Cooling storage

Abstract

The present invention provides a cooling storage unit that can control the rotation speed of the compressor so that the temperature inside the cooling duct approaches a preset target temperature. [Solution] The system comprises a cold air supply device 17 that supplies cold air into a cooling duct 40, a duct temperature sensor 18 that measures the temperature inside the cooling duct 40, and a control unit 19. The cold air supply device 17 includes a compressor 22. The control unit 19 performs the following: a first process in which, when condition (1) is met, a numerical value X1 is accumulated at predetermined time intervals S1, and the rotational speed of the compressor 22 is increased when the accumulated value is less than or equal to a predetermined value D1; a second process in which, when condition (2) is met, a numerical value X2 is accumulated at predetermined time intervals S2, and the rotational speed of the compressor 22 is decreased when the accumulated value is greater than or equal to a predetermined value D2; and a third process in which, when condition (3) is met, a numerical value X3 is accumulated at predetermined time intervals S3, and the rotational speed of the compressor 22 is decreased when the accumulated value is greater than or equal to a predetermined value D3.

Description

Technical Field

[0001] The technology disclosed in this specification relates to a cooling refrigerator.

Background Art

[0002] As a cooling refrigerator that can store fresh food and the like for a long time without drying, a constant temperature and high humidity chamber is known. For example, in the constant temperature and high humidity chamber (constant temperature and high humidity storage) disclosed in Patent Document 1 below, cold air is supplied from a cold air supply device to a cooling duct (space part) formed between a box body (inner box) and an inner storage box (inner storage box body), and by cooling the wall surface of the inner storage box, the storage chamber (inside the storage) which is the internal space of the inner storage box is indirectly cooled (so-called indirect cooling method). Further, as such a cold air supply device, a configuration in which a compressor, a condenser, a cooler, etc. are connected in circulation by a refrigerant pipe filled with a refrigerant is known.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In the above configuration, the temperature in the storage chamber is correlated with the temperature in the cooling duct. Therefore, based on the target temperature in the storage chamber, the target temperature in the cooling duct is set, and by controlling the temperature in the cooling duct so as to approach the target temperature, the temperature in the storage chamber can be controlled. As a method of controlling the temperature in the cooling duct, it is conceivable to control the rotation speed of the compressor to adjust the cooling capacity of the cold air supply device. In this case, it is required to control the rotation speed of the compressor so that the temperature in the cooling duct approaches a preset target temperature.

[0005] In the above configuration, it is preferable to suppress the temperature variation so as to make the temperature distribution (cooling condition) in the storage chamber uniform.

[0006] The technology disclosed in this specification has been completed based on the above circumstances, and an object is to provide a refrigerated storage capable of controlling the rotational speed of a compressor so that the temperature in a cooling duct approaches a preset target temperature. Further, it is preferable that a refrigerated storage capable of suppressing the temperature variation in the storage chamber can be provided.

Means for Solving the Problems

[0007] As means for solving the above problems, the refrigerated storage disclosed in this specification includes a heat-insulating box body, an inner box disposed inside the box body while forming a cooling duct serving as a passage for cold air between the box body, and having a storage chamber inside, a cold air supply device for supplying cold air into the cooling duct, a duct temperature sensor for measuring the temperature in the cooling duct, and a control unit. The cold air supply device includes a compressor, a condenser, a cooler, and a refrigerant pipe that circulates and connects the compressor, the condenser, and the cooler and in which a refrigerant is enclosed. When the temperature in the cooling duct measured by the duct temperature sensor is taken as a duct temperature measurement value TS and the preset target temperature in the cooling duct is taken as a target temperature TM, the control unit integrates the numerical value X1 calculated by the following formula (1) every predetermined time S1 when the following condition (1) is satisfied, and increases the rotational speed of the compressor when the integrated value becomes not more than a predetermined value D1; integrates the numerical value X2 calculated by the following formula (2) every predetermined time S2 when the following condition (2) is satisfied, and decreases the rotational speed of the compressor when the integrated value becomes not less than a predetermined value D2; and integrates the numerical value X3 calculated by the following formula (3) every predetermined time S3 when the following condition (3) is satisfied, and decreases the rotational speed of the compressor when the integrated value becomes not less than a predetermined value D3. It is characterized by performing the above.

[0008] Condition (1): TM < T2 < TM + predetermined value A1 Condition (2): TM - predetermined value A2 ≤ T ≤ TM Condition (3): TM - predetermined value A3 < T2 < TM - predetermined value A2 Numerical value X1 = T1 - T2 - predetermined value B1 ··· Equation (1) Numerical value X2 = T1 - T2 ··· Equation (2) Numerical value X3 = T1 - T2 + predetermined value B2 ··· Equation (3)

[0009] However, in the above conditions (1) to (3) and the above equations (1) to (3), A1 > 0 A2 > 0 A3 > 0 A3 > A2 B1 > 0 B2 > 0 T1: Duct temperature measurement value TS before the predetermined time S4 T2: Current duct temperature measurement value TS It is.

[0010] Also, when the control unit satisfies the following condition (5), the control unit can set the predetermined value B1 to a value smaller than the predetermined value B1 when satisfying the following condition (4), and execute the first process. Condition (4): TM + predetermined value A4 < T2 Condition (5): TM ≤ T2 ≤ TM + predetermined value A4 However, A4 < A1 A4 > 0 [[ID=;45]]It is.

[0011] In addition, the cooling storage disclosed in this specification includes a box body having heat insulation properties, an inner box body disposed inside the box body while forming a cooling duct serving as a cold air passage between the box body, the inside of which is a storage chamber, a cold air supply device that circulates and supplies cold air into the cooling duct, and an auxiliary member for suppressing variations in the temperature inside the storage chamber. <;

[0012] Also, the auxiliary member can be a shielding member that closes a part of the passage in the cooling duct.

[0013] Further, the cold air supply device includes a cooler that cools air passing through the inside by heat exchange, and a cooling fan that sucks air in the cooling duct and supplies the air cooled by the cooler into the cooling duct. The shielding member can be provided near the air suction port from the cooling duct to the cooling fan.

[0014] Also, the internal space of the storage chamber includes a first region and a second region having a smaller cooling load than the first region. The shielding member can be provided near the suction port in a passage arranged on the second region side of the cooling duct.

[0015] Further, the cold air supply device includes a cooler that cools air passing through the inside by heat exchange, and a cooling fan that sucks air in the cooling duct and supplies the air cooled by the cooler into the cooling duct. The shielding member can be provided near the air outlet from the cooler to the cooling duct.

[0016] Also, the internal space of the storage chamber includes a first region and a second region having a smaller cooling load than the first region. The shielding member can be provided near the air outlet in a passage arranged on the second region side of the cooling duct.

[0017] Further, the cold air supply device includes a cooler that cools air passing through the inside by heat exchange, and a plurality of cooling fans that suck air in the cooling duct and supply the air cooled by the cooler into the cooling duct. The auxiliary member can be an air guide provided between the plurality of cooling fans so as to divide the flow paths of the respective cooling fans.

[0018] Further, the cold air supply device includes a cooler that cools air passing through the inside by heat exchange, A plurality of cooling fans that suck air inside the cooling duct and supply the air cooled by the cooler into the cooling duct, and the auxiliary member can be a cover that covers each cooling fan so as to divide the flow paths of the respective cooling fans.

[0019] Also, the auxiliary member can be a heat insulating member provided in a lower passage disposed below the storage chamber inside the cooling duct.

Advantages of the Invention

[0020] According to the technology disclosed in this specification, it is possible to provide a cooling storage capable of controlling the rotational speed of a compressor so that the temperature inside the cooling duct approaches a preset target temperature. Also, it is easy to suppress variations in the temperature inside the storage chamber of the cooling storage.

Brief Description of the Drawings

[0021] [Figure 1] Perspective view showing a constant temperature and high humidity chamber according to Embodiment 1 of the present invention [Figure 2] Longitudinal sectional view of the constant temperature and high humidity chamber [Figure 3] Schematic diagram showing a cooling fan and a cooling duct [Figure 4] Perspective view of the drain guide viewed from below [Figure 5] Block diagram showing the electrical configuration of the constant temperature and high humidity chamber [Figure 6] Graph showing an example of the change mode of the duct temperature measurement value TS [Figure 7] Graph showing an example of the change mode of the duct temperature measurement value TS in a comparative example [Figure 8] Graph showing an example of the time change of the rotational speed of the compressor [Figure 9] Graph showing an example of the change mode of the duct temperature measurement value TS according to Embodiment 2 [Figure 10] Graph showing an example of the change mode of the duct temperature measurement value TS in a comparative example [Figure 11] Schematic diagram showing a cooling fan and a cooling duct according to Embodiment 3 [Figure 12] Schematic diagram showing the cooling fan and cooling duct according to Embodiment 4 [Figure 13] Schematic diagram showing the cooling fan and cooling duct according to Embodiment 5 [Figure 14] Schematic diagram showing the cooling fan and cooling duct according to Embodiment 6 [Figure 15] Cross-sectional perspective view of a temperature- and humidity-controlled storage unit. [Figure 16] Figure 15: Enlarged cross-sectional perspective view of the area around the cooling fan. [Figure 17] A cross-sectional perspective view of the constant temperature and humidity cabinet, cut along line II in Figure 15, showing an enlarged view of the area near the first shielding member. [Figure 18] Figure 15 shows a cross-sectional perspective view of a constant temperature and humidity cabinet, cut along line II-II, with the area near the cooling fan magnified. [Figure 19] Cross-sectional perspective view showing the area near the cooling fan according to Embodiment 7 [Figure 20] Enlarged longitudinal cross-sectional view of the area near the first passage according to Embodiment 8 [Modes for carrying out the invention]

[0022] <Embodiment 1> Embodiment 1 of the present invention will be described with reference to Figures 1 to 8. In this embodiment, a constant temperature and humidity storage cabinet 10 is exemplified as a cooling storage cabinet. The constant temperature and humidity storage cabinet 10 comprises a box body 11 and an interior box 30 housed inside the box body 11, the interior of which serves as a storage chamber 30S. As shown in Figure 2, the box body 11 is box-shaped with an opening at the front. As shown in Figure 1, six insulated doors 12 are rotatably attached to the box body 11. The insulated doors 12 are arranged to cover the front opening of the box body 11. As a result, the storage chamber 30S can be opened and closed by the insulated doors 12. Inside the storage chamber 30S, as shown in Figure 2, shelves 13 are arranged in multiple tiers for arranging stored items (food, etc.). Of the six insulated doors 12, the four on the left are double-hinged insulated doors 12 divided into upper and lower tiers, and the two on the right are single-hinged insulated doors 12 divided into upper and lower tiers.

[0023] The box body 11 comprises an outer box 11A made of metal plates and an inner box 11B made of metal plates housed inside the outer box 11A with a gap between them. Insulation material is filled between the outer box 11A and the inner box 11B. As a result, the box body 11 has thermal insulation properties. The inner box 30 is constructed by combining multiple thermally conductive metal plates such as stainless steel plates and has a box shape with an opening at the front. The inner box 30 is slightly smaller than the inner box 11B of the box body 11 and is housed inside the box body 11 with a certain space formed between it and the inner box 11B. This space formed between the inner box 30 and the inner box 11B is a cooling duct 40. As shown in Figures 2, 3, and 15, the interior box 30 comprises a bottom wall portion 30A that forms the bottom surface of the storage chamber 30S, a rear wall portion 30B that forms the back surface, a ceiling wall portion 30C that forms the ceiling, and a pair of left and right side wall portions 30DL (left wall portion) and 30DR (right wall portion).

[0024] The cooling duct 40 comprises a first passage 41 (an example of a downward passage), a second passage 42, a third passage 43, and a pair of fourth passages 44L and 44R. As shown in Figures 2 and 3, the first passage 41 is a space formed between the upward-facing inner surface of the inner box 11B and the outer surface of the bottom wall 30A, and is located below the storage chamber 30S. The second passage 42 is a space formed between the forward-facing inner surface of the inner box 11B and the outer surface of the rear wall 30B, and is located behind the storage chamber 30S. The third passage 43 is a space formed between the downward-facing inner surface of the inner box 11B and the outer surface of the ceiling wall 30C, and is located above the storage chamber 30S. The fourth passages 44L and 44R are formed between the side-facing inner surface of the inner box 11B and the side walls 30DL and 30DR of the inner box 30, and are spaces located to the side of the storage chamber 30S. The space located on the left side of the fourth passages 44L and 44R is called the fourth left passage 44L, and the space located on the right side is called the fourth right passage 44R.

[0025] The constant temperature and humidity chamber 10 also includes a cold air supply device 17 that supplies cold air into the cooling duct 40, a duct temperature sensor 18 that measures the temperature inside the cooling duct 40, and a control unit 19 (see Figure 5) that performs control of the cold air supply device 17, etc. As shown in Figure 2, the cold air supply device 17 includes a compressor 22, a condenser 23, a condenser fan 24 attached to the condenser 23, a cooler 27, a refrigerant pipe 28 filled with refrigerant, and a cooling fan 29. The refrigerant pipe 28 circulates through the compressor 22, the condenser 23, and the cooler 27, thereby forming a well-known cooling cycle.

[0026] As shown in Figure 2, a machine room 70 is formed above the box body 11. The machine room 70 houses a compressor 22, a condenser 23, and a condenser fan 24. The compressor 22 is a variable-speed inverter compressor, and its rotational speed can be switched in stages (for example, from 0 to 6 speeds). The compressor 22, condenser 23, and condenser fan 24 are mounted on an insulated base 26, and a cooler 27 is attached to the underside of the base 26. Also, as shown in Figure 1, an electrical box 25 (control box) housing the control unit 19 (see Figure 5), etc., is installed on the base 26. An operation box 60 (dashed line in Figure 1) is installed on the front side of the machine room 70. Inside the operation box 60 is an operation unit 61 (operation switch, see Figure 5) for performing operations and settings related to the constant temperature and high humidity cabinet 10.

[0027] As shown in Figure 2, the base 26 is attached to the box body 11 by blocking the window hole 16A formed in the ceiling wall portion 16 of the box body 11 from above. An air duct 50, which also serves as a drain pan, is provided in the ceiling wall portion 16, and a cooler chamber 45 is formed above the air duct 50. The cooler 27 is housed in the cooler chamber 45.

[0028] An intake port 50A is formed in the front part of the air duct 50, and an outlet port 50B is formed in the rear part. A cooling fan 29 (duct fan) is attached to the intake port 50A. The cooler 27 and the cooling fan 29 are positioned above the interior box 30. The cooling fan 29 draws air from the cooling duct 40 into the cooler chamber 45 and supplies air cooled by the cooler 27 to the cooling duct 40. As shown in Figure 3, multiple cooling fans 29 (three in Figure 3) are arranged in a row from left to right.

[0029] When the compressor 22 and condenser fan 24 are running and the cooling fan 29 is driven, the air in the third passage 43 of the cooling duct 40 is drawn into the cooler chamber 45 from the intake port 50A by the cooling fan 29, and is cooled by heat exchange as it passes through the cooler 27. The air cooled by the cooler 27 (cold air) is blown out from the outlet 50B into the second passage 42 at the rear of the storage chamber 30S, and then heads towards the first passage 41 below the storage chamber 30S. Then, as shown in Figure 3, from the first passage 41, it heads towards the fourth passages 44L and 44R on the left and right sides of the storage chamber 30S, respectively, and then returns to the third passage 43 from each of the fourth passages 44L and 44R. In this way, cold air is circulated and supplied into the cooling duct 40. This cold air cools each wall section (bottom wall section 30A, rear wall section 30B, ceiling wall section 30C, side walls 30DL, 30DR) that make up the interior box 30, thereby indirectly cooling the inside of the storage chamber 30S. As a result, the inside of the storage chamber 30S is cooled to a predetermined temperature while maintaining high humidity.

[0030] As shown in Figure 2, a drain guide 31 is positioned below the ceiling wall section 30C of the interior box 30. The drain guide 31 is a plate made of synthetic resin and is positioned opposite the lower surface of the ceiling wall section 30C at a distance from it. This allows condensation water generated on the lower surface of the ceiling wall section 30C to be collected by the drain guide 31. As shown in Figure 2, the drain guide 31 extends with a downward slope towards the rear (right side in Figure 2). As shown in Figure 4, multiple drain guides 31 are arranged in a left-right direction. Multiple grooves 32 are formed on the lower surface of the drain guide 31. The grooves 32 extend in the front-back direction. By providing such grooves 32, the hydrophilicity of the lower surface of the drain guide 31 can be increased. In addition, the lower surface of the drain guide 31 is shot-blasted, which roughens the surface and further increases its hydrophilicity. By increasing the hydrophilicity of the lower surface of the drain guide 31, water droplets (condensation, etc.) adhering to the lower surface of the drain guide 31 can be reliably drained backward along the lower surface of the drain guide 31, thereby preventing water droplets from falling onto items in the storage chamber 30S. Furthermore, by increasing the hydrophilicity of the lower surface of the drain guide 31, water droplets can be reliably drained backward without increasing the inclination angle of the drain guide 31, thereby preventing a decrease in the volume of the storage chamber 30S. Note that a groove 32 does not necessarily need to be formed on the lower surface of the drain guide 31.

[0031] Next, the electrical configuration of the constant temperature and humidity storage unit 10 will be described. As shown in Figure 5, the constant temperature and humidity storage unit 10 is equipped with a control unit 19. The control unit 19 is electrically connected to an operation unit 61, a memory unit 62, a timing unit 63, a condenser fan 24, a compressor 22, a cooling fan 29, a duct temperature sensor 18, and an ambient temperature sensor 71. Although not shown, an internal temperature sensor is provided in the storage chamber 30S to measure the temperature of the storage chamber 30S, and the control unit 19 is electrically connected to the internal temperature sensor. The control unit 19 is mainly composed of a CPU, for example, and the memory unit 62 is composed of ROM, RAM, etc.

[0032] The control unit 19 can control the operation of each device connected to it (condenser fan 24, compressor 22, cooling fan 29, etc.) by executing a computer program stored in the memory unit 62. The memory unit 62 also stores various setting values ​​related to the operation of the constant temperature and humidity cabinet 10. The timing unit 63 is used to keep time.

[0033] Next, the processing of the control unit 19 will be described. The temperature inside the storage room 30S is correlated with the temperature inside the cooling duct 40. Therefore, the control unit 19 sets a target temperature TM inside the cooling duct 40 based on the set temperature TA inside the storage room 30S set by the operator (user), and controls the temperature inside the cooling duct 40 to approach the target temperature TM, thereby controlling the temperature inside the storage room 30S. In other words, when the temperature inside the cooling duct 40 measured by the duct temperature sensor 18 (duct temperature measurement value TS) matches the target temperature TM, the temperature inside the storage room 30S (for example, the central part of the storage room 30S) becomes the set temperature TA. The operator can set the set temperature TA by operating the operation unit 61.

[0034] The control unit 19 can calculate the target temperature TM based on, for example, the following formulas (A) to (C). Note that the following formulas (A) to (C) are just examples, and the method for calculating the target temperature TM (the method for setting the target temperature TM) is not limited to these.

[0035] Target temperature TM = Set temperature TA - (Fixed bias E1 - Temperature correction value F1) - (Cumulative value of variable bias E2) ... Formula (A) Fixed bias E1 = {α(ambient temperature G1 - set temperature TA) + β × heater current ratio P1} / (1 + γ) ... Formula (B) Variable bias E2 = {Duct temperature measurement value TS1 - (Set temperature TA + Temperature correction value F1)} × 0.5 ... Formula (C)

[0036] In the above formulas (A) to (C), α, β, and γ are fixed values ​​determined by the test and are determined by the volume of the storage chamber 30S. The "cumulative value of variable bias E2" is the cumulative value obtained by adding E2 at predetermined time intervals (e.g., every 5 seconds). The duct temperature measurement value TS1 is, for example, the average value of the duct temperature measurement values ​​(temperature inside the cooling duct 40 measured by the duct temperature sensor 18) over a predetermined period (e.g., 60 seconds) going back from a predetermined time H1 before (e.g., 5 seconds before). The ambient temperature G1 is the temperature outside the box 11. The ambient temperature G1 can be measured, for example, by an ambient temperature sensor 71 (see Figure 5). The ambient temperature sensor 71 is, for example, located inside the operation box 60. The heater energization rate P1 is the energization rate of the heater 64 (front frame heater, see Figure 2) for preventing condensation, which is provided along the front opening edge of the box 11.

[0037] Furthermore, the temperature correction value F1 is a value that can be set to compensate for the difference between the set temperature TA and the actual internal temperature (for example, the central temperature of the storage chamber 30S). The operator can set the temperature correction value F1 in 0.1K increments by operating the operation box 60, for example. For example, if the set temperature TA is set to "0°C" and the actual internal temperature is -1°C, there is a 1K difference between the set temperature TA and the actual internal temperature. If the temperature correction value F1 is set to "-1K", the target temperature TM will be set to "+1K", so the actual internal temperature will be controlled to 0K, eliminating the difference between the set temperature TA and the actual internal temperature. In addition, by providing such a temperature correction value F1, the temperature correction value F1 can be set for each of the multiple types of constant temperature and humidity storage chambers with different volumes, and the difference between the set temperature TA and the actual internal temperature that may occur for each model of constant temperature and humidity storage chamber can be compensated for.

[0038] Next, the processing of the control unit 19 in the cooling operation will be described. In the following description, the temperature in the cooling duct 40 measured by the duct temperature sensor 18 is defined as the duct temperature measurement value TS. In the cooling operation, the operation of the cold air supply device 17 is controlled so that the duct temperature measurement value TS approaches the target temperature TM in the cooling duct 40. Note that the control unit 19 increases or decreases the rotational speed of the compressor 22 so that the duct temperature measurement value TS decreases at a predetermined rate (time drop rate).

[0039] Also, in the cooling operation, when the duct temperature measurement value TS is close to the target temperature TM, the control unit 19 executes control (referred to as control operation in the following description) such that the duct temperature measurement value TS follows the target temperature TM. The control operation is executed when the duct temperature measurement value TS is within a predetermined temperature range. Specifically, when (TM - predetermined value A3) < TS < (TM + predetermined value A1) is satisfied, the control unit 19 executes the control operation.

[0040] In the control operation, the control unit 19 executes the first process when the following condition (1) is satisfied. In the first process, the control unit 19 integrates the numerical value X1 calculated by the following mathematical formula (1) every predetermined time S1, and when the integrated value becomes equal to or less than the predetermined value D1, the rotational speed of the compressor 22 is increased by one step. Note that in the first process, after the rotational speed of the compressor 22 is increased by one step, the integrated value of the numerical value X1 is reset. The predetermined time S1 is set to, for example, 5 seconds, and the predetermined value D1 is set to, for example, "-1", but is not limited thereto and can be changed as appropriate. If the predetermined value D1 is too large, the rotational speed of the compressor 22 is likely to change too much, and if the predetermined value D1 is too small, there is a concern that the rotational speed of the compressor 22 is difficult to change. Therefore, the predetermined value D1 is preferably set within a range of, for example, -1 or less and -2 or more.

[0041] In the control operation, the control unit 19 executes the second process when the following condition (2) is satisfied. In the second process, the control unit 19 integrates the numerical value X2 calculated by the following mathematical formula (2) every predetermined time S2, and when the integrated value becomes equal to or greater than the predetermined value D2, the rotation speed of the compressor 22 is decreased by one step. In the second process, after the control unit 19 decreases the rotation speed of the compressor 22 by one step, the integrated value of the numerical value X2 is reset. The predetermined time S2 is set to, for example, 5 seconds, and the predetermined value D2 is set to, for example, "1", but is not limited thereto and can be changed as appropriate. If the predetermined value D2 is too large, the rotation speed of the compressor 22 becomes too difficult to change, and if the predetermined value D2 is too small, there is a concern that the rotation speed of the compressor 22 becomes too easy to change. For this reason, the predetermined value D2 is preferably set within a range of, for example, 1 or more and 2 or less.

[0042] In the control operation, the control unit 19 executes the third process when the following condition (3) is satisfied. In the third process, the control unit 19 integrates the numerical value X3 calculated by the following mathematical formula (3) every predetermined time S3, and when the integrated value becomes equal to or greater than the predetermined value D3, the rotation speed of the compressor is decreased by one step. In the third process, after the control unit 19 decreases the rotation speed of the compressor 22 by one step, the integrated value of the numerical value X3 is reset. The predetermined time S3 is set to, for example, 5 seconds, and the predetermined value D3 is set to, for example, "1", but is not limited thereto and can be changed as appropriate. If the predetermined value D3 is too large, the rotation speed of the compressor 22 becomes too difficult to change, and if the predetermined value D3 is too small, there is a concern that the rotation speed of the compressor 22 becomes too easy to change. For this reason, the predetermined value D3 is preferably set within a range of, for example, 1 or more and 2 or less.

[0043] Condition (1): TM < T2 < TM + predetermined value A1 Condition (2): TM - predetermined value A2 ≤ T2 ≤ TM Condition (3): TM - predetermined value A3 < T2 < TM - predetermined value A2 <C@> Numerical value X1 = T1 - T2 - predetermined value B1 ··· Mathematical formula (1) Numerical value X2 = T1 - T2 ··· Mathematical formula (2) Numerical value X3 = T1 - T2 + predetermined value B2 ... Formula (3)

[0044] However, in the above conditions (1) to (3) and the above formulas (1) to (3), A1>0 A2>0 A3>0 A3>A2 B1>0 B2>0 T1: Duct temperature measurement value TS before a predetermined time S4 T2: Current duct temperature measurement TS That is the case.

[0045] The predetermined value A1 (predetermined temperature) is set to, for example, 1°C (=1K), the predetermined value A2 (predetermined temperature) is set to, for example, 0.5°C, and the predetermined value A3 (predetermined temperature) is set to, for example, 1°C. It is preferable that the predetermined value A2 be set within the range of, for example, 0.1 to 0.9. The predetermined value B1 is set to, for example, "0.12", and the predetermined value B2 is set to, for example, "0.12". If the predetermined values ​​B1 and B2 are too small, the rotational speed of the compressor 22 may become too difficult to change, and if the predetermined values ​​B1 and B2 are too large, there is a concern that the rotational speed of the compressor 22 may become too easy to change. For this reason, it is preferable that the predetermined values ​​B1 and B2 be set within the range of, for example, 0.06 or more and 0.12 or less.

[0046] The predetermined time S4 ​​is set to, for example, 60 seconds, but is not limited to this. If the predetermined time S4 ​​is too short, the response of the duct temperature sensor 18 may not be able to keep up, and if it is too long, it may be difficult to detect temporary changes in the internal temperature, such as when the insulated door 12 is opened or closed. For this reason, it is preferable to set the predetermined time S4 ​​within the range of 10 seconds or more and 120 seconds or less. Note that the numerical values ​​of the predetermined values ​​A1, A2, A3, B1, B2 and predetermined time S4 ​​described above are examples and can be changed as appropriate. In addition, predetermined values ​​B1 and B2 may be the same value or may be different values.

[0047] The duct temperature measurement value TS may be the measurement value of the duct temperature sensor 18 at that time, or it may be the average value of the measurements of the duct temperature sensor 18 over a predetermined period (for example, 5 seconds) going back from that time. In other words, T2 may be the measurement value of the duct temperature sensor 18 at the present time, or it may be the average value of the measurements of the duct temperature sensor 18 over a predetermined period (for example, 5 seconds) going back from the present time. Also, T1 may be the measurement value of the duct temperature sensor 18 at a predetermined time S4 ​​before (for example, 60 seconds before), or it may be the average value of the measurements of the duct temperature sensor 18 over a predetermined period (for example, 5 seconds) going back from the predetermined time S4 ​​before.

[0048] Figure 6 shows an example of how the duct temperature measurement value TS changes when controlled operation is performed. In Figure 6, the case where the predetermined values ​​A1 = 1°C, A2 = 0.5°C, and A3 = 1°C is used as an example. In equations (1) to (3), if the duct temperature measurement value TS increases over time, "T1-T2" will be a negative value, and if the duct temperature measurement value TS decreases over time, "T1-T2" will be a positive value. In the following explanation, the state that satisfies condition (1) is referred to as state R1 (see arrow R1 in Figure 6), the state that satisfies condition (2) is referred to as state R2 (see arrow R2 in Figure 6), and the state that satisfies condition (3) is referred to as state R3 (see arrow R3 in Figure 6).

[0049] In state R1, as time progresses, the measured duct temperature TS increases (the value X1 becomes negative). This decreases the cumulative value of X1, and when this cumulative value falls below the predetermined value D1, the rotational speed of the compressor 22 increases. As a result, the cooling capacity of the cold air supply device 17 increases, and the measured duct temperature TS decreases. Equation (1) also includes the term "-predetermined value B1". Therefore, the value X1 is more likely to be negative than the values ​​X2 and X3. In other words, in state R1, the rotational speed of the compressor 22 is more likely to increase. To put it another way, "-predetermined value B1" is a term that makes it easier to increase the rotational speed of the compressor 22 in state R1. Therefore, as shown in Figure 6, in state R1, the measured duct temperature TS decreases and approaches the target temperature TM.

[0050] In state R2, as time passes, the duct temperature measurement value TS decreases (the numerical value X2 becomes a positive number), the cumulative value of the numerical value X2 increases, and when that cumulative value exceeds a predetermined value D2, the rotational speed of the compressor 22 is reduced by one step. In other words, in state R2, the control unit 19 controls the system to reduce the rotational speed of the compressor 22, which increased in state R1 (reducing the cooling capacity of the cold air supply device 17). This prevents the duct temperature measurement value TS from becoming too low in state R2.

[0051] In state R3, as time passes, the measured duct temperature TS decreases (the value X3 becomes a positive number), the cumulative value of X3 increases, and when this cumulative value exceeds the predetermined value D3, the rotational speed of the compressor 22 is reduced by one step. Also, equation (3) includes the term "+ predetermined value B2". For this reason, the value X3 is more likely to be a positive value compared to the values ​​X1 and X2. In other words, in state R3, the rotational speed of the compressor 22 is more likely to decrease compared to state R2. To put it another way, "+ predetermined value B2" is a term that makes it easier to reduce the rotational speed of the compressor 22 in state R3. As a result, as shown in Figure 6, in state R3, the rotational speed of the compressor 22 decreases further, resulting in an increase in the measured duct temperature TS, which approaches the target temperature TM.

[0052] From the above, in state R1, increasing the rotational speed of the compressor 22 lowers the duct temperature measurement value TS and brings it closer to the target temperature TM. In state R2, decreasing the rotational speed of the compressor 22 prevents the duct temperature measurement value TS from dropping too low. In state R3, further decreasing the rotational speed of the compressor 22 raises the duct temperature measurement value TS and brings it closer to the target temperature TM. As a result, as shown in Figure 6, the duct temperature measurement value TS can be controlled to track the target temperature TM.

[0053] If, in state R3, a process to increase the rotational speed of the compressor 22, such as the first process (a process that increases the rotational speed of the compressor 22 by one step when the cumulative value of the numerical value X3 falls below a predetermined value), is executed, then, depending on the circumstances, the duct temperature measurement value TS may become lower than (target temperature TM - predetermined value A3). In this embodiment, since no process to increase the rotational speed of the compressor 22 is executed in state R3, such a situation can be suppressed.

[0054] Furthermore, in state R3, if the rotational speed of the compressor 22 is reduced, the duct temperature measurement value TS increases, and the system returns to state R2. If, for example, in state R2, a process to increase the rotational speed of the compressor 22, such as the first process (a process that increases the rotational speed of the compressor 22 by one step when the cumulative value of the numerical value X2 falls below a predetermined value) is executed, the duct temperature measurement value TS will rise (T1-T2 is negative), resulting in an increase in the rotational speed of the compressor 22. As a result, the duct temperature measurement value TS will decrease as soon as the system returns from state R3 to state R2, returning to state R3. In other words, as shown in the comparative example in Figure 7, the system will be controlled to repeatedly transition between state R2 and state R3, and there is a risk that the duct temperature measurement value TS will remain below the target temperature TM. In this embodiment, the process to increase the rotational speed of the compressor 22 is not executed in state R2, but only after the system returns to state R1, thereby suppressing such a situation.

[0055] In this embodiment, the control unit 19 switches the rotational speed of the compressor 22 in stages based on the rotational speed table stored in the storage unit 62. The rotational speed table defines the rotational speed of the compressor 22 at each stage (0th to 6th speed). In this embodiment, the rotational speed of the compressor 22 is controlled using two types of rotational speed tables (first rotational speed table and second rotational speed table).

[0056] The first rotation speed table is set to 0th speed: 20Hz, 1st speed: 25Hz, 2nd speed: 34Hz, 3rd speed: 42Hz, 4th speed: 50Hz, 5th speed: 60Hz, and 6th speed: 70Hz. The second rotation speed table is set to 0th speed: 25Hz, 1st speed: 33Hz, 2nd speed: 40Hz, 3rd speed: 47Hz, 4th speed: 58Hz, 5th speed: 68Hz, and 6th speed: 80Hz. In other words, the rotation speeds at each stage are set higher in the second rotation speed table compared to the first rotation speed table. Note that the rotation speeds in the above rotation speed tables are examples and can be changed as needed.

[0057] When the insulated door 12 is not open, the control unit 19 controls the rotation speed of the compressor 22 based on the first rotation speed table (switching between rotation speed levels). Conversely, when the control unit 19 detects that the insulated door 12 has been opened, it controls the rotation speed of the compressor 22 based on the second rotation speed table.

[0058] When the insulated door 12 is opened, the temperature inside the storage room 30S rises, causing the temperature measured by the duct temperature sensor 18 to rise. In this case, the control unit 19 increases the rotational speed of the compressor 22 in stages, as shown in Figure 8, thereby increasing the cooling capacity of the cold air supply device 17. When the insulated door 12 is opened, the rotational speed of the compressor 22 is increased based on the second rotational speed table (dashed line in Figure 8). This allows the rotational speed of the compressor 22 to be higher compared to when the rotational speed of the compressor 22 is increased based on the first rotational speed table (solid line in Figure 7), thereby increasing the cooling capacity of the cold air supply device 17. As a result, the temperature inside the storage room 30S, which has risen due to the opening of the insulated door 12, can be quickly reduced.

[0059] Furthermore, in this embodiment, the cooling fan 29 is configured to be switchable between high-speed and low-speed operation. When the insulated door 12 is opened while the compressor 22 is stopped, the control unit 19 switches the cooling fan 29, which is operating at low speed, to high-speed operation. This allows the temperature of the storage room 30S, which has risen due to the opening of the insulated door 12, to be quickly reduced. The control unit 19 can determine that the insulated door 12 has been opened if the temperature inside the storage room 30S rises rapidly within a predetermined time. The temperature inside the storage room 30S can be estimated by referring to the temperature measured by the duct temperature sensor 18, but a temperature sensor that directly measures the temperature inside the storage room 30S may also be used. Alternatively, the opening of the insulated door 12 may be detected using a door switch.

[0060] Next, the effects of this embodiment will be explained. In formula (1) for calculating the numerical value X1, the term "-predetermined value B1" is included, so the numerical value X1 tends to be negative, and its cumulative value tends to decrease. In other words, the cumulative value of the numerical value X1 tends to be less than or equal to the predetermined value D1. For this reason, when condition (1) is met (when the duct temperature measurement value TS is higher than the target temperature TM), the rotational speed of the compressor 22 can be increased, and the cooling capacity of the cold air supply device 17 can be increased, thereby lowering the temperature inside the cooling duct 40 and bringing it closer to the target temperature TM.

[0061] Furthermore, when condition (2) is met (the duct temperature measurement TS is slightly lower than the target temperature TM), if the temperature inside the cooling duct 40 decreases over time, T1-T2 will become a positive value, and as the cumulative value increases, if it exceeds a predetermined value D2, the rotation speed of the compressor 22 will be reduced. This reduces the cooling capacity of the cold air supply device 17, making it easier to raise the temperature inside the cooling duct 40. In other words, it is possible to prevent the temperature inside the cooling duct 40 from becoming too low.

[0062] Furthermore, since formula (3) for calculating the numerical value X3 includes the term "+ predetermined value B2", the numerical value X3 tends to be positive, and its cumulative value tends to increase. In other words, the cumulative value of the numerical value X3 tends to be greater than or equal to the predetermined value D3. For this reason, when condition (3) is met (the duct temperature measurement value TS is significantly lower than the target temperature TM), the rotational speed of the compressor 22 can be reduced even more easily compared to when condition (2) is met, and the cooling capacity of the cold air supply device 17 can be reduced even more, making it easier to raise the temperature inside the cooling duct 40.

[0063] As described above, in the above configuration, when condition (1) is met, the temperature inside the cooling duct 40 can be lowered and brought closer to the target temperature TM by making it easier to increase the rotational speed of the compressor 22, and when condition (2) or condition (3) is met, the temperature inside the cooling duct 40 can be raised and brought closer to the target temperature TM by making it easier to decrease the rotational speed of the compressor 22. For this reason, the rotational speed of the compressor 22 can be controlled to approach the target temperature TM.

[0064] <Embodiment 2> Embodiment 2 will be described with reference to Figures 9 and 10. Parts identical to those in the above embodiment are denoted by the same reference numerals, and redundant explanations are omitted. In this embodiment, the processing of the control unit 19 in control operation differs from that of the above embodiment. In the first processing in control operation, the control unit 19 sets the predetermined value B1 of formula (1) to, for example, "0.12" when condition (4) is met, and sets the predetermined value B1 to, for example, "0.01" when condition (5) is met. In other words, in this embodiment, the control unit 19 executes the first processing while setting the predetermined value B1 when the following condition (5) is met to a smaller value than the predetermined value B1 when the following condition (4) is met.

[0065] Conditions (4) and (5) are further subdivisions of condition (1) described in Embodiment 1. In the following description, the state that satisfies condition (4) is referred to as state R1A (see arrow R1A in Figure 9), and the state that satisfies condition (5) is referred to as state R1B (see arrow R1B in Figure 9). In other words, state R1B is the state in which the duct temperature measurement value TS is closer to the target temperature TM than state R1A. The predetermined value A4 (predetermined temperature) is set to, for example, 0.2℃, but can be changed as appropriate.

[0066] Condition (4): TM + predetermined value A4 <T2 Condition (5): TM ≤ T2 ≤ TM + predetermined value A4 however, A4 <A1 A4>0 That is the case.

[0067] In state R1B, the predetermined value B1 is set to a smaller value than in state R1A. In other words, in state R1B, the cumulative value of the numerical value X1 does not decrease as easily as in state R1A, and does not easily fall below the predetermined value D1, making it difficult for the rotational speed of the compressor 22 to increase. As a result, as shown in Figure 9, in state R1B, the rotational speed of the compressor 22 does not increase, and the duct temperature measurement value TS is maintained at a state slightly higher than the target temperature TM. If this state continues for a long time, the rotational speed of the compressor 22 will increase, causing the duct temperature measurement value TS to drop slightly below the target temperature TM, and the state will change to R2. If the predetermined value A4 is too large, condition (5) will be met even though the temperature inside the storage chamber 30S has not decreased sufficiently, making it difficult for the rotational speed of the compressor 22 to increase. For this reason, it is preferable to set the predetermined value A4 within the range of 0 to 0.5. If the predetermined value B1 is too large when condition (5) is met, the rotational speed of the compressor 22 will increase easily, and the cooling capacity may become excessive. Therefore, when condition (5) is met, it is preferable to set the predetermined value B1 within the range of 0.01 or more and 0.05 or less.

[0068] Next, the effects of this embodiment will be explained. In equation (1), the smaller the predetermined value B1, the larger the numerical value X1. In other words, the cumulative value of the numerical value X1 increases more easily and is less likely to fall below the predetermined value D1, so the rotational speed of the compressor 22 is less likely to increase. Also, under condition (5), T2 (the current duct temperature measurement value TS) is closer to the target temperature TM than under condition (4). Therefore, by setting the predetermined value B1 when condition (5) is met to a smaller value than the predetermined value B1 when condition (4) is met, the rotational speed of the compressor 22 can be made less likely to increase. As a result, when condition (5) is met, in other words, when T2 is slightly higher than the target temperature TM (state R1B), the rotational speed of the compressor 22 increases, and the situation in which T2 falls below the target temperature TM can be suppressed. In other words, state R1B, where T2 is slightly higher than the target temperature TM, can be maintained for a longer period of time.

[0069] This prevents a situation in state R1 where, if the measured duct temperature TS is slightly higher than the target temperature TM, the rotational speed of the compressor 22 increases, and state R2 (where the measured duct temperature TS is slightly lower than the target temperature TM) is maintained for a long period of time (see comparative example in Figure 10).

[0070] <Embodiment 3> Embodiment 3 will be described with reference to Figure 11. Parts identical to those in the above embodiments are denoted by the same reference numerals, and redundant descriptions are omitted. In this embodiment, the configuration of the cooling fan 29 differs from that of the above embodiments. As shown in Figure 11, the cooling fan 29 in this embodiment is arranged in a two-part configuration in the left-right direction.

[0071] In this embodiment, the storage room 30S is divided into a first region 331S and a second region 332S. The first region 331S is a region with a large internal load and heat intrusion (i.e., a large cooling load), while the second region 332S is a region with a smaller internal load and heat intrusion (i.e., a smaller cooling load) compared to the first region 331S. In this embodiment, the first region 331S corresponds to the area corresponding to the four double-hinged insulated doors 12 (labeled 12A in Figure 1), and the second region 332S corresponds to the area corresponding to the two single-hinged insulated doors 12 (labeled 12B in Figure 1). The insulated doors 12A are equipped with heaters 14 to prevent condensation, and the operation of the heaters 14 tends to increase the amount of heat intrusion into the first region 331S. However, even if heater 14 is not provided, right-handed users open door 12A with their left hand and put in or take out stored items with their right hand, so the upper left door 12A tends to be opened and closed frequently, and the amount of heat entering the first region 331S tends to be large.

[0072] During cooling operation, the control unit 19 increases the rotation speed of the cooling fan 29 located above the first region 331S compared to the rotation speed of the cooling fan 29 located above the second region 332S. This allows more cold air to be circulated in the first region 331S, where the internal load and heat intrusion are large, and makes the temperature distribution within the storage chamber 30S more uniform.

[0073] <Embodiment 4> Embodiment 4 will be described with reference to Figure 12. Parts identical to those in the above embodiments are denoted by the same reference numerals, and redundant explanations are omitted. In this embodiment, the configuration of the cooling fan 29 differs from that of the above embodiments. As shown in Figure 12, the cooling fan 29 in this embodiment is arranged in a side-by-side configuration in the left-right direction, and the two cooling fans 29 are positioned above the first region 331S. In other words, the two cooling fans 29 are predominantly located on the first region 331S side. This allows more cold air to be circulated in the first region 331S, where the internal load and heat intrusion are large, and the temperature distribution within the storage chamber 30S can be made uniform.

[0074] <Embodiment 5> Embodiment 5 will be described with reference to Figure 13. Parts identical to those in the above embodiments are denoted by the same reference numerals, and redundant explanations are omitted. In this embodiment, the configuration of the cooling fan 29 differs from that of the above embodiments. As shown in Figure 13, the cooling fan 29 in this embodiment is arranged in a row of three in the left-right direction, with two cooling fans 29 positioned above the first region 331S and one cooling fan 29 positioned above the second region 332S. A first shielding member 510 (an example of an auxiliary member) is positioned inside the third passage 43 of the cooling duct 40. The first shielding member 510 is positioned above the boundary between the first region 331S and the second region 332S, and is configured to divide the third passage 43 into left and right sections. The inside of the third passage 43 is partially blocked by the first shielding member 510.

[0075] In this way, in the portion of the cooling duct 40 corresponding to the first region 331S, cold air is circulated mainly by two cooling fans 29, and in the portion of the cooling duct 40 corresponding to the second region 332S, cold air is circulated mainly by one cooling fan 29. As a result, more cold air can be circulated in the first region 331S, where the internal load and heat intrusion are large, thereby suppressing temperature variations within the storage chamber 30S and making the temperature distribution uniform. The portion of the cooling duct 40 corresponding to the first region 331S is the passage that goes through the third passage 43, the second passage 42, the first passage 41, and the fourth left passage 44L in that order and returns to the third passage 43. The portion of the cooling duct 40 corresponding to the second region 332S is the passage that goes through the third passage 43, the second passage 42, the first passage 41, and the fourth right passage 44R in that order and returns to the third passage 43.

[0076] <Embodiment 6> Embodiment 6 will be described with reference to Figures 14 to 18. The same reference numerals are used for parts identical to those in the above embodiments, and redundant explanations are omitted. This embodiment differs from Embodiment 5 in that the first shielding member 610 is positioned, and a second shielding member 620 (another example of an auxiliary member) and an air guide 630 (another example of an auxiliary member) are provided.

[0077] As shown in Figures 14 to 17, the first shielding member 610 of this embodiment is provided in the third passage 43 on the second region 332S side, near the air intake port 50A from the cooling duct 40 to the cooling fan 29. The first shielding member 610 is a plate-shaped member provided on the air inflow side of the intake port 50A in the third passage 43. The first shielding member 610 extends vertically so as to block a part of the third passage 43.

[0078] By arranging the first shielding member 610 in this manner, the amount of cold air circulating in the passage on the second region 332S side, where the cooling load is small and it is prone to excessive cooling (i.e., the passage that passes through the third passage 43, the second passage 42, the first passage 41, and the fourth right passage 44R in that order, and returns to the third passage 43), can be reduced. As a result, the temperature of the second region 332S rises, and the temperature difference with the first region 331S is mitigated. Consequently, temperature variations within the storage chamber 30S are suppressed, and the temperature distribution can be made more uniform.

[0079] As shown in Figures 17 and 18, the second shielding member 620 is provided in the second passage 42 on the second region 332S side, near the outlet 50B for cold air from the cooler 27 to the cooling duct 40. The second shielding member 620 extends in the left-right direction so as to block the upper part of the second passage 42 on the second region 332S side.

[0080] By arranging the second shielding member 620 in this manner, the amount of cold air circulating in the passage on the second region 332S side, where the cooling load is small and temperatures tend to be low, can be reduced. As a result, the temperature of the second region 332S rises, and the temperature difference with the first region 331S is mitigated. Consequently, temperature variations within the storage chamber 30S can be suppressed, resulting in a more uniform temperature distribution.

[0081] As shown in Figure 19, a total of two air guides 630 are provided between the three cooling fans 29 to divide the flow path of each cooling fan 29.

[0082] In this embodiment, when multiple cooling fans 29 are provided, the airflow from each cooling fan 29 interferes with each other, generating turbulence and causing variations in the airflow rate drawn into each cooling fan 29. As a result, it becomes difficult for the cool air to circulate, raising concerns that the temperature distribution within the cooling guide 40 and, consequently, the storage chamber 30S, will deteriorate. Therefore, by providing an air guide 630, the airflow paths of each cooling fan 29 can be separated, rectifying and suppressing the turbulence. This promotes the intake of air from the cooling duct 40 into the cooling fans 29, thereby suppressing temperature variations in the storage chamber 30S and making the temperature distribution more uniform.

[0083] <Embodiment 7> Embodiment 7 will be described with reference to Figure 19. The same reference numerals are used for parts identical to those in the above embodiments, and redundant explanations are omitted. This embodiment differs from Embodiment 6 in that a cover 730 (another example of an auxiliary member) is provided instead of an air guide 630.

[0084] As shown in Figure 19, the cover 730 covers the left, right, and top sides of each cooling fan 29, with a total of three covers provided for each cooling fan 29. In this way, the cover 730 divides the flow path of each cooling fan 29, thereby suppressing the turbulence described above. The cover 730 may be formed as a single component as long as it divides the flow path of each cooling fan 29. Note that the cooler 27 is not shown in Figure 19.

[0085] <Embodiment 8> Embodiment 8 will be described with reference to Figure 20. The same reference numerals are used for parts identical to those in the above embodiments, and redundant descriptions are omitted. This embodiment differs from the above embodiments in that a heat insulating member 840 (another example of an auxiliary member) is provided.

[0086] As shown in Figure 20, the heat insulating member 840 is provided in the first passage 41, which is a lower passage located below the storage chamber 30S within the cooling duct 40. The heat insulating member 840 in this embodiment is thin and is attached to the outer surface of the bottom wall portion 30A that constitutes the bottom surface of the storage chamber 30S.

[0087] Because cold air is heavy and tends to accumulate at the bottom, the lower part of the storage chamber 30S tends to be colder than the upper part. Therefore, by providing an insulating material 840 in the first passage 41, the situation in which the lower part of the storage chamber 30S becomes cold can be suppressed. As a result, temperature variations in the storage chamber 30S can be suppressed, and the temperature distribution can be made more uniform.

[0088] <Other Embodiments> The technologies disclosed herein are not limited to the embodiments described above in the description and drawings, but also include, for example, the following embodiments. (1) The installation location of the duct temperature sensor 18 is not limited to those exemplified in the above embodiment and can be changed as appropriate. (2) The number of insulated doors 12 is not limited to those exemplified in the above embodiment and can be changed as appropriate. [Explanation of Symbols]

[0089] 10... Constant temperature and humidity storage (cooled storage), 11... Enclosure, 17... Cold air supply device, 18... Duct temperature sensor, 19... Control unit, 22... Compressor, 23... Condenser, 27... Cooler, 28... Refrigerant pipe, 29... Cooling fan, 30... Inner enclosure, 30S... Storage room, 40... Cooling duct, 41... First passage (lower passage), 50A... Inlet, 50B... Outlet, 331S... First area, 332S... Second area, 510, 610... First shielding member (auxiliary member), 620... Second shielding member (auxiliary member), 630... Air guide (auxiliary member), 730... Cover (auxiliary member), 840... Insulation member (auxiliary member)

Claims

1. A box with thermal insulation properties, An interior box is positioned inside the box, forming a cooling duct that serves as a passage for cold air between it and the box, and its interior is a storage room. A cooling air supply device that circulates and supplies cold air into the cooling duct, A cooling storage unit comprising an auxiliary member for suppressing temperature fluctuations within the storage chamber.

2. The cooling storage unit according to claim 1, wherein the auxiliary member is a shielding member that blocks a portion of the passage in the cooling duct.

3. The aforementioned cold air supply device is A cooler that cools the air passing through its interior by heat exchange, The system includes a cooling fan that draws in air from the cooling duct and supplies the air cooled by the cooler into the cooling duct, The cooling storage unit according to claim 2, wherein the shielding member is provided near the air intake port from the cooling duct to the cooling fan.

4. The internal space of the storage chamber includes a first region and a second region having a smaller cooling load than the first region. The cooling storage unit according to claim 3, wherein the shielding member is provided near the intake port in a passage located on the second region side of the cooling duct.

5. The aforementioned cold air supply device is A cooler that cools the air passing through its interior by heat exchange, The system includes a cooling fan that draws in air from the cooling duct and supplies the air cooled by the cooler into the cooling duct, The cooling storage unit according to claim 2, wherein the shielding member is provided near the air outlet from the cooler to the cooling duct.

6. The internal space of the storage chamber includes a first region and a second region having a smaller cooling load than the first region. The cooling storage unit according to claim 5, wherein the shielding member is provided near the outlet in a passage located on the second region side of the cooling duct.

7. The aforementioned cold air supply device is A cooler that cools the air passing through its interior by heat exchange, The system includes a plurality of cooling fans that draw in air from within the cooling duct and supply air cooled by the cooler into the cooling duct, The cooling storage unit according to claim 1, wherein the auxiliary member is an air guide provided between the plurality of cooling fans so as to divide the flow paths of each cooling fan.

8. The aforementioned cold air supply device is A cooler that cools the air passing through its interior by heat exchange, The system includes a plurality of cooling fans that draw in air from within the cooling duct and supply air cooled by the cooler into the cooling duct, The cooling storage cabinet according to claim 1, wherein the auxiliary member is a cover that covers each cooling fan so as to divide the flow path of each cooling fan.

9. The cooling storage unit according to claim 1, wherein the auxiliary member is an insulating member provided in a lower passage located below the storage chamber within the cooling duct.

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