JP2021038897A - Refrigeration cycle device - Google Patents

Abstract

To provide a refrigeration cycle device accurately measuring a refrigerant temperature difference and improving accuracy in the control of a refrigerant throttle amount to enhance energy saving performance.SOLUTION: A refrigeration cycle device includes a compressor 11, a condenser 12, a throttle means 14, an evaporator 16, and a plurality of temperature sensors, namely upstream temperature sensors 21 and downstream temperature sensors detecting the temperature of a refrigerant pipe between the condenser and the throttle means. The plurality of upstream temperature sensors 21 and the plurality of downstream temperature sensors 22 are provided to the refrigerant pipe at least along a refrigerant flowing direction. Thereby, variation due to difference in refrigerant distribution in the refrigerant pipe or variation of measurement can be reduced and refrigerant temperature difference can be accurately measured. As a result, control accuracy of the refrigerant throttle amount can be improved, and refrigeration performance is maximized to improve energy saving performance.SELECTED DRAWING: Figure 3

Description

The present disclosure relates to a refrigerating cycle device such as a refrigerator equipped with a drawing means for varying the amount of drawing of the refrigerant.

Patent Document 1 discloses a refrigerator which is one of refrigerating cycle devices equipped with a conventional squeezing means. As shown in the refrigerating cycle configuration diagram of FIG. 8, this refrigerator includes a compressor 141, a condenser 142, a receiver 143, an expansion valve 144 as a throttle means, a capillary tube 145, an evaporator 146, a suction pipe 147, and an internal heat exchange. It has a unit 148 and a suction pipe temperature sensor 149. Then, the expansion valve 144 adjusts the throttle amount of the refrigerant according to the pipe temperature detected by the suction pipe temperature sensor 149 to avoid a decrease in efficiency of the refrigeration cycle 140 and improve energy saving.

FIG. 9 shows the control of the expansion valve 144, and the temperature of the object (not shown) to be cooled by using the refrigeration cycle 140 drops and approaches a stable state, and the cold heat supplied from the evaporator 146 becomes surplus. When the temperature of the suction pipe 147 detected by the suction pipe temperature sensor 149 drops below R1, the throttle amount of the expansion valve 144 is increased by a predetermined amount. As a result, the evaporation temperature of the evaporator 146 is lowered, the amount of refrigerant circulating is reduced, the refrigerating capacity supplied from the evaporator 146 is lowered, and the liquid refrigerant flowing out to the suction pipe 147 is recovered as surplus refrigerant in the receiver 143. This raises the temperature of the suction pipe 147.

On the other hand, when the temperature of the suction pipe 147 rises and exceeds R2, the throttle amount of the expansion valve 144 is reduced by a predetermined amount. As a result, the evaporation temperature of the evaporator 146 rises, the amount of refrigerant circulating increases, the refrigerating capacity supplied from the evaporator 146 increases, and the surplus refrigerant collected in the receiver 143 is supplied to the evaporator 146 for suction. The temperature of the tube 147 is lowered.

By controlling the amount of refrigerant with the expansion valve 144 so as to detect the temperature R of the suction pipe 147 and maintain it between R1 and R2 in this way, the efficiency of the refrigeration cycle 140 is reduced and the durability of the compressor 141 due to liquid compression is achieved. It avoids deterioration of sex and maximizes the refrigerating capacity to improve the energy saving of the refrigeration cycle.

Japanese Unexamined Patent Publication No. 5-196321

The present disclosure provides a refrigeration cycle apparatus that maximizes the refrigerating capacity and enhances energy saving by increasing the accuracy of measuring the refrigerant temperature for controlling the amount of the refrigerant and controlling the amount of the refrigerant.

The refrigeration cycle apparatus in the present disclosure includes at least a compressor, a condenser, a squeezing means, an evaporator, and a plurality of temperature sensors for detecting the temperature of a refrigerant pipe between the condenser and the squeezing means. The plurality of temperature sensors are provided in the refrigerant pipe at least along the flow direction of the refrigerant.

The refrigeration cycle apparatus of the present disclosure can reduce the variation due to the difference in the distribution of the refrigerant in the refrigerant pipe and the variation in the measurement, and can accurately measure the temperature difference of the refrigerant. Therefore, the control accuracy of the throttle amount of the refrigerant can be improved, the refrigerating capacity can be maximized, and the energy saving property can be improved.

Front view of the refrigerator as the refrigeration cycle device according to the first embodiment. Longitudinal section of the refrigerator according to the first embodiment Cycle configuration diagram of the refrigerator according to the first embodiment The figure which showed the control method of the expansion valve of the refrigeration cycle in Embodiment 1. The figure which showed the correlation between the output of the expansion valve control sensor of the refrigeration cycle and the refrigerant flow rate in Embodiment 1. The figure which shows the state which the temperature sensor in Embodiment 1 of this invention is attached to a refrigerant pipe. Sectional drawing of the refrigerant pipe in Embodiment 1 of this invention Conventional refrigeration cycle configuration diagram The figure which showed the control method of the expansion valve of the conventional refrigeration cycle

(Knowledge, etc. that was the basis of this disclosure)
At the time when the inventors came up with the present disclosure, most refrigeration cycle devices such as household refrigerators use natural refrigerants with a low global warming coefficient from the viewpoint of preventing global warming. Since the refrigerant is flammable and the amount of refrigerant that can be filled is limited, it is difficult to retain the surplus refrigerant. In addition, since a condenser that dissipates heat by natural convection from the outer shell of the refrigerator body or the like is used, the heat dissipation capacity changes greatly depending on the environmental conditions, and it is difficult to keep the condenser outlet at a predetermined supercooling degree. .. Therefore, in a refrigerating cycle device such as a household refrigerator, even if the suction pipe temperature sensor 149 detects the refrigerant temperature from the evaporator 146 and the refrigerant flow rate is controlled by a throttle means such as an expansion valve 144, the refrigerant flow rate is appropriately adjusted. It was difficult to control.

Appropriate control of the refrigerant flow rate is realized by controlling the expansion valve so that the degree of dryness (supercooling degree) at the outlet of the condenser becomes zero, instead of the control based on the output of the conventional suction pipe temperature sensor 149. Although it is possible, the method for directly measuring the dryness of the refrigerant at the outlet of the condenser has not been established at present. Therefore, as an alternative to direct measurement, the inventors have found that the dryness of the refrigerant can be indirectly measured by measuring the refrigerant temperature difference at the outlet of the condenser, and the refrigerating capacity is controlled by controlling the throttle amount from the refrigerant temperature difference. Found that can be maximized.

However, in this case, in order to estimate the dryness from the above-mentioned refrigerant temperature difference and control it accurately, it is necessary to measure a minute refrigerant temperature difference. Therefore, in a refrigerating cycle device such as a refrigerator in which the amount of refrigerant and the heat dissipation capacity of the condenser are limited, it is an issue to accurately measure a minute refrigerant temperature difference in order to save energy by using a drawing means. Therefore, the inventors have come to construct the subject matter of the present disclosure in order to solve the problem.

Therefore, the present disclosure provides a refrigeration cycle apparatus that improves the measurement accuracy of a minute refrigerant temperature difference, improves the control accuracy of the amount of refrigerant drawn, maximizes the refrigerating capacity, and enhances energy saving. ..

(Embodiment 1)
Hereinafter, a refrigerator will be described as an example of an embodiment of the refrigeration cycle apparatus with reference to FIGS. 1 to 7.

[1-1. Constitution]
FIG. 1 is a front view of a refrigerator as a refrigerating cycle device according to the embodiment of the present disclosure, FIG. 2 is a vertical sectional view of the refrigerator according to the first embodiment, and FIG. 3 is a cycle configuration diagram of the refrigerator according to the first embodiment. is there.

As shown in FIGS. 1 to 3, in this refrigerator, a metal (for example, iron plate) outer box that opens forward, an inner box made of hard resin (for example, ABS), and between the outer box and the inner box. The refrigerator body 30 has a heat insulating property and is made of a heat insulating material such as hard urethane foam filled with foam. In the refrigerator main body 30, there is a refrigerating chamber 31, an upper freezing chamber 32 arranged side by side under the refrigerating chamber 31, and an ice making chamber 33 arranged side by side, and a lower freezing chamber below the upper freezing chamber 32 and the ice making chamber 33 arranged side by side. 34. A vegetable compartment 35 is provided below the lower freezer compartment 34. The front surface of the refrigerator compartment 31 is freely opened and closed by, for example, a double door, and the front portions of the upper freezer compartment 32, the ice making chamber 33, the lower freezer compartment 34, and the vegetable compartment 35 are opened and closed by a drawer type door. It is freely blocked.

The refrigerating chamber 31 is usually set at 1 to 5 ° C. with a lower limit of a temperature at which it does not freeze for refrigerated storage. The vegetable compartment 35 is set to a temperature of 2 ° C. to 7 ° C., which is the same as or slightly higher than that of the refrigerator compartment 31, and if the temperature is lowered, the freshness of the leafy vegetables can be maintained for a long period of time. The upper freezing chamber 32 and the lower freezing chamber 35 are usually set at -22 to -18 ° C for freezing storage, but are set at a low temperature of, for example, -30 to -25 ° C for improving the freezing storage state. Sometimes. Further, the upper freezing chamber 32 may be a room that can be selected from the refrigerating temperature zone to the freezing temperature zone by using a damper mechanism or the like as the switching chamber.

The refrigerator main body 30 is provided with a refrigerating system 10 for cooling the refrigerating room 31, the upper freezing room 32, the ice making room 33, the lower freezing room 34, and the vegetable room 35, and the ability of the refrigerating system 10 to compress the refrigerant is variable. A mold compressor 11 is provided in the machine room 47 at the rear of the top surface, and an evaporator 16 serving as a cooler is provided in the cooling room 48 at the back surface.

As the refrigerant of the refrigeration system 10, isobutane, which is a flammable refrigerant having a small global warming potential, is used from the viewpoint of protecting the global environment. This hydrocarbon, isobutane, has a specific gravity about twice that of air at room temperature and atmospheric pressure (at 2.04 and 300K). As a result, the amount of refrigerant charged can be reduced as compared with the conventional case, the cost is low, and the amount of leakage in the unlikely event that the flammable refrigerant leaks is reduced, so that safety can be further improved.

Next, the configuration of the refrigeration system 10 will be described with reference to FIG.

The refrigeration system 10 is configured by connecting a compressor 11, a condenser 12, a dryer 13, an expansion valve 14 as a throttle means, a capillary tube 15, an evaporator 16, an accumulator 17, a suction pipe 18, and an internal heat exchange unit 19. There is. Further, the refrigeration system 10 is provided with an expansion valve control sensor 23 including a minute resistor 20, an upstream temperature sensor 21, and a downstream temperature sensor 22.

The microresistor 20 constituting the expansion valve control sensor 23 is composed of a small diameter tube having a length of 250 mm, and is a resistor corresponding to about 5% of the total resistance of the microresistors 20, the expansion valve 14, and the capillary tube 15 arranged in series. Has. The ratio of the minute resistance 20 to the total resistance is preferably 1 to 20%. If it is less than 1%, it becomes difficult to measure the state change of the refrigerant flowing inside. If it exceeds 20%, the heat exchange of the internal heat exchange unit 19 becomes insufficient, and the efficiency of the refrigeration system decreases. The ratio of the minute resistance 20 to the total resistance is shown by the ratio of the length when each resistance is replaced with the capillary tube 15 having the same inner diameter.

Here, the upstream temperature sensor 21 and the downstream temperature sensor 22 constituting the expansion valve control sensor 23 are provided in the refrigerant pipe along the flow direction of the refrigerant, and in this example, as shown in FIG. 6, around the pipe. (Although only the upstream temperature sensor 21 is shown in FIG. 6, a plurality of downstream flow temperature sensors 22 are also provided in the downstream portion of the minute resistor 20 (not shown)). Then, the upstream temperature sensor 21 and the downstream temperature sensor 22 measure the temperature on the upstream side and the downstream side of the minute resistance 20 that changes according to the state change of the refrigerant flowing inside the minute resistance 20, and the temperature difference is set. The expansion valve 14 has a variable throttle amount so as to approach the temperature difference, and the refrigeration system 10 is controlled to a predetermined state.

In the refrigeration system 10, the dryer 13 dries the refrigerant circulating in the refrigeration system 10, and is arranged downstream of the condenser 12 in order to efficiently contact the liquid refrigerant.

Further, the accumulator 17 stores the surplus refrigerant in the stable state, and is arranged downstream of the evaporator 16 in order to keep the temperature substantially the same as that of the evaporator 16. When the temperature of the object (not shown) to be cooled by the refrigerating system 10 rises, the amount of excess refrigerant stored in the accumulator 17 decreases and the amount of refrigerant circulating in the refrigerating system 10 increases, thereby increasing the refrigerating capacity. increase. Generally, in a freezing system such as a household refrigerator that radiates heat by natural convection from the outer shell of a housing such as the refrigerator body 30, a receiver is used to store excess refrigerant on the high pressure side of the freezing system. Therefore, as in the first embodiment, the accumulator 17 is used to store the surplus refrigerant on the low pressure side of the refrigeration system. Further, the amount of excess refrigerant stored in the accumulator 17 is about 10 to 30% of the total amount of refrigerant in the refrigeration system, and a function of adjusting the refrigerating capacity can be obtained with a relatively small amount. It is valid.

Further, by arranging the expansion valve 14 and the capillary tube 15 in series to form the throttle of the refrigerating system 10, the internal heat exchange unit 19 that exchanges heat between the capillary tube 15 and the suction tube 18 is realized. The enthalpy of the low-temperature refrigerant that circulates in the suction pipe 18 can be recovered to improve the efficiency of the freezing system 10.

[1-2. motion]
The operation and operation of the refrigerator configured as described above will be described below with reference to FIGS. 3 to 5.

When performing the cooling operation, the refrigerator operates the compressor 11 by minimizing the throttle amount of the expansion valve 14, that is, maximizing the amount of refrigerant circulating in the expansion valve 14. The refrigerant compressed by the compressor 11 dissipates heat in the condenser 12, condenses it, and then dries it in the dryer 13. Then, after passing through the expansion valve control sensor 23, the pressure is reduced by the expansion valve 14 and the capillary tube 15, and then the pressure is reduced by being supplied to the evaporator 16 to evaporate and return to the compressor 11 via the suction pipe 18. At this time, cooling is performed using the cold heat generated by the evaporator 16.

Here, when the temperature of the object (not shown) drops and approaches a stable state while the compressor 11 is operated with the throttle amount of the expansion valve 14 minimized, the outlet refrigerant of the condenser 12 is in a two-phase state. (Preferably, the dryness is 3 to 10% by weight). This means that even if the temperature of the object to be cooled (not shown) rises, the amount of excess refrigerant stored in the accumulator 17 decreases, and the amount of refrigerant circulating in the refrigerating system 10 increases, the outlet of the condenser 12 This is because the total resistance of the micro resistance 20, the expansion valve 14, and the capillary tube 15 arranged in series and the total amount of the refrigerant in the refrigerating system 10 are designed so that the refrigerant does not become supercooled.

Generally, in a freezing system such as a household refrigerator that dissipates heat by natural convection from the outer shell of the housing, if the outlet refrigerant of the condenser is designed to be overcooled, the heat dissipation capacity will increase depending on the environmental conditions. When the amount is increased, almost all the refrigerant in the refrigeration system stays in the condenser, and there is a concern that the amount of refrigerant circulation is abnormally reduced. Further, when the heat dissipation capacity is reduced due to environmental conditions, the surplus refrigerant that could not be condensed by the condenser cannot be stored in the accumulator 17 and is returned from the suction pipe 18 to the compressor 11, so that the durability of the compressor 11 is improved. There is a concern that it will decline.

Therefore, in the refrigeration system 10 of the present disclosure, as described above, the total resistance of the minute resistors 20, the expansion valve 14, and the capillary tube 15 arranged in series and the inside of the refrigeration system 10 so that the outlet refrigerant of the condenser 12 does not become supercooled. The total amount of refrigerant in the above is designed.

When the refrigerant from the condenser 12 in the two-phase state passes through the minute resistance 20 of the expansion valve control sensor 23, the temperatures of the upstream side and the downstream side of the minute resistance 20 are measured by the upstream temperature sensor 21 and the downstream temperature sensor 22. Is detected. Then, the expansion valve 14 is changed so that the temperature difference around the minute resistance 20 measured by the expansion valve control sensor 23 changes by a predetermined value or a predetermined amount as compared with the stable state in which the throttle amount of the expansion valve 14 is kept to the minimum. Control the aperture amount. As a result, the dryness of the outlet refrigerant of the condenser 12 is reduced, the freezing effect is increased, and the efficiency of the freezing system 10 can be improved.

Next, the basic control method of the expansion valve 14 will be described with reference to FIGS. 4 and 5.

The horizontal axis of FIG. 4 is the pressure loss generated according to the throttle amount of the expansion valve 14, and the vertical axis is the temperature difference S before and after the minute resistor 20 measured by the expansion valve control sensor 23.

As described above, when the temperature of the object (not shown) to be cooled by the refrigerating system 10 decreases and approaches a stable state while the compressor 11 is operated with the throttle amount of the expansion valve 14 minimized, The outlet refrigerant of the compressor 12 is in a two-phase state. At this time, the output of the expansion valve control sensor 23 indicates S0. Then, the throttle amount of the expansion valve 14 is increased so that the output of the expansion valve control sensor 23 is lower than S2. As a result, the dryness of the outlet refrigerant of the condenser 12 is reduced, the freezing effect is increased, and the efficiency of the freezing system 10 is improved.

On the other hand, when the dryness of the outlet refrigerant of the condenser 12 continues to decrease and the output of the expansion valve control sensor 23 falls below S1, the throttle amount of the expansion valve 14 is reduced. As a result, the output of the expansion valve control sensor 23 can be stabilized in a state indicating S1 to S2. The reason why the lower limit value S1 is provided for the output of the expansion valve control sensor 23 is that when the expansion valve 14 is throttled too much, the outlet refrigerant of the condenser 12 becomes supercooled, and almost all the refrigerant in the refrigeration system 10 is sent to the condenser 12. This is because there is a concern that the amount of refrigerant circulating will be abnormally reduced due to the stagnation. In such a case, the cooling capacity is insufficient and the refrigerator may become dull, so it is necessary to avoid it.

The horizontal axis of FIG. 5 is the temperature difference S before and after the minute resistor 20 measured by the expansion valve control sensor 23, which is the same as the vertical axis of FIG. 4, and the vertical axis of FIG. 5 is the vertical axis of FIG. The flow velocity V.

As described above, when the throttle amount of the expansion valve 14 is increased from the state where the output of the expansion valve control sensor 23 indicates S0, the dryness of the outlet refrigerant of the condenser 12 decreases and passes through the minute resistor 20. The flow velocity V of the refrigerant becomes slow, and as a result, the output of the expansion valve control sensor 23 decreases from S0 to S2. Similarly, when the throttle amount of the expansion valve 14 is adjusted to stabilize the output of the expansion valve control sensor 23 so as to indicate S1 to S2, the dryness of the outlet refrigerant of the condenser 12 is close to zero (preferably the dryness). It is stable at 0 to 1% by weight), and the flow velocity V of the refrigerant is stable near the minimum value. This is because the amount of refrigerant circulation is substantially constant when the refrigeration system 10 is in a stable state, so that when the outlet refrigerant of the condenser 12 becomes a liquid phase, the flow velocity V of the refrigerant passing through the minute resistor 20 becomes substantially minimum and condensation occurs. This is because the flow velocity V of the refrigerant passing through the minute resistor 20 increases as the dryness of the outlet refrigerant of the vessel 12 increases. Further, in general, since the specific volume of the gas phase with respect to the liquid phase is as large as about 50 times, the amount of change in the flow velocity V of the refrigerant passing through the minute resistor 20 having a dryness of 0 to 10% by weight is large, especially in this range. It can be said that it is easy to measure the state of the outlet refrigerant of the condenser 12 by the expansion valve control sensor 23.

By controlling the throttle amount of the expansion valve 14 so as to approach the set temperature difference according to the output of the expansion valve control sensor 23, that is, the detection temperature difference detected by the upstream temperature sensor 21 and the downstream temperature sensor 22. The dryness of the outlet refrigerant of the condenser 12 can be stabilized near zero (desirably 0 to 1% by weight of dryness), the refrigerating effect can be increased, and the efficiency of the refrigerating system 10 can be improved.

That is, the above-mentioned refrigerator main body 30 controls the expansion valve 14 so that the dryness of the condenser outlet approaches zero by using the expansion valve control sensor 23 including the minute resistance 20 and the temperature sensor that measures the temperature difference before and after the minute resistance 20. By doing so, the refrigerating capacity can be maximized by using the expansion valve 14 in the refrigerating system having no receiver at the outlet of the condenser, and highly efficient cooling operation can be performed.

Here, in the present embodiment, a plurality of the expansion valve control sensor 23 upstream temperature sensor 21 and downstream temperature sensor 22 are installed around the pipe, and the refrigerant temperature is calculated and detected based on the values measured by the plurality of temperature sensors. Therefore, the upstream temperature and the downstream temperature can be measured with high accuracy, and the measurement accuracy of the refrigerant temperature difference can be improved. Therefore, the throttle amount of the expansion valve can be controlled with high accuracy.

(Other embodiments)
As described above, the first embodiment has been described as an example of the technology disclosed in the present application. However, the technique in the present disclosure is not limited to this, and can be applied to embodiments in which changes, replacements, additions, omissions, etc. have been made.

Therefore, other embodiments will be illustrated below.

In the first embodiment, the microresistor 20 is composed of a small diameter tube, but this may be composed of a capillary tube. Since the capillary tube is flexible and can be easily processed, workability when installing the pipe can be improved. Further, as shown in FIG. 7, the minute resistor 20 may be configured by installing an orifice plate 82 smaller than the inner diameter of the refrigerant pipe 81 inside the refrigerant pipe 81. As a result, the minute resistor 20 can be configured in a space-saving manner.

[1-3. Effect, etc.]
As described above, in the present embodiment, the refrigerator detects the temperature of the compressor, the condenser, the squeezing means, the evaporator, and the refrigerant pipe between the condenser and the squeezing means. Since the plurality of temperature sensors are arranged at least along the flow direction of the refrigerant, it is possible to reduce the variation due to the difference in the distribution of the refrigerant in the refrigerant pipe and the variation in the measurement. The temperature difference can be measured accurately. Therefore, the control accuracy of the throttle amount of the refrigerant can be improved, the refrigerating capacity can be maximized, and the energy saving property can be improved.

Further, since a plurality of the temperature sensors are installed around the pipe of the refrigerant pipe, even if the temperature distribution of the refrigerant is not uniform, it is more accurate based on the detection temperature of the plurality of temperature sensors installed around the pipe of the refrigerant pipe. The refrigerant temperature can be obtained. Therefore, it is possible to improve the measurement accuracy of the refrigerant temperature difference, further maximize the refrigerating capacity, and improve the energy saving.

Further, since the upstream temperature sensor is arranged in the vicinity of the upstream of the throttle means among the plurality of temperature sensors, the state of the refrigerant at the point where the refrigerant is closest to the liquid and the dryness is small is determined. Can be detected. As a result, the dryness of the refrigerant at the outlet of the condenser can be estimated accurately, the amount of the refrigerant squeezed can be controlled more accurately, and energy saving can be improved.

Further, the refrigerant pipe provided with the temperature sensor has a smaller diameter than the condenser pipe, which increases the flow velocity of the refrigerant passing through the refrigerant pipe and increases the pressure loss, so that the upstream side of the refrigerant pipe is increased. The temperature drop that occurs when moving downstream from is large. As a result, a temperature difference is surely generated between the upstream and the downstream of the refrigerant pipe, and the temperature difference between the upstream and the downstream of the refrigerant pipe can be easily measured. Then, the dryness of the refrigerant at the outlet of the condenser can be estimated from the detected refrigerant temperature difference, and the control of the amount of throttle of the refrigerant can be optimized to improve energy saving.

Further, since the refrigerant pipe is composed of a capillary tube, the flow velocity of the refrigerant increases when passing through the capillary tube, and the pressure loss increases. Therefore, a temperature difference is surely generated in the refrigerant when moving from the upstream to the downstream of the capillary tube. This makes it possible to easily measure the temperature difference between two points of the refrigerant pipe. In addition, since the capillary tube is flexible, it is possible to improve the workability of installing the pipe.

Further, since the refrigerant pipe located between the plurality of temperature sensors is provided with an orifice plate having a diameter smaller than the inner diameter of the refrigerant pipe, pressure loss is caused by the passage of the refrigerant through the orifice plate. It occurs, and a temperature drop occurs before and after the orifice plate. This makes it possible to easily measure the temperature difference between two points of the refrigerant pipe. Further, the orifice plate may be installed in the refrigerant pipe, and can be installed in a space-saving manner.

In the above, one embodiment of the refrigeration cycle apparatus of the present disclosure has been described in this case, but since the above-described embodiment is for exemplifying the technique in the present disclosure, a patent claim is made. Various changes, replacements, additions, omissions, etc. can be made within the range of or equal to the above.

The refrigerating system apparatus according to the present disclosure can be applied to a refrigerating cycle apparatus for controlling the refrigerating capacity by adjusting the amount of drawing by the drawing means, and the amount of drawing by the drawing means can be accurately adjusted to improve energy saving. For example, it can be widely applied as a refrigerating cycle device such as an air conditioner equipped with a refrigerating cycle and a kitchen device as well as a refrigerating / refrigerating application product such as a household or commercial refrigerator.

10 Refrigeration system 11 Compressor 12 Condenser 13 Dryer 14 Expansion valve (squeezing means)
15 Capillary tube 16 Evaporator 17 Accumulator 18 Suction pipe 19 Internal heat exchange part 20 Micro resistance 21 Upstream temperature sensor 22 Downstream temperature sensor 23 Expansion valve control sensor 30 Refrigerant body 80 Temperature sensor 81 Refrigerant piping 82 Orifice plate

Claims (6)

At least, the compressor, the condenser, the squeezing means, the evaporator, and a plurality of temperature sensors for detecting the temperature of the refrigerant pipe between the condenser and the squeezing means are provided, and the plurality of temperature sensors are provided. , At least a refrigeration cycle device provided in the refrigerant pipe along the flow direction of the refrigerant. The refrigeration cycle device according to claim 1, wherein a plurality of the temperature sensors are installed around the pipe of the refrigerant pipe. The refrigeration cycle apparatus according to claim 1 or 2, wherein the temperature sensor is arranged in the vicinity of the upstream of the drawing means. The refrigerating cycle apparatus according to any one of claims 1 to 3, wherein the refrigerant pipe has a diameter smaller than that of the condenser pipe. The refrigerating cycle apparatus according to any one of claims 1 to 3, wherein the refrigerant pipe is composed of a capillary tube. The refrigerating cycle apparatus according to any one of claims 1 to 3, wherein the refrigerant pipe includes an orifice plate having a diameter smaller than the inner diameter of the refrigerant pipe.

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