Cycling test device and control method thereof

Abstract

The present invention relates to a test device for testing the performance of a battery and, more specifically, to a cycling test device for testing the performance of a battery by repeatedly charging and discharging the battery within a predetermined temperature for a long time. An embodiment of the present invention may provide a cycling test device comprising: a main line along which a compressor, a condenser, and an evaporator are sequentially connected to circulate a refrigerant; a heater for heating air cooled through the evaporator; a hot gas mixing line bypassed from the main line between the compressor and the condenser and connected to the main line between the condenser and the evaporator, in order to increase the temperature of the evaporator and limit the output of the heater, such that the hot gas discharged from the compressor is mixed with the low-temperature and low-pressure gas supplied from the condenser to the evaporator; and a controller for controlling the amount of hot gas supplied to the evaporator through the hot gas mixing line.

Description

Cycling test device and control method thereof

[0001] The present invention relates to a test device for testing the performance of a battery, and more specifically, to a cycling test device and a control method thereof for testing the performance of a battery by repeatedly charging and discharging the battery at a constant temperature for a long period of time.

[0002] This application claims the benefit of priority to Republic of Korea Patent Application No. 10-2024-00068108, filed May 24, 2024, Republic of Korea Patent Application No. 10-2024-0097362, filed July 23, 2024, and Republic of Korea Patent Application No. 10-2025-0067499, filed May 23, 2025, the entire contents of which are incorporated herein by reference.

[0003] Products like batteries and semiconductor components can generate heat during operation. Therefore, after manufacturing, the product is tested in various environments to verify its performance and quality.

[0004] Specifically, for batteries requiring repeated charging and discharging, such as secondary batteries, the battery can be tested by placing it in a designated space and charging and discharging it under constant temperature conditions for an extended period of time. This constant temperature can be the room temperature at which the battery is used, or it can be used to test battery performance under more severe temperature conditions, such as extremely low or very high temperatures. Devices capable of such performance tests are called cyclers, cycle chambers, cycling devices, or cycling test devices.

[0005] Meanwhile, battery testing using a cycling test device may be performed not only to verify or confirm the performance of a manufactured battery, but also during the battery design process.

[0006] Battery testing using cycling test equipment typically lasts for several months or longer. The purpose, shape, size, characteristics, and materials of a battery can vary greatly depending on its intended application. Therefore, a wide variety of battery types must be designed to meet customer requirements, necessitating a large number of cycling test equipment.

[0007] Cycling test equipment is typically equipped to perform constant-temperature operation (also known as constant-temperature operation or stationary operation) within a chamber containing a test space housing the battery. Therefore, refrigerators suitable for constant-temperature operation are being used in cycling test equipment. Of course, refrigerators that can accommodate both constant-temperature and variable-temperature operation conditions are being selected, allowing for temperature fluctuations within the chamber. Consequently, the installed refrigerator's performance control is limited, leading to unnecessary energy consumption.

[0008] The cycling test device is equipped with a refrigerator and a heater inside for temperature control, and an internal circulation fan circulates the air inside the chamber, and the circulated air passes through the evaporator and heater in sequence to control the temperature of the circulated air and supply it to the inside of the chamber, thereby controlling the temperature inside the chamber.

[0009] Specifically, the cycling test device may be equipped with a cooling heat exchanger for cooling and a heating heat exchanger for heating to maintain the temperature within the chamber at a constant level. Additionally, a circulation fan may be provided to circulate the air within the chamber. In other words, the chamber is controlled to a set temperature through convection heat control. To control the chamber temperature, a refrigerator, i.e., a cooling heat exchanger, and a heater, i.e., a heating heat exchanger, including a compressor, condenser, and evaporator, are provided. The evaporator portion of the refrigerator functions to remove heat from the chamber.

[0010] The heater may be a resistance heating heater, and the heater is driven by an active control method that controls the amount of heat generated according to the required heat load by controlling the heater output by controlling the amount of power (current) supplied to the heater electrode.

[0011] Refrigerators introduced for refrigeration can control cooling performance by controlling the compressor's operating rate. However, this control range is limited. Reciprocating compressors, particularly those commonly used in cycling test equipment, have extremely limited output control. Scroll compressors are also used, but when using small-capacity compressors, the output control range is also limited, limiting their effectiveness.

[0012] For example, inverter-driven small reciprocating compressors typically only allow control within a range of 80-100% of compressor output, or 20% of the total output range. Consequently, compressor operating rate control, necessary for controlling a refrigerator's cooling capacity, is extremely limited or impossible, limiting control of the refrigerator's cooling capacity (the amount of heat absorbed by the evaporator from the outside).

[0013] Accordingly, current cycling test equipment operates by maintaining the chamber's internal temperature by compensating for energy lost through absorption from the refrigerator with a heater, regardless of the heat load within the chamber. In other words, the chamber's internal temperature is maintained by first absorbing energy from the circulating gas through an evaporator, and then compensating for the temperature with a heater.

[0014] In particular, due to the characteristics of the test device that conducts performance tests while changing the temperature from 0 degrees or -30 to -40 degrees Celsius to a maximum of 70 to 80 degrees Celsius, as the control temperature inside the chamber rises, the energy dissipated through the evaporator of the refrigerator increases. This is because, while the temperature of the refrigerant supplied to the evaporator remains constant, as the temperature inside the chamber increases, the temperature change (dT) at the boundary where heat is exchanged in the evaporator increases, thereby increasing the heat flux density. As a result, a lot of heating energy is consumed to compensate for the unnecessary dissipated energy, and the dissipated energy is dissipated to the outside in the condenser section of the refrigerator, increasing the chamber heat load that dissipates heat from the chamber to the outside.

[0015] The heat removal capacity of the refrigeration evaporator is set to the chamber's minimum temperature standard, and the amount of heat removed through the evaporator corresponds to the difference between the evaporator's refrigerant temperature and the chamber's set temperature. In the case of the cycling test device, due to the wide temperature control range, a large amount of heat is removed through the evaporator equal to the temperature difference between the evaporator's refrigerant temperature and the chamber's maintenance temperature, reaching 70 to 80 degrees Celsius or even over 100 degrees Celsius, and that amount of energy is compensated for by the heater.

[0016] Meanwhile, during the operation of the cycling test device, when the door is opened and closed, moisture contained in the air flowing in from the outside can freeze on the surface of the evaporator, which is maintained at a low temperature during the circulating flow within the chamber. If this process occurs repeatedly, resulting in a large amount of ice forming on the evaporator surface, sufficient heat exchange with the evaporator is limited, causing low-energy refrigerant to be transferred to the compressor, potentially leading to a compressor failure known as "liquid compression."

[0017] To prevent compressor failure due to evaporator freezing, a defrosting process is typically introduced to remove ice formed on the evaporator surface. However, because the temperature inside the chamber fluctuates significantly during the defrosting process, the defrosting process can only be performed in a very limited manner in the refrigerator of a cycling test device, resulting in the actual occurrence of liquid compression.

[0018] The problems associated with these cycling test devices and control methods are not limited to cycling test devices. The same issues can also arise in devices or systems that require long-term storage of objects, such as secondary batteries, at a specific temperature. Therefore, there is a need to develop solutions applicable to air conditioning devices, air conditioning systems, and their control methods.

[0019] The present invention aims to solve the problems of conventional cycling test devices.

[0020] Through one embodiment of the present invention, it is intended to provide a test device and control method capable of controlling the cooling performance of an evaporator according to the amount of heat removal required to maintain temperature inside a chamber of a cycling test device.

[0021] Through one embodiment of the present invention, it is intended to provide a test device and control method capable of minimizing the amount of heat generated by a condenser that generates external heat in a cycling test device.

[0022] Through one embodiment of the present invention, it is intended to provide a test device and control method capable of suppressing the occurrence of liquid compression by controlling the temperature of an evaporator and the suction temperature of a compressor.

[0023] Through one embodiment of the present invention, it is intended to provide a test device and control method capable of preventing energy loss by controlling the required heat generation amount of a heater to a minimum.

[0024] Through one embodiment of the present invention, it is intended to provide a test device and control method capable of preventing energy loss by the heater and preventing supercooling through the evaporator by controlling the balancing of refrigerant flowing into the evaporator through the main line and the hot gas mixing line based on the output of the heater.

[0025] Through one embodiment of the present invention, it is intended to provide a test device and control method capable of preventing unnecessary energy loss in a compressor caused by an increase in the pressure of refrigerant flowing into the compressor during a process of controlling the cooling performance of an evaporator.

[0026] Through one embodiment of the present invention, in a situation where the output control of the compressor is difficult or limited, a test device and a control method are provided for controlling the heat exchange amount of the compressor and condenser, in which heat exchange occurs between the refrigerator and an external system, through balancing control of the refrigerant in the circulation circuit connected to the compressor, condenser, evaporator, and compressor.

[0027] Through one embodiment of the present invention, a test device and a control method are provided that can suppress the occurrence of liquid compression, which is a major cause of compressor failure, by controlling the temperature of an evaporator and the suction temperature of a compressor through balancing control of a refrigerant in a circulation circuit, thereby controlling freezing of the evaporator to a certain level or lower.

[0028] Through one embodiment of the present invention, a test device and a control method are provided that can control whether a step of operating the hot gas mixing line is performed and the amount of refrigerant supplied through the hot gas according to the operating mode of the chamber or the temperature range of the chamber by providing a hot gas mixing line separately from the main line of the refrigerator.

[0029] Through one embodiment of the present invention, a test device and a control method are provided that can control whether a step of operating the cooling line is performed and the amount of refrigerant supplied to a compressor through the cooling line, depending on the operating mode of the chamber or the temperature range of the chamber, by providing a cooling line separately from the main line of the refrigerator.

[0030] Through one embodiment of the present invention, it is intended to provide a test device and control method capable of effectively controlling the amount and temperature of refrigerant flowing into a compressor by providing a bypass line at the compressor suction end.

[0031] Through one embodiment of the present invention, it is intended to provide a test device and control method capable of operating the main line in stages through an opening / closing valve at an inlet end where refrigerant is introduced from the main line to the compressor and a bypass line that bypasses the opening / closing valve.

[0032] Through one embodiment of the present invention, it is intended to provide a test device and control method that can simplify control logic and reduce the capacity of a controller by cross-controlling the opening / closing valve of a main line and the opening / closing valve of a hot gas mixing line.

[0033] In order to achieve the above-described object, according to one embodiment of the present invention, a cycling test device that operates to maintain a temperature within a chamber at a constant temperature may be provided, comprising: a main line sequentially connecting a compressor, a condenser, and an evaporator so as to circulate a refrigerant; a heater that heats air cooled through the evaporator; a hot gas mixing line that is bypassed from the main line between the compressor and the condenser and connected to the main line between the condenser and the evaporator to increase the temperature of the evaporator and limit the output of the heater, and mixes hot gas discharged from the compressor with low-temperature, low-pressure gas supplied from the condenser to the evaporator; and a controller that controls the amount of hot gas supplied to the evaporator through the hot gas mixing line.

[0034] According to one embodiment of the present invention, a cycling test device may include a cooling heat exchanger for cooling and a heating heat exchanger for heating to maintain a constant temperature within a chamber, and a circulation fan for circulating the air within. The cooling heat exchanger may be referred to as a refrigerator. Since the evaporator, which is part of the refrigerator, exchanges heat with the circulating air within the chamber, the evaporator may be referred to as a cooling heat exchanger in the narrow sense.

[0035] The above cooling heat exchanger may include a compressor, a condenser, an evaporator, and a main line through which refrigerant is circulated by sequentially connecting the compressor, condenser, and evaporator.

[0036] The above heating heat exchanger may include a resistance heater capable of controlling output using resistance.

[0037] The circulating air inside the chamber can be cooled by passing through the evaporator and subsequently heated to a required temperature through the heater to control the temperature inside the chamber.

[0038] According to one embodiment of the present invention, in order to increase the temperature of the evaporator and limit the output of the heater, it is preferable that a hot gas mixing line be provided that is bypassed from the main line between the compressor and the condenser and connected to the main line between the condenser and the evaporator, and mixes the hot gas discharged from the compressor with the low-temperature, low-pressure gas supplied from the condenser to the evaporator.

[0039] It is preferable to include a control unit that controls the amount of hot gas supplied to the evaporator through the hot gas mixing line.

[0040] After being discharged from the condenser, the expanded refrigerant can be mixed with the hot gas and introduced into the evaporator.

[0041] It is preferable that the cooling performance in the evaporator be controlled to be lowered and the heat dissipation performance in the condenser be controlled to be lowered by the temperature increase of the refrigerant through the hot gas mixing line.

[0042] According to an embodiment of the present invention, the cycler test device preferably includes a pressure regulator valve provided in the main line to maintain the flow rate and pressure of the refrigerant sucked into the compressor constant even when there is a change in the amount of heat exchange in the condenser and evaporator and a change in the pressure of the refrigerant flowing in the main line and the hot gas mixing line.

[0043] The initial pressure of the above pressure regulator valve can be set to the pressure of the refrigerant sucked into the compressor under the condition that the refrigerant flows only through the main pipe.

[0044] The pressure upstream of the pressure regulator valve may vary depending on whether refrigerant flows through the hot gas mixing line or changes in the amount of heat exchange between the evaporator and condenser. Therefore, it is desirable to maintain the pressure and flow rate of the refrigerant sucked into the compressor through the pressure regulator valve constant despite such variable pressure.

[0045] The above control unit or controller can control the main line to operate in an operation mode in which the operating temperature band is lower than room temperature and control the operation of the hot gas mixing line to be excluded.

[0046] The above controller can control the main line to operate in an operating mode in which the operating temperature range is higher than room temperature and control the hot gas mixing line to operate by default. Controlling the operation of the hot gas mixing line may mean actively turning it on / off.

[0047] It is preferable to include a pressure-regulating valve installed in the main line to maintain a constant pressure of the refrigerant sucked into the compressor at an initially set pressure. The pressure of the refrigerant sucked into the compressor may increase due to the operation of the hot gas mixing line. In this case, the energy consumed by the compressor further increases. By controlling the operation of the hot gas mixing line, the reduction in cooling energy consumption can be effectively prevented from being offset by an increase in the energy consumption of the compressor.

[0048] In this embodiment, the pressure regulator is preferably a back pressure regulator (BPR) that maintains a constant pressure at the rear end, rather than a constant pressure at the front end. Therefore, even if the control environment changes, the energy consumed by the compressor's operation can be maintained at a constant level.

[0049] Cooling performance can be controlled by controlling the operating rate of the compressor itself, but the operating rate control range is very limited. Therefore, when the compressor operates at its normal operating rate, supercooling through the evaporator, supercooling compensation by the heater, and increased heat generation in the condenser are expected. To address this issue, according to the present embodiment, a portion of the refrigerant can be bypassed from the main line through a hot gas mixing line and introduced into the condenser.

[0050] It is preferable that the expanded refrigerant discharged from the condenser is mixed with the hot gas and then introduced into the evaporator.

[0051] By increasing the temperature of the refrigerant through the hot gas mixing line, the cooling performance in the evaporator can be controlled to decrease, and the heat dissipation performance in the condenser can be controlled to decrease.

[0052] It is preferable that the initially set pressure of the pressure regulator is set to the pressure of the refrigerant sucked into the compressor under the condition that the refrigerant flows only through the main pipe. The pressure on the upstream side of the pressure regulator may vary depending on the presence or absence of the refrigerant flowing through the hot gas mixing line or the change in the amount of heat exchange in the evaporator and condenser. That is, it is preferable that the pressure regulator control the refrigerant so that it is sucked into the compressor at the set pressure and flow rate despite such pressure variation. In other words, it is preferable that the pressure of the refrigerant sucked into the compressor is maintained constant by the pressure regulator even under the condition that the pressure of the refrigerant sucked into the compressor increases.

[0053] The output of the above heater is preferably limited to within 10%, preferably between 0% and 5%, under the condition that the temperature within the chamber is maintained at the set temperature. The output of the heater is fed back, and an increase in the output of the heater can be prevented and reduced through active control of the hot gas mixing line. In other words, the hot gas mixing line can be actively controlled to operate so as not to exceed the limited output.

[0054] The above set temperature may mean that the temperature within the chamber is a set temperature of 10 to 30 degrees, preferably 15 to 25 degrees, and more preferably 20 to 25 degrees, and the maintenance of the set temperature may mean that the temperature within the chamber is stabilized after the temperature within the chamber reaches the set temperature.

[0055] The cycling test device's default operation is to maintain a stable set temperature. Therefore, most operations are performed in this state, and it is desirable to effectively reduce energy consumption during this operation. Therefore, according to this embodiment, heater output is limited under operating conditions where the set temperature is stabilized and maintained, resulting in significant energy savings.

[0056] When the output of the heater is detected to be greater than the limited output, the amount of refrigerant flowing into the evaporator through the hot gas mixing line can be controlled so that the output of the heater is within the limited output.

[0057] In order to control the hot gas mixing ratio through the hot gas mixing line at the initial stage of setting, it is preferable to perform the initial setting by flowing an amount of refrigerant suitable for cooling performance only through the main line. In other words, normal operation can be performed after the total amount of refrigerant is appropriately set.

[0058] After the initial setting of the above refrigerant amount, the hot gas mixing ratio can be controlled by adjusting the opening rate of the hot gas mixing line so that the output of the heater is minimized while maintaining the temperature within the chamber at the set temperature. In other words, the opening rate can be set.

[0059] After the initial setting including the setting of the refrigerant amount and the opening rate is completed, the main line can be operated under control so that the temperature supplied to the evaporator is controlled while maintaining the initial setting value and changing the flow rate of the hot refrigerant of the hot gas mixing line.

[0060] In the above setting process, it is preferable to set an appropriate refrigerant flow rate through a needle valve provided in the hot gas mixing line, and then control operation through on / off of a solenoid valve provided in the hot gas mixing line.

[0061] The above main line is set to maintain cooling performance at a reference temperature using the refrigerant supplied from the compressor, and it is preferable to control the operation of the hot gas mixing line to control the heat removal amount of the evaporator in constant temperature operation at a temperature higher than the reference temperature.

[0062] It is preferable that refrigerant balancing control be performed to control the temperature of the refrigerant supplied to the evaporator by repeatedly controlling the on / off of the solenoid valve of the hot gas mixing line and controlling the opening rate of the flow control valve of the main line and the flow control valve of the hot gas mixing line.

[0063] The flow control valve of the above hot gas mixing line is a valve for controlling the flow rate of refrigerant and includes one of a pressure control valve, a constant temperature valve, and a constant pressure valve, and may include an automatic or manual control valve capable of arbitrary control.

[0064] In order to achieve the above-described object, according to one embodiment of the present invention, a cycling test device that operates to maintain a temperature within a chamber at a constant temperature may be provided, characterized in that it includes: a main line that sequentially connects a compressor, a condenser, and an evaporator so that a refrigerant circulates; a heater that heats air cooled through the evaporator; a hot gas mixing line that is bypassed from the main line between the compressor and the condenser and is connected to the main line between the condenser and the evaporator, and mixes hot gas discharged from the compressor with low-temperature, low-pressure gas supplied from the condenser to the evaporator; and a pressure-regulating valve that is provided in the main line and maintains a pressure of refrigerant sucked into the compressor at an initially set pressure, regardless of a change in the flow rate of hot gas supplied to the evaporator through the hot gas mixing line.

[0065] The above pressure regulator valve may be provided so that the pressure and flow rate of the refrigerant sucked into the compressor are maintained constant even under conditions in which the pressure of the refrigerant sucked into the compressor fluctuates due to changes in the flow rate of the refrigerant through various refrigerant lines, changes in the amount of heat exchange through the condenser and evaporator, and especially under conditions in which the pressure of the refrigerant sucked into the compressor increases.

[0066] By increasing the temperature of the refrigerant through the hot gas mixing line, the cooling performance in the evaporator can be controlled to decrease, and the heat dissipation performance in the condenser can be controlled to decrease.

[0067] It is preferable that the output of the above heater be limited to within 10%, preferably within 0% to 5%, under the condition that the temperature inside the chamber is maintained at room temperature.

[0068] If the output of the heater is detected to be greater than the limited output, a controller may be included that controls the amount of refrigerant flowing into the evaporator by repeatedly controlling the on / off of a solenoid valve provided in the hot gas mixing line, thereby controlling the output of the heater to be within the limited output.

[0069] According to the present embodiment, as one of the bypass lines, a cooling line may be included that is bypassed from the main line between the condenser and the evaporator and connected to the main line between the evaporator and the compressor to control the temperature of the refrigerant supplied to the compressor at a high temperature.

[0070] By the flow of refrigerant through the above cooling line, liquid compression in the compressor can be limited or prevented.

[0071] It is preferable that the refrigerant discharged from the above condenser and before expansion is bypassed through the above cooling line.

[0072] The bypass line may include an anti-freezing line that is connected to the main line between the evaporator and the compressor and bypasses the main line between the compressor and the condenser to prevent liquid compression occurring in the compressor due to freezing of the evaporator, and mixes hot gas discharged from the compressor with refrigerant discharged from the evaporator.

[0073] The above main line may be equipped with a solenoid valve for opening and closing the main line and a needle valve for controlling the opening rate of the main line. In the present embodiment, the solenoid valve is an electronic valve that opens and closes the opening rate through a control signal, and is an example of a shut-off valve, but is not necessarily limited to a solenoid valve. The needle valve is a valve that controls the flow rate by controlling the opening rate, and may be an electronic valve or a manual valve. Therefore, the needle valve in the present embodiment is an example of a flow control valve, but is not necessarily limited to a needle valve.

[0074] The above bypass line may be equipped with a solenoid valve for opening and closing the bypass line and a needle valve for controlling the opening rate of the bypass line. Similarly, examples of a shut-off valve and a flow control valve are provided, but are not necessarily limited thereto.

[0075] The above bypass line may be equipped with a capillary tube to reduce mechanical shock caused by changes in refrigerant pressure due to changes in the opening ratios of the main line and the bypass line. The capillary tube may also be an example of a flow control device.

[0076] The above solenoid valves are controlled on / off, and it is preferable that a needle valve and / or a capillary tube be provided at the rear end of the solenoid valve. The opening rate of the needle valve can be set, and the flow rate can be controlled by controlling the on / off of the solenoid valves, and the flow rate can be controlled by adjusting the opening rate of the needle valve while the solenoid valves are in the on state.

[0077] Meanwhile, it is desirable to omit the needle valve and capillary configuration in the defrost line, because when the defrost line is driven, both the main line and other lines can be closed.

[0078] The above cycling test device may be equipped to operate in multiple operating modes for each operating temperature band.

[0079] The operation of each bypass line can be preset for each operating mode. For example, in an operating mode for a specific temperature range, either the hot gas mixing line or the cooling line, or both, can be operated. Of course, in the operating mode for the lowest temperature range, neither the hot gas mixing line nor the cooling line can be operated. In this case, the main line can be operated.

[0080] The above heater is controlled to turn on when necessary to control the temperature inside the chamber, and when the heater is turned on, the output can be controlled to converge to a reference output value. As the output value of the heater increases, the energy consumed increases. An increase in the output value of the heater means that the amount of heat, or energy, that must be compensated for after cooling the air in the refrigerator increases. This means that the refrigerator cools the air more than necessary. Therefore, it is desirable to control the output value of the heater so that the output value of the heater converges to the reference output. This is desirable to control so that when the output value of the heater increases, the cooling load in the refrigerator is reduced, thereby lowering the output value of the heater.

[0081] Ultimately, according to the present embodiment, the output value of the heater is controlled to control the temperature inside the chamber, and the output value of the heater can be controlled to converge to a reference output. In addition, when the output value of the heater is sensed to be within a certain range or a certain value, the cooling load in the refrigerator can be controlled to be reduced. In particular, in the present embodiment, the temperature of the refrigerant flowing into the evaporator can be increased, thereby controlling the heat removal load in the evaporator to be reduced.

[0082] According to the present embodiment, the condenser includes a cooling fan that performs heat exchange between the refrigerant and the outside air, and the cooling fan preferably has RPM control performed by an inverter. Accordingly, the heat exchange amount of the condenser can be actively controlled, thereby controlling the temperature of the refrigerant discharged from the condenser.

[0083] For example, the RPM can be controlled from 100% to 80%. In this case, the heat exchange capacity of the condenser decreases, which can result in an increase in the temperature of the refrigerant discharged from the condenser. Since the refrigerant discharged from the condenser flows into the evaporator, the temperature of the refrigerant flowing into the evaporator can be increased.

[0084] In order to achieve the above-described object, according to one embodiment of the present invention, a control method of a cycling test device operated to control the temperature within a chamber may be provided, comprising: a main operation step of operating a main line in which a compressor, a condenser, and an evaporator are sequentially connected to circulate a refrigerant; and a hot gas operation step of operating a hot gas mixing line, which is bypassed in the main line between the compressor and the condenser and connected to the main line between the condenser and the evaporator, and is provided to mix hot gas discharged from the compressor with low-temperature, low-pressure gas discharged from the condenser and supply the mixture to the evaporator, and a control method of a cycling test device characterized in that whether or not the hot gas operation step is performed and the amount of refrigerant supplied through the hot gas are controlled according to the operation mode of the chamber, the temperature range of the chamber, or the operation mode and the temperature range of the chamber.

[0085] In addition, depending on the operating mode of the chamber, the temperature range of the chamber, or the operating mode and temperature range of the chamber, it is possible to control whether a cooling operation step for operating the cooling line is performed and the amount of refrigerant flowing into the compressor without passing through the evaporator through the cooling line.

[0086] In order to achieve the above-described object, according to one embodiment of the present invention, there is provided a control method of a cycling test device operated to control the temperature within a chamber, the control method comprising: a main operation step of operating a main line in which a compressor, a condenser, and an evaporator are sequentially connected to circulate a refrigerant; and a cooling operation step of operating a cooling line that is bypassed in the main line between the condenser and the evaporator and connected to the main line between the evaporator and the compressor, and provides low-temperature refrigerant discharged from the condenser to the compressor without passing through the evaporator, and characterized in that, depending on the operating mode of the chamber, the temperature range of the chamber, or the operating mode and the temperature range of the chamber, a control method of a cycling test device can be provided, characterized in that whether the cooling operation step is performed and the amount of refrigerant provided to the compressor through the cooling line are controlled.

[0087] The above operating mode may include a constant temperature mode that maintains the temperature inside the chamber at a set temperature and a conversion mode that raises or lowers the temperature inside the chamber.

[0088] In the above-described constant temperature mode and the conversion mode for lowering the temperature within the chamber, it is preferable that the hot gas operation step be performed.

[0089] Multiple operating modes may be provided depending on the temperature range of the chamber.

[0090] Among the above plurality of operation modes, an operation mode in which the hot gas operation step can be performed may be preset. In addition, among the above plurality of operation modes, an operation mode in which the cooling operation step can be performed may be preset.

[0091] The above main operation step may include a first step of supplying refrigerant to the compressor at a constant pressure and flow rate through a pressure-regulating valve that constantly controls the pressure and flow rate of the refrigerant supplied to the suction end of the compressor.

[0092] The above main operation step may include a second step of supplying refrigerant to the compressor by opening an on-off valve provided in parallel with the pressure regulator valve at the suction end of the compressor.

[0093] In order to increase the cooling performance in the evaporator, it is preferable to switch from the first stage to the second stage, and in order to decrease the cooling performance in the evaporator, it is preferable to switch from the second stage to the first stage.

[0094] It is preferable that the above hot gas operation step be performed by opening the hot gas opening / closing valve provided in the hot gas mixing line.

[0095] It is preferable that the above hot gas operation step be performed to increase the temperature of the refrigerant supplied to the evaporator and thereby reduce the cooling performance of the evaporator.

[0096] It is preferable to include a main opening / closing valve provided at the suction end of the compressor, and to control the operation of the main opening / closing valve and the hot gas opening / closing valve to be crossed.

[0097] It is preferable to include a compressor suction bypass line that supplies refrigerant to the compressor without passing through the main opening / closing valve.

[0098] It is preferable that the above compressor suction bypass line be provided with a pressure regulator valve that controls the pressure and flow rate of the refrigerant supplied to the suction end of the compressor.

[0099] In the constant temperature mode where the temperature inside the chamber is maintained constant, it is preferable to control the main opening / closing valve to be closed and the hot gas opening / closing valve to be opened.

[0100] In the conversion mode for lowering the temperature inside the chamber, it is preferable to control the main opening / closing valve to be opened, the hot gas opening / closing valve to be closed, or the main opening / closing valve to be opened and the hot gas opening / closing valve to be closed.

[0101] It is preferable that the main line on-off valve be a NOT (normally open type) valve and the hot gas on-off valve be a NCT (normally close type) valve so as to be signal-connected to the control unit through the same point, and that the control unit be controlled by a control unit that controls the operation of the cycling test device. Therefore, control can be easily achieved through a single control contact.

[0102] At or below the preset temperature or preset temperature range, it is preferable to exclude the performance of the hot gas operation step.

[0103] At or above the preset temperature or preset temperature range, it is preferable that the main operation step and the hot gas operation step are performed together.

[0104] It is preferable that the on / off operation of the hot gas mixing line is controlled in the above hot gas operation step.

[0105] The above hot gas mixing line is equipped with a flow control valve for controlling the flow rate of refrigerant, and it is preferable that the opening ratio of the flow control valve be set to a constant value.

[0106] In order to achieve the above-described object, according to one embodiment of the present invention, there is provided a control method for a cycling test device that is operated to maintain a temperature within a chamber at a constant temperature, the control method comprising: a main operation step of circulating refrigerant through a main line in which a compressor, a condenser, and an evaporator are sequentially connected and the refrigerant is circulated, and the refrigerant is supplied to the compressor through an on-off valve located at a suction end of the compressor; and a hot gas operation step of mixing hot gas discharged from the compressor with low-temperature, low-pressure gas discharged from the condenser through an on-off valve, and supplying the mixture to the evaporator, the mixture being bypassed in the main line between the compressor and the condenser and connected to the main line between the condenser and the evaporator, and the mixture being characterized in that the operation control of the on-off valve of the main line and the operation of the on-off valve of the hot gas mixing line are controlled to be alternated.

[0107] The above main line may include a compressor suction bypass line that supplies refrigerant to the compressor without passing through the main line's on-off valve.

[0108] Therefore, the main operation stage and the hot gas operation stage can be performed selectively.

[0109] It is preferable that the above compressor suction bypass line be provided with a pressure regulating valve or a pressure regulator valve that regulates the pressure and flow rate of the refrigerant supplied to the suction end of the compressor.

[0110] When the main line's on-off valve is opened and the main operation stage is performed, the refrigerant is not actually introduced into the compressor through the compressor suction bypass line and the pressure regulating valve mounted thereon due to the flow resistance. This is because the pressure regulating valve itself has a relatively high flow resistance.

[0111] On the other hand, when the on-off valve in the hot gas mixing line is open and the on-off valve in the main line is closed, the refrigerant can only flow into the compressor through the compressor suction bypass line. In other words, the refrigerant can only flow into the compressor through the pressure regulating valve.

[0112] During static operation to maintain the temperature inside the chamber constant, the on-off valve of the main line can be controlled to close and the on-off valve of the hot gas mixing line to open.

[0113] When the temperature inside the chamber is lowered during operation, the on-off valve of the main line can be controlled to open and the on-off valve of the hot gas mixing line can be controlled to close.

[0114] It is preferable that the opening / closing valves of the above main line and hot gas mixing line are solenoid valves.

[0115] The above cycling test device is operated in multiple operating modes according to the operating temperature range, and in an operating mode lower than room temperature among the operating modes, performance of the hot gas mixing line operating step may be excluded.

[0116] In the above driving modes, in the driving mode higher than room temperature, the main line driving step and the hot gas mixing line driving step can be controlled to be performed together.

[0117] The above room temperature can be set to approximately 23 to 26 degrees, and therefore, the operating mode as a temperature range including the room temperature can be set to have a temperature range of approximately 20 to 30 degrees.

[0118] In the above hot gas mixing line operation step, it can be performed through on / off operation control of the opening / closing valve of the hot gas mixing line.

[0119] The above hot gas mixing line is equipped with a flow control valve for controlling the flow rate of refrigerant, and the opening ratio of the flow control valve can be set to a constant value.

[0120] The opening rate of the above flow control valve can be set during the initial setting process of the above cycling test device.

[0121] It may include a heater that heats the air cooled through the above evaporator.

[0122] The hot gas operation step can be performed so that the output of the heater is limited to within 10%, preferably within 0% to 5%, under the condition that the temperature within the chamber is maintained at a set temperature.

[0123] The output of the above-mentioned limited heater may be based on the output of the heater under conditions in which the temperature within the chamber is maintained at a reference temperature. The reference temperature is a temperature lower than room temperature, and for example, the output of the heater under conditions in which the temperature within the chamber is maintained at 0 degrees may be used as the reference output.

[0124] In order to achieve the above-described object, according to one embodiment of the present invention, there is provided a cycling test device that operates to maintain a temperature within a chamber at a constant temperature, the cycling test device comprising: a main line that sequentially connects a compressor, a condenser, and an evaporator so that a refrigerant is circulated; a heater that heats air cooled through the evaporator; a hot gas mixing line that is bypassed from the main line between the compressor and the condenser and connected to the main line between the condenser and the evaporator to increase the temperature of the evaporator and limit the output of the heater, and mixes hot gas discharged from the compressor with low-temperature, low-pressure gas discharged from the condenser and mixed with low-temperature, low-pressure gas supplied to the evaporator; an on-off valve located at a suction end of the compressor in the main line; an on-off valve provided in the hot gas mixing line; and a controller that controls the operation of the on-off valve of the main line and the operation of the on-off valve of the hot gas mixing line to be alternated.

[0125] The features of each of the above-described embodiments may be commonly applied to other embodiments, as long as they are not mutually contradictory or exclusive.

[0126] Through one embodiment of the present invention, a test device and control method capable of controlling the cooling performance of an evaporator according to the amount of heat removal required to maintain temperature inside a chamber of a cycling test device can be provided.

[0127] Through one embodiment of the present invention, a test device and control method capable of minimizing the amount of heat generated by a condenser that generates external heat of a cycling test device can be provided.

[0128] Through one embodiment of the present invention, a test device and control method capable of suppressing the occurrence of liquid compression by controlling the temperature of an evaporator and the suction temperature of a compressor can be provided.

[0129] Through one embodiment of the present invention, a test device and control method can be provided that can prevent energy loss by controlling the required heat generation amount of a heater to a minimum.

[0130] Through one embodiment of the present invention, a test device and control method can be provided that can prevent energy loss due to the heater and prevent overcooling through the evaporator by controlling the balancing of refrigerant flowing into the evaporator through the main line and the hot gas mixing line based on the output of the heater.

[0131] Through one embodiment of the present invention, a test device and control method can be provided that can prevent unnecessary energy loss in a compressor caused by an increase in the pressure of refrigerant flowing into the compressor during a process of controlling the cooling performance of an evaporator.

[0132] Through one embodiment of the present invention, in a situation where the output control of the compressor is difficult or limited, a test device and a control method can be provided for controlling the heat exchange amount of the compressor and condenser, in which heat exchange occurs between the refrigerator and an external system, through balancing control of the refrigerant in the circulation circuit connected to the compressor, condenser, evaporator, and compressor.

[0133] Through one embodiment of the present invention, a test device and a control method can be provided that can suppress the occurrence of liquid compression, which is a major cause of compressor failure, by controlling the temperature of an evaporator and the suction temperature of a compressor through balancing control of a refrigerant in a circulation circuit, thereby controlling freezing of the evaporator to a certain level or lower.

[0134] Through one embodiment of the present invention, a test device and control method can be provided that can control whether a step of operating the hot gas mixing line is performed and the amount of refrigerant supplied through the hot gas according to the operating mode of the chamber or the temperature range of the chamber by providing a hot gas mixing line separately from the main line of the refrigerator.

[0135] Through one embodiment of the present invention, a test device and control method can be provided that can control whether a step of operating the cooling line is performed and the amount of refrigerant supplied to the compressor through the cooling line, depending on the operating mode of the chamber or the temperature range of the chamber, by providing a cooling line separately from the main line of the refrigerator.

[0136] Through one embodiment of the present invention, a test device and control method can be provided that can effectively control the amount and temperature of refrigerant flowing into a compressor by providing a bypass line at the compressor suction end.

[0137] Through one embodiment of the present invention, a test device and control method can be provided that can operate the main line in stages through an on-off valve at an inlet end where refrigerant flows into a compressor from a main line and a bypass line that bypasses the on-off valve.

[0138] Through one embodiment of the present invention, a test device and control method can be provided that can simplify control logic and reduce the capacity of a controller by cross-controlling the opening / closing valve of a main line and the opening / closing valve of a hot gas mixing line.

[0139] FIG. 1 is a schematic cross-sectional view of a cycling test device according to an embodiment of the present invention.

[0140] FIG. 2 is a schematic perspective view of a cycling test device according to an embodiment of the present invention.

[0141] Figure 3 is a circuit diagram of a refrigerator that can be applied to a cycling test device according to one embodiment of the present invention.

[0142] Figure 4 is a control configuration block diagram of a cycling test device according to one embodiment of the present invention.

[0143] Figure 5 is a table for an example of a driving scenario.

[0144] Figure 6 is a table for another embodiment of a driving scenario;

[0145] FIG. 7 is a circuit diagram of a refrigerator that can be applied to a cycling test device according to another embodiment of the present invention.

[0146] Figure 8 is a control logic according to one embodiment of the present invention, showing the operation logic from the perspective of refrigerant balancing.

[0147] Figure 9 shows the control logic according to one embodiment of the present invention, and illustrates the operation logic from the viewpoint of temperature change within the chamber.

[0148] Hereinafter, a cycling test device according to an embodiment of the present invention will be described in detail with reference to the attached drawings. For convenience, temperature in this specification means temperature unless otherwise specified.

[0149] Hereinafter, a test device according to an embodiment of the present invention will be described in detail with reference to FIGS. 1 and 2.

[0150] FIG. 1 schematically illustrates a cross-section of a cycling test device according to an embodiment of the present invention, and FIG. 2 schematically illustrates an external appearance of the cycling test device.

[0151] The test device (10) may include a cabinet (11) forming an outer shape. The cabinet (11) may be provided with a housing (20) forming a chamber (30) and a machine room (40) having components forming a refrigerator, which are provided separately from each other.

[0152] A control panel (50) may be provided on the front of the cabinet (11). The control panel (50) may be provided with an operating unit for inputting temperature conditions or time conditions within the chamber, and a display unit for indicating the current status. In addition, a control unit for controlling the operation of the test device may be provided within the control panel (50).

[0153] The test device (10) can be operated in multiple operating modes according to a temperature control pattern. The temperature control pattern may include a pattern for maintaining a set temperature, a pattern for increasing the temperature, and a pattern for decreasing the temperature. The device can be operated in a constant temperature mode for maintaining the current set temperature, a temperature increasing mode for increasing the temperature when the new set temperature becomes higher than the previous set temperature, and a temperature decreasing mode for decreasing the temperature when the new set temperature becomes lower than the previous set temperature. That is, the constant temperature mode can be performed after the temperature increasing mode or the temperature decreasing mode is temporarily performed. The operating mode can vary depending on the set temperature input by the user through the control panel and the change in the set temperature.

[0154] The test device (10) can be operated in multiple operating modes depending on the temperature range within which the set temperature falls. Since the test device (10) basically performs constant temperature operation, i.e., operation that continuously maintains the set temperature, the operating mode may vary depending on the set temperature, which is the temperature at which the constant temperature is maintained. For example, the temperature range is set at approximately 10-degree intervals, and multiple operating modes may be provided accordingly.

[0155] For example, if the set temperature is 25 degrees, the user can select the 20 to 30 degree operating mode, which corresponds to 25 degrees, and then select the set temperature. This selection can be performed by the user through the control panel (50). Of course, if the user only selects the set temperature, the operating mode corresponding to the set temperature can be automatically selected.

[0156] The housing (20) may include a chamber (30) having a test space (31) therein. It may also include a circulation duct (32) surrounding at least three sides of the chamber. For example, air discharged from one side of the chamber may move to the rear of the chamber and then be supplied into the chamber through the other side of the chamber. In other words, air circulation may be performed.

[0157] A plurality of chambers (30) may be provided in one test device (10), and as an example, two chambers are provided as shown in FIG. 2.

[0158] In the test space (31), various types of battery performance tests, such as battery charge / discharge tests, can be performed.

[0159] Specifically, the housing (20) may include a first case (21) forming a plurality of partition walls forming a test space (31) and a second case (22) partitioned from the first case (21).

[0160] The above first case (21) can be provided to have upper, lower, left, right, and rear walls, excluding the front that is connected to the outside through the door (60).

[0161] A circulation duct (32) may be provided or formed between the first case (21) and the second case (22). As illustrated, air within the chamber may be discharged through one side wall of the first case (21) and introduced to the rear of the first case (21), and then introduced into the chamber through the other side wall of the first case (21). A plurality of openings may be formed in one side wall and the other side wall of the first case (21) to allow air to flow in and out.

[0162] Battery testing can be performed over a very long period of time, and the start and end of testing for a particular battery are typically performed within the same chamber (30). This is because the input and output factors during the battery testing process are highly sensitive, and the accuracy of these factors can be compromised when the chamber (30) is changed. For this reason, when the type or number of batteries to be tested varies, a large number of test devices (10) are required.

[0163] During the battery testing process, heat may be generated within the battery. Battery testing is typically conducted at a constant temperature for extended periods of time. Therefore, a temperature control unit is required to control the temperature within the chamber (30) to maintain a constant temperature.

[0164] This temperature control can be achieved through the air circulating through the above-mentioned circulation duct (32). This temperature control method can be referred to as a convection type. Specifically, a heat exchanger is provided within the circulation duct (32) to absorb heat from the air. In other words, heat generated within the chamber can be removed through the heat exchanger within the circulation duct (32).

[0165] It is preferable that the above circulation duct (32) be provided in each chamber.

[0166] As illustrated, different heat exchangers may be arranged side by side within the circulation duct (32). For example, air discharged within the chamber may undergo heat exchange while passing through the heat exchanger (150). Here, the heat exchanger may be a part of the components forming the refrigeration cycle. From a refrigerant perspective, such a heat exchanger may be referred to as an evaporator. That is, the liquid refrigerant introduced into the evaporator absorbs heat from the surrounding air and changes into a gaseous refrigerant.

[0167] Additionally, the circulation duct (32) may be equipped with a heater (115). The heater may be provided to intentionally increase the temperature within the chamber. Of course, the heater (115) may be provided to supply heat during supercooling to compensate for the supercooling with appropriate cooling.

[0168] A circulation fan (170) may be provided to circulate air in the above circulation duct (32). The fan may be provided in the form of a sirocco fan that sucks in and discharges air, and when the fan is operated, air inside the chamber may be sucked in and the air may be discharged back into the chamber. The motor (171) that operates the circulation fan (170) may be provided in the machine room (40) rather than inside the circulation duct (32).

[0169] Below, a refrigerator or refrigeration cycle that can be applied to a test device according to one embodiment of the present invention will be described in more detail.

[0170] A refrigerator (100) may be provided as a temperature control unit to control the temperature inside the chamber, and a heater may also be added.

[0171] As illustrated in FIG. 3, the test device may include a refrigerator (100) or a refrigeration cycle. The refrigerator here may be referred to as a cooling heat exchanger in a broad sense for cooling.

[0172] The refrigerator (100) may include a compressor (120), a condenser (130), and an evaporator (150). The evaporator (150) is a heat exchanger that cools the air by exchanging heat with the air inside the chamber, and thus can be referred to as a cooling heat exchanger in the narrow sense.

[0173] And the refrigerator (100) may be configured to include a main line (110) through which refrigerant circulates by sequentially connecting a compressor (120), a condenser (130), and an evaporator (150). The main line (110) may be equipped with a solenoid valve (110a), as an example of an on-off valve for blocking the flow of refrigerant through the main line (110). Here, the main line (100) forms a closed loop, i.e., a waste oil path. The solenoid valve may be equipped in multiple numbers depending on the embodiment, and the installation location may also vary.

[0174] As the refrigerant flows along the main line (110), it removes heat from the chamber through the heat exchanger, i.e., the evaporator (150), and radiates the removed heat to the outside of the device through the condenser (160). Therefore, the evaporator (150) is provided inside the circulation duct (32), and the compressor (120) and the condenser (130) can be provided in the machine room (40). In fact, most of the components that make up the refrigerator (100) can be provided in the machine room (40).

[0175] A liquid separator (121) may be provided at the front end of the compressor (120), and the liquid separator (121) may separate gas and liquid from the incoming refrigerant so that the gaseous refrigerant may be introduced into the compressor (120). That is, the liquid separator (121) may be provided at the suction end of the compressor (120) to prevent liquid compression to a certain extent.

[0176] An oil separator (122) may be provided at the rear end of the compressor (120). The oil separator (122) may separate and recover oil from the refrigerant discharged from the compressor (120) and resupply it to the compressor (120).

[0177] The above refrigerator (100) may include a main line (110) as well as a bypass line (111, 112, 113, 114). The bypass line may be bypassed at a specific point of the main line (110) and connected to another specific point of the main line.

[0178] The above bypass line (111, 112, 113, 114) may include a hot gas mixing line (111). The hot gas mixing line may be provided by bypassing the main line (110) between the compressor (120) and the condenser (130) and connecting it to the main line between the condenser (130) and the evaporator (150).

[0179] Through the main line (110), the high-temperature, high-pressure gaseous refrigerant discharged from the compressor (120) passes through the condenser (160), is cooled and expanded, and then flows into the evaporator (150). That is, the low-temperature, high-pressure liquid refrigerant expands and then flows into the evaporator (150). In order to expand and block the flow of the refrigerant and control the flow rate, a blocking valve and a flow rate control valve may be provided. As an example of the blocking valve, a solenoid valve (110a) may be provided, and as an example of the flow rate control valve, a needle valve (110b) may be provided. Of course, a separate expansion valve or the like may be provided for the expansion of the refrigerant.

[0180] The above hot gas mixing line (111) may be provided so that the high temperature and high pressure gaseous refrigerant discharged from the compressor (120) flows into the evaporator (150) without passing through the condenser (160). That is, the hot gas may be provided so that it flows into the evaporator (150). The hot gas mixing line (111) may be provided with an on-off valve and a flow rate control valve for flow shielding and flow rate control. As an example of the shielding valve, a solenoid valve (111a) may be provided, and as an example of the flow rate control valve, a needle valve (111b) may be provided. In addition, a capillary tube (111c) may also be provided.

[0181] A hot gas mixing line (111) may be provided to mix hot gas discharged from a compressor with low-temperature, low-pressure gas supplied from a condenser to an evaporator to increase the refrigerant temperature of the evaporator (150).

[0182] When the main line (110) is opened and operated and the hot gas mixing line (111) is opened and operated, the hot gas in a high-temperature and high-pressure state discharged from the compressor and the gas in a low-temperature and low-pressure state discharged from the condenser (130) and expanded are mixed. In other words, the refrigerant in a hot gas state and the refrigerant in a low-temperature and low-pressure gas state can be mixed and then supplied to the evaporator (150).

[0183] Here, a portion of the refrigerant discharged from the compressor (120) may flow along the main line (110) and a portion may flow along the hot gas mixing line (111), and then be mixed in the main line (110) before being introduced into the evaporator (150). Therefore, the temperature of the refrigerant introduced into the evaporator may increase due to the mixing effect of the hot gas. Here, a check valve (110c) may be provided to prevent the mixed refrigerant from flowing back in the main line (111). That is, the hot gas mixing line (111) is connected to the main line (110) between the evaporator (150) and the check valve (110c), so that the refrigerant mixed with the hot gas may be sucked into the evaporator (150).

[0184] According to the present embodiment, the condition of the evaporator can be controlled through the hot gas mixing line (111). That is, by removing an appropriate amount of heat through the evaporator (150), excessive energy removal can be prevented. If excessive heat removal is performed through the evaporator (150), heat must be supplemented through the heater (115). Therefore, this means unnecessary energy consumption. Therefore, by controlling the amount of refrigerant introduced through the hot gas mixing line (111), the temperature of the refrigerant introduced into the evaporator can be controlled, thereby preventing excessive heat removal. The higher the temperature of the refrigerant introduced into the evaporator, the lower the amount of heat removal through the evaporator. This means that the greater the amount of refrigerant introduced into the hot gas mixing line (111), the lower the amount of heat removal through the evaporator.

[0185] By controlling the balance of the refrigerant flowing through the main line (110) and the hot gas mixing line (111), it is possible to control the cooling performance of the evaporator in an environment where the performance control of the compressor is limited. That is, it is possible to control the cooling performance of the evaporator according to the amount of heat removal required to maintain the temperature inside the chamber (heat flux required for the heat generation load and temperature change inside the chamber). In other words, the cooling performance of the evaporator can be controlled by controlling the temperature of the evaporator through controlling the balance (mass and heat balance) of the amount of refrigerant flowing through the main line and the hot gas mixing line.

[0186] In other words, by controlling the refrigerant balance in the main line (110) and the hot gas mixing line (111), the cooling performance of the evaporator can be controlled even in a situation where the performance control of the compressor is limited.

[0187] Here, it can be seen that the amount of refrigerant flowing into the condenser (130) through the main line (110) is reduced as the refrigerant flows through the hot gas mixing line (111). That is, it can be seen that only a portion of the high-temperature, high-pressure refrigerant discharged from the compressor (120) flows into the condenser (130). Accordingly, the heat load discharged to the outside of the device through the condenser (130) can be reduced.

[0188] Ultimately, by controlling the amount of refrigerant supplied to the evaporator through the hot gas mixing line (111) among the hot gases discharged from the compressor, the cooling performance of the evaporator and the heat load through the condenser can be controlled.

[0189] It is preferable that the pipe diameter of the hot gas mixing line be the same as that of the main line. This allows for very wide and active refrigerant balancing control between the hot gas mixing line and the main line. Furthermore, the hot gas mixing line can branch from the main line in a "Y" or "T" shape.

[0190] The above hot gas mixing line is preferably configured to allow refrigerant to flow in the following order: from the compressor to the solenoid valve, the control valve, and the evaporator. Accordingly, the operation of the hot gas mixing line can be controlled by controlling the on / off of the solenoid valve, and the flow rate of hot gas supplied to the evaporator can be controlled by controlling the control valve.

[0191] The control valve can be configured as a needle valve and can be equipped to automatically adjust the opening ratio or to allow arbitrary control on-site. Furthermore, two or more can be installed in series to facilitate flow control. It is desirable to design the control valve to ensure a smooth supply of refrigerant gas from the main line and hot gas from the hot gas mixing line to the evaporator, taking into account the differential pressure across the piping and each valve.

[0192] Meanwhile, the inventors of the present invention were able to confirm that when the refrigerant is bypassed through the hot gas mixing line (111), the pressure of the refrigerant flowing into the compressor increases. That is, as the refrigerant flows into the compressor at a pressure higher than the normal pressure, it was confirmed that an overload occurs in the compressor (120), and the energy consumed by the compressor (120) actually increases. As a result, it was confirmed that the energy used to compensate for supercooling with a heater decreases, but at the same time, the energy consumed by the compressor increases, so that the effect of operating the hot gas mixing line (111) is halved.

[0193] To solve this problem, a pressure regulator valve (123) that maintains a constant pressure and flow rate of the refrigerant flowing into the compressor (120) may be provided in the main line.

[0194] The above-mentioned pressure regulator valve can be defined as a valve that reduces the pressure of the refrigerant when the pressure is higher than the intended use and maintains a constant pressure. Furthermore, it can be defined as a valve that maintains not only a constant pressure but also a constant flow rate.

[0195] The above pressure regulator is provided at the front end of the compressor (120), and more preferably, the pressure regulator (123) is provided between the liquid separator (121) and the compressor (120).

[0196] The reference pressure of the pressure regulator valve can be set based on the pressure at the front end of the compressor during normal operation of the compressor with the hot gas mixing line (111) closed or during the initial setting process in which the refrigerant flows only through the main line (110). That is, even when the pressure and flow rate of the refrigerant flowing into the compressor fluctuate through refrigerant balancing control, the refrigerant can be introduced into the compressor at a constant pressure and flow rate. Even if the refrigerant is bypassed through the hot gas mixing line (111), the pressure and flow rate of the refrigerant flowing into the compressor are constant, thereby preventing additional energy consumption through the compressor. In addition, the expected effect through the hot gas mixing line (111) can be obtained. Therefore, it is possible to provide an optimized cycling test device through the simple addition of a pressure regulator valve that does not require additional control logic.

[0197] The above bypass lines (111, 112, 113, 114) may include a cooling line (114). The cooling line may be provided by being bypassed from the main line (110) between the condenser (150) and the evaporator (150) and connected to the main line (110) between the evaporator (150) and the compressor (120).

[0198] The above cooling line (114) can be connected to the main line (110) at the rear end of the evaporator (150) after the refrigerant is bypassed before being discharged from the condenser (130) and expanded. The refrigerant supplied through the cooling line (114) and the refrigerant discharged from the evaporator (150) can be mixed and then introduced into the compressor (120) through the liquid separator (121).

[0199] If the temperature inside the chamber is maintained high, especially if it is maintained higher than room temperature, the temperature of the refrigerant supplied to the compressor may increase. This is because the high temperature air is removed from the evaporator (150), so the amount of heat removed from the evaporator (150) may be excessive or unnecessary, and the overheated refrigerant may be discharged and introduced into the compressor. Therefore, it is desirable to control the temperature of the refrigerant supplied to the compressor, and this can be controlled through the cooling line (113). That is, the refrigerant, the temperature of which has been lowered by passing through the condenser (130), is supplied to the compressor through the cooling line (113), thereby controlling the temperature of the refrigerant introduced into the compressor (120).

[0200] Specifically, the compressor suction temperature can be controlled through refrigerant balancing control of the main line (110) and the cooling line (114), and the evaporator temperature can be controlled through refrigerant balancing control of the main line (110) and the hot gas mixing line (111). Through this, the occurrence of liquid compression, which is a major cause of refrigerator failure, can be effectively suppressed.

[0201] The cooling line (114) may be provided with a solenoid valve (114a) for opening and closing the line and a needle valve (114b) for controlling the flow rate of refrigerant. A check valve (114d) may be provided before the cooling line (114) is connected to the main line (110). Through the check valve (114d), the refrigerant supplied from the cooling line (114) may be prevented from flowing back into the cooling line (114) and the refrigerant discharged from the evaporator (150) may be prevented from flowing into the cooling line (114). It is preferable that the temperature control of the refrigerant flowing into the compressor through the cooling line (114) be performed in a mode that operates in a temperature range higher than room temperature. That is, the suction refrigerant temperature of the compressor can be controlled through the balance control of the amount (mass) and the amount of heat (heat) of the refrigerant flowing into the main line and the cooling line.

[0202] Meanwhile, the refrigerant can be controlled to flow in all of the main line, hot gas mixing line, and cooling line (114). In this case, the temperature of the refrigerant flowing into the evaporator and the temperature of the refrigerant sucked into the compressor can be controlled through balance control.

[0203] When the operating temperature range is higher than room temperature and less than approximately 50 degrees, refrigerant balance control through the main line (110), hot gas mixing line (111), and cooling line (114) may be required. At this time, it is desirable to control the heat load discharged to the outside through the condenser (130). For example, as described below, the heat load can be controlled by operating the RPM of the cooling fan (160) lower than the normal RPM.

[0204] The above bypass lines (111, 112, 113, 114) may include an anti-freeze line (112). The anti-freeze line (112) may be provided by bypassing the main line (110) between the compressor (120) and the condenser (130) and connecting to the main line between the evaporator (150) and the compressor (120). The refrigerant bypassed through the anti-freeze line (112) may be mixed with the refrigerant flowing through the main line (110) and may be introduced into the compressor (120) via the liquid separator (121). That is, the anti-freeze line (112) may be a line for mixing the hot gas discharged from the compressor (120) with the refrigerant discharged from the evaporator (150) and supplying the mixture to the compressor (120).

[0205] If freezing occurs in the evaporator (150), sufficient heat exchange may not be performed through the evaporator (150), and thus liquid refrigerant may flow into the compressor (120). The flow of liquid refrigerant into the compressor may be prevented to some extent through the liquid separator (121), but this may not be sufficient. If liquid refrigerant flows into the compressor (120) and liquid compression occurs, the refrigerant may not be sufficiently compressed, and thus freezing may occur in the evaporator (150) due to a lack of refrigerant. In other words, damage to the compressor (120) may occur due to liquid compression, or freezing may occur in the evaporator. Therefore, by preventing liquid compression, freezing in the evaporator can be prevented as a result.

[0206] The above bypass lines (111, 112, 113, 114) may include a defrost line (113). The defrost line (113) may be provided by bypassing the main line (110) between the compressor (120) and the condenser (130) and connecting it to the main line between the condenser (130) and the evaporator (150). The defrost line (114) may be a line for supplying hot gas discharged from the compressor to the evaporator. At this time, the inflow of refrigerant from the compressor to the condenser (130) may be blocked.

[0207] The above-mentioned defrost line (113) may have a similar bypass and connection position to the above-mentioned hot gas mixing line (111). Here, the defrost line (113) is a line for very actively removing ice formed on the surface of the evaporator, and therefore may be controlled to open only when the chamber door is opened and outside air is introduced into the chamber.

[0208] The chamber door is opened before and after the test begins. Furthermore, door opening can only be performed under very limited and special circumstances. This is because cycling tests, such as those for secondary batteries, are typically performed at a preset temperature for extended periods. Intentional door opening during the test can intentionally inflict temperature shock. However, normal testing must be performed again afterward. However, ice formation on the evaporator surface prevents the refrigerator (100) from operating normally. Therefore, in special circumstances where the door is detected to be open, the refrigerator (100) may perform a heater function to heat the evaporator rather than cooling the air. Of course, normal operation can be performed once the refrigerator (100) operation via the defrost line (113) is terminated.

[0209] A solenoid valve (113a) may be provided to open and close the defrost line (113). The solenoid valve (113a) may be operable to open the defrost line (114) for a certain period of time when the door is opened. At this time, the compressor (120) is preferably operated, but the main line (120) and other bypass lines are preferably closed. Of course, it is also preferable that the cooling fan (160) of the condenser is not operated.

[0210] In order to prevent the hot gas supplied through the above-mentioned defrosting line (114) from flowing back through the main line (110), a check valve (110c) may be provided in the main line (110). The hot gas mixing line (111) may be connected to the front end of the check valve (110c) in the above-mentioned main line (110), and the defrosting line (113) may be connected to the rear end.

[0211] Meanwhile, according to the present embodiment, it is preferable that the cooling fan (160) that performs heat exchange between the high-temperature, high-pressure refrigerant discharged from the compressor in the condenser (130) and the outside air be provided so as to be able to control the amount of heat exchange. For example, a plurality of cooling fans (160) may be provided, and the heat exchange amount may be controlled so that the greater the number of cooling fans being driven, the greater the heat exchange amount. For example, the cooling fan (160) may be provided so as to be inverter controlled. The amount of heat exchange may be controlled by controlling the RPM of the cooling fan (160) through inverter control.

[0212] When sufficient heat exchange is required through the condenser (130), the cooling fan (160) can be driven at 100%, and when excessive heat exchange is performed through the condenser (130), the cooling fan (160) can be controlled to be driven at, for example, 80% to 80% or less.

[0213] Specifically, the temperature of the refrigerant can be controlled by controlling the amount of heat removal from the condenser through the RPM control of the cooling fan (160). If the temperature inside the chamber remains high, the RPM of the condenser can be reduced to increase the temperature of the refrigerant supplied to the evaporator. This means that the amount of heat removed from the evaporator is reduced. In other words, the amount of heat removed from the evaporator can be controlled by controlling the amount of heat removed from the condenser. Therefore, energy consumption through the evaporator and heat generation outside the equipment can be reduced.

[0214] Hereinafter, the control configuration of a cycling test device according to an embodiment of the present invention will be described in detail with reference to FIG. 4.

[0215] The control unit (300) can control the operation of the refrigerator (100) according to a plurality of operation modes. The operation modes can be provided in a plurality of ways according to the operation temperature range. For example, if the operation temperature range is from 0 degrees to 70 degrees, it can be divided into five operation temperature ranges. The operation mode with the lowest set temperature (lowest mode) can have an operation temperature range between 0 degrees and 20 degrees, and the operation mode with the highest set temperature (highest mode) can have an operation temperature range between 50 degrees and 70 degrees.

[0216] Between the lowest and highest modes, multiple intermediate modes may be provided, with operating temperature bands spaced at 10-degree intervals. Meanwhile, the operating modes may include not only modes based on the operating temperature band, but also a door-open mode (defrost mode) that is performed when the door is opened.

[0217] The control unit (300) controls the compressor to operate continuously and can feedback control the output of the heater (115). Feedback control of the heater (115) can be performed by sensing the temperature inside the chamber or the temperature of the air flowing into the chamber through the temperature sensor (190).

[0218] The control unit (300) can very effectively perform cooling performance control of the evaporator, heat load control by the condenser, evaporator freezing prevention control, and refrigerant temperature control flowing into the compressor through refrigerant balancing control through the main line (110) and bypass lines (111, 112, 114).

[0219] This balancing control can be performed through the control of solenoid valves (110a, 111a, 112a, 114a) and needle valves (110b, 111b, 112b, 114) provided in the main line (110) and bypass lines (111, 112, 114). The solenoid valve is a valve that can be opened and closed automatically, and the needle valve can be said to be a valve that can control the opening rate.

[0220] The opening rate of the needle valves can be set during the initial setting process, and while driving, the on / off of the solenoid valves of the main line and the solenoid valves of each bypass line is repeatedly controlled, thereby performing refrigerant balancing control.

[0221] Meanwhile, in the present embodiments, the solenoid valve is a type of on / off controllable on-off valve, but is not necessarily limited thereto. Furthermore, the needle valve is a valve capable of controlling the flow rate, and various types of valves, such as a constant-temperature valve, a constant-pressure valve, a regulating valve, or a flow-regulating valve, may be provided for controlling the flow rate.

[0222] Additionally, depending on the driving mode, the control unit (300) can perform inverter control of the cooling fan (160). Of course, the circulation fan (170) that generates air circulation can be controlled to be constantly operated during driving.

[0223] Meanwhile, when a controlled expansion valve (140) is provided between the condenser (130) and the evaporator (150), the control unit (300) can control the operation of the expansion valve.

[0224] In this embodiment, the internal temperature range of the chamber can be divided into multiple temperature ranges, and the refrigerant can be balanced and controlled according to the divided temperature ranges. This can be accomplished by varying the amount of refrigerant flowing in the main line (110) and each bypass line (111, 112, 113, 114).

[0225] By varying the opening ratio of the main line (110) and the bypass line in each temperature band, i.e., operating mode, it is possible to perform refrigerant balance control. This opening ratio can be preset based on the output value of the heater (115).

[0226] Below, the driving scenario is described in detail with reference to FIGS. 5 and 6.

[0227] Line 1 refers to the hot gas mixing line, line 2 refers to the cooling line, line 3 refers to the anti-icing line, and line 4 refers to the defrosting line.

[0228] The stage in which the main line is operated can be called the main operation stage, the stage in which the hot gas mixing line is operated can be called the hot gas operation stage, and the stage in which the cooling line is operated can be called the cooling operation stage.

[0229] The operation of a compressor and condenser refers to a state in which it is actively or actively controlled to repeatedly start and stop. In refrigerant-flowing lines, operation also refers to a state in which the flow and stop of refrigerant are actively or actively controlled to repeatedly stop and start. In refrigerant-flowing lines, non-operation refers to the line being kept closed.

[0230] For example, in an operating mode where the operating temperature range is between 0 and 20 degrees Celsius, the hot gas mixing line, cooling line, anti-icing line, and defrost line remain closed and inactive. This means that variables through the hot gas mixing line, cooling line, anti-icing line, and defrost line are excluded from the operating control logic of the corresponding operating mode. In other words, in an operating mode where the operating temperature range is lower than room temperature, only the main operating stage can be performed.

[0231] First, the test device may undergo an initial setup process before operating normally. During the initial setup process, the appropriate refrigerant amount can be adjusted for refrigerant balancing. In other words, the appropriate refrigerant amount for the entire system can be adjusted.

[0232] Additionally, the pressure at the compressor suction end can be adjusted during the initial setup process. That is, by setting an appropriate pressure at the compressor suction end, the refrigerant can be automatically sucked into the compressor at the set pressure even under pressure changes at the compressor suction end during subsequent operation.

[0233] During the initial setup process, the flow control valve, for example, a needle valve, can be adjusted for setting. At this time, the flow control valve's opening rate can be adjusted with reference to the heater's output. In the test device, the heat removal amount of the evaporator can be controlled by adjusting the bypass line according to each temperature range during operation between 20 and 30 degrees Celsius, which has the most operating time. For example, the opening rate of the flow control valve can be set so that the heater output is within 5% under the condition that the temperature inside the chamber is maintained at room temperature. Here, the room temperature may be 25 degrees Celsius.

[0234] In the above initial setting process, the opening ratio of the control valve provided in the hot gas mixing line as well as other bypass lines can also be set.

[0235] Only after completing the initial setup and verifying that it is normal can the test device be operated normally.

[0236] For example, you can drive in sections of 20 to 30 degrees, 30 to 40 degrees, and 40 to 50 degrees. Of course, you can control these sections in more detail.

[0237] Accordingly, as illustrated in FIGS. 5 and 6, the operating modes of the cycling test device can be set to multiple modes, including 0-degree stationary operation. For example, the operating modes can be set to 0-degree stationary operation (T1), 25-degree stationary operation (T2), 35-degree stationary operation (T3), 45-degree stationary operation (T4), and 50-degree or higher operation (T5). In addition, a door-open operation (T6) can be added, assuming that the chamber door is open. Each operating mode can be performed by controlling the on / off of the bypass lines.

[0238] As described above, the opening ratio (refrigerant supply amount) of the main line and bypass lines can be operated normally by initially setting the opening ratio so that the heater output for each temperature zone has a value close to the reference point based on the heater output under the condition of maintaining 0 degrees, and controlling the on / off of each line after the initial setting.

[0239] In T1 mode, the operating temperature range is lower than room temperature. Therefore, normal operation is possible through the compressor and main line, and the condenser fan can operate at 100% capacity. This allows the refrigerator to operate in its initial mode, balancing the refrigerant volume and pressure. At this time, it is preferable not to operate the bypass line, including the hot gas mixing line. In other words, in T1 mode, only the main operation phase is performed, and the hot gas operation phase and the cooling operation phase can be preset to not be performed.

[0240] In T2 mode, the operating temperature range can be considered a room temperature range. Therefore, the operation is performed through the main line and the hot gas mixing line, and the hot refrigerant supplied from the hot gas mixing line can be set by controlling the valve opening rate of the hot gas mixing line so that the heater output converges to within 10%, preferably within 5%, and more preferably to 0% at the stage of maintaining the chamber temperature at 20 degrees. Of course, the setting of the valve opening rate has been set and verified during the initial setting process, and in this operation mode, the operation can be actively controlled by turning the solenoid valve on and off. Ultimately, by actively controlling the operation of the hot gas mixing line so that the heater output is minimized in the most frequently used room temperature operation range, the energy consumed for operation can be significantly reduced. That is, in T2 mode, the main operation stage and the hot gas operation stage can be preset to be performed, and the cooling operation stage can be preset not to be performed.

[0241] In T3 mode, the temperature inside the chamber increases compared to T2 mode. Therefore, in order to control the amount of heat removed from the evaporator accordingly, the temperature of the refrigerant can be increased or the amount of refrigerant supplied can be reduced to reduce the amount of heat removed from the evaporator. Preferably, the bypass line can be controlled to have the same amount of heat removed as in the T2 section. To this end, the opening rate of the hot gas mixing line can be set in the same manner as in the T2 section, and its operation can be controlled by a solenoid valve. In other words, in T3 mode, the main operation stage and the hot gas operation stage can be preset to be performed.

[0242] In addition, in the T3 mode, when the temperature of the refrigerant supplied to the compressor increases due to the increased evaporator heat removal, and thus the temperature of the compressor increases, in addition to the T2 mode, some of the cold refrigerant discharged from the condenser is not supplied to the evaporator, but is supplied to the compressor through a cooling line bypassing the compressor inlet pipe, thereby preventing the temperature of the compressor from rising. In this case, the amount of cold refrigerant supplied to the evaporator is reduced compared to the T2 mode, so that the overall temperature of the refrigerant supplied to the evaporator increases, so that the T3 mode can be controlled with the same heat removal amount as the T2 mode. In other words, by actively controlling the operation of the hot gas mixing line and the cooling line, the energy consumed for operation can be significantly reduced, and liquid compression can be effectively prevented. In addition, in the T3 mode, the fan operation rate of the condenser can be reduced, so that excessive heat exchange can be prevented through the condenser (130). The cooling fan (160) can be controlled to operate at, for example, 80% or less. That is, in T3 mode, the cooling operation step can be preset to be performed, and the RMP of the cooling fan can also be preset to be actively controlled.

[0243] The same control can be applied in T4 mode. Alternatively, the amount of hot gas supplied can be reduced, while the amount supplied to the cooling line can be increased. The amount of heat removed by the evaporator can be maintained at the same level as in T1 mode, while the compressor temperature rise can be suppressed. In other words, in T3 mode, the cooling operation phase can be preset to be performed, while the hot gas operation phase can be preset to not be performed.

[0244] T5 mode can be controlled in the same way as T4 mode, but the operating rate of the condenser cooling fan (160) may be different.

[0245] Therefore, as the operating temperature band increases, it is desirable to control the heat removal amount of the evaporator through the hot gas mixing line first, and then control in the direction of increasing the amount of refrigerant additionally supplied to the cooling line, so that the heat removal amount of the evaporator is maintained the same as the basic section T2 mode, i.e., the room temperature mode. Through this, the temperature increase of the compressor can also be controlled. In other words, multiple operating modes are provided depending on the temperature range of the chamber to be controlled, and depending on the operating mode, whether the hot gas operating step is performed and the amount of refrigerant supplied through the hot gas can be controlled. In addition, depending on the operating mode, whether the cooling operating step is performed and the amount of cold refrigerant supplied to the compressor can be controlled.

[0246] Meanwhile, in the door open mode (T6) where the door is open, the condenser fan, hot gas mixing line, and cooling line can be stopped and the refrigerant can be controlled to flow only through the defrost line.

[0247] According to this embodiment, by controlling the on / off control and opening rate of each of the main line and bypass lines in each mode, optimal cooling performance can be achieved, thereby effectively reducing energy consumption and external heat generation.

[0248] As illustrated in FIG. 6, another embodiment of the driving scenario may be similar to the aforementioned embodiment of the driving scenario. However, the control aspects of both T3 and T4 modes may differ.

[0249] In the T3 mode of this embodiment, operation of the cooling line can be stopped and only the operation of the hot gas mixing line can be controlled. This allows for greater focus on controlling the evaporator temperature through the hot gas mixing line, unlike the previous embodiment.

[0250] In the T4 mode of this embodiment, the operation of the cooling line and the hot gas mixing line can be controlled. This means that evaporator temperature control and compressor inlet refrigerant temperature control can be balanced. In contrast, the previous embodiment focuses more on compressor inlet refrigerant temperature control.

[0251] Here, the opening rate in the main line and bypass lines can be performed through needle valves (110b, 111b, 112b, 114b). After the refrigerant balance is set through each line by the needle valve, operation can be performed by adjusting the on / off value of the solenoid valves (110a, 111a, 112a, 114a) based on the line operation status for each temperature range.

[0252] Meanwhile, mechanical shock may occur in the bypass lines due to pressure changes that occur when conditions change during the operation of the refrigerator (100). Therefore, to reduce mechanical shock, a capillary tube (111c, 112c, 114c) may be provided to perform a buffering function. The capillary tube is preferably installed at the rear end of the needle valve based on the flow direction of the refrigerant. Similarly, the needle valve is preferably located at the rear end of the solenoid valve.

[0253] According to one embodiment of the present invention, a hot gas mixing line bypassed from the main line may be introduced to control the temperature of the evaporator, and an anti-icing line bypassed from the main line may be additionally installed to prevent the compressor from freezing. In addition, an inverter may be installed in the condenser fan to actively control the heat generation of the condenser through fan RPM control to control the heat generation of the condenser. Through this, the temperature of the refrigerant can be controlled, and when the temperature inside the chamber remains high, the fan operation rate of the condenser can be reduced to increase the temperature of the refrigerant supplied to the evaporator, thereby reducing the amount of heat removed from the evaporator. In other words, energy consumption through the evaporator and heat generation outside the chamber can be reduced.

[0254] Additionally, capillary tubes and / or flow control valves can be installed in bypass lines, excluding the main line. Capillary tubes are expected to buffer the mechanical shock caused by pressure changes in closed-loop refrigerant lines when conditions change. For example, fine-tuning a needle valve, such as a flow control valve, allows for refrigerant balancing for each operating section, allowing for specific operating conditions to be set for each operating section.

[0255] Operating conditions for each operating section can be set by setting the aperture ratio of each line. This setting can be performed based on the heater output value within the chamber.

[0256] Specifically, the heater output value can be set by adjusting the opening ratio of each pipe so that the heater output value for each temperature range has a value close to the reference condition under the condition that the temperature inside the chamber is maintained at 0 degrees.

[0257] After refrigerant balancing through the opening ratio of each initially set line, operation can be performed by adjusting the on / off value of the solenoid valve based on the operating status of the lines for each temperature range.

[0258] Figure 7 illustrates the configuration of a refrigerator (100), i.e., a cooling heat exchanger, according to another embodiment of the present invention.

[0259] For convenience of explanation, only the differences from the embodiment illustrated in Fig. 3 will be described in detail.

[0260] As illustrated, according to the present embodiment, the suction end of the compressor (120) may be provided with a compressor suction bypass line (110A). That is, instead of the refrigerant being sucked into the compressor through a single main line, selective refrigerant suction or simultaneous refrigerant suction may be possible through two lines.

[0261] Specifically, a main opening / closing valve (110a) may be provided at the suction end of the compressor (120). The main opening / closing valve (110a) may be provided to open / close the main line, and more specifically, may be provided to open / close the compressor suction end bypass line. That is, when the main opening / closing valve (110a) is opened, the flow of refrigerant through the compressor suction end bypass line is substantially blocked, and when the main opening / closing valve (110a) is closed, the flow of refrigerant through the compressor suction end bypass line is permitted.

[0262] The above compressor suction end bypass line (110A) may be equipped with a control valve, and more specifically, a pressure regulator valve (123). The function and operation of the pressure regulator valve (123) may be the same as in the above-described embodiment.

[0263] Accordingly, the main operating stage in which refrigerant flows through the main line (110) may include a first stage in which refrigerant is supplied to the compressor at a constant pressure and flow rate through a pressure-regulating valve (123), and a second stage in which refrigerant is supplied to the compressor by opening the on-off valve (110a). In addition, the first stage and the second stage may be selectively performed.

[0264] In order to increase the cooling performance in the evaporator (150), operation may be performed by switching from the first stage to the second stage, and conversely, in order to decrease the cooling performance in the evaporator (150), operation may be performed by switching from the second stage to the first stage.

[0265] As described above, a hot gas operation step may be performed to increase the temperature of the refrigerant supplied to the evaporator (150) and thereby reduce the cooling performance of the evaporator. At this time, the on / off valve (111a) of the hot gas mixing line is controlled to control the amount of hot gas flowing into the evaporator. The introduction of this hot gas into the evaporator may cause an increase in the amount and temperature of the refrigerant flowing into the compressor, and therefore, when the hot gas operation step is performed, it is desirable to control the amount and temperature of the refrigerant flowing into the compressor. To this end, when the hot gas operation step is performed, it is desirable that the second step of the main operation step be performed. That is, when the on / off valve (111a) of the hot gas mixing line is on, it is desirable that the main on / off valve (110a) be controlled to be off so that the second step can be performed. In addition, it is preferable that the main opening / closing valve (110a) be controlled to be turned on so that the first step is performed when the opening / closing valve (111a) of the hot gas mixing line is turned off.

[0266] Here, it can be seen that the on / off control of the mixing line's on / off valve (111a) and the main on / off valve (110a) is preferably cross-controlled. That is, the opening of one means the closing of the other, and the closing of one means the opening of the other. Here, considering that the main operating stage is the basic operating stage, it is preferable that the main on / off valve is a NO (normally open) type valve, and the on / off valve of the mixing line is a NC (normally close) type on / off valve.

[0267] A valve that opens when no control signal is applied and closes when a control signal is applied can be called a NO valve. Conversely, a valve that closes when no control signal is applied and opens when a control signal is applied can be called a NC valve.

[0268] By utilizing the cross-control characteristics of the above main on-off valve (110a) and the on-off valve (111a) of the mixing line, both can be controlled through a single control contact of the controller. In other words, since multiple valves can be controlled using a single control contact, an increase in the controller's capacity can be prevented, and easy control logic configuration is enabled.

[0269] Meanwhile, according to the present embodiment, the cooling line (114) may be configured as multiple lines instead of a single line. For example, the first cooling line (114A) may be connected near the output end of the evaporator, and the second cooling line (114B) may be connected near the input end of the compressor. That is, a second cooling line may be further added to more quickly provide the low-temperature refrigerant discharged from the condenser (130) to the compressor. In addition, the second cooling line may be connected to the rear end of the compressor suction end bypass line described above, so that it may not be affected by the pressure regulator valve (123) and the main opening / closing valve (110a).

[0270] Each of the first cooling line (114A) and the second cooling line (114B) may also be provided with an opening / closing valve (114a1, 114a2) and a control valve (114d1, 114d2).

[0271] According to the present embodiment, depending on the chamber's operating mode and the chamber's temperature range, it is possible to control whether a hot gas operation step is performed and the amount of refrigerant supplied via hot gas. Furthermore, according to the present embodiment, depending on the chamber's operating mode and the chamber's temperature range, it is possible to control whether a cooling operation step is performed, in which cold refrigerant is sucked into the compressor without passing from the condenser to the evaporator, and the amount of refrigerant supplied.

[0272] In particular, the cooling operation step may include a first cooling operation step in which on / off control of the first cooling line is performed, and a second cooling operation step in which on / off control of the second cooling line is performed. The second cooling operation step can lower the viscosity of the refrigerant flowing into the compressor more immediately than the first cooling operation step. For example, two or three operation modes in which the cooling operation step can be performed are illustrated in FIGS. 5 and 6. Accordingly, the first cooling operation step may be preset to be performed in an operation mode in which the temperature range is lower, and the second cooling operation step may be preset to be performed in an operation mode in which the temperature range is higher.

[0273] Hereinafter, the control logic according to one embodiment of the present invention will be described in more detail with reference to FIGS. 8 and 9.

[0274] After the initial setup step (S10) is performed prior to normal operation of the cycling test device, normal operation (S20) can be performed. During the initial setup process, an appropriate refrigerant flow rate in the main line can be set, and an appropriate refrigerant flow rate in each bypass line can be set. In addition, an appropriate pressure in the pressure regulator valve (123) can be set. During the initial setup process, it is possible to check whether the refrigerator (10) is operating normally and whether each control component is operating normally.

[0275] After the initial setting is completed, normal operation can be performed. As illustrated in FIGS. 8 and 9, normal operation (S10) can be performed through a preset temperature range-specific operation mode. That is, multiple operation modes are preset, and each operation mode can be set to be distinct from each other for each temperature range. As illustrated in FIGS. 5 and 6, for example, operation modes T1 to T5 can be set according to the temperature range, and additionally, an operation mode (T6) for opening the door can be set.

[0276] Depending on the set operation mode, the main operation step (S30) is basically performed, and the hot gas operation step (S40) and the cooling operation step (S50) can be selectively performed. Depending on the set operation mode, whether or not the hot gas operation step is performed can be preset. When the hot gas operation step is performed, the flow rate of the refrigerant through the hot gas mixing line can also be preset. In addition, depending on the set operation mode, whether or not the cooling operation step is performed can be preset. When the cooling operation step is performed, the flow rate of the refrigerant through the cooling line can also be preset.

[0277] For example, in an operating mode having a temperature range lower than room temperature, only the main operating step (S40) may be set to be performed. In a specific operating mode having a temperature range higher than room temperature, either the hot gas operating step (S40) or the cooling operating step (S50) may be set to be performed, or both may be set to be performed.

[0278] As illustrated in Figure 9, the setting can be changed from one operating mode to another. For example, if the set temperature is 25 degrees and the machine is operating in T2 operating mode, the set temperature can be changed to 0 degrees or 45 degrees. In other words, not only the set temperature but also the operating mode can be changed.

[0279] The operating mode that maintains the current set temperature can be called static operation or constant temperature operation, and can be called static mode or constant temperature mode (S60). That is, since the temperature inside the chamber is kept constant, in the constant temperature mode, as preset in the operation mode, the execution of the main operation stage (S40), hot gas operation stage (S50), and cooling operation stage (S50) and the control of the amount of refrigerant can be performed.

[0280] When the set temperature increases, a temperature-raising mode (S70) may be performed to adjust the chamber temperature to the newly set temperature. That is, in the operating mode for raising the chamber temperature, the amount of cooling heat generated by the evaporator may increase. Therefore, in the temperature-raising mode, a hot gas operation step may be performed to immediately increase the temperature of the refrigerant flowing into the evaporator. Furthermore, as the temperature-raising temperature increases further, a cooling operation step may be performed.

[0281] When the set temperature is lowered, a cooling mode (S80) may be performed to adjust the chamber temperature to the newly set temperature. In the cooling mode (S80), the cooling operation step may be set not to be performed, and if necessary, the hot gas operation step may be set to be performed.

[0282] Operation is performed transiently through the heating mode (S70) or cooling mode (S80) to converge to a new set temperature and stabilize, and only then can operation be performed in the constant temperature mode (S60).

[0283] The cycling test device and control method according to this embodiment can be extended to air conditioning devices or systems and their control methods. In this case, the chamber may be an indoor space, and the refrigerator and piping configurations may be configured to maintain the indoor space at a specific temperature.

[0284] As described in the detailed description of the invention.

Claims

In a cycling test device operated to maintain the temperature inside the chamber at a constant temperature, A main line in which refrigerant circulates by sequentially connecting a compressor, condenser, and evaporator; A heater that heats the air cooled through the above evaporator; A hot gas mixing line bypassed from the main line between the compressor and the condenser and connected to the main line between the condenser and the evaporator, mixing hot gas discharged from the compressor with low-temperature, low-pressure gas supplied from the condenser to the evaporator; and A cycling test device characterized by including a pressure-regulating valve that maintains the pressure of the refrigerant sucked into the compressor at a constant pressure at an initially set pressure regardless of changes in the flow rate of the hot gas supplied to the evaporator through the hot gas mixing line. In the first paragraph, A cycling test device characterized in that the cooling performance in the evaporator is controlled to be lowered and the heat dissipation performance in the condenser is controlled to be lowered by the temperature increase of the refrigerant through the hot gas mixing line. In the first paragraph, A cycling test device characterized in that the output of the heater is limited to within 10%, preferably within 0% to 5%, under the condition that the temperature inside the chamber is maintained at room temperature. In the third paragraph, A cycling test device characterized in that it includes a controller that controls the amount of refrigerant flowing into the evaporator by repeatedly controlling the on / off of a solenoid valve provided in the hot gas mixing line when the output of the heater is detected to be greater than the limited output, thereby controlling the output of the heater to be within the limited output. In the first paragraph, The above pressure regulator valve is provided on the main line, The initial pressure of the above pressure regulator valve is set to the pressure of the refrigerant sucked into the compressor under the condition that the refrigerant flows only through the main pipe. A cycling test device characterized in that the pressure on the upstream side of the pressure regulator valve varies depending on the presence or absence of refrigerant flow through the hot gas mixing line or the change in the amount of heat exchange in the evaporator and condenser. In paragraph 5, A cycling test device characterized in that the pressure and flow rate of the refrigerant sucked into the compressor are maintained constant by the pressure regulator valve even under conditions where the pressure of the refrigerant sucked into the compressor increases. In the first paragraph, It includes a hot gas opening / closing valve provided in the hot gas mixing line and a main line opening / closing valve provided in the suction end of the compressor. A cycling test device characterized in that the operations of the main line opening / closing valve and the hot gas opening / closing valve are controlled to be crossed. In paragraph 7, A cycling test device characterized by including a compressor suction bypass line that supplies refrigerant to the compressor without passing through the main line opening / closing valve. In paragraph 8, A cycling test device characterized in that the above-mentioned pressure valve is provided in the above-mentioned suction bypass line. In paragraph 9, A cycling test device comprising a control unit that controls the operation of the cycling test device, wherein the main line opening / closing valve is a NOT (normal open type) valve and the hot gas opening / closing valve is a NCT (normal close type) valve so that signals are connected to the control unit through the same point. In a control method of a cycling test device operated to control the temperature within a chamber, The main operation stage is to operate the main line in which the compressor, condenser and evaporator are sequentially connected to allow the refrigerant to circulate; and A hot gas operation step for operating a hot gas mixing line, which is connected to the main line between the condenser and the evaporator by bypassing the main line between the compressor and the condenser, and is provided to mix hot gas discharged from the compressor with low-temperature, low-pressure gas discharged from the condenser and supply the mixture to the evaporator, A control method for a cycling test device characterized in that it controls whether the hot gas operation step is performed and the amount of refrigerant supplied through the hot gas according to the operating mode of the chamber, the temperature range of the chamber, or the operating mode and temperature range of the chamber. In Article 11, A control method for a cycling test device, characterized in that the above operating mode includes a constant temperature mode for maintaining the temperature inside the chamber at a set temperature and a conversion mode for raising or lowering the temperature inside the chamber. In paragraph 12, A control method for a cycling test device, characterized in that the hot gas operation step is performed in the above-described constant temperature mode and the conversion mode for lowering the temperature within the chamber. In the first paragraph, A control method for a cycling test device, characterized in that a plurality of operating modes are provided according to the temperature range of the chamber, and an operating mode in which the hot gas operating step can be performed among the plurality of operating modes is preset. In Article 11, A control method for a cycling test device, characterized in that the above main operation step includes a first step of supplying refrigerant to the compressor at a constant pressure and flow rate through a pressure-regulating valve that constantly controls the pressure and flow rate of the refrigerant supplied to the suction end of the compressor. In Article 15, A control method for a cycling test device, characterized in that the main driving step includes a second step of supplying refrigerant to the compressor by opening an on-off valve provided in parallel with the pressure regulator valve at the suction end of the compressor. In Article 16, A control method for a cycling test device characterized in that the first stage is switched to the second stage to increase cooling performance in the evaporator, and the second stage is switched to the first stage to decrease cooling performance in the evaporator. In Article 11, The above hot gas operation step is performed by opening the hot gas opening / closing valve provided in the hot gas mixing line. A control method for a cycling test device, comprising a main opening / closing valve provided at the suction end of the compressor, characterized in that the operation of the main opening / closing valve and the hot gas opening / closing valve are controlled to be cross-operated. In Article 11, It includes a compressor suction bypass line that supplies refrigerant to the compressor without passing through the main opening / closing valve. A control method for a cycling test device, characterized in that the compressor suction bypass line is provided with a pressure regulator valve that controls the pressure and flow rate of refrigerant supplied to the suction end of the compressor. In any one of Articles 11 to 13, A control method for a cycling test device, comprising a control unit that controls the operation of the cycling test device, wherein the on-off valve of the main line is a NOT (normal open type) valve, and the on-off valve of the hot gas mixing line is a NCT (normal close type) valve, and the on-off valve of the main line and the on-off valve of the hot gas mixing line are connected to the control unit through the same contact point so that they operate alternately.

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