sample chamber 4 can be replaced | exchanged. A machine room 26 is formed in the lower part of the main body 2.

  Next, FIG. 3 shows the refrigerant circuit of the cooling unit of this embodiment of the vending machine 1. In this figure, reference numeral 27 denotes a compressor for compressing the refrigerant, which is installed in the machine room 26. The pipe 28 on the discharge side of the compressor 27 is connected to the first port of the four-way valve 29 as flow path switching means, and the second port of the four-way valve 29 is connected to the bridge circuit 32 via the pipe 31 . The bridge circuit 32 is composed of a parallel circuit of two sets of check valves 33 and 34 connected in series in the same forward direction, and check valves 35 and 36 (a total of four check valves). The pipe 28 is connected to the connection point between the check valves 33 and 34).

  The connection point between the check valves 34 and 36 is connected to the inlet of an expansion valve (electronic expansion valve) 38 as throttle means via a pipe 37, and the outlet of the expansion valve 38 is connected via a pipe 39 to the central cold temperature switching chamber 15 It is connected to the inlet of the indoor heat exchanger (the indoor heat exchanger for heat release RHE or the indoor heat exchanger for heat absorption EHE) 41 provided therein. A solenoid valve (open / close valve) 42 is connected in parallel to the expansion valve 38.

  The outlet of the indoor heat exchanger 41 is connected to the inlet of an expansion valve (electronic expansion valve) 44 as a throttling means via a pipe 43, and the outlet of the expansion valve 44 is in the cold switching chamber 15 at the right end via a pipe 46. It is connected to the inlet of the indoor heat exchanger (the indoor heat exchanger RHE for heat dissipation or the indoor heat exchanger EHE for heat absorption) for cold-temperature switching rooms provided in 47. That is, the expansion valve 44 is located downstream of the indoor heat exchanger 41 and upstream of the indoor heat exchanger 47. A solenoid valve (open / close valve) 48 is also connected in parallel to the expansion valve 44.

  Further, blowers 49, 51 are respectively provided in the respective cold switching chambers 15, 15. By means of the blowers 49, 51, the air in the respective cold switching chambers 15, 15 is ventilated to the respective indoor heat exchangers 41, 47. Further, the air heat-exchanged with them is circulated in the respective cold switching chambers 15, 15.

  The outlet of the indoor heat exchanger 47 is connected to the inlet of an expansion valve (electronic expansion valve) 53 as a throttling means via a pipe 52, and the outlet of the expansion valve 53 is provided in a dedicated cooling chamber 20 via a pipe 54. It is connected to the inlet of the indoor heat exchanger for the dedicated cooling chamber (the indoor heat exchanger for the cooling chamber serving as the heat absorbing indoor heat exchanger EHE) 56. That is, the expansion valve 53 is located on the refrigerant downstream side of the indoor heat exchanger 47 and on the refrigerant upstream side of the indoor heat exchanger 56. A solenoid valve (open / close valve) 57 is also connected in parallel to the expansion valve 53. Further, a blower 58 is provided also in the dedicated cooling chamber 20, and cold air heat-exchanged with the indoor heat exchanger 56 by the blower 58 is circulated in the dedicated cooling chamber 20.

  Thus, the indoor heat exchangers 41, 47, 56 are connected in series to the refrigerant flow. The outlet of the indoor heat exchanger 56 is connected to the connection point between the check valves 33 and 35 of the bridge circuit 32 through a pipe 59. The connection point between the check valves 35 and 36 of the bridge circuit 32 is connected to one end of the outdoor heat exchanger 62 via a pipe 61. The outdoor heat exchanger 62 is installed in the machine room 26 (outside the product storage room), and a fan 63 for ventilating the outside heat to the outdoor heat exchanger 62 is further installed in the machine room 26.

  The other end of the outdoor heat exchanger 62 is connected to the third port of the four-way valve 29 via the pipe 64, and the fourth port of the four-way valve 29 is connected to the inlet of the accumulator 67 via the pipe 66 There is. The outlet of the accumulator 67 is connected to the suction side of the compressor 27 via a pipe 68, and forms a refrigerant circuit of a cooling unit of the vending machine 1. Then, a predetermined amount of HFO-1234yf refrigerant is sealed in this refrigerant circuit in the embodiment.

  The four-way valve 29 communicates the first port to which the pipe 28 is connected to the second port to which the pipe 31 is connected, and the fourth port to which the pipe 64 is connected is connected to the fourth port. Switching the refrigerant flow path of the refrigerant circuit by switching between a state in which the first port is in communication with the third port and a state in which the second port is in communication with the fourth port. is there.

  Further, temperature sensors 69, 70, 71 are respectively attached to the pipes 43, 52, 59 on the outlet side of the indoor heat exchangers 41, 47, 56, and each indoor heat exchanger 41, as described later, A degree of refrigerant supercooling 47 or 56 or a degree of refrigerant superheat is detected.

  Further, in FIG. 3, C is a control device as a control means constituted by a general-purpose microcomputer, and a temperature sensor or the like (not shown) for detecting the temperature in each of the cold temperature switching chamber 15 and the dedicated cooling chamber 20 The operation of the compressor 27 and the blowers 49, 51, 58, 63 is controlled based on the outputs of the temperature sensors 69 to 71, and the valve openings of the expansion valves 38, 44, 53 are controlled. It controls switching and opening / closing of each solenoid valve 42, 48, 57. The control device C controls the number of rotations of the compressor 27 and the blowers 49, 51, 58, 63 by an inverter or the like.

  With the above configuration, the operation of this embodiment will now be described with reference to FIGS. 4 to 13. In each of the drawings, the solenoid valve shown in solid is in the closed state, and the blower is in the stopped state. Also, it is assumed that the solenoid valve shown in white indicates the open state and the blower indicates the operating state. Furthermore, the temperature sensor indicated by the solid fill indicates that the control device C controls using it. Further, the control device C controls each expansion valve based on the flowchart of FIG.

(1) H-C-C indoor heat absorption mode First of all, the central cold-temperature switching chamber 15 is heated, the right-most cold-temperature switching chamber 15 is cooled, and the cooling chamber 20 is Assuming that the heat can be absorbed therefrom without sufficiently cooling, the control device C executes the H-C-C indoor heat absorption mode shown in FIG. 4. In the HCC indoor heat absorption mode, the controller C controls the four-way valve 29 to cause the first port to communicate with the second port and the third port to communicate with the fourth port, The solenoid valves 42, 57 are opened and the solenoid valve 48 is closed.

  Then, the control device C operates the compressor 27 and the blowers 49, 51, 58, and the blower 63 is stopped. The compressor 27 is operated to compress the refrigerant and discharge it to the pipe 28. The high-temperature and high-pressure refrigerant (gas) discharged from the compressor 27 at about + 70 ° C. enters the bridge circuit 32 from the pipe 31 via the four-way valve 29 as shown by the arrows in FIG. Then, it flows into the indoor heat exchanger 41 through the check valve 34, the pipe 37, the solenoid valve 42, and the pipe 39, and the heat is radiated there. That is, at this time, the indoor heat exchanger 41 functions as a heat radiation indoor heat exchanger RHE. Warm air, which exchanges heat with the indoor heat exchanger 41 and is heated, is circulated by the blower 49 into the central cold switching chamber 15, whereby the goods in the central cold switching chamber 15 are heated to about + 55 ° C.

  The refrigerant (liquid / gas mixed state) which has dissipated heat by the indoor heat exchanger 41 and has dropped to a temperature of about + 60 ° C. flows out to the pipe 43 and is throttled by the expansion valve 44 and then passes through the pipe 46 to the indoor heat exchanger 47 , Where it evaporates and exerts an endothermic effect (eg, evaporation temperature-5 ° C). That is, at this time, the indoor heat exchanger 47 functions as a heat absorption indoor heat exchanger EHE. The cool air, which is cooled by heat exchange with the indoor heat exchanger 47, is circulated by the blower 51 into the cold switching chamber 15 at the right end, whereby the products in the cold switching chamber 15 at the right end are cooled to about + 5 ° C.

  The refrigerant flows out of the indoor heat exchanger 47 into the pipe 52, flows through the solenoid valve 57 and the pipe 54 and flows into the indoor heat exchanger 56, where it evaporates and exhibits an endothermic effect (e.g., an evaporation temperature of -5.degree. C.). The cool air, which is cooled by heat exchange with the indoor heat exchanger 56, is circulated by the blower 58 into the dedicated cooling chamber 20, whereby the products in the dedicated cooling chamber 20 are also cooled to about + 5 ° C.

  The refrigerant which has been evaporated by the indoor heat exchanger 56 and reaches a temperature of about 0 ° C. reaches the bridge circuit 32 through the pipe 59, passes through the check valve 35, enters the pipe 61, passes through the outdoor heat exchanger 62, and is pipe 64 It flows into the third port of the four-way valve 29. Then, the fourth port of the four-way valve 29 passes through the pipe 66 and enters the accumulator 67, where it is separated into gas and liquid, and then drawn from the pipe 68 into the compressor 27.

  As described above, by opening the solenoid valve 57, the indoor heat exchanger 47 and the indoor heat exchanger 56 can be regarded as one heat absorbing indoor heat exchanger EHE on the refrigerant circuit, and accordingly, the expansion valve 44 Is located on the refrigerant downstream side of the indoor heat exchanger 41, which serves as a heat release indoor heat exchanger RHE, on the refrigerant upstream side of the heat absorption indoor heat exchanger EHE.

  The control device C proceeds from step S1 to step S2 in the flowchart of FIG. 11 and proceeds from step S2 to step S12. Here, it is determined whether or not heat is radiated indoors, and since heat is currently radiated by the indoor heat exchanger 41, the control device C proceeds to step S4. Then, at step S4, the control device C sets a target with the degree of refrigerant superheat at the outlet of the indoor heat exchanger 56 of the cooling dedicated chamber 20 smaller than a predetermined upper limit and larger than a predetermined lower limit based on the output of the temperature sensor 71. Determine if it is within the range.

  Then, when the degree of refrigerant superheat at the outlet of the indoor heat exchanger 56 is not within the target range, the control device C proceeds to step S5 and the outlet of the indoor heat exchanger 56 obtained by the output of the temperature sensor 71 (described above Thus, the control of the expansion valve 44 based on the degree of superheat of the refrigerant of the heat receiving indoor heat exchanger EHE when the indoor heat exchangers 47 and 56 are regarded as one heat receiving indoor heat exchanger EHE is executed.

(1-1) Control of Degree of Superheat of Refrigerant FIG. 13 is a schematic diagram for explaining the degree of superheat of the refrigerant in the indoor heat exchanger 56 functioning as the indoor heat exchanger EHE for heat absorption. When the expansion of the expansion valve 44 is reduced to reduce the amount of refrigerant flowing into the indoor heat exchanger 56, the refrigerant flowing into the indoor heat exchanger 56 is evaporated early as shown on the left side of FIG. And then become a gas. As a result, the area contributing significantly to the cooling of the indoor heat exchanger 56 is reduced, the cooling effect is reduced, and the degree of refrigerant superheat at the outlet of the indoor heat exchanger 56 is also increased.

  On the other hand, when the valve opening degree of the expansion valve 44 is expanded to increase the amount of refrigerant flowing into the indoor heat exchanger 56, the refrigerant flowing into the indoor heat exchanger 56 evaporates substantially in the entire area as shown on the right side of FIG. You will come to As a result, the area greatly contributing to the cooling of the indoor heat exchanger 56 is increased, the cooling effect is enhanced, and the degree of refrigerant superheat at the outlet of the indoor heat exchanger 56 is also reduced.

  Based on the degree of refrigerant superheat at the outlet of the indoor heat exchanger 56 detected by the temperature sensor 71, the controller C controls the degree of opening of the expansion valve 44 in the direction in which the degree of refrigerant superheat falls within the aforementioned target range. . Specifically, in step S5, the controller C operates the expansion valve 44 by a fixed amount in the closing direction if the degree of refrigerant superheat is smaller than the target range, and operates the fixed amount in the opening direction if larger, and returns to step S1. Thereby, the cooling effect of each indoor heat exchanger 47 and 56 is adjusted, and the temperature inside the cold switching chamber 15 and the dedicated cooling chamber 20 at the right end is maintained at an appropriate temperature. That is, in this case, priority is given to the cooling of the cold switching chamber 15 and the dedicated cooling chamber 20 at the right end. Then, when the degree of refrigerant superheat at the outlet of the indoor heat exchanger 56 falls within the target range, the control device C proceeds from step S4 to step S3, and this time the indoor heat exchanger 41 obtained by the output of the temperature sensor 69 It shifts to the control of the expansion valve 44 based on the degree of refrigerant supercooling at the outlet.

(1-2) Control of Degree of Subcooling of Refrigerant FIG. 12 is a ph diagram illustrating the degree of supercooling of the refrigerant in the indoor heat exchanger 41 functioning as the indoor heat exchanger RHE for heat dissipation. If the amount of refrigerant flowing out of the indoor heat exchanger 41 is reduced by reducing the degree of opening of the expansion valve 44, the amount of heat released from the refrigerant in the indoor heat exchanger 41 shown in the upper side of FIG. The heating effect increases and the degree of refrigerant supercooling also increases (with subcooling in FIG. 12).

  On the other hand, when the valve opening degree of the expansion valve 44 is expanded to increase the amount of refrigerant flowing out from the indoor heat exchanger 41, the refrigerant flows out early from the indoor heat exchanger 41 as shown by a broken line in FIG. As a result, the amount of heat radiation decreases, so the heating effect decreases and the degree of refrigerant supercooling also decreases (no supercooling in FIG. 12).

  The controller C opens the expansion valve 44 in such a direction that the degree of refrigerant supercooling falls within a larger predetermined target range based on the degree of refrigerant supercooling at the outlet of the indoor heat exchanger 41 detected by the temperature sensor 69. Control the degree. Specifically, at step S3, the controller C operates the expansion valve 44 by a fixed amount in the closing direction if the degree of refrigerant supercooling is smaller than the predetermined target range, and operates the fixed amount in the opening direction if the degree is larger. Return to Thereby, the heating effect of the indoor heat exchanger 41 is secured, and the temperature inside the central cold-temperature switching chamber 15 is maintained at an appropriate temperature. That is, in this case, the heating of the central cold-temperature switching chamber 15 is also improved (secured) while giving priority to the cooling of the cold-temperature switching chamber 15 and the dedicated cooling chamber 20 at the right end.

  In order to heat the central cold-temperature switching chamber 15 in such a HCC indoor heat absorption mode, the amount of heat absorbed from the cooling dedicated chamber 20 and the cold-temperature switching chamber 15 at the right end by the indoor heat exchangers 56 and 47 is insufficient When it becomes (the cooling dedicated chamber 20 and the cold switching chamber 15 at the right end are cooled to the set temperature), the control device C shifts to the HCC outdoor heat absorption mode of FIG. 5.

(2) HCC outdoor heat absorption mode In this HCC outdoor heat absorption mode, the controller C stops the fans 51 and 58 from the state of FIG. 4 and operates the fan 63. The state of the four-way valve 29 and the flow of the refrigerant remain the same as in FIG. As a result, the refrigerant does not evaporate in the indoor heat exchangers 47 and 56 and heat absorption is not performed. Instead, the refrigerant flows into the outdoor heat exchanger 62 and evaporates, and from the outside air ventilated there Endothermic.

  Then, the control device C proceeds from step S2 to step S3 and executes control of the expansion valve 44 based on the degree of refrigerant supercooling of the outlet of the indoor heat exchanger 41 obtained by the output of the temperature sensor 69 as described above. That is, based on the degree of refrigerant supercooling at the outlet of the indoor heat exchanger 41 detected by the temperature sensor 69, the control device C sets the expansion valve 44 in a direction such that the degree of refrigerant supercooling falls within a larger predetermined target range. By controlling the valve opening degree, the heating effect of the indoor heat exchanger 41 is secured, and the heating of the central cold-temperature switching chamber 15 is prioritized by maintaining the inside of the central cold-temperature switching chamber 15 at an appropriate temperature.

  On the other hand, although heating of the central cold-temperature switching chamber 15 is sufficient (heat dissipation is excessive) in the HCC indoor heat absorption mode in reverse, cooling temperatures of the cooling dedicated chamber 20 and the right end by the indoor heat exchangers 56 and 47 are switched. When the cooling of the chamber 15 becomes insufficient, the control device C shifts to the HCC outdoor heat dissipation mode of FIG. 6.

(3) HCC outdoor heat dissipation mode In this HCC outdoor heat dissipation mode, the control device C controls the four-way valve 29 from the state of FIG. 4, and as shown in FIG. The flow path is switched to a state in which the second port is in communication with the fourth port. In addition, the blower 49 is stopped and the blower 63 is operated. Thus, the high temperature refrigerant discharged from the compressor 27 flows from the pipe 28 through the four-way valve 29 through the pipe 64 into the outdoor heat exchanger 62 as shown by the arrow in FIG.

  The refrigerant (liquid / gas mixed state) radiated by the outdoor heat exchanger 62 flows out to the pipe 61 and enters the bridge circuit 32. Then, it passes through the check valve 36, flows through the pipe 37, the solenoid valve 42 and the pipe 39, and then flows into the indoor heat exchanger 41. At this time, since the air is not ventilated to the indoor heat exchanger 41, the refrigerant flows out to the pipe 43 as it is, and after being throttled by the expansion valve 44, flows through the pipe 46 to the indoor heat exchanger 47 and is evaporated there. Exerts an endothermic effect. The cool air, which is cooled by heat exchange with the indoor heat exchanger 47, is circulated by the blower 51 into the cold switching chamber 15 at the right end, whereby the products in the cold switching chamber 15 at the right end are cooled to about + 5 ° C.

  The refrigerant flows out of the indoor heat exchanger 47 into the pipe 52, flows through the solenoid valve 57 and the pipe 54 into the indoor heat exchanger 56, and is evaporated there to exhibit an endothermic effect. The cool air, which is cooled by heat exchange with the indoor heat exchanger 56, is circulated by the blower 58 into the dedicated cooling chamber 20, whereby the products in the dedicated cooling chamber 20 are also cooled to about + 5 ° C.

  The refrigerant evaporated at the indoor heat exchanger 56 and brought to a temperature of about 0 ° C. reaches the bridge circuit 32 through the pipe 59 and flows from the pipe 31 to the second port of the four-way valve 29 through the check valve 33. Then, the fourth port of the four-way valve 29 passes through the pipe 66 and enters the accumulator 67, where it is separated into gas and liquid, and then drawn from the pipe 68 into the compressor 27.

  The control device C proceeds from step S2 to step S12, and here the indoor heat exchanger 41 does not dissipate heat, and since the outdoor heat exchanger 62 dissipates heat, the procedure proceeds from step S12 to step S5. Then, based on the degree of refrigerant superheat at the outlet of the indoor heat exchanger 56 detected by the temperature sensor 71 in this step S5, the degree of control of the expansion valve 44 is controlled in such a direction that the degree of refrigerant superheat falls within the aforementioned target range. By doing this, the cooling effect of each of the indoor heat exchangers 47 and 56 is adjusted, and the temperature inside the cold switching chamber 15 and the dedicated cooling chamber 20 at the right end is maintained at an appropriate temperature. When the heat is not radiated by the indoor heat exchanger 41 and is radiated by the outdoor heat exchanger 62, the central cold-temperature switching chamber 15 is not in a heated state, so the refrigerant supercooling degree control needs to be performed. (However, refrigerant supercooling control may be performed).

(4) H-H-C indoor heat absorption mode Next, the cold switching chamber 15 at the center and the cold switching chamber 15 at the right end are heated, and the inside of the dedicated cooling chamber 20 is not cooled sufficiently. From this point, assuming that heat absorption is possible, the controller C executes the H-H-C indoor heat absorption mode shown in FIG. 7. In the H-H-C indoor heat absorption mode, the controller C controls the four-way valve 29 to cause the first port to communicate with the second port and the third port to communicate with the fourth port, The solenoid valves 42, 48 are opened and the solenoid valve 57 is closed.

  Then, the control device C operates the compressor 27 and the blowers 49, 51, 58, and the blower 63 is stopped. The compressor 27 is operated to compress the refrigerant and discharge it to the pipe 28. The high-temperature and high-pressure refrigerant (gas) discharged from the compressor 27 enters the bridge circuit 32 from the pipe 31 via the four-way valve 29 as shown by the arrows in FIG. Then, it flows into the indoor heat exchanger 41 through the check valve 34, the pipe 37, the solenoid valve 42, and the pipe 39, and the heat is radiated there. That is, at this time, the indoor heat exchanger 41 functions as a heat radiation indoor heat exchanger RHE. Warm air, which exchanges heat with the indoor heat exchanger 41 and is heated, is circulated by the blower 49 into the central cold switching chamber 15, whereby the goods in the central cold switching chamber 15 are heated to about + 55 ° C.

  The refrigerant that has dissipated heat by the indoor heat exchanger 41 flows out into the pipe 43, flows through the solenoid valve 48 and the pipe 46 into the indoor heat exchanger 47, dissipates heat there, and exerts a heating action. That is, at this time, the indoor heat exchanger 47 functions as a heat radiation indoor heat exchanger RHE. The warm air, which is heated by heat exchange with the indoor heat exchanger 47, is circulated by the blower 51 into the cold switching chamber 15 at the right end, whereby the products in the cold switching chamber 15 at the right end are heated.

  The refrigerant flows out from the indoor heat exchanger 47 into the pipe 52, and after being throttled by the expansion valve 53, flows through the pipe 54 into the indoor heat exchanger 56, where it evaporates and exhibits an endothermic effect (for example, evaporation temperature -5 ° C). The cool air, which is cooled by heat exchange with the indoor heat exchanger 56, is circulated by the blower 58 into the dedicated cooling chamber 20, whereby the products in the dedicated cooling chamber 20 are also cooled to about + 5 ° C.

  The refrigerant which has been evaporated by the indoor heat exchanger 56 and reaches a temperature of about 0 ° C. reaches the bridge circuit 32 through the pipe 59, passes through the check valve 35, enters the pipe 61, passes through the outdoor heat exchanger 62, and is pipe 64 It flows into the third port of the four-way valve 29. Then, the fourth port of the four-way valve 29 passes through the pipe 66 and enters the accumulator 67, where it is separated into gas and liquid, and then drawn from the pipe 68 into the compressor 27. As described above, when the solenoid valve 48 is opened, the indoor heat exchanger 41 and the indoor heat exchanger 47 can be regarded as one heat radiating indoor heat exchanger RHE, and the expansion valve 53 is the heat radiating indoor heat. It is located on the refrigerant downstream side of the exchanger RHE and on the refrigerant upstream side of the indoor heat exchanger 56 which is the heat-absorption indoor heat exchanger EHE.

  The control device C proceeds from step S1 to step S6 in the flowchart of FIG. 11, proceeds from step S6 to step S7, and proceeds from step S7 to step S13. Here, it is determined whether or not heat is radiated indoors, and since heat is currently radiated by the indoor heat exchangers 41 and 47, the control device C proceeds to step S9. Then, in step S9, based on the output of the temperature sensor 71, the control device C sets a target with the degree of refrigerant superheat at the outlet of the indoor heat exchanger 56 of the cooling chamber 20 smaller than a predetermined upper limit and larger than the predetermined lower limit. Determine if it is within the range. When the degree of refrigerant superheat at the outlet of the indoor heat exchanger 56 is not within the target range, the controller C proceeds to step S10, and the refrigerant superheat at the outlet of the indoor heat exchanger 56 obtained by the output of the temperature sensor 71. The control of the expansion valve 53 based on the degree is executed.

  The control of the degree of refrigerant superheat at the outlet of the indoor heat exchanger 56 in this case is similar to that described above. That is, based on the degree of refrigerant superheat at the outlet of the indoor heat exchanger 56 detected by the temperature sensor 71, the control device C sets the valve opening degree of the expansion valve 53 in the direction in which the refrigerant superheat degree falls within the aforementioned target range. By controlling, the cooling effect of the indoor heat exchanger 56 is adjusted to keep the inside of the dedicated cooling chamber 20 at an appropriate temperature. That is, in this case, priority is given to the cooling of the cooling dedicated chamber 20. When the degree of refrigerant superheat at the outlet of the indoor heat exchanger 56 falls within the target range, the control device C proceeds from step S9 to step S8, and this time the indoor heat exchanger 47 obtained by the output of the temperature sensor 70 It shifts to control of expansion valve 53 based on the degree of refrigerant supercooling of an outlet.

  The control of the degree of refrigerant supercooling at the outlet of the indoor heat exchanger 47 in this case is the same as that described above. That is, based on the degree of refrigerant supercooling at the outlet of the indoor heat exchanger 47 detected by the temperature sensor 70, the controller C moves the expansion valve 53 in a direction such that the degree of refrigerant supercooling falls within a larger predetermined target range. By controlling the valve opening degree, the heating effect of the indoor heat exchangers 41 and 47 is secured, and the inside of each of the cold-temperature switching chambers 15, 15 is maintained at an appropriate temperature. That is, in this case, while giving priority to the cooling of the cooling dedicated chamber 20, the heating of the respective cold switching chambers 15, 15 is also improved (secured).

  When the amount of heat absorbed from the dedicated cooling chamber 20 by the indoor heat exchanger 56 for heating the respective cold switching chambers 15, 15 in the H-H-C indoor heat absorption mode becomes insufficient (cooling dedicated chamber The inside of 20 is in a state where it has cooled to the set temperature), and the control device C shifts to the HHC outside heat absorption mode in FIG.

(5) H-H-C outdoor heat absorption mode In this H-H-C outdoor heat absorption mode, the controller C stops the blower 58 from the state of FIG. 7 and operates the blower 63. The state of the four-way valve 29 and the flow of the refrigerant remain the same as in FIG. As a result, the refrigerant does not evaporate in the indoor heat exchanger 56 and no heat absorption is performed. Instead, the refrigerant flows into the outdoor heat exchanger 62 and evaporates, and the heat absorption is performed from the outside air ventilated there. Will come to do.

  Then, the control device C proceeds from step S7 to step S8, and executes control of the expansion valve 53 based on the degree of refrigerant supercooling of the outlet of the indoor heat exchanger 47 obtained by the output of the temperature sensor 70 as described above. That is, based on the degree of refrigerant supercooling at the outlet of the indoor heat exchanger 47 detected by the temperature sensor 70, the controller C moves the expansion valve 53 in a direction such that the degree of refrigerant supercooling falls within a larger predetermined target range. The heating effect of the indoor heat exchangers 41 and 47 is secured by controlling the degree of opening of the valve, and the heating of the respective cold switching chambers 15, 15 is prioritized by maintaining the insides of the respective cold switching chambers 15, 15 at an appropriate temperature. .

  On the other hand, the cooling of the dedicated cooling chamber 20 by the indoor heat exchanger 56 is insufficient even though heating of the respective cold switching chambers 15, 15 is sufficient (heat dissipation is excessive) in the HHC indoor heat absorption mode in reverse. When it becomes, the control apparatus C transfers to the H-H-C outdoor thermal radiation mode of FIG.

(6) H-H-C outdoor heat dissipation mode In this H-H-C outdoor heat dissipation mode, the control device C controls the four-way valve 29 from the state of FIG. 7 and, as shown in FIG. The flow path is switched to a state in which the second port is in communication with the fourth port. In addition, the blowers 49 and 51 are stopped, and the blower 63 is operated. Thereby, the high temperature refrigerant discharged from the compressor 27 flows from the pipe 28 through the four-way valve 29 through the pipe 64 into the outdoor heat exchanger 62 as shown by the arrow in FIG.

  The refrigerant (liquid / gas mixed state) radiated by the outdoor heat exchanger 62 flows out to the pipe 61 and enters the bridge circuit 32. Then, it passes through the check valve 36, flows through the pipe 37, the solenoid valve 42 and the pipe 39, and then flows into the indoor heat exchanger 41. At this time, since the air is not ventilated to the indoor heat exchanger 41, the refrigerant flows out to the pipe 43 as it is, and flows into the indoor heat exchanger 47 through the solenoid valve 48 and the pipe 46. Here again, since the air is not ventilated to the indoor heat exchanger 47, the refrigerant flows directly to the pipe 52, and after being throttled by the expansion valve 53, flows through the pipe 54 to the indoor heat exchanger 56 and is evaporated there. Demonstrates an endothermic effect. Cold air, which is cooled by heat exchange with the indoor heat exchanger 56, is circulated by the blower 58 into the dedicated cooling chamber 20, whereby the products in the dedicated cooling chamber 20 are cooled to about + 5 ° C.

  The refrigerant evaporated at the indoor heat exchanger 56 and brought to a temperature of about 0 ° C. reaches the bridge circuit 32 through the pipe 59 and flows from the pipe 31 to the second port of the four-way valve 29 through the check valve 33. Then, the fourth port of the four-way valve 29 passes through the pipe 66 and enters the accumulator 67, where it is separated into gas and liquid, and then drawn from the pipe 68 into the compressor 27.

  The control device C proceeds from step S6 to step S7, and further proceeds from step S7 to step S13. Here, since the indoor heat exchangers 41 and 47 do not dissipate heat but dissipated by the outdoor heat exchanger 62, The process proceeds from step S13 to step S10. Then, based on the degree of refrigerant superheat at the outlet of the indoor heat exchanger 56 detected by the temperature sensor 71 in this step S10, the valve opening degree of the expansion valve 53 is controlled in such a direction that the refrigerant superheat degree falls within the aforementioned target range. Thus, the cooling effect of the indoor heat exchanger 56 is adjusted to keep the inside of the dedicated cooling chamber 20 at an appropriate temperature. When the heat is not radiated by the indoor heat exchangers 41 and 47 but is radiated by the outdoor heat exchanger 62, the control of the degree of refrigerant supercooling is not performed since the cold switching chambers 15 are not heated. It is not necessary to do this (however, refrigerant supercooling control may be performed).

(7) C-C-C mode Next, in the case where both the central cold-temperature switching room 15 and the right-most cold-temperature switching room 15 are cooled, all commodity storage rooms including the cooling dedicated room 20 are cooled. The controller C executes a CCC mode shown in FIG. In the CCC mode, the controller C controls the four-way valve 29 to communicate the first port to the third port and the second port to the fourth port as shown in FIG. Switch the flow path to the In addition, the blowers 49, 51, 58, 63 are operated. Thus, the high temperature refrigerant discharged from the compressor 27 flows from the pipe 28 through the four-way valve 29 through the pipe 64 into the outdoor heat exchanger 62 as shown by the arrow in FIG.

  The refrigerant (liquid / gas mixed state) radiated by the outdoor heat exchanger 62 flows out to the pipe 61 and enters the bridge circuit 32. Then, it passes through the check valve 36 and enters the expansion valve 38 from the pipe 37, and after being throttled there, flows into the indoor heat exchanger 41 from the pipe 39 and evaporates there to exert the heat absorption effect. That is, in this case, it is located on the refrigerant downstream side of the outdoor heat exchanger 62 which radiates the refrigerant, and on the refrigerant upstream side of the indoor heat exchanger 41. The refrigerant coming out of the indoor heat exchanger 41 enters the pipe 43, passes through the solenoid valve 48 and the pipe 46 and flows into the indoor heat exchanger 47, where it evaporates and exhibits an endothermic effect.

  The refrigerant leaving the indoor heat exchanger 47 enters the pipe 52, passes through the solenoid valve 57 and the pipe 54 and flows into the indoor heat exchanger 56, where it evaporates and exhibits an endothermic effect. The cool air, which is cooled by heat exchange with the indoor heat exchangers 41, 47, 56, is circulated by the blowers 49, 51, 58 into the respective cold switching chambers 15, 15 and the dedicated cooling chamber 20, thereby each chamber The goods in 15, 15, 20 are cooled to about + 5 ° C.

  The refrigerant evaporated at the indoor heat exchanger 56 and brought to a temperature of about 0 ° C. reaches the bridge circuit 32 through the pipe 59 and flows from the pipe 31 to the second port of the four-way valve 29 through the check valve 33. Then, the fourth port of the four-way valve 29 passes through the pipe 66 and enters the accumulator 67, where it is separated into gas and liquid, and then drawn from the pipe 68 into the compressor 27.

  The control device C proceeds from step S1 to step S6 in FIG. 11 and proceeds from step S6 to step S11 to detect the degree of refrigerant superheat at the outlet of the indoor heat exchanger 56 detected by the temperature sensor 71. By controlling the opening degree of the expansion valve 38 in the direction to enter the above-mentioned target range, the cooling effect of each indoor heat exchanger 41, 47, 56 is adjusted, and the temperature in each chamber 15, 15, 20 is made appropriate. keep.

  As described above in detail, according to this embodiment, the refrigerant downstream side of the indoor heat exchanger RHE for heat radiation (the indoor heat exchanger 41 in FIGS. 4 to 6 and the indoor heat exchangers 41 and 47 in FIGS. 7 to 9) An expansion valve (FIG. 4) located on the refrigerant upstream side of the endothermic indoor heat exchanger EHE (the indoor heat exchangers 47 and 56 in FIGS. 4 to 6 and the indoor heat exchanger 56 in FIGS. 7 to 9). 6 to 7 includes the expansion valve 44, and FIGS. 7 to 9 the expansion valve 53), and the control device C for controlling the expansion valve. This control device C performs outdoor heat as shown in FIGS. When the refrigerant is absorbed by the exchanger 62, an expansion valve (see FIG. 5) based on the degree of refrigerant supercooling at the outlet of the heat radiation indoor heat exchanger RHE (in FIG. 5, the indoor heat exchanger 41, FIG. 8 the indoor heat exchanger 47). 5 controls the opening degree of the expansion valve 44, and in FIG. 8 the expansion valve 53), as shown in FIG. 4 and FIG. 7, the heat absorbing indoor heat exchanger When the refrigerant is absorbed by the HE (in FIG. 4, the indoor heat exchangers 47 and 56, and in FIG. 7 the indoor heat exchanger 56), the refrigerant superheating degree at the outlet of the heat-receiving indoor heat exchanger EHE (indoor heat exchanger 56) Since the valve opening degree of the expansion valve (the expansion valve 44 in FIG. 4 and the expansion valve 53 in FIG. 7) is controlled based on the above, the heat absorbing indoor heat exchanger EHE (in FIG. 4 the indoor heat exchangers 47 and 56). 7, when the refrigerant is not absorbed by the indoor heat exchanger 56) but absorbed by the outdoor heat exchanger 62, the indoor heat exchanger RHE for heat dissipation (in FIG. 5, the indoor heat exchanger 41, the indoor heat in FIG. 8) The heat is given priority to the heating in the product storage room (the central cold-temperature switching room 15 in FIG. 5; each cold-temperature switching room 15, 15 in FIG. 8) by the exchangers 41 and 47), and the indoor heat exchanger RHE for heat dissipation (FIG. 5). Overcooling of refrigerant at the outlet of the indoor heat exchanger 41 (in FIG. 8, the indoor heat exchanger 47) It is possible to control the expansion valve (FIG. 5, the expansion valve 44, expansion valve 53 in FIG. 8) based on.

  On the other hand, when the refrigerant is absorbed by the heat absorbing indoor heat exchanger EHE (in FIG. 4, the indoor heat exchangers 47 and 56, and in FIG. 7, the indoor heat exchanger 56), the heat absorbing indoor heat exchanger EHE (in FIG. Priority is given to cooling in the product storage room (the cold switching room 15 and the cooling dedicated room 20 at the right end in FIG. 4, the cooling dedicated room 20 in FIG. 7) by the heat exchangers 47 and 56 (in FIG. The expansion valve (FIG. 4, the expansion valve 44), based on the degree of superheat of the refrigerant at the outlet of the heat absorbing indoor heat exchanger EHE (the indoor heat exchangers 47, 56 in FIG. 4, the indoor heat exchanger 56 in FIG. 7). In 7, the valve opening degree of the expansion valve 53) can be controlled. As a result, it is possible to maintain the insides of the respective cold-temperature switching chambers 15, 15 and the dedicated cooling chamber 20 (product storage chamber) at an appropriate temperature.

  If priority is given to always heating the product storage room by the heat release indoor heat exchanger RHE, if there is insufficient cooling of the product storage room by the heat absorption indoor heat exchanger EHE, the outdoor heat exchanger 62 It is necessary to dissipate the refrigerant. However, since the external temperature is significantly lower than the temperature of the product storage room heated by the heat release indoor heat exchanger RHE, the high pressure side pressure of the refrigerant circuit is lowered, and the heat release is switched to the heat release indoor heat exchanger RHE. Sometimes it takes time for the high pressure side pressure to rise, and energy efficiency is degraded. In addition, although it is necessary to switch the flow path of the refrigerant by the four-way valve 29 in order to switch to the heat dissipation in the outdoor heat exchanger 62, as in the present invention, the heat absorbing indoor heat exchanger EHE (in FIG. In the case where the refrigerant is absorbed by the indoor heat exchanger 56) in FIG. 7, the expansion valve (the expansion valve 44 in FIG. 4, the expansion valve 53 in FIG. 7) based on the degree of refrigerant superheat at the outlet of the heat absorption indoor heat exchanger EHE. By controlling the above, it becomes possible to maintain each product storage room at an appropriate temperature with high efficiency without causing such a problem.

Further, when the heat absorbing indoor heat exchanger EHE (in FIG. 4, the indoor heat exchangers 47 and 56, and in FIG. 7, the indoor heat exchanger 56) absorbs heat from the refrigerant, the heat absorbing indoor heat exchanger EHE. If the degree of refrigerant superheat at the outlet of the valve is within the predetermined target range, the refrigerant at the outlet of the indoor heat exchanger RHE for heat release (in FIG. 4, the indoor heat exchanger 41, and in FIG. Since the expansion valve (the expansion valve 44 in FIG. 4 and the expansion valve 53 in FIG. 7) is controlled based on the degree of cooling, the heat absorbing indoor heat exchanger EHE (in FIG. 4 the indoor heat exchangers 47 and 56; In the state where the inside of the product storage room (the cool temperature switching room 15 and the cooling dedicated room 20 at the right end in FIG. 4 and the cooling dedicated room 20 in FIG. 7) cooled by the heat exchanger 56) is stably cooled Indoor heat exchanger RHE (in FIG. 4, the indoor heat exchanger 41; in FIG. 7, the indoor heat Switching to control of the expansion valve (expansion valve 44 in FIG. 4; expansion valve 53 in FIG. 7) according to the degree of refrigerant supercooling at the outlet of the converter 41, 47), and the indoor heat exchanger RHE for heat dissipation (in FIG. It also improves the heating of the product storage chamber (the central cold-temperature switching chamber 15 in FIG. 4, each cold-temperature switching chamber 15, 15 in FIG. 7) heated by the heat exchanger 41 (in FIG. 7, indoor heat exchangers 41, 47). Will be able to As a result, it is possible to smoothly achieve both cooling and heating in each product storage room .

Next, FIG. 14 shows a refrigerant circuit of the cooling unit of the reference example 1 of the vending machine 1 of the present invention. In this figure, 27 is a compressor for compressing the refrigerant as described above, and is installed in the machine room 26. The pipe 72 on the discharge side of the compressor 27 is connected to the first port of the three-way valve 73 as flow path switching means, and the second port of the three-way valve 73 is the three-way valve as flow path switching means It is connected to the 76 first port. The second port of the three-way valve 76 is connected to the indoor heat exchanger for the cold switching room provided in the central cold switching room 15 via the pipe 77 in the same manner as described above (radial indoor heat exchanger RHE or indoor heat for heat absorption It is connected to the inlet of the room temperature exchanger for the cold switching room 41 which is the exchanger EHE.

  The outlet of the indoor heat exchanger 41 is connected to a check valve 79 through a pipe 78, and the check valve 79 is connected through a pipe 81 to the cold switching chamber provided in the cold switching chamber 15 at the right end as described above. It is connected to the inlet of the indoor heat exchanger (the indoor heat exchanger RHE for heat release or the indoor heat exchanger for a cold-temperature switching room to be the heat exchanger indoor heat exchanger EHE) 47. In the check valve 79, the pipe 81 is in the forward direction. In addition, the third port of the three-way valve 76 is connected to the pipe 81 via the pipe 82.

  The outlet of the indoor heat exchanger 47 is connected to the first port of the three-way valve 84 as flow path switching means via the pipe 83, and the second port of the three-way valve 84 is expanded as the throttling means via the pipe 86 It is connected to the inlet of a valve (electronic expansion valve) 87. The outlet of the expansion valve 87 is connected to a pipe 77 via a pipe 88. An indoor heat exchanger for a dedicated cooling chamber provided in the dedicated cooling chamber 20 via a solenoid valve (on-off valve) 91 by a piping 89 through a piping 78 (a room for a dedicated cooling chamber to be the heat absorption indoor heat exchanger EHE It is connected to the inlet of the heat exchanger 56.

  The third port of the three-way valve 84 is connected to one end of the outdoor heat exchanger 62 provided in the machine room 26 (outside the product storage room) via the pipe 92 in the same manner as described above. The third port of the three-way valve 73 is connected to the pipe 92 via the pipe 93. The other end of the outdoor heat exchanger 62 is connected to the inlet of an expansion valve (electronic expansion valve) 96 as a throttling means via a pipe 94, and the outlet of the expansion valve 96 is connected to a check valve 98 via a pipe 97. ing. The check valve 98 is connected to the pipe 81 via the pipe 99, and the direction of the pipe 99 in the check valve 98 is forward.

A pipe 101 is connected to a pipe 94 at the other end of the outdoor heat exchanger 62, and the pipe 101 is connected to the inlet of an expansion valve (electronic expansion valve) 103 as a throttling means via an electromagnetic valve (opening / closing valve) 102. It is connected to the. The expansion valve 103 is connected to a pipe 89 via a pipe 104. The indoor heat exchanger 56 is connected via the pipe 104 to the inlet of the accumulator 67 as described above. The outlet of the accumulator 67 is connected to the suction side of the compressor 27 via a pipe 106, and forms a refrigerant circuit of a cooling unit of the vending machine 1 of this embodiment .

  Further, blowers 49 and 51 are provided in the respective cold switching chambers 15 and 15 in the same manner as described above, and the indoor heat exchangers 41 and 47 are provided with the respective blowers 51 and 51 in the respective cold switching chambers 15 and 15. The air is ventilated, and the air subjected to heat exchange with the air is circulated in each of the cold switching chambers 15, 15. In the same manner as described above, the blower 58 is also provided in the dedicated cooling chamber 20, and the blower 58 is configured to circulate cool air, which has been heat-exchanged with the indoor heat exchanger 56, in the dedicated cooling chamber 20. Furthermore, in the machine room 26, the same blower 63 as described above for ventilating the outdoor air to the outdoor heat exchanger 62 is installed.

  As described above, the control device C as a control means configured of a general-purpose microcomputer is based on the output of a temperature sensor (not shown) that detects the temperature in each of the cold switching chambers 15 and the cooling dedicated chamber 20. While controlling the operation of each blower 49, 51, 58, 63, and controlling the opening degree of each expansion valve 87, 96, 103, switching of the three-way valve 73, 76, 84 or each solenoid valve 91, 102 Control opening and closing. Also in this case, the control device C controls the number of revolutions of the compressor 27 and the fans 49, 51, 58, 63 by an inverter or the like.

With the above configuration, the operation of this embodiment will now be described with reference to FIGS. 15 to 19. In each of the drawings, the solenoid valve shown in solid is in the closed state, and the blower is in the stopped state. Also, it is assumed that the solenoid valve shown in white indicates the open state and the blower indicates the operating state. Furthermore, it is assumed that the three-way valve port indicated by the fill is closed.

(8) H--C--C mode First, when the cold switching chamber 15 at the right end is heated and the cold switching chamber 15 at the center is cooled, the controller C shown in FIG. Execute the C-C mode. In the H-C-C mode, the controller C controls the three-way valve 73 to cause the first port and the second port to communicate with each other, and controls the three-way valve 76 to communicate the first port and the third port. Make it communicate. Further, the three-way valve 84 is controlled to bring the first port and the second port into communication with each other, and the solenoid valve 91 is opened. Further, the expansion valve 87 is opened to control the valve opening degree.

  Then, the control device C operates the compressor 27 and the blowers 49, 51, 58, and the blower 63 is stopped. The compressor 27 is operated to compress the refrigerant and discharge it to the pipe 72. The high-temperature and high-pressure refrigerant (gas) discharged from the compressor 27 at about + 70 ° C. enters the three-way valve 76 from the pipe 74 through the three-way valve 73 as shown by the arrows in FIG. Then, it flows from the three-way valve 76 sequentially through the pipes 82 and 81 into the indoor heat exchanger 47, where it is dissipated. That is, at this time, the indoor heat exchanger 47 functions as a heat radiation indoor heat exchanger RHE. Warm air, which exchanges heat with the indoor heat exchanger 47 and is heated, is circulated by the blower 51 into the cold switching chamber 15 at the right end, whereby the products in the cold switching chamber 15 at the right end are heated to about + 55 ° C.

  The refrigerant (liquid / gas mixed state) that has dissipated heat by the indoor heat exchanger 47 and has dropped to a temperature of about + 60 ° C. flows out to the pipe 83 and flows into the expansion valve 87 via the three-way valve 84 and the pipe 86. Then, after being throttled by the expansion valve 87, it flows into the indoor heat exchanger 41 through the pipe 88, where it evaporates and exhibits an endothermic effect (e.g., evaporation temperature -5 [deg.] C.). That is, at this time, the indoor heat exchanger 41 functions as a heat absorption indoor heat exchanger EHE. The cool air, which is cooled by heat exchange with the indoor heat exchanger 41, is circulated by the blower 49 into the central cold switching chamber 15, whereby the products in the central cold switching chamber 15 are cooled to about + 5.degree.

  At least a part of the refrigerant in the indoor heat exchanger 41 evaporates, and the refrigerant exhibiting an endothermic effect flows out to the pipe 78 and flows into the indoor heat exchanger 56 through the solenoid valve 91 and the pipe 89, where the unvaporized refrigerant is Furthermore, it evaporates and exhibits an endothermic effect (for example, evaporation temperature -5 ° C). The cool air, which is cooled by heat exchange with the indoor heat exchanger 56, is circulated by the blower 58 into the dedicated cooling chamber 20, whereby the products in the dedicated cooling chamber 20 are also cooled to about + 5 ° C. The refrigerant which is evaporated by the indoor heat exchanger 56 and reaches a temperature of about 0 ° C. passes through the pipe 104 and enters the accumulator 67 where it is separated into gas and liquid, and then drawn into the compressor 27 through the pipe 106.

(8-1) Control of Blower As described above, in the HCC mode, the refrigerant throttled by the expansion valve 87 first flows into the indoor heat exchanger 41 for cooling the central cold-temperature switching chamber 15, and is evaporated, Next, it flows into the indoor heat exchanger 56 which cools the dedicated cooling chamber 20 and evaporates. Therefore, after the central cold switching chamber 15 on the upstream side with respect to the refrigerant flow cools, the cooling dedicated chamber 20 on the downstream side will cool, and the temperature of the product in the cooling dedicated chamber 20 rises. There is a problem that

  However, since the central cold-temperature switching chamber 15 is adjacent to the cold-temperature switching chamber 15 at the right end that is in use for heating, it is affected by the heat from the cold-temperature switching chamber 15 at the right end. Therefore, the cooling load of the central cold-temperature switching chamber 15 is greater than that of the dedicated cooling chamber 20.

  Based on these, first, the control device C is based on the difference between the temperature of the cooling dedicated chamber 20 cooled by the indoor heat exchanger 56 located on the refrigerant downstream side and the set temperature of the cooling dedicated chamber 20. By controlling the air flow rate (operating rate) of the blower 49 ventilating the indoor heat exchanger 41 located in the room, the heat absorption amount of the refrigerant in the indoor heat exchanger 56 is adjusted, and the temperature of the dedicated cooling chamber 20 increases. To avoid. Specifically, the operating rate of the blower 49 is calculated using the following formula (A) or formula (B).

Upstream fan operating rate (%) =
{Abs (upstream detected temperature-upstream set temperature) x upstream fan strengthening factor-abs (downstream detected temperature-downstream set temperature)} x temperature difference fan conversion factor + upstream fan reference operation rate · · · (A)
Note that the upstream detection temperature is the temperature in the central cold-temperature switching chamber 15 in this case, and the upstream set temperature is the preset temperature of the cold-temperature switching chamber 15. Further, in this case, the downstream detection temperature is the temperature in the dedicated cooling chamber 20, and the downstream set temperature is the preset temperature of the dedicated cooling chamber 20. Furthermore, the upstream fan strengthening coefficient is a coefficient for giving priority to the cooling in the central cold-temperature switching chamber 15 where the load increases as described above, over the cooling dedicated chamber 20. Further, the temperature difference fan conversion coefficient is a coefficient for converting the temperature difference into the operation rate of the blower, and the upstream fan reference operation rate is the reference operation rate of the blower 49 of the central cold temperature switching chamber 15 in this case. Depending on the difference between the room temperature and the set temperature, the operating rate of the blower 49 will rise and fall from this reference operating rate.

The above upstream fan strengthening factor may be multiplied by abs (downstream detected temperature−downstream preset temperature) as the upstream fan weakening factor, which is shown by the following equation (B).
Upstream fan operating rate (%) =
{Abs (upstream detection temperature-upstream set temperature)-abs (downstream detection temperature-downstream set temperature) x upstream fan weakening coefficient} x temperature difference fan conversion coefficient + upstream fan reference operation rate · · · (B)

  In any of the equations, abs (downstream detection temperature-downstream set temperature) is subtracted from abs (upstream detected temperature-upstream set temperature), so the temperature of the cooling dedicated chamber 20 located downstream of the refrigerant is If the temperature is higher than the set temperature and the difference is large, the operation rate (air volume) of the blower 49 of the central cold-temperature switching chamber 15 located on the upstream side of the refrigerant decreases. As a result, since the heat absorption amount of the refrigerant (the amount of evaporation of the refrigerant) in the indoor heat exchanger 49 is reduced, the heat absorption of the refrigerant (the amount of evaporation of the refrigerant) in the indoor heat exchanger 56 is increased. . The blower 58 is operated at a constant operation rate.

  FIG. 18 shows the temperature of each part when the control of the blower 49 is not performed, and FIG. 19 shows the temperature when the control of the blower 49 by the formula (A) or (B) is performed. In each figure, L1 is the air temperature in the central cold switching chamber 15 on the upstream side of the refrigerant, L2 is the air temperature in the dedicated cooling chamber 20 on the downstream side of the refrigerant, L3 is the product in the central cold switching chamber 15 The temperature L4 indicates the transition of the temperature of the product in the cooling chamber 20, respectively.

  When the blower 49 is not controlled but operated at a constant operation rate, the air temperature L1 in the central cold-temperature switching chamber 15 first decreases as shown in FIG. The air temperature L2 is decreasing. Further, the temperature L4 of the product in the dedicated cooling chamber 20 tends to be higher than the temperature L3 of the product in the central cold-temperature switching chamber 15.

  On the other hand, when the blower 49 is controlled by the equation (A) or (B), the air temperature L1 in the central cold-temperature switching chamber 15 and the air temperature L2 in the cooling chamber 20 are substantially the same as shown in FIG. It will decline. The temperature L4 of the product in the dedicated cooling chamber 20 was substantially the same as the temperature L3 of the product in the central cold-temperature switching chamber 15.

  In addition, as described above, the central cold-temperature switching chamber 15 is adjacent to the cold-temperature switching chamber 15 at the right end that is in use for heating, and is affected by heat from the cold-temperature switching chamber 15 at the right end. Although the cooling load of the central cold-temperature switching chamber 15 is larger than that of the central cold-temperature switching chamber 15, the refrigerant first starts to evaporate in the indoor heat exchanger 41 of the central cold-temperature switching chamber 15. Cooling of the switching chamber 15 is prioritized. Therefore, the central cold-temperature switching chamber 15 will be cooled smoothly even if the heat influence is exerted.

(9) H-H-C Mode Next, when the cold-temperature switching chambers 15, 15 are put into use for heating, the control device C executes the H-H-C mode shown in FIG. In the H-H-C mode, the controller C controls the three-way valve 73 to cause the first port and the second port to communicate with each other, and controls the three-way valve 76 to communicate the first port and the second port. Make it communicate. Further, the three-way valve 84 is controlled to bring the first port and the third port into communication, and the solenoid valve 91 is closed. Further, the expansion valve 103 is opened to control the valve opening degree.

  Then, the control device C operates the compressor 27 and the blowers 49, 51, 58, 63. The blower 63 is operated as needed when the heat of the indoor heat exchangers 41 and 47 is excessive and the blowers 49 and 51 stop. The compressor 27 is operated to compress the refrigerant and discharge it to the pipe 72. The high-temperature and high-pressure refrigerant (gas) discharged from the compressor 27 at about + 70 ° C. enters the three-way valve 76 from the pipe 74 through the three-way valve 73 as shown by the arrows in FIG. Then, it flows into the indoor heat exchanger 41 from the three-way valve 76 through the pipe 77 and radiates heat there. That is, at this time, the indoor heat exchanger 41 functions as a heat radiation indoor heat exchanger RHE. Warm air, which exchanges heat with the indoor heat exchanger 41 and is heated, is circulated by the blower 49 into the central cold switching chamber 15, whereby the goods in the central cold switching chamber 15 are heated to about + 55 ° C.

  The refrigerant (liquid / gas mixed state) which has dissipated heat by the indoor heat exchanger 41 and is partially condensed and lowered to a temperature of about + 60 ° C. flows out to the pipe 78 and passes through the check valve 79 and the pipe 81 to perform indoor heat exchange. Flows into the vessel 47 and radiates heat there. That is, at this time, the indoor heat exchanger 47 functions as a heat radiation indoor heat exchanger RHE. Warm air, which exchanges heat with the indoor heat exchanger 47 and is heated, is circulated by the blower 51 into the cold switching chamber 15 at the right end, whereby the products in the cold switching chamber 15 at the right end are also heated to about + 55 ° C.

  The refrigerant that has dissipated heat in the indoor heat exchanger 47 flows out to the pipe 83, and then flows into the expansion valve 103 through the three-way valve 84, the pipe 92, the outdoor heat exchanger 62, the pipe 101, and the solenoid valve 102 sequentially, and is throttled there. After that, it flows into the indoor heat exchanger 56 through the pipe 104, where the refrigerant evaporates and exhibits an endothermic effect (e.g., an evaporation temperature of -5 [deg.] C.). Cold air, which is cooled by heat exchange with the indoor heat exchanger 56, is circulated by the blower 58 into the dedicated cooling chamber 20, whereby the products in the dedicated cooling chamber 20 are cooled to about + 5 ° C. The refrigerant which is evaporated by the indoor heat exchanger 56 and reaches a temperature of about 0 ° C. passes through the pipe 104 and enters the accumulator 67 where it is separated into gas and liquid, and then drawn into the compressor 27 through the pipe 106.

(9-1) Control of Blower As described above, in the H-H-C mode, the refrigerant discharged from the compressor 27 first flows into the indoor heat exchanger 41 which heats the central cold-temperature switching chamber 15, and dissipates heat. Next, it flows into the indoor heat exchanger 47 which heats the cold-temperature switching chamber 15 at the right end and radiates heat. Therefore, when the central cold switching chamber 15 on the upstream side with respect to the refrigerant flow warms up, the cold switching chamber 15 on the right end downstream comes to warm up, and the temperature of the product in the cold switching chamber 15 on the right end There is a problem that becomes low.

  However, since the central cold-temperature switching chamber 15 is adjacent to the dedicated cooling chamber 20, it is affected by the cooling from the dedicated cooling chamber 20. Therefore, compared with the cold switching chamber 15 at the right end, the heating load of the central cold switching chamber 15 becomes large.

  Based on these, the control device C controls the upstream of the refrigerant based on the difference between the temperature of the cold switching chamber 15 at the right end heated by the indoor heat exchanger 47 located downstream of the refrigerant and the set temperature of the cold switching chamber 15 By controlling the air volume (operating rate) of the air blower 49 ventilated to the indoor heat exchanger 41 located on the side, the amount of heat release of the refrigerant in the indoor heat exchanger 47 is adjusted, and the temperature of the cold-temperature switching chamber 15 at the right end is low. Avoid the inconvenience.

  Specifically, the operating rate of the blower 49 is calculated using the formula (A) or the formula (B) as described above. That is, also in this case, if the temperature of the cold switching chamber 15 at the right end located downstream of the refrigerant is lower than the set temperature, and the difference is large, the operation of the blower 49 of the central cold switching chamber 15 located upstream of the refrigerant is operated. The rate (air volume) will decrease. As a result, the amount of heat released from the refrigerant in the indoor heat exchanger 49 is reduced, so the amount of heat released from the refrigerant in the indoor heat exchanger 47 is increased. The blower 51 is operated at a constant operation rate. As a result, the air temperatures in the respective cold switching chambers 15, 15 rise substantially in the same manner as described above, and the temperatures of the articles in the respective cold switching chambers 15, 15 become substantially the same.

  Further, as described above, since the central cold-temperature switching chamber 15 is adjacent to the cooling dedicated chamber 20 and is affected by the cooling from there, the heating of the central cold-temperature switching chamber 15 compared to the cold-temperature switching chamber 15 at the right end Although the load is increased, the refrigerant first starts to dissipate heat in the indoor heat exchanger 41 of the central cold switching chamber 15, so the heating of the central cold switching chamber 15 is prioritized. Therefore, the central cold-temperature switching chamber 15 is smoothly heated even if the cooling effect is exerted.

(10) C-C-C Mode Next, in order to cool each of the low-temperature switching chambers 15, 15, the control device C executes the C-C-C mode shown in FIG. In the C-C-C mode, the controller C controls the three-way valve 73 to cause the first port and the third port to communicate with each other, and controls the three-way valve 76 to communicate the first port and the third port. Make it communicate. Further, the three-way valve 84 is controlled to communicate the first port with the second port, the solenoid valve 91 is opened, and the solenoid valve 102 is closed. Further, the expansion valve 87 is fully opened, and the expansion valve 96 is opened to control the valve opening degree.

  Then, the control device C operates the compressor 27 and the blowers 49, 51, 58, 63. The compressor 27 is operated to compress the refrigerant and discharge it to the pipe 72. The high-temperature and high-pressure refrigerant (gas) discharged from the compressor 27 at about + 70 ° C. passes from the pipe 72 through the three-way valve 73 to the outdoor heat exchanger 62 from the pipe 93 as shown by the arrows in FIG. Heat is released. The heat is dissipated by the outdoor heat exchanger 62, and the condensed refrigerant flows through the pipe 94 into the expansion valve 96 and is throttled there, and then the pipe 97, the check valve 98, and the pipes 99 and 81 are sequentially passed through the indoor heat exchanger 47. Flow into and evaporate there.

  The refrigerant leaving the indoor heat exchanger 47 flows into the indoor heat exchanger 41 sequentially through the pipe 83, the three-way valve 84, the pipe 86, the expansion valve 87, and the pipe 88, and is also evaporated there. The refrigerant leaving the indoor heat exchanger 41 flows into the indoor heat exchanger 56 through the pipe 78, the solenoid valve 91, and the pipe 89 sequentially, and is also evaporated there. The cold air cooled by heat exchange with the indoor heat exchangers 47, 41, 56 is circulated by the blowers 51, 49, 58 into the respective chambers 15, 15, 20. The product is cooled to about + 5 ° C. The refrigerant which is evaporated by the indoor heat exchanger 56 and reaches a temperature of about 0 ° C. passes through the pipe 104 and enters the accumulator 67 where it is separated into gas and liquid, and then drawn into the compressor 27 through the pipe 106.

As described above in detail, in the H-C-C mode of this reference example , the two heat absorbing indoor heat exchangers EHE (the indoor heat exchanger 41 and the indoor heat exchanger 56 in FIG. 15) are in series with the refrigerant flow. The control device C is connected to the refrigerant downstream side by controlling the blower 49 that ventilates the heat-absorption indoor heat exchanger EHE (the indoor heat exchanger 41 in FIG. 15) located on the refrigerant upstream side. The heat absorption amount of the endothermic indoor heat exchanger EHE (the indoor heat exchanger 56 of FIG. 15) is adjusted. In the reference example , the temperature of the cooling dedicated chamber 20 cooled by the heat absorption indoor heat exchanger EHE (the indoor heat exchanger 56 in FIG. 15) where the control device C is located downstream of the refrigerant and the set temperature of the cooling dedicated chamber 20 If the difference between the two is large, the air volume of the blower 49 ventilating to the heat absorption indoor heat exchanger EHE (the indoor heat exchanger 41 in FIG. 15) located on the refrigerant upstream side is reduced. The heat absorption amount of the heat absorption indoor heat exchanger EHE (the indoor heat exchanger 41 in FIG. 15) is reduced by the control of the blower 49, and the heat absorption indoor heat exchanger EHE (the indoor heat in FIG. It becomes possible to secure the heat absorption amount of the exchanger 56). Thereby, the inside of the cooling dedicated chamber 20 cooled by the heat absorption indoor heat exchanger EHE (the indoor heat exchanger 56 in FIG. 15) located on the refrigerant downstream side can be cooled without any trouble, and the appropriate temperature can be maintained. Become.

  In this case, the cooling temperature switching chamber 15 at the right end heated by the heat radiation indoor heat exchanger RHE (the indoor heat exchanger 47 in FIG. 15) and the heat absorption indoor heat exchanger EHE located in the refrigerant upstream side (room heat in FIG. The central cold-temperature switching chamber 15 cooled by the exchanger 41) is configured to be adjacent, and the cold-temperature switching of the right end heated by the heat-dissipation indoor heat exchanger RHE (the indoor heat exchanger 47 in FIG. 15) The heat absorption indoor heat exchanger EHE (indoor heat exchanger 41 in FIG. 15) positioned on the refrigerant upstream side of the refrigerant that starts to absorb heat cools the central cold temperature switching chamber 15 where the load is increased by being adjacent to the chamber 15. This can be performed preferentially, and the cooling of the central cold-temperature switching chamber 15 can be smoothly performed.

Further, in the H-H-C mode of this reference example , two heat radiation indoor heat exchangers RHE (room heat exchangers 41 and 47 in FIG. 16) are connected in series to the refrigerant flow, and the control device C By controlling the blower 49 which ventilates the heat dissipating indoor heat exchanger RHE (the indoor heat exchanger 41 in FIG. 16) located on the refrigerant upstream side, the heat dissipating indoor heat exchanger RHE ( The heat release amount of the indoor heat exchanger 47) of FIG. 16 was adjusted. In the reference example , the control device C controls the temperature of the cold-temperature switching chamber 15 at the right end heated by the heat-dissipation indoor heat exchanger RHE (the indoor heat exchanger 47 in FIG. 16) located on the refrigerant downstream side. When the difference in the set temperature is large, the air volume of the blower 49 ventilating to the heat-dissipating indoor heat exchanger RHE (the indoor heat exchanger 41 in FIG. 16) located on the refrigerant upstream side is reduced. The amount of heat release of the heat-dissipation indoor heat exchanger RHE (the indoor heat exchanger 41 in FIG. 16) located on the side is reduced by control of the blower 49, and the heat-dissipation indoor heat exchanger RHE (FIG. It becomes possible to secure the heat radiation amount of the indoor heat exchanger 47). Thereby, the inside of the cold-temperature switching chamber 15 at the right end heated by the heat-dissipation indoor heat exchanger RHE (the indoor heat exchanger 47 in FIG. 16) located downstream of the refrigerant can be heated without any trouble and maintained at an appropriate temperature. It becomes possible.

  In this case, the cooling dedicated chamber 20 cooled by the heat absorption indoor heat exchanger EHE (the indoor heat exchanger 56 in FIG. 16) and the heat radiation indoor heat exchanger RHE located in the refrigerant upstream side (the indoor heat exchanger in FIG. 41) is configured to be adjacent to the central cold-temperature switching chamber 15 heated in 41), and is adjacent to the dedicated cooling chamber 20 cooled by the heat-absorption indoor heat exchanger EHE (indoor heat exchanger 56 in FIG. 16). The heating of the central cold-temperature switching chamber 15 where the heating load is increased by matching is preferentially given by the heat-dissipation indoor heat exchanger RHE (the indoor heat exchanger 41 in FIG. 16) located on the refrigerant upstream side where the refrigerant begins to dissipate heat. As a result, it is possible to smoothly heat the central cold-temperature switching chamber 15.

Further, the vending machine 1 of the first embodiment and the reference example 1 is provided in the two cold switching chambers 15, 15 and the respective cold switching chambers 15, 15 as product storage chambers capable of switching between cooling and heating. The indoor heat exchangers 41 and 47 as a plurality of cold-changing room indoor heat exchangers, the cooling dedicated chamber 20 as a cooling dedicated product storage chamber, and the room thermal for the cooling dedicated chamber provided in the cooling dedicated chamber 20 The indoor heat exchanger 56 as a exchanger is provided. Then, the indoor heat exchangers 41 and 47 function as a heat radiation indoor heat exchanger RHE or a heat absorption indoor heat exchanger EHE in each operation mode, and the indoor heat exchanger 56 functions as a heat absorption indoor heat exchanger EHE. However, according to the present invention, it is possible to maintain the temperature in each of the chambers 15, 15 and 20 at an appropriate temperature either in the use condition for heating the cold-temperature switching chamber 15 or in the use condition for cooling .

Next, FIG. 20 shows a reference example 2 of the present application. In this reference example , as shown in FIG. 20, it is assumed that the arrangement of the dedicated cooling chamber 20 and the low-temperature switching chambers 15, 15 is reversed from that of the first embodiment and the first embodiment . The cooling unit of the vending machine 1 of this embodiment is configured independently of the first cooling unit 107 for cooling the respective cold switching chambers 15 and 15 and the cooling dedicated chamber 20, and the first cooling unit 107. The cold switching chamber 15 at the left end of the case is heated, and a second cooling unit 108 capable of cooling the central cold switching chamber 15 and the cooling dedicated chamber 20 is provided.

  The compressor 109 of the first cooling unit 107 is disposed substantially at the center of the machine chamber 26, and the compressor 111 of the second cooling unit 108 is disposed below the inside of the cold-temperature switching chamber 15 at the left end.

In the cold switching chamber 15 at the left end, in addition to the compressor 111, the heat absorber 112 (the heat absorbing indoor heat exchanger EHE of this reference example ) of the first cooling unit 107 and the radiator 113 of the second cooling unit 108 ( The heat radiation indoor heat exchanger RHE of this reference example is disposed, and the heat absorber 114 of the first cooling unit 107 (heat absorption indoor heat exchanger EHE of this reference example ) and the second cooling unit 15 in the center are disposed. The heat absorber 116 (the heat-absorbing indoor heat exchanger EHE of this reference example ) of the cooling unit 108 is disposed, and the heat sink 117 of the first cooling unit 107 (the heat-receiving indoor heat exchanger of this reference example ) EHE) and the heat sink 118 (the heat absorption indoor heat exchanger EHE of this reference example ) of the second cooling unit 108 are arranged.

  The cold switching chamber 15 at the left end is provided with an electric heater 119 for compensating for the lack of heat when heating by the second cooling unit 108, and the cold switching chamber 15 at the center is an electric heater 121 for heating the same. Is provided. In addition, the fans 49, 51, 58 described above are provided in front of the heat absorbers 112, 116, 118 in the respective chambers 15, 15, 20, respectively.

  In the first cooling unit 107, the inlet side of a radiator 122 (an outdoor heat exchanger that dissipates the refrigerant) is connected to the discharge side of the compressor 109 disposed in the machine chamber 26, and the outlet side of the radiator 122 is an internal heat exchanger 123 Via the electromagnetic valve 124A and the capillary tube (throttle means) 126A, the electromagnetic valve 124B and the capillary tube (throttle means) 126B, and the electromagnetic valve 124C and the capillary tube (throttle means) 126C. It is connected to each inlet side of each heat absorber 112, 114, 117. Further, the outlet side of the heat absorber 117 where the refrigerants from the heat absorbers 112 and 114 merge is connected to the suction side of the compressor 109 via the internal heat exchanger 123 to constitute a refrigerant circuit.

  Further, in the second cooling unit 108, the inlet side of the radiator 113 is connected to the discharge side of the compressor 111 disposed in the cold switching chamber 15 at the left end, and the outlet side of the radiator 113 is via the electromagnetic valve 127C and the capillary tube 128C. The heat absorber 129 is connected to the inlet side of the heat absorber 129 (the outdoor heat exchanger for absorbing heat of refrigerant), and the outlet side of the heat absorber 129 is connected to the suction side of the compressor 111. The outlet side of the radiator 113 is further branched into two on the upstream side of the solenoid valve 127C, one is connected to the inlet side of the heat absorber 116 via the solenoid valve 127A and the capillary tube 128A, and the other is the solenoid valve 127B. , And the inlet side of the heat absorber 118 via the capillary tube 128B. The outlet side of the heat sink 116 is connected to the inlet side of the heat sink 118 (downstream side of the capillary tube 128B), and the outlet side of the heat sink 118 is connected to the inlet side of the heat sink 129 (downstream side of the capillary tube 128C) A refrigerant circuit is configured. That is, the heat absorber 116 provided in the central cold-temperature switching chamber 15 and the heat absorber 118 provided in the cooling dedicated chamber 20 are connected in series to the refrigerant flow of the second cooling unit 108.

  The radiator 122 of the first cooling unit 107, the internal heat exchanger 123, the solenoid valves 124A, 124B, 124C, the capillary tubes 126A, 126B, 126C, and the solenoid valves 127A, 127B, 127C, of the second cooling unit 108. The capillary tubes 128 A, 128 B, 128 C and the heat absorber 129 are disposed in the machine chamber 26. Further, a blower 63 for air cooling the inside is provided in the machine room 26, and these devices are controlled by the control device C.

  Furthermore, the arrangement configuration of the heat absorber 112 of the first cooling unit 107 and the compressor 111 and the radiator 113 of the second cooling unit 108 in the cold switching chamber 15 at the left end is directed from the front side to the rear side of the cold switching chamber 15 The heat absorber 112 of the first cooling unit 107, the radiator 113 of the second cooling unit 108, and the compressor 111 are arranged in this order.

In this case, carbon dioxide is used as the refrigerant of the second cooling unit 108, and a compressor that compresses the refrigerant at a supercritical pressure or higher is used as the compressor 111. The refrigerant of the first cooling unit 107 is carbon dioxide in the present embodiment but is not particularly limited. According to the configuration, room air in each of the cold switching chambers 15 and 15 and the dedicated cooling chamber 20 flows from the rear side to the front side, the upper side, and the rear duct (not shown) in this order. In 15, when the first cooling unit 107 and the second cooling unit 108 are in operation, for example, the surface temperature of the compressor 111 is + 80 ° C., and the refrigerant piping temperature on the discharge side of the compressor 111 is + 120 ° C. (radiator When the outlet temperature of the radiator 113 is + 60 ° C. (carbon dioxide as the refrigerant of the second cooling unit 108 is not isothermal change), the indoor air temperature after cooling the compressor 111 dissipates heat. The temperature is lower than the temperature of the heater 113, and heat can be dissipated from the radiator 113.

And, according to the configuration of the reference example , since the compressor 111 of the second cooling unit 108 is disposed in the cold switching chamber 15 at the left end, the exhaust heat from the compressor 111 due to the heat generation of the compressor 111 The cold switching chamber 15 at the left end can be heated. As a result, power consumption can be suppressed as compared with the conventional method of heating with an electric heater, and energy saving of the vending machine can be achieved. In addition, since the radiator 113 of the second cooling unit 108 is disposed in the cold switching chamber 15 at the left end, the cold switching chamber 15 at the left end can be heated by heat dissipation of the refrigerant in the radiator 113, thereby further saving energy. Can be

  Further, when the second cooling unit 108 is operated, the second cooling unit 108 is used only for the cooling dedicated chamber 20 by opening / closing control of the solenoid valves 127A, 127B, 127C, or the central cooling / heating switching chamber 15 and the cooling dedicated chamber It is possible to select whether to use for cooling both chambers 20 or to stop using the second cooling unit 108 for cooling the central cool switching room 15 and the dedicated cooling room 20.

  Further, the control device C turns ON / OFF the compressor 109 of the first cooling unit 107 and the compressor 111 of the second cooling unit 108 based on the temperatures in the respective cold switching chambers 15 and 15 and the dedicated cooling chamber 20. The compressor 109 of the first cooling unit 107 is ON-driven in synchronization with the ON operation of the compressor 111 of the second cooling unit 108. Thus, the heat radiation of the radiator 122 disposed in the machine room 26 on the side of the first cooling unit 107 is absorbed by the heat sink 129 disposed in the machine room 26 on the side of the second cooling unit 108, whereby the first cooling is performed. The heat radiation of the radiator 122 of the unit 107 side can be recovered without waste by the heat absorber 129 of the second cooling unit 108 side, and the second cooling unit is more than the heat absorber 129 of the second cooling unit 108 merely absorbs heat from the outside air. The efficiency of 108 can be increased.

  However, when the temperature in the central cold-temperature switching chamber 15 or the dedicated cooling chamber 20 reaches a predetermined value or more, the control device C drives the compressor 111 on the second cooling unit 108 side to maintain the temperature of the product. The compressor 109 on the side of the first cooling unit 107 is driven to be ON regardless of.

(11) Control of the blower 49 of the cold switching chamber 15 at the left end By disposing the compressor 111 of the second cooling unit 108 in the cold switching chamber 15 at the left end as described above, the exhaust heat from the compressor 111 is However, if the blower 49 is operated while the compressor 111 is stopped, the heat in the cold switching chamber 15 at the left end is dissipated to the outside. Therefore, when the controller C stops the compressor 111, the blower 49 also stops. Thereby, the temperature drop of the cold switching chamber 15 at the left end is suppressed.

  Further, the control device C starts the operation of the blower 49 a predetermined time before the start of the operation of the compressor 111, and rotates at a low speed. In FIG. 21, when the blower 49 is operated / stopped in synchronization with the operation (ON) / stop (OFF) of the compressor 111 (L5), the blower 49 is also stopped in synchronization with the stop (OFF) of the compressor 111. However, the temperature transition in the cold temperature switching chamber 15 at the left end of the left end (L6) when the fan 49 is started at a rotational speed of 30% (low speed) after 900 s (seconds) has elapsed after the stop is shown.

Here, in the reference example , in a state where the blower 49 is stopped after the compressor 111 is stopped, the compressor is slightly delayed for 900 seconds from the stop (broken line P1 at the left end after 920s shown in FIG. 21). It is assumed that 111 is turned on (the shortest time when the compressor 111 is stopped is previously obtained by experiment). Therefore, L6 in the drawing indicates the case where the control device C starts the operation of the blower 49 20s before the compressor 111 starts the operation.

As described above, when the operation of the blower 49 is started at a low speed before the compressor 111 starts the operation, the heat stored in the compressor 111 can be circulated in the cold switching chamber 15 at the left end. The inside of the cold switching chamber 15 is thereby warmed up, and the operation start (ON) of the compressor 111 is delayed. In the reference example , the start of the compressor 111 is delayed until the time point of broken line P2 (approximately 1370 s after stop) shown in FIG. As a result, the operation rate of the compressor 111 was reduced from 42% (in the case of L5) to 37% (in the case of L6), and energy saving could be realized.

In the reference example , when the compressor 111 is stopped, the blower 49 is also stopped. However, the present invention is not limited thereto. The number of rotations of the blower 49 is reduced to stop the compressor 49 at low speed (for example, 20% It is good also as a form to drive by etc.). In that case, the rotational speed of the blower 49 is increased to 30% a predetermined time before the compressor 111 starts operation.

Further, in the above reference example , by starting the operation of the blower 49 (or increasing the rotational speed) 900s after the stop of the compressor 111, the operation of the blower 49 can be started (or rotated) a predetermined time before the start of operation of the compressor 111 If the temperature in the cold switching chamber 15 at the left end falls to the lower limit value and restarts the compressor 111, the temperature is temporarily suspended, and the blower 49 is moved first. You may make it start (or raise rotation speed). That is, it is expected that the operation rate of the compressor 111 can be lowered also by the control of starting the operation of the blower 47 (or increasing the rotational speed) immediately before the start of the operation of the compressor 111.

(12) Control of the blower 51 of the central low-temperature switching chamber 15 Further, as described above, the heat absorber 116 provided in the central low-temperature switching chamber 15 and the heat absorber 118 provided in the dedicated cooling chamber 20 are the second cooling unit It is connected in series to the 108 refrigerant streams. Therefore, when the second cooling unit 108 is operated in a use condition for cooling the central cold-temperature switching chamber 15 and the solenoid valve 127A is opened, the refrigerant exiting the radiator 113 is throttled by the capillary tube 128A from the solenoid valve 127A. After that, it flows into the heat absorber 116 of the central cold-temperature switching chamber 15 to evaporate, and then flows into the heat absorber 118 of the cooling dedicated chamber 20 to evaporate.

Therefore, the control device C controls the temperature of the cooling dedicated chamber 20 cooled by the heat absorber 118 (the heat absorbing indoor heat exchanger (EHE) and the temperature of the cooling dedicated chamber 20 located on the refrigerant downstream side as in the first embodiment described above. The amount of refrigerant in the heat absorber 116 is controlled by controlling the air volume (operating ratio) of the blower 51 ventilating to the heat absorber 116 (heat absorption indoor heat exchanger EHE) located on the refrigerant upstream side based on the difference from the set temperature. The amount of heat absorption (the amount of evaporation is adjusted to avoid the problem that the temperature of the dedicated cooling chamber 20 rises.

  Specifically, the operating rate of the blower 51 is calculated using the formula (A) or the formula (B) as described above. That is, also in this case, if the temperature of the cooling dedicated chamber 20 located on the refrigerant downstream side is higher than the set temperature, and the difference is large, the operation rate of the blower 51 of the central cold temperature switching chamber 15 located on the refrigerant upstream side ( The volume of air) will be reduced. As a result, since the heat absorption amount (evaporation amount) of the refrigerant in the heat absorber 116 is reduced, the heat absorption amount (evaporation amount) of the refrigerant in the heat absorber 118 is increased. The blower 58 is operated at a constant operating rate. As a result, the air temperatures in the central cold-temperature switching chamber 15 and the dedicated cooling chamber 20 decrease substantially in the same manner as described above, and the temperatures of products in the respective chambers 15 and 20 also become substantially the same.

Moreover, in this reference example , in the operating state of the second cooling unit 108, the cold-temperature switching chamber 15 at the left end is in a use state where it is heated. Therefore, the central cold switching chamber 15 adjacent to the cold switching chamber 15 at the left end is thermally affected by the cold switching chamber 15 at the left end, and compared with the cooling dedicated chamber 20, the central cold switching chamber 15 The cooling load of the refrigerant is increased so that the refrigerant starts to absorb heat (evaporate) in the heat absorber 116 of the central cold switching chamber 15. Therefore, the cooling of the central cold switching chamber 15 is prioritized. Therefore, the central cold-temperature switching chamber 15 will be cooled smoothly even if the heat influence is exerted.

Furthermore, in this embodiment , capillary tubes 128A to 128C are adopted as the throttling means of the second cooling unit 108 and used in combination with the solenoid valves 127A to 127C. However, these are expanded as in the above embodiments and the like. You may comprise by a valve (electronic expansion valve).

  Then, without absorbing heat of refrigerant by heat absorbers 116 and 118 (room heat exchanger EHE for heat absorption) (therefore, expansion valves at their inlets are fully closed), heat absorber 129 (outdoor heat exchanger in this case) As in the first embodiment, the controller C controls the expansion valve at the inlet of the heat absorber 129 based on the degree of cooling supercooling at the outlet of the radiator 113 (the indoor heat exchanger RHE for heat dissipation) as in the first embodiment. Do. On the other hand, in the operating state in which the heat absorber 116 and / or the heat absorber 118 absorbs heat, the control device C controls the heat absorber 116 or the outlet of the heat absorber 118 based on the degree of refrigerant superheating as in the first embodiment. The expansion valves at their inlets may be controlled.

  Although not shown in the embodiment, when detecting the degree of refrigerant superheat or the degree of refrigerant supercooling with a temperature sensor, it is necessary to detect the evaporation temperature or condensation temperature of the refrigerant, so the refrigerant inlet or center of the heat exchanger A temperature sensor is provided in the part or the like, and a sensor (which calculates the temperature from the pressure) that measures the evaporation pressure or condensation pressure of the refrigerant is provided. The degree of refrigerant superheat is calculated from the heat exchanger outlet temperature-evaporation temperature, and the degree of refrigerant supercooling is calculated from the condensation temperature-heat exchanger outlet temperature.

1 Vending machine 2 Main body 15 cold temperature switching room (product storage room)
20 Cooling Room (Product Storage Room)
27, 109, 111 Compressor 29 Four-way valve 38, 44, 53, 87, 96, 103 Expansion valve (throttling means)
41, 47, 56 Room heat exchanger (room heat exchanger RHE for heat dissipation, room heat exchanger EHE for heat absorption)
49, 51, 58, 63 Blower 62 Outdoor heat exchanger 69, 70, 71 Temperature sensor 107 1st cooling unit 108 2nd cooling unit 113 Radiator (indoor heat exchanger RHE for heat dissipation)
116, 118, 129 Heat absorber (indoor heat exchanger EHE for heat absorption, outdoor heat exchanger)
C control device (control means)

Claims (2)

A plurality of product storage chambers configured in the main body, a compressor for compressing the refrigerant, a heat release indoor heat exchanger for radiating the refrigerant to heat the product storage chamber, and absorbing the refrigerant for the product storage chamber A vending machine comprising: a heat absorbing indoor heat exchanger for cooling; and an outdoor heat exchanger provided outside the product storage chamber for radiating or absorbing a refrigerant.
And a throttling means located downstream of the refrigerant for the heat dissipation indoor heat exchanger and located on the refrigerant upstream side of the heat absorption indoor heat exchanger, and control means for controlling the throttling means.
When the refrigerant is absorbed by the outdoor heat exchanger, the control means controls the expansion means based on the degree of refrigerant supercooling at the outlet of the heat-dissipation indoor heat exchanger.
When the refrigerant for heat absorption is absorbed by the heat absorption indoor heat exchanger, the throttling means is controlled based on the degree of refrigerant overheating of the heat absorption indoor heat exchanger outlet, and the degree of refrigerant overheating of the heat absorption indoor heat exchanger outlet is When it is within a predetermined target range, the throttling means is controlled based on the degree of refrigerant supercooling at the outlet of the heat radiation indoor heat exchanger . A plurality of cold switching chambers as the product storage chamber capable of switching between cooling and heating, and a plurality of indoor heat exchangers for cold switching chambers respectively provided in the respective cold switching chambers;
A cooling dedicated chamber as the product storage chamber dedicated to cooling and an indoor heat exchanger for the cooling dedicated chamber provided in the cooling dedicated chamber;
The cold-switching room indoor heat exchanger functions as the heat radiation indoor heat exchanger or the heat absorption indoor heat exchanger.
The vending machine according to claim 1, wherein the cooling-room-use indoor heat exchanger functions as the heat-absorbing indoor heat exchanger.

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