JP2016223748A - Refrigeration device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigeration device capable of achieving protection, energy saving and freezing capacity improvement of the refrigeration device by properly controlling an air blowing amount according to an operation condition of the refrigeration device under a situation where there is power limit.SOLUTION: A control device of a refrigeration cycle has means S203 for determining whether to use a plurality of evaporators or to use a single evaporator. Also, in the case where the plurality of evaporators are used, when temperatures T1, T2 in a chamber are higher than a first predetermined value X1, a first mode is selected. When the temperatures T1, T2 in the chamber are lower than the first predetermined value X1, a second mode is selected. In the case where the single evaporator is used, when the temperature of the chamber to be cooled is higher than a second predetermined value X2, a third mode is selected, and when the temperature in the chamber is lower than the second predetermined value X2, a fourth mode is selected. In the first mode and the fourth mode, a large amount of power is distributed to air blowing of a condenser.SELECTED DRAWING: Figure 2

Description

  The present invention is a refrigeration apparatus that cools the air in a warehouse with an evaporator provided in each of the plurality of warehouses, and a refrigeration apparatus in which a blower that blows air to the evaporator and the condenser is driven by electric power. It is about.

  The refrigeration apparatus described in Patent Document 1 relates to a refrigerator-freezer that performs cooling by circulating cold heat from an evaporator in a freezer to a refrigerator provided in parallel. This refrigeration apparatus has two adjacent refrigerators that can further improve the cooling performance by effectively using the power that can be supplied.

  When there is no need to cool the second refrigerator when it is necessary to cool the inside of the first refrigerator, the boundary electric fan at the boundary between the first refrigerator and the second refrigerator is stopped, and the boundary electric fan is stopped. By this, the electric power which produced surplus power is supplied to the electric fan for 1st refrigerators.

  Further, when at least the inside of the first refrigerator needs to be cooled, if the refrigerant pressure in the condenser decreases, there is no problem even if the air volume of the condenser electric fan is reduced. Reduce supply. And according to this reduced electric power, the electric power supplied to either the electric fan for 1st refrigerators, the boundary electric fan, or both is increased.

  However, the refrigeration apparatus described in Patent Document 1 is not a refrigeration apparatus having a plurality of evaporators arranged in parallel in the refrigeration cycle, but cool air supplied by a single evaporator from the first refrigerator by a boundary electric fan. 2 Supply to the refrigerator side.

  Next, Patent Document 2 discloses a refrigeration apparatus having a plurality of evaporators arranged in parallel in a refrigeration cycle. However, this refrigeration apparatus relates to prevention of stagnation of the refrigerant, and is not an apparatus that supplies electric power to the blower using limited electric power.

JP 2002-81825 A JP 2004-132635 A

  A commercial power source is used to cool the interior of the refrigerator when the freezer is stopped. However, there is a limitation on the power rating of the commercial power supply. When power is consumed exceeding the limit, the breaker of the switchboard that supplies commercial power is tripped and the power is shut off. It also induces power supply and wiring failures. A refrigeration apparatus having a plurality of evaporators has an evaporator blower in each evaporator. The plurality of evaporator fans and condenser fans consume electric power, but it is required to cool the interior efficiently while using limited electric power.

  In view of the above-described problems, the present invention can appropriately control the amount of air blown to the evaporator and the condenser in accordance with the operating state of the refrigeration apparatus, thereby protecting the refrigeration apparatus, saving power, and improving the refrigeration capacity. It aims at providing the freezing apparatus which can be performed. Descriptions of patent documents listed as prior art can be introduced or incorporated by reference as explanations of technical elements described in this specification.

In order to achieve the above object, the present invention employs the following technical means. That is, in the present invention, the refrigerant discharged from the compressor (2) flows through the condenser (4) and flows through the plurality of evaporators (9, 14) connected in parallel to return to the compressor (2). A cycle, a condenser blower (5) for cooling the condenser (4), and an evaporator blower (10, 15) for sending air to the respective evaporators (9, 14) to cool the respective interiors. A refrigeration apparatus for driving a condenser blower (5) and an evaporator blower (10, 15) with power from a power source, the power consumption of the condenser blower (5), and each evaporator blower ( 10 and 15) is set, and a control device (24) for controlling the amount of air blown by each blower is provided, and the control device (24) sends air to the plurality of evaporators (9, 14). Discriminating means (S203, S403) for determining whether to blow air to a single evaporator
In the case of sending air to the plurality of evaporators (9, 14), the first mode is set when at least the internal temperature (T1, T2) or the refrigerant pressure (P1) is higher than the first predetermined value (X1, Xp1). A first selection means (S205, S405) for selecting and selecting the second mode when the temperature in the storage or the pressure of the refrigerant is not higher than the first predetermined value;
In the case of blowing air to a single evaporator, the third mode is selected when at least the temperature in the cabinet to be cooled or the pressure of the refrigerant is higher than the second predetermined value (X2, Xp2), and the temperature in the cabinet or the refrigerant Second selection means (S209, S409) for selecting the fourth mode when the pressure is not higher than the second predetermined value,
In the first mode, the amount of air blown to the condenser is larger than the amount of air blown to each evaporator,
In the second mode, the amount of air sent to the condenser is less than the amount of air sent to each evaporator,
In the third mode, the amount of air blown to the condenser and the amount of air blown to the evaporator to be blown are not less than the amount of air blown in the second mode,
Further, the fourth mode is characterized in that the amount of air blown to the condenser is equal to or larger than the amount of air blow in the third mode.

  In the present invention, in the first mode in which the compressor is subjected to a high temperature load, the amount of air blown to the condenser, that is, the magnitude of the supplied power is made larger than the amount of air blown to each evaporator. Here, as a comparative example, for example, in the case of two evaporators, an example in which the amount of air blown to the condenser is fixed as one fifth (50 as a ratio) of the blower allowable power supply capacity (250 as a ratio) is given. explain. Compared to this comparative example, in the first mode, the air flow rate of the condenser is increased, the performance of the condenser is improved, and the pressure on the high pressure side of the compressor does not become extremely high.

  Further, in the fourth mode in which the compressor becomes a low temperature load and the amount of refrigerant returning to the compressor may decrease and the temperature of the compressor may increase, the amount of air blown to the condenser, that is, the magnitude of the supplied power is reduced. More than in the case of the third mode. Therefore, compared with the comparative example which fixes the ventilation volume to a condenser as 1/5 of initially allocated electric power, the ventilation volume of a condenser increases, the performance of a condenser improves, and a high voltage | pressure falls. As a result, the high pressure is reduced, the load on the compressor is reduced, the refrigerant flow rate is increased, and the compressor can be sufficiently cooled by the refrigerant.

  Thus, refrigeration cycle efficiency improves by optimizing the ventilation volume of a condenser more than the ventilation volume of an evaporator. As a result, under conditions where there is a limit to the power that can be supplied, it is possible to appropriately control the amount of air blown in accordance with the operating status of the refrigeration apparatus, thereby protecting the refrigeration apparatus, saving power, and improving the refrigeration capacity.

  In addition, the code | symbol in parentheses as described in a claim and said each means thru | or description is an example which shows the correspondence with the specific means as described in embodiment mentioned later easily, and limits the content of invention is not.

It is a block diagram of the refrigerating cycle of the freezing apparatus in 1st Embodiment of this invention. It is a flowchart which shows the control in 1st Embodiment. It is a table | surface which shows the allocation state of the electric power to each air blower in the comparative example with respect to 1st Embodiment. It is a table | surface which shows the allocation state of the electric power to each air blower in 1st Embodiment. It is a flowchart which shows the control in 2nd Embodiment of this invention.

  A plurality of modes for carrying out the present invention will be described below with reference to the drawings. In each embodiment, parts corresponding to the matters described in the preceding embodiment may be denoted by the same reference numerals, and redundant description may be omitted. In the case where a part of the configuration is described in each form, the other forms described above can be applied to the other parts of the configuration. Not only combinations of parts that clearly indicate that the combination is possible in each embodiment, but also the embodiments are partially combined even if they are not clearly specified unless there is a problem with the combination. It is also possible.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described in detail with reference to FIGS. FIG. 1 shows the configuration of the refrigeration cycle of the refrigeration apparatus in the first embodiment. The refrigeration vehicle includes a plurality of cold storages, and includes a first evaporator 9 and a second evaporator 14 that cool the inside of each cold storage. When the refrigeration vehicle is running, the refrigerant is discharged from the engine-driven compressor 1 driven by the engine of the refrigeration vehicle. When the refrigeration vehicle stops and is connected to a commercial power source, the refrigerant is driven by the commercial power source. A refrigerant is discharged from the compressor 2. In the present invention, the term “compressor” refers to the compressor 2 driven by a commercial power source. The compressor 2 driven by a commercial power source includes an electric motor that is rotated by being supplied with DC power converted from the commercial power source, and a compressor main body that is driven via a belt from the output shaft of the electric motor. . The compressor 2 may be an electric compressor that is driven by a DC power source.

  The high-pressure refrigerant discharged from the compressor 2 passes through the check valve 18 among the check valves 18 and 19, and further passes through the high-pressure switch including the refrigerant pressure switch 20 and the refrigerant sensor 30 to the oil separator 3. It reaches. The refrigerant sensor 30 detects the temperature and pressure of the refrigerant and inputs them to the control device 24.

  The oil from which the lubricating oil in the refrigerant is separated by the oil separator 3 is returned to the suction side of the compressor 2 via the capillary tube 3c. The refrigerant enters the condenser 4 and dissipates heat. Outside the vehicle air is blown from the condenser blower 5 to the condenser 4. A liquid receiver 6 is provided on the discharge side of the condenser 4, and the refrigerant discharged from the liquid receiver 6 further includes a first electromagnetic valve 7, a first expansion valve 8, and a second electromagnetic valve 12 that are connected in parallel. It flows into the first evaporator 9 and the second evaporator 14 through the second expansion valve 13. The first evaporator 9 and the second evaporator 14 include a first evaporator blower (also referred to as a first blower) 10 and a second evaporator blower (also referred to as a second blower) 15, respectively. Is blown, and the refrigerant evaporates in the first evaporator 9 and the second evaporator 14 to cool the internal air.

  The temperature of the internal air flowing into the first evaporator 9 and the second evaporator 14 is measured by the first internal temperature sensor 21 and the second internal temperature sensor 22, and the measurement signal is transmitted to the control device 24. Is done. In the control device 24, there are an electronic control device and a compressor 2, a condenser blower 5, a transformer for supplying power to the first blower 10 and the second blower 15, which are two evaporator blowers, a converter, and an electromagnetic switch Etc. are provided. The refrigerant flowing out from the first evaporator 9 and the second evaporator 14 returns to the suction side of the compressor 2 via the gas-liquid separator 11. An SPR (Suction Pressure Regulator) is provided on the suction side of the compressor 2.

  Next, the control in the control device 24 will be described based on the flowchart shown in FIG. When the control starts, in step S202, it is detected whether or not the refrigerated vehicle is stopped in a specific yard and connected to a commercial power source. When connected to the commercial power source, the process proceeds to step S203, and it is determined whether or not the both-side operation for cooling the inside of each cold storage using both the first evaporator 9 and the second evaporator 14 is selected. The two-side operation and the one-side operation of either the first evaporator 9 or the second evaporator 14 are selected by operating the operation panel 23 by the driver.

  For example, when the load to be cooled is stored in each warehouse, the both-side operation is selected. When the both-side operation is selected, the first internal temperature T1 and the second internal temperature T2 are read from the values of the first internal temperature sensor 21 and the second internal temperature sensor 22 in step S204. Next, in step S205, it is determined whether one of the first internal temperature T1 and the second internal temperature T2 is greater than a first predetermined value X1 that is a predetermined internal temperature set in advance. The first predetermined value X1 is set to 20 ° C. as an example. If either the first internal temperature T1 or the second internal temperature T2 is greater than the first predetermined value X1, the process proceeds to step S206. In step S206, control is performed in the first mode so that the air flow rate of the condenser blower 5, the air flow rate of the first air blower 10, and the air flow rate of the second air blower 15 become the air flow rate preset as the first mode. . That is, control is performed so that the air flow rate of the condenser blower 5 is larger than the air flow rates of the first blower 10 and the second blower 15.

  In the first embodiment, assuming that the ratio of power allocated to the entire blower in advance is 250, the amount of air blown by the condenser blower 5, that is, the ratio of power consumed by the condenser blower 5 is 100 ± 10. The ratio of the electric power consumed with the ventilation volume of the air blower 10 and the 2nd air blower 15 is set to 75 ± 10, respectively.

  For example, the power allocated to the entire blower in advance is the blower allowable power supply capacity 400 VA, and this 400 VA is expressed as 250 in proportion. In this case, the power consumed by the condenser blower 5 is set to 160 ± 10 VA, which is 40% (100/250) of 400 VA, and the power consumed by the blast volume of the first blower 10 and the second blower 15 is 400 VA, respectively. Each of them is 120 ± 10 VA which is 30% (75/250).

  The amount of blast is determined in proportion to the allocated power. The amount of air blown from these blowers is determined by controlling the magnitude of the DC voltage supplied to the blower. In this case, the actual air flow rate may be monitored by a sensor and feedback control may be performed, or open loop control may be performed in which a voltage calculated in advance by an experiment is applied to the air blower. When the blower uses an AC motor, the frequency or frequency and voltage of the AC power supplied to the blower is set to a preset value to supply power at a predetermined rate.

  If it is determined in step S205 that one of the first internal temperature T1 and the second internal temperature T2 is greater than the first predetermined value X1, the process proceeds to step S207. In step S207, in the second mode, control is performed so that the air flow rate of the condenser blower 5, the air flow rate of the first air blower 10, and the air flow rate of the second air blower 15 become the air flow rate preset as the second mode. . In this 1st Embodiment, if the ratio of the electric power previously allocated to the whole air blower is set to 250, the air blower amount for condensers, ie, the ratio of the electric power consumed with the air blower 5 for condensers, is set to 50 +/- 10. And the ratio of the electric power consumed by the 1st air blower 10 and the 2nd air blower 15 is 100 ± 10, respectively. Thereby, the cooling in the storage is given priority, and the amount of air in the storage supplied to each of the evaporators 9 and 14 is increased as compared with the first mode.

  Next, in step S203, it is determined as NO as a result of determining whether or not the both-side operation for cooling the interior of each warehouse is selected using both the first evaporator 9 and the second evaporator 14, for example, the first In the case of the one-side operation on the two evaporator 14 side, the process proceeds to step S208. In step S208, the second internal temperature T2, which is the internal temperature to be cooled, is read from the value of the second internal temperature sensor 22.

  Next, in step S209, it is determined whether or not the second internal temperature T2 is greater than a second predetermined value X2 that is a predetermined internal temperature. The second predetermined value X2 that is the predetermined internal temperature is set to −20 ° C. as an example. If the second internal temperature T2 is greater than the second predetermined value X2 that is the predetermined internal temperature, the process proceeds to step S210. In this step S210, in the third mode, the blower amount of the condenser blower 5, the blower amount of the first blower 10, and the blower amount of the second blower 15 are set to a ratio of the blown amount set in advance as the third mode. Power allocation is controlled. That is, assuming that the power allocated to the entire blower in advance is 250, the power supply for the condenser blower, that is, the supply power related to the blown amount is 100 ± 10. In addition, the air flow rate of the first blower 10 that is stopped in principle because of the one-side operation is 0 ± 10, and the air flow rate of the second blower 15 is 100 ± 10 to 200 ± 10.

  In step S209, when it is determined whether or not the second internal temperature T2 is greater than a second predetermined value X2 at which the predetermined internal temperature is reached, the second internal temperature T2 is determined from the second predetermined value X2 at which the predetermined internal temperature is reached. If not, the process proceeds to step S211. In step S211, in the fourth mode, the blower amount of the condenser blower 5, the blower amount of the first blower 10, and the blower amount of the second blower 15 are set to a ratio of the blown amount set in advance as the fourth mode. Power allocation is controlled. That is, control is performed so that the amount of air blown by the condenser blower, that is, the power consumed by the condenser blower is equal to or higher than the power consumed by the condenser blower 5 in the third mode.

  In the first embodiment, in the fourth mode, assuming that the power allocated to the entire blower in advance is 250, the supply power related to the condenser blower air flow rate, that is, the air flow rate, is 100 ± 10. In addition, the amount of air blown from the first blower 10 that is stopped in principle because of the one-side operation is 0 ± 10, and the amount of air blown from the second blower 15 is 100 ± 10 to 150 ± 10. Which value is specifically set to 100 ± 10 to 150 ± 10 can be set on the operation panel 23 with reference to the contents of the stored item, the internal temperature, and the like.

  In the fourth mode, the temperature in the cabinet to be cooled is relatively low, and the refrigeration apparatus is in a low temperature load state. In this low temperature load state, the surface temperature of the second evaporator 14 that is operating independently tends to decrease, and the evaporation of the refrigerant is small. Therefore, the expansion valve 13 restricts the refrigerant flow rate, the refrigerant flow rate returning to the compressor 2 decreases, and cooling of the compressor 2 by the refrigerant decreases. Therefore, the temperature of the compressor 2 will rise. In the first embodiment, the refrigeration apparatus increases the air flow rate of the condenser 4 when compared with the second mode when in the low temperature load state, and more than in the third mode. Thereby, the performance of the condenser 4 can be improved. Therefore, the refrigerant flow rate can be increased and the discharge temperature of the compressor 2 can be lowered, and an emergency stop of the refrigeration apparatus can be prevented.

(Operational effects of the first embodiment)
First, a refrigeration apparatus in the development process of the present invention will be described as a comparative example. In the in-vehicle refrigeration apparatus as a comparative example, as shown in the table of FIG. 3, the power of the commercial power supply is taken into consideration with the condenser blower 5 and the first and second condensers for the evaporator in consideration of the power limitation of the commercial power supply. 2 is assigned to the blowers 10 and 15 so that the total power does not exceed the limit power.

  When the ratio of the total power allocated to this blower is 250, the ratio of the power consumption of the condenser blower 5 is limited to about 50 ± 10 (fixed value), which is 1/5. For example, when the total power allocated to the blower is 400 VA determined by the rating of the transformer, the power consumption of the condenser blower 5 is limited to 1/5 of 80 ± 10 VA (fixed value). In addition, when the total power allocated to the blower is 400 VA (250 as a ratio) determined by the rating of the transformer, the blower volume for the evaporator blowers 10 and 15 is 40% of 250. It is set to consume 160 ± 10 VA, which is the ratio of. As described above, in the comparative example, the capacity of the condenser blower 5 is sacrificed so as not to exceed the power limit. However, there is the following problem.

  First, since the power consumption rate of the condenser blower 5 is fixed to about 50 ± 10, the high pressure switch composed of the refrigerant pressure switch 20 is reduced when the refrigeration machine needs to be operated. The refrigeration unit may stop operating. That is, the pressure on the high pressure side of the compressor 2 rises and the high pressure switch is activated during the first mode when the outside air temperature is high and the inside temperature is high during simultaneous operation of operating the plurality of evaporators 9 and 14. Sometimes. For this reason, an SPR is provided on the suction side of the compressor 2 or the rotational speed of the compressor 2 is reduced, but this is not sufficient.

  Second, when the evaporator 14 on one side is operated independently, the heat dissipation capability of the condenser 4 is reduced during the fourth mode, which is a high outside air temperature and a low inside temperature, and the refrigerant from the evaporator 14 The amount is reduced. Therefore, the amount of refrigerant returning to the compressor 2 decreases, and the amount of cooling by the refrigerant in the compressor 2 decreases. Therefore, the refrigerant discharge temperature from the compressor 2 rises and the life of the refrigerant hose may be reduced. In contrast to the comparative example, in the first embodiment, the power consumption of the condenser blower 5 and the power consumption of the blowers 10 and 15 are appropriately controlled by the control device 24.

  In other words, the control device 24 includes means S203 for determining whether to use the plurality of evaporators 9 and 14 to send air to the plurality of evaporators 9 and 14 or to send to the single evaporator 9 or 14. In the case where a plurality of evaporators 9 and 14 are used, the first mode is selected when the temperatures T1 and T2 in the warehouse are higher than the first predetermined value X1. The second mode is selected when the internal temperatures T1 and T2 are lower than the first predetermined value X1. For these selections, a first selection means S205 is provided in the control device 24.

  Further, in the case of using a single evaporator, the third mode is selected when the internal temperature to be cooled is higher than the second predetermined value X2, and when the internal temperature is lower than the second predetermined value X2. The fourth mode is selected. For these selections, a second selection means S209 is provided in the control device 24.

  When the first mode is selected by the control device 24, the amount of air blown to the condenser 4 (electric power) is made larger than the amount of air blown to each of the evaporators 9 and 14 (electric power). In the second mode, the amount of air blown to the condenser 4 is made smaller than the amount of air blown to the respective evaporators 9 and 14. In the third mode, the air flow rate to the condenser 4 and the air flow rate to the evaporator 9 or 14 to be used are equal to or greater than the air flow rate in the second mode. Further, in the fourth mode, the amount of air blown to the condenser 4 is set to be equal to or larger than the amount of air blown in the third mode.

  According to this, in the first mode in which the compressor 2 has a high temperature load, the amount of air blown to the condenser 4, that is, the amount of power supplied to the condenser blower 5 is evaporated to blow to the respective evaporators 9 and 14. The electric power supplied to the blowers 9 and 14 is increased. Therefore, compared with the comparative example of FIG. 3 which fixes the ventilation volume to the condenser 4 as a ratio equivalent to 50 of initially allocated electric power, the ventilation volume of the condenser 4 increases and the performance of a condenser improves. As a result, the pressure on the high pressure side of the compressor 2 does not become extremely high.

  Further, in the fourth mode in which the compressor 2 becomes a low-temperature load and the amount of refrigerant returning to the compressor 2 may decrease and the temperature of the compressor 2 may increase, the amount of air blown to the condenser 4, that is, supplied power Is larger than that in the third mode. Therefore, compared with the comparative example of FIG. 3 or the second mode in which the amount of air blown to the condenser 4 is fixed as 50 equivalent to the initially allocated power, the amount of air blown by the condenser 4 is increased and the performance of the condenser 4 is improved. High pressure decreases. As a result, the high pressure decreases, the load on the compressor 2 decreases, the refrigerant flow rate increases, and the compressor 2 can be sufficiently cooled by the refrigerant.

  Thus, compared with the comparative example, the refrigeration cycle efficiency is improved by further optimizing the amount of air blown to the condenser 4. As a result, it is possible to protect the refrigeration apparatus, save power, and improve the refrigeration capacity in a situation where the power that can be supplied is limited.

  In the first embodiment, the internal temperature is a detection value of a temperature sensor provided on the suction side of the evaporators 9 and 14. According to this, since the inside of the refrigerator is hot, the load on the refrigeration apparatus is large and the high-pressure side pressure of the compressor 2 tends to be high, and because the inside of the refrigerator is low, the load on the refrigeration apparatus is small. It is possible to accurately grasp the situation where the refrigerant return amount to the refrigerant is small and the temperature of the compressor 2 is likely to increase. Note that the blower allowable power supply capacity is, for example, the rated capacity of the transformer when the commercial power supply is converted into a DC power supply having a predetermined voltage for driving the blower. This rated capacity is 400 VA as an example.

(Second Embodiment)
Next, a second embodiment of the present invention will be described. In the following embodiments, the same components as those in the first embodiment described above are denoted by the same reference numerals, description thereof is omitted, and different configurations will be described. In addition, about 2nd Embodiment or less, the same code | symbol as 1st Embodiment shows the same structure, Comprising: The description which precedes is used.

  In the first embodiment, the internal temperature is compared with a predetermined value, and the operation state of the refrigeration apparatus is divided into a first mode to a fourth mode including a high temperature load state and a low temperature load state. However, it can be divided into four modes including a high temperature load mode and a low temperature load mode based on the refrigerant pressure P1 detected by the refrigerant sensor 30 shown in FIG. FIG. 5 shows the control of the second embodiment of the present invention.

  In FIG. 5, when the control is started, in step S402, it is detected whether or not the refrigerated vehicle is stopped in a specific yard and connected to a commercial power source. If it is connected to the commercial power source, the process proceeds to step S403, and it is determined whether or not the both-side operation for cooling the inside of each warehouse using both the first evaporator 9 and the second evaporator 14 is selected. The selection of the both-side operation and the one-side operation of either the first evaporator 9 or the second evaporator 14 is performed by the driver operating the operation panel 23.

  If the both-side operation is selected, the refrigerant pressure P1 is read from the value of the refrigerant sensor 30 in step S404. Next, in step S405, it is determined whether or not the refrigerant pressure P1 is greater than a first predetermined value Xp1 that is a predetermined refrigerant pressure. If the refrigerant pressure P1 is greater than the first predetermined value Xp1, the process proceeds to step S406. In step S406, in the first mode, control is performed so that the air flow rate of the condenser blower 5, the air flow rate of the first air blower 10, and the air flow rate of the second air blower 15 become preset air flow rates.

  That is, the supplied power is controlled so that the air flow rate of the condenser blower 5 is larger than the air flow rates of the first blower 10 and the second blower 15. In the first embodiment, assuming that the ratio of power allocated to the entire blower in advance is 250, the ratio of power for securing the amount of air blown by the condenser blower 5 is 100 ± 10, and the first blower 10 and the second blower 15 are used. The ratio of the electric power for securing the blast volume is 75 ± 10. The blower amount of the blower is determined by controlling the magnitude of the DC voltage supplied to the blower. In this case, 250, which is the upper limit value of the ratio of power that can be supplied to the blower, is determined by the rated capacity of the transformer in the conversion device that converts alternating current into direct current. The upper limit value may be determined by the limiter current of the breaker provided in the circuit. When the blower uses an AC motor, the frequency or frequency and voltage of the AC power supplied to the blower may be set to a preset value and the power may be limited.

  As a result of determining whether or not the refrigerant pressure P1 is greater than the first predetermined value Xp1 in step S405, if NO is determined, the process proceeds to step S407. Here, in the second mode, the power ratio is set so that the air flow rate of the condenser blower 5, the air flow rate of the first air blower 10, and the air flow rate of the second air blower 15 become the air flow rate preset as the second mode. Be controlled. That is, control is performed so that the amount of air blown from the condenser blower 5 is smaller than the amount of air blown from the first blower 10 and the second blower 15. In this first embodiment, if the ratio of the power allocated to the entire blower in advance is 250, the ratio of the power for determining the condenser air flow is set to 1/5, 50 ± 10, and the first blower 10 and the second blower The ratio of the electric power which determines the ventilation volume of the air blower 15 is set to 100 ± 10, respectively. Thereby, the cooling in the storage is given priority, and the amount of air in the storage blown to each of the evaporators 9 and 14 increases.

  Next, in step S403, as a result of determining whether or not the both-side operation for cooling the inside of each warehouse using both the first evaporator 9 and the second evaporator 14 is selected, it is determined as NO, and the one-side operation is performed. If there is, the process proceeds to step S408. In step S408, the refrigerant pressure P2 is read from the value of the refrigerant sensor 30. Next, in step S409, it is determined whether the refrigerant pressure P2 is greater than a second predetermined value Xp2.

  If the refrigerant pressure P2 is greater than the second predetermined value Xp2, the process proceeds to step S410. In this step S410, power is allocated so that the air flow rate of the condenser blower 5, the air flow rate of the first air blower 10, and the air flow rate of the second air blower 15 become the ratio of the air flow rate preset as the third mode. Be controlled. That is, assuming that the ratio of the power allocated to the entire blower in advance is 250, the blower amount of the condenser blower, that is, the ratio of the supplied power related to the blower amount is 50 ± 10 to 100 ± 10. In addition, the ratio of the air flow rate of the first blower 10 that is stopped due to the one-side operation is 0 ± 10, and the ratio of the air flow rate of the second blower 15 is 100 ± 10 to 200 ± 10.

  If the refrigerant pressure P2 is not greater than the second predetermined value Xp2, the process proceeds to step S411. Here, in the fourth mode, the blower amount of the condenser blower 5, the blower amount of the first blower 10, and the blower amount of the second blower 15 are controlled to be the preset air amount as the fourth mode.

  In the second embodiment, assuming that the ratio of power allocated to the entire blower in advance is 250, the ratio of power that determines the amount of air blown from the condenser blower 5 is 100 ± 10. And the electric power which determines the ventilation volume of the 1st air blower 10 which has stopped in principle because of the one side operation is set to 0, and the ratio of the electric power which determines the ventilation volume of the 2nd air blower 15 is set to 100 ± 10 to 150 ± 10. The specific value within the range of 100 ± 10 to 150 ± 10 for the proportion of power proportional to the air flow is determined on the operation panel 23 with reference to the contents of the stored item, the internal temperature, etc. Can be set by the driver. Further, it may be automatically set as a function such as the internal temperature in the automatic mode.

  In the fourth mode, the refrigeration apparatus is in a low temperature load state. In this low temperature load state, the surface temperature of the evaporator 14 tends to decrease and the refrigerant is less evaporated. Therefore, the expansion valve 13 restricts the refrigerant flow rate, the refrigerant flow rate returning to the compressor 2 decreases, and the cooling of the compressor 2 by the refrigerant decreases, so the temperature of the compressor 2 rises. In the second embodiment, the refrigeration apparatus can improve the performance of the condenser 4 by increasing the blast volume of the condenser 4 in the low temperature load state as compared with the second mode. Thereby, the refrigerant | coolant flow rate can be increased and the discharge temperature of the compressor 2 can be reduced, and the emergency stop of a freezing apparatus can be prevented. In the above description, the one-side operation for operating the second blower 15 and the second evaporator 14 has been described. However, the one-side operation for operating the first blower 10 and the first evaporator 9 may be used.

(Operational effect of the second embodiment)
In the second embodiment, the same effect as that of the first embodiment can be obtained. In the second embodiment, in FIG. 1 to be used, the refrigerant discharged from the compressor 2 is allowed to flow to the condenser 4, and is allowed to flow to a plurality of evaporators 9 and 14 connected in parallel to be returned to the compressor 2. You are using a cycle. Further, a condenser blower 5 for cooling the condenser 4 and evaporator blowers 10 and 15 for blowing air to the respective evaporators 9 and 14 to cool the inside of the respective cabinets are provided. The compressor 2, the condenser fan 5, and the evaporator fans 10 and 15 are driven by power from the power source. The power consumption of the condenser fan 5 and the power consumption of the evaporator fans 10 and 15 are set by the control device 24.

  The control device 24 includes a determination unit S403 that determines whether to blow air to the plurality of evaporators 9 and 14 or to blow the single evaporator 9 or 14. In addition, when the plurality of evaporators 9 and 14 are used to blow air to the plurality of evaporators 9 and 14, the first mode is selected when the refrigerant pressure P1 is higher than the first predetermined value Xp1. When the refrigerant pressure P1 is lower than the first predetermined value Xp1, the second mode is selected. For these selections, a first selection means S405 is provided in the control device 24.

  When the single evaporator 9 or 14 is used, the third mode is selected when the refrigerant pressure P2 is higher than the second predetermined value Xp2, and the fourth mode when the refrigerant pressure P2 is not higher than the second predetermined value Xp2. Is selected. For these selections, second selection means S409 is provided in the control device 24.

  In the second embodiment, the refrigerant pressure is the value of the refrigerant sensor 30 that detects the refrigerant pressure before flowing into the condenser 4 on the discharge side of the compressor 2. According to this, the compressor 2, that is, the situation where the load of the refrigeration apparatus is large and the pressure on the high pressure side of the compressor 2 is high, and the temperature of the compressor 2 is small and the refrigerant return amount to the compressor 2 is small. It is possible to accurately grasp the situation where the price is likely to increase.

  The merit of using the value of the refrigerant sensor 30 is that a non-new sensor necessary for control can be utilized. Moreover, the refrigerant pressure P2 of FIG. 5 measures the refrigerant pressure when the temperature of the refrigerant discharged from the compressor is 140 ° C. as an example. For this reason, it is preferable that the refrigerant sensor 30 of FIG. 1 can measure both the pressure and temperature of the refrigerant.

  And in the 1st mode in which the compressor 2 becomes a high temperature load, the ventilation volume of the condenser 4 increases, the performance of the condenser 4 improves, and the pressure of the high pressure side of the compressor 2 does not become extremely high. In the fourth mode in which the compressor 2 becomes a low temperature load, the amount of refrigerant returning to the compressor 2 decreases, the temperature of the compressor 2 rises, and the pressure on the discharge side of the compressor 2 tends to rise. The ventilation volume of the condenser 4 increases, the performance of the condenser 4 improves, and the high pressure decreases. In addition, the ratio of the amount of air blown to the second evaporator 14 that cools the inside of the warehouse, that is, the ratio of electric power, can also be a sufficient amount corresponding to 100 ± 10 to 150 ± 10. As a result, the load on the compressor 2 is reduced, the refrigerant flow rate is increased, the refrigerant return amount to the compressor 2 is not extremely reduced, and the compressor 2 can be sufficiently cooled by the refrigerant.

(Other embodiments)
In the above embodiment, the preferred embodiment of the present invention has been described. However, the present invention is not limited to the above embodiment, and various modifications can be made without departing from the gist of the present invention. It is. The structure of the said embodiment is an illustration to the last, Comprising: The scope of the present invention is not limited to the range of these description. The scope of the present invention is indicated by the description of the scope of claims, and further includes meanings equivalent to the description of the scope of claims and all modifications within the scope.

  An integrated heat exchanger in which the evaporator and the condenser are integrated may be used, or may be separate. The blower may be AC driven or DC driven. That is, the motor of the blower may be a DC motor or an AC motor.

  In the first embodiment, the mode is classified based on the internal temperature, and in the second embodiment, the mode is mainly classified based on the refrigerant pressure. However, the mode may be classified using both the internal temperature and the refrigerant temperature. . Further, the fourth mode may be classified using the outside air temperature. Furthermore, the compressor is divided into a compressor driven by the engine while the refrigeration vehicle is running and a compressor driven by the power from the commercial power supply when the vehicle stops at a specific yard. In common use, the electric compressor may be rotated by electric power from the generator during traveling.

  The power source is not limited to a commercial power source. An external power source, for example, a power source from a marine power source, a power source in a factory, or a power source from an in-vehicle generator may be used. Even with these power sources, it is possible to protect the refrigeration apparatus, save power, and improve the refrigeration capacity under a limited capacity.

  Further, the evaporator and the condenser may be installed at any place such as a vehicle ceiling or floor. A refrigerator equipped with an oil separator is preferred, but can be implemented without an oil separator. Although the description has been made on the assumption that the amount of blown air is proportional to the supplied power, in the case of a blower driven by a DC motor, it may be proportional to the supplied voltage.

  The power of the blower is proportional to the third power of the blown amount. Strictly speaking, the ratio of the electric power supplied to the blower and the ratio of the amount of blown air generated by the blower differ depending on the change in efficiency. However, since it is difficult to accurately measure the blown air volume, it is only necessary to allocate the power that can be allocated as the supplied power ratio to the blow air volume ratio. However, the present invention may measure the amount of blown air and allocate the supplied power as a result.

  The first mode in which the compressor 2 has a high temperature load and the fourth mode in which the compressor 2 has a low temperature load and the amount of refrigerant returning to the compressor 2 decreases to increase the temperature of the compressor 2 are discriminated. For this purpose, the internal temperature, the high-pressure side refrigerant pressure and the refrigerant temperature are used, but other sensor values such as the outside air temperature and the compressor surface temperature may be used. The mode may be determined from the values of these sensors to determine the first mode to the fourth mode located in a specific zone from the zone of the two-dimensional or three-dimensional map.

2 Compressor 4 Condenser 9, 14 Evaporator 5 Condenser Blower 10, 15 Evaporator Blower (First Blower 10, Second Blower 15)
24 Control device T1, T2 Inside temperature P1, P2 Refrigerant pressure X1, Xp1 First predetermined value X2, Xp2 Second predetermined value

Claims (4)

The refrigerant discharged from the compressor (2) flows to the condenser (4) and flows to the plurality of evaporators (9, 14) connected in parallel to return to the compressor (2); A condenser blower (5) for cooling the condenser (4), and an evaporator blower (10, 15) for sending air to each of the evaporators (9, 14) to cool the inside of the respective cabinets, A refrigeration apparatus that drives the condenser blower (5) and the evaporator blower (10, 15) with power from a power source,
A control device (24) for setting the power consumption of the condenser blower (5) and the power consumption of each of the evaporator fans (10, 15) and controlling the amount of air blown by each of the blowers,
The control device (24)
Discriminating means (S203, S403) for determining whether to blow air to a plurality of the evaporators (9, 14) or to blow the single evaporator,
In the case where the plurality of evaporators (9, 14) are blown, at least when the internal temperature (T1, T2) or the refrigerant pressure (P1) is higher than a first predetermined value (X1, Xp1). 1st selection means (S205, S405) which selects 1 mode, and selects the 2nd mode when the temperature in the above-mentioned store or the pressure of the above-mentioned refrigerant is not higher than the 1st predetermined value,
In the case of sending air to the single evaporator, the third mode is selected when at least the temperature in the cabinet to be cooled or the pressure of the refrigerant is higher than a second predetermined value (X2, Xp2), Second selection means (S209, S409) for selecting the fourth mode when the temperature or the pressure of the refrigerant is not higher than the second predetermined value,
In the first mode, the amount of air blown to the condenser is larger than the amount of air blown to each evaporator,
In the second mode, the amount of air blown to the condenser is less than the amount of air blown to each evaporator,
In the third mode, the amount of air blown to the condenser and the amount of air blown to the evaporator to be blown are not less than the amount of air blown in the second mode,
Furthermore, in the fourth mode, the refrigeration apparatus is configured such that the amount of air blown to the condenser is equal to or greater than the amount of air blown in the third mode. In the first mode, the air flow rate to the condenser is made larger than the air flow rate of the condenser in the second mode, and the air flow rate to the evaporator is the air flow rate in the second mode. In the fourth mode, when the amount of air blown to the condenser is equal to or larger than the amount of air blown in the third mode and the amount of air blown to the condenser is increased, the evaporation The refrigeration apparatus according to claim 1, wherein an air flow rate to the container is reduced from an air flow rate in the third mode. There are two evaporator fans, and when the ratio of the allowable power capacity of the fan is 250, in the first mode, the ratio of the magnitude of the supply power related to the amount of air blown to the condenser is 100 ± 10. And the ratio of the magnitude of the supplied power related to the amount of air blown to each evaporator is 75 ± 10,
In the second mode, the ratio of the magnitude of the supplied power related to the amount of air supplied to the condenser is 50 ± 10, and the ratio of the magnitude of the supplied power related to the quantity of air supplied to each evaporator is 100 respectively. ± 10,
In the third mode, the ratio of the amount of power supplied to the condenser is 50 ± 10 to 100 ± 10, and the amount of power supplied to the evaporator to be used is The ratio is 100 ± 10 to 200 ± 10,
In the fourth mode, the ratio of the magnitude of the supplied power related to the amount of air supplied to the condenser is 100 ± 10, and the ratio of the magnitude of the supplied power related to the quantity of air supplied to the evaporator to be used is 100 ±. The refrigeration apparatus according to claim 1, wherein the refrigeration apparatus is 10 to 150 ± 10.   The refrigeration apparatus according to claim 3, wherein the blower allowable power supply capacity is a rated capacity of a transformer in a device that converts a commercial power supply into a DC power supply having a predetermined voltage for driving the blower.

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