JP2008096028A - Freezing machine for refrigerator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a freezing machine for a refrigerator capable of preventing freezing of an object to be cooled without increasing energy consumption. <P>SOLUTION: A supplied air temperature Tout of an evaporator 16 cooling the air distributed from a blower 17 and directly supplying cold air toward an object to be cooled, is detected by an evaporator temperature sensor 22, and a control device 20 increases the air distribution by the blower 17, and lowers a refrigerant discharging capacity of a compressor 11, when the supplied air temperature Tout becomes lower than a certain first reference value Ts1 higher than a freezing temperature of the object to be cooled. Thus the supplied air temperature Tout is increased to prevent the freezing of the object to be cooled. Further as the cold air can be directly supplied toward the object to be cooled, the energy consumption by the refrigerating machine for the refrigerator is not increased. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a refrigerator freezer for refrigerated storage of food and the like, and is effective when applied to a refrigerated vehicle for storing and transporting food refrigerated.

Conventionally, Patent Document 1 discloses a refrigerated vehicle that transports refrigerated food or the like that is an object to be cooled. In the refrigerated vehicle of Patent Document 1, cold air is blown out only near the refrigerator inner wall surface, and the blown cold air is sucked from the refrigerator inner wall surface and forcedly circulated. Thereby, the site | part in which the cooling target object is mounted among the inside which is a cooling target space is maintained in a windless state, and the local freezing of the cooling target object is prevented.
Japanese Utility Model Publication No. 5-29812

  However, in the refrigerated vehicle of Patent Document 1, the part on which the cooling target is placed is in a non-winding state, so that it is difficult to cool the cooling target compared to the case where the cold air is blown directly toward the cooling target. Therefore, in order to sufficiently cool the object to be cooled, the vicinity of the inner wall surface of the refrigerator must be cooled more than necessary, so that the energy consumption of the refrigerator freezer increases.

  An object of this invention is to provide the refrigerator refrigerator which can prevent the freezing of a cooling target object without causing the increase in energy consumption in view of the said point.

  In order to achieve the above object, in the present invention, the blower (17) that blows air into the chamber, which is the space to be cooled, and the blown air blown from the blower (17) and the refrigerant are heat-exchanged to obtain the refrigerant. The evaporator (16) to be evaporated and the evaporator (16) constitute a refrigeration cycle. The compressor (11) for compressing and discharging the refrigerant on the downstream side of the evaporator (16), and the blower volume of the blower (17) A control means (20) for controlling and a blowing temperature detecting means (22) for detecting the blown air temperature (Tout) blown out from the evaporator (16) into the warehouse are provided, and the control means (20) It is characterized by a refrigerator refrigerator for increasing the amount of air blown from the blower (17) when Tout) becomes equal to or lower than a predetermined first reference temperature (Ts1).

  According to this, when the blown air temperature (Tout) becomes equal to or lower than the predetermined first reference temperature (Ts1), the control means (20) increases the amount of air blown from the blower (17). In 16), the amount of heat absorbed by the refrigerant from the blown air per unit amount of blown air can be reduced. As a result, the blown air temperature (Tout) can be increased.

  Therefore, by setting the first reference temperature (Ts1) to a value higher than the freezing temperature of the cooling object accommodated in the warehouse, for example, directly from the evaporator (16) toward the cooling object. Even if cold air is blown out, the object to be cooled is not frozen. Furthermore, since the cooling target is cooled by blowing the cold air directly toward the cooling target, the consumption energy of the refrigerator refrigerator is not increased.

  Further, in the refrigerator refrigerator having the above characteristics, the control means (20) has a function of controlling the refrigerant discharge capacity of the compressor (11), and the control means (20) has a first function of the blown air temperature (Tout). When the temperature becomes 1 reference temperature (Ts1) or lower, the refrigerant discharge capacity of the compressor (11) may be reduced.

  According to this, when the blown air temperature (Tout) becomes equal to or lower than the first reference temperature (Ts1), the control means (20) reduces the refrigerant discharge capacity of the compressor (11). The refrigeration capacity itself can be reduced and the blown air temperature (Tout) can be raised. As a result, the object to be cooled can be reliably prevented from freezing.

  Furthermore, in the refrigerator refrigerator described above, the control means (20) is configured such that the blown air temperature (Tout) is equal to or lower than the first reference temperature (Ts1), and the blower (17) has a maximum blown air volume. The refrigerant discharge capacity of the compressor (11) may be reduced when the compressor is in operation.

  According to this, as means for increasing the blown air temperature (Tout), priority can be given to means for increasing the blowing amount of the blower (17) over means for reducing the refrigerant discharge capacity of the compressor (11). Unnecessarily reducing the refrigeration capacity of the refrigerator refrigerator can be avoided. Moreover, it is possible to avoid a sudden rise in the blown air temperature (Tout) as compared to the case where the increase in the blower volume of the blower (17) and the reduction of the refrigerant discharge capacity of the compressor (11) are performed simultaneously.

  Furthermore, in the refrigerator for refrigerator, the internal temperature detection means (23) for detecting the internal temperature (Tin) in the internal storage, and the target temperature setting means (25) for setting the target temperature (Tset) in the internal storage. The control means (20) has a value (Tc) obtained by subtracting the target temperature (Tset) from the internal temperature (Tin) equal to or greater than a predetermined second reference value (Ts2), and the blown air temperature When (Tout) is equal to or less than the first reference value (Ts1) and the blower (17) is at the maximum flow rate, the refrigerant discharge capacity of the compressor (11) is reduced. May be.

  Here, when the value obtained by subtracting the target temperature (Tset) from the internal temperature (Tin) is equal to or higher than a predetermined second reference value, the internal temperature Tin needs to be rapidly decreased, The freezing capacity of the freezer is likely to be insufficient.

  On the other hand, according to the present invention, when the refrigerating capacity of the refrigerator freezer is likely to be insufficient, the means for decreasing the refrigerant discharge capacity of the compressor (11) as means for increasing the blown air temperature (Tout). On the other hand, since priority can be given to means for increasing the amount of air blown from the blower (17), unnecessary reduction of the refrigerating capacity can be avoided more appropriately.

  Further, in the refrigerator refrigerator having the above-described characteristics, the control means (20) is configured such that the blown air temperature (Tout) is equal to or lower than the first reference temperature (Ts1), and the refrigerant discharge capacity of the compressor (11) is minimized. When the mode is set, the air flow rate of the blower (17) may be increased.

  In this way, the control means (20) reduces the refrigerant discharge capacity of the compressor (11) as a means for increasing the blown air temperature (Tout) as compared with the means for increasing the air flow rate of the blower (17). Even if priority is given to the means, it is possible to avoid a sudden rise in the blown air temperature (Tout).

  In addition, the minimum mode of the refrigerant discharge capacity of the compressor (11) in the present invention does not mean only the state in which the compressor (11) discharges the refrigerant at the minimum flow rate, but the compressor (11) This means that the refrigerant is not discharged.

  Further, in the refrigerator refrigerator having the above-described characteristics, the first reference temperature (Ts1) determined in advance may be a value higher than the freezing temperature of the object to be cooled housed in the refrigerator.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

  An embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a schematic view of a refrigerated vehicle to which a refrigerator refrigerator 10 according to the present invention is applied, and shows a schematic vehicle-mounted state of the refrigerator refrigerator 10. In addition, a refrigerated vehicle is a vehicle which preserve | saves and conveys cooling objects, such as a foodstuff and a drink, at the low temperature of about 1-10 degreeC, and is also called a freezing vehicle, a frozen vehicle, etc.

  The refrigerated vehicle has a refrigerated compartment 2 for accommodating an object to be cooled behind a passenger compartment (operator compartment) 1 arranged at the forefront of the vehicle. Therefore, the inside of the refrigerator 2 becomes a cooling target space cooled by the refrigerator refrigerator 10. In addition, an opening / closing door 4 that opens and closes the opening 3 for carrying in / out the object to be cooled is provided at the rear part of the refrigerator 2.

  Next, the details of the refrigerator refrigerator 10 will be described with reference to FIG. FIG. 2 is an overall configuration diagram of the refrigerator refrigerator 10 of the present embodiment.

  First, in the refrigerator refrigerator 10, the compressor 11 sucks, compresses, and discharges refrigerant downstream of the evaporator 16, which will be described later, and is driven by the vehicle travel engine E through the electromagnetic clutch 11a and the belt V. Force is transmitted and it is driven to rotate. In the present embodiment, a known swash plate type variable displacement compressor capable of variably controlling the refrigerant discharge capacity by an external control signal is employed as the compressor 11.

  The swash plate type variable displacement compressor is configured such that the refrigerant discharge capacity can be adjusted by changing the discharge capacity. This discharge capacity is changed by controlling the pressure in a swash plate chamber (not shown) formed inside the compressor 11 and changing the inclination angle of the swash plate to change the stroke of the piston. The discharge capacity is the geometric volume of the working space where the refrigerant is sucked and compressed. Specifically, it is the cylinder volume between the top dead center and the bottom dead center of the piston stroke.

  Further, the pressure in the swash plate chamber is controlled by the electromagnetic capacity control valve 11b that changes the ratio of introducing the discharge refrigerant (high-pressure refrigerant) and the suction refrigerant (low-pressure refrigerant) into the swash plate chamber, and the discharge capacity is approximately 0% to 100%. % Can be varied. The electromagnetic capacity control valve 11b is driven by a control current In output from a control device 20 described later.

  Further, since the discharge capacity can be changed in the compressor 11 as described above, the operation of the compressor 11 can be substantially stopped by reducing the discharge capacity to about 0%. Therefore, it is good also as a clutchless structure which always connects the rotating shaft of the compressor 11 to a vehicle engine via a pulley and a belt.

  A condenser 12 is connected to the refrigerant discharge side of the compressor 11. The condenser 12 is a radiator that cools the refrigerant by exchanging heat between the refrigerant discharged from the compressor 11 and the outside air blown by the blower 13. The blower 13 is an electric blower that rotationally drives a centrifugal blower fan by an electric motor, and is rotationally driven by a control voltage output from the control device 20 described later.

  The refrigerant that has flowed out of the condenser 12 flows into a gas-liquid separator 14 (receiver) that separates the refrigerant into a gas-phase refrigerant and a liquid-phase refrigerant and stores excess refrigerant. An expansion valve 15 is connected to the liquid-phase refrigerant outlet side of the gas-liquid separator 14. The expansion valve 15 expands the liquid-phase refrigerant separated by the gas-liquid separator 14 under reduced pressure. In this embodiment, a known temperature type expansion valve is used.

  Specifically, the expansion valve 15 has a temperature sensing portion 15 a disposed in the suction side passage of the compressor 11, and the compressor suction side refrigerant is based on the temperature and pressure of the suction side refrigerant of the compressor 11. The degree of superheat of the compressor is detected, and the valve opening is adjusted so that the degree of superheat of the refrigerant on the compressor suction side becomes a predetermined value.

  An evaporator 16 is connected to the refrigerant outlet side of the expansion valve 15. The evaporator 16 evaporates the refrigerant by exchanging heat between the refrigerant decompressed and expanded by the expansion valve 15 and the blown air blown by the blower 17. When the refrigerant is evaporated, the evaporator 16 exhibits an endothermic effect and blows air. It is a cooler that cools air.

  As shown in FIG. 1, the evaporator 16 is mounted on the upper part of the front side of the vehicle inside the refrigerator 2, and is arranged so as to blow cool air directly from here toward the object to be cooled.

  The blower 17 is an electric blower that rotationally drives a centrifugal blower fan by an electric motor, and the number of rotations is controlled by a control voltage output from the control device 20 to be described later to control the amount of blown air. Further, the blower 17 sucks the air in the cabinet and circulates and blows air again toward the cabinet.

  The refrigerant suction side of the compressor 11 is connected to the refrigerant outlet side of the evaporator 16. Therefore, in this embodiment, a known vapor compression refrigeration cycle in which refrigerant circulates in the order of the compressor 11 → the condenser 12 → the gas-liquid separator 14 → the expansion valve 15 → the evaporator 16 → the compressor 11 is configured. The

  Next, the outline of the electric control unit of the present embodiment will be described. The control device 20 includes a known microcomputer including a CPU, a ROM, a RAM, and the like and peripheral circuits thereof. The control device 20 stores a program for controlling the air conditioner in the ROM, and performs various calculations and processes based on the program.

  On the input side of the control device 20, sensor detection signals are input from the internal temperature control sensor group, and various operation switches provided on the refrigerator operation panel 21 disposed in the vicinity of the instrument panel in the front of the passenger compartment 1. An operation signal is input from.

  Specifically, the internal temperature control sensor group includes an evaporator temperature sensor 22 and a blower 17 which are arranged in the air blowing portion of the evaporator 16 and detect the blown air temperature Tout blown from the evaporator 16 into the warehouse. An internal temperature sensor 23 that is disposed in the air suction portion and detects the internal temperature Tin is provided. Therefore, in the present embodiment, the evaporator temperature sensor 22 serves as the blowout temperature detection means, and the internal temperature sensor 23 serves as the internal temperature detection means.

  As the various operation switches, the refrigerator operation panel 21 is provided with an operation switch 24 that outputs an operation start signal of the refrigerator refrigeration apparatus 10, a temperature setting switch 25 that serves as a target temperature setting means for setting a target temperature in the refrigerator, and the like.

  On the other hand, an electromagnetic clutch 11a, an electromagnetic capacity control valve 11b, blowers 13, 17 and the like of the compressor 11 are connected to the output side of the control device 20, and the operation of these devices is controlled by an output signal of the control device 20. The Therefore, the control device 20 constitutes a control means for controlling the amount of air blown by the blower 17 and controlling the refrigerant discharge capacity of the compressor 11.

  Next, control processing executed by the control device 20 in the present embodiment will be described with reference to the flowchart of FIG. This control routine starts when the operation switch 24 is turned on while an ignition switch of a vehicle travel engine (not shown) is turned on.

  First, in step S1, initialization of flags, timers, and the like and initial setting of each component device of the refrigerator refrigerator 10 are performed. Specifically, as the initial setting of each component device, specifically, the electromagnetic clutch 11a of the compressor 11 is turned on (connected state), and the control current In is set so that the refrigerant discharge capacity of the compressor 11 is in the maximum discharge mode. The air flow rate of the blower 17 is set so as to be in the normal air flow mode.

  Here, in the control device 20 of the present embodiment, the refrigerant discharge capacity of the compressor 11 is controlled in several stages from the maximum mode to the minimum mode. Accordingly, the control current In of the electromagnetic capacity control valve 11b is output so that the refrigerant discharge capacity of the compressor 11 is maximized in the maximum discharge mode, and the refrigerant discharge capacity of the compressor 11 is minimized in the minimum discharge mode. The control current In is output.

  The minimum discharge mode of the compressor 11 in the present embodiment means a state in which the compressor 11 discharges the refrigerant at the minimum flow rate, and does not include a state in which the compressor 11 does not discharge the refrigerant. Therefore, in the following description, the state where the compressor 11 does not discharge the refrigerant is referred to as an off mode. Of course, the state in which the compressor 11 does not discharge the refrigerant may be included in the minimum discharge mode.

  In this off mode, more specifically, the controller 20 may turn off the energization of the electromagnetic clutch 11a, or the electromagnetic capacity control so as to reduce the discharge capacity of the compressor 11 to approximately 0%. The control current In of the valve 11b may be output.

  Further, in the present embodiment, the control device 20 controls the capacity of the blower 17 in two stages of the maximum air volume mode and the normal air volume mode. That is, in the maximum air volume mode, the control voltage is output so that the air volume of the blower 17 becomes maximum, and in the normal air volume mode, the control voltage is output so that the air volume is smaller than the maximum air volume and becomes a predetermined air volume. To do.

  Next, in step S2, an operation signal of the refrigerator operation panel 21 is read, in the next step S3, a detection signal detected by the internal temperature control sensor group is read, and in the next step S4, the internal temperature A value Tc obtained by subtracting the target temperature Tset set by the temperature setting switch 25 from the internal temperature Tin detected by the sensor 23 is calculated, and the process proceeds to step S5.

  In step S5, it is determined whether or not Tc is equal to or greater than a predetermined second reference value Ts2 (Ts2 = 3 ° C. in the present embodiment). When Tc is equal to or higher than Ts2, the internal temperature Tin is higher than the target temperature Tset, and it is necessary to perform cool-down control for rapidly decreasing the internal temperature Tin, and go to Step S6. Advance and cool down control. Details of the cool-down control in step S6 will be described later.

  If Tc is not equal to or higher than Ts2 in step S5, the process proceeds to step S7, and it is determined whether Tc is equal to or lower than 0 ° C. When Tc is 0 ° C. or lower, the internal temperature Tin is equal to or lower than the target temperature Tset, and it is assumed that the internal temperature is sufficiently cooled to the desired temperature. Set to OFF mode and go to step 10.

  If Tc is not below 0 ° C. in step S7, it is assumed that it is necessary to perform normal control to bring the internal temperature Tin close to the target temperature Tset, and the routine proceeds to step S9 where normal control is performed. Details of the normal control in step S9 will be described later.

  In step S10, the process waits for the control period τ (in this embodiment, τ = 10 seconds), and returns to step S2 when it is determined that the control period τ has elapsed.

  Next, details of the cool-down control in step S6 will be described with reference to the flowchart of FIG. First, in step S601, it is determined whether or not the blown air temperature Tout is equal to or lower than a predetermined first reference value Ts1 (Ts1 = 1 ° C. in the present embodiment). This Ts1 is determined as a value higher than the freezing temperature of the cooling object accommodated in the warehouse.

  As described above, in the present embodiment, since the cool air is directly blown out from the evaporator 16 toward the cooling target, the cooling target is frozen when the blown air temperature Tout becomes equal to or lower than the freezing temperature of the cooling target. There is a risk.

  Therefore, when the blown air temperature Tout is equal to or lower than Ts1 in step S601, the cooling target is assumed to be frozen, and the process proceeds to step S602, where the blower 17 is forcibly set to the maximum air volume mode. The process proceeds to S603. In step S603, it is determined whether or not the compressor 11 is in the minimum discharge mode.

  If the compressor 11 is in the minimum discharge mode at step S603, the compressor 11 is set to the off mode at step S604, and the process proceeds to step S10. On the other hand, if the compressor 11 is not in the minimum discharge mode in step S603, the discharge capacity of the compressor 11 is reduced by one step in step S605, and the process proceeds to step S10.

  If the blown air temperature Tout is not lower than Ts1 in step S601, it is determined that there is no risk of the object to be cooled freezing, and the process proceeds to step S606, where the blown air temperature Tout is 3 ° C. or higher. Determine whether. If the blown air temperature Tout is 3 ° C. or higher, it is determined that the refrigerating capacity of the refrigerator freezer 10 is insufficient, and the process proceeds to step S607.

  In step S607, it is determined whether or not the compressor 11 is in the maximum discharge mode. If the compressor 11 is in the maximum discharge mode in step S607, the blower 17 is forcibly set in the normal air volume mode in step S608, and the process proceeds to step S10. On the other hand, if the compressor 11 is not in the maximum discharge mode in step S607, the discharge capacity of the compressor 11 is increased by one step in step S609, and the process proceeds to step S10.

  Moreover, when the blowing air temperature Tout is not 3 degreeC or more in step S606, it is assumed that the refrigerating capacity of the refrigerator freezer 10 is not insufficient, and the process proceeds to step S10.

  Next, details of the normal control in step S9 will be described with reference to the flowchart of FIG. First, in step S901, it is determined whether or not the blown air temperature Tout is 3 ° C. or higher. If the blown air temperature Tout is 3 ° C. or higher, it is determined that the refrigerating capacity of the refrigerator freezer 10 is insufficient, and the process proceeds to step S902.

  In step S902, the blower 17 is forcibly set to the normal air volume mode, and the process proceeds to step S903. In step S903, it is determined whether or not the compressor 11 is in the maximum discharge mode.

  When the compressor 11 is in the maximum discharge mode in step S903, the process proceeds to step S10. On the other hand, if the compressor 11 is not in the maximum discharge mode in step S903, the process proceeds to step S904, the discharge capacity of the compressor 11 is increased by one step, and the process proceeds to step S10.

  If the blown air temperature Tout is not 3 ° C. or higher in step S901, it is determined that the refrigerating capacity of the refrigerator refrigerator 10 is not insufficient, and the flow proceeds to step S905, where the blown air temperature Tout is equal to or lower than Ts1. It is determined whether or not. As described above, when the blown air temperature Tout is equal to or lower than Ts1, the cooling target may be frozen.

  Therefore, if the blown air temperature Tout is equal to or lower than Ts1 in step S905, it is assumed that the cooling target may be frozen, and the process proceeds to step S906, and whether or not the compressor 11 is in the minimum discharge mode. Determine. When the compressor 11 is in the minimum discharge mode in step S906, the process proceeds to step S907, and it is determined whether or not the blower 17 is in the maximum air volume mode.

  If the blower 17 is in the maximum air volume mode in step S907, the compressor 11 is set to the off mode in step S908, and the process proceeds to step S10. On the other hand, if the blower 17 is not in the maximum air volume mode in step S907, the blower 17 is forcibly set in the maximum air volume mode in step S909, and the process proceeds to step S10.

  If the compressor 11 is not in the minimum discharge mode in step S906, the blower 17 is forcibly set to the normal air volume mode in step S910, and the discharge capacity of the compressor 11 is increased by one step in the next step S911. Decrease and go to step S10. Furthermore, when the blown air temperature Tout is not equal to or lower than Ts1 in step S905, the process proceeds to step S10 on the assumption that the cooling target is not likely to freeze.

  In the refrigerated vehicle of the present embodiment, the above control is performed. Therefore, in both the cool-down control and the normal control, when the blown air temperature Tout becomes equal to or lower than Ts1 (1 ° C.), the blast volume of the blower 17 is increased. Since the refrigerant discharge capacity of the compressor 11 is reduced, the blown air temperature Tout can be increased.

  As a result, the cooling object can be reliably prevented from freezing even when the cool air is blown directly from the evaporator 16 toward the cooling object. Furthermore, since the cool air can be blown directly toward the object to be cooled, the energy consumption of the refrigerator refrigerator is not increased.

  Further, in the cool-down control in which the refrigerating capacity of the refrigerator refrigerator 10 is insufficient as in the case where the value obtained by subtracting the target temperature Tset from the internal temperature Tin is equal to or higher than a predetermined second reference value, In order to increase the temperature Tout, priority is given to means for increasing the air flow rate of the blower 17 over means for reducing the refrigerant discharge capacity of the compressor 11, so that the refrigerating capacity of the refrigerator refrigerator is unnecessary. Reduction can be avoided.

  Moreover, in normal control, in order to raise the blowing air temperature Tout, even if it gives priority to reducing the refrigerant | coolant discharge capability of the compressor 11 with respect to increasing the ventilation volume of the air blower 17, it blows out rapidly. An increase in the air temperature Tout can be avoided.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows.

  (1) In the above-described embodiment, the compressor 11 adopts a swash plate type variable displacement compressor and employs refrigerant discharge capacity, but the type of the variable displacement compressor is not limited to this. In addition, the refrigerant discharge capacity is adjusted by changing the control current In output from the control device 20 to the electromagnetic capacity control valve 11b, but the adjustment of the refrigerant discharge capacity is not limited to this.

  For example, an electric compressor driven by an electric motor may be adopted, and the refrigerant discharge capacity may be adjusted by changing the rotation speed control of the motor. In addition, by adopting a fixed capacity compressor and intermittently controlling the energization of the electromagnetic clutch 11a, the refrigerant discharge capacity is adjusted by changing the ratio between the compressor operation time and the non-operation time (operation rate). May be.

  (2) In the above-described embodiment, in both the cool-down control and the normal control, the control device 20 performs the control for increasing the air flow rate of the blower 17 and the control for reducing the refrigerant discharge capacity of the compressor 11. Although the blown air temperature Tout is increased, either one of the controls may be performed.

  For example, in the cool-down control in which the refrigerating capacity of the refrigerator refrigerator 10 is insufficient, only control for increasing the air flow rate of the blower 17 is performed, and in normal control, only control for decreasing the refrigerant discharge capacity of the compressor 11 is performed. The blown air temperature Tout may be increased.

  (3) In the above-described embodiment, the control device 20 controls the capacity of the blower 17 in the two stages of the maximum air volume mode and the normal air volume mode, but may further control the capacity in multiple stages. Thereby, the raise degree of the blowing air temperature Tout by making the ventilation volume of the air blower 17 increase can be adjusted appropriately.

  (4) In the above embodiment, as shown in steps S606 and S901, when the blown air temperature Tout is 3 ° C. or higher, it is determined that the refrigerating capacity of the refrigerator refrigerator 10 is insufficient. Other values may be adopted as the determination reference value. Furthermore, you may enable it to set said determination reference value with the refrigerator operation panel 21. FIG.

  (5) In the above-described embodiment, the first reference value Ts1 is 1 ° C. and the second reference value Ts2 is 3 ° C., but other values may be adopted. That is, the first reference value Ts1 may be determined as a value higher than the freezing temperature of the object to be cooled housed in the warehouse, and the second reference value Ts2 is a value that can determine whether or not the cool-down control is necessary. It may be determined as

It is a mimetic diagram of a refrigeration vehicle to which the refrigerator refrigerator for one embodiment was applied. It is a whole block diagram of the refrigerator refrigerator for one embodiment. It is a flowchart which shows control of the control apparatus of one Embodiment. It is a flowchart which shows the principal part of control of the control apparatus of one Embodiment. It is a flowchart which shows another principal part of control of the control apparatus of one Embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 ... Compressor, 16 ... Evaporator, 17 ... Blower, 20 ... Control means,
22 ... blowing temperature detecting means, 23 ... internal temperature detecting means, 25 ... target temperature setting means,
Tout: blowing air temperature, Tin: internal temperature, Tset: target temperature,
Ts1: first reference temperature, Ts2: second reference value.

Claims (6)

A blower (17) that blows air into a cabinet that is a space to be cooled;
An evaporator (16) for causing the refrigerant to evaporate by exchanging heat between the blown air blown from the blower (17) and the refrigerant;
A compressor (11) that constitutes a refrigeration cycle together with the evaporator (16), and compresses and discharges the refrigerant downstream of the evaporator (16);
Control means (20) for controlling the amount of air blown from the blower (17);
A blowing temperature detection means (22) for detecting a blowing air temperature (Tout) blown out from the evaporator (16) into the warehouse;
The control means (20) is configured to increase the amount of air blown from the blower (17) when the blown air temperature (Tout) becomes equal to or lower than a predetermined first reference temperature (Ts1). Refrigerator for refrigerator. The control means (20) has a function of controlling the refrigerant discharge capacity of the compressor (11),
The control means (20) reduces the refrigerant discharge capacity of the compressor (11) when the blown air temperature (Tout) becomes equal to or lower than the first reference temperature (Ts1). The refrigerator for a refrigerator according to claim 1. The control means (20) is configured to compress the compressed air when the blown air temperature (Tout) is equal to or lower than the first reference temperature (Ts1) and the blower (17) has a maximum air flow. The refrigerator refrigerator according to claim 2, wherein the refrigerant discharge capacity of the machine (11) is lowered. A chamber temperature detection means (23) for detecting the chamber temperature (Tin) in the chamber;
A target temperature setting means (25) for setting a target temperature (Tset) in the chamber,
The control means (20) is configured such that a value (Tc) obtained by subtracting the target temperature (Tset) from the internal temperature (Tin) is equal to or greater than a predetermined second reference value (Ts2), and the blown air temperature When (Tout) is equal to or less than the first reference value (Ts1) and the blower (17) is at the maximum airflow, the refrigerant discharge capacity of the compressor (11) is reduced. The refrigerator for a refrigerator according to claim 3, wherein The control means (20), when the blown air temperature (Tout) is equal to or lower than the first reference temperature (Ts1), and the refrigerant discharge capacity of the compressor (11) is in the minimum mode, The refrigerator for a refrigerator according to claim 2, wherein the amount of air blown from the blower (17) is increased. The said 1st reference temperature (Ts1) determined beforehand is a value higher than the freezing temperature of the cooling target accommodated in the said store | warehouse | chamber, The one of Claim 1 thru | or 5 characterized by the above-mentioned. Refrigerator for refrigerator.

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