JP2020115066A - Constant-temperature high-humidity storage and operating method for the same - Google Patents

Abstract

To suppress a temperature change in a storage chamber in a constant-temperature high-humidity storage.SOLUTION: A constant-temperature high-humidity storage 1 indirectly cools inside of a storage chamber 30S by supplying cold air from a cold air supply device 21 including a variable-rotational frequency type compressor 24 into a cooling duct 40D formed between a heat insulating box 10 and an interior box 30 defining the storage chamber 30S. The constant-temperature high-humidity storage includes: a duct temperature sensor 81D measuring a duct temperature TD at each sampling time t; a data storage section (storage means) 103 in which duct cooling performance PD serving as a target of the duct temperature TD for causing a storage inner temperature TS to reach a preset storage inner temperature set value TSs are stored; a calculation section (calculation means) 104 calculating target rotational frequency CRt of the compressor 24 for lowering the duct temperature TD in accordance with the duct cooling performance PD on the basis of a duct temperature measurement value TDm; and an inverter circuit (compressor drive means) 105 changing the rotational frequency CR of the compressor 24 to the target rotational frequency CRt.SELECTED DRAWING: Figure 4

Description

The technique disclosed by the present specification relates to a constant temperature and high humidity chamber and a method of operating the same.

A constant temperature and high humidity chamber is known as a storage that can store fresh food for a long time without drying. For example, in the constant temperature and high humidity chamber disclosed in Patent Document 1 below, a space portion formed between a box body having a heat insulating wall and a storage room in which food or the like is stored is referred to as a cooling duct (referred to as a cool air duct). Sometimes used as). Cold air is supplied from the cold air supply device to the cooling duct to cool the wall surface of the storage chamber, so that the storage chamber is indirectly cooled (so-called indirect cooling system).

The cool air supply device provided in the constant temperature and high humidity chamber may have a known configuration in which a compressor, a condenser, a cooler and the like are circulated and connected by a refrigerant pipe containing a refrigerant. The condenser is provided with a condenser fan for air-cooling the condenser whose temperature has risen due to condensation heat generated during liquefaction condensation of the refrigerant. A duct fan is provided in the cooling duct to generate a circulating air flow passing through the cooler. When the compressor, the condenser fan, and the duct fan are driven, the air in the cooling duct is sucked and passes through the cooler. The cool air generated by heat exchange while passing through the cooler is discharged toward the cooling duct, so that the storage chamber is indirectly cooled as described above.

Conventionally, a constant speed compressor has been used as a compressor, and by driving/stopping this compressor, the temperature inside the storage chamber is maintained at a substantially constant cooling. That is, the operation of the cold air supply device is controlled by starting the compressor when the internal temperature becomes higher than the preset internal temperature value by a predetermined value or more, and stopping the compressor when the internal temperature becomes lower than the predetermined value by more than the predetermined value.

Japanese Patent Laid-Open No. 05-264158

For example, as described above, when the cool air supply device is controlled by driving/stopping the constant speed compressor, the cooling capacity changes binary depending on whether the compressor is driven or not, so the duct temperature in the cooling duct fluctuates greatly. However, along with this, the variation of the temperature inside the storage compartment also becomes large. In order to preserve fresh food while maintaining freshness, it is desirable to keep the temperature inside the refrigerator as constant as possible and reduce the temperature unevenness in the storage chamber. Therefore, a technique for suppressing temperature fluctuation in the storage chamber has been desired.

The technique disclosed in the present specification has been completed in view of the above circumstances and the like, and an object thereof is to effectively suppress the fluctuation of the temperature (in-store temperature) in the storage chamber in the constant temperature and high humidity chamber. ..

(1) In the constant temperature and high humidity chamber disclosed by the present specification, the inside of the heat insulating box while forming a cooling duct serving as a passage of cold air between the heat insulating box having a heat insulating wall and the heat insulating box. The internal box, which is located on the other side and whose inside is a storage chamber, and the condenser, the cooler, and the variable speed compressor are circulated and connected by a refrigerant pipe filled with a refrigerant to supply cool air into the cooling duct. A cool air supply device that indirectly cools the storage chamber, a duct temperature sensor that measures the duct temperature in the cooling duct at every predetermined sampling time regardless of the driving state of the compressor, and the storage chamber A storage means for storing cooling characteristics indicating a time-dependent change mode of the target duct temperature target value for the duct temperature for setting the internal chamber temperature of the chamber to a preset internal temperature set value; and the duct temperature. Based on the duct temperature measurement value measured by the sensor, the calculating means for calculating the target rotation speed of the compressor for lowering the duct temperature in accordance with the cooling characteristic, and the rotation speed of the compressor as the target rotation speed. Compressor driving means for changing the number according to the number.

According to the above configuration, by applying a variable rotation speed type compressor to an indirect cooling type constant temperature and high humidity chamber and performing inverter control, a constant temperature and high temperature which controls the temperature by driving/stopping the constant speed type compressor. The cooling capacity can be finely adjusted as compared with a wet box. Here, in the indirect cooling type constant temperature and high humidity chamber, rather than directly supplying the cool air from the cool air supply device into the storage chamber, by cooling the wall surface of the inner box with the cool air in the cooling duct, It is descending indirectly. That is, when the number of revolutions of the compressor is changed, it is the duct temperature, not the inside temperature, which is directly influenced and first fluctuates. Therefore, instead of controlling the compressor based on the internal temperature as in the conventional direct cooling type constant temperature oven equipped with an inverter compressor, the rotation speed of the compressor is controlled based on the duct temperature as in the above configuration. By changing the temperature, it is possible to further increase the dependency on the target temperature change mode. In addition, by continuing to measure the duct temperature at every predetermined sampling time even when the compressor is stopped, it is possible to detect the timing at which the compressor should be restarted as soon as possible, and respond accordingly. As a result, it is possible to effectively suppress the temperature fluctuation in the storage chamber in the constant temperature and high humidity chamber.

(2) Further, in the constant temperature and high humidity chamber disclosed by the present specification, in the above (1), the storage means stores temperature association data representing a relationship between the internal temperature and the duct temperature. However, the calculating means may calculate the duct temperature target value from the inside temperature setting value based on the temperature relational data.
In such a configuration, the temperature related data can be calculated from past measured values or the like in consideration of the size (capacity), arrangement, structure, performance, etc. of the related devices and members. According to the above configuration, the duct temperature target value can be appropriately determined by determining the duct temperature target value required to realize the internal cold storage temperature set value based on such temperature association data. ..

(3) Further, in the constant temperature and high humidity chamber disclosed by the present specification, in (1) or (2) above, the cooling characteristic is a target for a duct temperature drop rate defined according to the duct temperature. The target temperature may be calculated based on the duct temperature measurement value, and the target rotation speed for achieving the duct temperature drop rate target value may be calculated. ..
With such a configuration, the target rotation speed of the compressor can be calculated more easily and quickly according to the measured value of the duct temperature.

(4) Further, in the constant temperature and high humidity chamber disclosed by the present specification, in the above (3), the calculation means is the duct temperature for setting the internal temperature to a preset internal temperature set value. For calculating the duct temperature index value as an index, the compressor driving means, when the duct temperature measurement value is higher than the duct temperature upper limit value higher by a predetermined value than the duct temperature index value, the compressor When started, the duct temperature measurement value is lower than the duct temperature lower limit value lower by a predetermined value than the duct temperature index value, the compressor is stopped, and the duct temperature drop rate target value is the duct temperature index value. Is lower than the duct temperature lower limit value and higher than the duct temperature middle value and is a positive value in the first control temperature range of the duct temperature upper limit value or lower, and is lower than the duct temperature lower limit value and higher than the duct temperature lower limit value. It may be a negative value in the second control temperature region of.
According to such a configuration, when the duct temperature measurement value drops to the duct temperature intermediate value, the compressor rotation speed control unit positively corrects the rotation speed of the compressor to reduce the cooling capacity. descend. As a result, the measured value of the duct temperature is less likely to drop to the lower limit value, and the compressor is continuously operated for a longer period. As a result, the rise in the internal temperature due to the stop of the compressor is reduced, and the temperature fluctuation in the storage chamber is suppressed.

(5) Further, the constant temperature and high humidity chamber disclosed in the present specification is, in any of the above (1) to (4), provided in the storage chamber, and an internal temperature sensor for measuring the internal temperature. And an ambient temperature sensor that is provided outside the heat-insulating box and measures an ambient temperature, and the storage unit stores the duct temperature measurement value and the internal temperature measurement measured by the internal temperature sensor. From the ambient temperature measurement value and the ambient temperature measurement value measured by the ambient temperature sensor, the central temperature inferring data for inferring the central temperature in the refrigerator in the central portion of the storage chamber is further stored, and the calculating means is From the duct temperature measured value, the inside temperature measured value, and the ambient temperature measured value, while inferring the inside central temperature based on the central temperature estimation data, the inside central temperature was preset. It is also possible to calculate a target duct temperature index value for the duct temperature to be the inside temperature setting value.
According to such a configuration, from the measured value of the internal temperature by the internal temperature sensor installed in a specific location, the central temperature of the internal storage in the central part of the storage chamber is estimated, and this internal central temperature is the internal temperature set value. Is controlled so that Therefore, it becomes possible to maintain the entire storage chamber at a temperature close to the set temperature in the storage chamber in consideration of variations in the temperature in the storage chamber (internal temperature).

(6) Further, the constant temperature and high humidity chamber disclosed in the present specification further includes an accessory device that can affect the temperature inside the chamber according to the state in (5) above, and the storage means includes Additional data about the influence of the state of the auxiliary equipment on the central temperature in the refrigerator is further stored, the calculation means, the duct temperature measurement value, the internal temperature measurement value, and the ambient temperature measurement value, and the The central temperature in the refrigerator may be inferred based on the central temperature estimation data and the auxiliary data from the information on the state of the auxiliary equipment.
With such a configuration, for example, a dew condensation prevention heater is attached to a heat insulating door or a heat insulating box, and a constant temperature and high humidity chamber in which the temperature inside the chamber fluctuates depending on the energized state of the storage chamber with higher accuracy. It is possible to keep the whole inside the refrigerator temperature set value.

(7) Further, in the method for operating a constant temperature and high humidity chamber disclosed in the present specification, the heat insulation box having a heat insulation wall and a cooling duct serving as a passage for cold air are formed between the heat insulation box and the heat insulation box. The inner duct, which is arranged inside the heat-insulating box and whose inside is a storage chamber, and the condenser, the cooler, and the variable speed compressor are circulatively connected by a refrigerant pipe in which a refrigerant is sealed, and the cooling duct is provided. A cool air supply device that indirectly cools the storage chamber by supplying cool air into the storage chamber, and a duct temperature in the cooling duct for setting the storage chamber temperature in the storage chamber to a preset storage chamber temperature set value. A storage method in which a cooling characteristic indicating a mode of time-dependent change of the target duct temperature target value is stored, and a method for operating a constant temperature and high humidity chamber, which is irrespective of a driving state of the compressor. The duct temperature in the cooling duct is measured for each sampling time, and the target rotation speed of the compressor for lowering the duct temperature according to the cooling characteristic is calculated based on the measured duct temperature value. Is a method of operating a constant temperature and high humidity chamber in which the number of revolutions is changed according to the target number of revolutions.
With such a configuration, the constant temperature and high humidity can be operated while effectively suppressing the temperature fluctuation in the storage chamber.

According to the technique disclosed in the present specification, it is possible to suppress the temperature change in the storage chamber in the constant temperature and high humidity chamber.

1 is an exploded perspective view of a constant temperature and high humidity chamber according to an embodiment. Longitudinal section of constant temperature and high humidity 2 is a partially enlarged view of the vicinity of the cool air supply device. Block diagram showing a mechanism related to operation control of a constant temperature and high humidity chamber Flowchart showing an example of the operation of the constant temperature and high humidity chamber Flowchart showing an example of temperature control operation of constant temperature and high humidity Timing chart showing an example of temperature control of constant temperature and high humidity

<Embodiment>
Hereinafter, a constant temperature and high humidity chamber according to an embodiment will be described with reference to the drawings.
In the following description, the front left side of the paper in FIG. 1 is the front side or the front side (the back right side of the paper is the rear side or the back side), the front right side of the paper is the right side (the back left side of the paper is the left side), and the upper side is the upper side (the lower side is the lower side). ). In addition, about a some same member, the code|symbol may be attached|subjected to one member and a code|symbol may be abbreviate|omitted about another member. In addition, for parameters such as each temperature to be described later, a set value or an index value may be represented by subscripts of s, a target value of t, and a measured value of m.

[Outline of constant temperature and high humidity chamber]
As shown in FIGS. 1 to 3, in the present embodiment, a four-door type constant temperature and high humidity chamber for business 1 is illustrated. As shown in FIG. 1 and the like, the constant temperature and high humidity chamber 1 includes a heat insulating box (heat insulating box) 10 having a heat insulating wall, a machine room 20 arranged above the heat insulating box 10, and a heat insulating box 10. An interior box 30 that is housed inside and has a storage chamber 30S inside. As shown in FIG. 2 and the like, the heat insulating box 10 has a box shape that is opened forward. A cross-shaped heat insulating partition frame 19 is attached to the front opening of the heat insulating box 10 to form a total of four open areas. As shown in FIG. 1 and the like, a heat insulating door 18 having a packing attached to the back surface thereof is attached to these opening regions so as to be opened and closed in a double-sided double door structure. As a result, the storage chamber 30S can be opened and closed by the heat insulating door 18. In addition, inside the storage room 30S, a shelf network 31 for arranging stored items (foods, etc.) over a plurality of stages is arranged.

Specifically, the heat insulating box 10 includes an outer box 11 made of a metal plate, an inner box 12 made of a metal plate and housed inside the outer box 11 with a space between the outer box 11 and the inner box 12. And a heat insulating material 13 filled therein. The inner box 30 that defines the storage chamber 30S is configured by combining a plurality of heat-conductive metal plates such as stainless steel plates, and has a box shape that is open to the front. The inner box 30 is one size smaller than the inner box 12 of the heat insulating box 10, and is housed inside the heat insulating box 10 with a certain space formed between the inner box 30 and the inner box 12. The space formed between the inner box 30 and the inner box 12 is a cooling duct 40D. The inner box 30 includes a bottom wall portion 30A that forms the bottom surface of the storage chamber 30S, a back surface portion 30B, a ceiling wall portion 30C that forms the ceiling, and a pair of left and right side wall portions. The cooling duct 40D described above is formed outside the walls 30A, 30B, 30C and the like of the inner box 30 so as to surround the upper, left and right sides, the lower side, and the rear of the storage chamber 30S.

Specifically, the cooling duct 40D includes a first passage 41D, a second passage 42D, a third passage 43D, and a pair of fourth passages. As shown in FIG. 2, the first passage 41D is formed between the lower surface 12A of the inner surface of the heat insulation box 10 (inner box 12) facing upward and the outer surface of the bottom wall portion 30A, and the storage chamber 30S. It is a space arranged below. The second passage 42D is a space that is formed between the rear surface 12B facing the front of the inner surface of the heat insulating box 10 and the outer surface of the rear wall portion 30B, and is arranged behind the storage chamber 30S. Further, the third passage 43D is a space formed between the upper surface 12C of the inner surface of the heat insulating box 10 facing downward and the outer surface of the ceiling wall portion 30C, and arranged above the storage chamber 30S. Although not shown in the drawing, the fourth passage is formed between the side surface of the inner surface of the heat insulating box 10 that faces the side and the pair of left and right side wall portions of the inner box 30, and the left and right of the storage chamber 30S. It is a space arranged laterally. The inner surface (the lower surface 12A, the rear surface 12B, the upper surface 12C, and the side surface) of the heat insulating box 10 described above is formed by each panel member that forms the inner box 12.

A cold air supply device 21 is provided in the machine room 20. The cold air supply device 21 includes a condenser 22, a condenser fan 23 attached to the condenser 22, and a compressor 24. The compressor 24 is a variable rotation speed inverter compressor capable of controlling the rotation speed CR in a plurality of stages. As shown in the enlarged view of FIG. 3, the condenser 22, the condenser fan 23, and the compressor 24 are installed on a heat insulating base 26, and a cooler 27 is provided on the lower surface of the base 26. It is attached. As shown in FIG. 1, on the base 26, an electrical equipment box (control box) 25 storing a control unit 100 for controlling the cool air supply device 21 and the like is also installed. An operation box 90 is installed on the front side of the machine room 20. The operation box 90 has a target temperature setting unit 91 and an in-compartment temperature display unit 92. On the front surface of the constant temperature and high humidity room 1, the in-compartment temperature set value TSs is input and set, and the in-compartment temperature TS is confirmed. You can do it.

The base 26 is attached to the heat insulating box 10 so as to close the window hole 16A formed in the ceiling wall portion 16 of the heat insulating box 10 from above. An air duct 50 also serving as a drain pan is provided in the ceiling wall portion 16 of the heat insulating box 10, and a cooler chamber 45D is formed above the air duct 50 in the cooling duct 40D. The cooler 27 is attached so as to project downward from the base 26 and is housed in the cooler chamber 45D. The cooler 27 is circulated and connected to the cool air supply device 21 by a refrigerant pipe in which a refrigerant is sealed, and constitutes a known cooling cycle.

A suction port 50A is formed in the front portion of the air duct 50, and an air outlet 50B is formed in the rear portion thereof. A duct fan (cooling fan) 29 is attached to the suction port 50A. The cooler 27 and the duct fan 29 are arranged outside the interior box 30, more specifically, above the interior box 30 (ceiling wall portion 30C). The duct fan 29 sucks the air in the third passage 43D into the cooler chamber 45D and supplies the air cooled by the cooler 27 to the second passage 42D.

When the duct fan 29 is driven while operating the compressor 24 and the condenser fan 23 of the cold air supply device 21 configured as described above, the air in the third passage 43D of the cooling duct 40D is caused by the duct fan 29 from the suction port 50A. When the air is sucked into the cooler chamber 45D and passes through the cooler 27, it is cooled by heat exchange. The air (cool air) cooled by the cooler 27 is blown from the outlet 50B to the second passage 42D at the rear of the storage chamber 30S, and then goes to the first passage 41D below the storage chamber 30S. Then, after heading from the first passage 41D to the fourth passage on the left and right sides of the storage chamber 30S, it goes around from the fourth passage to the third passage 43D. In this way, cool air is circulated and supplied into the cooling duct 40D. By this cold air, the respective wall portions (bottom wall portion 30A, side wall portion, rear wall portion 30B, ceiling wall portion 30C) that form the interior box 30 are cooled, so that the inside of the storage chamber 30S is indirectly cooled. It Therefore, the inside of the storage chamber 30S is cooled to a predetermined temperature while maintaining high humidity.

As shown in FIG. 1 and FIG. 3 and the like, in the constant temperature and high humidity chamber 1 according to the present embodiment, a dew condensation prevention heater 70 is provided as an incidental device for suppressing dew condensation that occurs near the opening on the front side of the heat insulation box 10. Is provided. The dew condensation preventing heater 70 includes a main body side dew condensation preventing heater 70A provided along the opening on the front side of the heat insulating box 10 and a door side dew condensation preventing heater 70B provided in the heat insulating door 18. As shown in FIG. 3, these dew condensation preventing heaters 70 may be ones in which a cord heater is embedded in a heat insulating material filled in the heat insulating box 10 or the heat insulating door 18, for example. .. The arrangement of the main body side dew condensation prevention heater 70A and the door side dew condensation prevention heater 70B is not particularly limited. For example, in the present embodiment, as shown in FIG. 1, the main body side dew condensation prevention heater 70A is provided as one large rectangular frame along the opening on the front side of the heat insulating box 10. It may be embedded in the partition frame 19 and provided in the shape of four rectangular frames that individually surround each opening region. When these dew condensation preventing heaters 70 are energized, the heat generated from them affects the inside temperature TS in the storage chamber 30S.

[Configuration related to temperature control of constant temperature and high humidity chamber]
A configuration for suppressing the fluctuation of the internal temperature TS in the storage chamber 30S and maintaining the internal temperature TS substantially constant will be described.
As shown in FIG. 3, on the lower surface of the ceiling wall portion 30C of the interior box 30 forming the storage chamber 30S, that is, near the ceiling in the storage chamber 30S, the inside temperature for measuring the inside temperature TS A sensor 81S is provided. A duct temperature sensor 81D for measuring the duct temperature TD is provided on the windward side of the cooler 27 in the cooler chamber 45D of the cooling duct 40D. Further, although not shown in FIG. 3 and the like, an ambient temperature sensor 81A (see FIG. 4) for measuring the ambient temperature TA outside the heat insulating box 10 is provided on the substrate arranged inside the operation box 90. Has been. Although not shown in FIG. 3, a dew condensation prevention heater energization detection sensor (an example of an accessory equipment state detection sensor) 71 (see FIG. 4) is provided, and the main body side dew condensation prevention heater 70A and the door side dew condensation described above are provided. The energization state of the prevention heater 70B is detected. Further, as described above, the user inputs the inside temperature setting value TSs from the target temperature setting unit 91 (see FIGS. 1 and 4) provided in the operation box 90.

As shown in FIGS. 4 to 6, the temperature of the constant temperature and high humidity chamber 1 according to the present embodiment is controlled by a control unit 100 that includes a microcomputer and executes a predetermined program. The microcomputer, which is the main part of the control unit 100, is stored in the electrical equipment box 25 of the machine room 20 as described above.

As shown in the block diagram of FIG. 4, the temperature sensors 81D, 81S, 81A and the dew condensation prevention heater energization detection sensor (an example of an accessory equipment state detection sensor) 71 are connected to the input side of the control unit 100. ing. The information about the energization state of the dew condensation prevention heater 70 can be obtained by detecting with the dew condensation prevention heater energization detection sensor 71 or the like as in the present embodiment, and the dew condensation prevention heater controller that controls the energization state of the dew condensation prevention heater 70. It may be directly obtained from the above. Further, the target temperature setting unit 91 is configured to transmit the value of the internal temperature setting value TSs to the control unit 100.

As shown in FIG. 4, the control unit 100 is provided with a clock unit 102 that emits a clock signal, and the inside temperature sensor 81S, the duct temperature sensor 81D, and the ambient temperature sensor 81A connected to the input side. The measured values of the respective temperatures measured in step S1 and the energization states of the main body-side dew condensation prevention heater 70A and the door-side dew condensation prevention heater 70B detected by the dew condensation prevention heater energization detection sensor 71 are determined by the control unit 100 at constant sampling times. It is designed to be input to. Each value is input at constant sampling time t regardless of the driving state of the compressor 24, that is, while the compressor 24 is stopped during the operation of the constant temperature and high humidity chamber 1. The sampling time t is preferably a time width that is estimated to be optimal for monitoring from the average compressor start/stop cycle time calculated from the past operation results of similar constant temperature and high humidity chambers.

The control unit 100 is also provided with a data storage unit (storage means) 103. The data storage unit 103 stores a duct cooling characteristic (cooling characteristic) PD indicating a temporal change mode of a target duct temperature target value TDt for the duct temperature TD. The duct cooling characteristic PD is stored as a reference table created based on past measured data in consideration of the size (capacity) and performance of each device, an arithmetic expression calculated based on past measured data, and the like. Can be made. The present embodiment exemplifies a case where a reference table that defines the duct temperature drop rate target value RDt according to the duct temperature TD is stored as the cooling characteristic. The duct temperature drop rate RD is defined as the drop amount ΔTD/Δt of the duct temperature TD per unit time.

In the present embodiment, the data storage unit 103 provided in the control unit 100 further stores temperature related data X, central temperature estimation data Y, and incidental data Z. The temperature relational data X is data indicating the relationship between the inside temperature TS and the duct temperature TD. Further, the central temperature estimation data Y is data indicating the relationship between the duct temperature TD, the internal temperature TS and the ambient temperature TA and the internal central temperature TSc which is the temperature in the central portion of the storage chamber 30S. The incidental data Z is data indicating the influence of the energization state of the dew condensation prevention heater 70 on the inside temperature TSc of the refrigerator. These data X, Y, Z are, for example, the degree of influence of each parameter on the in-compartment central temperature TSc, which is calculated based on past measurement data in consideration of the size (capacity) and performance of each related device. Can be stored as a coefficient or the like. Based on these data X, Y, Z, the duct temperature measurement value TDm, the inside temperature measurement value TSm, the ambient temperature measurement value TAm, and the energization state of the dew condensation prevention heater 70, which are input to the control unit 100 at each sampling time. From this, it is possible to infer the central temperature TSc in the refrigerator. In addition, since the storage room 30S is not forcedly ventilated or blown, the storage room except for the positions closest to the respective wall parts forming the inner box 30 (for example, within 1.0 cm to 1.5 cm from the wall surface) The higher the inside of 30S, the higher the inside temperature TS. Since the inside temperature sensor 81S of the present embodiment is installed such that the temperature detecting portion is located below the ceiling wall portion 30C by 2 cm or more, the duct temperature measured value TDm<the inside central temperature TSc<the inside temperature measured value. TSm<ambient temperature measurement value TAm.

The control unit 100 is also provided with a calculation unit (calculation unit) 104 that performs calculation by a microcomputer or the like. The calculation unit 104 calculates the duct temperature index value TDs and the like based on the inside temperature setting value TSs input from the target temperature setting unit 91 while referring to each data X, Y, and Z. Further, based on the measured values TDm, TSm, TAm of the respective temperatures input from the respective temperature sensors 81D, 81S, 81A and the energization state of the dew condensation prevention heater 70, the duct cooling characteristic PD and the respective data X, Y, The target rotation speed CRt of the compressor 24 and the like are calculated while referring to Z.

As shown in FIG. 4, a compressor 24 is connected to the output side of the control unit 100 via an inverter circuit (compressor driving means) 105, and the rotation speed CR is appropriately set in multiple stages (for example, 6 stages). ) Can be changed to.

[An example of temperature control of constant temperature and high humidity]
An example of control will be described with reference to the flowcharts of FIGS. 5 and 6.
As shown in FIG. 5, when the power of the constant temperature and high humidity chamber 1 is turned on and started, and the internal temperature set value TSs is input from the target temperature setting unit 91 (S1), the arithmetic unit 104 causes the internal center of the internal chamber to be set. A duct temperature index value TDs serving as an index for the duct temperature TD is calculated in order to set the temperature TSc to the inside temperature setting value TSs (S2). The duct temperature index value TDs is calculated with reference to the data X, Y, Z stored in the data storage unit 103. Then, a duct temperature upper limit value TDh higher than the duct temperature index value TDs by a predetermined value, a duct temperature lower limit value TDl lower than the duct temperature index value TDs, and a duct temperature intermediate lower than the duct temperature index value TDs and higher than the duct temperature lower limit value TDl. The value TDc is determined (S3). As shown in FIG. 7, which will be described later, the temperature range between the duct temperature upper limit value TDh and the duct temperature lower limit value TDl is the control temperature region of the duct temperature TD. These values can be automatically determined from the duct temperature index value TDs, for example. Specifically, the duct temperature upper limit value TDh is 1.0K higher than the duct temperature index value TDs (TDh=TDs+1.0K), and the duct temperature lower limit value TDl is 1.0K lower than the duct temperature index value TDs ( TDl=TDs-1.0K), and the duct temperature intermediate value TDc can be 0.5K lower than the duct temperature index value TDs (TDc=TDs-0.5K). Subsequently, based on these values, the temperature control is executed according to the time-dependent change mode (duct cooling characteristic PD) of the target duct temperature TDt for making the duct temperature TD the duct temperature index value TDs. (S10). The temperature control of S10 is repeated until the power of the constant temperature and high humidity chamber 1 is turned off and the operation is completed (end).

Specifically, the temperature control of S10 is executed as follows, for example.
As shown in FIG. 6, while the power of the constant temperature and high humidity chamber 1 is ON, the duct temperature measurement value TDm is input to the control unit 100 at every predetermined sampling time t regardless of the driving state of the compressor 24. (S11). The duct temperature measurement value TDm is compared with the duct temperature upper limit value TDh determined in S3 (S12), and when it is larger than this (TDm>TDh), the compressor 24 is started (S13). When the duct temperature measurement value TDm is input while the compressor 24 is being driven (S14), the duct temperature measurement value TDm is compared with the duct temperature lower limit value TDl determined in S3 (S15). If it is smaller (TDm<TDl), the compressor 24 is stopped (S16). On the other hand, when the duct temperature measurement value TDm is equal to or higher than the duct temperature lower limit value TDl (TDm≧TDl), the calculation unit 104 calculates the duct temperature measurement value decrease rate RDm (S17). The calculated duct temperature drop rate RDm of the measured duct temperature is compared with the duct temperature drop target value RDt of the duct cooling characteristic PD (S18). By controlling the rotation speed CR of the inverter compressor 24 to increase or decrease based on the result of this comparison, the cooling capacity is adjusted, the duct temperature TD is brought close to the duct temperature index value TDs, and the inside temperature TSc of the inside of the refrigerator is almost the same. The temperature set value TSs is maintained. Specifically, when the measured duct temperature decrease rate RDm does not reach the duct temperature decrease rate target value RDt (RDm<RDt), the rotation speed CR of the compressor 24 is controlled to increase (S19). If the measured duct temperature decrease rate RDm is equal to the duct temperature decrease rate target value RDt (RDm=RDt), the rotation speed CR of the compressor 24 is maintained as it is (S20). When the measured duct temperature drop rate RDm is larger than the duct temperature drop rate target value RDt (RDm>RDt), the rotation speed CR of the compressor 24 is controlled to be lowered (S21). The above steps are repeated until the instruction to stop the operation of the constant temperature and high humidity chamber 1 is confirmed (S22), and the duct temperature TD is controlled so as to follow the duct cooling characteristic PD.

In S19 and S21 described above, the target rotation speed CRt of the compressor 24 for causing the duct temperature decrease rate RD to change along the duct cooling characteristic PD is calculated by the calculation unit 104. In the present embodiment, the target rotation speed CRt is set to an appropriate rotation speed in order to realize the duct temperature drop rate target value RDt defined in the reference table as the duct cooling characteristic PD. The calculated target rotation speed CRt is transmitted from the control unit 100 to the compressor 24 as a control signal via the inverter circuit 105, and the rotation speed CR is appropriately changed.

The duct cooling characteristic PD may be as shown in FIG. 7 as an example.
In the temperature control example shown in FIG. 7, the duct cooling characteristic PD is a combination of linear functions. When a straight line of a linear function is stored and selected as the time-dependent change mode (duct cooling characteristic PD) of the duct temperature target value TDt, the target duct temperature drop rate target value RDt for the duct temperature TD is Within the temperature range, it becomes a constant value regardless of the duct temperature measurement value TDm.

When the duct temperature measurement value TDm is in a region (TDm>TDh) higher than the duct temperature upper limit value TDh (TDm>TDh), the duct temperature drop rate target value RDt drives the compressor 24 at the maximum rotation speed CR _max . The duct temperature drop rate RD _max (constant value) that can be achieved at this time is set. Further, when the duct temperature measurement value TDm is within the region (supercooling region) lower than the duct temperature lower limit value TDl (TDm<TDl), the duct temperature drop rate target value RDt is the duct when the compressor 24 is stopped. The temperature drop rate RD ₀ (constant value). In the constant temperature and high humidity chamber 1 according to the present embodiment, the duct temperature decrease rate RD ₀ has a negative value (the duct temperature TD rises when the compressor 24 is stopped).

When the duct temperature measured value TDm is within the duct temperature upper limit value TDh or less and the duct temperature lower limit value TDl or more (control temperature region) (TDh≧TDm≧TD1), the duct temperature drop rate target value RDt is in two stages. It shall change. That is, in the first control temperature region of the duct temperature upper limit value TDh or less and the duct temperature intermediate value TDc or more (TDh≧TDm≧TDc) in the control temperature region, the duct temperature drop rate target value RDt is set to the value in the pull-down region. The following positive constant values are used. Further, in the second control temperature region which is lower than the duct temperature intermediate value TDc and is equal to or higher than the duct temperature lower limit value TDl (TDc>TDm≧TDl), the duct temperature drop rate target value RDt is set to a negative value equal to or higher than the value in the supercooling temperature region. It is a constant value. In this way, the rotational speed CR of the compressor 24 is positively reduced when the duct temperature measurement value TDm is lower than the duct temperature intermediate value TDc, and the continuous operation time of the compressor 24 is lengthened. You can In FIG. 7, the rotational speed CR of the compressor 24 is set to the maximum rotational speed CRmax in the pull-down region, and the duct temperature measurement value decrease rate RDm is reduced by gradually decreasing after reaching the first control temperature region. The duct temperature drop rate target value RDt in this temperature range is made to follow. When the temperature further decreases and reaches the second control temperature range, the rotation speed CR of the compressor is decreased to the minimum rotation speed CR _min, and the measured duct temperature decrease rate RDm is the duct temperature decrease rate target value in this temperature range. It is controlled so as to follow the RDt and become a negative value, that is, the duct temperature measurement value TDm increases slightly. After that, when the duct temperature measurement value TDm rises and reaches the first control temperature region of the duct temperature intermediate value TDc or more, the duct temperature drop rate target value RDt becomes a positive value, and therefore, the rotation speed of the compressor 24 again. The CR is increased and the duct temperature measurement value TDm is controlled to decrease.

Further, in the present embodiment, during the operation of the constant temperature and high humidity chamber 1 regardless of the driving state of the compressor 24, the inside temperature sensor 81S also measures the inside temperature TS to monitor whether the temperature control is appropriately performed. To do. It is preferable that the monitoring is performed based on the average temperature measurement value TSm of the inside of the storage for a certain period of time. In this way, it is possible to determine whether temperature control is appropriate or not without being confused by the temporary change in the internal temperature TS. At this time, for example, from the temporal change mode (duct cooling characteristic PD) of the duct temperature target value TDt, the temporal change mode of the internal chamber temperature target value TSt (internal chamber cooling characteristic based on the data X, Y, Z). PS) may be created, and the internal cooling characteristic PS may be compared with the actually measured internal temperature measurement value TSm to perform monitoring. Alternatively, conversely, the duct cooling characteristic PD is created and stored from the internal cooling characteristic PS stored in the data storage unit 103, and the rotation speed CR of the compressor 24 is performed based on the duct cooling characteristic PD, while the internal storage is performed. You may monitor the transition of the internal temperature TS based on the cooling characteristic PS. When it is determined that the temperature control is appropriately performed, the control is continued as it is, and when it is determined that the temperature control is not appropriate, the duct cooling characteristic PD is corrected at any time to perform the control. The correction of the control by monitoring the internal cold storage temperature TS is not shown in the figure).

[Effects of this embodiment]
As described above, the constant temperature and high humidity chamber 1 according to this embodiment has the following configuration (1).
(1) A heat-insulating box (heat-insulating box body) 10 having a heat-insulating wall and a cooling duct 40D serving as a passage for cold air are formed between the heat-insulating box 10 and the inside of the heat-insulating box 10 and the inside is a storage chamber. The interior box 30 of 30S, the condenser 22, the cooler 27, and the variable rotation speed compressor 24 are circulated and connected by the refrigerant pipe in which the refrigerant is sealed, and the cool air is supplied into the cooling duct 40D. A cool air supply device 21 that indirectly cools the inside of the storage chamber 30S, a duct temperature sensor 81D that measures the duct temperature TD in the cooling duct 40D at every predetermined sampling time t regardless of the driving state of the compressor 24, and a storage Duct cooling characteristics (cooling characteristics) showing a time-dependent change mode of the target duct temperature TDt for the duct temperature TD for setting the inside temperature TS in the chamber 30S to the preset inside temperature set value TSs. A compressor 24 for lowering the duct temperature TD in accordance with the duct cooling characteristic PD based on the data storage unit (storage means) 103 in which the PD is stored and the duct temperature measurement value TDm measured by the duct temperature sensor 81D. The calculation unit (calculation unit) 104 for calculating the target rotation speed CRt and the inverter circuit (compressor driving unit) 105 for changing the rotation speed CR of the compressor 24 according to the target rotation speed CRt.

According to the configuration of this embodiment of (1) above, the constant speed type compressor is turned on by applying the variable rotation speed type compressor 24 to the indirect cooling type constant temperature and high humidity chamber 1 and performing inverter control. The cooling capacity can be finely adjusted as compared with a constant temperature/high humidity chamber in which the temperature is controlled by controlling ON/OFF. Here, in the constant temperature and high humidity chamber 1 of the indirect cooling system, the wall surface of the inner box 30 is cooled by the cool air in the cooling duct 40D, instead of directly supplying the cool air from the cool air supply device 21 into the storage chamber 30S. This indirectly lowers the internal temperature TS. That is, when the rotational speed CR of the compressor 24 is changed, it is the duct temperature TD that is directly influenced and first fluctuates, not the inside temperature TS. Therefore, the compressor 24 is controlled based on the duct temperature TD by the configuration of (1) above, rather than controlling the compressor based on the internal temperature unlike the conventional direct cooling type constant temperature oven equipped with the inverter compressor. If the rotational speed CR of is changed, the duct temperature TD can be controlled with high accuracy, the target internal temperature TS can be expressed while following the duct cooling characteristic PD, and the temperature change can be suppressed. Further, the duct temperature TD 81D measures the duct temperature TD at every predetermined sampling time t even when the compressor 24 is stopped, and by continuing the control based on this, the duct temperature TD is sufficiently lowered, for example. The timing at which the compressor 24 should be stopped and then restarted can be detected and dealt with as soon as possible. As a result, temperature fluctuations in the storage chamber 30S in the constant temperature and high humidity chamber 1 can be effectively suppressed.

Further, the constant temperature and high humidity chamber 1 according to the present embodiment has the following configuration (2).
(2) In the above (1), the data storage unit 103 stores the temperature association data X representing the relationship between the inside temperature TS and the duct temperature TD, and the calculation unit 104 stores the temperature association data X in the data association unit X. Based on this, the duct temperature index value TDs is calculated from the inside temperature setting value TSs.

In (2) above, the temperature-related data X can be calculated from past measured values or the like in consideration of the size (capacity), arrangement, structure, performance, etc. of the related devices. The duct temperature index value TDs required to realize the internal temperature set value TSs is calculated based on the temperature related data X, and the duct temperature target value TDs and the duct temperature target value TDm are used to calculate the duct temperature target value. If TDt is determined, the duct temperature target value TDt for realizing the inside temperature set value TSs can be appropriately determined.

Moreover, the constant temperature and high humidity chamber 1 according to the present embodiment has the following configuration (3).
(3) In (1) or (2) above, the duct cooling characteristic PD is stored as a reference table in which a target duct temperature drop rate RDt, which is a target for the duct temperature drop rate RD, is defined according to the duct temperature TD. The calculation unit 104 calculates the target rotation speed CR for achieving the duct temperature drop rate target value RDt based on the duct temperature measurement value TDm.

According to the above configuration (3), the target cooling speed CRt of the compressor 24 according to the duct temperature measurement value TDm is calculated more by storing the duct cooling characteristic PD as a predetermined reference table. It can be done easily and quickly.

Further, the constant temperature and high humidity chamber 1 according to the present embodiment has the following configuration (4).
(4) In the above (3), the calculation unit 104 calculates the duct temperature index value TDs that is an index for the duct temperature TD for making the internal temperature TS the preset internal temperature set value TSs, The inverter circuit 105 activates the compressor 24 when the duct temperature measurement value TDm becomes higher than the duct temperature upper limit value TDh which is higher than the duct temperature index value TDs by a predetermined value (for example, +1.0K), and the duct temperature measurement value TDm. However, when it becomes lower than the duct temperature lower limit value TDl which is lower than the duct temperature index value TDs by a predetermined value (for example, -1.0K), the compressor 24 is stopped. The duct temperature drop rate target value RDt is lower than the duct temperature index value TDs (for example, -0.5K) and higher than the duct temperature lower limit value TDl. The duct temperature intermediate value TDc or more and the duct temperature upper limit value TDh or less. The first control temperature region has a positive value, and the second control temperature region having a duct temperature intermediate value TDc and a duct temperature lower limit value TDl or more has a negative value.

According to the configuration of (4), when the duct temperature measurement value TDm falls to the control temperature region and reaches the second control temperature region, the inverter circuit 105 positively reduces the rotation speed CR of the compressor 24. The cooling capacity is reduced. As a result, the duct temperature measurement value TDm is less likely to drop to the duct temperature lower limit value TDl, and the compressor 24 is continuously operated for a longer period. As a result, the rise in the internal temperature TS due to the stop of the compressor 24 is reduced, and the temperature fluctuation in the storage chamber 30S is suppressed.

Further, the constant temperature and high humidity chamber 1 according to the present embodiment has the following configuration (5).
(5) In any one of the above (1) to (4), the inside temperature sensor 81S provided inside the storage chamber 30S to measure the inside temperature TS, and the ambient temperature TA provided outside the heat insulation box 10. Further, an ambient temperature sensor 81A for measuring the temperature is measured, and the data storage unit 103 measures the duct temperature measurement value TDm, the internal temperature measurement value TSm measured by the internal temperature sensor 81S, and the ambient temperature sensor 81A. Further, central temperature estimation data Y for estimating the central temperature TSc in the storage in the central portion of the storage room 30S is further stored from the measured ambient temperature TAm, and the calculation unit 104 calculates the duct temperature measurement value TDm and the storage temperature. From the measured internal temperature value TSm and the measured ambient temperature value TAm, the in-compartment central temperature TSc is estimated based on the central temperature estimation data Y, and the in-compartment central temperature TSc is set to the preset in-compartment temperature set value TSs. The target duct temperature index value TDs for the duct temperature TD for the calculation is calculated.

According to the configuration of the above (5), from the inside temperature measurement value TSm by the inside temperature sensor 81S installed at a specific location (the upper part of the storage room 30S in the present embodiment), the inside center of the storage room 30S at the inside center. The temperature TSc is inferred, and the inside temperature of the inside TSc is controlled to be the inside temperature set value TSs. Therefore, it is possible to keep the entire storage chamber 30S near the storage temperature set value TSs in consideration of the variation in the temperature in the storage chamber 30S (storage temperature TS).

Moreover, the constant temperature and high humidity chamber 1 according to the present embodiment has the following configuration (6).
(6) In the above (5), a dew condensation prevention heater (an example of an accessory) 70 that affects the inside temperature TS in accordance with the energization state is further provided, and the data storage unit 103 has an energization state of the dew condensation prevention heater 70. The auxiliary data Z regarding the influence of the temperature on the inside temperature TSc of the refrigerator is further stored, and the calculation unit 104 causes the duct temperature measurement value TDm, the inside temperature measurement value TSm, the ambient temperature measurement value TAm, and the condensation prevention heater 70. From the information about the energized state of No. 2, the central temperature TSc in the refrigerator is estimated based on the central temperature estimation data Y and the auxiliary data Z.

According to the above configuration (6), the dew condensation preventing heater 70 is attached near the opening of the heat insulating door 18 and the heat insulating box 10, and the constant temperature and high humidity chamber 1 in which the inside temperature TS changes depending on the energized state is higher. It is possible to maintain the entire storage room 30S close to the inside temperature set value TSs with accuracy.

Moreover, the operating method of the constant temperature and high humidity chamber 1 according to the present embodiment has the configuration of (7) below.
(7) Interior with a heat insulating box 10 having a heat insulating wall and a cooling duct 40D serving as a passage for cold air formed between the heat insulating box 10 and the inside of the heat insulating box 10 to form a storage chamber 30S The box 30, the condenser 22, the cooler 27, and the variable rotation speed compressor 24 are circulatively connected by a refrigerant tube in which a refrigerant is sealed, and cool air is supplied into the cooling duct 40D to indirectly connect the inside of the storage chamber 30S. And a duct temperature target that is a target for the duct temperature TD in the cooling duct 40D for making the inside temperature TS in the storage chamber 30S to be a preset inside temperature set value TSs. A method for operating a constant temperature and high humidity chamber 1 comprising: a data storage unit 103 in which a duct cooling characteristic PD indicating a time-dependent change mode of a value TDt is stored; and a predetermined sampling time regardless of a driving state of a compressor 24. The duct temperature TD in the cooling duct 40D is measured every t, and the target rotational speed CRt of the compressor 24 for lowering the duct temperature TD in accordance with the duct cooling characteristic PD is calculated based on the duct temperature measurement value TDm, The rotation speed CR of the compressor 24 is changed according to the target rotation speed CRt.

According to the above configuration (7), the constant temperature and high humidity chamber 1 can be operated while effectively suppressing the fluctuation of the internal temperature TS in the storage chamber 30S.

<Other embodiments>
The technology disclosed in this specification is not limited to the embodiments described by the above description and the drawings, and the following embodiments are also included in the technical scope, for example.

(1) In the above embodiment, an example in which the duct cooling characteristic PD is represented by a combination of linear functions is shown, but the present invention is not limited to this. The duct cooling characteristic PD may be expressed as a quadratic or higher function.

(2) In the above embodiment, the user sets and inputs only the inside temperature setting value TSs to the target temperature setting unit 91, and based on the duct temperature index value TDs calculated from the inside temperature setting value TSs, the duct temperature upper limit is set. The case where the value TDh, the duct temperature lower limit value TDl, and the duct temperature intermediate value TDc are determined has been described, but the present invention is not limited to this. For example, the user can set and input the upper temperature limit value, the lower temperature limit value, the intermediate temperature value, etc. according to the purpose of use (food to be stored, etc.) and the installation environment of the constant temperature and high humidity chamber 1. May be. From these input values, the duct temperature upper limit value TDh, the duct temperature lower limit value TDl, and the duct temperature intermediate value TDc can be calculated with reference to the data X, Y, Z and the like.

(3) In the above embodiment, the control of the condenser fan 23 and the duct fan 29 was not particularly mentioned, but the rotational speeds of these may be controlled in conjunction with the rotational speed CR of the compressor 24. For example, it is preferable that the condenser fan 23 increase the rotational speed as the refrigerant supply amount of the cool air supply device 21 increases so that the temperature of the condenser 22 does not rise. Therefore, the rotation speed of the condenser fan 23 may be increased or decreased in the same manner as the rotation speed CR of the compressor 24, for example. Further, by changing the rotation speed of the duct fan 29, it is possible to adjust the cooling capacity by changing the circulation amount of the cool air. Therefore, the rotation speed of the duct fan 29 may be changed in a manner different from the rotation speed CR of the compressor 24, and these may be combined to perform control.

(4) The constant temperature and high humidity chamber is not limited to the one described in the above embodiment, and may be one configured to cool a plurality of independent storage chambers or one including a plurality of compressors, for example. Good. The specific temperature range of the inside temperature TS of the storage room is not particularly limited, and the present technology can be applied to a constant temperature and high humidity room having a storage room used for both refrigeration and freezing. Is.

DESCRIPTION OF SYMBOLS 1... Constant temperature and high humidity chamber, 10... Insulation box (insulation box), 21... Cold air supply device, 22... Condenser, 23... Condenser fan, 24... Compressor, 25... Electrical equipment box (control box), 27... Cooler, 29... Duct fan (cooling fan), 30... Interior box, 30S... Storage room, 40D... Cooling duct, 70... Dew condensation prevention heater (an example of auxiliary equipment), 71... Dew condensation prevention heater energization detection sensor (auxiliary equipment) 81A... Ambient temperature sensor, 81D... Duct temperature sensor, 81S... In-compartment temperature sensor, 91... Target temperature setting unit, 100... Control unit, 102... Timekeeping unit, 103... Data storage unit (memory) Means), 104... Calculation unit (calculation means), 105... Inverter circuit (compressor driving means), TD... Duct temperature, TDc... Duct temperature intermediate value, TDh... Duct temperature upper limit value, TD1... Duct temperature lower limit value, TDm ...Duct temperature measured value, TDs...duct temperature index value, TDt...duct temperature target value, TS...indoor temperature, TSc...indoor central temperature, TSm...indoor temperature measured value, TSs...indoor temperature set value, TSt ...Internal temperature target value, TA... Ambient temperature, TAm... Ambient temperature measured value, PD... Duct cooling characteristic (cooling characteristic), RD... Duct temperature drop rate, RDm... Duct temperature measured value drop rate, RDt... Duct temperature drop Rate target value, X... temperature related data, Y... central temperature estimation data, Z... auxiliary data

Claims (7)

An insulating box body having an insulating wall;
An inner box that is arranged inside the heat insulating box while forming a cooling duct to be a passage of cold air between the heat insulating box and the inside of which is a storage chamber,
A cool air supply device in which a condenser, a cooler, and a variable-speed compressor are circulatively connected by a refrigerant tube in which a refrigerant is sealed, and indirectly cools the storage chamber by supplying cool air into the cooling duct. When,
Regardless of the driving state of the compressor, a duct temperature sensor that measures the duct temperature in the cooling duct at every predetermined sampling time,
A storage unit that stores a cooling characteristic indicating a time-dependent change mode of a target duct temperature target value for the duct temperature for setting the internal temperature of the storage chamber to a preset internal temperature setting value,
Based on the duct temperature measurement value measured by the duct temperature sensor, a calculating means for calculating a target rotation speed of the compressor for lowering the duct temperature in accordance with the cooling characteristic,
A constant temperature and high humidity chamber, comprising: a compressor driving unit that changes the rotation speed of the compressor according to a target rotation speed. The storage means stores temperature relational data representing a relationship between the inside temperature and the duct temperature,
The constant temperature and high humidity chamber according to claim 1, wherein the calculation unit calculates the duct temperature target value from the internal temperature setting value based on the temperature relational data. The cooling characteristics include a target duct temperature drop rate target value for the duct temperature drop rate, which is defined according to the duct temperature.
The constant temperature and high humidity chamber according to claim 1 or 2, wherein the calculation means calculates the target rotation speed for achieving the duct temperature drop rate target value based on the duct temperature measurement value. The calculation means is
Calculating a duct temperature index value that is an index for the duct temperature to set the internal temperature to a preset internal temperature setting value,
The compressor driving means,
When the duct temperature measurement value becomes higher than the duct temperature upper limit value higher by a predetermined value than the duct temperature index value, the compressor is started,
When the duct temperature measurement value is lower than a duct temperature lower limit value lower by a predetermined value than the duct temperature index value, the compressor is stopped,
The duct temperature drop rate target value is
It is a positive value in the first control temperature range that is lower than the duct temperature index value and higher than the duct temperature lower limit value and is equal to or higher than the duct temperature intermediate value and is equal to or lower than the duct temperature upper limit value,
The constant temperature and high humidity chamber according to claim 3, wherein a negative value is set in a second control temperature range that is lower than the duct temperature intermediate value and is equal to or higher than the duct temperature lower limit value. An internal temperature sensor provided in the storage chamber for measuring the internal temperature,
An ambient temperature sensor, which is provided outside the heat insulating box and measures an ambient temperature, further comprises:
The storage means stores the duct temperature measured value, the internal temperature measured value measured by the internal temperature sensor, and the ambient temperature measured value measured by the ambient temperature sensor from the measured temperature in the central part of the storage chamber. Central temperature estimation data for estimating the inner central temperature is further stored,
The calculation means is
From the duct temperature measurement value, the internal temperature measurement value, and the ambient temperature measurement value, while inferring the internal chamber central temperature based on the central temperature estimation data,
The duct temperature index value as a target for the duct temperature for setting the inside temperature of the inside of the compartment to a preset inside temperature set value is calculated. Constant temperature and high humidity. According to the state, further equipped with incidental equipment that can affect the temperature in the refrigerator,
The storage means further stores incidental data on the influence of the state of the incidental equipment on the central temperature in the refrigerator,
From the information about the duct temperature measurement value, the inside temperature measurement value, the ambient temperature measurement value, and the state of the auxiliary equipment, the calculating means is based on the central temperature estimation data and the auxiliary data. The constant temperature and high humidity chamber according to claim 5, wherein the central temperature in the chamber is estimated. An insulating box body having an insulating wall;
An inner box that is arranged inside the heat insulating box while forming a cooling duct to be a passage of cold air between the heat insulating box and the inside of which is a storage chamber,
A cool air supply device in which a condenser, a cooler, and a variable-speed compressor are circulatively connected by a refrigerant tube in which a refrigerant is sealed, and indirectly cools the storage chamber by supplying cool air into the cooling duct. When,
A cooling characteristic indicating a time-dependent change mode of a target duct temperature target value for the duct temperature in the cooling duct for setting the internal cold storage temperature in the storage chamber to a preset internal cold storage temperature set value is stored. A method of operating a constant temperature and high humidity chamber, comprising:
Regardless of the driving state of the compressor, the duct temperature in the cooling duct is measured every predetermined sampling time,
Based on the duct temperature measurement value, calculate the target rotational speed of the compressor for lowering the duct temperature in accordance with the cooling characteristic,
A method of operating a constant temperature and high humidity chamber, wherein the rotation speed of the compressor is changed according to the target rotation speed.

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