WO2021106161A1

WO2021106161A1 - Cold heat source system and refrigeration cycle device

Info

Publication number: WO2021106161A1
Application number: PCT/JP2019/046629
Authority: WO
Inventors: 真哉東井上
Original assignee: 三菱電機株式会社
Priority date: 2019-11-28
Filing date: 2019-11-28
Publication date: 2021-06-03
Also published as: JP7154440B2; JPWO2021106161A1

Abstract

A cold heat source system (100) is configured so as to be connected to a load device (101) that includes a first evaporator (160) and a second evaporator (260). The cold heat source system (100) comprises: a first compressor (110) that is provided so as to correspond to the first evaporator (160); a second compressor (210) that is provided so as to correspond to the second evaporator (260); and a control device (190) that controls the first compressor (110) and the second compressor (210) according to a first evaluation value (TD1) and a second evaluation value (TD2) obtained by assigning different weights to the time when a first door (105) provided for a space (104) to be cooled where the load device (101) is installed is open.

Description

Cold heat source system and refrigeration cycle equipment

This disclosure relates to a cold heat source system and a refrigeration cycle device.

Japanese Patent Application Laid-Open No. 62-911178 discloses a refrigerator in which the frequency of power supplied to a compressor or fan device is changed by an inverter to adjust the cooling capacity. This refrigerator detects the number of times the door is opened and the opening time with a detection device within a certain period of time. Then, when at least one of the number of times the door is opened and the opening time detected by the detection device exceeds the threshold value, the frequency is increased by the inverter.

Jikkai Sho 62-91178

However, in a cold heat source system including a plurality of compressors, such as that used in a large freezing and refrigerating warehouse, the fluctuation of the heat load due to the opening and closing of the door is a cooling target space depending on the position of the door. Not uniform in the refrigerator. Therefore, it is necessary to appropriately control each compressor and adjust the refrigerating capacity.

An object of the present invention is to provide a cooling heat source system capable of uniformly cooling a cooling target space by appropriately controlling a plurality of compressors, and a refrigeration cycle device.

The present disclosure relates to a cold heat source system configured to be connected to a load device including a first evaporator and a second evaporator. The cold heat source system is provided in the cooling target space in which the first compressor provided corresponding to the first evaporator, the second compressor provided corresponding to the second evaporator, and the load device are installed. A control device for controlling the first compressor and the second compressor according to the first evaluation value and the second evaluation value, which are weighted differently with respect to the time when the first door is open, is provided.

According to the cold heat source system and the refrigeration cycle device of the present disclosure, the capacities of a plurality of compressors are appropriately controlled when the door is opened and closed, so that the temperature distribution of the cooling target space can be made uniform.

It is a figure which shows the structure of the refrigeration cycle apparatus of the study example. It is a waveform figure which compared and showed two kinds of control about opening and closing of a door in the structure of the refrigerating cycle apparatus of the study example. It is a figure which shows the structure of the cold heat source system and refrigerating cycle apparatus which concerns on Embodiment 1. FIG. It is a figure which showed the relationship between the opening / closing signal of each door, and a weighting coefficient. It is a waveform diagram for demonstrating the control in the structure of the refrigeration cycle apparatus of Embodiment 1. FIG. It is a flowchart which shows the process in each control part of the control apparatus of Embodiment 1. FIG. It is a figure which shows the structure of the cold heat source system and refrigerating cycle apparatus which concerns on Embodiment 2. FIG.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. Hereinafter, a plurality of embodiments will be described, but it is planned from the beginning of the application that the configurations described in the respective embodiments are appropriately combined. The same or corresponding parts in the drawings are designated by the same reference numerals, and the description thereof will not be repeated.

First, in order to facilitate understanding, a study example will be described before the description of the embodiment. In the study example, the control of a basic refrigeration cycle device having one compressor and one door will be described.

FIG. 1 is a diagram showing a configuration of a refrigeration cycle device of a study example. The refrigeration cycle device shown in FIG. 1 includes a cold heat source machine 2, a load device 3, and

extension pipes

82 and 86.

The cold heat source machine 2 is configured to be connected to the load device 3 by

extension pipes

82 and 86. The cold heat source machine 2 includes a compressor 10, a condenser 20, a fan 22, and

pipes

80, 81, and 87.

The flow path from the compressor 10 to the connection port to the load device 3 via the condenser 20 is configured to form a circulation flow path through which the refrigerant circulates together with the load device 3.

The load device 3 includes an expansion device 50, an evaporator 60, a fan 62, and

pipes

83, 84, 85. The expansion device 50 is, for example, a temperature expansion valve that is controlled independently of the cold heat source machine 2.

The compressor 10 compresses the refrigerant sucked from the pipe 87 and discharges it to the pipe 80. The compressor 10 is configured to adjust the operating frequency according to a control signal from the control device 91. By adjusting the operating frequency of the compressor 10, the circulation amount of the refrigerant is adjusted, and the refrigerating capacity of the refrigerating cycle device can be adjusted. Various types of compressors 10 can be adopted, and for example, scroll type, rotary type, screw type and the like can be adopted.

The condenser 20 condenses the refrigerant discharged from the compressor 10 to the pipe 80 and flows it to the pipe 81. The condenser 20 is configured such that a high-temperature and high-pressure gas refrigerant discharged from the compressor 10 exchanges heat with the outside air. By this heat exchange, the heat-dissipated refrigerant condenses and changes into a liquid phase. The fan 22 supplies the condenser 20 with outside air through which the refrigerant exchanges heat in the condenser 20. By adjusting the rotation speed of the fan 22, the refrigerant pressure on the discharge side of the compressor 10 can be adjusted.

The cold heat source machine 2 further includes a pressure sensor 97 and a control device 91.
The pressure sensor 97 detects the pressure PL of the suction refrigerant of the compressor 10 and outputs the detected value to the control device 91.

The control device 91 includes a CPU (Central Processing Unit) 92, a memory 94 (ROM (Read Only Memory) and RAM (Random Access Memory)), a receiving device 96 for inputting various signals, and the like. .. The CPU 92 expands the program stored in the ROM into a RAM or the like and executes the program. The program stored in the ROM is a program in which the processing procedure of the control device 91 is described. The control device 91 executes control of each device in the cold heat source machine 2 according to these programs. This control is not limited to software processing, but can also be processed by dedicated hardware (electronic circuit).

The load device 3 is installed in the cooling chamber 4, which is the cooling target space. The cooling chamber 4 is provided with a door 5 for taking in and out an object to be cooled, and an open / close detection device 98 for detecting the opening / closing of the door 5. The open / close detection device 98 transmits an open / close signal indicating the opening / closing of the door 5 to the control device 91 by wireless or wired communication. The control device 91 receives the open / close signal by the receiving device 96. The CPU 92 integrates the opening time of the door 5 from the open / close signal and stores it in the memory 94.

When the door 5 is opened, the control device 91 increases the refrigerating capacity of the refrigerating cycle device by increasing the operating frequency of the compressor 10 and prevents the temperature of the cooling chamber 4 from rising.

The control device 91 increases the operating frequency of the compressor 10 when the door opening time accumulated by the CPU 92 exceeds a certain time. The processing for increasing / decreasing the operating frequency of the compressor 10 will be described below.

FIG. 2 is a waveform diagram showing a comparison of two types of controls for opening and closing the door in the configuration of the refrigeration cycle device of the study example.

In FIG. 2, the door 5 is open at time t1 and the door is closed at time t4. At this time, an example of controlling the compressor 10 according to the opening and closing of the door 5 is shown by a solid line, and an example of controlling the compressor 10 according to a change in the temperature inside the refrigerator is shown by a broken line.

First, the waveform shown by the solid line will be explained. At times t0 to t1 in FIG. 2, the temperature inside the refrigerator is constant, and the operating frequency is also controlled to a constant frequency f0.

At time t1, the door 5 opens, and an open / close detection device 98 sends an open signal to the receiving device 96. At time t1, the CPU 92 starts the opening time integration process. Further, with the opening of the door, the temperature inside the refrigerator starts to rise from time t1.

At time t2, when the integrated value of the door opening time integrated by the CPU 92 reaches a certain constant value PA, the control device 91 increases the operating frequency of the compressor 10 from f0 to fA. Then, the cooling capacity of the load device 3 increases, and the temperature TA in the refrigerator starts to decrease.

When the door 5 is closed at time t4, a closing signal is transmitted from the open / close detection device 98 to the receiving device 96. Along with this, the CPU 92 stops the processing of integrating the door opening time. Then, the control device 91 changes the operating frequency of the compressor 10 between the frequency f0 before the door is opened and the frequency fA after the compressor speed is increased.

At time t5, after the internal temperature TA reaches the set temperature, the control device 91 changes the operating frequency of the compressor 10 to a predetermined frequency f0, and continues the operation of the compressor 10. The temperature inside the refrigerator may be detected by a temperature sensor (not shown), but the detection value of the pressure sensor 97 provided on the suction side of the compressor 10 may be substituted.

Next, the waveform shown by the broken line will be described. When the door 5 opens at time t1, at time t3, the temperature inside the refrigerator TB measured by a temperature sensor (not shown) reaches a predetermined threshold value. In response to this, the control device 91 increases the operating frequency of the compressor 10 from f0 to fB at time t3. Then, the cooling capacity of the load device 3 increases, and the temperature TB in the refrigerator starts to decrease. Since fB> fA, the descending speed of the internal temperature TB has a larger inclination than the descending speed of the internal temperature TA. Then, when the door 5 is closed at time t4, the inclination of the decrease in the temperature TB in the partition where the cooling load is reduced increases. Then, at time t6, after the internal temperature TB reaches the set temperature, the control device 91 changes the operating frequency of the compressor 10 to a predetermined frequency f0, and continues the operation of the compressor 10.

In this way, it is conceivable to detect the opening and closing of the door 5 by changing the temperature inside the refrigerator, but since it takes time for the temperature inside the refrigerator to rise to the threshold value, the temperature inside the refrigerator tends to rise significantly. is there. Therefore, when the door 5 is opened for a certain period of time and the temperature inside the refrigerator is expected to rise without waiting for the temperature inside the refrigerator to rise, it is better to increase the operating frequency of the compressor 10 to increase the temperature inside the refrigerator. It is preferable to keep it constant.

In the study example shown by the solid line, the intrusion of the heat load due to the opening of the door is simulated by the opening time of the door, and the compressor 10 is accelerated before the temperature inside the chamber reaches the threshold value. It is possible to suppress the temperature rise in the refrigerator more than in the study example. As a result, the temperature rise of the object to be cooled can be suppressed, and the quality of the object to be cooled can be ensured.

Further, in both the study examples shown by the solid line and the broken line, the operating frequency of the compressor 10 is increased in order to secure the target internal temperature. In the study example shown by the solid line, the change in frequency can be made smaller than that in the study example shown by the broken line in order to increase the operating frequency of the compressor 10 while the temperature rise in the refrigerator is still small. As a result, the compressor 10 can be operated within a range of high operating efficiency, and an energy saving effect can be expected by suppressing power consumption.

Embodiment 1.
In the first embodiment, a case where a plurality of compressors are included in the cold heat source will be described. Although the case where the cooling chamber has two doors is illustrated, the number of doors may be one.

FIG. 3 is a diagram showing a configuration of a cold heat source system and a refrigeration cycle device according to the first embodiment.

The refrigeration cycle device shown in FIG. 3 includes a cold heat source system 100, a load device 101, and extension pipes 182,186,282,286.

The cold heat source system 100 is configured to be connected to the load device 101 by extension pipes 182,186,282,286. The cold heat source system 100 includes a cold heat source machine 102 and a cold heat source machine 202. The load device 101 includes a cooler 103 and a cooler 203.

The cold heat source machine 102 includes a first compressor 110, a first condenser 120, and

pipes

180, 181 and 187. The cold heat source machine 202 includes a second compressor 210, a second condenser 220, and

pipes

280, 281, 287.

The flow path from the first compressor 110 to the connection port to the cooler 103 via the first condenser 120 is configured to form a circulation flow path through which the refrigerant circulates together with the cooler 103. The flow path from the second compressor 210 to the connection port to the cooler 203 via the second condenser 220 is configured to form a circulation flow path through which the refrigerant circulates together with the cooler 203.

The cooler 103 includes an expansion device 150, a first evaporator 160, a fan 162, and

pipes

183, 184, 185. The cooler 203 includes an expansion device 250, a second evaporator 260, a fan 262, and

pipes

283, 284, 285. As the

expansion devices

150 and 250, for example, a temperature expansion valve controlled independently of the cold heat source system 100 is used.

The first compressor 110 and the second compressor 210 compress the refrigerant sucked from the

pipes

187 and 287, respectively, and discharge the refrigerant to the

pipes

180 and 280. The first compressor 110 and the second compressor 210 are configured to adjust the operating frequency according to the control signals from the control devices 191,291, respectively. By adjusting the operating frequencies of the first compressor 110 and the second compressor 210, the circulation amount of the refrigerant can be adjusted, and the refrigerating capacity of the refrigeration cycle device can be adjusted. Various types can be adopted for the first compressor 110 and the second compressor 210, and for example, scroll type, rotary type, screw type and the like can be adopted.

The first condenser 120 and the second condenser 220 condense the refrigerant discharged from the first compressor 110 and the second compressor 210 into the

pipes

180 and 280, respectively, and flow them into the

pipes

181, 281. The first condenser 120 and the second condenser 220 are configured such that high-temperature and high-pressure gas refrigerants discharged from the first compressor 110 and the second compressor 210 exchange heat with the outside air, respectively. By these heat exchanges, the heat-dissipated refrigerant condenses and changes into a liquid phase. The

fans

122 and 222 supply the outside air through which the refrigerant exchanges heat in the first condenser 120 and the second condenser 220 to the first condenser 120 and the second condenser 220, respectively. By adjusting the rotation speeds of the

fans

122 and 222, the refrigerant pressures on the discharge side of the first compressor 110 and the second compressor 210 can be adjusted, respectively.

The cold heat source machine 102 further includes a pressure sensor 197 and a control device 191. The cold heat source machine 202 further includes a pressure sensor 297 and a control device 291.

The

pressure sensors

197 and 297 detect the pressures of the intake refrigerants of the first compressor 110 and the second compressor 210, respectively, and output the detected values to the

control devices

191, and 291.

The control device 191 includes a CPU 192, a memory 194 (ROM and RAM), a receiving device 196 for inputting various signals, and the like. The control device 291 includes a CPU 292, a memory 294 (ROM and RAM), a receiving device 296 for inputting various signals, and the like.

The

CPUs

192 and 292 expand the program stored in the ROM into a RAM or the like and execute it. The program stored in the ROM is a program in which the processing procedure of the

control devices

191 and 291 is described. The

control devices

191 and 291 execute control of each device in the cold

heat source machines

102 and 202, respectively, according to these programs. This control is not limited to software processing, but can also be processed by dedicated hardware (electronic circuit).

Both the

coolers

103 and 203 are installed in the cooling chamber 104, which is the cooling target space. The cooling chamber 104 is provided with a first door 105 and a second door 205 for taking in and out an object to be cooled, and open /

close detection devices

198 and 298 for detecting the opening and closing of the first door 105 and the second door 205, respectively. ing. The open /

close detection devices

198 and 298 transmit the first open / close signal D1 and the second open / close signal D2 indicating the open / close of the first door 105 and the second door 205 to the

control devices

191, and 291 respectively by wireless or wired communication. The control device 191 receives the first open / close signal D1 by the receiving device 196. The CPU 192 integrates the opening time of the first door 105 from the first opening / closing signal D1 and stores it in the memory 194. The control device 291 receives the second open / close signal D2 by the receiving device 296. The CPU 292 integrates the opening time of the second door 205 from the second open / close signal D2 and stores it in the memory 294.

In such a configuration, the individual first open / close signal D1 and the second open / close signal D2 are transmitted to the receiving

devices

196 and 296 provided in the individual cold

heat source machines

102 and 202, respectively. When the evaluation value calculated by multiplying the door coefficient weighted for each opening / closing door in each

CPU

192, 292 reaches a certain value or more, the frequency of the corresponding compressor is increased.

The details of the evaluation value calculated by multiplying the weighted door coefficient for each opening / closing door will be described below.

FIG. 4 is a diagram showing the relationship between the opening / closing signal of each door and the weighting coefficient. With reference to FIGS. 3 and 4, the receiving device 196 of the cold heat source machine 102 receives the first opening / closing signal D1 indicating the opening / closing of the first door 105 and the second opening / closing signal D2 indicating the opening / closing of the second door 205. As shown in the following equation (1), the CPU 192 multiplies the first integrated value TS1 of the opening time indicated by the first opening / closing signal D1 by the coefficient K11 to obtain the second integrated value TS2 of the opening time indicated by the second opening / closing signal D2. Multiply by the coefficient K12 to obtain the sum of these as the first evaluation value TD1.
TD1 = TS1 x K11 + TS2 x K12 ... (1)
The CPU 192 controls the increase / decrease of the operating frequency of the first compressor 110 based on the first evaluation value TD1.

Similarly, the receiving device 296 of the cold heat source machine 202 receives the first opening / closing signal D1 indicating the opening / closing of the first door 105 and the second opening / closing signal D2 indicating the opening / closing of the second door 205. As shown in the following equation (2), the CPU 292 multiplies the first integrated value TS1 of the opening time indicated by the first opening / closing signal D1 by the coefficient K21 to obtain the second integrated value TS2 of the opening time indicated by the second opening / closing signal D2. Multiply by the coefficient K22 to obtain the sum of these as the second evaluation value TD2.
TD2 = TS1 x K21 + TS2 x K22 ... (2)
The CPU 292 controls the increase / decrease of the operating frequency of the second compressor 210 based on the second evaluation value TD2.

Each coefficient can be determined based on the distance between the corresponding cooler and the door. When the cooler 103 is closer to the first door 105 than the cooler 203 and the cooler 203 is closer to the second door 205 than the cooler 103, K11> K12 and K21 <K22. Further, when the first door 105 is closer to the cooler 103 than the second door 205 and the second door 205 is closer to the cooler 203 than the first door, K11> K21 and K12 <K22. For example, as shown in FIG. 4, each coefficient can be defined as K11 = 1.0, K12 = 0.3, K21 = 0.3, K22 = 1.0. Each coefficient may be determined in consideration of not only a simple distance but also the flow of cold air.

FIG. 5 is a waveform diagram for explaining the control in the configuration of the refrigeration cycle apparatus of the first embodiment.

From time t11 to t12, the temperature inside the refrigerator is constant, and the operating frequency is also controlled to constant frequencies f110 and f210. At times t12 to t13, when the first door 105 is opened and the second door 205 is closed, the load on the cold heat source machine 102 side increases and the temperature rises. Further, the temperature of the cold heat source machine 202 side rises with a delay.

The

control devices

191 and 291 obtain the first evaluation value TD1 and the second evaluation value TD2 by multiplying the coefficients described in FIG. 4, respectively, and increase the frequency of the compressor when the determination threshold value TDth is reached. In the example shown in FIG. 5, the first evaluation value TD1 on the cold heat source machine 102 side having a large coefficient K11 of the first door 105 reaches the determination threshold value TDth earlier than the second evaluation value TD2 on the cold heat source machine 202 side. (T13). After a delay, the second evaluation value TD2 on the cold heat source machine 202 side reaches the determination threshold value TDth (t14).

At time t13, the operating frequency f110 of the first compressor 110 is increased, and both the internal temperatures T1 and T2 start to decrease. Further, at time t14, the operating frequency f210 of the second compressor 210 is increased, and the rate of decrease in the temperature inside the chambers T1 and T2 is increased.

At time t15, the first door 105 is closed, and the operating frequencies f110 and f210 are both lowered by one step accordingly. The operating frequencies f110 and f210 are returned to the same frequencies as before the first door 105 was opened, in response to the return of the internal temperature T1.

FIG. 6 is a flowchart showing processing in each control unit of the control device of the first embodiment. The processing of the flowchart shown in FIG. 6 is executed in each of the

control devices

191 and 291 shown in FIG.

First, in step S1, it is detected that the door is opened by either the first open / close signal D1 or the second open / close signal D2, and in step S2, the operations of the first evaluation value TD1 and the second evaluation value TD2 are performed by the control device, respectively. It will start at 191,291. In step S3, the calculations of the first evaluation value TD1 and the second evaluation value TD2 are executed by the following equations (1) and (2) already described.
TD1 = TS1 x K11 + TS2 x K12 ... (1)
TD2 = TS1 x K21 + TS2 x K22 ... (2)
Note that TS1 indicates the total opening time of the first door 105 obtained from the first opening / closing signal D1. Further, TS2 indicates the total opening time of the second door 205 obtained from the second opening / closing signal D2. K11, K12, K21, and K22 are the coefficients shown in FIG.

Subsequently, in step S4, the

control devices

191 and 291 determine whether or not the first evaluation value TD1 and the second evaluation value TD2 have reached the determination threshold value TDth, respectively. If the evaluation value has not reached the determination threshold value TDth (NO in S4), the process returns to step S3 and the operations of the first evaluation value TD1 and the second evaluation value TD2 are continued.

When either the first evaluation value TD1 or the second evaluation value TD2 reaches the determination threshold value (YES in S4), the operating frequency of the corresponding compressor is increased in step S5. Specifically, when the control device 191 detects that the first evaluation value TD1 has reached the determination threshold value TDth, the operating frequency of the first compressor 110 is increased. On the other hand, when the control device 291 detects that the second evaluation value TD2 has reached the determination threshold value TDth, the operating frequency of the second compressor 210 is increased.

In the first embodiment, when a plurality of cold heat source machines and a plurality of opening / closing doors are provided for the refrigerating warehouse, the position of the door and the cooling position covered by the cold heat source machine are linked to correspond to each cold heat source machine. The evaluation value is calculated by weighting the evaluation value of the door opening time. Then, the frequency of the compressor is increased only when the evaluation value exceeds the determination threshold value. This preferentially increases the capacity of the cold heat source unit near the position where cooling is required, while avoiding an inadvertent increase in the capacity of other cold heat source units. In this way, it is possible to avoid overcooling of the cooling chamber and realize energy-saving operation of the entire freezing and refrigerating warehouse system.

Embodiment 2.
FIG. 7 is a diagram showing a configuration of a cold heat source system and a refrigeration cycle device according to the second embodiment. The refrigeration cycle device of the second embodiment includes a cold heat source system 100A, a load device 101, and extension pipes 182,186,282,286. The cold heat source system 100A includes a cold heat source machine 102A and a cold heat source machine 202A.

In addition to the open /

close detection devices

198 and 298 shown in FIG. 3, the cooling chamber 104 is provided with

mass detection devices

199 and 299. The mass detection device 199 is configured to detect the mass of the object to be cooled carried in from the first door 105. The mass detection device 299 is configured to detect the mass of the object to be cooled carried in from the second door 205. As these mass detection devices, for example, a load sensor installed on the floor can be used.

The cold heat source machine 102A includes a control device 191A instead of the control device 191 in the configuration of the cold heat source machine 102 shown in FIG. The control device 191A includes a receiving device 196A instead of the receiving device 196 in the configuration of the control device 191 shown in FIG. The receiving device 196A receives the mass signals W1 and W2 transmitted from the

mass detecting devices

199 and 299 in addition to the first opening / closing signal D1 and the second opening / closing signal D2.

Since the other configurations of the cold

heat source machines

102A and 202A are the same as those of the cold

heat source machines

102 and 202 shown in FIG. 3, the description will not be repeated. Further, since the load device 101 is the same as that of the first embodiment, the description will not be repeated.

As described above, in the refrigeration cycle device of the second embodiment,

mass detection devices

199 and 299 are provided on each door. The mass signals W1 and W2 from the

mass detection devices

199 and 299 are transmitted to the receiving device 196A and also transmitted to the receiving device 296A.

In the CPU 192, the first evaluation value TD1 and the second evaluation value TD2 calculated in the first embodiment are corrected by using the coefficient corresponding to the mass.

In general, the heat capacity of the object to be cooled has a correlation with mass rather than volume. Therefore, in the present embodiment, the mass of the object to be cooled carried into the cooling chamber 104 is measured, and the evaluation value is corrected accordingly.

There is a high possibility that the object to be cooled will be placed near the door where the object to be cooled has been brought in. Therefore, the mass detected by the mass detection device 199 is reflected in the evaluation value by increasing the coefficient corresponding to the first door 105 and decreasing the coefficient corresponding to the second door 205. Further, the mass detected by the mass detection device 299 is reflected in the evaluation value by increasing the coefficient corresponding to the second door 205 and decreasing the coefficient corresponding to the first door 105.

Consider the load of the cooler 103 near the first door 105. For example, the cooler 103 when the object to be cooled having a large mass is stored from the second door 205 is larger than the amount of increase in the load of the cooler 103 when the object to be cooled having a small mass is stored from the first door 105. It is possible that the amount of increase in the load of the door will be larger. In such a case, the refrigerating capacity of the

coolers

103 and 203 should be appropriately increased by appropriately determining the coefficient for reflecting the mass in the evaluation value and controlling the first compressor 110 and the second compressor 210. Can be done.

Specifically, the

mass detection devices

199 and 299 are assumed to be load meters that measure the gravity of each forklift that carries the pallet on which the object to be cooled is placed. In this case, the mass of the forklift known in advance may be subtracted and treated as the mass of the object to be cooled.

In accordance with FIG. 4, the mass signal W1 coefficient K _W 11 coefficients to be reflected in the control of the cold heat source apparatus 102, a mass signal W1 and the coefficient K _W 12 coefficients to be reflected in the control of the cold heat source apparatus 202. Further, the coefficient for reflecting the mass signal W2 in the control of the cold heat source machine 102 is a coefficient K _W 21, and the coefficient for reflecting the mass signal W2 in the control of the cold heat source machine 202 is a coefficient K _W 22. When the cooler 103 is closer to the mass detection device 199 on the first door 105 side than the cooler 203, K _W 11> K _W 12, and the cooler 203 is closer to the mass detection device on the second door 205 side than the cooler 103. When it is close to the device 299, K _W 21 <K _W 22. Further, when the mass detection device 199 is closer to the cooler 103 than the mass detection device 299 and the mass detection device 299 is closer to the cooler 203 than the mass detection device 199, K _W 11> K _W 21, K _W 12 <K. _W 22.

As shown in the following equations (3) and (4), the corrected evaluation values TD1A and TD2A can be obtained by multiplying each term by a value obtained by multiplying the mass by a coefficient. In the following equation, W ₁ indicates the mass indicated by the mass signal _{W 1, and W 2} indicates the mass indicated by the mass signal W 2.
TD1A = TS1 x K11 x W ₁ x K _W 11 + TS2 x K12 x W ₂ x K _W 12 ... (3)
TD2A = TS1 x K21 x W ₁ x K _W 21 + TS2 x K22 x W ₂ x K _W 22 ... (4)
Alternatively, as shown in the following equations (5) and (6), the corrected evaluation values TD1A and TD2A can be obtained by simply adding the values obtained by multiplying the mass by the coefficient.
TD1A = TS1 x K11 + W ₁ x K _W 11 + TS2 x K12 + W ₂ x K _W 12 ... (5)
TD2A = TS1 x K21 + W ₁ x K _W 21 + TS2 x K22 + W ₂ x K _W 22 ... (6)
By measuring the mass of the object to be cooled in this way, the heat load of the object to be cooled can be directly predicted. Therefore, by reflecting the evaluation values TD1A and TD2A in consideration of the heat load of the object to be cooled in the control of the heat source machine, the temperature adjustment in the refrigerator can be controlled more smoothly.

(Summary)
The embodiments of the present application will be summarized below with reference to the drawings again.

The cold heat source system 100 shown in FIG. 3 is configured to be connected to a load device 101 including a first evaporator 160 and a second evaporator 260. The cold heat source system 100 is a cooling system in which a first compressor 110 provided corresponding to the first evaporator 160, a second compressor 210 provided corresponding to the second evaporator 260, and a load device 101 are installed. The first compressor 110 and the second compressor are respectively according to the first evaluation value TD1 and the second evaluation value TD2 obtained by applying different weights to the time when the first door 105 provided in the chamber 104 is open. A control device 190 for controlling the machine 210 is provided.

In the present embodiment, the control device 190 is divided and arranged in the

control devices

191 and 291 provided corresponding to the first compressor 110 and the second compressor 210, respectively, but the control devices 190 are combined into one. You may be. Further, the control devices 190 which are divided into three or more may cooperate to realize the control device 190.

Weighting of the first integrated value TS1, which is the opening time of the first door 105, is performed by the coefficients K11 and K21 shown in FIG. Although FIG. 3 shows an example in which the cooling chamber 104 is provided with two doors, the number of doors may be one. In this case, the calculation of each evaluation value may be performed by setting TS2 = 0 in the equations (1) and (2).

With such a configuration, it is possible to suppress the temperature rise in the cooling chamber and the variation in the temperature distribution in the cooling chamber. As a result, excessive cooling can be avoided and energy consumption can be reduced.

The control device 190 is configured to receive the first opening / closing signal D1 indicating the opening / closing of the first door 105. The control device 190 is configured to calculate the first evaluation value TD1 and the second evaluation value TD2 using the first integrated value TS1 indicating the total opening time of the first door 105 from the first opening / closing signal D1. As shown in the formulas (1) and (2), the first evaluation value TD1 includes a value obtained by multiplying the first integrated value TS1 by the coefficient K11. The second evaluation value TD2 includes a value obtained by multiplying the first integrated value TS1 by the coefficient K21.

Further, the control device 190A shown in FIG. 7 corrects the first evaluation value TD1 and the second evaluation value TD2 based on the mass signal W1 indicating the weight of the object to be cooled carried from the first door 105 into the cooling chamber 104. It is configured to do. The corrected evaluation values TD1A and TD2A are exemplified by the equations (3) to (6).

The opening and closing of the door often involves bringing in the object to be cooled. When the object to be cooled has a large heat capacity, the temperature inside the refrigerator is raised. With the configuration as shown in FIG. 7, when an object to be cooled having a large heat capacity is stored, the cooling capacity is further increased, so that the temperature rise in the refrigerator can be suppressed.

The cooling chamber 104 shown in FIG. 3 is further provided with a second door 205 provided at a position different from that of the first door 105. The control device 190 reflects the values obtained by weighting the first evaluation value TD1 and the second evaluation value TD2 differently with respect to the time when the second door 205 is open.

The control device 190 is configured to receive the first opening / closing signal D1 indicating the opening / closing of the first door 105 and the second opening / closing signal D2 indicating the opening / closing of the second door 205.

The control device 190 has a first integrated value TS1 indicating the total opening time of the first door 105 obtained from the first opening / closing signal D1 and a total of the opening times of the second door 205 obtained from the second opening / closing signal D2. The first evaluation value TD1 and the second evaluation value TD2 are calculated by using the second integrated value TS2 indicating the above and the coefficients K11, K21, K12, and K22.

As shown in the equation (1), the first evaluation value TD1 includes a value obtained by multiplying the first integrated value TS1 by the coefficient K11 and a value obtained by multiplying the second integrated value TS2 by the coefficient K12. Further, as shown in the equation (2), the second evaluation value TD2 includes a value obtained by multiplying the first integrated value TS1 by the coefficient K21 and a value obtained by multiplying the second integrated value TS2 by the coefficient K22.

The control device 190A shown in FIG. 7 has a mass signal W1 indicating the weight of the object to be cooled carried from the first door 105 into the cooling chamber 104 and the weight of the object to be cooled carried from the second door 205 into the cooling chamber 104. The first evaluation value TD1 and the second evaluation value TD2 are corrected based on the mass signal W2 indicating the above.

Specifically, the correction is performed as shown in the equations (3) and (4) or the equations (5) and (6).

In this embodiment, a refrigeration cycle device including the above-mentioned cold

heat source system

100 or 100A and a load device 101 is also disclosed.

Although the present embodiment has been described above by exemplifying a refrigerator equipped with a refrigerating cycle device, the refrigerating cycle device disclosed in the present embodiment may be used as an air conditioner or the like.

The embodiments disclosed this time should be considered to be exemplary in all respects and not restrictive. The scope of the present invention is shown by the claims rather than the description of the embodiments described above, and is intended to include all modifications within the meaning and scope equivalent to the claims.

2,102,102A, 202,202A Cold heat source machine, 3,101 load device, 4,104 cooling room, 5 doors, 10 compressors, 20,120,220 condensers, 22,122,222 fans, 50,150 , 250 Inflator, 60 Evaporator, 80,81,83,84,85,87,180,181,183,184,185,187,280,281,283,284,285,287 Piping, 82,86, 182,186,282,286 extension pipe, 91,190,190A,191,191A,291 control device, 94,194,294 memory, 96,196,196A,296,296A receiver, 97,197,297 pressure sensor , 98,198,298 Open / close detection device, 100,100A Cold heat source system, 103,203 Cooler, 105 1st door, 110 1st compressor, 160 1st evaporator, 199,299 Mass detector, 205 2nd Door, 210 second compressor, 260 second evaporator.

Claims

A cold heat source system configured to be connected to a load device including a first evaporator and a second evaporator.
A first compressor provided corresponding to the first evaporator and
A second compressor provided corresponding to the second evaporator and
The first compression is performed according to the first evaluation value and the second evaluation value obtained by differently weighting the time when the first door provided in the cooling target space in which the load device is installed is open. A cold heat source system including a machine and a control device for controlling the second compressor.
The control device is configured to receive a first open / close signal indicating the opening / closing of the first door.
The control device uses the first integrated value indicating the total opening time of the first door obtained from the first opening / closing signal, the first coefficient, and the second coefficient to obtain the first evaluation value and the said. It is configured to calculate the second evaluation value,
The first evaluation value includes a value obtained by multiplying the first integrated value by the first coefficient.
The cold heat source system according to claim 1, wherein the second evaluation value includes a value obtained by multiplying the first integrated value by the second coefficient.
The control device is configured to correct the first evaluation value and the second evaluation value based on a signal indicating the weight of the object to be cooled carried into the cooling target space from the first door. The cold heat source system according to claim 1.
The cooling target space is further provided with a second door provided at a position different from that of the first door.
The cold heat source according to claim 1, wherein the control device reflects a value obtained by weighting the first evaluation value and the second evaluation value differently with respect to the time when the second door is open. system.
The control device is configured to receive a first open / close signal indicating the opening / closing of the first door and a second opening / closing signal indicating the opening / closing of the second door.
The control device combines the first integrated value indicating the total opening time of the first door obtained from the first opening / closing signal and the total opening time of the second door obtained from the second opening / closing signal. It is configured to calculate the first evaluation value and the second evaluation value using the second integrated value shown and the first to fourth coefficients.
The first evaluation value includes a value obtained by multiplying the first integrated value by the first coefficient and a value obtained by multiplying the second integrated value by the third coefficient.
The cold heat source system according to claim 4, wherein the second evaluation value includes a value obtained by multiplying the first integrated value by the second coefficient and a value obtained by multiplying the second integrated value by the fourth coefficient. ..
The control device indicates a first signal indicating the weight of the object to be cooled carried into the space to be cooled from the first door and a weight of the object to be cooled to be carried into the space to be cooled from the second door. The cooling heat source system according to claim 4, wherein the first evaluation value and the second evaluation value are corrected based on the second signal.
A refrigeration cycle device including the cold heat source system according to any one of claims 1 to 6 and the load device.