JP2014137198A - Cooling device and showcase - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a cooling device capable of stably maintaining temperatures of a plurality of storage portions cooled at different temperatures even if a single evaporator is used.SOLUTION: This cooling device 100 includes: a single evaporator 40 configured to be able to cool an upper storage 51 and a lower storage 52; and an oblique air plate 60 inserted into the evaporator 40 so as to separate the single evaporator 40 into an evaporator region 40a for cooling the upper storage 51 to a low temperature set value TL and an evaporator region 40b for controlling the lower storage 52 to an intermediate temperature set value TM different from the low temperature set value TL.

Description

  The present invention relates to a cooling device, and more particularly, to a cooling device and a showcase including a single evaporator configured to be able to cool a first housing portion and a second housing portion.

  Conventionally, a cooling device such as a showcase provided with a single evaporator configured to be able to cool the first housing portion and the second housing portion is known (see, for example, Patent Document 1).

  FIG. 3 of Patent Document 1 includes a single evaporator disposed in a circulation passage for circulating cold air, and the evaporator can maintain the upper display section and the lower display section at different refrigeration temperatures. An open showcase (cooling device) is disclosed. In the open showcase described in FIG. 3 of this Patent Document 1, circulating cold air for the upper display section is formed using the low temperature region of the upper half of the evaporator, and the lower display is performed using the high temperature region of the lower half. It forms a circulating cold for the division. That is, paying attention to the evaporation of the gas-liquid two-phase refrigerant inside the heat transfer tube extending from the upper part toward the lower part while meandering in the horizontal direction inside the vertically installed evaporator, the refrigerant containing more liquid phase While utilizing the difference between the amount of heat exchange when evaporating and the amount of heat exchange when the refrigerant containing more gas phase evaporates, the circulating air flowing through the upper half of the evaporator is cooled to a lower temperature. The circulating air flowing in the lower half is configured not to be cooled as much as the circulating air flowing in the upper half.

Japanese Utility Model Publication No.4-1378

  However, in the open showcase (cooling device) described in Patent Document 1, it is possible to set two sections (upper display section and lower display section) to different refrigeration temperatures using a single evaporator. On the other hand, since the air passages of the two sections communicate with each other in a single evaporator, there is a disadvantage that the temperature of one section tends to affect the temperature of the other section. For this reason, there is a problem that it is difficult to stably maintain the temperatures of the two sections (upper display section and lower display section).

  The present invention has been made to solve the above-described problems, and one object of the present invention is to provide a plurality of storage units that are cooled to different temperatures even when a single evaporator is used. It is an object to provide a cooling device and a showcase that can stably maintain the respective temperatures together.

  The cooling device according to the first aspect of the present invention includes a single evaporator configured to be able to cool the first housing portion and the second housing portion, a single evaporator, and the first housing portion as the first housing portion. A partition member inserted into the evaporator so as to be separated into a first evaporator region cooled to a temperature and a second evaporator region controlled to a second temperature different from the first temperature. .

  In the cooling device according to the first aspect of the present invention, as described above, the single evaporator, the first evaporator region that cools the first housing portion to the first temperature, and the second housing portion are set to the first temperature. By providing a partition member that is inserted into the evaporator so as to be separated into a second evaporator region that is controlled to a different second temperature, the partition member allows the single evaporator to be connected to the first evaporator region and the second evaporator region. Since it is separated into the evaporator region, the first evaporator region and the second evaporator region can be provided independently without communicating with each other. Thereby, using the first evaporator region to cool the first housing part to the first temperature, and using the second evaporator region to control the second housing part to the second temperature, Since the first evaporator region and the second evaporator region can be performed independently without affecting each other, only the first evaporator region is involved in the cooling of the first accommodating portion, and the second evaporation is performed. The evaporator area is not affected, and only the second evaporator area is involved in the temperature control of the second housing portion, and the first evaporator area is not affected. As a result, even when a single evaporator is used, both the temperature of the first housing part (cooling temperature) and the temperature of the second housing part (control temperature) cooled to different temperatures can be stably maintained. Can do.

  In the cooling device according to the first aspect, preferably, the first ventilation path corresponding to the first evaporator area and the second ventilation path corresponding to the second evaporator area are separated from each other by a partition member to form a single evaporator. The first accommodating part is cooled to the first temperature by the air blown from the first ventilation path, and the second accommodating part is blown by the blown air from the second ventilation path. It is configured to be cooled to the second temperature. If comprised in this way, a single evaporator will be isolate | separated by a partition member, without connecting mutually to the 1st ventilation path corresponding to a 1st evaporator area | region, and the 2nd ventilation path corresponding to a 2nd evaporator area | region. Therefore, the blown air from the first ventilation path can be guided only to the first housing part, and the first housing part can be easily maintained at the cooling temperature of the first temperature, and the blown air from the second ventilation path. The second housing part can be easily maintained at the cooling temperature composed of the second temperature by guiding the gas to the second housing part only.

  In the cooling device according to the first aspect, preferably, the partition member is configured such that an insertion position in the evaporator can be changed, and the first evaporator region in the evaporator is changed according to the insertion position of the partition member. And the area ratio between the second evaporator region is changed, and the first temperature of the first housing part cooled by the first evaporator region and the second temperature of the second housing part cooled by the second evaporator region are changed. The temperature relationship between the two temperatures is changeable. If comprised in this way, the 1st temperature of a 1st accommodating part and the 2nd temperature of a 2nd accommodating part can be mutually approached or moved away by changing the insertion position of the partition member with respect to an evaporator. Furthermore, depending on the insertion position of the partition member, the first temperature can be lowered below the second temperature, or conversely, the first temperature can be raised above the second temperature. Thereby, while being able to set the cooling temperature of a 1st accommodating part and the cooling temperature of a 2nd accommodating part to each desired temperature relationship, the cooling temperature of a 1st accommodating part and the 1st are maintained, maintaining a desired temperature relationship. Both the cooling temperatures of the two housing parts can be stably maintained.

  In the cooling device according to the first aspect described above, preferably, the evaporator includes a heat transfer tube through which the refrigerant flows, and a plate-like fin member attached to the surface of the heat transfer tube with a predetermined interval, The member has a comb-like shape having a slit portion formed corresponding to each of the plurality of fin members, and the comb-like partition with the fin member sandwiched in the thickness direction by the slit portion. A single evaporator is configured to be separated into a first evaporator region and a second evaporator region by inserting a member into the evaporator. If comprised in this way, the comb-tooth-shaped partition member which has several slit parts will be easily inserted toward the inside of a plate fin type evaporator, and a 1st evaporator area | region and a 2nd evaporator area | region will be ensured. Can be separated. Further, by inserting the partition member into the evaporator with the plurality of slit portions sandwiching the fin members corresponding to the respective slit portions in the thickness direction, the partition member can be stably held inside the evaporator. .

  In the cooling device according to the first aspect, preferably, a refrigerant temperature detection unit that detects a refrigerant temperature of the evaporator, an electronic expansion valve that controls an amount of the refrigerant flowing into the evaporator according to the opening degree, and an electronic expansion And a controller that controls the opening of the valve. The controller is detected by the refrigerant temperature detector in a state where the evaporator is separated into the first evaporator region and the second evaporator region by the partition member. The cooling of the first accommodating part at the first temperature and the second accommodating part at the second temperature by changing the opening of the electronic expansion valve based on the refrigerant temperature of the evaporator and controlling the refrigerant flow rate. Is configured to do. If constituted in this way, not only can a single evaporator be separated into a first evaporator region and a second evaporator region by a partition member to form an air-side circulation channel, but in this state, By further adjusting the flow rate on the refrigerant side (opening control of the electronic expansion valve) based on the refrigerant temperature of the evaporator detected by the refrigerant temperature detection unit, the cooling temperature of the first storage unit is easily controlled to the first temperature. And the cooling temperature of a 2nd accommodating part can be easily controlled to 2nd temperature.

  In the configuration including the refrigerant temperature detection unit, the electronic expansion valve, and the control unit, the evaporator is preferably configured such that the refrigerant after flowing through the first evaporator region flows through the second evaporator region. The refrigerant temperature detector is disposed on the downstream side of the electronic expansion valve and in the vicinity of the partition member, the first refrigerant temperature detector for detecting the refrigerant temperature flowing into the first evaporator area, and the first evaporator area And a second refrigerant temperature detector that detects a refrigerant temperature in the vicinity of the boundary between the second evaporator region and a third refrigerant temperature detector that detects a refrigerant temperature flowing out from the second evaporator region. The first and second refrigerant superheating levels in the first evaporator region based on the refrigerant temperature detected by the first refrigerant temperature detecting unit and the refrigerant temperature detected by the second refrigerant temperature detecting unit are 0 degrees or less. The cold state detected by the second refrigerant temperature detection unit. The opening degree control of the electronic expansion valve is performed so that the second superheat degree of the refrigerant in the second evaporator region based on the temperature and the refrigerant temperature detected by the third refrigerant temperature detection unit becomes a value larger than 0 degree. It is configured as follows. If comprised in this way, while being able to maintain a 1st accommodating part easily and stably at 1st temperature, a 2nd accommodating part can be easily and stably maintained at 2nd temperature.

  In the case where the evaporator is configured such that the refrigerant after flowing through the first evaporator region flows through the second evaporator region, preferably, a compressor capable of controlling the refrigerant discharge amount by changing the rotation speed is provided. In addition, the control unit maintains the first storage unit at the first temperature by controlling the opening degree of the electronic expansion valve and controlling the rotational speed of the compressor, and controls the second storage unit by controlling the opening degree of the electronic expansion valve. It is configured to perform control to maintain two temperatures. With this configuration, when it is difficult to maintain the first housing portion at the first temperature only by opening control of the electronic expansion valve, the refrigerant circulation amount is changed in accordance with the change in the rotation speed of the compressor. It is possible to easily adjust the heat exchange performance (cooling capacity) of the first evaporator region by adjusting the refrigerant evaporation temperature (low-pressure side refrigerant pressure) in the one evaporator region. The heat exchange performance (cooling capacity) of the second evaporator region can be adjusted by controlling the degree of superheat of the refrigerant by controlling the opening degree of the electronic expansion valve within a range in which the heat exchange performance of the first evaporator region can be adjusted. it can. Thereby, the cooling temperature (1st temperature) of a 1st accommodating part and the cooling temperature (2nd temperature) of a 2nd accommodating part can each be adjusted correctly.

  In this case, preferably, the control unit maintains the first temperature and the first accommodation in a state where the first superheat degree of the refrigerant in the first evaporator region is maintained at 0 degrees or less based on the opening degree control of the electronic expansion valve. Based on the difference from the detected temperature of the part, the rotation speed of the compressor is changed to maintain the first accommodating part at the first temperature, and the refrigerant in the second evaporator region is controlled based on the opening degree control of the electronic expansion valve In a state where the second superheat degree is maintained at a value greater than 0 degrees, control is performed to maintain the second housing portion at the second temperature based on the difference between the second temperature and the detected temperature of the second housing portion. It is configured. If comprised in this way, while obtaining the desired cooling capability for maintaining a 1st accommodating part at 1st temperature in a 1st evaporator area | region by the change of the refrigerant | coolant circulation amount accompanying the rotation speed change of a compressor, while performing electronic expansion The desired cooling capacity for maintaining the second accommodating portion at the second temperature can be obtained also in the second evaporator region by controlling the opening of the valve. As a result, the cooling temperature (first temperature) of the first housing part and the cooling temperature (second temperature) of the second housing part can be adjusted more accurately.

  In the cooling device according to the first aspect, preferably, the partition member is configured so that the first evaporator region in the evaporator is disposed above the second evaporator region, and the partition member is a cooling member. It is installed inside the evaporator in a state having an inclination angle capable of discharging the molten water when the frost generated in the first evaporator region is melted with the operation toward the second evaporator region below. If comprised in this way, even if it is a case where the removal operation (defrost operation) of the frost which generate | occur | produced in the 1st evaporator area | region during operation of a cooling device was performed, it has an inclination angle and is installed in the inside of an evaporator Molten water (drain water) can flow along the partition member without being retained in the first evaporator region and drained downward by the partition member thus formed. Therefore, even if the frost removal operation is performed in a state where the single evaporator is partitioned by the partition member, the molten water (drain water) affects the heat exchange performance (cooling capacity) of the first evaporator region. Stable cooling operation can be continued without giving

  The showcase according to the second aspect of the present invention includes a first storage unit that stores products cooled at a first temperature, and a second storage unit that stores products that can be cooled at a second temperature different from the first temperature. A single evaporator configured to be able to cool the first storage portion and the second storage portion, a single evaporator, a first evaporator region for cooling the first storage portion to the first temperature, and a first evaporator And a partition member that is inserted into the evaporator so as to be separated into a second evaporator region that is controlled to a second temperature.

  In the showcase according to the second aspect of the present invention, as described above, the single evaporator, the first evaporator region that cools the first storage portion to the first temperature, and the second storage portion are set to the first temperature. By providing a partition member that is inserted into the evaporator so as to be separated into a second evaporator region that is controlled to a different second temperature, the partition member allows the single evaporator to be connected to the first evaporator region and the second evaporator region. Since it is separated into the evaporator region, the first evaporator region and the second evaporator region can be provided independently without communicating with each other. Thereby, using the first evaporator region to cool the first housing part to the first temperature, and using the second evaporator region to control the second housing part to the second temperature, Since the first evaporator region and the second evaporator region can be performed independently without affecting each other, only the first evaporator region is involved in the cooling of the first accommodating portion, and the second evaporation is performed. The evaporator area is not affected, and only the second evaporator area is involved in the temperature control of the second housing portion, and the first evaporator area is not affected. As a result, even when a showcase is configured using a single evaporator, both the temperature of the first container (cooling temperature) and the temperature of the second container (control temperature) cooled to different temperatures are used. It can be maintained stably.

  According to the present invention, as described above, even when a single evaporator is used, both the temperature of the first housing portion and the temperature of the second housing portion that are cooled to different temperatures can be stably maintained. Can do.

It is the schematic diagram which showed schematic structure of the cooling device by one Embodiment of this invention. It is sectional drawing which showed the structure of the showcase which comprises the cooling device by one Embodiment of this invention. It is the figure which showed the structure of the evaporator integrated in the showcase which comprises the cooling device by one Embodiment of this invention. It is the top view which showed the structure of the swash plate inserted in the inside of the evaporator by one Embodiment of this invention. It is an expanded sectional view of the showcase which showed the state by which the swash plate was attached inside the evaporator by one Embodiment of this invention. It is the block diagram which showed the control structure of the cooling device by one Embodiment of this invention. It is the figure which showed the processing flow of the control part at the time of the cooling operation of the cooling device by one Embodiment of this invention. It is sectional drawing which showed the structure of the showcase by the 1st modification of one Embodiment of this invention. It is sectional drawing which showed the structure of the showcase by the 2nd modification of one Embodiment of this invention. It is sectional drawing which showed the structure of the oblique wind board by the 3rd modification of one Embodiment of this invention.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments embodying the present invention will be described below with reference to the drawings.

  With reference to FIGS. 1-6, the structure of the cooling device 100 by one Embodiment of this invention is demonstrated. Below, the schematic structure of the cooling device 100 is demonstrated first, and the structure of the showcase 2 is demonstrated in detail after that.

As shown in FIG. 1, the cooling device 100 according to the present embodiment includes a refrigerator 1 that can form a predetermined refrigeration cycle using carbon dioxide (CO ₂ ) as a refrigerant, and an open type that displays and sells products ( And an open type showcase 2. The showcase 2 installed in the store is connected to a refrigerator (outdoor unit) 1 installed outdoors via a refrigerant pipe (liquid pipe) 3a and a refrigerant pipe (gas pipe) 3b.

  The refrigerator 1 includes a compressor 10 and a gas cooler (heat radiator) 20 connected to the compressor 10 by a discharge pipe 3c. The compressor 10 has a role of compressing the gas refrigerant sucked from the low pressure side in the refrigeration cycle and discharging it to the high pressure side (discharge pipe 3c). Here, an inverter compressor capable of controlling the refrigerant discharge amount by changing the rotation speed is used as the compressor 10. The gas cooler 20 has a function of cooling the refrigerant in the superheated gas state that circulates inside using external air blown by the blower 21. The refrigerant condensed (liquefied) in the gas cooler 20 flows through the refrigerant pipe 3 a and flows into the electronic expansion valve 30.

  The showcase 2 includes an electronic expansion valve 30 and an evaporator 40 connected downstream of the electronic expansion valve 30 by a refrigerant pipe 3d. The electronic expansion valve 30 has a role of expanding and reducing (reducing pressure) the refrigerant cooled (liquefied) by the gas cooler 20 and supplying the refrigerant to the evaporator 40. Here, the electronic expansion valve 30 is configured to open and close the valve mechanism using the driving force of the stepping motor 31 driven by pulse control. Note that the liquid refrigerant expanded and throttled by the electronic expansion valve 30 flows into the evaporator 40 from the refrigerant pipe 3d in a gas-liquid two-phase state composed of a gas phase and a liquid phase.

  The evaporator 40 has a function of evaporating (vaporizing) the gas-liquid two-phase refrigerant supplied from the electronic expansion valve 30. That is, the refrigerant evaporates while obtaining a predetermined latent heat of vaporization from the inlet to the outlet of the evaporator 40, and at this time, heat is taken away from the air circulating inside the showcase 2 to form cooling air. . Further, the refrigerant after evaporation in the evaporator 40 is in a gas state containing a large amount of gas phase, and is circulated in the order of the refrigerant pipe (gas pipe) 3b and the suction pipe 3e and returned to the compressor 10.

Thus, in the cooling device 100, the refrigerant (CO ₂ ) discharged from the compressor 10 is discharged along the direction of the arrow P along the discharge pipe 3c, the gas cooler 20, the refrigerant pipe 3a, the electronic expansion valve 30, the refrigerant pipe 3d, The cycle of flowing in the order of the evaporator 40, the refrigerant pipe 3b, and the suction pipe 3e and returning to the compressor 10 is repeated. In the cooling device 100, the refrigerator 1 is provided with a control unit 70 for controlling the operation of the refrigerator 1 and the showcase 2. As a result, the inside of the showcase 2 is maintained at a predetermined cooling (refrigeration) temperature by operating the refrigerator 1. The inside of the showcase 2 described here indicates an upper storage 51 and a lower storage 52 for storing the displayed products 101 and 102, respectively, as shown in FIG.

  Moreover, the showcase 2 is provided with the main-body part 50 installed in a floor surface, as shown in FIG. The main body 50 includes an upper storage 51 and a lower storage 52 whose front side (Y1 side) is open. In this case, the upper storage 51 is disposed on the upper side (Z2 side) and the lower storage 52 is disposed on the lower side (Z1 side). The products 101 and 102 displayed in the upper storage 51 and the lower storage 52 are taken out from the front side. The upper storage 51 and the lower storage 52 are examples of the “first storage” and the “second storage” of the present invention, respectively.

  In addition, a duct-like air passage 53 is provided on the back side of the bottom 51a, the ceiling 51b, and the back (Y2 side) wall 51c of the upper storage 51, and the bottom 52a of the lower storage 52, the ceiling A duct-like air passage 53 is provided on the back side of the portion 52b and the wall portion 52c on the back side (Y2 side). Also, a blower 55 is attached to the air passage 53, and the cold air for cooling / preserving the product 101 displayed in the upper storage 51 in the state of the low temperature set value TL passes through the air passage 53 in the direction of arrow A. It circulates to. Similarly, an air blower 56 is attached to the air passage 54, and cold air for cooling / preserving the product 102 displayed in the lower storage 52 in the state of the set value TM for medium temperature is indicated in the air passage 54 with an arrow. Circulate in the B direction. Here, in the showcase 2, for example, as the low temperature set value TL, the refrigeration temperature can be set to any temperature in the range of 3 ° C. to 8 ° C., and the intermediate temperature set value TM is set as the refrigeration temperature. Can be set to any temperature in the range of 15 ° C. or higher and 20 ° C. or lower. That is, the low temperature set value TL is set to be in a temperature range relatively lower than the medium temperature set value TM. The air passages 53 and 54 are examples of the “first ventilation path” and the “second ventilation path” in the present invention, respectively. The low temperature set value TL and the medium temperature set value TM are examples of the “first temperature” and the “second temperature” in the present invention, respectively.

  Further, an air outlet 53a serving as an outlet of the air passage 53 is formed in the vicinity of the front edge (Y1 side) of the ceiling 51b of the upper storage 51, and air is formed in the vicinity of the front edge of the bottom 51a of the upper storage 51. A suction port 53 b is formed as an inlet of the passage 53. Similarly, an air outlet 54a serving as an outlet of the air passage 54 is formed in the vicinity of the front edge (Y1 side) of the ceiling 52b of the lower storage 52, and the front edge of the bottom 52a of the lower storage 52 is formed. A suction port 54b serving as an inlet of the air passage 54 is formed in the vicinity of the portion. Thereby, the cold air flowing through the air passage 53 is blown out from the blowout port 53 a to the upper housing 51 and is sucked from the suction port 53 b and returned to the air passage 53. In addition, the cool air flowing through the air passage 54 is blown out from the outlet 54 a to the lower storage 52 and is sucked in from the suction port 54 b and returned to the air passage 54.

  Further, an evaporator 40 is disposed between the wall portions 51c and 52c on the back side (Y2 side) of the upper storage case 51 and the lower storage case 52 and the back surface portion 50a (Y2 side) of the main body 50. Yes. The evaporator 40 is formed in a substantially plate shape, and the evaporator 40 is installed in a vertically placed state in portions of air passages 53 and 54 extending in the vertical direction (Z direction).

  Further, when the evaporator 40 installed in the main body 50 is viewed from the front side corresponding to the front side of the showcase 2 (see FIG. 2), as shown in FIG. A pair of end plates (end plates) 41 arranged parallel to each other, a heat transfer tube (evaporation pipe) 42 that reciprocates between the left and right end plates 41 in the X1 direction and the X2 direction, and a straight tube of the heat transfer tube 42 And a plurality of thin fin members 43 each of which is press-fitted into a fin collar portion 43a formed of a through-hole and fixed at a predetermined interval L (fin pitch) in the X direction. That is, the evaporator 40 is a plate fin type air heat exchanger. 3 schematically shows how the heat transfer tube 42 reciprocates between the end plates 41. Actually, as shown in FIGS. 2 and 4, the heat transfer tube 42 is an evaporator. It is configured to repeatedly reciprocate in the fore-and-aft direction of 40 (the direction of the number of coils). Therefore, in the evaporator 40, the refrigerant flows into the heat transfer pipe (evaporation pipe) 42 from the Z2 side (upper side) and the X1 side inlet 42a of the evaporator 40, and between the left and right end plates 41 in the X direction ( The refrigerant pipe (gas pipe) flows out in the Z1 direction (downward direction) while reciprocating sequentially in the horizontal direction and the Y direction (front-rear direction), and flows out from the outlet part 42b on the Z1 side (lower side) and X1 side. ) It is configured to flow into 3b.

  Here, in this embodiment, as shown in FIG. 2 and FIG. 5, a swash plate 60 is attached to the evaporator 40. The swash plate 60 has a substantially constant inclination angle along the width direction (Y2 direction) of the end plate 41 from the front side (Y1 side) of the evaporator 40 toward the inside of the evaporator 40 and is inclined downward. Has been inserted. That is, the swash plate 60 is fixed inside the evaporator 40 in a state where the cross section has a substantially linear shape without bending in the front-rear direction (bending downward). The swash plate 60 separates the single evaporator 40 into an evaporator area 40a disposed on the upper side (Z2 side) and an evaporator area 40b disposed on the lower side (Z1 side) on the air side. It is comprised so that. That is, by inserting the swash plate 60, the evaporator region 40a is included in a part of the air passage 53 through which the cool air for cooling the upper storage 51 circulates, and the lower storage 52 The evaporator region 40b is included in a part of the air passage 54 through which the cool air for cooling the air circulates. In FIG. 5, the evaporator regions 40 a and 40 b are illustrated using thick two-dot chain lines. The evaporator regions 40a and 40b are examples of the “first evaporator region” and the “second evaporator region” in the present invention, respectively. The swash plate 60 is an example of the “partition member” in the present invention.

  In the present embodiment, the swash plate 60 is configured to be able to be inserted into the evaporator 40 at an arbitrary position along the number of stages of the heat transfer tubes 42 (vertical direction: Z direction). That is, the ratio of the heat exchange area (the ratio of the heat transfer area) between the evaporator region 40a and the evaporator region 40b in the evaporator 40 according to the insertion position of the swash plate 60 along the Z direction (vertical direction). It can be changed to any ratio. In this case, as an example of the insertion position, the swash plate 60 is inserted between the sixth and seventh stages from the uppermost stage of the heat transfer tube 42. Thereby, the single evaporator 40 is divided into an evaporator region 40a (upper region having a relatively large heat transfer area) corresponding to six stages of the heat transfer tubes 42 and the remaining four stages of the heat transfer tubes 42. It is separated on the air side into a corresponding evaporator region 40b (a lower region having a relatively small heat transfer area).

  Therefore, in the showcase 2, the upper storage 51 is cooled by the cool air that flows through the air passage 53 and is cooled by the evaporator region 40a having a relatively large heat exchange area (heat transfer area) and blown out from the outlet 53a. The lower container is cooled by the cool air blown from the outlet 54a after being cooled to the set value TL and cooled by the evaporator region 40b that flows through the air passage 54 and has a relatively small heat exchange area (heat transfer area). 52 is cooled to the set value TM for medium temperature. Thus, in the showcase 2, the heat on the air side of each of the two heat exchange regions (evaporator regions 40a and 40b) is changed according to the position of the swash plate 60 inserted into the single evaporator 40. While the exchange area is adjusted, the relationship between the cooling temperature of the upper storage 51 cooled by the evaporator region 40a and the cooling temperature of the lower storage 52 cooled by the evaporator region 40b (in this embodiment) The low temperature set value TL of the upper storage 51 <the relationship that the lower storage 52 has a medium temperature set value TM) can be appropriately set.

  The structure of the swash plate 60 will be described in more detail. As shown in FIG. 4, the swash plate 60 includes a comb tooth portion having a plurality of slit portions 61 formed corresponding to each of the plurality of fin members 43. 62 is included. That is, the swash plate 60 is formed in a comb-like shape when seen in a plan view. Then, the comb-like oblique wind plate 60 (comb portion 62) is placed inside the evaporator 40 as a whole in a state where the fin member 43 is sandwiched between the slit portions 61 in the thickness direction (X direction in FIG. 3). It is configured to be inserted. Note that the swash plate 60 is preferably made of, for example, a resin material that is easy to reduce in weight and has a slight stretchability in the longitudinal direction (X direction). The reason is that the interval L between the fin members 43 actually has a predetermined dimensional tolerance, and the individual fin members 43 may be formed in a corrugated shape by pressing so that the surface has peaks and valleys. For this reason, each fin member 43 can be easily inserted into the corresponding slit portion 61 by providing elasticity to the swash plate 60 side, and the swash plate 60 (comb teeth portion 62) is all the fin members. This is because it is necessary to sandwich 43 integrally in the thickness direction (X direction). When the swash plate 60 is made of a resin-based material, the fin member 43 is securely gripped by using the stretchability, so that the swash plate 60 slides downward from the insertion position by its own weight. And stably held at a predetermined position inside the evaporator 40. Thereby, it is not necessary to separately provide a fixing member for fixing the swash plate 60 to the end plate 41 or the like.

  The evaporator 40 incorporates a defrosting electric heater (not shown). This electric heater has a function of periodically melting frost adhered to the fin members 43 in the evaporator regions 40 a and 40 b during the cooling operation of the upper storage 51 and the lower storage 52 by the timer control by the control unit 70. ing.

  Here, in this embodiment, as shown in FIG. 5, the swash plate 60 inserted into the evaporator 40 has an upper surface so that the back side (Y2 side) is lower than the front side (Y1 side). 60a is inclined. That is, when the operation for removing the frost generated in the evaporator region 40 a during the cooling operation (defrost operation) is performed, the molten water (drain water) due to the melting of the frost travels through the fin member 43 and the upper surface of the swash plate 60. After reaching 60a, the inclined upper surface 60a is configured to slide down obliquely toward the rear. Further, the molten water that flows rearward is drained from the minute gap between the fin members 43 in the vicinity of the back surface portion 50a toward the lower evaporator region 40b without staying in the lower region of the evaporator region 40a. It is configured. Further, the molten water also flows down along the fin member 43 in the evaporator region 40b and accumulates in a drain pan (receiving tray) (not shown), and then is discharged to the outside of the main body 50 through a water pipe connected to the drain pan. The

  In the present embodiment, as shown in FIG. 1, refrigerant temperature sensors 81, 82, and 83 for detecting the temperature of the refrigerant flowing through the heat transfer pipe 42 are attached to the evaporator 40. Specifically, as shown in FIG. 3, the refrigerant temperature sensor 81 is attached in the vicinity of the inlet portion 42 a of the heat transfer tube 42. Further, the refrigerant temperature sensor 82 is attached in the vicinity of the intermediate portion of the heat transfer tube 42. In this case, the refrigerant temperature sensor 82 is located near the boundary between the evaporator region 40a and the evaporator region 40b (the heat transfer tube 42 is located outside the end plate 41 between the sixth and seventh steps from the uppermost stage of the heat transfer tube 42). At the portion folded back 180 degrees). That is, the refrigerant temperature sensor 82 is attached in the vicinity of the position where the swash plate 60 that separates the evaporator region 40a and the evaporator region 40b is inserted. Further, the refrigerant temperature sensor 83 is attached in the vicinity of the outlet portion 42 b of the heat transfer tube 42. Therefore, the refrigerant temperature sensor 81 has a function of detecting the refrigerant temperature T1 that flows downstream of the electronic expansion valve 30 and flows into the evaporator region 40a, and the refrigerant temperature sensor 82 includes the evaporator region 40a and the evaporator region 40b. Has a function of detecting the refrigerant temperature T2 in the vicinity of the boundary. The refrigerant temperature sensor 83 has a function of detecting the refrigerant temperature T3 flowing out from the evaporator region 40b. Further, the refrigerant temperature sensors 81 to 83 are connected to the control unit 70 (see FIG. 6), respectively. The refrigerant temperature sensors 81 to 83 are examples of the “first refrigerant temperature detection unit”, “second refrigerant temperature detection unit”, and “third refrigerant temperature detection unit” of the present invention, respectively.

  In the present embodiment, during operation of the cooling device 100, the refrigerant temperature sensors 81 to 83 detect the evaporator 40 in a state where the evaporator 40 is separated into the evaporator region 40a and the evaporator region 40b by the swash plate 60. The opening degree of the electronic expansion valve 30 is controlled by the control unit 70 (see FIG. 6) based on the refrigerant temperature in the evaporator 40. Specifically, the superheat degree SH1 of the refrigerant in the evaporator region 40a based on the refrigerant temperature T1 detected by the refrigerant temperature sensor 81 and the refrigerant temperature T2 detected by the refrigerant temperature sensor 82 is 0 degrees or less (SH1 ≦ 0). ), And the superheat degree SH2 of the refrigerant in the evaporator region 40b is based on the refrigerant temperature T2 detected by the refrigerant temperature sensor 82 and the refrigerant temperature T3 detected by the refrigerant temperature sensor 83. The opening degree of the electronic expansion valve 30 is controlled so as to be a value larger than 0 degree (SH2> 0). The superheat degrees SH1 and SH2 are examples of the “first superheat degree” and the “second superheat degree” in the present invention, respectively.

  As shown in FIG. 2, an air temperature sensor 84 is attached to the main body 50 in the vicinity of the outlet 53 a corresponding to the outlet duct 53 c of the air passage 53, and also corresponds to the outlet duct 54 c of the air passage 54. An air temperature sensor 85 is attached in the vicinity of the outlet 54a. The air temperature sensor 84 circulates in the air passage 53 in the direction of arrow A and has a function of detecting the blown air temperature Ta of the air (cold air) supplied from the blowout port 53 a to the upper housing 51, and the air temperature sensor 85. Has a function of detecting the blown air temperature Tb of the air (cold air) supplied through the air passage 54 in the arrow B direction and supplied from the blowout port 54a to the lower housing 52. Air temperature sensors 84 and 85 are connected to control unit 70 (see FIG. 6). The blown air temperatures Ta and Tb are examples of the “detected temperature of the first housing portion” and the “detected temperature of the second housing portion” of the present invention, respectively.

  And in this embodiment, in addition to the opening degree control of the electronic expansion valve 30 mentioned above by the control part 70 during cooling operation, in addition to performing rotation speed control of the compressor 10 (refer FIG. 1), the upper storage 51 Is maintained at a low temperature set value TL (3 ° C. or higher and 8 ° C. or lower). That is, the control unit 70 maintains the refrigerant superheat degree SH1 in the evaporator region 40a based on the opening degree control of the electronic expansion valve 30 (see FIG. 1) with respect to the low temperature set value TL. The number of revolutions of the compressor 10 is adjusted based on the difference in the blown air temperature Ta from the evaporator region 40a (air passage 53) detected by the air temperature sensor 84, so that the cooling temperature of the upper storage 51 is set to a low temperature set value TL. (3 degreeC or more and 8 degrees C or less) It is comprised so that it may be maintained.

  In the present embodiment, in addition to the temperature control (rotational speed control of the compressor 10) on the upper storage 51 side described above, the lower storage 52 is set to the intermediate temperature set value TM by the opening degree control of the electronic expansion valve 30. (15 degreeC or more and 20 degrees C or less) It is comprised so that it may maintain. That is, the air temperature with respect to the intermediate temperature set value TM in a state where the control unit 70 maintains the superheat degree SH2 of the refrigerant in the evaporator region 40b at a value larger than 0 degrees based on the opening degree control of the electronic expansion valve 30. Based on the difference in the blown air temperature Tb from the evaporator region 40b (air passage 54) detected by the sensor 85, the cooling temperature of the lower storage 52 is maintained at the set value TM for medium temperature (15 ° C. or more and 20 ° C. or less). It is comprised so that.

  Thus, in the cooling device 100, only the adjustment of the air side heat exchange area (adjustment of the ratio of the heat transfer area between the evaporator region 40a and the evaporator region 40b in the evaporator 40) by the swash plate 60 is possible. First, the degree of opening of the electronic expansion valve 30 is controlled to adjust the heat exchange performance (cooling capacity) of the evaporator region 40b on the refrigerant side, and the number of revolutions of the compressor 10 is controlled to exchange heat in the evaporator region 40a. The performance (cooling capacity) is adjusted. As a result, the blown air temperature Ta from the evaporator region 40a and the blown air temperature Tb from the evaporator region 40b are made different from each other (Ta <Tb), and the upper storage 51 is set at the low temperature set value TL and lower. Control is performed so that the side storage 52 is cooled by the set value TM for medium temperature.

  As shown in FIGS. 2 and 5, in the showcase 2, the evaporator regions 40 a and 40 b are separated on the air side using the swash plate 60, but strictly speaking, the swash plate 60 There is a portion where a minute gap is generated at the contact interface between the slit portion 61 (see FIG. 4) and the fin member 43 (see FIG. 4). A very small amount of air (cold air) leaks from the evaporator region 40a side to the evaporator region 40b side through the minute gap, or leaks from the evaporator region 40b side to the evaporator region 40a side. there is a possibility. For this reason, in this embodiment, based on the detected values of the refrigerant temperature sensors 81 to 83 and the air temperature sensors 84 and 85, the opening degree of the electronic expansion valve 30 and the rotational speed of the compressor 10 are based on the above-described control method. Thus, even in a situation where the circulating air on one side slightly leaks from the gap between the swash plate 60 and the fin member 43 to the other side, the evaporating temperature (low pressure) on the refrigerant side and the degree of superheat Is controlled so that the blown air temperatures Ta and Tb fall within the respective set values. That is, even when the temperature adjustment of the cold air cannot be compensated only by adjusting the heat exchange area on the air side of the evaporator 40 by the swash plate 60, the cold air is added by the control on the refrigerant side (adjustment control of the refrigerant circulation amount). The temperature is adjusted more reliably. Therefore, the upper housing 51 has the low temperature set value TL and the lower housing without the blown air temperatures Ta and Tb being greatly affected by the air leaking from one side to the other through the gap of the swash plate 60. The storage 52 is stably maintained at the set value TM for medium temperature.

  Moreover, as a control structure of the cooling device 100, as shown in FIG. 6, in addition to the control part 70 which consists of CPU, ROM71 and RAM72 are provided. The control unit 70 makes a predetermined determination based on the input signals from the refrigerant temperature sensors 81 to 83 and the air temperature sensors 84 and 85, and the compressor 10 and the blower 21 that constitute the refrigerator 1, and the showcase. 2 is configured to appropriately control various functional components such as the electronic expansion valve 30 and the blowers 55 and 56 that constitute the component 2.

  In addition to the control program executed by the control unit 70, the ROM 71 includes an opening degree control table (not shown) used for opening degree control of the electronic expansion valve 30 and a frequency control table related to the rotational speed control of the compressor 10. (Not shown) and the like are stored. The opening degree control table defines a change amount (number of pulses) of the valve opening degree according to the values of the superheats SH1 and SH2 calculated from the refrigerant temperature sensors 81 to 83. The RAM 72 is used as a working memory for temporarily storing control parameters including a low temperature setting value TL and an intermediate temperature setting value TM used when the control program is executed.

  Next, a processing flow of the control unit 70 when the cooling operation is performed by the cooling device 100 according to the present embodiment will be described with reference to FIGS. In the following, the upper storage 51 of the showcase 2 is set to the low temperature set value TL (any temperature between 3 ° C. and 8 ° C.) and the lower storage 52 is set to the intermediate temperature set value TM ( The control contents after the cooling device 100 starts the cooling operation in the state set to any temperature between 15 ° C. and 20 ° C. will be described.

  As shown in FIG. 7, first, in step S1, the refrigerant temperatures T1 to T3 of the refrigerant flowing through the evaporator 40 are acquired by the control unit 70 (see FIG. 6). That is, as shown in FIG. 3, the refrigerant temperature T1 near the inlet 42a of the heat transfer tube 42 by the refrigerant temperature sensor 81, the refrigerant temperature T2 near the intermediate portion of the heat transfer pipe 42 by the refrigerant temperature sensor 82, and the refrigerant temperature sensor 83 The refrigerant temperature T3 in the vicinity of the outlet portion 42b of the heat transfer tube 42 is acquired.

  In step S2, as shown in FIG. 7, it is determined whether or not the superheat degree SH1 (= T2-T1) of the refrigerant in the vicinity of the intermediate portion of the heat transfer tube 42 is 0 degrees or less (SH1 ≦ 0). It is judged by. If it is determined in step S2 that the superheat degree SH1 is greater than 0 degree (SH1> 0), the process proceeds to step S3, and the opening of the electronic expansion valve 30 (see FIG. 6) is increased by a predetermined amount. Is done. That is, in the degree of superheat SH1> 0, the refrigerant completion point of the refrigerant exists in a position closer to the inlet part 42a than the vicinity of the intermediate part to which the refrigerant temperature sensor 82 of the evaporator 40 (heat transfer tube 42) is attached. As the refrigerant is vaporized (gasified) between the evaporation completion point in the evaporator 40 and the vicinity of the intermediate portion, the heat exchange performance in this section is reduced, and the refrigerant in the evaporator region 40a (see FIG. 3). The heat exchange performance (cooling capacity) on the side is not sufficiently exhibited. Therefore, control is performed to increase the refrigerant flow rate by increasing the opening of the electronic expansion valve 30 by a predetermined amount. Specifically, the control signal corresponding to the number of pulses for changing the opening degree of the electronic expansion valve 30 from the current state to the opening degree larger by a predetermined amount with respect to the stepping motor 31 (see FIG. 1) from the control unit 70. Is sent. Thereby, the stepping motor 31 is rotated, and the opening degree of the electronic expansion valve 30 is increased. The cooling device 100 continues the cooling operation in a state where the electronic expansion valve 30 is increased by a predetermined amount.

  Further, when it is determined in step S2 that the current superheat degree SH1 is 0 degrees or less (gas-liquid two-phase state), the heat exchange performance (cooling capacity) on the refrigerant side of the evaporator region 40a and the evaporator region 40b. ), The flow proceeds to the flow after step S4.

  First, in step S <b> 4, the current blown air temperature Ta supplied from the air passage 53 (see FIG. 2) to the upper storage 51 is acquired by the control unit 70. In step S5, the set temperature for the upper storage 51 (see FIG. 2) stored in the RAM 72 (see FIG. 6) and previously grasped by the control unit 70 (low temperature setting in the range of 3 ° C. to 8 ° C.). The value TL) and the current blown air temperature Ta are compared by the control unit 70. That is, the control unit 70 determines whether or not the difference ΔT1 (= Ta−TL) between the set temperature (low temperature set value TL) and the blown air temperature Ta is zero. If it is determined that ΔT1 is not substantially equal to 0 (ΔT1≈0 other than 0), the process proceeds to step S6, and whether ΔT1 is positive or negative is determined.

  If it is determined in step S6 that ΔT1> 0 (the blown air temperature Ta is higher than the low temperature setting value TL), the rotational speed of the compressor 10 is increased by a predetermined amount in step S7. That is, a control signal corresponding to a frequency for changing the rotational speed of the compressor 10 from the current state to a rotational speed higher by a predetermined amount is transmitted from the control unit 70 to an electric motor (not shown). Thereby, a rotation frequency is changed and the rotation speed of the compressor 10 is increased. If it is determined in step S6 that ΔT1 <0 (the blown air temperature Ta is lower than the low temperature setting value TL), the rotational speed of the compressor 10 is decreased by a predetermined amount in step S8. That is, a control signal corresponding to a frequency for changing the rotational speed of the compressor 10 from the current state to a rotational speed lower by a predetermined amount is transmitted from the control unit 70 to an electric motor (not shown). Thereby, a rotation frequency is changed and the rotation speed of the compressor 10 is reduced.

  In step S5, the set temperature (low temperature set value TL in the range of 3 ° C. to 8 ° C.) and the blown air temperature Ta are substantially equal (ΔT1 is 0 or a value in the vicinity thereof: ΔT1≈0). If it is determined, the rotational speed of the compressor 10 is maintained at the current value, and the process proceeds to step S9. As described above, in this embodiment, the superheat degree SH1 in the evaporator region 40a is maintained at 0 degrees or less based on the opening degree control of the electronic expansion valve 30, and from the evaporator region 40a with respect to the low temperature set value TL. Control is performed to change the rotational speed of the compressor 10 based on the difference ΔT1 in the blown air temperature Ta to maintain the upper storage 51 at the low temperature set value TL. In addition, the change width of the rotation speed of the compressor 10 differs according to the magnitude of ΔT1. When ΔT1 is relatively small, the change range of the rotation speed of the compressor 10 is also relatively small, and when ΔT1 is relatively large, the change width of the rotation speed of the compressor 10 is also relatively large.

  Thereafter, in step S <b> 9, the current blown air temperature Tb supplied from the air passage 54 (see FIG. 2) to the lower storage 52 is acquired by the control unit 70.

  In step S10, the set temperature (the set value TM for medium temperature in the range of 15 ° C. to 20 ° C.) of the lower storage 52 (see FIG. 2) stored in the RAM 72 and previously grasped by the control unit 70 The current blown air temperature Tb is compared by the control unit 70. That is, the control unit 70 determines whether or not the difference ΔT2 (= Tb−TM) between the set temperature (medium temperature set value TM) and the blown air temperature Tb is zero. If it is determined that ΔT2 is not approximately equal to 0 (ΔT2≈other than 0), the process proceeds to step S11, and whether ΔT2 is positive or negative is determined.

  If it is determined in step S11 that ΔT2> 0 (the blown air temperature Tb is higher than the intermediate temperature setting value TM), the opening degree of the electronic expansion valve 30 is increased by a predetermined amount in step S12. That is, a control signal corresponding to the number of pulses for changing the opening of the electronic expansion valve 30 from the current state to a larger opening by a predetermined amount is transmitted from the control unit 70 to the stepping motor 31. The opening is increased. If it is determined in step S11 that ΔT2 <0 (the blown air temperature Tb is lower than the intermediate temperature setting value TM), the opening degree of the electronic expansion valve 30 is decreased by a predetermined amount in step S13. . That is, a control signal corresponding to the number of pulses for changing the opening of the electronic expansion valve 30 from the current state to an opening smaller by a predetermined amount is transmitted from the control unit 70 to the stepping motor 31. The opening is reduced. As described above, the refrigerant in the evaporator region 40b (see FIG. 2) is controlled by controlling the flow rate of the refrigerant flowing through the evaporator 40 (heat transfer pipe 42) by controlling the opening degree of the electronic expansion valve 30 based on the positive / negative of the difference ΔT2. The heat exchange performance (cooling capacity) on the side is adjusted.

  If it is determined in step S10 that the set temperature (the set value TM for medium temperature) and the blown air temperature Tb are substantially equal (ΔT2 is 0 or a value in the vicinity thereof: ΔT2≈0), the electronic expansion is performed. The opening degree of the valve 30 is maintained at the current value, and this control flow ends. After the completion of the control flow, the control flow shown in FIG. 7 is executed again after a predetermined control period has elapsed. In this manner, the opening degree control of the electronic expansion valve 30 is performed by the control unit 70 during the cooling operation.

  In the present embodiment, as described above, the single evaporator 40, the evaporator region 40a that cools the upper storage 51 to the low temperature set value TL, and the lower storage 52 that has the intermediate temperature that is different from the low temperature set value TL. By providing a swash plate 60 that is inserted into the evaporator 40 so as to be separated into an evaporator region 40b that is cooled to the set value TM for use, the single evaporator 40 can be made into the evaporator region by the swash plate 60 40a and the evaporator region 40b are separated, the evaporator region 40a and the evaporator region 40b can be provided independently without communicating with each other. Accordingly, the upper storage 51 is cooled to the low temperature set value TL using the evaporator region 40a, and the lower storage 52 is cooled to the intermediate temperature set value TM using the evaporator region 40b. Can be performed independently without affecting each other in the evaporator region 40a and the evaporator region 40b. Therefore, only the evaporator region 40a is involved in cooling the upper storage 51 and the evaporator region. 40b is not affected, and only the evaporator region 40b is involved in cooling the lower storage 52, and the evaporator region 40a is not affected. As a result, even when a single evaporator 40 is used, the cooling temperature (low temperature setting value TL) of the upper storage 51 and the cooling temperature (intermediate temperature setting value) of the lower storage 52 that are cooled to different temperatures. TM) can be maintained stably together.

  In the present embodiment, the air passage 53 corresponding to the evaporator region 40 a and the air passage 54 corresponding to the evaporator region 40 b are formed inside the single evaporator 40 with the swash plate 60 interposed therebetween. Then, the upper housing 51 is cooled to the low temperature set value TL by the air blown from the air passage 53 (air outlet 53a), and the lower housing 52 is kept at a medium temperature by the air blown from the air passage 54 (air outlet 54a). It is configured to cool to the set value TM. As a result, the single evaporator 40 is separated by the swash plate 60 from the air passage 53 corresponding to the evaporator region 40a and the air passage 54 corresponding to the evaporator region 40b without communicating with each other. The air blown from 53 can be guided only to the upper storage 51 to easily maintain the upper storage 51 at the low temperature set value TL, and the air blown from the air passage 54 is guided only to the lower storage 52. Thus, the lower storage 52 can be easily maintained at the set value TM for medium temperature.

  Further, in the present embodiment, the swash plate 60 is configured so that the insertion position in the evaporator 40 can be changed, and the evaporator region 40a in the evaporator 40 and the evaporation are evaporated according to the insertion position of the swash plate 60. By changing the ratio of the heat exchanger area (heat transfer area) to the evaporator area 40b, the cooling temperature of the upper storage 51 cooled by the evaporator area 40a and the lower storage cooled by the evaporator area 40b The temperature relationship with the cooling temperature of the storage 52 (in this embodiment, a relationship where the low temperature setting value TL <the intermediate temperature setting value TM) is configured to be changeable. Accordingly, the low temperature setting value TL of the upper storage 51 and the intermediate temperature setting value TM of the lower storage 52 are moved closer to or away from each other by changing the insertion position of the swash plate 60 with respect to the evaporator 40. Can do. Furthermore, depending on the insertion position of the swash plate 60, the low temperature set value TL is made lower than the medium temperature set value TM, or conversely, the low temperature set value TL (first temperature) is set to the medium temperature set value TM ( It can also be raised above the second temperature. As a result, the cooling temperature of the upper storage 51 and the cooling temperature of the lower storage 52 can be set to a desired temperature relationship, respectively, and the cooling temperature of the upper storage 51 and the desired temperature relationship can be maintained. Both cooling temperatures of the lower storage 52 can be stably maintained.

  In the present embodiment, the evaporator 40 includes a heat transfer tube 42 through which the refrigerant flows, and a plate-like fin member 43 that is attached to the surface of the heat transfer tube 42 with a predetermined interval. 60 is formed in a comb-like shape having slit portions 61 formed corresponding to each of the plurality of fin members 43. And the single evaporator 40 is made into the evaporator area | region 40a by inserting the comb-tooth-shaped oblique wind plate 60 in the inside of the evaporator 40 in the state by which the fin member 43 was inserted | pinched by the thickness direction by the slit part 61. FIG. It isolate | separates into the evaporator area | region 40b. Accordingly, the comb-like oblique wind plate 60 having a plurality of slit portions 61 is easily inserted into the plate fin type evaporator 40 to reliably separate the evaporator region 40a and the evaporator region 40b. can do. Further, the swash plate 60 is inserted into the evaporator 40 by inserting the swash plate 60 into the evaporator 40 with the plurality of slit portions 61 sandwiching the fin members 43 corresponding to the respective slit portions 61 in the thickness direction. It can be held stably.

  Moreover, in this embodiment, the refrigerant | coolant temperature sensors 81-83 which detect the refrigerant | coolant temperature of the evaporator 40, the electronic expansion valve 30 which controls the quantity of the refrigerant | coolant which flows into the evaporator 40 according to an opening degree, and an electronic expansion valve The control part 70 which controls the opening degree of 30 is provided. The evaporator 40 detected by the refrigerant temperature sensors 81 to 83 in a state where the evaporator 40 is separated into the evaporator region 40a (air passage 53) and the evaporator region 40b (air passage 54) by the swash plate 60. By changing the opening of the electronic expansion valve 30 based on the refrigerant temperature T1 to T3 of 40 and controlling the refrigerant flow rate, the blown air temperature Ta from the evaporator region 40a and the blown air temperature Tb from the evaporator region 40b are controlled. Are configured to be different from each other, and the control unit 70 is configured to control cooling the upper storage 51 with the low temperature set value TL and the lower storage 52 with the intermediate temperature set value TM. Thus, if the single evaporator 40 is separated into the evaporator area 40a and the evaporator area 40b by the swash plate 60, the air passage 53 and the air passage 54 (air-side circulation flow path) can be configured. In this state, the flow rate adjustment (opening control of the electronic expansion valve 30) on the refrigerant side based on the refrigerant temperatures T1 to T3 of the evaporator 40 detected by the refrigerant temperature sensors 81 to 83 is further performed, whereby the upper housing is accommodated. The storage 51 can be easily controlled to the low temperature setting value TL, and the lower storage 52 can be easily controlled to the intermediate temperature setting value TM.

  Further, in the present embodiment, the evaporator 40 is configured so that the refrigerant after flowing through the evaporator region 40a flows through the evaporator region 40b, and is located downstream of the electronic expansion valve 30 and in the evaporator region 40a. A refrigerant temperature sensor 81 that detects the refrigerant temperature T1 that flows in; a refrigerant temperature sensor 82 that is disposed in the vicinity of the swash plate 60 and that detects the refrigerant temperature T2 in the vicinity of the boundary between the evaporator region 40a and the evaporator region 40b; A refrigerant temperature sensor 83 for detecting the refrigerant temperature T3 flowing out from the evaporator region 40b is provided. And the superheat degree SH1 of the refrigerant | coolant in the evaporator area | region 40a based on the refrigerant | coolant temperature T1 detected by the refrigerant | coolant temperature sensor 81 and the refrigerant | coolant temperature T2 detected by the refrigerant | coolant temperature sensor 82 will be in the gas-liquid two-phase state of 0 degree | times or less. And the superheat degree SH2 of the refrigerant in the evaporator region 40b based on the refrigerant temperature T2 detected by the refrigerant temperature sensor 82 and the refrigerant temperature T3 detected by the refrigerant temperature sensor 83 becomes a value larger than 0 degrees. Thus, the control unit 70 is configured to control the opening degree of the electronic expansion valve 30. Accordingly, the upper storage 51 can be easily and stably maintained at the low temperature set value TL, and the lower storage 52 can be easily and stably maintained at the intermediate temperature set value TM. . Further, in the case of showcase 2 (see FIG. 2), a relatively large cooling capacity can be generated in the evaporator region 40a and a relatively small cooling capacity can be generated in the evaporator region 40b. The blown air temperature Ta from the evaporator region 40a can be lowered more easily than the blown air temperature Tb from the evaporator region 40b.

  Moreover, in this embodiment, the compressor 10 which can control refrigerant | coolant discharge amount by the change of rotation speed is provided. The upper storage 51 is maintained at the low temperature set value TL (3 ° C. or more and 8 ° C. or less) by the opening control of the electronic expansion valve 30 and the rotation speed control of the compressor 10, and the opening of the electronic expansion valve 30 is controlled. The control unit 70 is configured to perform control to maintain the lower storage 52 at the intermediate temperature setting value TM (15 ° C. or more and 20 ° C. or less) by the control. As a result, when it is difficult to maintain the upper storage 51 at the low temperature set value TL only by controlling the opening degree of the electronic expansion valve 30, the refrigerant circulation amount is changed along with the change in the rotation speed of the compressor 10 to evaporate. It is possible to easily adjust the heat exchange capacity (cooling capacity) of the evaporator area 40a by adjusting the evaporation temperature of the refrigerant in the evaporator area 40a. The heat exchange capacity (cooling capacity) of the evaporator area 40b can be adjusted by controlling the degree of superheat of the refrigerant by controlling the opening degree of the electronic expansion valve 30 within a range in which the heat exchange capacity of the evaporator area 40a can be adjusted. . Thereby, the cooling temperature (low temperature setting value TL) of the upper storage 51 and the cooling temperature (medium temperature setting value TM) of the lower storage 52 can be adjusted more accurately.

  In the present embodiment, the refrigerant superheat degree SH1 in the evaporator region 40a is maintained at 0 degrees or less (SH1 ≦ 0) based on the opening degree control of the electronic expansion valve 30. While changing the rotation speed of the compressor 10 based on the difference ΔT1 of the blown air temperature Ta from the evaporator region 40a, the upper storage 51 is maintained at the low temperature setting value TL (3 ° C. or more and 8 ° C. or less), and the electronic In the state where the superheat degree SH2 of the refrigerant in the evaporator region 40b is maintained at a value larger than 0 degree (SH2> 0) based on the opening degree control of the expansion valve 30, from the evaporator region 40b with respect to the intermediate temperature set value TM Based on the difference ΔT2 in the blown air temperature Tb, the control unit 70 is configured to perform control to maintain the lower storage 52 at the intermediate temperature setting value TM (15 ° C. or more and 20 ° C. or less). Thus, a desired cooling capacity for maintaining the upper storage 51 at the low temperature set value TL is obtained in the evaporator region 40a by changing the refrigerant circulation amount accompanying the change in the rotation speed of the compressor 10, and the electronic expansion valve 30 is obtained. By controlling the opening degree, it is possible to obtain a desired cooling capacity for maintaining the lower housing 52 at the intermediate temperature set value TM also in the evaporator region 40b. As a result, the cooling temperature of the upper storage 51 (low temperature setting value TL) and the cooling temperature of the lower storage 52 (medium temperature setting value TM) can be adjusted more accurately.

  Moreover, in this embodiment, the evaporator area | region 40a in the evaporator 40 is arrange | positioned above the evaporator area | region 40b with the swash plate 60. FIG. And the slanted wind plate 60 in the evaporator 40 in the state which has the inclination angle which can discharge | emit the molten water at the time of melting | dissolving the frost which generate | occur | produced in the evaporator area | region 40a with the cooling operation toward the lower evaporator area | region 40b. Is installed. As a result, even when the operation for removing frost generated in the evaporator region 40a (defrost operation) is performed during the operation of the cooling device 100, the inclination installed at the inside of the evaporator 40 with an inclination angle. The melted water (drain water) can flow along the upper surface 60a of the oblique wind plate 60 without being retained in the evaporator region 40a by the wind plate 60 and drained downward. Therefore, even if the frost removal operation is performed in a state in which the single evaporator 40 is partitioned by the swash plate 60, the molten water (drain water) is heat exchange performance (cooling capacity) of the evaporator region 40a. Stable cooling operation can be continued without affecting the operation.

(First modification)
Next, with reference to FIG. 2 and FIGS. 6-8, the 1st modification of the said embodiment is demonstrated. In the first modification, an example in which the heat exchange area (heat transfer area) of the evaporator region 240b is configured to be larger than the heat exchange area of the evaporator region 240a by changing the insertion position of the swash plate 60 will be described. To do. The evaporator regions 240a and 240b are examples of the “first evaporator region” and the “second evaporator region” in the present invention, respectively. In the drawing, the same reference numerals as those in the above embodiment are attached to the same components as those in the above embodiment.

  In the showcase 202 according to the first modification of the embodiment of the present invention, as shown in FIG. 8, the mounting position in the height direction (Z direction) of the evaporator 40 inside the main body 50 is set to the showcase 2 (FIG. 2). Reference) is moved downward (Z1 direction). Here, the size of the upper storage 51 and the lower storage 52 is the same as in the case of the showcase 2, and the layout of the air passages 53 and 54 that separate the upper storage 51 and the lower storage 52 is also used. It has not changed. Therefore, the insertion position in the height direction (Z direction) of the swash plate 60 is moved relatively closer to the upper side of the evaporator 40 than in the case of the showcase 2 (see FIG. 2). In this case, the swash plate 60 is inserted between the third and fourth stages from the uppermost stage of the heat transfer tube 42. As a result, the single evaporator 40 is divided into an evaporator region 240a (upper region having a relatively small heat transfer area) corresponding to three stages of the heat transfer tubes 42 and the remaining seven stages of the heat transfer tubes 42. It is separated on the air side into a corresponding evaporator region 240b (a lower region having a relatively large heat transfer area).

  Therefore, the showcase 202 is configured such that the upper storage 51 is cooled to the intermediate temperature set value TM by the cold air that flows through the air passage 53 and is cooled by the evaporator region 240a having a relatively small heat exchange area. Has been. On the other hand, the lower housing 52 is cooled to the low temperature set value TL by the cool air that flows through the air passage 54 and is cooled by the evaporator region 240b having a relatively large heat exchange area. . In the first modification, the intermediate temperature setting value TM that is the refrigeration temperature of the upper storage 51 and the low temperature setting value TL that is the refrigeration temperature of the lower storage 52 are respectively “first temperature” of the present invention. ”And“ second temperature ”.

  The opening degree control of the electronic expansion valve 30 (see FIG. 6) and the compressor 10 (see FIG. 6) based on the detection values of the refrigerant temperature sensors 81 to 83 (see FIG. 6) and the air temperature sensors 84 and 85 (see FIG. 6). 6), the same control content as the control content described in the above embodiment (the control processing flow from step S1 to S13 shown in FIG. 7) is applied. Further, the refrigerant temperature sensor 82 is moved along with the change of the insertion position of the swash plate 60, and near the boundary between the evaporator region 240a and the evaporator region 240b (the third and fourth stages from the uppermost stage of the heat transfer tube 42). The heat transfer tube 42 is configured to detect a refrigerant temperature T2 in a portion where the heat transfer tube 42 is folded 180 degrees outside the end plate 41.

  And in the 1st modification, in the state where superheat degree SH1 of the refrigerant in evaporator field 240a was maintained below 0 degrees by control part 70 (refer to Drawing 6) based on opening control of electronic expansion valve 30, The compressor based on the difference ΔT1 (= Ta−TM) of the air temperature Ta discharged from the evaporator region 240a (air passage 53) detected by the air temperature sensor 84 with respect to the set value TM for medium temperature (15 ° C. to 20 ° C.). The upper housing 51 is configured to be maintained at the intermediate temperature set value TM by changing the number of rotations of ten. Furthermore, the low temperature set value TL (3 (3) is maintained in a state where the control unit 70 maintains the superheat degree SH2 of the refrigerant in the evaporator region 240b at a value larger than 0 degrees based on the opening degree control of the electronic expansion valve 30. The lower storage 52 is set for low temperature based on the difference ΔT2 (= Tb−TL) of the blown air temperature Tb from the evaporator region 240b (air passage 54) detected by the air temperature sensor 85 with respect to (° C. to 8 ° C.). It is configured to be maintained at the value TL. In addition, about the other structure of the showcase 202 in a 1st modification, it is the same as that of the said embodiment.

  In the first modification, the ratio of the heat exchange area between the evaporator region 240a and the evaporator region 240b in the evaporator 40 is changed by changing the insertion position of the swash plate 60 with respect to the evaporator 40 as described above. The upper storage 51 is changed to be maintained at the intermediate temperature setting value TM, and the lower storage 52 is maintained at the low temperature setting value TL. As described above, the cooling temperature of the upper storage 51 (intermediate temperature setting value TM) and the cooling temperature of the lower storage 52 (low temperature setting value TL) can be set by simply changing the insertion position of the swash plate 60. The temperature relationship can be set, and the cooling temperature of the upper storage 51 and the cooling temperature of the lower storage 52 can both be stably maintained while maintaining the desired temperature relationship.

(Second modification)
Next, with reference to FIG. 2 and FIGS. 6-9, the 2nd modification of the said embodiment is demonstrated. In the second modification, the height position of the suction duct portion 53c in the air passage 53 and the height of the outlet duct portion 54c in the air passage 54 are changed without changing the fixing position of the evaporator 40 in the height direction (Z direction). Thus, an example in which the heat exchange area of the evaporator region 240b is configured to be larger than the heat exchange area of the evaporator region 240a will be described. In the drawing, the same reference numerals as those in the above embodiment are attached to the same components as those in the above embodiment.

  In the showcase 302 according to the second modification of the embodiment of the present invention, as shown in FIG. 9, the attachment position of the evaporator 40 is the same as that of the showcase 2 (see FIG. 2), while the suction duct Both the formation position (height position) of the portion 53c and the blowing duct portion 54c are moved upward (Z2 direction). Thereby, the swash plate 60 is inserted between the third and fourth stages from the uppermost stage of the heat transfer tube 42 in the evaporator 40, and the upper side of the case of the showcase 202 (see FIG. 8). The storage volume of the storage 351 is smaller than that of the upper storage 51 and the storage volume of the lower storage 352 is configured to be larger than that of the lower storage 52.

  Therefore, in the showcase 302, the upper storage 351 is cooled to the intermediate temperature set value TM by the cool air that is circulated through the air passage 53 and cooled by the evaporator region 240a having a relatively small heat exchange area (heat transfer area). In addition, the lower storage 352 is configured to be cooled to the low temperature set value TL by the cool air that is circulated through the air passage 54 and cooled by the evaporator region 240b having a relatively large heat exchange area. . The upper storage 351 and the lower storage 352 are examples of the “first storage unit” and the “second storage unit” of the present invention, respectively. In the second modification, the intermediate temperature setting value TM that is the refrigeration temperature of the upper storage 351 and the low temperature setting value TL that is the refrigeration temperature of the lower storage 352 are the “first temperature” of the present invention. ”And“ second temperature ”.

  The opening degree control of the electronic expansion valve 30 (see FIG. 6) and the compressor 10 (see FIG. 6) based on the detection values of the refrigerant temperature sensors 81 to 83 (see FIG. 6) and the air temperature sensors 84 and 85 (see FIG. 6). 6), the same control content as the control content described in the above embodiment (the control processing flow from step S1 to S13 shown in FIG. 7) is applied. In addition, about the other structure of the showcase 302 in a 2nd modification, it is the same as that of the said 1st modification.

  In the second modification, as described above, the ratio of the heat exchange area between the evaporator region 240a and the evaporator region 240b in the evaporator 40 is changed by changing the insertion position of the swash plate 60, and the upper side. The storage 351 is maintained at the intermediate temperature set value TM, and the lower storage 352 is maintained at the low temperature set value TL. Therefore, a desired temperature relationship between the cooling temperature of the upper storage 351 (medium temperature setting value TM) and the cooling temperature of the lower storage 352 (low temperature setting value TL) simply by changing the insertion position of the swash plate 60. In addition, both the cooling temperature of the upper storage 351 and the cooling temperature of the lower storage 352 can be stably maintained while maintaining a desired temperature relationship.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is shown not by the above description of the embodiments but by the scope of claims for patent, and further includes all modifications within the meaning and scope equivalent to the scope of claims for patent.

  For example, in the first embodiment and the first and second modifications of the above embodiment, a refrigerator (outdoor unit) 1 disposed outdoors is connected to a showcase 2 (202, 302) in a store. Although the example which comprised the cooling device 100 was shown, this invention is not limited to this. That is, the present invention is applied to a so-called refrigerator built-in type (integrated type) cooling device in which a refrigerator unit (condensing unit) including the compressor 10 and the gas cooler 20 is built in the showcase 2 (202, 302). The invention may be applied.

  Moreover, in the said embodiment, the 1st modification of the said embodiment, and the 2nd modification, the example which comprised the piping connection of one showcase (evaporator 40) with respect to the one refrigerator 1, and comprised the cooling device 100 However, the present invention is not limited to this. The present invention may be applied to a cooling device in which a plurality of showcases 2 (202, 302) are connected in parallel to one refrigerator 1.

  In the above embodiment, the first temperature of the present invention (low temperature set value TL) is in the range of 3 ° C. to 8 ° C. and the second temperature of the present invention (medium temperature set value TM) is 15 ° C. to 20 ° C. Although an example in which the temperature is in the range of ° C. or lower is shown, the present invention is not limited to this. As the set value ranges of the first temperature and the second temperature, ranges other than those described above may be applied to each. In the first and second modifications of the above embodiment, the first temperature of the present invention (medium temperature setpoint TM) is set in the range of 15 ° C. to 20 ° C. and the second temperature of the present invention (low temperature). Although the example in which the set value TL) is in the range of 3 ° C. or more and 8 ° C. or less is shown, other ranges may be applied to each as in the above case.

  Moreover, in the said embodiment and the 1st modification of the said embodiment, and a 2nd modification, goods 101 and 102 can store the upper storage 51 (351) and the lower storage 52 (352) which can be stored at mutually different refrigeration temperatures. However, the present invention is not limited to this example. If it is a cooling device provided with the 1st storage part and the 2nd storage part which can store goods at mutually different refrigeration temperature or freezing temperature, for example, ice creams which need frozen storage in the 1st storage part other than a showcase Applying the present invention to a cooling device such as a vending machine capable of displaying (storing) and ice confectionery and displaying and selling cold beverage (can beverage) products that require refrigerated storage in the second storage unit Also good. The showcase 2 (202, 302) is not limited to an open type in which the front side of the main body 50 is opened, but may be a closed type having an open / close door that is opened and closed when a product is taken out. Further, the present invention may be applied to a showcase in which an open type and a closed type are mixed.

  Moreover, in the said embodiment and the 1st modification of the said embodiment, and the 2nd modification, it showed about the example which comprised the swash plate 60 using the resin material which can be expanded and contracted a little, but this invention is shown to this. Not limited. Depending on the size of the evaporator 40 (distance between the end plates 41), the swash plate 60 may be formed using a metal material such as an aluminum plate or a stainless plate.

  Moreover, in the said embodiment, the 1st modification of the said embodiment, and a 2nd modification, in the state in which the cross section had a substantially linear shape, without bending the swash plate 60 along the front-back direction (bending down). Although an example in which the evaporator 40 is inserted and fixed in the oblique direction is shown, the present invention is not limited to this. For example, the swash plate 160 may be configured as in the third modification shown in FIG. Specifically, as shown in FIG. 10, the swash plate 160 has a tip portion side (Y2 side) obliquely downward, starting from the middle of a comb tooth portion 162 formed in a comb tooth shape (see FIG. 4). It is formed so as to have a bent portion 163 that bends. Even if the swash plate 160 having such a bent portion 163 is inserted into the evaporator 40, the upper surface 160a of the swash plate 160 is inclined downward at the bent portion 163, so that frost melt water (drain water). Can be effectively discharged. In the third modification, the bent portion 163 is linearly inclined, but the bent portion may have a gentle curve (curved surface) shape so as to hang downward. Further, the upper surface 160a may be continuously formed with a gentle curve (curved surface) from the front side toward the inside of the evaporator 40 without actively providing the bent portion 163. The swash plate 160 is an example of the “partition member” in the present invention.

  Moreover, although the said embodiment showed about the example which comprised the showcase 2 so that the upper side container 51 might be cooled to the setting value TL for low temperature, and the lower side container 52 might be cooled to the setting value TM for medium temperature, this book The invention is not limited to this. Depending on the product, the showcase 2 may be configured so that the upper storage 51 (first storage) is cooled while the lower storage 52 (second storage) is not cooled. In this case, for the evaporator region 40a (first evaporator region) in the evaporator 40, the “first superheat degree” of the present invention is set to around 0 degrees (first superheat degree≈0 degrees: almost no superheat degree) ) While controlling the “second superheat degree” of the present invention to a value larger than 0 degree (state of superheated steam) for the evaporator area 40b (second evaporator area). It is possible to control the air temperature such that the lower housing 52 (second housing portion) is hardly cooled by making 40b hardly function. Here, as a method of maintaining the superheat degree (first superheat degree) of the evaporator region 40a in the vicinity of 0 degree, it may be maintained in the vicinity of 0 degree only by the opening degree control of the electronic expansion valve 30, or the electronic expansion. The opening degree control of the valve 30 and the rotation speed control of the compressor 10 may be used in combination and maintained near 0 degrees. In addition, when the rotation speed control of the latter compressor 10 is used in combination, the first superheat degree can be more stably maintained in the vicinity of 0 degrees, and accordingly, the heat exchange effective area (evaporation) of the evaporator region 40a is correspondingly increased. The operation state in which the inside of the heat transfer tube 42 in the vessel region 40a is in a gas-liquid two-phase state and the heat transfer area effective for heat exchange is ensured as much as possible. That is, when the same cooling capacity is obtained, the number of revolutions of the compressor 10 is decreased (the evaporation temperature of the refrigerant is increased), so that the power consumption of the cooling device 100 can be reduced.

  Moreover, in the said embodiment, the 1st modification of the said embodiment, and a 2nd modification, while using the air temperature sensor 84, while detecting the blowing air temperature Ta of the air supplied to the upper storage 51 (351), An example in which the air temperature sensor 85 is used to detect the blown air temperature Tb of the air supplied to the lower storage 52 (352) and to control the temperature of the low temperature set value TL and the intermediate temperature set value TM. However, the present invention is not limited to this. You may attach not only the blowing air temperature but the air temperature sensor 84 (85) in the position which can detect the predetermined temperature in the upper side storage 51 (lower side storage 52). For example, the temperature of each container may be controlled by detecting the air temperature near the bottom 51a (52a), or the temperature control of each container by detecting the air temperature near the ceiling 51b (52b). May be performed. Furthermore, the temperature of each container may be controlled by detecting the air temperature near the wall 51c (52c) on the back side (Y2 side) of the product 101 (102).

  Moreover, in the said embodiment, the 1st modification of the said embodiment, and a 2nd modification, it shows about the example which installed the evaporator 40 in the vertical installation state along the direction (up-down direction) where the air passages 53 and 54 extend. However, the present invention is not limited to this. Depending on the duct shape of the air passages 53 and 54 inside the showcase 2, the evaporator 40 may be installed obliquely with respect to the vertical direction (Z direction). Also, the number of heat transfer tubes 42 of the evaporator 40 (the number of coils and the number of rows) is not limited. Further, the refrigerant flowing out of the electronic expansion valve 30 flows through the evaporator region 40a (first evaporator region), and further, the refrigerant after flowing through the evaporator region 40a flows through the evaporator region 40b (second evaporator region). If it is the evaporator 40 comprised so, the flow path layout of the heat exchanger tube (evaporation pipe) 42 inside the evaporator 40 is not ask | required.

  Moreover, in the said embodiment, the 1st modification of the said embodiment, and a 2nd modification, it evaporates so that a refrigerant | coolant may distribute | circulate from the upper stage side to the lower stage side in the heat exchanger tube (evaporation pipe) 42 which comprises a refrigerant flow path. Although the example which comprised the container 40 was shown, this invention is not limited to this. The evaporator 40 may be configured such that the refrigerant that has flowed out of the electronic expansion valve 30 flows from the lower stage side to the upper stage side in the heat transfer tube 42.

  Moreover, although the said embodiment, the 1st modification of the said embodiment, and the 2nd modification showed about the example which operates the cooling device 100 using a carbon dioxide refrigerant, this invention is not limited to this. A natural refrigerant other than the carbon dioxide refrigerant may be used, or an alternative chlorofluorocarbon refrigerant having an ozone layer depletion coefficient of zero may be used.

  Moreover, in the said embodiment and the 1st modification of the said embodiment, and a 2nd modification, the flow drive which processes the control process regarding the driving | operation of the cooling device 100 of the control part 70 in order along a process flow for convenience of explanation. Although described using the flowchart of the mold, the present invention is not limited to this. In the present invention, the processing of the control unit 70 may be performed by event driven type (event driven type) processing that executes processing in units of events. In this case, it may be performed by a complete event drive type or a combination of event drive and flow drive.

DESCRIPTION OF SYMBOLS 1 Refrigerator 2, 202, 302 Showcase 10 Compressor 30 Electronic expansion valve 40 Evaporator 40a, 240a Evaporator area | region (1st evaporator area | region)
40b, 240b Evaporator area (second evaporator area)
42 Heat transfer tubes 43 Fin members 51, 351 Upper housing (first housing)
52, 352 Lower storage (second storage)
53 Air passage (first ventilation passage)
54 Air passage (second ventilation passage)
60, 160 Oblique plate (partition member)
61 Slit part 70 Control part 81 Refrigerant temperature sensor (1st refrigerant | coolant temperature detection part)
82 Refrigerant temperature sensor (second refrigerant temperature detector)
83 Refrigerant temperature sensor (third refrigerant temperature detector)
100 Cooling device 101, 102 Product TL Low temperature setting value (first temperature, second temperature)
TM Medium temperature setpoint (first temperature, second temperature)
Ta blown air temperature (detected temperature of the first housing part)
Tb blown air temperature (detected temperature of the second housing part)
SH1 Superheat (first superheat)
SH2 Superheat (second superheat)

Claims (10)

A single evaporator configured to be able to cool the first storage portion and the second storage portion;
A first evaporator region that cools the first storage unit to a first temperature, and a second evaporator region that controls the second storage unit to a second temperature different from the first temperature. And a partition member inserted into the evaporator so as to be separated. A first ventilation path corresponding to the first evaporator region and a second ventilation path corresponding to the second evaporator region are formed inside the single evaporator with the partition member therebetween. Has been
The first housing part is cooled to the first temperature by the air blown from the first ventilation path, and the second housing part is cooled to the second temperature by the air blown from the second ventilation path. The cooling device according to claim 1, configured as described above. The partition member is configured to be able to change the insertion position inside the evaporator,
The area of the first evaporator region and the second evaporator region in the evaporator is changed according to the insertion position of the partition member, whereby the first cooled by the first evaporator region. 3. The temperature relationship between the first temperature of one storage portion and the second temperature of the second storage portion cooled by the second evaporator region is configured to be changeable. Cooling system. The evaporator includes a heat transfer tube through which a refrigerant flows, and a plate-like fin member attached to the surface of the heat transfer tube with a predetermined interval.
The partition member has a slit portion formed corresponding to each of the plurality of fin members and is formed in a comb shape,
The comb-shaped partition member is inserted into the evaporator while the fin member is sandwiched in the thickness direction by the slit portion, so that the single evaporator is connected to the first evaporator region. The cooling device according to any one of claims 1 to 3, wherein the cooling device is configured to be separated into the second evaporator region. A refrigerant temperature detector for detecting the refrigerant temperature of the evaporator;
An electronic expansion valve that controls the amount of refrigerant flowing into the evaporator according to the opening;
A control unit for controlling the opening of the electronic expansion valve;
In the state where the evaporator is separated into the first evaporator region and the second evaporator region by the partition member, the control unit sets the refrigerant temperature of the evaporator detected by the refrigerant temperature detection unit. Based on this, by changing the opening of the electronic expansion valve to control the flow rate of the refrigerant, control is performed to cool the first accommodating portion at the first temperature and the second accommodating portion at the second temperature. The cooling device according to claim 1, configured as described above. The evaporator is configured such that the refrigerant after flowing through the first evaporator region flows through the second evaporator region,
The refrigerant temperature detection unit is disposed on the downstream side of the electronic expansion valve and in the vicinity of the partition member and a first refrigerant temperature detection unit that detects a refrigerant temperature flowing into the first evaporator region. A second refrigerant temperature detector that detects a refrigerant temperature in the vicinity of the boundary between the evaporator region and the second evaporator region; and a third refrigerant temperature detector that detects a refrigerant temperature flowing out of the second evaporator region. Including
The control unit has a first superheat degree of the refrigerant in the first evaporator region based on the refrigerant temperature detected by the first refrigerant temperature detection unit and the refrigerant temperature detected by the second refrigerant temperature detection unit. In the second evaporator region based on the refrigerant temperature detected by the second refrigerant temperature detection unit and the refrigerant temperature detected by the third refrigerant temperature detection unit, the gas-liquid two-phase state of 0 degrees or less The cooling device according to claim 5, wherein the opening degree of the electronic expansion valve is controlled so that the second superheat degree of the refrigerant becomes a value larger than 0 degree. A compressor capable of controlling the refrigerant discharge rate by changing the rotational speed;
The control unit maintains the first housing portion at the first temperature by controlling the opening of the electronic expansion valve and controlling the rotational speed of the compressor, and controls the second by controlling the opening of the electronic expansion valve. The cooling device according to claim 6, wherein the cooling device is configured to perform control for maintaining the accommodating portion at the second temperature.   The control unit is configured to maintain the first temperature and the first accommodation in a state where the first superheat degree of the refrigerant in the first evaporator region is maintained at 0 degrees or less based on the opening degree control of the electronic expansion valve. The rotation speed of the compressor is changed based on a difference from the detected temperature of the part to maintain the first housing part at the first temperature, and the second evaporation is performed based on the opening degree control of the electronic expansion valve. In the state where the second superheat degree of the refrigerant in the container region is maintained at a value larger than 0 degree, the second accommodating portion is changed based on the difference between the second temperature and the detected temperature of the second accommodating portion. The cooling device according to claim 7, wherein the cooling device is configured to perform control to maintain the second temperature. The partition member is configured such that the first evaporator region in the evaporator is disposed above the second evaporator region,
The partition member has an inclination angle at which the molten water generated when the frost generated in the first evaporator region is melted together with the cooling operation can be discharged toward the second evaporator region below. The cooling device according to any one of claims 1 to 8, wherein the cooling device is installed in the inside. A first housing part for housing the product cooled at the first temperature;
A second accommodating portion for accommodating a commodity that can be cooled at a second temperature different from the first temperature;
A single evaporator configured to be able to cool the first housing portion and the second housing portion;
The single evaporator is separated into a first evaporator region that cools the first housing part to the first temperature and a second evaporator region that controls the second housing part to the second temperature. And a partition member inserted into the evaporator.

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